WO2004088139A1 - 往復動型圧縮機 - Google Patents
往復動型圧縮機 Download PDFInfo
- Publication number
- WO2004088139A1 WO2004088139A1 PCT/JP2003/014565 JP0314565W WO2004088139A1 WO 2004088139 A1 WO2004088139 A1 WO 2004088139A1 JP 0314565 W JP0314565 W JP 0314565W WO 2004088139 A1 WO2004088139 A1 WO 2004088139A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- discharge
- cylinder
- passage
- cylinder block
- reciprocating compressor
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
- F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
Definitions
- the present invention relates to a reciprocating compressor suitable for compressing a working fluid such as a refrigerant gas, and more particularly to a structure excellent in reducing pulsation of discharge gas.
- a cylinder block having a plurality of cylinder bores, a piston reciprocating in the cylinder bore, and a front cylinder head fixed to one end of the cylinder block via a valve plate.
- a front-side compression chamber formed on the front-side cylinder head formed on the rear-side cylinder head fixed to the other end of the cylinder block via a valve plate, and a front-side cylinder head.
- a discharge port that communicates with one of the discharge passages to an external circuit, and other discharge passages other than the discharge passage that communicates with the discharge port communicate with the front-side discharge chamber and the rear-side discharge chamber;
- a discharge passage communicating with a discharge port is communicated via a guide passage (see Japanese Patent Application Laid-Open No. 11-117589).
- the refrigerant gas discharged into the compression chamber is sent from the discharge port to the external circuit via the discharge path, the guide path, and the discharge path communicating with the discharge port which are not connected to the discharge port.
- Drift in the discharge passage not communicating with the discharge port This has the advantage that pulsation can be reduced by effectively making these discharge passages function as mufflers.
- the working refrigerant discharged to the front discharge chamber and the rear discharge chamber in the discharge passage is discharged from the respective discharge refrigerants.
- the flow from the chamber to the discharge passage is in the opposite direction, and it collides and joins in the middle of the discharge passage, so that it is easy to pulsate in the first place. For this reason, in a compressor having such a characteristic discharge path, it is necessary to take measures to further reduce the pulsation of the working fluid that has joined in the discharge path.
- the present invention has been made in view of such circumstances, and has as its main object to reduce discharge pulsation caused by the above-described structure, and to reduce vibration and noise. It is another object of the present invention to provide a reciprocating compressor capable of reducing discharge pulsation and reducing oil outflow. Disclosure of the invention
- a reciprocating compressor includes a cylinder block having a plurality of cylinder bores, a piston that reciprocates in the cylinder bore, and a valve at one end of the cylinder block.
- a first cylinder head fixed via a plate, a second cylinder head fixed via a valve plate to the other end of the cylinder block, and a first cylinder head
- a first discharge chamber for introducing a working fluid discharged from a first compression chamber formed on one end side of the cylinder bore, and a first discharge chamber formed on the second cylinder head
- a second discharge chamber for introducing a working fluid discharged from a second compression chamber formed at the other end of the cylinder block; a plurality of discharge passages formed in the cylinder block;
- a discharge port provided in the cylinder head, the discharge port communicating one of the discharge passages to an external circuit, and the other of the first and second discharge passages other than the discharge passage communicating with the discharge port.
- a reciprocating compressor configured to communicate through a guideway to a discharge passage communicating with the discharge port, the discharge passage communicating with the discharge port, the discharge passage communicating with the discharge port, A communicating portion between the discharge passage and the first and second discharge chambers is communicated with at least one of the first and second discharge chambers through a restricting portion having a passage cross section smaller than that of the communicating portion. Is set to be equal to or less than an area corresponding to a circular section having a diameter of 1.5 mm.
- the working fluid discharged to the first discharge chamber and the second discharge chamber is guided from another discharge passage other than the discharge passage communicating with the discharge port. It is guided to a discharge passage communicating with the discharge port through the passage, and then is discharged from the discharge port to an external circuit.
- the discharge passage communicating with the discharge port is connected to the first discharge chamber through the throttle. Even if the pressure and the compressor are left for a long time and restarted, the working fluid discharged into the discharge chamber is communicated with the discharge port through the throttle part because the pressure and the compressor are left for a long time and restarted. Since the pressure is directly guided to the communicating discharge passage, the pressure balance in the discharge passage communicating with the discharge port is broken, and the discharge pulsation is reduced in the predetermined rotation speed region.
- the discharge chamber remains at the discharge port via the throttle. Even if the suction pressure of the compressor rises due to the temperature rise in the passenger compartment, the oil in the compressor is pushed out together with the liquid refrigerant by the increased suction pressure even if the suction pressure of the compressor rises due to the temperature rise in the vehicle interior. This eliminates the shortage of internal circulation tools in the compressor.
- the size of the throttle is large, it will be easier to guide the working fluid to the discharge passage communicating with the discharge port, bypassing the other discharge passages.However, if the passage area of the throttle is large, the throttle function will be reduced. Discharge pulsation increases. For this reason, by setting the size of the throttle portion to be equal to or less than the area corresponding to a circular cross section with a diameter of 1.5 mm, it is possible to achieve both reduction of oil outflow inside the compressor and reduction of discharge pulsation. Become.
- the discharge passage communicating with the discharge port is formed above the other discharge passages.
- a reciprocating compressor includes a cylinder block having a plurality of cylinder bores, a piston reciprocating in the cylinder bore, and one end of the cylinder hook fixed via a valve plate. And a second cylinder head fixed to the other end of the cylinder block via a valve plate.
- a first discharge chamber formed in the first cylinder head for introducing a working fluid discharged from a first compression chamber formed at one end side of the cylinder bore;
- a discharge passage provided in the cylinder block or the cylinder head, the discharge passage communicating one of the discharge passages to an external circuit, and a discharge passage other than the discharge passage communicating with the discharge opening.
- a reciprocating compressor configured to communicate with the first and second discharge chambers and a discharge passage communicating with the discharge port via a guide path.
- the first and second discharge chambers may be communicated with each other through a throttle portion having a reduced passage cross section.
- the working fluid discharged to the first discharge chamber and the second discharge chamber is supplied from another discharge passage other than the discharge passage communicating with the discharge port via the inner passage.
- the fluid is guided to the discharge passage communicating with the discharge port, and then is discharged from the discharge port to the external circuit.
- the working fluid guided to the other discharge passages is converged by the throttle before being merged in the guide passage. Since the pulsation is reduced, the pulsation of the joined working fluid can be reduced, and as a result, the discharge pulsation can be reduced.
- the path length from the first discharge chamber to the guide path and the path from the second discharge chamber to the guide path It is preferable that the length is formed substantially equal, or the axial size of the first discharge chamber and the axial size of the second discharge chamber are formed substantially equal.
- the throttle portion may be formed on the valve plate or on the cylinder block, and may be formed on the cylinder block and the valve interposed between the cylinder block and the valve plate. Alternatively, it may be formed by a gap with the gasket (claims 6, 7, 8).
- discharge pulsation In order to enhance the damping effect of the above, in addition to the above-described configuration, a throttle may be formed at or immediately before the discharge port.
- FIG. 1 is a side view showing the appearance of a reciprocating compressor according to the present invention.
- FIG. 2 is a diagram showing an end surface of the cylinder block viewed along the line AA in FIG.
- FIG. 3 is a cross-sectional view showing the reciprocating compressor according to the present invention, and shows a cross section taken along line XX of FIG.
- FIG. 4 is a cross-sectional view taken along line YY of FIG.
- Fig. 5 shows the valve plate
- Fig. 5 (a) shows the front valve plate.
- FIG. 5B is a view showing the rear valve plate.
- FIG. 6 is an enlarged cross-sectional view showing the throttle unit shown in FIG. 4 and its vicinity.
- FIG. 7 is an enlarged cross-sectional view illustrating another configuration example of the throttle unit illustrated in FIG.
- FIG. 8 is an enlarged cross-sectional view illustrating another configuration example of the throttle unit illustrated in FIG.
- FIG. 9 is a large cross-sectional view showing another example of the configuration of the throttle unit shown in FIG.
- FIG. 10 is a sectional view showing another configuration example of the reciprocating compressor according to the present invention.
- FIG. 11 shows the relationship between the ratio (Wr / Wf) of the axial thickness Wf of the front discharge chamber 18a in the axial direction to the axial thickness Wr of the rear discharge chamber 18b (Wr / Wf) and the discharge pulsation level.
- FIG. 4 is a characteristic diagram showing a relationship.
- FIG. 12 is a cross-sectional view showing another configuration example of the reciprocating compressor according to the present invention.
- FIG. 12 (a) shows a configuration example in which a throttle portion is provided on a valve plate.
- FIG. 13 is a cross-sectional view showing still another configuration example of the reciprocating compressor according to the present invention. This shows an example of a configuration in which the throttle portion is provided in the middle of the discharge passage and at the discharge port.
- FIG. 14 is a characteristic diagram showing the relationship between the rotation speed and the discharge pulsation level of the compressor provided with the throttle unit and the compressor not provided with the throttle unit.
- a reciprocating compressor 1 is used for a refrigeration cycle using a refrigerant as a working fluid.
- the compressor 1 includes a front side cylinder block 2 and a front side cylinder block.
- the rear side cylinder block 4 assembled with the O-ring 3 via a gasket (not shown) or a metal contact, and the valve plate 5 on the front side (left side in the figure) of the front side cylinder block port 2
- Each of the cylinder blocks 2 and 4 has a shaft support hole 10 for rotatably supporting a shaft 9 to be described later, and a circle parallel to the shaft support hole 10 and centered on the shaft 9.
- a plurality of (for example, five) cylinder bores 11 equidistantly arranged on the circumference, two discharge passages 12a, 12b provided in parallel with the cylinder bore 11, and low-pressure operation
- the suction passages 13 a and 13 b through which the fluid flows are formed.
- One discharge passage 12 a is connected to a discharge port 16 communicating with an external circuit formed in the cylinder head 8 through a communication port 15 formed in the valve plate ⁇ or the like. It is connected.
- the other discharge passage 12 b is connected to a discharge passage 12 a via a guide passage 17 and to a discharge chamber 18 a formed in a front cylinder head 6 described later. It communicates through a communication port 19 formed in the valve plate 5 and communicates with a discharge chamber 18 b formed in the rear cylinder head 8 through a communication port 21 formed in the valve plate 7. Communication.
- the discharge port 16 communicating with the discharge passage 12a may be formed on the outer peripheral surface of the cylinder block.
- suction passages 13 a and 13 b are connected to the swash plate housing chamber 22 described below, and the suction chambers formed in the cylinder heads 6 and 8 via the swash plate housing chamber 22. It is connected to a low-pressure passage 24 communicating with 23a and 23b.
- a double-headed piston 25 is slidably inserted into each of the cylinder bores 11.
- reference numeral 26 denotes a bolt hole formed between the adjacent cylinder bores 11 for inserting a fastening bolt.
- swash plate storage chambers 22 are formed by assembling the respective cylinder blocks.
- the chamber 22 is inserted into the shaft support holes 10 formed in the front side cylinder block 2 and the rear side cylinder block 4, and one end of the chamber 22 is connected to the cylinder head 6 on the front side.
- a shaft 9 that protrudes and mounts an amateur of an electromagnetic clutch (not shown) is provided.
- a swash plate 27 that rotates integrally with the shaft 9 is fixedly mounted on the shaft 9 in the swash plate storage chamber 22.
- the swash plate 27 is rotatably supported on the front cylinder block 2 and the rear cylinder block 4 via a thrust bearing 28, and is formed in a hemispherical shape provided so as to sandwich the peripheral edge part back and forth. It is moored through a pair of shoes 29 to a shoe pocket 30 formed at the center of the double-headed piston 25. Therefore, when the shaft 9 rotates and the swash plate 27 rotates, the rotational movement of the swash plate 27 is reciprocated by the double-headed biston 25 via the shear 29. And the reciprocating motion of the double-headed piston 25 changes the capacity of the compression chamber 31 formed between the piston 25 and the valve plates 5 and 7 in the cylinder bore 11. Has become.
- each of the valve plates 5 and 7 is formed with a suction hole 32 and a discharge hole 33 corresponding to each of the cylinder bores 11, and has a front side and a rear side.
- the cylinder heads 6 and 8 have suction chambers 23 a and 23 b for containing the working fluid supplied to the compression chamber 31, and a discharge chamber 18 for containing the working fluid discharged from the compression chamber 31. a and 18 b are defined.
- the suction chambers 23a and 23b communicate with the compression chamber 31 through the suction holes 32 of the nozzle plates 5 and 7, and the discharge chambers 18a and 18b It is formed continuously around the suction chambers 23 a, 23 b and communicates with the compression chamber 31 via the discharge holes 33 of the valve plates 5, 7.
- reference numeral 60 denotes a through hole formed at a position facing the suction passages 13a and 13b when the valve plates 5 and 7 are stacked on the cylinder blocks 2 and 4.
- 1 is a through hole formed at a position facing the low-pressure passage 24
- 62 is a through hole formed at a position facing the bolt mounting hole 26
- 63 is a shaft support hole 10 And a through hole formed at a position opposed to.
- the suction hole 32 is opened and closed by a suction valve 35 provided on the end face of the valve plate 5, 7 on the side of the cylinder opening, and the discharge hole 33 is provided on the cylinder head side of the valve plate 5, 7. It is opened and closed by a discharge valve 36 provided on the end face.
- Reference numeral 37 denotes a gasket provided on the cylinder block side of the knob plates 5 and 7 to seal between the cylinder blocks 2 and 4 via a suction valve 35.
- Reference numeral 38 denotes a knob plate.
- a gasket provided on the cylinder head side of 5, 7 to seal between the cylinder heads 6, 8 via the discharge valve 36.
- the discharge passage 12 a communicates with the front side discharge chamber 18 via the throttle portion 40.
- the diaphragm 40 is shown in FIG.
- the orifice-shaped through-hole 41 formed in the front-side valve plate 5 defines the size of the narrowed portion 40 as the communication ports 15, 19,
- the passage cross section is set smaller than 21.
- the suction chamber 23 through the suction hole 32 and the suction valve 3 5 from the suction chambers 23a and 23b.
- the working fluid compressed in the compression chamber 31 flows into the front cylinder via the discharge hole 33 and the discharge valve 36.
- the head or the head on the rear cylinder is discharged to the discharge chambers 18a and 18b.
- the working fluid discharged into the discharge chambers 18a and 18b enters the discharge passage 12b through the communication ports 19 and 21 and the discharge passage 12a through the throttle portion 40.
- the working fluid that has entered the discharge passage 12 b collides and joins at a substantially intermediate portion of the discharge passage 12 b, merges, and is guided to the discharge passage 12 a through the guide passage 17. . Then, in the middle part of the discharge passage 12 a, it joins with the working fluid introduced from the front side discharge chamber 18 a through the throttle part 40,
- the pressure is sent from the discharge port 16 to the external circuit via the communication port 15. Therefore, the working fluid discharged into the discharge chamber is restricted by the communication ports 19 and 21 and is restricted by the communication port 15 and guided to the discharge port 16.
- the pressure fluid in the passage is broken by the working fluid flowing into the passage 12a, and the discharge pulsation is attenuated in a predetermined rotation speed region.
- the working fluid of the external circuit is returned through the pipe, so that the lower discharge passage 12b is provided with the working fluid. Will be filled with.
- the pressures in the discharge chambers 18a and 18b increase.
- the working fluid that has accumulated in the discharge passage 12 b tends to be pushed out as it is discharged, but the front discharge chamber 18 a Since the discharge passage 12a communicates with the discharge passage 12a via the throttle portion 40, the pressure in the front discharge chamber 18a is guided to the discharge passage 12a through the throttle portion 40. For this reason, the working fluid filled in the lower discharge passages 12b is not pushed out at a stretch, and the outflow of oil in the compressor is reduced.
- the size of the narrowed portion 40 By the way, from the viewpoint of facilitating the processing and increasing the productivity, it is preferable to increase the size of the narrowed portion 40.
- the pulsation level of the working fluid increases, so the size of the throttle portion 40 that can both prevent oil outflow and reduce discharge pulsation is required. Is done.
- the present inventors have found that in order to reduce oil spill and attenuate discharge pulsation to such an extent that it does not hinder the external cycle, the size of the throttle portion (orifice hole) is large. It has been found that it is preferable to set the diameter to be equal to or less than the area corresponding to a circular section having a diameter of 1.5 mm.
- the oil spill at the time of starting the compressor is reduced, the discharge pulsation is suppressed to an allowable range, and the vibration and unpleasant sound of the pipe due to the pulsation are reduced. It becomes possible to reduce.
- the throttle portion 40 is formed by the through hole 41 formed in the valve plate 5
- the throttle portion 40 is, as shown in FIG. Even if it is formed by the formed orifice-shaped through hole 42, as shown in FIG. 8, the cylinder block 2 and the suction valve 35 or the gasket 37 (in the figure, the suction valve 35) And the passage area may be narrowed.
- a small space 43 communicating with the discharge passageway 12a is defined in the discharge chamber 18a, and the small space 43 is formed into a slit 44 in the remaining part of the discharge chamber 18a. May be formed in the cylinder head 6 by communicating with each other through the cylinder.
- the configuration in which the discharge passage 12a is communicated with the front-side discharge chamber 18a through the throttle portion 40 is shown.
- it may be configured to communicate with the rear-side discharge chamber 18b via a throttle.
- the passage length Lr of the discharge passage 12b from the chamber 18b to the guide path 17 is set to be substantially equal, and the working fluid of the front discharge chamber 18a and the working fluid of the rear discharge chamber 18b are almost equal.
- the front-side discharge chamber 18a of the discharge passage 12b is connected to the guide path 17.
- the narrowed portions 50a and 5Ob having a relatively small passage cross-section may be formed in the middle of the path leading to and the middle of the path leading from the rear discharge chamber 18b to the guide path 17.
- the constricted portions 50a, 5 Ob are provided with orifice-shaped through holes 51a, 5 lb in which the passage cross section of the discharge passage 12b is made relatively small in the cylinder blocks 2, 4, and the discharge chambers 18a, 5
- the working fluid 18b may be passed through the throttle portions 50a and 5Ob and collide.
- the axial thickness of the front discharge chamber 18a in the axial direction is Wf
- the axial thickness of the rear discharge chamber 18b in the axial direction is Wr
- the throttle portions 50a and 50b provided in front of the guide path 17 are formed by orifice-like through holes 5la and 5lb formed in the front cylinder port 2.
- the throttle portions 50a and 50b can be formed by providing orifice-shaped through holes 52a and 52b in the valve plates 5 and 7, as shown in FIG.
- the cylinder works 2 and 4 and the suction valve 35 or gasket 37 (in the figure) May be formed by narrowing the passage area with the suction valve 35).
- a throttle portion 50c having a relatively small passage cross section may be further provided at or immediately before the discharge port 16. Good.
- the cross section of the discharge passage communicating with the discharge port is smaller than the cross section of the discharge passage communicating with the first and second discharge chambers. It communicates with at least one of the first and second discharge chambers via a small throttle, and the size of the throttle is set so as not to exceed the area corresponding to the cross section of the passage having a diameter of 1.5 mm.
- the other discharge passage can be connected to the other discharge passage.
- the pulsation of the guided working fluid is reduced by the throttle portion before it joins in the guide path. Discharge pulsation can be reduced. Therefore, it is possible to reduce the generation of vibration and noise of the compressor and the piping due to the pulsation.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004570190A JPWO2004088139A1 (ja) | 2003-03-28 | 2003-11-17 | 往復動型圧縮機 |
EP03772805A EP1612419A4 (en) | 2003-03-28 | 2003-11-17 | RECIPROCATING |
US10/550,546 US7607897B2 (en) | 2003-03-28 | 2003-11-17 | Reciprocating compressor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003091581 | 2003-03-28 | ||
JP2003-091581 | 2003-03-28 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004088139A1 true WO2004088139A1 (ja) | 2004-10-14 |
Family
ID=33127284
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2003/014565 WO2004088139A1 (ja) | 2003-03-28 | 2003-11-17 | 往復動型圧縮機 |
Country Status (4)
Country | Link |
---|---|
US (1) | US7607897B2 (ja) |
EP (1) | EP1612419A4 (ja) |
JP (1) | JPWO2004088139A1 (ja) |
WO (1) | WO2004088139A1 (ja) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100873371B1 (ko) * | 2007-12-26 | 2008-12-10 | 학교법인 두원학원 | 왕복동식 압축기의 밸브 플레이트 |
FR2942655B1 (fr) * | 2009-02-27 | 2013-04-12 | Danfoss Commercial Compressors | Compresseur frigorifique a pistons |
WO2014115122A2 (en) * | 2013-01-28 | 2014-07-31 | Dattatraya Rajaram Shelke | System and methods for compression of air or working fluid |
JP6164135B2 (ja) | 2014-03-27 | 2017-07-19 | 株式会社豊田自動織機 | 圧縮機 |
JP2016148292A (ja) * | 2015-02-12 | 2016-08-18 | 株式会社豊田自動織機 | 両頭ピストン式圧縮機 |
CN108518331B (zh) * | 2018-03-26 | 2019-06-28 | 淮安市新盛压缩机配件有限公司 | 一种低磨损斜盘式空调压缩机 |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11117859A (ja) * | 1997-10-20 | 1999-04-27 | Zexel:Kk | 斜板式圧縮機 |
Family Cites Families (23)
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JPS599757B2 (ja) * | 1977-10-12 | 1984-03-05 | 株式会社日立製作所 | 圧縮機 |
JPS57202781U (ja) * | 1981-06-19 | 1982-12-23 | ||
JPS5927164U (ja) * | 1982-08-12 | 1984-02-20 | 株式会社ボッシュオートモーティブ システム | 複動式圧縮機 |
JPS61207884A (ja) * | 1985-03-12 | 1986-09-16 | Diesel Kiki Co Ltd | 圧縮機の脈動低減機構 |
JPH0717827Y2 (ja) * | 1987-03-11 | 1995-04-26 | 株式会社豊田自動織機製作所 | 圧縮機のマフラー機構 |
US4768928A (en) * | 1988-01-25 | 1988-09-06 | General Motors Corporation | Axial piston swash plate compressor muffler arrangement |
EP0330965B1 (en) * | 1988-03-02 | 1991-05-08 | Nippondenso Co., Ltd. | Variable-capacity swash-plate type compressor |
US5173032A (en) * | 1989-06-30 | 1992-12-22 | Matsushita Electric Industrial Co., Ltd. | Non-clutch compressor |
US5100306A (en) * | 1990-03-16 | 1992-03-31 | Ford Motor Company | Noise reducing compressor gasket and head assembly |
US5139392A (en) * | 1991-04-15 | 1992-08-18 | General Motors Corporation | Multi-cylinder swash plate compressor discharge gas flow arrangement |
JP3301570B2 (ja) * | 1993-12-27 | 2002-07-15 | 株式会社豊田自動織機 | 往復動型圧縮機 |
US5765996A (en) * | 1994-04-08 | 1998-06-16 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Vibration preventing structure in swash plate type compressor |
US5809865A (en) * | 1996-02-15 | 1998-09-22 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston-type compressor with reduced vibration |
JP3266504B2 (ja) * | 1996-04-19 | 2002-03-18 | 株式会社ゼクセルヴァレオクライメートコントロール | 斜板式圧縮機 |
JPH10103228A (ja) * | 1996-09-30 | 1998-04-21 | Toyota Autom Loom Works Ltd | 両頭ピストン式圧縮機 |
US6318980B1 (en) * | 1997-12-26 | 2001-11-20 | Sanden Corporation | Shape of suction hole and discharge hole of refrigerant compressor |
JP3820766B2 (ja) * | 1998-03-06 | 2006-09-13 | 株式会社豊田自動織機 | 圧縮機 |
JP3924985B2 (ja) * | 1999-04-15 | 2007-06-06 | 株式会社豊田自動織機 | 圧縮機の吐出脈動減衰装置 |
JP2001082331A (ja) * | 1999-09-14 | 2001-03-27 | Toyota Autom Loom Works Ltd | 圧縮機における脈動抑制構造 |
JP4153160B2 (ja) * | 2000-09-04 | 2008-09-17 | カルソニックカンセイ株式会社 | 斜板式圧縮機の脈動低減構造 |
JP4692866B2 (ja) * | 2001-07-05 | 2011-06-01 | 株式会社ヴァレオサーマルシステムズ | 斜板式圧縮機 |
US6575708B2 (en) * | 2001-09-13 | 2003-06-10 | Delphi Technologies, Inc. | Compressor head with improved oil retention |
KR100723811B1 (ko) * | 2001-10-10 | 2007-05-31 | 한라공조주식회사 | 사판식 압축기 |
-
2003
- 2003-11-17 WO PCT/JP2003/014565 patent/WO2004088139A1/ja active Application Filing
- 2003-11-17 EP EP03772805A patent/EP1612419A4/en not_active Withdrawn
- 2003-11-17 US US10/550,546 patent/US7607897B2/en not_active Expired - Fee Related
- 2003-11-17 JP JP2004570190A patent/JPWO2004088139A1/ja active Pending
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11117859A (ja) * | 1997-10-20 | 1999-04-27 | Zexel:Kk | 斜板式圧縮機 |
Non-Patent Citations (1)
Title |
---|
See also references of EP1612419A4 * |
Also Published As
Publication number | Publication date |
---|---|
US7607897B2 (en) | 2009-10-27 |
JPWO2004088139A1 (ja) | 2006-07-06 |
EP1612419A1 (en) | 2006-01-04 |
EP1612419A4 (en) | 2007-01-03 |
US20060140785A1 (en) | 2006-06-29 |
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