WO2004061306A1 - Compresseur a cylindree variable de type a plateau oscillant concu pour un cycle de refrigeration supercritique - Google Patents

Compresseur a cylindree variable de type a plateau oscillant concu pour un cycle de refrigeration supercritique Download PDF

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Publication number
WO2004061306A1
WO2004061306A1 PCT/JP2003/016638 JP0316638W WO2004061306A1 WO 2004061306 A1 WO2004061306 A1 WO 2004061306A1 JP 0316638 W JP0316638 W JP 0316638W WO 2004061306 A1 WO2004061306 A1 WO 2004061306A1
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WO
WIPO (PCT)
Prior art keywords
valve
swash plate
refrigeration cycle
refrigerant
type variable
Prior art date
Application number
PCT/JP2003/016638
Other languages
English (en)
Japanese (ja)
Inventor
Hiroshi Kanai
Shunichi Furuya
Original Assignee
Zexel Valeo Climate Control Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zexel Valeo Climate Control Corporation filed Critical Zexel Valeo Climate Control Corporation
Priority to US10/540,471 priority Critical patent/US20060083628A1/en
Priority to EP03789631A priority patent/EP1586774A4/fr
Priority to JP2004564511A priority patent/JPWO2004061306A1/ja
Publication of WO2004061306A1 publication Critical patent/WO2004061306A1/fr

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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
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • 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
    • F04B27/1009—Distribution members

Definitions

  • the present invention relates to a swash plate type variable displacement compressor used for a supercritical refrigeration cycle.
  • Various configurations are conventionally known for the intake valve and the discharge valve of a swash plate type variable displacement compressor that compresses the refrigerant of a refrigeration cycle.
  • a discharge valve in which a valve body is pressed against a valve seat of a discharge port in an elastically deformed state.
  • the structure of this type of discharge valve is also disclosed in, for example, Japanese Patent Application Laid-Open No. 61-44074 and Japanese Patent Application Laid-Open No. 2001-150300.
  • lubricating oil is mixed in the refrigerant of the refrigeration cycle, and in order to ensure good opening and closing operation of the suction valve and the discharge valve, the surface tension of the lubricating oil that goes around the gap between the valve body and the valve seat is considered. There is a need. Although the surface tension of the lubricating oil is important for ensuring the tightness of the valve, it becomes a resistance when the valve opens, so if it is larger than necessary, the operation of the valve will be delayed and the compressor will not operate. It also causes the vibration and noise of the vehicle to increase. JP-A-7-167058 and JP-A-7-168062 disclose the valve element and the valve even when the valve element is closed in order to deal with such a problem.
  • a valve structure configured to leave a slight gap between the seat and the seat is disclosed.
  • the suction valve and the discharge valve have been given importance in such a configuration as to prevent vibration and noise.
  • Cool C 0 2 The internal pressure of a refrigeration cycle that uses a medium is extremely high when compared to a refrigeration cycle that uses a chlorofluorocarbon-based refrigerant.
  • the pressure on the high-pressure side may exceed the critical point of the refrigerant depending on operating conditions such as air temperature. is there.
  • the critical point is the limit on the high-pressure side where the gas and liquid layers coexist (that is, the limit on the high-temperature side), and is the end point of one of the vapor pressure curves.
  • the pressure, temperature and density at the critical point are the critical pressure, critical temperature and critical density, respectively.
  • the refrigerant does not condense.
  • This type of supercritical refrigeration cycle is installed in, for example, an automobile and used for air conditioning in a vehicle.
  • a compressor used in a supercritical refrigeration cycle is also described, for example, in Japanese Patent Application Publication No. 2002-25707.
  • the compressor described in this publication is configured such that the stroke of the piston can be changed according to the inclination of a swash plate provided rotatably.
  • the piston is held by the cylinder so as to be able to reciprocate, and the cylinder is provided with a suction valve for sucking the refrigerant and a discharge valve for discharging the refrigerant.
  • the refrigerant circulating in the refrigeration cycle is drawn into the cylinder from the suction valve, compressed, and discharged from the discharge valve to the outside of the cylinder.
  • the compressor is connected to a power engine of a vehicle and is operated by the power of the power engine.
  • the supercritical refrigeration cycle is significantly different from the conventional chlorofluorocarbon-based refrigeration cycle in terms of pressure resistance, and the compressor for the supercritical refrigeration cycle also has a superior structure based on the pressure resistance and other factors. A creative ingenuity is required.
  • a clutchless compressor connected to a driving engine of the vehicle without using a clutch.
  • its swash plate rotates constantly even when the refrigerant is not compressed, and the minimum stroke of the piston is usually about 5% or less of the maximum stroke. I have. In recent years, it has become a very important issue for such a clutchless compressor to reduce the number of revolutions at startup.
  • the pressure of the refrigerant when the compressor is started is about 7.2 MPa in a 30 ° C atmosphere.
  • the pressure of the refrigerant when the compressor is started is about 0.67 MPa under a 30 ° C atmosphere.
  • the bore diameter of the silicon Sunda is 1 5. 0 ⁇ 2 1.
  • the volume of Siri Sunda is 2 0 ⁇ 3 3 cm 3, inhalation the opening area of the port in the valve and discharge valve are 7. 0 ⁇ 2 9. 0 mm 2.
  • Bo ⁇ the diameter of the silicon Sunda is 3 2 to 4 0 mm, the volume of Siri Sunda is 9 0 cm 3 ⁇ 1 7 0 cm 3, intake valves and the opening area of the port at the discharge valve 3 8.5 - a 1 1 3. 0 mm 2.
  • the present invention has been made in view of such circumstances, and an object thereof is to achieve an improvement in performance of a swash plate type variable displacement compressor for a supercritical refrigeration cycle. Disclosure of the invention
  • the invention described in claim 1 of the present application is a compressor used in a supercritical refrigeration cycle, wherein the swash plate is rotatably provided, a piston connected to the swash plate, and the piston is moved.
  • a swash plate type variable capacity compressor comprising: a suction valve for sucking the refrigerant of the supercritical refrigeration cycle; and a discharge valve for discharging the refrigerant.
  • the suction valve is provided with a flexible valve body at a suction port for sucking the refrigerant, and the swash plate type variable capacity compressor rotates the swash plate when the refrigerant starts to be compressed.
  • a swash plate type variable displacement compressor having a configuration in which the valve body is pressed against the valve seat of the suction port in an elastically deformed state. According to such a configuration, the performance of the swash plate type variable displacement compressor for the supercritical refrigeration cycle is surely improved.
  • the inventor of the present application conducted various trial manufactures and experiments on various valve structures in order to obtain a suitable valve structure in a swash plate type variable displacement compressor for a supercritical refrigeration cycle.
  • the suction valve is more important than the discharge valve from the viewpoint of reducing the number of revolutions at startup.
  • the suction valve which was the most effective in securing startability, durability, and good opening and closing operations of the valve element, has flexibility in the suction port for sucking refrigerant.
  • the valve body was mounted, and the valve body was pressed against the valve seat of the suction port with a slight elastic deformation.
  • the valve element of the suction valve is designed in consideration of appropriate internal stress after being mounted on the suction port.
  • the present invention focuses on a very important structure in the details of the swash plate type variable displacement compressor used in the supercritical refrigeration cycle, and as a result, with a very simple structural device, This is a swash plate type variable displacement compressor that has achieved a remarkable effect of dramatically improving the performance of such a compressor.
  • the valve body is The swash plate type having a configuration in which the deflection of the valve body when the suction port is attached is lmm or less and the external force received by the valve body from the valve seat of the suction port is 1.8 N or less at this time. It is a variable capacity compressor. That is, if the deflection of the valve body is set to 1 mm or less and the external force that the valve body receives from the valve seat of the suction port is set to 1.8 N or less, the valve body can be smoothly opened and closed while maintaining the opening and closing operation. It is possible to ensure good seating properties between the valve and the valve seat.
  • the invention described in claim 3 of the present application is the invention according to claim 1 or 2, wherein the supercritical refrigeration cycle is a refrigeration cycle for air conditioning in a vehicle mounted on an automobile, and the swash plate type variable displacement compressor includes a clutch.
  • a swash plate type variable displacement compressor configured to be a clutchless compressor that is connected to the drive engine of the vehicle without intervention. That is, the swash plate type variable displacement compressor of the present invention reliably reduces the number of revolutions of the swash plate when the refrigerant starts to be compressed, and as a clutchless compressor used in a refrigeration cycle for air conditioning in a vehicle, It can be used very suitably.
  • FIG. 1 is a schematic diagram showing a supercritical refrigeration cycle according to an embodiment of the present invention.
  • Figure 2 is a schematic diagram showing a supercritical refrigeration cycle according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view showing a swash plate type variable displacement compressor for a supercritical refrigeration cycle according to an embodiment of the present invention.
  • FIG. 2 is a front view showing a valve plate and a cylinder-side valve element plate according to the embodiment of the present invention.
  • FIG. 2 is a front view showing a valve plate and a valve plate on a rear housing side according to the embodiment of the present invention.
  • Fig. 5 is a front view showing a valve plate and a valve plate on a rear housing side according to the embodiment of the present invention.
  • FIG. 3 is a cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • Fig. 6 is a cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • FIG. 2 is an exploded cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • Fig. 7 is an exploded cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • FIG. 3 is a cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • Fig. 8 is a cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • FIG. 3 is a cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • Fig. 9 is a cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • FIG. 3 is a cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • Fig. 1 1
  • FIG. 2 is an exploded cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • Fig. 1 2 is an exploded cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • FIG. 3 is a cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • Fig. 13 is a cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • FIG. 2 is an exploded cross-sectional view illustrating a suction valve and a discharge valve according to the embodiment of the present invention.
  • the supercritical refrigeration cycle 1 of the present embodiment is a refrigeration cycle for in-vehicle air conditioning mounted on an automobile, and includes a swash plate type variable capacity compressor 10 for compressing a solvent, and the compressor 10 A radiator 20 for cooling the refrigerant compressed by the radiator 20, an expansion valve 30 for decompressing and expanding the refrigerant cooled by the radiator 20, and an evaporator 4 for evaporating the refrigerant decompressed by the expansion valve 30.
  • an accumulator 50 that separates the refrigerant flowing out of the evaporator 40 into a gas phase and a liquid phase and sends the gas phase refrigerant to the compressor 10, and a high-pressure refrigerant and a low-pressure refrigerant.
  • Internal heat exchanger that improves cycle efficiency by exchanging heat
  • refrigerant is used a C 0 2, the pressure of the high pressure side of the supercritical refrigeration cycle 1, Ri by the use conditions such as air temperature, exceed the critical point of the refrigerant.
  • the refrigerant contains lubricating oil for facilitating the driving of the compressor 10.
  • the swash plate type variable displacement compressor 10 of this example includes a front nozzle 110, a cylinder block 120, a rear nozzle 130, and a valve plate. 140, rotatable drive shaft 200, lug plate 300 provided in drive shaft 200, drive shaft 200, and lug plate 300
  • the swash plate type variable capacity compressor 100 is configured such that the swash plate 400 rotates together with the drive shaft 200 and the lag plate 300 and the piston 500 reciprocates, whereby a series The refrigerant is sucked into the compressor 600, compressed and discharged, and the control valve 700 controls the pressure acting on the piston 500, whereby the swash plate 400 is controlled.
  • the stroke of the piston 500 changes with the inclination of 0 to control the refrigerant discharge amount.
  • the minimum stroke of BISTON 500 is set at about 5% or less of the maximum stroke.
  • a plurality of screws 500 and a plurality of cylinders 600 are arranged at equal intervals around the rotation axis of the drive shaft 200.
  • the drive shaft 200 is mounted on the front housing 110 and the cylinder block 120 via a bearing.
  • the drive shaft 200 is connected to the engine, which is the drive engine of the vehicle, without going through a clutch. That is, the swash plate type variable capacity compressor 10 is a so-called clutchless compressor.
  • Front Tohau The inside of the jing 110 is a crank chamber 111 provided with a lug plate 300 and a swash plate 400.
  • the cylinder block 120 is a member constituting a plurality of cylinders 600.
  • the lag plate 300 is a member fixed to the drive shaft 200, and an arm portion 310 for connecting the swash plate 400 is provided at a key portion thereof.
  • the swash plate 400 is provided with a guide section 420 to which a shroud 410 is mounted, and is mounted to the drive shaft 200 so that the slide can be moved and the inclination angle can be changed. I have.
  • a spring 430 that urges the swash plate 400 and the biston 500 to a certain extent on the cylinder 600 side. Have been.
  • Each of the bistons 500 is anchored to the cylinder 410 and is in contact with the bores 6100 of the cylinder 600. Reciprocate each time.
  • the control valve 700 controls the internal pressure of the crankcase 111.
  • the inclination of the swash plate 400 and the stroke of the biston 500 change according to the internal pressure of the crankcase 111.
  • the valve plate 140 is a member that forms a suction valve 150 that sucks refrigerant into the cylinder 600 and a discharge valve 160 that discharges refrigerant from the cylinder 600. It is arranged between 20 and the rear housing 130. Further, on both sides of the valve plate 140, a cylinder-side valve body plate 151 and a rear housing-side valve body plate 161 which will be described in detail later are mounted by screws. By disposing such a valve plate 140 in each cylinder 120, a suction valve 150 and a discharge valve 160 are provided, respectively. The coolant is compressed between the piston 500 and the valve plate 140.
  • the rear housing 130 is provided with a control valve 700 and a suction chamber 1311 and a discharge chamber 1332 between the control housing and the valve plate 140.
  • flow passages through which the refrigerant flows are provided at key points of the compressor 1, and the low-pressure gas that has circulated through the refrigeration cycle 1 before being compressed is introduced into the suction chamber 13 1.
  • the low-pressure gas in the suction chamber 13 1 is sucked into the cylinder 600 from the suction valve 150 when biston 500 moves back, and becomes high-pressure gas when biston 500 moves further forward. From the discharge port 160 to the discharge chamber 132.
  • the high-pressure gas in the discharge chamber 132 circulates through the refrigeration cycle again.
  • the control valve 700 is communicated with the crank chamber 11 1, the suction chamber 13 1, and the discharge chamber 13 2 through predetermined flow paths, and when the pressure of the low-pressure gas decreases, When the bellows provided therein expands, the valve moves and the high-pressure gas is led to the crank chamber 11. When the pressure of the low-pressure gas rises, the pulp closes due to the contraction of the bellows, and the high-pressure gas guided to the crankcase 11 is cut.
  • the swash plate 400 reciprocates in a state where the average of the internal pressure of each cylinder 600 and the internal pressure of the crankcase 111 are balanced. That is, the inclination of the swash plate 400 and the stroke of the biston 500 are controlled by the valve opening of the control valve 700, and the discharge amount of the high-pressure gas is controlled by the piston. It increases as the stroke of 500 increases and decreases as the stroke decreases.
  • the pressure of the refrigerant at the time of starting the swash plate type variable capacity compressor 10 is about 7.2 MPa in a 30 ° C atmosphere. Further, the diameter of the bore 6 1 0 Siri Sunda 6 0 0 1 5. 0 to 2 1. 0 mm, the volume of silicon Sunda 6 0 0 2 0 ⁇ 3 3 cm 3, the intake valve 1 5 0 and a discharge valve The opening area of each of the ports 14 1 and 142 in 16 0 is 7.0-29.0 mm 2 .
  • the valve plate 140 has a plurality of suction ports 141 communicating each cylinder 600 and the suction chamber 131, and each cylinder 600 and the discharge chamber 132. And a plurality of discharge ports 1 and 2 communicating with each other.
  • the cylinder valve plate 15 1 has a valve body 15 2 of the suction valve 150 corresponding to each suction port 14 1, and a hole 15 3 corresponding to each discharge port 14 2.
  • the valve plate 16 1 has a valve 16 2 of the discharge valve 16 corresponding to each discharge port 14 2, and a hole 16 corresponding to the suction port 14 1. 3 and a plurality of such members (see FIGS. 3 and 4).
  • the suction valve 150 of the present example has a flexible valve element 152 mounted on a suction port 141 for sucking a refrigerant into a cylinder 600.
  • the valve element 152 of the suction valve 150 is pressed against one surface of the valve plate 140 serving as a valve seat of the suction port 141 in a slightly elastically deformed state.
  • the discharge valve 160 of the present example has a flexible valve element 162 attached to a discharge port 142 that discharges refrigerant from the inside of the cylinder 600. .
  • the valve element 162 of the discharge valve 160 is pressed against the other surface of the valve plate 140 serving as the valve seat of the discharge port 142 in a slightly elastically deformed state.
  • Reference numeral 164 in the figure denotes a retainer that regulates the opening of the valve element 162 of the discharge valve 160.
  • the retainer 164 is screwed to the valve plate 140 (see FIG. 5).
  • valve element 152 of the suction valve 150 provided on the cylinder side valve element plate 151 is plastically deformed in a curved shape with the tip protruding toward the valve plate 140.
  • the cylinder side plate plate 151 is attached to the valve plate 140, and it is forcibly elastically deformed.
  • the valve element 152 is plastically deformed by press working, and the deflection 3 when attached to the suction port 141 is 1 mm or less (more specifically, 50 to 200 2111). Has become.
  • the plate thickness of the material of the valve element 152 of the suction valve 150 is desirably 0.2 to 0.3 mm, and is 0.25 mm in this example. Its modulus of longitudinal elasticity of the material, 2.
  • the external force P received from the valve seat of port 14 1 is 1.8 N or less in order to ensure the smooth opening and closing operation of valve body 152.
  • the more desirable range of the external force P is 1.2 N or less, and the most desirable range is 0.2 to 0.7 N.
  • the spring constant k of the valve element 152 is about 4.0 N / mm and the deflection is 150 / m, the external force P is about 0.6 N.
  • the spring constant k depends on the longitudinal elastic modulus of the material and the shape of the valve element 152.
  • valve element 162 of the discharge valve 160 provided on the rear housing-side valve element plate 161 is the same as the above-described valve element 152 of the suction valve 150. That is, the valve body 1 6 2 flexure (5 2 of the discharge valve 1 6 0 is equal to or less than lmm, the external force P that the valve body 1 6 2 of the discharge valve 1 6 0 receives from port 1 4 2 of the valve seat Is 1.8 N or less.
  • valve element 15 2 of the suction valve 15 0 and the valve element 16 2 of the discharge valve 16 0 are opened and closed by the differential pressure of the crank chamber 1 1 1, the suction chamber 1 3 1, and the discharge chamber 1 3 2 respectively. It works (see Figs. 7 and 8).
  • the inventor of the present application repeated a comparison experiment of the number of revolutions at the time of startup between the swash plate type variable displacement compressor 10 of the present example and the cylinder side valve plate 151, which was replaced, under different conditions. went.
  • the replaced cylinder-side valve body plate is flat, and the valve body 150 of the suction valve 150 is elastic on the surface of the valve plate 140, which is the valve seat of the suction port 141. It is not pressed in a deformed state.
  • the rotation speed at startup of the swash plate type variable displacement compressor 10 of this example is 30 to 70% lower than the rotation speed at startup of the cylinder-side valve plate 151, which has been replaced. It was within the range of the center.
  • FIG. 9 is a comparison graph of the number of revolutions at startup before and after replacement of the valve element of the intake valve, that is, before and after the improvement. According to such an experiment, it has been proved that the swash plate type variable capacity compressor 10 of the present example has a surely reduced rotation speed of the swash plate when the refrigerant starts to be compressed.
  • valve element 152 of the suction valve 150 and the shape of the valve element 162 of the discharge valve 160 can be changed as appropriate, and are not limited to those illustrated in the drawings.
  • the valve body 15 2 of the suction valve 150 or the valve body 16 2 of the discharge valve 160 has a tip formed into a hemispherical shape, and has a circular shape. It is also possible that the spherical surface is in contact with the edge of the suction port 141 or the discharge port 142.
  • the tip is preferably formed by pressing.
  • the male threaded part B passing therethrough is screwed into the female thread N provided on the valve plate 140.
  • the distal end portion is elastically deformed in a state of being pressed against the edge of the suction port 141 or the discharge port 142.
  • the flat valve elements 15 2 and 16 2 are elastically deformed and pressed against the surface of the curved valve plate 140. It is also possible. In this case, plastic deformation of the valve bodies 15 2 and 16 2 can be omitted.
  • the swash plate type variable displacement compressor of the present invention can be suitably used as a compressor for a supercritical refrigeration cycle in which the pressure on the high pressure side exceeds the critical point of the refrigerant.

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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

La présente invention concerne un compresseur à cylindrée variable de type à plateau oscillant (10) qui est utilisé pour un cycle de réfrigération supercritique (1). Ce compresseur comprend un plateau oscillant rotatif (400), des pistons (500) qui sont reliés à ce plateau oscillant, ainsi que des cylindres (600) qui retiennent de façon mobile les pistons. Les cylindres présentent un clapet d'aspiration (150) à travers lequel un fluide réfrigérant est aspiré pour le cycle de réfrigération supercritique et un clapet d'évacuation (160) à travers lequel le fluide réfrigérant est évacué. Le clapet d'aspiration est constitué d'un port d'aspiration (141) à partir duquel le fluide réfrigérant est aspiré et d'un corps souple de clapet (152) qui est monté sur le port d'aspiration. Afin de réduire le nombre de rotations du plateau oscillant lorsque le fluide réfrigérant commence à être comprimé, le corps de clapet est fixé par ajustement pressé dans un siège de clapet du port d'aspiration, le corps de clapet subissant une déformation élastique.
PCT/JP2003/016638 2002-12-27 2003-12-24 Compresseur a cylindree variable de type a plateau oscillant concu pour un cycle de refrigeration supercritique WO2004061306A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US10/540,471 US20060083628A1 (en) 2002-12-27 2003-12-24 Swach plate type variable displayment compressor for supercritical refrigeration cycle
EP03789631A EP1586774A4 (fr) 2002-12-27 2003-12-24 Compresseur a cylindree variable de type a plateau oscillant concu pour un cycle de refrigeration supercritique
JP2004564511A JPWO2004061306A1 (ja) 2002-12-27 2003-12-24 超臨界冷凍サイクル用の斜板式可変容量コンプレッサ

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002-380867 2002-12-27
JP2002380867 2002-12-27

Publications (1)

Publication Number Publication Date
WO2004061306A1 true WO2004061306A1 (fr) 2004-07-22

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US (1) US20060083628A1 (fr)
EP (1) EP1586774A4 (fr)
JP (1) JPWO2004061306A1 (fr)
WO (1) WO2004061306A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006069883A1 (fr) * 2004-12-23 2006-07-06 BSH Bosch und Siemens Hausgeräte GmbH Compresseur pour un appareil frigorifique
JP2007278180A (ja) * 2006-04-06 2007-10-25 Sanden Corp 往復動圧縮機
WO2009017157A1 (fr) * 2007-08-01 2009-02-05 Sanden Corporation Machine à fluide de type à spirale
JP2021055631A (ja) * 2019-09-30 2021-04-08 株式会社豊田自動織機 圧縮機及びその製造方法

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4408389B2 (ja) * 2004-05-10 2010-02-03 サンデン株式会社 斜板式圧縮機
US20060053051A1 (en) * 2004-09-07 2006-03-09 Philip Goodman Genergraphic websites
DE102004061940A1 (de) * 2004-12-22 2006-07-06 Aerolas Gmbh, Aerostatische Lager- Lasertechnik Kolben-Zylinder-Einheit
DE102004062307A1 (de) * 2004-12-23 2006-07-13 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter
DE102004062302A1 (de) * 2004-12-23 2006-07-13 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter und Antriebsaggregat dafür
DE102004062305A1 (de) * 2004-12-23 2006-07-13 BSH Bosch und Siemens Hausgeräte GmbH Verdichtergehäuse
DE102004062298A1 (de) * 2004-12-23 2006-07-13 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter
US20080000348A1 (en) * 2004-12-23 2008-01-03 Bsh Bosch Und Siemens Hausgerate Gmbh Linear Compressor
DE102004062300A1 (de) * 2004-12-23 2006-07-13 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter
DE102004062301A1 (de) * 2004-12-23 2006-07-13 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter und Antriebsaggregat dafür
DE112008002024A5 (de) * 2007-08-25 2010-07-29 Ixetic Mac Gmbh Hubkolbenmaschine
JP5188572B2 (ja) * 2008-04-30 2013-04-24 三菱電機株式会社 空気調和装置
JP5240311B2 (ja) * 2011-03-15 2013-07-17 株式会社豊田自動織機 ピストン式圧縮機のシリンダブロックおよびピストン式圧縮機のシリンダブロック加工方法
DK178434B1 (en) * 2015-01-02 2016-02-22 Producteers As Automatic Filter Cleaning System
CN109611224B (zh) * 2018-11-30 2021-06-08 恒天九五重工有限公司 一种防止工程机械启动时产生故障的方法
US20220364554A1 (en) * 2021-05-13 2022-11-17 Walmsley Developments Pty Ltd Portable pump

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6144074U (ja) * 1984-08-24 1986-03-24 ダイキン工業株式会社 圧縮機に用いる吐出弁構造
JPH0861242A (ja) * 1994-08-10 1996-03-08 Iwata Air Compressor Mfg Co Ltd 往復圧縮機及び吸込弁
JPH09256958A (ja) * 1996-03-21 1997-09-30 Sanden Corp 圧縮機の起動負荷低減装置
JP2002257037A (ja) * 2001-02-23 2002-09-11 Sanden Corp 斜板式圧縮機

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS594203Y2 (ja) * 1975-07-16 1984-02-06 エヌオーケー株式会社 リ−ドバルブ
JPS5951262U (ja) * 1982-09-28 1984-04-04 カルソニックカンセイ株式会社 コンプレツサ用バルブの構造
JPS6154566U (fr) * 1984-09-14 1986-04-12
JPH0756258B2 (ja) * 1985-10-04 1995-06-14 株式会社豊田自動織機製作所 可変容量圧縮機
JPH0243573U (fr) * 1988-09-19 1990-03-26
BR8901306A (pt) * 1989-03-16 1990-10-16 Brasil Compressores Sa Valvula de palheta para compressor hermetico
BR9002967A (pt) * 1990-06-19 1991-12-24 Brasil Compressores Sa Valvula para compressor hermetico de refrigeracao
JP3226141B2 (ja) * 1993-12-16 2001-11-05 株式会社豊田自動織機 容積型圧縮機の弁装置
JP3232839B2 (ja) * 1993-12-24 2001-11-26 株式会社豊田自動織機 圧縮機の弁装置
US5584670A (en) * 1994-04-15 1996-12-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Piston type variable displacement compressor
JP2000329066A (ja) * 1999-05-19 2000-11-28 Toyota Autom Loom Works Ltd ピストン式圧縮機における吸入弁構造
BR0003292A (pt) * 2000-07-17 2002-02-26 Brasil Compressores S A Arranjo de válvulas de sucção e de descarga para compressor hermético de pequeno porte

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6144074U (ja) * 1984-08-24 1986-03-24 ダイキン工業株式会社 圧縮機に用いる吐出弁構造
JPH0861242A (ja) * 1994-08-10 1996-03-08 Iwata Air Compressor Mfg Co Ltd 往復圧縮機及び吸込弁
JPH09256958A (ja) * 1996-03-21 1997-09-30 Sanden Corp 圧縮機の起動負荷低減装置
JP2002257037A (ja) * 2001-02-23 2002-09-11 Sanden Corp 斜板式圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP1586774A4 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006069883A1 (fr) * 2004-12-23 2006-07-06 BSH Bosch und Siemens Hausgeräte GmbH Compresseur pour un appareil frigorifique
JP2007278180A (ja) * 2006-04-06 2007-10-25 Sanden Corp 往復動圧縮機
WO2009017157A1 (fr) * 2007-08-01 2009-02-05 Sanden Corporation Machine à fluide de type à spirale
JP2021055631A (ja) * 2019-09-30 2021-04-08 株式会社豊田自動織機 圧縮機及びその製造方法

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US20060083628A1 (en) 2006-04-20
EP1586774A1 (fr) 2005-10-19
EP1586774A4 (fr) 2011-03-09

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