EP1433956B1 - Spiralverdichter - Google Patents

Spiralverdichter Download PDF

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Publication number
EP1433956B1
EP1433956B1 EP03029176A EP03029176A EP1433956B1 EP 1433956 B1 EP1433956 B1 EP 1433956B1 EP 03029176 A EP03029176 A EP 03029176A EP 03029176 A EP03029176 A EP 03029176A EP 1433956 B1 EP1433956 B1 EP 1433956B1
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EP
European Patent Office
Prior art keywords
scroll member
chamber
movable scroll
back pressure
pressure 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 - Lifetime
Application number
EP03029176A
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English (en)
French (fr)
Other versions
EP1433956A1 (de
Inventor
Kazuya Kimura
Izuru Shimizu
Susumu Tarao
Yumin Hishinuma
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.)
Toyota Industries Corp
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Toyota Industries Corp
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Filing date
Publication date
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Publication of EP1433956A1 publication Critical patent/EP1433956A1/de
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Publication of EP1433956B1 publication Critical patent/EP1433956B1/de
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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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F04C2210/261—Carbon dioxide (CO2)

Definitions

  • the present invention relates to a scroll compressor as defined in the preamble of claim 1.
  • a scroll compressor is known from US-A-6 086 342 .
  • the scroll compressor is part of a refrigeration cycle in a vehicle air conditioner for compressing refrigerant.
  • a scroll compressor of such type includes a fixed scroll member and a movable scroll member.
  • the fixed scroll member has a spiral wall and a base plate, and is fixedly connected to a housing of the compressor.
  • the movable scroll member has a spiral wall and a base plate, and is engaged with the spiral wall of the fixed scroll member. As the movable scroll member orbits, compression chambers defined between both the spiral walls progressively reduce in volume, thus compressing refrigerant gas.
  • the back surface of the movable scroll member is recessed to form a pocket for applying back pressure, and the pocket for applying back pressure is shut by a fixed wall provided in a housing of the compressor.
  • a back pressure chamber is formed.
  • a volume-reducing compression chamber communicates with the back pressure chamber through an introducing passage. Accordingly, force (force based upon the back pressure) that resists against force (thrust load) based upon pressure in the compression chambers is applied to the movable scroll member due to the pressure in the back pressure chamber, so that sliding resistance is reduced between the movable scroll member and the fixed wall. Additionally, the movable scroll member is pressed against the fixed scroll member, so that sealing performance of the compression chambers improve.
  • the pressure in the back pressure chamber is appropriately adjusted by variation in the amount of a clearance (passing cross-sectional area) between the movable scroll member and the fixed scroll wall.
  • a clearance passing cross-sectional area
  • the clearance between the movable scroll member and the fixed wall increases. Accordingly, the amount of refrigerant gas delivered from the back pressure chamber to a relatively low pressure region through the clearance increases, so that an excessive rise in the pressure in the back pressure chamber is prevented.
  • the clearance between the movable scroll member and the fixed wall reduces. Accordingly, the amount of refrigerant gas delivered from the back pressure chamber to the relatively low pressure region through the clearance reduces, so that undesirable reduction in the pressure in the back pressure chamber is prevented.
  • the pressure in the back pressure chamber is adjusted in a much higher range than that when fluorocarbon refrigerant is employed. Accordingly, in order to appropriately adjust the pressure in the back pressure chamber, the clearance between the movable scroll member and the fixed wall need be much narrower at the maximum. Thus, a rise in cost for manufacturing becomes a further serious problem. Therefore, there is a need for providing a scroll compressor that has a reasonable structure and optionally and appropriately adjusts pressure in a back pressure chamber.
  • the scroll compressor comprises a fixed scroll member and an orbiting scroll member engaged with the fixed scroll member, wherein a compression chamber is formed therein between for reducing in volume by orbiting the scroll members relative to each other.
  • the compressor discloses a back pressure chamber for forcing the movable scroll member relative to the fixed scroll member, and seal members for sealing the back pressure chamber as well as for enabling a slidable movement of the movable scroll member relative to the housing.
  • a scroll compressor according to the present invention is applied to an electric compressor for use in a refrigeration cycle of a vehicle air conditioner.
  • carbon dioxide is employed as refrigerant of the refrigeration cycle.
  • the left side and the right side of FIG. 1 respectively correspond to the front side and the rear side of the electric compressor.
  • a housing 11 of the electric compressor includes a first housing element 21 and a second housing element 22.
  • the first housing element 21 and the second housing element 22 are fixedly connected with each other.
  • the first housing element 21 has a cylindrical portion 23 and a bottom portion 24, which connects with the rear end of the cylindrical portion 23 (on the right side of FIG. 1 ).
  • the first housing element 21 forms a cylinder with a bottom at one end and is formed by die-casting an aluminum alloy.
  • the second housing element 22 forms a cylinder with a bottom on the front side (the left side of FIG. 1 ) and is formed by die-casting an aluminum alloy.
  • a cylindrical shaft support portion 24a extends from the center of an inner wall surface of the bottom portion 24 in the first housing element 21.
  • a shaft support member 32 which has an insertion hole 32a formed through the center thereof, is fixedly connected to an opening end of the cylindrical portion 23 in the first housing element 21.
  • a rotary shaft 33 is accommodated in the first housing element 21. The rear end (the right end) of the rotary shaft 33 is rotatably supported by the shaft support portion 24a of the first housing element 21 through a bearing 34. The front end (the left side) of the rotary shaft 33 is inserted through the insertion hole 32a of the shaft support member 32, and is rotatably supported by the shaft support member 32 through a bearing 35 in the insertion hole 32a.
  • a motor chamber 12 is defined in the housing 11 and is located on the rear side of FIG. 1 relative to the shaft support member 32.
  • a stator 36 is provided on the inner circumferential surface of the cylindrical portion 23 of the first housing element 21.
  • a rotor 37 is secured to the rotary shaft 33 so as to be located inside the stator 36.
  • the stator 36 and the rotor 37 constitute the electric motor 13.
  • the electric motor 13 integrally rotates the rotor 37 and the rotary shaft 33 by electric power externally supplied to the stator 36.
  • a fixed scroll member 41 is accommodated in the first housing element 21 and is located near the opening end of the cylindrical portion 23.
  • the fixed scroll member 41 includes a disc-shaped base plate 61, a cylindrical outer circumferential wall 62 and a spiral wall 63.
  • the outer circumferential wall 62 extends from the outer periphery of the base plate 61.
  • the spiral wall 63 extends from the base plate 61 and is located inside the outer circumferential wall 62.
  • a disc-shaped center frame or a fixed wall 31 is arranged between the fixed scroll member 41 and the shaft support member 32.
  • a through hole 31 a is formed through the center of the center frame 31.
  • An annular contact portion 31 b is located at the opening end near the motor chamber 12 in the through hole 31 a and protrudes inward.
  • the fixed scroll member 41 is connected to the outer periphery of the center frame 31 by the distal end surface of the outer circumferential wall 62.
  • An annular shim 68 is interposed at a joint between the fixed scroll member 41 and the center frame 31.
  • the base plate 61 of the fixed scroll member 41, the outer circumferential wall 62 of the fixed scroll member 41 and the center frame 31 surround to define a scroll chamber 15 in the housing 11.
  • a crankshaft 43 is provided at the end surface of the rotary shaft 33 near the center frame 31.
  • the crankshaft 43 is mostly arranged in the through hole 31 a of the center frame 31.
  • a bushing 44 is fixedly fitted around the crankshaft 43.
  • a movable scroll member 45 is accommodated in the scroll chamber 15 and is rotatably supported on the bushing 44 through a bearing 46 so as to face the fixed scroll member 41.
  • a balancer 44a is provided at the end of the bushing 44 near the shaft support member 32.
  • the balancer 44a relieves imbalance on the rotary shaft 33 due to uneven arrangement of the movable scroll member 45 around an axis L of the rotary shaft 33.
  • the balancer 44a is accommodated in a balancer chamber 14 outside the through hole 31 a.
  • the balancer chamber 14 is defined between the shaft support member 32 and the center frame 31.
  • the balancer chamber 14 communicates with the motor chamber 12 through a clearance of the bearing 35. Accordingly, the balancer chamber 14 has the same atmospheric pressure as that of the motor chamber 12.
  • the movable scroll member 45 includes a disc-shaped base plate 65 and a spiral wall 66 that extends toward the fixed scroll member 41.
  • a boss 67 is provided near the center of a back surface of the base plate 65 and protrudes therefrom.
  • the boss 67 is fitted around the bushing 44 through the bearing 46 in the through hole 31 a of the center frame 31.
  • An annular tip seal 77 is provided at the distal end of the boss 67.
  • the boss 67 slidably contacts with the contact portion 31 b of the center frame 31 by the tip seal 77. Accordingly, in the through hole 31 a, the tip seal 77 blocks communication between an inner space of the boss 67 communicating with the balancer chamber 14 and an outer space of the boss 67.
  • the fixed scroll member 41 and the movable scroll member 45 engage with each other by the respective spiral walls 63, 66 in the scroll chamber 15, while the distal end of the spiral wall 63 and the distal end of the spiral wall 66 contact with the base plate 65 of the movable scroll member 45 and the base plate 61 of the fixed scroll member 41, respectively. Accordingly, the base plate 61 and the spiral wall 63 of the fixed scroll member 41 and the base plate 65 and the spiral wall 66 of the movable scroll member 45 define compression chambers 47 in the scroll chamber 15.
  • a self-rotation blocking mechanism 48 is provided between the base plate 65 of the movable scroll member 45 and the center frame 31 facing the base plate 65.
  • the self-rotation blocking mechanism 48 includes a plurality of cylindrical holes 48a and a plurality of pins 48b (only one of them is shown in FIG. 1 ).
  • the cylindrical holes 48a are recessed in radially outer portions of the back surface 65a of the base plate 65 in the movable scroll member 45.
  • the pins 48b are buried in an end surface 31 c of the center frame 31 and are loosely fitted therein.
  • a suction chamber 51 is defined between the outer circumferential wall 62 of the fixed scroll member 41 and the outermost circumferential portion of the spiral wall 66 of the movable scroll member 45.
  • a suction passage 39 is formed in radially outer portions of the shaft support member 32, the shim 68 and the center frame 31 for interconnecting the suction chamber 51 and the motor chamber 12.
  • a suction port 50 is formed in the cylindrical portion 23 of the first housing element 21 and is located to correspond with the motor chamber 12.
  • the suction port 50 connects with an external conduit, which further connects with an evaporator (not shown) of an external refrigerant circuit.
  • the suction port 50 communicates with the motor chamber 12. Accordingly, relatively low pressure refrigerant gas from the external refrigerant circuit is introduced into the suction chamber 51 through the suction port 50, the motor chamber 12 and the suction passage 39.
  • a discharge chamber 52 is defined between the second housing element 22 and the fixed scroll member 41.
  • a discharge port 53 for communicating with the discharge chamber 52 is formed in the second housing element 22.
  • the discharge port 53 connects with an external conduit, which further connects with a gas cooler (not shown) of the external refrigerant circuit. Accordingly, relatively high pressure refrigerant gas in the discharge chamber 52 is delivered to the external refrigerant circuit through the discharge port 53.
  • a discharge hole 41 a is formed through the center of the base plate 61 of the fixed scroll member 41.
  • the compression chamber 47 near the center communicates with the discharge chamber 52 through the discharge hole 41 a.
  • a discharge valve 55 constituted of a reed valve is arranged on the base plate 61 of the fixed scroll member 41 for opening and closing the discharge hole 41 a.
  • the opening degree of the discharge valve 55 is regulated by a retainer 56, which is fixedly arranged on the base plate 61 of the fixed scroll member 41.
  • the movable scroll member 45 orbits around the axis (the axis L of the rotary shaft 33) of the fixed scroll member 41 through the crankshaft 43.
  • the self-rotation of the movable scroll member 45 is blocked by the self-rotation blocking mechanism 48, so that only the orbital movement of the movable scroll member 45 is permitted.
  • the compression chambers 47 reduce in volume as the compression chambers 47 move from the radially outer side of the spiral walls 63, 66 of the respective scroll members 41, 45 toward the center of the spiral walls 63, 66.
  • relatively low pressure refrigerant gas introduced from the suction chamber 51 to the compression chambers 47 is compressed.
  • the compressed refrigerant gas is discharged to the discharge chamber 52 through the discharge hole 41 a by pushing away the discharge valve 55.
  • a back pressure chamber 16 is located on the side of the back surface 65a of the base plate 65 of the movable scroll member 45.
  • the base plate 65 and the boss 67 of the movable scroll member 45 and the center frame 31 surround to define the back pressure chamber 16. Communication between the back pressure chamber 16 and the balancer chamber 14 is blocked by the tip seal 77, which is interposed between the boss 67 of the movable scroll member 45 and the contact portion 31 b of the center frame 31.
  • annular groove 65b for accommodating a seal is recessed in radially outer portion relative to the cylindrical recesses 48a so as to surround the cylindrical recesses 48a.
  • An annular seal member 75 constituted of a tip seal is fitted in the groove 65b.
  • the back surface 65a of the movable scroll member 45 slidably and elastically contacts with an end surface 31c of the center frame 31 by the seal member 75. Namely, the seal member 75 is interposed at a clearance CL between the back surface 65a of the movable scroll member 45 and the end surface 31c of the center frame 31. Communication between the back pressure chamber 16 and the suction chamber 51 through the entire clearance CL is blocked by the seal member 75.
  • a maximum distance of the clearance CL between the movable scroll member 45 and the center frame 31, that is, a thrust clearance between the movable scroll member 45 and the center frame 31, is adjusted in an appropriate distance in such a manner that a shim 68 having an appropriate thickness is selected from a plurality of shims 68 having different thicknesses and is assembled to the clearance CL when the electric compressor is manufactured.
  • an introducing passage 76 is formed in the base plate 65 of the movable scroll member 45 so as to extend through the base plate 65 in thickness.
  • Two introducing passages 76 are provided.
  • the back pressure chamber 16 and a volume-reducing (compressing) compression chamber 47A which is a relatively high pressure region, are interconnected through one introducing passage 76.
  • the back pressure chamber 16 and a volume-reducing compression chamber 47B which is different from the compression chamber 47A, are interconnected through the other introducing passage 76.
  • the introducing passages 76 are symmetrically located in the base plate 65 from each other with an angle of 180 degrees with respect to the axis of the crankshaft 43, and respectively open to the corresponding compression chambers 47A, 47B.
  • a fixed throttle 76a is arranged in each of the introducing passages 76.
  • the back surface 65a of the base plate 65 forms two accommodating recesses 65c, with which the opening of each introducing passage 76 on the side of the back pressure chamber 16 communicates.
  • a check valve 78 constituted of a reed valve is accommodated in each of the accommodating recesses 65c. The check valves 78 each permit refrigerant gas supplied from the compression chambers 47A, 47B to the back pressure chamber 16, and block the refrigerant gas returned from the back pressure chamber 16 to the compression chambers 47A, 47B.
  • a portion 75a for lowering sealing performance (hereinafter, a seal lowering portion 75a) relative to the other portion is provided for the seal member 75.
  • the seal lowering portion 75a is formed by splitting a portion of the annular seal member.
  • the back pressure chamber 16 and the suction chamber 75 which is a relatively low pressure region, are interconnected through the seal lowering portion 75a of the seal member 75 in the clearance CL between the movable scroll member 45 and the center frame 31.
  • dimensions of the seal lowering portion 75a (a split portion in the seal member 75) are exaggeratedly illustrated for easier understanding.
  • the seal lowering portion 75a is formed by an extremely narrow clearance.
  • a relatively high pressure region means a region where relatively high pressure refrigerant gas, which is compressed by the fixed scroll member 41 and the movable scroll member 45, exists
  • a relatively low pressure region means a region where relatively low pressure refrigerant gas, which is yet to be compressed by the fixed scroll member 41 and the movable scroll member 45, exists.
  • the check valve 78 opens so that the relatively high pressure refrigerant gas in the volume-reducing compression chambers 47A, 47B is introduced into the back pressure chamber 16 through the respective introducing passages 76. Accordingly, the pressure in the back pressure chamber 16 rises so that force (back pressure force) F1 urging the movable scroll member 45 toward the fixed scroll member 41 is applied based upon the pressure in the back pressure chamber 16.
  • force (thrust load) F2 based upon the pressure in the compression chambers 47 is applied to the movable scroll member 45 toward a direction to leave the fixed scroll member 41. Accordingly, a position of the movable scroll member 45 relative to the center frame 31 is determined in accordance with a balance between the force F1 and the force F2.
  • the passing cross-sectional area of refrigerant gas increases at the seal lowering portion 75a of the seal member 75. Accordingly, the amount of refrigerant gas delivered from the back pressure chamber 16 to the suction chamber 51 increases so that the pressure in the back pressure chamber 16 falls to reduce the force F1.
  • the passing cross-sectional area of refrigerant gas reduces at the seal lowering portion 75a of the seal member 75. Accordingly, the amount of refrigerant gas delivered from the back pressure chamber 16 to the suction chamber 51 reduces so that the pressure in the back pressure chamber 16 rises to increase the force F1.
  • the movable scroll member 45 varies the clearance CL (distance) between the back surface 65a and the end surface 31 c of the center frame 31 in such a manner that the force F1 based upon the pressure in the back pressure chamber 16 becomes an appropriate magnitude in a correspondence with the force F2 based upon the pressure in the compression chambers 47.
  • the passing cross-sectional area of the seal lowering portion 75a is thereby autonomously adjusted.
  • the adjustment of the pressure in the back pressure chamber 16 is predetermined in such a manner that a state, where the force F1 applied to the movable scroll member 45 slightly exceeds the force F2, is maintained for a relatively long time.
  • the balancer chamber 14 is defined as a relatively low pressure region, while the tip seal 77 for separating the balancer chamber 14 from the back pressure chamber 16 is defined as a seal member. As shown in FIG. 4 , the tip seal 77 is partially split to form a seal lowering portion 77a for lowering sealing performance, and the back pressure chamber 16 and the balancer chamber 14 are interconnected through the seal lowering portion 77a.
  • the movable scroll member 45 is displaced in a direction in which the distal end of the boss 67 approaches the contact portion 31 b of the center frame 31. Accordingly, a clearance between the distal end surface of the boss 67 and the contact portion 31 b of the center frame 31 reduces, so that the passing cross-sectional area for refrigerant gas reduces at the seal lowering portion 77a of the tip seal 77.
  • the amount of refrigerant gas delivered from the back pressure chamber 16 to the balancer chamber 14 reduces, and the pressure in the back pressure chamber 16 rises to increase the force F1.
  • the same advantageous effects such as appropriate adjustment of pressure in the back pressure chamber 16 with a relatively low-cost structure, are obtained.
  • the back pressure chamber 16 and the balancer chamber 14 are interconnected not through the seal lowering portion 75a but through another passage 81.
  • a differential pressure regulating valve 82 is arranged in the passage 81 for opening when differential pressure between the back pressure chamber 16 and the balancer chamber 14 is equal to or greater than a predetermined value.
  • the differential pressure regulating valve 82 includes a spherical valve body 82a, a coil spring 82b and a spring seat 82c.
  • the pressure in the back pressure chamber 16 and the pressure in the balancer chamber 14 are respectively applied to the front side and the rear side of the valve body 82a.
  • the coil spring 82b urges the valve body 82a in a direction to close the valve.
  • the passing cross-sectional area of the seal lowering portion 75a is adjusted in response to a balance between the force F1 based upon the pressure in the back pressure chamber 16 and the force F2 based upon the pressure in the compression chambers 47.
  • the pressure in the back pressure chamber 16 is adjusted by utilizing two valves (the seal lowering portion 75a and the differential pressure regulating valve 82) each having different characteristic. Accordingly, a region where only one of the valves 75a and 82 cannot appropriately adjust pressure may be mutually covered by combination with the other of the valves 82 and 75a. Thus, the pressure in the back pressure chamber 16 is further appropriately adjusted.
  • one portion of the annular seal member 75 is split to form the seal lowering portion 75a.
  • a plurality of portions of a seal member such as two, three, four, five or six portions, is split to form portion for lowering sealing performance at plural portions of the seal member.
  • the seal lowering portion 75a is formed by partially splitting the annular seal member 75.
  • the annular shape of the seal member is maintained, while a groove is partially formed in the seal member.
  • a seal lowering portion for lowering sealing performance is formed.
  • two volume-reducing compression chambers 47A, 47B independently communicate with the back pressure chamber 16 through the respective introducing passages 76.
  • two introducing passages 76 which respectively extend from two compression chambers 47A, 47B, are integrated on the way and the integrated one introducing passage communicates with the back pressure chamber 16.
  • relatively high pressure refrigerant gas is introduced from the volume-reducing compression chambers 47A, 47B to the back pressure chamber 16.
  • the compression chamber 47 near the center (the compression chamber 47 completes compression) or the discharge chamber 52 is defined as a relatively high pressure region, while the upstream portion of the introducing passage 76 communicates with the relatively high pressure region, so that the high pressure refrigerant gas, which is higher in pressure than the refrigerant gas in the volume-reducing compression chambers 47A, 47B, is introduced to the back pressure chamber 16.
  • a scroll compressor is embodied as the electric compressor.
  • the scroll compressor is not limited to the electric compressor.
  • a scroll compressor driven by an engine of a vehicle, a hybrid type scroll compressor having an electric motor and an engine as drive sources, may be employed.

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

Claims (9)

  1. Spiralverdichter, mit:
    einem Gehäuse (11), das eine stationäre Wand (31) umfasst und einen Hochdruckbereich (47, 47A, 47B, 52) und einen Niederdruckbereich (14, 51) begrenzt,
    einem stationären Spiralelement (41) mit einer Grundplatte (61) und einer sich von der Grundplatte (61) erstreckenden Spiralwand (62), wobei das stationäre Spiralelement (41) mit dem Gehäuse (11) fest verbunden ist,
    einem beweglichen Spiralelement (45) mit einer Grundplatte (65) und einer sich von der Grundplatte (65) erstreckenden Spiralwand (66), wobei das bewegliche Spiralelement (45) mit dem stationären Spiralelement (41) im Eingriff ist,
    einer Rückdruckkammer (16), die in dem Gehäuse (11) an einer rückseitigen Seite (65a) der Grundplatte (65) des beweglichen Spiralelements (45) zwischen dem beweglichen Spiralelement (45) und der stationären Wand (31) begrenzt ist,
    einem Einlassdurchgang (76), der die Rückdruckkammer (16) mit dem Hochdruckbereich (47, 47A, 47B, 52) verbindet,
    einer Verdichtungskammer (47), die zwischen dem stationären Spiralelement (41) und dem beweglichen Spiralelement (45) begrenzt ist, wobei das Volumen der Verdichtungskammer (47) durch Kreisen des beweglichen Spiralelements (45) relativ zu dem stationären Spiralelement (41) zunehmend abnimmt und dadurch Gas verdichtet,
    einem ringförmigen Dichtelement (75, 77) zum Abdichten der Rückdruckkammer (16), das an einem von dem beweglichen Spiralelement (45) oder der stationären Wand (31) vorgesehen ist und auf dem anderen von dem beweglichen Spiralelement (45) oder der stationären Wand (31) gleiten kann,
    dadurch gekennzeichnet, dass
    ein dichtungsmindernder Abschnitt (75a; 77a) zum Mindern einer Dichtwirkung in dem Dichtelement (75, 77) ausgebildet ist, um die Rückdruckkammer (16) mit dem Niederdruckbereich (14, 51) zu verbinden, wobei der dichtungsmindernde Abschnitt (75a, 77a) durch teilweises Aufspalten des Dichtungselements (75, 77) oder durch eine Nut in dem Dichtungselement (75, 77) gebildet ist.
  2. Spiralverdichter nach Anspruch 1, wobei das bewegliche Spiralelement (45) in einer Spiralkammer (15) untergebracht ist, die durch Verbinden des stationären Spiralelements (41) mit der stationären Wand (31) an einer Verbindungsstelle begrenzt ist,
    dadurch gekennzeichnet, dass eine Zwischenlage (68) an der Verbindungsstelle zwischen dem stationären Spiralelement (41) und der stationären Wand (31) zwischengelegt ist, um ein Schubspiel (CL) zwischen dem beweglichen Spiralelement (45) und der stationären Wand (31) anzupassen.
  3. Spiralverdichter nach einem der Ansprüche 1 oder 2, mit einer Drehwelle (33), einem Wellenhalteelement (32) und einem Auswuchtelement (44a),
    dadurch gekennzeichnet, dass
    die Drehwelle (33) eine Kurbelwelle (43) zum Halten des beweglichen Spiralelements (45) umfasst,
    das Wellenhalteelement (32) fest mit der stationären Wand (31) auf einer dem beweglichen Spiralelement (45) abgewandten Seite in dem Gehäuse (11) verbunden ist und drehbar die Drehwelle (33) hält, wobei eine Auswuchtelementkammer (14) zwischen der stationären Wand (31) und dem Wellenhalteelement (32) begrenzt ist, und
    das Auswuchtelement (44a) für die Kurbelwelle (43) vorgesehen und in der Auswuchtelementkammer (14) untergebracht ist.
  4. Spiralverdichter nach einem der Ansprüche 1 bis 3, wobei die Rückdruckkammer (16) zusätzlich zu dem dichtungsmindernden Abschnitt (77a) über einen Durchgang (81) mit dem Niederdruckbereich (14) verbunden ist,
    dadurch gekennzeichnet, dass
    ein Druckunterschiedregelventil (82) in dem Durchgang (81) angeordnet ist, um den Durchgang (81) zu öffnen, wenn ein Druckunterschied zwischen der Rückdruckkammer (16) und dem Niederdruckabschnitt (14) gleich oder höher als ein vorbestimmter Wert ist.
  5. Spiralverdichter nach einem der Ansprüche 1 bis 4, wobei der Hochdruckbereich (47, 47A, 47B, 52) zwei volumenmindernde Verdichtungskammern (47A, 47B) umfasst, die jeweils mit der Rückdruckkammer (16) über den Einlassdurchgang (76) verbunden sind.
  6. Spiralverdichter nach Anspruch 5, wobei zwei volumenmindernde Verdichtungskammern (47A, 47B) jeweils mit der Rückdruckkammer (16) über die jeweiligen unabhängigen Einlassdurchgänge (76) verbunden sind.
  7. Spiralverdichter nach einem der Ansprüche 1 bis 6, wobei der Einlassdurchgang (76) in der Grundplatte (65) des beweglichen Spiralelements (45) ausgebildet ist.
  8. Spiralverdichter nach einem der Ansprüche 1 bis 7, wobei Kohlenstoffdioxid als Kühlmittel des Kühlkreislaufs verwendet wird.
  9. Spiralverdichter nach einem der Ansprüche 1 bis 8, wobei der Verdichter von einem Elektromotor (13) angetrieben wird.
EP03029176A 2002-12-20 2003-12-18 Spiralverdichter Expired - Lifetime EP1433956B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002370997A JP4007189B2 (ja) 2002-12-20 2002-12-20 スクロールコンプレッサ
JP2002370997 2002-12-20

Publications (2)

Publication Number Publication Date
EP1433956A1 EP1433956A1 (de) 2004-06-30
EP1433956B1 true EP1433956B1 (de) 2012-02-29

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EP03029176A Expired - Lifetime EP1433956B1 (de) 2002-12-20 2003-12-18 Spiralverdichter

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EP1433956A1 (de) 2004-06-30
JP2004204680A (ja) 2004-07-22
JP4007189B2 (ja) 2007-11-14
US20040136854A1 (en) 2004-07-15

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