EP2489877A1 - Compresseur - Google Patents

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Publication number
EP2489877A1
EP2489877A1 EP10823374A EP10823374A EP2489877A1 EP 2489877 A1 EP2489877 A1 EP 2489877A1 EP 10823374 A EP10823374 A EP 10823374A EP 10823374 A EP10823374 A EP 10823374A EP 2489877 A1 EP2489877 A1 EP 2489877A1
Authority
EP
European Patent Office
Prior art keywords
suction
valve
valve plate
pressure chamber
gap
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.)
Withdrawn
Application number
EP10823374A
Other languages
German (de)
English (en)
Inventor
Keigo Usui
Yusuke Ise
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.)
Marelli Corp
Original Assignee
Calsonic Kansei Corp
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 Calsonic Kansei Corp filed Critical Calsonic Kansei Corp
Publication of EP2489877A1 publication Critical patent/EP2489877A1/fr
Withdrawn legal-status Critical Current

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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
    • F04B27/1009—Distribution members

Definitions

  • the present invention relates to a compressor, especially, to a compressor that has a suction valve for opening and closing a suction hole of a valve plate.
  • a swash plate type variable capacity compressor is disclosed.
  • a valve plate is provided between a cylinder block on which plural cylinder bores are formed and a rear housing in which a high-pressure chamber and a low-pressure chamber are formed.
  • suction holes for communicating the cylinder bores with the low-pressure chamber.
  • suction valve for opening and closing the suction hole.
  • discharge holes for communicating the cylinder bores with the high-pressure chamber.
  • a discharge valve for opening and closing the discharge hole.
  • the suction valves are bent toward the cylinder bores due to a suctioning operation of pistons to open the suction holes, so that refrigerant is suctioned from the low-pressure chamber to the cylinder bores.
  • the discharge valves are bent toward the high-pressure chamber due to a discharging operation of the pistons to open the discharge holes, so that high-pressure refrigerant in the cylinder bores is discharged to the high-pressure chamber.
  • a stroke displacement of the pistons changes according to a tilting angle of a swash plate, so that a capacity of refrigerant to be compressed changes.
  • suctioning refrigerant into the cylinder bores and compressing the refrigerant in the cylinder bores are sequentially done, and then the high-pressure refrigerant is discharged to the high-pressure chamber.
  • lubrication oil is mixed in refrigerant to keep lubricity within the compressor. Therefore, the lubrication oil infiltrates between an opening edge portion of the suction hole on the valve plate and the suction valve, so that it is concerned that the suction valve may be fixed on the valve plate. In this case, a desired volume of refrigerant cannot be suctioned into the cylinder bores upon suctioning. In addition, if the suction valve that had been fixed on the valve plate suddenly separates from the valve plate, noises may be generated.
  • Patent Document 2 disclosed is a compressor in which suction valves are prevented from fixing on a valve plate by providing gaps between the suction valves and the valve plate.
  • An object of the present invention is to provide a compressor that can supply a desired volume of refrigerant into a cylinder bore without a fixation of a suction vale on a valve plate and can be easily produced.
  • An aspect of the present invention provides a compressor that includes a front housing that has a crank chamber therein; a cylinder block that is fixed with the front housing and has a cylinder bore therein; a rear housing that is fixed with the cylinder block with interposing a valve plate therebetween and includes a low-pressure chamber and a high-pressure chamber therein; the valve plate that is provided between the cylinder block and the rear housing and on which a suction hole for communicating the cylinder bore and the low-pressure chamber is formed; and a suction valve disk that is attached on a side of the valve plate facing to the cylinder block and has a suction valve for opening and closing the suction hole, wherein a gap with a predetermined width is provided between the suction valve disk and an opening edge portion of the suction hole, and the width of the gap is set to 13 to 15% of a thickness of the suction valve disk.
  • the gap is provided between the opening edge portion of the suction hole and the suction valve and the width of the gap is set to 13 to 15% of the thickness of the suction valve disk, so that a fixation of the suction valve on the valve plate can be prevented. Therefore, noise-and-vibration performance can improve and thereby generation of undesired noises can be prevented.
  • the fixation of the suction valve on the valve plate can be prevented, a desired volume of refrigerant can be surely supplied into the cylinder bore.
  • the width of the gap is 0.065 to 0.175mm when it is presented not as a relative value to the thickness of the suction valve disk but as an absolute value. According to this, the above-explained advantages can be achieved.
  • a groove is provided outside the opening edge portion. According to this, the fixation of the suction valve on the valve plate can be further prevented by introducing refrigerant gas into the groove.
  • the gap is formed by a press working. According to this, it can be easily produced without using extra parts and can reduce a production cost.
  • a compressor 100 includes a housing 1, a valve plate 5 and a suction valve disk 12.
  • the valve plate 5 is assembled in the housing 1.
  • the suction valve disk 12 includes suction valves 11 for opening and closing suction holes 10 that communicate with a low-pressure chamber 8.
  • the suction holes 10 are provided closer to a center of the valve plate 5, and discharge holes 16 are provided closer to an outer circumference of the valve plate 5 (see Fig. 5 ).
  • the housing 1 is comprised of a front housing 2, a cylinder block 3 and a rear housing 4.
  • a crank chamber 6 is formed in the front housing 2.
  • the cylinder block 3 is fixed with the front housing 2.
  • Plural cylinder bores 7 are arranged in the cylinder block 3.
  • the rear housing 4 is fixed with the cylinder block 3, and includes the low-pressure chamber 8 for suctioning refrigerant and a high-pressure chamber 9 for discharging compressed refrigerant.
  • the six cylinder bores 7 are formed in the cylinder block 3 along its circumferential direction.
  • the plural cylinder bores 6 are formed about a drive shaft 30 at even intervals.
  • Pistons 31 each of which is reciprocated are accommodated in the cylinder bores 7, respectively.
  • the pistons 31 are coupled with a swash plate 32 that rotates in the crank chamber 6.
  • the low-pressure chamber 8 In the rear housing 4, formed are the low-pressure chamber 8 and the high-pressure chamber 9 for refrigerant gas.
  • the low-pressure chamber 8 is connected to an outlet side of a not-shown evaporator on a refrigeration cycle.
  • the high-pressure chamber 9 is connected to an inlet side of a not-shown condenser on the refrigeration cycle.
  • the valve plate 5 is provided between the cylinder bores 7 and the rear housing 4.
  • the suction holes 10 are formed closer to the center on the valve plate 5 with associated with the six cylinder bores 7, and the suction holes 16 are formed closer to the outer circumference. As explained above, the suction holes 10 is opened and closed by the suction valves 11, and the discharge holes 11 are opened and closed by the discharge valves 17.
  • a drive mechanism 33 is rotatably supported.
  • a pulley 34 that receives a drive force from a not-shown engine is supported via a bearing 35, and an end of the drive shaft 30 is rotatably supported.
  • the pulley 34 and the drive shaft 30 are engaged and disengaged by a magnetic clutch.
  • the drive shaft 30 is provides so as to penetrate the crank chamber 6. As explained above, the drive shaft 30 is rotated by receiving the drive force from the pulley 34.
  • a lug plate 37 is provided in the crank chamber 6, and integrally fixed with the drive shaft 30.
  • a journal 39 to which the swash plate 32 is fixed is attached to the drive shaft 30.
  • the lug plate 37 and the journal 39 are coupled with each other via a link mechanism 38. Due to a rotation of the drive shaft 30, the lug plate 37 transfers the drive force to the journal 39 through the link mechanism 38.
  • the pistons 31 are coupled to a circumference of the swash plate 32 that is fixed with the journal 39, and the pistons 32 reciprocate due to the rotation of the drive shaft 30. Refrigerant is compressed by the reciprocation of the pistons 31.
  • valve plate 5 and the suction valve disk 12 will be explained in detail with reference to Figs. 2 to 6 .
  • the valve plate 5 is a circular plate, and the six discharge holes 16 are formed closer to its outer circumference at even intervals along its circumferential direction. These discharge holes 16 communicate the six cylinder bores 7 in the cylinder block 3 with the high-pressure chamber 9 in the rear housing 4.
  • the six suction holes 10 are formed, on an inward side of the six discharge holes 16, at even intervals along its circumferential direction. These suction holes 10 communicate the six cylinder bores 7 in the cylinder block 3 with the low-pressure chamber 8 in the rear housing 4.
  • the suction valve disk 12 is provided on one side of the valve plate 5 facing to the cylinder block 3, and a discharge valve disk 22 is provided on another side of the valve plate 5 facing to the rear housing 4.
  • the suction valve disk 12 opens the suction hole(s) 10 when suctioning refrigerant into the cylinder bore (s) 7, and closes the suction hole(s) 10 when compressing refrigerant in the cylinder bore(s) 7.
  • the discharge valve disk 22 opens the discharge hole (s) 16 when compressing refrigerant in the cylinder bore (s) 7, and closes the discharge hole (s) 16 when suctioning refrigerant into the cylinder bore(s) 7.
  • the suction valve disk 12 is constituted by a circular thin plate-shaped disk base 15, the suction valves 11 provided along a circumferential direction of the disk base 15 at even intervals, and communication holes 19 that are communicated with the discharge holes 16 on the valve plate 5.
  • the suction valve 10 is comprised of a valve body 18 provided at an inward of a U-shaped slit 20 and a pair of bridging portions 21 that connects the valve body 18 with the disk base 15 between the communication hole 19 and the slit 20.
  • a gap 14 having a predetermined width is formed between the suction valve disk 12 and an opening edge portion 23 of the suction hole 10.
  • the width S of this gap 14 is set to 13 to 15% of a thickness t of the suction valve disk 12.
  • the gap 14 is formed by reducing a thickness of the opening edge portion 23 smaller than that of a base portion 5a of the valve plate 5.
  • the gap 14 is set within a range of the predetermined width 0.065 to 0.175mm.
  • a groove 13 surrounding the suction hole 10 is formed around the suction hole 10.
  • the opening edge portion 23 is formed between the groove 13 and the suction hole 10.
  • a thickness of the valve plate 5 associated with the groove 13 is smaller than the thickness of the opening edge portion 23.
  • Fig. 6 shows measurement results under a representative condition about noise-and-vibration performance and compressor performance with respect to the width S of the gap 14. Its horizontal axis refers to the width S of the gap 14, its vertical right axis refers to noise-and-vibration performance as pulsation ( ⁇ Ps), and its vertical left axis refers to compressor performance (Gr).
  • a line A indicates a criterion for noise-and-vibration performance, and a line B indicates a criterion for compressor performance.
  • a line C indicates a measurement result of noise-and-vibration performance of the suction valve 11
  • a line D indicates a measurement result of compressor performance.
  • a portion of the line C beyond the noise-and-vibration performance criterion A doesn't meet the performance criterion, so that generated noises and vibrations may become problems.
  • a portion of the line C below the noise-and-vibration performance criterion A meets the performance criterion, so that generated noises and vibrations may not become problems. Therefore, where the line C runs above the noise-and-vibration performance criterion A, i.e. when the width S is less than 0.065mm, the noise-and-vibration performance may have problems. But, when the width S is not less than 0.065mm, the noise-and-vibration performance may not have problems.
  • a minimum value for the width S of the gap 14 is determined, so that the minimum width S of the gap 14 between the suction valve 11 and the opening edge portion 23 is set to 0.065mm.
  • a portion of the line D located beyond the compressor performance criterion B meets the performance criterion, so that a desired volume of refrigerant can be supplied into the cylinder bores 7.
  • a portion of the line D below the compressor performance criterion B doesn't meet the performance criterion, so that the desired volume of refrigerant cannot be supplied into the cylinder bores 7. Therefore, where the line C runs under the compressor performance criterion B, i.e. when the width S is more than 0.175mm, the compressor performance may have problems. But, when the width S is not more than 0.175mm, the compressor performance may not have problems.
  • a maximum value for the width S of the gap 14 is determined, so that the maximum width S of the gap 14 between the suction valve 11 and the opening edge portion 23 is set to 0.175mm.
  • the predetermined width S of the gap 14 is set within a range of 0.065 to 0.175mm, the noise-and-vibration performance and the compressor performance can be met and the fixation of the suction valves 11 on the valve plate 5 can be prevented.
  • the range of the predetermined width S of the gap 14 is set in the range within 0.065 to 0.175mm as explained above.
  • a minimum value of the thickness t of the valve plate 5 i.e. a minimum thickness required for functioning as the valve plate 5
  • a maximum value of the thickness t of the valve plate 5 i.e. a maximum thickness capable of being installed in a compressor
  • a ratio (S/t) of the minimum value 0.065mm of the predetermined width S to the maximum value 0.5mm of the thickness t is about 13%.
  • a ratio ( S / t ) of the maximum value 0.175mm of the predetermined width S to the minimum value 0.3mm of the thickness t is about 50%.
  • the width S of this gap 14 between the suction valve disk 12 and the opening edge portion 23 of the suction hole 10 on the valve plate 5 is set to 13 to 15% of the thickness t of the suction valve disk 12.
  • the suction hole 10 is closed by the suction valve 11 on the side of valve plate 5 facing to the cylinder block 3.
  • the discharge hole 16 is closed by the discharge valve 17 on the other side facing to the rear housing 4.
  • the gap 14 is provided between the opening edge portion 23 of the suction hole 10 and the suction valve 11 and the gap 14 is set with the range of 13 to 15% of the thickness of the suction valve disk 12 (0.065 to 0.175mm), so that the fixation of the suction valve 11 on the valve plate 5 can be prevented. Therefore, noise-and-vibration performance can improve and thereby generation of undesired noises can be prevented. In addition, since the fixation of the suction valve 11 on the valve plate 5 can be prevented, the desired volume of refrigerant can be surely supplied into the cylinder bores 7.
  • the fixation of the suction valve 11 on the valve plate 5 can be further prevented by introducing refrigerant gas into the groove 13.
  • the gap 14 is formed by a press working, it can be easily produced without using extra parts and can reduce a production cost.
  • the groove 13 can become a space for receiving an extruded volume upon forming the gap 14 by a press working, the extruded volume can be prevented from heaving on a valve seat surface by forming the groove 13.
  • the groove 13 is provided on the side of the valve plate 5 facing to the suction valve 11 and the gap 14 is provided at the opening edge portion 23 between the suction hole 10 and the groove 13, as explained above.
  • an opening edge portion and a groove may be provided on the other side of the valve plate 5 facing to the discharge valve 17 (see Fig. 2 ).
  • the six cylinder bores 7 are formed in the cylinder block 3 in the present embodiment, the number of them may not be six.
  • the number of the cylinder bores 7 may be five, seven or the other.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP10823374A 2009-10-13 2010-10-12 Compresseur Withdrawn EP2489877A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009236498A JP2011085029A (ja) 2009-10-13 2009-10-13 圧縮機
PCT/JP2010/067854 WO2011046106A1 (fr) 2009-10-13 2010-10-12 Compresseur

Publications (1)

Publication Number Publication Date
EP2489877A1 true EP2489877A1 (fr) 2012-08-22

Family

ID=43876156

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10823374A Withdrawn EP2489877A1 (fr) 2009-10-13 2010-10-12 Compresseur

Country Status (5)

Country Link
US (1) US20120195784A1 (fr)
EP (1) EP2489877A1 (fr)
JP (1) JP2011085029A (fr)
CN (1) CN102575663A (fr)
WO (1) WO2011046106A1 (fr)

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES1000848Y (es) * 1986-10-23 1988-11-01 Goenaga Churruca Jose Maria Dispositivo perfeccionado de valvula de aspiracion para compresores de aire
BR9002967A (pt) * 1990-06-19 1991-12-24 Brasil Compressores Sa Valvula para compressor hermetico de refrigeracao
JP3326909B2 (ja) 1993-10-07 2002-09-24 株式会社豊田自動織機 斜板式可変容量圧縮機
JPH08261154A (ja) * 1995-03-22 1996-10-08 Toyota Autom Loom Works Ltd ピストン型圧縮機
US6565336B1 (en) * 1998-05-06 2003-05-20 Carrier Corporation Normally unseated suction valve
JP2001193647A (ja) * 2000-01-17 2001-07-17 Sanden Corp 往復動型圧縮機
JP2002332960A (ja) * 2001-05-10 2002-11-22 Toyota Industries Corp シューの製造方法
JP2005042695A (ja) * 2003-07-07 2005-02-17 Calsonic Kansei Corp 圧縮機の弁構造
CN1860295A (zh) * 2003-09-30 2006-11-08 康奈可关精株式会社 压缩机和吸入阀结构
JP4395400B2 (ja) * 2004-03-31 2010-01-06 カルソニックカンセイ株式会社 圧縮機の弁構造
JP2008031857A (ja) * 2006-07-26 2008-02-14 Calsonic Kansei Corp 圧縮機
JP2008095522A (ja) * 2006-10-06 2008-04-24 Sanden Corp 吸入弁機構

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2011046106A1 *

Also Published As

Publication number Publication date
US20120195784A1 (en) 2012-08-02
JP2011085029A (ja) 2011-04-28
CN102575663A (zh) 2012-07-11
WO2011046106A1 (fr) 2011-04-21

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