WO2012086637A1 - 多気筒回転式圧縮機及び冷凍サイクル装置 - Google Patents

多気筒回転式圧縮機及び冷凍サイクル装置 Download PDF

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Publication number
WO2012086637A1
WO2012086637A1 PCT/JP2011/079491 JP2011079491W WO2012086637A1 WO 2012086637 A1 WO2012086637 A1 WO 2012086637A1 JP 2011079491 W JP2011079491 W JP 2011079491W WO 2012086637 A1 WO2012086637 A1 WO 2012086637A1
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WO
WIPO (PCT)
Prior art keywords
blade
cylinder
chamber
pressure
valve
Prior art date
Application number
PCT/JP2011/079491
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
平山　卓也
フェルディ モナスリ ジャフェット
仁 古根村
勝吾 志田
和 高島
平野　浩二
Original Assignee
東芝キヤリア株式会社
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 JP2010283560A external-priority patent/JP5703013B2/ja
Priority claimed from JP2011068818A external-priority patent/JP5588903B2/ja
Application filed by 東芝キヤリア株式会社 filed Critical 東芝キヤリア株式会社
Priority to CN201180051555.3A priority Critical patent/CN103180613B/zh
Publication of WO2012086637A1 publication Critical patent/WO2012086637A1/ja

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Classifications

    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • 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
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves

Definitions

  • Embodiments of the present invention relate to a multi-cylinder rotary compressor and a refrigeration cycle apparatus including the multi-cylinder rotary compressor and constituting a refrigeration cycle.
  • a multi-cylinder rotary compressor having a plurality of cylinder chambers in the compression mechanism is frequently used.
  • full capacity operation that performs compression action in multiple cylinder chambers at the same time, ability to perform compression action in one cylinder chamber, stop compression action in the other cylinder chamber, and reduce compression work It is advantageous if switching to half operation is possible.
  • the compression mechanism of a multi-cylinder compressor disclosed in Japanese Patent Application Laid-Open No. 2010-163927 enables the suspension of compression operation in one cylinder chamber by separating the tip of one blade from the roller circumferential surface.
  • a cylinder resting mechanism is provided. If the cylinder resting mechanism is not functioned, the full capacity operation is performed in which the compression operation is performed in both cylinder chambers.
  • Japanese Patent Publication No. 2008-520901 discloses a multi-cylinder rotary compressor that reciprocates a blade.
  • a back pressure introduction passage is communicated with the blade back chamber of one of the blades.
  • the tip of the blade is separated from the roller circumferential surface, and the half capacity operation is stopped to stop the compression operation in one cylinder chamber, or both cylinder chambers Full-capacity operation is possible with compression operation.
  • the cylinder resting mechanism in the multi-cylinder rotary compressor disclosed in Japanese Patent Application Laid-Open No. 2010-163927 is provided with a pressure introduction passage, and a high pressure gas or Low pressure gas is guided. That is, the pressure introduction passage is provided in an intermediate partition plate that covers the cylinder end surface, and all of the openings facing the blade back chamber are located in a range in which the blade moves.
  • the blade may tilt obliquely in the height direction as it reciprocates. If the blade tilts in the height direction of the blade under some conditions, the end face corner of the blade collides with the corner of the opening of the pressure introduction path, and noise may be generated, and the reciprocation may be locked. .
  • the lubricating oil that collects in the bottom of the sealed case enters the blade back chamber and the back pressure introduction passage that communicates therewith as the blade reciprocates.
  • the operation time is extended for a long time, a phenomenon occurs in which the blade back chamber and the back pressure introduction passage are filled with lubricating oil, resulting in a decrease in lubricity and an increase in noise at each sliding portion of the compression mechanism.
  • the present embodiment is based on the above circumstances, and it is assumed that a plurality of cylinders are provided and the compression capacity is variable. Provided are a multi-cylinder rotary compressor that prevents locking, has low noise, and is highly reliable, and a refrigeration cycle apparatus that includes this multi-cylinder rotary compressor and improves the refrigeration cycle efficiency.
  • a multi-cylinder rotary compressor that makes it difficult to collect lubricating oil in the blade back chamber and the back pressure introduction passage to improve reliability and reduce noise, and a refrigeration cycle efficiency provided with this multi-cylinder rotary compressor
  • a refrigeration cycle apparatus that can improve the performance of the above is provided.
  • the multi-cylinder rotary compressor and the refrigeration cycle apparatus in the present invention are configured as follows.
  • the compression mechanism unit is provided with an intermediate partition plate, and each inner diameter unit Cylinder chambers into which low-pressure gas is introduced are formed, and a blade back chamber communicating with the cylinder chambers via a blade groove is provided, and the first cylinder and the second cylinder are provided.
  • a bearing that is provided on an end face of the second cylinder and closes the cylinder chamber together with the intermediate partition plate; and the rotating shaft having an eccentric portion that is accommodated in each of the first and second cylinder chambers; A roller that is fitted to the eccentric portion of the rotating shaft and moves eccentrically in the cylinder chamber as the rotating shaft rotates, and is movably accommodated in the blade groove.
  • One of the blade back chambers of the blade that divides the cylinder chamber into two chambers in a state in which the tip is in contact with the roller peripheral wall and the blade back chamber provided in the first cylinder and the second cylinder.
  • a back pressure introduction passage having an opening opening from the end face side of the cylinder, and a high pressure or a low pressure is led to the one blade back chamber through the back pressure introduction passage, and the blade rear end portion in a state where the high pressure is led.
  • a high back pressure is applied to the blade and the tip of the blade is brought into contact with the roller peripheral wall to perform the compression operation in the cylinder chamber.
  • the blade tip is separated from the roller peripheral wall in a state where the low pressure is introduced, and compression is performed in the cylinder chamber.
  • Pressure switching means for stopping the operation, and the outer opening corner of the back pressure introduction passage farther from the rotation shaft is the end face of the blade rear end located in the cylinder resting state. Corner Positioned on the outer peripheral side than.
  • the refrigeration cycle apparatus includes the above-described multi-cylinder rotary compressor, a condenser, an expansion device, and an evaporator to constitute a refrigeration cycle.
  • the compression mechanism parts each have a cylinder chamber.
  • the first blade and the second blade, the blade back chamber formed on the rear end side of the second blade, and the blade back chamber communicated with each other.
  • a back pressure introduction passage for applying back pressure to the blade of 2 a communication passage communicating the blade back chamber and the internal space of the sealed case, and a check valve mechanism for opening and closing the communication passage, Check valve The high pressure is introduced into the blade back chamber, the communication path is closed when the second blade moves in the direction of enlarging the volume of the blade back chamber, and the second blade reduces the volume of the blade back chamber. When moving in the direction, the communication path is configured to be opened.
  • the refrigeration cycle apparatus includes the above-described multi-cylinder rotary compressor, a condenser, an expansion device, and an evaporator to constitute a refrigeration cycle.
  • FIG. 1 is a schematic longitudinal sectional view of a multi-cylinder rotary compressor according to the first embodiment.
  • FIG. 2 is an exploded perspective view of a main part of the multi-cylinder rotary compressor.
  • FIG. 3 is an enlarged vertical sectional view of a main part (X part) of the multi-cylinder rotary compressor.
  • FIG. 4 is a cross-sectional plan view of the main part of the multi-cylinder rotary compressor.
  • FIG. 5 is a configuration diagram of the refrigeration cycle of the refrigeration cycle apparatus including the multi-cylinder rotary compressor.
  • FIG. 6 is a schematic longitudinal sectional view of a multi-cylinder rotary compressor according to the second embodiment.
  • FIG. 7 is an enlarged view of a Y portion in FIG. 6 according to the multi-cylinder rotary compressor.
  • FIG. 8 is a longitudinal sectional view taken along the line TT of FIG. 7 according to the multi-cylinder rotary compressor.
  • FIG. 9 is a schematic longitudinal sectional view of a multi-cylinder rotary compressor according to the third embodiment.
  • FIG. 10 is a characteristic diagram of efficiency with respect to the flow area ratio between the flow path resistance portion and the pipe in the multi-cylinder rotary compressor.
  • FIG. 1 is a schematic longitudinal sectional view of a multi-cylinder rotary compressor M according to this embodiment.
  • reference numeral 1 denotes a sealed case.
  • a compression mechanism 3 is provided in the lower part of the sealed case 1, and an electric motor part 4 is provided in the upper part.
  • the electric motor unit 4 and the compression mechanism unit 3 are integrally connected via a rotating shaft 5.
  • the compression mechanism section 3 includes a first cylinder 6A on the upper side and a second cylinder 6B on the lower side.
  • the main bearing 7A is attached and fixed to the upper end surface of the first cylinder 6A
  • the auxiliary bearing 7B is attached and fixed to the lower end surface of the second cylinder 6B.
  • An intermediate partition plate 2 is interposed between the first cylinder 6A and the second cylinder 6B.
  • the rotary shaft 5 penetrates through the cylinders 6A and 6B, and integrally includes a first eccentric portion 5a and a second eccentric portion 5b having the same diameter and a phase difference of about 180 °.
  • Each eccentric part 5a, 5b is assembled so that it may be located in the internal diameter part of cylinder 6A, 6B.
  • the first roller 9a is fitted to the circumferential surface of the first eccentric portion 5a
  • the second roller 9b is fitted to the circumferential surface of the second eccentric portion 5b.
  • the inner diameter portion of the first cylinder 6A is closed by the main bearing 7A and the intermediate partition plate 2 to form a first cylinder chamber Sa.
  • the inner diameter portion of the second cylinder 6B is closed by the intermediate partition plate 2 and the auxiliary bearing 7B, thereby forming a second cylinder chamber Sb.
  • the first cylinder chamber Sa and the second cylinder chamber Sb are designed to have the same diameter and height.
  • the peripheral walls of the first and second rollers 9a and 9b can be moved eccentrically while being in line contact with the peripheral walls of the first and second cylinder chambers Sa and Sb via the lubricating oil film.
  • the respective rollers 9a and 9b are accommodated in the cylinder chambers Sa and Sb.
  • the discharge muffler 8a that is doubled is attached to the main bearing 7A and covers the discharge valve mechanism provided on the main bearing 7A. Each discharge muffler 8a is provided with a discharge hole.
  • a single discharge muffler 8b is attached to the auxiliary bearing 7B and covers a discharge valve mechanism provided in the auxiliary bearing 7B. The discharge muffler 8b is not provided with a discharge hole.
  • the discharge valve mechanism of the main bearing 7A faces the first cylinder chamber Sa, opens when the chamber rises to a predetermined pressure due to the compression action, and discharges the compressed gas into the discharge muffler 8a.
  • the discharge valve mechanism of the sub-bearing 7B faces the second cylinder chamber Sb and opens when the chamber pressure rises to a predetermined pressure due to the compression action, and discharges compressed gas into the discharge muffler 8b.
  • a discharge gas guide path is provided across the auxiliary bearing 7B, the second cylinder 6B, the intermediate partition plate 2, the first cylinder 6A and the main bearing 7A.
  • the discharge gas guide path guides the high-pressure gas discharged from the second cylinder chamber Sb to the lower discharge muffler 8b through the discharge valve mechanism into the upper double discharge muffler 8a.
  • An oil reservoir 14 for collecting lubricating oil is formed on the inner bottom of the sealed case 1.
  • the solid line crossing the flange portion of the main bearing 7 ⁇ / b> A indicates the oil level of the lubricating oil, and almost all of the compression mechanism portion 3 is immersed in the lubricating oil in the oil reservoir portion 14.
  • An oil supply passage for supplying lubricating oil is provided across the lower end surface of the rotating shaft 5 and each sliding portion of the compression mechanism portion 3.
  • FIG. 2 is an exploded perspective view showing a part of the compression mechanism unit 3 according to the embodiment. Only the main part is shown, and details are omitted.
  • a blade groove 10a is connected to the first cylinder chamber Sa, which is an inner diameter portion, and a first blade back chamber 11a is further provided from the blade groove 10a.
  • a first blade 12a is movably accommodated in the blade groove 10a, and its front end can project into and out of the second cylinder chamber Sa, and its rear end can project into and out of the first blade back chamber 11a.
  • a blade groove 10b is connected to a second cylinder chamber Sb which is an inner diameter portion, and a second blade back chamber 11b is further provided from the blade groove 10b.
  • a second blade 12b is movably accommodated in the blade groove 10b, and its front end can project into and out of the second cylinder chamber Sb, and its rear end can project into and out of the second blade back chamber 11b.
  • the tip portions of the first and second blades 12a and 12b are formed in a substantially arc shape in plan view, and these tip portions protrude into the opposing first and second cylinder chambers Sa and Sb.
  • the first and second rollers 9a and 9b shown in FIG. 1 which are circular in plan view are in line contact with the peripheral walls of the first and second rollers 9a and 9b regardless of their rotation angles.
  • the first cylinder 6A is provided with a lateral hole Wf that communicates the first blade back chamber 11a and the outer peripheral surface of the cylinder 6A, and the spring member 13 is accommodated therein.
  • the spring member 13 is interposed between the rear end face of the first blade 12a and the inner peripheral wall of the sealed case 1, and applies an elastic force (back pressure) to the first blade 12a.
  • the front end is affected by the pressure of the second silicid chamber Sb
  • the rear end is affected by the pressure of the second blade back chamber 11b
  • the pressure difference between the front and rear ends Back pressure is applied or not applied.
  • FIG. 3 is an enlarged vertical cross-sectional view of the second blade back chamber 11b, which is a main part of the compression mechanism unit 3, and the peripheral part, showing the X part in FIG. 1 in an enlarged manner.
  • FIG. 4 is a plan view showing the second blade back chamber 11b, which is the main part, with the intermediate partition plate 2 removed.
  • a permanent magnet 17 is attached to the second blade back chamber 11 b via a holding member 16.
  • the magnetic force of the permanent magnet 17 is such that the rear end portion of the second blade 12b can be magnetically attracted when the rear end portion of the second blade 12b comes into contact with the holding member 16 or moves to a very close position. is there.
  • the permanent magnet 17 is a rare earth magnet, and can obtain a large magnetic force with a small volume, thereby improving space efficiency.
  • the holding member 16 is formed by sheet metal processing of an austenitic stainless agent which is a non-magnetic material. The magnetic force is efficiently transmitted from the permanent magnet 17 to the second blade 12b without leaking, preventing a decrease in magnetic attraction force, high rigidity, and good manufacturability.
  • the second blade back chamber 11b includes a large-diameter first hole Wa continuous with the blade groove 10b, and a small-diameter semicircular second hole continuous with the first hole Wa.
  • the holding member 16 includes a claw portion that holds the upper, lower, left, and right end surfaces of the permanent magnet 17 and two bent portions Wd that are integrally extended on the opposite side of the claw portion. The curvature radius of the bent portion Wd is larger than that of the first hole Wa.
  • the permanent magnet 17 is held on the claw portion of the holding member 16 and both the bent portions Wd are elastically deformed in a direction in contact with each other, and inserted into the first hole portion Wa and the second hole portion Wb. If the elastic force to the bent portion Wd is removed after the insertion, the permanent magnet 17 and the claw portion of the holding member 16 can be inserted into the second hole portion Wb, and the bent portion Wd of the holding member 16 is inserted into the first hole.
  • the permanent magnet 17 can be positioned by elastically contacting the peripheral wall of the portion Wa.
  • FIG. 3 and FIG. 1 will be described.
  • the upper surface opening of the second blade back chamber 11b in the second cylinder 6B is closed by the intermediate partition plate 2 attached to the upper end surface of the second cylinder 6B.
  • the lower surface opening of the second blade back chamber 11b is provided at a position protruding outward from the peripheral end surface of the flange portion of the auxiliary bearing 7B, and the lower surface opening opens into the sealed case 1 as it is.
  • the lower surface opening of the second blade back chamber 11b is closed by a closing member (bearing side member) 18 attached along a part of the outer peripheral wall of the flange portion of the auxiliary bearing 7B. That is, the upper and lower opening portions of the second blade back chamber 11b are closed by the intermediate partition plate 2 and the closing member 18 to form a sealed structure.
  • the closing member 18 is made of cast iron material, or is made of SMF type 3 (iron-carbon based sintered alloy) or SMF type 4 (iron-carbon-copper based sintered alloy), both of which are complicated. A material that can reliably manufacture the internal structure by molding is selected.
  • a hole Wg is provided from the end surface facing the flange portion peripheral end surface of the auxiliary bearing 7B of the closing member 18 to an intermediate portion, and the pressure control pipe 19 is inserted and connected thereto. Furthermore, the tip of the hole Wg is provided so as to intersect and communicate with the lower end of the recess Wh that opens from the upper end surface of the closing member 18 that is the end surface side of the second cylinder 6B to the second blade back chamber 11b. It is done.
  • the pressure control pipe 19 communicates with the second blade back chamber 11b through the hole Wg and the recess Wh provided in the closing member 18.
  • These hole Wg and recess Wh constitute a back pressure introduction passage 20. That is, the second blade back chamber 11b is closed by the intermediate partition plate 2 and the closing member 18, and has a sealed structure, but the back pressure introduction passage 20 communicates with this lower end surface.
  • the pressure control pipe 19 and the back pressure introduction passage 20 constitute a part of a blade back pressure control mechanism (pressure switching means) K described later.
  • the blade back pressure control mechanism K selects and guides the high pressure gas (discharge pressure) or the low pressure gas (suction pressure) to the second blade back chamber 11b, and the pressure of the back pressure on the rear end portion of the second blade 12b. It controls switching.
  • the concave portion Wh constituting the back pressure introduction passage 20 opens to the lower end surface of the second blade back chamber 11b as described above. Strictly speaking, most of the concave portion Wh is opposed to the first hole Wa constituting the second blade back chamber 11b, but the remaining part and the outer opening corner portion ha far from the rotary shaft 5 are opposed. Is opposed to the second hole Wb.
  • the outer opening corner portion ha of the recess Wh is located immediately below the permanent magnet 17 attached to the second blade back chamber 11b. Even in the state where the second blade 12b is magnetically attracted to the permanent magnet 17, the outer opening corner portion ha of the recess Wh has a certain distance on the outer peripheral side from the lower end surface corner portion bb of the rear end portion of the second blade 12b. Will be located.
  • the intermediate partition plate 2 that closes the upper surface opening of the second blade back chamber 11b is provided with a first buffer recess space 21 that opens to the second blade back chamber 11b.
  • the buffer recess space 21 is almost opposite to the first hole Wa constituting the second blade back chamber 11b, like the recess Wh constituting the back pressure introduction passage 20.
  • the remaining part of the first buffer recess space 21 and the outer opening corner 21a far from the rotation shaft 5 are positioned on the outer peripheral side of the second hole Wb. Even if the second blade 12b is magnetically attracted to the permanent magnet 17, the upper end surface corner bc of the rear end of the second blade 12b is a certain distance from the outer opening corner 21a of the first buffer recess space 21. Exist.
  • both bent portions Wd of the holding member 16 is provided so as not to face the concave portion Wh and the first buffer concave space 21 constituting the back pressure introduction passage 20. Accordingly, the upward movement of the permanent magnet 17 and the holding member 16 is restricted by the intermediate partition plate 2, and the downward movement is restricted by the closing member 18. At least a part of the permanent magnet 17 is provided so as not to face the recess Wh and the first buffer recess space 21, and the vertical movement is restricted by the intermediate partition plate 2 and the closing member 18. You may do it.
  • a second buffer recess space 22 is provided so as to communicate with the back pressure introduction passage 20.
  • the second buffer recess space 22 is provided between the second blade back chamber 11b and the outer peripheral wall of the second cylinder 6B.
  • the lower surface is open and the upper surface is somewhat different from the upper surface of the second cylinder 6B. It is in the state which left the wall thickness of.
  • a communication hole 23 is provided between the hole Wg constituting the back pressure introduction passage 20 and the second buffer recess space 22, and the second buffer recess substantially with respect to the back pressure introduction passage 20.
  • a space 22 is opened.
  • the tip of the pressure control pipe 19 inserted into the hole Wg faces a part of the communication hole 23, but there is no hindrance to the effect of the second buffer recess space 22 unless it is completely closed.
  • a discharge refrigerant pipe P is connected to the upper end of the sealed case 1 constituting the multi-cylinder rotary compressor M.
  • the refrigerant pipe P is sequentially connected to devices constituting a heat pump refrigeration cycle, which will be described later, and is connected to an accumulator 25 that is attached and fixed to the sealed case 1 via a fixture.
  • the accumulator 25 and the sealed case 1 are connected via a refrigerant pipe PP for suction.
  • the refrigerant pipe PP passes through the sealed case 1 and is connected to the peripheral end surface of the intermediate partition plate 2.
  • the intermediate partition plate 2 is provided with a branch guide path (not shown) that branches into a bifurcated shape in the axial direction from the peripheral surface portion to which the refrigerant pipe PP is connected.
  • One branch guide path communicates with the first cylinder chamber Sa, and the other branch guide path communicates with the second cylinder chamber Sb. Therefore, the accumulator 25 and the first cylinder chamber Sa and the second cylinder chamber Sb in the multi-cylinder rotary compressor M are always in communication.
  • the pressure control pipe 19 extends to a position above the upper ends of the sealed case 1 and the accumulator 25, and a pressure switching valve 27 described later is provided at this end.
  • the pressure switching valve 27 uses a four-way switching valve used in an air conditioner equipped with a heat pump refrigeration cycle capable of switching between cooling and heating operations, thereby reducing costs.
  • the first branch pipe (high pressure pipe) 28 is branched from the refrigerant pipe P connected to the upper end of the sealed case 1, and this is connected to the first port pa of the pressure switching valve 27.
  • the pressure control pipe 19 is connected to the second port pb, and the second branch pipe (low pressure pipe) 29 branched from the refrigerant pipe P on the refrigerant introduction side of the accumulator 25 is connected to the third port pc. Is done.
  • the fourth port pd is always closed by the plug 30.
  • the valve body 31 accommodated therein includes a position where the third port pc and the fourth port pd communicate with each other as shown in the figure, and a second port pb and a third port as indicated by a two-dot chain line. The operation is switched electromagnetically to a position communicating with pc.
  • the first port pa is always open, and the fourth port pd is always closed.
  • a four-way switching valve which is a standard product used in a refrigeration cycle constituting a normal heat pump air conditioner, is used. Instead of this four-way switching valve, a three-way valve is used, or a plurality of pressure switching valves 27 are used. The same effect can be obtained by combining the on-off valves.
  • the blade back pressure control mechanism K includes the pressure switching valve 27, the pressure control pipe 19, the first branch pipe 28 and the second branch pipe 29, and the back pressure introduction passage 20 provided in the closing member 18.
  • the high pressure and the low pressure can be switched and guided to the second blade back chamber 11b, and the back pressure can be applied to the second blade 12b.
  • FIG. 5 is a configuration diagram of a heat pump refrigeration cycle when the refrigeration cycle apparatus is applied to an air conditioner R.
  • a four-way switching valve 50 is connected to the refrigerant pipe P connected to the multi-cylinder rotary compressor M, and the four-way switching valve 50 is connected to the four-way switching valve 50 through an outdoor heat exchanger 51, an expansion device 52, and an indoor heat exchanger 53. Connected to the switching valve 50. Further, the four-way switching valve 50 is connected to the accumulator 25, and the accumulator 25 and the multi-cylinder rotary compressor M are communicated with each other through the suction refrigerant pipe PP as described above.
  • the gas refrigerant compressed by the multi-cylinder rotary compressor M and discharged to the refrigerant pipe P as will be described later is indicated by a solid line arrow from the four-way switching valve 50. Then, it is led to the outdoor heat exchanger 51, exchanges heat with the outside air, condenses, and turns into liquid refrigerant. That is, the outdoor heat exchanger 51 functions as a condenser.
  • the liquid refrigerant led out from the outdoor heat exchanger 51 is guided to the expansion device 52 and adiabatically expands. Then, it is guided to the indoor heat exchanger 53 and evaporates by exchanging heat with the indoor air blown here, and takes away the latent heat of evaporation from the indoor air to perform an indoor cooling action. That is, the indoor heat exchanger 53 becomes an evaporator.
  • the evaporative refrigerant derived from the indoor heat exchanger 53 is sucked into the multi-cylinder rotary compressor M through the four-way switching valve 50, compressed as described above, and circulated through the refrigeration cycle.
  • the four-way switching valve 50 When the heating operation is selected, the four-way switching valve 50 is switched, and the gas refrigerant discharged from the multi-cylinder rotary compressor M to the refrigerant pipe P passes through the four-way switching valve 50 and the indoor heat exchanger 53 as indicated by a broken line arrow.
  • the heat is exchanged with room air to condense.
  • the indoor air absorbs the heat of condensation of the indoor heat exchanger 53 serving as a condenser, so that the temperature rises and an indoor heating action is obtained.
  • the liquid refrigerant led out from the indoor heat exchanger 53 is led to the expansion device 52, adiabatically expands and led to the outdoor heat exchanger 51 to evaporate.
  • the evaporative refrigerant derived from the outdoor heat exchanger 51 which is an evaporator, is sucked into the multi-cylinder rotary compressor M from the four-way switching valve 50, compressed as described above, and circulated through the refrigeration cycle.
  • blade back chamber 11b will be in a communication state.
  • an operation signal is sent to the motor unit 4 and the rotary shaft 5 is driven to rotate.
  • the first and second rollers 9a and 9b move eccentrically in the cylinder chambers Sa and Sb.
  • the first blade 12a is pressed and urged by the spring member 13, and the tip end portion slidably contacts the peripheral wall of the roller 9a to bisect the inside of the first cylinder chamber Sa.
  • the low-pressure refrigerant gas evaporated in the indoor heat exchanger 53 is guided from the accumulator 25 to the refrigerant pipe PP on the suction side, and is guided to the two branch guide paths provided in the intermediate partition plate 2 of the multi-cylinder rotary compressor M. The Then, the air is sucked into the first cylinder chamber Sa and the second cylinder chamber Sb from the respective branch guide paths.
  • the low-pressure gas refrigerant filling the second blade back chamber 11b applies a low-pressure back pressure to the rear end portion of the second blade 12b.
  • the tip of the second blade 12b facing the second cylinder chamber Sb is in a low pressure atmosphere, and the rear end of the second blade 12b facing the second blade back chamber 11b is also in a low pressure atmosphere. No differential pressure is generated between the front and rear ends of 12b.
  • the tip of the second blade 12b does not protrude into the cylinder chamber Sb and maintains its position.
  • the second roller 9b fitted to the eccentric portion 5b of the rotary shaft 5 continues to idle, and no compression action is performed in the second cylinder chamber Sb. That is, in the second cylinder chamber Sb, a cylinder resting operation state is set.
  • the first blade 12 a receives the elastic force of the spring member 13.
  • the tip of the blade 12a abuts on the peripheral wall of the first roller 9a, and divides the first cylinder chamber Sa into two chambers, a compression chamber and a suction chamber.
  • the roller 9a moves eccentrically, the volume on the compression chamber side decreases, and the sucked gas is gradually compressed to increase the pressure.
  • the discharge valve mechanism When the pressure is increased to a predetermined pressure, the discharge valve mechanism is opened and the high pressure gas is discharged to the discharge mufflers 8a and 8b. Further, it is guided into the sealed case 1 and fills here.
  • the filled high-pressure gas refrigerant in the hermetic case 1 is discharged to the refrigerant pipe P, constitutes a refrigeration cycle as described above, and performs an indoor cooling action.
  • the valve element 31 of the pressure switching valve 27 When the full capacity operation is selected, the valve element 31 of the pressure switching valve 27 is switched to the position indicated by the solid line in FIG. 1, and the first port pa and the second port pb communicate with each other. Therefore, the refrigerant pipe P on the discharge side connected to the sealed case 1, the first branch pipe 28, the pressure switching valve 27, the pressure control pipe 19, the back pressure introduction passage 20 of the closing member 18, and the second The blade back chamber 11b is communicated.
  • the low-pressure gas refrigerant evaporated in the indoor heat exchanger 53 is led from the accumulator 25 to the suction side refrigerant pipe PP, and is sucked into the first cylinder chamber Sa and the second cylinder chamber Sb via the branch guide path.
  • the gas refrigerant whose pressure has been increased by the compression action as described above is filled in the sealed case 1.
  • the gas refrigerant is guided from the sealed case 1 to the refrigerant pipe P on the discharge side and circulates in the refrigeration cycle described above.
  • a part of the gas refrigerant is diverted from the refrigerant pipe P to the first branch pipe 28 and introduced into the second blade back chamber 11b from the pressure switching valve 27, the pressure control pipe 19, and the back pressure introduction passage 20 of the closing member 18. Is done.
  • the high pressure gas refrigerant guided to the second blade back chamber 11b causes the rear end portion of the second blade 12b to receive a high pressure.
  • the front end of the second blade 12b faces the second cylinder chamber Sb and is in a low pressure atmosphere, a differential pressure is generated between the front end and the rear end. Therefore, the second blade 12 b magnetically attracted to the permanent magnet 17 is easily separated from the permanent magnet 17.
  • the second blade 12b receives a high back pressure and is urged toward the tip.
  • the blade blade 10b reciprocates in the blade groove 10b while the tip of the second blade 12b is in contact with the peripheral surface of the second roller 9b.
  • the second blade 12b bisects the second cylinder chamber Sb into a compression chamber and a suction chamber, and a compression action is performed. Accordingly, the first cylinder chamber Sa and the second cylinder chamber Sb are simultaneously compressed and the full capacity operation is performed.
  • the rear end portion of the second blade 12b is magnetically attracted to the permanent magnet 17 attached to the second blade back chamber 11b via the holding member 16, and is in close contact with the holding member 16. .
  • the rear end of the second blade 12b reciprocates in the second blade back chamber 11b and moves to a position where there is a slight gap from the holding member 16.
  • the outer opening corner portion ha of the recess Wh constituting the back pressure introduction passage 20 is located on the outer peripheral side with respect to the lower end surface corner portion bb of the rear end portion of the second blade 12b located in the cylinder resting operation state. Configured to do.
  • the thickness dimension of the second cylinder 6B in which the blade groove 10b and the blade back chamber 11b are provided with respect to the height direction dimension of the second blade 12b. Is formed slightly larger, and a clearance is secured from the second blade 12b.
  • a multi-cylinder rotary type that is free from noise generation, can maintain a quiet operation, and can prevent the movement of the second blade 12b from being locked while the second blade 12b is tilted, thereby improving the compression reliability.
  • a compressor M can be provided.
  • the outer opening corner 21a which is a part of the opening in the first buffer recess space 21 is more peripheral than the upper end corner bc of the second blade 12b positioned in the cylinder resting state. Configured to be located on the side.
  • the second blade 12b may reciprocate while being tilted, or may be magnetically attracted to the permanent magnet 17 via the holding member 16 while being tilted.
  • the generation of noise due to mutual contact can be prevented, the movement of the second blade 12b can be prevented from being locked, and the compression reliability can be improved.
  • a first buffer recess space 21 communicating with the second blade back chamber 11b is provided in the intermediate partition plate 2 which is the upper side of the second blade back chamber 11b.
  • a second buffer recess space 22 communicating with the back pressure introduction passage 20 is provided across the closing member 18 on the upper side of the back pressure introduction passage 20 and the second cylinder 6B.
  • any of the buffer recess spaces 21 and 22 high-pressure and low-pressure gases that have been led to the second blade back chamber 11 b or that have been led to accumulate without any escape, and remain as they are.
  • a low-pressure gas refrigerant is guided to the pressure control pipe 19 and the back pressure introduction passage 20 to fill the second blade back chamber 11b and apply a low pressure back pressure to the second blade 12b.
  • the sealed case 1 is filled with compressed high pressure gas and is in a high pressure state. Therefore, the lubricating oil collected in the oil reservoir 14 is also affected and becomes high pressure.
  • the rotary shaft 5 is provided with a lubricating oil supply path for guiding the lubricating oil in the oil reservoir 14 to each sliding portion of the compression mechanism 3.
  • the lubricating oil affected by the high pressure of the oil reservoir 14 enters the back pressure introduction passage 20 through the clearance as well as the lubricating oil supply passage, and further enters the second blade back chamber 11b. There is a possibility that the pressure control pipe 19 will rise.
  • full capacity operation may be started under conditions where the outside air is extremely cold.
  • the high-pressure gas refrigerant is guided from the pressure switching valve 27 to the second blade back chamber 11 b through the pressure control pipe 19 and the back pressure introduction passage 20.
  • the gas refrigerant is condensed and changed into a liquid refrigerant. That is, the non-compressed fluid is the same as the lubricating oil described above, and this may fill the second blade back chamber 11b, the back pressure introduction passage 20, and the pressure control pipe 19.
  • the pressure control pipe 19, the back pressure introduction passage 20 and the second blade back chamber 11b are filled with the non-compressed fluid, but due to the influence of heat generated by the action of the compression mechanism section 3, Gas content evaporates from the incompressible fluid.
  • first buffer recess space 21 is opened with respect to the second blade back chamber 11b, and gas is accumulated.
  • the second buffer recess space 22 is also open to the back pressure introduction passage 20, and gas is accumulated there.
  • a cushioning effect that reduces the pressure pulsation caused by the reciprocating motion of the second blade 12b is obtained by the gas accumulated in the buffer recess spaces 21 and 22. Excessive force can be prevented from acting on the rear end portion of the second blade 12b, vibration and noise can be reduced, pipe rupture can be prevented, and reliability can be improved.
  • the internal volume of the first buffer recess space 21 and the second buffer recess space 22 is determined from the bottom dead center where the second blade 12b protrudes most into the second cylinder chamber Sb.
  • the effect described above can be further increased by setting the amount to be greater than or equal to the amount of displacement when moving from Sb to the most retreating top dead center.
  • the first partition recess space 21 is provided in the intermediate partition plate 2 and the recess member Wh constituting the back pressure introduction passage 20 is provided in the closing member 18, but at least a part of the holding member 16 or the permanent magnet 17. However, it provided so that it might not oppose the said recessed part Wh and the 1st recessed part space 21 for buffers.
  • the second blade back chamber 11b can be reliably incorporated without shifting in the vertical direction. Even during the compression operation, the permanent magnet 17 and the holding member 16 do not fall out of the second blade back chamber 11b, and the multi-cylinder rotary compressor M with high manufacturability and reliability can be obtained.
  • the gas refrigerant guided from the accumulator 25 through the refrigerant pipe PP on the suction side is branched in the intermediate partition plate 2 to be divided into the first cylinder chamber Sa and the second cylinder chamber.
  • Sb the structure led to Sb, it is not limited to this.
  • two suction refrigerant pipes may be extended from the accumulator 25 so as to directly communicate with the first cylinder chamber Sa and the second cylinder chamber Sb.
  • the second cylinder chamber Sb is configured to be in a cylinderless operation state, it may be changed to a configuration in which the first cylinder chamber Sa is set to a cylinderless operation state.
  • the excluded volumes of the first cylinder chamber Sa and the second cylinder chamber Sb are different, it is needless to say that the same effect can be obtained.
  • the closing member 18 provided with the back pressure introduction passage 20 is provided along the outer peripheral end of the auxiliary bearing 7B, the flange portion of the auxiliary bearing 7B is enlarged to close the second blade back chamber 11b, and directly Alternatively, the back pressure introduction passage 20 may be provided to eliminate the need for the closing member 18. Therefore, the part where the back pressure introduction passage 20 is provided is called a “bearing side member”.
  • a first buffer recess space 21 that opens to the second blade back chamber 11b is provided in the intermediate partition plate 2, and the second buffer use that opens to the back pressure introduction passage 20 in the closing member 18 that is a bearing side member.
  • the recessed space 22 is provided, the present invention is not limited to this, and only one of the first buffer recessed space 21 and the second buffer recessed space 22 may be provided.
  • FIG. 6 is a schematic longitudinal sectional view of a multi-cylinder rotary compressor N according to the second embodiment.
  • reference numeral 101 denotes a sealed case.
  • a compression mechanism 103 is provided in the lower part of the sealed case 101, and an electric motor part 104 is provided in the upper part.
  • the electric motor unit 104 and the compression mechanism unit 103 are integrally connected via a rotating shaft 105.
  • the compression mechanism 103 includes a first cylinder 106A on the upper side and a second cylinder 106B on the lower side.
  • the main bearing 107A is attached and fixed to the upper end surface of the first cylinder 106A
  • the auxiliary bearing 107B is attached and fixed to the lower end surface of the second cylinder 106B.
  • An intermediate partition plate 102 is interposed between the first cylinder 106A and the second cylinder 106B.
  • the rotation shaft 105 penetrates through the cylinders 106A and 106B, and integrally includes a first eccentric portion 105a and a second eccentric portion 105b having the same diameter and a phase difference of about 180 °.
  • Each eccentric part 105a, 105b is assembled so that it may be located in the internal diameter part of cylinder 106A, 106B.
  • the first roller 109a is fitted to the circumferential surface of the first eccentric portion 105a
  • the second roller 109b is fitted to the circumferential surface of the second eccentric portion 105b.
  • the inner diameter portion of the first cylinder 106A is closed by the main bearing 107A and the intermediate partition plate 102 to form a first cylinder chamber Za.
  • the inner diameter portion of the second cylinder 106B is closed by the intermediate partition plate 102 and the auxiliary bearing 107B, thereby forming a second cylinder chamber Zb.
  • the first cylinder chamber Za and the second cylinder chamber Zb are designed to have the same diameter and height.
  • Each of the peripheral walls of the first and second rollers 109a and 109b can be moved eccentrically while being in line contact with the peripheral walls of the first and second cylinder chambers Za and Zb via a lubricating oil film, respectively.
  • the rollers 109a and 109b are accommodated in the cylinder chambers Za and Zb.
  • the discharge muffler 108a that is doubled is attached to the main bearing 107A and covers the discharge valve mechanism provided on the main bearing 107A. Each discharge muffler 108a is provided with a discharge hole. A single discharge muffler 108b is attached to the auxiliary bearing 107B and covers a discharge valve mechanism provided in the auxiliary bearing 107B. The discharge muffler 108b is not provided with a discharge hole.
  • the discharge valve mechanism of the main bearing 107A is opposed to the first cylinder chamber Za and is opened when the chamber rises to a predetermined pressure due to the compression action, and discharges compressed gas into the discharge muffler 108a.
  • the discharge valve mechanism of the sub-bearing 7B faces the second cylinder chamber Zb, opens when the chamber pressure rises to a predetermined pressure due to the compression action, and discharges the compressed gas into the discharge muffler 108b.
  • a discharge gas guide path is provided across the auxiliary bearing 107B, the second cylinder 106B, the intermediate partition plate 102, the first cylinder 106A, and the main bearing 107A.
  • the discharge gas guide path guides the high-pressure gas discharged from the second cylinder chamber Zb to the lower discharge muffler 108b through the discharge valve mechanism into the upper double discharge muffler 108a.
  • an oil reservoir 114 for collecting lubricating oil is formed at the inner bottom of the sealed case 101, and almost all of the compression mechanism 103 is immersed in the lubricating oil in the oil reservoir 114.
  • An oil supply passage for supplying the lubricating oil of the oil reservoir 114 is provided across the lower end surface of the rotating shaft 105 and the sliding portions of the compression mechanism 103.
  • FIG. 2 is an exploded perspective view showing a part of the compression mechanism 103 according to the embodiment, schematically showing only the main part, and omitting the details.
  • a blade groove 110a is connected to a first cylinder chamber Za that is an inner diameter portion, and a first blade back chamber 111a is further provided from the blade groove 110a.
  • a first blade 112a is movably accommodated in the blade groove 110a, and its front end can protrude into the first cylinder chamber Za, and the rear end can protrude into the first blade back chamber 111a.
  • a blade groove 110b is connected to a second cylinder chamber Zb which is an inner diameter portion, and a second blade back chamber 111b is further provided from the blade groove 110b.
  • a second blade 112b is movably accommodated in the blade groove 110b, and its front end can project into and out of the second cylinder chamber Zb, and its rear end can project into and out of the second blade back chamber 111b.
  • the tip portions of the first and second blades 112a and 112b are formed in a substantially arc shape in plan view, and these tip portions protrude into the opposing first and second cylinder chambers Za and Zb.
  • the first and second rollers 109a and 109b shown in FIG. 6 which are circular in plan view are in line contact with the peripheral walls of the first and second rollers 109a and 109b regardless of their rotation angles.
  • the first cylinder 106A is provided with a lateral hole Wf that communicates the first blade back chamber 111a and the outer peripheral surface of the cylinder 106A, and a spring member (elastic member) 113 is accommodated therein.
  • the spring member 113 is interposed between the rear end face of the first blade 112a and the inner peripheral wall of the sealing case 101, and applies an elastic force (back pressure) to the first blade 112a.
  • the differential pressure between the front end and the rear end is influenced by the pressure of the second cylinder chamber Zb and the rear end is affected by the pressure of the second blade back chamber 111b.
  • the back pressure is applied or not applied.
  • a permanent magnet 115 is attached to the rear peripheral wall of the second blade back chamber 111b. This magnetic force is such that the rear end portion of the blade 112b can be magnetically attracted when the rear end portion of the second blade 112b comes into contact with the permanent magnet 115 or moves very close. If a certain amount of high pressure is applied, the second blade 112 b is easily detached from the permanent magnet 115.
  • the upper surface opening of the second blade back chamber 111b is closed by the intermediate partition plate 102 attached to the upper end surface of the second cylinder 106B.
  • the lower surface opening of the second blade back chamber 111b is provided at a position protruding outward from the peripheral end surface of the flange portion of the auxiliary bearing 107B, and the lower surface opening opens into the sealed case 101 as it is.
  • the lower surface opening of the second blade back chamber 111b is located along a part of the outer peripheral wall of the flange portion of the auxiliary bearing 107B, and is closed by a closing member 118 that is attached to the second cylinder 106B via the attachment bolt 116. Is done.
  • the upper and lower surfaces of the second blade back chamber 111b are closed by the intermediate partition plate 102 and the closing member 118, and the second blade back chamber 111b forms a sealed structure.
  • the closing member 118 is made of cast iron, or is made of SMF type 3 (iron-carbon based sintered alloy) or SMF type 4 (iron-carbon-copper based sintered alloy). That is, in order to manufacture the closing member 118, a material that can reliably manufacture a complicated internal structure by molding is selected.
  • FIG. 7 is an enlarged view of the closing member 118 portion which is a Y portion shown in FIG. 6, and FIG. 8 is a longitudinal sectional view taken along the line TT shown in FIG.
  • FIGS. 6, 7, and 8 the main part of the compression mechanism 103 will be described with reference to FIGS. 6, 7, and 8.
  • a part of the upper surface of the closing member 118 facing the second blade back chamber 111b is opened. As shown in FIG. 8, the opening is a recess 119 provided up to the vicinity of the lower surface of the closing member 118. .
  • a hole 120a is provided from one side surface of the closing member 118, and the tip of the hole 120a is a semicircular portion 120b formed in a semicircular cutout in a part of the bottom surface of the recess 119.
  • a hole portion is also provided in the sealed case 101 portion facing the hole portion 120a of the closing member 118, and a pressure control pipe F1 constituting a back pressure introduction passage H described later is inserted into the hole portion 120a. A seal is applied.
  • the distal end portion of the pressure control pipe F ⁇ b> 1 extending from the hermetic case 1 to the inside thereof is inserted into and connected to the hole 120 a of the closing member 118.
  • the communication path 122 is also a lubricating oil communication path that connects the second blade back chamber 111b and the oil reservoir 114 formed at the bottom of the inside of the sealed case 101. Further, the communication path 122 is opened and closed by a check valve mechanism G attached to the lower surface of the closing member 118.
  • the check valve mechanism G has a valve hole 123 that opens to the lower surface of the closing member 118 at the lower end of the communication passage 122, communicates with the communication passage 122, and a valve seat that is formed along the periphery of the valve hole 123. 124, and a valve body 125 that contacts and separates from the valve seat 124 to open and close the valve hole 123.
  • the valve body 125 is of a reed valve type in which one end is attached and fixed to the lower surface of the closing member 118 via a mounting bolt 127, and the other end faces the valve hole 123 and is a free end.
  • the width dimension of the valve body 125 is slightly larger than the diameter of the valve hole 123, and the valve body 125 is deformed according to the pressure that the other end of the valve body 125 receives from the communication path 122 through the valve hole 123. Or do not deform.
  • a valve presser 126 formed in a curved shape on the lower surface of the valve body 125 is attached together with the valve body 125 by a mounting bolt 127, and the valve body 125 is curved and deformed in accordance with the curved shape of the valve presser 126.
  • the strength of the valve presser 126 is greater than that of the valve body 125, and the maximum bending amount of the valve body 125 can be regulated. That is, the valve body 125 is a reed valve type in which the maximum opening amount is regulated by the valve presser 126.
  • the “valve body” is referred to as a “reed valve”.
  • FIG. 8 shows a state where the reed valve 125 is curved to the maximum and the valve hole 123 is opened.
  • the flow path area A1 between the reed valve 125 and the valve seat 124 indicated by hatching in the figure is expressed by the product of ⁇ , the inner diameter ⁇ Dv of the valve seat 124, and the average distance L between the valve seat 124 and the reed valve 125. Is done.
  • the inner peripheral area A2 of the valve seat 124 is represented by ⁇ ⁇ (Dv / 2) 2 . Since the flow path area A1 between the reed valve 125 and the valve seat 124 is smaller than the inner peripheral area A2 of the valve seat 124 (A1 ⁇ A2), ⁇ ⁇ ⁇ Dv ⁇ L ⁇ ⁇ (Dv / 2) 2 It becomes.
  • the pressure control pipe F1 which is the back pressure introduction passage H constitutes a part of the blade back pressure control mechanism C.
  • This blade back pressure control mechanism C selects and guides the high pressure gas (discharge pressure) or low pressure gas (suction pressure) to the second blade back chamber 111b, and the pressure of the back pressure on the rear end portion of the second blade 112b. It controls switching.
  • a discharge refrigerant pipe F is connected to the upper end of the sealed case 101 constituting the multi-cylinder rotary compressor N.
  • the refrigerant pipe F is sequentially connected to devices constituting the heat pump refrigeration cycle, and is connected to an upper end portion of an accumulator 132 that is attached and fixed to the sealed case 101 via a fixture 131.
  • the lower end of the accumulator 132 and the sealed case 101 are connected via a refrigerant pipe Fa for suction.
  • the refrigerant pipe Fa passes through the sealed case 101 and is connected to the peripheral end surface of the intermediate partition plate 102.
  • the intermediate partition plate 102 is provided with a branch guide path (not shown) that branches into a bifurcated shape from the peripheral surface portion to which the refrigerant pipe Fa is connected in the axial direction.
  • One branch guide path communicates with the first cylinder chamber Za, and the other branch guide path communicates with the second cylinder chamber Zb. Therefore, the accumulator 132 and the first cylinder chamber Za and the second cylinder chamber Zb in the multi-cylinder rotary compressor N are always in communication.
  • the pressure control pipe F1 extends to a position above the upper ends of the sealed case 101 and the accumulator 132, and a pressure switching valve 133 described later is provided at this end.
  • the pressure switching valve 133 uses a four-way switching valve used in an air conditioner equipped with a heat pump refrigeration cycle capable of switching between cooling and heating operations to reduce costs.
  • a first branch pipe (high pressure pipe) 135 is branched from the refrigerant pipe F connected to the upper end portion of the sealed case 101, and this is connected to the first port fa of the pressure switching valve 133.
  • a pressure control pipe F1 is connected to the second port fb, and a second branch pipe (low pressure pipe) 136 branched from the refrigerant pipe F on the refrigerant introduction side of the accumulator 132 is connected to the third port fc.
  • the fourth port fd is always closed by the plug 137.
  • the inverted U-shaped valve 138 accommodated therein includes a position where the third port fc and the fourth port fd communicate with each other as shown in the figure, and a position where the second port fb and the fourth port fd communicate with each other as indicated by a two-dot chain line. 3 is electromagnetically switched to a position communicating with the port fc.
  • the first port fa is always open, and the fourth port fd is always closed.
  • the first port fa and the second port fb communicate directly, and the third port fc and the fourth port fd communicate via the inverted U-shaped valve 138. .
  • the fourth port fd is blocked by the plug 137, only communication between the first port fa and the second port fb remains.
  • the second port fb and the third port fc communicate with each other via the inverted U-shaped valve 138, and the first port fa And the fourth port fd communicate directly.
  • the fourth port fd is closed by the plug 137, only the communication between the second port fb and the third port fc remains.
  • the pressure switching valve 133 a four-way switching valve, which is a standard product used in a refrigeration cycle constituting a normal heat pump air conditioner, is used, but a three-way valve is used instead of the four-way switching valve, or a plurality of switching valves are used. The same effect can be obtained by combining the on-off valves.
  • the blade back pressure control mechanism C includes the pressure switching valve 133, the pressure control pipe F1, the first branch pipe 135 and the second branch pipe 136, and the back pressure introduction passage H provided in the closing member 118.
  • the high pressure and the low pressure can be switched and guided to the second blade back chamber 111b, and the back pressure can be applied to the second blade 112b.
  • FIG. 5 is a configuration diagram of a heat pump refrigeration cycle when the refrigeration cycle apparatus is applied to an air conditioner R.
  • the blade back pressure control mechanism C described above is omitted.
  • a four-way switching valve 150 is connected to the refrigerant pipe F connected to the multi-cylinder rotary compressor N, and the four-way switching valve 150 is connected to the outdoor heat exchanger 151, the expansion device 152, and the indoor heat exchanger 153.
  • the indoor heat exchanger 153 is connected to the accumulator 132 via the four-way switching valve 150, and is further connected to the multi-cylinder rotary compressor N and the suction refrigerant pipe Fa, but is not shown here.
  • the gas refrigerant compressed by the multi-cylinder rotary compressor N and discharged to the refrigerant pipe F as will be described later is indicated by the solid arrow from the four-way switching valve 150. Then, it is guided to the outdoor heat exchanger 151 and is condensed by exchanging heat with the outside air to be converted into a liquid refrigerant. That is, the outdoor heat exchanger 151 acts as a condenser.
  • the liquid refrigerant led out from the outdoor heat exchanger 151 is led to the expansion device 152 and adiabatically expands. Then, it is guided to the indoor heat exchanger 153 to evaporate by exchanging heat with the indoor air and takes away the latent heat of vaporization from the indoor air to perform the indoor cooling action. That is, the indoor heat exchanger 153 is an evaporator.
  • the evaporative refrigerant derived from the indoor heat exchanger 153 is sucked into the multi-cylinder rotary compressor N through the four-way switching valve 150, compressed as described above, and circulated through the refrigeration cycle.
  • the four-way switching valve 150 When the heating operation is selected, the four-way switching valve 150 is switched, and the gas refrigerant discharged from the multi-cylinder rotary compressor N to the refrigerant pipe F passes through the four-way switching valve 150 and the indoor heat exchanger 153 as indicated by a broken line arrow. The heat is exchanged with room air to condense. The indoor air absorbs the heat of condensation of the indoor heat exchanger 153 serving as a condenser, so that the temperature rises and an indoor heating action is obtained.
  • the liquid refrigerant led out from the indoor heat exchanger 153 is led to the expansion device 152, adiabatically expands, is led to the outdoor heat exchanger 151, and evaporates.
  • the evaporative refrigerant derived from the outdoor heat exchanger 151 as an evaporator is sucked into the multi-cylinder rotary compressor N from the four-way switching valve 150, compressed as described above, and circulated through the refrigeration cycle.
  • switching between a half capacity operation (cylinder operation) and a full capacity operation (normal operation) can be selected.
  • the above-described refrigeration cycle during the cooling operation is configured, and the inverted U-shaped valve 138 housed in the pressure switching valve 133 of the blade back pressure control mechanism C is switched.
  • the pressure switching valve 133 is controlled so that the second port fb and the third port fc communicate with each other as shown by a two-dot chain line in FIG.
  • a refrigerant pipe F communicating with the accumulator 132 from the indoor heat exchanger 153, a second branch pipe 136, a pressure switching valve 133, a pressure control pipe F1, a back pressure introduction passage H, and a second blade back chamber 111b are provided. It becomes a communication state.
  • an operation signal is sent to the motor unit 104, and the rotary shaft 105 is driven to rotate.
  • the first and second rollers 109a and 109b move eccentrically in the cylinder chambers Za and Zb.
  • the first blade 112a is pressed and urged by the spring member 113, and the tip end part slidably contacts the peripheral wall of the roller 109a to bisect the inside of the first cylinder chamber Za.
  • the low-pressure refrigerant gas evaporated in the indoor heat exchanger 153 is led from the accumulator 132 to the refrigerant pipe Fa on the suction side, and is guided to the two branch guide paths provided in the intermediate partition plate 102 of the multi-cylinder rotary compressor N. The Then, the air is sucked into the first cylinder chamber Za and the second cylinder chamber Zb from the respective branch guide paths.
  • the low-pressure gas refrigerant that fills the second blade back chamber 111b applies a low-pressure back pressure to the rear end portion of the second blade 112b.
  • the tip of the second blade 112b facing the second cylinder chamber Zb is in a low pressure atmosphere, and the rear end of the second blade 112b facing the second blade back chamber 111b is also in a low pressure atmosphere. No differential pressure is generated between the front end portion and the rear end portion of 112b.
  • the tip of the second blade 112b is kicked by the roller 109b and moves backward.
  • the rear end portion of the second blade 112b is in contact with or close to the permanent magnet 115 attached to the second blade back chamber 111b, and the second blade 112b is magnetically attracted to the permanent magnet 115.
  • the tip of the second blade 112b does not protrude into the second cylinder chamber Zb and maintains its position.
  • the second roller 109b fitted to the eccentric portion 105b of the rotating shaft 105 continues to idle, and no compression action is performed in the second cylinder chamber Zb. That is, in the second cylinder chamber Zb, a cylinder resting operation state is set.
  • the first blade 112a receives the elastic force of the spring member 113.
  • the tip of the blade 112a abuts on the peripheral wall of the first roller 109a, and divides the first cylinder chamber Za into two chambers, a compression chamber and a suction chamber.
  • the roller 109a moves eccentrically, the volume on the compression chamber side decreases, and the sucked gas is gradually compressed to increase the pressure.
  • the discharge valve mechanism When the pressure is increased to a predetermined pressure, the discharge valve mechanism is opened and the high pressure gas is discharged to the discharge mufflers 108a and 108b. Further, it is led into the sealed case 101 and fills here.
  • the high-pressure gas refrigerant filled in the sealed case 101 is discharged to the refrigerant pipe F, and constitutes the refrigeration cycle as described above to perform an indoor cooling function.
  • the cylinder idle operation state where the compression action is not performed in the second cylinder chamber Zb is supported, and the compression operation is performed only in the first cylinder chamber Za.
  • the inside of the sealed case 101 is filled with the high-pressure gas compressed in the first cylinder chamber Za and is in a high-pressure atmosphere.
  • the lubricating oil in the oil reservoir 114 formed at the inner bottom of the sealed case 101 is also in a high pressure state, and the reed valve 125 constituting the check valve mechanism G receives high pressure from the lower surface side.
  • a low-pressure gas refrigerant is guided to a back pressure introduction passage H formed on the upper surface side of the reed valve 125.
  • the reed valve 125 is formed in a straight shape under the influence of high pressure, and one end thereof contacts the valve seat 124 and closes the valve hole 123.
  • the flow path area A1 between the reed valve 125 and the valve seat 124, which is a hatched portion in FIG. 8, does not exist, and the communication path 122 is completely closed.
  • the lubricating oil in the oil reservoir 114 does not flow into the back pressure introduction passage H and the second blade back chamber 111b through the communication passage 122.
  • a low-pressure gas refrigerant is guided to the pressure control pipe F1 and the back pressure introduction passage H, fills the second blade back chamber 111b, and applies a low pressure back pressure to the second blade 112b.
  • the sealed case 101 is filled with compressed high pressure gas and is in a high pressure state, and the lubricating oil collected in the oil reservoir 114 is also affected by the high pressure.
  • the rotating shaft 105 is provided with a lubricating oil supply path that guides the lubricating oil in the oil reservoir 114 to each sliding portion of the compression mechanism 103, and the lubricating oil affected by the high pressure in the oil reservoir 114 is guided. Since the check valve mechanism G acts to close the valve hole 123 and the communication path 122, the lubricating oil in the oil reservoir 114 is guided to the second blade back chamber 111b through the clearance, and the second blade 112b. Ensure lubricity.
  • the U-shaped valve 138 of the pressure switching valve 133 is switched to the solid line position in FIG. 6, and the first port fa and the second port fb communicate with each other. Accordingly, the discharge side refrigerant pipe F connected to the sealed case 101, the first branch pipe 135, the pressure switching valve 133, the pressure control pipe F1, the back pressure introduction passage H of the closing member 118, and the second The blade back chamber 111b communicates.
  • the low-pressure gas refrigerant evaporated in the indoor heat exchanger 153 is guided from the accumulator 132 to the refrigerant pipe Fa on the suction side, and is sucked into the first cylinder chamber Za and the second cylinder chamber Zb through the branch guide path.
  • the gas refrigerant whose pressure has been increased due to the compression action is filled in the sealed case 101.
  • the high-pressure gas refrigerant is guided from the sealed case 1 to the refrigerant pipe F on the discharge side and circulates in the above-described refrigeration cycle.
  • a part of the high-pressure gas refrigerant is diverted from the refrigerant pipe F to the first branch pipe 135, and the pressure switching valve 133, the pressure control pipe F1, and the back pressure introduction passage H of the closing member 118 to the second blade back chamber 111b. be introduced.
  • the rear end portion of the second blade 112b receives a high back pressure.
  • the front end portion of the second blade 112b faces the second cylinder chamber Zb and is in a low pressure atmosphere. Differential pressure is generated at the end. Therefore, the second blade 112 b that has been magnetically attracted by the permanent magnet 115 until then is easily separated from the permanent magnet 115 and is pressed and urged toward the tip end side.
  • the blade groove 110b reciprocates while the tip of the second blade 112b is in contact with the peripheral surface of the second roller 109b.
  • the second blade 112b bisects the second cylinder chamber Zb into a compression chamber and a suction chamber, and a compression action is performed.
  • the first cylinder chamber Za and the second cylinder chamber Zb simultaneously perform the compression action and the full capacity operation is performed.
  • the lubricating oil in the oil reservoir 114 is also affected by the high-pressure by the gas refrigerant filling the sealed case 101.
  • the reed valve 125 that has closed the valve hole 123 during the half-capacity operation is changed to the same high-pressure atmosphere at the upper and lower parts, so it should maintain the straight shape that is the same posture as during the half-capacity operation. is there.
  • the second blade 112b moves in the direction of expanding the volume of the second blade back chamber 111b on the second cylinder chamber Zb side (forward movement).
  • the volume of the second blade back chamber 111b is moved (returned) in the direction of reducing the volume.
  • the second blade back chamber 111b becomes negative pressure when the second blade 112b moves in the direction of enlarging the volume of the blade back chamber 111b, and the high pressure gas in the back pressure introduction passage H and the communication passage 122 is transferred to the blade back chamber. It is sucked into 111b. As a result, the reed valve 125 also moves toward the blade back chamber 111b and closes the valve hole 123.
  • the high pressure gas that has been positively sucked into the blade back chamber 111b is transferred to the back pressure introduction passage H and the communication passage 122. Extruded.
  • the reed valve 125 is separated from the valve seat 124 and opens the valve hole 123.
  • the reed valve 125 opens and closes the valve hole 123 as the blade 112b reciprocates.
  • the low pressure gas refrigerant is guided to the pressure control pipe F1 and the back pressure introduction passage H to fill the second blade back chamber 111b.
  • the compressed high-pressure gas is filled in the sealed case 101 and is in a high-pressure state, and the lubricating oil collected in the oil reservoir 114 is also affected by the high pressure.
  • Lubricating oil in the oil reservoir 114 enters the second blade back chamber 111b through the clearance, and further is guided to the back pressure introduction passage H over time, and rises in the pressure control pipe F1. If the half capacity operation is continued for a long time, the back pressure introduction passage H is likely to be filled with lubricating oil. Then, there is a case where the full-capacity operation is switched as it is.
  • full capacity operation may be started under conditions where the outside air is extremely cold.
  • the high-pressure gas refrigerant is led from the pressure switching valve 133 to the second blade back chamber 111b through the pressure control pipe F1 and the back pressure introduction passage H, and the gas refrigerant condenses and passes over time. It turns into a refrigerant.
  • both the lubricating oil and the liquid refrigerant described above are incompressible fluids, and these may fill the second blade back chamber 111b, the back pressure introduction passage H, and the pressure control pipe F1.
  • the gas component evaporates from the incompressible fluid due to the heat generated by the action of the compression mechanism 3, and only pure liquid remains.
  • the reciprocating motion of the second blade 112b is directly received by the incompressible fluid that is completely liquid in the second blade back chamber 111b, and there is almost no buffering effect. If the high rotation operation is performed as it is, the flow of the incompressible fluid cannot follow the reciprocating operation of the second blade 112b.
  • the rear end portion of the second blade 112b receives an excessive resistance force and lacks smooth operation.
  • Pressure pulsation which is a fluctuation in pressure energy of the incompressible fluid in the back pressure introduction passage H, becomes large, and there is a possibility that problems such as vibration, noise, and pipe rupture may occur.
  • the check valve mechanism G Opens the communication path 22.
  • the incompressible fluid filling the second blade back chamber 11 b and the back pressure introduction passage H is discharged to the oil reservoir 114.
  • the incompressible fluid in the back pressure introduction passage H and the pressure control pipe F1 is promptly transferred to the oil reservoir 114 in the sealed case 101. Discharged. Problems such as pressure pulsation as described above can be avoided, and a decrease in the oil level of the oil reservoir 114 can also be prevented.
  • the high pressure guided to the back pressure introduction passage H during full capacity operation is a high pressure gas refrigerant that is compressed by the compression mechanism 103 and discharged from the sealed case 101. Due to the pumping action of the second blade 112b and the check valve mechanism G, the high-pressure gas quickly discharges the incompressible fluid from the back pressure introduction passage H into the sealed case 101, and the abnormally high pressure in the second blade back chamber 111b. Is surely prevented.
  • the communication passage 122 provided in the closing member 118 is provided in the lower portion of the back pressure introduction passage H, and the valve hole 123 constituting the check valve mechanism G is provided in the lowermost portion of the communication passage 122.
  • the incompressible fluid filling the back pressure introduction passage H is a liquid and is affected by gravity, the incompressible fluid is smoothly discharged from the valve hole 123 into the sealed case 101.
  • the flow path area A1 between the reed valve 125 and the valve seat 124 is smaller than the inner peripheral area A2 of the valve seat 124. (A1 ⁇ A2). Due to the structure of the reed valve 125, when the flow path area between the reed valve 125 and the valve seat 124 is reduced when the reed valve 125 is fully opened, the flow resistance increases, and the flow rate passing through the valve hole 123 can be suppressed. On the other hand, the reed valve 125 opens with a smaller pressure difference when the inner peripheral area of the valve seat 124 is larger.
  • the reed can be reliably made with a small pressure difference.
  • the valve 125 can be opened and the flow rate passing through the valve hole 123 can be suppressed.
  • the incompressible fluid is quickly absorbed by the pump action of the second blade 112b and the check valve mechanism G.
  • the air is discharged from the communication passage 122 and the valve hole 123 into the sealed case 101.
  • the back pressure introduction passage H is filled with high pressure gas, and a back pressure is applied to the second blade 112b.
  • the check valve mechanism G operates and continues to open and close the communication passage 122 and the valve hole 123. For this reason, the high pressure gas filling the back pressure introduction passage H applies back pressure to the second blade 112 b and, at the same time, re-enters the sealed case 101 from the communication passage 122 and the valve hole 123.
  • the flow path area A1 between the reed valve 125 and the valve seat 124 is configured to be smaller than the inner peripheral area A2 of the valve seat 124 when the reed valve 125 is fully opened. Therefore, the reed valve 125 can be reliably opened with a small pressure difference, and the flow rate of the high-pressure gas that passes through the valve hole 123 and re-enters the sealed case 101 is reduced, so that loss can be reduced.
  • FIG. 9 is a longitudinal sectional view of a multi-cylinder rotary compressor Na in the third embodiment.
  • the same components as those in the multi-cylinder rotary compressor N described in the second embodiment are denoted by the same reference numerals, and a new description is omitted.
  • a discharge refrigerant pipe F is connected to an upper end portion of the sealed case 101, and a first branch pipe 135A constituting a part of the blade back pressure control mechanism C is branched from the refrigerant pipe F to switch the pressure. Connected to the first port fa of the valve 133.
  • the pipe diameter of a predetermined length from the part branched from the refrigerant pipe F is formed smaller than the pipe diameter of the part connected to the first port fa of the pressure switching valve 133. The difference is that the flow path resistance unit 140 is provided.
  • the pressure control pipe F1 and the back pressure introduction passage H are filled with high pressure gas.
  • the operating frequency of the compressor N increases and the flow rate of the high-pressure gas that is diverted from the refrigerant pipe F to the first branch pipe 135A increases.
  • the first branch pipe 135A is provided with a flow path resistance section 140 having a reduced pipe diameter with a predetermined length.
  • the flow path resistance unit 140 regulates the flow rate of the high pressure gas in place of the effective flow path resistance for the high pressure gas having an increased flow velocity. Therefore, the flow rate of the high-pressure gas that passes through the valve hole 123 and re-enters the sealed case 101 is reduced, so that loss can be reduced and high performance is obtained.
  • the full capacity operation is switched to the half capacity operation
  • the low pressure gas is switched from the pressure switching valve 133 to the pressure control pipe F1. Since the first branch pipe 135A is provided with the flow path resistance unit 140, since the high-pressure gas is led to the pressure switching valve 133 in the full capacity operation, the switching operation of the switching valve 133 is smooth. The operation can be switched quickly.
  • the channel cross-sectional area of the channel resistance unit 140 is E1
  • the channel area of the pipe portion other than the channel resistance unit 140 in the first branch pipe 135A is E2. It is a characteristic view of the efficiency with respect to the flow path area ratio between the first branch pipe 135A and the first branch pipe. From the figure, it can be seen that the range of 1/50 ⁇ E1 / E2 ⁇ 1/10 is the best.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2011/079491 2010-12-20 2011-12-20 多気筒回転式圧縮機及び冷凍サイクル装置 WO2012086637A1 (ja)

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JP2011-068818 2011-03-25
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CN108425847A (zh) * 2018-04-03 2018-08-21 上海新源动力有限公司 一种自动换向摆动气缸式气体循环泵

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CN103452842A (zh) * 2013-08-22 2013-12-18 广东美芝制冷设备有限公司 压缩机

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JP2008520901A (ja) * 2005-02-23 2008-06-19 エルジー エレクトロニクス インコーポレイティド 容量可変型ロータリ圧縮機及びこれを備える冷却システム
JP2009203861A (ja) * 2008-02-27 2009-09-10 Toshiba Carrier Corp 密閉型圧縮機および冷凍サイクル装置
JP2010163926A (ja) * 2009-01-14 2010-07-29 Toshiba Carrier Corp 多気筒回転式圧縮機および冷凍サイクル装置

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JP2010163927A (ja) * 2009-01-14 2010-07-29 Toshiba Carrier Corp 多気筒回転式圧縮機および冷凍サイクル装置
CN103189653B (zh) * 2010-12-24 2015-09-23 东芝开利株式会社 多汽缸旋转式压缩机及制冷循环装置

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JP2008520901A (ja) * 2005-02-23 2008-06-19 エルジー エレクトロニクス インコーポレイティド 容量可変型ロータリ圧縮機及びこれを備える冷却システム
JP2009203861A (ja) * 2008-02-27 2009-09-10 Toshiba Carrier Corp 密閉型圧縮機および冷凍サイクル装置
JP2010163926A (ja) * 2009-01-14 2010-07-29 Toshiba Carrier Corp 多気筒回転式圧縮機および冷凍サイクル装置

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CN108425847A (zh) * 2018-04-03 2018-08-21 上海新源动力有限公司 一种自动换向摆动气缸式气体循环泵
CN108425847B (zh) * 2018-04-03 2024-02-23 上海新源动力有限公司 一种自动换向摆动气缸式气体循环泵

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