EP3553315B1 - Discharge valve structure for compressor - Google Patents

Discharge valve structure for compressor Download PDF

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Publication number
EP3553315B1
EP3553315B1 EP17881648.4A EP17881648A EP3553315B1 EP 3553315 B1 EP3553315 B1 EP 3553315B1 EP 17881648 A EP17881648 A EP 17881648A EP 3553315 B1 EP3553315 B1 EP 3553315B1
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EP
European Patent Office
Prior art keywords
valve
discharge
end portion
valve seat
reed
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
EP17881648.4A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3553315A4 (en
EP3553315A1 (en
Inventor
Hiroyuki Ishida
Hideyuki Takahashi
Takayuki Endo
Hao He
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 Japan Co Ltd
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Valeo Japan Co Ltd
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 Valeo Japan Co Ltd filed Critical Valeo Japan Co Ltd
Publication of EP3553315A1 publication Critical patent/EP3553315A1/en
Publication of EP3553315A4 publication Critical patent/EP3553315A4/en
Application granted granted Critical
Publication of EP3553315B1 publication Critical patent/EP3553315B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04B27/12—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 having plural sets of cylinders or pistons
    • 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
    • F04B39/1066—Valve plates
    • 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

Definitions

  • the present invention relates to a compressor valve structure, and particularly, to a discharge valve structure in which a valve plate is disposed between a cylinder block and a cylinder head, wherein ports formed in the valve plate are opened and closed by reed valves.
  • a reciprocating compressor one that includes a cylinder block having formed therein cylinder bores; pistons which move reciprocally linearly in the cylinder bores; a cylinder head which, being provided on the opposite side of the cylinder block from the side on which the pistons are inserted, has formed demarcated therein a suction and a discharge chamber in which to temporarily store a working fluid; and a valve plate disposed between the cylinder block and the cylinder head, has been publicly known.
  • the cylinder bores and the suction and discharge chambers communicate with each other via ports provided in the valve plate, and the individual ports are opened and closed by valve elements (suction valves, discharge valves) each formed of a reed valve with elasticity.
  • the leading end portion of the reed valve comes into abutment with the valve plate, thereby blocking the circulation of a working fluid passing through the port (closed valve) .
  • the reed valve comes out of abutment with the valve plate due to the difference between the pressures of the working fluid which act on the leading ends of the reed valve, allowing the circulation of the working fluid (open valve).
  • the contact width in which the leading end of the reed valve comes into abutment with the valve plate preferably has a width enough to be sealable so as for the working fluid not to leak out, but if the area in which the leading end portion of the reed valve comes into contact with a valve seat portion is too large, there is a problem in that the reed valve is inhibited from opening due to the surface tension of a lubricant which is interposed between the leading end portion of the reed valve and the valve seat portion when the valve is closed, causing a decrease in performance or a vibration. For this reason, it is necessary to appropriately control the contact width in which the leading end of the reed valve comes into abutment with the valve plate.
  • annular groove 101 is formed around a port 100 in a valve plate 3 disposed between a cylinder block and a cylinder head, thereby forming an annular valve seat 102 on the periphery of the open end of the port 100, and a leading end portion 103a of a reed valve 103 is brought into abutment with the valve seat 102 elastically, thus opening and closing the port 100.
  • the outer edge of the leading end portion 103a of the reed valve 103 is brought into coincidence with the outer edge of the valve seat 102 (the inner edge of the annular groove 101), thus preventing the leading end portion 103a of the reed valve 103 from sticking out into the annular groove 101.
  • a compressor having a discharge valve structure according to the preambe of claim 1 is known from JP-A-2011-226464 .
  • the speed at which the leading end portion of the reed valve 103 when closed hits against the valve seat 102 is very high, and so when the area of abutment with the valve seat 102 is small, the reed valve 103 hits against the valve seat 102 at a high speed, so that a high surface pressure acts momentarily on the surface of the valve seat 102 with which the reed valve 103 is in abutment.
  • the invention having been contrived taking into consideration these circumstances, has for its principal problem to provide a compressor valve structure wherein no break occurs in a reed valve or a valve seat even when in high speed operation, and a stiction of the reed valve caused by a lubricant can also be reduced, enabling a stable operation to be maintained.
  • the compressor valve structure according to the invention is a valve structure used in a compressor, which includes a cylinder block having formed therein cylinder bores; pistons which move reciprocally linearly in the cylinder bores; a cylinder head having formed therein a space in which to temporarily store a working fluid; a valve plate which, being provided between the cylinder block and the cylinder head, has formed therein ports which provide communication between the cylinder bores and the space; and reed valves which open and close the ports in the valve plate, wherein an annular valve seat with which each of the reed valves comes into abutment is provided on the periphery of the open end of each of the ports in the valve plate, the radial width of the valve seat is formed to be larger on the side corresponding to the leading end portion of the reed valve than on the side corresponding to the base end portion of the reed valve, and the outer edge of the leading end portion of the reed valve is positioned
  • the outer edge of the leading end portion of the reed valve is positioned inside the outer edge of the valve seat, with the reed valve closing the port, it is difficult for a lubricant to flow into between the reed valve and the valve seat along the outer edge of the reed valve, reducing the problem of a stiction of the reed valve (the problem of a disorder of valve opening timing due to the adhesion of the lubricant), and at the same time, the whole of the valve seat surface does not serve as an adsorption surface even when the lubricant flows into between the reed valve and the valve seat, so that it is possible to suppress the disorder of valve opening timing due to the adhesion of the lubricant.
  • valve seat may be formed by providing a plurality of inconsecutive recesses around the port in the valve plate, but the dimensional control of the valve plate is cumbersome, and so an annular valve seat may be formed on the periphery of the opening of the port by forming an annular groove around the port in the valve plate.
  • the reed valve is formed so that a moment of inertia of area of the base end side thereof is higher than a moment of inertia of area of the leading end side.
  • the moment of inertia of area of the base end side is made higher by gradually increasing the width of the reed valve as it goes from the leading end portion to the base end portion.
  • the leading end side radial width of the reed valve is formed to be larger than the base end side radial width, and at the same time, the outer edge of the leading end portion of the reed valve is positioned inside the outer edge of the valve seat, so that it is possible, by effectively increasing the contact area of the reed valve on the leading end side which has a high power of impact when the valve is closed, to reduce the surface pressure between the reed valve and the valve seat when the valve is closed. Because of this, it is possible to avoid a problem in that the reed valve is broken, or the valve seat is damaged, by the power of impact generated when the reed valve hits against the valve seat.
  • Fig. 1 shows a piston type compressor 1 using the valve structure according to the present invention.
  • the piston type compressor 1 is configured having a cylinder block 2, a cylinder head 4 which is assembled to the rear side of the cylinder block 2 via a valve plate 3, and a front housing 6 which, being assembled so as to cover the front side of the cylinder block 2, defines a crankcase 5 on the front side of the cylinder block 2.
  • the front housing 6, cylinder block 2, valve plate 3, and cylinder head 4 are axially fastened by not-shown fastening bolts, configuring a housing 7 of the compressor.
  • a drive shaft 8 disposed in the crankcase 5 is rotatably retained in the front housing 6 and the cylinder block 2 via a bearing 9 (only the cylinder block side thereof is shown) .
  • the drive shaft 8 protrudes from the front housing 6 and is connected to a not-shown travelling engine via a belt and a pulley, and the power of the travelling engine is transmitted to the drive shaft 8, causing the drive shaft 8 to rotate.
  • Single head pistons 13 are reciprocally slidably inserted in their respective cylinder bores 12.
  • a swash plate 14 which rotates in synchronism with the rotation of the drive shaft 8 is provided on the drive shaft via a hinge ball 15.
  • Engaging portions 13a of the single head pistons 13 are retained in engagement with the peripheral portion of the swash plate 14 via a pair of shoes 16 provided one on each of the front and back of the swash plate peripheral portion.
  • a suction port 20 and a discharge port 30 are formed in the valve plate 3 so as to correspond to each of the cylinder bores 12. Also, a suction chamber 18, in which to store a working fluid to be supplied to the compression chambers 17, and a discharge chamber 19, in which to store the working fluid discharged from the compression chambers 17, are demarcated in the cylinder head 4.
  • the suction chamber 18 is formed in the central portion of the cylinder head 4, and the discharge chamber 19 is annularly formed around the suction chamber 18.
  • the suction chamber 18 can communicate with the compression chambers 17 via the suction ports 20 which are opened and closed by respective suction valves 21 to be described hereafter.
  • the discharge chamber 19 can communicate with the compression chambers 17 via the discharge ports 30 which are opened and closed by respective discharge valves 31 to be described hereafter.
  • a suction valve seat 22 which is superimposed on and attached to the cylinder block side end surface of the valve plate 3 and has formed therein the suction valves 21, and a gasket 23, which is superimposed on the suction valve seat 22 and is sandwiched and fixed between the valve plate 3 and the cylinder block 2, are provided between the valve plate 3 and the cylinder block 2.
  • a discharge valve seat 32 which is superimposed on and attached to the cylinder head side end surface of the valve plate 3 and has formed therein the discharge valves 31, and a gasket 34, which is superimposed on the discharge valve seat 32 and is sandwiched and fixed between the valve plate 3 and the cylinder head 4 and with portions of which opposite to the discharge valves 31 retainers 33 are formed integrally, are provided between the valve plate 3 and the cylinder head 4.
  • the cylinder block 2, gasket 23, suction valve seat 22, valve plate 3, discharge valve seat 32, gasket 34, and cylinder head 4 are positioned by not-shown positioning pins and fixed pressed against each other by the fastening bolts which fasten the component members of the housing 7.
  • the suction chamber 18 communicates with a not-shown suction opening which is connected to the low-pressure side (the outlet side of an evaporator) of an external refrigerant circuit via a suction passage which is radially extended so as to pass through the discharge chamber 19.
  • the discharge chamber 19 communicates with a discharge space 41, which is formed in the peripheral wall portion of the cylinder block 2, via a passage formed in the gasket 34, valve plate 3, suction valve seat 22, gasket 23, and cylinder block 2.
  • the discharge space 41 is defined by the cylinder block 2 and a covering 42 attached thereto and is connected to the high-pressure side (the inlet side of a radiator) of the external refrigerant circuit via a discharge opening 43 formed in the covering 42.
  • the suction valve seat 22 being superimposed on and attached to the cylinder block side end surface of the valve plate 3 shown in Fig. 2 (a) , is configured having an aggregation of the plurality of suction valves 21 which open and close the respective suction ports 20, as shown in Fig. 2 (b) .
  • the suction valves 21 are circumferentially formed at predetermined spaced intervals so as to correspond to the number of cylinder bores 12, and through holes 28 through which to insert the fastening bolts, through holes through which to insert the not-shown positioning pins, and the like, are formed, in the suction valve seat 22.
  • a through hole 24 which avoids interference with the suction port 30 is formed in the base end portion of each of the suction valves 21.
  • Each of the suction valves 21 is configured of a partial portion of the suction valve seat 22, and by forming a U-shaped punched-out slit 25 in the vicinity of the periphery of the suction valve seat 22, is integrally extended from radially outside to inside. That is, a leading end portion 21a of each of the suction valves 21 is disposed radially inside a base end portion 21b (the leading end portion 21a is disposed so as to be closer to the center of the suction valve seat 22 than the base end portion 21b).
  • Each of the suction valves 21 is formed as a cantilevered reed valve, and as shown in Fig. 3 , too, the leading end portion 21a is made to serve as a seat portion which is seated on a valve seat 26 formed around the suction port 20 in the valve plate 3.
  • Through holes which avoid interference with the cylinder bores 12 are circumferentially formed at predetermined spaced intervals so as to correspond to the number of cylinder bores 12, and through holes through which to insert the fastening bolts, through holes through which to insert the positioning pins, and the like, are formed, in the gasket 23 interposed between the suction valve seat 22 and the cylinder block 2.
  • the discharge valve seat 32 being superimposed on and attached to the cylinder head side end surface of the valve plate 3 shown in Fig 4(a) , is configured having an aggregation of the plurality of discharge valves 31 which open and close the respective discharge ports 30, as shown in Fig. 4(b) .
  • the discharge valves 31 are circumferentially formed at predetermined spaced intervals so as to correspond to the number of cylinder bores 12. Also, through holes 35 which avoid interference with the suction ports 20, not-shown through holes through which to insert the positioning pins, and the like, are formed in the discharge valve seat 32.
  • Each of the discharge valves 31, being configured of a partial portion of the discharge valve seat 32, is integrally radially extended from the seat central portion. That is, a leading end portion 31a of each of the discharge valves 31 is disposed radially outside a base end portion 31b (the leading end portion 31a is disposed so as to be farther away from the center of the discharge valve seat 32 than the base end portion 31b) .
  • Each of the discharge valves 31 is formed as a cantilevered reed valve, and as shown in Fig. 5 , too, the leading end portion 31a is made to serve as a seat portion which is seated on a valve seat 36 formed around the discharge port 30 in the valve plate 3.
  • Through holes which avoid interference with the suction ports 20 are circumferentially formed at predetermined spaced intervals so as to correspond to the number of cylinder bores, and through holes through which to insert the fastening bolts, through holes through which to insert the positioning pins, and the like, are formed, in the gasket 34 interposed between the discharge valve seat 32 and the cylinder head 4, and each of the retainers 33 is formed integrally with the portion of the gasket 34 opposite to the discharge valve 31 so as to separate gradually from the discharge valve 31 as it goes from the base end portion 31b to the leading end portion 31a of the discharge valve 31.
  • valve seat 26, on which the suction valve 21 is seated, and the valve seat 36, on which the discharge valve 31 is seated, are formed integrally with the periphery of the opening of the suction port 20 and with the periphery of the opening of the discharge port 30, respectively, in the valve plate 3.
  • Fig. 6 shows a valve structure wherein the valve seat 36 on which the discharge valve 31, out of the two valves, is seated is formed integrally with the valve plate 3, and hereafter, a description will be given, focusing on the valve structure on this discharge side.
  • the valve seat 36 by forming an annular groove 37 around the discharge port 30 in the valve plate 3, is annularly formed on the periphery of the opening of the discharge port 30, and is formed flush with the cylinder head side end surface of the valve plate 3.
  • the valve seat 36 is not formed having a uniform width (radial width) all over the circumference, and the radial width thereof is set to increase toward the leading end side of the discharge valve (reed valve) 31 (the radial width of the valve seat 36 corresponding to the leading end side of the discharge valve 31 is set to be larger than the radial width corresponding to the base end side).
  • the radial width of the valve seat 36 is formed to increase gradually as it goes from radially inside to outside the valve plate 3. Also, in this example, an outer edge of the valve seat 36 is formed in a continuous circular arc curve.
  • the circular-arc outer edge of the leading end portion of the discharge valve 31 is formed so as to be positioned inside the outer edge of the valve seat 36, that is, inside the inner edge of the annular groove 37. Because of this, the outer edge of the leading end portion of the discharge valve 31 is brought into abutment with a wide valve seat surface, which corresponds to the leading end side of the discharge valve 31, without sticking out into the annular groove 37.
  • valve seat 36 has all over the circumference a uniform width which is the same as the leading end side width of the discharge valve 31 (even though the radial width of the valve seat 36 corresponding to the base end side of the discharge valve 31 has as large a width as the width corresponding to the leading end side), the same advantageous effect can be obtained in that the leading end side contact area of the leading end portion 31a of the discharge valve 31 is increased, reducing stress.
  • the width of the valve seat 36 corresponding to the base end portion of the discharge valve 31 is formed to be smaller than the width corresponding to the leading end side, coupled with the fact that the outer edge of the leading end portion of the discharge valve 31 is positioned inside the outer edge of the valve seat 36, it does not happen that the area of contact between the discharge valve 31 and the valve seat 36 increases in excess, and thus the above-described concern does not arise.
  • the discharge valve 31, by the width thereof being formed to increase gradually as it goes from the leading end portion to the base end portion, is configured so that a moment of inertia of area of the base end side is made higher than a moment of inertia of area of the leading end side.
  • Figs. 7 and 8 are diagrams wherein the behaviors of the pressure (cylinder pressure) in the compression chamber 17, and of the opening height (valve lift) of the discharge valve, with respect to the rotation angle of the shaft, at high speed operation, are analytically calculated. These examples use as analysis conditions the rotation speed: 9000 rpm, the discharge chamber pressure: 15 bar, the suction pressure: 2 bar, and the maximum opening height (maximum opening degree) of the discharge valve: 1 mm.
  • the opening degree of the discharge valve 31 changes under the influence of the inertial force deriving from the discharge valve's own mass in addition to the balance between the force based on the difference between the pressures acting on the front and back of the valve (the difference between the cylinder pressure and the discharge chamber pressure) and the spring force of the discharge valve 31, and when the discharge valve 31 reaches the retainer 33, the opening degree of the discharge valve 31 is maintained at the maximum opening degree (in the drawing, at the rotation angle shown by II).
  • the speed of the piston 13 decreases toward the top dead center, and so the cylinder pressure starts to drop. Then, when the force based on the difference between the pressures acting on the front and back of the discharge valve 31 cannot exceed the spring force of the discharge valve 31 when at the maximum opening degree, the opening degree of the discharge valve 31 starts to decrease (in the drawing, at or after the rotation angle shown by III).
  • the opening degree of the discharge valve 31 changes under the influence of the inertial force deriving from the discharge valve's own mass in addition to the balance between the force based on the difference between the pressures acting on the front and back of the valve (the difference between the cylinder pressure and the discharge chamber pressure) and the spring force of the discharge valve 31, and when the discharge valve 31 reaches the retainer 33, the opening degree of the discharge valve is confined at the maximum opening degree (in the drawing, at the angle of rotation shown by II'). Even in this kind of discharge valve 31, as the moment of inertia of area of the base end side is higher than the leading end side one, the time at which a maximum lift is reached is more delayed than heretofore known.
  • the opening degree of the discharge valve 31 starts to decrease (in the drawing, at or after the angle of rotation shown by III') .
  • the discharge valve 21 is formed so that the moment of inertia of area of the base end side is higher than the leading end side one, the discharge valve 31 starts to be closed earlier than the heretofore conventional discharge valve. Also, as the leading end portion side width of the valve is smaller than the base end portion side width, the leading end portion side mass of the valve is not so large, and the response speed of the discharge valve can be effectively increased.
  • the discharge side valve structure has heretofore been described, but as for the radial width of the valve seat, the suction side valve structure also adopts the same configuration, and thereby it is possible to exert the same working effect.
  • valve seat 26 on which the leading end portion 21a of the suction valve 21 is seated is annually formed on the periphery of the opening of the suction port 20 by forming the annular groove 27 around the suction port 20 in the valve plate 3, as shown in Fig. 2 , while the suction valve 21 is extended from radially outside to inside the suction valve seat 22, and the leading end portion 22a is positioned radially inside the base end portion 22b, so that the radial width of the valve seat 26 is formed to increase gradually as it goes from the base end side to the leading end side of the suction valve 21 (as it goes from radially outside to inside the valve plate 3). Also, with the suction port 20 being closed by the suction valve 21, the outer edge of the leading end portion 21a of the suction valve 21 may be positioned inside the outer edge of the valve seat 26.
  • the radial width of the valve seat 26 corresponding to the base end side of the suction valve 21 is formed to be smaller than that on the side corresponding to the leading end portion of the suction valve 21, it is possible to reduce the stiction of a lubricant, and thus possible to reduce a disorder of valve opening timing.
  • the width is formed to increase gradually as it goes from the leading end portion to the base end portion of the reed valve (discharge valve 31), thereby making the moment of inertia of area of the base end side of the reed valve (discharge valve 31) higher than the moment of inertia of area of the leading end, but the mode of increasing the moment of inertia of area of the base end side not being limited to this, for example, even though not covered by the present invention, the thickness of the reed valve may be gradually increased toward the base end side.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP17881648.4A 2016-12-12 2017-12-08 Discharge valve structure for compressor Active EP3553315B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016240052 2016-12-12
PCT/JP2017/044187 WO2018110449A1 (ja) 2016-12-12 2017-12-08 圧縮機の弁構造

Publications (3)

Publication Number Publication Date
EP3553315A1 EP3553315A1 (en) 2019-10-16
EP3553315A4 EP3553315A4 (en) 2020-04-29
EP3553315B1 true EP3553315B1 (en) 2021-07-07

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ID=62559144

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Application Number Title Priority Date Filing Date
EP17881648.4A Active EP3553315B1 (en) 2016-12-12 2017-12-08 Discharge valve structure for compressor

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EP (1) EP3553315B1 (ja)
JP (1) JPWO2018110449A1 (ja)
CN (1) CN110073105B (ja)
WO (1) WO2018110449A1 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021125838A1 (de) 2021-10-05 2023-04-06 Solo Kleinmotoren Gmbh Kolben-Hochdruckpumpe mit kleinem Fördervolumen

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7241915B2 (ja) * 2019-12-04 2023-03-17 三菱電機株式会社 圧縮機
CN114251252A (zh) * 2021-12-24 2022-03-29 广东美芝制冷设备有限公司 阀片、阀组件、压缩机以及制冷系统

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60222577A (ja) * 1984-04-20 1985-11-07 Tokico Ltd 圧縮機
US5586874A (en) * 1994-11-15 1996-12-24 Sanden Corporation Reed valve arrangement for a reciprocating compressor
JP2002242837A (ja) * 2001-02-14 2002-08-28 Sanyo Electric Co Ltd 冷媒圧縮機
JP4872480B2 (ja) * 2006-06-23 2012-02-08 パナソニック株式会社 圧縮機
JP2010169077A (ja) 2008-12-25 2010-08-05 Toyota Industries Corp 圧縮機
JP5559720B2 (ja) * 2010-03-31 2014-07-23 株式会社豊田自動織機 圧縮機
JP5652613B2 (ja) * 2011-03-08 2015-01-14 サンデン株式会社 圧縮機の弁装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021125838A1 (de) 2021-10-05 2023-04-06 Solo Kleinmotoren Gmbh Kolben-Hochdruckpumpe mit kleinem Fördervolumen

Also Published As

Publication number Publication date
WO2018110449A1 (ja) 2018-06-21
CN110073105A (zh) 2019-07-30
EP3553315A4 (en) 2020-04-29
CN110073105B (zh) 2021-12-03
JPWO2018110449A1 (ja) 2019-10-24
EP3553315A1 (en) 2019-10-16

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