(19)
(11)EP 0 380 439 B1

(12)EUROPEAN PATENT SPECIFICATION

(45)Mention of the grant of the patent:
12.01.1994 Bulletin 1994/02

(21)Application number: 90630024.9

(22)Date of filing:  23.01.1990
(51)International Patent Classification (IPC)5F04C 18/02

(54)

Scroll compressor with axial compliancy

Spiralverdichter mit axialer Anpassung

Compresseur à volute avec conformité axiale


(84)Designated Contracting States:
DE ES FR IT

(30)Priority: 23.01.1989 US 299574

(43)Date of publication of application:
01.08.1990 Bulletin 1990/31

(73)Proprietor: CARRIER CORPORATION
Syracuse New York 13221 (US)

(72)Inventors:
  • Fraser, Howard Henry
    Lafayette, New York 13084 (US)
  • Etemad, Shahrokh
    Stratford, Connecticut 06497-2452 (US)
  • Lane, William Robinson
    Dewitt, New York 13214 (US)

(74)Representative: Waxweiler, Jean et al
Dennemeyer & Associates Sàrl P.O. Box 1502
1015 Luxembourg
1015 Luxembourg (LU)


(56)References cited: : 
EP-A- 0 143 526
GB-A- 2 202 905
DE-A- 3 522 854
US-A- 4 600 369
  
      
    Note: Within nine months from the publication of the mention of the grant of the European patent, any person may give notice to the European Patent Office of opposition to the European patent granted. Notice of opposition shall be filed in a written reasoned statement. It shall not be deemed to have been filed until the opposition fee has been paid. (Art. 99(1) European Patent Convention).


    Description


    [0001] The present invention relates to an axial compliance means in a scroll compressor and to a method for manufacturing same.

    Background Of The Invention



    [0002] During the compression process in a scroll compressor the pressure of the gas being compressed acts against the scroll elements tending to separate them both radially and axially. To achieve axial compliancy and axial sealing between the scroll elements, a sealed, high pressure chamber can be created between the back of the orbiting scroll and the crankcase. The chamber should not have any radial or axial interference with the Oldham coupling ring, the orbiting scroll slots, the crankcase slots and the internal bore. Such a sealed high pressure pocket can be created by using two annular O-ring grooves such that the O-rings are compressed against the back of the orbiting scroll. The major disadvantage of this design is the size limitation of the sealed high pressure gas pocket. One way of increasing the area is to enlarge the diameter of the Oldham coupling ring which results in a wider crankcase and thus a larger compressor shell diameter. Generally, the compressor shell diameter is dictated by the motor frame necessary to produce the required output and anything larger is undesirable.

    [0003] US-A-4 600 369 discloses a scroll compressor having annular grooves and seals forming an annular chamber, but does not disclose a fixed scroll or anti-rotation means. Without anti-rotation means, there is no loss of available space due to the movement of the Oldham ring.

    [0004] GB-A-2,202,905 is directed to the lubrication structure of a scroll compressor. There is no fluid pressure biasing of the orbiting scroll in any practical sense other than the lubricant supplied to the thrust bearing at a low pressure.

    [0005] In EP-A-0 143 526 there is described an axial compliance means in a scroll compressor according to the preamble of claim 1. Specifically, EP-A-0 143 526 discloses, in a scroll compressor having a fixed scroll means, an orbiting scroll means in operative engagement with the fixed scroll means crankcase means with a central opening therein, and rotation means coacting with the orbiting scroll means and the crankcase means to limit the orbiting scroll means to orbiting motion, an axial compliance means comprising pocket means located between the orbiting scroll means and the crankcase means, the pocket means being surrounded by groove means, seal means located in the groove means, the orbiting scroll means movably engaging the seal means and coacting therewith to isolate the pocket means, and means for supplying pressurized fluid to the pocket means for providing an axial force to the orbiting scroll means. A method for manufacturing an axial compliance means according to the preamble of claim 6 is also known from EP-A-0 143 526.

    [0006] It is an object of this invention to provide axial compliancy using pocket means configured to combine an efficient use of the available space with ease of manufacture.

    [0007] It is another object of this invention to provide axial compliancy using the orbiting scroll without increasing bearing loading and without increasing the orbiting scroll outer diameter envelope.

    [0008] To achieve this, the axial compliance means of the invention is characterized by the features claimed in the characterizing portion of claim 1 and the method of the invention is characterized by the features set forth in the characterizing portion of claim 6. Basically, according to the invention, axial compliancy is achieved in the orbiting scroll without increasing the bearing loading or the outer diameter envelope of the orbiting scroll by locating one or two fluid pockets in the crankcase facing the back of the orbiting scroll and shaped to efficiently use the available space.

    [0009] Advantageous embodiments of the invention are claimed in the subclaims.

    [0010] The ideal configuration provides a pocket(s) with the maximum area. The available area for the pocket(s) surrounds the bearing and the boss of the orbiting scroll and has an outer boundary of a generally figure eight shape due to the coaction of the Oldham coupling ring and slots. Obviously, the available area is not of a simple configuration. Using the waist portion of the figure eight shape as the axis of symmetry, the available area can be generally defined by: (1) a pair of kidney shaped pockets; (2) a pair of crescent shaped pockets defined by two symmetrical circular cuts; or (3) a pair of symmetrical circular cuts and a central circular cut are made such that their combined outer periphery is of a figure eight shape with a central circular periphery to define an annular pocket.

    [0011] It is a feature of this invention to locate the pocket(s) in a housing which overhangs the bearing.

    [0012] It is a further feature of this invention to locate the bearing support close to the gas compression force by overhanging the pocket(s) and thereby minimizing the tipping moment.

    [0013] It is another feature of this invention to lift the orbiting scroll off the crankcase so that it rides on the seals and thereby reduces frictional forces due to the reduced loading.

    [0014] It is an additional feature of this invention to permit the Oldham coupling groove to be located close to the center to thereby reduce the envelope of the compressor. These objects, and others as will become apparent hereinafter, are accomplished by the present invention.

    Brief Description Of The Drawings



    [0015] For a fuller understanding of the present invention, reference should now be made to the following detailed description thereof taken in conjunction with the accompanying drawings wherein:

    Figure 1 is a vertical sectional view taken along line 1-1 of Figure 3 of a portion of a scroll compressor which is in the unenergized state employing the present invention;

    Figure 2 is a vertical sectional view taken along line 2-2 of Figure 3 of a portion of a scroll compressor with the axial compliance mechanism energized;

    Figure 3 is a horizontal sectional view taken along 3-3 of Figure 1;

    Figure 4 is a view corresponding to Figure 3 but showing a second embodiment of the invention;

    Figure 5 is a view corresponding to Figure 3 but showing a third embodiment of the invention; and

    Figure 6 is a partial sectional view taken along line 6-6 of Figure 3.


    Description Of The Preferred Embodiment



    [0016] In the Figures, the numeral 10 generally designates a low side scroll compressor. Muffler/separator plate 14 overlies fixed scroll 20 and defines a high pressure chamber 13 within shell 12. Crankcase 40 overhangs crankshaft 60 and is bolted or otherwise suitably secured to fixed scroll 20. Orbiting scroll 30 has a wrap 31 which is in operative engagement with wrap 21 of fixed scroll 20 while one side of plate portion 32 engages fixed scroll 20 and the other side coacts with Oldham ring 64, as is conventional.

    [0017] Additionally, the other side of plate portion 32 also is in sealing engagement with seals 66 and 68 which are located in kidney shaped grooves 42 and 43 which surround pockets 50 and 52, respectively. Pockets 50 and 52 are in fluid communication with discharge pressure in high pressure chamber 13 via a flow path which is best illustrated in Figures 1, 3 and 6 and which serially includes passage 14-1 in muffler separator plate 14, bores 20-1 and 2 in fixed scroll 20, bore 40-1 and bore 40-2 which branches into bores 40-3 and 40-4 which are in fluid communication with pockets 50 and 52, respectively.

    [0018] When the scroll compressor 10 is in operation, gas at discharge pressure is delivered from outlet port 16, through muffler/separator plate 14 into high pressure chamber 13 which is connected to the compressor discharge line (not illustrated). The gas at discharge pressure is supplied from chamber 13 to pockets 50 and 52 via passage 14-1 and bores 20-1 and 2 and 40-1 to 4. The high pressure fluid in pockets 50 and 52 acts on the plate 32 of the orbiting scroll 30 lifting orbiting scroll 30 off of the crankcase 40 so that orbiting scroll 30 rides on seals 66 and 68 as shown in Figure 2. A small net force acting on the fixed scroll 30 tends to keep fixed scroll 20 and orbiting scroll 30 in axial contact in opposition to the separating forces produced in compressing gas due to the coaction of the fixed and orbiting scrolls while greatly reducing friction forces.

    [0019] In machining the embodiment of Figures 1-3, two kidney shaped grooves 42 and 43 are machined or otherwise suitably formed in crankcase 40. Circular or other suitably shaped seals 66 and 68 may then be placed in grooves 42 and 43.

    [0020] In the Figure 4 embodiment, two displaced circular grooves 142 and 143 in the form of interlocked rings are machined or otherwise suitably formed in crankcase 140 resulting in the formation of two crescent shaped pockets 150 and 152. The seal 166 is in the shape of two interlocked rings corresponding to grooves 142 and 143. All of the extreme positions of Oldham ring 164 are illustrated to show the available area for pockets 150 and 152. Fluid pressure would be supplied to pockets 150 and 152 via bores 140-3 and 140-4, respectively, in the same manner as the embodiment of Figures 1-3.

    [0021] In the Figure 5 embodiment, there are two displaced circular grooves 242 and 243 in the form of interlocking rings, as in the Figure 4 embodiment, plus a third circular groove 244 surrounding opening 241 in crankcase 240. The seal 266 is located only in the outermost portion of grooves 242 and 243 and seal 268 is in groove 244. As a result, there is a single annular pocket, 250, formed and defined by the area between seals 266 and 268. Because there is only one pocket, the fluid communication with pocket 250 can be by bore 240-3 but otherwise in the same manner as the embodiments of Figures 1-4. The location of bore 240-3 can be changed so that it is a vertical path rather than a slanted path in order to simplify machining.

    [0022] Although preferred embodiments of the present invention have been illustrated and described, other changes will occur to those skilled in the art. For example, although discharge pressure is described as supplied to the pockets, intermediate pressure can be used. It is therefore intended that the scope of the present invention is to be limited only by the scope of the appended claims.


    Claims

    1. Axial compliance means in a scroll compressor (10) having a fixed scroll means (20), an orbiting scroll means (30) in operative engagement with said fixed scroll means (20), crankcase means (40;140;240) with a central opening ( ;241) therein, and anti-rotation means (64;164; ) coacting with said orbiting scroll means (30) and said crankcase means (40;140;240) to limit said orbiting scroll means (30) to orbiting motion, said axial compliance means comprising:
       pocket means (50,52;150,152;250) located between said orbiting scroll means (30) and said crankcase means (40;140;240), said pocket means (50,52;150,152;250) being surrounded by groove means (42,43;142,143;242,243,244),
       seal means (66,68;166;266,268) located in said groove means (42,43;142,143;242,243,244), said orbiting scroll means (30) movably engaging said seal means (66,68;166;266,268) and coacting therewith to isolate said pocket means (50,52;150,152;250), and
       means (40-3,40-4;140-3,140-4;240-3) for supplying pressurized fluid to said pocket means (50,52;150,152;250) for providing an axial force to said orbiting scroll means (30),
       characterized in that said pocket means (50,52;150,152;250) is formed in a generally flat annular surface of said crankcase means (40;140;240), and
       said groove means (42,43;142,143;242, 243,244) has an outer periphery having portions at varying distances from said central opening ( ;241) such that said outer periphery is at a non-uniform distance from said anti-rotation means (64;164; ) so as to maximize said pocket means (50,52;150,152;250).
     
    2. The axial compliance means of claim 1, characterized in that said scroll compressor (10) includes a crankshaft (60) and said crankcase means (40;140;240) overhangs said crankshaft (60) whereby said pocket means (50,52;150,152;250) can be located close to the portion of said orbiting scroll means (30) subjected to the highest axial forces due to gas compression.
     
    3. The axial compliance means of claim 1, characterized in that said pocket means is two pockets (50,52) and said pocket means (50, 52), groove means (42,43) and seal means (66,68) are generally kidney shaped and symmetrically located with respect to said central opening in said crankcase means (40).
     
    4. The axial compliance means of claim 1, characterized in that said pocket means is a pair of crescent shaped pockets (150,152) which meet each other at each of their ends and said seal means (166) is in the shape of two interlocked rings (166).
     
    5. The axial compliance means of claim 1 characterized in that said groove is in the form of two displaced interlocked rings (242,243) such that said outer periphery is continuous and a third ring (244) within a common area defined by said interlocked rings (242,243) and spaced from each of said interlocked rings (242,243), said seal means (266,268) being located only in the portion of said grooves means (242,243,244) which is defined by said outer periphery and by said third ring (244).
     
    6. A method for manufacturing axial compliance means for a scroll compressor (10) having a fixed scroll (20), and orbiting scroll (30) in operative engagement with said fixed scroll (20), a crankcase (40;140;240) with a central opening ( ;241) herein and anti-rotation means (64;164; ) coacting with said orbiting scroll (30) and said crankcase (40;140;240) to limit said orbiting scroll (30) to orbiting motion, said method comprising the steps of:
       providing pocket means (50,52;150,152;250) between said orbiting scroll (30) and said crankcase (40;140;240) and grooves means (42,43;142,143;242, 243,244) surrounding the pocket means (50,52; 150,152;250),
       forming fluid path means (40-3,40-4;140-3,140-4;240-3) in the crankcase (40;140;240) terminating in the pocket means (50,52;150,152;250),
       locating sealing means (66,68;166;266,268) in the groove means (42,43;142,143;242,243,244),
       securing the crankcase (40;140;240) to the fixed scroll (20) with said orbiting scroll (30) therebetween and in engagement with the sealing means (66,68;166;266,268) to thereby isolate said pocket means (50,52;150,152;250) whereby when pressurized fluid is supplied to said pocket means (50,52;150,152;250) via said fluid path means (40-3,40-4;140-3,140-4;240-3) an axial force is provided to said orbiting scroll (30),
       characterized by forming said pocket means (50,52;150,152;250) in a generally flat annular surface of the crankcase (40;140;240), and
       forming said grooves means (42,43;142, 143;242,243,244) surrounding the pocket means with an outer periphery having portions at varying distances from said central opening ( ;241) such that said outer periphery is at a non-uniform distance from said anti-rotation means (64;164; ) so as to maximize said pocket means (50,52;150,152;250).
     
    7. The method of claim 6, characterized in that the step of forming the pocket means (50,52) includes the forming of two kidney shaped pockets (50,52) symmetrically located in the crankcase (40) with respect to the central opening.
     
    8. The method of claim 6, characterized in that the step of forming the groove means includes the step of forming two displaced interlocking rings (142,143) defining a pair of crescent shapes in which the pocket means (150,152) are located.
     
    9. The method of claim 6, characterized in that the step of forming groove means includes forming two displaced interlocked rings (242,243) such that the outer periphery is continuous and a third ring (244) within a common area defined by the interlocked rings (242,243,244) includes the locating of sealing means (266,268) only in the portion of the groove means (242,243,244) which is defined by the outer periphery and by the third ring (244).
     


    Ansprüche

    1. Axial nachgiebige Einrichtung in einem Spiralkompressor (10), der eine feste Spiraleinrichtung (20) hat, eine umlaufende Spiraleinrichtung (30) in operativer Berührung mit der festen Spiraleinrichtung (20), eine Kurbelgehäuseinrichtung (40; 140; 240) mit einer zentralen Öffnung ( ; 241) darin, und eine Antidreheinrichtung (64; 164; ), die mit der umlaufenden Spiraleinrichtung (30) und der Kurbelgehauseeinrichtung (40; 140; 240) zusammenwirkt, um die umlaufende Spiraleinrichtung (30) auf eine Umlaufbewegung zu begrenzen, wobei die axial nachgiebige Einrichtung aufweist:
    eine Tascheneinrichtung (50, 52; 150, 152; 250), die zwischen der umlaufenden Spiraleinrichtung (30) und der Kurbelgehäuseeinrichtung (40; 140; 240) angeordnet ist, wobei die Tascheneinrichtung (50, 52; 150, 152; 250) durch eine Nuteinrichtung (42, 43; 142, 143; 242, 243, 244) umgeben ist,
    eine Dichteinrichtung (66, 68; 166; 266, 268), die in der Nuteinrichtung (42, 43; 142, 143; 242, 243, 244) angeordnet ist, wobei die umlaufende Spiraleinrichtung (30) die Dichteinrichtung (66, 68; 166; 266, 268) beweglich berührt und mit derselben zusammenwirkt, um die Tascheneinrichtung (50, 52; 150, 152; 250) zu isolieren, und
    eine Einrichtung (40-3, 40-4; 140-3, 140-4; 240-3) zum Versorgen der Tascheneinrichtung (50, 52; 150, 152; 250) mit Druckfluid zum Ausüben einer axialen Kraft auf die umlaufende Spiraleinrichtung (30),
    dadurch gekennzeichnet, daß die Tascheneinrichtung (50, 52; 150, 152; 250) in einer insgesamt ebenen, ringförmigen Oberfläche der Kurbelgehäuseeinrichtung (40; 140; 240) gebildet ist, und
    die Nuteinrichtung (42, 43; 142, 143; 242, 243, 244) einen äußeren Umfang hat, der Teile in verschiedenen Abständen von der zentralen Öffnung ( ; 241) hat, so daß der äußere Umfang in einem ungleichförmigen Abstand von der Antidreheinrichtung (64; 164; ) ist, um so die Tascheneinrichtung (50, 52; 150, 152; 250) zu maximieren.
     
    2. Axial nachgiebige Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Spiralkompressor (10) eine Kurbelwelle (60) aufweist und daß die Kurbelgehauseeinrichtung (40; 140; 240) über der Kurbelwelle (60) hängt, wodurch die Tascheneinrichtung (50, 52; 150, 152; 250) nahe bei dem Teil der umlaufenden Spiraleinrichtung (30) angeordnet werden kann, welcher den höchsten axialen Kräften aufgrund der Gaskompression ausgesetzt ist.
     
    3. Axial nachgiebige Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Tascheneinrichtung aus zwei Taschen (50, 52) besteht und daß die Tascheneinrichtung (50, 52), die Nuteinrichtung (42, 43) und die Dichteinrichtung (66, 68) insgesamt nierenförmig und symmetrisch in bezug auf die zentrale Öffnung in der Kurbelgehäuseeinrichtung (40) angeordnet sind.
     
    4. Axial nachgiebige Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Tascheneinrichtung aus einem Paar sichelförmiger Taschen (150, 152) besteht, die sich gegenseitig an jedem ihrer Enden treffen, und daß die Dichteinrichtung (166) die Form von zwei verschachtelten Ringen (166) hat.
     
    5. Axial nachgiebige Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Nut die Form von zwei versetzten, verschachtelten Ringen (242, 243) hat, so daß der äußere Umfang durchgehend ist und ein dritter Ring (244) innerhalb eines gemeinsamen Querschnitts durch die verschachtelten Ringe (242, 243) gebildet und von jedem der verschachtelten Ringe (242, 243) beabstandet ist, wobei die Dichteinrichtung (266, 268) nur in dem Teil der Nuteinrichtung (242, 243, 244) angeordnet ist, der durch den äußeren Umfang und durch den dritten Ring (244) definiert ist.
     
    6. Verfahren zum Herstellen einer axial nachgiebigen Einrichtung für einen Spiralkompressor (10), der eine feste Spirale (20) und eine umlaufende Spirale (30) in operativem Eingriff mit der festen Spirale (20) hat, ein Kurbelgehäuse (40; 140; 240) mit einer zentralen Öffnung ( ; 241) darin hat und eine Antidreheinrichtung (64; 164; ) hat, die mit der umlaufenden Spirale (30) und dem Kurbelgehäuse (40; 140; 240) zusammenwirkt, um die umlaufende Spirale (30) auf die Umlaufbewegung zu beschränken, wobei das Verfahren die Schritte beinhaltet:
    Schaffen einer Tascheneinrichtung (50, 52; 150, 152; 250) zwischen der umlaufenden Spirale (30) und dem Kurbelgehäuse (40; 140; 240) und der Nuteinrichtung (42, 43; 142, 143; 242, 243, 244), welche die Tascheneinrichtung (50, 52; 150, 152; 250) umgibt,
    Herstellen einer Fluidwegeinrichtung (40-3, 40-4; 140-3, 140-4; 240-3) in dem Kurbelgehäuse (40; 140; 240), die in der Tascheneinrichtung (50, 52; 150, 152; 250) endigt, Anordnen einer Dichteinrichtung (66, 68; 166; 266, 268) in der Nuteinrichtung (42, 43; 142, 143; 242, 243 244), Befestigen des Kurbelgehäuses (40; 140; 240) an der festen Spirale (20) mit der umlaufenden Spirale (30) dazwischen und in Eingriff mit der Dichteinrichtung (66, 68; 166; 266, 268), um dadurch die Tascheneinrichtung (50, 52; 150, 152; 250) zu isolieren, wodurch, wenn unter Druck stehendes Fluid der Tascheneinrichtung (50, 52; 150, 152; 250) über die Fluidwegeinrichtung (40-3, 40-4; 140-3, 140-4; 240-3) zugeführt wird, eine axiale Kraft auf die umlaufende Spirale (30) ausgeübt wird,
    gekennzeichnet durch Bilden der Tascheneinrichtung (50, 52; 150, 152; 250) in einer insgesamt ebenen ringförmigen Oberfläche des Kurbelgehäuses (40; 140; 240), und
    Bilden der Nuteinrichtung (42, 43; 142, 143; 242, 243, 244), die die Tascheneinrichtung umgibt, mit einem äußeren Umfang, der Teile in variierenden Abständen von der zentralen Öffnung ( ; 241) hat, so daß der äußere Umfang in einem ungleichförmigen Abstand von der Antidreheinrichtung (64; 164; ) ist, um so die Tascheneinrichtung (50, 52; 150, 152; 250) zu maximieren.
     
    7. Verfahren nach Anspruch 6, dadurch gekennzeichnet, daß der Schritt des Bildens der Tascheneinrichtung (50, 52) beinhaltet, zwei nierenförmige Taschen (50, 52) zu bilden, die in dem Kurbelgehäuse (40) symmetrisch in bezug auf die zentrale Öffnung angeordnet sind.
     
    8. Verfahren nach Anspruch 6, dadurch gekennzeichnet, daß der Schritt des Bildens der Nuteinrichtung den Schritt beinhaltet, zwei versetzte, ineinandergreifende Ringe (142, 143) zu bilden, die ein Paar Sichelformen definieren, in welchen die Tascheneinrichtungen (50, 152) angeordnet werden.
     
    9. Verfahren nach Anspruch 6, dadurch gekennzeichnet, daß der Schritt des Bildens der Nuteinrichtung beinhaltet, daß zwei versetzte verschachtelte Ringe (242, 243) gebildet werden, so daß der äußere Umfang durchgehend ist, und ein dritter Ring (244) innerhalb eines gemeinsamen Querschnittes, der durch die verschachtelten Ringe (242, 243, 244) definiert wird, und daß die Dichteinrichtung (266, 268) nur in dem Teil der Nuteinrichtung (242, 243, 244) aufgenommen wird, der durch den äußeren Umfang und durch den dritten Ring (244) definiert wird.
     


    Revendications

    1. Moyen procurant une élasticité axiale dans un compresseur à volutes (10) comportant un moyen de volute fixe (20), un moyen de volute orbitante (30) en contact d'entraînement avec ledit moyen de volute fixe (20), un moyen de vilebrequin (40; 140; 240) dans lequel est pratiquée une ouverture centrale ( ; 241), ainsi qu'un moyen d'antirotation (64; 164; ) agissant conjointement avec ledit moyen de volute orbitante (30) et avec ledit moyen de vilebrequin (40; 140; 240) pour limiter le mouvement dudit moyen de volute orbitante (30) à un mouvement orbital, ledit moyen procurant une élasticité axiale comprenant :
       un moyen de poches (50, 52; 150, 152; 250) disposé entre ledit moyen de volute orbitante (30) et ledit moyen de vilebrequin (40; 140; 240), ledit moyen de poches (50, 52; 250, 152; 250) étant entouré par un moyen de rainures (42, 43; 142, 143; 242, 243, 244);
       des moyens d'étanchéification (66, 68; 166; 266, 268) logés dans ledit moyen de rainures (42, 43; 142, 143; 242, 243, 244), ledit moyen de volute orbitante (30) venant se mettre en contact par mouvement avec ledit moyen d'étanchéification (66, 68; 166; 266, 268) et agissant conjointement avec ce dernier pour isoler ledit moyen de poches (50, 52; 150, 152; 250); et
       des moyens (40-3, 40-4; 140-3, 140-4; 240-3) pour approvisionner du fluide sous pression audit moyen de poches (50, 52; 150, 152; 250) afin de procurer une force axiale audit moyen de volute orbitante (30),
       caractérisé en ce que ledit moyen de poches (50, 52; 150, 152; 250) est pratiqué dans une surface annulaire généralement plate dudit moyen de vilebrequin (40; 140; 240), et
       ledit moyen de rainures (42, 43; 142, 143; 242, 243, 244) comportent une périphérie externe possédant des portions dont les distances varient par rapport à ladite ouverture centrale ( ; 241) de telle sorte que ladite périphérie externe se trouve à une distance non uniforme dudit moyen d'antirotation (64; 164; ) de façon à maximiser ledit moyen de poches (50, 52; 150, 152; 250).
     
    2. Moyen procurant une élasticité axiale selon la revendication 1, caractérisé en ce que ledit compresseur à volutes (10) englobe un vilebrequin (60) et ledit moyen de vilebrequin (40; 140; 240) surplombe ledit vilebrequin (60), ce qui permet audit moyen de poches (50, 52; 150; 152; 250) de venir se disposer à proximité de la portion dudit moyen de volute orbitante (30) soumis aux forces axiales les plus élevées provenant de la compression du gaz.
     
    3. Moyen procurant une élasticité axiale selon la revendication 1, caractérisé en ce que ledit moyen de poches représente deux poches (50, 52) et ledit moyen de poches (50, 52), ledit moyen de rainures (42, 43) et ledit moyen d'étanchéification (66, 68) sont généralement réniformes et disposés symétriquement par rapport à ladite ouverture centrale dans ledit moyen de vilebrequin (40).
     
    4. Moyen procurant une élasticité axiale selon la revendication 1, caractérisé en ce que ledit moyen de poches représente une paire de poches (150, 152) en forme de croissant, qui se rencontrent l'une l'autre à chacune de leurs extrémités et ledit moyen d'étanchéification (166) a la forme de deux anneaux enchevêtrés (166).
     
    5. Moyen procurant une élasticité axiale selon la revendication 1, caractérisé en ce que ladite rainure a la forme de deux anneaux enchevêtrés décalés (242, 243), si bien que ladite périphérie externe est continue, et d'un troisième anneau (244) à l'intérieur d'une aire commune définie par lesdits anneaux enchevêtrés (242, 243) et espacé de chacun desdits anneaux enchevêtrés (242, 243), ledit moyen d'étanchéification (266, 268) étant disposé uniquement dans la portion dudit moyen de rainures (242, 243, 244), qui est définie par ladite périphérie externe et par ledit troisième anneau (244).
     
    6. Procédé pour fabriquer un moyen procurant une élasticité axiale pour un compresseur à volutes (10) comportant une volute fixe (20) et volute orbitante (30) en contact d'entraînement avec ladite volute fixe (20), un vilebrequin (40; 140; 240) dans lequel est pratiquée une ouverture centrale ( ; 241), ainsi qu'un moyen d'antirotation (64; 164; ) agissant conjointement avec ladite volute orbitante (30) et avec ledit vilebrequin (40; 140; 240) pour limiter le mouvement de ladite volute orbitante (30) à un mouvement orbital, ledit procédé comprenant les étapes consistant à :
       procurer un moyen de poches (50, 52; 150, 152; 250) entre ladite volute orbitante (30) et ledit vilebrequin (40; 140; 240) et un moyen de rainures (42, 43; 142, 143; 242, 243, 244) entourant le moyen de poches (50, 52; 150, 152; 250);
       former un moyen de voies de fluide (40-3, 40-4; 140-3, 140-4; 240-3) dans le vilebrequin (40; 140; 240) se terminant dans le moyen de poches (50, 52; 150, 152; 250);
       disposer des moyens d'étanchéification (66, 68; 166; 266, 268) dans le moyen de rainures (42, 43; 142, 143; 242, 243, 244);
       fixer le vilebrequin (40; 140; 240) à la volute fixe (20), ladite volute orbitante (30) se trouvant entre eux, et en contact avec les moyens d'étanchéification (66, 68; 166; 266, 268) pour ainsi isoler ledit moyen de poches (50, 52; 150, 152; 250), par lequel, lorsque du fluide sous pression approvisionne ledit moyen de poches (50, 52; 150, 152; 250) via ledit moyen de voie de fluide (40-3, 40-4; 140-3, 140-4; 240-3), une force axiale s'exerce sur ladite volute orbitante (30),
       caractérisé par le fait de façonner ledit moyen de poches (50, 52; 150, 152; 250) dans une surface annulaire généralement plate du vilebrequin (40; 140; 240); et
       façonner ledit moyen de rainures (42, 43; 142, 143; 242, 243, 244) entourant le moyen de poches à l'aide d'une périphérie externe possédant des portions dont les distances varient par rapport à ladite ouverture centrale ( ; 241) de telle sorte que ladite périphérie externe se trouve à une distance non uniforme dudit moyen d'antirotation (64; 164; ) de façon à maximiser ledit moyen de poches (50, 52; 150, 152; 250).
     
    7. Procédé selon la revendication 6, caractérisé en ce que l'étape de façonnage du moyen de poches (50, 52) englobe le façonnage de deux poches réniformes (50, 52) disposées symétriquement dans le vilebrequin (40) par rapport à l'ouverture centrale.
     
    8. Procédé selon la revendication 6, caractérisé en ce que l'étape de façonnage du moyen de rainures englobe l'étape de façonnage de deux anneaux décalés et enchevêtrés (142, 143) définissant une paire de formes de croissant dans lesquelles est disposé le moyen de poches (150, 152).
     
    9. Procédé selon la revendication 6, caractérisé en ce que l'étape de façonnage du moyen de rainures englobe le façonnage de deux anneaux enchevêtrés décalés (242, 243), si bien que ladite périphérie externe est continue, et d'un troisième anneau (244) à l'intérieur d'une aire commune définie par lesdits anneaux enchevêtrés (242, 243) et englobe la disposition desdits moyens d'étanchéification (266, 268) uniquement dans la portion du moyen de rainures (242, 243, 244), qui est définie par la périphérie externe et par le troisième anneau (244).
     




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