EP0069531A2 - Kompressor vom Spiraltyp mit verbessertem Auslassmechismus - Google Patents

Kompressor vom Spiraltyp mit verbessertem Auslassmechismus Download PDF

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Publication number
EP0069531A2
EP0069531A2 EP82303420A EP82303420A EP0069531A2 EP 0069531 A2 EP0069531 A2 EP 0069531A2 EP 82303420 A EP82303420 A EP 82303420A EP 82303420 A EP82303420 A EP 82303420A EP 0069531 A2 EP0069531 A2 EP 0069531A2
Authority
EP
European Patent Office
Prior art keywords
scroll
valve
fluid
end plate
chamber
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
EP82303420A
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English (en)
French (fr)
Other versions
EP0069531A3 (en
EP0069531B1 (de
Inventor
Masaharu Hiraga
Akihiro Kawano
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
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Publication of EP0069531A2 publication Critical patent/EP0069531A2/de
Publication of EP0069531A3 publication Critical patent/EP0069531A3/en
Application granted granted Critical
Publication of EP0069531B1 publication Critical patent/EP0069531B1/de
Expired 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/102—Geometry of the inlet or outlet of the outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/50—Inlet or outlet
    • F05B2250/502—Outlet

Definitions

  • This invention relates to a fluid displacement apparatus, and more particularly, to a scroll type compressor having an improved fluid discharge mechanism.
  • Scroll type fluid displacement apparatus are well known in the prior art.
  • U.S. Patent No. 801,182 discloses a scroll type apparatus including two scroll members each having a circular end plate and a spiroidal or involute spiral element. These scroll members are maintained angularly and radially offset so that both spiral elements interfit to make a plurality of line contacts between their spiral curved surfaces to thereby seal off and define at least one pair of fluid pockets.
  • the relative orbital motion of the two scroll members shifts the line contacts along the spiral curved surfaces and, therefore, the fluid pockets change in volume. Since the volume of the fluid pockets increases or decreases dependent on the direction of orbital motion, the scroll type fluid displacement apparatus is applicable to compress, expand or pump fluids.
  • an orbiting spiral element and a fixed spiral element make four line contacts at points A-D.
  • a pair of fluid pockets are defined between line contacts D,C and line contacts A,B.
  • the fluid pockets are defined not only be the walls of the spiral elements, but also by the end plates from which these spiral elements extend.
  • the pair of fluid pockets are interconnected as the spiral elements reach a certain stage in the rotation and subsequently the pockets merge to form a central single pocket which defines the center portion of both spiral elements.
  • the volume of the single pocket is reduced by further revolution of the orbiting spiral element by 90° increments.
  • outer spaces which are open at,stage,change to form new sealed off fluid pockets in which additional fluid is enclosed. Accordingly, assuming circular end plates seal the axial facing ends of respective spiral elements and if one of the end plates is provided with discharge port at the center thereof, fluid is taken into the fluid pockets at the radial outer portions and is discharged from discharge port after compression.
  • a valve member is disposed on the outside of the discharge port to control the closing and opening of discharge port.
  • the valve member includes a valve plate and valve retainer.
  • the valve plate and valve retainer are fixed on the end surface of end plate on the opposite side from which spiral element extends.
  • the pressure in the center pocket increases due to the reduction in volume of central pocket during orbital motion of orbiting spiral element.
  • the valve plate is pushed against the valve retainer to open the discharge port.
  • the compressed fluid within the central pocket discharges into the discharge chamber. Accordingly, the compressed fluid within the central pocket is discharged by revolution of the orbiting spiral element.
  • the central pocket When the outer side wall of the inner end portion of the orbiting spiral element crosses over the edge of the discharge port, the central pocket is connected with the adjacent radial pair of fluid pockets. This increases the volume of the central pocket so that the remaining compressed fluid within the central pocket is re-expanded. After re-expansion of the compressed fluid, the pressure in the expanded central pocket is lower than the pressure in discharge chamber to thereby close the discharge port via the valve plate. Upon re-expansion of the compressed fluid in the central pocket, the pressure in the adjacent radial pair of fluid pockets is suddenly raised. Therefore, the compression power of the fluid within the new central pocket is increased and the pressure of the pair of fluid pockets is raised.
  • One solution for reducing the re-expansion volume is to change the configuration of the curve of the outer and inner side walls of the spiral elements.
  • the inner end of the outer side wall can be extended inwardly to the circumference of the generating circle.
  • the outer portion of the inner side wall which extends from the contact point on the inner side wall where interference of the spiral elements occurs to the terminal end, then forms the involute.
  • the inner end of the outer side wall and the contact point on the inner side wall are connected by a suitable curve which is drawn to avoid actual interference between the spiral elements.
  • the maximum open area of the discharge port which still results in a minimized re-expansion volume, is obtained by placing the discharge port near the center of the generating circle and inscribing the discharge port on the outer side wall of the fixed spiral element and the inner side wall of the orbiting spiral element.
  • the open area of the discharge port must be made larger than the above described maximum area of the discharge port in order to reduce the pressure loss of passing fluid. Accordingly, since the configuration-of discharge port influences the re-expansion volume, in actual practice the above described compressor does not result in a reduced re-expansion volume without at the same time increasing pressure loss.
  • a scroll type compressor including a housing having a fluid inlet port and a fluid outlet port, a fixed scroll joined with said housing and having a first end plate from which a first wrap extends into the interior of said housing, an orbiting scroll having a second end plate from which a second wrap extends, said first and second wraps interfitting at an angular and radial offset to make a plurality of line contacts to define at least one pair of sealed off fluid pockets and a central fluid pocket, a driving mechanism operatively connected to said orbiting scroll to effect the orbital motion of said orbiting scroll, and a rotation preventing means for preventing the rotation of said orbiting scroll so that the volume of the fluid pockets changes during the orbital motion of said scroll, characterised in that the inner end portion of each of said wraps having a bulbous shaped enlarged portion, a valve chamber is formed on one of said enlarged portions, a discharge hole is formed through the inner side wall of said one enlarged portion at a position near the center of the generating circle of
  • FIGS la-ld show end views of a compressor wherein the end plates are removed to show the spiral elements.
  • Spiral elements 1 and 2 are angularly offset and interfit with one another.
  • orbiting spiral element 1 and fixed spiral element 2 make four line contacts at points A-D.
  • a pair of fluid pockets 3a and 3b are defined between line contacts D,C and line contacts A,B as shown by the dotted regions.
  • Fluid pockets 3a and 3b are defined not only by the walls of spiral elements 1 and 2, but also by the end plates from which these spiral elements extend.
  • the pair of fluid pockets 3a and 3b are interconnected as the spiral elements pass between the stages shown in Figure lc and Figure ld. Then, as shown in Figure la, both pockets 3a and 3b merge to form a central single pocket 5 which defines the center portion of both spiral elements 1 and 2.
  • the volume of the single pocket is reduced by further revolution of the orbiting spiral element by 90 0 increments as shown in Figures lb, 1c and ld.
  • outer spaces which open in the stage shown in Figure lb change as shown in Figures lb, lc and ld to form new sealed off fluid pockets in which additional fluid is enclosed.
  • FIG. 2 is a perspective view of the center portion of one scroll member and Figure 3 is a sectional view taken along line III-III in Figure 2.
  • discharge port 4 is formed in end plate 6 and a valve member 7 is disposed on the outside of discharge port 4 to control the closing and opening of discharge port 4.
  • Valve member 7 includes valve plate 71 and valve retainer 72.
  • Valve plate 71 and valve retainer 72 are fixed on the end surface of end plate 6 on the opposite side from which spiral element 2 extends by bolt 73 as shown in Figure 3.
  • the pressure in center pocket 5 increases due to the reduction in volume of central pocket 5 during orbital motion of orbiting spiral element 1.
  • valve plate 71 When the pressure in central pocket 5 is higher than the pressure in discharge chamber 8, valve plate 71 is pushed against valve retainer 72 to open discharge port 4. As a result, the compressed fluid within central pocket 5 discharges into discharge chamber 8. Accordingly, the compressed fluid within central pocket 5 is dicharged by revolution of orbiting spiral element 1.
  • central pocket 5 is connected with the adjacent radial pair of fluid pockets 3a and 3b. This increases the volume of the central pocket so that the remaining compressed fluid within central pocket 5 is re-expanded. After re-expansion of the compressed fluid, the pressure in the expanded central pocket is lower than the pressure in discharge chamber 8 to thereby close discharge port 4 via valve plate 71. Upon re-expansion of the compressed fluid in the central pocket, the pressure in the adjacent radial pair of fluid pockets is suddenly raised. Therefore, the compression power of the fluid within the new central pocket is increased and the pressure of the pair of fluid pockets is raised.
  • the compressor includes compressor housing 10 having front end plate 11 and cup shaped casing 12 fastened to an end surface of front end plate 11.
  • An opening 111 is formed in the center of front end plate 11 for supporting drive shaft 13.
  • An annular projection 112, concentric with opening 111, is formed on the rear end surface of front end plate 11 facing cup shaped casing 12.
  • annular projection 112 bites into an inner wall of the opening of cup shaped casing 12.
  • Cup shaped casing 12 is fixed on the rear end surface of front end plate 11 by a fastening device, such as bolts and nuts, so that the opening of cup shaped casing 12 is covered by front end plate 11.
  • An 0-ring 14 is placed between the outer peripheral surface of annular projection 112 and the inner side wall of cup shaped casing 12 to seal the mating surface between front end plate 11 and cup shaped casing 12.
  • Front end plate 11 has annular sleeve 15 projecting from the front end surface thereof; this sleeve 15 surrounds drive shaft 15 to define a shaft seal cavity.
  • Shaft seal assembly 16 is assembled on drive shaft 15 within the shaft seal cavity.
  • sleeve 15 is attached to the front end surface 6f front end plate 11 by screws (not shown).
  • An O-ring 17 is placed between the front end surface of front end plate 11 and an end surface of sleeve 15 to seal the mating surface of front end plate 11 and annular sleeve 15.
  • sleeve 15 may be formed integral with front-end plate 11.
  • a pulley 18 is rotatably supported by bearing 19 on the outer surface of sleeve-15.
  • An electromagnetic coil 20, which is received in an annular cavity of pulley 18, is mounted on the outer surface of sleeve 15 by support plate 201.
  • An armature plate 21 is elastically supported on the outer end of drive shaft 13 which extends from sleeve 15.
  • a magnetic clutch is formed by pulley 18, magnetic coil 20 and armature plate 21.
  • a number of elements are located within the inner chamber of cup shaped casing 12 including fixed scroll 22, orbiting scroll 23, a driving mechanism for orbiting scroll 22 and rotation preventing/thrust bearing device 24 for orbiting scroll 22.
  • the inner chamber of cup shaped casing 12 is formed between the inner wall of cup shaped casing 12 and the rear end surface of front end plate 11.
  • Fixed scroll 22 includes circular end plate 221, wrap or spiral element 222 affixed to or extending from one end surface of end plate 221, and a plurality of internal bosses 223 axially projecting from the end surface of end plate 221 on the side opposite spiral element 222.
  • the end surface of each boss 223 is seated on the inner surface of end plate portion 121 of cup shaped casing 12 and is fixed to end plate portion 121 by a plurality of bolts 25, one of which is shown in Figure 4.
  • fixed scroll 22 is fixedly disposed within cup shaped casing 12.
  • Circular end plate 221 of fixed scroll 22 partitions the inner chamber of cup shaped casing 12 into discharge chamber 26 having bosses 223, and suction chamber 27, in which spiral element 222 of fixed scroll 22 is located.
  • Sealing member 28 is disposed within circumferential groove 224 of circular end plate 221 for sealing the outer peripheral surface of circular end plate 221 and the inner wall of cup shaped casing 12.
  • Orbiting scroll 23 which is disposed in suction chamber 27, includes circular end plate 231 and wrap or spiral element 232 affixed to or extending from one end surface of circular end plate 231.
  • the spiral elements 222 and 232 interfit at angles of 180° and a predetermined radial offset.
  • the spiral elements define at least a pair of fluid pockets between their interfitting surfaces.
  • Orbiting scroll 23 is connected to the driving mechanism and rotation preventing/thrust bearing device 24 to effect the orbital motion of orbiting scroll 23 by the rotation of drive shaft 13 to thereby compress fluid passing through the compressor, as described above in connection with Figures la-1d.
  • drive shaft 13 which is rotatably supported by sleeve 15 through bearing 29, has a disk shaped rotor 131 at its inner end.
  • Disk shaped rotor 131 is also rotatably supported by front end plate 11 through bearing 30 located within opening 111 of front end plate 11.
  • a crank pin or drive pin 132 projects axially from an axial end surface of disk shaped rotor 131 and is radially offset from the center of drive shaft 13.
  • Circular end.plate 231 of orbiting scroll 23 has tubular boss 233 axially projecting from the end surface opposite to the end surface from which spiral element 232 extends.
  • a discoid or short axial bushing 31 fits into boss 233, and is rotatably supported therein by a bearing, such as needle bearing 32.
  • An eccentric hole 33 is formed on bushing 31; eccentric hole 33 is radially offset from the center of bushing 31.
  • Drive pin 132 which is surrounded by bearing 34, fits into eccentric hole 33. Therefore, bushing 31 is driven by the revolution of drive pin- 132 to thereby rotate within bearing 32.
  • the spiral element of the orbiting scroll is pushed against the spiral element of the fixed scroll due to the moment created between the driving point and the reaction force acting point of the pressurized gas to secure the line contacts and effect radial sealing.
  • Rotation preventing/thrust bearing device 24 is placed between the inner end surface of front end plate 11 and the end surface of circular end plate 231 which faces the inner end surface of front end plate 11, as shown in Figure 4.
  • Rotation preventing/thrust bearing device 24 includes fixed ring 241 and sliding ring 242.
  • Fixed ring 241 is secured to the inner end surface of annular projection 112 by pins (not shown), and provided with a pair of keyways 241a and 241b in an axial end siirface facing orbiting scroll 23.
  • Sliding ring 242 is disposed in a hollow space between fixed ring 241 and circular end plate 231 of orbiting scroll 23, and provided with a pair of keys 242a and 242b on the axial end surface facing fixed ring 241, which are received in keyways 241a and 241b. Therefore, sliding ring 242 is slidable in the radial direction by the guide of keys 242a and 242b within keyways 241a and 241b.
  • Sliding ring 242 is also provided with a pair of keys 242c and 242d on its opposite surface. Keys 242c and 242d are arranged along a diameter perpendicular to the diameter along which keys 242a and 242b are arranged.
  • Circular end plate 231 of orbiting scroll 23 is provided with a pair of keyways (in Figure 6 only one keyway 231a is shown; the other keyway is disposed diametrically opposite to keyway 231a) on a surface facing sliding ring 242 in which are received keys 242c and 242d. Therefore, orbiting scroll 23 is slidable in a radial direction by the guide of keys 242c and 242d within the keyways of circular end plate 242.
  • orbiting scroll 23 is slidable in one radial direction with sliding ring 242, and is slidable in another radial direction independently.
  • the second radial direction is perpendicular to the first direction. Therefore, orbiting scroll 23 is prevented from rotation, but is permitted to move in two radial directions perpendicular to one another.
  • sliding ring 242 is provided with a plurality of pockets or holes 34 which are formed in an axial direction.
  • a bearing means such as balls 243, each having a diameter which is larger than the thickness of sliding ring 242, are retained in pockets 34. Balls 243 contact and roll on the surface of fixed ring 241 and circular end plate 231. Therefore, the axial thrust load from orbiting scroll 23 is supported on fixed ring 241 through balls 243.
  • Each spiral element 222 and 232 has a bulbous shaped enlarged portion 222a and 232a.at its inner end portion.
  • Each enlarged portion 222a and 232a is suitably curved for securing the line contacts and moving the line contacts along the curved surface without interferring with the relative movement of the spiral elements.
  • Both enlarged portions 222a and 232a have the same configuration in order to form a pair of symmetrically sealed off fluid pockets. If the enlarged portions did not have the same configuration, the pair of sealed off fluid pockets would not be symmetrical and, accordingly, a pressure difference would exist between the pair of fluid pockets which would cause an improper torque and vibration of the compressor.
  • Valve chamber 35 which operates as the discharge chamber, is formed on the center of enlarged portion 222a of fixed scroll 22.
  • one end of valve chamber 35 facing end plate 231 of orbiting scroll 23 is closed and the other end of valve chamber 35 is open to discharge chamber 26.
  • Discharge hole 36 is formed through the inner side wall of enlarged portion 222a of fixed scroll 22 at a position near the center of the generating circle of spiral element 222 to interconnect the central pocket of the spiral elements and valve chamber 35, and thereby reduce the pressure loss of passing fluid.
  • the central - pocket is connected to discharge chamber 26 through discharge hole 36 and valve chamber 35.
  • Valve member 37 which includes an annular shaped valve plate 371 (a check valve) and a valve retainer 372, is disposed within valve chamber 35.
  • Valve plate-371 includes reed valve 371a which is formed of spring metal so that valve plate 371 is usually pushed against the inner surface of valve chamber 35 by the spring force of valve plate 371. Therefore, the opening and closing of discharge hole 36 is controlled by reed valve 371a of valve plate 371.
  • Valve retainer 372 is Ic-cated within the inner side of valve plate 37L to prevent the extreme bending of reed valve 371a as shown in Figure 8.
  • the axial movement of valve member 37 is prevented by stopper plate 38 which is fixed on the end surface of end plate 221 by screw 39 on the opposite side from which spiral element 222 extends.
  • orbiting scroll 23 is connected to the driving mechanism and rotation preventing/thrust bearing device 24 to effect the orbital motion of orbiting scroll 23 at a circular radius Ro upon rotation of drive shaft 13.
  • the fluid or refrigerant gas introduced into suction chamber 27 from an external fluid circuit through an inlet port 40 on cup shaped casing 12 is taken into the fluid pockets formed between the spiral elements.
  • fluid in the fluid pockets is moved to the center of the spiral elements with a consequent reduction of volume. Compressed fluid is discharged into discharge chamber 26 from the central pocket through discharge hole 36 and valve chamber 35, and therefrom through outlet port 41 on cup shaped casing 12 to an external fluid circuit.
  • spiral elements 222 and 232 interfit at an angular and radial offset to make a plurality of line contacts so that a pair of fluid pockets 3a and 3b are defined by the outer radial portions of the spiral elements and a central fluid pocket 5 is defined at the center of the spiral elements.
  • the pair of fluid pockets 3a and 3b shift angularly and radially toward the center of interfitting spiral elements 222 and 232 with the volume of each fluid pocket being gradually reduced as shown in Figures 7a-7d.
  • the pair of fluid pockets 3a and 3b are connected to one another when the spiral elements pass stages shown in Figure 7b and Figure 7c, i.e., when the line contact between the inner side wall of enlarged portion 222a of fixed scroll 22 and the inner side wall of enlarged portion 232a of orbiting scroll 23 crosses over the edge of discharge hole 36, the pair of fluid pockets 3a and 3b are connected to one another through discharge hole 36. As shown in Figure 7d, both pockets 3a and 3b are completely connected to one another to form a single central pocket 5. The volume of the new single pocket 5 is further reduced by further revolution of 90° as shown in Figures 7a, 7b and 7c and, the pressure in central pocket 5 is increased.
  • central pocket 5 is connected to the radial adjacent fluid pockets as shown in Figure 7c. Since, in this stage, the volume of the new central pocket which is connected to the pair of fluid pockets is enlarged, the remaining compressed fluid in the central pocket is re-expanded within the new central pocket Therefore, the pressure in central pocket 5 decreases and the volume of the pair of fluid pockets which are connected to the central pocket increases. Accordingly, the pressure in the new central pocket is lower than the pressure in valve chamber 35. Thus, reed valve 371a is pushed against the inner surface of valve chamber 35 due to the pressure difference and the opening of discharge hole 36 is closed by reed valve 371a. Then, another compression stage begins.
  • FIGS 9 and 10 show another embodiment in which the construction of the valve chamber of the enlarged portion of the fixed spiral element is modified.
  • the end of valve chamber 35 facing end plate 231 of orbiting scroll 23 is opened and the other end of valve chamber 35 is closed by end plate 221 of fixed scroll 22.
  • a connecting hole 42, which is connected between valve chamber 35 and discharge chamber 26, is formed through end plate 221.
  • central pocket 5 is connected to discharge chamber 26 through discharge hole 36, valve chamber 35 and connecting hole 42.
  • Valve member 37 is located between the end surface of end plate 221; snap ring 43 disposed on the inner surface of valve chamber 35 prevents axial movement of valve member 37.
EP19820303420 1981-06-29 1982-06-29 Kompressor vom Spiraltyp mit verbessertem Auslassmechismus Expired EP0069531B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP101711/81 1981-06-29
JP10171181A JPS582490A (ja) 1981-06-29 1981-06-29 スクロ−ル型圧縮機

Publications (3)

Publication Number Publication Date
EP0069531A2 true EP0069531A2 (de) 1983-01-12
EP0069531A3 EP0069531A3 (en) 1983-02-23
EP0069531B1 EP0069531B1 (de) 1986-02-26

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19820303420 Expired EP0069531B1 (de) 1981-06-29 1982-06-29 Kompressor vom Spiraltyp mit verbessertem Auslassmechismus

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Country Link
EP (1) EP0069531B1 (de)
JP (1) JPS582490A (de)
AU (1) AU547803B2 (de)
DE (1) DE3269360D1 (de)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0122066A1 (de) * 1983-03-15 1984-10-17 Sanden Corporation Verdrängermaschine nach dem Spiralprinzip mit einer Einrichtung zum Verhindern der Axial-Bewegung des Antriebslagers
US4609334A (en) * 1982-12-23 1986-09-02 Copeland Corporation Scroll-type machine with rotation controlling means and specific wrap shape
EP0105684B1 (de) * 1982-09-26 1987-05-06 Sanden Corporation Kühlkompressor der Spiralbauart mit Spiralbauteil
EP0295664A2 (de) * 1987-06-16 1988-12-21 Sanden Corporation Verdichter
US5174736A (en) * 1990-07-16 1992-12-29 Mitsubishi Jukogyo Kabushiki Kaisha Scroll-type compressor with cover member for suction and discharge cavities
US5224848A (en) * 1990-04-27 1993-07-06 Sanyo Electric Co., Ltd. Scroll compressor with discharge valve opened by centrifugal force
US5249943A (en) * 1991-06-27 1993-10-05 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Scroll type compressor having recessed buffer means in a spiral wrap flat face
WO1997017543A1 (de) * 1995-11-06 1997-05-15 Bitzer Kühlmaschinenbau Gmbh Spiralverdichter
EP0834655A1 (de) * 1996-10-07 1998-04-08 Zexel Corporation Bauweise für Auslassventil
FR2820175A1 (fr) 2001-01-27 2002-08-02 Danfoss As Procede et compresseur spiral pour comprimer un fluide compressible
WO2003058101A1 (de) * 2002-01-12 2003-07-17 Manfred Max Rapp Rückschlagventil mit federzunge
EP1291563A3 (de) * 2001-09-05 2003-12-03 Hydraulik-Ring Gmbh Rückschlagventil sowie Ventil mit einem solchen Rückschlagventil
US7600531B2 (en) 2005-03-18 2009-10-13 Hydraulik-Ring Gmbh Valve with check valve

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DE102009050779B4 (de) 2009-10-27 2016-05-04 Hilite Germany Gmbh Schwenkmotornockenwellenversteller mit einer Reibscheibe und Montageverfahren
DE102010045358A1 (de) 2010-04-10 2011-10-13 Hydraulik-Ring Gmbh Schwenkmotornockenwellenversteller mit einem Hydraulikventil
DE102010019005B4 (de) 2010-05-03 2017-03-23 Hilite Germany Gmbh Schwenkmotorversteller
DE102010061337B4 (de) 2010-12-20 2015-07-09 Hilite Germany Gmbh Hydraulikventil für einen Schwenkmotorversteller
CN117548712B (zh) * 2024-01-11 2024-03-29 山西金石锻造股份有限公司 一种多孔异型法兰加工装置及其使用方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3473728A (en) * 1966-10-06 1969-10-21 Paul Vulliez Volumetric apparatus such as a vacuum pump or the like,having an exact circular translation cycle
DE2160582A1 (de) * 1971-12-07 1973-06-14 Leybold Heraeus Gmbh & Co Kg Verdraengerpumpe mit evolventenfoermigen vorspruengen
EP0012614A1 (de) * 1978-12-15 1980-06-25 Sankyo Electric Company Limited Verbesserungen an Fluidumkompressoren mit ineinandergreifenden Spiralvorsprüngen

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3473728A (en) * 1966-10-06 1969-10-21 Paul Vulliez Volumetric apparatus such as a vacuum pump or the like,having an exact circular translation cycle
DE2160582A1 (de) * 1971-12-07 1973-06-14 Leybold Heraeus Gmbh & Co Kg Verdraengerpumpe mit evolventenfoermigen vorspruengen
EP0012614A1 (de) * 1978-12-15 1980-06-25 Sankyo Electric Company Limited Verbesserungen an Fluidumkompressoren mit ineinandergreifenden Spiralvorsprüngen

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0105684B1 (de) * 1982-09-26 1987-05-06 Sanden Corporation Kühlkompressor der Spiralbauart mit Spiralbauteil
US4609334A (en) * 1982-12-23 1986-09-02 Copeland Corporation Scroll-type machine with rotation controlling means and specific wrap shape
EP0122066A1 (de) * 1983-03-15 1984-10-17 Sanden Corporation Verdrängermaschine nach dem Spiralprinzip mit einer Einrichtung zum Verhindern der Axial-Bewegung des Antriebslagers
EP0295664A2 (de) * 1987-06-16 1988-12-21 Sanden Corporation Verdichter
EP0295664A3 (en) * 1987-06-16 1989-07-26 Sanden Corporation Compressor
US4940342A (en) * 1987-06-16 1990-07-10 Sanden Corporation Compressor with a radial bearing for supporting a drive shaft
US5224848A (en) * 1990-04-27 1993-07-06 Sanyo Electric Co., Ltd. Scroll compressor with discharge valve opened by centrifugal force
US5174736A (en) * 1990-07-16 1992-12-29 Mitsubishi Jukogyo Kabushiki Kaisha Scroll-type compressor with cover member for suction and discharge cavities
US5249943A (en) * 1991-06-27 1993-10-05 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Scroll type compressor having recessed buffer means in a spiral wrap flat face
WO1997017543A1 (de) * 1995-11-06 1997-05-15 Bitzer Kühlmaschinenbau Gmbh Spiralverdichter
WO1997017545A1 (de) * 1995-11-06 1997-05-15 Bitzer Kühlmaschinenbau Gmbh & Co. Kg Spiralverdichter
EP0834655A1 (de) * 1996-10-07 1998-04-08 Zexel Corporation Bauweise für Auslassventil
FR2820175A1 (fr) 2001-01-27 2002-08-02 Danfoss As Procede et compresseur spiral pour comprimer un fluide compressible
US6648617B2 (en) 2001-01-27 2003-11-18 Danfoss A/S Method and scroll compressor for compressing a compressible medium
EP1291563A3 (de) * 2001-09-05 2003-12-03 Hydraulik-Ring Gmbh Rückschlagventil sowie Ventil mit einem solchen Rückschlagventil
US6899126B2 (en) 2001-09-05 2005-05-31 Hydraulik-Ring Gmbh Check valve and valve arrangement comprising such a check valve
DE10143433B4 (de) * 2001-09-05 2013-09-26 Hilite Germany Gmbh Proportionalventil
WO2003058101A1 (de) * 2002-01-12 2003-07-17 Manfred Max Rapp Rückschlagventil mit federzunge
US7600531B2 (en) 2005-03-18 2009-10-13 Hydraulik-Ring Gmbh Valve with check valve

Also Published As

Publication number Publication date
DE3269360D1 (en) 1986-04-03
JPS582490A (ja) 1983-01-08
AU547803B2 (en) 1985-11-07
EP0069531A3 (en) 1983-02-23
EP0069531B1 (de) 1986-02-26
AU8539382A (en) 1983-01-06

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