WO2019242865A1 - 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
WO2019242865A1
WO2019242865A1 PCT/EP2018/066799 EP2018066799W WO2019242865A1 WO 2019242865 A1 WO2019242865 A1 WO 2019242865A1 EP 2018066799 W EP2018066799 W EP 2018066799W WO 2019242865 A1 WO2019242865 A1 WO 2019242865A1
Authority
WO
WIPO (PCT)
Prior art keywords
coupling
compressor
centrifugal force
mass
orbital
Prior art date
Application number
PCT/EP2018/066799
Other languages
German (de)
English (en)
Inventor
Dimitri Gossen
Original Assignee
Bitzer Kühlmaschinenbau Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bitzer Kühlmaschinenbau Gmbh filed Critical Bitzer Kühlmaschinenbau Gmbh
Priority to CN201880093478.XA priority Critical patent/CN112119218B/zh
Priority to PCT/EP2018/066799 priority patent/WO2019242865A1/fr
Priority to EP18737172.9A priority patent/EP3810935B1/fr
Publication of WO2019242865A1 publication Critical patent/WO2019242865A1/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 compressor body arranged in a stationary manner and a second compressor body movable orbiting relative to the stationary arranged compressor body, the first and second spiral ribs of which are designed in the form of a circular involute and form compression chambers 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 the direction parallel to a central axis of the stationary arranged compressor body and guides movements in the direction transverse to the central axis, an eccentric drive for the Spiral compressor unit, which is driven by a drive motor and rotates on the orbital orbit around the central axis of a drive shaft and relative to the drive shaft le has a driver rotatably mounted about an eccentric drive axis, which in turn interacts with a driver receptacle of the second compressor body, an orbital compensating mass which counteracts an imbalance due to the compressor body moving
  • Such compressors are known from the prior art, for example WO 2018/019372.
  • the coupling unit does not counteract the orbiting compressor body and that the coupling unit can be transferred from the centrifugal force decoupling state to the centrifugal force decoupling state or vice versa by means of a positioning device.
  • the coupling unit has two
  • Coupling elements includes, one of which is connected to the orbital orbit balancing mass and one to the driver.
  • the coupling elements can preferably be brought into the centrifugal force coupling and the centrifugal force decoupling state by movement relative to one another.
  • the coupling elements can be connected to the orbital orbit balancing mass and the driver in a wide variety of ways. For example, a movable connection would be conceivable.
  • a particularly advantageous solution provides that one coupling element is firmly connected to the orbital orbit balancing mass or the driver and the other coupling element is firmly connected to the entrainer or the orbital orbit balancing mass.
  • the coupling elements can be of any design.
  • Coupling elements is a coupling body and another of the coupling elements is a receptacle in 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 rests against a portion of the receptacle in the centrifugal force-coupling state and thus interacts with the receptacle and is arranged in the centrifugal-force-decoupling state without contact with the receptacle, so that the coupling body and the receptacle do not interact ,
  • the coupling body could be constructed in a wide 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 compensation 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 brings the coupling unit into the centrifugal force coupling state above the switching speed, so that the positioning device only reacts to the speed of the drive shaft brings about either the centrifugal force decoupling state or the centrifugal force coupling state.
  • the positioning device can theoretically be arranged on the orbital orbit balancing mass or on the driver.
  • a particularly favorable solution provides that the positioning device is arranged on the drive shaft.
  • the positioning device can be implemented in a structurally particularly simple manner if it has a positioning body which is attached to the drive shaft by means of a guide body with at least one
  • Guide body is movable depending on the speed.
  • the speed-dependent movement of the positioning body can be implemented in a wide variety of ways.
  • a solution which is particularly simple in terms of construction 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 itself reacts to the rotational speed of the drive shaft in that the centrifugal force acting on it has the tendency to move the positioning body away from the drive shaft, while the spring-elastic force accumulator counteracts this centrifugal force.
  • the positioning body assumes a position close to the drive shaft up to the switchover speed due to the force effect of the resilient energy store and from the switchover speed the centrifugal force of the positioning body overcomes the force of the spring-elastic force store and thus the resilient one
  • the energy accumulator moves at an increasing distance from the drive shaft.
  • the positioning body is provided with a positioning surface which acts on the coupling unit as a function of a radial position of the positioning body. It is preferably provided that the positioning body brings the coupling unit into its centrifugal force decoupling state in a first position, which corresponds to a rotational speed below the switchover speed, and in a position that corresponds to a speed above the switchover speed brings the coupling unit into its centrifugal force coupling state.
  • Centrifugal force of the unit consisting of the compressor body and driver acts on the spiral ribs and at a speed above the changeover speed the centrifugal force of the compressor body and the driver is counteracted by the orbital orbit compensation mass.
  • the positioning element can be used to bring the coupling element connected to the orbital orbit compensation mass into the centrifugal force-coupling or the centrifugal force-decoupling state relative to the coupling element connected to the driver.
  • the positioning device together with the coupling element, the orbital orbit compensation mass in the
  • centrifugal force decoupling state or brings the centrifugal force coupling state.
  • centrifugal force decoupling state and the centrifugal force decoupling state have so far been given no further details.
  • An advantageous solution provides for the orbital orbit balancing mass in the centrifugal force decoupling state of the coupling unit with its center of gravity to be at a distance from the mass balancing plane and in the centrifugal force coupling state of the coupling unit with its center of gravity to be 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 gravity 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 limitation unit is effective between the drive shaft and the orbital orbit compensation mass.
  • a position range of the orbital orbit compensation mass can be determined relative to the drive shaft and relative to the
  • 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 balancing plane running through it and that the first movement limiting unit sets the orbital orbit balancing mass on a side opposite the eccentric drive axis on a side perpendicular to the mass balancing plane and through the central axis of the drive shaft
  • the first movement limiting unit aligns the orbital orbit balancing mass in such a way that a center of gravity of the same remains within an unbalance tolerance range which extends beyond the mass balancing plane and on both sides thereof, so that the first movement limiting unit causes excessively large ones have the orbital orbital balancing mass prevent the imbalance caused.
  • the first movement limitation unit is provided with a first stop element held on the orbital track compensation element, in particular on its guide body, or on the drive shaft and a first stop element, which cooperates with the first stop element, in particular accommodates it, on the drive shaft or the orbital track compensation mass , in particular their guide body, arranged second stop element is formed.
  • a first stop element held on the orbital track compensation element in particular on its guide body, or on the drive shaft
  • a first stop element which cooperates with the first stop element, in particular accommodates it, on the drive shaft or the orbital track compensation mass , in particular their guide body, arranged second stop element is formed.
  • the guide body is firmly connected to the orbital orbit compensation mass.
  • a particularly simple and robust constructional implementation provides that the orbital orbit compensation mass is rotatably supported about the eccentric axis by means of an eccentric drive pin interacting 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 compensation mass interacts with the drive shaft by means of the guide body and is guided on the drive shaft and can thus be guided in a defined orientation relative to the drive shaft.
  • the effect of the eccentric drive pin on the guide body essentially serves to move the guide body with the orbital orbit balancing mass in such a way that the orbital orbit balancing mass follows the orbital orbit of the driver and produces the necessary mass balancing.
  • the orbital orbital compensation mass is guided through the guide body engaging the drive shaft on a path that runs in a path plane that runs parallel to an alignment plane running perpendicular to the central axis of the drive shaft.
  • any tilting moments that may still occur are transferred from the orbital orbit compensation mass to the drive shaft by means of the guide body and thus essentially do not generate any tilting moments acting on the eccentric drive shaft.
  • the guide of the guide body on the drive shaft can be in
  • 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 which 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 to span the alignment surface.
  • the guide body it is also advantageous for spatial reasons if the guide body is arranged between the alignment surface of the drive shaft and the driver. In this case, it is possible, despite the provision of the guide body, to make the eccentric drive spatially small.
  • the guide body is plate-shaped, that is, in the direction of the central axes, the smallest possible extension in relation to its extension transverse to the central axis.
  • the guide body is guided by the drive shaft and, in particular, to ensure it in all operating states, if 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 so that this
  • the axial guide can be designed in a wide variety of ways.
  • the axial guide is preferably designed such that it is on a side opposite the guide body on the guide surface
  • the eccentric drive has the eccentric drive pin driving the driver and a coupling body coupling the orbital orbit compensation mass to the driver.
  • the coupling body also represents a mass balancing body.
  • the eccentric drive has an eccentric drive pin driving the driver and a coupling body coupling the orbital orbit compensation mass to the driver.
  • the coupling body also represents a mass balancing body.
  • the coupling pin is arranged fixed on the guide body and engages in the recess in the driver.
  • FIG. 1 is a perspective view of a first embodiment of a compressor according to the invention.
  • FIG. 2 shows a longitudinal section along line 2-2 in FIG. 4;
  • FIG. 3 shows a schematic illustration of interlocking spiral ribs and the orbital movement of one of the spiral ribs and a representation of the orbital path of the movable spiral rib relative to the stationary spiral rib;
  • Fig. 4 is a section along line 4-4 in Fig. 2;
  • Fig. 5 is a section along line 5-5 in Fig. 2;
  • FIG. 6 shows an enlarged illustration of a region A in FIG. 5;
  • FIG. 7 shows a section along line 7-7 in FIG. 2;
  • Fig. 8 is an exploded view of a cooperation between one
  • Eccentric drive journal an orbital orbit balancing mass, a driver in the compressor according to the invention and a positioning device;
  • Fig. 9 is a schematic geometric representation of the relative location of the
  • FIG. 10 shows a plan view of a guide body with the orbital orbit balancing mass in its position on the drive shaft with an eccentric drive pin penetrating the guide body and a coupling pin corresponding to line 10-10 in FIG. 11;
  • Fig. 11 is an enlarged section along line 11-11 in Fig. 10;
  • Fig. 12 is a section along line 12-12 in Fig. 10; 13 shows a section similar to FIG. 10 with the first movement limitation unit active;
  • FIG. 14 shows a section similar to FIG. 10 with the first movement limitation unit inactive
  • Fig. 15 is a section along line 15-15 in Fig. 11 in the area of a
  • FIG. 16 shows a representation similar to FIG. 9 to explain the relationships according to FIG. 15;
  • Fig. 17 shows a section similar to Fig. 15 in a centrifugal force decoupling
  • FIG. 18 shows a representation similar to FIG. 9 to explain the relationships in FIG
  • Fig. 19 is an enlarged perspective view of the drive shaft with the
  • a first exemplary embodiment shown in FIG. 1 of a compressor according to the invention for a gaseous medium, in particular a refrigerant, designated as a whole by 10, comprises a compressor housing, designated as a whole by 12, which has a first end-side housing section 14, a second end-side housing section 16 and one between the two End-side housing sections 14 and 16 arranged intermediate section 18.
  • a spiral compressor unit designated as a whole by 22 is provided in the first housing section 14, which has a first one in the compressor housing 12, in particular in the first one
  • Housing section 14 stationary compressor body 24 and a second compressor body 26 movable relative to the stationary compressor body 24.
  • the first compressor body 24 comprises a compressor body base 32, above which a first spiral rib 34 rises
  • the second compressor body 26 likewise comprises a compressor body base 36, above which a second spiral rib 38 rises.
  • the compressor bodies 24 and 26 are arranged relative to one another in such a way that the spiral ribs 34, 38 interlock to form, as shown in FIG. 3, at least one, preferably a plurality of compressor chambers 42 between them, in which a compression of the gaseous medium, for example of Refrigerant, 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 with a compressor orbital path radius VOR, the volume of the compressor chambers 42 being reduced and ultimately compressed gaseous medium through a central outlet 52 (FIG. 2) emerges while the gaseous medium to be sucked in is sucked in radially on the outside with respect to the central axis 44 through compressor chambers 42 opening on the circumference.
  • a compression of the gaseous medium for example of Refrigerant
  • the compressor chambers 42 are sealed relative to one another in particular by virtue of the fact that the spiral ribs 34, 38 are provided on the end face with axial sealing elements 54 and 58, which bear against the respective bottom surface 62, 64 of the respective 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 received as a whole in a first housing body 72 of the compressor housing 12, which has an end cover section 74 and a cylindrical ring section 76 integrally molded on the end cover section 74, which in turn engages with a ring shoulder in a sleeve body 82 of the housing body 72 which engages 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 also attached to the compressor body base 32
  • molded support fingers 92 supported on a contact surface 94 in the housing body 72.
  • 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 fixed in a stationary manner 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 has a carrier surface 114 which faces the axial support surface 102 (FIGS. 2, 5), but on which the compressor body base 36 with the axial support surface 102 does not rest, but instead on which a plate-shaped sliding body 116, designated as a whole by 116, rests with a sliding support surface 118, the sliding body 116 with a sliding support surface 122 (FIGS. 2 and 5) opposite the sliding support surface 118, the axial support surface 102 (FIGS. 2 and 4) against movements parallel to the central axis 44 but slidably guides 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 track 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 are relative to the sliding body 116 moves, on the other hand the sliding body 116 in turn in turn moves relative to the carrier element 118.
  • the sliding body 116 there is sliding between the compressor body base 36 and the sliding body 116 due to a movement of the axial support surface 102 relative to the sliding support surface 122 of the sliding body 116, and the sliding contact surface 118 of the sliding body 116 is also sliding relative to the carrier surface 114 of the carrier element 112.
  • the sliding body 116 is provided with play relative to the carrier element 112 by a guide shown in FIGS. 5 and 6 and designated as a whole by 132 guided, wherein the guide with play 132 comprises a guide recess 134 provided in the sliding body 116, which one
  • Has diameter DF and includes a guide pin 136 anchored in the carrier element 112, the diameter DS of which is smaller than the diameter DF, so that half of the difference DF-DS defines a guide orbital radius with which the sliding body 116 performs an orbiting movement relative to the Carrier element 112 can perform.
  • the movements of the sliding body 116 build up 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 carrier surface 114 and the sliding support surface 118.
  • the guide orbital radius FOR is 0.01 times the compressor orbital radius or more
  • the carrier element 112 is made of an aluminum alloy at least in the region 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 provided, for example 112 is available in the area of the carrier surface 114 for building up the lubricating film in the intermediate space.
  • the sliding body 116 itself is designed as a plate-shaped, ring-shaped part made of spring steel and thus the sliding bearing surface 118 facing the carrier surface 114 represents a smooth spring steel surface, the formation of the lubricating film is additionally promoted.
  • the material pair made of the aluminum alloy which is softer in the area of the carrier surface 114 than spring steel, and the spring steel in
  • the support element 112 is not only provided with the support 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 furthermore fixed 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 opposite axial support surface 102.
  • the build-up of the lubricating film between the slide support surface 122 and the axial support surface 102 is promoted in that the slide support surface 122 and the axial support surface 102, in the overlap region in which they
  • Interaction is formed as a coherent ring surface 124 or 126, ie in the circumferential direction U around the central axis and in its entire radial extent, the ring surface 126 of the axial support surface 102 in particular starting from an inner contour IK with a radius IR thereof extends to an outer contour AK, the radius IR being less than two-thirds of an outer radius AR.
  • the ring surface 124 of the slide support surface 122 is dimensioned such that the ring surface 126 of the axial support surface 102 always rests on the entire surface of the slide support surface 122 during all relative movements.
  • the axial support surface 102 and the sliding support surface 122 cooperating therewith, as well as the carrier surface 114 and the sliding support surface 118 cooperating therewith, all lie radially within a coupling 164 having a plurality of coupling element sets 162, which are at equal radial distances from of the central axis 44 and at equal angular intervals in the circumferential direction U around the central axis 44 and together form a coupling 164 which prevents the second movable compressor body 26 from rotating itself.
  • each of these coupling element sets 162 comprises, as the first coupling element 172, a pin body 174 which has a cylindrical outer surface 176 and engages with this cylindrical outer 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 to one another.
  • This second coupling element 182 is guided in a third coupling element 192, which is provided as one in the carrier element 112
  • Recording 194 is formed for the ring body 184 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, the diameter DRI of the cylindrical
  • the inner surface 186 is larger than a diameter DSK of the cylindrical outer surface 176 of the pin body 174.
  • Each set of coupling elements 162 in turn forms an orbital guide, the maximum orbital radius OR of which corresponds to the orbiting movement 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 in each case one of the coupling element sets 162 is effective in order to prevent the self-rotation of the second movable compressor body 26, the effectiveness of each coupling element set 162 from one coupling element set 162 to the inside in six coupling element sets 162 after passing through an angular range of 60 ° Direction of rotation of the next clutch element set 162 changes.
  • Coupling element sets 162 improved, on the other hand improved the lubrication in the area of the same and furthermore also reduced the noise generation 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 are adequately lubricated, in particular lubrication between the cylindrical outer surface 176 of the pin body 174 and the cylindrical inner surface 186 of the annular body 184 and lubrication between the cylindrical outer surface 188 of the annular body 184 and the cylindrical inner wall surface 196 recording 194.
  • the clutch element sets 162 are the
  • Receptacles 194 in the carrier element 112 are open on both sides in the axial direction, the annular bodies 184 being held by a stop element 198 projecting radially inwards on their sides facing away from the second compressor body 26.
  • the compressor body base 36 is provided with star-shaped projections 212 which extend radially outwards and engage in spaces 214 between support fingers 92 which follow one another in a circumferential direction U about the central axis 44, so that the coupling elements 172 also lie in these spaces 214 and are thus arranged within the housing body 72 at the greatest possible radial distance from the central axis 44 (FIG. 7).
  • This positioning of the clutch element sets 162 predetermined by the greatest possible radial distance of the coupling elements 172 at a radial distance from the central axis 44 which is also as large as possible has the advantage that, due to the large lever arm, the forces acting on the clutch element sets 162 are kept as small as possible can be, which has an advantageous effect on the component dimensioning.
  • a lubricant bath 210 is formed in the compressor housing 12, in particular in the region of the first housing body 72, at a lowest point in the direction of gravity, from which lubricant emerges during operation
  • the movable compressor body 24 is driven (as shown in FIG. 2) 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 inside the stator 224, which is arranged on a drive shaft 228 which runs coaxially to the central axis 44 of the stationary compressor body 24.
  • 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 inside the stator 224, which is arranged on a drive shaft 228 which runs coaxially to the central axis 44 of the stationary compressor body 24.
  • the drive shaft 228 is mounted on the one hand in a bearing unit 232 facing the compressor, 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 located 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.
  • the drive shaft 228 drives the movable compressor body 26 via an eccentric drive, designated as a whole by 242, which moves orbiting around the central axis 44 of the stationary compressor body 24.
  • the eccentric drive 242 comprises, in particular, an eccentric drive pin 244 which is held in the drive shaft 228 and preferably fixedly inserted therein, which moves a driver 246 on the orbital track 48 about the central axis 44, which in turn is rotatably received by the eccentric drive pin 244 in a drive pin receptacle 247 is mounted in the driver 246 about an eccentric axis 245 on the eccentric drive pin 244 and is also mounted rotatably about the central axis 46 of the orbitally movable compressor body 26 in a rotary bearing 248, in particular a rolling element bearing designed as a fixed bearing, the rotary bearing 248 rotating the driver 246 relative to the orbitally movable compressor body 26 around the central axis 46, as shown in FIGS. 7 and 8.
  • the second compressor body 26 is provided with an integrated driver receptacle 249 which receives the rotary bearing 248.
  • the driver receptacle 249 is relative to the flat side 98 of the
  • the compressor body base 36 is reset and thus arranged integrated in the compressor body base 36, so that the driving forces acting on the movable compressor body 26 act 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 small tilting moment seen in the direction of the central axis 44, the axial guide 96 is axially supported on the axial support surface 102 between the driver receptacle 249 and the drive motor 222 and is movably guided transversely to the central axis 44.
  • the driver receptacle 249 as shown in FIGS.
  • the compressor orbital radius VOR is 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, can each move radially outward so far from the central axis 44 that the spiral ribs 34, 38 are in contact with one another at the point of contact 322 and seal the compression chambers 42 tightly.
  • the distance of the eccentric axis 245 from the central axis 44 of the stationary compressor body 24 is selected to be larger than the intended compressor orbital radius VOR, that is to say the distance between the central axes 44 and 46 from one another, and so large that the eccentric axis 245 extends outside of one through the two central axes 44 and 46
  • 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 from the movable compressor body 26 together with the mass of the driver 246 and the rotary bearing 248, on the other hand, whose center of gravity SOS lies in the central axis plane ME, and is also referred to as the mass balancing plane ME, since all the centers of gravity contributing to the best possible mass balancing should be close to or in this.
  • an orbital orbital balancing mass 252 (FIG. 10) is preferably also provided, which counteracts the unbalance caused by the unit 250 comprising the compressor body 26, driver 246 and rotary bearing 248 moving on the orbital orbital 48 and compensates them as far as possible, the
  • Orbital orbit balancing mass 252 with its center of gravity SOAGM is arranged as close as possible to the mass balancing plane ME, as shown in FIGS. 10 or 13 and 14.
  • the orbital orbital balancing mass 252 lies in particular on an eccentric drive journal 244 and the central axis 46,
  • the orbital orbit compensation 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 comprises a pin receptacle 256 which the eccentric drive pin 244 driving the driver 246 passes through in order to receive the bearing body 254 rotatably about the eccentric axis 245.
  • the guide body 254 is on an alignment surface 262 of the drive shaft 228 facing it, for example on the end face 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 running perpendicular to the central axis 44 of the drive shaft 228 266 slidably so that with all rotary movements about the eccentric axis 245 the parallel alignment of the guide body 254 to the alignment plane 266 is maintained and thus the orbital orbit balancing mass 252 moves on a track 268 around the drive shaft 228 which runs in a track plane 269 parallel to the alignment plane 266 (Fig. 10, 11).
  • Drive shaft 228 also largely avoided the transfer of tilting moments from the guide body 254 to the eccentric drive pin 244.
  • an axial guide 272 for the guide body 254 relative to the drive shaft 228 is provided, as shown in FIG. 11, which has a projection 274, for example a collar, arranged on the eccentric drive pin 244 , and which the guide body 254 against movement in Secures the direction of the central axis 44 away from the alignment surface 262 and, for this purpose, engages, for example, in a recess 276 which is different from the
  • a stop body 282 which is fixedly connected to the guide body 254 and arranged at a distance from the eccentric drive pin 244 engages in a recess 284 in the drive shaft 228, which extends from the end face 262 thereof into the drive shaft 228 and receives the stop body 282 with play and thus the guide body 254 limited turning work and the eccentric axis 245 relative to the drive shaft 228 allows.
  • the stop body 282 is preferably designed as the head of a coupling pin 292 which passes through the guide body 252 and is explained in more detail below and which in turn also interacts with the driver 246.
  • the coupling pin 292 is fixed to the
  • the coupling pin 292 passes through a receiving bore 288 in the guide body 254 and is fixed therein 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 the guide body 254 to be rotated relative to the eccentric drive axis 245, which is within an angular range of at least 2 ° (degree of angle) to a maximum of 4 ° (degree of angle), or better still a maximum of 6 ° (degree of angle), in order to enable tolerance compensation , wherein 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 most optimal possible orbital mass balancing takes place (FIG. 14).
  • the first movement limitation unit 280 is in particular like this
  • the unit 260 comprising the orbital orbit balancing mass 252 and the guide body 254, the orbital orbital balancing mass 252, so that a center of gravity SOAGM of the unit 260 comprising the orbital orbital balancing mass 252, the guide body 254 and the coupling pin 292 a coupling unit 300 on a side of the transverse plane QE opposite the eccentric pin 244 and within an unbalance tolerance range UWT which extends beyond the mass balancing plane ME and lies on both sides of the mass balancing plane ME in FIGS. 13 and 14, so that the possible unbalances are balanced tolerable measure are limited.
  • the unit 260 consisting of the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 with the center of gravity SOAGM brings about the best possible mass balancing with the unit 250 comprising the orbiting compressor body 26 with the rotary bearing 248 and the driver 246 with the center of mass SOS, if the mass center
  • the focus is on SOAGM and SOS 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, in particular at high speeds of the drive shaft 228.
  • the coupling pin 292 which is fixedly attached to the guide body 254, is designed as a mass compensation body (FIG. 8), and is arranged on the guide body 254 on a side of the mass balance plane ME opposite the eccentric drive pin 244 (FIG. 10) and thus leads with the eccentric drive pin 244 together in turn to form a mass distribution that is at least approximately symmetrical to the mass balancing plane ME.
  • a pin axis 294 of the coupling pin 292 and the eccentric axis 245 are preferably arranged mirror-symmetrically to the mass balancing plane ME, and the eccentric drive pin 244 and the coupling pin 292 preferably have approximately the same mass
  • the coupling unit 300 In order to have the possibility of a coupling between the orbital orbit balancing mass 252 and the driver 246, which can be rotated relative to the eccentric drive pin 244, the coupling unit 300 also has a pin axis 294 which forms a receptacle in addition to the coupling pin 292
  • the coupling pin 292 and the recess 296 are arranged relative to one another in such a way that the coupling pin 292 bears against a partial region 304 of an inner wall surface 298 of the recess 296 lying in the direction of rotation D can, which gives the possibility of the centrifugal force FZsos of the unit 250 formed from the
  • Centrifugal force FZsos counteracts, since the unit 260 from the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 296 strives to rotate its center of gravity SOAGM in the direction of rotation D about the eccentric axis 245 (and consequently to move away from the mass balancing plane ME) while the centrifugal force FZsos causes the unit 250 comprising the orbiting compressor body 26, the driver 246 and the rotary bearing 248 to move counter to the direction of rotation D about the eccentric axis 245 (FIG. 16).
  • the unit 260 comprising the orbital orbit compensation mass 252, the guide body 254 and the coupling pin 292 with its center of gravity SOAGM on a side of the transverse plane opposite the center of mass SOS QE lies and has the tendency to rotate in the direction of rotation D about the eccentric axis 245 (FIG. 16).
  • Coupling pin 292 acts - as shown in FIG. 16 - in the partial area 304, with respect to the eccentric axis 245, a torque generated by the force FDSOAGM on the driver 246, which acts on the driver 246 due to the centrifugal force FZsos
  • Eccentric axis 245 related torque 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 means that the center of gravity SOAGM in the centrifugal force coupling state is close to, or preferably in, the mass balancing plane ME on a side of the center axis 44 opposite the center of mass SOS , and thus the essentially optimal mass balance to the unit 250 comprising the orbiting compressor body 26, the driver 246 and the rotary bearing 248.
  • the coupling unit 300 is decoupled from centrifugal force 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 there is no contact between the coupling pin 292 and the
  • an as The whole, designated 332 is a speed-dependent positioning device for determining or releasing the rotational positions of the unit 260 from the orbital orbit compensation 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 a
  • 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 formed on the circumference and forms a guide surface 342, along which a positioning body 344 is movably guided 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.
  • a force acts on the positioning body 344 through the spring 346, 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 can thus be moved in a direction radially to the central axis 44 in a direction opposite to the force of the spring 346 from a position lying against the radially inner stop 352 into a position lying against the radially outer stop 348.
  • the spring 346 is dimensioned such that at low speeds of the drive shaft 228 the positioning body 344 bears against the radially inner stop 352 and moves away from it with increasing speed and bears against the radially outer stop 348 from a defined switching speed, as shown in FIG 17 and 15 is shown.
  • the positioning body 344 is preferably provided with a positioning surface 354 which runs obliquely to the central axis 334 and in the simplest case has a course which tapers conically to the central axis 334 in the direction of the radially inner stop 352.
  • the positioning surface 354 of the positioning body 344 is used for
  • 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 (FIGS. 15, 17 and 19).
  • the positioning surface 354 acts on the actuating body 358 with its region that is radially outer in relation to the central axis 334 and places it thereby the unit 260 made of orbital orbit 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 gravity SOAGM is at a distance from the mass balance plane ME. Furthermore, in this rotational position, 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 composed of orbital track compensation mass 252, guide body 254 and coupling pin 292 from the unit 250 from the orbiting compressor body 26, the driver 246 and the rotary bearing 248 is in the state decoupled from centrifugal force, and the center of mass SOS of this unit 250 generates the speed-dependent centrifugal force FZsos (FIGS. 17 and 18) lying in the mass balancing plane ME.
  • the unit 250 thus develops the full centrifugal force FZsos from the orbiting compressor body 26, the driver 246 and the rotary bearing 248 at low speeds in the sense of an increase in the compressor orbital radius VOR which together with the force FC to the contact force in the
  • Positioning body 344 is moved outwards by the centrifugal force increasing with the speed radially to the central axis 44 against the force of the spring 346 and finally abuts the radially outer stop 348, causes the positioning surface 354 to move increasingly radially outwards and thus releases the actuating body 358 that the unit 260 is relative to the
  • the coupling unit 300 is in the centrifugal force coupling state in which the unit 260 comprising the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 in the manner already described of the centrifugal force FZsos counteracts and reduces this (Fig. 16).
  • the solution according to the invention thus makes it possible to operate the compressor in such a way that the coupling unit 300 is in the centrifugal force decoupling state at low speeds and thus the unit 250, comprising the orbitally movable compressor body 26, the driver 246 and the rotary bearing 248 with their full centrifugal force FZsos is effective, so that this centrifugal force FZsos together with the force FC caused by the eccentric drive 242 on the orbitally movable
  • Compressor body 26 acting force FA acts on the contact point 322 of the spiral ribs 34, 38 and thus holds the spiral ribs 34, 38 in contact with the contact point 322 in order to achieve the tightest possible seal between them.
  • FA centrifugal force
  • the solution according to the invention thus creates the advantage, starting from low speeds, at very low speeds in the first

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

Abstract

L'invention concerne un compresseur comprenant un carter (12) de compresseur, un ensemble compresseur à spirale (22) agencé dans le carter (12) de compresseur et muni d'un premier corps de compresseur fixe (24) et d'un second corps de compresseur (26) mobile par rapport au corps de compresseur fixe (24), un entraînement excentrique (242) de l'ensemble compresseur à spirale (22) comportant un entraîneur (246) entraîné par un moteur d'entraînement (222) et tournant autour de l'axe médian (44) d'un arbre d'entraînement (228) sur la trajectoire orbitale (48), et un contrepoids (252) de trajectoire orbitale agissant à l'encontre d'un balourd provoqué par le déplacement du corps de compresseur (26) sur la trajectoire orbitale (48). L'invention vise à améliorer ledit compresseur de manière à pouvoir garantir la stabilité à long terme du guidage de l'entraîneur (246) dans le logement d'entraîneur, même à des vitesses de rotation élevées. À cet effet, le contrepoids (252) de trajectoire orbitale est couplé à l'entraînement excentrique (242) de telle manière qu'il se déplace en fonction du déplacement de l'entraîneur (246) sur la trajectoire orbitale (48), mais en est découplé eu égard à la transmission des couples de basculement à l'entraîneur, et l'entraîneur et le contrepoids orbital peuvent agir à l'état de couplage de la force centrifuge et à l'état de découplage de la force centrifuge.
PCT/EP2018/066799 2018-06-22 2018-06-22 Compresseur à spirale muni d'un contrepoids de trajectoire orbitale découplable WO2019242865A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201880093478.XA CN112119218B (zh) 2018-06-22 2018-06-22 具有可解耦的轨道平衡块的螺旋式压气机
PCT/EP2018/066799 WO2019242865A1 (fr) 2018-06-22 2018-06-22 Compresseur à spirale muni d'un contrepoids de trajectoire orbitale découplable
EP18737172.9A EP3810935B1 (fr) 2018-06-22 2018-06-22 Compresseur à spirale muni d'un contrepoids de trajectoire orbitale découplable

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
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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WO2019242865A1 true WO2019242865A1 (fr) 2019-12-26

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EP (1) EP3810935B1 (fr)
CN (1) CN112119218B (fr)
WO (1) WO2019242865A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09195957A (ja) * 1996-01-17 1997-07-29 Nippon Soken Inc スクロール型圧縮機
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
WO2018019372A1 (fr) 2016-07-27 2018-02-01 Bitzer Kühlmaschinenbau Gmbh Compresseur

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5496157A (en) * 1994-12-21 1996-03-05 Carrier Corporation Reverse rotation prevention for scroll compressors
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

Patent Citations (3)

* Cited by examiner, † Cited by third party
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
JPH09195957A (ja) * 1996-01-17 1997-07-29 Nippon Soken Inc スクロール型圧縮機
WO2018019372A1 (fr) 2016-07-27 2018-02-01 Bitzer Kühlmaschinenbau Gmbh Compresseur

Also Published As

Publication number Publication date
EP3810935B1 (fr) 2023-11-29
EP3810935A1 (fr) 2021-04-28
CN112119218A (zh) 2020-12-22
CN112119218B (zh) 2023-01-06

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