EP3491245A1 - Compresseur - Google Patents

Compresseur

Info

Publication number
EP3491245A1
EP3491245A1 EP16748088.8A EP16748088A EP3491245A1 EP 3491245 A1 EP3491245 A1 EP 3491245A1 EP 16748088 A EP16748088 A EP 16748088A EP 3491245 A1 EP3491245 A1 EP 3491245A1
Authority
EP
European Patent Office
Prior art keywords
compressor
compressor according
pin
drive shaft
driver
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP16748088.8A
Other languages
German (de)
English (en)
Other versions
EP3491245B1 (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
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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 Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Publication of EP3491245A1 publication Critical patent/EP3491245A1/fr
Application granted granted Critical
Publication of EP3491245B1 publication Critical patent/EP3491245B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/02—Rotary-piston machines or pumps 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
    • F04C2/025—Rotary-piston machines or pumps 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 the moving and the stationary member having co-operating elements in spiral form
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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

Definitions

  • the invention relates to a compressor, comprising a compressor housing, a arranged in the compressor housing volute compressor unit with a first, stationary compressor body and a second, movable relative to the stationary compressor body movable compressor body, which formed in the form of a Kreisvolvente first and second spiral ribs mesh to form compressor chambers when the second compressor body is moved relative to the first compressor body on an orbital track, an axial guide which moves the movable one
  • Compressor body against movements in the direction parallel to a central axis of the stationarily arranged compressor body is supported and at
  • a drive motor for such a compressor can be operated variable in number of revolutions, for example by means of an inverter, or at a constant speed.
  • these compressors is - especially at high speeds, which may be, for example, more than 6,000 revolutions per minute - the problem that the leadership of the driver in the driver receiving, has low long-term stability, especially if in the driver receiving a roller bearing, such as a cylindrical roller bearing, the Storage of the driver is provided.
  • the invention is therefore an object of the invention to improve a compressor of the generic type such that even at high speeds, the long-term stability of the leadership of the driver can be ensured in the driver seat.
  • Movement of the driver moves on the orbital track, but is decoupled with respect to the transmission of tilting moments on the driver.
  • the solution according to the invention is therefore based on the knowledge unknown from the prior art that in the known solutions with a rigid connection of the driver and Orbitalbahnaus GmbHsmasse at high speeds the Orbitalbahnaus GmbHsmasse with high tilting moments acts on the driver and thus the storage of the driver in the driver , Especially if this is done by a roller bearing, such as a cylindrical roller bearing, is exposed to high wear, since such bearings are exposed to occurring tilting moments increased wear.
  • the solution of the invention now solves the problem existing in the known solutions of acting on the driver with overturning orbital trajectory compensation by decoupling the driver of the Orbitalbahnaus GmbHsmasse such that it can no longer act with significant tilting moments on the driver. With regard to the guidance of the Orbitalbahnaus GmbHsmasse no further details were given.
  • a particularly simple and structurally favorable solution provides that the Orbitalbahnaus GmbHsmasse is guided by a force acting between the driver and the drive shaft eccentric drive pin on the orbital track.
  • the object mentioned in the present invention is also achieved in that the orbital path compensation mass engages with a guide body on the eccentric drive pin, in particular is rotatably mounted on this.
  • the guide body is firmly connected to the Orbitalbahnaus GmbHsmasse. It is particularly favorable if the eccentric drive pin passes through a pin receptacle of the guide body.
  • a structurally particularly favorable solution provides that the orbital track compensation mass is guided on the drive shaft by means of a guide body cooperating with the drive shaft.
  • the action of the eccentric drive pin on the guide body essentially serves to move the guide body with the orbital track balancing mass so that the orbital track balancing mass follows the orbital track of the driver and produces the required mass balance.
  • the orbital path compensation mass prefferably be guided by the guide body acting on the drive shaft on a path which runs in a web plane which runs parallel to an alignment plane extending perpendicular to the center axis of the drive shaft.
  • the leadership 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 and also with regard to the leadership of the guide body stable solution provides that the provided on the drive shaft alignment surface is an end face of the drive shaft.
  • the guide body can be optimally supported on the alignment surface when the guide body is arranged over the alignment surface.
  • the guide body is plate-shaped, that is to say in the direction of the center axes, a dimension which is as small as possible transversely to the central axis, relative to its extent.
  • the guide body is guided relative to the drive shaft by an axial guide.
  • the axial guide is designed so that this
  • Guide surface of the guide body holds in contact with the alignment surface of the drive shaft to ensure a sufficiently precise guidance of the guide body and thus the Orbitalbahnaus GmbHsmasse relative to the drive shaft.
  • the axial guide can be designed in different ways.
  • the axial guide is formed so that it is a guide body on one of the guide surface opposite side
  • Such an element may be formed in a variety of ways.
  • the element is a screw head of an engaging in the drive shaft screw.
  • Another solution provides that the element is a retaining ring fixed relative to the drive.
  • a further advantageous solution provides that the element is a projection arranged on the eccentric drive pin.
  • the axial guidance can be achieved by means of a screw engaging on the drive shaft and / or a collar on the eccentric drive pin and / or a pin formed on the drive shaft
  • the guide body and the orbital track compensation mass are able to align relative to the eccentric drive pin in accordance with the respective imbalance. Furthermore, in order to make it possible for the guide body and the orbital track compensation mass to be able to align relative to the eccentric drive pin in accordance with the respective imbalance, it is preferably provided that the guide body is rotatable to a limited extent relative to the eccentric drive pin.
  • Tailored on the orbital track generated unbalance to counteract this as well as possible.
  • a first movement limiting unit is preferably effective between the drive shaft and the guide body, which allows a limited free rotation of the guide body about the eccentric pin axis.
  • the limited free rotation is in the range of 0.5 ° (angular degree) to 5 °, preferably in the range of 1 ° to 3 °.
  • the movement limiting unit can be realized by independent elements.
  • a particularly advantageous solution provides, however, that the movement limiting unit is realized by the elements of the axial guide, so that the axial guide on the one hand causes the movement of the guide body in the axial direction, that is, in the direction of the central axes of either the drive shaft or the second movable compressor body and on the other hand simultaneously serves as a movement limiting unit.
  • the eccentric drive pin and the drive pin receptacle cooperate in a contact region which is penetrated by a median plane which is perpendicular to the central axis of the movable second compressor body and in the direction of the central axis of a centrally acting between the second compressor body and the driver pivot bearing runs for the driver and that there is a gap between the eccentric drive pin and the drive pin receptacle on both sides of the contact area.
  • the position of the median plane can also be defined by the fact that it runs centrally perpendicular to the eccentric pin axis and in the direction of the eccentric pin axis through the pivot bearing for the driver.
  • eccentric drive pin and the drive pin receiving cooperate in a central portion of the drive pin receiving, wherein in particular the central portion is defined by the fact that it is penetrated by the median plane.
  • the drive pin receptacle in the central portion has a smaller diameter, than in both sides of the central portion lying and each forming a gap end portions of the drive pin receptacle.
  • the central portion of the drive pin receiving a maximum of half, more preferably more than a third, the extension of the drive pin receiving in the direction of
  • the end sections arranged on both sides of the central section differ by a maximum of a factor of 2 in terms of their extent in the direction of the eccentric pin axis.
  • Eccentric drive pin acts on the drive pin receiving, is located as close to the center plane.
  • Orbitalbahnaus provides a particularly favorable solution that the Orbitalbahnaus GmbHsmasse is coupled by means of a coupling body with the driver for rotational drive by the driver in a rotational movement of the same about the Exzenterantriebszapfen.
  • the coupling body is preferably arranged fixed to one of the guide body and driver and engages in a recess in the other of the guide body and driver.
  • the coupling body is arranged with play in the recess.
  • the coupling body and the recess are arranged so that the coupling body abuts in normal operation of the compressor to a portion of a wall surface of the recess and consequently without an overdetermined positioning of the coupling body and
  • the coupling body is designed as a coupling pin with which can be realized in a simple manner the connection for rotational drive between the Orbitalbahnaus GmbHsmasse and the driver.
  • an advantageous development of the solution according to the invention provides that the coupling pin is fixedly arranged on the guide body and engages in the recess in the driver.
  • the coupling pin and the recess cooperate in a contact area, which is penetrated by a median plane perpendicular to the pin axis of the coupling pin and in the direction of the coupling pin centered between the second compressor body and the driver effective pivot bearing for the driver runs, and that there is a gap between the coupling pin and the recess on both sides of the contact region.
  • the coupling pin and the recess cooperate in a central portion of the recess. This can be realized, for example, simply by the fact that the
  • Recess in the central portion has a smaller diameter than in the lying on either side of the central portion and each forming a gap end portions of the recess.
  • the central portion of the recess extends over a maximum of half the extent of the recess in the direction of the pin axis.
  • the end sections arranged on both sides of the central section differ by a maximum of a factor of 2 in terms of their extent in the direction of the journal axis.
  • the eccentric drive has the eccentric driving pin driving the driver and a coupling body coupling the orbital track compensation mass to the driver.
  • the coupling body also represents a mass balancing body.
  • the conditional by the Exzenterantriebszapfen and asymmetric to the mass balance level unbalance of the Exzenterantriebszapfen can compensate in a simple manner and thus improve the smoothness of the compressor.
  • an advantageous solution that the Exzenterantriebszapfen and the coupling body are arranged on opposite sides of a mass balance plane to compensate in addition to the coupling of the Orbitalbahnaus concurssmasse with the driver even the conditional by the Exzenterantriebszapfen unbalance and to improve the smoothness.
  • an advantageous solution provides that the mass balance plane through the central axis of the drive shaft and the central axis of the orbiting
  • movable compressor body runs through and is precisely defined by these two central axes in their position and orientation.
  • the coupling body has a mass which deviates from the mass of the eccentric drive spigot by a maximum of 20%, more preferably a maximum of 10% in order to achieve the greatest possible compensation of the imbalance caused by the eccentric drive spigot ,
  • the coupling body is designed as a mass balance pin.
  • a pin axis of the mass balance pin is arranged at the same distance from the mass balance plane, such as an eccentric pin axis of the eccentric drive pin.
  • the pin axis of the mass balance pin runs essentially parallel, preferably parallel, to the eccentric drive axis of the eccentric pin.
  • the pin axis of the mass balance pin and the eccentric pin axis of the eccentric pin extend parallel to the mass balance plane.
  • the mass balance pin on the drive shaft or on the driver.
  • a particularly favorable solution provides that the mass balance pin is held on the guide body of the Orbitalbahnaus GmbHsmasse and thus moved with this and is aligned relative to the Exzenterantriebszapfen.
  • the mass balance body as a mass balance pin is further preferably provided that the mass balance pin engages in the recess provided in the driver.
  • the orbital track compensation mass described above is arranged symmetrically to the mass balance plane and thus does not cause unbalanced imbalance to the mass balance plane.
  • a particularly favorable solution further provides that the orbital track compensation mass is arranged on a side of the eccentric drive pin and the mass balance body opposite a perpendicular to the mass balance plane and extending through the central axis of the drive shaft geometric transverse plane.
  • the drive shaft has a section facing the compressor, which faces a compressor
  • Imbalance compensation mass and the eccentric drive pin carries and in particular the mass balance body and the Orbitalbahnausrete leads.
  • the imbalance compensation mass is arranged between a rotor of the drive motor and a front bearing unit on the drive shaft.
  • Compressor facing away portion which carries a compressor imposing imbalance compensation mass. Also in this imbalance compensation mass is preferably provided that this is arranged between the rotor of the drive motor and a rear bearing unit of the drive shaft.
  • these imbalance compensation masses which are arranged on the drive shaft, that they are also formed and arranged symmetrically to the mass balance plane.
  • Fig. 1 is a perspective view of a first embodiment of a compressor according to the invention
  • Fig. 2 is a longitudinal section along line 2-2 in Fig. 4;
  • FIG. 3 is a schematic illustration of interdigitated spiral ribs and the orbital motion 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 is an enlarged view of a region A in FIG. 5;
  • Fig. 7 is a section along line 7-7 in Fig. 2; 8 is an exploded view of a cooperation between an eccentric drive pin of an orbital path compensation mass and a driver in the compressor according to the invention;
  • Figure 10 is a plan view of a guide body with the Orbitalbahnaus GmbHsmasse in its position on the drive shaft with the guide body by cross-eccentric drive pin.
  • FIG. 11 is an enlarged section along line 11-11 in FIG. 4;
  • Fig. 12 is a section along line 12-12 in Fig. 11 only with
  • FIG. 13 is a section similar to FIG. 12 when the first movement limitation unit is active;
  • FIG. 14 shows a section along line 14-14 in the region of a cam receiver of the movable compressor body with a driver in FIG. 11 in the position according to FIG. 12;
  • FIG. 15 shows a section similar to FIG. 14 in the position according to FIG. 13;
  • 16 is an enlarged section along line 16-16 in FIG. 4 by one
  • Fig. 17 is a side view of a drive shaft with that of this
  • FIG. 19 shows a section similar to FIG. 11 through a third embodiment of a compressor according to the invention
  • Fig. 20 is a section similar to Fig. 11 by a fourth embodiment of a compressor according to the invention.
  • FIG. 1 shows a compressor according to the invention designated as a whole by 10 for a gaseous medium, in particular a refrigerant, comprising a compressor housing designated as a whole by 12, which has a first end housing section 14, a second end housing section 16 and between the end housing sections 14 and 16 arranged intermediate portion 18 has.
  • a spiral compressor unit 22 which has a first one in the compressor housing 12, in particular in the first
  • Housing portion 14 stationary arranged compressor body 24 and a second relative to the stationary arranged compressor body 24 movable compressor body 26 has.
  • 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 above which a second spiral rib 38 rises.
  • the compressor bodies 24 and 26 are arranged relative to one another such that the spiral ribs 34, 38 engage in one another, as shown in FIG. 3, between at least one, preferably a plurality of compressor chambers 42 to form, in which a compression of the gaseous medium, for example of refrigerant, takes place in that the second compressor body 26 with its center axis 46 is moved about a central axis 44 of the first compressor body 24 on an orbital path 48 having a compressor orbital trajectory VOR, wherein the volume of the compression chambers 42 is reduced and ultimately compressed gaseous medium exits through a central outlet 52 (FIG. 2) while gaseous medium being aspirated is sucked radially outwardly relative to the central axis 44 by circumferentially opening compressor chambers 42.
  • a compression of the gaseous medium for example of refrigerant
  • the sealing of the compression chambers 42 relative to each other also takes place, in particular, in that the spiral ribs 34, 38 are provided at the end with axial sealing elements 54 and 58 which abut sealingly 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 and 32 and lie in a plane perpendicular to the central axis 44, respectively.
  • the spiral compressor unit 22 is accommodated as a whole in a first housing body 72 of the compressor housing 12, which has a front-side cover portion 74 and a front side cover portion 74 integrally formed cylindrical annular portion 76, which in turn engages with a ring projection in a sleeve body 82 of the housing body 72, the a central housing body 84 forming the intermediate section 18 is formed, wherein the central housing body 84 is 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, whose first compressor body 24 is connected to the compressor body base 32
  • the first compressor body 24 is fixed immovably in the housing body 72 against all movements parallel to the support surface 94.
  • the first compressor body 24 is fixed within the first housing body 72 and thus also within the compressor housing 12 in a precisely defined position stationary.
  • Compressor housing 12 positioned first compressor body 24 and is supported in the direction parallel to the central axis 44 such that the Axialêtlemente 58 remain on the bottom surface 64 and not lift from this, while the compressor body base 36 with the Axialstütz construction 102 transversely to the central axis 44 slidably relative to the axial guide 96 can move ( Figures 2 and 4).
  • the axial guide 96 is formed by a carrier element 112 which has a carrier surface 114 facing the axial support surface 102 (FIGS. 2, 5) but on which the compressor body base 36 does not rest with the axial support surface 102 on which a slider plate 116, which is designated as a whole by 116 and in particular plate-shaped, rests with a sliding support surface 118, wherein the sliding body 116 with one of the sliding support surface 118 opposite Gleitstütz requirements 122 ( Figures 2 and 5), the Axialstütz requirements 102 ( Figures 2 and 4) against movements but supported slidably with respect to movements transverse to the central axis 44 leads. This prevents an axial movement of the second compressor body 26 in the direction of the central axis 44, a movement in a plane transversely,
  • the axial guide 96 provides that upon movement of the second compressor body 26 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 the Axialstützamide 102 moves relative to the slider 116 On the other hand, on the other hand, the sliding body 116 in turn moves relative to the support member 118.
  • the sliding body 116 is provided by a device shown in FIG. 5 and 6 shown and designated as a whole with 132 guide with play relative to the support member 112, wherein the guide with game 132 includes a sliding body 116 provided in the guide recess 134 which includes a
  • Diameter DF as well as an anchored in the support member 112 guide pin 136 whose diameter DS is smaller than the diameter DF, so that half of the difference DF-DS defines a predominantlysorbitalradius with which the slider 116 is an orbiting movement relative to the support member 112th can perform.
  • the movements of the slider 116 is a structure of a
  • 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 area of the carrier surface 114, in addition, improved lubrication is ensured by lubricant entering the pores of the carrier element 112 and thus via the surface structures of the carrier element 112 in FIG Area of the support surface 114 is available for the construction of the lubricating film in the intermediate space.
  • the sliding body 116 itself is formed as a plate-shaped, annular part made of spring steel and thus the support surface 114 facing the sliding support surface 118 is a smooth Federstahlober Chemistry, the formation of the lubricating film is additionally promoted.
  • the support member 112 is not only provided with the support surface 114 on which the slider 116 rests, but also with the support surfaces 94 on which the support fingers 92 of the first compressor body 24 are supported. This makes it possible to determine the position of the first compressor body 24 and the position of the second compressor body 26 in the direction of the central axis 44 relative to each other by suitable design of the support member 112, in particular by a single surface of the support member 112, which both the support surface 114 as also includes the bearing surfaces 94 takes place.
  • the support member 112 is further arranged both axially in the direction of the central axis 44 and against rotational movements about the central axis 44 fixed in the housing body 72.
  • the compressor body base 36 is recessed in a radially inward edge region 152 and in a radially outward edge region 154 having a tapered relative to the axial support surface 102 and opposed to the axial support surface 102 Edge surface 156 and 158 provided, which leads together with the Gleitauflage Structure 122 to a wedge-shaped radially outwardly or radially inwardly opening gap, which facilitates the access of lubricant.
  • the structure of the lubricating film between the Gleitstütz configuration 122 and the Axialstschreib structure 102 is promoted by the fact that the Gleitstschreib construction 122 and the Axialstschreib construction 102, in the overlap region in which they cooperate as contiguous, that is in the direction of rotation U order the central axis and in their entire radial extent uninterrupted annular surfaces 124 and 126 are formed, wherein in particular the annular surface 126 of the AxialstNeill requirements 102 extends from an inner contour IK with a radius IR thereof up to an outer contour AK, wherein the radius IR less than two-thirds of an outer radius AR.
  • annular surface 124 of the Gleitstschreib structure 122 is dimensioned so that the annular surface 126 of the Axialstschreib materials 102 always rests fully on all relative movements to the Gleitstschreib structure 122 on this.
  • the Axialstütz requirements 102 and the cooperating with this Gleitstütz phenomenon 122 and the support surface 114 and the cooperating Gleitauflage requirements 118 are all radially within a plurality of coupling element sets 162 having coupling 164, which at equal radial distances from the central axis 44 and at equal angular intervals in the circumferential direction U are arranged about the central axis 44 and together form a coupling 164, which prevents a self-rotation of the second movable compressor body 26.
  • Each of these coupling element sets 162 comprises, as shown in FIGS. 2, 6 and 7, as a first coupling element 172 a pin body 174, which has a cylindrical outer 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 having a cylindrical inner surface 186 and a cylindrical outer surface 188 which are coaxial with each other.
  • This second coupling element 182 is guided in a third coupling element 192, which is provided as one provided in the carrier element 112
  • Receiving 194 is formed for the annular body 184 and which has a cylindrical inner wall surface 196.
  • a diameter DI of the inner wall surface 196 is greater than a diameter DRA of the cylindrical outer surface 188 of the annular body 184 and a diameter DRI of the cylindrical inner surface 186 inevitably smaller than the diameter DRA of the cylindrical outer surfaces 188 of the annular body 184, wherein also 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 174th
  • each coupling element set 162 in turn forms an orbital guide whose maximum orbital radius OR for the orbital motion 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 each case one of the coupling element sets 162 is effective to prevent the self-rotation of the second movable compressor body 26, wherein, for example, with six coupling element sets 162 after passing through an angular range of 60 °, the effectiveness of each coupling element set 162 of a coupling element set 162 to the coupling element set next in the direction of rotation 162nd replaced.
  • Recording 194 is effective, on the one hand, the wear resistance of
  • Improved coupling element sets 162 on the other hand, the lubrication improved in the same area and also reduces the noise generated by the coupling element sets 162, which results from the change of effectiveness of a coupling element set 162 to the other coupling element set 162. It is particularly essential that the coupling element sets 162 undergo sufficient lubrication, in particular lubrication between the cylindrical 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 196th the recording 194.
  • the compressor body base 36 is provided with star-shaped projections 212 extending radially outwards, which engage in intermediate spaces 214 between supporting fingers 92 which follow each other in a direction of rotation U about the center axis 44, so that the coupling elements 172 likewise engage in these Gaps 214 are located and thus within the housing body 72 in the largest possible radial distance from the central axis 44 are arranged (Fig. 7).
  • This predetermined by the greatest possible radial distance of the coupling elements 172 positioning the coupling element sets 162 in a radial distance as possible from the central axis 44 has the advantage that due to the large lever arm acting on the coupling element sets 162 forces can be kept as small as possible , which has a positive effect on the component dimensioning.
  • the inventive concept of the lubrication of the axial guide 96 and the coupling element sets 162 is particularly advantageous if the center axes 44 and 46 of the compressor body 24 and 26 lying normally, that is a maximum of an angle of 30 ° to a horizontal run, in the compressor housing 12, in particular in the region of the first housing body 72 at a lowermost position in the direction of gravity lubricant bath 210 forms, from the lubricant in operation
  • the drive of the movable compressor body 24 is effected (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 disposed on a drive shaft 228 which is coaxial with 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 disposed on a drive shaft 228 which is coaxial with the central axis 44 of the stationary compressor body 24.
  • the drive shaft 228 is mounted on the one hand in a compressor-facing bearing unit 232 arranged between the drive motor 222 and the spiral 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 on a side of the drive motor 222 opposite the bearing unit 232
  • the compressor-remote storage unit 234 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 side. Of the inlet chamber 88 formed by the second housing body 86 thereby sucked medium, in particular the refrigerant flows through the
  • the drive shaft 228 drives the movable compressor body 26 via an eccentric drive indicated 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 held in the drive shaft 228, which moves a carrier 246 on the orbital path 48 about the central axis 44, which in turn rotatably engages about an eccentric pin axis 245 in a drive journal receptacle 247 in the driver 246 by rotatably receiving the eccentric drive pin 244 the eccentric drive pin 244 is mounted and also rotatably about the central axis 46 of the orbiting movable compressor body 26 rotatably mounted in a pivot bearing 248, in particular designed as a fixed bearing Wälz redesignowski, wherein the pivot bearing 248, a rotation of the driver 246 relative to the orbiting movable compressor body 26 to the Center axis 46 allowed, as shown in FIG. 7 and 8 shown.
  • the second compressor body 26 For receiving the pivot bearing 248, as shown in FIGS. 11, the second compressor body 26 is provided with an integrated catch receptacle 249 which receives the pivot 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 forces acting on the movable compressor body 26 driving forces on one of the spiral rib 38 side facing the Flat side 98 of the compressor body base 36 are effective and thus drive with low tilting moment the movable compressor body 26, viewed axially through the axial guide 96 in the direction of the central axis 44 between the Mit Menume 249 and the drive motor 222 on the Axialstütz construction 102 and guided transversely to the central axis 44 movable is.
  • the cam receiver 249 as shown in FIGS. 2 and 11 surrounded by the radial direction to the central axis 46 outer Axialstützamide 102 and the AxialstNeillamide 102 is in turn of the radial direction to the central axis 44 outer coupling element sets 162 of the self-rotation surrounded by the second compressor body 26 preventing coupling 164.
  • 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, is variably adjustable, so that the movable one
  • Compressor body 26, and thus also the central axis 46, each so far away from the central axis 44 can move away radially outwardly that the spiral ribs 34, 38 abut each other and the compressor chambers 42 close tight.
  • the distance of the eccentric pin axis 245 from the central axis 44 of the stationary compressor body 24 is greater than the intended Verêtrorbitalradius VOR, that is, the distance of the center axes 44 and 46 from each other, and so large that the eccentric pin axis 245 outside of a through the two center axes 44th and 46 through
  • Compressor body 26 radially to the central axis 44 outwardly moving force FC leads, in the through the central axis 44 and the central axis 46th
  • the center axis ME defined by the central axes 44 and 46 represents a plane of symmetry to a system formed by the mass of the drive shaft 228 and the mass of the movable compressor body 26 together with the mass of the driver 246 and is also referred to as the mass balance plane ME.
  • an orbital path compensation mass 252 is additionally provided, which is the imbalance by the on the orbital path 48
  • moving compressor body 26 counteracts and this as possible
  • the orbital path compensation mass 252 is formed and arranged symmetrically to the mass balance plane ME, as shown in Fig. 10.
  • the orbital path compensation mass 252 lies, in particular, on a side of the eccentric drive pin 244 facing away from a perpendicular to the mass balance plane ME and through the central axis 44 extending transverse plane QE.
  • the orbital path compensation mass 252 is not held on the driver 246 but is mounted with a guide body 254 on the drive shaft 228, in particular on the eccentric drive pin 244.
  • the guide body 254 comprises a pin receptacle 256 which passes through the eccentric drive pin 244 in order to rotatably receive the bearing body 254 about the eccentric pin axis 245.
  • the guide body 254 is slidably guided on an alignment surface 262 of the drive shaft 224 facing the alignment surface 262 on a guide surface 264 of the guide body 254 facing the alignment surface 262 parallel to an alignment plane 266 running perpendicular to the center axis 44 of the drive shaft 228 on an alignment surface 266 facing the drive shaft 228, so that during all rotational movements about the eccentric pin axis 245, the parallel alignment of the guide body 245 to the alignment plane 266 is maintained and thus the orbital path compensation mass 252 moves on a path 268 about the drive shaft 228, which runs in a parallel to the alignment plane 266 web plane 269.
  • an axial guide 272 is provided for the guide body 254 relative to the drive shaft 228, which is formed in a first embodiment as a screw 274 having a recess or an opening 276 of the guide body 254 with a Shank portion 278 interspersed, with a Threaded portion 282 in line with the central axis 44 coaxial threaded bore 284 engages in the drive shaft 228 and with a screw head 286 the opening 276 on a driver 246 facing side 287 of the guide body 254 overlaps the guide body 254 by means of the guide surface 264 in contact with the alignment surface 262nd to keep.
  • the opening 276 is dimensioned so large that a limited relative movement of the guide body 254 to the screw 274 and thus also a limited relative rotation of the unit of orbital track balancing mass 252 and guide body 254 about the eccentric pin axis
  • the recess or opening 276 and the shaft portion 278 of the screw 274 form a first movement limiting unit 288 for the relative movement of the guide body 254 to the drive shaft 228.
  • the movement limiting unit 288 preferably allows relative rotation of the guide body 254 relative to the eccentric drive pin axis
  • rotatable driver 246 is provided as a coupling body, a coupling pin 292 which is fixedly arranged on the guide body 254.
  • the driver 246 is provided with a recess 296 which receives the coupling pin 292 with play, thereby rotating the driver 246 about the eccentric pin axis 245 to
  • the coupling pin 292 and the recess 296 are arranged so that the coupling pin 292 rests in normal operation on a front lying in the direction of rotation portion of an inner wall surface 298 of the recess 296.
  • the mass not taken into account in the mass balance described above is the mass of the eccentric drive pin 244, which is arranged asymmetrically with respect to the mass balance plane ME and in particular leads to oscillations at high rotational speeds of the drive shaft 228.
  • eccentric drive pin 244 in addition to the engaging in the drive shaft 228 eccentric drive pin 244 still arranged on the guide body 254 coupling pin 292 as mass balance body (Fig. 8), which is arranged on the guide body 254 on a the Exzenterantriebszapfen 244 opposite side of the mass balance plane ME (Fig. 10) and thus together with the eccentric drive pin 244 in turn leads to a mass balance plane ME at least approximately symmetrical mass distribution.
  • a trunnion axis 294 of the coupling pin 292 and the eccentric pin axis 245 are arranged mirror-symmetrically with respect to the mass balance plane ME, and also preferably the eccentric drive pin 244 and the coupling pin 292 have approximately the same mass (FIG. 10).
  • the fixation of the coupling pin 292 takes place at the
  • Guide body 254 characterized in that the coupling pin 292 passes through a receiving bore 312 in the guide body 254 and is fixed in this by a press fit.
  • the coupling pin 292 is still provided with a head 314 which rests on a side of the guide body 254 facing away from the driver 246 (FIG. 16).
  • the drive shaft 228 is still provided with a compressor-facing imbalance compensation mass 322 and a compressor imbalance compensation mass 324 (FIGS. 2 and 17).
  • the compressor-facing imbalance compensation mass 322 is preferably between the drive motor 222 and the compressor-facing bearing unit 232 on a compressor-facing portion 326 of the drive shaft 228 and radially within winding heads 332 of a stator winding
  • the compressor imbalance balancing mass 324 is preferably located on a compressor facing away portion 328 of the drive shaft 228 and between the drive motor 222 and the compressor facing away from storage unit 234, as well as radially within winding heads 334 of the stator winding.
  • the axial guide 272 'for the guide body 254 is formed by a pin 342 integrally formed on the drive shaft 228, which engages with a shaft portion 344 the opening 276 of the guide body 254 and a securing ring 346 carries, which the aperture 276 is arranged radially overlapping on the driver 246 side facing 287 and thus the guide body 254 in the same manner as the screw head 286 positioned so that the guide surface 264 is held on the alignment surface 262 in abutment.
  • the shaft portion 344 also cooperates with the aperture 276 and forms the first movement limiting unit 288 '.
  • the first movement limiting unit 288 is further formed by the head 314 of the mass balance pin 292, which mates with play in an end recess or recess 362 in the drive shaft 228.
  • the relative dimension of the head 314 and the recess 362 limited rotation of the guide body 254 relative to the drive shaft 228 set.
  • the central portion 372 has an extension in the direction of the eccentric pin axis 245 which corresponds to a maximum of half, more preferably a maximum of one third of the extension of Antrisbszapfenage in this direction.
  • End sections 382 and 384 of the drive pin receptacle 247 '' whose diameter is greater than that of the middle section 372 and which extend in the direction of the eccentric pin axis 245 approximately with the same extent, which means that in particular the end sections 382, 384, are arranged on both sides of the middle section 372 differ by less than a factor of 2 in their extension, so that in the region thereof in each case a gap 386, 388 between the end portions 382 and 384 and the eccentric drive pin 244 remains.
  • the eccentric drive pin 244 acts in this embodiment, the driver 246 only in the central portion 372 and thus only in the region of the median plane 374, so that thereby the pivot bearing 248 by the action of the Exzenterantriebszapfens 244 and the driver 246 experiences no tilting moments.
  • Coupling pin 292 formed so that the coupling pin 292 in a central portion 392 of the extension 296 '' 'acts on this, wherein the central portion 392 has a similar or comparable extent in the direction of the pin axis 294 as the central portion 372 of the drive pin receptacle 247' '.
  • both sides of the central portion 392 end portions 394 and 396 of the recess 296 '' are provided, whose diameter is greater than that of the central portion 392, so that also between the
  • End sections 394 and 396 column 402 and 404 form.
  • end portions 394 and 396 extend in the direction of the journal axis 294 approximately the same extent as the end portions 382 and 384, so that relative to the central portion 392 are the same relations as between the central portion 372 and the end portions 382 and 384th
  • the coupling pin 292 acts in this embodiment, the driver 246 also only in the central portion 392 and thus only in the region of the median plane 374, so that by the coupling pin 292 also no overturning moment acts on the driver 246.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'objet de l'invention est d'améliorer un compresseur comprenant un carter, une unité compresseur à spirales qui est agencée dans le carter de compresseur et qui est pourvue d'un premier corps de compresseur monté fixe et d'un deuxième corps de compresseur mobile par rapport au corps de compresseur monté fixe, un entraînement excentrique pour l'unité compresseur à spirales, lequel comporte un entraîneur entraîné par un moteur d'entraînement et tournant autour de l'axe médian d'un arbre d'entraînement sur la trajectoire orbitale, un contrepoids de trajectoire orbitale agissant à l'encontre d'un balourd provoqué par le déplacement du corps de compresseur sur la trajectoire orbitale, de manière à pouvoir garantir la stabilité à long terme du guidage de l'entraîneur dans le logement de ce dernier, y compris à des vitesses élevées. À cet effet, selon l'invention, le contrepoids de trajectoire orbitale est accouplé à l'entraînement excentrique de manière à se déplacer en fonction du mouvement de l'entraîneur sur la trajectoire orbitale, mais est découplé en ce qui concerne la transmission des couples de renversement à l'entraîneur.
EP16748088.8A 2016-07-27 2016-07-27 Compresseur Active EP3491245B1 (fr)

Applications Claiming Priority (1)

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PCT/EP2016/067943 WO2018019372A1 (fr) 2016-07-27 2016-07-27 Compresseur

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EP3491245A1 true EP3491245A1 (fr) 2019-06-05
EP3491245B1 EP3491245B1 (fr) 2024-03-27

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Publication number Priority date Publication date Assignee Title
CN112119218B (zh) 2018-06-22 2023-01-06 比泽尔制冷设备有限公司 具有可解耦的轨道平衡块的螺旋式压气机
JP2020165394A (ja) * 2019-03-29 2020-10-08 株式会社豊田自動織機 スクロール型電動圧縮機
DE102020133438A1 (de) 2020-12-14 2022-06-15 Bitzer Kühlmaschinenbau Gmbh Scrollmaschine, insbesondere Scrollkompressor oder -expander und Kälteanlage
EP4083374A3 (fr) * 2021-04-28 2022-11-16 Dabir Surfaces, Inc. Pompe é spirales avec coupleur moteur flottant
DE102022120679A1 (de) 2022-08-16 2024-02-22 Bitzer Kühlmaschinenbau Gmbh Scrollmaschine und Kälteanlage
DE102022120678A1 (de) 2022-08-16 2024-02-22 Bitzer Kühlmaschinenbau Gmbh Scrollmaschine mit Einspritzung sowie Kälteanlageollmaschine mit Einspritzung sowie Kälteanlage
DE102022120681A1 (de) 2022-08-16 2024-02-22 Bitzer Kühlmaschinenbau Gmbh Scrollmaschine und Kälteanlage

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JPS5819875B2 (ja) * 1980-03-18 1983-04-20 サンデン株式会社 スクロ−ル型圧縮機
JPH063192B2 (ja) * 1982-12-08 1994-01-12 三菱電機株式会社 スクロ−ル圧縮機
JPS59126096A (ja) * 1982-12-29 1984-07-20 Toyoda Autom Loom Works Ltd スクロ−ル型圧縮機における回転スクロ−ル部材の駆動機構
AU587222B2 (en) * 1985-01-28 1989-08-10 Sanden Corporation Drive system for the orbiting scroll of a scroll type fluid compressor
JPS61250393A (ja) * 1985-04-26 1986-11-07 Shin Meiwa Ind Co Ltd スクロール形オイルフリー式真空ポンプ
US5104302A (en) * 1991-02-04 1992-04-14 Tecumseh Products Company Scroll compressor including drive pin and roller assembly having sliding wedge member
US5366357A (en) * 1992-02-28 1994-11-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Scroll type compressor having a counterweight mounted with a clearance on a driveshaft
US5366360A (en) * 1993-11-12 1994-11-22 General Motors Corporation Axial positioning limit pin for scroll compressor
JP3781460B2 (ja) * 1995-03-17 2006-05-31 株式会社デンソー スクロール型圧縮機
JPH11182461A (ja) * 1997-12-15 1999-07-06 Sanden Corp スクロール型圧縮機
JP2014214702A (ja) * 2013-04-26 2014-11-17 三菱電機株式会社 スクロール圧縮機

Also Published As

Publication number Publication date
US20190170139A1 (en) 2019-06-06
CN109312745A (zh) 2019-02-05
EP3491245B1 (fr) 2024-03-27
CN109312745B (zh) 2020-12-01
WO2018019372A1 (fr) 2018-02-01
US11326593B2 (en) 2022-05-10

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