Scroll compressor having axial guide support

Abstract

To be as lightweight and compact, for example for automotive technology, a scroll compressor further includes an axial guide that supports the movable compressor body to prevent movements in the direction parallel to a centre axis of the stationary compressor body and, in the event of movements, guides it in the direction transverse to the centre axis. A coupling prevents the movable compressor body from rotating freely. The axial guide supports a compressor body base, which carries the scroll vane, of the second compressor body against an axial support face, in that the axial support face abuts a sliding body such that it is slidable transversely to the centre axis. The sliding body is slidable transversely to the centre axis, on a carrier element that is arranged in the compressor housing.

Claims

1. A compressor, including a compressor housing, a scroll compressor unit that is arranged in the compressor housing and has a first, stationary compressor body and a second compressor body that is movable in relation to the stationary compressor body, whereof first and second scroll vanes, in the shape of a circle involute, engage in one another to form compressor chambers when the second compressor body is moved in relation to the first compressor body on an orbital path, an axial guide that supports the movable compressor body to prevent movements in a direction parallel to a centre axis of the stationary compressor body and, in an event of movements, guides it in a direction transverse to the centre axis, a drive motor that drives an eccentric drive for the scroll compressor unit, wherein the eccentric drive has an entrainer that is driven by the drive motor, that revolves on a path about a central axis of a drive shaft and that cooperates with an entrainer receptacle in the second compressor body, and a coupling that prevents the second compressor body from rotating freely, the coupling that prevents free rotation has at least two coupling element sets that include at least two coupling elements, one of the coupling elements is held on a compressor body base of the second compressor body, one of the coupling elements is formed by a pin body, wherein one of the coupling elements takes the form of a cylindrical receptacle, the compressor body base of the second compressor body is provided with pockets that have openings facing the cylindrical receptacles of the coupling element sets, wherein the openings in the pockets are positionable to overlap in each case with two cylindrical receptacles that are arranged succeeding one another in the peripheral direction.

2. The compressor according to claim 1, wherein one of the coupling elements is held on the carrier unit.

3. The compressor according to claim 1, wherein the coupling that prevents free rotation has more than two coupling element sets.

4. The compressor according to claim 1, wherein the coupling element sets are arranged at equal angular spacings around the centre axis of the orbital path.

5. The compressor according to claim 1, wherein one of the coupling elements takes the form of an annular body arranged in the cylindrical receptacle.

6. The compressor according to claim 5, wherein the annular body is seated in the cylindrical receptacle loosely.

7. The compressor of claim 1, wherein the axial guide supports the compressor body base, which carries the scroll vane, of the second compressor body against an axial support face, in that the axial support face abuts a sliding body such that the axial support face is slidable transversely to the centre axis, the sliding body for its part being supported, such that the sliding body is slidable transversely to the centre axis, on a carrier element that is arranged in the compressor housing.

8. A compressor, including a compressor housing, a scroll compressor unit that is arranged in the compressor housing and has a first, stationary compressor body and a second compressor body that is movable in relation to the stationary compressor body, whereof first and second scroll vanes, in the shape of a circle involute, engage in one another to form compressor chambers when the second compressor body is moved in relation to the first compressor body on an orbital path, an axial guide that supports the movable compressor body to prevent movements in a direction parallel to a centre axis of the stationary compressor body and, in an event of movements, guides it in a direction transverse to the centre axis, a drive motor that drives an eccentric drive for the scroll compressor unit, wherein the eccentric drive has an entrainer that is driven by the drive motor, that revolves on a path about a central axis of a drive shaft and that cooperates with an entrainer receptacle in the second compressor body, and a coupling that prevents the second compressor body from rotating freely, the coupling that prevents free rotation has at least two coupling element sets that include at least two coupling elements, one of the coupling elements is held on a compressor body base of the second compressor body, one of the coupling elements is formed by a pin body, wherein one of the coupling elements takes the form of a cylindrical receptacle, the compressor body base of the second compressor body is provided with pockets that have openings facing the cylindrical receptacles of the coupling element sets, wherein the axial guide supports the compressor body base, which carries the scroll vane, of the second compressor body against an axial support face, in that the axial support face abuts a sliding body such that the axial support face is slidable transversely to the centre axis, the sliding body for its part being supported, such that the sliding body is slidable transversely to the centre axis, on a carrier element that is arranged in the compressor housing, wherein the axial support face is supported on an annular face of the sliding body that surrounds the centre axis.

9. The compressor according to claim 1, wherein the sliding body is movable in two dimensions, in relation to the compressor body base and in relation to the carrier element.

10. The compressor according to claim 1, wherein the sliding body is movably guided in a two-dimensional guidance with play in relation to at least one of the compressor body base and the carrier element.

11. The compressor according to claim 1, wherein the axial guide supports the second compressor body against an axial support face that is formed by the latter such that the second compressor body is slidable transversely in relation to the centre axis, and the axial support face is formed by the compressor body base of the second compressor body that carries the scroll vane.

12. A compressor, including a compressor housing, a scroll compressor unit that is arranged in the compressor housing and has a first, stationary compressor body and a second compressor body that is movable in relation to the stationary compressor body, whereof first and second scroll vanes, in the shape of a circle involute, engage in one another to form compressor chambers when the second compressor body is moved in relation to the first compressor body on an orbital path, an axial guide that supports the movable compressor body to prevent movements in a direction parallel to a centre axis of the stationary compressor body and, in an event of movements, guides it in a direction transverse to the centre axis, a drive motor that drives an eccentric drive for the scroll compressor unit, wherein the eccentric drive has an entrainer that is driven by the drive motor, that revolves on a path about a central axis of a drive shaft and that cooperates with an entrainer receptacle in the second compressor body, and a coupling that prevents the second compressor body from rotating freely, the coupling that prevents free rotation has at least two coupling element sets that include at least two coupling elements, one of the coupling elements is held on a compressor body base of the second compressor body, one of the coupling elements is formed by a pin body, wherein one of the coupling elements takes the form of a cylindrical receptacle, the compressor body base of the second compressor body is provided with pockets that have openings facing the cylindrical receptacles of the coupling element sets, wherein the axial guide supports the second compressor body against an axial support face that is formed by the latter such that second compressor body is slidable transversely in relation to the centre axis, and the axial support face is formed by a compressor body base of the second compressor body that carries the scroll vane, wherein the axial support face abuts a sliding body such that the axial support face is slidable transversely to the centre axis, and wherein the axial support face is supported on an annular face of the sliding body that surrounds the centre axis.

13. The compressor according to claim 1, wherein the entrainer receptacle is integrated in the compressor body base of the second compressor body.

14. The compressor according to claim 13, wherein the entrainer receptacle is arranged on the compressor body base of the second compressor body such that the entrainer receptacle does not project beyond an axial support face of the second compressor body in the direction parallel to the centre axis.

15. The compressor according to claim 1, wherein the centre axis of the stationary compressor body extends in a level disposition.

16. The compressor according to claim 1, wherein the drive shaft of the drive motor extends in a level disposition.

17. The compressor according to claim 1, wherein the compressor housing is made from an aluminum alloy.

18. A compressor, including a compressor housing, a scroll compressor unit that is arranged in the compressor housing and has a first, stationary compressor body and a second compressor body that is movable in relation to the stationary compressor body, whereof first and second scroll vanes, in the shape of a circle involute, engage in one another to form compressor chambers when the second compressor body is moved in relation to the first compressor body on an orbital path, an axial guide that supports the movable compressor body to prevent movements in a direction parallel to a centre axis of the stationary compressor body and, in an event of movements, guides it in a direction transverse to the centre axis, a drive motor that drives an eccentric drive for the scroll compressor unit, wherein the eccentric drive has an entrainer that is driven by the drive motor, that revolves on a path about a central axis of a drive shaft and that cooperates with an entrainer receptacle in the second compressor body, and a coupling that prevents the second compressor body from rotating freely, the coupling that prevents free rotation has at least two coupling element sets that include at least two coupling elements, one of the coupling elements is held on a compressor body base of the second compressor body, a first coupling element of the coupling element sets is formed by a pin body having a cylindrical outer surface, said first coupling element of the coupling element sets engages a second coupling element of the coupling element sets formed by an annular body, said annular body having a cylindrical internal face engaged by said pin body and a cylindrical external face, said cylindrical external face engaging a cylindrical internal wall of a third coupling element of the coupling element sets which takes the form of a cylindrical receptacle, a diameter of the cylindrical internal face of the annular body being greater than a diameter of the cylindrical outer surface of the pin body and a diameter of the cylindrical internal wall of the cylindrical receptacle is greater than a diameter of the cylindrical external face of the annular body, such that the annular body is seated in the cylindrical receptacle loosely.

19. The compressor according, to claim 18 wherein the compressor body base of the second compressor body is provided with pockets that have openings facing the cylindrical receptacles of the coupling element sets.

20. The compressor according to claim 19, wherein the openings in the pockets are positionable to overlap in each case with two cylindrical receptacles that are arranged succeeding one another in the peripheral direction.

21. The compressor according to claim 18, wherein one of the coupling elements is held on the carrier unit.

22. The compressor according to claim 18, wherein the coupling that prevents free rotation has more than two coupling element sets.

23. The compressor according to claim 18, wherein the coupling element sets are arranged at equal angular spacings around the centre axis of the orbital path.

24. The compressor according to claim 18 wherein the second coupling element has the cylindrical internal face coaxially arranged with respect to its cylindrical external face.

25. The compressor according to claim 18 wherein the second coupling element defines an internal hole, wherein a central axis of the cylindrical receptacle intersects and passes axially through the internal hole.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 shows a perspective illustration of a compressor according to the invention;

(2) FIG. 2 shows a longitudinal section through the compressor according to the invention, in a plane of section extending through a centre axis of a stationary compressor body;

(3) FIG. 3 shows a cross section through a scroll compressor unit, in the region of the mutually engaging scroll vanes, and an illustration of an orbital path of the movable scroll vane in relation to the stationary scroll vane;

(4) FIG. 4 shows a longitudinal section according to FIG. 2 on a larger scale, in the region of the movable compressor body and an axial guide for the movable compressor body;

(5) FIG. 5 shows a section on an even larger scale, through a partial region of the axial guide, in the region of guidance with play for a sliding body of the axial guide;

(6) FIG. 6 shows a plan view of the axial guide, with the sliding body and a carrier element that carries the latter;

(7) FIG. 7 shows a perspective illustration of the axial guide, together with coupling elements of a coupling for preventing it from rotating freely, including a plurality of coupling element sets;

(8) FIG. 8 shows a plan view of a flat side of the movable compressor body, opposite the scroll vane;

(9) FIG. 9 to FIG. 14 show a schematic illustration of the cooperation between the coupling element sets of the coupling that prevents free rotation;

(10) FIG. 15 shows a section along the line 15-15 in FIG. 4; and

(11) FIG. 16 shows a section along the line 16-16 in FIG. 15.

DETAILED DESCRIPTION OF THE INVENTION

(12) An exemplary embodiment illustrated in FIG. 1, of a compressor according to the invention which is designated 10 as a whole, and is for a gaseous medium, in particular a refrigerant, includes a compressor housing which is designated 12 as a whole and has a first end housing portion 14, a second end housing portion 16 and an intermediate portion 18 arranged between the end housing portions 14 and 16.

(13) As illustrated in FIG. 2, provided in the first housing portion 14 is a scroll compressor unit which is designated 22 as a whole and has a first compressor body 24, which is arranged to be stationary in the compressor housing 12, in particular in the first housing portion 14, and a second compressor body 26, which is movable in relation to the stationary compressor body 24.

(14) The first compressor body 24 includes a compressor body base 32 surmounted by a first scroll vane 34, and the second compressor body 26 likewise includes a compressor body base 36 surmounted by a second scroll vane 38.

(15) The compressor bodies 24 and 26 are arranged in relation to one another such that the scroll vanes 34, 38 engage in one another in order to form between them, as illustrated in FIG. 3, at least one and preferably a plurality of compressor chambers 42 in which the gaseous medium, for example refrigerant, is compressed in that the second compressor body 26 moves with its centre axis 46 about a centre axis 44 of the first compressor body 24 on an orbital path 48 having a compressor orbital path radius VOR, wherein the volume of the compressor chambers 42 decreases and ultimately compressed gaseous medium emerges through a central outlet 52, while gaseous medium to be drawn in is drawn in on the radially outer side in relation to the centre axis 44, through peripherally opening compressor chambers.

(16) The compressor chambers 42 are also sealed off from one another in particular in that the scroll vanes 34, 38 are provided on their end side with axial sealing elements 54 and 58 respectively, which abut sealingly against the respective bottom face 62, 64 of the respectively other compressor body 26, 24, wherein the bottom faces 62, 64 are formed by the respective compressor body base 36 and 32 respectively and lie in a plane extending perpendicular to the centre axis 46.

(17) The scroll compressor unit 22 is received as a whole in a first housing body 72 of the compressor housing 12, wherein this housing body 72 has an end cover portion 74 and a cylindrical annular portion 76 that is integrally formed in one piece with the end cover portion 74 and for its part engages by means of an annular projection 78 in an end bushing 82 of a central housing body 84 that forms the intermediate portion 18, wherein the central housing body 84 is terminated at a side opposite the first housing body 72 by a second housing body 86 that forms an inlet chamber 88 for the gaseous medium.

(18) Here, by means of the cylindrical annular portion 76, the first housing body 72 surrounds a receptacle 92 for the scroll compressor unit 22, and this receptacle has a bearing face 94 for the compressor body base 32 of the first compressor body 24.

(19) In particular, the first compressor body 24 is immovably fixed in the receptacle 92 in a manner preventing any movement parallel to the bearing face 94.

(20) In this way, the first compressor body 24 is fixed within the first housing body 72 and thus also within the compressor housing 12 such that it is stationary in a precisely defined position.

(21) The second, movable compressor body 26, which has to move on the orbital path 48 about the centre axis 44 in relation to the first compressor body 24, is guided in relation to the centre axis 44 in the axial direction by an axial guide, which is designated 96 as a whole and supports and guides the compressor body base 36 at a flat side 98 remote from the scroll vane 38, in the region of an axial support face 102, such that the compressor body base 36 of the second compressor body 26 is supported, in relation to the first compressor body 24 that is positioned stationary in the compressor housing 12, and in the direction parallel to the centre axis 44, such that the axial sealing elements 58 remain against the bottom face 64 and do not lift away therefrom, wherein at the same time the compressor body base 36 can move with the axial support face 102 such that it can slide transversely to the centre axis 44 in relation to the axial guide 96.

(22) For this purpose, as illustrated in FIG. 4, the axial guide 96 is formed by a carrier element 112, which is made in particular from an open-pored sintered material and has a carrier face 114 that faces the axial support face 102 but on which the compressor body base 36 does not lie by means of the axial support face 102, but rather on which there lies a sliding body 116, in particular plate-like and designated 116 as a whole, having a sliding bearing face 118, wherein the sliding body 116 guides the axial support face 102 in a manner supported by means of a sliding support face 122 opposing the sliding bearing face 118, to prevent movements parallel to the centre axis 44, but supported such that it is slidable in respect of movements transverse to the centre axis 44.

(23) In this way, an axial movement of the second compressor body 26 in the direction of the centre axis 44 is prevented, but a movement in a plane transverse, in particular perpendicular, to the centre axis 44 is made possible.

(24) Here, the axial guide 96 according to the present invention provides, in the event of a movement of the second compressor body 26 on the orbital path 48 about the centre axis 44 of the first compressor body 24, on the one hand for the second compressor body 26 to move with the compressor body base 36 and the axial support face 102 thereof in relation to the sliding body 116, and on the other hand for the sliding body 116 itself to move in relation to the carrier element 112.

(25) In this way, sliding takes place between the compressor body base 36 and the sliding body 116 as a result of a movement of the axial support face 102 in relation to the sliding support face 122 of the sliding body 116, and moreover the sliding bearing face 118 of the sliding body 116 slides in relation to the carrier face 114 of the carrier element 112.

(26) To improve lubrication, for example the sliding support face 122 and the sliding bearing face 118 of the sliding body 116 are provided with recesses 123, in particular micro-recesses, which form receptacles for a lubricant and contribute to distribution of the lubricant, as illustrated by way of example in FIG. 6 in conjunction with the sliding support face 122.

(27) In order to predetermine the limited two-dimensional movability of the sliding body 116 in relation to the carrier element 112 and parallel to a plane E perpendicular to the centre axis 44, the sliding body 116 is guided in relation to the carrier element 112 by a guidance with play which is designated 132 as a whole, wherein the guidance with play 132 includes a guide cutout 134 that is provided in the sliding body 116 and has a diameter DF, and also includes a guide pin 136 that is anchored in the carrier element 112 and whereof the diameter DS is smaller than the diameter DF, with the result that half of the difference DF-DS defines a guide orbital radius FOR by means of which the sliding body 116 can perform an orbital movement in relation to the carrier element 112.

(28) In order to ensure that a sufficient film of lubricant is formed between the axial support face 102 of the compressor body base 36 and the sliding support face 122 of the sliding body 116, and between the carrier face 114 and the sliding bearing face 118, the carrier element 112 is provided with radially outward pockets 142 that extend below an outer edge region 144 of the sliding body 116 and thus facilitate the access of lubricant into an intermediate space 146 between the carrier face 114 and the sliding bearing face 118.

(29) Further, because of the movement of the sliding body 116 with the guide orbital radius FOR in relation to the carrier element 112, the intermediate space 146 is filled with a film of lubricant 147 in a manner similar to the mode of operation of a hydrodynamic bearing.

(30) For a stable film of lubricant 147, it is sufficient if the guide orbital radius FOR is 0.01 times the compressor orbital radius VOR or more, in particular 0.05 times the compressor orbital radius VOR or more.

(31) In particular, the guide orbital radius FOR is 0.3 times the compressor orbital radius VOR or less, or, better, 0.2 times the compressor orbital radius VOR or less.

(32) Further, as a result of the fact that the carrier element 112 is made, at least in the region of the carrier face 114, from an open-pored sintered material, in addition improved lubrication is ensured in that lubricant enters the pores of the carrier element 112 and is thus retained in the region of the carrier face 114 for the purpose of forming the film of lubricant 147 in the intermediate space 146, by way of the pores of the carrier element 112.

(33) The formation of the film of lubricant 147 in the intermediate space is additionally assisted by the fact that the sliding body 116 itself takes the form of a plate-like annular part and made of spring steel, and so the sliding bearing face 118 facing the carrier face 114 creates a smooth surface of spring steel.

(34) Further, the pairing of materials made from open-pored sintered material, which is softer in the region of the carrier face 114 than spring steel, and the spring steel in the region of the sliding bearing face 118 has advantageous properties when used over the long term, because of the resistance to wear.

(35) In order furthermore to ensure that a film 149 of lubricant is formed in an intermediate space 148 between the sliding support face 122 and the axial support face 102, the compressor body base 36 is provided, in a radially outward and a radially inward region 152, with an edge surface 154 that extends inclined to the axial support face 102, is set back in relation to the axial support face 102 and, together with the sliding bearing face 122, results in an intermediate space 158 that opens radially outwardly or radially inwardly in the shape of a wedge and facilitates the access of lubricant to the intermediate space 148.

(36) As illustrated in FIGS. 4, 6, 7 and 8, the axial support face 102 and the sliding support face 122 cooperating therewith and the carrier face 114 and the sliding bearing face 118 cooperating therewith are all arranged radially outwardly of a plurality of coupling element sets 162, which are arranged at the same radial spacings from the centre axis 44 and at the same angular spacings peripherally around the centre axis 44, and together form a coupling 164 that prevents the second, movable compressor body 26 from rotating freely.

(37) Each of these coupling element sets 162 includes, as illustrated in FIGS. 4 and 6 to 8, as the first coupling element 172 a pin body 174 that has a cylindrical surface 176 and, by means of this cylindrical surface 176, engages in a second coupling element 182.

(38) The second coupling element 182 is formed by an annular body 184 that has a cylindrical internal face 186 and a cylindrical external face 188, which are arranged coaxially to one another.

(39) This second coupling element 182 is guided in a third coupling element 192, which takes the form of a receptacle 194, provided in the carrier element 112, for the annular body 184 and has a cylindrical internal wall surface 196. As shown in FIG. 9, the second coupling element 182 defines an internal hole 183, wherein a central axis 185 of the cylindrical receptacle 194 intersects and passes axially through the internal hole 183.

(40) Here, in particular a diameter DI of the internal wall surface 196 is greater than a diameter DRA of the cylindrical external face 188 of the annular body 184, and a diameter DRI of the cylindrical internal face 186 is necessarily smaller than the diameter DRA of the cylindrical external face 188 of the annular body 184, wherein moreover the diameter DRI of the cylindrical internal face 186 is greater than a diameter DSK of the cylindrical superficial face 176 of the pin body 174.

(41) In this way, each coupling element set 162 forms a separate orbital guide, whereof the maximum orbital radius OR for the orbital movement corresponds to DI/2-(DRA-DRI)-DSK/2.

(42) By dimensioning the orbital radius OR of the coupling element sets 162 such that it is slightly greater than the compressor orbital radius VOR, defined by the compressor bodies 24 and 26 of the scroll compressor unit 22, the movable compressor body 26 is guided in relation to the stationary compressor body 24 by the coupling 164 such that, as illustrated in FIGS. 9 to 14, in each case one of the coupling element sets 162 acts to prevent free rotation of the second, movable compressor body 26, wherein, for example if there are six coupling element sets 162, after an angular range of 60° has been covered, the action of each coupling element set 162 changes from one coupling element set 162 to the succeeding coupling element set 162 in the direction of rotation.

(43) Because each coupling element set 162 has three coupling elements 172, 182 and 192, and in particular an annular body 184 acts between the respective pin body 174 and the respective receptacle 194, on the one hand the resistance to wear of the coupling element sets 162 is improved and on the other the lubrication in the region thereof is improved, and moreover the development of noise in the coupling element sets 162, produced by the change in action from one coupling element set 162 to the next coupling element set 162, is also reduced.

(44) Here, it is in particular essential that the coupling element sets 162 are given sufficient lubrication, in particular lubrication between the cylindrical superficial face 176 of the pin body 174 and the cylindrical internal face 186 of the annular body 184, and lubrication between the cylindrical external face 188 of the annular body 184 and the cylindrical internal wall surface 196 of the receptacle 194.

(45) One possibility provides for the coupling element sets 162 to pass through the sliding body 116, in particular for the pin bodies 174 to pass through openings 198 (FIG. 7) in the sliding body 116, as a result of which lubricant from the lubricant films 147 and 149 can be supplied to the coupling element sets 162.

(46) In order to assist lubrication, as illustrated in FIGS. 8 and 15, there are provided in the compressor body base 36, between the bores 202 receiving the first coupling elements 172, pockets 204 which have, in the flat side 98 that delimits the compressor body base 36, an opening 206 which has an angular extent in relation to the centre axis 46 of the compressor body base 36 such that, as illustrated in FIG. 15, they can overlap in individual rotational positions with two receptacles 194 of the coupling element sets 162 that succeed one another in the direction of rotation, with the result that the pockets 204 are in a position to perform an exchange of lubricant between successive coupling element sets 162 and thus to enable a uniform supply of lubricant to all the coupling element sets 162.

(47) Preferably, the pockets 204 are arranged such that they extend on either side of a geometric arc 208 about the centre axis 46 which bisects the bores 202 in order always to achieve optimum overlap with the receptacles 194.

(48) The concept according to the invention, of lubrication of the axial guide 96 and the coupling element sets 162, is particularly advantageous if in the normal case the centre axes 44 and 46 of the compressor bodies 24 and 26 extend in a level position, that is to say at an angle of at most 30° to the horizontal, in which case there is formed in the compressor housing 12, in particular in the region of the first housing body 72, at the lowest point with respect to the direction of gravity, a bath 210 of lubricant out of which lubricant swirls up during operation and in so doing is received and distributed in the manner described.

(49) The movable compressor body 24 is driven by a drive motor which is designated 212 as a whole and which has in particular a stator 214 that is held in the central housing body 84 and a rotor 216 that is arranged within the stator 214 and is arranged on a drive shaft 218 that extends coaxially in relation to the centre axis 44 of the stationary compressor body 24.

(50) The drive shaft 218 is mounted on the one hand in a bearing unit 222 that is arranged between the drive motor 212 and the scroll compressor unit 22 and in the central housing body 84, and on the other in a bearing unit 224 that is arranged on an opposite side of the drive motor 212 to the bearing unit 222.

(51) Here, the bearing unit 224 is mounted for example in the second housing body 86, which closes off the central housing body 84 on an opposite side to the first housing body 72.

(52) Medium that is drawn in here, in particular the refrigerant, flows from the inlet chamber 88 formed by the second housing body 86 and through the electric motor 212 in the direction of the bearing unit 222, flows around the latter and then flows in the direction of the scroll compressor unit 22.

(53) By way of an eccentric drive which is designated 232 as a whole, the drive shaft 218 drives the movable compressor body 26, which moves in an orbit around the centre axis 44 of the stationary compressor body 24.

(54) The eccentric drive 232 in particular includes an eccentric pin 234 that is held in the drive shaft 218 and moves an entrainer 236 on an orbital path around the centre axis 44, the entrainer 236 being mounted rotatably on the eccentric pin 234 and itself being mounted rotatably in a pivot bearing 238, wherein the pivot bearing 238 allows the entrainer 236 to rotate in relation to the movable compressor body 26.

(55) The entrainer 236 is rotatable to a limited extent in relation to the eccentric pin 234 and in relation to the entrainer receptacle 242, and enables the radius of the orbital movement of the movable compressor body 26 to be adapted so that the scroll vanes 34 and 38 are kept bearing against one another.

(56) For receiving the pivot bearing 238, as illustrated in FIGS. 2, 4 and 16, the second compressor body 26 is provided with an entrainer receptacle 242 that receives the pivot bearing 238.

(57) The entrainer receptacle 242 is in this case set back in relation to the flat side 98 of the compressor body base 36 and is thus arranged in a manner integrated within the compressor body base 36, with the result that the drive 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 scroll vane 38 and thus drive the movable compressor body 26 with a small moment of tilt, the movable compressor body 26 being supported axially against the axial support face 102 by the axial guide 96, between the entrainer receptacle 242 and the electric motor 212 as seen in the direction of the centre axis 44, and guided movably in a direction transverse to the centre axis 44.