WO2002038960A1 - Dispositif pour circulation de fluide en spirale - Google Patents

Dispositif pour circulation de fluide en spirale Download PDF

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Publication number
WO2002038960A1
WO2002038960A1 PCT/JP2001/009681 JP0109681W WO0238960A1 WO 2002038960 A1 WO2002038960 A1 WO 2002038960A1 JP 0109681 W JP0109681 W JP 0109681W WO 0238960 A1 WO0238960 A1 WO 0238960A1
Authority
WO
WIPO (PCT)
Prior art keywords
scroll
fluid machine
type fluid
motor
operation chamber
Prior art date
Application number
PCT/JP2001/009681
Other languages
English (en)
Japanese (ja)
Inventor
Yoshio Miyake
Eiji Tsutsui
Yasutaka Konishi
Original Assignee
Ebara Corporation
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 JP2000339171A external-priority patent/JP2002138974A/ja
Priority claimed from JP2000388923A external-priority patent/JP2002188584A/ja
Priority claimed from JP2001121423A external-priority patent/JP2002317777A/ja
Priority claimed from JP2001179216A external-priority patent/JP2002371977A/ja
Priority claimed from JP2001179217A external-priority patent/JP2002371979A/ja
Application filed by Ebara Corporation filed Critical Ebara Corporation
Priority to AU2002211012A priority Critical patent/AU2002211012A1/en
Publication of WO2002038960A1 publication Critical patent/WO2002038960A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • F01C17/063—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with only rolling movement
    • 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
    • F04C23/008—Hermetic pumps

Definitions

  • the present invention relates to an oil-free scroll type fluid machine that compresses and transfers gas in an unlubricated state, and particularly relates to a scroll type fluid machine that is optimally used as a blower for compressing and transferring combustible gas and the like. It relates to fluid machinery. Background art
  • the scroll-type fluid machine was confined in a spiral-shaped compression operation chamber by combining spiral wraps, fixing one, and orbiting the other while preventing rotation, and performing relative movement of the wrap. It compresses and transfers fluid by gradually reducing the volume of gas.
  • Such scroll-type fluid machines have lower noise and lower pressure pulsation than lathe-rotary-type fluid machines, and are therefore widely used, for example, for small-sized air-conditioning refrigerators and compressors. .
  • the entire oil-lubricated whirlpool compressor used in the air conditioner is housed in a pressure vessel by hermetic welding, and has a structure that does not leak the handled gas.
  • This structure can be used only when the lubricating fluid (oil) is cold. This is because practical problems do not occur even if they are mixed into the medium, and maintenance-free design with a long service life using lubricating oil is possible. Therefore, it was difficult to apply this structure to an oil-free scroll-type fluid machine that does not allow oil to be mixed into the handled gas.
  • seal components for example, a fluorine resin is composed of a resin material cost (Teflon) and the like, wasting (wear) Then decreases the efficiency of the fluid machine (Thus, for example, periodically at 10,000 hours about operating time Maintenance (part replacement) is required.
  • resin material cost Teflon
  • Thus for example, periodically at 10,000 hours about operating time Maintenance (part replacement) is required.
  • Oil-free compressors are generally equipped with a pressure tank and a pressure switch on the discharge side, and when the tank pressure falls below the required pressure with the use of air, the compressor starts operating and the tank pressure rises above the specified pressure. When it rises, the compressor is stopped. As a result, the operation time at a pressure higher than the required pressure is substantially increased, which contributes to accelerated wear of the sealing parts. Frequent startup and shutdown of the seal component causes rapid rises in the temperature of the seal component due to sliding heat at startup and a decrease in the temperature at the time of the stop in a short period of time, which is another factor that accelerates the deterioration of the seal component.
  • bearings are used, and when using ball bearings, they are generally replaced in about 20,000 hours (operating time).
  • life of the bearing the magnitude of the load, the total number of rotations, the ambient temperature, and the like are the determining factors, and show the same tendency as the above-mentioned sealing parts. If the housing in which the outer ring of the bearing fits is made of an aluminum alloy, it is necessary to prevent the housing from settling (creeping). For this reason, a method of fixing the outer ring of the bearing to the housing using a retaining plate and a method of providing an elastic material ring such as a resin around the outer ring of the outer ring of the bearing have been used.
  • Particularly rotation inhibiting mechanism portion for preventing rotation of the orbiting disk port Lumpur since the required function of absorbing the variation in assembly accuracy, creep prevention was generally difficult (and load the higher pressure region As a result, the motor generates heat and, at the same time, the heat generated by the compressor increases, and in some cases, the heat generated by the motor and the heat received from the compressor may cause deterioration of the motor and bearings. Frequent repetition of stoppage is one of the factors that hasten the deterioration of motors etc. from a mechanical and thermal point of view.
  • the force for pressing the tip seal against the head plate should be kept as low as possible, and the force should be reduced to the total length of the tip seal in the longitudinal direction. It is necessary to work uniformly without variation. For this purpose, it is necessary to minimize the tilting and rattling of the swivel spool caused by the clearance between the inner and outer rings of the ball bearing that rotatably supports the main shaft.
  • the Oldham ring is used to prevent the orbiting scroll from rotating, the axial length of the compressor can be kept relatively short.
  • a grease-enclosed sealed ball bearing is combined to prevent rotation. Because of the necessity of configuring 0, the axial length of the compressor tends to be long.
  • the center of gravity in the axial direction of the force centrifuge 780 and the orbiting scroll 730 for ensuring the balance of the wheel are different, and a couple may occur during operation, causing imbalance (dynamic imbalance). There is. Therefore, another force is required to correct this dynamic balance.
  • the present invention has been made in view of the above-mentioned problems, and is a maintenance-free scroll-type fluid machine that has no leakage of inflow gas and can be used for compressing and transferring flammable gas and the like.
  • a first object is to provide a scroll-type fluid machine that can be used as a free blower.
  • a second object of the present invention is to provide an oil-free scroll-type fluid machine that is maintenance-free and has a long service life.
  • a third object of the present invention is to provide a high-efficiency, long-life oil-free scroll-type fluid machine in which the orbiting scroll is prevented from falling and rattling to a minimum. It is a fourth object of the present invention to provide an oil-free scroll-type fluid machine capable of making the entire apparatus compact by shortening the axial length.
  • a first aspect of the present invention provides a method according to a first aspect of the present invention, in which a rotating scroll is prevented from rotating around a fixed scroll and a rotating scroll.
  • a scroll-type fluid machine in which a spiral compression operation chamber whose volume gradually decreases toward the inner peripheral side is defined, and the inflow gas is transferred while being compressed as the volume of the compression operation chamber is reduced.
  • a motor rotor is attached to a drive shaft for driving the above-mentioned swivel ring, a motor stator is provided, and one end is opened and the other end is closed.
  • a scroll-type fluid machine wherein a motor stator is arranged, and the fixed scroll is hermetically connected directly or via another member to an open end of the motor casing.
  • the motor stator is integrally provided in the motor casing by resin molding. This ensures that the following particular tens Wa Tsu Toklas, leakage-free oil-free type gas low output scroll type fluid machine of the (compressor Ya blower) can be conveniently achieved (and the motor ⁇ is Because it is molded with resin, even if the motor winding is short-circuited or overheated for any reason, it is safe without affecting the flammable gas.
  • a spiral scroll in which the volume is gradually reduced from the outer peripheral side to the inner peripheral side with the orbital movement of the orbiting scroll that prevents the orbiting scroll from rotating.
  • the compression operation chamber is partitioned and the inflowing gas is compressed and transferred as the volume of the compression operation chamber is reduced.
  • a scroll type fluid machine characterized in that an axial gap between the orbiting scroll and the orbiting scroll is set to a minimum.
  • a contact-type seal component (tip seal) is formed in the gap along the axial direction between the fixed scroll and the orbiting scroll that defines the compression working chamber. Therefore, it is possible to construct a blower that has a long service life and is maintenance-free, for example, has a maximum generated pressure of less than 100 kPa.
  • the maintenance interval depends on the durability of the contact-type seal component (tip seal) provided in the axial gap between the fixed scroll and the orbiting scroll.
  • the tip seal is generally replaced every 10,000 hours (operating time). Therefore, by removing this tip seal and extending the life of the bearing that has been designed and selected based on the premise that maintenance is performed simultaneously with replacement of the tip seal, the entire equipment can be made maintenance-free.
  • the function as a compressor with a high generated pressure or a function as a high vacuum pump will not be satisfied.
  • the maximum generated pressure is extremely small at 100 kPa or less, If it is a relatively high pressure blower, there is no problem in performance.
  • the gap is set to 0.15 mm or less.
  • the gap is set to 0.15 mm or less.
  • desired performance can be secured.
  • this gap By controlling this gap to, for example, about 0.02 to 0.05 mm, high pressure and high vacuum are maintained, and the maximum generated pressure is used as a blower of less than 100 kPa. It can be developed.
  • the above-described squeal type fluid machine is used while immersed in water.
  • submerging the scroll type fluid machine, which has excellent quietness, in the water eliminates the propagation of vibrations from the main body, resulting in a quieter device.
  • a third aspect of the present invention provides a method according to a third aspect of the present invention, comprising: In a scroll-type fluid machine in which a spiral-shaped compression operation chamber whose volume is gradually reduced toward the partition is formed, and inflow gas is transferred while being compressed as the volume of the compression operation chamber is reduced.
  • a scroll fluid machine characterized in that a frequency converter or a driving driver for controlling the rotation speed of a motor is provided in a motor casing containing a motor stator surrounding the periphery of a motor rotor fixed to a shaft. It is.
  • the incoming gas of the scroll type fluid machine is passed around a motor and a frequency converter or a driver for driving, and the incoming gas is used for cooling them.
  • a scroll compressor or the like in which a motor and a frequency converter are integrated not only the heat generated by the motor and the frequency converter, but also the heat generated in the process of compressing the air by the compressor section, the motor and the frequency converter Act on etc. Therefore, by utilizing the flow of the surrounding air flowing into the compressor section to effectively cool the motor and the frequency converter, etc., the life of the scroll type fluid machine can be prolonged, and the frequency conversion can be performed. The effect can be promoted by incorporating a device into a fluid machine.
  • a pressure sensor is provided in the discharge pressure section, and a pressure control operation is performed based on a signal from the pressure sensor.
  • a pressure tank and a pressure switch are provided on the discharge side, and when the tank pressure falls below the required pressure with the use of air, the compressor starts operating and the tank pressure rises to the specified pressure. When it rises above, the compressor is stopped.
  • the operation time at a pressure higher than the required pressure is substantially increased, which contributes to accelerated wear of the sealing parts. Frequent startup and shutdown of the seal component causes rapid rise and fall in temperature of the seal component due to sliding heat during startup in a short period of time, which is another factor that accelerates the deterioration of the seal component.
  • the magnitude of the load, the total number of revolutions, the ambient temperature, etc. are the determining factors, and show the same tendency as the above seal parts.
  • the higher the load is the higher the load in the operation is in the high pressure range, so that the motor generates heat and, at the same time, the heat generated by the compressor increases. Therefore, in some cases, the heat generated by the motor and the heat received from the compressor may cause deterioration of the motor / bearing. Also, frequent repetition of starting and stopping is one of the factors that hasten the deterioration of a motor or the like from a mechanical and thermal viewpoint.
  • a spiral compression operation chamber whose volume gradually decreases from the outer circumference to the inner circumference in accordance with the orbital motion that prevented the rotation of
  • the magnetic force acting between the magnet provided on the fixed member and the magnet provided on the orbiting scroll is provided with a rotation preventing mechanism for preventing rotation of the rotating scroll by rotation.
  • bearings are used, and when using ball bearings, they are generally replaced in about 20,000 hours (operating time). Regarding the life of this bearing, the magnitude of the load, the total number of revolutions, the ambient temperature, and the like are the determining factors and show the same tendency as the above seal parts. If the housing in which the outer ring of the bearing fits is made of an aluminum alloy, it is necessary to prevent the housing from settling (creeping). For this reason, a method of fixing the outer ring of the bearing to the housing using a retaining plate and a method of providing an elastic material ring such as a resin around the outer ring of the outer ring of the bearing have been used.
  • the anti-rotation mechanism components that prevent the rotation of the revolving spool need to have a function of absorbing variations in assembly accuracy, and it has been difficult to take measures to prevent creep. Therefore, by providing the anti-rotation mechanism that prevents the orbiting scroll from rotating by magnetic force, the ball bearings and pink cranks conventionally used in the anti-rotation mechanism are no longer necessary, and the non-contact type mechanism is used. Not only that, it is a very quiet device with no noise. In addition, since the positioning is performed by the magnet, there is also an effect of absorbing variations in assembly accuracy. In addition, since no ball bearings are used, there is no need to worry about the outer ring leave. Furthermore, since the mechanism is simplified and the number of parts can be reduced, the manufacturing cost can be reduced and the equipment can be made more compact.
  • the rotation preventing mechanism comprises: a ring-shaped or cylindrical first magnet having an inner radius substantially equal to a turning radius of the turning scale; A pin-shaped or rod-shaped second magnet is disposed at a position approximately the same distance as the scroll turning radius and in parallel with the axis of the first magnet so as to face the first magnet.
  • the rotation preventing mechanism is provided, for example, at three locations on the same plane, and reliably prevents the rotating scroll from rotating by three sets of magnets.
  • the first magnet it is preferable to configure the first magnet so that the inner magnet and the outer magnet have different polarities (N pole and S pole).
  • the inner and outer peripheries have different polarities, for example, by magnetizing summary cobalt or two ring-shaped magnets are fitted into the inner and outer peripheries, the magnetic force at the innermost and outermost peripheries will increase. It is known to increase, and the following effects can be obtained.
  • the movement locus of the second magnet is less likely to shift. That is, the second magnet moves smoothly along the circumferential direction of the first magnet.
  • the orbital scroll is prevented from rotating, and the orbiting scroll moves from the outer peripheral side to the inner peripheral side.
  • a scroll-type fluid machine in which a spiral-shaped compression operation chamber whose volume is gradually reduced toward the side is formed, and inflow gas is transferred while being compressed as the volume of the compression operation chamber is reduced.
  • a frequency converter or driver for controlling the rotation speed of the motor, and a rotation preventing mechanism for preventing the rotation of the orbiting scroll by the magnetic force acting between the magnet provided on the fixed member and the magnet provided on the orbiting scroll.
  • a scroll-type fluid machine comprising: a starter that ensures an appropriate starting time at the time of starting.
  • step-out is likely to occur if there is a large and shocking torque fluctuation. Therefore, for example, by performing a so-called soft start using a frequency converter, the step-out phenomenon of the magnet can be prevented, and the magnet can be downsized because an excessive magnetic force is not required. Moreover, by further utilizing the functions of the frequency converter and the like, it is possible to synergistically achieve the simplification and long life of the rotation preventing mechanism.
  • a rotation preventing mechanism for the turning scroll between the fixed scroll and the turning scroll.
  • the positioning between the turning scroll and the motor-side fixing member is substantially unnecessary, and at the same time, the positioning (knock pin) between the motor-side fixing member and the fixed scroll is substantially unnecessary.
  • the overall structure is extremely simple and can contribute to increased productivity.
  • the axial play between the rotating component and the fixed component can be substantially reduced to zero. That is, since the rotating scroll is always stably attracted to the fixed scroll by the magnet and rotated, the clearance management of the tip seal portion becomes easy. In addition, even if the tip seal is slightly worn, Since the scroll moves to the fixed scroll side to maintain the clearance, performance can be maintained for a long time.
  • a sixth aspect of the present invention is a method according to a sixth aspect of the present invention, wherein a fixed scroll and an orbiting scroll are moved between an outer peripheral side and an inner peripheral side along with a revolving motion that prevents the orbiting scroll from rotating.
  • a scroll-type fluid machine in which a spiral compression operation chamber whose volume gradually decreases toward the bottom is formed and the inflowing gas is compressed and transferred as the volume of the compression operation chamber is reduced, the motor is driven.
  • a scroll-type fluid machine comprising: a biasing member that rotates together with a motor rotor and biases a main shaft that revolves the orbiting scroll toward the motor.
  • the orbiting scroll can be biased toward the motor (the side opposite to the fixed scroll) via the main shaft. Therefore, by reliably supporting the orbiting scroll via, for example, three crankpin bearings, it is possible to minimize the tilting and rattling of the orbiting scroll. As a result, it is possible to minimize the amount of leakage while reducing the sliding loss by minimizing the force for pressing the tip seal against the head plate, or to eliminate the tip seal.
  • the urging member a method utilizing a leaf spring (wavy washer) formed by bending a washer in a wavy shape and a bearing nut may be used.
  • a vortex whose volume is gradually reduced from the outer peripheral side to the inner peripheral side between the fixed scroll and the orbiting scroll in accordance with the revolving motion that prevents the orbiting scroll from rotating.
  • the motor rotor is driven by the motor.
  • the main shaft that rotates together with the main shaft and rotates the orbit
  • an auxiliary bearing disposed at the motor-side end portion so as to be rotatably supported.
  • an inner diameter of an inner ring of the main bearing is larger than an outer diameter of an outer ring of the auxiliary bearing and an outer diameter of the motor rotor.
  • the motor rotor and the auxiliary bearing are previously mounted on the main shaft, and the main shaft is sunk inside an inner ring of the main bearing. Secure the inner ring.
  • a biasing member that biases the main shaft toward the motor using a leaf spring (wave-shaped washer) and a bearing nut can be easily attached to the main bearing portion.
  • a spindle assembly with a motor rotor and auxiliary bearings attached to the spindle is prepared in advance, this spindle assembly is sunk under the inner ring of the main bearing, and a leaf spring is arranged on the opposite side of the main bearing from the motor.
  • the volume is sequentially reduced from the outer peripheral side to the inner peripheral side between the fixed scroll and the orbiting scroll in accordance with the orbital motion that prevents the orbiting scroll from rotating.
  • the above-mentioned fixed scroll and orbiting scroll have the above-mentioned structure.
  • a groove is formed on the tip end surface of the wrap that defines the compression operation chamber and extends over substantially the entire length of the wrap, and a chip seal is inserted inside the groove while an elastic body is interposed. It is a scroll type fluid machine.
  • the force that presses the tip seal against the head plate should be kept as low as possible. It is necessary to ensure that the force acts uniformly and uniformly over the entire length of the tip seal in the longitudinal direction. Therefore, for example, an elastic body made of a sponge-like foam, preferably an elastic body made of a silicon foam having excellent heat resistance and durability, a small permanent residual strain, and a small spring constant is used on the back side of the chip seal. In this case, the sliding loss of the tip seal can be reduced.
  • the sliding loss of the tip seal can be reduced more effectively by using a combination of the above-mentioned structure that minimizes the tilt of the orbiting scroll and rattling and a foam with a small spring constant. .
  • the function as a seal component can be fully exhibited even if the force for pressing the tip seal against the head plate is kept low.
  • a scroll-type fluid machine in which a compression operation chamber having a compression shape is defined and the inflowing gas is compressed and transferred as the volume of the compression operation chamber is reduced, the motor rotor and the motor rotor are driven by the motor.
  • a main shaft that rotates integrally and revolves the orbiting scroll is rotatably supported by a main bearing and an auxiliary bearing arranged at the motor-side end, and a pair of force counterweights are provided on both sides of the main shaft with the main bearing interposed therebetween. It is a scroll type fluid machine characterized by being provided.
  • the shape around the motor stator becomes a simple shape with a force-up, and the resin mold motor (excellent in water resistance, airtightness, etc.) with the motor stator embedded in the motor casing is formed. Adoption becomes easy.
  • the volume is sequentially increased from the outer peripheral side to the inner peripheral side in accordance with the revolving motion that prevented the rotation of the rotating scroll.
  • a scroll type fluid machine in which a convoluted spiral compression operation chamber is defined and the inflow gas is transferred while being compressed as the volume of the compression operation chamber is reduced, the gas inside the compression operation chamber is formed.
  • a scroll type fluid machine characterized by having a magnetic fluid seal mechanism for preventing leakage from a high pressure side to a low pressure side.
  • the magnetic fluid sealing mechanism includes: a first magnet attached to a groove formed at a wrap end of the fixed scale or the rotating scale; (1) A magnetic fluid disposed in the groove in which the magnet is inserted, and a second magnet provided on the fixed scroll or the orbiting scroll side of the end plate in the orbiting scroll or the fixed scroll.
  • a non-contact type seal can be substantially formed, and power consumption due to sliding loss and reduction of the handled fluid can be achieved. It is possible to increase the efficiency of the equipment by suppressing leakage, and at the same time, it is possible to provide a long-life machine that requires no maintenance. Further, the above-mentioned magnetic fluid sealing mechanism can exhibit a sealing function without keeping the axial gap between the scrolls so small, so that the orbiting scroll falls due to the gap between the inner and outer rings of the ball bearing and the like. It is not necessary to control the The structure of the vessel is also simplified, which can lead to an improvement in productivity. In this case, if the first magnet has a stronger magnetic force than the second magnet, it is possible to prevent the magnetic fluid from being strongly attracted to the second magnet and scattered.
  • a first aspect of the present invention provides a method according to a first aspect of the present invention, in which the outer peripheral side is provided between a fixed scroll and an orbiting scroll in accordance with a revolving motion that prevents the orbiting scroll from rotating.
  • a scroll-type fluid machine that defines a spiral compression operation chamber whose volume gradually decreases from the inner side toward the inner side, and compresses and transfers inflowing gas as the volume of the compression operation chamber decreases.
  • a slewing bearing provided at one end of a main shaft, an auxiliary bearing provided at the other end of the main shaft, and a main bearing provided between the slewing bearing and the auxiliary bearing.
  • a scroll-type fluid machine characterized in that at least a part of the scroll-type fluid machine is arranged so as to be located on the fixed scroll side of the end plate of the orbiting scroll.
  • the orbiting bearing does not protrude from the end plate of the orbiting scroll toward the motor casing, so the distance from the tip of the orbiting scroll wrap to the main bearing is reduced, and the axial length of the device is reduced. Can be shortened.
  • the center of gravity in the axial direction of the turning scroll and the counterweight can be configured to be the same, an imbalance due to a couple during operation does not occur. In this case, it is not necessary to separately provide a force contour for correcting the dynamic balance, so that the length of the device in the axial direction can be shortened and the entire device can be made compact.
  • the orbiting scroll is prevented from rotating around the outer peripheral side due to the revolving motion that prevents the rotation of the orbiting scroll.
  • a scroll-type compression operation chamber whose volume gradually decreases from the inner side to the inner side is defined, and the inflow gas is compressed and transported as the volume of the compression operation chamber decreases.
  • a slewing bearing provided at one end of a main shaft, an auxiliary bearing provided at the other end of the main shaft, a main bearing provided between the slewing bearing and the auxiliary bearing, and a motor attached to the main shaft And a rotor, wherein the motor rotor is disposed on an outer peripheral side of the main bearing.
  • the length of the device in the axial direction can be shortened and the entire device can be made compact.
  • a housing portion of the motor rotor is provided integrally with the main shaft.
  • a counterweight portion for ensuring the balance of the rotating system is provided on the spindle.
  • the productivity is improved because the structure of the apparatus is simplified and the number of parts is reduced. Further, by providing a power center portion on the main shaft, a quiet device with less vibration can be realized without increasing the number of parts.
  • a mass body counter weight part
  • a mass body is provided integrally at two locations in the axial direction of the main shaft to offset the couple imbalance that occurs slightly. Since the power weight can be provided at the same time, the couple imbalance can be rationally canceled without consuming any special space. Therefore, a compact, low-vibration, and quiet device can be realized.
  • the first magnet provided on the motor casing or the fixed scroll and the first magnet provided on the orbiting scroll are provided.
  • a rotation preventing mechanism for preventing rotation of the revolving scroll by a magnetic force acting between the first magnet and the second magnet is provided.
  • the anti-rotation mechanism of an oil-free scroll type fluid machine generally uses a combination of ball bearings. Ball bearings are consumable parts and are generally replaced after about 20,000 hours (operating time). ⁇ The life of this bearing depends on the size of the load, the total number of revolutions, the ambient temperature, and other factors. If the housing in which the outer ring of the bearing fits is made of aluminum alloy, etc., it is necessary to prevent the housing from creeping (creeping).
  • the above configuration eliminates the need for the ball bearings and crank pins conventionally used in the anti-rotation mechanism, and provides a non-contact type anti-rotation mechanism.
  • the life of the anti-rotation mechanism is semi-permanent. .
  • the orbiting scroll is positioned by the magnet, it is possible to absorb variations in assembly accuracy.
  • the mechanism is simplified and the number of parts can be reduced, so that manufacturing costs can be reduced and equipment can be made more compact.
  • unlike a rotation prevention mechanism using a ball bearing since it is a non-contact type, it has no noise and is extremely quiet.
  • FIG. 1 is a sectional view showing a squeal type fluid machine according to a first embodiment of the present invention.
  • FIG. 2 is a sectional view showing a scroll type fluid machine according to a second embodiment of the present invention.
  • FIG. 3 is a sectional view showing a scroll type fluid machine according to a third embodiment of the present invention.
  • FIG. 4 is a diagram schematically showing the rotation preventing mechanism of the orbiting scroll of FIG.
  • FIG. 5 is a sectional view showing a scroll type fluid machine according to a fourth embodiment of the present invention.
  • FIG. 6 is a sectional view showing a squeal type fluid machine according to a fifth embodiment of the present invention.
  • FIG. 7 is a longitudinal sectional view showing a scroll type fluid machine according to a sixth embodiment of the present invention.
  • FIG. 8 is a partially enlarged view of the magnetic fluid sealing mechanism shown in FIG.
  • FIG. 9 is a sectional view showing a squeal type fluid machine according to a seventh embodiment of the present invention.
  • FIG. 10 is a sectional view showing a scroll type fluid machine according to an eighth embodiment of the present invention.
  • FIG. 11 is a sectional view showing a scroll type fluid machine according to a ninth embodiment of the present invention.
  • FIG. 12 is a sectional view showing a conventional scroll type fluid machine.
  • BEST MODE FOR CARRYING OUT THE INVENTION a scroll type fluid machine according to an embodiment of the present invention will be described with reference to the drawings.
  • FIG. 1 shows a scroll type fluid machine according to a first embodiment of the present invention.
  • This scroll-type fluid machine has a cylindrical motor stator 10.
  • the motor stator 10 has a power-up motor casing 12 having one end closed and the other end opened.
  • the inside is buried integrally by, for example, molding of a polyester resin. As a result, airtightness inside and outside the motor casing 12 is ensured. Power is supplied to the motor stator 10 from a power supply lead line 11.
  • a motor rotor 14 made of a permanent magnet is disposed inside the motor casing 12, and the motor rotor 14 rotates in the motor casing 12 by a main bearing 16 and an auxiliary bearing 18. It is fixed to the main shaft 20, which is a freely supported drive shaft.
  • a fixed part of the bearings 16 and 18 of the motor casing 12 is provided with a housing 22 made of, for example, a thin stainless steel plate in a cup shape, and the outer ring of the bearings 16 and 18 is provided with a groove.
  • a crankshaft 24 having an axis eccentric with this axis by the amount of eccentricity e is connected to the body, and a rolling bearing is attached to the crankshaft 24.
  • a substantially disk-shaped orbiting scroll 28 is rotatably connected via a orbiting bearing 26 made of. Further, between the orbiting scroll 28 and the following bracket 62, two pins 30a and 30b having their axes at positions eccentric by the same eccentricity e as the above eccentricity e are provided. Crank pins 32 are provided at three locations along the circumferential direction. The crank pin 32 constitutes a rotation preventing (preventing) mechanism of the turning scroll 28.
  • One of the pins 30a of the crank pin 32 is a bearing 34 fixed to the bracket 62.
  • the other pin 30b is attached to the orbiting scroll 28. It is rotatably supported by the fixed bearing 36.
  • crankshaft 24 performs a revolving motion with the eccentricity e as a radius along with the rotation of the main shaft 20, and the revolving motion of the crankshaft 24 also causes the turning scroll 28 to change the eccentricity e.
  • a revolving motion with a radius is performed, and the rotation of the orbiting scroll 28 is prevented (prevented) by the crankpin 32.
  • the main shaft 20 is provided with a balance weight 38 for ensuring the balance of the rotating system.
  • a stationary scroll 44 having a suction port 40 and a discharge port 42 is provided.
  • the end plate 46 of the orbiting scroll 28 is provided with a wrap 48 having an involute curve protruding toward the fixed scroll 44 or a curved shape similar to this, and the fixed scroll 44 is provided.
  • the end plate 50 of 44 is provided with a wrap 52 having an involute curve or a curve shape similar to the involute curve projecting toward the revolving scroll 28.
  • a convoluted spiral compression operation chamber 54 is defined by both wraps 48, 52, and this compression operation chamber 54 is closed by both end plates 46, 50.
  • the gas that has flowed into the compression operation chamber 54 is sequentially transferred while being compressed as the volume of the compression operation chamber 54 decreases due to the revolving motion that prevented the rotation of the orbiting scroll 28.
  • a tubular bracket 62 is arranged between the motor casing 12 and the fixed scroll 44.
  • One end of the bracket 62 is positioned at the opening end of the motor casing 12 by a white-light, and is fastened by bolts via an O-ring 64.
  • the other end of the bracket 62 is positioned at the open end of the fixed scroll 44 by an armor, and is fastened by a bolt via an O-ring 66.
  • the motor rotor 14 and the main shaft 20 rotate in a body, and the crank rotates with this rotation.
  • the axis 24 and the orbiting scroll 28 perform a synchronized orbital motion.
  • the rotation of the orbiting scroll 28 is prevented by the crank pin 32.
  • the gas flows from the suction port 40 to the revolving scroll 28 Gas flows into the compression operation chamber 54 composed of the fixed scroll 44 and the compression operation chamber 54 is sequentially reduced from the outer peripheral side to the inner peripheral side by the action of the two wraps 48, 52, so that gas is generated. Is compressed and transferred to a high pressure, and is discharged out of the machine through the discharge port 42.
  • the inside of the motor casing 12 is hermetically sealed so that the gas such as combustible gas flowing into the compression operation chamber 54 can be compressed and transferred without leaking.
  • the gas such as combustible gas flowing into the compression operation chamber 54
  • the entire fluid machine can be submerged in water to cool the main body by water cooling (in this case, the intake pipe and the discharge pipe are exposed to the atmosphere).
  • water cooling in this case, the intake pipe and the discharge pipe are exposed to the atmosphere.
  • FIG. 2 shows a squeal type fluid machine according to a second embodiment of the present invention.
  • this scroll-type fluid machine the distance S1 between the tip of the wrap 48 of the orbiting scroll 28 and the end plate 50 of the fixed scroll 44, and the wrap 52 of the fixed scroll 44
  • the distance S2 between the tip of the fin and the end plate 46 of the swivel scroll 28 is minimized, preferably set to 0.15 mm or less, so that the tip seals 56, 58 shown in FIG. Is omitted.
  • an optimal scroll type fluid machine is configured by using the blower as a blower having a maximum generated pressure of lOOKPa or less.
  • the life / maintenance interval of an oil-free scroll type fluid machine largely depends on the durability of the tip seals 56, 58. , 5 8 replaced It is. Therefore, by removing the tip seals 56 and 58 and extending the life of the bearings that were designed and selected on the assumption that maintenance will be performed at the same time as replacement of the tip seals 56 and 58, the entire equipment will be maintained. It can be free.
  • the function as a compressor with a high generated pressure or a function as a high vacuum pump is not satisfied.However, for example, when the maximum generated pressure is a very small air volume of 100 kPa or less There is no performance problem with a relatively high pressure blower.
  • the distance S 1 between the tip of the wrap 48 of the revolving scroll 28 and the end plate 50 of the fixed scroll 44 and the tip of the wrap 52 of the fixed scroll 44 and the revolving scroll 28 The desired performance can be ensured by setting the distance S2 from the end plate 46 to 0.15 mm or less, but this gap is controlled to, for example, about 0.02 to 0.05 mm. In this way, high pressure and high vacuum can be maintained, and the application of the equipment can be expanded as a blower with a maximum generated pressure of 100 kPa or less.
  • the oil-free scroll type which can be used for compressing and transferring flammable gas without leaking inflow gas and which can be easily maintained.
  • a fluid machine and a long-life oil-free scroll type blower can be provided. Also, since it can be used submerged in water, it is possible to develop applications that take quietness into account.
  • FIG. 3 shows a scroll-type fluid machine according to a third embodiment of the present invention.
  • This scroll-type fluid machine has a motor casing 110 made in the form of a force-pump made of, for example, aluminum alloy, and a motor stator 111 is provided on an inner peripheral portion of the motor casing 110. 2 is shrink-fitted and fixed.
  • Motor casing A bracket 114 made of, for example, aluminum alloy is fixed to an open end of the bracket 110 via a bolt 115.
  • the motor rotor 1 16 consisting of permanent magnets is fixed to the main shaft 1 18 which is the drive shaft, and the main shaft 1 18 is fixed to the bracket 114 and the motor case by the main bearing 120 and the auxiliary bearing 122. It is rotatably supported on the ring 110.
  • the main bearings 120, the auxiliary bearings 122, and the later-described slewing bearings 130 are all constituted by ceramic ball bearings using silicon nitride as a material, ensuring high durability.
  • -A crankshaft 126 having a balance weight 124 for securing the balance of the rotating system is connected to the main shaft 118, and the end of the crankshaft 126 has a head plate 128a
  • An orbiting scroll 128 having an involute curve or a wrap 128 b having a curved shape similar to the above is rotatably connected via an orbiting bearing 130 made of a ball bearing.
  • crankshaft 126 is connected to the spindle 118 so as to have an axis eccentric from the axis of the spindle 118 by an eccentric distance e.
  • the crank shaft 1 26 With the rotation (rotation) of the main shaft 1 18, the crank shaft 1 26 performs a revolving motion with the eccentric distance e as a radius around the axis of the main shaft 1 18, and the crank shaft 1 2 6
  • the orbiting scrolls 128 also perform a orbital movement with the eccentric distance e as a radius.
  • the substantially scroll-shaped fixed scroll 1 3 2 having a discharge port 1 3 2 a in the center is attached to the opening end of the bracket 1 14 with a bolt 1 3 4 They are connected and arranged.
  • the end plate 13 2 b of the fixed scroll 13 2 is provided with an involute curve projecting toward the orbiting scroll 128 side or a wrap 13 2 c having a curved shape similar thereto.
  • the orbiting scroll 128 and the fixed scroll 132 are moved between the orbiting scroll 128 and the fixed scroll 132 in association with the orbital motion that prevents the orbiting scroll 128 from rotating.
  • a spiral compression operation chamber 1 36 whose volume decreases gradually from the circumferential side to the peripheral side is defined by both wraps 1 28 b and 132 c, and this compression operation chamber 1 36 is formed. Both end plates 1 28 a and 13 2 b are closed. As a result, the gas flowing into the compression operation chamber 1336 is sequentially transferred while being compressed as the volume of the compression operation chamber 1336 is reduced due to the revolving motion that prevented the orbiting scroll 128 from rotating. It is being done.
  • tip seals 138 and 140 are mounted respectively.
  • the tip seals 138 and 140 for example, use is made of a resin made of PPS (polyphenylene sulfide) to which a fluororesin is added to improve the slidability. Is performed.
  • the rotation preventing mechanism 150 includes a ring-shaped permanent magnet (first magnet) 152 provided on the fixed scroll 13 and a pin-shaped permanent magnet (second magnet) provided on the orbiting scroll 128. 1 5 4
  • the ring-shaped permanent magnet 15 2 is formed by fitting two ring-shaped permanent magnets 15 56 a and 15 56 b made of, for example, summary cobalt, and fitted to the fixed scroll 13 2. Have been.
  • the outer ring-shaped permanent magnets 15 6 a are fixed such that the rotating scroll 1 28 side has the N pole and the fixed scroll 13 2 side has the S pole, and the inner ring-shaped permanent magnet 15 6 b is The swivel scroll 1 2 8 side is fixed to the S pole, and the fixed scroll 1 32 side to the N pole.
  • An extremely narrow donut-shaped strong magnetic field ring (S pole) is formed.
  • the radius of the inner circumference of the ring-shaped permanent magnets 152 that is, the radius d of the ring-shaped permanent magnets 1556b located inside is set to be equal to the eccentric distance (scroll radius) e ( pin-shaped).
  • the permanent magnets 15 4 are arranged such that their axis is parallel to the axis of the ring-shaped permanent magnets 15 2 and at the same distance as the eccentric distance e.
  • the orbiting scroll and the motor required for the conventional scroll fluid machine are provided.
  • Positioning of the side fixing member (eg, bracket) and positioning of the motor side fixing member (bracket) and the fixing scroll (eg, knock pin) are substantially unnecessary.
  • the overall structure is extremely simple and can contribute to increased productivity.
  • the play in the axial direction between the rotating component and the fixed component can be made substantially zero.
  • the orbiting scroll 1 2 8 rotates while being constantly attracted to the fixed scroll 1 32 by the magnet, so that Not only does clearance management of the tip seals 1 3 8 and 1 40 become easy, but even if the tip seals 1 3 8 and 1 4 0 are slightly worn, the orbiting scroll 1 2 8 has a fixed scroll 1 3 2 It moves to the side to maintain clearance, so performance can be maintained for a long time.
  • a rotation prevention mechanism may be provided between the turning scale and the bracket.
  • both scrolls 128, 132 and bracket 114 aluminum die cast is used for the materials of both scrolls 128, 132 and bracket 114 from the viewpoint of productivity.
  • the gas compressed by the scrolls 128, 132 generates heat by adiabatic compression, and the heat expands the aluminum having a large linear expansion coefficient, so that the axis between the scrolls 128, 132 is expanded.
  • at least one of the scrolls 1, 2, 1, 2 and 3 was subjected to tef-coating or soaked dicing treatment on at least one of the surfaces. Care is taken so that the two do not stick.
  • a number of cooling fins are provided on the outer surfaces of both scrolls 128, 132 and bracket 114 to reduce the temperature rise.
  • a driving driver 160 for supplying a DC voltage and a current of a prescribed frequency to the motor stator 112, that is, electric power, is mounted.
  • Power cable 1 6 2 is connected to 0.
  • the driving driver 160 converts AC commercial power (for example, frequency 50 Hz, voltage 200 V) into DC power, supplies the DC power to the motor stator 112, and It controls the rotation speed.
  • a frequency converter may be used instead of the driving driver.
  • a suction port 114 a is provided at a position of the bracket 114 facing the driving driver 160.
  • the drive driver 160 and the motor are cooled by passing through the periphery of the motor 110, and then guided to the fluid machine from the suction port 114a.
  • a pressure sensor 164 that detects the discharge pressure and sends this signal to a control unit provided in the driving driver 160 is provided at the discharge port 1332a of the fixed scroll 1332. Then, the control unit issues a variable speed operation command to the driving driver 160 based on the signal of the pressure sensor 164 so that the discharge pressure is maintained at a specified pressure.
  • the motor stator 112 when power is supplied to the motor stator 112, the motor rotor 116 and the main shaft 118 rotate in a body, and the crank rotates with this rotation.
  • the axis 1 26 and the revolving scroll 1 2 8 make synchronized orbital motion.
  • the rotation of the orbiting scroll 128 is prevented by the rotation prevention mechanism 150.
  • the gas was compressed from the suction port 114a through the compression operation chamber 13 composed of the revolving scroll 1 28 and the fixed scroll 1 32. 6, and the wraps 128b, 132c gradually reduce the compression operation chamber 136 from the outer side to the inner side, so that the gas is transferred while being compressed. It becomes high pressure and is discharged out of the machine from the outlet 1 32 a.
  • the rotational speed of the motor is controlled by the driving driver 160.
  • the fluid machine can be easily operated at a variable speed.
  • the average operating pressure and rotation speed in the furnace are reduced, and a longer life can be realized. That is, since the operation is performed at a necessary and sufficient pressure and rotation speed, wasteful consumption of the chip seal and the bearing can be prevented, and power consumption can be reduced because there is no waste in the operation.
  • the soft Tosuta bets via the driving driver 1 6 0 at start-up also possible to perform soft toss top respectively when stopping
  • the step-out easily occurs when there is a large and impulsive torque fluctuation. In this manner, the so-called soft start, By performing a soft stop, the step-out phenomenon of the magnet can be prevented, and the magnet can be downsized because excessive magnetic force is not required.
  • the simplification of the rotation preventing mechanism 150 and the extension of the life thereof can be synergistically achieved.
  • FIG. 5 shows a scroll-type fluid machine according to a fourth embodiment of the present invention.
  • This scroll-type fluid machine has, for example, a cup-shaped motor casing 212 that secures airtightness inside and outside by integrally molding the motor stator 210 with polyester resin.
  • a bracket 214 is fixed to an open end of the motor casing 211.
  • the motor rotor 2 16 composed of a permanent magnet is fixed to the main shaft 2 18 with an adhesive or the like, and the main shaft 2 18 is disposed at a central portion along the length direction of the main shaft 2 18.
  • the bracket 2 14 and the motor casing 2 12 are rotatably supported via the main bearing 220 and the auxiliary bearing 222 arranged at the motor end.
  • the main bearing 220 and the auxiliary bearing 222, and the later-described swivel bearing 238 and crank pin bearings 264, 266 are all silicon nitride. High durability is ensured by ceramic ball bearings made of elemental material.
  • the inner diameter D of the inner ring 220a is the outer diameter d1 of the outer ring 222 of the auxiliary bearing 222 and the outer diameter d of the motor rotor 211.
  • Those larger than 2 (D> dl, D> d2) are used.
  • the auxiliary bearing 222 and the motor rotor 216 can pass through the inside of the inner ring 220a of the main bearing 220 while being attached to the main shaft 218.
  • the main bearing 222 is formed by screwing a bearing nut 224 onto the main shaft 218 from the motor side, so that the inner ring 220 is formed by a flange provided on the bearing nut 224 and the main shaft 218.
  • a leaf spring as an urging member is formed by bending a washer in a wavy shape between the extension portion 2 14 b and the outer ring 220 b of the main bearing 220. 6 are interposed.
  • the c- shaft 2 18 urged toward the motor by the elastic force of the main shaft 2 18 and the leaf spring 2 26 has a main bearing 2 0 2
  • a first counterweight 230 is provided at a position opposite to the motor with respect to the motor, and a second counterweight 234 is provided at a position on the motor side. Accordingly, the mechanical imbalance caused by the centrifugal force accompanying the orbiting movement of the orbiting scroll 2336 described below is canceled by these two counterweights 230 and 234.
  • crankshaft 232 is provided at the end of the main shaft 218 opposite to the motor.
  • the end plate 236a is involuted.
  • a swivel scroll 23 6 having a wrap 23 36 b having a curved shape or a curved shape similar to the curved shape is rotatably connected via a swivel bearing 2 38 made of a ball bearing.
  • the crank shaft 2 32 is connected to the main shaft 218 so as to have an axis eccentric from the axis of the main shaft 218 by the amount of eccentricity e.
  • the crankshaft 2 32 With the rotation (rotation) of 8, the crankshaft 2 32 performs a revolving motion around the axis of the main shaft 2 18 with the eccentricity e as the radius, and the revolving motion of the crankshaft 2 32 Thus, the orbiting scroll 2 36 also performs a revolving motion with the eccentric amount e as a radius.
  • Scroll 240 is arranged. Then, a bracket 2 14 and a scroll casing 2 4 2 are interposed between the fixed scroll 2 4 0 and the motor casing 2 1 2 and a through bolt 2 4 4 is passed over and tightened. These members are fixed to the body.
  • the end plate 240c of the fixed scroll 240 is provided with a wrap 240d having an involute curve or a curve shape similar to the involute curve protruding toward the orbiting scroll 2336.
  • the volume between the orbiting scroll 23 and the fixed scroll 240 is changed from the outer peripheral side to the inner peripheral side with the orbital motion of the orbiting scroll 2 36 which prevents the rotation of the orbiting scroll 2 36.
  • the spiral compression operation chamber 24 6 is defined by both wraps 2 36 b and 240 d, and this compression operation chamber 24 6 is formed by both end plates 2 36 a and 24 0 c It is blocked by.
  • This wrap 2 is attached to the tip of the wrap 2 3 6 b
  • a groove 2336c is provided to extend, and a tip seal 248 is provided inside this groove 2336c to contact the end plate 240c of the fixed scale 240 and seal it. It is inserted with a force S and an elastic body 250 interposed.
  • a groove 2 extending over almost the entire length of the wrap 240 d in the length direction thereof is also provided on the tip surface of the wrap 240 d of the fixed scroll 240.
  • the tip seals 248 and 252 for example, a resin material made of PPS (polyphenylene sulfide) and having a slidability improved by adding a fluorine resin or the like is used. Is done.
  • the elastic bodies 250 and 254 are made of, for example, a sponge-like foam, preferably a silicone foam having excellent heat resistance and durability, low permanent distortion, and low spring constant. You. In this way, the elastic loss of the elastic members 250 and 255 on the back side of the chip seals 248 and 252 can reduce the sliding loss of the chip seals 248 and 252. it can.
  • the spring constants of the elastic bodies 250 and 254 are set to be small, and the force of the tip seals 248 and 252 pressed against the end plates 240c and 236a is minimized. And the force is the tip seal 2 4 8 ⁇ 2
  • the rotation prevention mechanism 260 includes a crank pin 26 having two pins 26 a and 26 b having an axis at a position eccentric by the same eccentric amount e as the eccentric amount e.
  • One of the pins 26 2 a of the crank pin 26 2 is rotatably supported by a crank pin bearing 26 4 fixed to a screen casing 24 24, and the other pin 26 2 b is It is rotatably supported by a crank pin bearing 266 fixed to the revolving scroll 236.
  • crank pin 26 2 causes the revolving motion of the revolving scroll 23 2 to also make the revolving motion of the eccentricity e as the radius. The rotation is stopped by the crank pin 26 2.
  • the scroll-type fluid machine can be used not only for general air blowing but also for a device for increasing the pressure of a gas such as nitrogen without leaking to the outside.
  • Fixed screen 2 4 0 and scroll opening 2 4 2 are, for example, PPS (polyphenylenesulfide). It is manufactured using resin and aluminum alloy.
  • the main shaft 218 is biased toward the motor side (opposite to the fixed scroll) via the leaf spring 226 to thereby provide the main shaft 218 with the main shaft 218.
  • the connected orbiting scroll 2 36 can be biased toward the motor. Therefore, by reliably supporting the swivel scroll 23 6 via, for example, three crank pin bearings 26 4 and 26 6, the tilt of the swivel scroll 23 6 can be minimized. Can be suppressed. As a result, it is possible to minimize the amount of leakage while minimizing the force for pressing the tip seals 2 48, 2 52 against the end plates 240 c, 2 36 a to reduce sliding loss.
  • the inner diameter D of the inner ring 220a of the main bearing 220 is equal to the outer diameter d1 of the outer ring 222 of the auxiliary bearing 222 and the motor rotor 216.
  • the main shaft 218 is urged toward the motor side by using a plate spring (wave washer) 226 and bearing nut 224, for example, by using an outer diameter d2 larger than
  • the biasing member can be easily attached to the storage section of the main bearing 220.
  • the above-mentioned swivel scroll 236 can fall down and rattle. Combined with the effect of minimizing the sliding loss, the sliding loss of the tip seals 248 and 255 can be effectively reduced.
  • the inner diameter of the inner ring 220a of the main bearing 220 is provided. Even if a structure is adopted in which the outer diameter of the motor rotor 2 16 is smaller than that of the above, a sufficient size as a counter weight, that is, a mass can be ensured.
  • the first counterweight 230 is fitted to the main shaft 218 by shrink fitting or crimping.
  • the motor rotor 216 made of a permanent magnet is fixed to the main shaft 218 using, for example, an adhesive.
  • the inner ring of the auxiliary bearing 222 is pressed into the motor-side end of the main shaft 218, and the inner ring of the slewing bearing 238 is pressed into the opposite end of the motor, and the nut is used to rotate the main shaft. 2 1 8 Fix so that it does not come off.
  • the outer ring of the slewing bearing 238 is inserted into the housing of the slewing scroll 236, and it is fixed so that it does not come out of the housing by using a set screw.
  • the scroll casing 242 is inserted from the shaft end on the motor side, and assembled so that the crankpin thread and the three-dimensional body are accommodated in the housing of the scroll mouth casing 242.
  • the counterweights 230 are provided at three places of the scroll casings 242 so that the crank pin housing of the scroll casing 242 does not hit the first counterweight 230. Dive between housings.
  • the O-ring 27 2 and the bracket 2 14 are inserted into the motor-side portion of the scroll casing 24 2 on the motor side.
  • a leaf spring (corrugated washer) 222 and a main bearing 220 are inserted into the bearing housing 214a of the bracket 214, and the main bearing 220 is inserted using the bearing nut 222.
  • the leaf spring 226 is compressed in the axial direction by a predetermined amount, and the reaction force urges the main shaft 218 also to the motor side, and this urging force causes the turning scale 236 to rotate the crank pin 236. It is the force that presses the motor side through 62.
  • a leaf spring may be provided between 222 and motor casing 211.
  • the bearing nut 2 24 and the second counter weight 2 shown in Fig. 5 may be provided between 222 and motor casing 211.
  • the mounting position in the axial direction of 34 may be reversed, and the main bearing 220 and the second counterweight 234 may be simultaneously tightened and fixed by the bearing nut 222.
  • the fixed scroll 240 is fixed to the scroll casing 242 on the side opposite to the motor.
  • the grooves 2336c and 240e provided at the end surfaces of the wraps 2336b and 240d of the scrolls 236 and 240, respectively, were first filled with silicon foam. Insert the elastic bodies 250 and 254 consisting of a body, etc., and then insert the tip seals 248 and 252.
  • An O-ring 276 is interposed at the outer peripheral portion of the fixed scroll 240, and the mounting angle is determined by a positioning pin (not shown). Adjustment of the axial gap at the tip of the wrap is performed by sandwiching a shim (not shown) between the fixed scroll 240 and the scroll casing 240.
  • FIG. 6 shows a scroll fluid machine according to a fifth embodiment of the present invention.
  • the distance S 1 between the tip of the wrap 23 6 b of the orbiting scroll 23 6 b and the end plate 240 c of the fixed scroll 24, and the fixed scroll 24 The distance S2 between the tip of the lap 2400 d and the end plate 236 a of the revolving scroll 23 6 is minimized, preferably, is set to 0.15 mm or less.
  • the seals 2 4 8 and 2 52 are omitted.
  • a long-lasting, maintenance-free blower having a maximum generated pressure of 100 kPa or less, for example, is used to form an optimal scale type fluid machine.
  • the service life of the oil-free scroll type fluid machine ⁇ maintenance The contact interval largely depends on the durability of the tip seals 248 and 252. Generally, the tip seals 248 and 252 are replaced every 10,000 hours (operating time). Designed on the premise that maintenance is carried out simultaneously with replacement of the tip seals 248, 252 by removing 8, 25, 2 and extending the life of the selected bearings, so that the entire equipment can be maintained on a maintenance free basis. Can be
  • the distance S1 between the tip of the wrap 2 36 b of the revolving scroll 2 36 and the end plate 240 c of the fixed scroll 240 and the wrap 24 of the fixed scroll 240 The desired performance can be ensured by setting the distance S2 between the tip of 0d and the end plate 236a of the turning scale 236 to 0.15 mm or less.
  • a high pressure or high vacuum is maintained, for example, as a blower with a maximum generated pressure of 10 OkPa or less. Can be developed.
  • the swivel scroll 2 36 can be fixed to the tension force to minimize the fall of the swivel scroll 2 36.
  • the amount of leakage is small and sufficient for practical use.
  • the swirling is achieved. It is possible to provide an oil-free scroll-type fluid machine with high efficiency and a long life, in which the fall of the first scroll is minimized.
  • FIG. 7 shows a scroll type fluid machine according to a sixth embodiment of the present invention.
  • This scroll-type fluid machine has a power casing 312 made of aluminum alloy and has a motor stator 310 housed therein.
  • a main bearing case 3 14 is fixed to an open end of the motor casing 3 12.
  • the motor rotor 316 made of a permanent magnet is fixed to the main shaft 318 with an adhesive or the like.
  • the main shaft 3 18 is connected to the main bearing case 3 14 via a main bearing 3 20 arranged at the center along the axial direction and an auxiliary bearing 3 2 2 arranged at the motor side end. It is rotatably supported by the motor casing 312.
  • a crankshaft 332 having an axis at a position eccentric from this axis by an eccentric distance e is connected to the body.
  • a substantially disk-shaped swing scroll 3336 is rotatably connected to a tip of the crankshaft 3332 via a swing bearing 3358 made of a ball bearing. Accordingly, with the rotation (rotation) of the main shaft 3 18, the crankshaft 332 revolves around the axis of the main shaft 3 18 with the eccentric distance e as the radius. With the orbital movement of, the orbiting scroll 336 also performs a orbital movement with the eccentric distance e as the radius.
  • Each of the main bearing 320, the auxiliary bearing 322, and the slewing bearing 338 is composed of a ceramic ball bearing using silicon nitride as a material, and high durability is secured.
  • a substantially scroll-shaped fixed scroll 3 4 0 having a suction port 3 4 0 a at the outer periphery and a discharge port 3 4 0 b at the center.
  • a wrap 3336b having an involute curve protruding toward the fixed scroll 3400 side or a curve shape similar thereto is erected.
  • fixed screen The main bearing case 3 14 and the scroll casing 3 4 2 are interposed between the roll 3 4 0 and the motor casing 3 1 2 and these members are tightened by passing through the bolts 3 4 4 and tightening. Is fixed to the body.
  • end plate 3400c of the fixed scroll 3400 is provided with a wrap 3400d formed of an involute curve or a similar curve shape protruding toward the revolving scroll 3336. I have.
  • the scroll-type fluid machine can be used not only for general air blowing but also for a device that pressurizes a gas such as nitrogen without leaking to the outside.
  • the anti-rotation mechanism 360 includes a crank pin 365 having two pins 36a and 36b having axes at positions eccentric by the same distance e as the eccentric distance e. .
  • One of the pins 36 2 a of the crank pin 36 2 is rotatably supported by a crank pin bearing 36 4 fixed to a scroll casing 34 2, and the other pin 36 2 b is It is rotatably supported by a crank pin bearing 36 6 fixed to the orbiting scroll 3 36.
  • crankshaft 3332 causes the pin 3632b on the side of the rotary pin 3336 of the crankpin 362 to rotate around the other pin 3622a.
  • a revolving motion is performed with the eccentric distance e as the radius.
  • the revolving motion of 36 2 also causes the revolving scroll 3 36 to perform revolving motion with the eccentric distance e as the radius, and the rotation of the revolving scroll 3 36 is stopped by the crank pin 3 62.
  • Each of the crankpin bearings 364 and 366 is composed of a ceramic ball bearing using silicon nitride as a material, and high durability is ensured.
  • the rotation of the rotating scale 3 36 is prevented from rotating by the rotation preventing mechanism 360, and only the revolving motion is performed by the rotation of the main shaft 3 18.
  • a winding compression operation chamber 3446 is defined by both wraps 336b and 3400d.
  • the compression operation chamber 346 is closed by both end plates 336 a and 340 c, and gas flowing into the compression operation chamber 346 from the suction port 340 a is supplied to the orbiting scroll 3. Due to the orbital motion that prevented the rotation of 36, the compression operation chamber 346 is sequentially transferred from the discharge port 340b while being compressed as the volume of the compression operation chamber 346 is reduced.
  • a magnetic fluid seal mechanism for maintaining the pressure of the compression operation chamber 346 is provided at the tip of the wrap 336b, 340d of both scrolls 336, 340, respectively. .
  • the details of the magnetic fluid sealing mechanism will be described later.
  • the materials of motor casing 312, main bearing case 314, swivel scroll 336, fixed scroll 3400, and scroll casing 342 are made of PPS from the viewpoint of productivity. (Polyphenylene sulfide) Resin and aluminum alloy are used.
  • the main shaft 318 is provided with force contours 330, 334 for ensuring the balance of the rotating system.
  • the first counter weight 330 is located on the opposite side of the main bearing 320 from the motor, and the second counter weight G 3 34 is arranged on the motor side with respect to the main bearing 3 20.
  • FIG. 8 is a partially enlarged view of the magnetic fluid seal mechanism shown in FIG.
  • the tip of the wrap 3 36 b of the revolving scroll 33 6 is formed with a groove 33 36 c extending over substantially the entire length of the wrap 33 36 b in the longitudinal direction.
  • a string-shaped permanent magnet 350 (a first magnet) having a rectangular cross section is inserted in the inside of 36 c along the length direction of the wrap 3 36 b.
  • the reference numeral 350 is fitted and fixed inside the groove 336c using an adhesive or the like.
  • the magnetic fluid 348 is arranged in the groove 336c in which the string-shaped permanent magnet 350 is inserted.
  • a plate-shaped permanent magnet 341 (second magnet) is fixed with an adhesive or the like on the end of the rotating scale 3336 of the fixed scale 3340 on the end plate 3400c.
  • the magnetic fluid 348 is sandwiched between different magnetic poles (the north pole of the string-shaped permanent magnet 350 and the south pole of the plate-shaped permanent magnet 341).
  • a bridge composed of the magnetic fluid 348 is formed between the string-shaped permanent magnet 350 and the plate-shaped permanent magnet 341, and the gas handled in the compression operation chamber 346 is moved to the high pressure side.
  • a magnetic fluid sealing mechanism for preventing leakage from the air to the low pressure side is formed.
  • the plate-shaped permanent magnet 341 is formed with a spiral wrap hole 341a through which the wrap provided on the fixed scale 340 is inserted. I have.
  • a groove 3400 e force S extending over substantially the entire length of the wrap 3400 d in the longitudinal direction is also provided on the leading end surface of the wrap 3400 d of the fixed scroll 340.
  • a string-shaped permanent magnet 354 (first magnet) having a rectangular cross section is inserted into the groove 340e along the length direction of the wrap 340d. ing.
  • the string-shaped permanent magnet 354 is fitted and fixed in the groove 340e using an adhesive or the like.
  • the magnetic fluid 352 is disposed in the groove 340e to which the string-shaped permanent magnet 354 is attached.
  • the plate-shaped permanent magnet 337 (second magnet) is fixed to the fixed scroll 3340 a side of the rotating scroll 3336 by adhesive or the like. 352 is sandwiched between different magnetic poles (the south pole of the string-shaped permanent magnet 3554 and the north pole of the plate-shaped permanent magnet 3337). As a result, a bridge made of the magnetic fluid 52 is formed between the string-shaped permanent magnets 354 and the plate-shaped permanent magnets 337, and the gas handled in the compression operation chamber 346 is set at the high pressure side. A magnetic fluid sealing mechanism is formed to prevent leakage to the low pressure side.
  • the plate-shaped permanent magnet 337 has a spiral wrap hole 337a through which a wrap 336b provided in the orbiting scroll 336 is inserted.
  • the gap between the surface of the permanent magnet 337 and the surface of the permanent magnet 337 is as large as about 1 mm, and does not require high assembly accuracy as in the conventional case using a tip seal.
  • the above-described string-shaped permanent magnet 350 preferably has a stronger magnetic force than the plate-shaped permanent magnet 341.
  • the magnetic force of the string-shaped permanent magnet 350 is weaker than that of the plate-shaped permanent magnet 341, the magnetic fluid 348 is strongly attracted to the plate-shaped permanent magnet 341, and as a result, the magnetic fluid 3 This is because 48 may be scattered.
  • the string-shaped permanent magnet 3 5 4 is different from the plate-shaped permanent magnet 3 3 7 It is preferable to have a very strong magnetic force.
  • a non-contact type seal can be practically constituted by using a magnetic fluid seal mechanism instead of the conventional contact type tip seal.
  • power consumption due to sliding loss and leakage of handled fluid can be suppressed, and the efficiency of the equipment can be improved.
  • the two magnetic fluid sealing mechanisms can exert a sealing function without keeping the axial gap between the scrolls so small, the rotating scroll generated by the inner and outer ring gap of the ball bearing and the like can be used. It is not necessary to extremely suppress the fall and rattling, and therefore, the structure of the device is simplified, which can lead to an improvement in productivity.
  • FIG. 9 is a sectional view showing a squeal type fluid machine according to a seventh embodiment of the present invention.
  • This scroll-type fluid machine has, for example, a cup-shaped motor casing 412 in which airtightness between the inside and outside is ensured by integrally molding the motor stator 410 with polyester resin. ing.
  • the motor stator 4 1 0 Inside the power leads 4 1 4 Electric power is supplied from the t Motake one Thing 4 1 2 are arranged the motor rotor 4 1 6 comprising a permanent magnet, the motor
  • the rotor 416 is fixed to the main shaft 418 by an adhesive or the like.
  • the main shaft 4 18 is connected to a motor bearing 4 1 2 via a main bearing 4 2 0 arranged at the center along the axial direction and an auxiliary bearing 4 2 2 arranged at the motor side end. It is supported rotatably.
  • a crankshaft 4 24 having an axis at a position eccentric from this axis by an eccentric distance e is connected to the body.
  • a substantially disk-shaped orbiting scroll 4330 is rotatably connected to a tip of the crankshaft 4 2 4 via a orbiting bearing 4 2 6 composed of a ball bearing. I have.
  • crankshaft 424 performs a revolving motion centered on the axis of the main shaft 418 and having an eccentric distance e as a radius along with the rotation (rotation) of the main shaft 418.
  • the orbiting scroll 4 3 0 also makes a revolving motion with the eccentric distance e as the radius.
  • the slewing bearing 4 26 in the present embodiment is composed of two ball bearings arranged in the axial direction. A bearing 4 27 is disposed between these ball bearings, and the main shaft 4 1 Orbiting scroll for 8 4 4 3 0 Falling is suppressed.
  • Each of the main bearing 420, the auxiliary bearing 422, and the slewing bearing 426 is constituted by a ceramic ball bearing using silicon nitride as a material, and high durability is secured.
  • O-rings for preventing creep are arranged on the outer rings of these ball bearings 420, 422 and 426.
  • a substantially force-shaped fixed scroll 4400 having a suction port 44a at the outer periphery and a discharge port 44b at the center is arranged.
  • a wrap 4334 having an involute curve or a curved shape similar to the involute curve protruding toward the fixed scroll 4440 is provided.
  • a tip seal 436 that comes into contact with and seals the end plate 442 of the fixed scroll 4440 is attached to the tip of the wrap 434 of the revolving scroll 4340.
  • the end plate 4442 of the fixed scroll 4440 is provided with a wrap 4444 having an involute curve or a curve shape similar to the involute curve protruding toward the swivel scroll 4340.
  • a tip seal 4 46 that is in contact with and seals the end plate 4 32 of the orbiting scroll 4 30 is attached.
  • the tip seals 4 3 6 and 4 4 6 are, for example, PPS (polyphenylene sulfide).
  • a resin material is used which has improved slidability by adding a fluororesin or the like to the base.
  • a PPS (polyphenylene sulfide) resin or an aluminum alloy is used from the viewpoint of productivity.
  • An O-ring 428 is provided at a portion between the motor casing 412 and the fixed scroll 440.
  • the motor casing 4 1 2 and the fixed scroll 4 4 0 are bolted together via the O-ring 4 2 8, whereby the motor casing 4 1 2 and the fixed scroll 4 4 0 are connected.
  • the airtightness of the interior defined by the space is ensured, and the gas flowing between the suction port 4400a and the space between the both sides 4300, 4440 can be discharged from other than the discharge port 4400b. Leaks are to be prevented. Therefore, this scroll-type fluid machine can be used not only for general air blowing but also for, for example, a device for increasing the pressure of a gas such as nitrogen without leaking to the outside.
  • the rotation preventing mechanism 450 includes a ring-shaped permanent magnet (first magnet) 452 provided on the motor casing 41 and a pin-shaped permanent magnet (second magnet) provided on the orbiting scroll 43. 5 4.
  • the ring-shaped permanent magnet 452 is formed by fitting two ring-shaped permanent magnets 452a and 4552b made of, for example, summary cobalt, to each other. It is fitted to.
  • the outer ring-shaped permanent magnet 4 52 a is fixed so that the revolving scroll 43 0 side becomes the N pole and the motor casing 41 2 side becomes the S pole, and the inner ring-shaped permanent magnet is formed.
  • 4 5 2 b is a rotating scroll 4 3 0 side is S pole, motor casing 4 It is fixed so that 12 side is N pole.
  • the magnetic force along the inner diameter of the ring-shaped permanent magnet 45 52 b located on the inner side is strengthened, and the rotating scroll 43 0 side is positioned radially opposite to this inner diameter.
  • An extremely narrow doughnut-shaped magnetic ring (S pole) is formed.
  • the radius of the inner circumference of the ring-shaped permanent magnet 452, that is, the radius d of the ring-shaped permanent magnet 452b located inside is set to be equal to the eccentric distance (scroll radius) e described above.
  • the pin-shaped permanent magnet 454 is made of, for example, summary cobalt, and its axis is positioned parallel to the axis of the ring-shaped permanent magnet 452 and at the same distance as the eccentric distance e. It is arranged facing the ring-shaped permanent magnet 4 52.
  • the pin-shaped permanent magnet 4 54 is fixed to the revolving scroll 4 30 so that the motor casing 12 has the N pole.
  • the ring-shaped permanent magnets 45 2 and the pin-shaped permanent magnets 45 54 attract each other, and the pin-shaped permanent magnets 45 54 are located on the inner periphery of the ring-shaped permanent magnets 45 2. It moves in a non-contact manner so as to trace over the inner periphery of the ring-shaped permanent magnet 4 52 b) to prevent the rotating scroll 4 330 from rotating.
  • the orbiting scroll and the motor-side fixing member required for the conventional scroll type fluid machine are provided.
  • a bracket and the positioning of the motor-side fixing member (bracket) and the fixing scroll (eg, a knock pin) are substantially unnecessary.
  • the overall structure is extremely simple and can contribute to increased productivity.
  • the play in the axial direction between the rotating component and the fixed component can be made substantially zero.
  • the rotating scale 4 3 0 Since the casing is rotated while being constantly sucked into the casing 4 1 2 side, not only the clearance management of the tip seals 4 3 6 and 4 4 6 is easy but also the tip seals 4 3 6 and 4 4 6 Even if worn, the orbiting scroll 4330 moves to the motor casing 4122 to maintain the clearance, so that performance can be maintained for a long time.
  • the above-described rotation preventing mechanism can be provided between the turning scroll 43 and the fixed scroll 44.
  • the rotation of the rotating scale 4330 is prevented from rotating by the rotation preventing mechanism 450, and only the revolving motion is performed by the rotation of the main shaft 418.
  • the volume gradually decreases from the outer circumference to the inner circumference due to the revolving motion that prevented the rotation of the rotating scroll / roller 4300.
  • a spiral compression operation chamber C is defined by both wraps 4 3 4 and 4 4 4.
  • the compression operation chamber C is closed by both end plates 432, 4442, and the gas flowing into the compression operation chamber C from the suction port 44a prevents the rotation of the swirling scroll 4330. Due to the revolving motion described above, the compression operation chamber C is sequentially transferred from the discharge port 450b while being compressed as the volume of the operation chamber C decreases.
  • a part of the slewing bearing 426 is located closer to the fixed scale 4440 than the end plate 432 of the swivel scale 4330. It is arranged as follows. As a result, the slewing bearing 4 2 6 does not protrude from the end plate 4 3 2 of the slewing scroll 4 3 2 to the motor casing 4 1 2 side, so the tip of the wrap 4 3 4 of the slewing scroll 4 3 0 The distance from the shaft to the main bearing 420 can be reduced, and the axial length of the device can be shortened.
  • the main shaft 4 18 has a rotating shaft between the main bearing 4 20 and the slewing bearing 4 26.
  • a power entry 460 is provided to ensure system balance.
  • a center-of-gravity adjusting weight 438 that protrudes toward the motor is provided on the outer peripheral end of the end plate 432 of the revolving scroll 4330.
  • the center-of-gravity adjusting weight 438 is arranged such that the center of gravity in the axial direction of the revolving scroll 4330 and the counterweight 460 is substantially the same.
  • the motor rotor 416 made of a permanent magnet is fixed to the main shaft 418 using an adhesive.
  • the counterweight 460 is previously provided integrally with the main shaft 418 by shrink-fitting or press-contact. Then, the inner rings of the main bearings 420 and the auxiliary bearings 422 are press-fitted and fixed to the main shaft 418, and the inner rings of the slewing bearings 426 are press-fitted and fixed to the opposite motor side.
  • the outer ring of the slewing bearing 4 26 is inserted into the housing of the slewing scroll 4 30. Also, using an adhesive, etc., three sets of ring-shaped permanent magnets 452 are fixed to the motor casing 412 and three sets of pin-shaped permanent magnets 454 are fixed to the motor side of the rotary scroll 430. I do.
  • the corrugated washer 429 is inserted into the housing of the auxiliary bearing 422 of the motor casing 412, and then the spindle assembly with the orbiting scroll 430 is attached to the motor casing 412. insert.
  • a fixed scroll 4440 is fixed to the open end of the motor casing 4122.
  • an O-ring 428 is provided on the outer peripheral portion of the fixed scroll 440, and the mounting angle of the fixed scroll 440 is determined by a positioning pin (not shown).
  • the axial gap at the end of each wrap 4 3 4, 4 4 4 is adjusted by inserting a shim (not shown) between the fixed scroll 4 4 0 and the motor casing 4 12. .
  • the squeal type fluid machine of the present embodiment can be submerged in water to cool the main body by water cooling (in this case, the intake pipe and the discharge pipe are exposed to the air).
  • water cooling in this case, the intake pipe and the discharge pipe are exposed to the air.
  • FIG. 10 is a sectional view showing a scroll type fluid machine according to an eighth embodiment of the present invention.
  • Members or elements having the same functions or functions as those of the above-described seventh embodiment are denoted by the same reference numerals, and parts that are not particularly described are the same as those of the seventh embodiment.
  • a so-called inner rotor type motor in which the motor rotor 4 16 is arranged on the inner peripheral side of the main bearing 420 is used.
  • FIG. As shown in the figure, since the main bearings 420 and the motor rotors 416 are sequentially arranged in the axial direction, the axial length of the device cannot be sufficiently reduced.
  • a so-called flat motor in which a motor rotor is arranged on the outer peripheral side of the main bearing is used, and the axial length of the device is extremely reduced.
  • the main shaft 4 18 in the present embodiment has a disk-shaped rotor housing 5 extending outwardly between the main bearing 4 20 and the slewing bearing 4 26. 15 are provided integrally.
  • a donut-shaped motor rotor 5 16 made of a permanent magnet is fixed to the rotor housing 5 15 so as to be located on the outer peripheral side of the main bearing 4 20.
  • a flat motor stator 510 used in the flat motor is arranged at a position on the motor casing 4122 side facing the motor rotor 516.
  • a counterweight portion 560 for securing the balance of the rotating system is integrally provided on the outer peripheral portion of the rotor housing 515.
  • the motor is provided on the outer peripheral side of the main bearing 420. Since the rotors 5 16 are arranged, the axial length of the device can be further reduced as compared with the seventh embodiment. Also, the couple imbalance can be canceled by only one counterweight section 560, and the counterweight section 560 can be integrated with the main shaft 418, so that the components can be integrated. A quiet device with little vibration can be realized without increasing the number of points.
  • the motor rotor 516 made of a permanent magnet is fixed to the rotor housing 515 using an adhesive.
  • the rotary housing 5 15 is previously provided integrally with the main shaft 4 18.
  • the inner ring of the main bearing 420 and the auxiliary bearing 422 is press-fitted and fixed to the main shaft 418, and the inner ring of the slewing bearing 426 is press-fitted and fixed to the side opposite to the motor.
  • the outer ring of the orbiting bearing 426 is inserted into the housing of the orbiting scroll 4330.
  • three sets of ring-shaped permanent magnets 452 are fixed to the motor casing 412 and three sets of pin-shaped permanent magnets 454 are fixed to the motor side of the rotary scroll 430. I do.
  • the corrugated washer is inserted into the housing of the auxiliary bearing 4 22 of the motor casing 4 1 2, and then, the spindle assembly with the rotating scroll 4 3 0 attached is inserted into the motor casing 4 12. .
  • a fixed scale 4440 is fixed to the open end of the motor casing 4122.
  • FIG. 11 is a sectional view showing a scroll type fluid machine according to a ninth embodiment of the present invention.
  • Members or elements having the same functions or functions as those of the above-described eighth embodiment are denoted by the same reference numerals, and parts that are not particularly described are the same as those of the eighth embodiment.
  • a so-called outer rotor type motor is used. That is, as shown in FIG. 11, the main shaft 4 18 in the present embodiment is provided with a power-up rotor housing 6 15 between the main bearing 4 20 and the slewing bearing 4 26. Have been.
  • the inner periphery of the rotor housing 615 is fixed, for example, by shrink fitting so as to be located on the outer periphery of the main rotor 420 and the motor rotor 616 consisting of permanent magnets.
  • a motor stator 610 is arranged at a position on the inner peripheral side facing the motor rotor 616. Further, two counterweight portions 660a and 660b for securing the balance of the rotating system are provided on the outer peripheral portion of the rotor housing 615.
  • the motor rotor 616 is arranged on the outer peripheral side of the main bearing 420, the axial length of the device is further increased as compared with the seventh embodiment. Can be shorter. Further, in the seventh or eighth embodiment described above, a couple imbalance remains slightly, but as in the present embodiment, the two counterweight portions 660 a and 660 are provided. By providing b integrally with the main shaft 4 18, a couple imbalance that occurs slightly can be offset. As a result, a couple imbalance can be rationally canceled without consuming a special space, and a compact, low-vibration, and quiet device can be realized.
  • the concave portion 439 is formed on the fixed scroll 440 side of the center of the orbiting scroll 430. This is provided so that the mounted state of the rotating body such as the orbiting scroll 430 can be easily checked, for example, after the assembly of the scroll type fluid machine is completed. That is, from the discharge port 4 For example, a nail-shaped rod is inserted into the recess 439, and by moving the rod, it is confirmed by hand that the turning scroll 4430 rotates smoothly. Since the concave portion 439 in the above-described embodiment is provided at the center of the rotary scroll 430, that is, at a position that does not slide with the fixed scroll 4400, the rotation by manual rotation described above is performed. There is no problem even if the recesses 4 3 9 are scratched when checking.
  • the orbiting scroll has a structure in which the orbiting bearing does not project from the end plate of the orbiting scale to the motor casing side.
  • the distance from the tip of the wrap to the main bearing can be reduced, and the axial length of the device can be shortened.
  • the center of gravity in the axial direction of the revolving scroll and the counterweight can be configured to be the same, unbalance occurs due to couple during operation. In this case, it is not necessary to separately provide a force center for correcting the dynamic balance, so that the length of the device in the axial direction can be shortened and the entire device can be made compact.
  • the present invention relates to an oil-free scroll type fluid machine that compresses and transfers gas in an unlubricated state, and is particularly suitable for a scroll type fluid machine used as a blower for compressing and transferring combustible gas and the like. .

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne une pompe motorisée centrifuge (non volumétrique) pouvant s'utiliser dans une petite zone de sortie à volume d'eau extrêmement réduit, de structure plutôt simple et de petite taille, et comprenant un stator de moteur tubulaire (10), un rotor de moteur (20) à aimant permanent (30), formant une seule pièce avec une turbine (32) et placé à l'intérieur du stator (10), et un logement de pompe (44) fixé à la partie d'extrémité d'ouverture d'un carter de moteur (12) de façon à couvrir la turbine (32), un palier à pression dynamique (54) étant formé entre la face frontale de la turbine (32) et une rainure hélicoïdale (52) disposée dans la surface interne du logement de pompe (44) face à la face frontale de la turbine (32).
PCT/JP2001/009681 2000-11-07 2001-11-06 Dispositif pour circulation de fluide en spirale WO2002038960A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2002211012A AU2002211012A1 (en) 2000-11-07 2001-11-06 Scroll fluid machinery

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
JP2000-339171 2000-11-07
JP2000339171A JP2002138974A (ja) 2000-11-07 2000-11-07 スクロール型流体機械
JP2000388923A JP2002188584A (ja) 2000-12-21 2000-12-21 スクロール型流体機械
JP2000-388923 2000-12-21
JP2001121423A JP2002317777A (ja) 2001-04-19 2001-04-19 スクロール型流体機械
JP2001-121423 2001-04-19
JP2001179216A JP2002371977A (ja) 2001-06-13 2001-06-13 スクロール型流体機械
JP2001179217A JP2002371979A (ja) 2001-06-13 2001-06-13 スクロール型流体機械
JP2001-179216 2001-06-13
JP2001-179217 2001-06-13

Publications (1)

Publication Number Publication Date
WO2002038960A1 true WO2002038960A1 (fr) 2002-05-16

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109209886A (zh) * 2017-07-07 2019-01-15 上海海立电器有限公司 一种转子式压缩机
EP3153708B1 (fr) * 2015-10-06 2019-07-17 Pfeiffer Vacuum Gmbh Pompe a spirales et procede destine au fonctionnement d'une pompe a spirales
EP4083374A3 (fr) * 2021-04-28 2022-11-16 Dabir Surfaces, Inc. Pompe é spirales avec coupleur moteur flottant
EP4212726A1 (fr) * 2022-01-14 2023-07-19 LG Electronics, Inc. Compresseur à spirales
WO2023187379A1 (fr) * 2022-03-30 2023-10-05 Edwards Limited Pompe à spirale

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01106989A (ja) * 1987-10-20 1989-04-24 Matsushita Electric Ind Co Ltd スクロール圧縮機
JPH03156185A (ja) * 1989-11-10 1991-07-04 Shin Meiwa Ind Co Ltd スクロール形流体機械
JPH03249386A (ja) * 1990-02-28 1991-11-07 United Technol Corp <Utc> スクロール圧縮機内の軸受荷重を減少する方法及び装置
JPH0526187A (ja) * 1991-07-18 1993-02-02 Tokico Ltd スクロール式流体機械
JPH0643285U (ja) * 1992-11-16 1994-06-07 株式会社神戸製鋼所 スクロール圧縮機
JPH06241178A (ja) * 1993-02-17 1994-08-30 Mitsubishi Electric Corp スクロール圧縮機
JPH08144985A (ja) * 1994-11-18 1996-06-04 Tokico Ltd スクロール式流体機械
JP2000097170A (ja) * 1998-09-24 2000-04-04 Sanyo Electric Co Ltd 無給油式スクロール流体機械及びその製造方法

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01106989A (ja) * 1987-10-20 1989-04-24 Matsushita Electric Ind Co Ltd スクロール圧縮機
JPH03156185A (ja) * 1989-11-10 1991-07-04 Shin Meiwa Ind Co Ltd スクロール形流体機械
JPH03249386A (ja) * 1990-02-28 1991-11-07 United Technol Corp <Utc> スクロール圧縮機内の軸受荷重を減少する方法及び装置
JPH0526187A (ja) * 1991-07-18 1993-02-02 Tokico Ltd スクロール式流体機械
JPH0643285U (ja) * 1992-11-16 1994-06-07 株式会社神戸製鋼所 スクロール圧縮機
JPH06241178A (ja) * 1993-02-17 1994-08-30 Mitsubishi Electric Corp スクロール圧縮機
JPH08144985A (ja) * 1994-11-18 1996-06-04 Tokico Ltd スクロール式流体機械
JP2000097170A (ja) * 1998-09-24 2000-04-04 Sanyo Electric Co Ltd 無給油式スクロール流体機械及びその製造方法

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3153708B1 (fr) * 2015-10-06 2019-07-17 Pfeiffer Vacuum Gmbh Pompe a spirales et procede destine au fonctionnement d'une pompe a spirales
CN109209886A (zh) * 2017-07-07 2019-01-15 上海海立电器有限公司 一种转子式压缩机
EP4083374A3 (fr) * 2021-04-28 2022-11-16 Dabir Surfaces, Inc. Pompe é spirales avec coupleur moteur flottant
EP4212726A1 (fr) * 2022-01-14 2023-07-19 LG Electronics, Inc. Compresseur à spirales
US12000394B2 (en) 2022-01-14 2024-06-04 Lg Electronics Inc. Scroll compressor
WO2023187379A1 (fr) * 2022-03-30 2023-10-05 Edwards Limited Pompe à spirale

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