US20060083628A1 - Swach plate type variable displayment compressor for supercritical refrigeration cycle - Google Patents

Swach plate type variable displayment compressor for supercritical refrigeration cycle Download PDF

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Publication number
US20060083628A1
US20060083628A1 US10/540,471 US54047105A US2006083628A1 US 20060083628 A1 US20060083628 A1 US 20060083628A1 US 54047105 A US54047105 A US 54047105A US 2006083628 A1 US2006083628 A1 US 2006083628A1
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United States
Prior art keywords
valve
swash plate
refrigerant
type variable
refrigerating cycle
Prior art date
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Abandoned
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US10/540,471
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English (en)
Inventor
Hiroshi Kanai
Shunichi Furuya
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Thermal Systems Japan Corp
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Zexel Valeo Climate Control Corp
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Filing date
Publication date
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Assigned to ZEXEL VALEO CLIMATE CONTROL CORPORATION reassignment ZEXEL VALEO CLIMATE CONTROL CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FURUTA, SHUNICHI, KANAI, HIROSHI
Publication of US20060083628A1 publication Critical patent/US20060083628A1/en
Abandoned legal-status Critical Current

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    • 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 capacity compressor which is used for a supercritical refrigerating cycle.
  • various structures are known for a suction valve and a discharge valve of a swash plate type variable capacity compressor which compresses a refrigerant of a refrigerating cycle.
  • the discharge valve has a valve body press-contacted in an elastically deformed state to the valve seat of a discharge port.
  • the structure of this type of discharge valve is disclosed in, for example, Japanese Utility Model Laid-Open Publication No. Sho 61-44074 and Japanese Patent Application Laid-Open Publication No. 2001-153000.
  • the refrigerant of the refrigerating cycle is mixed with a lubricating oil, and it is necessary to consider the surface tension of the lubricating oil which enters the gap between the valve body and the valve seat in order to secure good opening and closing operations of the suction valve and the discharge valve.
  • the surface tension of the lubricating oil is important to secure the hermeticity of the valve but becomes a resistance when the valve body opens. Therefore, if the surface tension is larger than it is required, the valve body operates with delay, and vibrations and noises of the compressor increase.
  • Hei 7-180662 disclose a valve structure which is configured to leave a small gap between the valve body and the valve seat even when the valve body is in a closed state in order to deal with the problems.
  • the suction valve and the discharge valve of the swash plate type variable capacity compressor used for the refrigerating cycle were considered important to have a structure which should prevent vibrations, noises and the like.
  • a refrigerating cycle using CO 2 as the refrigerant has a very high inner pressure in comparison with the refrigerating cycle using a fleon refrigerant, and particularly a pressure on a high-pressure side happens to exceed the critical point of the refrigerant depending on use conditions such as a temperature.
  • the critical point is a limit on the high-pressure side (namely, a limit on a high-temperature side) in a state that a gas layer and a liquid layer coexist and is an end point at one end of a vapor pressure curve.
  • a pressure, a temperature and a density at the critical point become a critical pressure, a critical temperature and a critical density, respectively.
  • the pressure exceeds the critical point of the refrigerant in a radiator of the refrigerating cycle, the refrigerant does not condensate.
  • This type of supercritical refrigerating cycle is mounted on, for example, an automobile and used for air conditioning of the car interior.
  • a compressor to be used for the supercritical refrigerating cycle is also described in, for example, Japanese Patent Laid-Open Publication No. 2002-257037.
  • the compressor described in this publication is configured such that the piston stroke is variable depending on the inclination of a swash plate which is disposed rotatably.
  • the piston is held to be reciprocally movable in the cylinder, and the cylinder is provided with a suction valve for sucking a refrigerant and a discharge valve for discharging the refrigerant.
  • the refrigerant which circulates the refrigerating cycle is sucked into the cylinder through the suction valve, compressed and discharged out of the cylinder through the discharge valve.
  • the compressor is coupled with a motor vehicle engine and operated by the engine power.
  • the supercritical refrigerating cycle has a pressure resistance performance which is quite different from the conventional refrigerating cycle using the fleon refrigerant, and the compressor for the supercritical refrigerating cycle has been also demanded to have a more outstanding structure considering its pressure resistance performance and the like.
  • the compressor for the supercritical refrigerating cycle has a high operating pressure. Therefore, even a leakage of the refrigerant through a small gap degrades the performance.
  • the compressor described in this publication is provided with an elastic member which pushes the valve body of the suction valve against the valve seat to eliminate a gap which is produced between the valve body and the valve seat.
  • the compressor which is operated by the power of a motor vehicle engine, is important to secure a startup property when the driving engine is started.
  • this compressor when this compressor is compared with a compressor of the refrigerating cycle using a fleon refrigerant, the cylinder capacity becomes relatively small because of a problem of pressure resistance. Therefore, an influence of the leakage of the refrigerant at the suction valve or the discharge valve is conspicuous and the seat surfaces of the valve body and the valve seat also become small. And, there are problems that the lubricating oil which enters between them becomes rather insufficient, and good opening and closing operations of the valve body are hardly secured.
  • the refrigerant has a pressure of about 7.2 MPa in an atmosphere of 30° C. when the compressor is actuated.
  • the refrigerant has a pressure of about 0.67 MPa in an atmosphere of 30° C. when the compressor is actusted. Therefore, the compressor of the supercritical refrigerating cycle secures a high pressure resistance by setting the cylinder capacity and the port opening area small.
  • the compressor of the supercritical refrigerating cycle has a cylinder with a bore diameter of 15.0 to 21.0 mm, a capacity of 20 to 33 cm 3 , and a suction valve and a discharge valve with a port's opening area of 7.0 to 29.0 mm 2 .
  • the compressor of the refrigerating cycle using the fleon refrigerant has a cylinder with a bore diameter of 32 to 40 mm, a capacity of 90 cm 3 to 170 cm 3 , and a suction valve and a discharge valve with a port's opening area of 38.5 to 113.0 mm 2 .
  • the supercritical refrigerating cycle has a relatively large gap between the cylinder and the piston with respect to the cylinder capacity when the piston reaches the top dead center. This is also one of the causes to increase the number of rotations at the time of actuation of the supercritical refrigerating cycle.
  • the present invention has been made in view of the above circumstances and an object is to achieve an improvement of performance of a swash plate type variable capacity compressor for a supercritical refrigerating cycle.
  • the invention described in claim 1 of the present application is a swash plate type variable capacity compressor to be used for a supercritical refrigerating cycle comprising: a swash plate which is disposed rotatably, a piston which is coupled with the swash plate and a cylinder which holds the piston movably, the cylinder is provided with a suction valve for sucking a refrigerant of the supercritical refrigerating cycle and a discharge valve for discharging the refrigerant, wherein the suction valve has valve bodies having flexibility attached to suction ports for sucking the refrigerant, and the swash plate type variable capacity compressor has the valve bodies press-contacted in an elastically deformed state against the valve seats of the suction ports to decrease the number of rotations of the swash plate when the refrigerant is started to be compressed.
  • the performance of the swash plate type variable capacity compressor for a supercritical refrigerating cycle is improved securely.
  • the inventors of the present invention have prototyped various types of valve structures and conducted experiments in order to obtain a suitable valve structure for the swash plate type variable capacity displacement compressor for a supercritical refrigerating cycle. According to the conducted experiments, it was found that the elimination of the gaps between the valve bodies and the valve seats described above was more significant for the suction valve than for the discharge valve in view of the reduction of the number of rotations on startup. Further, the suction valve, which was most effective to secure a startup property, endurance and good opening and closing operations of the valve bodies, has the valve bodies having flexibility fitted to the suction ports for sucking the refrigerant and the valve bodies press-contacted in a slightly elastically deformed state against the valve seats of the suction ports. The valve bodies of the suction valve are designed considering an appropriate inner stress applied after fitting to the suction ports.
  • the cases that the valve bodies of the suction valve were press-contacted and not in an elastically deformed state against the valve seats were compared by experiments.
  • the number of rotations on startup in the case of press-contacted was 30 to 70% of that on startup in the case of not press-contacted.
  • the reduction of the number of rotations of the swash plate when the refrigerant is started to be compressed according to the present invention is based on the comparison with the case that the valve bodies of the suction valve are not press-contacted in an elastically deformed state against the valve seats.
  • the present invention has been made with attention paid to a quite significant structure in detail of the swash plate type variable capacity compressor used for a supercritical refrigerating cycle.
  • the swash plate type variable capacity compressor has achieved a conspicuous effect of considerably improving the performance of the compressor by devising a very simple structure.
  • the invention described in claim 2 of the present application is the swash plate type variable capacity compressor according to claim 1 , wherein the valve body has deflection of 1 mm or less when the valve bodies are fitted to the suction ports, and the valve bodies receive an external force of 1.8 N or less from the valve seats of the suction ports.
  • the seating property of the valve bodies and the valve seats can be secured finely, while securing the smooth opening and closing operations of the valve bodies, by determining the deflection of the valve bodies to 1 mm or less and the external force received by the valve bodies from the valve seats of the suction ports to 1.8 N or less.
  • the invention described in claim 3 of the present application is the swash plate type variable capacity compressor according to claim 1 or 2 , wherein the supercritical refrigerating cycle is a refrigerating cycle for air conditioning of a car interior to be mounted in an automobile, and the swash plate type variable capacity compressor is a clutchless compressor which is coupled with a motor vehicle engine without via a clutch.
  • the swash plate type variable capacity compressor of the present invention has securely reduced the number of rotations of the swash plate when the refrigerant is started to be compressed and can be used quite suitably as a clutchless compressor used for a refrigerating cycle for air conditioning of a car interior.
  • FIG. 1 is a diagram schematically showing a supercritical refrigerating cycle according to an embodiment of the present invention
  • FIG. 2 is a sectional view showing a swash plate type variable capacity compressor for a supercritical refrigerating cycle according to an embodiment of the present invention
  • FIG. 3 is a front view showing a valve plate and a cylinder-side valve body plate according to an embodiment of the present invention
  • FIG. 4 is a front view showing a valve plate and a rear housing-side valve body plate according to an embodiment of the present invention
  • FIG. 5 is a sectional view showing a suction valve and a discharge valve according to an embodiment of the present invention
  • FIG. 6 is an exploded sectional view showing a suction valve and a discharge valve according to an embodiment of the present invention
  • FIG. 7 is a sectional view showing a suction valve and a discharge valve according to an embodiment of the present invention.
  • FIG. 8 is a sectional view showing a suction valve and a discharge valve according to an embodiment of the present invention.
  • FIG. 9 is a comparative graph of the number of rotations on startup before and after an improvement according to an embodiment of the present invention.
  • FIG. 10 is a sectional view showing a suction valve and a discharge valve according to an embodiment of the present invention.
  • FIG. 11 is an exploded sectional view showing a suction valve and a discharge valve according to an embodiment of the present invention.
  • FIG. 12 is a sectional view showing a suction valve and a discharge valve according to an embodiment of the present invention.
  • FIG. 13 is an exploded sectional view showing a suction valve and a discharge valve according to an embodiment of the present invention.
  • a supercritical refrigerating cycle 1 of this embodiment is a refrigerating cycle for air conditioning of a car interior mounted on a car and provided with a swash plate type variable capacity compressor 10 which compresses a refrigerant, a radiator 20 which cools the refrigerant compressed by the compressor 10 , an expansion valve 30 which reduces the pressure to expand the refrigerant cooled by the radiator 20 , an evaporator 40 which evaporates the refrigerant decompressed by the expansion valve 30 , an accumulator 50 which separates the refrigerant flowed out of the evaporator 40 into a gas layer and a liquid layer and sends the refrigerant of the gas layer to the compressor 10 , and an inner heat exchanger 60 which performs heat exchange between a high-pressure side refrigerant and a low-pressure side refrigerant to improve the efficiency of the cycle.
  • the refrigerant CO 2 is used, a high-pressure side pressure of the supercritical refrigerating cycle 1 exceeds the critical point of the refrigerant depending on use conditions such as a temperature and the like. Further, the refrigerant contains the lubricating oil which smoothly drives the compressor 10 .
  • the swash plate type variable capacity compressor 10 of this embodiment is provided with a front housing 110 , a cylinder block 120 , a rear housing 130 , a valve plate 140 , a drive shaft 200 which is provided rotalably, a lag plate 300 which is provided on the drive shaft 200 , a swash plate 400 which is mounted on the drive shaft 200 and the lag plate 300 , a piston 500 which is coupled to the swash plate 400 via a shoe 410 , a cylinder 600 which holds the piston 500 to be movable reciprocally, and a control valve 700 which controls a pressure acting on the piston 500 .
  • This swash plate type variable displacement compressor 10 controls a discharge amount of the refrigerant by taking the refrigerant into the cylinder 600 , compressing and discharging it by moving the piston 500 reciprocally by rotating the swash plate 400 together with the drive shaft 200 and the lag plate 300 , and changing an inclination of the swash plate 400 and a stroke of the piston 500 by controlling a pressure of the control valve 700 acting on the piston 500 .
  • the piston 500 is set to have a minimum stroke which is about 5% or less of a maximum stroke.
  • the piston 500 and the cylinder 600 are in plural and at equal intervals about the axis of rotation of the drive shaft 200 .
  • the drive shaft 200 is installed in the front housing 110 and the cylinder block 120 via bearings. Further, the drive shaft 200 is coupled to an engine, which is a motor vehicle engine, without via a clutch.
  • the swash plate type variable capacity compressor 10 is a so-called clutchless compressor.
  • the interior of the front housing 110 is a crank chamber 111 in which the lag plate 300 and the swash plate 400 are disposed.
  • the cylinder block 120 is a member which constitutes a plurality of cylinders 600 .
  • the lag plate 300 is a member which is fixed to the drive shaft 200 and has an arm portion 310 , which couples the swash plate 400 , disposed on its required portion.
  • the swash plate 400 is provided with a guide portion 420 to which a shoe 410 is fitted, and mounted on the drive shaft 200 to be slidable and to have a variable inclined angle.
  • a spring 430 is disposed between the lag plate 300 and the swash plate 400 to push the swash plate 400 and the piston 500 toward the cylinder 600 to some extent.
  • the individual pistons 500 are tethered to the shoe 410 and in contact with a bore 610 of the cylinder 600 and are moved reciprocally with respect to the cylinder 600 when the swash plate 400 rotates.
  • the control valve 700 controls the inner pressure of the crank chamber 111 .
  • the inclination of the swash plate 400 and the stroke of the piston 500 are variable depending on the inner pressure of the crank chamber 111 .
  • the valve plate 140 is a member which constitutes a suction valve 150 for sucking the refrigerant into the cylinder 600 and a discharge valve 160 for discharging the refrigerant from the cylinder 600 , and which is disposed between the cylinder block 120 and the rear housing 130 .
  • a cylinder-side valve body plate 151 and a rear housing-side valve body plate 161 to be described in detail later are screwed to either surface of the valve plate 140 .
  • the individual cylinder blocks 120 are provided with the suction valve 150 and the discharge valve 160 by disposing the valve plate 140 .
  • the refrigerant is compressed between the piston 500 and the valve plate 140 .
  • the rear housing 130 mounts the control valve 700 and also constitutes a suction chamber 131 and a discharge chamber 132 with respect to the valve plate 140 .
  • a flow path for flowing the refrigerant is disposed at required portions of the compressor 10 , and a low-pressure gas before compression circulated through the refrigerating cycle 1 is guided into the suction chamber 131 .
  • the low-pressure gas in the suction chamber 131 is sucked into the cylinder 600 through the suction valve 150 when the piston 500 moves to return, and it becomes a high-pressure gas and is led into the discharge chamber 132 through the discharge valve 160 when the piston 500 moves forward.
  • the high-pressure gas in the discharge chamber 132 circulates the refrigerating cycle again.
  • the control valve 700 is communicated with the crank chamber 111 , the suction chamber 131 and the discharge chamber 132 through predetermined passages, and it is so configured that when the pressure of the low-pressure gas drops, a bellows provided in its interior swells to open the valve, and the high-pressure gas is guided to the crank chamber 111 . Further, when the pressure of the low-pressure gas increases, the bellows contracts to close the valve, and the high-pressure gas guided to the crank chamber 111 is cut off.
  • the swash plate 400 moves reciprocally in a state that the average of the inside pressures of the individual cylinders 600 and the inside pressure of the crank chamber 111 are balanced.
  • the inclination of the swash plate 400 and the stroke of the piston 500 are controlled by an opening degree of the control valve 700 , and the discharge amount of the high-pressure gas increases when the stroke of the piston 500 increases and decreases when it becomes small.
  • the pressure of the refrigerant at the time when the swash plate type variable capacity compressor 10 is actuated is about 7.2 MPa in an atmosphere at 30° C.
  • the bore 610 of the cylinder 600 has a diameter of 15.0-21.0 mm
  • the cylinder 600 has a volume of 20-33 cm 3
  • individual ports 141 , 142 at the suction valve 150 and the discharge valve 160 have an opening area of 7.0-29.0 mm 2 .
  • the valve plate 140 is a member which is provided with the plural suction ports 141 which communicate the individual cylinders 600 with the suction chamber 131 , and the plural discharge ports 142 which communicate the individual cylinders 600 with the discharge chamber 132 .
  • the cylinder-side valve body plate 151 is a member which is provided with plural valve bodies 152 of the suction valve 150 corresponding to the individual suction ports 141 , and plural holes 153 corresponding to the individual discharge ports 142 .
  • the rear housing-side valve body plate 161 is a member which is provided with plural valve bodies 162 of the discharge valve 160 corresponding to the individual discharge ports 142 , and plural holes 163 corresponding to the suction ports 141 (see FIG. 3 and FIG. 4 ).
  • the suction valve 150 of this embodiment has the valve bodies 152 having flexibility fitted to the suction ports 141 which suck the refrigerant into the cylinders 600 .
  • the valve bodies 152 of the suction valve 150 are press-contacted in a slightly elastically deformed state against one surface of the valve plate 140 as valve seats of the suction ports 141 .
  • the discharge valve 160 of this embodiment has the valve bodies 162 having flexibility fitted to the discharge ports 142 which discharge the refrigerant from the insides of the cylinders 600 .
  • the valve bodies 162 of the discharge valve 160 are press-contacted in a slightly elastically deformed state against the other surface of the valve plate 140 as valve seats of the discharge ports 142 .
  • 164 is a retainer which regulates the opening degree of the valve body 162 of the discharge valve 160 .
  • the retainer 164 is screwed to the valve plate 140 (see FIG. 5 ).
  • valve bodies 152 of the suction valve 150 formed on the cylinder-side valve body plate 151 are plastically deformed in a curved form to protrude the leading ends toward the valve plate 140 (see FIG. 6 ) to mount the cylinder-side valve body plate 151 on the valve plate 140 and are elastically deformed by force.
  • the valve bodies 152 are plastically deformed by pressing, and deflection ä 1 when attached to the suction ports 141 is 1 mm or less (more specifically, 50 to 200 ⁇ m).
  • a thickness of a material for the valve bodies 152 of the suction valve 150 is desirably 0.2-0.3 mm, and it is 0.25 mm in this embodiment.
  • This material has a modulus of longitudinal elasticity of about 2.06 ⁇ 10 5 N/mm 2 .
  • an external force P which is received by the valve bodies 152 of the suction valve 150 from the valve seats of the ports 141 is 1.8 Nor less to secure smooth opening and closing operations of the valve bodies 152 .
  • a more desirable range of the external force P is 1.2 N or less, and the most desirable range is 0.2-0.7 N.
  • the spring constant k of the valve body 152 is about 4.0 N/mm and deflection ä 1 is 150 ⁇ m, its external force P becomes about 0.6 N.
  • the spring constant k depends on the modulus of longitudinal elasticity of the material and the shape of the valve body 152 .
  • valve bodies 162 of the discharge valve 160 disposed on the rear housing-side valve body plate 161 is the same as that of the valve bodies 152 of the above-described suction valve 150 .
  • deflection ä 2 of the valve bodies 162 of the discharge valve 160 is 1 mm or less
  • the external force P which is received by the valve bodies 162 of the discharge valve 160 from the valve seats of the ports 142 is 1.8 N or less.
  • valve bodies 152 , 162 are coated with PTFE or the like in order to improve a seating property with the valve seats.
  • the valve bodies 152 of the suction valve 150 and the valve bodies 162 of the discharge valve 160 each perform opening and closing operations depending on a differential pressure between the crank chamber 111 , the suction chamber 131 and the discharge chamber 132 (see FIG. 7 and FIG. 8 ).
  • the inventors of the present invention have repeated comparative experiments about the number of rotations on startup under different conditions on the swash plate type variable capacity compressor 10 of this embodiment and one with its cylinder-side valve body plate 151 changed.
  • the changed cylinder-side valve body plate has a flat shape, and the valve bodies 152 of the suction valve 150 are not press-contacted in an elastically deformed state against the surface of the valve plate 140 as valve seats of the suction ports 141 .
  • the number of rotations of the swash plate type variable capacity compressor 10 of this embodiment at the time of actuation was in a range of 30 to 70% of that at the time of actuation of one with the cylinder-side valve body plate 151 changed.
  • FIG. 9 is a comparative graph of the number of rotations on startup before and after the exchange of the valve bodies of the suction valve, namely before and after the improvement. According to the experiment, the swash plate type variable capacity compressor 10 of this embodiment was proved that the number of rotations of the swash plate when the refrigerant was started to be compressed was decreased securely.
  • valve bodies 152 of the suction valve 150 and the shape of the valve bodies 162 of the discharge valve 160 can be changed their designs appropriately and are not limited to those exemplified in the drawings.
  • the valve bodies 152 of the suction valve 150 or the valve bodies 162 of the discharge valve 160 can also be structured to form their leading ends into a hemispherical shape such that the spherical surfaces are contacted to the edges of the circular suction ports 141 or discharge ports 142 .
  • the leading end may be formed by pressing.
  • valve bodies 152 of the suction valve 150 or the valve bodies 162 of the discharge valve 160 have a male screw part B, which is screw-engaged, with a female thread portion N which is formed in the valve plate 140 , to thereby elastically deform their leading ends in a state pressed against the edges of the suction ports 141 or the discharge ports 142 .
  • valve bodies 152 , 162 may also be structured as shown in FIG. 12 and FIG. 13 such that the flat valve bodies 152 , 162 are elastically deformed to press-contact against the surface of the curved valve plate 140 .
  • the plastic deformation of the valve bodies 152 , 162 can be omitted.
  • the swash plate type variable capacity compressor of the present invention can be used suitably as a compressor of a supercritical refrigerating cycle having a high-pressure side pressure exceeding the critical point of a 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)
US10/540,471 2002-12-27 2003-12-24 Swach plate type variable displayment compressor for supercritical refrigeration cycle Abandoned US20060083628A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2002380867 2002-12-27
JP2002380867 2002-12-27
PCT/JP2003/016638 WO2004061306A1 (fr) 2002-12-27 2003-12-24 Compresseur a cylindree variable de type a plateau oscillant concu pour un cycle de refrigeration supercritique

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

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US20080000348A1 (en) * 2004-12-23 2008-01-03 Bsh Bosch Und Siemens Hausgerate Gmbh Linear Compressor
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US20080008607A1 (en) * 2004-12-23 2008-01-10 Bsh Bosch And Siemens Hausgerate Gmbh Linear Compressor And Corresponding Drive Unit
US20080019852A1 (en) * 2004-12-23 2008-01-24 Jan Brand Linear Compressor
US20080089796A1 (en) * 2004-12-23 2008-04-17 Bsh Bosch Und Siemens Hausgerate Gmbh Linear Compressor And Corresponding Drive Unit
US20080152516A1 (en) * 2004-12-23 2008-06-26 Bsh Bosch Und Siemens Hausgerate Gbmh Compressor Housing
US20080267797A1 (en) * 2004-12-23 2008-10-30 Bsh Bosch Und Siemens Hausgerate Gmbh Linear Compressor
US20110113802A1 (en) * 2008-04-30 2011-05-19 Mitsubishi Electric Corporation Air conditioner
US20120237369A1 (en) * 2011-03-15 2012-09-20 Kabushiki Kaisha Toyota Jidoshokki Cylinder block of piston-type compressor and method for manufacturing the same
US20170291130A1 (en) * 2015-01-02 2017-10-12 Producteers A/S Automatic Filter Cleaning System
CN109611224A (zh) * 2018-11-30 2019-04-12 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
EP4089281A1 (fr) * 2021-05-13 2022-11-16 Walmsley Developments Pty Ltd Pompe portable

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DE102004062297A1 (de) 2004-12-23 2006-07-13 BSH Bosch und Siemens Hausgeräte GmbH Verdichter für ein Kältegerät
JP2007278180A (ja) * 2006-04-06 2007-10-25 Sanden Corp 往復動圧縮機
JP2009036069A (ja) * 2007-08-01 2009-02-19 Sanden Corp スクロール型流体機械
WO2009027001A1 (fr) * 2007-08-25 2009-03-05 Ixetic Mac Gmbh Machine à piston alternatif
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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EP1586774A4 (fr) 2011-03-09
EP1586774A1 (fr) 2005-10-19

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