EP3810935B1 - Compresseur à spirale muni d'un contrepoids de trajectoire orbitale découplable - Google Patents

Compresseur à spirale muni d'un contrepoids de trajectoire orbitale découplable Download PDF

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Publication number
EP3810935B1
EP3810935B1 EP18737172.9A EP18737172A EP3810935B1 EP 3810935 B1 EP3810935 B1 EP 3810935B1 EP 18737172 A EP18737172 A EP 18737172A EP 3810935 B1 EP3810935 B1 EP 3810935B1
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EP
European Patent Office
Prior art keywords
coupling
compressor
force
centrifugal
drive shaft
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EP18737172.9A
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German (de)
English (en)
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EP3810935A1 (fr
Inventor
Dimitri Gossen
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
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Bitzer Kuehlmaschinenbau GmbH and Co KG
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Publication of EP3810935A1 publication Critical patent/EP3810935A1/fr
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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
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/807—Balance weight, counterweight
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps

Definitions

  • the invention relates to a compressor, comprising a compressor housing, a spiral compressor unit arranged in the compressor housing with a first, stationary compressor body and a second compressor body which can be moved in orbit relative to the stationary compressor body, the first and second spiral ribs of which are designed in the form of a circular involute to form compressor chambers interlock when the second compressor body is moved relative to the first compressor body on an orbital path, an axial guide which supports the movable compressor body against movements in a direction parallel to a central axis of the stationary compressor body and guides movements in a direction transverse to the central axis, an eccentric drive for the Scroll compressor unit, which has a driver driven by a drive motor and rotating on the orbital path around the central axis of a drive shaft and rotatably mounted relative to the drive shaft about an eccentric drive axis, which in turn interacts with a driver receptacle of the second compressor body, one of an imbalance caused by the moving on the orbital path Compressor body counteracting and also rotatably mounted around
  • Such compressors are from the prior art, for example WO 2018/019372 known.
  • a compressor of the type described at the outset in that the driver and the orbital orbital balancing mass can be coupled to one another with a coupling unit in such a way that the coupling unit is effective when the drive shaft is rotating in a centrifugal force-coupling state in such a way that the orbital orbital balancing mass is subject to a centrifugal force of at least one Driver and the unit comprising the orbiting compressor body counteracts that the coupling unit is effective when the drive shaft is rotating in a centrifugal force decoupling state in such a way that the orbital path balancing mass does not counteract the centrifugal force of the unit comprising at least the driver and the orbiting compressor body and that the coupling unit is separated from the centrifugal force decoupling by means of a positioning device State can be converted into the centrifugal force decoupling state or vice versa.
  • the coupling unit comprises two coupling elements, one of which is connected to the orbital orbit balancing mass and one to the driver.
  • the coupling elements can be brought into the centrifugal force-coupling and centrifugal-force-decoupling states by a movement relative to one another.
  • the coupling elements can be connected to the orbital orbit balancing mass and the driver in a variety of ways.
  • a particularly advantageous solution provides that a coupling element is firmly connected to the orbital orbit balancing mass or the driver and the other coupling element is firmly connected to the driver or the orbital orbit balancing mass.
  • the coupling elements can be designed in any way.
  • a structurally particularly favorable solution provides that one of the coupling elements is a coupling body and another of the coupling elements is a receptacle into which the coupling body engages.
  • the coupling body engages in the receptacle with play in order to be able to realize the centrifugal force coupling state and the centrifugal force decoupling state.
  • a particularly favorable solution provides that the coupling body in the centrifugal force-coupling state rests against a portion of the receptacle and thus interacts with the receptacle and is arranged in contactless relation to the receptacle in the centrifugal force-decoupling state, so that the coupling body and the receptacle do not interact.
  • the coupling body could be constructed in a variety of ways.
  • the coupling body is designed as a coupling pin.
  • a particularly simple implementation of the coupling unit provides that the coupling pin is connected to the orbital orbit balancing mass and engages in the receptacle connected to the driver.
  • the positioning device operates in a speed-controlled manner and, in particular, brings the coupling unit into the centrifugal force-decoupling state below a switching speed of the drive shaft and, above the switching speed, brings the coupling unit into the centrifugal-force-coupling state, so that the positioning device reacts only to the speed of the drive shaft either the centrifugal force-decoupling state or brings about the centrifugal force coupling state.
  • the positioning device can theoretically be arranged on the orbital orbit balancing mass or the driver.
  • a particularly favorable solution provides that the positioning device is arranged on the drive shaft.
  • a positioning device allows the coupling elements to interact in the centrifugal-force-coupling state and, in the centrifugal-force-decoupling state, positions the coupling elements in a contact-free manner relative to one another and thus prevents the coupling elements from interacting.
  • the positioning device can be constructed in a particularly simple manner if it has a positioning body, which is guided on the drive shaft by means of a guide body with at least one component in the radial direction to the central axis and can be moved along the guide body depending on the speed.
  • the speed-dependent movement of the positioning body can be implemented in a variety of ways.
  • a structurally particularly simple solution provides that the positioning body is acted upon by means of a spring-elastic force accumulator against a centrifugal force acting on the positioning body.
  • the positioning body assumes a position close to the drive shaft up to the switching speed due to the force effect of the spring-elastic energy storage and from the switching speed onwards the centrifugal force of the positioning body overcomes the force of the spring-elastic energy storage and thus the spring-elastic energy storage moves to an increasing distance moved by the drive shaft.
  • the positioning body is provided with a positioning surface which acts on the coupling unit depending on a radial position of the positioning body.
  • the positioning body brings the coupling unit into its centrifugal force-decoupling state in a first position which corresponds to a speed below the switching speed, and brings the coupling unit into its centrifugal force-coupling state in a position which corresponds to a speed above the switching speed.
  • the positioning device can be used to bring the coupling element connected to the orbital orbit balancing mass relative to the coupling element connected to the driver into the centrifugal force-coupling or centrifugal-force-decoupling state.
  • the positioning device brings the orbital orbit balancing mass together with the coupling element into the centrifugal force decoupling state or the centrifugal force coupling state.
  • An advantageous solution provides that the orbital orbit balancing mass is in the centrifugal force decoupling state of the coupling unit with its center of mass at a distance from the mass compensation plane and in the centrifugal force coupling state of the coupling unit with its center of mass close to or even better in the mass balancing plane.
  • this solution has the great advantage that at higher speeds in the centrifugal force-coupling state of the coupling unit, the center of mass of the orbital orbit balancing mass is close to or preferably in the mass balancing plane and thus an optimal mass balancing is available.
  • a first movement limiting unit is effective between the drive shaft and the orbital orbit balancing mass.
  • a position range of the orbital path compensation mass relative to the drive shaft and relative to the compressor body can be specified in a simple manner.
  • a particularly favorable solution provides that the central axis of the drive shaft and a central axis of the movable second compressor body define a mass compensation plane running through it and that the first movement limiting unit places the orbital path compensation mass on a side opposite the eccentric drive axis of a geometrical plane running perpendicular to the mass compensation plane and through the central axis of the drive shaft Transverse plane holds.
  • the first movement limiting unit aligns the orbital orbit balancing mass in such a way that a center of mass thereof remains within an unbalance tolerance range extending across the mass balancing plane and on both sides thereof, so that excessive unbalances caused by the orbital orbit balancing mass can be prevented by the first movement limiting unit.
  • the first movement limiting unit allows the guide body to rotate freely about the eccentric drive axis in an angular range of 0.5° (angular degrees) to 5° (angular degrees).
  • the first movement limiting unit is supported by a first stop element held on the orbital orbit compensation element, in particular on its guide body, or on the drive shaft, and a first stop element which interacts with the first stop element, in particular receiving it, on the drive shaft or the orbital orbit compensation mass, in particular its guide body , arranged second stop element is formed.
  • the guide body is firmly connected to the orbital orbit balancing mass.
  • a particularly simple and robust design implementation provides that the orbital track balancing mass is rotatably mounted about the eccentric axis by an eccentric drive pin that interacts with the driver and the drive shaft.
  • the eccentric drive pin passes through a pin receptacle of the guide body.
  • a further advantageous solution provides that the orbital orbit balancing mass interacts with the drive shaft by means of the guide body and is guided on the drive shaft and can therefore be guided in a defined orientation relative to the drive shaft.
  • the action of the eccentric drive pin on the guide body essentially serves to move the guide body with the orbital path compensation mass in such a way that the orbital path compensation mass follows the orbital path of the driver and produces the required mass compensation.
  • the orbital path balancing mass is guided by the guide body acting on the drive shaft on a path which runs in a path plane which runs parallel to an alignment plane which runs perpendicular to the central axis of the drive shaft.
  • the guidance of the guide body on the drive shaft can be implemented in a variety of ways.
  • a favorable solution provides that the guide body is guided with a guide surface on an alignment surface of the drive shaft.
  • the alignment surface provided on the drive shaft it would be conceivable, for example, to arrange the alignment surface on a collar of the drive shaft.
  • a particularly simple solution that is also stable with regard to the guidance of the guide body provides that the alignment surface provided on the drive shaft is an end face of the drive shaft.
  • the guide body can be optimally supported on the alignment surface if the guide body is arranged across the alignment surface.
  • the guide body is arranged between the alignment surface of the drive shaft and the driver.
  • the guide body is plate-shaped, that is to say it has the smallest possible extent in the direction of the central axes in relation to its extent transversely to the central axis.
  • the guide body is guided by the drive shaft and in particular to ensure this in as many operating states as possible, it is preferably provided that the guide body is guided relative to the drive shaft by an axial guide.
  • the axial guide is designed such that it holds the guide surface of the guide body in contact with the alignment surface of the drive shaft in order to ensure sufficiently precise guidance of the guide body and thus the orbital orbit balancing mass relative to the drive shaft.
  • the axial guide can be designed in a wide variety of ways.
  • the axial guide is preferably designed in such a way that it comprises an element which acts on the guide body on a side opposite the guide surface.
  • the eccentric drive has the eccentric drive pin driving the driver and a coupling body that couples the orbital track balancing mass to the driver.
  • the coupling body also represents a mass balancing body.
  • the eccentric drive has an eccentric drive pin that drives the driver and a coupling body that couples the orbital track compensation mass to the driver.
  • the coupling body also represents a mass balancing body.
  • an advantageous development of the solution according to the invention provides that the coupling pin is arranged in a fixed manner on the guide body and engages in the recess in the driver.
  • FIG. 1 Illustrated first exemplary embodiment of a compressor according to the invention, designated as a whole by 10, for a gaseous medium, in particular a refrigerant, comprises a compressor housing, designated as a whole by 12, which has a first end housing section 14, a second end housing section 16 and one between the end housing sections 14 and 16 arranged intermediate section 18.
  • a scroll compressor unit designated as a whole by 22, is provided in the first housing section 14, which has a first compressor body 24 which is stationarily arranged in the compressor housing 12, in particular in the first housing section 14, and a second compressor body 26 which is movable relative to the stationary compressor body 24.
  • the first compressor body 24 includes a compressor body base 32 over which a first spiral rib 34 rises and the second compressor body 26 also includes a compressor body base 36 over which a second spiral rib 38 rises.
  • the compressor bodies 24 and 26 are arranged relative to one another so that the spiral ribs 34, 38 mesh with one another, as shown in Fig. 3 shown to form at least one, preferably several, compressor chambers 42 between them, in which the gaseous medium, for example refrigerant, is compressed in that the second compressor body 26 moves with its central axis 46 about a central axis 44 of the first compressor body 24 on an orbital path 48 moves with a compressor orbital orbit radius VOR, whereby the volume of the compressor chambers 42 is reduced and ultimately compressed gaseous medium flows through a central outlet 52 ( Fig. 2 ) exits, while gaseous medium to be sucked in is sucked in through compressor chambers 42 that open on the circumference, radially on the outside with respect to the central axis 44.
  • the gaseous medium for example refrigerant
  • the sealing of the compressor chambers 42 relative to one another takes place in particular in that the spiral ribs 34, 38 are provided on the front side with axial sealing elements 54 and 58, which rest sealingly on the respective bottom surface 62, 64 of the other compressor body 26, 24, the bottom surfaces 62 , 64 are formed by the respective compressor body base 36 or 32 and each lie in a plane running perpendicular to the central axis 44.
  • the scroll compressor unit 22 is accommodated as a whole in a first housing body 72 of the compressor housing 12, which has a front cover section 74 and a cylindrical ring section 76 which is integrally formed on the front cover section 74 and which in turn engages with a ring shoulder in a sleeve body 82 of the housing body 72, which is attached a central housing body 84 forming the intermediate section 18 is formed, the central housing body 84 being closed on a side opposite the first housing body 72 by a second housing body 86, which forms an inlet chamber 88 for the gaseous medium.
  • the sleeve body 82 encloses the scroll compressor unit 22, the first compressor body 24 of which is supported on a contact surface 94 in the housing body 72 with support fingers 92 molded onto the compressor body base 32.
  • the first compressor body 24 is immovably fixed in the housing body 72 against all movements parallel to the support surface 94.
  • the first compressor body 24 is thus stationarily fixed in a precisely defined position within the first housing body 72 and thus also within the compressor housing 12.
  • the axial guide 96 is formed by a carrier element 112, which is one of the axial support surfaces 102 ( Fig. 2 , 5 ) facing support surface 114, on which, however, the compressor body base 36 with the axial support surface 102 does not rest, but on which a sliding body 116, denoted as a whole by 116 and in particular plate-shaped, rests with a sliding support surface 118, the sliding body 116 having a sliding support surface opposite the sliding support surface 118 122 ( Fig. 2 and 5 ) the axial support surface 102 ( Fig. 2 and 4 ) is supported against movements parallel to the central axis 44 but is supported in a sliding manner with respect to movements transverse to the central axis 44.
  • the axial guide 96 provides that when the second compressor body 26 moves on the orbital path 48 about the central axis 44 of the first compressor body 24, on the one hand, the second compressor body 26 with the compressor body base 36 and its axial support surface 102 moves relative to the sliding body 116 , on the other hand, the sliding body 116 in turn moves relative to the carrier element 118.
  • the sliding body 116 is through an in Fig. 5 and 6 shown and designated as a whole by 132 guided with play relative to the carrier element 112, the guide with play 132 comprising a guide recess 134 provided in the sliding body 116, which has a diameter DF, and a guide pin 136 anchored in the carrier element 112, the diameter of which DS is smaller than the diameter DF, so that half of the difference DF-DS defines a guiding orbital radius with which the sliding body 116 can carry out an orbiting movement relative to the carrier element 112.
  • the movements of the sliding body 116 result in the build-up of a sufficient lubricating film between the axial support surface 102 of the compressor body base 36 and the sliding support surface 122 of the sliding body 116 as well as the support surface 114 and the sliding support surface 118.
  • the guide orbital radius FOR is 0.01 times the compressor orbital radius or more, in particular 0.05 times the compressor orbital radius or more.
  • the carrier element 112 is made of an aluminum alloy at least in the area of the carrier surface 114, improved lubrication is additionally ensured by the fact that lubricant enters the pores of the carrier element 112 and thus via the surface structures of the carrier element 112 provided, for example Area of the carrier surface 114 is available for building up the lubricating film in the gap.
  • the sliding body 116 itself is designed as a plate-shaped, annular part made of spring steel and thus the sliding support surface 118 facing the carrier surface 114 represents a smooth spring steel surface, the formation of the lubricating film is additionally promoted.
  • the material pairing of the aluminum alloy, which is softer than spring steel in the area of the support surface 114, and the spring steel in the area of the sliding support surface 118 has advantageous long-term running properties due to its wear resistance.
  • the carrier element 112 is not only provided with the carrier surface 114 on which the sliding body 116 rests, but also with the support surfaces 94 on which the support fingers 92 of the first compressor body 24 are supported.
  • the carrier element 112 is also arranged firmly in the housing body 72 both axially in the direction of the central axis 44 and against rotational movements about the central axis 44.
  • the compressor body base 36 is in a radially inner edge region 152 and in a radially outer edge region 154 with an inclined relative to the axial support surface 102 and set back from the axial support surface 102
  • Edge surface 156 or 158 is provided, which together with the sliding support surface 122 leads to a wedge-shaped gap that opens radially outwards or radially inwards, which facilitates the access of lubricant.
  • the build-up of the lubricating film between the sliding support surface 122 and the axial support surface 102 is promoted by the fact that the sliding support surface 122 and the axial support surface 102, in the overlap area in which they interact, are contiguous, that is in the circumferential direction U around the central axis and in their entire radial extent uninterrupted annular surfaces 124 and 126 are formed, in particular the annular surface 126 of the axial support surface 102 extending from an inner contour IK with a radius IR thereof to an outer contour AK, the radius IR being less than two-thirds of an outer radius AR.
  • annular surface 124 of the sliding support surface 122 is dimensioned such that the annular surface 126 of the axial support surface 102 always rests over its entire surface during all relative movements to the sliding support surface 122.
  • Each of these coupling element sets 162 includes, as shown in FIGS Fig. 2 , 6 and 7 shown, as the first coupling element 172 a pin body 174, which has a cylindrical lateral surface 176 and engages with this cylindrical lateral surface 176 in a second coupling element 182.
  • the second coupling element 182 is formed by an annular body 184 which has a cylindrical inner surface 186 and a cylindrical outer surface 188 which are arranged coaxially with one another.
  • This second coupling element 182 is guided in a third coupling element 192, which is designed as a receptacle 194 for the ring body 184 provided in the carrier element 112 and which has a cylindrical inner wall surface 196.
  • a diameter DI of the inner wall surface 196 is larger than a diameter DRA of the cylindrical outer surface 188 of the ring body 184 and a diameter DRI of the cylindrical inner surface 186 is inevitably smaller than the diameter DRA of the cylindrical outer surfaces 188 of the ring body 184, whereby the diameter DRI of the cylindrical Inner surface 186 is larger than a diameter DSK of the cylindrical lateral surface 176 of the pin body 174.
  • each set of coupling elements 162 in turn forms an orbital guide whose maximum orbital radius OR for the orbiting movement corresponds to DI/2-(DRA-DRI)/2-DSK/2.
  • the movable compressor body 26 is guided relative to the stationary compressor body 24 by the coupling 164 in such a way that that, in each case one of the coupling element sets 162 is effective to prevent the self-rotation of the second movable compressor body 26, for example with six coupling element sets 162 after passing through an angular range of 60 °, the effectiveness of each coupling element set 162 from one coupling element set 162 to the next coupling element set 162 in the direction of rotation changes.
  • each coupling element set 162 has three coupling elements 172, 182 and 192 and in particular an annular body 184 is effective between the respective pin body 174 and the respective receptacle 194, on the one hand the wear resistance of the coupling element sets 162 is improved, and on the other hand the lubrication in the area thereof is improved and also reduces the noise generated by the coupling element sets 162, which arises from the change in effectiveness from one coupling element set 162 to the other coupling element set 162.
  • the coupling element sets 162 experience sufficient lubrication, in particular lubrication between the cylindrical lateral surface 176 of the pin body 174 and the cylindrical inner surface 186 of the ring body 184 and lubrication between the cylindrical outer surface 188 of the ring body 184 and the cylindrical inner wall surface 196 of recording 194.
  • the receptacles 194 in the carrier element 112 are open on both sides in the axial direction, the ring bodies 184 being held on their sides facing away from the second compressor body 26 by a stop element 198 which projects radially inwards.
  • openings 202, 204 are provided in the carrier element 112, which allow the passage of lubricant and sucked-in refrigerant.
  • the compressor body base 36 is provided with star-shaped extensions 212 which extend radially outwards and which engage in spaces 214 between support fingers 92 which follow one another in a direction of rotation U around the central axis 44, so that the coupling elements 172 also engage in these Intermediate spaces 214 lie and are therefore arranged within the housing body 72 at the largest possible radial distance from the central axis 44 ( Fig. 7 ).
  • This positioning of the coupling element sets 162, which is predetermined by the largest possible radial distance between the coupling elements 172, at the largest possible radial distance from the central axis 44, has the advantage that the forces acting on the coupling element sets 162 can be kept as small as possible due to the large lever arm , which has an advantageous effect on component dimensioning.
  • the inventive concept of lubrication of the axial guide 96 and the coupling element sets 162 is particularly advantageous when the central axes 44 and 46 of the compressor bodies 24 and 26 are normally horizontal, that is to say at a maximum angle of 30 ° to a horizontal, wherein in the compressor housing 12, in particular in the area of the first housing body 72, a lubricant bath 210 is formed at a point lowest in the direction of gravity, from which lubricant is whirled up during operation and thereby absorbed and distributed in the manner described.
  • the movable compressor body 24 is driven (as in Fig. 2 shown) by a drive motor designated as a whole by 222, for example an electric motor, which in particular has a stator 224 held in the central housing body 84 and a rotor 226 arranged within the stator 224, which is arranged on a drive shaft 228 which is coaxial with the central axis 44 the stationary compressor body 24 runs.
  • a drive motor designated as a whole by 222, for example an electric motor, which in particular has a stator 224 held in the central housing body 84 and a rotor 226 arranged within the stator 224, which is arranged on a drive shaft 228 which is coaxial with the central axis 44 the stationary compressor body 24 runs.
  • the drive shaft 228 is mounted, on the one hand, in a bearing unit 232 facing the compressor, which is arranged between the drive motor 222 and the scroll compressor unit 22 and in the central housing body 84, and, on the other hand, in a bearing unit 234 facing away from the compressor, which is arranged on a side of the drive motor 222 opposite the bearing unit 232.
  • the bearing unit 234 facing away from the compressor is mounted, for example, in the second housing body 86, which closes the central housing body 84 on a side opposite the first housing body 72.
  • Medium in particular the refrigerant, flows from the inlet chamber 88 formed by the second housing body 86 through the drive motor 222 in the direction of the bearing unit 232 facing the compressor, flows around it and then flows in the direction of the scroll compressor unit 22.
  • the drive shaft 228 drives the movable compressor body 26 via an eccentric drive designated as a whole by 242, which moves in an orbiting manner around the central axis 44 of the stationary compressor body 24.
  • the eccentric drive 242 in particular includes an eccentric drive pin 244 held in the drive shaft 228, preferably firmly inserted therein, which moves a driver 246 on the orbital path 48 about the central axis 44, which in turn moves through a rotatable receptacle of the eccentric drive pin 244 in a drive pin receptacle 247 in the driver 246 is rotatably mounted on the eccentric drive pin 244 about an eccentric axis 245 and is also rotatably mounted about the central axis 46 of the orbiting compressor body 26 in a rotary bearing 248, in particular a rolling element bearing designed as a fixed bearing, the rotary bearing 248 allowing the driver 246 to rotate relative to the orbitally movable compressor body 26 about the central axis 46 is allowed, as in Fig. 7 and 8th shown.
  • the second compressor body 26 is provided with an integrated driver receptacle 249, which accommodates the pivot bearing 248.
  • the driver receptacle 249 is set back relative to the flat side 98 of the compressor body base 36 and is thus arranged integrated in the compressor body base 36, so that the driving forces acting on the movable compressor body 26 are effective on a side of the flat side 98 of the compressor body base 36 facing the spiral rib 38 and thus drive the movable compressor body 26 with a low tilting moment, which is axially supported by the axial guide 96 in the direction of the central axis 44 between the driver receptacle 249 and the drive motor 222 on the axial support surface 102 and is guided movably transversely to the central axis 44.
  • the driver receptacle is 249, as in the Fig. 2 and 11 shown surrounded by the axial support surface 102, which is external in the radial direction to the central axis 46, and the axial support surface 102 is in turn surrounded by the coupling element sets 162, which are external in the radial direction to the central axis 44, of the coupling 164, which prevents the self-rotation of the second compressor body 26.
  • the compressor orbital radius VOR defined by the distance of the central axis 46 of the movable compressor body 24 from the central axis 44 of the stationary compressor body 24 and the drive shaft 228, variably adjustable, so that the movable compressor body 26, and thus also the central axis 46, respectively can move radially outwards so far from the central axis 44 that the spiral ribs 34, 38 rest against each other under force at the point of contact 322 and seal the compressor chambers 42.
  • the distance of the eccentric axis 245 from the central axis 44 of the stationary compressor body 24 is chosen to be larger than the intended compressor orbital radius VOR, that is, the distance between the central axes 44 and 46 from one another, and so large that the eccentric axis 245 is outside one through the two central axes 44 and 46 running through the central axis plane ME and opposite to a direction of rotation D of the drive shaft 228 at a distance from this ( Fig. 9 ).
  • the resulting eccentric action of the eccentric drive pin 244 on the driver 246 causes a force FA which, based on the central axis 46 of the driver 246, acts on the central axis 46 and the driver 246 Together with the movable compressor body 26, the force FC moves radially outwards to the central axis 44, which is in the central axis plane ME running through the central axis 44 and the central axis 46 acts and places the spiral ribs 34, 38 against one another, and which leads to a force FO acting tangentially to the orbital path 48, which moves the driver 246 together with the movable compressor body 26 on the orbital path 48 around the central axis 44 moves in a direction of rotation D ( Fig. 9 ).
  • the central axis plane ME defined by the central axes 44 and 46 represents a reference plane for a system, formed from the mass of the drive elements comprising the eccentric drive 242 on the one hand and the mass of the unit 250 made up of the movable compressor body 26 together with the mass of the driver 246 and the pivot bearing 248 on the other hand , whose center of mass SOS lies in the central axis plane ME, and is also referred to as the mass balance plane ME, since all centers of mass contributing to the optimal possible mass balance should be close to or in this.
  • An orbital orbit balancing mass 252 ( Fig. 10 ) is provided, which counteracts the imbalance caused by the unit 250 moving on the orbital path 48 consisting of compressor body 26, driver 246 and pivot bearing 248 and compensates for it as far as possible, the orbital path balancing mass 252 with its center of mass SOAGM being arranged as close as possible to the mass compensation plane ME, as in Fig. 10 or 13 and 14 shown.
  • the orbital orbit balancing mass 252 lies in particular on a side of a transverse plane QE which runs perpendicular to the mass balancing plane ME and runs through the central axis 44, facing away from the eccentric drive pin 244 and the central axis 46, in particular on the opposite side.
  • the orbital orbit balancing mass 252 is not held on the driver 246 but is mounted on the drive shaft 228 with a guide body 254, in particular on the eccentric drive pin 244.
  • the guide body 254 includes a pin receptacle 256, which the eccentric drive pin 244 driving the driver 246 passes through in order to accommodate the bearing body 254 so that it can rotate about the eccentric axis 245.
  • the guide body 254 is slidably guided on an alignment surface 262 of the drive shaft 228 facing it, for example on the front side of the drive shaft 228, with a guide surface 264 of the guide body 254 facing the alignment surface 262, parallel to an alignment plane 266 running perpendicular to the central axis 44 of the drive shaft 228, so that During all rotational movements about the eccentric axis 245, the parallel alignment of the guide body 254 to the alignment plane 266 is maintained and the orbital orbit balancing mass 252 thus moves on a path 268 around the drive shaft 228, which runs in a path plane 269 parallel to the alignment plane 266 ( Fig. 10 , 11 ).
  • an axial guide 272 is provided for the guide body 254 relative to the drive shaft 228, which has a projection 274 arranged on the eccentric drive pin 244, for example a collar, and which protects the guide body 254 against movement in Direction of the central axis 44 away from the alignment surface 262 and for this purpose, for example, engages in a recess 276, which extends limitedly into the guide body 254 from a side 278 of the guide body 254 facing the driver 246.
  • a stop body 282 firmly connected to the guide body 254 and arranged at a distance from the eccentric drive pin 244, which engages in a recess 284 in the drive shaft 228, which extends from its end face 262 into the drive shaft 228 and the stop body 282 with play takes up and thus allows the guide body 254 a limited rotational work and the eccentric axis 245 relative to the drive shaft 228.
  • the stop body 282 is preferably designed as the head of a coupling pin 292 which passes through the guide body 252 and will be explained in more detail below and which in turn also cooperates with the driver 246.
  • the coupling pin 292 is fixed to the guide body 254 in that the coupling pin 292 passes through a receiving hole 288 in the guide body 254 and is fixed in it by a press fit.
  • the coupling pin 292 is also provided with its head 282, which rests on a side of the guide body 254 facing away from the driver 246 ( Fig. 12 ).
  • the first movement limiting unit 280 preferably allows a relative rotation of the guide body 254 about the eccentric drive axis 245, which lies within an angular range of at least 2° (angular degrees), up to a maximum of 4° (angular degrees), even better a maximum of 6° (angular degrees), in order to enable tolerance compensation , whereby the orbital orbit balancing mass 252 should be aligned relative to the drive shaft 228, in particular relative to the central axis 44, in such a way that the orbital mass balancing is as optimal as possible ( Fig. 14 ).
  • the first movement limiting unit 280 is in particular dimensioned so that - without any additional action - the unit 260, comprising the orbital orbit balancing mass 252 and the guide body 254, the orbital orbit balancing mass 252, aligns itself in such a way that a center of mass SOAGM of the unit 260 made up of orbital orbit balancing mass 252, guide body 254 and the coupling pin 292 of a coupling unit 300 on a side of the transverse plane QE opposite the eccentric pin 244 and within a plane extending beyond the mass compensation plane ME and on both sides of the mass compensation plane ME in Fig. 13 and Fig. 14
  • the remaining unbalance tolerance range UWT remains, so that the possible unbalances are limited to a tolerable level.
  • the unit 260 consisting of the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 with the center of mass SOAGM brings about the optimal possible mass balance to the unit 250 consisting of the orbiting compressor body 26 with the pivot bearing 248 and the driver 246 with the center of mass SOS when the centers of mass are SOAGM and SOS are as close as possible to the mass balance level ME.
  • the mass not taken into account in the mass balancing described above is the mass of the eccentric drive pin 244, which is arranged asymmetrically to the mass balancing plane ME and leads to vibrations, particularly at high speeds of the drive shaft 228.
  • the coupling pin 292 which is firmly arranged on the guide body 254, acts as a mass balancing body ( Fig. 8 ), formed and arranged on the guide body 254 on a side of the mass compensation plane ME opposite the eccentric drive pin 244 ( Fig. 10 ) and thus together with the eccentric drive pin 244 leads to a mass distribution that is at least approximately symmetrical to the mass compensation plane ME.
  • a pin axis 294 of the coupling pin 292 and the eccentric axis 245 are arranged mirror-symmetrically to the mass compensation plane ME and, moreover, the eccentric drive pin 244 and the coupling pin 292 preferably have approximately the same mass ( Fig. 13, 14 ).
  • the coupling unit 300 includes, in addition to the coupling pin 292 with its pin axis 294, a recess 296 in the driver 246 which forms a receptacle and into which the coupling pin 292 is located extends and which receives the coupling pin 292 with play, so that a second movement limiting unit is available to prevent a rotational movement of the driver 246 about the eccentric axis 245 in order to avoid a tolerance-sensitive and possibly also overdetermined connection of the driver 246 relative to the guide body 254 and thus in turn relative to the drive shaft 228 through the precise mounting of the driver 246 relative to the eccentric drive pin 244 and the additional connection of the driver 246 to the coupling pin 292, which in turn is also rotatably mounted about the eccentric drive pin 244 ( Fig. 14 ).
  • the coupling pin 292 and the recess 296 are arranged relative to one another in such a way that the coupling pin 292 can rest on a partial region 304 of an inner wall surface 298 of the recess 296 which is located at the front in the direction of rotation D, which makes it possible to resist the centrifugal force FZsos Unit 250, formed from the orbiting compressor body 26, the driver 246 and the pivot bearing 248, which acts in the sense of increasing the compressor orbital radius VOR in addition to the force FC and thus generates a speed-dependent contact force in a contact point 322 of the spiral ribs 34, 38 to counteract.
  • the unit 260 consisting of the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 lies with its center of mass SOAGM on a side of the transverse plane QE opposite the center of mass SOS and has the tendency to rotate in the direction of rotation D around the eccentric axis 245 ( Fig. 16 ).
  • the coupling pin 292 acting on the recess 296 in the partial area 304 acts - as in Fig. 16 shown - in the partial area 304, based on the eccentric axis 245, a torque generated by the force FD SOAGM on the driver 246, which corresponds to the torque acting on the driver 246 due to the centrifugal force FZsos, also related to the eccentric axis 245 and generated by the force FDsos, counteracts and thereby reduces the centrifugal force FZsos to the centrifugal force FZR. This reduction in the centrifugal force FZsos depends on the mass in the center of mass SOAGM.
  • the above-mentioned arrangement of the coupling pin 292 and the recess 296 can ensure that the center of mass SOAGM in the centrifugal force-coupling state lies close to or preferably in the mass compensation plane ME on a side of the central axis 44 opposite the center of mass SOS, and thus essentially optimal mass balance to the unit 250 consisting of the orbiting compressor body 26, the driver 246 and the pivot bearing 248.
  • FIG. 17 and 18 A realization of an in Fig. 17 and 18
  • the centrifugal force decoupling state of the coupling unit 300 shown occurs due to a mutual rotation of the unit 260 about the eccentric axis 245 opposite to the direction of rotation D and a displacement of the pin axis 294 opposite to the direction of rotation into a position 294e ( Fig. 17 and 18 ), so that contact between the coupling pin 292 and the recess 296 is no longer possible, and the center of mass SOAGM is at a distance from the mass compensation plane ME.
  • the speed-dependent centrifugal force FZsos acting in the center of mass SOS is fully effective in the contact point 322 of the spiral ribs 34, 38, while the unit 260 consisting of the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 with its center of mass SOAGM relative to the drive shaft 228, as follows described in detail, the center of mass SOAGM lies on a side of the transverse plane QE opposite the center of mass SOS and at a short distance from the mass compensation plane ME.
  • the entire speed-dependent positioning device is provided for determining or releasing the rotational positions of the unit 260 consisting of the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 relative to the drive shaft 228.
  • This positioning device 332 comprises a guide body 336 which can be fixed in the drive shaft 228 and extends with its central axis 334 radially to the drive shaft 228, which in the simplest case is designed as a cylindrical pin which can be fixed in a receiving bore 338 of the drive shaft 228, for example by a screw 339 passing through it is, which forms a guide surface 342 on the circumference, along which a positioning body 344 is guided movably parallel to the central axis 334 and thus radially to the drive shaft 228.
  • the positioning body 344 is acted upon by a spring 346, which is supported on the one hand with a radially inner end on the positioning body 344 and with a radially outer end on a stop 348, which is designed, for example, as a disk body fixed to the guide body 336 by means of the screw 339 is.
  • the spring 346 acts on the positioning body 344, which acts on the positioning body 344 in the direction of a radially inner stop 352, which is formed, for example, on the guide body 336.
  • the positioning body 344 is thus movable in a direction radial to the central axis 44 in the opposite direction to the force of the spring 346 from a position resting on the radially inner stop 352 to a position resting on the radially outer stop 348.
  • the spring 346 is dimensioned so that at low speeds of the drive shaft 228 the positioning body 344 rests on the radially inner stop 352 and moves away from this as the speed increases and from a defined switching speed onwards it rests on the radially outer stop 348, as shown in Fig. 17 and 15 is shown.
  • the positioning body 344 is preferably provided with a positioning surface 354 running obliquely to the central axis 334, which in the simplest case has a conically tapering course to the central axis 334 in the direction of the radially inner stop 352.
  • the positioning surface 354 of the positioning body 344 serves to influence a rotational position of the unit 260 made up of orbital path compensation mass 252 and guide body 254 together with the coupling pin 292, relative to the drive shaft 228, with a change in the rotational position by rotating the unit 260 about the eccentric drive pin 244, in particular its eccentric axis 245, is possible.
  • the guide body 254 is provided with an extension 356, on which an actuating body 358 which interacts with the positioning surface 354 is arranged ( Fig. 15 , 17 and 19 ).
  • the positioning body 344 is as in Fig. 17 shown, in the position in which it rests against the radially inner stop 352, the positioning surface 354 acts on the actuating body 358 with its area lying radially outer with respect to the central axis 334 and thereby places the unit 260 consisting of orbital path compensation mass 252, guide body 254 and coupling pin 292 in a rotational position about the eccentric axis 245 relative to the drive shaft 228, in which the center of mass SOAGM is at a distance from the mass compensation plane ME.
  • the position of the recess 296 relative to the coupling pin 292 is such that they do not touch each other in this position of the positioning body 344, so that the unit 260 consisting of orbital orbit balancing mass 252, guide body 254 and coupling pin 292 is removed from the orbiting unit 250 Compressor body 26, the driver 246 and the pivot bearing 248 is in the centrifugal force decoupled state, and the center of mass SOS of this unit 250 is the speed-dependent centrifugal force FZsos ( Fig. 17 and 18 ) generated.
  • the unit 250 consisting of the orbiting compressor body 26, the driver 246 and the pivot bearing 248, thus develops the full centrifugal force FZsos at low speeds in the sense of an increase in the compressor orbital radius VOR, which together with the force FC contributes to the contact force in the contact point 322 of the spiral ribs 34, 38 ( Fig. 18 ).
  • the positioning body 344 Increasing the speed up to the switching speed, at which the positioning body 344 is moved radially outwards to the central axis 44 against the force of the spring 346 by the centrifugal force that increases with the speed and finally rests against the radially outer stop 348, causes the positioning surface 354 increasingly moves radially outwards and releases the actuating body 358 so that the unit 260 can pivot relative to the eccentric axis 245 in the direction of rotation D and can move until the coupling pin 292 comes to rest on the portion 304 of the wall surface 298 of the recess 296 and thus between the unit 260 made up of the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 and the unit 250 made up of the orbiting compressor body 26, the driver 246 and the pivot bearing 248, the coupling unit 300 is in the centrifugal force coupling state in which the unit 260 from the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 counteracts and reduces
  • the solution according to the invention thus creates the possibility of operating the compressor in such a way that at low speeds the coupling unit 300 is in the centrifugal force decoupling state and thus the unit 250, comprising the orbiting movable compressor body 26, the driver 246 and the pivot bearing 248 with their full centrifugal force FZsos is effective, so that this centrifugal force FZsos together with the force FC, which is created by the force FA acting on the orbiting movable compressor body 26 due to the eccentric drive 242 ( Fig. 18 ), acts on the contact point 322 of the spiral ribs 34, 38 and thus keeps the spiral ribs 34, 38 in contact with the contact point 322 in order to achieve the tightest possible seal between them.
  • the coupling unit 300 transitions from the centrifugal force decoupling state ( Fig. 18 ) into the centrifugal force-coupling state ( Fig. 17 ) in which the Centrifugal force FZsos generated by the unit 250 is reduced to the centrifugal force FZR by coupling the unit 250 with the unit 260, so that overall when high speeds are reached, the force between the spiral ribs 34, 38 in the contact point 322 can be limited.
  • the solution according to the invention thus creates, on the one hand, the advantage of achieving a sufficiently high force between the spiral ribs 34, 38 at very low speeds in the contact point 322, and on the other hand, the force in the contact point 322 between the spiral ribs at high speeds 34, 38 to a level at which no damage to the spiral ribs 34, 38 occurs.

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

Claims (19)

  1. Compresseur, comprenant un carter de compresseur (12), une unité compresseur à spirales (22) disposée dans le carter de compresseur (12) avec un premier corps de compresseur (24) disposé de manière fixe et un deuxième corps de compresseur (26) mobile par rapport au corps de compresseur (24) disposé de manière fixe, dont les première et deuxième nervures spiralées (34, 38) réalisées sous forme d'une développante de cercle s'interpénètrent avec formation de chambres de compresseur (42), lorsque le deuxième corps de compresseur (26) est déplacé par rapport au premier corps de compresseur (24) sur une trajectoire orbitale (48), un guidage axial (96), lequel soutient le corps de compresseur (26) mobile vis-à-vis de mouvements dans une direction parallèle à un axe médian (44) du corps de compresseur (24) disposé de manière fixe et le guide lors de mouvements dans une direction transversale par rapport à l'axe médian (44), un entraînement excentrique (242) pour l'unité compresseur à spirales (22), qui présente un entraîneur (246) entraîné par un moteur d'entraînement (222) et tournant sur la trajectoire orbitale (48) autour de l'axe médian (44) d'un arbre d'entraînement (228) et monté de manière à pouvoir tourner par rapport à l'arbre d'entraînement (228) autour d'un axe d'entraînement d'excentrique (245), qui coopère pour sa part avec un logement d'entraîneur (249) du deuxième corps de compresseur (26), un contrepoids de trajectoire orbitale (252) agissant à l'encontre d'un balourd dû au corps de compresseur (26) se déplaçant sur la trajectoire orbitale (48) et également monté de manière à pouvoir tourner autour de l'axe d'excentrique (245) et un couplage (164) empêchant une rotation automatique du deuxième corps de compresseur (26),
    caractérisé en ce que l'entraîneur (246) et le contrepoids de trajectoire orbitale (252) peuvent être couplés l'un à l'autre au moyen d'une unité de couplage (300), de telle sorte que l'unité de couplage (300) lorsque l'arbre d'entraînement (228) est en rotation dans un état de couplage de force centrifuge agit de telle sorte que le contrepoids de trajectoire orbitale (252) agit à l'encontre d'une force centrifuge (FZsos) d'une unité (250) comprenant au moins l'entraîneur (246) et le corps de compresseur (26) en orbite, que l'unité de couplage (300) lorsque l'arbre d'entraînement (228) est en rotation dans un état de découplage de force centrifuge agit de telle sorte que le contrepoids de trajectoire orbitale (252) n'agit pas à l'encontre de la force centrifuge (FZsos) de l'unité (250) comprenant au moins l'entraîneur (246) et le corps de compresseur (26) en orbite, et que l'unité de couplage (300) peut être amenée au moyen d'un dispositif de positionnement (332) à partir de l'état de découplage de force centrifuge dans l'état de couplage de force centrifuge ou inversement.
  2. Compresseur selon la revendication 1, caractérisé en ce que l'unité de couplage (300) comprend deux éléments de couplage (292, 296), dont l'un est relié au contrepoids de trajectoire orbitale (252) et l'un à l'entraîneur (246), qu'en particulier les éléments de couplage (292, 296) peuvent être amenés par un mouvement l'un par rapport à l'autre dans l'état de couplage de force centrifuge et l'état de découplage de force centrifuge.
  3. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un élément de couplage (292) est relié fixement au contrepoids de trajectoire orbitale (252) ou à l'entraîneur (246) et l'autre élément de couplage (296) est relié fixement à l'entraîneur (246) ou au contrepoids de trajectoire orbitale (252).
  4. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un des éléments de couplage est un corps de couplage (292) et un autre des éléments de couplage un logement (296), dans lequel le corps de couplage (292) s'insère, qu'en particulier le corps de couplage (292) s'insère avec du jeu dans le logement (296), qu'en particulier le corps de couplage (292) dans l'état de couplage de force centrifuge s'applique sur une zone partielle (304) du logement (296) et dans l'état de découplage de force centrifuge est disposé sans contact par rapport au logement (296).
  5. Compresseur selon la revendication 4, caractérisé en ce que le corps de couplage (292) est réalisé sous la forme d'un tourillon de couplage, qu'en particulier le tourillon de couplage (292) est relié au contrepoids de trajectoire orbitale (252) et s'insère dans le logement (296) relié à l'entraîneur (246).
  6. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le dispositif de positionnement (332) fonctionne de manière commandée par la vitesse de rotation et au-dessous d'une vitesse de rotation de commutation amène l'unité de couplage (300) dans l'état de découplage de force centrifuge et au-dessus de la vitesse de rotation de commutation amène l'unité de couplage (300) dans l'état de couplage de force centrifuge.
  7. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le dispositif de positionnement (332) est disposé sur l'arbre d'entraînement (228).
  8. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le dispositif de positionnement (332) dans l'état de couplage de force centrifuge admet une coopération des éléments de couplage (292, 296) et dans l'état de découplage de force centrifuge positionne les éléments de couplage (292, 296) sans contact l'un par rapport à l'autre.
  9. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le dispositif de positionnement (332) présente un corps de positionnement (344), lequel est guidé sur l'arbre d'entraînement (228) au moyen d'un corps de guidage (336) avec au moins une composante dans la direction radiale par rapport à l'axe médian (44) et mobile le long du corps de guidage (336) en fonction de la vitesse de rotation, qu'en particulier le corps de positionnement (344) est sollicité au moyen d'un accumulateur de force élastique (346) à l'encontre d'une force centrifuge agissant sur le corps de positionnement (344), qu'en particulier le corps de positionnement (344) est pourvu d'une surface de positionnement (354), qui agit en fonction d'une position radiale du corps de positionnement (344) sur l'unité de couplage (300), qu'en particulier le corps de positionnement (344) dans une première position, qui correspond à une vitesse de rotation au-dessous de la vitesse de rotation de commutation, amène l'unité de couplage (300) dans son état de découplage de force centrifuge et dans une position, qui correspond à une vitesse de rotation au-dessus de la vitesse de rotation de commutation, amène l'unité de couplage (300) dans son état de couplage de force centrifuge.
  10. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'avec le dispositif de positionnement (332) l'élément de couplage (292) relié au contrepoids de trajectoire orbitale (252) peut être amené par rapport à l'élément de couplage (296) relié à l'entraîneur (246) dans l'état de couplage de force centrifuge ou l'état de découplage de force centrifuge, qu'en particulier le dispositif de positionnement (332) amène le contrepoids de trajectoire orbitale (252) conjointement avec l'élément de couplage (292) dans l'état de découplage de force centrifuge ou l'état de couplage de force centrifuge.
  11. Compresseur selon l'une quelconque des revendications 6 à 10, caractérisé en ce que le contrepoids de trajectoire orbitale (252) dans l'état de découplage de force centrifuge de l'unité de couplage (300) est distant avec son centre de gravité (SOAGM) du plan d'équilibrage des masses (ME) et dans l'état de couplage de force centrifuge de l'unité de couplage (300) se situe avec son centre de gravité (SOAGM) près de ou dans le plan d'équilibrage des masses (ME).
  12. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une première unité de limitation de mouvement (280) agit entre l'arbre d'entraînement (228) et le contrepoids de trajectoire orbitale (252).
  13. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'axe médian (44) de l'arbre d'entraînement (228) et un axe médian (46) du deuxième corps de compresseur (26) mobile fixent un plan d'équilibrage des masses (ME) s'étendant à travers ceux-ci, et que la première unité de limitation de mouvement (280) maintient le contrepoids de trajectoire orbitale (252) sur une face d'un plan transversal géométrique (QE) s'étendant perpendiculairement au plan d'équilibrage des masses (ME) et à travers l'axe médian (44) de l'arbre d'entraînement (228) opposée à l'axe d'excentrique (245) .
  14. Compresseur selon la revendication 12 ou 13, caractérisé en ce que la première unité de limitation de mouvement (288) oriente le contrepoids de trajectoire orbitale (252) de sorte qu'un centre de gravité (SOAGM) de celui-ci reste à l'intérieur d'une zone de tolérance de balourd s'étendant au-delà du plan d'équilibrage des masses (ME) et de part et d'autre de celui-ci.
  15. Compresseur selon l'une quelconque des revendications 12 à 14, caractérisé en ce que la première unité de limitation de mouvement (280) admet une possibilité de rotation libre du corps de guidage (254) autour de l'axe d'excentrique (245) dans une plage angulaire de 0,5° (degré angulaire) à 5° (degré angulaire).
  16. Compresseur selon l'une quelconque des revendications 12 à 15, caractérisé en ce que la première unité de limitation de mouvement (280) est formée par un premier élément de butée (282) maintenu sur le contrepoids de trajectoire orbitale (252), en particulier sur le corps de guidage (254) de celui-ci, ou l'arbre d'entraînement (228) et un deuxième élément de butée (284) coopérant avec le premier élément de butée (282), en particulier recevant celui-ci, et disposé sur l'arbre d'entraînement (228) ou sur le contrepoids de trajectoire orbitale (252), en particulier sur le corps de guidage (254) de celui-ci.
  17. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le contrepoids de trajectoire orbitale (252) est monté de manière à pouvoir tourner sur l'axe d'entraînement d'excentrique (245) avec un corps de guidage (254), qu'en particulier le corps de guidage (254) est relié fixement au contrepoids de trajectoire orbitale (252).
  18. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le contrepoids de trajectoire orbitale (252) est monté par un tourillon d'entraînement d'excentrique (244) coopérant avec l'entraîneur (246) et l'arbre d'entraînement (228) de manière à pouvoir tourner autour de l'axe d'entraînement d'excentrique (245), qu'en particulier le tourillon d'entraînement d'excentrique (244) travers un logement de tourillon (256) du corps de guidage (254).
  19. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le contrepoids de trajectoire orbitale (252) coopère au moyen du corps de guidage (254) avec l'arbre d'entraînement (228) et est guidé sur l'arbre d'entraînement (228).
EP18737172.9A 2018-06-22 2018-06-22 Compresseur à spirale muni d'un contrepoids de trajectoire orbitale découplable Active EP3810935B1 (fr)

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PCT/EP2018/066799 WO2019242865A1 (fr) 2018-06-22 2018-06-22 Compresseur à spirale muni d'un contrepoids de trajectoire orbitale découplable

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Publication number Priority date Publication date Assignee Title
JP3467746B2 (ja) * 1994-05-27 2003-11-17 株式会社豊田自動織機 スクロール型圧縮機
US5496157A (en) * 1994-12-21 1996-03-05 Carrier Corporation Reverse rotation prevention for scroll compressors
JPH09195957A (ja) * 1996-01-17 1997-07-29 Nippon Soken Inc スクロール型圧縮機
CN201437775U (zh) * 2009-07-01 2010-04-14 松下·万宝(广州)压缩机有限公司 旋转式压缩机
EP3491245B1 (fr) 2016-07-27 2024-03-27 BITZER Kühlmaschinenbau GmbH Compresseur

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CN112119218B (zh) 2023-01-06
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CN112119218A (zh) 2020-12-22

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