EP0069531B1 - Compresseur à volutes ayant un mécanisme de refoulement corrigé - Google Patents

Compresseur à volutes ayant un mécanisme de refoulement corrigé Download PDF

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Publication number
EP0069531B1
EP0069531B1 EP19820303420 EP82303420A EP0069531B1 EP 0069531 B1 EP0069531 B1 EP 0069531B1 EP 19820303420 EP19820303420 EP 19820303420 EP 82303420 A EP82303420 A EP 82303420A EP 0069531 B1 EP0069531 B1 EP 0069531B1
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EP
European Patent Office
Prior art keywords
valve
scroll
end plate
fluid
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.)
Expired
Application number
EP19820303420
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German (de)
English (en)
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EP0069531A3 (en
EP0069531A2 (fr
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
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Filing date
Publication date
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Publication of EP0069531A2 publication Critical patent/EP0069531A2/fr
Publication of EP0069531A3 publication Critical patent/EP0069531A3/en
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Publication of EP0069531B1 publication Critical patent/EP0069531B1/fr
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.
  • one of the two scroll members is fixedly disposed and the other is driven to make an orbital motion by a driving mechanism, as shown in EP-A-0 012 614.
  • a driving mechanism as shown in EP-A-0 012 614.
  • 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 by 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 one 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.
  • DE-A-2 160 582 discloses a scroll-type pump comprising a first scroll having a wrap with a bulbous shaped enlarged portion and a second scroll orbiting relatively to the first scroll.
  • the enlarged inner portion is provided with a valve chamber, a discharge hole and a valve member disposed within the valve chamber.
  • the re-expansion volume is not so sufficiently reduced and the valve member is complicated in structure.
  • a scroll type compressor including a housing having a fluid inIet ⁇ ort 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 orbiting scroll, characterised in that the inner end portion of each of said wraps has a bulbous shaped enlarged portion, a valve chamber is formed in the enlarged portion of said first wrap, a discharge hole is formed through the inner side wall of said enlarged portion at a position near the
  • FIGs 1a-1d 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 1c and Figure 1d. Then, as shown in Figure 1a, 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° increments as shown in Figures 1b, 1c and 1d. During the course of revolution, outer spaces which open in the stage shown in Figure 1b change as shown in Figures 1b, 1c and 1d 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 discharged 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.
  • An outer peripheral surface of 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 of front end plate 11 by screws (not shown).
  • An 0-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 each 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 1a-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 surface 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 231 a 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 interfering 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 371 a of valve plate 371.
  • Valve retainer 372 is located within the inner side of valve plate 371 to prevent the extreme bending of reed valve 371 a 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 a 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 371 a. 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.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (6)

1. Compresseur de type à volutes comprenant un carter (10) muni d'un orifice d'entrée de fluide (40) et d'un orifice de sortie de fluide (41), une volute fixe (22) reliée au carter (10) et comportant une première plaque d'extrémité (221) d'où part un premier enroulement (222) pénétrant à l'intérieur du carter (10), une volute orbitale (23) munie d'une seconde plaque d'extrémité (231) d'où part un second enroulement (232), ces premier et second enroulements (222, 232) s'emboîtent avec un décalage angulaire et radial pour former un certain nombre de lignes de contact définissant au moins une paire de poches à fluide étanches et une poche à fluide centrale, un mécanisme d'entraînement (13-132-31-32) relié en fonctionnement à la volute orbitale (23) pour produire le mouvement orbital de cette volute orbitale (23), et des moyens anti-rotation (24) permettant d'empêcher la rotation de la volute orbitale (23) de façon que le volume des poches à fluide change pendant le mouvement orbital de la volute orbitale (23), compresseur caractérisé en ce que la partie d'extrémité intérieure de chacun des enroulements (222, 232) comporte une partie agrandie en forme de bulbe (222a, 232a), en ce qu'une chambre de soupape (35) est formée dans la partie agrandie (222a) du premier enroulement (222), en ce qu'un trou de refoulement (36) est percé dans la paroi latérale intérieure de la partie agrandie (222a) dans une position voisine du centre du cercle générateur de la volute orbitale (23), de manière à relier la poche à fluide centrale à la chambre de soupape (35), en ce qu'un élément de soupape (37) est placé dans la chambre de soupape (35) pour commander l'ouverture et la fermeture du trou de refoulement (36), et en ce que l'élément de soupape (37) comprend une plaque de soupape de forme annulaire (371) muni d'une soupape à anche (371 a) et d'un élément de retenue de soupape (372) placé du côté intérieur de la plaque de soupape (371).
2. Compresseur de type à volutes selon la revendication 1, caractérisé en ce que la volute fixe (22) est fixée à l'intérieur du carter (10) et en ce que la première plaque d'extrémité (221) sépare l'intérieur du carter (10) en une chambre de refoulement (26) et une chambre d'aspiration (27), la chambre de soupape (35) étant reliée à la chambre de refoulement (26).
3. Compresseur de type à volutes selon la revendication 1, caractérisé en ce que l'extrémité axiale de la chambre de soupape (35) venant en face de la seconde plaque d'extrémité (231), est fermée, et en ce que l'autre extrémité axiale est ouverte sur la première plaque d'extrémité (221), l'élément de soupape (37) étant disposé entre la surface d'extrémité axiale intérieure de la chambre de soupape (35) et une plaque de butée (38) fixée sur la surface d'extrémité de la première plaque d'extrémité (221) pour limiter le mouvement axial de la plaque de soupape (371).
4. Compresseur de type à volutes selon la revendication 1, caractérisé en ce que l'extrémité axiale de la chambre de soupape (35) venant en face de la seconde plaque d'extrémité (231) est ouverte, et en ce que l'autre extrémité axiale est fermée par la première plaque d'extrémité (221), le compresseur de type à volutes comprenant en outre un trou de liaison (42) percé dans la première plaque d'extrémité (221) pour relier la chambre de soupape (35) à la chambre de refoulement (26), l'élément de soupape (37) étant monté entre la surface d'extrémité de la première plaque d'extrémité (221) et un anneau de blocage (43) placé sur la surface intérieure de la chambre de soupape (35) pour limiter le mouvement axial de l'élément de soupape (37).
5. Compresseur de type à volutes selon la revendication 1, caractérisé en ce que le trou de refoulement (36) présente une forme circulaire.
6. Compresseur de type à volutes selon la revendication 1, caractérisé en ce que le trou de refoulement (36) présente une forme ovale.
EP19820303420 1981-06-29 1982-06-29 Compresseur à volutes ayant un mécanisme de refoulement corrigé Expired EP0069531B1 (fr)

Applications Claiming Priority (2)

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

Publications (3)

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

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19820303420 Expired EP0069531B1 (fr) 1981-06-29 1982-06-29 Compresseur à volutes ayant un mécanisme de refoulement corrigé

Country Status (4)

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

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10103775A1 (de) * 2001-01-27 2002-08-14 Danfoss As Verfahren und Spiralverdichter zur Verdichtung eines kompressiblen Mediums
DE102005013085B3 (de) * 2005-03-18 2006-06-01 Hydraulik-Ring Gmbh Ventil mit Rückschlagventil
US8453616B2 (en) 2009-10-27 2013-06-04 Hilite Germany Gmbh Vane-type motor cam phaser with a friction disc and mounting method
US8505582B2 (en) 2010-05-03 2013-08-13 Hilite Germany Gmbh Hydraulic valve
US8662040B2 (en) 2010-04-10 2014-03-04 Hilite Germany Gmbh Oscillating-motor camshaft adjuster having a hydraulic valve
US8752514B2 (en) 2010-12-20 2014-06-17 Hilite Germany Gmbh Hydraulic valve for an oscillating motor adjuster

Families Citing this family (12)

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Publication number Priority date Publication date Assignee Title
JPS5958187A (ja) * 1982-09-26 1984-04-03 Sanden Corp スクロ−ル型圧縮機
US4609334A (en) * 1982-12-23 1986-09-02 Copeland Corporation Scroll-type machine with rotation controlling means and specific wrap shape
JPS59142480U (ja) * 1983-03-15 1984-09-22 サンデン株式会社 スクロ−ル型流体装置
JPH0216071Y2 (fr) * 1987-06-16 1990-05-01
ES2077226T3 (es) * 1990-04-27 1995-11-16 Sanyo Electric Co Compresor de espirales.
JP2680722B2 (ja) * 1990-07-16 1997-11-19 三菱重工業株式会社 圧縮機
JPH051882U (ja) * 1991-06-27 1993-01-14 株式会社豊田自動織機製作所 スクロール型圧縮機
WO1997017543A1 (fr) * 1995-11-06 1997-05-15 Bitzer Kühlmaschinenbau Gmbh Compresseur helicoidal
JPH10110691A (ja) * 1996-10-07 1998-04-28 Zexel Corp 吐出弁構造
DE10143433B4 (de) 2001-09-05 2013-09-26 Hilite Germany Gmbh Proportionalventil
DE10200911A1 (de) * 2002-01-12 2003-10-09 Manfred Max Rapp Rückschlagventil mit Federzunge
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

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Publication number Priority date Publication date Assignee Title
FR93048E (fr) * 1966-10-06 1969-01-31 Vulliez Paul Appareil columétrique tel que pompe ou analogue a cycle de translation circulaire.
DE2160582A1 (de) * 1971-12-07 1973-06-14 Leybold Heraeus Gmbh & Co Kg Verdraengerpumpe mit evolventenfoermigen vorspruengen
JPS5581296A (en) * 1978-12-15 1980-06-19 Sanden Corp Positive-displacement fluid compressor

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10103775A1 (de) * 2001-01-27 2002-08-14 Danfoss As Verfahren und Spiralverdichter zur Verdichtung eines kompressiblen Mediums
DE10103775B4 (de) * 2001-01-27 2005-07-14 Danfoss A/S Verfahren und Spiralverdichter zur Verdichtung eines kompressiblen Mediums
DE102005013085B3 (de) * 2005-03-18 2006-06-01 Hydraulik-Ring Gmbh Ventil mit Rückschlagventil
US8453616B2 (en) 2009-10-27 2013-06-04 Hilite Germany Gmbh Vane-type motor cam phaser with a friction disc and mounting method
US8794201B2 (en) 2009-10-27 2014-08-05 Hilite Germany Gmbh Vane-type motor cam phaser with a friction disc and method for mounting a friction disc on a rotor
US8662040B2 (en) 2010-04-10 2014-03-04 Hilite Germany Gmbh Oscillating-motor camshaft adjuster having a hydraulic valve
US8505582B2 (en) 2010-05-03 2013-08-13 Hilite Germany Gmbh Hydraulic valve
US8752514B2 (en) 2010-12-20 2014-06-17 Hilite Germany Gmbh Hydraulic valve for an oscillating motor adjuster

Also Published As

Publication number Publication date
EP0069531A3 (en) 1983-02-23
DE3269360D1 (en) 1986-04-03
AU8539382A (en) 1983-01-06
JPS582490A (ja) 1983-01-08
AU547803B2 (en) 1985-11-07
EP0069531A2 (fr) 1983-01-12

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