EP0592119A1 - Drehkolbenverdrängermaschine - Google Patents

Drehkolbenverdrängermaschine Download PDF

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Publication number
EP0592119A1
EP0592119A1 EP93307361A EP93307361A EP0592119A1 EP 0592119 A1 EP0592119 A1 EP 0592119A1 EP 93307361 A EP93307361 A EP 93307361A EP 93307361 A EP93307361 A EP 93307361A EP 0592119 A1 EP0592119 A1 EP 0592119A1
Authority
EP
European Patent Office
Prior art keywords
displacement apparatus
rotary piston
fluid displacement
cylindrical
piston type
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Withdrawn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
EP93307361A
Other languages
English (en)
French (fr)
Inventor
Tsuyoshi Fukui
Norio Kitano
Toshihito Takaoka
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.)
Sanden Corp
Original Assignee
Sanden 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 Sanden Corp filed Critical Sanden Corp
Publication of EP0592119A1 publication Critical patent/EP0592119A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid

Definitions

  • the present invention relates to a rotary piston type incompressible fluid displacement apparatus, and more particularly, to a sealing mechanism for a vane used in the rotary piston type incompressible fluid displacement apparatus.
  • Rotary piston type incompressible fluid displacement apparatuses are well known in the art.
  • a conventional rotary piston type incompressible fluid displacement apparatus for an oil pump is illustrated in Figure 1.
  • the rotary piston incompressible fluid displacement apparatus 500 includes a generally annular cylindrical-shaped housing 510 and a pair of circular plates (not shown) closing the opposite axial opening ends of housing 510. Housing 510 and the pair of circular plates cooperatively define cylindrical chamber 511.
  • a drive shaft (not shown), having longitudinal axis X' which is coaxial to the longitudinal axis of cylindrical chamber 511, rotatably penetrates cylindrical chamber 511.
  • Cylindrical piston member 520 is disposed within cylindrical chamber 511 and is fixedly connected to the drive shaft.
  • the longitudinal axis X of piston member 520 is radially offset from the longitudinal axis X' of the drive shaft.
  • the opposite axial end surfaces of piston member 520 are in fluid tight contact with the inner surface of the pair of circular plates, respectively.
  • Housing 510 includes a cylindrical projection 512 projecting radially outwardly from an outer surface of one peripheral portion thereof. Outlet and inlet ports 514 and 513 are formed on the outer peripheral surface of housing 510 at positions which are in front of and to the rear of the cylindrical projection 512 with respect to the rotational "A" of the drive shaft, respectively.
  • a cavity 512a having a first portion 512b and a second portion 512c is axially formed through cylindrical projection 512.
  • First portion 512b of cavity 512a is a circular configuration in transverse cross section and is located at an axial outer end region of cylindrical projection 512.
  • the second portion 512c of cavity 512a is a rectangular configuration in transverse cross section and is linked to an axial inner end of the first portion 512b of cavity 512a.
  • a valve member or vane 515 having a rectangular-shaped transverse cross section is slidably disposed within second portion 512c of cavity 512a.
  • Snap ring 516 is fixedly disposed at an inner peripheral surface of an axial inner end region of first portion 512b of cavity 512a.
  • Rectangular plate 517 is disposed within second portion 512c of cavity 512a between valve member 515 and snap ring 516.
  • An inner peripheral surface of second portion 512c of cavity 512a, valve member 515 and rectangular plate 517 cooperatively define chamber 512d.
  • a cylindrical depression 515a is formed at an axial outer end surface of valve member 515.
  • Bias spring 518 which is disposed within second portion 512c of cavity 512a between rectangular plate 517 and cylindrical depression 515a, radially inwardly urges valve member 515 into contact with piston member 520.
  • a circular hole 517a is centrally formed in rectangular plate 517. Atmospheric pressure is continuously conducted into chamber 512d via circular hole 517a. Therefore, valve member 515 is radially inwardly urged by virtue of a first force generated by receiving the substantially constant atmospheric pressure at its axial outer end surface and the force due to restoring force of bias spring 518.
  • piston member 520 faces an inner surface of one peripheral portion of housing 510 with a small air gap 521.
  • piston member 520 contacts valve member 515 as seen at 522.
  • Air gap 521 is substantially sealed by an oil film and shifts along the inner peripheral surface of housing 510 in the rotational direction "A" of the drive shaft.
  • the axial line contact 522 between piston member 520 and valve member 515 reciprocatingly shifts along the axial inner end surface of valve member 515 in the radial direction.
  • Sealed air gap 521 and the axial line contact 522 divide cylindrical chamber 511 into(n)th sealed-off fluid pocket 511a and (n+1)th sealed-off fluid pocket 511b.
  • the (n)th and (n+1)th sealed-off fluid pockets 511a and 511b are located in front of and to the rear of the axial line contact 522 with respect to the rotational direction "A" of the drive shaft, respectively.
  • valve member 515 is radially outwardly urged by virtue of the force generated from the pressure in the (n)th and (n+1)th sealed-off fluid pockets 511a and 511b.
  • piston member 520 rotates around the longitudinal axis X' of the drive shaft in the same rotational direction of the drive shaft.
  • the pressure in the (n+1)th sealed-off fluid pocket 511b gradually decreases, the volume of the (n+1) sealed-off fluid pocket 511b gradually increases and oil begins flowing into fluid pocket 511b from inlet port 513 as indicated by arrow "B" in Figure 1.
  • valve member 515 is urged radially outwardly by virtue of the pressure in the (n)th sealed-off fluid pocket 511a.
  • valve member 515 receives oppositely directed second and third forces.
  • the second force is generated by the pressure in the (n)th sealed-off fluid pocket 511a directed against the front portion of the axial inner end surface of valve member 515.
  • the second force urges valve member 515 radially outwardly.
  • the third force is resultant of the first force generated by the substantially constant pressure, e.g., atmospheric pressure, at the axial outer end surface of valve member 515 and the restoring force of bias spring 518.
  • the third force urges valve member 515 radially inwardly.
  • the second force which radially outwardly urges valve member 511 also sharply increases and then is substantially maintained at its increased value.
  • the pressure in the (n)th sealed-off fluid pocket 511a does not increase to a boundary value at which the second force equals the third force, whereby valve member 515 would lose contact with piston member 520.
  • the contact force between the outer surface of piston member 520 and the axial inner end surface of valve member 515 is unacceptably increased, especially when the apparatus 500 operates at a low rotational speed and high oil temperature (or low viscosity). Moreover, the increased biasing results in an excessive loss of power and an abnormal abrasion of the contact surfaces between the piston member 520 and the valve member 515.
  • the rotary piston type incompressible fluid displacement apparatus of the preferred embodiments includes a casing enclosing a cylindrical chamber.
  • a rotatable drive shaft axially penetrates through the cylindrical chamber.
  • a cylindrical piston member is disposed within the cylindrical chamber and is operatively connected to the drive shaft.
  • a valve element or a vane is radially slidably disposed within a bore which is formed at an inner surface of one peripheral portion of the casing.
  • a bias spring is resiliently disposed within the bore so as to urge the valve element into contact with an outer surface of the cylindrical piston member.
  • An axis of the cylindrical piston member is radially offset from an axis of the drive shaft by a predetermined distance.
  • the casing, the cylindrical piston member and the valve element cooperatively define a first chamber portin into which an incompressible fluid, such as an oil, is taken and a second chamber portion through which the oil is pumped.
  • An inlet port is formed through the casing on one side of the vane.
  • An outlet port is formed through the casing on the other side of the vane.
  • a conducting means such a groove, is axially formed through a central portion of one end surface of the valve element. The conducting means conducts oil on the high pressure side of the piston into a hollow space disposed radially outwardly of the valve element. Consequently, the high pressure oil acting on the rear end of the vane assures its contact with the piston member.
  • Figure 1 is a longitudinal sectional view of a rotary piston type incompressible fluid displacement apparatus in accordance with the prior art.
  • Figure 2 is a longitudinal sectional view of a rotary piston type incompressible fluid displacement apparatus in accordance with a first preferred embodiment.
  • Figure 3 is a view taken along line 3-3 of Figure 2.
  • Figure 4 is a view taken along arcuate line 4-4 of Figure 2.
  • Figure 5 is a view similar to Figure 4 showing a second preferred embodiment.
  • Figure 6 is a view similar to Figure 4 showing a third preferred embodiment.
  • Apparatus 10 is incorporated in a refrigerant compressor as an oil pumping device which supplies lubricating oil from an oil sump to the frictional surfaces of the internal component parts of the compressor.
  • the apparatus 10 includes an annular cylindrical member 11 and a pair of circular plates 12 and 13 which are disposed within annular cylindrical member 11.
  • the pair of circular plates 12 and 13 are fixedly connected to annular cylindrical member 11 by means of, for example, screws (not shown).
  • Ring member 14 is also disposed within annular cylindrical member 11 and is fixedly sandwiched by circular plates 12 and 13 by means of, for example, screws (not shown).
  • the pair of circular plates 12 and 13 and ring member 14 cooperatively define cylindrical chamber 110.
  • the apparatus 10 further includes a drive shaft 20, which is also the drive shaft of the compressor.
  • Drive shaft 20 rotatably penetrates circular plates 12 and 13.
  • Drive shaft 20 includes annular projection 21 projecting radially outwardly from an outer peripheral surface thereof.
  • Annular projection 21 functions as a cylindrical piston member.
  • the longitudinal axis X of annular projection 21 is radially offset from the longitudinal axis X' of the drive shaft 20.
  • the longitudinal axis X' of the drive shaft 20 is coaxial to the longitudinal axis of cylindrical chamber 110.
  • the opposite axial end surfaces of annular projection 21 are in fluid tight contact with the inner surface of the pair of the circular plates 12 and 13, respectively.
  • a bore 30 having a rectangular-shaped transverse cross-section is radially formed through ring member 14.
  • Outlet and inlet ports 32 and 31 are formed through ring member 14 at positions which are in front of and to the rear of bore 30 with respect to the rotational direction "A" of drive shaft 20, respectively.
  • Inlet and outlet ports 31 and 32 are linked to bores 311 and 321, which are formed through annular cylindrical member 11, respectively.
  • a valve member or vane 40 having a rectangular shaped transverse cross section is slidably disposed within bore 30.
  • An axial inner end portion of valve member 40 is U-shaped in longitudinal cross section.
  • Bias spring 41 is resiliently disposed within bore 30 between the axial outer end surface of valve member 40 and the inner surface of annular cylindrical member 11. Bias spring 41 radially inwardly urges valve member 40 into contact with annular projection 21.
  • the outer surface of one peripheral portion of annular projection 21 faces an inner surface of one peripheral portion of ring member 14 with a small air gap 211 while the outer surface of another peripheral portion of annular projection 21 is in contact at 212 with the axial inner end surface of valve member 40.
  • At gap 211 is substantially sealed by an oil film and shifts along the inner peripheral surface of ring member 14 in the rotational direction "A" of drive shaft 20.
  • the axial line contact 212 between annular projection 21 and valve member 40 reciprocatingly shifts along the U-shaped axial inner end surface of valve member 40.
  • Sealed air gap 211 and axial line contact 212 divide cylindrical chamber 110 into (n)th sealed-off fluid pocket 110a and (n+1)th sealed-off fluid pocket 110b.
  • The(n)th and (n+1)th sealed-off fluid pockets 110a and 110b are located in front of and to the rear of the axial line contact 212 with respect to the rotational direction "A" of drive shaft 20, respectively.
  • the portion of the axial inner end surface of valve member 40 located in front of axial line contact 212 with respect to the rotational direction of the drive shaft receives pressure in the (n)th sealed-off fluid pocket 110a while the portion of the axial inner end surface of valve member 40 located to the rear of the axial line contact 212 receives pressure in the (n+1)th sealed-off fluid pocket 110b. Accordingly, valve member 40 is urged radially outwardly by virtue of the pressure in the (n)th and (n+1)th sealed-off fluid pockets 110a and 110b.
  • an axial groove 400 having a rectangular-shaped transverse cross section is formed at a central portion of the front side surface of valve member 40.
  • Axial groove 400 forms a communication conduit between (n)th sealed-off fluid pocket 110a and a hollow space 30a located radially outwardly of the end face of valve member 40. Therefore, valve member 40 is urged radially inwardly by a first force due to the pressure in the (n)th sealed-off fluid pocket 110a at the axial outer end surface thereof.
  • the depth of axial groove 400 is designed so that a bottom surface 440a (Fig. 4) of groove 400 does not pass the axial line contact 212 between the annular projection 21 and the valve member 40.
  • annular projection 21 rotates around the longitudinal axis X' of the drive shaft 20 and sealed air gap 211 shifts along the inner peripheral surface of ring member 14.
  • annular projection 21 is positioned as illustrated in Figure 2, the volume of the (n+1)th sealed-off fluid pocket 110b is increasing.
  • oil from the oil sump flows into the (n+1)th sealed-off fluid pocket 110b through a pipe member (not shown), bore 311 and inlet port 31 as indicated by arrows "B" in Figure 2.
  • the volume of the (n)th sealed-off fluid pocket 110a is decreasing and the oil in the high pressure (n)th sealed-off fluid pocket is elected through outlet port 32 and bore 321 as indicated by arrow "C" in Figure 2.
  • the pressure in the (n+1)th sealed-off fluid pocket 110b gradually decreases while the pressure in the (n)th sealed-off fluid pocket 110a sharply increases.
  • the pressure of the oil in the (n)th sealed-off fluid pocket 110a is substantially maintained at its increased value during the remainder of the oil delivery stroke.
  • Valve member 40 receives oppositely directed second and third forces. More particularly, the second force is generated by the pressure in the (n)th sealed-off fluid pocket 110a at the front portion of the axial inner end surface of valve member 40. The second force urges valve member 40 radially outwardly.
  • the third force is the resultant of the first force generated by the pressure in the (n)th sealed-off fluid pocket 110a at the axial outer end surface of valve member 40 and the restoring force of bias spring 41. The third force urges valve member 40 radially inwardly.
  • valve member 40 Since the portion of the axial inner end surface of valve member 40 exposed to the high pressure oil is smaller than the axial outer end surface of valve member 40 exposed to the high pressure oil, valve member 40 is continually urged radially inwardly by virtue of the restoring force of bias spring 41 and the differential between the first force and the second force.
  • the spring constant of bias spring 41 is selected to avoid generating an excessive contact force between annular projection 21 and valve member 40 so that an excessive loss of power and abnormal abrasion of the contact surfaces can be avoided.
  • Figures 5 and 6 illustrate second and third preferred embodiments, respectively.
  • the same numerals are used to denote the corresponding elements shown in Figure 4, and an explanation of those elements is omitted.
  • the effect of the second and third preferred embodiments is similar to that of the first preferred embodiment so that an explanation thereof is also omitted.
  • a pair of axial hollow portions 401 having triangular cross sections are formed at both radial end portions of valve member 40.
  • Axial hollow portions 401 permit fluid communication between the (n)th sealed-off fluid pocket 110a and hollow space 30a disposed at the radial outer end of valve member 40.
  • valve member 40 is urged radially inwardly by the pressure in the (n)th sealed-off fluid pocket 110a at the axial outer end surface of valve member 40.
  • axial hollow portions 401 are positioned completely in front of axial line contact 212.
  • an axial groove 141 having a rectangular-shaped transverse cross section is formed at a central portion of a front side surface of bore 30 with respect to the rotational direction "A" of drive shaft 20.
  • Axial groove 141 establishes a fluid communication path between the (n)th sealed-off fluid pocket 110a and hollow space 30a disposed at the radial outer end of valve member 40. Therefore, valve member 40 is urged radially inwardly by the pressure in the (n)th sealed-off fluid pocket 110a acting upon the axial outer end surface of valve member 40.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Reciprocating Pumps (AREA)
EP93307361A 1992-09-21 1993-09-17 Drehkolbenverdrängermaschine Withdrawn EP0592119A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP7133992U JPH0630490U (ja) 1992-09-21 1992-09-21 ベーンタイプポンプ
JP71339/92 1992-09-21

Publications (1)

Publication Number Publication Date
EP0592119A1 true EP0592119A1 (de) 1994-04-13

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ID=13457652

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93307361A Withdrawn EP0592119A1 (de) 1992-09-21 1993-09-17 Drehkolbenverdrängermaschine

Country Status (2)

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EP (1) EP0592119A1 (de)
JP (1) JPH0630490U (de)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5602361A (en) * 1994-03-18 1997-02-11 Oea, Inc. Hybrid inflator
US5616883A (en) * 1994-03-18 1997-04-01 Oea, Inc. Hybrid inflator and related propellants
US5630618A (en) * 1994-03-18 1997-05-20 Oea, Inc. Hybrid inflator with a valve
US5711546A (en) * 1994-03-18 1998-01-27 Oea, Inc. Hybrid inflator with coaxial chamber
US5821448A (en) * 1994-03-18 1998-10-13 Oea, Inc. Compact hybrid inflator
US6168401B1 (en) 1998-05-04 2001-01-02 Luk Automobiltechnik Gmbh & Co. Kg Hydraulic conveying device
WO2011015122A1 (zh) * 2009-08-04 2011-02-10 Wang Haijun 机械运动与流体运动的互转换装置
WO2013152706A1 (zh) * 2012-04-12 2013-10-17 艾默生环境优化技术(苏州)有限公司 转子泵以及包括转子泵的旋转机械
CN105841387A (zh) * 2016-05-30 2016-08-10 广东美芝制冷设备有限公司 制冷装置及压缩机

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB520016A (en) * 1938-03-21 1940-04-11 Bosch Gmbh Robert Improvements in or relating to rolling or other rotary piston compressors
US3221665A (en) * 1962-01-11 1965-12-07 Hartmann Mfg Co Hydraulic pump or motor with hydraulic pressure-responsive vane
GB1186345A (en) * 1966-04-27 1970-04-02 John Thomas Flitcroft A Rotary Fluid Motor or Pump
US3521981A (en) * 1968-08-30 1970-07-28 Edward Krzyszczuk Pump or compressor
JPS5888486A (ja) * 1981-11-20 1983-05-26 Fujitsu General Ltd ロ−タリ式圧縮機
JPS6487891A (en) * 1987-09-30 1989-03-31 Toshiba Corp Rotary compressor
JPH01262395A (ja) * 1988-04-11 1989-10-19 Daikin Ind Ltd 回転式圧縮機

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59229090A (ja) * 1983-06-10 1984-12-22 Matsushita Refrig Co 回転式圧縮機

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB520016A (en) * 1938-03-21 1940-04-11 Bosch Gmbh Robert Improvements in or relating to rolling or other rotary piston compressors
US3221665A (en) * 1962-01-11 1965-12-07 Hartmann Mfg Co Hydraulic pump or motor with hydraulic pressure-responsive vane
GB1186345A (en) * 1966-04-27 1970-04-02 John Thomas Flitcroft A Rotary Fluid Motor or Pump
US3521981A (en) * 1968-08-30 1970-07-28 Edward Krzyszczuk Pump or compressor
JPS5888486A (ja) * 1981-11-20 1983-05-26 Fujitsu General Ltd ロ−タリ式圧縮機
JPS6487891A (en) * 1987-09-30 1989-03-31 Toshiba Corp Rotary compressor
JPH01262395A (ja) * 1988-04-11 1989-10-19 Daikin Ind Ltd 回転式圧縮機

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 13, no. 299 (M - 847)<3647> 11 July 1989 (1989-07-11) *
PATENT ABSTRACTS OF JAPAN vol. 14, no. 23 (M - 920)<3966> 17 January 1990 (1990-01-17) *
PATENT ABSTRACTS OF JAPAN vol. 7, no. 187 (M - 236)<1332> 16 September 1983 (1983-09-16) *

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5679915A (en) * 1994-03-18 1997-10-21 Oea, Inc. Method of assembling a hybrid inflator
US5711546A (en) * 1994-03-18 1998-01-27 Oea, Inc. Hybrid inflator with coaxial chamber
US5623116A (en) * 1994-03-18 1997-04-22 Oea, Inc. Hybrid inflator and related propellants
US5627337A (en) * 1994-03-18 1997-05-06 Oea, Inc. Hybrid inflator and related propellants
US5630618A (en) * 1994-03-18 1997-05-20 Oea, Inc. Hybrid inflator with a valve
US5675102A (en) * 1994-03-18 1997-10-07 Oea, Inc. Method of assembling a hybrid inflator and related propellants
US5616883A (en) * 1994-03-18 1997-04-01 Oea, Inc. Hybrid inflator and related propellants
US5821448A (en) * 1994-03-18 1998-10-13 Oea, Inc. Compact hybrid inflator
US5602361A (en) * 1994-03-18 1997-02-11 Oea, Inc. Hybrid inflator
US6168401B1 (en) 1998-05-04 2001-01-02 Luk Automobiltechnik Gmbh & Co. Kg Hydraulic conveying device
WO2011015122A1 (zh) * 2009-08-04 2011-02-10 Wang Haijun 机械运动与流体运动的互转换装置
WO2013152706A1 (zh) * 2012-04-12 2013-10-17 艾默生环境优化技术(苏州)有限公司 转子泵以及包括转子泵的旋转机械
US9562530B2 (en) 2012-04-12 2017-02-07 Emerson Climate Technologies (Suzhou) Co., Ltd. Rotor pump and rotary machinery comprising the same, the rotor pump including a pump body forming an accommodation cavity, a pump wheel rotating in the accommodation cavity and a sealing plate having an eccentric hole that is eccentric relative to a rotation axis of the pump wheel, where a shaft portion of the pump wheel is rotatably fitted in the eccentric hole
CN105841387A (zh) * 2016-05-30 2016-08-10 广东美芝制冷设备有限公司 制冷装置及压缩机
CN105841387B (zh) * 2016-05-30 2019-09-13 广东美芝制冷设备有限公司 制冷装置及压缩机

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