Compressor

Abstract

A compressor comprising a compressor housing (12), a scroll compressor unit (22) arranged in the compressor housing (12) with a first, stationary compressor body (24) and a second compressor body (26) movable relative to the stationary compressor body (24), the first and second spiral ribs (34, 38) of which are designed in the form of a circular involute and engage with one another to form compressor chambers (42) when the second compressor body (26) is moved relative to the first compressor body (24) on an orbital path (48), an axial guide (96) which supports the movable compressor body (26) against movements in a direction parallel to a central axis (44) of the stationary compressor body (24) and guides it during movements in a direction transverse to the central axis (44), an eccentric drive (242) for the scroll compressor unit (22),which has a driver (246) driven by the drive motor (222) and rotating on the orbital path (48) around the central axis (44) of a drive shaft (228), which in turn cooperates with a driver receptacle (282) of the second compressor body (26), and a coupling (164) preventing self-rotation of the second compressor body (26), wherein the eccentric drive (242) has an eccentric drive pin (244) driving the driver (246) and a mass balancing body (254), and wherein the eccentric drive pin (244) and the mass balancing body (254) are arranged on opposite sides of a mass balancing plane (ME), characterized in that the mass balancing body is designed as a mass balancing pin (254), that the mass balancing pin (254) is an element of a movement limiting unit (264) for the driver (246) is.,

Description

[0001] The invention relates to a compressor comprising a compressor housing, a scroll compressor unit arranged in the compressor housing with a first, stationary compressor body and a second compressor body movable relative to the stationary compressor body, the first and second spiral ribs of which are designed in the form of a circular involute interlocking to form compressor 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 a direction parallel to a central axis of the stationary compressor body and guides it during movements in a direction transverse to the central axis, a drive motor which drives an eccentric drive for the scroll compressor unit, which has a driver which is driven by the drive motor and rotates on the orbital path around the central axis of a drive shaft,which in turn cooperates with a driver receptacle of the second compressor body, and a coupling preventing self-rotation of the second compressor body, wherein the eccentric drive has an eccentric drive pin driving the driver and a mass balancing body, and wherein the eccentric drive pin and the mass balancing body are arranged on opposite sides of a mass balancing plane.

[0002] Such compressors are known from DE 199 53 690 A1. In these compressors, mass balancing is achieved by mass balancing bodies arranged on opposite sides of the drive shaft and on the same side of the drive shaft. This poses the problem of achieving the smoothest possible operation.

[0003] The invention is based on the object of further improving the smooth running of a compressor of the type described above.

[0004] This object is achieved according to the invention in a compressor of the type described at the outset in that the mass balancing body is designed as a mass balancing pin and that the mass balancing pin is an element of a movement limiting unit for the driver.

[0005] The advantage of the solution according to the invention is that the use of the mass balancing body makes it possible to compensate in a simple manner for the imbalance caused by the eccentric drive pin and, in particular, for the imbalance which is asymmetrical to the mass balancing plane, and that, with regard to the mass distribution, conditions as similar as possible to those of the eccentric drive pin are created.

[0006] No further details were given in this context regarding the course of the mass balance plane.

[0007] It is preferably provided that the mass balance plane runs through the center axis of the drive shaft and the center axis of the orbiting compressor body, and thus these two center axes are precisely defined in their position and orientation.

[0008] In order to achieve the smoothest possible running, it is preferably provided that the mass balancing body has a mass that deviates by a maximum of 20%, even better a maximum of 10%, from the mass of the eccentric drive pin in order to achieve the greatest possible compensation for the imbalance caused by the eccentric drive pin.

[0009] It is particularly advantageous if the mass balancing body has essentially the same mass, in particular the same mass, as the eccentric drive pin.

[0010] With regard to the arrangement of the pin axes of the mass balance pin and the eccentric drive pin, it is preferably provided that a pin axis of the mass balance pin is arranged at the same distance from the mass balance plane as an eccentric pin axis of the eccentric drive pin.

[0011] Furthermore, no further details have been provided regarding the alignment of the pin axes.

[0012] It is particularly advantageous if the pin axis of the mass balancing pin runs essentially parallel, preferably parallel to the eccentric pin axis of the eccentric pin.

[0013] Furthermore, it is particularly advantageous if the pin axis of the mass balancing pin and the eccentric pin axis of the eccentric pin run parallel to the mass balancing plane.

[0014] In connection with the use of an eccentric drive pin in the eccentric drive, it was not further specified how the eccentric drive pin should be arranged.

[0015] In particular, it is possible to arrange the eccentric pin firmly either in the drive shaft or in the driver and to provide that it engages rotatably in a bearing bore in the driver or in the drive shaft.

[0016] A particularly preferred solution provides that the eccentric drive pin is fixedly arranged in the drive shaft and engages in the bearing bore provided in the driver.

[0017] Furthermore, within the scope of the solution according to the invention, it is possible for the mass balance pin to be arranged in a fixed manner either in the drive shaft or in the driver and to engage in a recess in the driver or in the drive shaft which accommodates it with play.

[0018] This solution also advantageously provides that the mass balancing pin is firmly arranged in the drive shaft and engages in the recess provided in the driver.

[0019] For example, the recess in the driver is designed in such a way that it allows at least limited rotation of the driver about the eccentric pin axis and relative to the mass balancing pin.

[0020] This can be achieved, for example, by ensuring that the recess is large enough or designed as a clearance to allow the intended rotation of the driver relative to the eccentric drive pin.

[0021] In extreme cases, the recess is designed as such a large clearance in the driver that, within the scope of the intended rotation, there is no contact between the driver and the mass balance pin.

[0022] Such a movement limiting unit can be realized particularly advantageously if the recess forms a stop surface which limits pivoting of the driver in the sense of a reduction of the compressor orbital radius by interaction with the mass balancing pin.

[0023] In a solution which is particularly easy to implement in terms of construction, it is preferably provided that the recess is arranged so as to enclose the mass balancing pin with its inner wall surfaces and that a wall surface area thereof forms the stop surface.

[0024] In the simplest case, the recess can be designed as a bore which is chosen to be large enough that a wall surface area of ​​the inner wall surface of this bore comes into contact with the mass balancing pin and thus forms the stop surface.

[0025] It is preferably provided that in a normal state in which the spiral ribs abut one another, the inner wall surface of the recess extends on all sides at a distance from the mass balancing pin, so that no interaction occurs between the recess and the mass balancing pin.

[0026] Only when the normal state is left do the mass balance pin and the inner wall surface interact with the wall surface area forming the stop surface, when the compressor orbital radius has been reduced from a normal state value to such an extent that it reaches the minimum value, which can be defined by the relative arrangement of the stop surface and the mass balance pin.

[0027] Within the scope of the inventive solution, no detailed information on the overall unbalance correction carried out was described.

[0028] An advantageous solution is to provide the driver with an orbital track balancing mass.

[0029] This orbital balancing mass serves in particular to compensate for the imbalance caused by the second movable compressor body moving on the orbital path.

[0030] In particular, it is provided that the orbital balancing mass is arranged symmetrically to the mass balancing plane and thus does not cause any asymmetric imbalance to the mass balancing plane.

[0031] A particularly advantageous solution provides that the orbital path balancing mass is arranged on a side opposite the eccentric drive pin and the mass balancing pin of a geometric transverse plane running perpendicular to the mass balancing plane and through the center plane of the drive shaft.

[0032] With regard to further unbalance compensation, in particular of the drive shaft, no further details have been given in connection with the solutions described so far.

[0033] An advantageous solution provides that the drive shaft has a section facing the compressor, which interacts with the eccentric drive pin and the mass balancing body and carries an unbalance balancing mass facing the compressor

[0034] It is preferably provided that this unbalance compensation mass is arranged between a rotor of the drive motor and a front bearing unit on the drive shaft.

[0035] Furthermore, a favorable solution provides that the drive shaft has a section facing away from the compressor, which carries an unbalance compensation mass facing away from the compressor.

[0036] This unbalance compensation mass is also preferably arranged between the rotor of the drive motor and a rear bearing unit of the drive shaft.

[0037] Preferably, these unbalance compensation masses, which are arranged on the drive shaft, are also designed and arranged symmetrically to the mass compensation plane.

[0038] Further features and advantages of the invention are the subject of the following description and the drawings of some embodiments.

[0039] The drawing shows: Fig. 1 is a perspective view of a first embodiment of a compressor according to the invention; Fig. 2 shows a longitudinal section through the first embodiment of the compressor according to the invention, in a horizontal sectional plane passing through a central axis of a stationary compressor body; Fig. 3 a longitudinal section through the first embodiment of the compressor similar Fig. 2 in a vertical sectional plane passing through the central axis of the stationary compressor body; Fig. 4 is a schematic representation of intermeshing spiral ribs and the orbiting movement of one of the spiral ribs and a representation of an orbital path of the movable spiral rib relative to the stationary spiral rib; Fig. 5 a cross section through a scroll compressor unit along line 5-5 in Fig. 3 in the area of ​​the interlocking spiral ribs; Fig. 6 a section along line 6-6 in Fig. 3; Fig. 7 a section along line 7-7 in Fig. 3; Fig. 8 an enlarged view of area A in Fig. 7; Fig. 9 a plan view of a drive shaft with a driver driven by it; Fig. 10 a schematic geometric representation of the relative position of the center axes of the compressor bodies and an eccentric pin axis; Fig. 11 a section through the driver with an orbital orbit balancing mass in the normal state value of the compressor orbital radius; Fig. 12 a cut similar Fig. 11 at a minimum value of the compressor orbit radius and Fig. 13 a side view of a drive shaft with the driver driven by it.

[0040] One in Fig. The first exemplary embodiment of a compressor according to the invention, designated as a whole by 10, for a gaseous medium, in particular a refrigerant, shown in Figure 1, 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 an intermediate section 18 arranged between the end-side housing sections 14 and 16.

[0041] As in Fig. 2 to Fig. 8, a scroll compressor unit, designated as a whole by 22, is provided in the first housing section 14, which has a first compressor body 24 arranged stationary in the compressor housing 12, in particular in the first housing section 14, and a second compressor body 26 movable relative to the stationary compressor body 24.

[0042] The first compressor body 24 includes a compressor body base 32 above which a first spiral rib 34 extends, and the second compressor body 26 also includes a compressor body base 36 above which a second spiral rib 38 extends.

[0043] The compressor bodies 24 and 26 are arranged relative to each other so that the spiral ribs 34, 38 engage with each other to form, as shown in Fig. 4, to form between them at least one, preferably several compressor chambers 42, in which a compression of the gaseous medium, for example of refrigerant, takes place in that the second compressor body 26 moves with its central axis 46 around a central axis 44 of the first compressor body 24 on an orbital path 48 with a compressor orbital path radius VOR, wherein the volume of the compressor chambers 42 is reduced and ultimately compressed gaseous medium exits through a central outlet 52, while gaseous medium to be sucked in is sucked in radially outwardly relative to the central axis 44 through compressor chambers 42 opening on the circumference.

[0044] The sealing of the compressor chambers 42 relative to one another is achieved in particular by the fact that the spiral ribs 34, 38 are provided on the end face with axial sealing elements 54 and 58, respectively, which bear sealingly against the respective bottom surface 62, 64 of the respective other compressor body 26, 24, wherein the bottom surfaces 62, 64 are formed by the respective compressor body base 36 and 32, respectively, and lie in a plane running perpendicular to the central axis 44.

[0045] The scroll compressor unit 22 is accommodated as a whole in a first housing body 72 of the compressor housing 12, which has a front cover section 74 and a cylindrical ring section 76 which is integrally formed on the front cover section 74 and which in turn engages with a ring shoulder 78 in a sleeve body 82 of the housing body 72, which is integrally formed on a central housing body 84 forming the intermediate section 18, wherein the central housing body 84 is closed off 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.

[0046] The sleeve body 82 encloses the scroll compressor unit 22, the first compressor body 24 of which is supported on a contact surface 94 in the housing body 72 by support fingers 92 formed on the compressor body base 32.

[0047] In particular, the first compressor body 24 is immovably fixed in the housing body 72 against all movements parallel to the support surface 94.

[0048] Thus, the first compressor body 24 is fixed stationary within the first housing body 72 and thus also within the compressor housing 12 in a precisely defined position.

[0049] The second movable compressor body 26, which must move on the orbital path 48 around the central axis 44 relative to the first compressor body 24, is guided in the axial direction relative to the central axis 44 by an axial guide, designated as a whole by 96, which supports and guides the compressor body base 36 on an underside 98 facing away from the spiral rib 38, specifically in the region of an axial support surface 102, so that the compressor body base 36 of the second compressor body 26 is supported relative to the first compressor body 24, which is stationary in the compressor housing 12, and in a direction parallel to the central axis 44 in such a way that the axial sealing elements 58 remain on the base surface 64 and do not lift off therefrom, wherein at the same time the compressor body base 36 with the axial support surface 102 can move transversely to the central axis 44 in a sliding manner relative to the axial guide 96 ( Fig. 2, Fig. 3 and Fig. 6).

[0050] For this purpose, as described in the Fig. 2, Fig. 3 and Fig. 7, the axial guide 96 is formed by a support element 112, which is made in particular from an open-pore sintered material and which has a support surface 114 facing the axial support surface 102, on which support surface 114 the compressor body base 36 with the axial support surface 102 does not rest, but on which a sliding body 116, designated as a whole by 116, in particular plate-shaped, with a sliding support surface 118 rests, wherein the sliding body 116, with a sliding support surface 122 opposite the sliding support surface 118, supports the axial support surface 102 against movements parallel to the central axis 44 but guides it in a sliding manner with regard to movements transverse to the central axis 44.

[0051] This prevents an axial movement of the second compressor body 26 in the direction of the central axis 44, but enables a movement in a plane transverse, in particular perpendicular, to the central axis 44.

[0052] The axial guide 96 according to the present invention provides that when the second compressor body 26 moves on the orbital path 48 about the central axis 44 of the first compressor body 24, on the one hand the second compressor body 26 with the compressor body base 36 and its axial support surface 102 moves relative to the sliding body 116, while on the other hand the sliding body 116 in turn moves relative to the carrier element 118.

[0053] Thus, sliding occurs between the compressor body base 36 and the sliding body 116 by a movement of the axial support surface 102 relative to the sliding support surface 122 of the sliding body 116 and, in addition, a sliding of the sliding support surface 118 of the sliding body 116 relative to the support surface 114 of the support element 112 occurs.

[0054] To improve lubrication, for example, the sliding support surface 122 and the sliding bearing surface 118 of the sliding body 116 are provided with depressions, in particular micro-depressions, which form receptacles for a lubricant and contribute to the distribution of the lubricant.

[0055] In order to specify the limited two-dimensional mobility of the sliding body 116 parallel to a plane E perpendicular to the central axis 44 relative to the carrier element 112, the sliding body 116 is provided with a Fig. 7 and Fig. 8 and designated as a whole by 132, wherein the guide with play 132 comprises a guide recess 134 provided in the sliding body 116, which has a diameter DF, and a guide pin 136 anchored in the support 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 can perform an orbiting movement relative to the support element 112.

[0056] The movements of the sliding body 116 result in the build-up of a sufficient lubricating film between the axial support surface 102 of the compressor body base 36 and the sliding support surface 122 of the sliding body 116 as well as the carrier surface 114 and the sliding support surface 118.

[0057] For a stable lubricating film, it is sufficient if the guide orbital radius FOR is 0.01 times the compressor orbital radius or more, in particular 0.05 times the compressor orbital radius or more.

[0058] Furthermore, for example, due to the fact that 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 in that lubricant enters the pores of the carrier element 112 and is thus available for building up the lubricating film in the intermediate space via the surface structures of the carrier element 112 provided, for example, in the region of the carrier surface 114.

[0059] The fact that the sliding body 116 itself is designed as a plate-shaped, annular part made of spring steel and thus the sliding support surface 118 facing the support surface 114 represents a smooth spring steel surface further promotes the formation of the lubricating film.

[0060] Furthermore, the material pairing of the aluminum alloy, which is softer than spring steel in the area of ​​the support surface 114, and the spring steel in the area of ​​the sliding support surface 118 has advantageous continuous running properties due to its wear resistance.

[0061] In the solution according to the invention, the support element 112 is provided not only 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.

[0062] 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 one another by a suitable design of the support element 112, wherein this is done in particular by a single surface of the support element 112, which comprises both the support surface 114 and the support surfaces 94.

[0063] Furthermore (as in Fig. 3 and 5 to 7) the rotationally fixed fixing of the support fingers 92 relative to the carrier element 112 by positioning pins 142 passing through both the carrier element 112 and the support fingers 92.

[0064] The carrier element 112 is further arranged in the housing body 72 both axially in the direction of the central axis 44 and also fixed against rotational movements about the central axis 44.

[0065] In order to further ensure the build-up of a lubricating film of lubricant between the sliding support surface 122 and the axial support surface 102, the compressor body base 36 is provided in a radially inner edge region 152 and in a radially outer edge region 154 with an edge surface 156 or 158 which runs inclined relative to the axial support surface 102 and is set back from the axial support surface 102, which, together with the sliding support surface 122, leads to a wedge-shaped intermediate space which opens radially outwards or radially inwards and which facilitates the access of lubricant.

[0066] Furthermore, the build-up of the lubricating film between the sliding support surface 122 and the axial support surface 102 is promoted in that the sliding support surface 122 and the axial support surface 102 are designed, in the overlapping area in which they interact, as continuous annular surfaces 124 and 126, respectively, that is to say in the circumferential direction U around the central axis and in their entire radial extent uninterrupted, wherein in particular the annular surface 126 of the axial support surface 102 extends from an inner contour IK with a radius IR thereof to an outer contour AK, wherein the radius IR is less than two-thirds of an outer radius AR.

[0067] Furthermore, the annular surface 124 of the sliding support surface 122 is dimensioned such that the annular surface 126 of the axial support surface 102 always rests on the sliding support surface 122 over its entire surface during all relative movements thereto.

[0068] As in the Fig. 2 to 7, 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, are all located radially inside a coupling 164 comprising a plurality of coupling element sets 162 which are arranged at equal radial distances from the central axis 44 and at equal angular distances in the direction of rotation U around the central axis 44 and together form a coupling 164 which prevents self-rotation of the second movable compressor body 26.

[0069] Each of these coupling element sets 162 comprises, as shown in the Fig. 2, Fig. 7 and Fig. 8, 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.

[0070] 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 each other.

[0071] This second coupling element 182 is guided in a third coupling element 192, which is designed as a receptacle 194 provided in the carrier element 112 for the annular body 184 and which has a cylindrical inner wall surface 196.

[0072] In particular, 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 is necessarily smaller than the diameter DRA of the cylindrical outer surfaces 188 of the annular body 184, wherein, in addition, the diameter DRI of the cylindrical inner surface 186 is greater than a diameter DSK of the cylindrical outer surface 176 of the pin body 174.

[0073] Thus, each coupling element set 162 in turn forms an orbital guide whose maximum orbital radius OR for the orbiting motion corresponds to DI / 2-(DRA-DRI) / 2-DSK / 2.

[0074] By dimensioning the orbital radius OR of the coupling element sets 162 such that it is slightly larger 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 relative to the stationary compressor body 24 by the coupling 164 in such a way that one of the coupling element sets 162 is effective in order to prevent the self-rotation of the second movable compressor body 26, wherein, for example, in the case of six coupling element sets 162, after passing through an angular range of 60°, the effectiveness of each coupling element set 162 changes from one coupling element set 162 to the next coupling element set 162 in the direction of rotation.

[0075] Due to the fact that each coupling element set 162 has three coupling elements 172, 182 and 192 and in particular an annular body 184 is effective between the respective pin body 174 and the respective receptacle 194, on the one hand the wear resistance of the coupling element sets 162 is improved, on the other hand the lubrication in the area thereof is improved and in addition the noise generation by the coupling element sets 162 is reduced, which noise arises from the change in effectiveness from one coupling element set 162 to the other coupling element set 162.

[0076] It is particularly essential that the coupling element sets 162 are sufficiently lubricated, in particular lubrication between the cylindrical outer surface 176 of the pin body 174 and the cylindrical inner surface 186 of the ring body 184 as well as lubrication between the cylindrical outer surface 188 of the ring body 184 and the cylindrical inner wall surface 196 of the receptacle 194.

[0077] For optimal lubrication of the coupling element sets 162, the receptacles 194 in the carrier element 112 are open on both sides in the axial direction, wherein the annular bodies 184 are held on their sides facing away from the second compressor body 26 by a stop element 198 projecting radially inwards.

[0078] In addition, further through-openings 202, 204 are provided in the carrier element 112, which allow the passage of lubricant and sucked-in refrigerant.

[0079] To accommodate the coupling elements 172 designed as pin bodies 174, the compressor body base 36 is provided with star-shaped extensions 212 extending radially outwards, which engage in spaces 214 between support fingers 92 which follow one another in a direction of rotation U around the central axis 44, so that the coupling elements 172 are also located in these spaces 214 and are thus arranged within the housing body 72 at the greatest possible radial distance from the central axis 44.

[0080] This positioning of the coupling element sets 162 at a radial distance from the central axis 44 which is also as large as possible, which is determined by the largest possible radial distance between the coupling elements 172, has the advantage that, due to the large lever arm, the forces acting on the coupling element sets 162 can be kept as small as possible, which has an advantageous effect on the component dimensioning.

[0081] The inventive concept of the lubrication of the axial guide 96 and the coupling element sets 162 is particularly advantageous when the center axes 44 and 46 of the compressor bodies 24 and 26 normally run horizontally, that is to say at a maximum angle of 30° to a horizontal, wherein in the compressor housing 12, in particular in the region of the first housing body 72, a lubricant bath 210 is formed at a point which is lowest in the direction of gravity, from which lubricant is whirled up during operation and is thereby absorbed and distributed in the manner described.

[0082] The drive of the movable compressor body 24 takes place (as in Fig. 2 and Fig. 3) by a drive motor designated as a whole by 222, for example an electric motor, which in particular has a stator 224 held in the central housing body 84 and a rotor 226 arranged within the stator 224, which is arranged on a drive shaft 228 which runs coaxially to the central axis 44 of the stationary compressor body 24.

[0083] The drive shaft 228 is mounted on the one hand in a bearing unit 232 facing the compressor, which is arranged between the drive motor 222 and the scroll compressor unit 22 and in the central housing body 84, and on the other hand in a bearing unit 234 facing away from the compressor, which is arranged on a side of the drive motor 222 opposite the bearing unit 232.

[0084] The bearing unit 234 facing away from the compressor is mounted, for example, in the second housing body 86, which closes off the central housing body 84 on a side opposite the first housing body 72.

[0085] From the inlet chamber 88 formed by the second housing body 86, sucked-in medium, in particular the refrigerant, flows through the drive motor 222 in the direction of the bearing unit 232 facing the compressor, flows around it and then flows in the direction of the scroll compressor unit 22.

[0086] The drive shaft 228 drives the movable compressor body 26 via an eccentric drive designated as a whole by 242, which moves in an orbital manner around the central axis 44 of the stationary compressor body 24.

[0087] The eccentric drive 242 comprises in particular an eccentric drive pin 244 held in the drive shaft 228, which moves a driver 246 on the orbital path 48 about the central axis 44, which in turn is rotatably mounted on the eccentric pin 244 about an eccentric pin axis 245 by a rotatable receptacle of the eccentric drive pin 244 in a bearing bore 247 in the driver 246 and is also rotatably mounted in a pivot bearing 248 about the central axis 46 of the orbitingly movable compressor body 26, wherein the pivot bearing 248 allows rotation of the driver 246 relative to the orbitingly movable compressor body 26, as in Fig. 9 and Fig. 10 shown.

[0088] Due to the rotatability of the driver 246 about the eccentric pin axis 245 and about the central axis 46, in particular 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 compressor body 26 can move radially outwards away from the central axis 44 so far that the spiral ribs 34, 38 abut one another and the compressor chambers 42 are tightly closed.

[0089] For this purpose, in particular, the distance of the eccentric pin axis 245 from the central axis 44 of the stationary compressor body 24 is selected to be greater than the intended compressor orbital radius VOR, that is, the distance between the central axes 44 and 46 from one another, and so large that the eccentric pin axis 245 lies outside a central axis plane ME running through the two central axes 44 and 46 and opposite to a direction of rotation D of the drive shaft 228 at a distance therefrom.

[0090] Due to this arrangement of the central axes 44 and 46 and the eccentric pin axis 245, the resulting eccentric action of the eccentric drive pin 244 on the driver 246 causes a force FA which, with respect to the central axis 46 of the driver 246, leads to a force FC acting on the central axis 46 and moving the driver 246 together with the movable compressor body 26 radially outwards to the central axis 44, which force acts in the central axis plane ME running through the central axis 44 and the central axis 46, and to which a force FO acting tangentially to the orbital path 48 leads, which moves the driver 246 together with the movable compressor body 26 on the orbital path 48 around the central axis 44.

[0091] The center axis plane ME defined by the center 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.

[0092] The driver 246 is further provided with an orbital balancing mass 252 held on one side of the driver for mass balancing, which counteracts the imbalance caused by the compressor body 26 moving on the orbital path 48 and compensates for this as far as possible, wherein the orbital path balancing mass 252 is also designed and arranged symmetrically to the mass balancing plane ME, as shown in Fig. 11 shown.

[0093] In this case, the orbital orbit balancing mass 252 lies in particular on a side facing away from the eccentric drive pin 244 of a transverse plane QE running perpendicular to the mass balancing plane ME and through the central axis 44.

[0094] The mass not taken into account in the mass balancing described above is the mass of the eccentric drive pin 244, which is arranged asymmetrically to the mass balancing plane ME and leads to vibrations, particularly at high speeds of the drive shaft 228.

[0095] For this reason, in addition to the eccentric drive pin 244, a mass balancing pin 254 is provided in the drive shaft 228, which is arranged on a side of the mass balancing plane ME opposite the eccentric drive pin 244 and thus, together with the eccentric drive pin 244, again leads to a mass distribution that is at least approximately symmetrical to the mass balancing plane ME.

[0096] Preferably, a pin axis 256 of the mass balance pin 254 and the eccentric pin axis 245 are arranged mirror-symmetrically to the mass balance plane MR and, in addition, the eccentric drive pin 244 and the mass balance pin 254 preferably have approximately the same mass.

[0097] In order to allow the mass balancing pin 254 to protrude into the driver 246, the driver 246 is provided with a recess 258 which accommodates the mass balancing pin 254 with play, so that a limited rotational movement of the driver 246 about the eccentric pin axis 255 is possible to adapt the compressor orbital radius VOR to machining inaccuracies of the spiral ribs 34, 38 or liquid impacts or pressure surges.

[0098] Preferably form, as in Fig. 12, the mass balance pin 254 with at least one surface area 262 of an inner wall surface 264 of the recess 258 has a movement limiting unit 266 which, starting from a normal state, only allows a reduction of the compressor orbital radius VOR from a normal state value down to a minimum value.

[0099] For further mass balancing, the drive shaft 228 is provided with an unbalance balancing mass 272 facing the compressor and an unbalance balancing mass 274 facing away from the compressor ( Fig. 2, Fig. 3 and Fig. 13).

[0100] The compressor-facing unbalance compensation mass 272 is preferably arranged between the drive motor 222 and the compressor-facing bearing unit 232 on a compressor-facing section 276 of the drive shaft 228, which lies on the same side of the transverse plane QE as the orbital path compensation mass 252 and is arranged symmetrically to the mass compensation plane ME.

[0101] The unbalance compensation mass 274 facing away from the compressor is preferably located on a section 278 of the drive shaft 228 facing away from the compressor and between the drive motor 222 and the bearing unit 234 facing away from the compressor.

[0102] To accommodate the pivot bearing 248, as shown in the Fig. 2 and Fig. 3, the second compressor body 26 is provided with an integrated driver holder 282 which accommodates the pivot bearing 248.

[0103] The driver receptacle 282 is set back relative to the flat side 98 of the compressor body base 36 and is thus arranged so as to be integrated in the compressor body base 36, so that the drive forces acting on the movable compressor body 26 are effective on a side of the flat side 98 of the compressor body base 36 facing the spiral rib 38 and thus drive the movable compressor body 26 with a low tilting moment, which is axially supported by the axial guide 96 in the direction of the central axis 44 between the driver receptacle 282 and the drive motor 222 on the axial support surface 102 and is guided so as to be movable transversely to the central axis 44.

[0104] In the solution according to the invention, the driver receptacle 282, as shown in the Fig. 2, Fig. 3 and Fig.6 is surrounded by the axial support surface 102 which is located on the outside in the radial direction to the central axis 46, and the axial support surface 102 is in turn surrounded by the coupling element sets 162 of the coupling 164 which prevents the self-rotation of the second compressor body 26 and which are located on the outside in the radial direction to the central axis 44.

Claims

[1] A compressor comprising a compressor housing (12), a scroll compressor unit (22) arranged in the compressor housing (12) with a first, stationary compressor body (24) and a second compressor body (26) movable relative to the stationary compressor body (24), the first and second spiral ribs (34, 38) of which are designed in the form of a circular involute and engage with one another to form compressor chambers (42) when the second compressor body (26) is moved relative to the first compressor body (24) on an orbital path (48), an axial guide (96) which supports the movable compressor body (26) against movements in a direction parallel to a central axis (44) of the stationary compressor body (24) and guides it during movements in a direction transverse to the central axis (44), an eccentric drive (242) for the scroll compressor unit (22),which has a driver (246) driven by the drive motor (222) and rotating on the orbital path (48) around the central axis (44) of a drive shaft (228), which in turn cooperates with a driver receptacle (282) of the second compressor body (26), and a coupling (164) preventing self-rotation of the second compressor body (26), wherein the eccentric drive (242) has an eccentric drive pin (244) driving the driver (246) and a mass balancing body (254), and wherein the eccentric drive pin (244) and the mass balancing body (254) are arranged on opposite sides of a mass balancing plane (ME), , characterized by that the mass balancing body is designed as a mass balancing pin (254), that the mass balancing pin (254) is an element of a movement limiting unit (264) for the driver (246). [2] Compressor according to claim 1, characterized bythat the mass balance plane (ME) passes through the central axis (44) of the drive shaft (228) and the central axis (46) of the orbiting compressor body (26). [3] Compressor according to claim 1 or 2, characterized by that the mass balancing pin (254) has a mass that deviates by a maximum of 20% from the mass of the eccentric drive pin (244). [4] Compressor according to one of claims 1 or 2, characterized by that the mass balancing pin (254) has substantially the same mass as the eccentric drive pin (244). [5] Compressor according to one of the preceding claims, characterized by that a pin axis (256) of the mass balancing pin (254) is arranged at the same distance from the mass balancing plane (ME) as an eccentric pin axis (245) of the eccentric drive pin (244). [6] Compressor according to one of the preceding claims, characterized bythat the pin axis (256) of the mass balancing pin (254) runs essentially parallel to the eccentric pin axis (245) of the eccentric drive pin (244). [7] Compressor according to one of the preceding claims, characterized by that a pin axis (256) of the mass balancing pin (254) and the eccentric pin axis (245) of the eccentric drive pin (244) run parallel to the mass balancing plane (ME). [8] Compressor according to one of the preceding claims, characterized by that the eccentric drive pin (244) is arranged either in the drive shaft (228) or in the driver (246) and rotatably engages in a bearing bore (267) in the driver (246) or in the drive shaft (228). [9] Compressor according to one of claims 5 to 8, characterized bythat the mass balancing pin (254) is arranged in a fixed manner either in the drive shaft (228) or in the driver (246) and engages in a recess (258) in the driver (246) or in the drive shaft (228) which receives it with play. [10] Compressor according to claim 9 characterized by that the recess (258) forms a stop surface (262) which limits pivoting of the driver (246) in the sense of a reduction of the compressor orbital radius (VOR) by interaction with the mass balancing pin (254). [11] Compressor according to claim 10, characterized by that the recess (258) is arranged to enclose the mass balancing pin (254) with its inner wall surfaces (264) and that a wall surface area thereof forms the stop surface (262). [12] Compressor according to one of the preceding claims 9 to 11, characterized bythat in a normal state in which the spiral ribs (34, 38) abut one another, the inner wall surface (264) of the recess (258) extends on all sides at a distance from the mass balancing pin (254). [13] Compressor according to one of the preceding claims, characterized by that the driver (246) is provided with an orbital track balancing mass (252). [14] Compressor according to claim 13, characterized by that the orbital balancing mass (252) is arranged symmetrically to the mass balancing plane (ME). [15] Compressor according to claim 13 or 14, characterized by that the orbital path balancing mass (252) is arranged on a side opposite the eccentric drive pin (244) and the mass balancing body (254) of a geometric transverse plane (QE) running perpendicular to the mass balancing plane (ME) and through the central axis (44) of the drive shaft (228). [16] Compressor according to one of the preceding claims, characterized bythat the drive shaft (228) has a compressor-facing section (276) which cooperates with the eccentric drive pin (244) and carries the mass balancing body (254) and an unbalance balancing mass (272) facing the compressor. [17] Compressor according to claim 16, characterized by that the unbalance compensating mass (272) is arranged between a rotor (226) of the drive motor (222) and a front bearing unit (232) on the drive shaft (228). [18] Compressor according to one of the preceding claims, characterized by that the drive shaft (228) has a section (278) facing away from the compressor, which carries an unbalance compensation mass (274) facing away from the compressor. [19] Compressor according to claim 18, characterized by that the unbalance compensating mass (274) is arranged between the rotor (226) of the drive motor (222) and a rear bearing unit (234) of the drive shaft (228).

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