EP0926345A2 - Forme des passages d'aspiration et de refoulement pour compresseur de réfrigération - Google Patents

Forme des passages d'aspiration et de refoulement pour compresseur de réfrigération Download PDF

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Publication number
EP0926345A2
EP0926345A2 EP98124026A EP98124026A EP0926345A2 EP 0926345 A2 EP0926345 A2 EP 0926345A2 EP 98124026 A EP98124026 A EP 98124026A EP 98124026 A EP98124026 A EP 98124026A EP 0926345 A2 EP0926345 A2 EP 0926345A2
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EP
European Patent Office
Prior art keywords
suction
discharge
valve plate
valve
piston cylinder
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.)
Granted
Application number
EP98124026A
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German (de)
English (en)
Other versions
EP0926345A3 (fr
EP0926345B1 (fr
Inventor
Masayuki c/o Sanden Corporation Kurihara
Iwao c/o Sanden Corporation Uchikado
Yoshio c/o Sanden Corporation Kimura
Tetsuya c/o Sanden Corporation Noda
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Sanden Corp
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Sanden Corp
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Publication date
Application filed by Sanden Corp filed Critical Sanden Corp
Publication of EP0926345A2 publication Critical patent/EP0926345A2/fr
Publication of EP0926345A3 publication Critical patent/EP0926345A3/fr
Application granted granted Critical
Publication of EP0926345B1 publication Critical patent/EP0926345B1/fr
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
    • 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
    • F04B39/108—Adaptations or arrangements of distribution members the members being reed valves circular reed valves

Definitions

  • the present invention relates to a refrigerant compressor used for an automotive air-conditioning system. More particularly, the present invention relates to shapes of suction holes and discharge holes provided in a valve plate of a compressor.
  • Compressor 100 comprises front housing 30, housing 27, valve plate 1, and rear housing 32.
  • a drive shaft 34 which is supported rotatably by needle bearings 35 and 36.
  • cam rotor 37 which is fixed to drive shaft 34 engages the inner wall of front housing 30 via thrust bearing 38.
  • Cam rotor 37 rotates when drive shaft 34 is rotated.
  • Hinge mechanism 39 couples cam rotor 37 with inclined plate 40.
  • Inclined plate 40 rotates with cam rotor 37.
  • Wobble plate 43 engages with inclined plate 40 via thrust bearing 41 and needle bearing 42.
  • a wobbling motion is induced in inclined plate 40, so that inclined plate 40 wobbles while rotating.
  • This motion of inclined plate 40 transfers to wobble plate 43.
  • Rotation of wobble plate 43 is inhibited by engagement with a guide bar 44. Therefore, only the wobbling component of the motion of inclined plate 40 is transferred from inclined plate 40 to wobble plate 43.
  • Wobble plate 43 has a wobbling motion, but does not rotate with drive shaft 34.
  • Rod 45 is connected by spherical coupling to wobble plate 43 and to a plurality of pistons 46. When wobble plate 43 wobbles, each of pistons 46 reciprocates in one of a plurality of cylinders 71.
  • Suction valve reed 22, discharge valve reed 2, and valve retainer 3 are fixed by bolt 47 to valve plate 1.
  • Suction holes 5 and discharge holes 4 correspond to each piston cylinder 71.
  • Suction chamber 72 and discharge chamber 70 are formed by valve plate 1 and the rear housing 32; and are separated by inside partition plate 33.
  • each piston 46 reciprocates in its respective piston cylinder 71.
  • the suction phase is executed, and when piston 46 is moving rightward, the compression phase is executed.
  • suction phase refrigerant gas in suction chamber 72 is drawn into piston cylinder 71 through suction hole 5. Due to the pressure variance between suction chamber 72 and piston cylinder 71, the refrigerant gas in suction chamber 72 flows to suction hole 5, passes through suctation hole 5, opens suction valve reed 22, and enters piston cylinder 71. Suction valve reed 22 prohibits a reverse flow of refrigerant gas into suction chamber 72 during the compression phase.
  • the refrigerant gas in piston cylinder 71 is discharged into discharge chamber 70 through discharge hole 4. Due to the pressure variance between piston under 71 and discharge chamber 70, the refrigerant gas passes, through discharge hole 4, opens discharge valve reed 2, and enters discharge chamber 70. Discharge valve reed 2 prohibits a reverse flow of the refrigerant gas into piston cylinder 71 during the suction phase.
  • Fig. 2a depicts a cross-sectional view of valve plate 1 from the rear housing side of valve plate 1.
  • Fig. 2b depicts a cross-sectional view of valve plate 1 from the cylinder head side of valve plate 1.
  • rear housing 32 is fixed to housing 27 by a plurality of bolts 130.
  • Suction holes 5 and discharge holes 4 are disposed equiangularly around the center CO and correspond to piston cylinders 71.
  • Suction chamber 72 and discharge chamber 70 are separated by inside partition plate 33.
  • Discharge valve reed 2 within inside partition plate 33 is substantially star-shaped.
  • the arms of discharge valve reed 2 cover discharge holes 4.
  • suction valve reed 22 also is substantially star-shaped. Within each arm, a hole 22h enables the discharge gas to flow therethrough.
  • Fig. 3 depicts valve plate 1 as viewed from the side of valve plate 1 facing discharge chamber 70.
  • Discharge holes 4 and suction holes 5 are disposed equiangularly with respect to the center C of valve plate 1.
  • Fig. 4 and Fig. 5 are corresponding radial, cross-sectional views of valve plate 1 of Fig. 1.
  • Valve reed 2 is fixed between valve plate 1 and valve retainer 3.
  • Discharge holes 4 have side walls which are substantially perpendicular to the opposing surfaces of valve plate 1.
  • Fig. 4 and Fig. 5 depict valve plate 1 during the compression phase.
  • the refrigerant gas When the refrigerant gas is discharged from cylinders 71, it strikes, pushes, and displaces valve reed 2.
  • the refrigerant gas flows into discharge chamber 70 through a gap created between valve reed 2 and valve plate 1.
  • refrigerant gas flow impinges against reed valve 2 in Fig. 4 its flow path may be diverted at an angle substantially perpendicular to valve plate 1. Turbulence in the refrigerant gas flow may be created due to the abrupt change in the direction of flow. Further, a portion of the refrigerant gas flow impinging against valve reed 2 may not enter discharge chamber 70, and may instead return to piston cylinder 71.
  • turbulence of the refrigerant gas flow may result in flow resistance at discharge hole 4.
  • Such flow resistance lowers the volumetric efficiency, a primary measure of the performance of compressor 100.
  • the turbulence of flow also disturbs the motion of valve reed 2 and impedes valve reed 2 from discretely and completely opening and closing.
  • the turbulence of flow in discharge holes 4 may cause noise in compressor 100. Similar problems may occur with respect to suction holes 5.
  • a compressor according to the present invention is equipped with a valve plate that has suction passages and discharge passages.
  • each of the discharge passages includes a first piston cylinder-side opening having an area, a discharge chamber-side opening having an area, and a sidewall extending between the openings. At least a portion of the discharge passage sidewall is tapered. The discharge chamber-side opening area is greater than the piston cylinder-side opening area.
  • each of the suction passages includes a second piston cylinder-side opening having an area, a suction chamber-side opening having an area, and a sidewall extending between the openings. At least a portion of the suction passage sidewall is tapered.
  • the piston cylinder-side opening area is greater than the suction chamber-side opening area.
  • the sidewalls of the passages may include a substantially cylindrical portion. Further, the tapered portion of the sidewalls of the passages may be less than the thickness of the valve plate. Even with partial tapering, the objects of the present invention may be achieved.
  • the flow path of the refrigerant gas may bend gradually.
  • the flow path of the refrigerant gas does not strike the valve reed perpendicularly, but instead flows along the tapered portion of the sidewall.
  • any turbulence of the refrigerant is reduced in the suction holes or discharge holes, so that the volumetric efficiency of the compressor may be improved and associated noise suppressed.
  • FIG. 6 a plan view of a valve plate 11 from discharge chamber 70 in accordance to an embodiment of the present invention is depicted.
  • Discharge holes 14 and suction holes 15 are disposed equiangularly in valve plate 11 with respect to center C.
  • Figs. 7 and 8 are cross-sectional views of the discharge mechanism during a compression phase.
  • Valve reed 12 is fixed between valve plate 11 and valve retainer 13.
  • a sidewall 16 of discharge hole 14 is formed as a convex tapered surface. Small circular opening 16a is on the piston cylinder end of sidewall 16. Large circular opening 16b is on the discharge chamber end of sidewall 16.
  • hole area Sa is defined by small circular opening 16a
  • hole area Sb is defined by large circular opening 16b.
  • area Sb is about 1.5 times greater than area Sa.
  • the curve of sidewall 16 allows area Sa on the piston cylinder-side surface of valve plate 11 to increase gradually to area Sb on the discharge chamber-side surface of valve plate 11.
  • a viscous fluid that flows near a wall of a chamber, or tube, flows along the surface.
  • the refrigerant gas flows along sidewall 16 when discharge hole 14 is open, as indicated by the arrows in Fig. 7 and Fig. 8.
  • the direction of flow of the refrigerant gas gradually bends in a lateral direction according to Figs. 7 and 8.
  • the refrigerant gas is prevented from colliding directly upon valve reed 12. As a result, turbulence of the refrigerant gas within discharge hole 14 is reduced. Therefore, the shape of discharge hole 14 improves the volumetric efficiency of compressor 100.
  • Figs. 10-13 depict another embodiment of the present invention.
  • a plan view of valve plate 11 from the discharge chamber-side is depicted.
  • Discharge holes 14' and suction holes 15 are disposed equiangularly in valve plate 11 with respect to the center C.
  • Figs. 11 and 12 depict the cross-sectional views of the discharge mechanism during the compression phase.
  • Valve reed 12 is fixed between valve plate 11 and valve retainer 13.
  • Discharge hole 14' includes partially convex sidewall 16' and cylindrical portion 19'.
  • Small circular opening 16a' is the piston cylinder-end circumference of sidewall 16'.
  • Large elliptical opening 16b' is the discharge chamber-end opening of sidewall 16'.
  • large elliptical opening 16b' extends to only the radially outer side of discharge hole 14' with respect to center C of valve plate 11.
  • hole area Sa' is defined by small circular opening 16a'
  • hole area Sb' is defined by large elliptical opening 16b'.
  • area Sb' is about 1.5 times greater than area Sa'.
  • the curve of partially tapered sidewall 16' allows area Sa' on the piston cylinder-side surface of valve plate 11 to increase gradually to area Sb' on the discharge chamber-side surface of valve plate 11.
  • the circumference of discharge hole 14' increases from the piston cylinder-side surface to the discharge chamber-side surface of valve plate 11.
  • Figs. 14-17 depict another embodiment of the present invention.
  • a plan view of valve plate 11 from the discharge chamber side is depicted.
  • Discharge holes 14'' and suction holes 15 are disposed equiangularly in valve plate 11 with respect to the center C.
  • valve seat grooves 110 are provided around each discharge hole 14''. Valve seat groove 110 prevents valve reed 12 from sticking to valve place 11.
  • Figs. 15 and 16 depict the cross-sectional view of the discharge mechanism during the compression phase.
  • Valve reed 12 is fixed between valve plate 11 and valve retainer 13.
  • Discharge hole 14'' comprises a tapered sidewall 16'' and a perpendicular part 17''.
  • Small circular opening 16a'' is the piston cylinder-end opening of perpendicular part 17''.
  • Large circular opening 16b'' is the discharge chamber-end opening of sidewall 16''.
  • opening area Sa'' is defined by small circular opening 16a'' and opening area Sb'' is defined by large circular opening 16b''.
  • area Sb'' is approximately 1.5 times greater than area Sa''. Therefore, tapered sidewall 16'' allows area Sa'' on the piston cylinder-side surface of valve plate 11 to increase gradually to area Sb'' on the discharge chamber-side surface of valve plate 11. Further, with reference to Fig. 16, the height of perpendicular part 17'' is greater than or equal to zero.
  • Figs. 18-21 depict another embodiment of the present invention.
  • a plan view of valve plate 11 seen from the discharge chamber-side is depicted.
  • Discharge holes 14''' and suction holes 15 are disposed equiangularly in valve plate 11 with respect to center C.
  • Figs. 19 and 20 depict the cross-sectional view of the discharge mechanism during the compression phase.
  • Valve reed 12 is fixed between valve plate 11 and valve retainer 13.
  • Discharge hole 14''' comprises a partially tapered sidewall 16''', a cylindrical portion 19''' and a perpendicular part 17'''.
  • Small circular opening 16a''' is the piston cylinder-end opening of perpendicular part 17''.
  • Large elliptical opening 16b''' is the discharge chamber-end opening of tapered sidewall 16'''.
  • large elliptical opening 16b''' extends to the radially outer side of discharge hole 14''' with respect to center C of valve plate 11.
  • opening area Sa''' is defined by small circular opening 16a'''
  • opening area Sb''' is defined by large elliptical opening 16b'''.
  • area Sb''' is about 1.5 times greater than area Sa'''. Therefore, partially tapered sidewall 16''' allows area Sa''' on the piston cylinder-side surface of valve plate 11 to increase gradually to area Sb''' on the discharge chamber-side surface of valve plate 11.
  • Figs. 22-25 depict another embodiment of the present invention.
  • a plan view of valve plate 21 from the piston cylinder-side is depicted.
  • Discharge holes 24 and suction holes 25 are disposed equiangularly in valve plate 21 with respect to the center C.
  • Figs. 23 and 24 depict the cross-sectional view of the suction mechanism during the suction phase.
  • vibration of valve reed 22 is limited by a groove 23 provided at end of housing 27.
  • Suction hole 25 includes a convex tapered sidewall 26. Small circular opening 26a is the suction chamber-end opening of tapered sidewall 26. Large circular opening 26b is the piston cylinder-end opening of tapered sidewall 26.
  • opening area S2a is defined by small circular opening 26a
  • opening area S2b is defined by large circular opening 26b.
  • area S2b is about 1.5 times greater than area S2a.
  • the curve of convex tapered sidewall 26 allows area S2a on the suction chamber-side surface of valve plate 21 to increase gradually to area S2b on the piston cylinder-side surface of valve plate 21.
  • the circumference of suction hole 25 increases from the suction chamber-side surface of valve plate 21 to the piston cylinder surface.
  • the shapes of the holes depicted in Fig. 6-21 and described with respect to discharge holes are applicable to and suitable for suction holes.
  • the present invention provides a convex tapered sidewall or a tapered sidewall with cylindrical portions in a discharge hole or in a suction hole, or both.
  • the turbulence of the refrigerant flow passing through the discharge holes or the suction holes, or both may be reduced. Accordingly, it is possible to decrease the flow resistance for the refrigerant gas through the discharge holes and suction holes, so that the volumetric efficiency of the compressor may be improved and related noise suppressed.
  • the present invention is applicable to any type of compressor that has a reed valve mechanism.
  • the present invention may be applied to swash plate-type compressors, wobble plate-type compressor, or scroll-type compressor.
  • the present invention has been described in detail in connection with preferred embodiments, the invention is not limited thereto. It will be understood by those of ordinary skill in the art that variations and modifications may be made within the scope of this invention, as defined by the following claims.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP19980124026 1997-12-26 1998-12-17 Forme des passages d'aspiration et de refoulement pour compresseur de réfrigération Expired - Lifetime EP0926345B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP36003797 1997-12-26
JP36003797 1997-12-26

Publications (3)

Publication Number Publication Date
EP0926345A2 true EP0926345A2 (fr) 1999-06-30
EP0926345A3 EP0926345A3 (fr) 2000-03-08
EP0926345B1 EP0926345B1 (fr) 2001-10-24

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EP19980124026 Expired - Lifetime EP0926345B1 (fr) 1997-12-26 1998-12-17 Forme des passages d'aspiration et de refoulement pour compresseur de réfrigération

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EP (1) EP0926345B1 (fr)
KR (1) KR100552312B1 (fr)
DE (1) DE69802160T2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2787869A1 (fr) * 1998-12-24 2000-06-30 Sanden Corp Compresseur de refrigerant
EP2886864A4 (fr) * 2012-07-25 2016-09-21 Daikin Ind Ltd Condenseur
EP4098171A2 (fr) 2021-05-14 2022-12-07 BSH Hausgeräte GmbH Appareil domestique doté d'un compresseur contenant une soupape à lames

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB760815A (en) * 1953-04-23 1956-11-07 Carrier Engineering Co Ltd Improvements in or relating to reciprocating compressors
DE2451207C3 (de) * 1974-10-29 1981-10-29 Robert Bosch Gmbh, 7000 Stuttgart Ventilsitzplatte für einen Kolbenverdichter
US4580604A (en) * 1983-06-23 1986-04-08 Mitsubishi Denki Kabushiki Kaisha Discharging valve device for a compressor
US4642037A (en) * 1984-03-08 1987-02-10 White Consolidated Industries, Inc. Reed valve for refrigeration compressor
HU198788B (en) * 1986-04-07 1989-11-28 Finoszerelvenygyar Pressure valve system of piston cooling compressor
JP2709967B2 (ja) * 1989-11-28 1998-02-04 三田工業株式会社 自動原稿搬送装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2787869A1 (fr) * 1998-12-24 2000-06-30 Sanden Corp Compresseur de refrigerant
DE19962050C2 (de) * 1998-12-24 2002-06-13 Sanden Corp Kompressor mit einem Auslaßventilmechanismus und einem Ansaugventilmechanismus
EP2886864A4 (fr) * 2012-07-25 2016-09-21 Daikin Ind Ltd Condenseur
EP4098171A2 (fr) 2021-05-14 2022-12-07 BSH Hausgeräte GmbH Appareil domestique doté d'un compresseur contenant une soupape à lames

Also Published As

Publication number Publication date
KR19990066867A (ko) 1999-08-16
EP0926345A3 (fr) 2000-03-08
EP0926345B1 (fr) 2001-10-24
DE69802160T2 (de) 2002-06-06
KR100552312B1 (ko) 2006-05-23
DE69802160D1 (de) 2001-11-29

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