WO2015125596A1 - Discharge mechanism for displacement compressor - Google Patents

Discharge mechanism for displacement compressor Download PDF

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Publication number
WO2015125596A1
WO2015125596A1 PCT/JP2015/052878 JP2015052878W WO2015125596A1 WO 2015125596 A1 WO2015125596 A1 WO 2015125596A1 JP 2015052878 W JP2015052878 W JP 2015052878W WO 2015125596 A1 WO2015125596 A1 WO 2015125596A1
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WO
WIPO (PCT)
Prior art keywords
valve
chamber
flat
plate
wall surface
Prior art date
Application number
PCT/JP2015/052878
Other languages
French (fr)
Japanese (ja)
Inventor
哲哉 荒田
Original Assignee
哲哉 荒田
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2014032791A external-priority patent/JP2014129815A/en
Priority claimed from JP2014082416A external-priority patent/JP2014132176A/en
Priority claimed from JP2014138475A external-priority patent/JP2014206173A/en
Application filed by 哲哉 荒田 filed Critical 哲哉 荒田
Priority to JP2016504017A priority Critical patent/JP6582164B2/en
Publication of WO2015125596A1 publication Critical patent/WO2015125596A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/005—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of dissimilar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/102—Geometry of the inlet or outlet of the outlet

Definitions

  • the present invention is applied to a positive displacement compressor such as a rotary piston type or a swing type including a rolling piston type and a scroll type in which a compression chamber is formed by a vertical side wall surface of a circular arc curve used in a refrigeration and air conditioning apparatus or the like.
  • the present invention relates to a positive displacement compressor including a discharge mechanism for compressing and flowing out working gas in a compression chamber.
  • Refrigeration and air conditioning equipment products are widely used as air conditioners and refrigeration / refrigerator equipment. Most of them use the displacement compressor to cool the living space, heat, or refrigerate / freeze the food using the change in the state of the refrigerant by compressing the refrigerant from low pressure to high pressure. Most of the power consumed by these devices is consumed by the installed compressor.
  • the main factors for reducing the efficiency of the positive displacement compressor are leakage of working gas from the discharge chamber to the compression chamber or from the compression chamber to the suction chamber, which is a low pressure space, the magnitude of the discharge passage resistance, and the working gas from the discharge chamber.
  • Over-compression phenomenon in which the pressure in the compression chamber rises above the discharge pressure before flowing out, and discharge before the rise to the recompression loss or discharge pressure due to the reverse flow of high-pressure gas from the dead space before the discharge valve to the compression chamber For example, there is insufficient compression loss in which the chamber communicates and the discharge gas flows backward to the compression chamber.
  • the discharge mechanism applied to many positive displacement rotary compressors used in conventional refrigeration and air conditioning equipment is equipped with a thin plate-like reed valve that opens and closes due to the pressure difference between the front and rear at the outlet of the discharge hole provided in the cylinder. (For example, refer patent document 3 and patent document 4.).
  • a protrusion provided at the tip of a blade that partitions the low pressure chamber and the compression chamber is inserted into a discharge hole provided in the cylinder during the discharge stroke of the working gas. In some cases, the volume of the dead space is reduced (see, for example, Patent Document 3).
  • the suction at the time of start-up is applied to a hook engaging portion provided on an end surface sliding on the front head wall surface of a plate-like blade for partitioning between the suction chamber and the compression chamber of a conventional positive displacement rotary compressor equipped with a cylindrical roller.
  • the hook attached to the front head protrudes into the hook locking portion to stop the movement of the blade, and the suction chamber and the compression chamber are opened.
  • a configuration in which the hook is detached from the hook engaging portion when the pressure difference with the continuation of operation exceeds a certain value without being compressed, and the blade hits the roller and partitions and compresses the suction chamber and the compression chamber (For example, refer to Patent Document 5).
  • two blades are provided adjacent to each other to separate the suction chamber and the compression chamber of the positive displacement rotary compressor, and the pressure in the blade rear side space that presses the two blades toward the piston is applied to the two blades. It was configured to be an intermediate pressure between the low-pressure chamber and the compression chamber partitioned by ( For example, see Patent Document 4. ).
  • a part of the wrap winding start center part of the orbiting piston applied to the positive displacement scroll compressor is separated so as to be able to move independently of the orbiting piston main body and to be in sliding contact with the inner wall of the fixed cylinder for a certain section. (For example, refer to Patent Document 6).
  • a part of the central part of the wrap winding forming a compression chamber formed in a spiral shape is separated, and it is constituted by a valve presser, a fixing, a rotating pin, and a supporting spring.
  • a wrap valve see, for example, Patent Document 7).
  • the orbiting piston is provided in the cylindrical space provided in the center of the spiral wall of the fixed cylinder in the wrap at the center of the fixed cylinder.
  • the cylindrical discharge valve is rotated in conjunction with the movement of the cylinder and the compression chamber space and the discharge chamber are opened and closed (see, for example, Patent Document 8).
  • An annular ring is mounted in the inner pocket (ring-shaped groove) to form a compression chamber inside and outside the ring, and the Oldham ring is swung to the compression piston and suction side while pressing the inner and outer blades against the annular piston.
  • the space (inflow chamber) is adjacent to the blade plate (blade), and refrigerant (working gas) is discharged from a discharge port provided in the cylinder through a discharge valve (reed valve).
  • the discharge port becomes a dead space and recompression loss occurs, the working gas leaks into the suction chamber from the tip of the blade plate and the gap between the upper and lower end surfaces that partition the compression chamber and the previous inflow chamber, and the blade tip seal Since the portion is in the shape of a ring, there is a problem that the sealing performance is lowered because the line contact seal becomes narrower.
  • the thin plate-like reed valve used in the discharge mechanism requires an elastic function in addition to the sealing property, the plate thickness cannot be increased, and the strength is low and there is a problem in reliability.
  • the former invalid space is used for the former
  • the second invalid space is used for the latter because it is not used for the flow of working gas between the discharge port and the blade plate and between the suction port and the blade plate, which are necessary for processing.
  • the gas in the first invalid space remains without being discharged, so that the volume of foreign matter enters into the sliding surface of the blades and becomes damaged, or the volume rapidly expands in the second invalid space. As a result, cavitation due to vacuum occurred and the sliding surface of the blades was damaged.
  • the thin reed valve used in the discharge mechanism requires an elastic function in addition to the sealing property, and the plate thickness cannot be increased and the strength is low. There was a problem that the reed valve was damaged due to time and self-excited vibration, and the noise increased.
  • a hook is hooked on a hook engaging portion of a plate-like blade that partitions the suction chamber and the compression chamber, and the movement of the blade is locked at the time of start-up or capacity control so that the suction chamber communicates with the compression chamber.
  • the compression chamber when the compression chamber is started in a state where it is filled with liquid, the liquid only rotates in the compression chamber, but it is compressed at the moment when the hook that holds the blade is released and the blade partitions the suction chamber and the compression chamber. There was a problem that the compressor was damaged due to abnormally high pressure caused by liquid compression in the room.
  • one of the upper and lower end surfaces of the lap valve slides on the bottom surface of the installed scroll member, and the other surface slides on the other scroll member. There was a problem that the torsional moment was applied and the top and bottom surfaces were damaged.
  • the valve port basically opens and closes according to the rotation angle of the valve body. Since it is not a mechanism that operates with the differential pressure before and after the valve, it is not possible to follow the pressure change in products that change the relationship between the suction pressure and the discharge pressure, which is common for refrigeration and air conditioning equipment. There has been a problem in that compression failure such as shortage occurs and efficiency is lowered.
  • the present invention eliminates or greatly reduces the leakage of working gas, over-compression phenomenon, re-compression loss, under-compression loss, etc. in the compression mechanism that is a factor that reduces the efficiency of the compressor by the conventional discharge mechanism. It aims at providing the compressor provided with the discharge mechanism which aimed at high efficiency, and improved the intensity
  • the positive displacement compressor provided with the discharge mechanism which has the capacity
  • a movable mechanism member having an arcuate vertical wall surface at an eccentric shaft portion of a drive shaft that is supported by a fixed component member having an arcuate vertical wall surface fixed to an airtight container or the like. Is attached to one end of a compression chamber formed by sandwiching a flat end plate having a flat surface above and below a crescent-shaped columnar space formed by an arcuate vertical surface by rotational movement or swiveling movement of the movable mechanism member.
  • a discharge mechanism for reducing the compression chamber space and compressing and discharging the working gas is provided.
  • a valve mounting chamber having an approximately rectangular cross section of the same height and parallel to the vertical wall surface forming the compression chamber of the fixed component and opening to the vertical wall surface of the compression chamber;
  • a plate-shaped valve body with a rectangular cross section having a shape that allows the tip portion to be in close contact with the vertical wall surface of the movable mechanism member forming the compression chamber as a valve seat in a valve storage chamber configured by providing a back chamber on the opposite side
  • the upper and lower end surfaces and the flat end plate are in sliding contact with each other through a minute gap, and the vertical wall surface on the compression chamber side of the valve storage chamber and the wall surface of the plate valve body are also in sliding contact with each other.
  • a valve mechanism comprising an auxiliary member including a member, a sealing member around the plate-shaped valve body, and an elastic body such as a spring mounted on one end of the plate-shaped valve body is mounted in the valve storage chamber. It is a positive displacement compressor provided with the constituted discharge mechanism.
  • the valve mechanism composed of the plate-like valve body and the auxiliary machine member is housed in the valve housing chamber provided in the fixed component member, and the tip of the plate-like valve body is placed on the circle of the movable mechanism member.
  • a discharge mechanism configured to be in sliding contact with the arcuate vertical wall surface can be disposed adjacent to the compression chamber.
  • the side wall surface of the valve mounting chamber adjacent to the compression chamber or the side wall surface of the plate-like valve body in surface contact with the side wall surface is recessed by one step from the side wall surface.
  • a discharge mechanism in which a pressure pocket which is a space where a boundary line does not communicate with the back chamber is formed, and a passage communicating the compression chamber and the pressure pocket is provided on a side wall surface of the plate-like valve body or the valve storage chamber.
  • the sliding area between the plate-like valve body and the side wall surface of the valve mounting chamber is reduced, and the compression chamber pressure is introduced into the pressure pocket to separate the side wall surfaces.
  • the operability of the plate-like valve body is improved.
  • one end is opened in an oil tank provided in a lower part of an oil reservoir or a sealed container for storing oil separated from discharge gas provided in the fixed component, and the other end is a valve of the flat end plate.
  • An oil filling hole that opens into the mounting chamber, an oil receiving hole provided in the upper end surface of the plate-like valve body, an introduction groove, and a hole and groove in the tip oil groove at the tip are intermittently communicated with the oil reservoir or the seal.
  • the positive displacement compressor according to claim 1 further comprising a discharge mechanism configured to guide oil in the container to a tip oil groove of the plate-like valve body.
  • the lubricating oil in the hermetic container is supplied by the differential pressure from the oil groove at the front end to the valve seat of the movable mechanism member in which the front end of the plate-like valve body is in sliding contact with the intermittently. It can be used to seal minute gaps and lubricate sliding parts.
  • a discharge mechanism in which the linear expansion coefficient of the material forming the fixed component member or the valve mounting chamber of the valve storage chamber and the material used for the plate-like valve body is approximately the same.
  • the positive displacement compressor according to any one of claims 1 to 3.
  • a minute gap is secured between the periphery of the plate-shaped valve body and the upper and lower end surfaces and side walls of the valve mounting chamber in consideration of leakage of the working fluid and slidability. Even if a large temperature fluctuation occurs inside the compressor, the gap does not change because the linear expansion coefficient of the member related to the gap is the same.
  • a turning motion in which the amount of eccentricity of the eccentric shaft is a revolution radius by a turning mechanism that prevents rotation and makes a revolving motion provided between the fixed component member and the movable mechanism member.
  • the valve seat is formed on a swing piston as a movable mechanism member with a vertical wall surface parallel to the axis of the drive shaft, and has a wall surface serving as an envelope of the wall parallel to the axis of the drive shaft forming the compression chamber of the swing piston.
  • the revolving motion of the revolving piston without rotation can be achieved by using the revolving mechanism, so that the speed of the movable mechanism member can be reduced and the wall surface of the compression chamber of the fixed cylinder is formed by the envelope groove. be able to.
  • a flat valve seat having a flat surface with a straight line having a length more than twice the turning radius is extended as a straight protrusion at one end of an arc protrusion formed by bending a belt-like plate having a rectangular cross section into a cylindrical shape.
  • a swiveling piston is formed by allowing the swiveling protrusions in contact with each other to stand upright on one side of a swirling disk of a circular plate.
  • a fixed cylinder is formed by providing two valve mounting chambers that are arranged opposite to each other.
  • a discharge mechanism which is mounted in the valve mounting chambers of the two valve storage chambers facing each other across the flat valve seat which is the linear protrusion, and is configured such that the tip of the plate-like valve body abuts on the linear protrusion.
  • the plate-like valve body which is also one of the features of the present invention used in the specific configuration of the fixed cylinder and the swing piston as an example of the fixed component member and the movable mechanism member and the discharge mechanism thereof A specific configuration of the tip is shown.
  • a turning piston is formed by bending the circular protrusion into a circular shape having one round or less to form a cylindrical shape, and the turning protrusion provided with the linear protrusion on the end is brought upright on a turning disk. Then, the linear protrusions of the fixed cylinder provided with suction holes and discharge holes in the inflow chamber provided at one end where the envelope groove is recessed in the thick end plate and the outflow chamber which is a linear parallel groove as the other end are provided.
  • the valve storage chamber arranged symmetrically across the valve is provided with a discharge mechanism configured by loosely inserting the swiveling protrusion into the envelope groove after mounting a valve mechanism composed of a plate-shaped valve body and an auxiliary member.
  • the side wall surface of the compression chamber for compressing the working gas is formed by the swiveling protrusion, its envelope groove, and the side wall surface of the plate-like valve body, and the straight protrusion of the swiveling piston is placed in the outflow chamber of the fixed cylinder.
  • the tip of the plate-like valve element for the inner and outer compression chambers housed in the two valve mounting chambers of the valve storage chamber can be slidably contacted with the straight protrusion side wall surface and the back chamber.
  • a functional discharge mechanism is configured by housing auxiliary members such as springs.
  • the invention according to claim 8 is a length more than twice the turning radius corresponding to the eccentric amount of the eccentric shaft in a tangential direction from the inner terminal portion of the spiral protrusion formed by bending a belt-shaped plate having a rectangular cross section.
  • a swiveling projection which is formed by extending a straight protrusion extending integrally with the spiral protrusion, is erected on a swiveling disk to form a swiveling piston.
  • a suction hole and a discharge hole are provided in each of the outer end portion of the envelope groove recessed in the thick end plate formed by the swiveling motion of the swirling protrusion and the linear groove at the inner end portion as the outflow chamber,
  • a compression cylinder is formed by meshing a fixed cylinder having valve storage chambers symmetrically on both sides of the outflow chamber and the respective swiveling projections and the envelope groove, and then the plate-like valve body and the auxiliary in each valve storage chamber 7.
  • valve formed by the valve mounting chamber and the back chamber in which the compression chamber is formed by the swiveling piston in which the swirling protrusion is formed in a spiral shape and the fixed cylinder formed by the envelope groove of the swirling protrusion.
  • a functional discharge mechanism is constituted by a plate-like valve body whose tip is shaped so that the compression chamber pressure acts on the storage chamber and a valve mechanism body constituted by an auxiliary member such as a spring on the back side thereof.
  • an involute curve or an arc curve having a smaller curvature connected on the same tangent line is formed on the inner side of the outer spiral protrusion obtained by applying the involute curve on the inflow chamber side to the spiral protrusion of the swirl protrusion.
  • the inner spiral protrusion is connected by the linear protrusion extending in the tangential direction, thereby providing a discharge piston configured by two types of curves, a swing piston that forms a swing protrusion with one straight line, the fixed cylinder, and a valve mechanism body.
  • the space in the center of the fixed cylinder including the outflow chamber of the linear groove can be used effectively, so that a sufficient size is secured.
  • a discharge mechanism that can sufficiently function can be configured.
  • a valve mounting chamber formed on a side wall surface of the outflow chamber provided at a terminal end of the envelope groove and having a rectangular cross-sectional space with a parallel wall surface at the same height as the envelope groove.
  • a fixed cylinder is provided with a valve storage chamber formed from a back chamber provided in the back and a pressure introducing hole for communicating the back chamber with the inside of the discharge space.
  • An approximately rectangular plate-like valve body is accommodated in the valve mounting chamber side wall surface of the fixed cylinder in the valve mounting chamber, and an elastic body such as a spring and the like are supported between the plate valve body in the rear chamber and the fixed cylinder.
  • a discharge mechanism constructed by mounting the plate-like valve body in a slidable manner along the side wall surface of the valve mounting chamber by storing it in the valve storage chamber as a valve mechanism body composed of an auxiliary member which is a member.
  • the plate-shaped valve body can be formed as a rectangular parallelepiped, the configuration of the discharge mechanism can be simplified, and the sealing performance and operability around the plate-shaped valve body are improved.
  • the invention according to claim 11 is provided with a low pressure introduction hole that communicates with a low pressure passage provided at one end of a flat surface of a cylindrical space formed in a fixing member that closes the upper and lower surfaces of the rectangular groove of the valve mounting chamber and the other end side.
  • a locking control chamber formed from a communication hole communicating with the valve mounting chamber is provided.
  • An elastic body such as a spring is attached to the inner cavity of the locking member formed of a two-stage cylinder having a large-diameter cylindrical portion and a small-diameter pin portion, and is stored in the locking control chamber.
  • the pin portion of the locking member is allowed to play at any one of the upper and lower end surfaces or the side wall seal surface that slides on the fixed member surface in a state where the front end portion of the body is stored in the valve storage chamber inside the compression chamber.
  • a discharge mechanism including a plate-like valve body provided with a locking hole at an insertable position.
  • the pin portion of the locking member when the spring force attached to the cavity is larger than the load due to the control differential pressure acting before and after the locking member, for example, when the compressor is stopped, the pin portion of the locking member Is inserted into the locking hole of the plate-like valve body, the plate-like valve body is locked and does not move. In this state, a large gap twice as large as the maximum turning radius is maintained between the tip of the plate-like valve body and the linear protrusion of the turning piston, which is a flat seat.
  • the control differential pressure becomes larger than the spring force, the pin portion of the locking member is detached from the locking hole of the plate-like valve body, and the plate-like valve body becomes operable.
  • the invention according to a twelfth aspect is configured by accommodating a plate-shaped valve body having a laminated structure formed by being divided into a plurality of pieces so as to be parallel to the bottom surface of the valve mounting chamber and approximately in the same plane, in the valve mounting chamber. 12.
  • the plate-like valve element is divided into a plurality of parts along the height direction of the vertical wall surface of the flat valve seat, which is the linear protrusion of the orbiting piston, so that the linear protrusion is
  • the plate-like valve body is deformed due to the difference or temperature, the sliding contact of the entire tip is maintained because the plate-like valve body follows the deformation.
  • the plate-like valve body is slid onto the flat valve seat at a constant width equal to or less than 1 ⁇ 2 of the valve plate thickness on the outflow chamber side of the tip formed by a rectangular parallelepiped flat gate valve.
  • a flat gate surface that is in contact with the flat valve seat that has a pressure receiving surface at the tip by providing an inclined surface or step that is recessed from the flat seal surface with a gap to the flat valve seat is provided on the compression chamber side.
  • a minute gap is provided between the front and rear side wall surfaces of the flat gate valve and the four surfaces of the upper and lower end surfaces, and reciprocating sliding is possible on the side wall surface of the valve mounting chamber.
  • the positive displacement compressor according to any one of claims 10 to 12, further comprising a discharge mechanism that is mounted on the compressor.
  • the flat valve seat on which the flat seal surface of the flat gate gate valve is seated is also flat, it comes into sliding contact with the surface seal secured.
  • the compression chamber pressure is on the back side of the pressure receiving surface provided with a gap between the flat gate seat on the compression chamber side of the flat gate gate tip. It is configured to act toward the chamber.
  • the flat gate valve opens from the flat sealing surface toward the compression chamber side at the central portion with a width equal to or less than 1 ⁇ 2 of the side wall surface height at the central portion of the flat gate valve tip.
  • the wind pressure receiving portion that is partially opened at the inclined surface on the compression chamber side.
  • the width of the parallel groove of the valve mounting chamber is formed larger than the thickness of the flat gate valve, and a substantially rectangular parallelepiped valve auxiliary material corresponding to the difference is provided in the valve.
  • the mounting gate is juxtaposed with the flat gate valve, and an opening is provided on the distal end side of the valve auxiliary member to communicate the compression chamber side and the outflow chamber side. The distal end is slidably contacted with the flat valve seat of the revolving piston linear protrusion.
  • the positive displacement compressor according to claim 13 further comprising a discharge mechanism configured such that the flat gate valve and the valve auxiliary member operate independently of each other.
  • the stability of the valve operation is improved and the operability of the valve is improved. Additional functions can also be provided in the valve aid.
  • a region for adjusting the width of the valve mounting chamber is widened, and the same width as the envelope groove can be obtained.
  • a detent portion in which a fixed width in the height direction of the rear chamber side end surface of the flat gate valve is provided in the valve mounting chamber so as to protrude toward the outflow chamber side like a ridge.
  • a rolling element such as a rolling bearing having a diameter that is larger than the thickness of the valve auxiliary member and slightly smaller than a value obtained by subtracting the thickness of the flat gate valve from the width of the valve mounting chamber is provided with the valve mounting chamber and the valve mounting chamber.
  • the positive displacement compressor according to claim 15 further comprising a discharge mechanism configured such that one or more valve auxiliary members are mounted so as to be able to roll between side wall surfaces of the flat gate valve. It is.
  • the rolling elements attached to the valve auxiliary member are connected to the flat gate valve and the valve. It will be sandwiched between the side walls of the mounting chamber.
  • the flat valve seat which is a linear protrusion of the swivel piston, moves to the back chamber side, the speed doubled to the moving speed is added from the rolling element to the flat gate valve, and the flat gate valve is It will be pushed up to the back room side.
  • the relationship between the linear protrusion and the flat seal surface of the flat-plate gate valve tip portion that is in surface contact with the linear protrusion of the orbiting piston is maintained, and the linear protrusion and the outflow chamber side of the envelope groove are maintained.
  • the mounting angle of the side wall surface on the envelope groove side of the valve mounting chamber with respect to the parallel groove at the end portion is inclined by about several degrees from the vertical surface, and the relative angle between the flat plate gate valve tip and the side wall surface is similarly adjusted.
  • the flat plate gate as a force for opening the front end portion by pushing the front end portion of the flat gate valve away from the linear protrusion and pushing it toward the back chamber.
  • the force due to the differential pressure acting on the side wall support surface can be used. If the angle formed with the flat plate gate valve side wall support surface with respect to the straight protrusion is made smaller than a right angle by tilting the back surface portion toward the outflow chamber, the pushing force at the tip portion decreases, but the component force that becomes the pushing force of the load on the side wall surface Occurs and increases according to the tilt angle. Conversely, when the angle formed with the side wall support surface is increased, the force relationship is reversed. Therefore, the tilt method may be selected according to the situation.
  • the front end portion of the flat gate valve can be slidably contacted with the linear protrusion, and is provided in a concave groove that is dug down from approximately the center portion toward the front end portion on the side of the flat plate gate valve side wall.
  • a discharge mechanism comprising a reed valve and a retainer for supporting deformation at the back of the reed valve so as to close the discharge hole communicating with the compression chamber side. It is a compressor.
  • the compressed gas can flow out easily by operating with the differential pressure across the valve.
  • a reed valve used conventionally since it is mounted on a flat gate valve, which is a small member, compared to the case where it is mounted on a conventional fixed cylinder, the workability is improved as the degree of freedom of material selection increases.
  • the invention according to claim 19 is characterized in that the valve mounting chamber formed of a parallel groove having the same width and height as the envelope groove of the fixed cylinder has both ends on the opposite side of the envelope groove and the same width as the envelope groove.
  • the groove width of the valve mounting chamber is larger than the thickness of the flat gate valve, a rectangular parallelepiped side spacer corresponding to the difference is not projected into the envelope groove.
  • valve mounting chamber and the back chamber that form the valve storage chamber in the outflow chamber formed at one end thereof using the same cutter as the envelope groove formed in the fixed cylinder.
  • the invention according to claim 20 is a substantially rectangular parallelepiped having the same height as the flat gate valve provided with a side wall seal surface on the outflow chamber side of the valve mounting chamber and provided with a tip end portion that is in sliding contact with the swiveling protrusion.
  • a discharge mechanism comprising: a valve mechanism configured by assembling an elastic body such as a spring, if necessary, between a fixed cylinder in the back chamber; and The positive displacement compressor according to any one of 19.
  • the flat gate valve and the shape of the valve auxiliary material are mounted in the valve mounting chamber as a set, so that the flat gate valve protrudes greatly in the envelope groove on the back side thereof. Since the valve auxiliary material supports it, the operation stability can be improved and an additional function for improving the operability of the valve can be provided in the valve auxiliary material. In addition, a region for adjusting the width of the valve mounting chamber can be expanded to be the same as the envelope groove.
  • the invention according to claim 21 is characterized in that a part of the side wall surface on the side of the flat plate gate valve is recessed to widen the outflow passage and is combined with a partition plate provided with a detour, from the flat plate gate valve side wall support surface to the side of the partition plate.
  • a rectangular flat valve stabilization plate extending vertically toward the side is integrally fixed on the side wall support surface of the flat gate valve, and one end is opened between the valve stabilization plate and the tip, and the other end is in the valve mounting chamber. 21.
  • a discharge mechanism is configured by mounting a flat gate valve provided with a communication hole opened in a side wall seal surface in sliding contact.
  • the compression gate pressure flows into the lower part of the valve stabilizing plate from the communication hole and, together with the pressure flowing into the tip, pushes up the flat gate valve toward the back chamber.
  • the fluid pressure acts on the valve stabilizing plate and further presses it toward the back chamber side, and the flat gate valve
  • the open state is stably maintained.
  • the invention according to claim 22 is based on a value obtained by subtracting the thickness of the flat gate valve from the width of the valve mounting chamber, which is larger than the thickness of the partition plate juxtaposed with the flat gate valve in the valve mounting chamber.
  • One or more rolling elements such as rolling bearings having a slightly smaller diameter are mounted on the partition plate in a state where the rolling elements can roll between the valve mounting chamber and the side wall surface of the flat gate valve. 21.
  • the rolling elements attached to the partition plate are connected to the flat gate valve and the valve. It will be sandwiched between the side walls of the mounting chamber.
  • the flat valve seat which is a linear protrusion of the swivel piston, moves to the back chamber side, the speed doubled to the moving speed is added from the rolling element to the flat gate valve, and the flat gate valve is It will push up to the back room side instantly.
  • the invention according to claim 23 is a partial ring having a vertical wall surface on the same bottom surface as the end portion of the fixed cylinder envelope groove and having the same height as the envelope groove, and both ends open to the outflow chamber.
  • Both ends of the ring groove having a uniform groove width whose diameter of the inner wall of the cylinder, which is the outer diameter of the groove, is approximately twice the envelope groove width and whose center is approximately coincident with the groove width center of the outflow chamber are open to the outflow chamber.
  • Two spaces from the end face of the intermediate member mounted at the center of the space to be the valve storage chamber to the opening of the outflow chamber are configured as the valve mounting chamber.
  • An arc gate valve as a plate-like valve element formed by an arc having a range of about 1/4 to less than half of the circle is rotatably inserted into the valve mounting chamber so as to face the linear protrusion, and the arc gate 13.
  • a discharge mechanism configured by mounting an elastic member such as a spring in two back chambers, which are spaces between the valve and the intermediate member, is provided. This is a positive displacement compressor.
  • part of the force accompanying the differential pressure of the working gas acting on the tip and side wall seal surfaces of the arc gate valve before the compression chamber pressure rises and enters the discharge stroke is Because of the arc shape of the cylinder, it acts as a component force that opens the arc gate valve, so that the operability is improved and the overcompression power is reduced.
  • the discharge mechanism including the outflow chambers of the inner and outer compression chambers is provided as one cylinder. It can be integrated into space saving and processing within a narrow range by storing in a space.
  • a communication hole is provided between a passage in a discharge space where dynamic pressure is generated due to a gas flow or a compression chamber near the discharge mechanism and the back chamber provided in two places.
  • the arc gate valve can be opened with a compression chamber pressure comparable to the outflow chamber pressure.
  • the invention according to claim 25 is an arc gate valve having a laminated structure in which arc gate valves divided into a plurality of pieces so as to overlap each other on the arc side wall surface of the valve mounting chamber are slidably mounted independently.
  • 25. The positive displacement compressor according to claim 23, wherein the discharge mechanism is configured.
  • the flat valve seat of the linear protrusion and the seal portion at the tip of the multiple arc gate valve become a plurality, and the sealing performance between the compression chamber and the outflow chamber is improved and the dead space at the tip of the compression chamber is increased.
  • the opening and closing operability of the multiple arc gate valve is improved by reducing the outer peripheral side of the force of an elastic body such as a spring provided on the back surface of the multiple arc gate valve and setting the inner peripheral side larger.
  • the U-shaped tower portion integrally formed by the inner side wall surface of the valve mounting chamber of the ring groove and the side wall surface of the outflow chamber is separated as a U-shaped grooved cylinder and the U
  • the end face of the grooved cylinder is attached to the bottom surface of the cylindrical chamber with a plurality of pins or bolts, and an intermediate member is mounted between the inner wall of the cylinder and the outer wall of the U-shaped grooved cylinder, and the valve storage chamber is composed of a valve mounting chamber and a back chamber.
  • the U-shaped tower constituting the valve mounting chamber wall of the valve storage chamber is separated and separated from the fixed cylinder into a separate U-grooved cylinder so that the envelope groove width is approximately twice or more. Since the inside of the cylindrical inner wall having a diameter of 5 mm can be formed in the cylindrical chamber, the inner wall of the cylinder can be processed using the end mill used for processing the envelope groove as it is.
  • the distal end portion of a substantially cuboid valve seat mounted on the swivel disk in the valve mounting chamber provided on the outflow chamber side of the fixed cylinder envelope groove is connected to the swivel piston.
  • a flap valve which is a plate-like valve body, is rotatably mounted in a pin hole provided in the center of the arcuate end surface on the back chamber side on a rotating pin that is slidably contacted with a linear protrusion and fixed upright on the valve seat.
  • the front end of the flap valve has a semicircular arc shape on the compression chamber side, and a sealing surface is provided on the outflow chamber side in sliding contact with the linear protrusion, and a back spring is mounted between the valve seat and the fixed cylinder on the back chamber side.
  • a side spring such as a spring provided between the flap valve and the side wall surface on the valve mounting chamber outflow chamber side, and the total height of the valve seat and the flap valve is approximately equal to the height of the valve mounting chamber.
  • the pressure receiving area related to opening and closing of the valve can be made larger than that of the flat gate valve, and the operability is improved. Therefore, it is not necessary to introduce a pressure lower than that of the outflow chamber to the back chamber constituting the valve storage chamber as described in any one of claims 6 to 10. Further, since the working gas remaining between the envelope groove side wall surface of the valve storage chamber and the flap valve when the valve is closed flows out to the back side of the valve storage chamber, almost no recompression loss occurs.
  • the movable mechanism member is obtained by rotating or swiveling or swinging the movable mechanism member mounted on the eccentric shaft of the drive shaft by mounting a hollow cylindrical cylindrical piston having both end surfaces parallel and flat.
  • a crescent-shaped columnar space formed by incorporating the cylindrical piston into the fixed cylinder as the fixed component in which the cylindrical inner wall surface obtained as the envelope of the wall surface is provided in the center and both end surfaces are formed parallel and flat is flattened.
  • a space formed by being sandwiched by a flat cover member can be directly moved into a parallel groove having one end formed in a rectangular shape on the cylindrical inner wall surface of the fixed cylinder, and the tip portion is in sliding contact with the outer wall surface of the cylindrical piston.
  • a suction chamber and a compression chamber are formed by partitioning with a substantially rectangular parallelepiped partition plate.
  • a valve storage chamber is formed by a valve mounting chamber formed by enlarging the width of the parallel groove of the fixed cylinder to which the partition plate is mounted and an outflow chamber provided at the back thereof, and the compression chamber side of the valve mounting chamber
  • a support member is provided between the side wall surfaces of the substantially rectangular parallelepiped gate valve and the partition plate, the front end portion of which has a side wall seal surface that is in sliding contact with the side wall surface of the cylindrical piston and the outer surface of the cylindrical piston is in sliding contact with the outer wall surface of the cylindrical piston.
  • a discharge mechanism is provided in which an outflow passage is provided to the chamber side, and a valve mechanism that is configured by attaching an elastic body such as a spring to the outflow chamber is assembled to the outflow chamber.
  • the partition corresponding to the blade used for the flat gate valve and the positive displacement rotary compressor whose compression chamber pressure is applied to the valve storage chamber formed by the valve mounting chamber and the back chamber.
  • the center position of the tip portion that is the center of the plate thickness of the flat gate valve is decentered from a center line that passes through the center of the inner wall surface of the fixed cylinder and is parallel to the side wall surface of the valve mounting chamber.
  • the flat gate gate tip is formed by a general flat surface or a circular arc convex toward the cylindrical piston having the center on the parallel center line, so that it is in a range of more than half of the valve tip.
  • the compression chamber pressure always acts to secure the opening force of the valve, and the operability is improved.
  • a low-pressure introduction hole communicating with a low-pressure passage at one end of a flat surface of a cylindrical space formed by a main cover or a sub-cover that is the flat lid member that sandwiches the fixed cylinder and the cylindrical piston.
  • a locking control chamber formed from a communication hole communicating with the valve mounting chamber is provided on the end side, and a spring is provided in an inner cavity portion of the cylindrical portion formed by a two-stage cylinder having a large diameter cylindrical portion and a small diameter pin portion.
  • the locking member is placed on one of the upper and lower end surfaces or the side wall seal surface that slides on the flat lid member in a state in which the distal end portion of the flat gate valve is housed in the valve mounting chamber inside the compression chamber.
  • a discharge mechanism including the flat gate valve having a locking hole at a position where the pin portion can be loosely inserted.
  • the engagement is applied.
  • the pin portion of the stopper member is loosely inserted into the locking hole of the flat gate valve, and the flat gate valve does not move. In this state, a large gap twice as large as the maximum turning radius is maintained between the flat plate gate valve tip and the cylindrical piston which is a flat seat.
  • the control differential pressure becomes larger than the spring force due to the operation of the compressor, the pin portion of the locking member is detached from the locking hole of the flat gate valve, and the flat gate valve can be operated.
  • the pressure in the compression chamber is switched to a low pressure state, and at the same time, the tip of the plate-like valve body is moved to the valve mounting chamber as the valve seat of the swing piston or cylindrical piston, which is a movable mechanism member, approaches the valve mounting chamber. Since it closes instantaneously from a state without any gas, there is no delay in closing, and there is almost no recompression loss due to the backflow of the working gas in the outflow chamber to the compression chamber.
  • a plate-like valve body such as a flat gate valve with a large plate thickness and high rigidity is used for the discharge valve, there is almost no deformation due to a pressure difference acting on the front and back, so that the sealing performance is high, and the plate-like valve body and partition plate
  • the flat seal surface is provided at the tip of the plate-like valve body, so that the sealing performance is further enhanced. There is almost no leakage between the outflow chamber and the compression chamber or between the inflow chamber and the efficiency of the compressor can be improved.
  • a rolling element such as a rolling bearing between the plate-like valve element and the valve mounting chamber side wall surface.
  • a plate-like valve body such as the flat gate valve is provided on the fixed cylinder at the start-up when the pressure in the compressor is in a balanced state. Since the passage between the compression chamber and the outflow chamber is opened, even if a liquid such as lubricating oil flows into the compression chamber, it is discharged into the discharge space as it is and does not cause abnormal high pressure. Sex is obtained.
  • the capacity control valve provided in the middle of the discharge pipe extending from the outflow chamber is operated to Is introduced into the locking control chamber, the pressure becomes equal to the outflow chamber, the locking member operates, the plate-like valve element is locked to the fixed cylinder, and the working gas in the compression chamber is moved to the suction side. Since the process returns, the capacity control mechanism is easily configured.
  • FIG. 2 is a cross-sectional view taken along the line AA in FIG. It is a top view of the turning piston applied to FIG. It is a top view of the fixed cylinder applied to FIG. It is the elements on larger scale of the discharge mechanism A which looked at 12 arrows in FIG.
  • FIG. 6 is a sectional view taken along line BB in FIG. 5.
  • 1 is a flat gate valve R8 used in the discharge mechanism A of FIG. 1, in which (a) is a front view thereof, and (b) is a sectional view taken along the line CC of (a).
  • FIG. 26 is a sectional view taken along line FF in FIG. 25. It is a top view of the turning piston applied to FIG. It is a top view of the fixed cylinder applied to FIG. It is the elements on larger scale of the discharge mechanism C which looked at 312 arrow concerning Example 10 of other invention.
  • FIG. 30 is a cross-sectional view developed along the center line G of FIG. 29.
  • (A) of the circular arc gate valve R which concerns on Example 10 of other invention is the upper end surface
  • (b) is the side view seen from the circular arc inside of (a). It is explanatory drawing for setting the front-end
  • (A) of the intermediate member which concerns on Example 10 of other invention is the upper end surface
  • (b) is the side view seen from the circular arc inside of (a).
  • 10 is a pressure control mechanism in the back chamber according to Embodiment 10 of another invention, (a) shows a state diagram before operation of the control valve, and (b) shows communication between the back chamber and the compression chamber by operating the control valve.
  • FIG. 51 is a cross-sectional view taken along line MNOP in FIG. 50.
  • FIG. 2 which is a longitudinal sectional view of the ring compressor 1 in FIG. 1 and a sectional view taken along line AA in FIG. 1, the fixed cylinders 6 mounted on the frame 5 fixed in the sealed container 2 and their A revolving mechanism 20 using a revolving piston 7 and an Oldham ring is provided between them, and a lower part of a drive shaft 22 supported by a bearing provided at the center of the frame is directly connected to an electric motor 23.
  • a ring-shaped swiveling protrusion 7a having a rectangular cross section is loosely inserted into an envelope groove 6a which is a ring-shaped cavity having a rectangular cross section of the fixed cylinder shown in FIG. 1 and FIG.
  • the space formed on the outer wall surface side of the swiveling protrusion 7a of the envelope groove 6a is an outer compression chamber
  • the space formed on the inner wall surface side of the swiveling protrusion 7a of the envelope groove 6a is an inner compression chamber.
  • the shape of the orbiting piston 7 is a constant width and height in the section from the point P to the point Q in the figure formed by bending a belt-like plate having a rectangular cross section into a cylindrical shape having one round or less.
  • a circular protrusion 7b formed of a circular arc protrusion and a tangent direction of point Q at one end thereof are linearly the same cross-sectional shape and extend a certain length to point R, and are united with the circular protrusion to stand upright on the rotating disk 7d.
  • a swiveling protrusion 7a is formed by the straight protrusion 7c.
  • the orbiting piston 7 is inserted into the bearing boss 7e and performs a revolving motion without rotation, that is, an orbiting motion, with the eccentric shaft of the drive shaft 22 and the swiveling mechanism 20 attached to the orbiting piston.
  • the shape of the fixed cylinder 6 is such that the envelope groove 6a having a constant width and a rectangular cross section obtained by using the envelope formed by the swiveling motion of the arc projection 7b as a side wall surface is formed on the fixed end plate 6b.
  • a suction hole 6e and a discharge hole 6f are provided on each side of the envelope groove 6a provided with an inflow chamber 6c for working gas and an outflow chamber 6d at the other end.
  • the outflow chamber 6d is formed as a straight groove because the minimum width is determined as the envelope groove of the straight protrusion 7c.
  • valve mounting chamber 6h formed by a parallel groove having the same bottom surface as the envelope groove that opens opposite to the inner and outer wall surfaces of the outflow chamber 6d provided with the discharge hole 6f provided by extending the envelope groove 6b, and the back thereof Two pairs of valve storage chambers 6h, which are paired with a back chamber 6j provided in the same space, are provided. Further, the back chamber 6j is provided with an outflow chamber 6c or a pressure introducing hole 6k communicating with the discharge space 21 shown in FIG.
  • the discharge mechanism A12 is a rear chamber in which a flat plate gate valve R8 and a flat plate gate valve L9, each of which is provided symmetrically with the tip portion sandwiched between the linear protrusions 7c of the orbiting piston, are mounted in the valve mounting chambers 6h.
  • an elastic body such as a spring is provided so as to press the flat gate valves R and L against the linear protrusion side.
  • the other end of the pressure introducing hole 6k opened to the back chamber 6j shown in FIG. 4 is any one on the passage of the discharged working gas from the discharge hole 6f including the outflow chamber 6d to the discharge pipe 4 shown in FIG.
  • the discharge passage 15 is open.
  • the back chamber 6j which is a part of the valve storage chamber 6g, stores a valve complement material such as a back spring 11 that presses the flat gate valve, and flows out by communicating with the discharge passage 15. A lower pressure than the chamber 6c can be introduced.
  • the flat plate gate valve R8 and the flat plate gate valve L9 mounted in each valve mounting chamber 6h are configured as a rectangular parallelepiped having the same height as the straight projection 7c, and the tip portion is slidably in contact with the straight projection side wall surface serving as a valve seat.
  • the shapes of the gate valves R8 and L9 are in a line-symmetrical relationship with respect to the flat surface of the linear protrusion.
  • a discharge mechanism for the outer compression chamber is shown unless otherwise specified. Therefore, the shape of the flat gate valve L can be specified because the symmetrical shape with respect to the front end 8h plane of the flat gate valve R8 for the outer compression chamber becomes the flat gate valve L9 for the inner compression chamber. Omit.
  • FIG. 7 and 8 show the detailed shape of the flat gate valve R8 as a representative of the flat gate valves R and L.
  • the flat plate gate valve R8 is formed by providing various grooves, stages, and holes from the flat portion of the rectangular parallelepiped external shape to the inside. Details thereof will be described below.
  • FIG. 7A is a front view of the side wall surface of the flat gate valve R8 on the compression chamber side, and FIG.
  • the side wall surface has a side wall seal surface 8c slidably in contact with the valve mounting chamber 6h, a pressure pocket 8k recessed from the side wall, a communication hole 8m provided inside the same surface as the side wall seal surface, and a seal groove on the back surface portion 8b side. 8p is provided. Further, the communication hole 8m is opened in the space of the pressure pocket provided in the same manner as the pressure pocket on the side wall support surface 8d opposite to the side wall seal surface 8c.
  • two elongated holes 8n for mounting an elastic body such as a spring that opens to the back surface portion 8b are provided inside the valve. Further, the details of the hole 8 and the groove provided in the upper end view which is the right side view of the tip 8a having a complicated shape and the right side view of FIG. 8A and FIG. This will be described in detail with reference to FIG.
  • a flat seal surface 8g slidably in contact with the side wall surface of the linear protrusion 7c, a pressure receiving surface 8h recessed from the surface, and a wind pressure receiver formed with a large inclined surface facing the compression chamber at its center.
  • An oil groove 8r extending from the surface 8j and an oil receiving hole 8q provided on the upper end surface extends to the flat seal surface 8g at the tip.
  • the width in the plate thickness direction of the flat seal surface 8g is formed from about 1/6 to 1/2 or less of the plate thickness.
  • the length Ls of the straight protrusion 7c shown in FIG. 3 is set to be twice the turning radius because the flat seal face 8g of the flat gate valve shown in FIG. The minimum length plus the width is required.
  • FIG. 6 which is a cross-sectional view taken along the line BB of FIG. 5, shows the relationship between the locking member 30 mounted in the cylindrical locking control chamber 6 n provided on the fixed end plate 6 b of the fixed cylinder and the flat gate valve R 8. The relationship is shown.
  • the appearance of the locking member 30 is shown in FIG.
  • a cylindrical portion 30a and a pin portion 30b having a smaller diameter are formed in a two-stage cylindrical shape.
  • a hollow portion 30d is provided in the cylindrical portion, and a seal end surface 30c, which is a ring-shaped end surface, is provided in the locking control chamber 6m.
  • the shape can be in close contact with the end face.
  • the locking member 30 formed in this way aligns the pin portion 30b together with the locking spring 31 in the locking control chamber 6m of the fixed end plate 6b with the locking hole 6q of the fixed end plate 6b.
  • the locking mechanism is configured by loosely attaching toward the flat gate valve R side. Such a configuration can be applied to the inner and outer compression chambers or the discharge mechanism for each compression chamber.
  • One end of the communication pipe 32 for introducing the suction pressure is opened at the end face of the latch control chamber 6m where the latch spring 31 is mounted, and the latch hole opened at the upper end face of the flat gate valve on the opposite side.
  • the pressure in the back chamber 6j or the outflow chamber is introduced from 6q.
  • the pressure in the normal compressor is usually uniform, that is, the suction pressure and the discharge pressure are equal. Therefore, the pressure in the locking control chamber 6m is also uniform, and the locking member 30 has Only the load of the locking spring 31 is acting. Accordingly, the pin portion 30b of the locking member is pressed onto the upper end surfaces of the flat gate valves R and L by being pressed by the locking spring.
  • the oil receiving hole 8q and the locking hole 6q of the flat gate valve R are pushed by the back spring 11 or the linear protrusion 7c and the flat gate valve moves in the valve mounting chamber 6h.
  • the pin portion 30b enters the oil receiving hole 8q so that the flat gate valve R does not move and is fixed.
  • the gas flowing out from the compression chamber enters the outflow chamber and flows out into the discharge space, so that the pressure in the discharge space, that is, the back chamber gradually increases.
  • the locking member 30 is pushed, the pin portion 30 b is detached from the locking hole 6 q, and the flat gate valves R and L move in the valve mounting chamber.
  • the compression chamber is sealed by sitting on the side wall surface of the straight protrusion, which is the valve seat at the tip.
  • P pressure
  • suffix s represents the inflow chamber
  • d represents the outflow chamber or discharge space
  • c represents the pressure state of the compression chamber.
  • co represents an outer compression chamber
  • ci represents an inner compression chamber.
  • the arrow in the inflow chamber 6d indicates the moving direction of the linear protrusion 7c integrated with the orbiting piston, and the arrow in the inner and outer compression chambers indicates the gas flow direction during the discharge stroke.
  • FIG. 6A shows a state immediately after the linear protrusion 7c is closest to the side wall surface of the outflow chamber 6d and the discharge stroke of the outer compression chamber is completed, and immediately before the linear protrusion 7c moves downward.
  • the flat gate valve R8 reaches the innermost part of the back chamber 6j of the valve mounting chamber 6h, the moving speed becomes zero, and the back spring 11 is contracted most, while the flat gate valve L9 protrudes most from the valve mounting chamber 6h to the compression chamber side.
  • the back spring 11 is in the most extended state.
  • the pressure Pco of the outer compression chamber becomes equal to the inflow chamber pressure, that is, the suction pressure Ps, while the pressure Pci of the inner compression chamber is lower than the outflow chamber pressure, that is, the discharge pressure Pd, and the tip of the flat gate valve L9 is formed by the linear protrusion 7c.
  • the sealing is ensured by sliding contact with the side wall surface, and the compression is continued.
  • the pressure Pci is increased to the flat gate valve L. 9 acts on the pressure receiving surface 9h in the pressure pocket 9k and at the tip, and the flat gate valve L9 is pushed to the outflow chamber 6d side and at the same time is pushed to the back chamber 6j side to greatly increase the sliding frictional force between the side wall surfaces.
  • the flat gate valve L9 is easily pushed to the back chamber 6j side, and the leading end of the valve is detached from the side wall surface of the straight projection 7c so that the passage opens as indicated by the valve opening in the figure.
  • the gas in the compression chamber flows into the outflow chamber in the direction indicated by the arrow.
  • the pressure Pci of the inner compression chamber becomes equal to the inflow chamber pressure, that is, the suction pressure Ps, while the pressure Pco of the outer compression chamber is lower than the outflow chamber pressure, that is, the discharge pressure Pd.
  • the sealing is ensured by sliding contact with the side wall surface, and the compression is continued.
  • the pressure Pco in the outer compression chamber 13 which has become larger than the outflow chamber pressure Pd acts on the pressure pocket 8k of the flat gate valve R8 and the pressure receiving surface 8h at the tip, so that the flat gate valve R moves toward the outflow chamber 6d.
  • the flat gate valve R8 is easily pushed to the back chamber 6j side while the sliding friction force between the side wall surfaces is greatly reduced by being pushed to the back chamber 6j side, and the tip of the valve is a straight protrusion 7c.
  • the passage opens as shown by the valve opening in the figure away from the side wall surface, and the gas in the compression chamber flows into the outflow chamber in the direction indicated by the arrow.
  • the dead space that is one of the causes of recompression loss which becomes a problem during the discharge stroke corresponds to a space sandwiched between the gap between the tip end portion 8a of the flat gate valves R and L and the side wall of the linear protrusion 7c. Since the space is extremely small, there is almost no recompression loss due to the dead space.
  • the figure is divided into a plurality of flat gate valves R48 having the same planar shape parallel to the bottom surface of the valve mounting chamber 6h, and each is provided with a slot 48g for mounting a back spring. Then, the connecting pin 51 is inserted into a pin hole provided in each divided member, and a plurality of flat gate valves are stacked and connected. Of course, this also applies to the flat gate valve L for the inner compression chamber.
  • the linear protrusion 7c serving as a valve seat is deformed under the influence of pressure or temperature change, but the amount of deformation is larger on the tip side than on the fixed end on the swivel disk side as in the bending of the beam. .
  • the flat gate valve R according to the second embodiment can partially move following the amount of deformation, and the gap in the flat seal surface at the tip can be minimized to eliminate the decrease in efficiency.
  • this embodiment is configured by mounting one or a plurality of rolling elements 76 such as a rolling bearing between the flat gate valve R68 and the side wall surface on the outflow chamber side of the valve mounting chamber 6h.
  • the rolling element 76 has a wheel portion 76a mounted on an axle 76b, and is arranged such that the wheel portion protrudes from the tens of hundreds of microns to the side wall support surface of the flat gate valve R. It is configured to be rotatable between the parts or between the axle and the flat gate valve. Of course, this also applies to the flat gate valve L for the inner compression chamber.
  • valve housing of the fixed cylinder 86 is maintained in a state in which the surface contact state between the side wall surface of the linear protrusion 7c and the flat seal surface of the flat gate valve R and the clearance between the compression chamber side end portions are maintained.
  • the valve mounting chamber 86h forming the chamber 86g has an angle of about several degrees on the side of the envelope groove side of the valve mounting chamber with respect to the tangent of the linear protrusion and the end portion of the envelope groove 86b on the outflow chamber 86d side.
  • the relative angle between the front end portion of the flat plate gate valve R88 and the flat plate gate valve L89 and the side wall surface of the flat plate gate valve R89 is set to a shape that matches the inclination angle.
  • a valve storage chamber 106g is constituted by a long-arc shaped rear chamber 106j having a semicircular arc at both ends at the same width as the envelope groove at the back of the valve mounting chamber 106h having a rectangular cross section, and a rectangular parallelepiped having the same height in the valve mounting chamber.
  • the flat plate gate valve R8 of the first embodiment which is slidably mounted with a small gap between the side piece 116 that is closely fixed to the side wall surface of the outflow chamber in the shape and the side wall surface of the envelope groove side valve mounting chamber; It consists of a flat gate valve L9.
  • the productivity can be improved because the outflow chamber 106d and the valve storage chamber 106g including the valve mounting chamber 106g and the back chamber 106j can be easily processed by using one cutter for processing the envelope groove 6a. Will improve.
  • FIG. 16 shows the shape of the flat gate valve R148
  • FIG. 18 shows the shape of the valve auxiliary member 156.
  • a restraining portion 148t is provided on the back surface portion 148b of the flat gate valve R148 so as to protrude as a portion against which the end surface of the valve auxiliary member 156 is applied.
  • the tip portion 148a and the side wall seal surface 148k having other shapes are the same as those of the flat gate valves R and L in the first embodiment.
  • the valve auxiliary member 156 shown in FIG. 18 is equipped with one or a plurality of rolling elements 167 such as rolling bearings.
  • the rolling element 167 is configured by mounting a wheel portion on the axle, and is disposed such that the wheel portion protrudes from the tens to hundreds of microns from the side wall support surface of the valve auxiliary member 156. It is configured to be rotatable between the parts or between the axle and the valve auxiliary material. Of course, this also applies to the flat gate valve L for the inner compression chamber.
  • FIG. 7 In the configuration in which the flat gate valve R of FIG. 7 is mounted in the valve storage chamber composed of the valve mounting chamber and the back chamber similar to FIG. 5 of the first embodiment, in this embodiment, FIG. A flat gate valve R168 as shown in FIG.
  • the difference between the flat gate valve R168 and the flat gate valve R of the first embodiment shown in FIG. There is no pressure receiving surface or wind pressure receiving surface at the distal end portion 168a so as to block the discharge hole 168j communicating with the compression chamber provided in the concave groove 168g that passes through the distal end portion dug into a substantially U shape at the center of the side wall support surface 168d.
  • a reed valve 176 and a retainer 177 for supporting the reed valve 176 on the back are mounted.
  • the present invention can also be applied to the discharge mechanism A and the flat gate valve L for the inner compression chamber.
  • FIG. 21 In the configuration in which the flat gate valve R of FIG. 7 is mounted in the valve storage chamber composed of the valve mounting chamber and the back chamber similar to FIG. 5 of the first embodiment, in this embodiment, FIG. A flat gate valve R188 as shown in FIG. 21 and its operation mechanism are used.
  • the flat gate valve R168 is different from the flat plate gate valve R of the first embodiment shown in FIG. 7 in that the wind pressure receiving surface at the front end and the side wall seal surface and the side wall support surface are not communicated. It has a simplified configuration. Instead, as a mechanism for assisting the opening operation by separating the flat gate valve R188 and the flat gate valve L189 from the side wall surface of the linear protrusion 7c as a valve seat, the former is equipped with a rotating disk 196, and the latter is equipped with a rotating disk. 196 and an auxiliary disk 198 are separately mounted between them.
  • one end is fixed to the turning disc of the turning piston at a position away from the turning radius from the center of the rotating disk 196 rotatably mounted around the shaft fixed to the fixed cylinder.
  • a swivel pin 197 is attached to the shaft, and the diameter of the outer periphery of the swivel pin 197 is reduced so that the pin is mounted in the cylindrical space of the fixed cylinder.
  • the peripheral speed of the outer diameter is greater than the maximum speed of the swivel protrusion.
  • a rotary shaft fixed to a fixed cylinder so as to be in sliding contact with the outer diameter of the rotary disc 196 between the rotary disc 196 and the flat gate valve L189.
  • An auxiliary disk 198 having a heart is attached. A part of the outer peripheral portion of the auxiliary disk 198 protrudes within the gap between the valve mounting chamber 186h and the side wall surface of the flat gate valve L, and the rotational force is transmitted from the rotating disk 196 to the auxiliary disk 198. This is within a range in which the flat gate valve L is pushed by the linear protrusion 7c and moves to the back chamber side.
  • the main difference between the discharge mechanism A and the discharge mechanism B is that the operation of the valve mechanism body constituted by the plate-like valve body provided opposite to the linear protrusion 7c and the auxiliary member is particularly different.
  • the operation of the valve mechanism body constituted by the plate-like valve body provided opposite to the linear protrusion 7c and the auxiliary member is particularly different.
  • FIG. 22 is an enlarged cross-sectional view of a component part of the discharge mechanism B212
  • FIG. 23 is an external perspective view in which the flap valve 218 for the discharge mechanism B and its related members are disassembled
  • FIG. It is explanatory drawing of the operation state of B.
  • the configuration of the flap valve R208 applied to the outer compression chamber will be described, but the configuration can also be applied to the flap valve L209 for the inner compression chamber.
  • a rectangular parallelepiped valve seat 210 is loosely inserted into the valve mounting chambers 206h of the inner and outer compression chambers 13 and 14 symmetrically across the linear protrusion 7c, and can come into surface contact with the side wall surface of the linear protrusion 7c.
  • a flap valve R208 provided with a pin hole parallel to the side wall surface of the valve mounting chamber is fixed to the valve seat 210 at the central portion of the circular arc having a convex arc shape on the opposite front end surface and the back chamber side on the opposite side.
  • the rotating pin 216 is attached.
  • a discharge mechanism B212 is configured as a pair for the inner compression chamber and a valve mechanism for the outer compression chamber, which is composed of a side spring 218 and a back spring 217 mounted between the valve seat and the fixed cylinder.
  • FIG. 4B shows a state in which the inner compression chamber pressure is higher than the outflow chamber pressure and the flap valve L209 is operated in the same manner as the outer compression chamber flap valve R.
  • the main difference between the discharge mechanism A, the discharge mechanism B, and the discharge mechanism C is in the shape of a plate-shaped valve body that is provided facing the linear protrusion of the orbiting piston. That is, the former flat gate valve and flap valve are based on a rectangular parallelepiped plate-like valve body, but the latter is greatly different in that it is formed by bending the plate into an arc.
  • the former flat gate valve and flap valve are based on a rectangular parallelepiped plate-like valve body, but the latter is greatly different in that it is formed by bending the plate into an arc.
  • FIG. 25 is a longitudinal sectional view of the scroll positive displacement compressor 301
  • FIG. 26 is a sectional view taken along line FF of FIG.
  • FIG. 27 shows a plan view of the orbiting scroll, or orbiting piston 307, which is the main member constituting the compression mechanism
  • FIG. 28 shows a plan view of the fixed scroll or fixed cylinder 306.
  • the scroll type positive displacement compressor 301 is provided with a fixed cylinder 306 mounted on a frame 321 fixed in an airtight container 302, and a swing piston 307 and a swing mechanism 320 between them.
  • the lower part of the drive shaft 322 supported by the bearing of the central frame is directly connected to the electric motor 323.
  • a swiveling projection 307a of a swiveling piston formed by bending a constant thickness plate into an envelope groove 306a having a cross-section with the U-shaped bottom portion of the fixed cylinder down is loosely inserted between the side walls.
  • a plurality of sealed spaces are formed by closing the upper and lower sides of the crescent-shaped space formed by the closed end plate 306b and the swivel disc 307e.
  • the swiveling piston 307 has a plate-like swiveling shape having a swirling protrusion 307a mainly composed of a swirling protrusion 307b formed by bending a belt-like equal thickness plate in a spiral shape.
  • the disk 307d is erected on one side, and a bearing boss that is pivotally connected to the eccentric shaft of the drive shaft is provided at approximately the center on the opposite side.
  • the orbiting piston 307 is inserted into the bearing boss and performs a revolving motion without rotation, that is, an orbiting motion, by the eccentric shaft of the drive shaft 322 and the swiveling mechanism 320 attached to the orbiting piston.
  • a straight protrusion 307c having the same rectangular cross section as that of the spiral protrusion 307b and extending in the tangential manner linearly at a height equal to or more than twice the length of the turning radius and standing upright on the turning disk 307d.
  • a turning protrusion 307a is configured.
  • spiral protrusion 307b is an involute curve between the outer P point and the Q point, and the connection portion with the involute curve is the same tangent between the Q point and the R point, and is larger than the extended radius of the involute curve.
  • a circular protrusion 307a is formed by two straight curved lines having a reduced arc radius and the straight protrusion 307c between the R point and the S point.
  • the fixed cylinder 306 has a constant width envelope groove 306a obtained by using the envelope formed by the swiveling motion of the swiveling protrusion 307a as a wall surface.
  • a working gas inflow chamber 306c is provided at one end on the outer peripheral side of the envelope groove 306a, and an outflow chamber 306e is provided on the inner peripheral side with the same bottom surface as the envelope groove 306a.
  • a suction hole 306d and a discharge hole 306n are provided in 306c and the outflow chamber 306e, respectively.
  • the outflow chamber 306e is formed as a straight groove because the minimum width is determined as the envelope groove of the straight protrusion 307c.
  • a part of a cylindrical outer wall having a diameter of about twice or more the width of the envelope groove on the same bottom surface as the envelope groove 306a and the outflow chamber 306e is connected to the inner and outer wall surfaces of the envelope groove.
  • a ring-shaped valve storage chamber 306g is formed with the back chamber 306j.
  • Each of the valve mounting chambers 306h has a fine oil supply hole 306q
  • the back chamber 306j has an outflow chamber 306c or a pressure introduction hole 306n communicating with the discharge space 325.
  • Two pin holes 306m are provided in the center.
  • FIG. 29 which is an enlarged view of the discharge mechanism C indicated by the arrow 312 in the center of FIG. 26 and FIG. 30 which is a cross-sectional view developed along the center line G indicated by the arrow in FIG.
  • the configuration and function of the discharge mechanism C312 will be described in detail with reference to FIG. 31 showing the shape of the arc gate valve R308 which is a body.
  • the description will focus on the configuration of the arc gate valve R308 applied to the outer compression chamber.
  • the present invention is also applicable to an arc gate valve L309 for the inner compression chamber that is configured symmetrically with respect to the straight protrusion 307c.
  • the linear projection 7c is slidably provided with a small gap between the inner and outer wall surfaces and upper and lower end surfaces of the valve mounting chambers 306h for the inner and outer compression chambers 313 and 314 with the linear projection 7c interposed therebetween.
  • 307c Arc gate valve R308 and arc gate valve L309 which are in sliding contact with both wall surfaces are mounted, and a back spring 310 is mounted between the intermediate member 311 positioned by a set pin 316 in the back chamber 306j and the arc gate valve.
  • the end surfaces of the envelope groove 306a, the outflow chamber 306e, and the valve mounting chamber 306h are closed by the end surface of the swivel disk 307d to constitute the discharge mechanism C312.
  • the back spring 310 is a member that cushions the assistance or shock of the operation of the arc gate valve R308 and the arc gate valve L309, and can be replaced with another elastic body.
  • the configuration and function of the locking mechanism using the locking member 330 provided on the fixed end plate 306b of the fixed cylinder in FIG. 30 are the same as those in FIGS.
  • FIG. 31A shows the shape of the upper end surface of the arc gate valve R306, and FIG. 31B shows a side view seen from the right side of FIG. (A)
  • the arc shape of the side wall seal surface 308c and the side wall support surface 308d showing the inner and outer wall surfaces in the figure is formed by an arc having a circumferential length in the range from about 1/4 turn to less than half turn. It has a shape that can be mounted with a small gap in 306h.
  • An oil introduction hole 308n that connects an oil receiving hole 308m recessed in the upper end surface 308e and a tip oil groove 308p provided in the tip portion 308a is provided, and in a state where the compression chamber pressure is lower than the discharge pressure, the fixed cylinder
  • the oil intermittently supplied from the oil injection hole 306q to the oil receiving hole 308s by the differential pressure enters the tip oil groove 308p through the oil introduction hole, and seals the tip part, the side wall seal surface or each part in sliding contact with each other. Used for lubrication.
  • FIG. 32 is a schematic diagram showing the method of forming the shape of the tip portion that is in sliding contact with the side wall surface of the linear protrusion 307c.
  • FIG. 32 shows the relationship between the valve mounting chamber 306h, the envelope groove 306a, the inner and outer wall surfaces of the outflow chamber 306e, and the side wall surface of the linear protrusion 307c that makes a swiveling motion.
  • a method of forming the R shape will be described using these relationships and the positional relationship from the point A to the point D indicated by the arrows in the figure showing the groove center line of the ring-shaped valve storage chamber 306g.
  • point A is the intersection of the straight outflow chamber outer wall and the valve mounting chamber wall that is an arc-shaped groove
  • point B is the intersection of the groove center line and envelope groove outer wall
  • point C is the groove center line and envelope. The intersection with the side wall surface which added the thickness of the linear protrusion 307c to the groove inner wall is shown.
  • the point D is the line OH obtained by adding ⁇ HOF, which is equal to the angle of ⁇ EOG, to the angle of ⁇ EOF, and the outer wall of the arcuate valve mounting chamber
  • ⁇ HOF which is equal to the angle of ⁇ EOG
  • ⁇ EOF the angle of ⁇ EOF
  • the intersection of The shape of the tip portion 308a of the arc gate valve R308 is formed by an arc or a parabola that protrudes from the A point, the B point, and the D point and has a convex center. The same applies to the tip of the arc gate valve L309.
  • the length of the linear protrusion 307c shown in FIG. 29 is set to be twice the turning radius so that the point B at the tip of the circular gate valve R shown in FIG. The minimum length including the distance between the points A and B at the tip is required.
  • the arc gate valve R and arc gate valve L are also recessed one step on the side wall seal surface and side wall support surface that slide in contact with the side wall surface of the valve mounting chamber 306h on the envelope groove 306a side.
  • FIG. 33A shows a top view of the intermediate member 311
  • FIG. 33B shows a side view of the intermediate member 311 as viewed from the inside of the arc in FIG. (A)
  • the top surface 311e is provided with a pin hole 311f for mounting at a fixed position on the bottom surface of the back chamber, and both side wall end surfaces 311c are provided.
  • a plurality of spring holes 311d are provided.
  • FIG. 34 shows a pressure control mechanism for the pressure in the back chamber 306j.
  • A The figure shows the state before the operation of the control valve 317 in the state where the pressure in the inflow chamber and the discharge space before the compressor operation is equal, and (b) shows the discharge space pressure more than the inflow chamber after the compressor operation. In this state, the control valve 317 is in a sufficiently high state and the back chamber and the compression chamber communicate with each other.
  • FIG. 35 (a) is a section in which the pressure in the outer compression chamber 313 is lower than the pressure in the back chamber 306j, and the tip of the linear protrusion 307c operates as shown by the arrow in the figure to connect the arc gate valve R308 to the valve mounting chamber.
  • the tip 308a of the arc gate valve R is in close contact with the side wall surface of the linear protrusion 307c and the side wall seal surface 308c on the compression chamber side is in close contact with the side wall surface of the valve mounting chamber 306h. Therefore, the compression of the working gas is continued in a state where the sealing performance between the compression chamber and the outflow chamber and between the back chamber is ensured.
  • the arcuate gate valve R308 is located in the valve mounting chamber and the rear chamber in a state where the linear protrusion 307c is close to the side wall surface of the envelope groove 306a and there is little space in the outer compression chamber.
  • the moving speed in the direction perpendicular to the side wall surface of the linear protrusion is maximized at the center of the envelope groove and becomes almost zero in the state closest to the envelope groove side wall surface because of the swiveling motion. .
  • the dead space that is one of the causes of recompression loss that becomes a problem immediately after the end of the discharge stroke corresponds to a space sandwiched between the gaps between the tip ends of the arc gate valves R and L and the side walls of the linear protrusions.
  • the space can be reduced by setting an appropriate arc shape of the tip.
  • FIG. 6 (d) shows a state in which the compression of the inner compression chamber 314 advances and the pressure becomes higher than the back chamber pressure and enters the discharge stroke, and acts on the distal end portion 309a of the arc gate valve L309 for the inner compression chamber.
  • the pressure of the back chamber becomes larger than the pressure in the back chamber, and the tip of the arc gate valve L moves away from the side wall surface of the linear protrusion and moves toward the back chamber, so that it opens and compresses in the same direction as the linear protrusion.
  • the chamber working gas flows into the outflow chamber.
  • the operation of the arc gate valve L for the inner compression chamber 309 is basically the same as that of the arc gate valve R for the outer compression chamber 308, but the timing of the operation is as shown in FIGS. Different.
  • an outer arc gate valve R360 and an inner arc gate valve R361 having different curvatures obtained by dividing a plurality of arc gate valves in the radial direction are mounted as a set in the valve mounting chamber 306h for the outer compression chamber 313.
  • the inner arc chamber 314 is also symmetrically mounted with an outer arc gate valve L362 and an inner arc gate valve L363 as a set.
  • an outer spring 364 and an inner spring 365 are disposed on the intermediate member 366 and the arc gate valve, respectively.
  • the operation mode of the eleventh embodiment is basically the same as the eleventh embodiment shown in FIG. 35, and will be briefly described below.
  • the tip of the outer arc gate valve R360 separates from the side wall surface of the linear protrusion 307c due to the differential pressure, and the valve mounting chamber is pushed toward the back chamber.
  • the differential pressure acts on the entire tip, so that the opening operability of the valve is enhanced, and at the same time, the differential pressure acts on the tip of the inner arc gate valve R361.
  • the inner arc gate valve R is easily opened by the frictional force effect caused by the movement of the outer arc gate valve R, and the working gas compressed in the outer compression chamber flows out to the outflow chamber.
  • FIG. 37 shows a plan view of a fixed cylinder 386 applied to the twelfth embodiment.
  • a cylindrical chamber 386h which is a cylindrical space having the same floor surface as the envelope groove, is provided on the inner side where a cylindrical inner wall 386g connected to the envelope groove 386a is formed in the same manner as in the eleventh embodiment.
  • a U-shaped pin hole 386k, a lubrication hole 386q, a pressure introducing hole 386n, and a pin hole 386m are provided symmetrically around a discharge hole 386f provided as a through hole in the vicinity of the center, and a U-shaped pin hole 386k. Other than the above, they are provided in the same manner as in FIG.
  • FIG. 38 (a) is a plan view of the U-shaped grooved cylinder 397 and FIG. 38 (b) is a side view of the side surface of FIG. 38 (a), in which a U-shaped outflow chamber 397b is formed on the inner side of the cylindrical outer wall 397a. Is provided with a pin hole 397e. By inserting the pin inserted into the pin hole 397e into the pin hole 386k of FIG. 37, a valve storage chamber and an outflow chamber as shown in FIG. 28 are formed.
  • FIGS. 1-10 A thirteenth embodiment of the discharge mechanism D applied to a rotary positive displacement compressor as a type of positive displacement compressor of the present invention will be described below with reference to FIGS.
  • the configuration is one cylinder, that is, one cylinder, but application to two cylinders is also possible.
  • FIG. 39 shows a cross-sectional view of the compression mechanism portion of the rotary compressor 401.
  • FIG. 40 which is a plan view of the fixed cylinder 406
  • the inner wall surface 406b of the cylindrical space of the fixed cylinder is formed with a suction hole 406a into which a working gas flows and a constant lateral width that is opposed to a parallel plane.
  • the valve mounting chamber 406d in which the upper and lower surfaces in the height direction of the groove to be formed are closed with a front head and a rear head to form a prismatic cavity having a rectangular cross section, and discharged into the sealed container at the same height as the valve mounting chamber.
  • a valve storage chamber 406c formed by a mushroom-like cavity is formed which is combined with an outflow chamber 406e having a discharge hole communicating with the space.
  • FIG. 41 shows an enlarged view surrounded by an alternate long and short dash line in FIG. A valve including a flat gate valve S413, a partition plate 414, a stopper 415, and an elastic body such as a support spring 416 and an operation spring 417 between the member and the fixed cylinder 406, to which an L-shaped valve stabilization plate 420 is fixed.
  • the discharge mechanism D412 is configured by storing the mechanism body in the valve storage chamber 406c. The shape of the elements constituting the valve mechanism and the characteristic functions and operations of the discharge mechanism D will be described below.
  • FIG. 42 shows the shape of the flat gate valve S413
  • FIG. 43 shows an external perspective view of the valve stabilizing plate 420
  • FIG. 44 shows the shape of the partition plate 414
  • FIG. 45 shows the shape of the stopper 415.
  • FIG. 42 (a) is a front view
  • FIG. 42 (b) the right end of the tip 413a, which is formed in a substantially rectangular parallelepiped shape, is slidably in contact with the cylindrical surface 407a so as to seal between the compression chamber 411 and the outflow chamber 406e. It has an arc shape.
  • the left half of the tip portion is formed as a flat surface or an inclined surface so that the compression chamber pressure is always applied and the dead space is reduced by maintaining a floating state without sliding against the cylindrical surface 407a.
  • the dead space will increase.
  • the pressure pocket 413f is provided in the side wall seal surface 413c of the flat gate valve S that is in sliding contact with the side wall surface of the valve mounting chamber 406d on the compression chamber side, the contact area is reduced and the side wall seal surface is moved to the side wall seal surface. For the same pressing load, the surface pressure increases and the sealing performance is improved. Further, the central position where the compression chamber pressure acts on the side wall seal surface 413f is closer to the center on the back surface portion 413e side, and the inclination of the flat gate valve S is suppressed, so that a more stable operation can be secured.
  • a valve stabilizing plate 420 formed of an L-shaped thin plate as shown in an external perspective view of FIG. 43 is fixed by spot welding or the like.
  • the protruding pressure receiving portion 420a may be provided, so that it may be integrally formed with the flat gate valve S with a sintered alloy or a resin material.
  • the HL dimension and BL dimension in the figure will be described later.
  • a communication passage 413 h having one end opened to the side wall seal surface 413 c of the flat gate valve S and the other end opened to the lower portion of the pressure receiving portion 420 a of the valve stabilizing plate is the flat gate valve S.
  • An operating spring hole 413g is provided in the back surface portion 413e as necessary.
  • the shape of the partition plate 414 is shown in FIG. 44A, which is a rear view, and in FIG.
  • the shape of the tip portion 414a which is formed in a substantially rectangular parallelepiped as a whole, is an arc having a central convex shape as shown in FIG. 5 (b) with the aim of sealing the space between the suction chamber 410 and the outflow chamber 406e in sliding contact with the cylindrical outer surface 407a. is doing.
  • a pressure pocket similar to that of the flat gate valve S may be provided on the side wall seal surface 414b of the partition plate 414 that is in sliding contact with the side wall surface of the valve mounting chamber 406d.
  • the contact area is reduced, the surface pressure is increased for the same pressing load on the side wall seal surface, and the sealing performance is improved.
  • the center position where the outflow chamber pressure acts on the side wall seal surface 414b is closer to the center on the back surface portion 414e side, the inclination of the gate valve 414 is suppressed, and a more stable operation can be secured.
  • a side wall passage 414d serving as a working gas passage is provided between the square columnar valve support portions 414e provided on both sides, and the detour is formed by one step in the center of the surface.
  • a path 414g is provided.
  • the back surface portion 414c is provided with a spring hole 13e for an operating spring.
  • valve stabilizing plate 43 related to the shape of the valve stabilizing plate in FIG. 43 is set to be close to the valve support portion 414e of the partition plate shown in FIG. 44, and the BL size is on the side wall passage 414d side of the partition plate. The dimensions should be close enough not to touch the wall.
  • FIG. 45 (a) A front view of the stopper 415 attached to the outflow chamber 406e in FIG. 41 is shown in FIG. 45 (a), and a top view thereof is shown in FIG. ing.
  • the arc-shaped support end portions 415a at both ends are placed on arc portions provided at both ends of the outflow chamber 406e, and are supported and attached with a support spring 416 between the flat portion and the flat portion of the outflow chamber.
  • the spring hole 415b provided in the flat portion is a hole through which the operation spring 417 mounted between the rear portion of the partition plate or flat gate valve S and the flat portion of the outflow chamber is passed.
  • the front control head or the rear head is provided with a locking control chamber, a locking hole, a locking member, and the like that form the locking mechanism shown in FIG. It has the same configuration and function.
  • FIGS. 4A to 4D shown in FIG. 46 are views showing a state in which the cylindrical piston 407 rotates in synchronization with the drive shaft and the discharge mechanism D412 operates, and is described in the center. 0 °, 90 °, 180 °, and 270 ° represent rotation angles starting from FIG.
  • FIG. 5A shows a state where the cylindrical piston is closest to the partition plate 414 in the discharge mechanism D provided in the fixed cylinder 406, and shows a state where the cylindrical piston is slidably contacted with the center of the convex arc of the tip portion 414a.
  • the compression chamber 411 communicates with the suction chamber 410 and is in the same pressure state as the suction pressure.
  • the pressure pocket between the side wall surface of the valve mounting chamber 406d and the side wall seal surface 414b of the partition plate and the side wall seal surface 413c of the flat gate valve S increases the area of the suction chamber pressure or the compression chamber pressure. Each is pressed against the side wall surface of the valve mounting chamber from the differential pressure of the outflow chamber pressure and sealed.
  • the rotation of the cylindrical piston advances and passes through the suction hole 406a shown on the right side.
  • the compression chamber 411 becomes a sealed space and the compression of the working gas is started, but the pressure is still sucked. It is in a low pressure state close to the pressure. Therefore, the sliding contact portion of the partition plate tip with the cylindrical surface 407a moves to the suction chamber 410 side and the area where the low pressure acts is reduced, but an operating spring with a larger load acts from the outflow chamber side. Therefore, the sealing performance at the tip is ensured. Further, the sealing force of the side wall surface is the same as in FIG.
  • the load on the side wall seal surface of the partition plate is the same because the differential pressure is the same as in FIG. (A), except that the position of the center of action has moved to the suction chamber side.
  • the center of action exceeds the side wall surface and enters the suction chamber side, a moment around the K point, which is the end of the side wall seal surface, acts on the partition plate, and the partition plate tilts, causing problems in terms of performance and durability.
  • the discharge mechanism D is configured not to generate the moment due to the length of the side wall surface, the pressure pocket, or the like.
  • the region where the sliding contact portion of the tip portion with the cylindrical surface 407a moves to the compression chamber side and the compression chamber pressure acts is the same as in FIG. Even in the section where the outflow chamber pressure is higher than the compression chamber pressure, the sealing force at the tip is ensured. Further, the sealing force of the side wall seal surface is such that, in the region where the outflow chamber pressure is higher than the compression chamber pressure, the sealing state is continued by the differential pressure and the position of the center of action has moved to the compression chamber side. Since the length of the side wall surface and the pressure pocket are set so that the center of action does not exceed the side wall seal surface and enter the compression chamber side, the moment does not act on the flat plate gate valve S to tilt.
  • the center of the cylindrical surface 407a and the center of the tip of the flat plate gate valve S are made to coincide with each other, so that when the tip is seated on the cylindrical outer surface 407a, it flows out to the left flat portion 413b.
  • the working gas in the compression chamber is separated from the valve mounting chamber side wall surface through the communication passage 413h to the lower part of the valve stabilizing plate.
  • the flat gate valve S is pushed up to the outflow chamber side with a small differential pressure between the compression chamber pressure and the outflow chamber pressure, enters the discharge stroke, the compression chamber and the outflow chamber communicate with each other, and the working gas in the compression chamber flows out. It will flow out into the room.
  • the pressure-receiving part 420a of the valve stabilizer fixed to the side wall support surface of the flat gate valve S is a bypass 4 of the partition plate.
  • the working gas outlet passage 418 sandwiched between the valve support portions 414d below the lower end of 14f is disposed so as to be closed with a small gap.
  • the working gas flows into the tip 413a and the pressure at the tip is reduced by the amount of dynamic pressure.
  • the dynamic pressure accompanying the flow of the working gas acting on the valve stabilizer increases the push-up effect. It does not close under the influence of the part, and it becomes a stable movement without causing vibration.
  • the back surface portion collides with the stopper 415 and is seated, but the stopper is between the outflow chamber wall surface. Since the supporting spring is provided and elastically supported, the impact at the time of collision of the flat gate valve S is buffered, so that noise is not generated and members are not damaged.
  • the diagram returns to (a) and shows a state immediately after the end of the discharge stroke of the compression chamber.
  • the pressure in the compression chamber communicates with the suction chamber and becomes a low pressure state equal to the suction pressure. Therefore, the pressure at the lower end of the flat plate gate valve S and the pressure receiving portion of the valve stabilizer is lowered and the flat plate gate valve S is pushed down. Since the flat gate valve S is closed at once, there is no recompression loss in which the working gas flows backward.
  • one or a plurality of rolling elements 456 such as rolling bearings are mounted between the partition plate 454 and the side wall surface on the outflow chamber side of the valve mounting chamber 406d.
  • the rolling element 456 has a wheel portion mounted on the axle, and is disposed so that the wheel portion protrudes several tens to several hundreds of microns from the maximum width of the side wall support surface of the partition plate. It is configured to be rotatable between the wheel portions or between the axle and the partition plate.
  • FIG. 48 is a cross-sectional view of the scroll positive displacement compressor 501 of the fifteenth embodiment. Since the structure of the longitudinal sectional view is the same as that of FIG. 25 of the tenth embodiment, a detailed description thereof is omitted.
  • the fixed scroll is mounted on a frame (not shown) fixed in the sealed container 502 or fixed directly to the sealed container. That is, a rotating scroll (not shown) for preventing rotation is provided between the fixed cylinder 506 and the frame, that is, a rotating piston 507, and the lower part of the drive shaft supported at the center of the frame is directly connected to the motor. Has been.
  • FIG. 27 of the eleventh embodiment in which the shape of the swivel piston is basically the same and FIG. 50 which is a plan view of the fixed cylinder 506. Accordingly, the description of the configuration of the orbiting piston is omitted here, and FIG. 27 is used when necessary.
  • the shape of the fixed cylinder 506 shown in FIG. 50 is such that an envelope groove 506a having a rectangular cross section having a constant width obtained by using the envelope formed by the swiveling motion of the swiveling projection 507a is provided on one surface of the fixed end plate 506b having a thick plate thickness.
  • the working gas inflow chamber 506c is provided at one end on the outer peripheral side of the envelope groove 506a and the groove termination chamber 506j is provided at the other end on the inner peripheral side with the same bottom surface as the envelope groove 506a.
  • Each of 506j is provided with a suction hole 506d and a communication hole 506k communicating with the discharge space or suction passage.
  • valve mounting chamber 506g and the outflow chamber 506h provided at the back of the groove termination chamber 506j having the same bottom surface as the envelope groove at two locations opened on the inner and outer walls of the groove termination chamber 506j in FIG.
  • two valve storage chambers 506f are formed, and in each of the valve mounting chambers 506g, fine hole locking holes 506n are opened, and in the outflow chamber 506h, discharge holes 506e are opened.
  • the compression chamber is formed by loosely inserting the swiveling protrusions 507a and the circular arc protrusions 507c of the swiveling piston so as to engage with each other in the envelope groove 506a of the fixed cylinder, and the inner and outer wall surfaces of the protrusions and the inner and outer wall surfaces of the envelope groove 506a.
  • the outer compression chamber 510 and the inner compression chamber 511 are formed by closing the upper and lower sides of the space formed therebetween.
  • the turning piston is fixed by inserting the eccentric portion of the drive shaft for transmitting power into the turning bearing of the turning piston and providing a turning mechanism for preventing the turning piston from rotating. Swing motion with respect to the cylinder.
  • FIG. 48 shows a discharge mechanism E512 that causes the working gas to flow out from the compression chamber provided in the vicinity of the groove end chamber 506j, in which the envelope groove 506a is extended, as shown by an arrow 512 in FIG. 48 surrounded by a one-dot chain line.
  • FIG. 50 shows a partially enlarged view taken in the direction of arrow 512
  • FIG. 51 shows a cross-sectional view taken along line MNOP in FIG.
  • the configuration of the discharge mechanism E will be described below based on these drawings.
  • the structure of the discharge mechanism E512 is such that the valve storage chamber 506f for the outer compression chamber 510 and the valve storage chamber 506f for the inner compression chamber 511 are arranged symmetrically across the groove end chamber 506j in which the communication hole 506k opens and the linear protrusion 507c. Has been.
  • a flat plate gate valve R513 and a partition plate 515 are mounted as one set in the valve mounting chamber 506g for the outer compression chamber 510, and a flat plate gate valve L514 and a partition plate 516 are mounted as a set for the other inner compression chamber 511.
  • each outlet chamber 506h is provided with a stopper 516 and an elastic body such as a support spring 519 and an operating spring 520 as a set in each valve storage chamber 506f.
  • the support spring 519 elastically supports the stopper 518
  • the operation spring 520 is an elastic body that constantly presses the partition plate and the flat gate valve toward the linear protrusion 507c. If there is no hindrance, the operating spring for the flat gate valve can be omitted.
  • the shape of the flat gate valve R513 for the outer compression chamber is basically the same as that shown in FIG. 42 and the shape of the partition plate 515 as shown in FIG. However, the flat gate valve R and the shape of the tip of the partition plate are different.
  • the shape shown in FIG. 7 is applied to the tip of the flat projection 507c which is the seating surface of the flat gate valves R and L, and the tip of the straight projection 507c which is the seating surface of the partition plate is slidable.
  • a flat surface is applied to the part.
  • the fixed control cylinder which forms the locking mechanism shown in FIG. 6 of the first embodiment, a locking hole and a locking member, and an oil supply hole for supplying oil are provided in the fixed cylinder. It has configuration and function.
  • the volume of the inner and outer compression chambers whose one ends are closed by the flat gate valve R or L decreases, so that the working gas in the compression chamber is compressed and pressure Rises.
  • the tip portion of the flat gate valve R is in sliding contact with the side wall surface of the linear protrusion due to the swiveling movement of the linear protrusion 507c. Since the seal surface is in sliding contact with the side wall seal surface of the valve mounting chamber 506h, the compression of the working gas is continued in a state where the sealing performance between the compression chamber and the outflow chamber is ensured.
  • the pressure acting on the tip portion of the flat gate valve R becomes larger than the pressure in the outflow chamber, and the flat gate valve R flows out due to the differential pressure.
  • the tip portion is separated from the side wall surface of the linear protrusion, opens in the same direction as the linear protrusion movement direction, and the compressed working gas in the outer compression chamber flows out to the outflow chamber.
  • the valve stabilizing plate fixed to the side wall support surface of the flat gate valve R assists the opening operation of the flat gate valve R as described above. Therefore, the operability of the valve is good and the discharge stroke is small.
  • the outer compression chamber 510 Immediately after the discharge stroke of the outer compression chamber 510 ends, the outer compression chamber is switched to the compression chamber pressure in the low pressure state on the outside, so that the pressure at the lower end of the flat gate gate valve R and the pressure receiving portion of the valve stabilizing plate is reduced.
  • the force that pushes down the gate valve R acts and closes the straight protrusions instantly, so there is almost no recompression loss in which the working gas flows backward, and there is no impact due to the seating of the flat gate valve R. There is no problem.
  • the operation of the discharge mechanism E with respect to the inner compression chamber 511 is basically the same as that of the outer compression chamber 510, but the timing of the operation is shifted by about 180 °. This timing shift has the effect of reducing the torque fluctuation of the drive shaft, the pressure pulsation of the working gas, and the maximum flow velocity.
  • the operation of the discharge mechanism E at the start-up for the fifteenth embodiment is the same as the operation at the start-up using FIG. 6 of the first embodiment.
  • the operating principle of the locking mechanism is the same as that at the time of starting, and the pressure in the locking control chamber and the outflow chamber is equalized, so that the pin portion of the locking member becomes the locking hole of the flat gate valves R and L. It enters and the movement of the flat gate valves R and L stops.
  • piping connected to the discharge hole opened in the outflow chamber 506h The control valve provided in the middle is switched to change the communication space from the discharge side to the suction side.
  • the locking mechanism operates, that is, the pin portion of the locking member fits into the locking hole of the flat gate valve R, and the flat gate valve R stops, so that the working gas in the compression chamber returns to the inflow chamber.
  • the ring type, rotary type and scroll type positive displacement compressors used for air conditioning and refrigeration have been described as examples that can be used industrially.
  • the swing is a positive displacement compressor other than that.
  • Application to a compressor, a pump for air and a vacuum pump is possible.
  • Valve auxiliary material 411 ... Compression chambers 414, 515, 516 ... Partition plates 414a, 515a, 516a ... Tip 414b 515b, 516b ... Valve support portions 414c, 515c, 516c ... Side wall support surfaces 17, 119 ... Outflow passages 12, 92, 112, 152, 192 ... Discharge mechanism A 210 ... Valve seat 212 ... Discharge mechanism B 308 ... Round gate valve R 309 ... Circular gate valve L 407 ... Cylindrical piston 413 ... Flat gate valve S 312, 352... Discharge mechanism C 412: Discharge mechanism D 512: Discharge mechanism E

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Abstract

[Problem] To provide a displacement compressor that is provided with a discharge mechanism that is highly efficient and that greatly reduces factors that lower the efficiency of a compression mechanism unit, such as internal leakage of a working gas, excessive compression, recompression loss, and under-compression loss. [Solution] A discharge mechanism configured such that a vertical wall surface of a piston that turns or rotates configures a compression chamber and is used as a valve seat, a tip part of a plate valve, such as a flat-plate gate valve, is in sliding contact with the valve seat, the plate valve is fitted to a valve fitting chamber that is one part of a valve housing chamber that opens at one end into the compression chamber, which is formed in a fixed cylinder, and the plate valve is actuated by an elastic body, etc. or pressure that is introduced into the valve housing chamber and that acts on the plate valve.

Description

容積型圧縮機の吐出機構Displacement mechanism of positive displacement compressor
本発明は、冷凍空調用機器などに用いられる円弧曲線の垂直な側壁面で圧縮室が形成されるローリングピストン式やスクロール式を含む旋回ピストン式ないしは揺動式のような容積型圧縮機に適用されている圧縮室内の作動ガスを圧縮し流出させるための吐出機構を備えた容積型圧縮機に関する。 The present invention is applied to a positive displacement compressor such as a rotary piston type or a swing type including a rolling piston type and a scroll type in which a compression chamber is formed by a vertical side wall surface of a circular arc curve used in a refrigeration and air conditioning apparatus or the like. The present invention relates to a positive displacement compressor including a discharge mechanism for compressing and flowing out working gas in a compression chamber.
冷凍空調機器製品は空調機や冷凍・冷蔵庫用機器として広く普及している。それらの大半は、容積形圧縮機を用いて冷媒を低圧から高圧へと圧縮することによる冷媒の状態変化を利用して居住空間の冷房、暖房ないしは食物の冷蔵・冷凍を行っている。それらの機器で消費される電力の大半は搭載されている圧縮機で消費される。 Refrigeration and air conditioning equipment products are widely used as air conditioners and refrigeration / refrigerator equipment. Most of them use the displacement compressor to cool the living space, heat, or refrigerate / freeze the food using the change in the state of the refrigerant by compressing the refrigerant from low pressure to high pressure. Most of the power consumed by these devices is consumed by the installed compressor.
前記容積形圧縮機の効率を低下させる主な要因として、吐出室から圧縮室ないしは圧縮室から低圧空間である吸入室への作動ガスの漏れ、吐出通路抵抗の大きさ、吐出室に作動ガスが流出する前に圧縮室圧力が吐出圧力より上昇する過圧縮現象、さらには吐出弁の手前にある死空間からの高圧ガスの圧縮室への逆流による再圧縮損失や吐出圧力まで上昇する手前で吐出室が連通して吐出ガスが圧縮室へ逆流する圧縮不足損失などが挙げられる。 The main factors for reducing the efficiency of the positive displacement compressor are leakage of working gas from the discharge chamber to the compression chamber or from the compression chamber to the suction chamber, which is a low pressure space, the magnitude of the discharge passage resistance, and the working gas from the discharge chamber. Over-compression phenomenon in which the pressure in the compression chamber rises above the discharge pressure before flowing out, and discharge before the rise to the recompression loss or discharge pressure due to the reverse flow of high-pressure gas from the dead space before the discharge valve to the compression chamber For example, there is insufficient compression loss in which the chamber communicates and the discharge gas flows backward to the compression chamber.
このような機器で省エネルギー化を図る上で該圧縮機の高効率化は効果的である。加えて、当該製品の使用環境が厳しく圧縮機の寿命でおよそ製品寿命が決定されるので該圧縮機の耐久性は重要となる。 In order to save energy with such a device, increasing the efficiency of the compressor is effective. In addition, since the use environment of the product is severe and the product life is determined by the life of the compressor, the durability of the compressor is important.
従来の旋回駆動のリング式容積形圧縮機に於いて、圧縮室を構成する旋回リングの内外壁面にブレードを設け、作動ガスを圧縮して高圧ガスを流出させる通路とリード弁で構成された吐出機構が固定シリンダに設けられている。（例えば、特許文献１参照。） In a conventional rotary displacement ring-type compressor, blades are provided on the inner and outer wall surfaces of the swirl ring that constitutes the compression chamber, and the discharge is composed of a passage that compresses the working gas and flows out the high-pressure gas, and a reed valve. A mechanism is provided in the fixed cylinder. (For example, refer to Patent Document 1.)
吐出機構が圧縮機の効率を低下させる要因である前記作動ガスの漏れ、過圧縮現象、再圧縮損失、圧縮不足損失等が大きく関わっている。（例えば、特許文献２参照。） The leakage of the working gas, the over-compression phenomenon, the re-compression loss, the under-compression loss, and the like, which are factors that cause the discharge mechanism to reduce the efficiency of the compressor, are greatly involved. (For example, see Patent Document 2.)
従来の冷凍空調用機器に用いられる容積型ロータリ圧縮機の多くに適用されている吐出機構は、シリンダに設けた吐出孔の出口に前後の圧力差で開閉する薄板状のリード弁を装着して構成されている（例えば、特許文献３および特許文献４参照。）。 The discharge mechanism applied to many positive displacement rotary compressors used in conventional refrigeration and air conditioning equipment is equipped with a thin plate-like reed valve that opens and closes due to the pressure difference between the front and rear at the outlet of the discharge hole provided in the cylinder. (For example, refer patent document 3 and patent document 4.).
また、従来の容積型ロータリ圧縮機に適用された吐出機構には、低圧室と圧縮室を仕切るブレードの先端部に設けた突起を作動ガスの吐出行程時にシリンダに設けた吐出孔内に突入させて死空間の容積を減少させる構成もみられた（例えば、特許文献３参照。）。 Also, in a discharge mechanism applied to a conventional positive displacement rotary compressor, a protrusion provided at the tip of a blade that partitions the low pressure chamber and the compression chamber is inserted into a discharge hole provided in the cylinder during the discharge stroke of the working gas. In some cases, the volume of the dead space is reduced (see, for example, Patent Document 3).
また、従来の円筒状のローラを内装した容積型ロータリ圧縮機の吸入室と圧縮室間を仕切る板状のブレードのフロントヘッド壁面上を摺動する端面に設けたフック係止部に起動時吸入側と吐出側の圧力差がない状態の時に、フロントヘッドに装着されたフックが該フック係止部に突出して該ブレードの動きを止めて、吸入室と圧縮室間を開口状態にすることで圧縮しなくするとともに運転の継続に伴う前記圧力差が一定値を超えることで該フックがフック係止部から離脱して該ブレードが該ローラ上に当り吸入室と圧縮室を仕切り圧縮される構成となっていた（例えば、特許文献５参照。）。 Also, the suction at the time of start-up is applied to a hook engaging portion provided on an end surface sliding on the front head wall surface of a plate-like blade for partitioning between the suction chamber and the compression chamber of a conventional positive displacement rotary compressor equipped with a cylindrical roller. When there is no pressure difference between the suction side and the discharge side, the hook attached to the front head protrudes into the hook locking portion to stop the movement of the blade, and the suction chamber and the compression chamber are opened. A configuration in which the hook is detached from the hook engaging portion when the pressure difference with the continuation of operation exceeds a certain value without being compressed, and the blade hits the roller and partitions and compresses the suction chamber and the compression chamber (For example, refer to Patent Document 5).
また、前記容積型ロータリ圧縮機の吸入室と圧縮室間を仕切るブレードを隣接させて２枚設けるとともに該２枚のブレードをピストン側に押付ける該ブレード背面側空間の圧力を該２枚のブレードで仕切られた低圧室と圧縮室の中間圧力となるように構成されていた（
例えば、特許文献４参照。）。 In addition, two blades are provided adjacent to each other to separate the suction chamber and the compression chamber of the positive displacement rotary compressor, and the pressure in the blade rear side space that presses the two blades toward the piston is applied to the two blades. It was configured to be an intermediate pressure between the low-pressure chamber and the compression chamber partitioned by (
For example, see Patent Document 4. ).
また、容積型スクロール圧縮機に適用された旋回ピストンのラップ巻き始め中央部の一部を分離し旋回ピストン本体と独立した動きを可能として固定シリンダの包絡溝内壁に一定区間摺接するように構成されていた（例えば、特許文献６参照。）。 Also, a part of the wrap winding start center part of the orbiting piston applied to the positive displacement scroll compressor is separated so as to be able to move independently of the orbiting piston main body and to be in sliding contact with the inner wall of the fixed cylinder for a certain section. (For example, refer to Patent Document 6).
また、別の容積型スクロール圧縮機の例では、渦巻き形状で形成される圧縮室を形成するラップ巻き始め中央部の一部を分離するとともに弁押えと固定用と回転用ピンおよび支持バネで構成されたラップ弁を用いた機構があった（例えば、特許文献７参照。） Further, in another example of the positive displacement scroll compressor, a part of the central part of the wrap winding forming a compression chamber formed in a spiral shape is separated, and it is constituted by a valve presser, a fixing, a rotating pin, and a supporting spring. There has been a mechanism using a wrap valve (see, for example, Patent Document 7).
また、旋回ピストンと固定シリンダで圧縮機構部が構成された容積型スクロール圧縮機に適用された吐出機構では、固定シリンダ中央部のラップ内に固定シリンダの渦巻き壁中央に設けた円筒空間に旋回ピストンの動きに連動して円筒状の吐出弁が回転して圧縮室空間と吐出室が開閉する構成となっていた（例えば、特許文献８参照。）。 Moreover, in the discharge mechanism applied to the positive displacement scroll compressor in which the compression mechanism part is constituted by the orbiting piston and the fixed cylinder, the orbiting piston is provided in the cylindrical space provided in the center of the spiral wall of the fixed cylinder in the wrap at the center of the fixed cylinder. The cylindrical discharge valve is rotated in conjunction with the movement of the cylinder and the compression chamber space and the discharge chamber are opened and closed (see, for example, Patent Document 8).
特開Ｈ０６－２８８３５８号公報JP H06-288358 A 特開２０１１－２１４５０６号公報JP 2011-214506 A 特開平０５－０７１４８５号公報Japanese Patent Laid-Open No. 05-071485 特開平０５－０７９４８０号公報Japanese Patent Application Laid-Open No. 05-0779480 特開平０５－１０６５７６号公報JP 05-106576 A 特開平０８－１７０５９３号公報Japanese Patent Laid-Open No. 08-170593 特開２０００－３１４３８４号公報JP 2000-314384 A 特開２００５－２６４８２７号公報JP 2005-264827 A
以下、先行技術文献により従来の圧縮機構部に設けられた吐出機構ないしは吐出機構に隣接して設けられ吸入室と圧縮室を仕切るブレードと係わる課題について説明する。 Hereinafter, problems related to a discharge mechanism provided in a conventional compression mechanism unit or a blade provided adjacent to the discharge mechanism and partitioning the suction chamber and the compression chamber will be described according to prior art documents.
該吐出機構が圧縮機の効率を低下させる要因である前記作動ガスの吐出側からの漏れ、圧縮室内の圧力が吐出圧力よりも大きく上昇する過圧縮現象、圧縮された作動ガスが死空間に滞留した後圧縮室内に逆流する再圧縮損失、圧縮室内の圧力が吐出圧力に達する前に吐出側と連通する圧縮不足損失等が大きく関わっている。 Leakage from the discharge side of the working gas, which is a factor that reduces the efficiency of the compressor by the discharge mechanism, an overcompression phenomenon in which the pressure in the compression chamber rises higher than the discharge pressure, and the compressed working gas stays in the dead space Then, the recompression loss that flows back into the compression chamber, the undercompression loss that communicates with the discharge side before the pressure in the compression chamber reaches the discharge pressure, and the like are greatly related.
内部ポケット（リング状の溝）内に環状リングを装着して該リングの内外に圧縮室を形成し、オルダムリングで前記環状ピストンに内外ブレード押付けた状態で旋回運動をさせて圧縮室と吸入側の空間（流入室）は羽根板（ブレード）を挟んで隣接しているとともにシリンダに設けた排出口から排出バルブ（リード弁）を介して冷媒（作動ガス）が排出される特許文献１記載の構成では、排出口が死空間となり再圧縮損失が発生する問題、圧縮室と前期流入室を仕切る羽根板の先端や上下端面の隙間から吸入室に作動ガスが漏れる問題、加えて羽根板先端シール部がリング状にあることからシール幅が狭くなる線接触シールとなるのでシール性が低下する問題があった。 An annular ring is mounted in the inner pocket (ring-shaped groove) to form a compression chamber inside and outside the ring, and the Oldham ring is swung to the compression piston and suction side while pressing the inner and outer blades against the annular piston. The space (inflow chamber) is adjacent to the blade plate (blade), and refrigerant (working gas) is discharged from a discharge port provided in the cylinder through a discharge valve (reed valve). In the configuration, the discharge port becomes a dead space and recompression loss occurs, the working gas leaks into the suction chamber from the tip of the blade plate and the gap between the upper and lower end surfaces that partition the compression chamber and the previous inflow chamber, and the blade tip seal Since the portion is in the shape of a ring, there is a problem that the sealing performance is lowered because the line contact seal becomes narrower.
さらには、前記吐出機構に用いられている薄板状のリード弁はシール性に加えて弾性機能も必要とされるので板厚を厚くできなくて強度が低く信頼性に問題があった。 Furthermore, since the thin plate-like reed valve used in the discharge mechanism requires an elastic function in addition to the sealing property, the plate thickness cannot be increased, and the strength is low and there is a problem in reliability.
当該構成の圧縮機では加工上必要となる排出口と羽根板間および吸入口と羽根板間は作動ガスの流れに利用されることはないので前者を第一無効空間、後者を第二無効空間と呼ぶ
と、第一無効空間のガスは排出されないで残るので吹き溜まり状態となって体積した異物が羽根板の摺動面に進入して損傷する問題や第二無効空間では容積が急激に膨張して真空状態によるキャビテーションが発生して羽根板の摺動面が損傷する問題があった。 In the compressor having the above configuration, the former invalid space is used for the former, and the second invalid space is used for the latter because it is not used for the flow of working gas between the discharge port and the blade plate and between the suction port and the blade plate, which are necessary for processing. In this case, the gas in the first invalid space remains without being discharged, so that the volume of foreign matter enters into the sliding surface of the blades and becomes damaged, or the volume rapidly expands in the second invalid space. As a result, cavitation due to vacuum occurred and the sliding surface of the blades was damaged.
次に、リング状の溝を有するシリンダの一箇所に設けた該溝を仕切るブレードを両側から挟むように設けた揺動ブッシュに装着したリング状のピストンで形成される内外圧縮室の作動ガスを流出させるシリンダに設けた吐出口とその出口に装着した吐出弁で吐出機構が構成される特許文献２の記載では、該吐出口が死空間となり再圧縮損失が生じて効率が低下する問題と揺動ブッシュ前後の隙間は内外圧縮室に連通しているので内部漏れが発生して効率が低下する問題があった。 Next, the working gas in the inner and outer compression chambers formed by the ring-shaped pistons attached to the swing bushes provided so as to sandwich the blades partitioning the grooves provided at one location of the cylinder having the ring-shaped grooves from both sides. In the description of Patent Document 2 in which a discharge mechanism is configured by a discharge port provided in a cylinder to be discharged and a discharge valve mounted at the outlet thereof, the discharge port becomes a dead space and recompression loss occurs, resulting in a decrease in efficiency. Since the gap before and after the dynamic bush communicates with the inner and outer compression chambers, there is a problem in that internal leakage occurs and efficiency decreases.
圧縮室からの作動ガスを流出させる吐出孔に薄板状のリード弁を装着した特許文献３ないしは特許文献４記載の構成では、吐出行程終了直後に死空間となる吐出孔に残留する高圧ガスの低圧となった圧縮室への逆流による再圧縮損失が増大することおよびリード弁の流出側空間の吐出圧力よりも低い圧縮室の圧力状態では剛性の低いリード弁の変形によりシール部からの漏れが増大し効率が大幅に低下する問題があった。 In the configuration described in Patent Document 3 or Patent Document 4 in which a thin plate-like reed valve is attached to the discharge hole through which the working gas flows out from the compression chamber, the low pressure of the high-pressure gas remaining in the discharge hole that becomes a dead space immediately after the end of the discharge stroke Increased recompression loss due to back flow into the compression chamber and increased leakage from the seal due to deformation of the reed valve with low rigidity in the compression chamber pressure state lower than the discharge pressure of the reed valve outflow side space However, there is a problem that the efficiency is greatly reduced.
加えて、前記吐出機構に用いられている薄板状のリード弁はシール性に加えて弾性機能も必要とされ板厚を厚くできず強度が低く開口時の弁受けとしてのリテーナ衝突時や逆圧時および自励振動によるリード弁の疲労破損さらには騒音が増大する問題があった。 In addition, the thin reed valve used in the discharge mechanism requires an elastic function in addition to the sealing property, and the plate thickness cannot be increased and the strength is low. There was a problem that the reed valve was damaged due to time and self-excited vibration, and the noise increased.
上記死空間となる吐出孔にブレード先端に設けた突起を圧縮行程から吐出行程に掛けて突入させて該死空間の容積を減らす特許文献３記載構成では、吐出孔内の作動ガスの流出面積が減少して流出抵抗の増大による過圧縮現象増大に加えて吐出行程終了直後の吐出孔内から該突起が離脱を開始する瞬間、吐出孔内の圧力が急激に低下してブレードがロック状態となりブレード先端部がピストン壁面から離脱して吸入室と圧縮室が連通して作動ガスが吸入室へ漏れて効率が大きく低下する問題があった。 In the configuration described in Patent Document 3 in which the protrusion provided at the blade tip is inserted into the discharge hole serving as the dead space from the compression stroke to the discharge stroke to reduce the volume of the dead space, the outflow area of the working gas in the discharge hole is reduced. In addition to increasing the overcompression phenomenon due to increased outflow resistance, at the moment when the protrusion starts to detach from the discharge hole immediately after the end of the discharge stroke, the pressure in the discharge hole suddenly drops and the blade becomes locked and the tip of the blade There is a problem in that the efficiency is greatly reduced because the suction part and the compression chamber communicate with each other and the working gas leaks to the suction chamber.
次に、吸入室と圧縮室間を仕切る板状のブレードのフック係止部にフックを掛けて起動時や容量制御時にブレードの動きを係止させて吸入室と圧縮室を連通させる特許文献５記載構成では、圧縮室が液体で満たされた状態で起動すると液体は圧縮室内を回転するのみであるが、ブレードを係止したフックが外れてブレードが吸入室と圧縮室を仕切った瞬間に圧縮室内で液圧縮による異常高圧が発生し圧縮機が破損する問題あった。また、通常の運転から容量制御運転に移行すると、ブレードの動きが係止されて吸入室と圧縮室を連通させると吐出通路内の吐出圧力と圧縮室内の吸入圧力との差圧で吐出弁ないしはブレード部での漏れが発生して性能が低下する問題があった。 Next, a hook is hooked on a hook engaging portion of a plate-like blade that partitions the suction chamber and the compression chamber, and the movement of the blade is locked at the time of start-up or capacity control so that the suction chamber communicates with the compression chamber. In the described configuration, when the compression chamber is started in a state where it is filled with liquid, the liquid only rotates in the compression chamber, but it is compressed at the moment when the hook that holds the blade is released and the blade partitions the suction chamber and the compression chamber. There was a problem that the compressor was damaged due to abnormally high pressure caused by liquid compression in the room. Also, when shifting from the normal operation to the capacity control operation, when the movement of the blade is locked and the suction chamber and the compression chamber are communicated with each other, the pressure difference between the discharge pressure in the discharge passage and the suction pressure in the compression chamber is used. There was a problem that leakage occurred at the blade part and the performance deteriorated.
また、従来の容積型ロータリ圧縮機の吸入室と圧縮室間を仕切るブレードを２枚設けたブレード間の空間を吸入室圧力と圧縮室圧力の中間圧力に保持する特許文献６記載構成では、該中間圧力がブレード上下端面の微小隙間からの作動ガスの漏れを前提としているが、該漏れ量は微小隙間の大きさのバラツキや油によるシール状況にブレードの動作により変動するので該中間圧力を制御できない問題や制御できないことによるブレード動作や中間圧力の不安定な状況から圧縮機の特性全体が不安定な挙動を繰り返す問題があった。 Further, in the configuration described in Patent Document 6 in which the space between the blades provided with two blades separating the suction chamber and the compression chamber of the conventional positive displacement rotary compressor is held at an intermediate pressure between the suction chamber pressure and the compression chamber pressure, The intermediate pressure is based on the premise that the working gas leaks from the minute gaps on the upper and lower ends of the blade. However, the amount of leakage varies depending on the variation in the size of the minute gaps and the sealing situation due to oil, so the intermediate pressure is controlled. There was a problem that the entire characteristics of the compressor repeated unstable behavior due to problems that could not be controlled and blade operation due to inability to control and intermediate pressure unstable conditions.
また、容積型スクロール圧縮機を構成する旋回ピストン巻き始めラップの先端部に設けた溝内に圧縮室間を仕切るシール部材を挿着した特許文献６記載の構成では、該シール部材に差圧で動作する弁機能はないので圧力変動には対応できず圧縮不良としての過圧縮動力や圧縮不足動力の軽減はできず、設計点以外での効率向上に効果がない問題があった。さらに、該シール部材の厚さをラップよりも大きくできず、該シール部材の側壁面前後に作用する圧縮室圧力の差圧力とそれに伴うモーメントにより破損する問題があった。 Moreover, in the structure of patent document 6 which inserted the sealing member which partitions off between compression chambers in the groove | channel provided in the front-end | tip part of the revolving piston winding start lap which comprises a positive displacement scroll compressor, it is a pressure difference to this sealing member. Since there is no valve function to operate, pressure fluctuation cannot be dealt with, and over-compression power and under-compression power as compression failure cannot be reduced, and there is a problem that efficiency is not improved except for the design point. Further, the thickness of the seal member cannot be made larger than that of the wrap, and there is a problem that the seal member is damaged due to the differential pressure of the compression chamber pressure acting before and after the side wall surface of the seal member and the accompanying moment.
渦巻き形状で形成される圧縮室を形成するラップ巻き始め中央部の一部を分離するとともに弁押えと固定用と回転用ピンおよび支持バネで構成されたラップ弁による特許文献７記載の吐出機構では、ラップ弁、渦巻き状突起および弁押え間のシールは微小隙間とラップ厚さで規制された小さな円弧間で行っていることからシール性が悪く圧縮室間の漏れが増大し大きく効率を低下させる問題があった。 In the discharge mechanism described in Patent Document 7, a part of the central part of the wrap winding that forms a compression chamber formed in a spiral shape is separated and a wrap valve composed of a valve presser, a fixing pin, a rotating pin and a support spring is used. The seal between the wrap valve, spiral projection and valve presser is done between a small arc regulated by a small gap and lap thickness, resulting in poor sealing performance and increased leakage between compression chambers, greatly reducing efficiency. There was a problem.
また、ラップ弁内外側壁間の差圧で作用する大きな荷重はラップ弁を支持する該渦巻き状突起厚さ以下の径の複数のピンで支えているので強度不足による破損問題や変形によりラップ弁と渦巻き状突起間の隙間が拡大して漏れが増大し効率が低下する問題があった。 In addition, since a large load acting on the pressure difference between the inner and outer walls of the wrap valve is supported by a plurality of pins with a diameter less than the thickness of the spiral protrusion supporting the wrap valve, There was a problem that the gap between the spiral projections was enlarged, the leakage increased, and the efficiency was lowered.
さらには、ラップ弁の上下端面の一方は設置されたスクロール部材の底面上を摺動し他方の面は相手のスクロール部材上を摺動するので該上下端面の摺動摩擦抵抗の差によりラップ弁に捩りモーメントが作用して上下面で抉り破損する問題があった。 Furthermore, one of the upper and lower end surfaces of the lap valve slides on the bottom surface of the installed scroll member, and the other surface slides on the other scroll member. There was a problem that the torsional moment was applied and the top and bottom surfaces were damaged.
また、固定シリンダの渦巻き壁中央に設けた円筒空間に円筒状の吐出弁を装着した吐出機構を設けた特許文献８記載の構成では、弁体の回転角に従い弁口が開閉するが基本的に弁前後の差圧で動作する機構ではないので、冷凍空調機器には一般的な吸入圧力と吐出圧力の関係が変化するような製品に於いては、圧力変化に追従できなくて過圧縮や圧縮不足などの圧縮不良が発生して効率を低下させる問題があった。 Further, in the configuration described in Patent Document 8 in which a discharge mechanism in which a cylindrical discharge valve is mounted in a cylindrical space provided in the center of the spiral wall of the fixed cylinder is provided, the valve port basically opens and closes according to the rotation angle of the valve body. Since it is not a mechanism that operates with the differential pressure before and after the valve, it is not possible to follow the pressure change in products that change the relationship between the suction pressure and the discharge pressure, which is common for refrigeration and air conditioning equipment. There has been a problem in that compression failure such as shortage occurs and efficiency is lowered.
本発明は、従来の吐出機構により圧縮機の効率を低下させる要因となっている圧縮機構部での作動ガスの漏れ、過圧縮現象、再圧縮損失および圧縮不足損失等を無くすか大きく減じて高効率化を図ると同時に弁部の強度及び動作性を高めて高い信頼性と低騒音化を図った吐出機構を備えた圧縮機を提供することを目的とする。 The present invention eliminates or greatly reduces the leakage of working gas, over-compression phenomenon, re-compression loss, under-compression loss, etc. in the compression mechanism that is a factor that reduces the efficiency of the compressor by the conventional discharge mechanism. It aims at providing the compressor provided with the discharge mechanism which aimed at high efficiency, and improved the intensity | strength and operativity of a valve part, and aimed at high reliability and noise reduction.
さらには、起動時の信頼性向上と圧縮室内の作動ガスを吸入側にバイパスさせる容量制御機能を有する吐出機構を備えた容積型圧縮機を提供することを目的とする。 Furthermore, it aims at providing the positive displacement compressor provided with the discharge mechanism which has the capacity | capacitance control function which improves the reliability at the time of starting, and bypasses the working gas in a compression chamber to the suction side.
請求項１記載の発明は、密閉容器などに固定された内側に円弧状の垂直壁面を有する固定構成部材に支承されて回転する駆動軸の偏心軸部に円弧状の垂直壁面を有する可動機構部材を装着して円弧状の垂直面で形成される三日月状の柱状空間の上下に平坦面を有する平坦端板で挟み込んで形成される圧縮室の一端に該可動機構部材の回転運動ないしは旋回運動により圧縮室空間を減少させて作動ガスを圧縮し流出させる吐出機構を設ける。 According to the first aspect of the present invention, there is provided a movable mechanism member having an arcuate vertical wall surface at an eccentric shaft portion of a drive shaft that is supported by a fixed component member having an arcuate vertical wall surface fixed to an airtight container or the like. Is attached to one end of a compression chamber formed by sandwiching a flat end plate having a flat surface above and below a crescent-shaped columnar space formed by an arcuate vertical surface by rotational movement or swiveling movement of the movable mechanism member. A discharge mechanism for reducing the compression chamber space and compressing and discharging the working gas is provided.
該吐出機構を装着した容積型圧縮機に於いて、該固定構成部材の該圧縮室を形成する垂直壁面に平行で同一高さのおよそ断面矩形で該圧縮室垂直壁面に開口する弁装着室とその反対側に背面室を設けて構成される弁収納室内に該圧縮室を形成する該可動機構部材の垂直壁面を弁座として先端部が密着できる形状を有する断面矩形の板状弁体を装着し、上下端面と該平坦端板間は微小隙間を介して摺接し該弁収納室の圧縮室側の垂直壁面と板状弁体の壁面間も摺接する構成とし、該板状弁体の支持部材や板状弁体周囲のシール部材および板状弁体の一端に装着されるバネのような弾性体などを含めた補機部材で構成される弁機構体を該弁収納室内に装着して構成された吐出機構を備えたことを特徴とする容積型圧縮機である。 In a positive displacement compressor equipped with the discharge mechanism, a valve mounting chamber having an approximately rectangular cross section of the same height and parallel to the vertical wall surface forming the compression chamber of the fixed component and opening to the vertical wall surface of the compression chamber; A plate-shaped valve body with a rectangular cross section having a shape that allows the tip portion to be in close contact with the vertical wall surface of the movable mechanism member forming the compression chamber as a valve seat in a valve storage chamber configured by providing a back chamber on the opposite side The upper and lower end surfaces and the flat end plate are in sliding contact with each other through a minute gap, and the vertical wall surface on the compression chamber side of the valve storage chamber and the wall surface of the plate valve body are also in sliding contact with each other. A valve mechanism comprising an auxiliary member including a member, a sealing member around the plate-shaped valve body, and an elastic body such as a spring mounted on one end of the plate-shaped valve body is mounted in the valve storage chamber. It is a positive displacement compressor provided with the constituted discharge mechanism.
この発明によれば、該固定構成部材に設けた弁収納室に板状弁体と補機部材で構成される弁機構体を収納するとともに該板状弁体の先端部を可動機構部材の円弧状の垂直壁面に摺接させて構成される吐出機構を圧縮室に隣接して配置することができる。このような構成から吐出行程の最終段階で残存する圧縮室空間である死空間を小さくできることや流出通
路が短くできることさらには吐出弁を剛性の高い板状弁体で形成することができる。 According to this invention, the valve mechanism composed of the plate-like valve body and the auxiliary machine member is housed in the valve housing chamber provided in the fixed component member, and the tip of the plate-like valve body is placed on the circle of the movable mechanism member. A discharge mechanism configured to be in sliding contact with the arcuate vertical wall surface can be disposed adjacent to the compression chamber. With this configuration, the dead space, which is the compression chamber space remaining in the final stage of the discharge stroke, can be reduced, the outflow passage can be shortened, and the discharge valve can be formed of a highly rigid plate-shaped valve element.
請求項２に記載の発明は、圧縮室に隣接する前記弁装着室の側壁面ないしはその側壁面に面接触する前記板状弁体の側壁面の何れかに該側壁面より一段凹ました周囲の境界線が前記背面室に連通しない空間である圧力ポケットを形成し、該圧縮室と該圧力ポケットを連通する通路を該板状弁体ないしは該弁収納室の側壁面に設けて構成した吐出機構を備えたことを特徴とする請求項１記載の容積型圧縮機である。 According to a second aspect of the present invention, the side wall surface of the valve mounting chamber adjacent to the compression chamber or the side wall surface of the plate-like valve body in surface contact with the side wall surface is recessed by one step from the side wall surface. A discharge mechanism in which a pressure pocket which is a space where a boundary line does not communicate with the back chamber is formed, and a passage communicating the compression chamber and the pressure pocket is provided on a side wall surface of the plate-like valve body or the valve storage chamber The positive displacement compressor according to claim 1, further comprising:
この発明によれば、該板状弁体と該弁装着室の側壁面間の摺動面積が減少するとともに該圧力ポケットに圧縮室圧力が導入されて該側壁面間が離反されることにより該該板状弁体の動作性が向上することになる。 According to the present invention, the sliding area between the plate-like valve body and the side wall surface of the valve mounting chamber is reduced, and the compression chamber pressure is introduced into the pressure pocket to separate the side wall surfaces. The operability of the plate-like valve body is improved.
請求項３に記載の発明は、前記固定構成部材に設けた吐出ガスから分離された油を溜める貯油池ないしは密閉容器の下部に設けた油槽に一端を開口し他端を前記平坦端板の弁装着室内に開口する注油孔と前記板状弁体の上端面に設けた油受孔と導入溝および先端部の先端油溝それぞれの孔や溝と間欠的に連通させて該貯油池ないしは該密閉容器内の油を該板状弁体の先端油溝に導くように構成された吐出機構を備えたことを特徴とする請求項１ないしは２記載の容積型圧縮機である。 According to a third aspect of the present invention, one end is opened in an oil tank provided in a lower part of an oil reservoir or a sealed container for storing oil separated from discharge gas provided in the fixed component, and the other end is a valve of the flat end plate. An oil filling hole that opens into the mounting chamber, an oil receiving hole provided in the upper end surface of the plate-like valve body, an introduction groove, and a hole and groove in the tip oil groove at the tip are intermittently communicated with the oil reservoir or the seal. 3. The positive displacement compressor according to claim 1, further comprising a discharge mechanism configured to guide oil in the container to a tip oil groove of the plate-like valve body.
この発明によれば、該板状弁体の先端部が間欠的に摺接している該可動機構部材の弁座との間に先端油溝から密閉容器内の潤滑油を差圧により供給して微小隙間部のシールや摺動部の潤滑に用いることができる。 According to this invention, the lubricating oil in the hermetic container is supplied by the differential pressure from the oil groove at the front end to the valve seat of the movable mechanism member in which the front end of the plate-like valve body is in sliding contact with the intermittently. It can be used to seal minute gaps and lubricate sliding parts.
請求項４に記載の発明は、前記固定構成部材ないしは前記弁収納室の弁装着室を形成する材料と前記板状弁体に用いる材料の線膨張係数をおよそ同一で構成した吐出機構を備えたことを特徴とする請求項１乃至３の何れかに記載の容積型圧縮機である。 According to a fourth aspect of the present invention, there is provided a discharge mechanism in which the linear expansion coefficient of the material forming the fixed component member or the valve mounting chamber of the valve storage chamber and the material used for the plate-like valve body is approximately the same. The positive displacement compressor according to any one of claims 1 to 3.
この発明によれば、該板状弁体の周囲と該弁装着室の上下端面や側壁間には作動流体の漏れや摺動性を考慮して微小な隙間が確保されている。この隙間は圧縮機内部で大きな温度の変動が生じても該隙間が関係する部材の線膨張係数が同一で構成されているので該隙間が変動することはない。 According to this invention, a minute gap is secured between the periphery of the plate-shaped valve body and the upper and lower end surfaces and side walls of the valve mounting chamber in consideration of leakage of the working fluid and slidability. Even if a large temperature fluctuation occurs inside the compressor, the gap does not change because the linear expansion coefficient of the member related to the gap is the same.
請求項５に記載の発明は、前記の固定構成部材と可動機構部材との間に設けた自転を阻止し公転運動をさせる旋回機構により前記偏心軸の偏心量を公転半径とする旋回運動を行う可動機構部材としての旋回ピストンに前記弁座を駆動軸の軸線に平行な垂直壁面で形成するとともに該旋回ピストンの圧縮室を形成する駆動軸の軸線に平行な壁面の包絡線となる壁面を有する前記固定構成部材を固定シリンダとして構成した吐出機構を備えたことを特徴とする請求項１乃至４の何れかに記載の容積型圧縮機である。 According to a fifth aspect of the present invention, a turning motion is provided in which the amount of eccentricity of the eccentric shaft is a revolution radius by a turning mechanism that prevents rotation and makes a revolving motion provided between the fixed component member and the movable mechanism member. The valve seat is formed on a swing piston as a movable mechanism member with a vertical wall surface parallel to the axis of the drive shaft, and has a wall surface serving as an envelope of the wall parallel to the axis of the drive shaft forming the compression chamber of the swing piston. The positive displacement compressor according to any one of claims 1 to 4, further comprising a discharge mechanism in which the fixed component member is configured as a fixed cylinder.
この発明によれば、旋回機構を用いて該旋回ピストンを自転のない公転運動をさせることができることから該可動機構部材の速度を小さくできることと該固定シリンダの圧縮室の壁面を包絡溝で形成することができる。 According to the present invention, the revolving motion of the revolving piston without rotation can be achieved by using the revolving mechanism, so that the speed of the movable mechanism member can be reduced and the wall surface of the compression chamber of the fixed cylinder is formed by the envelope groove. be able to.
請求項６に記載の発明は、矩形断面の帯状板を曲げて円筒状に形成した円弧突起の一端に前記旋回半径の倍以上の長さの直線で平坦面の平坦弁座を直線突起として延接した旋回突起をおよそ円形板の旋回ディスクの片面側に直立させて旋回ピストンを形成する。 According to a sixth aspect of the present invention, a flat valve seat having a flat surface with a straight line having a length more than twice the turning radius is extended as a straight protrusion at one end of an arc protrusion formed by bending a belt-like plate having a rectangular cross section into a cylindrical shape. A swiveling piston is formed by allowing the swiveling protrusions in contact with each other to stand upright on one side of a swirling disk of a circular plate.
該旋回突起の旋回運動から形成される円弧状と直線状の包絡溝の一端に設けた直線状の平行壁面を有する流出室に一端が開口して該包絡溝と同一底面を有し該直線突起を挟んで対向して配置された２箇所の弁装着室を設けて固定シリンダが形成される。該直線突起であ
る該平坦弁座を挟んで対向する2箇所の該弁収納室の弁装着室内に装着し該板状弁体の先端部を該直線突起に当接させて構成した吐出機構を備えたことを特徴とする請求項５記載の容積型圧縮機である。 One end of an outflow chamber having a straight parallel wall surface provided at one end of an arcuate and straight envelope groove formed by the swiveling motion of the swivel protrusion and having the same bottom surface as the envelope groove, the linear protrusion A fixed cylinder is formed by providing two valve mounting chambers that are arranged opposite to each other. A discharge mechanism which is mounted in the valve mounting chambers of the two valve storage chambers facing each other across the flat valve seat which is the linear protrusion, and is configured such that the tip of the plate-like valve body abuts on the linear protrusion. The positive displacement compressor according to claim 5, wherein the positive displacement compressor is provided.
この発明によれば、該固定構成部材や該可動機構部材の１例としての固定シリンダおよび旋回ピストンの具体的な構成やこれの吐出機構に用いる本発明の一つの特徴でもある該板状弁体先端部の具体的な構成が示されている。 According to the present invention, the plate-like valve body which is also one of the features of the present invention used in the specific configuration of the fixed cylinder and the swing piston as an example of the fixed component member and the movable mechanism member and the discharge mechanism thereof A specific configuration of the tip is shown.
請求項７に記載の発明は、前記円弧突起を１周以下の円形状に曲げて円筒状にした一端に前記直線突起を設けた旋回突起を旋回ディスクに直立させて旋回ピストンを形成する。
そして、前記包絡溝を厚い端板に凹設した一端に設けた流入室と他端となる直線状の平行溝である流出室それぞれに吸入孔と吐出孔を設けた固定シリンダの該直線突起を挟んで対称に配置した前記弁収納室に板状弁体と補助部材で構成される弁機構体を装着した上で該包絡溝内に該旋回突起を遊挿して構成した吐出機構を備えたことを特徴とする請求項６記載の容積型圧縮機である。 According to a seventh aspect of the present invention, a turning piston is formed by bending the circular protrusion into a circular shape having one round or less to form a cylindrical shape, and the turning protrusion provided with the linear protrusion on the end is brought upright on a turning disk.
Then, the linear protrusions of the fixed cylinder provided with suction holes and discharge holes in the inflow chamber provided at one end where the envelope groove is recessed in the thick end plate and the outflow chamber which is a linear parallel groove as the other end are provided. The valve storage chamber arranged symmetrically across the valve is provided with a discharge mechanism configured by loosely inserting the swiveling protrusion into the envelope groove after mounting a valve mechanism composed of a plate-shaped valve body and an auxiliary member. The positive displacement compressor according to claim 6.
この発明によれば、作動ガスを圧縮する圧縮室の側壁面は、該旋回突起とその包絡溝および該板状弁体の側壁面で形成され、旋回ピストンの直線突起を固定シリンダの流出室内での旋回運動を可能とすることにより該弁収納室の2箇所の弁装着室に収納した内外圧縮室用の板状弁体の先端部を直線突起側壁面に摺接可能とするとともに背面室にバネなどの補助部材を収納して機能的な吐出機構が構成されている。 According to the present invention, the side wall surface of the compression chamber for compressing the working gas is formed by the swiveling protrusion, its envelope groove, and the side wall surface of the plate-like valve body, and the straight protrusion of the swiveling piston is placed in the outflow chamber of the fixed cylinder. The tip of the plate-like valve element for the inner and outer compression chambers housed in the two valve mounting chambers of the valve storage chamber can be slidably contacted with the straight protrusion side wall surface and the back chamber. A functional discharge mechanism is configured by housing auxiliary members such as springs.
請求項８に記載の発明は、断面矩形の帯状板を渦巻き状に曲げて形成した渦巻き突起の内側終端部から接線方向に前記偏心軸の偏心量に相当する旋回半径の倍以上の長さで延設した直線突起を該渦巻き突起と一体に形成した旋回突起を旋回ディスクに直立させて旋回ピストンを形成する。 The invention according to claim 8 is a length more than twice the turning radius corresponding to the eccentric amount of the eccentric shaft in a tangential direction from the inner terminal portion of the spiral protrusion formed by bending a belt-shaped plate having a rectangular cross section. A swiveling projection, which is formed by extending a straight protrusion extending integrally with the spiral protrusion, is erected on a swiveling disk to form a swiveling piston.
その旋回突起の旋回運動で形成される厚い端板に凹設した包絡溝の外側端部を流入室とし内側端部の直線状溝を流出室としたそれぞれに吸入孔と吐出孔を設け、該流出室の両側に線対称的に弁収納室を設けた固定シリンダとそれぞれの該旋回突起と該包絡溝を噛み合わせて圧縮室を形成した上で各弁収納室に前記板状弁体と補助部材で構成した弁機構体を装着した吐出機構を備えたことを特徴とする請求項６記載の容積型圧縮機である。 A suction hole and a discharge hole are provided in each of the outer end portion of the envelope groove recessed in the thick end plate formed by the swiveling motion of the swirling protrusion and the linear groove at the inner end portion as the outflow chamber, A compression cylinder is formed by meshing a fixed cylinder having valve storage chambers symmetrically on both sides of the outflow chamber and the respective swiveling projections and the envelope groove, and then the plate-like valve body and the auxiliary in each valve storage chamber 7. The positive displacement compressor according to claim 6, further comprising a discharge mechanism equipped with a valve mechanism composed of a member.
この発明によれば、旋回突起を渦巻き形状で形成した該旋回ピストンとその旋回突起の包絡溝で形成した該固定シリンダとで圧縮室が形成された該弁装着室と背面室で形成される弁収納室に先端部を圧縮室圧力が作用する形状にした板状弁体およびそれらの背面側にバネ等補助部材で構成した弁機構体により機能的な吐出機構が構成される。 According to the present invention, the valve formed by the valve mounting chamber and the back chamber in which the compression chamber is formed by the swiveling piston in which the swirling protrusion is formed in a spiral shape and the fixed cylinder formed by the envelope groove of the swirling protrusion. A functional discharge mechanism is constituted by a plate-like valve body whose tip is shaped so that the compression chamber pressure acts on the storage chamber and a valve mechanism body constituted by an auxiliary member such as a spring on the back side thereof.
請求項９に記載の発明は、前記旋回突起の渦巻き突起に前記流入室側のインボリュート曲線を適用した外渦巻き突起の内側には同一接線で接続した曲率がより小さいインボリュート曲線ないしは円弧曲線で形成した内渦巻き突起の内側を接線方向に延長した前記直線突起で接続することで２種類の曲線と１つの直線で旋回突起を形成した旋回ピストンと前記固定シリンダと弁機構体で構成した吐出機構を備えたことを特徴とする請求項８記載の容積型圧縮機である。 According to the ninth aspect of the present invention, an involute curve or an arc curve having a smaller curvature connected on the same tangent line is formed on the inner side of the outer spiral protrusion obtained by applying the involute curve on the inflow chamber side to the spiral protrusion of the swirl protrusion. The inner spiral protrusion is connected by the linear protrusion extending in the tangential direction, thereby providing a discharge piston configured by two types of curves, a swing piston that forms a swing protrusion with one straight line, the fixed cylinder, and a valve mechanism body. The positive displacement compressor according to claim 8, wherein the positive displacement compressor is provided.
この発明によれば、前記旋回ピストンの渦巻き突起を２種類の曲線で形成することにより直線状溝の流出室を含めて前記固定シリンダ中央部の空間を有効に利用できるので十分な大きさを確保して機能が十分に発揮できる吐出機構が構成できる。 According to the present invention, by forming the spiral projection of the swivel piston with two kinds of curves, the space in the center of the fixed cylinder including the outflow chamber of the linear groove can be used effectively, so that a sufficient size is secured. Thus, a discharge mechanism that can sufficiently function can be configured.
請求項１０に記載の発明は、前記包絡溝の終端に設けた前記流出室側壁面に該包絡溝と同
一高さで奥に向けて平行壁面の断面矩形の空間で形成される弁装着室とその奥に設けた背面室から形成される弁収納室を設けるとともに該背面室と吐出空間内とを連通する圧導入孔を設けた固定シリンダとする。 According to a tenth aspect of the present invention, there is provided a valve mounting chamber formed on a side wall surface of the outflow chamber provided at a terminal end of the envelope groove and having a rectangular cross-sectional space with a parallel wall surface at the same height as the envelope groove. A fixed cylinder is provided with a valve storage chamber formed from a back chamber provided in the back and a pressure introducing hole for communicating the back chamber with the inside of the discharge space.
この固定シリンダの弁装着室側壁面におよそ直方体の板状弁体を該弁装着室に収納するとともに該背面室内の該板状弁体と該固定シリンダ間にバネ等の弾性体とそれを支える部材である補機部材から構成される弁機構体として該弁収納室に収納することで該板状弁体を該弁装着室の側壁面に沿って摺接可能に装着して構成した吐出機構を備えたことを特徴とする請求項５乃至９の何れかに記載の容積型圧縮機である。 An approximately rectangular plate-like valve body is accommodated in the valve mounting chamber side wall surface of the fixed cylinder in the valve mounting chamber, and an elastic body such as a spring and the like are supported between the plate valve body in the rear chamber and the fixed cylinder. A discharge mechanism constructed by mounting the plate-like valve body in a slidable manner along the side wall surface of the valve mounting chamber by storing it in the valve storage chamber as a valve mechanism body composed of an auxiliary member which is a member. The positive displacement compressor according to claim 5, wherein the positive displacement compressor is provided.
この発明によれば、該板状弁体を直方体で形成できることから該吐出機構の構成を簡素にでき、該板状弁体の周囲のシール性や動作性が良好となる。 According to this invention, since the plate-shaped valve body can be formed as a rectangular parallelepiped, the configuration of the discharge mechanism can be simplified, and the sealing performance and operability around the plate-shaped valve body are improved.
請求項１１に記載の発明は、前記弁装着室の矩形溝上下面を塞ぐ固定部材に形成した円筒空間の平坦面の一端に設けた低圧通路に連通する低圧導入孔と他端側に設けた該弁装着室内に連通する連通孔から形成された係止制御室が設けられている。 The invention according to claim 11 is provided with a low pressure introduction hole that communicates with a low pressure passage provided at one end of a flat surface of a cylindrical space formed in a fixing member that closes the upper and lower surfaces of the rectangular groove of the valve mounting chamber and the other end side. A locking control chamber formed from a communication hole communicating with the valve mounting chamber is provided.
そして、大径の円筒部と小径のピン部の2段円筒で形成された係止部材の内側空洞部にバネなどの弾性体を装着して該係止制御室に収納するとともに前記板状弁体の先端部が圧縮室内より内側の該弁収納室内に収納された状態で固定部材面上を摺動する上下端面ないしは側壁シール面の内何れか一箇所に該係止部材のピン部が遊挿可能な位置に係止穴を設けた板状弁体で構成された吐出機構を備えたことを特徴とする請求項１０記載の容積型圧縮機である。 An elastic body such as a spring is attached to the inner cavity of the locking member formed of a two-stage cylinder having a large-diameter cylindrical portion and a small-diameter pin portion, and is stored in the locking control chamber. The pin portion of the locking member is allowed to play at any one of the upper and lower end surfaces or the side wall seal surface that slides on the fixed member surface in a state where the front end portion of the body is stored in the valve storage chamber inside the compression chamber. 11. The positive displacement compressor according to claim 10, further comprising a discharge mechanism including a plate-like valve body provided with a locking hole at an insertable position.
この発明によれば、該空洞部に装着されたバネ力が該係止部材の前後に作用する制御差圧による荷重よりも大きい場合、例えば圧縮機の停止時等では該係止部材のピン部が該板状弁体の係止穴に挿入された状態にあるので、該板状弁体が係止されて移動することはない。この状態での該板状弁体先端部と平坦座面である旋回ピストンの直線突起との間は最大旋回半径の２倍の大きな隙間が保持された状態となっている。しかし、該制御差圧が該バネ力よりも大きくなると該係止部材のピン部が該板状弁体の係止穴から離脱して該板状弁体が動作可能な状態となる。 According to this invention, when the spring force attached to the cavity is larger than the load due to the control differential pressure acting before and after the locking member, for example, when the compressor is stopped, the pin portion of the locking member Is inserted into the locking hole of the plate-like valve body, the plate-like valve body is locked and does not move. In this state, a large gap twice as large as the maximum turning radius is maintained between the tip of the plate-like valve body and the linear protrusion of the turning piston, which is a flat seat. However, when the control differential pressure becomes larger than the spring force, the pin portion of the locking member is detached from the locking hole of the plate-like valve body, and the plate-like valve body becomes operable.
請求項１２に記載の発明は、前記弁装着室底面に平行でおよそ同一平面形状となるように複数に分割して形成した積層構造の板状弁体を該弁装着室内に収納して構成された吐出機構を備えたことを特徴とする請求項１０ないしは１１記載の容積型圧縮機である。 The invention according to a twelfth aspect is configured by accommodating a plate-shaped valve body having a laminated structure formed by being divided into a plurality of pieces so as to be parallel to the bottom surface of the valve mounting chamber and approximately in the same plane, in the valve mounting chamber. 12. The positive displacement compressor according to claim 10, further comprising a discharge mechanism.
この発明によれば、前記旋回ピストンの直線突起である平坦弁座の垂直壁面の高さ方向に沿って前記板状弁体を複数に分割して構成することにより、該直線突起が前後の圧力差ないしは温度で変形した場合に、その変形に応じて該板状弁体が追従するので、該先端部全体の摺接が維持されることになる。 According to this invention, the plate-like valve element is divided into a plurality of parts along the height direction of the vertical wall surface of the flat valve seat, which is the linear protrusion of the orbiting piston, so that the linear protrusion is When the plate-like valve body is deformed due to the difference or temperature, the sliding contact of the entire tip is maintained because the plate-like valve body follows the deformation.
請求項１３に記載の発明は、前記板状弁体をおよそ直方体の平板ゲート弁で形成した先端部の流出室側に該弁板厚の1／２以下の一定幅で前記平坦弁座に摺接する平坦シール面を設けるとともに圧縮室側には該平坦弁座に対して隙間を設けた該平坦シール面より凹ました傾斜面ないしは段差を設けて先端部に受圧面を形成した平板ゲート弁を圧縮室側の側壁面に開口する前記弁装着室に該平板ゲート弁の前後側壁面と上下端面の4面との間に微小隙間を設けるとともに該弁装着室の該側壁面に往復摺動が可能に装着して構成された吐出機構を備えたことを特徴とする請求項１０乃至１２の何れかに記載の容積型圧縮機である。 According to a thirteenth aspect of the present invention, the plate-like valve body is slid onto the flat valve seat at a constant width equal to or less than ½ of the valve plate thickness on the outflow chamber side of the tip formed by a rectangular parallelepiped flat gate valve. A flat gate surface that is in contact with the flat valve seat that has a pressure receiving surface at the tip by providing an inclined surface or step that is recessed from the flat seal surface with a gap to the flat valve seat is provided on the compression chamber side. In the valve mounting chamber that opens to the side wall surface on the chamber side, a minute gap is provided between the front and rear side wall surfaces of the flat gate valve and the four surfaces of the upper and lower end surfaces, and reciprocating sliding is possible on the side wall surface of the valve mounting chamber. The positive displacement compressor according to any one of claims 10 to 12, further comprising a discharge mechanism that is mounted on the compressor.
この発明によれば、該平板ゲート弁先端部の平坦シール面が着座する該平坦弁座も平面なので面シールを確保した状態で摺接することになる。また、該平板ゲート弁の圧縮室圧力に対する動作性向上の観点から、該平板ゲート弁先端部の圧縮室側には該平坦弁座との間に隙間を設けた受圧面に圧縮室圧力が背面室に向けて作用するように構成されている。 According to the present invention, since the flat valve seat on which the flat seal surface of the flat gate gate valve is seated is also flat, it comes into sliding contact with the surface seal secured. In addition, from the viewpoint of improving the operability of the flat gate valve with respect to the compression chamber pressure, the compression chamber pressure is on the back side of the pressure receiving surface provided with a gap between the flat gate seat on the compression chamber side of the flat gate gate tip. It is configured to act toward the chamber.
請求項１４に記載の発明は、前記平板ゲート弁先端部のおよそ中央部に該側壁面高さの１／２以下の幅でおよそ中央部に前記平坦シール面から圧縮室側に向けて開口する数十度に傾斜させた風圧受面を設けて構成された吐出機構を備えたことを特徴とする請求項１３記載の容積型圧縮機である。 In the invention according to claim 14, the flat gate valve opens from the flat sealing surface toward the compression chamber side at the central portion with a width equal to or less than ½ of the side wall surface height at the central portion of the flat gate valve tip. 14. The positive displacement compressor according to claim 13, further comprising a discharge mechanism having a wind pressure receiving surface inclined at several tens of degrees.
この発明によれば、該平板ゲート弁先端部の圧縮室側には該平坦シール面より低くして隙間を設けた受圧面に加えて圧縮室側に部分的に傾斜面で開口させた風圧受面を先端部に設けることにより、該平板ゲート弁の開口力と安定性に対する動作性が向上する。 According to this invention, in addition to the pressure receiving surface that is lower than the flat seal surface and provided with a gap at the compression chamber side at the tip of the flat gate valve, the wind pressure receiving portion that is partially opened at the inclined surface on the compression chamber side. By providing the surface at the tip, the operability for the opening force and stability of the flat gate valve is improved.
請求項１５に記載の発明は、前記弁装着室の平行溝の幅を前記平板ゲート弁の厚さよりも大きく形成した上で、その差に相当する板厚のおよそ直方体の弁補助材を該弁装着室内に該平板ゲート弁と並置し、該弁補助材の先端部側に圧縮室側と流出室側を連通する開口部を設け先端部を前記旋回ピストン直線突起の前記平坦弁座に摺接させるとともに該平板ゲート弁と該弁補助材が互いに独立して動作するように構成された吐出機構を備えたことを特徴とする請求項１３ないしは１４記載の容積型圧縮機である。 In the invention according to claim 15, the width of the parallel groove of the valve mounting chamber is formed larger than the thickness of the flat gate valve, and a substantially rectangular parallelepiped valve auxiliary material corresponding to the difference is provided in the valve. The mounting gate is juxtaposed with the flat gate valve, and an opening is provided on the distal end side of the valve auxiliary member to communicate the compression chamber side and the outflow chamber side. The distal end is slidably contacted with the flat valve seat of the revolving piston linear protrusion. 15. The positive displacement compressor according to claim 13, further comprising a discharge mechanism configured such that the flat gate valve and the valve auxiliary member operate independently of each other.
この発明によれば、該平板ゲート弁と形状の弁補助材を一組にして該弁装着室内に装着することにより、弁動作の安定性が高められるとともに該弁の動作性を向上するための付加機能を弁補助材に設けることもできる。また、該弁装着室の幅を調整する領域が広がり該包絡溝と同じ幅にすることも可能となる。 According to the present invention, by mounting the flat gate valve and the valve auxiliary material having a shape as a set in the valve mounting chamber, the stability of the valve operation is improved and the operability of the valve is improved. Additional functions can also be provided in the valve aid. In addition, a region for adjusting the width of the valve mounting chamber is widened, and the same width as the envelope groove can be obtained.
請求項１６に記載の発明は、前記弁装着室内に前記平板ゲート弁の背面室側端面の高さ方向の一定幅を庇のように前記流出室側に張り出した拘止部を設けて並置した前記弁補助材にその厚さよりも大きく且つ該弁装着室の幅から該平板ゲート弁の厚さを引いた値よりも僅かに小さい直径を有する転がり軸受などの転動体を該弁装着室と該平板ゲート弁の側壁面間上で転動可能な状態で該弁補助材に１個ないしは複数個装着して構成された吐出機構を備えたことを特徴とする請求項１５記載の容積型圧縮機である。 According to a sixteenth aspect of the present invention, there is provided a detent portion in which a fixed width in the height direction of the rear chamber side end surface of the flat gate valve is provided in the valve mounting chamber so as to protrude toward the outflow chamber side like a ridge. A rolling element such as a rolling bearing having a diameter that is larger than the thickness of the valve auxiliary member and slightly smaller than a value obtained by subtracting the thickness of the flat gate valve from the width of the valve mounting chamber is provided with the valve mounting chamber and the valve mounting chamber. 16. The positive displacement compressor according to claim 15, further comprising a discharge mechanism configured such that one or more valve auxiliary members are mounted so as to be able to roll between side wall surfaces of the flat gate valve. It is.
この発明によれば、圧縮室圧力が流出室圧力より上昇してその差圧により該平板ゲート弁が流出室側に押されると弁補助材に装着した該転動体が該平板ゲート弁と該弁装着室側壁間に挟み込まれることなる。その時該旋回ピストンの直線突起である平坦弁座が背面室側に移動している場合には、その移動速度に倍化した速度が転動体から該平板ゲート弁に付加されて該平板ゲート弁を背面室側に押し上げることになる。吐出行程が終了して該平板ゲート弁が背面室内の圧力やバネ力等で該直線突起側に押されるときには、拘止部に押されて弁補助材も同時に押されて該直線突起側壁面に着座することになる。 According to this invention, when the compression chamber pressure rises above the outflow chamber pressure and the flat gate valve is pushed to the outflow chamber due to the differential pressure, the rolling elements attached to the valve auxiliary member are connected to the flat gate valve and the valve. It will be sandwiched between the side walls of the mounting chamber. At that time, when the flat valve seat, which is a linear protrusion of the swivel piston, moves to the back chamber side, the speed doubled to the moving speed is added from the rolling element to the flat gate valve, and the flat gate valve is It will be pushed up to the back room side. When the discharge stroke is completed and the flat gate valve is pushed to the linear protrusion side by the pressure or spring force in the back chamber, it is pushed by the restraining portion and the valve auxiliary material is pushed at the same time on the side wall surface of the linear protrusion. Will sit down.
請求項１７に記載の発明は、旋回ピストンの前記直線突起に面接触する前記平板ゲート弁先端部の平坦シール面との隙間の関係を維持した上で該直線突起と前記包絡溝の流出室側終端部の平行溝に対する前記弁装着室の包絡溝側の側壁面取り付け角度を垂直面から数度前後の角度を傾斜させて設けるとともに該平板ゲート弁先端部と側壁面の相対角度も同様に合わせた形状で構成された吐出機構を備えたことを特徴とする請求項１３ないしは１４記載の容積型圧縮機である。 According to the seventeenth aspect of the present invention, the relationship between the linear protrusion and the flat seal surface of the flat-plate gate valve tip portion that is in surface contact with the linear protrusion of the orbiting piston is maintained, and the linear protrusion and the outflow chamber side of the envelope groove are maintained. The mounting angle of the side wall surface on the envelope groove side of the valve mounting chamber with respect to the parallel groove at the end portion is inclined by about several degrees from the vertical surface, and the relative angle between the flat plate gate valve tip and the side wall surface is similarly adjusted. 15. The positive displacement compressor according to claim 13, further comprising a discharge mechanism configured in a different shape.
この発明によれば、該平板ゲート弁の先端部を該直線突起から離反させて背面室へ向けて押し上げて先端部を開口させる力として先端部と背面室間の差圧に加えて該平板ゲート弁
を傾斜させることにより側壁支持面に作用する差圧による力を利用することができる。該直線突起に対する該平板ゲート弁側壁支持面となす角度を背面部を流出室側に倒して直角より小さくすると先端部の押上げ力は減少するが側壁面の荷重の押上げ力となる分力が発生して傾斜角に応じて増加する。逆に上記側壁支持面となす角度を大きくするとその力関係は逆となる。従って、状況に応じて傾斜方式を選択すればよいことになる。 According to this invention, in addition to the pressure difference between the front end portion and the back chamber, the flat plate gate as a force for opening the front end portion by pushing the front end portion of the flat gate valve away from the linear protrusion and pushing it toward the back chamber. By tilting the valve, the force due to the differential pressure acting on the side wall support surface can be used. If the angle formed with the flat plate gate valve side wall support surface with respect to the straight protrusion is made smaller than a right angle by tilting the back surface portion toward the outflow chamber, the pushing force at the tip portion decreases, but the component force that becomes the pushing force of the load on the side wall surface Occurs and increases according to the tilt angle. Conversely, when the angle formed with the side wall support surface is increased, the force relationship is reversed. Therefore, the tilt method may be selected according to the situation.
請求項１８に記載の発明は、前記平板ゲート弁先端部を前記直線突起に摺接可能とし、該平板ゲート弁側壁支持面側のおよそ中央部から先端部に向けて掘り下げた凹溝内に設けた圧縮室側に連通する吐出孔を塞ぐようにリード弁とそれの背面で変形を支えるリテーナを装着して構成された吐出機構を備えたことを特徴とする請求項１３ないしは１４記載の容積型圧縮機である。 According to an eighteenth aspect of the present invention, the front end portion of the flat gate valve can be slidably contacted with the linear protrusion, and is provided in a concave groove that is dug down from approximately the center portion toward the front end portion on the side of the flat plate gate valve side wall. 15. The positive displacement type according to claim 13, further comprising: a discharge mechanism comprising a reed valve and a retainer for supporting deformation at the back of the reed valve so as to close the discharge hole communicating with the compression chamber side. It is a compressor.
この発明によれば、従来から用いられているリード弁を該平板ゲート弁に装着することにより弁の前後差圧で容易に動作して圧縮ガスを流出させることができる。また、従来の固定シリンダに装着する場合と比べて小さな部材である平板ゲート弁に装着するので、材料選択の自由度が広がるのと加工性が良好となる。 According to the present invention, by attaching a reed valve used conventionally to the flat gate valve, the compressed gas can flow out easily by operating with the differential pressure across the valve. In addition, since it is mounted on a flat gate valve, which is a small member, compared to the case where it is mounted on a conventional fixed cylinder, the workability is improved as the degree of freedom of material selection increases.
請求項１９に記載の発明は、前記固定シリンダの包絡溝と同じ幅と高さの平行溝で形成される弁装着室が該包絡溝に開口する反対側に両端部を該包絡溝と同じ幅の円弧形状とした背面室を形成し、該弁装着室の溝幅が該平板ゲート弁の厚さよりも大きい場合、その差に相当する幅の直方体のサイドスペーサを該包絡溝内に突出しないように該弁装着室の流出室側側壁面に密着させて固定シリンダに繋止して構成された吐出機構を備えたことを特徴とする請求項１３乃至１８の何れかに記載の容積型圧縮機である。 The invention according to claim 19 is characterized in that the valve mounting chamber formed of a parallel groove having the same width and height as the envelope groove of the fixed cylinder has both ends on the opposite side of the envelope groove and the same width as the envelope groove. When the groove width of the valve mounting chamber is larger than the thickness of the flat gate valve, a rectangular parallelepiped side spacer corresponding to the difference is not projected into the envelope groove. The positive displacement compressor according to any one of claims 13 to 18, further comprising a discharge mechanism configured to be in close contact with the side wall surface of the outflow chamber of the valve mounting chamber and fixed to a fixed cylinder. It is.
この発明によれば、固定シリンダに形成する包絡溝と同じカッターを用いてその一端に形成する流出室に弁収納室を形成する弁装着室および背面室を加工することができる。 According to the present invention, it is possible to process the valve mounting chamber and the back chamber that form the valve storage chamber in the outflow chamber formed at one end thereof using the same cutter as the envelope groove formed in the fixed cylinder.
請求項２０に記載の発明は、前記弁装着室流出室側の側壁面を側壁シール面とし旋回突起の前記旋回突起に摺接する先端部を設けた前記平板ゲート弁と同じ高さのおよそ直方体の仕切板を該平板ゲート弁とで１セットにして対向する2箇所の該弁装着室内に装着するとともに該平板ゲート弁と該仕切板との間に設けた互いの側壁面を支える弁支持部を設けた間にはそれら先端部から背面室側に抜ける流出通路を設けている。さらにはその背面室の固定シリンダとの間に必要に応じてバネなどの弾性体を組み付けて構成した弁機構体を装着して構成される吐出機構を備えたことを特徴とする請求項１３乃至１９の何れかに記載の容積型圧縮機である。 The invention according to claim 20 is a substantially rectangular parallelepiped having the same height as the flat gate valve provided with a side wall seal surface on the outflow chamber side of the valve mounting chamber and provided with a tip end portion that is in sliding contact with the swiveling protrusion. A valve support for supporting the side wall surfaces provided between the flat gate valve and the partition plate and mounted in the two valve mounting chambers facing each other with the flat plate gate valve as a set. While being provided, an outflow passage is provided through the front end portion to the back chamber side. 14. A discharge mechanism comprising: a valve mechanism configured by assembling an elastic body such as a spring, if necessary, between a fixed cylinder in the back chamber; and The positive displacement compressor according to any one of 19.
この発明によれば、該平板ゲート弁と形状の弁補助材を一組にして該弁装着室内に装着することにより、該平板ゲート弁が包絡溝内を大きく突出した状態でもその裏面側で該弁補助材が支えているので、動作の安定性が高められるとともに該弁の動作性を向上するための付加機能を弁補助材に設けることもできる。また、該弁装着室の幅を調整する領域が広がり該包絡溝と同じにすることも可能となる。 According to the present invention, the flat gate valve and the shape of the valve auxiliary material are mounted in the valve mounting chamber as a set, so that the flat gate valve protrudes greatly in the envelope groove on the back side thereof. Since the valve auxiliary material supports it, the operation stability can be improved and an additional function for improving the operability of the valve can be provided in the valve auxiliary material. In addition, a region for adjusting the width of the valve mounting chamber can be expanded to be the same as the envelope groove.
請求項２１に記載の発明は、前記平板ゲート弁側の側壁面の一部を凹まして前記流出通路を広げて迂回路を設けた仕切板と組み合わせる前記平板ゲート弁側壁支持面から該仕切板側に向け垂直に延びた矩形平板の弁安定板を該平板ゲート弁の側壁支持面上で一体固定するとともに該弁安定板と先端部との間に一端が開口し他端が前記弁装着室に摺接する側壁シール面に開口する連通孔を設けた平板ゲート弁を装着して吐出機構を構成したことを特徴とする請求項２０記載の容積型圧縮機である。 The invention according to claim 21 is characterized in that a part of the side wall surface on the side of the flat plate gate valve is recessed to widen the outflow passage and is combined with a partition plate provided with a detour, from the flat plate gate valve side wall support surface to the side of the partition plate. A rectangular flat valve stabilization plate extending vertically toward the side is integrally fixed on the side wall support surface of the flat gate valve, and one end is opened between the valve stabilization plate and the tip, and the other end is in the valve mounting chamber. 21. The positive displacement compressor according to claim 20, wherein a discharge mechanism is configured by mounting a flat gate valve provided with a communication hole opened in a side wall seal surface in sliding contact.
この発明によれば、圧縮室圧力が流出室圧力より上昇してその差圧により該平板ゲート弁
が流出室側に押されて弁装着室側壁面と該側壁シール面間に隙間が生じると該連通孔から圧縮室圧力が該弁安定板下部に流入して先端部に流入した圧力とともに該平板ゲート弁を背面室側に押上げることになる。その後、該平板ゲート弁先端部が該直線突起から離脱してガス通路が開口して圧縮ガスが流入するとその流体圧力が該弁安定板に作用して背面室側にさらに押付けて該平板ゲート弁の開口状態を安定的に保持することになる。 According to the present invention, when the compression chamber pressure rises above the outflow chamber pressure and the flat gate valve is pushed toward the outflow chamber by the differential pressure, a gap is generated between the valve mounting chamber side wall surface and the side wall seal surface. The compression gate pressure flows into the lower part of the valve stabilizing plate from the communication hole and, together with the pressure flowing into the tip, pushes up the flat gate valve toward the back chamber. Thereafter, when the tip of the flat gate valve is detached from the linear protrusion and the gas passage is opened and compressed gas flows in, the fluid pressure acts on the valve stabilizing plate and further presses it toward the back chamber side, and the flat gate valve Thus, the open state is stably maintained.
請求項２２に記載の発明は、前記弁装着室内に前記平板ゲート弁と並置した前記仕切板にその厚さよりも大きく且つ該弁装着室の幅から該平板ゲート弁の厚さを引いた値よりも僅かに小さい直径を有する転がり軸受などの転動体を該弁装着室と該平板ゲート弁の側壁面間上で転動可能な状態で該仕切板に１個ないしは複数個装着して構成された吐出機構を備えたことを特徴とする請求項２０記載の容積型圧縮機である。 The invention according to claim 22 is based on a value obtained by subtracting the thickness of the flat gate valve from the width of the valve mounting chamber, which is larger than the thickness of the partition plate juxtaposed with the flat gate valve in the valve mounting chamber. One or more rolling elements such as rolling bearings having a slightly smaller diameter are mounted on the partition plate in a state where the rolling elements can roll between the valve mounting chamber and the side wall surface of the flat gate valve. 21. The positive displacement compressor according to claim 20, further comprising a discharge mechanism.
この発明によれば、圧縮室圧力が流出室圧力より上昇してその差圧により該平板ゲート弁が流出室側に押されると該仕切板に装着した該転動体が該平板ゲート弁と該弁装着室側壁間に挟み込まれることなる。その時該旋回ピストンの直線突起である平坦弁座が背面室側に移動している場合には、その移動速度に倍化した速度が転動体から該平板ゲート弁に付加されて該平板ゲート弁を背面室側に瞬時に押し上げることになる。 According to this invention, when the compression chamber pressure rises above the outflow chamber pressure and the flat gate valve is pushed to the outflow chamber side by the differential pressure, the rolling elements attached to the partition plate are connected to the flat gate valve and the valve. It will be sandwiched between the side walls of the mounting chamber. At that time, when the flat valve seat, which is a linear protrusion of the swivel piston, moves to the back chamber side, the speed doubled to the moving speed is added from the rolling element to the flat gate valve, and the flat gate valve is It will push up to the back room side instantly.
請求項２３に記載の発明は、前記固定シリンダ包絡溝の終端部である流出室と同一底面で該包絡溝と同じ高さの垂直壁面を有し両端が該流出室に開口する部分的なリング溝の外径である円筒内壁の直径が該包絡溝幅のおよそ２倍以上で中心が該流出室の溝幅中心とおよそ一致させた均一な溝幅を有するリング溝両端が該流出室に開口する空間を弁収納室としたその中央部に装着した中間部材の端面から該流出室開口部までの２箇所の空間を弁装着室として構成する。 The invention according to claim 23 is a partial ring having a vertical wall surface on the same bottom surface as the end portion of the fixed cylinder envelope groove and having the same height as the envelope groove, and both ends open to the outflow chamber. Both ends of the ring groove having a uniform groove width whose diameter of the inner wall of the cylinder, which is the outer diameter of the groove, is approximately twice the envelope groove width and whose center is approximately coincident with the groove width center of the outflow chamber are open to the outflow chamber. Two spaces from the end face of the intermediate member mounted at the center of the space to be the valve storage chamber to the opening of the outflow chamber are configured as the valve mounting chamber.
その弁装着室内に回動可能に１／４周前後から半周以下の範囲の円弧で形成した板状弁体としての円弧ゲート弁を該直線突起に対して対向させて挿着するとともに該円弧ゲート弁と該中間部材に挟まれた空間である2箇所の背面室にバネなどの弾性部材を装着して構成された吐出機構を備えたことを特徴とする請求項１０乃至１２の何れかに記載の容積型圧縮機である。 An arc gate valve as a plate-like valve element formed by an arc having a range of about 1/4 to less than half of the circle is rotatably inserted into the valve mounting chamber so as to face the linear protrusion, and the arc gate 13. A discharge mechanism configured by mounting an elastic member such as a spring in two back chambers, which are spaces between the valve and the intermediate member, is provided. This is a positive displacement compressor.
この発明によれば、圧縮室圧力が上昇して吐出行程に入る前の前記円弧ゲート弁の先端部および側壁シール面に作用する作動ガスの差圧に伴う力の一部は、該円弧ゲート弁の円弧形状のために該円弧ゲート弁を開口させる分力として作用するので動作性が向上して過圧縮動力が軽減することに加えて内外圧縮室の流出室を含めた吐出機構を１つの円筒空間に収納することによる省スペース化と狭い範囲の加工に集約することができる。 According to the present invention, part of the force accompanying the differential pressure of the working gas acting on the tip and side wall seal surfaces of the arc gate valve before the compression chamber pressure rises and enters the discharge stroke is Because of the arc shape of the cylinder, it acts as a component force that opens the arc gate valve, so that the operability is improved and the overcompression power is reduced. In addition, the discharge mechanism including the outflow chambers of the inner and outer compression chambers is provided as one cylinder. It can be integrated into space saving and processing within a narrow range by storing in a space.
請求項２４に記載の発明は、ガスの流れに伴う動圧が発生する吐出空間内の通路ないしは吐出機構近傍の圧縮室と２箇所に設けた前記背面室との間に連通孔を設けて構成された吐出機構を備えたことを特徴とする請求項２３記載の容積型圧縮機である。 According to a twenty-fourth aspect of the present invention, a communication hole is provided between a passage in a discharge space where dynamic pressure is generated due to a gas flow or a compression chamber near the discharge mechanism and the back chamber provided in two places. 24. The positive displacement compressor according to claim 23, further comprising a discharge mechanism.
この発明によれば、該円弧ゲート弁が開口動作する抵抗力として摺動摩擦抵抗、油膜による粘性抵抗さらには慣性力などが加わることを想定して、該円弧ゲート弁に作用する圧縮室圧力よりも低い圧縮室圧力が該背面室に導入できるので、流出室圧力と同程度の圧縮室圧力で該円弧ゲート弁が開口できることになる。 According to the present invention, assuming that a sliding frictional resistance, a viscous resistance due to an oil film, an inertial force, and the like are applied as a resistance force for opening the arc gate valve, it is more than the compression chamber pressure acting on the arc gate valve. Since a low compression chamber pressure can be introduced into the back chamber, the arc gate valve can be opened with a compression chamber pressure comparable to the outflow chamber pressure.
請求項２５に記載の発明は、前記弁装着室の円弧側壁面に互いに重着するように複数に分割した円弧ゲート弁をそれぞれが独立して摺動可能に装着した積層構造の円弧ゲート弁で吐出機構を構成したことを特徴とする請求項２３ないしは２４記載の容積型圧縮機である。 The invention according to claim 25 is an arc gate valve having a laminated structure in which arc gate valves divided into a plurality of pieces so as to overlap each other on the arc side wall surface of the valve mounting chamber are slidably mounted independently. 25. The positive displacement compressor according to claim 23, wherein the discharge mechanism is configured.
この発明によれば、該直線突起の平坦弁座と多重円弧ゲート弁の先端部のシール部が複数となり圧縮室と流出室間のシール性が向上するとともに圧縮室側の先端部の死空間が単一円弧ゲート弁に比べて小さくできる。さらには、該多重円弧ゲート弁の背面部に設けるバネ等の弾性体の力の外周側を小さくし内周側を大きく設定することにより該多重円弧ゲート弁の開閉の動作性が向上する。 According to the present invention, the flat valve seat of the linear protrusion and the seal portion at the tip of the multiple arc gate valve become a plurality, and the sealing performance between the compression chamber and the outflow chamber is improved and the dead space at the tip of the compression chamber is increased. Smaller than a single arc gate valve. Furthermore, the opening and closing operability of the multiple arc gate valve is improved by reducing the outer peripheral side of the force of an elastic body such as a spring provided on the back surface of the multiple arc gate valve and setting the inner peripheral side larger.
請求項２６に記載の発明は、前記リング溝の弁装着室の内側側壁面と前記流出室の側壁面とで一体に形成されたＵ字塔部分をＵ字溝付円柱として分離するとともに該Ｕ字溝付円柱の端面を該円筒室の底面に複数のピンないしはボルトで取り付けて前記円筒内壁とＵ字溝付円柱外壁間に中間部材を装着して弁装着室と背面室とで弁収納室を構成した吐出機構を備えたことを特徴とする請求項２３乃至２５の何れかに記載の容積型圧縮機である。 According to a twenty-sixth aspect of the present invention, the U-shaped tower portion integrally formed by the inner side wall surface of the valve mounting chamber of the ring groove and the side wall surface of the outflow chamber is separated as a U-shaped grooved cylinder and the U The end face of the grooved cylinder is attached to the bottom surface of the cylindrical chamber with a plurality of pins or bolts, and an intermediate member is mounted between the inner wall of the cylinder and the outer wall of the U-shaped grooved cylinder, and the valve storage chamber is composed of a valve mounting chamber and a back chamber. 26. The positive displacement compressor according to any one of claims 23 to 25, further comprising a discharge mechanism configured as described above.
この発明によれば、該弁収納室の弁装着室内壁を構成するＵ字塔を分離して固定シリンダから切り離した別部材のＵ字溝付円柱とすることで包絡溝幅のおよそ２倍以上の直径の円筒内壁の内側を円筒室で形成することができるので包絡溝の加工に用いるエンドミルをそのまま用いて円筒内壁が加工できることになる。 According to the present invention, the U-shaped tower constituting the valve mounting chamber wall of the valve storage chamber is separated and separated from the fixed cylinder into a separate U-grooved cylinder so that the envelope groove width is approximately twice or more. Since the inside of the cylindrical inner wall having a diameter of 5 mm can be formed in the cylindrical chamber, the inner wall of the cylinder can be processed using the end mill used for processing the envelope groove as it is.
請求項２７に記載の発明は、前記固定シリンダ包絡溝の流出室側に設けた前記弁装着室内の前記旋回ディスク上に装着した直動可能なおよそ直方体の弁台座の先端部を前記旋回ピストンの直線突起に摺接させた上で該弁台座上に直立固定した回転ピンに背面室側の円弧状端面中央に設けたピン用穴に回転可能に板状弁体であるフラップ弁を装着する。 According to a twenty-seventh aspect of the present invention, the distal end portion of a substantially cuboid valve seat mounted on the swivel disk in the valve mounting chamber provided on the outflow chamber side of the fixed cylinder envelope groove is connected to the swivel piston. A flap valve, which is a plate-like valve body, is rotatably mounted in a pin hole provided in the center of the arcuate end surface on the back chamber side on a rotating pin that is slidably contacted with a linear protrusion and fixed upright on the valve seat.
そのフラップ弁の先端部は圧縮室側を半円弧状とし流出室側は前記直線突起に摺接するシール面を設けるとともに該弁台座と背面室側の固定シリンダとの間に背面バネを装着しさらには該フラップ弁と弁装着室流出室側の側壁面との間に設けたゼンマイ等の側面バネなどで構成した上で該弁台座と該フラップ弁高さの合計を該弁装着室高さとおよそ一致させて相対的に摺動可能に構成された吐出機構を備えたことを特徴とする請求項５乃至９の何れかに記載の容積型圧縮機である。 The front end of the flap valve has a semicircular arc shape on the compression chamber side, and a sealing surface is provided on the outflow chamber side in sliding contact with the linear protrusion, and a back spring is mounted between the valve seat and the fixed cylinder on the back chamber side. Is composed of a side spring such as a spring provided between the flap valve and the side wall surface on the valve mounting chamber outflow chamber side, and the total height of the valve seat and the flap valve is approximately equal to the height of the valve mounting chamber. The positive displacement compressor according to any one of claims 5 to 9, further comprising a discharge mechanism configured to be relatively slidable.
この発明によれば、板状弁体の一形式である回転ドアのようなフラップ弁を用いることにより、該弁の開閉に関わる受圧面積を前記平板式ゲート弁よりも大きく取れて動作性が向上するので、請求項６乃至１０の何れかに記載したような弁収納室を構成する背面室に流出室より低い圧力を導入する必要がない。また、該弁を閉じる時の弁収納室の包絡溝側壁面と該フラップ弁間に残留する作動ガスは弁収納室の奥側に流出するので再圧縮損失は殆ど発生しない。 According to the present invention, by using a flap valve such as a revolving door which is a type of plate-like valve body, the pressure receiving area related to opening and closing of the valve can be made larger than that of the flat gate valve, and the operability is improved. Therefore, it is not necessary to introduce a pressure lower than that of the outflow chamber to the back chamber constituting the valve storage chamber as described in any one of claims 6 to 10. Further, since the working gas remaining between the envelope groove side wall surface of the valve storage chamber and the flap valve when the valve is closed flows out to the back side of the valve storage chamber, almost no recompression loss occurs.
請求項２８に記載の発明は、前記可動機構部材を両端面が平行平坦な中空円柱体の円筒ピストンを駆動軸の偏心軸に装着して回転または旋回ないしは揺動させて得られる該円筒ピストン外壁面の包絡線として得られる円筒状の内壁面を中央部に設け両端面を平行平坦に形成した前記固定構成部材としての固定シリンダに該円筒ピストンを組み込んで形成される三日月状の柱状空間を平坦な平坦蓋部材で挟み込んで形成される空間を該固定シリンダ円筒状の内壁面に一端が矩形状で開口する平行溝内に直動可能にして先端部を該円筒ピストンの外壁面に摺接させたおよそ直方体の仕切板で仕切って吸入室と圧縮室が形成される。 According to a twenty-eighth aspect of the invention, the movable mechanism member is obtained by rotating or swiveling or swinging the movable mechanism member mounted on the eccentric shaft of the drive shaft by mounting a hollow cylindrical cylindrical piston having both end surfaces parallel and flat. A crescent-shaped columnar space formed by incorporating the cylindrical piston into the fixed cylinder as the fixed component in which the cylindrical inner wall surface obtained as the envelope of the wall surface is provided in the center and both end surfaces are formed parallel and flat is flattened. A space formed by being sandwiched by a flat cover member can be directly moved into a parallel groove having one end formed in a rectangular shape on the cylindrical inner wall surface of the fixed cylinder, and the tip portion is in sliding contact with the outer wall surface of the cylindrical piston. A suction chamber and a compression chamber are formed by partitioning with a substantially rectangular parallelepiped partition plate.
該仕切板を装着する固定シリンダの該平行溝の溝幅を大きく拡大して形成した弁装着室とその奥に設けた流出室とで弁収納室を形成し、該弁装着室の圧縮室側の側壁面に摺接する側壁シール面を有し先端部が該円筒ピストン外壁面に摺接するおよそ直方体の平板ゲート弁と該仕切板との側壁面間に支持部材を設けそれらの先端部から該流出室側に抜ける流出
通路を設けるとともに該流出室には必要に応じてバネなどの弾性体を装着して組み付けて構成した弁機構体を該弁収納室に装着して構成される吐出機構を備えたことを特徴とする請求項５乃至９の何れかに記載の容積型圧縮機である。 A valve storage chamber is formed by a valve mounting chamber formed by enlarging the width of the parallel groove of the fixed cylinder to which the partition plate is mounted and an outflow chamber provided at the back thereof, and the compression chamber side of the valve mounting chamber A support member is provided between the side wall surfaces of the substantially rectangular parallelepiped gate valve and the partition plate, the front end portion of which has a side wall seal surface that is in sliding contact with the side wall surface of the cylindrical piston and the outer surface of the cylindrical piston is in sliding contact with the outer wall surface of the cylindrical piston. A discharge mechanism is provided in which an outflow passage is provided to the chamber side, and a valve mechanism that is configured by attaching an elastic body such as a spring to the outflow chamber is assembled to the outflow chamber. The positive displacement compressor according to any one of claims 5 to 9, wherein the compressor is a positive displacement compressor.
この発明によれば、該弁装着室と背面室で形成される弁収納室に先端部を圧縮室圧力が作用する形状にした平板ゲート弁と容積型ロータリ圧縮機に用いられるブレードに相当する仕切板およびそれらの背面側にバネ等を組合せた弁機構体を装着することにより、圧縮室と低圧側吸入室間をシールした上で作動ガスの吐出機構からの漏れの少ない圧縮行程と死空間が少なく流出抵抗が少ない上に剛性の高い平板ゲート弁を用いたロータリ式容積型圧縮機に適用可能な機能的で高性能な吐出機構が構成できる。 According to this invention, the partition corresponding to the blade used for the flat gate valve and the positive displacement rotary compressor whose compression chamber pressure is applied to the valve storage chamber formed by the valve mounting chamber and the back chamber. By attaching a valve mechanism that combines springs and the like to the plates and their back side, the compression process and the dead space with less leakage from the working gas discharge mechanism are obtained after sealing between the compression chamber and the low-pressure side suction chamber. A functional and high-performance discharge mechanism that can be applied to a rotary positive displacement compressor that uses a flat gate valve that has low outflow resistance and high rigidity, can be configured.
請求項２９に記載の発明は、前記平板ゲート弁の板厚の中心となる先端部中央位置を、前記固定シリンダ内壁面の中心を通る前記弁装着室の側壁面に平行な中心線から前記偏心軸のおよそ偏心量相当の距離を反吸入室側である圧縮室側に寄せて該平板ゲート弁を配置して構成される吐出機構を備えたことを特徴とする請求項２８記載の容積型圧縮機である。 According to a twenty-ninth aspect of the present invention, the center position of the tip portion that is the center of the plate thickness of the flat gate valve is decentered from a center line that passes through the center of the inner wall surface of the fixed cylinder and is parallel to the side wall surface of the valve mounting chamber. 29. The positive displacement compression according to claim 28, further comprising a discharge mechanism configured such that the flat gate valve is disposed so that a distance corresponding to an eccentric amount of the shaft is brought close to the compression chamber side which is the anti-suction chamber side. Machine.
この発明によれば、該平板ゲート弁先端部を一般的な平坦面ないしは前記平行な中心線上に中心を有する円筒ピストン側に凸な円弧で形成することにより該弁先端部の半分以上の範囲で圧縮室圧力が常に作用して弁の開口力が確保されて動作性が良好となる。 According to the present invention, the flat gate gate tip is formed by a general flat surface or a circular arc convex toward the cylindrical piston having the center on the parallel center line, so that it is in a range of more than half of the valve tip. The compression chamber pressure always acts to secure the opening force of the valve, and the operability is improved.
請求項３０に記載の発明は、前記固定シリンダおよび円筒ピストンを挟み込む前記平坦蓋部材であるメインカバーないしはサブカバーで形成された円筒空間の平坦面の一端に低圧通路に連通する低圧導入孔と他端側に前記弁装着室に連通する連通孔から形成された係止制御室を設け、大径の円筒部と小径のピン部の2段円筒で形成された該円筒部の内側空洞部にバネなどの弾性体を収納して形成された係止部材を該係止制御室に収納する。 According to a thirty-third aspect of the present invention, there is provided a low-pressure introduction hole communicating with a low-pressure passage at one end of a flat surface of a cylindrical space formed by a main cover or a sub-cover that is the flat lid member that sandwiches the fixed cylinder and the cylindrical piston. A locking control chamber formed from a communication hole communicating with the valve mounting chamber is provided on the end side, and a spring is provided in an inner cavity portion of the cylindrical portion formed by a two-stage cylinder having a large diameter cylindrical portion and a small diameter pin portion. A locking member formed by storing an elastic body such as is stored in the locking control chamber.
さらに前記平板ゲート弁の先端部が圧縮室内より内側の弁装着室内に収納された状態で該平坦蓋部材上を摺動する上下端面ないしは側壁シール面の内何れか一箇所に該係止部材のピン部が遊挿可能な位置に係止穴を設けた該平板ゲート弁で構成された吐出機構を備えたことを特徴とする請求項２９記載の容積型圧縮機である。 Furthermore, the locking member is placed on one of the upper and lower end surfaces or the side wall seal surface that slides on the flat lid member in a state in which the distal end portion of the flat gate valve is housed in the valve mounting chamber inside the compression chamber. 30. The positive displacement compressor according to claim 29, further comprising a discharge mechanism including the flat gate valve having a locking hole at a position where the pin portion can be loosely inserted.
この発明によれば、該空洞部に装着されたバネ力が該係止部材の前後に作用する制御差圧による荷重よりも大きい場合、例えば圧縮機内の圧力が均一となる停止時等では該係止部材のピン部が該平板ゲート弁の係止穴に遊挿されて該平板ゲート弁は移動しない。この状態での該平板ゲート弁先端部と平坦座面である円筒ピストンとの間は最大旋回半径の２倍の大きな隙間が保持された状態となっている。しかし、圧縮機の運転により該制御差圧が該バネ力よりも大きくなると該係止部材のピン部が平板ゲート弁の係止穴から離脱して平板ゲート弁が動作可能な状態となる。 According to the present invention, when the spring force attached to the cavity is larger than the load due to the control differential pressure acting before and after the locking member, for example, when the pressure in the compressor is uniform, the engagement is applied. The pin portion of the stopper member is loosely inserted into the locking hole of the flat gate valve, and the flat gate valve does not move. In this state, a large gap twice as large as the maximum turning radius is maintained between the flat plate gate valve tip and the cylindrical piston which is a flat seat. However, when the control differential pressure becomes larger than the spring force due to the operation of the compressor, the pin portion of the locking member is detached from the locking hole of the flat gate valve, and the flat gate valve can be operated.
本発明の平板ゲート弁、フラップ弁さらには円弧ゲート弁などの板状弁体の先端部が弁座に摺接する構成では、吐出行程終了時圧縮室のガスが残留する無駄な空間である死空間を小さくできるので、圧縮室への作動ガスの逆流による再圧縮損失を殆ど無くして高効率化が図れる。 In the configuration in which the tip of a plate-like valve body such as a flat gate valve, flap valve or arc gate valve of the present invention is in sliding contact with the valve seat, a dead space which is a useless space in which the gas in the compression chamber remains at the end of the discharge stroke Therefore, it is possible to achieve high efficiency by eliminating almost no recompression loss due to the backflow of the working gas to the compression chamber.
吐出行程終了直後、圧縮室内の圧力は低圧状態に切り替わると同時に前記板状弁体の先端部は可動機構部材である旋回ピストンや円筒ピストンの弁座が該弁装着室に最接近して殆ど隙間のない状態から瞬時に閉じるので閉じ遅れがなく、流出室の作動ガスが圧縮室へ逆流に伴う再圧縮損失が殆どなく高効率となる。 Immediately after the end of the discharge stroke, the pressure in the compression chamber is switched to a low pressure state, and at the same time, the tip of the plate-like valve body is moved to the valve mounting chamber as the valve seat of the swing piston or cylindrical piston, which is a movable mechanism member, approaches the valve mounting chamber. Since it closes instantaneously from a state without any gas, there is no delay in closing, and there is almost no recompression loss due to the backflow of the working gas in the outflow chamber to the compression chamber.
板厚が厚く剛性の高い平板ゲート弁などの板状弁体を吐出弁に用いているので前後に作用する圧力差による変形が殆どないのでシール性が高いことと該板状弁体や仕切板の側壁シール面に設けた段差面に導入する圧力により弁装着室側壁面への高い密着性に加えて該板状弁体先端部に平坦シール面を設けた構成では一層シール性が高まることから流出室と圧縮室間ないしは流入室間の漏れが殆どなくなり圧縮機の高効率化が図れる。 Since a plate-like valve body such as a flat gate valve with a large plate thickness and high rigidity is used for the discharge valve, there is almost no deformation due to a pressure difference acting on the front and back, so that the sealing performance is high, and the plate-like valve body and partition plate In addition to high adhesion to the valve mounting chamber side wall surface due to the pressure introduced into the step surface provided on the side wall seal surface, the flat seal surface is provided at the tip of the plate-like valve body, so that the sealing performance is further enhanced. There is almost no leakage between the outflow chamber and the compression chamber or between the inflow chamber and the efficiency of the compressor can be improved.
吐出行程に際して、前記平板ゲート弁などの板状弁体を動作させる手段として、（１）該板状弁体の背面室方向に圧縮室圧力を作用させる受圧面、風圧受面、弁安定板さらには動作圧空間などを設けたこと、（２）該平板ゲート弁を傾斜させたこと、（３）該板状弁体と前記弁装着室側壁面との間に転がり軸受のような転動体を設けたこと、（４）旋回ピストンに連動した回転盤を用いたこと、（５）該板状弁体の圧縮室側側壁面に作用する直接利用したフラップ弁やリード弁を設けたことなどにより、該板状弁体の動作性が良好となるので、該弁の閉じ遅れや圧縮室圧力の過圧縮現象の発生がなくて高効率化が図れる。 As means for operating the plate-like valve body such as the flat gate valve in the discharge stroke, (1) a pressure receiving surface for applying a compression chamber pressure toward the back chamber of the plate-like valve body, a wind pressure receiving surface, a valve stabilizing plate, Provided an operating pressure space, (2) inclined the flat gate valve, and (3) provided a rolling element such as a rolling bearing between the plate-like valve element and the valve mounting chamber side wall surface. (4) The use of a rotating disk interlocked with the orbiting piston, (5) The provision of a flap valve or reed valve used directly on the compression chamber side wall surface of the plate-like valve body, etc. Since the operability of the plate-like valve element is improved, there is no delay in closing the valve and the occurrence of an overcompression phenomenon of the compression chamber pressure, so that high efficiency can be achieved.
前記固定シリンダに設けた係止制御室内に係止部材を遊着した構成では、圧縮機内の圧力がバランス状態にある起動時に於いて、該固定シリンダに前記平板ゲート弁などの板状弁体が係止されたて圧縮室と流出室間の通路が開口状態となるので、圧縮室に潤滑油などの液体が流入してもそのまま吐出空間に排出されて異常高圧が発生することもなく高い信頼性が得られる。 In the configuration in which the locking member is loosely mounted in the locking control chamber provided in the fixed cylinder, a plate-like valve body such as the flat gate valve is provided on the fixed cylinder at the start-up when the pressure in the compressor is in a balanced state. Since the passage between the compression chamber and the outflow chamber is opened, even if a liquid such as lubricating oil flows into the compression chamber, it is discharged into the discharge space as it is and does not cause abnormal high pressure. Sex is obtained.
また、通常の運転から駆動軸の回転数を維持した状態で作動ガスの循環量を軽減する場合には、該流出室から伸びた吐出管途中に設けた容量制御弁を操作して吸入通路内の圧力を該係止制御室内に導入することにより流出室と圧力が等しくなり係止部材が動作して該板状弁体が該固定シリンダに係止され、圧縮室内の作動ガスは吸入側に戻ることから容量制御機構が簡単に構成されることになる。 Also, when reducing the circulating amount of the working gas while maintaining the rotational speed of the drive shaft from the normal operation, the capacity control valve provided in the middle of the discharge pipe extending from the outflow chamber is operated to Is introduced into the locking control chamber, the pressure becomes equal to the outflow chamber, the locking member operates, the plate-like valve element is locked to the fixed cylinder, and the working gas in the compression chamber is moved to the suction side. Since the process returns, the capacity control mechanism is easily configured.
本発明の実施例１に係る容積型圧縮機の横断面図である。It is a cross-sectional view of the positive displacement compressor according to Embodiment 1 of the present invention. 図１のA－A断面図である。FIG. 2 is a cross-sectional view taken along the line AA in FIG. 図１に適用した旋回ピストンの平面図である。It is a top view of the turning piston applied to FIG. 図１に適用した固定シリンダの平面図である。It is a top view of the fixed cylinder applied to FIG. 図２で１２矢視した吐出機構Ａの部分拡大図である。It is the elements on larger scale of the discharge mechanism A which looked at 12 arrows in FIG. 図５のＢ－Ｂ断面図である。FIG. 6 is a sectional view taken along line BB in FIG. 5. 図１の吐出機構Ａに用いる平板ゲート弁Ｒ８であり、（ａ）はその正面図、（ｂ）は（ａ）のＣ－Ｃ断面図である。1 is a flat gate valve R8 used in the discharge mechanism A of FIG. 1, in which (a) is a front view thereof, and (b) is a sectional view taken along the line CC of (a). 図１の吐出機構Ａに用いる平板ゲート弁Ｒ８であり、（ａ）はその側面図、（ｂ）は（ａ）のＤ矢視図である。It is flat plate valve R8 used for discharge mechanism A of Drawing 1, (a) is the side view, and (b) is a D arrow line view of (a). 図１の吐出機構Ａに用いる係止部材３０の外観図である。It is an external view of the locking member 30 used for the discharge mechanism A of FIG. 本発明の吐出機構Ａの動作状態を表わした図であり、（ａ）図から（ｄ）図へと順に駆動軸に同期して旋回ピストンが回転した状態を示し、中央に記載した０°、９０°、１８０°および２７０°は（ａ）図を起点にした回転角を表わしている。It is a figure showing the operation state of the discharge mechanism A of the present invention, and shows a state in which the turning piston is rotated in synchronization with the drive shaft in order from FIG. 90 °, 180 °, and 270 ° represent rotation angles starting from FIG. 本発明の実施例２に係る平板ゲート弁Ｒの正面図である。It is a front view of the flat gate valve R which concerns on Example 2 of this invention. 本発明の実施例３に係る平板ゲート弁Ｒの（ａ）は正面図、（ｂ）は（ａ）の側面図である。(A) of the flat gate valve R which concerns on Example 3 of this invention is a front view, (b) is a side view of (a). 本発明の実施例３に係る転動体の分解図である。It is an exploded view of the rolling element which concerns on Example 3 of this invention. 本発明の実施例４に係る９２矢視した吐出機構Ａの部分拡大図である。It is the elements on larger scale of the discharge mechanism A which looked at 92 arrows concerning Example 4 of this invention. 本発明の実施例５に係る１１２矢視した吐出機構Ａの部分拡大図である。It is the elements on larger scale of the discharge mechanism A which looked at 112 arrows concerning Example 5 of this invention. 本発明の実施例６に係る１５２矢視した吐出機構Ａの部分拡大図である。It is the elements on larger scale of the discharge mechanism A which looked at 152 arrows which concern on Example 6 of this invention. 本発明の実施例６に係る平板ゲート弁Ｒの（ａ）はその正面図、（ｂ）は（ａ）の側面図である。(A) of the flat gate valve R which concerns on Example 6 of this invention is the front view, (b) is a side view of (a). 本発明の実施例６に係る弁補助材の（ａ）はその正面図、（ｂ）は（ａ）の側面図である。(A) of the valve auxiliary material which concerns on Example 6 of this invention is the front view, (b) is a side view of (a). 本発明の実施例６に係る吐出機構Ａの動作説明図で、（ａ）は平板ゲート弁Ｒの動作前、（ａ）は動作後を示す。It is operation | movement explanatory drawing of the discharge mechanism A which concerns on Example 6 of this invention, (a) shows before operation | movement of the flat gate valve R, (a) shows after operation | movement. 本発明の実施例７に係る平板ゲート弁Ｒの（ａ）はその上下端面に平行な中央断面図、（ｂ）は（ａ）の裏面図である。(A) of the flat gate valve R which concerns on Example 7 of this invention is a center sectional view parallel to the upper-lower-end surface, (b) is a back view of (a). 本発明の実施例８に係る１９２矢視した吐出機構Ａの部分拡大図である。It is the elements on larger scale of the discharge mechanism A which looked at 192 based on Example 8 of this invention. 他の発明の実施例９に係る２１２矢視した吐出機構Ｂの部分拡大図である。It is the elements on larger scale of the discharge mechanism B which looked at 212 arrows concerning Example 9 of other invention. 他の発明の実施例９に係るフラップ弁Ｒ構成部材の展開図である。It is an expanded view of the flap valve R structural member which concerns on Example 9 of other invention. 他の発明の実施例９に係る吐出機構Ｂの動作説明図で、（ａ）はフラップ弁Ｒが動作した状態、（ｂ）はフラップ弁Ｌが動作した状態を示す。It is operation | movement explanatory drawing of the discharge mechanism B which concerns on Example 9 of another invention, (a) shows the state which the flap valve R operated, (b) shows the state which the flap valve L operated. 他の発明の実施例１０に係る容積型圧縮機の縦断面図である。It is a longitudinal cross-sectional view of the positive displacement compressor which concerns on Example 10 of other invention. 図２５のＦ－Ｆ断面図である。FIG. 26 is a sectional view taken along line FF in FIG. 25. 図２５に適用した旋回ピストンの平面図である。It is a top view of the turning piston applied to FIG. 図２５に適用した固定シリンダの平面図である。It is a top view of the fixed cylinder applied to FIG. 他の発明の実施例１０に係る３１２矢視した吐出機構Ｃの部分拡大図である。It is the elements on larger scale of the discharge mechanism C which looked at 312 arrow concerning Example 10 of other invention. 図２９の中心線Ｇに沿って展開した断面図である。FIG. 30 is a cross-sectional view developed along the center line G of FIG. 29. 他の発明の実施例１０に係る円弧ゲート弁Ｒの（ａ）はその上端面、（ｂ）は（ａ）の円弧内側から見た側面図である。(A) of the circular arc gate valve R which concerns on Example 10 of other invention is the upper end surface, (b) is the side view seen from the circular arc inside of (a). 他の発明の実施例１０に係る円弧ゲート弁Ｒの先端形状を設定するための説明図である。It is explanatory drawing for setting the front-end | tip shape of the circular arc gate valve R which concerns on Example 10 of other invention. 他の発明の実施例１０に係る中間部材の（ａ）はその上端面、（ｂ）は（ａ）の円弧内側から見た側面図である。(A) of the intermediate member which concerns on Example 10 of other invention is the upper end surface, (b) is the side view seen from the circular arc inside of (a). 他の発明の実施例１０に係る背面室内の圧力制御機構であり、（ａ）はその制御弁動作前の状態図を示し、（ｂ）は制御弁が動作して背面室と圧縮室が連通した状態図を示す図である。10 is a pressure control mechanism in the back chamber according to Embodiment 10 of another invention, (a) shows a state diagram before operation of the control valve, and (b) shows communication between the back chamber and the compression chamber by operating the control valve. FIG. 他の発明の実施例１０に係る吐出機構Ｃの動作状態を表わした図であり、（ａ）図から（ｄ）図へと順に駆動軸に同期して旋回ピストンが回転した状態を示し、中央に記載した０°、９０°、１８０°および２７０°は（ａ）図を起点にした回転角を表わしている。It is a figure showing the operation state of the discharge mechanism C which concerns on Example 10 of another invention, and shows the state which the turning piston rotated in synchronization with the drive shaft in order from FIG. 0 °, 90 °, 180 °, and 270 ° described in (a) represent rotation angles starting from FIG. 他の発明の実施例１１に係る３５２矢視した吐出機構Ｃの部分拡大図である。It is the elements on larger scale of the discharge mechanism C which looked at 352 arrows which concern on Example 11 of other invention. 他の発明の実施例１２に係る固定シリンダの平面図である。It is a top view of the fixed cylinder which concerns on Example 12 of other invention. 他の発明の実施例１２に係るＵ字溝付円柱の（ａ）はその上端面図、（ｂ）は（ａ）のＵ字溝側から見た側面図である。(A) of the cylinder with a U-shaped groove which concerns on Example 12 of other invention is the upper end figure, (b) is the side view seen from the U-shaped groove side of (a). 他の発明の実施例１３に係る容積型圧縮機の横断面図である。It is a cross-sectional view of the positive displacement compressor which concerns on Example 13 of other invention. 図３９に適用した固定シリンダの平面図である。It is a top view of the fixed cylinder applied to FIG. 他の発明の実施例１３に係る４１２矢視した吐出機構Ｄの部分拡大図である。It is the elements on larger scale of the discharge mechanism D which looked at 412 arrow concerning Example 13 of other invention. 他の発明の実施例１３に係る平板ゲート弁Ｓの（ａ）はその正面図、（ｂ）は（ａ）のＨ－Ｈ断面図である。(A) of the flat gate valve S which concerns on Example 13 of other invention is the front view, (b) is HH sectional drawing of (a). 他の発明の実施例１３に係る弁安定板の外観図である。It is an external view of the valve stabilizer which concerns on Example 13 of other invention. 他の発明の実施例１３に係る仕切板の（ａ）はその正面図、（ｂ）は（ａ）のＪ－Ｊ断面図である。(A) of the partition plate based on Example 13 of another invention is the front view, (b) is JJ sectional drawing of (a). 他の発明の実施例１３に係るストッパの（ａ）はその正面図、（ｂ）は（ａ）の上から見た端面図である。(A) of the stopper which concerns on Example 13 of other invention is the front view, (b) is the end elevation seen from the top of (a). 他の発明の実施例１３に係る吐出機構Ｄの動作状態を表わした図であり、（ａ）図から（ｄ）図へと順に駆動軸に同期して旋回ピストンが回転した状態を示し、中央に記載した０°、９０°、１８０°および２７０°は（ａ）図を起点にした回転角を表わしている。It is a figure showing the operation state of the discharge mechanism D which concerns on Example 13 of other invention, and shows the state which the turning piston rotated in synchronization with the drive shaft in order from Fig. (A) figure to (d) figure, 0 °, 90 °, 180 °, and 270 ° described in (a) represent rotation angles starting from FIG. 他の発明の実施例１４に係る仕切板の（ａ）はその正面面、（ｂ）は（ａ）のＫ－Ｋ断面図である。(A) of the partition plate concerning Example 14 of other invention is the front surface, (b) is KK sectional drawing of (a). 他の発明の実施例１５に係る容積型圧縮機５０１の横断面図である。It is a cross-sectional view of the positive displacement compressor 501 according to Embodiment 15 of another invention. 他の発明の実施例１５に係る固定シリンダの平面図である。It is a top view of the fixed cylinder which concerns on Example 15 of other invention. 他の発明の実施例１５に係る５１２矢視した吐出機構Ｅの部分拡大図である。It is the elements on larger scale of the discharge mechanism E which looked at 512 arrows which concern on Example 15 of other invention. 図５０のＭ－Ｎ－Ｏ－Ｐ線に沿った断面図である。FIG. 51 is a cross-sectional view taken along line MNOP in FIG. 50.
以下、数種類の容積形圧縮機に適用した様々な吐出機構の実施形態を、図面を参照しながら説明する。 Hereinafter, embodiments of various discharge mechanisms applied to several types of positive displacement compressors will be described with reference to the drawings.
ここでは、本発明の容積形圧縮機の一形式としての旋回駆動式リング型圧縮機に適用した吐出機構Ａの実施例１を図１～図１０に従って説明する。 Here, a first embodiment of a discharge mechanism A applied to a swivel drive type ring compressor as one type of positive displacement compressor of the present invention will be described with reference to FIGS.
図１のリング型圧縮機１の縦断面図と当該図のＡ－Ａ断面図である図２に示すように、密閉容器２内に固定されたフレーム５上に装着した固定シリンダ６とそれらの間に旋回ピストン７とオルダムリングを用いた旋回機構２０が設けられ、該フレームの中央部に設けた軸受に支持された駆動軸２２の下部を電動機２３に直結して構成されている。 As shown in FIG. 2 which is a longitudinal sectional view of the ring compressor 1 in FIG. 1 and a sectional view taken along line AA in FIG. 1, the fixed cylinders 6 mounted on the frame 5 fixed in the sealed container 2 and their A revolving mechanism 20 using a revolving piston 7 and an Oldham ring is provided between them, and a lower part of a drive shaft 22 supported by a bearing provided at the center of the frame is directly connected to an electric motor 23.
図１と図２に示した固定シリンダの矩形断面のリング状空洞である包絡溝６a内に長方形断面でリング状の旋回突起７ａが遊挿されて内外圧縮室が形成されている。ここで、該包絡溝６ａの該旋回突起７ａ外壁面側に形成される空間が外圧縮室で、該包絡溝６ａの該旋回突起７ａ内壁面側に形成される空間が内圧縮室である。 A ring-shaped swiveling protrusion 7a having a rectangular cross section is loosely inserted into an envelope groove 6a which is a ring-shaped cavity having a rectangular cross section of the fixed cylinder shown in FIG. 1 and FIG. Here, the space formed on the outer wall surface side of the swiveling protrusion 7a of the envelope groove 6a is an outer compression chamber, and the space formed on the inner wall surface side of the swiveling protrusion 7a of the envelope groove 6a is an inner compression chamber.
旋回ピストン７の形状は、図３の平面図に示すように、長方形断面の帯状板を１周以下の円筒状に曲げて形成した図中のＰ点からＱ点の区間の一定の幅と高さの円弧の突起で形成された円弧突起７ｂとその一端であるＱ点の接線方向に直線的に同一断面形状でＲ点まで一定長さ延長させ該円弧突起と一体にして旋回ディスク７ｄに直立させた直線突起７ｃとで旋回突起７ａが形成されている。 As shown in the plan view of FIG. 3, the shape of the orbiting piston 7 is a constant width and height in the section from the point P to the point Q in the figure formed by bending a belt-like plate having a rectangular cross section into a cylindrical shape having one round or less. A circular protrusion 7b formed of a circular arc protrusion and a tangent direction of point Q at one end thereof are linearly the same cross-sectional shape and extend a certain length to point R, and are united with the circular protrusion to stand upright on the rotating disk 7d. A swiveling protrusion 7a is formed by the straight protrusion 7c.
該旋回ピストン７は、軸受ボス７ｅに挿入され駆動軸２２の偏心軸と該旋回ピストンに装着された旋回機構２０とで自転のない公転運動すなわち旋回運動を行う。 The orbiting piston 7 is inserted into the bearing boss 7e and performs a revolving motion without rotation, that is, an orbiting motion, with the eccentric shaft of the drive shaft 22 and the swiveling mechanism 20 attached to the orbiting piston.
固定シリンダ６の形状は、図４に示しているように、該円弧突起７ｂの旋回運動で形成される包絡線を側壁面として得られる一定幅で断面矩形の包絡溝６ａを固定端板６ｂの片面に掘り下げて設けるとともに該包絡溝６aの一端に作動ガスの流入室６ｃを他端に流出室６ｄを設けたそれぞれに吸入孔６ｅと吐出孔６ｆが設けてられている。なお、該流出室６ｄは該直線突起７ｃの包絡溝として最小幅が決まるのでおよそ直線溝として形成される。 As shown in FIG. 4, the shape of the fixed cylinder 6 is such that the envelope groove 6a having a constant width and a rectangular cross section obtained by using the envelope formed by the swiveling motion of the arc projection 7b as a side wall surface is formed on the fixed end plate 6b. A suction hole 6e and a discharge hole 6f are provided on each side of the envelope groove 6a provided with an inflow chamber 6c for working gas and an outflow chamber 6d at the other end. The outflow chamber 6d is formed as a straight groove because the minimum width is determined as the envelope groove of the straight protrusion 7c.
また、該包絡溝６ｂを延長して設けた吐出孔６ｆを配した流出室６ｄ内外壁面に対向して開口する該包絡溝と同一底面を有する平行溝で形成された弁装着室６ｈとその奥の同一空間内に設けた背面室６ｊとを対とした弁収納室6hが対向して２対設けられている。さらに、該背面室６ｊには流出室６ｃないしは図１に示した吐出空間２１に連通する圧導入孔６ｋが設けられている。 Further, the valve mounting chamber 6h formed by a parallel groove having the same bottom surface as the envelope groove that opens opposite to the inner and outer wall surfaces of the outflow chamber 6d provided with the discharge hole 6f provided by extending the envelope groove 6b, and the back thereof Two pairs of valve storage chambers 6h, which are paired with a back chamber 6j provided in the same space, are provided. Further, the back chamber 6j is provided with an outflow chamber 6c or a pressure introducing hole 6k communicating with the discharge space 21 shown in FIG.
図２の１２矢視図を拡大した図５に吐出機構Ａ１２の全体の断面構成を示し、図５のＢ－Ｂ断面図を図６に示す。吐出機構Ａ１２は旋回ピストンの直線突起７ｃに先端部を挟んで対称に配置して一対設けたおよそ直方体の平板ゲート弁Ｒ８と平板ゲート弁Ｌ９をそれぞれの該弁装着室６ｈ内に装着した背面室側には平板ゲート弁ＲとＬを該直線突起側に押付けるようにバネなどの弾性体を設けて構成されている。 FIG. 5, which is an enlarged view taken along the arrow 12 in FIG. 2, shows the overall cross-sectional configuration of the discharge mechanism A 12, and FIG. 6 shows a cross-sectional view along BB in FIG. The discharge mechanism A12 is a rear chamber in which a flat plate gate valve R8 and a flat plate gate valve L9, each of which is provided symmetrically with the tip portion sandwiched between the linear protrusions 7c of the orbiting piston, are mounted in the valve mounting chambers 6h. On the side, an elastic body such as a spring is provided so as to press the flat gate valves R and L against the linear protrusion side.
また、図４に示す該背面室６ｊに開口する圧導入孔６ｋの他端は流出室６ｄを含めた吐出孔６ｆから図１に示す吐出管４までの吐出された作動ガスの通路上の何れかで、例えば吐出通路１５に開口している。 Further, the other end of the pressure introducing hole 6k opened to the back chamber 6j shown in FIG. 4 is any one on the passage of the discharged working gas from the discharge hole 6f including the outflow chamber 6d to the discharge pipe 4 shown in FIG. For example, the discharge passage 15 is open.
該弁収納室６ｇの一部である背面室６ｊには、該平板ゲート弁を押付ける背面バネ１１のような弾性体である弁補完材を収納するとともに前記吐出通路１５と連通させることで流出室６ｃより低い圧力を導入することができる。 The back chamber 6j, which is a part of the valve storage chamber 6g, stores a valve complement material such as a back spring 11 that presses the flat gate valve, and flows out by communicating with the discharge passage 15. A lower pressure than the chamber 6c can be introduced.
各弁装着室6hに装着した該平板ゲート弁Ｒ８と平板ゲート弁Ｌ９は直線突起７ｃと同一高さの直方体で弁座となる該直線突起側壁面に先端部を摺接する構成であり、該平板ゲート弁Ｒ８とＬ９の形状は、該直線突起の平坦面を基準とする線対称形状の関係にある。
以下の説明では、特に断りが無い場合には外圧縮室用の吐出機構を示す。よって、外圧縮室用の平板ゲート弁Ｒ８の先端部８ｈ平面を基準線とした対称形状が内圧縮室用の平板ゲート弁Ｌ９となるので平板ゲート弁Ｌの形状は特定可能なので詳細な説明を割愛する。 The flat plate gate valve R8 and the flat plate gate valve L9 mounted in each valve mounting chamber 6h are configured as a rectangular parallelepiped having the same height as the straight projection 7c, and the tip portion is slidably in contact with the straight projection side wall surface serving as a valve seat. The shapes of the gate valves R8 and L9 are in a line-symmetrical relationship with respect to the flat surface of the linear protrusion.
In the following description, a discharge mechanism for the outer compression chamber is shown unless otherwise specified. Therefore, the shape of the flat gate valve L can be specified because the symmetrical shape with respect to the front end 8h plane of the flat gate valve R8 for the outer compression chamber becomes the flat gate valve L9 for the inner compression chamber. Omit.
平板ゲート弁ＲとＬの形状を代表して平板ゲート弁Ｒ８の詳細な形状を図７と８に示す。直方体の外観形状の平坦部から内側に向けて様々な溝や段落しさらには穴を設けて該平板ゲート弁Ｒ８が形成されている。それらの詳細は以下で説明する。 7 and 8 show the detailed shape of the flat gate valve R8 as a representative of the flat gate valves R and L. The flat plate gate valve R8 is formed by providing various grooves, stages, and holes from the flat portion of the rectangular parallelepiped external shape to the inside. Details thereof will be described below.
平板ゲート弁Ｒ８の圧縮室側の側壁面を正面図として図７（ａ）に示し、その図のＣ－Ｃ断面図を（ｂ）図に示す。該側壁面には前記弁装着室６ｈに摺接する側壁シール面８ｃとそれより凹ました圧力ポケット８ｋと該側壁シール面と同一面の内側に設けた連通孔８ｍさらには背面部８ｂ側にシール溝８ｐが設けられている。さらに、該側壁シール面８ｃの反対側の側壁支持面８ｄに前記圧力ポケットと同様に設けられた圧力ポケットの空間内に該連通孔８ｍが開口している。 FIG. 7A is a front view of the side wall surface of the flat gate valve R8 on the compression chamber side, and FIG. The side wall surface has a side wall seal surface 8c slidably in contact with the valve mounting chamber 6h, a pressure pocket 8k recessed from the side wall, a communication hole 8m provided inside the same surface as the side wall seal surface, and a seal groove on the back surface portion 8b side. 8p is provided. Further, the communication hole 8m is opened in the space of the pressure pocket provided in the same manner as the pressure pocket on the side wall support surface 8d opposite to the side wall seal surface 8c.
また、該弁内部には背面部８ｂに開口するバネなどの弾性体を装着する長穴８ｎが２箇所設けられている。また、複雑な形状をしている先端部８ａや（ａ）図の右側面図である上端図に設けられた穴や溝の詳細は、該上端図である図８（ａ）とその（ａ）図のＤ矢示図である（ｂ）図を用いて詳しく説明する。 Further, two elongated holes 8n for mounting an elastic body such as a spring that opens to the back surface portion 8b are provided inside the valve. Further, the details of the hole 8 and the groove provided in the upper end view which is the right side view of the tip 8a having a complicated shape and the right side view of FIG. 8A and FIG. This will be described in detail with reference to FIG.
それの先端部８ａには該直線突起７ｃ側壁面に摺接する平坦シール面８ｇ、その面より凹んでいる受圧面８ｈとそのおよそ中央部で圧縮室側に大きな傾斜面を向けて形成した風圧受面８ｊ、さらに上端面に設けた油受穴８ｑから伸びた油溝８ｒが先端部の該平坦シール面８ｇまで延びている。なお、該平坦シール面８ｇの板厚方向の幅は、該板厚の１／６前後から1／２以下で形成されている。 A flat seal surface 8g slidably in contact with the side wall surface of the linear protrusion 7c, a pressure receiving surface 8h recessed from the surface, and a wind pressure receiver formed with a large inclined surface facing the compression chamber at its center. An oil groove 8r extending from the surface 8j and an oil receiving hole 8q provided on the upper end surface extends to the flat seal surface 8g at the tip. The width in the plate thickness direction of the flat seal surface 8g is formed from about 1/6 to 1/2 or less of the plate thickness.
なお、図３に示した直線突起７ｃの長さＬｓは、図５に示した平板ゲート弁の平坦シール面８ｇが該直線突起側壁面から離脱しないため旋回半径の２倍に該平坦シール面の幅を加えた長さが最小限必要となる。 The length Ls of the straight protrusion 7c shown in FIG. 3 is set to be twice the turning radius because the flat seal face 8g of the flat gate valve shown in FIG. The minimum length plus the width is required.
次に、該平板ゲート弁Ｒ８を固定シリンダ６に一時的に係止する係止機構の構成を図６とその係止部材３０の外観図である図９を用いて説明する。図５のＢ－Ｂ断面図である図６には、固定シリンダの固定端板６ｂに設けた円筒状の係止制御室６ｎ内に装着された係止部材３０と該平板ゲート弁Ｒ８との関係が示されている。 Next, the structure of a locking mechanism for temporarily locking the flat gate valve R8 to the fixed cylinder 6 will be described with reference to FIG. 6 and FIG. 9 which is an external view of the locking member 30. FIG. 6, which is a cross-sectional view taken along the line BB of FIG. 5, shows the relationship between the locking member 30 mounted in the cylindrical locking control chamber 6 n provided on the fixed end plate 6 b of the fixed cylinder and the flat gate valve R 8. The relationship is shown.
係止部材３０の外観形状を図９に示す。円筒部３０ａとそれよりも小さな径のピン部３０ｂの２段円筒形状で形成され、円筒部内には空洞部３０ｄが設けられ、そのリング状の端面であるシール端面３０ｃは該係止制御室６ｍ端面に密着できる形状となっている。このように形成された係止部材３０は図６に示すように固定端板６ｂの係止制御室６ｍ内に係
止バネ３１とともにピン部３０ｂを固定端板６ｂの係止孔６ｑに位置合わせして平板ゲート弁Ｒ側に向けて遊着して係止機構が構成されている。このような構成は内外圧縮室用ないしは圧縮室個別の吐出機構に適用可能である。 The appearance of the locking member 30 is shown in FIG. A cylindrical portion 30a and a pin portion 30b having a smaller diameter are formed in a two-stage cylindrical shape. A hollow portion 30d is provided in the cylindrical portion, and a seal end surface 30c, which is a ring-shaped end surface, is provided in the locking control chamber 6m. The shape can be in close contact with the end face. As shown in FIG. 6, the locking member 30 formed in this way aligns the pin portion 30b together with the locking spring 31 in the locking control chamber 6m of the fixed end plate 6b with the locking hole 6q of the fixed end plate 6b. Then, the locking mechanism is configured by loosely attaching toward the flat gate valve R side. Such a configuration can be applied to the inner and outer compression chambers or the discharge mechanism for each compression chamber.
該係止制御室６ｍの係止バネ３１を装着している端面には吸入圧力を導入する連通管３２の一端が開口し、その反対側である平板ゲート弁の上端面に開口する係止孔６ｑから背面室６ｊないしは流出室内の圧力が導入される構成となっている。 One end of the communication pipe 32 for introducing the suction pressure is opened at the end face of the latch control chamber 6m where the latch spring 31 is mounted, and the latch hole opened at the upper end face of the flat gate valve on the opposite side. The pressure in the back chamber 6j or the outflow chamber is introduced from 6q.
次に、該係止機構の動作について説明する。リング型圧縮機１の起動直前では、通常圧縮機内の圧力は均一すなわち吸入圧力と吐出圧力が等しい状態となっているので、係止制御室６ｍ内の圧力も均一であり係止部材３０には係止バネ３１の荷重のみ作用している。従って、該係止バネに押されて該係止部材のピン部３０ｂは平板ゲート弁ＲとＬの上端面上に押付けられている。この状態で該圧縮機を起動すると背面バネ１１ないしは直線突起７ｃに押されて該平板ゲート弁が弁装着室６ｈ内を移動する際に平板ゲート弁Ｒの油受穴８ｑと該係止孔６ｑが合致した位置にくるとピン部３０ｂが該油受穴８ｑに入り込み該平板ゲート弁Ｒの動きがなくなり固定された状態となる。 Next, the operation of the locking mechanism will be described. Immediately before the start of the ring compressor 1, the pressure in the normal compressor is usually uniform, that is, the suction pressure and the discharge pressure are equal. Therefore, the pressure in the locking control chamber 6m is also uniform, and the locking member 30 has Only the load of the locking spring 31 is acting. Accordingly, the pin portion 30b of the locking member is pressed onto the upper end surfaces of the flat gate valves R and L by being pressed by the locking spring. When the compressor is started in this state, the oil receiving hole 8q and the locking hole 6q of the flat gate valve R are pushed by the back spring 11 or the linear protrusion 7c and the flat gate valve moves in the valve mounting chamber 6h. When the positions coincide with each other, the pin portion 30b enters the oil receiving hole 8q so that the flat gate valve R does not move and is fixed.
このように平板ゲート弁ＲとＬが開口した状態で運転状態が継続されても圧縮室から流出したガスは流出室に入り吐出空間に流出するので、吐出空間すなわち背面室の圧力は徐々に上昇する。その圧力と吸入圧力との差が係止バネ３１荷重以上になると係止部材３０が押されて係止孔６ｑからピン部３０ｂが離脱し、平板ゲート弁ＲとＬの弁装着室内の移動が可能となり、該先端部の弁座である直線突起側壁面に着座して圧縮室が密閉される。 Thus, even if the operation state is continued with the flat gate valves R and L opened, the gas flowing out from the compression chamber enters the outflow chamber and flows out into the discharge space, so that the pressure in the discharge space, that is, the back chamber gradually increases. To do. When the difference between the pressure and the suction pressure exceeds the load of the locking spring 31, the locking member 30 is pushed, the pin portion 30 b is detached from the locking hole 6 q, and the flat gate valves R and L move in the valve mounting chamber. The compression chamber is sealed by sitting on the side wall surface of the straight protrusion, which is the valve seat at the tip.
上記の如く構成された実施例１の吐出機構A１２を装着したリング型圧縮機１の通常の運転時に於ける該吐出機構の動作状態を図１０の（ａ）図から（ｄ）図を用いて説明する。（ａ）図から（ｄ）図へと順に駆動軸に同期して旋回ピストンが回転した状態を示し、その回転角は９０°ピッチなので、（ａ）図を起点として０°、９０°、１８０°および２７０°と回転した状態を表わしている。 The operation state of the discharge mechanism during normal operation of the ring compressor 1 equipped with the discharge mechanism A12 of Example 1 configured as described above is shown in FIGS. 10 (a) to 10 (d). explain. (A) From figure (d) to figure (d) shows the state in which the orbiting piston is rotated in synchronization with the drive shaft, and the rotation angle is 90 ° pitch. Therefore, (a) 0 °, 90 °, 180 starting from the figure. It represents the rotated state of ° and 270 °.
図中のＰは圧力を示し、サフィックスｓは流入室、ｄは流出室ないしは吐出空間、ｃは圧縮室のそれぞれの圧力状態を示している。さらに、ｃｏは外圧縮室、ｃｉは内圧縮室を示している。流入室６ｄ内の矢印は、旋回ピストンと一体となった直線突起７ｃの移動方向を示しており、内外圧縮室内の矢印は吐出行程時のガスの流れ方向を示している。 In the drawing, P represents pressure, suffix s represents the inflow chamber, d represents the outflow chamber or discharge space, and c represents the pressure state of the compression chamber. Further, co represents an outer compression chamber, and ci represents an inner compression chamber. The arrow in the inflow chamber 6d indicates the moving direction of the linear protrusion 7c integrated with the orbiting piston, and the arrow in the inner and outer compression chambers indicates the gas flow direction during the discharge stroke.
（ａ）図では、直線突起７ｃが流出室６ｄの側壁面に最接近して外圧縮室の吐出行程が終了した直後で直線突起７ｃが下側に移動する直前の状態を示している。平板ゲート弁Ｒ８は弁装着室６ｈの背面室６ｊの最も奥まで到達して移動速度は０となり背面バネ１１が最も縮んでいる反面平板ゲート弁Ｌ９は弁装着室６ｈから圧縮室側に最も突出して背面バネ１１が最も伸びた状態となっている。 FIG. 6A shows a state immediately after the linear protrusion 7c is closest to the side wall surface of the outflow chamber 6d and the discharge stroke of the outer compression chamber is completed, and immediately before the linear protrusion 7c moves downward. The flat gate valve R8 reaches the innermost part of the back chamber 6j of the valve mounting chamber 6h, the moving speed becomes zero, and the back spring 11 is contracted most, while the flat gate valve L9 protrudes most from the valve mounting chamber 6h to the compression chamber side. The back spring 11 is in the most extended state.
この状態では、外圧縮室の圧力Ｐｃｏは流入室圧力すなわち吸入圧力Ｐｓと等しくなる一方内圧縮室の圧力Ｐｃｉは流出室圧力すなわち吐出圧力Ｐｄより低く平板ゲート弁Ｌ９の先端部は直線突起７ｃの側壁面に摺接してシール性が確保され圧縮が継続される。 In this state, the pressure Pco of the outer compression chamber becomes equal to the inflow chamber pressure, that is, the suction pressure Ps, while the pressure Pci of the inner compression chamber is lower than the outflow chamber pressure, that is, the discharge pressure Pd, and the tip of the flat gate valve L9 is formed by the linear protrusion 7c. The sealing is ensured by sliding contact with the side wall surface, and the compression is continued.
（ａ）図から９０°回転した（ｂ）図では、直線突起７ｃが流出室６ｄ溝のおよそ中央部に旋回しながら移動している。それに伴い、平板ゲート弁Ｒ８の先端部は直線突起７ｃ側壁面に摺接しながら移動しているので、外圧縮室の圧力Ｐｃｏは流出室圧力Ｐｄより低い状態で圧縮動作が継続される。 (A) In FIG. (B) rotated by 90 ° from the figure, the linear protrusion 7c moves while turning to the approximately central part of the outflow chamber 6d groove. Along with this, the distal end portion of the flat gate valve R8 moves while being in sliding contact with the side wall surface of the linear protrusion 7c, so that the compression operation is continued with the pressure Pco in the outer compression chamber being lower than the outflow chamber pressure Pd.
一方、流出室圧力Ｐｄよりも大きくなった内圧縮室１４では圧力Ｐｃｉが平板ゲート弁Ｌ
９の圧力ポケット９ｋ内と先端部の受圧面９ｈに作用して該平板ゲート弁Ｌ９が流出室６ｄ側に押されると同時に背面室６ｊ側に押されて側壁面間の摺動摩擦力が大幅に軽減した状態で、平板ゲート弁Ｌ９が容易に背面室６ｊ側に押され該弁の先端部が直線突起７ｃ側壁面から離脱して図中に弁開口と記しているように通路が開口して矢印で示した方向で圧縮室のガスが流出室に流出する。 On the other hand, in the inner compression chamber 14 which has become larger than the outflow chamber pressure Pd, the pressure Pci is increased to the flat gate valve L.
9 acts on the pressure receiving surface 9h in the pressure pocket 9k and at the tip, and the flat gate valve L9 is pushed to the outflow chamber 6d side and at the same time is pushed to the back chamber 6j side to greatly increase the sliding frictional force between the side wall surfaces. In the reduced state, the flat gate valve L9 is easily pushed to the back chamber 6j side, and the leading end of the valve is detached from the side wall surface of the straight projection 7c so that the passage opens as indicated by the valve opening in the figure. The gas in the compression chamber flows into the outflow chamber in the direction indicated by the arrow.
（ｂ）図からさらに９０°回転した（ｃ）図では、直線突起７ｃが流出室６ｄの側壁面に最接近して内圧縮室の吐出行程が終了した直後で該直線突起が上側に移動する直前の状態を示している。従って、平板ゲート弁Ｌ９は弁装着室６ｈの背面室６ｊの最も奥まで到達して背面バネ１１が最も縮んでいる反面平板ゲート弁Ｒ８は弁装着室６ｈから圧縮室側に最も突出して背面バネ１１が最も伸びた状態となっている。 (B) Further rotated 90 ° from the figure. In FIG. (C), the straight protrusion 7c moves upward immediately after the discharge stroke of the inner compression chamber is completed with the straight protrusion 7c closest to the side wall surface of the outflow chamber 6d. The previous state is shown. Accordingly, the flat gate valve L9 reaches the innermost part of the back chamber 6j of the valve mounting chamber 6h and the back spring 11 is contracted most, while the flat gate valve R8 protrudes most from the valve mounting chamber 6h toward the compression chamber and protrudes from the back spring. 11 is the most extended state.
この時、内圧縮室の圧力Ｐｃｉは流入室圧力すなわち吸入圧力Ｐｓと等しくなる一方外圧縮室の圧力Ｐｃｏは流出室圧力すなわち吐出圧力Ｐｄより低く、平板ゲート弁Ｒ８の先端部は直線突起７ｃの側壁面に摺接してシール性が確保され圧縮が継続される。 At this time, the pressure Pci of the inner compression chamber becomes equal to the inflow chamber pressure, that is, the suction pressure Ps, while the pressure Pco of the outer compression chamber is lower than the outflow chamber pressure, that is, the discharge pressure Pd. The sealing is ensured by sliding contact with the side wall surface, and the compression is continued.
（ｃ）図から９０°回転した（ｄ）図では、直線突起７ｃが流出室６ｄ溝のおよそ中央部に旋回しながら上方に移動している。それに伴い、平板ゲート弁Ｌ９の先端部は直線突起７ｃ側壁面に摺接しながらさらに上方に移動するが、内圧縮室の圧力Ｐｃｉは流出室圧力Ｐｄより低いので圧縮動作が継続される。 (C) In the figure (d) rotated 90 degrees from the figure, the linear protrusion 7c is moving upward while turning to the approximately central part of the outflow chamber 6d groove. Accordingly, the tip of the flat gate valve L9 moves further upward while sliding on the side wall surface of the linear protrusion 7c, but the compression operation is continued because the pressure Pci in the inner compression chamber is lower than the outflow chamber pressure Pd.
一方、流出室圧力Ｐｄよりも大きくなった外圧縮室１３の圧力Ｐｃｏが平板ゲート弁Ｒ８の圧力ポケット８ｋ内と先端部の受圧面８ｈに作用して該平板ゲート弁Ｒが流出室６ｄ側に押されると同時に背面室６ｊ側に押されて側壁面間の摺動摩擦力が大幅に軽減した状態で、平板ゲート弁Ｒ８が容易に背面室６ｊ側に押され該弁の先端部が直線突起７ｃ側壁面から離れて図中に弁開口と記しているように通路が開口して矢印で示した方向で圧縮室のガスが流出室に流出する。 On the other hand, the pressure Pco in the outer compression chamber 13 which has become larger than the outflow chamber pressure Pd acts on the pressure pocket 8k of the flat gate valve R8 and the pressure receiving surface 8h at the tip, so that the flat gate valve R moves toward the outflow chamber 6d. At the same time as being pushed, the flat gate valve R8 is easily pushed to the back chamber 6j side while the sliding friction force between the side wall surfaces is greatly reduced by being pushed to the back chamber 6j side, and the tip of the valve is a straight protrusion 7c. The passage opens as shown by the valve opening in the figure away from the side wall surface, and the gas in the compression chamber flows into the outflow chamber in the direction indicated by the arrow.
このような動作状態に於いて、背面室６ｈに流出室６ｄ圧力よりも動圧ないしは通路抵抗分低い圧力を導入する構成では、内外圧縮室１２圧力と該流出室圧力の差が殆どない状態で開口するので、内外圧縮室圧力が流出室圧力よりも上昇する過圧縮現象の発生はない。 In such an operating state, in the configuration in which a dynamic pressure or a pressure lower than the pressure of the outflow chamber 6d is introduced into the back chamber 6h than the pressure of the outflow chamber 6d, there is almost no difference between the inner and outer compression chamber 12 pressures and the outflow chamber pressure. Since it opens, there is no occurrence of an overcompression phenomenon in which the inner and outer compression chamber pressures rise above the outflow chamber pressure.
また、吐出行程時に問題となる再圧縮損失の原因の一つである死空間は、平板状ゲート弁ＲとＬの先端部８ａ隙間と直線突起７ｃ側壁間に挟まれた空間に相当するが、その空間は極めて少ないので死空間による再圧縮損失は殆どない。 In addition, the dead space that is one of the causes of recompression loss which becomes a problem during the discharge stroke corresponds to a space sandwiched between the gap between the tip end portion 8a of the flat gate valves R and L and the side wall of the linear protrusion 7c. Since the space is extremely small, there is almost no recompression loss due to the dead space.
次に、吐出行程終了前後では、直線突起７ｃ側壁面と包絡溝６ｂ側壁面間が最接近した位置が包絡溝から平板状ゲート弁先端部を経て流出室側に移行するに従い下流側の圧縮室圧力が吸入側の流入室と同程度の圧力に瞬時に低下し該弁が閉じる。 Next, before and after the end of the discharge stroke, as the position where the side wall surface of the linear protrusion 7c and the envelope groove 6b are closest is shifted from the envelope groove to the outflow chamber side through the flat gate gate tip, the downstream compression chamber The pressure instantaneously drops to a pressure comparable to that of the inlet chamber on the suction side, and the valve closes.
このように隣接する内外圧縮室圧力が瞬時に低下すると直線突起７ｃが弁装着室6h入り口に最接近し平板ゲート弁ＲとＬの先端部である平坦シール面が近傍にあり、先端部隙間に圧縮室の低圧が流入し背面室圧力との大きな差圧と背面バネ力の力により該平板ゲート弁ＲとＬが直線突起側壁面に瞬時に着座して内外圧縮室と流出室を遮断するので、該弁の閉じ遅れはなく作動ガスの流出室からの逆流も阻止できる。 When the pressure in the adjacent inner and outer compression chambers decreases instantaneously in this way, the straight projection 7c comes closest to the inlet of the valve mounting chamber 6h, and the flat seal surface which is the tip of the flat gate valves R and L is in the vicinity, and the tip clearance is Since the low pressure of the compression chamber flows in and the flat gate valves R and L are instantly seated on the side walls of the straight protrusions by the large differential pressure from the back chamber pressure and the force of the back spring force, the inner and outer compression chambers and the outflow chamber are shut off. In addition, there is no delay in closing the valve, and backflow of the working gas from the outflow chamber can be prevented.
次に、前記吐出機構Ａの平板ゲート弁ＲとＬを用いた実施例１の一部を変更した実施例２について、図１１を用いて説明する。 Next, a second embodiment in which a part of the first embodiment using the flat gate valves R and L of the discharge mechanism A is changed will be described with reference to FIG.
同図に示すように、弁装着室６ｈ底面に平行な平面形状が同一である複数個の平板ゲート弁Ｒ４８に分割して構成されそれぞれに背面バネ装着用の長穴４８ｇが設けられている。そして、各分割された部材内部に設けたピン穴に連係ピン５１を挿入し複数枚の平板ゲート弁を積層連結して構成している。当然内圧縮室用の平板ゲート弁Ｌにも適用される。 As shown in the figure, it is divided into a plurality of flat gate valves R48 having the same planar shape parallel to the bottom surface of the valve mounting chamber 6h, and each is provided with a slot 48g for mounting a back spring. Then, the connecting pin 51 is inserted into a pin hole provided in each divided member, and a plurality of flat gate valves are stacked and connected. Of course, this also applies to the flat gate valve L for the inner compression chamber.
このような構成では、圧力や温度変化の影響を受けて弁座となる直線突起７ｃが変形するが、その変形量は梁の曲げと同様に該旋回ディスク側の固定端よりも先端側が大きくなる。その際、実施例２の平板ゲート弁Ｒは、その変形量に追従して部分的に移動でき先端部の平坦シール面の隙間を最小にして効率低下をなくすことができる。 In such a configuration, the linear protrusion 7c serving as a valve seat is deformed under the influence of pressure or temperature change, but the amount of deformation is larger on the tip side than on the fixed end on the swivel disk side as in the bending of the beam. . At that time, the flat gate valve R according to the second embodiment can partially move following the amount of deformation, and the gap in the flat seal surface at the tip can be minimized to eliminate the decrease in efficiency.
次に、前記吐出機構Ａの平板ゲート弁ＲとＬに用いた実施例１の一部を変更した実施例３について、図１２および図１３を用いて説明する。 Next, a third embodiment in which a part of the first embodiment used for the flat gate valves R and L of the discharge mechanism A is changed will be described with reference to FIGS.
図１２に示すように、本実施形態は平板ゲート弁Ｒ６８と弁装着室６ｈの流出室側の側壁面との間に転がり軸受などの転動体７６を１個ないしは複数個装着して構成される。該転動体７６は図１３に示すように車軸７６ｂに車輪部７６ａを装着し、平板ゲート弁Ｒの側壁支持面よりも車輪部が数十から数百ミクロン突出するように配置され、車軸と車輪部間ないしは車軸と平板ゲート弁間で回転可能に構成されている。当然内圧縮室用の平板ゲート弁Ｌにも適用される。 As shown in FIG. 12, this embodiment is configured by mounting one or a plurality of rolling elements 76 such as a rolling bearing between the flat gate valve R68 and the side wall surface on the outflow chamber side of the valve mounting chamber 6h. . As shown in FIG. 13, the rolling element 76 has a wheel portion 76a mounted on an axle 76b, and is arranged such that the wheel portion protrudes from the tens of hundreds of microns to the side wall support surface of the flat gate valve R. It is configured to be rotatable between the parts or between the axle and the flat gate valve. Of course, this also applies to the flat gate valve L for the inner compression chamber.
このような構成に於いて、圧縮室圧力が上昇して流出室圧力よりも大きくなると、圧縮室圧力を導入している圧力ポケットからの押付け力などにより平板ゲート弁Ｒの車輪部７６ａ外周が弁装着室の流出側の側壁面に着座して転がるので、平板ゲート弁Ｒの背面室側への移動すなわち弁開口に対する摩擦抵抗が大きく軽減する。 In such a configuration, when the compression chamber pressure rises and becomes larger than the outflow chamber pressure, the outer periphery of the wheel portion 76a of the flat gate valve R is caused by the pressing force from the pressure pocket introducing the compression chamber pressure. Since it sits and rolls on the side wall surface on the outflow side of the mounting chamber, the movement of the flat gate valve R toward the back chamber, that is, the frictional resistance against the valve opening is greatly reduced.
次に、前記吐出機構Ａの平板ゲート弁ＲとＬに用いた実施例１の一部を変更した実施例４について、図１４を用いて説明する。 Next, a fourth embodiment in which a part of the first embodiment used for the flat gate valves R and L of the discharge mechanism A is changed will be described with reference to FIG.
同図に示すように、前記直線突起７ｃ側壁面と前記平板ゲート弁Ｒの平坦シール面との面接触状態と圧縮室側先端部の隙間を維持した状態に於いて、固定シリンダ８６の弁収納室８６ｇを形成する弁装着室８６ｈを該直線突起と包絡溝８６ｂの流出室８６ｄ側終端部の接線に対する該弁装着室の包絡溝側の側壁面取り付け角度は直角を基準として数度前後の角度を傾斜させて設けた平板ゲート弁Ｒ８８と平板ゲート弁Ｌ８９の先端部と側壁面の相対角度も前記傾斜角度に合わせた形状とする。 As shown in the figure, the valve housing of the fixed cylinder 86 is maintained in a state in which the surface contact state between the side wall surface of the linear protrusion 7c and the flat seal surface of the flat gate valve R and the clearance between the compression chamber side end portions are maintained. The valve mounting chamber 86h forming the chamber 86g has an angle of about several degrees on the side of the envelope groove side of the valve mounting chamber with respect to the tangent of the linear protrusion and the end portion of the envelope groove 86b on the outflow chamber 86d side. The relative angle between the front end portion of the flat plate gate valve R88 and the flat plate gate valve L89 and the side wall surface of the flat plate gate valve R89 is set to a shape that matches the inclination angle.
このように該平板ゲート弁の背面部側を流出室側に傾斜させた場合には、圧縮室圧力が流出室圧力より上昇して平板ゲート弁が弁装着室の流出室側側壁面に押付けられると該側壁面の傾斜方向に滑り上がる荷重が加算されて平板ゲート弁ＲとＬの開口が容易となる。 When the back side of the flat gate valve is inclined to the outflow chamber in this way, the compression chamber pressure rises above the outflow chamber pressure and the flat gate valve is pressed against the outflow chamber side wall surface of the valve mounting chamber. And the load sliding up in the inclination direction of the side wall surface is added to facilitate opening of the flat gate valves R and L.
次に、前記吐出機構Ａの実施例１の一部を変更した実施例５について、図１５を用いて説明する。 Next, a fifth embodiment in which a part of the first embodiment of the discharge mechanism A is changed will be described with reference to FIG.
実施例１のような内外圧縮室それぞれの弁装着室と背面室から構成される弁収納室に於いて、図４に示す固定シリンダの包絡溝６ｂと同一底面同一幅を有する図１５に示すおよそ矩形断面の弁装着室１０６ｈの奥に該包絡溝と同一幅で両端に半円弧を設けた長円弧形状の背面室１０６ｊから弁収納室１０６ｇを構成するとともに該弁装着室内に同一高さの直方体形状で流出室奥側の側壁面に密着固定したサイドピース１１６と包絡溝側弁装着室側
壁面との間に微小隙間を設けて摺動可能に装着した実施例１の前記平板ゲート弁Ｒ８と平板ゲート弁Ｌ９から構成される。 In the valve storage chamber composed of the valve mounting chamber and the back chamber of each of the inner and outer compression chambers as in the first embodiment, the same bottom surface and the same width as the envelope groove 6b of the fixed cylinder shown in FIG. A valve storage chamber 106g is constituted by a long-arc shaped rear chamber 106j having a semicircular arc at both ends at the same width as the envelope groove at the back of the valve mounting chamber 106h having a rectangular cross section, and a rectangular parallelepiped having the same height in the valve mounting chamber. The flat plate gate valve R8 of the first embodiment, which is slidably mounted with a small gap between the side piece 116 that is closely fixed to the side wall surface of the outflow chamber in the shape and the side wall surface of the envelope groove side valve mounting chamber; It consists of a flat gate valve L9.
このような実施例５では、該包絡溝６ａを加工する一つのカッターを用いて容易に流出室１０６ｄおよび弁装着室１０６ｇと背面室１０６ｊから成る弁収納室１０６ｇを加工することができるので生産性が向上する。 In the fifth embodiment, the productivity can be improved because the outflow chamber 106d and the valve storage chamber 106g including the valve mounting chamber 106g and the back chamber 106j can be easily processed by using one cutter for processing the envelope groove 6a. Will improve.
次に、前記吐出機構Ａの実施例１の一部を変更した実施例６について、図１６から図１９を用いて説明する。 Next, a sixth embodiment in which a part of the first embodiment of the discharge mechanism A is changed will be described with reference to FIGS.
実施例６の弁装着室と背面室から構成される弁収納室に於いて、図１６に示すように、一方の弁装着室１４６ｈには平板ゲート弁Ｒ１４８と弁補助材１５６が一対並置されている。図１７に平板ゲート弁Ｒ１４８の形状を示し、図１８に弁補助材１５６の形状を示す。 In the valve storage chamber composed of the valve mounting chamber and the back chamber of the sixth embodiment, as shown in FIG. 16, a pair of flat gate valve R148 and valve auxiliary member 156 are juxtaposed in one valve mounting chamber 146h. Yes. FIG. 17 shows the shape of the flat gate valve R148, and FIG. 18 shows the shape of the valve auxiliary member 156.
該平板ゲート弁Ｒ１４８の背面部１４８ｂには弁補助材１５６の端面を当てる部分として突出させて拘止部１４８ｔを設けている。その他の形状である先端部１４８ａや側壁シール面１４８ｋなどは実施例１の平板ゲート弁RとLに同じである。 A restraining portion 148t is provided on the back surface portion 148b of the flat gate valve R148 so as to protrude as a portion against which the end surface of the valve auxiliary member 156 is applied. The tip portion 148a and the side wall seal surface 148k having other shapes are the same as those of the flat gate valves R and L in the first embodiment.
図１８に示した弁補助材１５６は１個ないしは複数個の転がり軸受などの転動体１６７を装着している。その転動体１６７は、図１３と同様、車軸に車輪部を装着して構成され弁補助材１５６の側壁支持面よりも車輪部が数十から数百ミクロン突出するように配置され、車軸と車輪部間ないしは車軸と該弁補助材間で回転可能に構成されている。当然内圧縮室用の平板ゲート弁Ｌにも適用される。 The valve auxiliary member 156 shown in FIG. 18 is equipped with one or a plurality of rolling elements 167 such as rolling bearings. As in FIG. 13, the rolling element 167 is configured by mounting a wheel portion on the axle, and is disposed such that the wheel portion protrudes from the tens to hundreds of microns from the side wall support surface of the valve auxiliary member 156. It is configured to be rotatable between the parts or between the axle and the valve auxiliary material. Of course, this also applies to the flat gate valve L for the inner compression chamber.
このような実施例７の動作状態を図１９の（ａ）と（ｂ）図で説明する。（ａ）図は、圧縮室１５３圧力が流出室１４６ｄ圧力よりも低い状態を示しており、開口前の該平板ゲート弁Ｒは弁座の直線突起側壁面に着座して圧縮室の密閉状態が継続されている。 The operation state of the seventh embodiment will be described with reference to FIGS. 19 (a) and 19 (b). (A) The figure shows a state in which the pressure in the compression chamber 153 is lower than the pressure in the outflow chamber 146d, and the flat gate valve R before opening is seated on the side wall surface of the straight protrusion of the valve seat so that the compression chamber is sealed. It has been continued.
（ｂ）図は、圧縮室圧力が流出室圧力より上昇してその差圧により該平板ゲート弁Rが流出室側に押されると該転動体１６７が該側壁支持面１４８ｄと弁装着室側壁面間で挟み込まれる。その際、弁補助材１５６は直線突起１４７ｃに押されて背面室側に移動しているので、転動体の弁装着室側壁面上を転がる回転力が同時に接触している該平板ゲート弁Ｒにも回転速度が倍化されて伝わり背面室側に瞬時に移動する。その後、圧縮室内のガスが該弁補助材のガス通路１５６ｂから流出室に流出される。その際、背面室内に平板ゲート弁Rの移動に対する緩衝機構を設ければ衝突音は防止できることは容易に考えられる。 (B) The figure shows that when the compression chamber pressure rises above the outflow chamber pressure and the flat gate valve R is pushed to the outflow chamber side by the differential pressure, the rolling element 167 and the side wall surface of the valve mounting chamber are 148d. It is sandwiched between. At that time, since the valve auxiliary member 156 is pushed by the linear protrusion 147c and moves to the back chamber side, the rotational force rolling on the valve mounting chamber side wall surface of the rolling element simultaneously contacts the flat plate gate valve R. However, the rotation speed is doubled and it moves to the back chamber side instantly. Thereafter, the gas in the compression chamber flows out from the gas passage 156b of the valve auxiliary material to the outflow chamber. At that time, it is easily considered that a collision noise can be prevented if a buffer mechanism for the movement of the flat gate valve R is provided in the back chamber.
次に、前記吐出機構Ａの実施例１の一部を変更した実施例７について、図２０を用いて説明する。 Next, a seventh embodiment in which a part of the first embodiment of the discharge mechanism A is changed will be described with reference to FIG.
実施例１の図５と同様な弁装着室と背面室から構成される弁収納室に図７の平板ゲート弁Rを装着する構成に於いて、当該実施形態では、図７に代って図２０に示すような平板ゲート弁Ｒ１６８を用いる。 In the configuration in which the flat gate valve R of FIG. 7 is mounted in the valve storage chamber composed of the valve mounting chamber and the back chamber similar to FIG. 5 of the first embodiment, in this embodiment, FIG. A flat gate valve R168 as shown in FIG.
該平板ゲート弁Ｒ１６８が図７に示した実施例１の平板ゲート弁Rと異なる点は、
先端部１６８aに受圧面や風圧受面がなく側壁支持面１６８ｄのおよそ中央部にコ字状に掘り下げた先端部に抜ける凹溝１６８ｇ内に設けた圧縮室に連通する吐出孔１６８ｊを塞ぐようにリード弁１７６とそれを背面で支えるリテーナ１７７を装着して構成されている。当然内圧縮室用の吐出機構Ａや平板ゲート弁Ｌにも適用可能である。 The difference between the flat gate valve R168 and the flat gate valve R of the first embodiment shown in FIG.
There is no pressure receiving surface or wind pressure receiving surface at the distal end portion 168a so as to block the discharge hole 168j communicating with the compression chamber provided in the concave groove 168g that passes through the distal end portion dug into a substantially U shape at the center of the side wall support surface 168d. A reed valve 176 and a retainer 177 for supporting the reed valve 176 on the back are mounted. Of course, the present invention can also be applied to the discharge mechanism A and the flat gate valve L for the inner compression chamber.
該平板ゲート弁Ｒ１６８の先端部には圧縮室圧力が作用する空間がないので、常に直線突起７ｃの側壁面である平坦弁座に密着した状態にあり、圧縮室圧力が流出室圧力より上昇すると一般的なリード弁と同様に吐出孔１６８ｊからリード弁１７６を押し開けて圧縮されたガスが流出室内に流出することになる。 Since there is no space where the compression chamber pressure acts at the tip of the flat gate valve R168, it is always in close contact with the flat valve seat which is the side wall surface of the linear protrusion 7c, and the compression chamber pressure rises above the outflow chamber pressure. As with a general reed valve, the gas compressed by pushing the reed valve 176 through the discharge hole 168j flows out into the outflow chamber.
次に、前記吐出機構Ａの実施例１の一部を変更した実施例８について、図２１を用いて説明する。 Next, an eighth embodiment in which a part of the first embodiment of the discharge mechanism A is changed will be described with reference to FIG.
実施例１の図５と同様な弁装着室と背面室から構成される弁収納室に図７の平板ゲート弁Rを装着する構成に於いて、当該実施形態では、図７に代って図２１に示すような平板ゲート弁Ｒ１８８とその動作機構を用いる。 In the configuration in which the flat gate valve R of FIG. 7 is mounted in the valve storage chamber composed of the valve mounting chamber and the back chamber similar to FIG. 5 of the first embodiment, in this embodiment, FIG. A flat gate valve R188 as shown in FIG. 21 and its operation mechanism are used.
該平板ゲート弁Ｒ１６８が図７に示した実施例１の平板ゲート弁Rと異なる点は、先端部の風圧受面や側壁シール面と側壁支持面を連通する孔がないことなど、全体的に簡素化された構成となっている。その代わりに平板ゲート弁R１８８と平板ゲート弁Ｌ１８９を弁座である直線突起７ｃの側壁面から離脱させて開口動作を補助する機構として、前者には回転円盤１９６を装着し、後者には回転円盤１９６とそれの間に補助円盤１９８を別途装着している。 The flat gate valve R168 is different from the flat plate gate valve R of the first embodiment shown in FIG. 7 in that the wind pressure receiving surface at the front end and the side wall seal surface and the side wall support surface are not communicated. It has a simplified configuration. Instead, as a mechanism for assisting the opening operation by separating the flat gate valve R188 and the flat gate valve L189 from the side wall surface of the linear protrusion 7c as a valve seat, the former is equipped with a rotating disk 196, and the latter is equipped with a rotating disk. 196 and an auxiliary disk 198 are separately mounted between them.
図２１に示すように、固定シリンダに固定された軸部を回転中心にして回転自在に軸着された該回転円盤１９６の中心から旋回半径離れた位置に一端を旋回ピストンの旋回ディスクに固定した旋回ピン１９７を軸着し、その外周部のおよそ半周の径を小さくして固定シリンダの円筒空間に遊装している。そして、外圧縮室用の平板ゲート弁Ｒ１８８に用いる場合には、弁装着室１８６ｈと該平板ゲート弁Ｒの側壁面間の隙間の範囲内でしかも平板ゲート弁Ｒが直線突起７ｃに押されて背面室側に移動する範囲内に於いて、該回転円盤１９６の外周部の一部を突出させている。 As shown in FIG. 21, one end is fixed to the turning disc of the turning piston at a position away from the turning radius from the center of the rotating disk 196 rotatably mounted around the shaft fixed to the fixed cylinder. A swivel pin 197 is attached to the shaft, and the diameter of the outer periphery of the swivel pin 197 is reduced so that the pin is mounted in the cylindrical space of the fixed cylinder. When the flat gate valve R188 for the outer compression chamber is used, the flat gate valve R is pushed by the linear protrusion 7c within the gap between the valve mounting chamber 186h and the side wall surface of the flat gate valve R. A part of the outer peripheral portion of the rotating disk 196 is protruded within the range of movement to the back chamber side.
なお、旋回ピストンの旋回半径で回転する該旋回ピン１９７の外側に該回転円盤１９６の外径を設けているので、その外径の周速度は旋回突起の最大速度よりも大きくなる。 Since the outer diameter of the rotating disk 196 is provided outside the swivel pin 197 that rotates at the swivel radius of the swivel piston, the peripheral speed of the outer diameter is greater than the maximum speed of the swivel protrusion.
内圧縮室用の平板ゲート弁Ｌ１８９に用いる場合には、該回転円盤１９６と平板ゲート弁Ｌ１８９との間に、該回転円盤１９６の外径と摺接するように固定シリンダに固定された回転用軸心を有する補助円盤１９８を装着している。そして、弁装着室１８６ｈと該平板ゲート弁Ｌの側壁面間の隙間の範囲内で該補助円盤１９８の外周部の一部を突出させるが、該補助円盤１９８に回転円盤１９６から回転力が伝わるのは、平板ゲート弁Ｌが直線突起７ｃに押されて背面室側に移動する範囲内に於いてである。 When used for the flat gate valve L189 for the inner compression chamber, a rotary shaft fixed to a fixed cylinder so as to be in sliding contact with the outer diameter of the rotary disc 196 between the rotary disc 196 and the flat gate valve L189. An auxiliary disk 198 having a heart is attached. A part of the outer peripheral portion of the auxiliary disk 198 protrudes within the gap between the valve mounting chamber 186h and the side wall surface of the flat gate valve L, and the rotational force is transmitted from the rotating disk 196 to the auxiliary disk 198. This is within a range in which the flat gate valve L is pushed by the linear protrusion 7c and moves to the back chamber side.
実施例８の動作を以下で説明する。旋回突起７ｃに平板ゲート弁Ｒが押されて背面室側に移動している状態に於いて、外圧縮室１３圧力が流出室１８６ｄの圧力よりも上昇すると、その差圧力に押されて平板ゲート弁Ｒ１８８が流出室側に移動して側壁支持面が該平板ゲート弁Ｒよりも速い速度の周速で回転している該回転円盤１９６に接触すると瞬時に該平板ゲート弁Ｒが背面室側に押上げられてガス通路が開口する。 The operation of the eighth embodiment will be described below. When the pressure of the outer compression chamber 13 is higher than the pressure of the outflow chamber 186d in a state where the flat gate valve R is pushed by the swiveling projection 7c and moves to the back chamber side, the flat gate is pushed by the differential pressure. When the valve R188 moves to the outflow chamber side and the side wall support surface comes into contact with the rotating disk 196 rotating at a higher peripheral speed than the flat plate gate valve R, the flat plate gate valve R is instantaneously moved to the back chamber side. The gas passage is opened by being pushed up.
内圧縮室１４が流出室１８６ｄの圧力よりも上昇した場合も同様であり、該平板ゲート弁Ｌよりも速い速度の周速で回転している該補助円盤１９８に接触すると瞬時に該平板ゲート弁Ｌが背面室側に押上げられてガス通路が開口することになる。 The same applies to the case where the inner compression chamber 14 rises above the pressure in the outflow chamber 186d. When the inner compression chamber 14 comes into contact with the auxiliary disk 198 rotating at a higher peripheral speed than the plate gate valve L, the plate gate valve is instantaneously contacted. L is pushed up to the back chamber side, and the gas passage is opened.
次に、前記吐出機構Ａを代表する実施例１の一部を変更して吐出機構Ｂとした実施例９について、図２２から図２４を用いて説明する。 Next, a ninth embodiment in which a part of the first embodiment representing the discharge mechanism A is changed to a discharge mechanism B will be described with reference to FIGS.
該吐出機構Ａと該吐出機構Ｂの主な違いは、直線突起７ｃを挟んで対向して設ける板状弁体とその補機部材で構成される弁機構体の特に動作が大きく異なっている。以下、具体的な構成とその機能について説明する。 The main difference between the discharge mechanism A and the discharge mechanism B is that the operation of the valve mechanism body constituted by the plate-like valve body provided opposite to the linear protrusion 7c and the auxiliary member is particularly different. Hereinafter, a specific configuration and its function will be described.
図２２は吐出機構Ｂ２１２の構成部位を拡大した断面図を示し、図２３は該吐出機構Ｂ用のフラップ弁２１８とその関連部材を分解した外観斜視図を示しており、図２４は該吐出機構Ｂの動作状態の説明図である。以下、外圧縮室用に適用されるフラップ弁Ｒ２０８の構成について説明するが、内圧縮室用のフラップ弁Ｌ２０９にも適用可能である。 FIG. 22 is an enlarged cross-sectional view of a component part of the discharge mechanism B212, FIG. 23 is an external perspective view in which the flap valve 218 for the discharge mechanism B and its related members are disassembled, and FIG. It is explanatory drawing of the operation state of B. Hereinafter, the configuration of the flap valve R208 applied to the outer compression chamber will be described, but the configuration can also be applied to the flap valve L209 for the inner compression chamber.
図２２に示すように、直線突起７ｃを挟んで対称的に内外圧縮室１３と１４それぞれの弁装着室２０６ｈ内に直方体の弁台座２１０を遊挿し、該直線突起７ｃ側壁面に面接触可能でおよそ凸形状の先端面とその反対側の背面室側も凸円弧形状をした円弧中央部に弁装着室の側壁面に平行なピン用穴を設けたフラップ弁Ｒ２０８を該弁台座２１０に固定された回転ピン２１６に装着している。 As shown in FIG. 22, a rectangular parallelepiped valve seat 210 is loosely inserted into the valve mounting chambers 206h of the inner and outer compression chambers 13 and 14 symmetrically across the linear protrusion 7c, and can come into surface contact with the side wall surface of the linear protrusion 7c. A flap valve R208 provided with a pin hole parallel to the side wall surface of the valve mounting chamber is fixed to the valve seat 210 at the central portion of the circular arc having a convex arc shape on the opposite front end surface and the back chamber side on the opposite side. The rotating pin 216 is attached.
また、図２３に示すように、該弁台座２１０上で該フラップ弁Ｒと弁装着室２０６ｈの流出室側壁面との間に該弁台座に固定したセットピン２１９に装着されたゼンマイのような側面バネ２１８と該弁台座と前記固定シリンダ間に装着した背面バネ２１７から構成される外圧縮室用弁機構体に内圧縮室用と対にして吐出機構Ｂ２１２が構成されている。 Further, as shown in FIG. 23, like the mainspring mounted on the set pin 219 fixed to the valve seat between the flap valve R and the outflow chamber side wall surface of the valve mounting chamber 206h on the valve seat 210. A discharge mechanism B212 is configured as a pair for the inner compression chamber and a valve mechanism for the outer compression chamber, which is composed of a side spring 218 and a back spring 217 mounted between the valve seat and the fixed cylinder.
上記の如くフラップ弁Ｒ２０８とフラップ弁Ｌ２０９で構成された吐出機構B２１２の動作について図２４の（ａ）図と（ｂ）図を用いて説明する。（ａ）図では、駆動軸の回転に伴い外圧縮室２１３の圧力が流出室２０６ｃ圧力よりも上昇すると側壁面の広い受圧面積による差圧がフラップ弁Ｒ２０８の前後に作用して弾性の範囲で側面バネ２１８を変形させながら回転ピン２１６回りに回転することで、弁座である直線突起７ｃ側壁面から該スラップ弁Ｒ先端部が瞬時に離れて該先端部の隙間から流出室に向けて圧縮室のガスが流出する。その際、該弁台座２１０は直線突起７ｃ側壁面に摺接した状態が保持される。 The operation of the discharge mechanism B212 constituted by the flap valve R208 and the flap valve L209 as described above will be described with reference to FIGS. 24 (a) and 24 (b). (A) In the figure, when the pressure in the outer compression chamber 213 rises above the pressure in the outflow chamber 206c with the rotation of the drive shaft, the differential pressure due to the wide pressure-receiving area on the side wall surface acts on the front and rear of the flap valve R208 and is within an elastic range. By rotating around the rotation pin 216 while deforming the side spring 218, the tip of the slap valve R is instantaneously separated from the side wall surface of the linear protrusion 7c, which is a valve seat, and compressed toward the outflow chamber from the gap of the tip. Chamber gas flows out. At this time, the valve pedestal 210 is held in a state of sliding contact with the side wall surface of the linear protrusion 7c.
また、内圧縮室２１４用のフラップ弁Ｌ２０９は圧縮室圧力が流出室圧力よりも低い状態なので、座面である直線突起７ｃ側壁面に先端部が摺接している。一方（ｂ）図では、内圧縮室圧力が流出室圧力よりも上昇して外圧縮室用フラップ弁Ｒと同様にフラップ弁Ｌ２０９が動作した状態を表わしている。 In addition, since the flap valve L209 for the inner compression chamber 214 is in a state where the compression chamber pressure is lower than the outflow chamber pressure, the tip end portion is in sliding contact with the side wall surface of the linear protrusion 7c that is the seat surface. On the other hand, FIG. 4B shows a state in which the inner compression chamber pressure is higher than the outflow chamber pressure and the flap valve L209 is operated in the same manner as the outer compression chamber flap valve R.
次に、前記実施例１のリング式の容積型圧縮機と異なるスクロール式圧縮機に適用した吐出機構Ｃとしての実施例１０について、図２５から図３５を用いて説明する。 Next, a tenth embodiment as a discharge mechanism C applied to a scroll compressor different from the ring-type positive displacement compressor of the first embodiment will be described with reference to FIGS.
前記吐出機構Ａ、吐出機構Ｂおよび吐出機構Ｃの主な違いは、旋回ピストンの直線突起を挟んで対向して設ける板状弁体の形状にある。すなわち、前者の平板ゲート弁やフラップ弁は直方体の板状弁体を基本としているが、後者は板を円弧状に曲げて形成されている点が大きく異なっている。以下、具体的な構成とその機能について説明する。 The main difference between the discharge mechanism A, the discharge mechanism B, and the discharge mechanism C is in the shape of a plate-shaped valve body that is provided facing the linear protrusion of the orbiting piston. That is, the former flat gate valve and flap valve are based on a rectangular parallelepiped plate-like valve body, but the latter is greatly different in that it is formed by bending the plate into an arc. Hereinafter, a specific configuration and its function will be described.
図２５にスクロール式容積型圧縮機３０１の縦断面図を示し、図２５のＦ－Ｆ線断面図を図２６に示す。その圧縮機構部を構成する主要部材である旋回スクロールすなわち旋回ピストン３０７の平面図を図２７に示し、固定スクロールすなわち固定シリンダ３０６の平面図を図２８に示す。 FIG. 25 is a longitudinal sectional view of the scroll positive displacement compressor 301, and FIG. 26 is a sectional view taken along line FF of FIG. FIG. 27 shows a plan view of the orbiting scroll, or orbiting piston 307, which is the main member constituting the compression mechanism, and FIG. 28 shows a plan view of the fixed scroll or fixed cylinder 306.
スクロール式容積型圧縮機３０１は、図２５と図２６に示すように、密閉容器３０２内に固定されたフレーム３２１上に装着した固定シリンダ３０６とそれらの間に旋回ピストン３０７と旋回機構３２０を設けた中央部のフレームの軸受に支持された駆動軸３２２の下部を電動機３２３に直結して構成されている。 25 and 26, the scroll type positive displacement compressor 301 is provided with a fixed cylinder 306 mounted on a frame 321 fixed in an airtight container 302, and a swing piston 307 and a swing mechanism 320 between them. The lower part of the drive shaft 322 supported by the bearing of the central frame is directly connected to the electric motor 323.
図２６に示すように、圧縮室は固定シリンダのコ字の底部を下にした断面の包絡溝３０６a内に等厚板を曲げて成形した旋回ピストンの旋回突起３０７ａを遊挿して互いの側壁間に形成される三日月状空間の上下を固定端板３０６ｂと旋回ディスク３０７eで蓋をして閉じた密閉空間として複数形成される。 As shown in FIG. 26, in the compression chamber, a swiveling projection 307a of a swiveling piston formed by bending a constant thickness plate into an envelope groove 306a having a cross-section with the U-shaped bottom portion of the fixed cylinder down is loosely inserted between the side walls. A plurality of sealed spaces are formed by closing the upper and lower sides of the crescent-shaped space formed by the closed end plate 306b and the swivel disc 307e.
旋回ピストン３０７の形状は、図２７の平面図に示すように、帯状等厚板を渦巻き状に曲げて形成した渦巻き突起３０７ｂを主体とする旋回突起３０７ａをおよそ円形で剛性を有する板状の旋回ディスク３０７ｄの片面側に直立させ、その反対側のおよそ中央に駆動軸の偏心軸に枢結する軸受ボスを設けて構成される。該旋回ピストン３０７は、軸受ボスに挿入され駆動軸３２２の偏心軸と該旋回ピストンに装着された旋回機構３２０とで自転のない公転運動すなわち旋回運動を行う。 As shown in the plan view of FIG. 27, the swiveling piston 307 has a plate-like swiveling shape having a swirling protrusion 307a mainly composed of a swirling protrusion 307b formed by bending a belt-like equal thickness plate in a spiral shape. The disk 307d is erected on one side, and a bearing boss that is pivotally connected to the eccentric shaft of the drive shaft is provided at approximately the center on the opposite side. The orbiting piston 307 is inserted into the bearing boss and performs a revolving motion without rotation, that is, an orbiting motion, by the eccentric shaft of the drive shaft 322 and the swiveling mechanism 320 attached to the orbiting piston.
また、渦巻き突起３０７ｂと同一の矩形断面で中央側の端部を接線方法に直線的に旋回半径の２倍以上の長さと同じ高さで延長させ旋回ディスク３０７ｄに直立させた直線突起３０７ｃとで旋回突起３０７ａが構成される。 In addition, a straight protrusion 307c having the same rectangular cross section as that of the spiral protrusion 307b and extending in the tangential manner linearly at a height equal to or more than twice the length of the turning radius and standing upright on the turning disk 307d. A turning protrusion 307a is configured.
加えて、渦巻き突起３０７ｂは、外側のＰ点からＱ点の間はインボリュート曲線で、Ｑ点からＲ点の間は該インボリュート曲線との接続部が同一接線でインボリュート曲線の伸開線半径よりも円弧半径を小さくした円弧曲線の２つの曲線で形成され、その先のＲ点からＳ点間の前記直線突起３０７ｃとで旋回突起３０７ａが形成されている。 In addition, the spiral protrusion 307b is an involute curve between the outer P point and the Q point, and the connection portion with the involute curve is the same tangent between the Q point and the R point, and is larger than the extended radius of the involute curve. A circular protrusion 307a is formed by two straight curved lines having a reduced arc radius and the straight protrusion 307c between the R point and the S point.
固定シリンダ３０６の形状は、図２８の平面形状に示すように、旋回突起３０７ａの旋回運動で形成される包絡線を壁面として得られる一定幅の包絡溝３０６ａを厚い板厚の固定端板３０６ｂの片面に設け、包絡溝３０６ａの外周側一端に作動ガスの流入室３０６ｃを内周側に流出室３０６ｅを包絡溝３０６ａと同一底面を有して設けてられており、該包絡溝３０６ａと流入室３０６ｃと流出室３０６ｅそれぞれに吸入孔３０６ｄと吐出孔３０６ｎが設けられている。なお、該流出室３０６eは該直線突起３０７ｃの包絡溝として最小幅が決まるのでおよそ直線溝として形成される。 As shown in the planar shape of FIG. 28, the fixed cylinder 306 has a constant width envelope groove 306a obtained by using the envelope formed by the swiveling motion of the swiveling protrusion 307a as a wall surface. A working gas inflow chamber 306c is provided at one end on the outer peripheral side of the envelope groove 306a, and an outflow chamber 306e is provided on the inner peripheral side with the same bottom surface as the envelope groove 306a. A suction hole 306d and a discharge hole 306n are provided in 306c and the outflow chamber 306e, respectively. The outflow chamber 306e is formed as a straight groove because the minimum width is determined as the envelope groove of the straight protrusion 307c.
当該図の中央には、該包絡溝３０６ａおよび流出室３０６ｅと同一底面で該包絡溝幅のおよそ２倍以上の直径で円筒形状の外壁の一部を該包絡溝の内外側壁面に接続させて包絡溝幅で開口する円筒内壁の内側には該円筒内壁の円弧と同一中心を有する円弧形状の外壁の２箇所を該流出室の側壁面に接続させて形成されるＵ字塔３０６ｋの外壁と該円筒内壁との間に形成される部分的なリング状の矩形断面溝で形成され該流出室を挟んで対向して配置された円弧溝形状の２箇所の弁装着室３０６ｈの中間に設けた背面室３０６ｊとでリング状の弁収納室３０６ｇが形成されている。 In the center of the figure, a part of a cylindrical outer wall having a diameter of about twice or more the width of the envelope groove on the same bottom surface as the envelope groove 306a and the outflow chamber 306e is connected to the inner and outer wall surfaces of the envelope groove. An outer wall of a U-shaped tower 306k formed by connecting two places of an arc-shaped outer wall having the same center as the arc of the inner wall of the cylinder to the side wall surface of the outflow chamber, is formed on the inner side of the inner wall of the cylinder opening with an envelope groove width. Provided in the middle of two arc groove-shaped valve mounting chambers 306h formed by a partial ring-shaped rectangular cross-sectional groove formed between the cylindrical inner wall and opposed to each other across the outflow chamber A ring-shaped valve storage chamber 306g is formed with the back chamber 306j.
それぞれの弁装着室３０６ｈ内には細孔の注油孔３０６ｑが開口し、背面室３０６ｊ内には流出室３０６ｃないしは吐出空間３２５に連通する圧導入孔３０６ｎが開口し、リング状該弁収納室の中央部にはピン穴３０６ｍが２箇所設けられている。 Each of the valve mounting chambers 306h has a fine oil supply hole 306q, and the back chamber 306j has an outflow chamber 306c or a pressure introduction hole 306n communicating with the discharge space 325. Two pin holes 306m are provided in the center.
次に、図２６の中央部に３１２矢視で示した吐出機構Cの拡大図である図２９と図２９の矢視した中心線Gに沿って展開した断面図である図３０および板状弁体である円弧ゲート弁R３０８の形状を示した図３１を用いて、該吐出機構C３１２の構成と機能を詳しく説明する。以下、外圧縮室用に適用される円弧ゲート弁R３０８の構成を中心に説明するが、
直線突起３０７ｃを挟んで左右対称に構成された内圧縮室用の円弧ゲート弁L３０９にも適用可能である。 Next, FIG. 29 which is an enlarged view of the discharge mechanism C indicated by the arrow 312 in the center of FIG. 26 and FIG. 30 which is a cross-sectional view developed along the center line G indicated by the arrow in FIG. The configuration and function of the discharge mechanism C312 will be described in detail with reference to FIG. 31 showing the shape of the arc gate valve R308 which is a body. Hereinafter, the description will focus on the configuration of the arc gate valve R308 applied to the outer compression chamber.
The present invention is also applicable to an arc gate valve L309 for the inner compression chamber that is configured symmetrically with respect to the straight protrusion 307c.
図２９に示すように、直線突起７ｃを挟んで対称的に内外圧縮室３１３と３１４用それぞれの弁装着室３０６ｈ内外壁面および上下端面間に微小な隙間を設けて摺動可能とするとともに直線突起３０７ｃ両側壁面に摺接する円弧ゲート弁R３０８と円弧ゲート弁L３０９を装着し、背面室３０６ｊ内にセットピン３１６で位置決めして配置した中間部材３１１と該円弧ゲート弁との間に背面バネ３１０を装着するとともに包絡溝３０６ａや流出室３０６ｅおよび弁装着室３０６ｈの端面を前記旋回ディスク３０７ｄ端面で塞いで吐出機構C３１２が構成されている。 As shown in FIG. 29, the linear projection 7c is slidably provided with a small gap between the inner and outer wall surfaces and upper and lower end surfaces of the valve mounting chambers 306h for the inner and outer compression chambers 313 and 314 with the linear projection 7c interposed therebetween. 307c Arc gate valve R308 and arc gate valve L309 which are in sliding contact with both wall surfaces are mounted, and a back spring 310 is mounted between the intermediate member 311 positioned by a set pin 316 in the back chamber 306j and the arc gate valve. At the same time, the end surfaces of the envelope groove 306a, the outflow chamber 306e, and the valve mounting chamber 306h are closed by the end surface of the swivel disk 307d to constitute the discharge mechanism C312.
但し、該背面バネ３１０は該円弧ゲート弁R３０８と円弧ゲート弁L３０９の動作の補助ないしは衝撃を緩衝する部材であり、他の弾性体で置き換えることは可能である。なお、図３０の固定シリンダの固定端板３０６ｂに設けた係止部材３３０などによる係止機構の構成と機能は前記図６と図９と同一なのでここでは説明を省略する。 However, the back spring 310 is a member that cushions the assistance or shock of the operation of the arc gate valve R308 and the arc gate valve L309, and can be replaced with another elastic body. The configuration and function of the locking mechanism using the locking member 330 provided on the fixed end plate 306b of the fixed cylinder in FIG. 30 are the same as those in FIGS.
図３１の（a）図に円弧ゲート弁R３０６の上端面形状を示し、（ｂ）図に（ａ）図の右側から見た側面図を示す。（ａ）図の内外側壁面を示す側壁シール面３０８ｃと側壁支持面３０８ｄの円弧形状は、周方向の長さが１／４周前後から半周以下の範囲の円弧で形成され、前記弁装着室３０６ｈに微小な隙間を設けて装着できる形状となっている。 FIG. 31A shows the shape of the upper end surface of the arc gate valve R306, and FIG. 31B shows a side view seen from the right side of FIG. (A) The arc shape of the side wall seal surface 308c and the side wall support surface 308d showing the inner and outer wall surfaces in the figure is formed by an arc having a circumferential length in the range from about 1/4 turn to less than half turn. It has a shape that can be mounted with a small gap in 306h.
その上端面３０８eに窪んだ油受穴３０８ｍと先端部３０８ａに設けた先端油溝３０８ｐとを連結する油導入孔３０８ｎが設けられており、圧縮室圧力が吐出圧力よりも低い状態において、固定シリンダの注油孔３０６ｑから該油受孔３０８ｓに差圧により間欠的に供給された油が該油導入孔を介して先端油溝３０８ｐに入り、先端部や側壁シール面ないしは摺接する各部位のシールや潤滑に用いられる。 An oil introduction hole 308n that connects an oil receiving hole 308m recessed in the upper end surface 308e and a tip oil groove 308p provided in the tip portion 308a is provided, and in a state where the compression chamber pressure is lower than the discharge pressure, the fixed cylinder The oil intermittently supplied from the oil injection hole 306q to the oil receiving hole 308s by the differential pressure enters the tip oil groove 308p through the oil introduction hole, and seals the tip part, the side wall seal surface or each part in sliding contact with each other. Used for lubrication.
（ａ）図に示す先端部３０８ａのＲ形状は、直線突起３０７ｃの側壁面に摺接する該先端部の形状を形成する方法は模式図で示した図３２から与えられる。図３２は、該弁装着室３０６ｈと包絡溝３０６ａおよび流出室３０６ｅの内外側壁面と旋回運動をする直線突起３０７ｃ側壁面との関係を示している。これらの関係とリング状の弁収納室３０６ｇの溝中心線を示した図中の一点鎖線と矢視で示したＡ点からＤ点の位置関係を用いてＲ形状の形成方法を説明する。 (A) The R shape of the tip portion 308a shown in the figure is given from FIG. 32, which is a schematic diagram showing the method of forming the shape of the tip portion that is in sliding contact with the side wall surface of the linear protrusion 307c. FIG. 32 shows the relationship between the valve mounting chamber 306h, the envelope groove 306a, the inner and outer wall surfaces of the outflow chamber 306e, and the side wall surface of the linear protrusion 307c that makes a swiveling motion. A method of forming the R shape will be described using these relationships and the positional relationship from the point A to the point D indicated by the arrows in the figure showing the groove center line of the ring-shaped valve storage chamber 306g.
図３２のＡ点は直線状の流出室外壁と円弧状の溝である弁装着室内壁の交点、Ｂ点は該溝中央線と包絡溝外壁の交点、そしてＣ点は該溝中央線と包絡溝内壁に直線突起３０７ｃの厚さを加えた側壁面との交点を示している。一点鎖線ＥＯを該包絡溝ないしは流出室の中央線とした場合、Ｄ点は∠ＥＯＧの角度と等しい角度である∠ＨＯＦを∠ＥＯＦの角度に加えた線ＯＨと円弧状の弁装着室外壁との交点を示している。これらＡ点、Ｂ点およびＤ点を通るおよそ中央を凸とする円弧ないしは放物線で円弧ゲート弁R３０８の先端部３０８aの形状を形成する。円弧ゲート弁L３０９の先端部も同様である。 32, point A is the intersection of the straight outflow chamber outer wall and the valve mounting chamber wall that is an arc-shaped groove, point B is the intersection of the groove center line and envelope groove outer wall, and point C is the groove center line and envelope. The intersection with the side wall surface which added the thickness of the linear protrusion 307c to the groove inner wall is shown. When the alternate long and short dash line EO is the center line of the envelope groove or the outflow chamber, the point D is the line OH obtained by adding で HOF, which is equal to the angle of ∠EOG, to the angle of ∠EOF, and the outer wall of the arcuate valve mounting chamber The intersection of The shape of the tip portion 308a of the arc gate valve R308 is formed by an arc or a parabola that protrudes from the A point, the B point, and the D point and has a convex center. The same applies to the tip of the arc gate valve L309.
なお、図２９に示した直線突起３０７ｃの長さは、図３２に示した円弧ゲート弁Rの先端部のＢ点が該直線突起面から離脱しないように旋回半径の２倍に円弧ゲート弁R先端部のＡ点とＢ点間の距離を加えた長さが最小限必要となる。 The length of the linear protrusion 307c shown in FIG. 29 is set to be twice the turning radius so that the point B at the tip of the circular gate valve R shown in FIG. The minimum length including the distance between the points A and B at the tip is required.
また、前記平板ゲート弁と同様、該円弧ゲート弁Ｒと円弧ゲート弁Ｌも包絡溝３０６ａ側の弁装着室３０６ｈ側壁面に面接触して摺動する側壁シール面や側壁支持面に一段凹ました非摺接面である段差面である圧力ポケットを設けることで動作性や摺動性が向上する。 As with the flat gate valve, the arc gate valve R and arc gate valve L are also recessed one step on the side wall seal surface and side wall support surface that slide in contact with the side wall surface of the valve mounting chamber 306h on the envelope groove 306a side. By providing a pressure pocket which is a step surface which is a non-sliding contact surface, operability and slidability are improved.
図３３の（a）図に中間部材３１１の上面図を示し、（ｂ）図に（ａ）図の円弧内側から見た側面図を示す。（ａ）図に見られるように背面室３０６ｊに収納可能な円弧形状となっており、上面３１１ｅには背面室底面の定位置に装着するためのピン穴３１１ｆを設け、両側壁端面３１１ｃにはバネ穴３１１ｄが複数設けられている。 33A shows a top view of the intermediate member 311, and FIG. 33B shows a side view of the intermediate member 311 as viewed from the inside of the arc in FIG. (A) As shown in the figure, it has an arc shape that can be accommodated in the back chamber 306j. The top surface 311e is provided with a pin hole 311f for mounting at a fixed position on the bottom surface of the back chamber, and both side wall end surfaces 311c are provided. A plurality of spring holes 311d are provided.
図３４は、背面室３０６ｊ内圧力に対する圧力制御機構を示している。（ａ）図は圧縮機運転前の流入室と吐出空間の圧力が等しい状態にあり制御弁３１７動作前の状態図を示し、（ｂ）は圧縮機運転後の流入室よりも吐出空間圧力が十分に高くなった状態にあり制御弁３１７が動作して背面室と圧縮室が連通した状態を示している。 FIG. 34 shows a pressure control mechanism for the pressure in the back chamber 306j. (A) The figure shows the state before the operation of the control valve 317 in the state where the pressure in the inflow chamber and the discharge space before the compressor operation is equal, and (b) shows the discharge space pressure more than the inflow chamber after the compressor operation. In this state, the control valve 317 is in a sufficiently high state and the back chamber and the compression chamber communicate with each other.
以下、前記吐出機構Ｃ３１２を用いた実施例１０の機能や動作を、図３５を用いて説明する。（ａ）図から（ｄ）図へと順に駆動軸に同期して旋回ピストンが９０°ピッチで回転した状態を表わしている。外圧縮室３１３に対する吐出機構Ｃの動作を中心に説明するが、内圧縮室３１４にも同様に適用可能である。 Hereinafter, functions and operations of the tenth embodiment using the discharge mechanism C312 will be described with reference to FIG. From (a) to (d), the swivel piston is rotated at a 90 ° pitch in synchronization with the drive shaft. The operation of the discharge mechanism C with respect to the outer compression chamber 313 will be mainly described, but the same applies to the inner compression chamber 314 as well.
図３５の（ａ）図は、外圧縮室３１３圧力が背面室３０６ｊの圧力より低い区間であり、直線突起３０７ｃの先端部は図中の矢印の如く動作して円弧ゲート弁Ｒ３０８を弁装着室３０６ｈ内に押し込み、該円弧ゲート弁Ｒの先端部３０８ａは直線突起３０７ｃの側壁面に密着していることと圧縮室側の側壁シール面３０８ｃは圧力差の関係から弁装着室３０６ｈ側壁面に密着していることから圧縮室と流出室間および背面室間のシール性が確保された状態で作動ガスの圧縮が継続される。 FIG. 35 (a) is a section in which the pressure in the outer compression chamber 313 is lower than the pressure in the back chamber 306j, and the tip of the linear protrusion 307c operates as shown by the arrow in the figure to connect the arc gate valve R308 to the valve mounting chamber. The tip 308a of the arc gate valve R is in close contact with the side wall surface of the linear protrusion 307c and the side wall seal surface 308c on the compression chamber side is in close contact with the side wall surface of the valve mounting chamber 306h. Therefore, the compression of the working gas is continued in a state where the sealing performance between the compression chamber and the outflow chamber and between the back chamber is ensured.
次の（ｂ）図では、外圧縮室３１３の圧縮行程が進み吐出行程に入る状態を示している。すなわち、外圧縮室用の円弧ゲート弁Ｒの先端部３０８ａに作用する圧力が背面室３０６ｊの圧力よりも大きくなり該円弧ゲート弁Ｒ先端部が直線突起３０７ｃの弁座である側壁面から離脱して背面室側に移動することで該先端部が直線突起と同じ移動方向で開口し外圧縮室３１３内の作動ガスが該流出室から吐出空間に流出される。 In the next figure (b), a state is shown in which the compression stroke of the outer compression chamber 313 advances and enters the discharge stroke. That is, the pressure acting on the distal end portion 308a of the arc gate valve R for the outer compression chamber becomes larger than the pressure in the back chamber 306j, and the distal end portion of the arc gate valve R is detached from the side wall surface that is the valve seat of the linear protrusion 307c. By moving to the back chamber side, the tip end portion opens in the same movement direction as the linear protrusion, and the working gas in the outer compression chamber 313 flows out from the outflow chamber to the discharge space.
このような状態に於いて、背面室３０６ｊ圧力を流出室３０６ｅ圧力よりも動圧ないしは通路抵抗分低い圧力を導入している構成では、外圧縮室と該流出室との差圧が殆どない状態で開口するので、外圧縮室圧力が流出室よりも上昇する過圧縮現象の発生はない。 In such a state, in the configuration in which the pressure in the back chamber 306j is lower than the pressure in the outflow chamber 306e or the pressure lower than the outflow chamber 306e, there is almost no differential pressure between the outer compression chamber and the outflow chamber. Therefore, there is no occurrence of an overcompression phenomenon in which the outer compression chamber pressure rises higher than the outflow chamber.
外圧縮室３１３の吐出行程終了直後の（ｃ）図では、直線突起３０７ｃが包絡溝３０６ａの側壁面に近接して外圧縮室の空間が少ない状態で円弧ゲート弁Ｒ３０８が弁装着室と背面室内に収納され、旋回運動の関係から該直線突起の側壁面に垂直な方向の移動速度は包絡溝中央で最大となった後は減少して包絡溝側壁面に最接近した状態では殆ど０となる。 In FIG. 10C immediately after the end of the discharge stroke of the outer compression chamber 313, the arcuate gate valve R308 is located in the valve mounting chamber and the rear chamber in a state where the linear protrusion 307c is close to the side wall surface of the envelope groove 306a and there is little space in the outer compression chamber. The moving speed in the direction perpendicular to the side wall surface of the linear protrusion is maximized at the center of the envelope groove and becomes almost zero in the state closest to the envelope groove side wall surface because of the swiveling motion. .
（ｃ）図の状態から直線突起３０７ｃが図中の矢印の如く移動して包絡溝の外圧縮室を形成する側壁面から最接近直後の次の瞬間には外圧縮室の圧力は瞬時に低圧に変化するが、円弧ゲート弁Ｒの先端部が直線突起側壁面間直にあり、該先端部に外圧縮室の低圧が流入して背面室圧力との大きな差圧力と背面室のバネ３１０力により該円弧ゲート弁Ｒが直線突起側壁面に瞬時に着座するので、外圧縮室と流出室間を瞬時に遮断して該円弧ゲート弁Ｒの閉じ遅れがなく作動ガスの流出室から圧縮室への逆流も阻止できる上に該円弧ゲート弁Ｒの着座による衝撃もないので音や部材の損傷の問題もない。 (C) The pressure in the outer compression chamber is instantaneously reduced at the next moment immediately after the closest approach from the side wall surface where the linear protrusion 307c moves as shown by the arrow in the drawing to form the outer compression chamber of the envelope groove. However, the tip of the arc gate valve R is directly between the side walls of the straight protrusions, and the low pressure of the outer compression chamber flows into the tip, and a large differential pressure from the back chamber pressure and the spring 310 force of the back chamber As a result, the arc gate valve R is instantly seated on the side wall surface of the linear protrusion, so that the outer compression chamber and the outflow chamber are instantaneously blocked, and there is no delay in closing the arc gate valve R to the compression chamber from the working gas outflow chamber. In addition, since there is no impact due to the seating of the arc gate valve R, there is no problem of sound or damage to members.
また、吐出行程終了直後に問題となる再圧縮損失の原因の一つである死空間は、円弧ゲート弁ＲとＬの先端部隙間と直線突起側壁間に挟まれた空間に相当するが、図３２で説明したように適正な先端部の円弧形状の設定からその空間は少なくできる。 In addition, the dead space that is one of the causes of recompression loss that becomes a problem immediately after the end of the discharge stroke corresponds to a space sandwiched between the gaps between the tip ends of the arc gate valves R and L and the side walls of the linear protrusions. As described in 32, the space can be reduced by setting an appropriate arc shape of the tip.
さらに回転した（ｄ）図では、内圧縮室３１４の圧縮が進み圧力が背面室圧力より高くな
り吐出行程に入る状態を示しており、内圧縮室用の円弧ゲート弁Ｌ３０９の先端部３０９ａに作用する圧力が背面室の圧力よりも大きくなり該円弧ゲート弁Ｌの先端部が直線突起の側壁面から離脱して該背面室側に移動することで直線突起の移動方向と同じ方向で開口し圧縮室の作動ガスが流出室に流出する。以上の如く、内圧縮室３０９用円弧ゲート弁Ｌの動作は外圧縮室３０８用円弧ゲート弁Ｒと基本的に同様であるが、動作のタイミングは（ｂ）と（ｄ）図で示したように異なる。 Further, FIG. 6 (d) shows a state in which the compression of the inner compression chamber 314 advances and the pressure becomes higher than the back chamber pressure and enters the discharge stroke, and acts on the distal end portion 309a of the arc gate valve L309 for the inner compression chamber. The pressure of the back chamber becomes larger than the pressure in the back chamber, and the tip of the arc gate valve L moves away from the side wall surface of the linear protrusion and moves toward the back chamber, so that it opens and compresses in the same direction as the linear protrusion. The chamber working gas flows into the outflow chamber. As described above, the operation of the arc gate valve L for the inner compression chamber 309 is basically the same as that of the arc gate valve R for the outer compression chamber 308, but the timing of the operation is as shown in FIGS. Different.
次に、前記吐出機構Ｃを代表する実施例１０の一部を変更した実施例１１について、実施例１０の図２９に相当する実施例１１の図３６を用いて説明する。 Next, an eleventh embodiment in which a part of the tenth embodiment representing the discharge mechanism C is changed will be described with reference to FIG. 36 of the eleventh embodiment corresponding to FIG. 29 of the tenth embodiment.
実施例１０と実施例１１の主な相違点を図２９と図３６を比較して説明する。内外圧縮室３１３と３１４を形成する包絡溝およびリング状の弁収納室を含む固定シリンダと旋回突起３０７ｃ含む旋回ピストンの構成は同一であり、異なるのは円弧ゲート弁ＲないしはＬを複数に分割した構成にある。 The main differences between the tenth embodiment and the eleventh embodiment will be described by comparing FIG. 29 and FIG. The configuration of the fixed cylinder including the envelope groove and the ring-shaped valve storage chamber forming the inner and outer compression chambers 313 and 314 and the swing piston including the swing protrusion 307c are the same, and the difference is that the arc gate valve R or L is divided into a plurality of parts. In the configuration.
図３６では、外圧縮室３１３用弁装着室３０６ｈに円弧ゲート弁を径方向で複数分割した曲率の異なる外円弧ゲート弁Ｒ３６０と内円弧ゲート弁Ｒ３６１を一組として装着している。内圧縮室用３１４にも対称的に外円弧ゲート弁Ｌ３６２と内円弧ゲート弁Ｌ３６３を一組として装着されている。それに中間部材３６６と該円弧ゲート弁それぞれに配置した外バネ３６４と内バネ３６５が配置されている。 In FIG. 36, an outer arc gate valve R360 and an inner arc gate valve R361 having different curvatures obtained by dividing a plurality of arc gate valves in the radial direction are mounted as a set in the valve mounting chamber 306h for the outer compression chamber 313. The inner arc chamber 314 is also symmetrically mounted with an outer arc gate valve L362 and an inner arc gate valve L363 as a set. In addition, an outer spring 364 and an inner spring 365 are disposed on the intermediate member 366 and the arc gate valve, respectively.
該実施例１１の動作形態は、図３５で示した実施例１１と基本的に差異はないので、以下簡単に説明する。 The operation mode of the eleventh embodiment is basically the same as the eleventh embodiment shown in FIG. 35, and will be briefly described below.
外圧縮室３１３圧力が背面室３０６ｊの圧力よりも高くなるとその差圧力により外円弧ゲート弁Ｒ３６０の先端部が直線突起３０７ｃ側壁面から離れて弁装着室内を背面室側に押されて先端部が僅かに開口すると該先端部全体に該差圧力が作用するので、該弁の開口動作性が高まると同時に内円弧ゲート弁Ｒ３６１の先端部にも該差圧力が作用する。そして、外円弧ゲート弁Ｒの動きによる摩擦力効果により内円弧ゲート弁Ｒが容易に開口して、外圧縮室で圧縮された作動ガスが流出室に流出する。 When the pressure in the outer compression chamber 313 becomes higher than the pressure in the back chamber 306j, the tip of the outer arc gate valve R360 separates from the side wall surface of the linear protrusion 307c due to the differential pressure, and the valve mounting chamber is pushed toward the back chamber. When the valve is slightly opened, the differential pressure acts on the entire tip, so that the opening operability of the valve is enhanced, and at the same time, the differential pressure acts on the tip of the inner arc gate valve R361. The inner arc gate valve R is easily opened by the frictional force effect caused by the movement of the outer arc gate valve R, and the working gas compressed in the outer compression chamber flows out to the outflow chamber.
次に、前記吐出機構Ｃの実施例１０の一部を変更した実施例１２について、図３７および図３８を用いて説明する。実施例１０に対する実施例１２の主な相違点は、固定シリンダの構成方法にある。その他の旋回ピストンおよび円弧ゲート弁を含む弁機構体は同じ構成が適用可能である。 Next, a twelfth embodiment in which a part of the tenth embodiment of the discharge mechanism C is changed will be described with reference to FIGS. The main difference between the tenth embodiment and the twelfth embodiment is the method of configuring the fixed cylinder. The same structure can be applied to the valve mechanism including the other swing piston and the arc gate valve.
図３７に実施例１２に適用する固定シリンダ３８６の平面図を示す。中央に包絡溝３８６ａに連結する円筒内壁３８６ｇが実施例１１と同様の形態で形成された内側には該包絡溝と同一床面を有する円筒状空間である円筒室３８６ｈが設けられている。その中央近傍に貫通孔として設けられた吐出孔３８６ｆの周囲には対称的に配置されたＵ字ピン穴３８６ｋ、注油孔３８６ｑ、圧導入孔３８６ｎそしてピン穴３８６ｍが設けられ、Ｕ字ピン穴３８６ｋ以外は図２８と同様に設けられている。 FIG. 37 shows a plan view of a fixed cylinder 386 applied to the twelfth embodiment. A cylindrical chamber 386h, which is a cylindrical space having the same floor surface as the envelope groove, is provided on the inner side where a cylindrical inner wall 386g connected to the envelope groove 386a is formed in the same manner as in the eleventh embodiment. A U-shaped pin hole 386k, a lubrication hole 386q, a pressure introducing hole 386n, and a pin hole 386m are provided symmetrically around a discharge hole 386f provided as a through hole in the vicinity of the center, and a U-shaped pin hole 386k. Other than the above, they are provided in the same manner as in FIG.
図３８の（ａ）図のＵ字溝付円柱３９７の平面図と（ｂ）の（ａ）図の側面図には円柱外壁３９７ａの内側にＵ字形状の流出室３９７ｂを形成し設置面３９７ｃにはピン孔３９７ｅが設けられている。このピン孔３９７ｅに挿入したピンを図３７のピン穴３８６ｋに嵌め込むことで図２８に示すような弁収納室および流出室が形成される。 38 (a) is a plan view of the U-shaped grooved cylinder 397 and FIG. 38 (b) is a side view of the side surface of FIG. 38 (a), in which a U-shaped outflow chamber 397b is formed on the inner side of the cylindrical outer wall 397a. Is provided with a pin hole 397e. By inserting the pin inserted into the pin hole 397e into the pin hole 386k of FIG. 37, a valve storage chamber and an outflow chamber as shown in FIG. 28 are formed.
このように図２８の固定シリンダからＵ字塔を分離して図３８の固定シリンダ形状とすることにより図２８で示した狭い溝の弁収納室の加工は不要となるので生産性が向上する。 In this way, by separating the U-shaped tower from the fixed cylinder of FIG. 28 to form the fixed cylinder of FIG. 38, the processing of the narrow groove valve storage chamber shown in FIG.
以下、本発明の容積型圧縮機の一形式としてのロータリ式の容積型圧縮機に適用した吐出機構Ｄの実施例１３を図３９～図４６に従って説明する。これらの図では、１気筒すなわち１シリンダの構成となっているが、２気筒への適用も可能である。 A thirteenth embodiment of the discharge mechanism D applied to a rotary positive displacement compressor as a type of positive displacement compressor of the present invention will be described below with reference to FIGS. In these drawings, the configuration is one cylinder, that is, one cylinder, but application to two cylinders is also possible.
図３９はロータリ式圧縮機４０１の圧縮機構部に対する横断面図を表わす。可動機構部材である駆動軸の偏心軸に装着された円筒状の円筒ピストン４０７、密閉容器４０２内に固定された中央部に円筒空間を有する固定機構部材である固定シリンダ４０６、その固定シリンダ端面に駆動軸を支える軸受を設けたフロントヘッドとその反対側に同じ駆動軸を支える軸受を設けたリアヘッドで構成し、これら円筒ピストン４０７、固定シリンダ４０６、フロントヘッドおよびリアヘッドで囲まれた三日月状の密閉空間として該圧縮機の圧縮室４１１と吸入孔４０６ａが開口する流入室４１０が形成されている。 FIG. 39 shows a cross-sectional view of the compression mechanism portion of the rotary compressor 401. A cylindrical piston 407 having a cylindrical shape mounted on an eccentric shaft of a drive shaft that is a movable mechanism member, a fixed cylinder 406 that is a fixed mechanism member having a cylindrical space in a central portion fixed in the sealed container 402, and an end surface of the fixed cylinder It is composed of a front head provided with a bearing supporting the drive shaft and a rear head provided with a bearing supporting the same drive shaft on the opposite side, and is sealed in a crescent shape surrounded by the cylindrical piston 407, the fixed cylinder 406, the front head and the rear head. As a space, a compression chamber 411 of the compressor and an inflow chamber 410 in which a suction hole 406a is opened are formed.
そして、固定シリンダ４０６の平面図である図４０に示すように、該固定シリンダの円筒空間の内壁面４０６ｂには作動ガスが流入する吸入孔４０６aと一定横幅で開口し平行平面で対面させて形成される溝の高さ方向の上下面をフロントヘッドとリアヘッドで塞ぐことでおよそ断面矩形の角柱状空洞を形成した弁装着室４０６ｄとその奥に該弁装着室と同じ高さで密閉容器内吐出空間と連通する吐出孔が開口する流出室４０６eとを合わせたキノコ状の空洞で形成される弁収納室４０６ｃが形成されている。 Then, as shown in FIG. 40 which is a plan view of the fixed cylinder 406, the inner wall surface 406b of the cylindrical space of the fixed cylinder is formed with a suction hole 406a into which a working gas flows and a constant lateral width that is opposed to a parallel plane. The valve mounting chamber 406d, in which the upper and lower surfaces in the height direction of the groove to be formed are closed with a front head and a rear head to form a prismatic cavity having a rectangular cross section, and discharged into the sealed container at the same height as the valve mounting chamber. A valve storage chamber 406c formed by a mushroom-like cavity is formed which is combined with an outflow chamber 406e having a discharge hole communicating with the space.
図３９の４１２矢視の一点鎖線で囲まれた拡大図を図４１に示す。Ｌ字形の弁安定板４２０を固着した平板ゲート弁Ｓ４１３、仕切板４１４、ストッパ４１５および前記部材と固定シリンダ４０６との間に支持バネ４１６や動作バネ４１７などの弾性体を含めて構成された弁機構体を該弁収納室４０６ｃに収納して吐出機構Ｄ４１２が構成される。該弁機構体を構成する要素の形状と該吐出機構Ｄの特徴的な機能と動作を以下で説明する。 FIG. 41 shows an enlarged view surrounded by an alternate long and short dash line in FIG. A valve including a flat gate valve S413, a partition plate 414, a stopper 415, and an elastic body such as a support spring 416 and an operation spring 417 between the member and the fixed cylinder 406, to which an L-shaped valve stabilization plate 420 is fixed. The discharge mechanism D412 is configured by storing the mechanism body in the valve storage chamber 406c. The shape of the elements constituting the valve mechanism and the characteristic functions and operations of the discharge mechanism D will be described below.
該平板ゲート弁Ｓ４１３の形状を図４２に、弁安定板４２０の外観斜視図を図４３に、仕切板４１４の形状を図４４に、ストッパ４１５の形状を図４５に示す。 42 shows the shape of the flat gate valve S413, FIG. 43 shows an external perspective view of the valve stabilizing plate 420, FIG. 44 shows the shape of the partition plate 414, and FIG. 45 shows the shape of the stopper 415.
該平板ゲート弁Ｓの形状は正面図である図４２（ａ）図とそのＨ－Ｈ断面図である（ｂ）図に示す。全体をおよそ直方体で形成されたその先端部４１３ａは、断面の（ｂ）図に示すように、右半分は円筒面４０７ａに摺接して圧縮室４１１と流出室４０６ｅ間をシールする狙いから中央凸の円弧形状をしている。一方該先端部の左半分は円筒面４０７ａに摺接しなくて浮いた状態を保つことで圧縮室圧力を常時作用させることと死空間を少なくするために平坦面ないしは傾斜面で形成されている。しかし、同じ機能であれば平坦面に拘る必要はないが、右半分と同様の円弧形状にすると死空間が増加する。 The shape of the flat gate valve S is shown in FIG. 42 (a), which is a front view, and FIG. As shown in the cross-sectional view (b), the right end of the tip 413a, which is formed in a substantially rectangular parallelepiped shape, is slidably in contact with the cylindrical surface 407a so as to seal between the compression chamber 411 and the outflow chamber 406e. It has an arc shape. On the other hand, the left half of the tip portion is formed as a flat surface or an inclined surface so that the compression chamber pressure is always applied and the dead space is reduced by maintaining a floating state without sliding against the cylindrical surface 407a. However, if it is the same function, there is no need to be concerned with a flat surface, but if it has the same arc shape as the right half, the dead space will increase.
また、圧縮室側の弁装着室４０６ｄ側壁面に摺接している平板ゲート弁Ｓの側壁シール面４１３ｃには圧力ポケット４１３ｆが設けられていることから、接触面積が減少し、該側壁シール面への同じ押付け荷重に対して、面圧が増大してシール性が向上する。また、圧縮室圧力が側壁シール面４１３ｆに作用する中心位置が背面部４１３ｅ側のより中央に近い位置となり、該平板ゲート弁Ｓの傾斜が押えられてより安定した動作が確保できる。 Further, since the pressure pocket 413f is provided in the side wall seal surface 413c of the flat gate valve S that is in sliding contact with the side wall surface of the valve mounting chamber 406d on the compression chamber side, the contact area is reduced and the side wall seal surface is moved to the side wall seal surface. For the same pressing load, the surface pressure increases and the sealing performance is improved. Further, the central position where the compression chamber pressure acts on the side wall seal surface 413f is closer to the center on the back surface portion 413e side, and the inclination of the flat gate valve S is suppressed, so that a more stable operation can be secured.
平板ゲート弁Ｓの側壁支持面４１３ｄには、図４３の外観斜視図に示すようなＬ字形状の薄板で形成された弁安定板４２０がスポット溶接などで固着されている。なお、機能上固定部４２０ｂは無くても突き出た受圧部４２０ａがあれば良いので、焼結合金や樹脂材などで平板ゲート弁Ｓと一体に成形しても良い。図中のＨＬ寸法とＢＬ寸法は後述する。 On the side wall support surface 413d of the flat gate valve S, a valve stabilizing plate 420 formed of an L-shaped thin plate as shown in an external perspective view of FIG. 43 is fixed by spot welding or the like. In addition, since there is no need for the functionally fixed portion 420b, the protruding pressure receiving portion 420a may be provided, so that it may be integrally formed with the flat gate valve S with a sintered alloy or a resin material. The HL dimension and BL dimension in the figure will be described later.
加えて、図４２に見られるように、一端が平板ゲート弁Ｓの側壁シール面４１３ｃに開口し、他端が該弁安定板の受圧部４２０ａ下部に開口する連通路４１３ｈが該平板ゲート弁Ｓ内に設けられ、その背面部４１３ｅには必要に応じて動作バネ用穴４１３ｇを設ける。 In addition, as shown in FIG. 42, a communication passage 413 h having one end opened to the side wall seal surface 413 c of the flat gate valve S and the other end opened to the lower portion of the pressure receiving portion 420 a of the valve stabilizing plate is the flat gate valve S. An operating spring hole 413g is provided in the back surface portion 413e as necessary.
仕切板４１４の形状は裏面図である図４４（ａ）図とそのＪ－Ｊ断面図である（ｂ）図に示す。全体をおよそ直方体で形成されたその先端部４１４aの形状は、円筒外面４０７ａに摺接して吸入室４１０と流出室４０６ｅ間をシールする狙いから（ｂ）図に示すように中央凸の円弧形状をしている。 The shape of the partition plate 414 is shown in FIG. 44A, which is a rear view, and in FIG. The shape of the tip portion 414a, which is formed in a substantially rectangular parallelepiped as a whole, is an arc having a central convex shape as shown in FIG. 5 (b) with the aim of sealing the space between the suction chamber 410 and the outflow chamber 406e in sliding contact with the cylindrical outer surface 407a. is doing.
また、弁装着室４０６ｄの側壁面に摺接している仕切板４１４の側壁シール面４１４ｂに該平板ゲート弁Ｓと同様の圧力ポケットを設けても良い。これにより接触面積が減少し、側壁シール面への同じ押付け荷重に対して面圧が増大してシール性が向上する。また、流出室圧力が側壁シール面４１４ｂに作用する中心位置が背面部４１４ｅ側のより中心に近い位置となるので、仕切弁４１４の傾斜が押えられてより安定した動作が確保できる。 Further, a pressure pocket similar to that of the flat gate valve S may be provided on the side wall seal surface 414b of the partition plate 414 that is in sliding contact with the side wall surface of the valve mounting chamber 406d. As a result, the contact area is reduced, the surface pressure is increased for the same pressing load on the side wall seal surface, and the sealing performance is improved. Further, since the center position where the outflow chamber pressure acts on the side wall seal surface 414b is closer to the center on the back surface portion 414e side, the inclination of the gate valve 414 is suppressed, and a more stable operation can be secured.
図４４の（ａ）図に示すように、両サイドに設けた角柱状の弁支持部４１４eとの間に作動ガスの通路となる側壁通路４１４ｄを設け、その面の中央部に一段凹ました迂回路４１４ｇを設けている。背面部４１４ｃには動作バネ用のバネ用穴１３eを設けている。 As shown in FIG. 44 (a), a side wall passage 414d serving as a working gas passage is provided between the square columnar valve support portions 414e provided on both sides, and the detour is formed by one step in the center of the surface. A path 414g is provided. The back surface portion 414c is provided with a spring hole 13e for an operating spring.
なお、該弁安定板の形状に関わる図４３中のＨＬ寸法は、図４４にある該仕切板の弁支持部４１４ｅに接触しない程度で近接させる寸法とし、ＢＬ寸法は仕切板の側壁通路４１４ｄ側壁面に接触しない程度で近接させた寸法とする。 43 related to the shape of the valve stabilizing plate in FIG. 43 is set to be close to the valve support portion 414e of the partition plate shown in FIG. 44, and the BL size is on the side wall passage 414d side of the partition plate. The dimensions should be close enough not to touch the wall.
図４１の流出室４０６ｅに装着されているストッパ４１５の正面図を図４５の（ａ）図に示し、その上面図を（ｂ）図に示すように角丸長方形の一方が開口した形状をしている。両端の円弧形状の支持端部４１５ａは、流出室４０６ｅの両端に設けた円弧部に据え込まれるとともに平坦部と流出室の平坦部との間に支持バネ４１６を取り付けて挟着される。また、平坦部に設けたバネ穴４１５ｂは仕切板ないしは平板ゲート弁Ｓの背面部と流出室の平坦部との間に装着する動作バネ４１７を通すための穴である。 A front view of the stopper 415 attached to the outflow chamber 406e in FIG. 41 is shown in FIG. 45 (a), and a top view thereof is shown in FIG. ing. The arc-shaped support end portions 415a at both ends are placed on arc portions provided at both ends of the outflow chamber 406e, and are supported and attached with a support spring 416 between the flat portion and the flat portion of the outflow chamber. Further, the spring hole 415b provided in the flat portion is a hole through which the operation spring 417 mounted between the rear portion of the partition plate or flat gate valve S and the flat portion of the outflow chamber is passed.
なお、前記実施例１の図６に示した係止機構を形成する係止制御室と係止孔および係止部材などと給油のための給油孔を前記フロントヘッドないしはリアヘッドに設けており、前記同様の構成と機能を有している。 In addition, the front control head or the rear head is provided with a locking control chamber, a locking hole, a locking member, and the like that form the locking mechanism shown in FIG. It has the same configuration and function.
以下、本発明の実施例１３に適用した吐出機構Ｄ４１２の動作状態を、図４６を用いて説明する。 Hereinafter, the operation state of the discharge mechanism D412 applied to the thirteenth embodiment of the present invention will be described with reference to FIG.
図４６に示した（ａ）図から（ｄ）図の４図は、駆動軸に同期して円筒ピストン４０７が回転して吐出機構Ｄ４１２が動作する状態を示した図であり、中央に記載した０°、９０°、１８０°および２７０°は（ａ）図を起点にした回転角を表わしている。 FIGS. 4A to 4D shown in FIG. 46 are views showing a state in which the cylindrical piston 407 rotates in synchronization with the drive shaft and the discharge mechanism D412 operates, and is described in the center. 0 °, 90 °, 180 °, and 270 ° represent rotation angles starting from FIG.
（ａ）図では固定シリンダ４０６に設けた吐出機構Ｄのうち特に仕切板４１４に円筒ピストンが最接近した状態を示し、先端部４１４ａの凸円弧中央に摺接した状態を示している。圧縮室４１１は吸入室４１０と連通して吸入圧力と同じ圧力状態となっている。 FIG. 5A shows a state where the cylindrical piston is closest to the partition plate 414 in the discharge mechanism D provided in the fixed cylinder 406, and shows a state where the cylindrical piston is slidably contacted with the center of the convex arc of the tip portion 414a. The compression chamber 411 communicates with the suction chamber 410 and is in the same pressure state as the suction pressure.
運転中、流出室４０６ｅ内は高圧の吐出圧力の雰囲気にあるので、仕切板先端部４１４ａの右側半分と平板ゲート弁Ｓ先端部４１３ａの左側半分は低圧である吸入圧力の作用に加えて流出室側に設けた動作バネ４１７により、仕切板および平板ゲート弁Ｓは円筒ピストン側に押付けられて各先端部は流出室と吸入室ないしは圧縮室間をシールしている。 During operation, since the inside of the outflow chamber 406e is in an atmosphere of high discharge pressure, the right half of the partition plate tip 414a and the left half of the flat gate valve S tip 413a are in addition to the action of the suction pressure that is low pressure. By the operating spring 417 provided on the side, the partition plate and the flat gate valve S are pressed against the cylindrical piston side, and each tip portion seals between the outflow chamber and the suction chamber or the compression chamber.
さらには、弁装着室４０６ｄの側壁面と仕切板の側壁シール面４１４ｂおよび平板ゲート弁Ｓの側壁シール面４１３ｃとの間は圧力ポケットによりそれぞれが吸入室圧力ないしは圧縮室圧力の領域が多くなっており、流出室圧力の差圧からそれぞれが弁装着室側壁面に押付けられてシールされている。 Furthermore, the pressure pocket between the side wall surface of the valve mounting chamber 406d and the side wall seal surface 414b of the partition plate and the side wall seal surface 413c of the flat gate valve S increases the area of the suction chamber pressure or the compression chamber pressure. Each is pressed against the side wall surface of the valve mounting chamber from the differential pressure of the outflow chamber pressure and sealed.
次に円筒ピストンの回転が進んで右側に図示された吸入孔４０６ａを通り過ぎた（ｂ）図では、圧縮室４１１は密閉された空間となり作動ガスの圧縮が開始されるが、その圧力はまだ吸入圧力に近い低い圧力状態にある。よって、仕切板先端部の円筒面４０７ａとの摺接部が吸入室４１０側に移動して低圧が作用する領域が減少しているが、それ以上に大きな荷重の動作バネが流出室側から作用しているので、先端部のシール性が確保されている。また、側壁面のシール力は（ａ）図と同様である。 Next, the rotation of the cylindrical piston advances and passes through the suction hole 406a shown on the right side. In FIG. 5B, the compression chamber 411 becomes a sealed space and the compression of the working gas is started, but the pressure is still sucked. It is in a low pressure state close to the pressure. Therefore, the sliding contact portion of the partition plate tip with the cylindrical surface 407a moves to the suction chamber 410 side and the area where the low pressure acts is reduced, but an operating spring with a larger load acts from the outflow chamber side. Therefore, the sealing performance at the tip is ensured. Further, the sealing force of the side wall surface is the same as in FIG.
平板ゲート弁Ｓ先端部の円筒面４０７ａとの摺接部が圧縮室の反対側に移動して圧縮室圧力が作用する領域が増大しているので、その差圧の影響は大きくなり圧縮室圧力が上昇しても先端部のシール力は確保される。また、側壁面のシール力は、流出室圧力が圧縮室圧力よりも高い領域では（ａ）図と同様のシール状態が継続される。 Since the sliding contact portion of the tip of the flat gate valve S with the cylindrical surface 407a moves to the opposite side of the compression chamber and the compression chamber pressure acts on the region, the effect of the differential pressure increases and the compression chamber pressure increases. Even if it rises, the sealing force at the tip is secured. Further, the sealing force of the side wall surface is the same as that shown in FIG. 5A in the region where the outflow chamber pressure is higher than the compression chamber pressure.
さらに円筒ピストンの回転が進んで最も吐出機構Ｄから離れた位置にある（ｃ）図では、圧縮室の容積が減少して（ｂ）図よりも圧力が上昇する。仕切板先端部の円筒面４０７ａとの摺接部が（ａ）図と同じ中央に移動して低圧が作用する領域が戻ることと動作バネの作用から、先端部のシール性が確保される。 Furthermore, in the figure (c) which is further away from the discharge mechanism D due to further rotation of the cylindrical piston, the volume of the compression chamber decreases and the pressure rises more than in the figure (b). The sliding property of the tip of the partition plate with the cylindrical surface 407a is moved to the same center as in FIG. 4A, the region where the low pressure acts is returned, and the sealing performance of the tip is secured.
また、仕切板の側壁シール面に対する荷重は（ａ）図と差圧が同じなので同様となるが、作用中心点の位置が吸入室側に移動している点が異なる。その作用中心が側壁面を超えて吸入室側に入ると仕切板に側壁シール面の端部であるＫ点回りのモーメントが作用して、仕切板が傾斜して性能や耐久性面で問題が発生するが、該吐出機構Ｄでは、側壁面の長さや圧力ポケットなどから該モーメントが発生しない構成となっている。 Further, the load on the side wall seal surface of the partition plate is the same because the differential pressure is the same as in FIG. (A), except that the position of the center of action has moved to the suction chamber side. When the center of action exceeds the side wall surface and enters the suction chamber side, a moment around the K point, which is the end of the side wall seal surface, acts on the partition plate, and the partition plate tilts, causing problems in terms of performance and durability. Although generated, the discharge mechanism D is configured not to generate the moment due to the length of the side wall surface, the pressure pocket, or the like.
一方平板ゲート弁Ｓでは、先端部の円筒面４０７ａとの摺接部が圧縮室側に移動して圧縮室圧力が作用する領域が（ａ）図と同様となるが、圧縮室圧力が上昇しても、流出室圧力が圧縮室圧力よりも高い区間では、先端部のシール力は確保される。また、側壁シール面のシール力は、流出室圧力が圧縮室圧力よりも高い領域では、その差圧によりシール状態が継続されることと作用中心の位置が圧縮室側に移動しているが、その作用中心が側壁シール面を超えて圧縮室側に入らないように側壁面の長さや圧力ポケットが設定されているので、平板ゲート弁Ｓにモーメントが作用して傾斜することはない。 On the other hand, in the flat gate valve S, the region where the sliding contact portion of the tip portion with the cylindrical surface 407a moves to the compression chamber side and the compression chamber pressure acts is the same as in FIG. Even in the section where the outflow chamber pressure is higher than the compression chamber pressure, the sealing force at the tip is ensured. Further, the sealing force of the side wall seal surface is such that, in the region where the outflow chamber pressure is higher than the compression chamber pressure, the sealing state is continued by the differential pressure and the position of the center of action has moved to the compression chamber side. Since the length of the side wall surface and the pressure pocket are set so that the center of action does not exceed the side wall seal surface and enter the compression chamber side, the moment does not act on the flat plate gate valve S to tilt.
さらに円筒ピストンの回転が進み最も左側に位置している（ｄ）図では、圧縮室の容積がさらに減少し圧力が上昇して平板ゲート弁Ｓを流出室側に押上げて圧縮室内の作動ガスを吐出させる吐出行程に入った状態を示している。 Further, in the figure (d) where the rotation of the cylindrical piston advances and is located on the leftmost side, the volume of the compression chamber further decreases, the pressure rises, and the flat gate valve S is pushed up to the outflow chamber side to operate the working gas in the compression chamber. The state which entered into the discharge stroke which discharges is shown.
この円筒ピストンの位置では、円筒面４０７ａの中心と平板ゲート弁Ｓ先端部中央を一致させた構成となっているので、該先端部が該円筒外面４０７ａに着座した状態では左側平坦部４１３ｂに流出室よりも高い圧縮室圧力が作用することに加えて側壁シール面の圧力ポケット４１３ｆにも作用して弁装着室側壁面から離反することで圧縮室の作動ガスが連通路４１３ｈから弁安定板下部に流入することから圧縮室圧力と流出室圧力の少ない差圧で平板ゲート弁Ｓが流出室側に押上げられて、吐出行程に入り圧縮室と流出室が連通し圧縮室内の作動ガスが流出室内に流出することになる。 At the position of the cylindrical piston, the center of the cylindrical surface 407a and the center of the tip of the flat plate gate valve S are made to coincide with each other, so that when the tip is seated on the cylindrical outer surface 407a, it flows out to the left flat portion 413b. In addition to acting on the pressure pocket 413f on the side wall seal surface in addition to the action of the compression chamber pressure higher than that of the chamber, the working gas in the compression chamber is separated from the valve mounting chamber side wall surface through the communication passage 413h to the lower part of the valve stabilizing plate. Therefore, the flat gate valve S is pushed up to the outflow chamber side with a small differential pressure between the compression chamber pressure and the outflow chamber pressure, enters the discharge stroke, the compression chamber and the outflow chamber communicate with each other, and the working gas in the compression chamber flows out. It will flow out into the room.
平板ゲート弁Ｓの側壁支持面に固着した弁安定板の受圧部４２０ａは、仕切板の迂回路４
１４ｆ下端より下側の弁支持部４１４ｄに挟まれた作動ガスの流出通路４１８に小さな隙間を設けて塞ぐように配置されている。 The pressure-receiving part 420a of the valve stabilizer fixed to the side wall support surface of the flat gate valve S is a bypass 4 of the partition plate.
The working gas outlet passage 418 sandwiched between the valve support portions 414d below the lower end of 14f is disposed so as to be closed with a small gap.
このような状態に於いて、圧縮室圧力が流出室圧力よりも高く該先端部と連通路４１３ｈから作動ガスが流入して該受圧部２０ａ下部空間圧力が高まると平板ゲート弁Ｓを押上げる力が加算されて、圧縮室圧力と該流出室圧力の差が殆どない状態で該平板ゲート弁Ｓが開口するので、圧縮室圧力が流出室圧力よりも大きく上昇する過圧縮現象の発生ない。 In such a state, when the pressure of the compression chamber is higher than the pressure of the outflow chamber and the working gas flows in from the tip portion and the communication passage 413h and the space pressure under the pressure receiving portion 20a increases, the force that pushes up the flat gate valve S Are added, and the flat gate valve S opens in a state where there is almost no difference between the compression chamber pressure and the outflow chamber pressure, so that the overcompression phenomenon in which the compression chamber pressure rises higher than the outflow chamber pressure does not occur.
また、該先端部４１３ａに作動ガスが流入することで動圧分先端部の圧力が低下するが、弁安定板に作用する作動ガスの流れに伴う動圧は押上げ効果を増大させるので、先端部の影響で閉じることはないし振動も起こらないで安定した動きとなる。 In addition, the working gas flows into the tip 413a and the pressure at the tip is reduced by the amount of dynamic pressure. However, the dynamic pressure accompanying the flow of the working gas acting on the valve stabilizer increases the push-up effect. It does not close under the influence of the part, and it becomes a stable movement without causing vibration.
また、平板ゲート弁Ｓが先端部と背面部に作用する圧力で流出室側に押上げられた時、背面部はストッパ４１５に衝突して着座するが、該ストッパは流出室壁面との間に支持バネを設けて弾性支持されているので、平板ゲート弁Ｓ衝突時の衝撃は緩衝されて騒音の発生や部材が損傷することない。 Further, when the flat gate valve S is pushed up to the outflow chamber side by the pressure acting on the tip portion and the back surface portion, the back surface portion collides with the stopper 415 and is seated, but the stopper is between the outflow chamber wall surface. Since the supporting spring is provided and elastically supported, the impact at the time of collision of the flat gate valve S is buffered, so that noise is not generated and members are not damaged.
円筒ピストン６がさらに回転すると（ａ）図に戻り、圧縮室の吐出行程終了直後の状態を示す。この時圧縮室圧力は、吸入室と連通して吸入圧力に等しい低圧状態となるので、平板ゲート弁Ｓ先端部と弁安定板の受圧部下部空間圧力が低下し平板ゲート弁Ｓを押し下げて、一気に平板ゲート弁Ｓを閉じるので、作動ガスが逆流する再圧縮損失はなくなる。 When the cylindrical piston 6 further rotates, the diagram returns to (a) and shows a state immediately after the end of the discharge stroke of the compression chamber. At this time, the pressure in the compression chamber communicates with the suction chamber and becomes a low pressure state equal to the suction pressure. Therefore, the pressure at the lower end of the flat plate gate valve S and the pressure receiving portion of the valve stabilizer is lowered and the flat plate gate valve S is pushed down. Since the flat gate valve S is closed at once, there is no recompression loss in which the working gas flows backward.
次に、前記吐出機構Ｄの実施例１３の一部を変更した実施例１４について、図４７を用いて説明する。実施例１３に対する実施例１４の主な相違点は、仕切板の構成にあり、他の主要な構成は同じである。 Next, an embodiment 14 in which a part of the embodiment 13 of the discharge mechanism D is changed will be described with reference to FIG. The main difference between the thirteenth embodiment and the fourteenth embodiment is the configuration of the partition plate, and the other main configurations are the same.
図４７を図４４と対比して判るように、本実施形態は仕切板４５４と弁装着室４０６ｄの流出室側の側壁面との間に転がり軸受などの転動体４５６を１個ないしは複数個装着して構成されている。前記の図１６と同様に、該転動体４５６は車軸に車輪部を装着し、仕切板の側壁支持面の最大幅よりも車輪部が数十から数百ミクロン突出するように配置され、車軸と車輪部間ないしは車軸と仕切板間で回転可能に構成されている。 As can be seen by comparing FIG. 47 with FIG. 44, in this embodiment, one or a plurality of rolling elements 456 such as rolling bearings are mounted between the partition plate 454 and the side wall surface on the outflow chamber side of the valve mounting chamber 406d. Configured. Similar to FIG. 16, the rolling element 456 has a wheel portion mounted on the axle, and is disposed so that the wheel portion protrudes several tens to several hundreds of microns from the maximum width of the side wall support surface of the partition plate. It is configured to be rotatable between the wheel portions or between the axle and the partition plate.
このような構成に於いて、圧縮室圧力が流出室圧力より上昇してその差圧により該平板ゲート弁Ｓが流出室側に押されると該転動体４５６が該側壁シール面４５４ｂと弁装着室側壁面間で挟み込まれる。その際、仕切板４５４は円筒ピストン円筒面に押されて流出室側に移動しているので、転動体の弁装着室側壁面上を転がる回転力が同時に接触している平板ゲート弁Ｓにも回転速度が倍化されて伝わり流出室側に瞬時に移動する。 In such a configuration, when the compression chamber pressure rises above the outflow chamber pressure and the flat gate valve S is pushed to the outflow chamber side by the differential pressure, the rolling element 456 is moved to the side wall seal surface 454b and the valve mounting chamber. It is sandwiched between the side wall surfaces. At that time, since the partition plate 454 is pushed by the cylindrical piston cylindrical surface and moves to the outflow chamber side, the plate gate valve S to which the rotational force rolling on the valve mounting chamber side wall surface of the rolling element is simultaneously in contact is also applied. The rotation speed is doubled and transmitted to the outflow chamber side instantly.
次に、本発明の容積型圧縮機の一形式としてのスクロール式容積型圧縮機に適用した吐出機構Eの実施例１５を図４８から図５１に従って説明する。 Next, a fifteenth embodiment of the discharge mechanism E applied to the scroll type positive displacement compressor as one type of positive displacement compressor of the present invention will be described with reference to FIGS.
図４８に実施例１５のスクロール式容積型圧縮機５０１の横断面図を示す。縦断面図の構造は実施例１０の図２５と同様なのでここでの詳細説明は省くが、密閉容器５０２内に固定されたフレーム（図示しない）上に装着ないしは該密閉容器に直接固定した固定スクロールすなわち固定シリンダ５０６とフレームとの間に旋回スクロールすなわち旋回ピストン５０７と自転を防止する旋回機構（図示しない）が設けられ、フレームの中央部に支持された駆動軸の下部を電動機に直結して構成されている。 FIG. 48 is a cross-sectional view of the scroll positive displacement compressor 501 of the fifteenth embodiment. Since the structure of the longitudinal sectional view is the same as that of FIG. 25 of the tenth embodiment, a detailed description thereof is omitted. However, the fixed scroll is mounted on a frame (not shown) fixed in the sealed container 502 or fixed directly to the sealed container. That is, a rotating scroll (not shown) for preventing rotation is provided between the fixed cylinder 506 and the frame, that is, a rotating piston 507, and the lower part of the drive shaft supported at the center of the frame is directly connected to the motor. Has been.
圧縮室含む圧縮機構部の構成を、旋回ピストンの形状が基本的に同じである前記実施例１１の図２７と固定シリンダ５０６の平面図である図５０を用いて説明をする。従って、ここでは旋回ピストンの構成の説明は省き必要な場合には図２７を用いる。 The configuration of the compression mechanism including the compression chamber will be described with reference to FIG. 27 of the eleventh embodiment in which the shape of the swivel piston is basically the same and FIG. 50 which is a plan view of the fixed cylinder 506. Accordingly, the description of the configuration of the orbiting piston is omitted here, and FIG. 27 is used when necessary.
図５０に示す固定シリンダ５０６の形状は、旋回突起５０７ａの旋回運動で形成される包絡線を壁面として得られる一定幅の断面矩形の包絡溝５０６ａを厚い板厚の固定端板５０６ｂの片面に設け、包絡溝５０６ａの外周側一端に作動ガスの流入室５０６ｃを内周側他端に溝終端室５０６ｊを包絡溝５０６ａと同一底面を有して設けてられており、流入室５０６ｃと溝終端室５０６ｊそれぞれに吸入孔５０６ｄと吐出空間ないしは吸入通路に連通する連通孔５０６ｋが設けられている。 The shape of the fixed cylinder 506 shown in FIG. 50 is such that an envelope groove 506a having a rectangular cross section having a constant width obtained by using the envelope formed by the swiveling motion of the swiveling projection 507a is provided on one surface of the fixed end plate 506b having a thick plate thickness. The working gas inflow chamber 506c is provided at one end on the outer peripheral side of the envelope groove 506a and the groove termination chamber 506j is provided at the other end on the inner peripheral side with the same bottom surface as the envelope groove 506a. Each of 506j is provided with a suction hole 506d and a communication hole 506k communicating with the discharge space or suction passage.
そして、図５０の溝終端室５０６ｊの内外側壁それぞれに開口する2箇所に該包絡溝と同一底面を有し該溝終端室５０６ｊを挟んで弁装着室５０６ｇとその奥に設けた流出室５０６ｈとで弁収納室５０６ｆが２箇所形成されており、それぞれの弁装着室５０6ｇ内には細孔の係止孔５０６ｎが開口し、流出室５０６ｈ内には吐出孔５０６ｅが開口している。 50. The valve mounting chamber 506g and the outflow chamber 506h provided at the back of the groove termination chamber 506j having the same bottom surface as the envelope groove at two locations opened on the inner and outer walls of the groove termination chamber 506j in FIG. Thus, two valve storage chambers 506f are formed, and in each of the valve mounting chambers 506g, fine hole locking holes 506n are opened, and in the outflow chamber 506h, discharge holes 506e are opened.
圧縮室は、図４８に示すように、旋回ピストンの旋回突起５０７ａと円弧突起５０７ｃを固定シリンダの包絡溝５０６ａ内互いに咬合するように遊挿入してそれら突起内外側壁面と包絡溝５０６ａ内外側壁面との間で形成される空間の上下を塞いで外圧縮室５１０と内圧縮室５１１が形成される。 As shown in FIG. 48, the compression chamber is formed by loosely inserting the swiveling protrusions 507a and the circular arc protrusions 507c of the swiveling piston so as to engage with each other in the envelope groove 506a of the fixed cylinder, and the inner and outer wall surfaces of the protrusions and the inner and outer wall surfaces of the envelope groove 506a. The outer compression chamber 510 and the inner compression chamber 511 are formed by closing the upper and lower sides of the space formed therebetween.
図示はされてないが、実施例１１と同様に、動力を伝達する駆動軸の偏心部を旋回ピストンの旋回軸受に挿入するとともに旋回ピストンの自転を阻止する旋回機構を設けることにより旋回ピストンが固定シリンダに対して旋回運動をする。 Although not shown in the drawing, as in the case of the eleventh embodiment, the turning piston is fixed by inserting the eccentric portion of the drive shaft for transmitting power into the turning bearing of the turning piston and providing a turning mechanism for preventing the turning piston from rotating. Swing motion with respect to the cylinder.
図４８の一点鎖線で囲んで示した５１２矢視に包絡溝５０６ａを延長した先の溝終端室５０６ｊ近傍に設けた作動ガスを圧縮室から流出させる吐出機構Ｅ５１２を示している。その５１２矢視の部分拡大図を図５０に示し、図５０におけるＭ－Ｎ－Ｏ－Ｐ断面図を図５１に示す。これらの図を基に吐出機構Ｅの構成を以下で説明する。 48 shows a discharge mechanism E512 that causes the working gas to flow out from the compression chamber provided in the vicinity of the groove end chamber 506j, in which the envelope groove 506a is extended, as shown by an arrow 512 in FIG. 48 surrounded by a one-dot chain line. FIG. 50 shows a partially enlarged view taken in the direction of arrow 512, and FIG. 51 shows a cross-sectional view taken along line MNOP in FIG. The configuration of the discharge mechanism E will be described below based on these drawings.
吐出機構Ｅ５１２の構成は、連通孔５０６ｋが開口する溝終端室５０６ｊと直線突起５０７ｃを挟んで外圧縮室５１０用の弁収納室５０６ｆと内圧縮室５１１用の弁収納室５０６ｆが左右対称に配置されている。 The structure of the discharge mechanism E512 is such that the valve storage chamber 506f for the outer compression chamber 510 and the valve storage chamber 506f for the inner compression chamber 511 are arranged symmetrically across the groove end chamber 506j in which the communication hole 506k opens and the linear protrusion 507c. Has been.
外圧縮室５１０用弁装着室５０６ｇには平板ゲート弁Ｒ５１３と仕切板５１５を１組とし、他方の内圧縮室５１１用には平板ゲート弁Ｌ５１４と仕切板５１６を１組として装着されている。これらに加えて、それぞれの流出室５０６ｈにはストッパ５１６とその支持バネ５１９および動作バネ５２０等の弾性体を１セットとしてそれぞれの弁収納室５０６ｆに装着されている。 A flat plate gate valve R513 and a partition plate 515 are mounted as one set in the valve mounting chamber 506g for the outer compression chamber 510, and a flat plate gate valve L514 and a partition plate 516 are mounted as a set for the other inner compression chamber 511. In addition to these, each outlet chamber 506h is provided with a stopper 516 and an elastic body such as a support spring 519 and an operating spring 520 as a set in each valve storage chamber 506f.
但し、該支持バネ５１９はストッパ５１８を弾性的に支持し、該動作バネ５２０は該仕切板および該平板ゲート弁を直線突起５０７ｃ側に常時押付ける弾性体であり、該平板ゲート弁の動作上支障がなければ、該平板ゲート弁用の動作バネは省略できる。 However, the support spring 519 elastically supports the stopper 518, and the operation spring 520 is an elastic body that constantly presses the partition plate and the flat gate valve toward the linear protrusion 507c. If there is no hindrance, the operating spring for the flat gate valve can be omitted.
外圧縮室用平板ゲート弁Ｒ５１３の形状は前記図４２と仕切板５１５の形状は図４４と基本同一なので、ここでは詳細な説明を省略する。しかし、平板ゲート弁Ｒおよび仕切板の先端部の形状は異なる。該平板ゲート弁ＲとＬの座面である直線突起５０７ｃ側壁面に摺接する先端部には前記図７の形状が適用され、該仕切板の座面である直線突起５０７ｃ側壁面に摺接する先端部は平坦面が適用される。 The shape of the flat gate valve R513 for the outer compression chamber is basically the same as that shown in FIG. 42 and the shape of the partition plate 515 as shown in FIG. However, the flat gate valve R and the shape of the tip of the partition plate are different. The shape shown in FIG. 7 is applied to the tip of the flat projection 507c which is the seating surface of the flat gate valves R and L, and the tip of the straight projection 507c which is the seating surface of the partition plate is slidable. A flat surface is applied to the part.
なお、前記実施例１の図６に示した係止機構を形成する係止制御室と係止孔および係止部材などと給油のための給油孔を前記固定シリンダに設けており、前記同様の構成と機能を有している。 In addition, the fixed control cylinder which forms the locking mechanism shown in FIG. 6 of the first embodiment, a locking hole and a locking member, and an oil supply hole for supplying oil are provided in the fixed cylinder. It has configuration and function.
実施例１５の吐出機構Ｅの動作を以下に示す。但し、図５１で示した溝終端室５０６ｊに開口する連通孔５０６ｋは吐出空間に連通させて吐出圧力を導入する構成とする。 Operation | movement of the discharge mechanism E of Example 15 is shown below. However, the communication hole 506k opened in the groove termination chamber 506j shown in FIG. 51 is configured to communicate with the discharge space and introduce the discharge pressure.
旋回突起５０７ａ外壁側に形成される外圧縮室５１０ないしは該旋回突起内壁側に形成される内圧縮室５１１に流入室から作動ガスが流入した後、駆動軸の回転に伴い旋回運動をする旋回ピストン５０７により内外圧縮室内の作動ガスが吐出機構Ｅ側に移動するに伴い一端が平板ゲート弁ＲないしはＬで閉じられた内外圧縮室の容積が減少するために圧縮室内の作動ガスが圧縮されて圧力が上昇する。 A swiveling piston that swirls with the rotation of the drive shaft after working gas flows from the inflow chamber into the outer compression chamber 510 formed on the outer wall side of the swiveling protrusion 507a or the inner compression chamber 511 formed on the inner wall side of the swiveling protrusion. As the working gas in the inner and outer compression chambers moves to the discharge mechanism E side by 507, the volume of the inner and outer compression chambers whose one ends are closed by the flat gate valve R or L decreases, so that the working gas in the compression chamber is compressed and pressure Rises.
外圧縮室５１０の圧力が流出室５０６ｈの圧力よりも低い区間では、直線突起５０７ｃの旋回運動により該平板ゲート弁Ｒの先端部は該直線突起の側壁面に摺接すると同時に圧縮室側の側壁シール面は弁装着室５０6hの側壁シール面に摺接しているので圧縮室と流出室間のシール性が確保された状態で作動ガスの圧縮が継続される。 In a section where the pressure in the outer compression chamber 510 is lower than the pressure in the outflow chamber 506h, the tip portion of the flat gate valve R is in sliding contact with the side wall surface of the linear protrusion due to the swiveling movement of the linear protrusion 507c. Since the seal surface is in sliding contact with the side wall seal surface of the valve mounting chamber 506h, the compression of the working gas is continued in a state where the sealing performance between the compression chamber and the outflow chamber is ensured.
外圧縮室５１０の圧縮が進み圧縮室圧力が流出室圧力より高くなると、平板ゲート弁Ｒの先端部に作用する圧力が流出室の圧力よりも大きくなり、差圧力により該平板ゲート弁Ｒが流出室５０６ｈ側に移動することで先端部が直線突起の側壁面から離れて直線突起の移動方向と同じ方向で開口し外圧縮室内の圧縮された作動ガスが流出室に流出する。その際、平板ゲート弁Ｒの側壁支持面に固定した弁安定板は、前述の如く平板ゲート弁Ｒの開口動作を助けるので、該弁の動作性は良好で損失の少ない吐出行程となる。 When the compression of the outer compression chamber 510 progresses and the compression chamber pressure becomes higher than the outflow chamber pressure, the pressure acting on the tip portion of the flat gate valve R becomes larger than the pressure in the outflow chamber, and the flat gate valve R flows out due to the differential pressure. By moving to the chamber 506h side, the tip portion is separated from the side wall surface of the linear protrusion, opens in the same direction as the linear protrusion movement direction, and the compressed working gas in the outer compression chamber flows out to the outflow chamber. At this time, the valve stabilizing plate fixed to the side wall support surface of the flat gate valve R assists the opening operation of the flat gate valve R as described above. Therefore, the operability of the valve is good and the discharge stroke is small.
外圧縮室５１０の吐出行程終了直後では、外圧縮室は外側の低圧状態にある圧縮室圧力に切り替わっているので、平板ゲート弁Ｒ先端部と弁安定板の受圧部下部空間圧力が低下し平板ゲート弁Ｒを押し下げる力が作用して、瞬時に直線突起間を閉じるので作動ガスが逆流する再圧縮損失は殆ど無くなるとともに該平板ゲート弁Ｒの着座による衝撃もないために音や部材の損傷の問題もない。 Immediately after the discharge stroke of the outer compression chamber 510 ends, the outer compression chamber is switched to the compression chamber pressure in the low pressure state on the outside, so that the pressure at the lower end of the flat gate gate valve R and the pressure receiving portion of the valve stabilizing plate is reduced. The force that pushes down the gate valve R acts and closes the straight protrusions instantly, so there is almost no recompression loss in which the working gas flows backward, and there is no impact due to the seating of the flat gate valve R. There is no problem.
一方、内圧縮室５１１に対する吐出機構Ｅの動作は外圧縮室５１０と基本的に同様であるが、動作のタイミングがおよそ１８０°前後ずれる。このタイミングのずれは、駆動軸のトルク変動や作動ガスの圧力脈動および最大流速を減じる効果がある。 On the other hand, the operation of the discharge mechanism E with respect to the inner compression chamber 511 is basically the same as that of the outer compression chamber 510, but the timing of the operation is shifted by about 180 °. This timing shift has the effect of reducing the torque fluctuation of the drive shaft, the pressure pulsation of the working gas, and the maximum flow velocity.
実施例１５に対する起動時に於ける該吐出機構Ｅの動作は、実施例１の図６を用いた起動時の動作説明と同様となる。 The operation of the discharge mechanism E at the start-up for the fifteenth embodiment is the same as the operation at the start-up using FIG. 6 of the first embodiment.
次に、駆動軸の回転数を変化させないで圧縮機の作動ガスの量を減少させる手段すなわち容量制御の運転方法として、前記係止機構を用いた場合について説明する。 Next, the case where the locking mechanism is used as a means for reducing the amount of working gas of the compressor without changing the rotational speed of the drive shaft, that is, an operation method of capacity control will be described.
その係止機構の動作原理は前記起動時の場合と同様であり、係止制御室内と流出室内の圧力が等しくなることにより係止部材のピン部が平板ゲート弁ＲとＬの係止穴に入り込んで該平板ゲート弁ＲとＬの動きが停止する。 The operating principle of the locking mechanism is the same as that at the time of starting, and the pressure in the locking control chamber and the outflow chamber is equalized, so that the pin portion of the locking member becomes the locking hole of the flat gate valves R and L. It enters and the movement of the flat gate valves R and L stops.
内外圧縮室の作動ガスが圧縮されて流出室を介して吐出している状態から作動ガスが吐出空間に流出するのを停止させるには、流出室５０６ｈに開口する吐出孔に接続されている配管途中に設けた制御弁を切り替えて連通している空間を吐出側から吸入側に変更する。このような状態では該係止機構が動作すなわち該係止部材のピン部が平板ゲート弁Ｒの係止穴に嵌り該平板ゲート弁Ｒが停止することにより圧縮室内の作動ガスが流入室に再び入
り循環を繰り返すことで、吐出側への流出が停止することになる。 In order to stop the working gas from flowing into the discharge space from the state in which the working gas in the inner and outer compression chambers is compressed and discharged through the outflow chamber, piping connected to the discharge hole opened in the outflow chamber 506h The control valve provided in the middle is switched to change the communication space from the discharge side to the suction side. In such a state, the locking mechanism operates, that is, the pin portion of the locking member fits into the locking hole of the flat gate valve R, and the flat gate valve R stops, so that the working gas in the compression chamber returns to the inflow chamber. By repeating the entry and circulation, the outflow to the discharge side is stopped.
以上より、吐出機構Ｅ５０１を用いたスクロール式の容積型圧縮機では、平板ゲート弁ＲとＬの開口の遅れや閉じ遅れがないこと、該先端部の死空間が殆どないことに加えて弁収納室の流出室と圧縮室ないしは溝終端部に連通する流入室との漏れも殆どなくなるので高効率化が図れる。 As described above, in the scroll type positive displacement compressor using the discharge mechanism E501, there is no delay in opening and closing the flat gate valves R and L, and there is almost no dead space at the tip, and the valve is accommodated. Leakage between the outflow chamber of the chamber and the inflow chamber communicating with the compression chamber or the end of the groove is almost eliminated, so that high efficiency can be achieved.
産業上利用可能な実施例として、上記では空調用や冷凍用などに用いられるリング式、ロータリ式およびスクロール式の容積型圧縮機を取り上げて説明したが、それ以外の容積型圧縮機であるスイング式圧縮機、空気用ポンプおよび真空ポンプへの適用は可能である。 In the above description, the ring type, rotary type and scroll type positive displacement compressors used for air conditioning and refrigeration have been described as examples that can be used industrially. However, the swing is a positive displacement compressor other than that. Application to a compressor, a pump for air and a vacuum pump is possible.
１、４０１、５０１…容積型圧縮機
６、１０６、２０６、３０６、４０６、５０６…固定シリンダ
6ａ、１０６ａ、２０６ａ、３０６ａ、４０６ａ、５０６ａ…包絡溝
６ｄ、１０６ｄ、２０６ｄ、３０６ｄ、４０６ｄ、５０６ｄ…流出室
６ｈ、１０６ｈ、１４６ｈ、２０６ｈ、３０６ｄ、４０６ｄ、５０６ｄ…弁装着室
６ｊ、１０６ｊ、１４６ｊ、２０６ｊ、３０６ｄ、４０６ｄ、５０６ｄ…背面室
７、１０７、３０７、５０７…旋回ピストン
７ａ、１０７ａ、３０７ａ、５０７ａ…旋回突起
７ｃ、１０７ｃ、３０７ｃ、５０７ｃ…直線突起
８、４８、６８、８８、１４８、１６８、１８８…平板ゲート弁Ｒ
８ａ、１１２ａ…先端部
９、４９、６９、８９、１４９、１６９、１８９…平板ゲート弁Ｌ
１２ｃ、１１２ｃ…側壁シール面
１２ｄ、１１２ｄ…側壁支持面
１０６ｍ、５０６ｍ…係止制御室
１０６ｎ、５０６ｎ…係止孔
１３、２１３、３１３…外圧縮室
１４、２１４、３１４…内圧縮室
６ｅ、１１２ｅ…係止穴
３０、３３０、５２２…係止部材
３１、３３１、５２３…係止バネ
１３６、１５６…弁補助材
４１１…圧縮室
４１４、５１５、５１６…仕切板
４１４ａ、５１５ａ、５１６ａ…先端部
４１４ｂ、５１５ｂ、５１６ｂ…弁支持部
４１４ｃ、５１５ｃ、５１６ｃ…側壁支持面
１７、１１９…流出通路
１２、９２、１１２、１５２、１９２…吐出機構Ａ
２１０…弁台座
２１２…吐出機構Ｂ
３０８…円弧ゲート弁Ｒ
３０９…円弧ゲート弁Ｌ
４０７…円筒ピストン
４１３…平板ゲート弁Ｓ
３１２、３５２…吐出機構Ｃ
４１２…吐出機構Ｄ
５１２…吐出機構Ｅ DESCRIPTION OF SYMBOLS 1,401,501 ... Positive displacement compressor 6, 106, 206, 306, 406, 506 ... Fixed cylinder
6a, 106a, 206a, 306a, 406a, 506a ... envelope grooves 6d, 106d, 206d, 306d, 406d, 506d ... outflow chambers 6h, 106h, 146h, 206h, 306d, 406d, 506d ... valve mounting chambers 6j, 106j, 146j 206j, 306d, 406d, 506d ... Back chamber 7, 107, 307, 507 ... Revolving piston 7a, 107a, 307a, 507a ... Revolving protrusion 7c, 107c, 307c, 507c ... Linear protrusion 8, 48, 68, 88, 148 168, 188 ... Flat gate valve R
8a, 112a ... tip 9, 49, 69, 89, 149, 169, 189 ... flat gate valve L
12c, 112c ... sidewall seal surfaces 12d, 112d ... sidewall support surfaces 106m, 506m ... locking control chambers 106n, 506n ... locking holes 13, 213, 313 ... outer compression chambers 14, 214, 314 ... inner compression chambers 6e, 112e ... Locking holes 30, 330, 522 ... Locking members 31, 331, 523 ... Locking springs 136, 156 ... Valve auxiliary material 411 ... Compression chambers 414, 515, 516 ... Partition plates 414a, 515a, 516a ... Tip 414b 515b, 516b ... Valve support portions 414c, 515c, 516c ... Side wall support surfaces 17, 119 ... Outflow passages 12, 92, 112, 152, 192 ... Discharge mechanism A
210 ... Valve seat 212 ... Discharge mechanism B
308 ... Round gate valve R
309 ... Circular gate valve L
407 ... Cylindrical piston 413 ... Flat gate valve S
312, 352... Discharge mechanism C
412: Discharge mechanism D
512: Discharge mechanism E

Claims (30)

  1. 密閉容器などに固定された内側に円弧状の垂直壁面を有する固定構成部材に支承されて回転する駆動軸の偏心軸部に円弧状の垂直壁面を有する可動機構部材を装着して円弧状の垂直面で形成される三日月状の柱状空間の上下に平坦面を有する平坦端板で挟み込んで形成される圧縮室の一端に該可動機構部材の回転運動ないしは旋回運動により圧縮室空間を減少させて作動ガスを圧縮し流出させる吐出機構を装着した容積型圧縮機に於いて、
    該固定構成部材の該圧縮室を形成する垂直壁面に平行で同一高さのおよそ断面矩形で該圧縮室垂直壁面に開口する弁装着室とその反対側に背面室を設けて構成される弁収納室内に該圧縮室を形成する該可動機構部材の垂直壁面を弁座として先端部が密着できる形状を有する断面矩形の板状弁体を装着し、上下端面と該平坦端板間は微小隙間を介して摺接し該弁収納室の圧縮室側の垂直壁面と板状弁体の壁面間も摺接する構成とし、該板状弁体の支持部材や板状弁体周囲のシール部材および板状弁体の一端に装着されるバネのような弾性体などを含めた補機部材で構成される弁機構体を該弁収納室内に装着して構成された吐出機構を備えたことを特徴とする容積型圧縮機。     A movable mechanism member having an arcuate vertical wall surface is mounted on an eccentric shaft portion of a drive shaft that is supported by a stationary component member having an arcuate vertical wall surface that is fixed to an airtight container or the like and rotates. Operates by reducing the compression chamber space by rotating or swiveling the movable mechanism member at one end of the compression chamber formed by sandwiching flat end plates with flat surfaces above and below the crescent-shaped columnar space formed by the surface In a positive displacement compressor equipped with a discharge mechanism that compresses and flows out gas,
    A valve housing configured by providing a valve mounting chamber that opens to the vertical wall surface of the compression chamber and has a back chamber on the opposite side thereof, which is approximately rectangular in cross-section and parallel to the vertical wall surface forming the compression chamber of the fixed component. A plate-shaped valve body with a rectangular cross section having a shape that allows the tip to be in close contact with the vertical wall surface of the movable mechanism member forming the compression chamber as a valve seat is installed in the chamber, and there is a small gap between the upper and lower end surfaces and the flat end plate. A vertical wall surface on the compression chamber side of the valve storage chamber and a wall surface of the plate-shaped valve body are also slidably contacted, and a support member for the plate-shaped valve body, a sealing member around the plate-shaped valve body, and a plate-shaped valve A volume comprising a discharge mechanism configured by mounting a valve mechanism composed of an auxiliary member including an elastic body such as a spring mounted on one end of the body in the valve storage chamber. Mold compressor.
  2. 前記圧縮室に隣接する前記弁装着室の側壁面ないしはその側壁面に面接触する前記板状弁体の側壁面の何れかに該側壁面より一段凹ました周囲の境界線が前記背面室に連通しない空間である圧力ポケットを形成し、該圧縮室と該圧力ポケットを連通する通路を該板状弁体ないしは該弁収納室の側壁面に設けて構成した吐出機構を備えたことを特徴とする請求項１記載の容積型圧縮機。 One of the side wall surfaces of the valve mounting chamber adjacent to the compression chamber or the side wall surface of the plate-like valve body in surface contact with the side wall surface is recessed by one step from the side wall surface, and the surrounding boundary line communicates with the back chamber. A discharge mechanism comprising a pressure pocket that is a non-operating space and a passage that connects the compression chamber and the pressure pocket is provided on a side wall surface of the plate-like valve body or the valve storage chamber. The positive displacement compressor according to claim 1.
  3. 前記固定構成部材に設けた吐出ガスから分離された油を溜める貯油池ないしは密閉容器の下部に設けた油槽に一端を開口し他端を前記平坦端板の弁装着室内に開口する注油孔と前記板状弁体の上端面に設けた油受孔と導入溝および先端部の先端油溝それぞれと間欠的に連通させて該貯油池ないしは該密閉容器内の油を該板状弁体の先端油溝に導くように構成された吐出機構を備えたことを特徴とする請求項１ないしは２記載の容積型圧縮機。 An oil supply hole for storing oil separated from discharge gas provided in the fixed component member or an oil tank provided at a lower portion of a sealed container and having an other end opened in the valve mounting chamber of the flat end plate An oil receiving hole provided on the upper end surface of the plate-shaped valve body, an introduction groove, and a tip oil groove at the distal end are intermittently communicated with each other so that the oil in the reservoir or the sealed container is transferred to the tip oil of the plate-shaped valve body. 3. The positive displacement compressor according to claim 1, further comprising a discharge mechanism configured to guide the groove.
  4. 前記固定構成部材ないしは前記弁収納室を形成する材料と前記板状弁体に用いる材料の線膨張係数をおよそ同一で構成した吐出機構を備えたことを特徴とする請求項１乃至３の何れかに記載の容積型圧縮機。 4. The discharge mechanism according to claim 1, further comprising: a linear expansion coefficient of a material that forms the fixed component member or the valve housing chamber and a material used for the plate-like valve body. The positive displacement compressor described in 1.
  5. 前記の固定構成部材と可動機構部材との間に設けた自転を阻止し公転運動をさせる旋回機構により前記偏心軸の偏心量を公転半径とする旋回運動を行う可動機構部材としての旋回ピストンに前記弁座を駆動軸の軸線に平行な垂直壁面で形成するとともに該旋回ピストンの圧縮室を形成する駆動軸の軸線に平行な壁面の包絡線となる壁面を有する前記固定構成部材を固定シリンダとして構成した吐出機構を備えたことを特徴とする請求項１乃至４の何れかに記載の容積型圧縮機。 The revolving piston as a movable mechanism member that performs a revolving motion with the amount of eccentricity of the eccentric shaft as a revolving radius by a revolving mechanism that prevents rotation and revolves provided between the fixed component member and the movable mechanism member. The valve seat is formed of a vertical wall surface parallel to the axis of the drive shaft, and the fixed component member having a wall surface that is an envelope of the wall surface parallel to the axis of the drive shaft forming the compression chamber of the orbiting piston is configured as a fixed cylinder. The positive displacement compressor according to any one of claims 1 to 4, further comprising a discharge mechanism formed.
  6. 矩形断面の帯状板を曲げて円弧状に形成した円弧突起の一端を前記旋回半径の倍以上の長さの直線で平坦面の平坦弁座を直線突起とした旋回突起をおよそ円形板の旋回ディスクの片面側に直立させて形成した旋回ピストンの旋回突起の旋回運動から形成される包絡溝の一端に設けた直線状の平行壁面を有する流出室に一端が開口して該包絡溝と同一底面を有し該直線突起を挟んで対向して配置された２箇所の弁装着室を設けて固定シリンダを形成するとともに該直線突起を挟んで対向する2箇所の該弁装着室内に装着し該板状弁体の先端部を該直線突起に当接させて構成した吐出機構を備えたことを特徴とする請求項５記載の容積型圧縮機。 A circular disc swivel disc having a circular projection formed by bending a belt-like plate having a rectangular cross section into a circular arc and having one end of a circular arc projection that is a straight line longer than the turning radius and a flat valve seat on a flat surface as a straight projection. One end is opened to the outflow chamber having a linear parallel wall surface provided at one end of the envelope groove formed by the swiveling motion of the swiveling protrusion of the swiveling piston formed upright on one side of the same, and the same bottom surface as the envelope groove is formed. And having two valve mounting chambers arranged opposite to each other across the linear protrusion to form a fixed cylinder and mounted in the two valve mounting chambers opposed across the linear protrusion to form the plate 6. The positive displacement compressor according to claim 5, further comprising a discharge mechanism configured such that a distal end portion of the valve body is brought into contact with the linear protrusion.
  7. 前記円弧突起を１周以下の円弧形状に曲げて形成した部分円筒の一端に前記直線突起を設けた旋回突起を旋回ディスクに直立させて構成した旋回ピストン、
    該旋回突起から形成される包絡溝を厚い端板に凹設した一端に設けた流入室と他端の直線状平行溝である流出室それぞれに吸入孔と吐出孔を設けた固定シリンダの該直線突起を挟んで対称に配置した前記弁収納室に板状弁体と補助部材で構成される弁機構体を装着した上で該包絡溝内に該旋回突起を遊挿して構成した吐出機構を備えたことを特徴とする請求項６記載の容積型圧縮機。     A revolving piston comprising a revolving protrusion in which a straight protrusion is provided at one end of a partial cylinder formed by bending the circular protrusion into an arc shape having a circumference of 1 round or less;
    The straight line of the fixed cylinder provided with the suction hole and the discharge hole in each of the inflow chamber provided at one end where the envelope groove formed from the swiveling projection is recessed in the thick end plate and the outflow chamber which is a linear parallel groove at the other end A discharge mechanism configured by loosely inserting the swiveling protrusion into the envelope groove after mounting a valve mechanism composed of a plate-like valve body and an auxiliary member on the valve storage chamber disposed symmetrically across the protrusion; The positive displacement compressor according to claim 6, wherein the positive displacement compressor is provided.
  8. 断面矩形の帯状板を渦巻き状に曲げて形成した渦巻き突起の内側終端部から接線方向に前記偏心軸の偏心量に相当する旋回半径の倍以上の長さで延設した直線突起を該渦巻き突起と一体に形成した旋回突起を旋回ディスクに直立させて構成した旋回ピストンとその該旋回突起の旋回運動で形成される厚い端板に凹設した包絡溝の外側端部を流入室とし内側端部の直線状溝を流出室としたそれぞれに吸入孔と吐出孔を設け、該流出室の直線状溝の両側に線対称的に弁収納室を設けた固定シリンダとそれぞれの該旋回突起と該包絡溝を噛み合わせて圧縮室を形成した上で該弁収納室２箇所に前記板状弁体と補助部材で構成した弁機構体を装着した吐出機構を備えたことを特徴とする請求項６記載の容積型圧縮機。 A linear protrusion extending from the inner terminal portion of a spiral protrusion formed by bending a belt-like plate having a rectangular cross section in a tangential direction with a length more than double the turning radius corresponding to the eccentric amount of the eccentric shaft. The swiveling piston formed integrally with the swiveling disk and the outer end of the envelope groove recessed in the thick end plate formed by the swiveling motion of the swiveling protrusion are used as the inflow chamber and the inner end. Each of which has a straight groove as an outflow chamber, a suction hole and a discharge hole, and a fixed cylinder in which valve storage chambers are provided symmetrically on both sides of the straight groove in the outflow chamber, and each of the swiveling protrusions and the envelope 7. A discharge mechanism is provided, wherein a compression chamber is formed by meshing a groove, and a valve mechanism composed of the plate-like valve body and an auxiliary member is mounted at two locations in the valve storage chamber. Positive displacement compressor.
  9. 前記旋回突起の渦巻き突起に前記流入室側のインボリュート曲線を適用した外渦巻き突起の内側には同一接線で接続した曲率がより小さいインボリュート曲線ないしは円弧曲線で形成した内渦巻き突起の内側を接線方向に延長した前記直線突起で接続することで２種類の曲線と１つの直線で旋回突起を形成した旋回ピストンと前記固定シリンダと弁機構体で構成した吐出機構を備えたことを特徴とする請求項８記載の容積型圧縮機。 Applying the involute curve on the inflow chamber side to the spiral protrusion of the swirl protrusion, the inside of the inner spiral protrusion formed by an involute curve or an arc curve having a smaller curvature connected on the inner side of the outer spiral protrusion is connected in the tangential direction. 9. A discharge mechanism comprising a swiveling piston having a swivel projection formed by two types of curves and a single straight line, a fixed cylinder, and a valve mechanism connected by the extended straight protrusion. The positive displacement compressor as described.
  10. 前記包絡溝の終端に設けた前記流出室側壁面に該包絡溝と同一高さで奥に向けて平行壁面の断面矩形の空間で形成される弁装着室とその奥に設けた背面室から形成される弁収納室を設けるとともに該背面室と吐出空間内とを連通する圧導入孔を設けた固定シリンダ、およそ直方体の板状弁体を該弁装着室に収納するとともに該背面室内の該板状弁体と該固定シリンダ間にバネ等の弾性体とそれを支える部材である補機部材から構成される弁機構体として該弁収納室に収納することで該板状弁体を該弁装着室の側壁面に沿って摺接可能に装着して構成した吐出機構を備えたことを特徴とする請求項５乃至９の何れかに記載の容積型圧縮機。 Formed on the side wall surface of the outflow chamber provided at the end of the envelope groove from a valve mounting chamber formed by a space of a rectangular cross-section of a parallel wall surface at the same height as the envelope groove and a back chamber provided at the back thereof A fixed cylinder provided with a pressure introduction hole for communicating the back chamber and the inside of the discharge space, a plate-shaped valve body having a substantially rectangular parallelepiped shape is accommodated in the valve mounting chamber and the plate in the back chamber The plate-like valve body is mounted on the valve by housing it in the valve storage chamber as a valve mechanism body comprising an elastic body such as a spring and an auxiliary member which is a member supporting the elastic body between the valve body and the fixed cylinder. The positive displacement compressor according to any one of claims 5 to 9, further comprising a discharge mechanism configured to be slidably mounted along a side wall surface of the chamber.
  11. 前記弁装着室の矩形溝上下面を塞ぐ固定部材に形成した円筒空間の平坦面の一端に設けた低圧通路に連通する低圧導入孔と他端側に設けた該弁装着室内に連通する連通孔から形成された係止制御室を設け、大径の円筒部と小径のピン部の2段円筒で形成された係止部材の内側空洞部にバネなどの弾性体を装着して該係止制御室に収納するとともに前記板状弁体の先端部が圧縮室内より内側の該弁収納室内に収納された状態で固定部材面上を摺動する上下端面ないしは側壁シール面の内何れか一箇所に該係止部材のピン部が遊挿可能な位置に係止穴を設けた板状弁体で構成された吐出機構を備えたことを特徴とする請求項１０記載の容積型圧縮機。 From the low-pressure introduction hole communicating with the low-pressure passage provided at one end of the flat surface of the cylindrical space formed in the fixing member that closes the upper and lower surfaces of the rectangular groove of the valve mounting chamber and the communication hole communicating with the valve mounting chamber provided at the other end side An engagement control chamber is provided, and an elastic body such as a spring is attached to the inner cavity of the engagement member formed of a two-stage cylinder of a large diameter cylindrical portion and a small diameter pin portion. And the tip of the plate-shaped valve body is accommodated in any one of the upper and lower end surfaces or the side wall seal surface that slides on the fixed member surface in a state where the distal end portion is accommodated in the valve accommodating chamber inside the compression chamber. 11. The positive displacement compressor according to claim 10, further comprising a discharge mechanism constituted by a plate-shaped valve body provided with a locking hole at a position where the pin portion of the locking member can be loosely inserted.
  12. 前記弁装着室底面に平行でおよそ同一平面形状となるように複数に分割して形成した積層構造の板状弁体を該弁装着室内に収納して構成された吐出機構を備えたことを特徴とする請求項１０ないしは１１記載の容積型圧縮機。 A discharge mechanism configured to accommodate a plate-like valve body having a laminated structure formed in a plurality of parts so as to be parallel to the bottom surface of the valve mounting chamber and approximately in the same plane is housed in the valve mounting chamber. The positive displacement compressor according to claim 10 or 11.
  13. 前記板状弁体をおよそ直方体の平板ゲート弁で形成した先端部の流出室側に該弁板厚の1／２以下の一定幅で前記平坦弁座に摺接する平坦シール面を設けるとともに圧縮室側には該平坦弁座に対して隙間を設けた該平坦シール面より凹ました傾斜面ないしは段差を設けて先端部に受圧面を形成した平板ゲート弁を圧縮室側の側壁面に開口する前記弁装着室に該平板ゲート弁の前後側壁面と上下端面の4面との間に微小隙間を設けるとともに該弁装着室の該側壁面に往復摺動が可能に装着して構成された吐出機構を備えたことを特徴とする請求項１０乃至１２の何れかに記載の容積型圧縮機。 A flat sealing surface that slides on the flat valve seat with a constant width equal to or less than 1/2 of the valve plate thickness is provided on the outflow chamber side of the tip portion formed by the flat plate gate valve having a substantially rectangular parallelepiped shape and the compression chamber. A flat plate gate valve having a pressure receiving surface at the tip by providing an inclined surface or a step that is recessed from the flat sealing surface provided with a gap with respect to the flat valve seat is opened on the side wall surface on the compression chamber side. Discharge mechanism constructed by providing a minute gap between the front and rear side wall surfaces of the flat gate valve and the upper and lower end surfaces in the valve mounting chamber and reciprocally sliding on the side wall surface of the valve mounting chamber The positive displacement compressor according to claim 10, wherein the positive displacement compressor is provided.
  14. 前記平板ゲート弁先端部のおよそ中央部に該側壁面高さの１／２以下の幅でおよそ中央部に前記平坦シール面から圧縮室側に向けて開口する数十度に傾斜させた風圧受面を設けて構成された吐出機構を備えたことを特徴とする請求項１３記載の容積型圧縮機。 A wind pressure receiver that is inclined at tens of degrees that opens from the flat seal surface toward the compression chamber at the center at a width that is half or less the height of the side wall surface at the center of the flat gate gate tip. The positive displacement compressor according to claim 13, further comprising a discharge mechanism having a surface.
  15. 前記弁装着室の平行溝の幅を前記平板ゲート弁の厚さよりも大きく形成した上で、その差に相当する板厚でおよそ直方体の弁補助材を該弁装着室内に該平板ゲート弁と並置し、該弁補助材の先端部側に圧縮室側と流出室側を連通する開口部を設け先端部を前記旋回ピストン直線突起の前記平坦弁座に摺接させるとともに該平板ゲート弁と該弁補助材が互いに独立して動作するように構成された吐出機構を備えたことを特徴とする請求項１３ないしは１４記載の容積型圧縮機。 After forming the width of the parallel groove of the valve mounting chamber to be larger than the thickness of the flat gate valve, an approximately rectangular parallelepiped valve auxiliary material is juxtaposed with the flat gate valve in the valve mounting chamber with a plate thickness corresponding to the difference. An opening for communicating the compression chamber side and the outflow chamber side is provided on the distal end portion side of the valve auxiliary member, the distal end portion is slidably contacted with the flat valve seat of the revolving piston linear protrusion, and the flat gate valve and the valve 15. The positive displacement compressor according to claim 13, further comprising a discharge mechanism configured such that the auxiliary members operate independently of each other.
  16. 前記弁装着室内に前記平板ゲート弁背面室側端面の高さ方向の一定幅を庇のように前記流出室側に張り出した拘止部を設けて並置した前記弁補助材にその厚さよりも大きく且つ該弁装着室の幅から該平板ゲート弁の厚さを引いた値よりも僅かに小さい直径を有する転がり軸受などの転動体を該弁装着室と該平板ゲート弁の側壁面間上で転動可能な状態で該弁補助材に１個ないしは複数個装着して構成された吐出機構を備えたことを特徴とする請求項１５記載の容積型圧縮機。 In the valve mounting chamber, a fixed width in the height direction of the flat gate gate rear chamber side end surface is provided with a restraining portion projecting toward the outflow chamber side like a ridge, and the valve auxiliary material juxtaposed is larger than the thickness thereof. A rolling element such as a rolling bearing having a diameter slightly smaller than the value obtained by subtracting the thickness of the flat gate valve from the width of the valve mounting chamber is rolled between the valve mounting chamber and the side wall surface of the flat gate valve. 16. The positive displacement compressor according to claim 15, further comprising a discharge mechanism configured to be mounted on one or more valve auxiliary members in a movable state.
  17. 旋回ピストンの前記直線突起に面接触する前記平板ゲート弁先端部の平坦シール面との隙間の関係を維持した上で該直線突起と前記包絡溝の流出室側終端部の平行溝に対する前記弁装着室の包絡溝側の側壁面取り付け角度を垂直面から数度前後の角度を傾斜させて設けるとともに該平板ゲート弁先端部と側壁面の相対角度も同様に合わせた形状で構成された吐出機構を備えたことを特徴とする請求項１３ないしは１４記載の容積型圧縮機。 The valve mounting on the parallel groove at the outflow chamber side end portion of the envelope groove while maintaining the relationship of the clearance between the flat seal surface of the flat gate gate tip end portion in surface contact with the linear protrusion of the orbiting piston A discharge mechanism having a shape in which the side wall surface mounting angle on the envelope groove side of the chamber is inclined at an angle of about several degrees from the vertical surface and the relative angle between the flat gate gate tip and the side wall surface is also matched. 15. The positive displacement compressor according to claim 13, further comprising a positive displacement compressor.
  18. 前記平板ゲート弁先端部を前記直線突起に摺接可能とし、該平板ゲート弁側壁支持面側のおよそ中央部から先端部に向けて掘り下げた凹溝内に設けた圧縮室側に連通する吐出孔を塞ぐようにリード弁とそれの背面で変形を支えるリテーナを装着して構成された吐出機構を備えたことを特徴とする請求項１３ないしは１４記載の容積型圧縮機。 Discharge hole communicating with the compression chamber side provided in the concave groove dug down from about the center part of the flat gate gate valve side wall support surface side toward the front end part so that the flat gate valve front end part can be slidably contacted 15. The positive displacement compressor according to claim 13, further comprising a discharge mechanism configured to be mounted with a reed valve and a retainer that supports deformation on the back surface of the reed valve so as to close the valve.
  19. 前記固定シリンダの包絡溝と同じ幅と高さの平行溝で形成される弁装着室が該包絡溝に開口する反対側に両端部を該包絡溝と同じ幅の円弧形状とした背面室を形成し、該弁装着室の溝幅が該平板ゲート弁の厚さよりも大きい場合、その差に相当する幅の直方体のサイドスペーサを該包絡溝内に突出しないように該弁装着室の流出側側壁面に密着させて固定シリンダに繋止して構成された吐出機構を備えたことを特徴とする請求項１３乃至１８の何れかに記載の容積型圧縮機。 A valve mounting chamber formed of parallel grooves having the same width and height as the envelope groove of the fixed cylinder forms a back chamber having an arc shape with both ends at the same width as the envelope groove on the opposite side to the envelope groove. When the groove width of the valve mounting chamber is larger than the thickness of the flat gate valve, the side spacer of the rectangular parallelepiped having a width corresponding to the difference does not protrude into the envelope groove. The positive displacement compressor according to any one of claims 13 to 18, further comprising a discharge mechanism configured to be in close contact with a wall surface and fixed to a fixed cylinder.
  20. 前記弁装着室流出室側の側壁面を側壁シール面とし旋回突起の前記旋回突起に摺接する先端部を設けた前記平板ゲート弁と同じ高さのおよそ直方体の仕切板を該平板ゲート弁とで１セットにして対向する2箇所の該弁装着室内に装着するとともに該平板ゲート弁と該仕切板との間に設けた互いの側壁面を支える弁支持部を設けた間にはそれら先端部から背面室側に抜ける流出通路を設け、さらにはその背面室の固定シリンダとの間に必要に応じてバネなどの弾性体を組み付けて構成した弁機構体を装着して構成される吐出機構を備えたことを特徴とする請求項１３乃至１９の何れかに記載の容積型圧縮機。 A partition plate having a substantially rectangular parallelepiped shape having the same height as that of the flat gate valve provided with a side wall seal surface on the valve mounting chamber outflow chamber side as a side wall seal surface and provided with a distal end portion that is in sliding contact with the swivel protrusion is provided with the flat plate gate valve. Between the two valve mounting chambers that face each other as a set, and between the valve support portions that support the side wall surfaces provided between the flat gate valve and the partition plate, Provided with a discharge mechanism that is provided with an outflow passage that opens to the back chamber side, and is further equipped with a valve mechanism body that is configured by assembling an elastic body such as a spring between the back cylinder and the fixed cylinder of the back chamber. The positive displacement compressor according to claim 13, wherein the positive displacement compressor is provided.
  21. 前記平板ゲート弁側の側壁面の一部を凹まして前記流出通路を広げて迂回路を設けた仕切板と組み合わせる前記平板ゲート弁側壁支持面から該仕切板側に向け垂直に延びた矩形平板の弁安定板を該平板ゲート弁の側壁支持面上で一体固定するとともに該弁安定板と先端部との間に一端が開口し他端が前記弁装着室に摺接する側壁シール面に開口する連通孔を設けた平板ゲート弁を装着して吐出機構を構成したことを特徴とする請求項２０記載の容
    積型圧縮機。     A rectangular flat plate extending vertically from the flat plate gate valve side wall support surface to the partition plate side in combination with a partition plate in which a part of the side wall surface on the flat plate gate valve side is recessed and the outflow passage is widened to provide a detour. The valve stabilizing plate is integrally fixed on the side wall supporting surface of the flat gate valve, and one end is opened between the valve stabilizing plate and the tip portion, and the other end is connected to the side wall sealing surface that is in sliding contact with the valve mounting chamber. 21. The positive displacement compressor according to claim 20, wherein a discharge mechanism is configured by mounting a flat gate valve provided with a hole.
  22. 前記弁装着室内に前記平板ゲート弁と並置した前記仕切板にその厚さよりも大きく且つ該弁装着室の幅から該平板ゲート弁の厚さを引いた値よりも僅かに小さい直径を有する転がり軸受などの転動体を該弁装着室と該平板ゲート弁の側壁面間上で転動可能な状態で該仕切板に１個ないしは複数個装着して構成された吐出機構を備えたことを特徴とする請求項２０記載の容積型圧縮機。 A rolling bearing having a diameter larger than the thickness of the partition plate juxtaposed with the flat gate valve in the valve mounting chamber and slightly smaller than a value obtained by subtracting the thickness of the flat gate valve from the width of the valve mounting chamber. Characterized in that it comprises a discharge mechanism configured such that one or more rolling elements are mounted on the partition plate in a state in which rolling elements such as can be rolled between the valve mounting chamber and the side wall surface of the flat gate valve. The positive displacement compressor according to claim 20.
  23. 前記固定シリンダ包絡溝の終端部である流出室と同一底面で該包絡溝と同じ高さの垂直壁面を有し両端が該流出室に開口する部分的なリング溝の外径である円筒内壁の直径が該包絡溝幅のおよそ２倍以上で中心が該流出室の溝幅中心とおよそ一致させた均一な溝幅を有するリング溝両端が該流出室に開口する空間を弁収納室としたその中央部に装着した中間部材の端面から該流出室開口部までの２箇所の空間を弁装着室として構成し、その弁装着室内に回動可能に１／４周前後から半周以下の範囲の円弧で形成した板状弁体としての円弧ゲート弁を該直線突起に対して対向させて挿着するとともに該円弧ゲート弁と該中間部材に挟まれた空間である2箇所の背面室にバネなどの弾性部材を装着して構成された吐出機構を備えたことを特徴とする請求項１０乃至１２の何れかに記載の容積型圧縮機。 A cylindrical inner wall that is the outer diameter of a partial ring groove that has a vertical wall surface at the same bottom surface as the outflow chamber that is the terminal portion of the fixed cylinder envelope groove and has the same height as the envelope groove, and both ends open to the outflow chamber. The valve storage chamber is a space in which both ends of the ring groove having a uniform groove width whose diameter is approximately twice or more than the envelope groove width and whose center is approximately coincident with the groove width center of the outflow chamber are open to the outflow chamber. Two spaces from the end face of the intermediate member mounted at the center to the outflow chamber opening are configured as a valve mounting chamber, and an arc in a range from about 1/4 turn to less than a half turn is rotatable in the valve mounting chamber. A circular gate valve as a plate-shaped valve body formed in the above is inserted so as to face the linear protrusion, and a spring or the like is provided in two back chambers that are sandwiched between the circular gate valve and the intermediate member. Equipped with a discharge mechanism configured with an elastic member The positive displacement compressor according to any one of claims 10 to 12.
  24. ガスの流れに伴う動圧が発生する吐出空間内の通路ないしは該吐出機構近傍の圧縮室と２箇所に設けた前記背面室との間に連通孔を設けて構成された吐出機構を備えたことを特徴とする請求項２３記載の容積型圧縮機。 A discharge mechanism having a communication hole provided between a passage in a discharge space where dynamic pressure is generated due to a gas flow or a compression chamber in the vicinity of the discharge mechanism and the back chamber provided in two places is provided. The positive displacement compressor according to claim 23.
  25. 前記弁装着室の円弧側壁面に互いに重着するように複数に分割した円弧ゲート弁をそれぞれが独立して摺動可能に装着した積層構造の円弧ゲート弁で吐出機構を構成したことを特徴とする請求項２３ないしは２４記載の容積型圧縮機。 The discharge mechanism is configured by an arc gate valve having a laminated structure in which an arc gate valve divided into a plurality of pieces so as to overlap each other on the arc side wall surface of the valve mounting chamber is slidably mounted independently. 25. The positive displacement compressor according to claim 23 or 24.
  26. 前記リング溝の弁装着室の内側側壁面と前記流出室の側壁面とで一体に形成されたＵ字塔部分をＵ字溝付円柱として分離するとともに該Ｕ字溝付円柱の端面を該円筒室の底面に複数のピンないしはボルトで取り付けて前記円筒内壁とＵ字溝付円柱外壁間に中間部材を装着して弁装着室と背面室とで弁収納室を構成した吐出機構を備えたことを特徴とする請求項２３乃至２５の何れかに記載の容積型圧縮機。 The U-shaped tower portion formed integrally with the inner side wall surface of the valve mounting chamber of the ring groove and the side wall surface of the outflow chamber is separated as a U-shaped grooved cylinder, and the end surface of the U-shaped grooved cylinder is the cylinder. A discharge mechanism is provided in which a valve housing chamber is constituted by a valve mounting chamber and a back chamber by attaching an intermediate member between the cylindrical inner wall and the U-shaped grooved columnar outer wall by attaching a plurality of pins or bolts to the bottom surface of the chamber. The positive displacement compressor according to any one of claims 23 to 25.
  27. 前記固定シリンダ包絡溝の流出室側に設けた前記弁装着室内の前記旋回ディスク上に装着した直動可能なおよそ直方体の弁台座の先端部を前記旋回ピストンの直線突起に摺接させた上で該弁台座上に直立固定した回転ピンに背面室側の円弧状端面中央に設けたピン用穴に回転可能に板状弁体であるフラップ弁を装着し、そのフラップ弁の先端部は圧縮室側を半円弧状とし流出室側は前記直線突起に摺接するシール面を設けるとともに該弁台座と背面室側の固定シリンダとの間に背面バネを装着しさらには該フラップ弁と弁装着室流出室側の側壁面との間に設けたゼンマイ等の側面バネなどで構成した上で該弁台座と該フラップ弁高さの合計を該弁装着室高さとおよそ一致させて相対的に摺動可能に構成された吐出機構を備えたことを特徴とする請求項５乃至９の何れかに記載の容積型圧縮機。 After the front end portion of a substantially cuboid valve seat mounted on the swivel disc in the valve mounting chamber provided on the outflow chamber side of the fixed cylinder envelope groove is brought into sliding contact with the linear protrusion of the swivel piston. A flap valve, which is a plate-like valve body, is rotatably mounted in a pin hole provided in the center of the arcuate end surface on the back chamber side on a rotating pin fixed upright on the valve seat, and the tip of the flap valve is a compression chamber The side of the outflow chamber has a semicircular arc shape, and a sealing surface is provided in sliding contact with the linear protrusion, and a back spring is mounted between the valve seat and the fixed cylinder on the back chamber side, and the flap valve and the valve mounting chamber flow out. It is composed of a spring such as a spring provided between the side wall of the chamber and the like, and the total height of the valve seat and the flap valve can be slid relative to the valve mounting chamber. It is characterized by having a discharge mechanism configured in Displacement compressor according to any one of claims 5 to 9.
  28. 前記可動機構部材を両端面が平行平坦な中空円柱体の円筒ピストンを駆動軸の偏心軸に装着して回転または旋回ないしは揺動させて得られる該円筒ピストン外壁面の包絡線として得られる円筒状の内壁面を中央部に設け両端面を平行平坦に形成した前記固定構成部材としての固定シリンダに該円筒ピストンを組み込んで形成される三日月状の柱状空間を平坦な平坦蓋部材で挟み込んで形成される空間を該固定シリンダ円筒状の内壁面に一端が矩形状で開口する平行溝内に直動可能にして先端部を該円筒ピストンの外壁面に摺接させたおよそ直方体の仕切板で仕切って吸入室と圧縮室を形成した容積型圧縮機に於いて、
    該仕切板を装着する固定シリンダの該平行溝の溝幅を大きく拡大して形成した弁装着室と
    その奥に設けた流出室とで弁収納室を形成し、該弁装着室の圧縮室側の側壁面に摺接する側壁シール面を有し先端部が該円筒ピストン外壁面に摺接するおよそ直方体の平板ゲート弁と該仕切板との側壁面間に支持部材を設けそれらの先端部から該流出室側に抜ける流出通路を設けるとともに該流出室には必要に応じてバネなどの弾性体を装着して組み付けて構成した弁機構体を該弁収納室に装着して構成される吐出機構を備えたことを特徴とする請求項５乃至９の何れかに記載の容積型圧縮機。     A cylindrical shape obtained as an envelope of the outer wall surface of the cylindrical piston obtained by rotating or swiveling or swinging the movable mechanism member mounted on the eccentric shaft of the drive shaft by attaching a cylindrical piston of a hollow cylindrical body whose both end surfaces are parallel and flat. A crescent-shaped columnar space formed by incorporating the cylindrical piston into the fixed cylinder as the fixed component member, in which the inner wall surface is provided in the central portion and the both end surfaces are formed parallel and flat, is sandwiched between flat flat lid members. The space is divided by an approximately rectangular parallelepiped partition plate which is movable in a parallel groove having one end opened rectangularly on the cylindrical inner wall surface of the fixed cylinder and whose tip is in sliding contact with the outer wall surface of the cylindrical piston. In a positive displacement compressor having a suction chamber and a compression chamber,
    A valve storage chamber is formed by a valve mounting chamber formed by enlarging the width of the parallel groove of the fixed cylinder to which the partition plate is mounted and an outflow chamber provided at the back thereof, and the compression chamber side of the valve mounting chamber A support member is provided between the side wall surfaces of the substantially rectangular parallelepiped gate valve and the partition plate, the front end portion of which has a side wall seal surface that is in sliding contact with the side wall surface of the cylindrical piston and the outer surface of the cylindrical piston is in sliding contact with the outer wall surface of the cylindrical piston. A discharge mechanism is provided in which an outflow passage is provided to the chamber side, and a valve mechanism that is configured by attaching an elastic body such as a spring to the outflow chamber is assembled to the outflow chamber. The positive displacement compressor according to any one of claims 5 to 9, wherein the positive displacement compressor is provided.
  29. 前記平板ゲート弁の板厚の中心となる先端部中央位置を、前記固定シリンダ内壁面の中心を通る前記弁装着室の側壁面に平行な中心線から前記偏心軸のおよそ偏心量相当の距離を反吸入室側である圧縮室側に寄せて該平板ゲート弁を配置して構成される吐出機構を備えたことを特徴とする請求項２８記載の容積型圧縮機。 The center position of the tip portion that is the center of the plate thickness of the flat gate valve is set to a distance corresponding to the amount of eccentricity of the eccentric shaft from a center line that passes through the center of the inner wall surface of the fixed cylinder and is parallel to the side wall surface of the valve mounting chamber. 29. The positive displacement compressor according to claim 28, further comprising a discharge mechanism configured by disposing the flat gate valve toward the compression chamber side which is the anti-suction chamber side.
  30. 前記固定シリンダおよび円筒ピストンを挟み込む前記平坦蓋部材であるメインカバーないしはサブカバーで形成された円筒空間の平坦面の一端に低圧通路に連通する低圧導入孔と他端側に前記弁装着室に連通する連通孔から形成された係止制御室を設け、大径の円筒部と小径のピン部の2段円筒で形成された該円筒部の内側空洞部にバネなどの弾性体を収納して形成された係止部材を該係止制御室に収納するとともに前記平板ゲート弁の先端部が圧縮室内より内側の弁装着室内に収納された状態で該平坦蓋部材上を摺動する上下端面ないしは側壁シール面の内何れか一箇所に該係止部材のピン部が遊挿可能な位置に係止穴を設けた該平板ゲート弁で構成された吐出機構を備えたことを特徴とする請求項２８ないしは２９記載の容積型圧縮機。 One end of a flat surface of a cylindrical space formed by the main cover or sub-cover that is the flat lid member that sandwiches the fixed cylinder and the cylindrical piston communicates with a low-pressure introduction hole that communicates with the low-pressure passage and the other end side communicates with the valve mounting chamber. A locking control chamber formed from a communicating hole is provided, and an elastic body such as a spring is housed in an inner cavity portion of the cylindrical portion formed by a two-stage cylinder of a large diameter cylindrical portion and a small diameter pin portion. The upper and lower end surfaces or the side walls that slide on the flat lid member in a state where the engaged locking member is accommodated in the engagement control chamber and the tip of the flat gate valve is accommodated in the valve mounting chamber inside the compression chamber. 29. A discharge mechanism comprising the flat gate valve provided with a locking hole at a position where the pin portion of the locking member can be loosely inserted in any one of the sealing surfaces. 30. The positive displacement compressor according to 29.
PCT/JP2015/052878 2014-02-24 2015-02-02 Discharge mechanism for displacement compressor WO2015125596A1 (en)

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JP2014082416A JP2014132176A (en) 2014-04-14 2014-04-14 Discharge mechanism of scroll type compressor
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