EP3491245B1 - Compressor - Google Patents

Description

The invention relates to a compressor, comprising a compressor housing, a spiral compressor unit arranged in the compressor housing with a first, stationary compressor body and a second compressor body movable relative to the stationary compressor body, the first and second spiral ribs of which are designed in the form of an involute and interlock 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 movements in a direction transverse to the central axis, an eccentric drive for the Scroll compressor unit, which has a driver driven by a drive motor and a driver rotating on the orbital path around the central axis of a drive shaft, which in turn interacts with a driver receptacle of the second compressor body, an orbital path balancing mass that counteracts an imbalance caused by the compressor body moving on the orbital path, and a self-rotation of the second compressor body preventing clutch.

Such compressors are known from the prior art. JPS59126096A discloses a scroll compressor according to the preamble of claim 1.

A drive motor for such a compressor can be operated at a variable speed, for example by means of a converter, or at a constant speed.

With these compressors - especially at high speeds, which can be over 6,000 revolutions per minute, for example - there is the problem that the guidance of the driver in the driver receptacle has a low long-term stability, especially if there is a rolling element bearing in the driver receptacle, for example a cylindrical roller bearing. is intended for storage of the driver.

The invention is therefore based on the object of improving a compressor of the generic type in such a way that the long-term stability of the guidance of the driver in the driver receptacle can be guaranteed even at high speeds.

This object is achieved according to the invention in a compressor of the type described above in that the orbital track balancing mass is coupled to the eccentric drive in such a way that it moves in accordance with the movement of the driver on the orbital track, but is decoupled with regard to the transmission of tilting moments to 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 between the driver and the orbital path compensation mass at high speeds, the orbital path compensation mass acts on the driver with high tilting moments and thus the storage of the driver in the driver receptacle , especially if this is done by a rolling element bearing, for example a cylindrical roller bearing, is exposed to high wear, since such bearings are exposed to increased wear when tilting moments occur.

The solution according to the invention now solves the problem that exists in the known solutions of the orbital path compensation mass acting on the driver with tilting moments by decoupling the driver from the orbital path compensation mass in such a way that it can no longer act on the driver with significant tilting moments.

No further information was provided regarding the guidance of the orbital orbit balancing mass.

In principle, it would be conceivable to store and guide the orbital orbit balancing mass relative to the drive shaft using a bearing element provided on the drive shaft.

A particularly simple and structurally favorable solution provides that the orbital track balancing mass is guided on the orbital track by an eccentric drive pin acting between the driver and the drive shaft.

This solution has the great advantage that the already existing eccentric drive pin, which is effective between the driver and the drive shaft, can be used to guide the orbital path balancing mass so that it follows the orbital path of the driver in order to achieve the required mass compensation due to the eccentricity of the Orbital path of the driver on the drive shaft without a transfer of tilting moments from the orbital path balancing mass to the driver.

Alternatively or additionally, the task mentioned at the outset is also achieved according to the invention in that the orbital orbit balancing mass engages the eccentric drive pin with a guide body, in particular is rotatably mounted on it.

In this case, a particularly simple connection can be established between the orbital orbit balancing mass and the eccentric drive pin.

For this purpose, the guide body is preferably firmly connected to the orbital orbit balancing mass.

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 orbit balancing mass is guided on the drive shaft by means of a guide body that interacts with the drive shaft.

This solution creates additional relief for the eccentric drive pin, as additional guidance of the guide body relative to the drive shaft is now possible.

The action of the eccentric drive pin on the guide body essentially serves to move the guide body with the orbital path compensation mass in such a way that the orbital path compensation mass follows the orbital path of the driver and produces the required mass compensation.

According to the invention, the orbital orbit balancing mass is guided by the guide body acting on the drive shaft on a path which runs in a path plane which runs parallel to an alignment plane which runs perpendicular to the central axis of the drive shaft.

The interaction between the guide body and the drive shaft ensures that any tilting moments that may still occur are transferred from the orbital orbit balancing mass to the drive shaft by means of the guide body and thus essentially do not generate any tilting moments acting on the eccentric drive shaft.

The guidance of the guide body on the drive shaft can be implemented in a variety of ways.

According to the invention, the guide body is guided with a guide surface on an alignment surface of the drive shaft.

With regard to the alignment surface provided on the drive shaft, it would be conceivable, for example, to arrange the alignment surface on a collar of the drive shaft.

A particularly simple solution that is also stable with regard to the guidance of the guide body provides that the alignment surface provided on the drive shaft is an end face of the drive shaft.

Furthermore, the guide body can be optimally supported on the alignment surface if the guide body is arranged across the alignment surface. With regard to the arrangement of the guide body, it is also advantageous for spatial reasons if the guide body is arranged between the alignment surface of the drive shaft and the driver.

In this case, despite the provision of the guide body, it is possible to design the eccentric drive in a spatially small manner.

It is particularly advantageous if the guide body is plate-shaped, that is to say it has the smallest possible extent in the direction of the central axes in relation to its extent transversely to the central axis. In order to ensure that the guide body is guided by the drive shaft and in particular to ensure this in as many operating states as possible, it is provided that the guide body is guided relative to the drive shaft by an axial guide.

The axial guide is designed in such a way that it holds the guide surface of the guide body in contact with the alignment surface of the drive shaft in order to ensure sufficiently precise guidance of the guide body and thus of the orbital orbit balancing mass relative to the drive shaft.

The axial guide can be designed in a wide variety of ways.

The axial guide is preferably designed in such a way that it comprises an element which acts on the guide body on a side opposite the guide surface.

Such an element can be designed in a wide variety of ways. In particular, it is provided that the element is a screw head of a screw engaging in the drive shaft.

Another solution provides that the element is a locking ring fixed relative to the drive shaft.

A further advantageous solution provides that the element is a projection arranged on the eccentric drive pin.

For example, the axial guidance can be implemented by means of a screw engaging on the drive shaft and/or a collar on the eccentric drive pin and/or a pin with a locking ring formed onto the drive shaft.

In order to further allow the guide body and the orbital track balancing mass to be able to align themselves relative to the eccentric drive pin according to the respective unbalance, it is preferably provided that the guide body can be rotated to a limited extent relative to the eccentric drive pin.

Such limited rotatability ensures, on the one hand, that the alignment of the guide body and thus the orbital orbital compensation mass relative to the eccentric drive pin remains within the limits of a permissible rotation, for example when the compressor is at a standstill, but on the other hand, the guide body with the orbital orbital compensation mass has the opportunity to move in accordance with the Movement of the driver on the orbital path to align the imbalance generated in order to counteract this as best as possible.

For this purpose, 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 limitation unit can be implemented using independent elements.

A particularly favorable embodiment of the movement limiting unit provides that the first movement limiting unit is formed by a stop body held on the guide body or the drive shaft and a recess which receives the stop body and is arranged on the drive shaft or the guide body.

However, a particularly advantageous solution provides that the movement limiting unit is implemented 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 also serves as a movement limitation unit.

Furthermore, it is favorable if the orbital orbit balancing mass is arranged on a side opposite the eccentric drive pin of a geometric transverse plane that runs perpendicular to the mass balancing plane and through the central axis of the drive shaft.

Alternatively or in addition to the above-described features of a solution according to the invention, a further solution to the problem mentioned at the outset provides that the eccentric drive pin is arranged in a fixed manner in the drive shaft and engages in a drive pin receptacle in the driver, so that the driver is positioned within the driver by the action of the eccentric drive pin on it Drive pin holder is driven.

In this case, it is particularly favorable if the eccentric drive pin and the drive pin receptacle cooperate in a contact area which is penetrated by a central plane which is perpendicular to the central axis of the movable second compressor body and in the direction of the central axis of a pivot bearing acting between the second compressor body and the driver 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.

Alternatively, the position of the center plane can also be defined by the fact that it runs perpendicular to the eccentric pin axis and in the direction of the eccentric pin axis centrally through the pivot bearing for the driver.

This solution has the great advantage that the eccentric drive pin, with its force moving the driver on the orbital path, acts as close as possible to this central plane of the pivot bearing and thus ensures that the force of the eccentric drive pin does not lead to tilting moments acting on the driver, which in turn reduces the stability of the pivot bearing for the driver.

It is particularly advantageous if the eccentric drive pin and the drive pin receptacle cooperate in a central section of the drive pin receptacle, the central section in particular being defined in that it is penetrated by the central plane.

In particular, it is provided that the drive pin receptacle in the middle section has a smaller diameter than in the end sections of the drive pin receptacle that lie on both sides of the middle section and each form a gap.

It is preferably provided that the middle section of the drive pin receptacle extends at most over half, even better at most over a third, of the extension of the drive pin receptacle in the direction of the eccentric pin axis.

Furthermore, it is preferably provided that the end sections arranged on both sides of the middle section differ by a maximum of a factor of 2 in terms of their extent in the direction of the eccentric pin axis.

This ensures that the contact area in which the eccentric drive pin acts on the drive pin receptacle is located as close as possible to the center plane.

Alternatively or in addition to the solutions described above, a particularly favorable solution provides that the orbital orbit balancing mass is coupled to the driver by means of a coupling body for rotational driving by the driver during a rotational movement of the same around the eccentric drive pin.

The advantage of this solution can therefore be seen in the fact that the orbital path compensation mass is always aligned in such a way that it compensates for the eccentric movement of the movable compressor body, including the driver and the driver receptacle, caused by the arrangement and orientation of the driver.

This can be achieved particularly easily in that the coupling body is effective between the guide body and the driver.

The coupling body is preferably arranged in a fixed manner on one of the guide body and driver and engages in a recess in the other of the guide body and driver.

It is preferably provided that the coupling body is arranged in the recess with play.

Such a game is advantageously provided if both the guide body with the orbital path balancing mass and the driver are each arranged rotatably relative to the eccentric drive pin and thus the coupling body is to be arranged at a distance from the eccentric drive pin, so that there is no play between the coupling body and the recess Overdetermination of the connection between the position of the coupling body and the recess relative to the eccentric drive pin would result.

The intended play thus avoids overdetermination and also serves to facilitate lubrication.

In particular, the coupling body and the recess are arranged in such a way that during normal operation of the compressor the coupling body rests against a portion of a wall surface of the recess and consequently, even without an overdetermined positioning of the coupling body and recess, there is still a defined orientation of the orbital orbit mass relative to the driver.

A particularly advantageous solution provides that the coupling body is designed as a coupling pin, with which the connection for rotational driving between the orbital orbit balancing mass and the driver can be easily implemented.

Furthermore, an advantageous development of the solution according to the invention provides that the coupling pin is arranged in a fixed manner on the guide body and engages in the recess in the driver.

In order to avoid tilting moments acting on the driver via the coupling pin, it is preferably provided that the coupling pin and the recess interact in a contact area which is penetrated by a central plane which is perpendicular to the pin axis of the coupling pin and in the direction of the coupling pin in the middle of a between second compressor body and the driver effective rotary bearing for the driver, and that there is a gap between the coupling pin and the recess on both sides of the contact area.

This means that, in the same way as when the driver is driven by the eccentric drive pin, a transmission of tilting moments can be largely avoided.

In particular, it is preferably provided that the coupling pin and the recess cooperate in a central section of the recess.

This can be easily achieved, for example, by the recess in the middle section having a smaller diameter than in the end sections of the recess lying on both sides of the middle section and each forming a gap.

With regard to the extent of the middle section, no further comments were made in connection with the above statements.

It is preferably provided that the central section of the recess extends a maximum of half of the extent of the recess in the direction of the pin axis.

Furthermore, it is preferably provided that the end sections arranged on both sides of the middle section differ by a maximum of a factor of 2 in terms of their extent in the direction of the pin axis.

The task mentioned at the beginning is also achieved as an alternative or in addition to the solutions described so far in that the eccentric drive has the eccentric drive pin driving the driver and a coupling body that couples the orbital track balancing mass to the driver.

It is particularly advantageous in this context if the coupling body also represents a mass balancing body. With this solution, the imbalance of the eccentric drive pin caused by the eccentric drive pin and which is asymmetrical to the mass compensation plane can be easily compensated for and thus improve the smooth running of the compressor.

An advantageous solution provides that the eccentric drive pin and the coupling body are arranged on opposite sides of a mass compensation plane in order to easily compensate for the unbalance caused by the eccentric drive pin in addition to coupling the orbital track balancing mass with the driver and to improve smooth running.

No further information has been provided yet regarding the course of the mass balancing level.

An advantageous solution provides that the mass balancing plane runs through the central axis of the drive shaft and the central axis of the orbiting compressor body and is precisely defined in its position and orientation by these two central axes.

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

Furthermore, it is preferably provided that the coupling body has essentially the same mass, in particular the same mass, as the eccentric drive pin.

In order to create the same conditions as possible with regard to the mass distribution as with the eccentric drive pin, it is preferably provided that the coupling body is designed as a mass balancing pin.

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

Furthermore, no further information has yet been provided regarding the alignment of the axes.

It is particularly favorable if the pin axis of the mass balancing pin runs essentially parallel, preferably parallel, to the eccentric drive axis of the eccentric pin.

Furthermore, it is particularly favorable 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.

No further information has yet been provided regarding the arrangement of the mass balance pin.

For example, it would be conceivable to arrange the mass balancing pin on the drive shaft or on the driver.

A particularly favorable solution provides that the mass balancing pin is held on the guide body of the orbital orbit balancing mass and is therefore moved with it and aligned relative to the eccentric drive pin.

If the mass balancing body is designed as a mass balancing pin, it is also preferably provided that the mass balancing pin engages in the recess provided in the driver.

As part of the solution according to the invention, no detailed information on the overall unbalance compensation carried out was described.

In particular, it is provided that the orbital orbit balancing mass described above is arranged symmetrically to the mass balancing plane and thus does not cause any asymmetrical imbalance to the mass balancing plane.

A particularly favorable solution further provides that the orbital orbit balancing mass is arranged on a side of a geometric transverse plane that runs perpendicular to the mass balancing plane and through the central axis of the drive shaft, which is opposite the eccentric drive pin and the mass balancing body.

With regard to further unbalance compensation, in particular the drive shaft, no further information was provided in connection with the solutions described so far.

An advantageous solution provides that the drive shaft has a section facing the compressor, which carries an imbalance compensation mass facing the compressor and the eccentric drive pin and in particular guides the mass compensation body and the orbital path compensation mass.

The unbalance compensation mass is preferably arranged between a rotor of the drive motor and a front bearing unit on the drive shaft.

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

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

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

Further features and advantages of the invention are the subject of the following description and the graphic representation of some exemplary embodiments.

Fig. 1

eine perspektivische Darstellung eines ersten Ausführungsbeispiels eines erfindungsgemäßen Kompressors;

Fig. 2

einen Längsschnitt längs Linie 2-2 in Fig. 4;

Fig. 3

eine schematische Darstellung von ineinandergreifenden Spiralrippen und der orbitierenden Bewegung einer der Spiralrippen und eine Darstellung der Orbitalbahn der bewegbaren Spiralrippe relativ zur stationären Spiralrippe;

Fig. 4

einen Schnitt längs Linie 4-4 in Fig. 2;

Fig. 5

einen Schnitt längs Linie 5-5 in Fig. 2;

Fig. 6

eine vergrößerte Darstellung eines Bereichs A in Fig. 5;

Fig. 7

einen Schnitt längs Linie 7-7 in Fig. 2;

Fig. 8

eine Explosionsdarstellung eines Zusammenwirkens zwischen einem Exzenterantriebszapfen einer Orbitalbahnausgleichsmasse und einem Mitnehmer bei dem erfindungsgemäßen Kompressor;

Fig. 9

eine schematische geometrische Darstellung der relativen Lage der Mittelachsen der Verdichterkörper und einer Exzenterzapfenachse;

Fig. 10

eine Draufsicht auf einen Führungskörper mit der Orbitalbahnausgleichsmasse in seiner Position auf der Antriebswelle mit den Führungskörper durchgreifendem Exzenterantriebszapfen;

Fig. 11

einen vergrößerten Schnitt längs Linie 11-11 in Fig. 4;

Fig. 12

einen Schnitt längs Linie 12-12 in Fig. 11 allerdings nur mit Darstellung der Unwuchtausgleichsmasse und des Führungskörpers;

Fig. 13

einen Schnitt ähnlich Fig. 12 bei aktiver erster Bewegungsbegrenzungseinheit;

Fig. 14

einen Schnitt längs Linie 14-14 im Bereich einer Mitnehmeraufnahme des bewegbaren Verdichterkörpers mit einem Mitnehmer in Fig. 11 in der Stellung gemäß Fig. 12;

Fig. 15

einen Schnitt ähnlich Fig. 14 in der Stellung gemäß Fig. 13;

Fig. 16

einen vergrößerten Schnitt längs Linie 16-16 in Fig. 4 durch einen Massenausgleichszapfen;

Fig. 17

eine Seitenansicht einer Antriebswelle mit dem von dieser angetriebenen Mitnehmer;

Fig. 18

einen vergrößerten Schnitt längs Linie 18-18 in Fig. 4 durch ein zweites Ausführungsbeispiel eines erfindungsgemäßen Kompressors;

Fig. 19

einen Schnitt ähnlich Fig. 11 durch ein drittes Ausführungsbeispiel eines erfindungsgemäßen Kompressors und

Fig. 20

einen Schnitt ähnlich Fig. 11 durch ein viertes Ausführungsbeispiel eines erfindungsgemäßen Kompressors.

Show in the drawing:

Fig. 1

a perspective view of a first embodiment of a compressor according to the invention;

Fig. 2

make a longitudinal cut along the line 2-2 in Fig. 4 ;

Fig. 3

a schematic representation of interlocking spiral ribs and the orbiting movement of one of the spiral ribs and a representation of the orbital trajectory of the movable spiral rib relative to the stationary spiral rib;

Fig. 4

a cut along line 4-4 in Fig. 2 ;

Fig. 5

a cut along line 5-5 in Fig. 2 ;

Fig. 6

an enlarged view of an area A in Fig. 5 ;

Fig. 7

a cut along line 7-7 in Fig. 2 ;

Fig. 8

an exploded view of an interaction between an eccentric drive pin of an orbital orbit balancing mass and a driver in the compressor according to the invention;

Fig. 9

a schematic geometric representation of the relative position of the central axes of the compressor bodies and an eccentric pin axis;

Fig. 10

a top view of a guide body with the orbital orbit balancing mass in its position on the drive shaft with an eccentric drive pin passing through the guide body;

Fig. 11

an enlarged section along line 11-11 in Fig. 4 ;

Fig. 12

a cut along line 12-12 in Fig. 11 However, only with a representation of the unbalance compensation mass and the guide body;

Fig. 13

a cut similar Fig. 12 when the first movement limitation unit is active;

Fig. 14

a cut along line 14-14 in the area of a driver receptacle of the movable compressor body with a driver in Fig. 11 in the position according to Fig. 12 ;

Fig. 15

a cut similar Fig. 14 in the position according to Fig. 13 ;

Fig. 16

an enlarged section along the line 16-16 in Fig. 4 through a mass balance pin;

Fig. 17

a side view of a drive shaft with the driver driven by it;

Fig. 18

an enlarged section along the line 18-18 in Fig. 4 by a second embodiment of a compressor according to the invention;

Fig. 19

a cut similar Fig. 11 by a third embodiment of a compressor according to the invention and

Fig. 20

a cut similar Fig. 11 by a fourth embodiment of a compressor according to the invention.

An in Fig. 1 Illustrated first exemplary embodiment of a compressor according to the invention, designated as a whole by 10, for a gaseous medium, in particular a refrigerant, comprises a compressor housing, designated as a whole by 12, which has a first end housing section 14, a second end housing section 16 and one between the end housing sections 14 and 16 arranged intermediate section 18.

As in Fig. 2 to Fig. 7 shown, a scroll compressor unit, designated as a whole by 22, is provided in the first housing section 14, which has a first compressor body 24 which is stationarily arranged in the compressor housing 12, in particular in the first housing section 14, and a second compressor body 26 which is movable relative to the stationary compressor body 24.

The first compressor body 24 includes a compressor body base 32 over which a first spiral rib 34 rises and the second compressor body 26 also includes a compressor body base 36 over which a second spiral rib 38 rises.

The compressor bodies 24 and 26 are arranged relative to one another so that the spiral ribs 34, 38 mesh with one another, as shown in Fig. 3 shown to form at least one, preferably several, compressor chambers 42 between them, in which the gaseous medium, for example refrigerant, is compressed in that the second compressor body 26 moves with it its central axis 46 is moved forward about a central axis 44 of the first compressor body 24 on an orbital path 48 with a compressor orbital path radius, the volume of the compressor chambers 42 being reduced and ultimately compressed gaseous medium passing through a central outlet 52 ( Fig. 2 ) exits, while gaseous medium to be sucked in is sucked in through compressor chambers 42 that open on the circumference, radially on the outside with respect to the central axis 44.

The sealing of the compressor chambers 42 relative to one another takes place in particular in that the spiral ribs 34, 38 are provided on the front side with axial sealing elements 54 and 58, which rest sealingly on the respective bottom surface 62, 64 of the other compressor body 26, 24, the bottom surfaces 62 , 64 are formed by the respective compressor body base 36 or 32 and each lie in a plane running perpendicular to the central axis 44.

The scroll compressor unit 22 is accommodated as a whole in a first housing body 72 of the compressor housing 12, which has a front cover section 74 and a cylindrical ring section 76 which is integrally formed on the front cover section 74 and which in turn engages with a ring shoulder in a sleeve body 82 of the housing body 72, which is attached to a central housing body 84 forming the intermediate section 18 is formed, the central housing body 84 being closed on a side opposite the first housing body 72 by a second housing body 86, which forms an inlet chamber 88 for the gaseous medium.

The sleeve body 82 encloses the scroll compressor unit 22, the first compressor body 24 of which is supported on a contact surface 94 in the housing body 72 with support fingers 92 molded onto the compressor body base 32.

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

The first compressor body 24 is thus stationarily fixed in a precisely defined position within the first housing body 72 and thus also within the compressor housing 12.

The second movable compressor body 26, which must move on the orbital path 48 about the central axis 44 relative to the first compressor body 24, is guided in the axial direction with respect to the central axis 44 by an axial guide designated as a whole by 96, which connects the compressor body base 36 to one of the The spiral rib 38 supports and guides the underside 98 facing away from the spiral rib 38, specifically in the area 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 positioned stationarily in the compressor housing 12 and in the direction parallel to the central axis 44 in such a way that the axial sealing elements 58 remain on the bottom surface 64 and do not lift off from it, while at the same time the compressor body base 36 with the axial support surface 102 can slide transversely to the central axis 44 relative to the axial guide 96 ( Fig. 2 and 4 ).

For this, as in Fig. 2 shown, the axial guide 96 is formed by a carrier element 112, which is one of the axial support surfaces 102 ( Fig. 2 , 5 ) facing support surface 114, on which, however, the compressor body base 36 with the axial support surface 102 does not rest, but on which a sliding body 116, designated as a whole by 116 and in particular plate-shaped, rests with a sliding support surface 118, the sliding body 116 having a sliding support surface opposite the sliding support surface 118 122 ( Fig. 2 and 5 ) the axial support surface 102 ( Fig. 2 and 4 ) is supported against movements parallel to the central axis 44 but is supported in a sliding manner with respect to movements transverse to the central axis 44.

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

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 , on the other hand, the sliding body 116 in turn moves relative to the carrier element 118.

Thus, a sliding between the compressor body base 36 and the sliding body 116 takes place through a movement of the axial support surface 102 relative to the sliding support surface 122 of the sliding body 116 and the sliding support surface 118 of the sliding body 116 also slides relative to the support surface 114 of the support element 112.

In order to specify the limited two-dimensional mobility of the sliding body 116 parallel to a plane perpendicular to the central axis 44 relative to the support element 112, the sliding body 116 is through an in Fig. 5 and 6 shown and designated as a whole by 132 guided with play relative to the carrier element 112, the guide with play 132 comprising a guide recess 134 provided in the sliding body 116, which has a diameter DF, and a guide pin 136 anchored in the carrier element 112, the diameter of which DS is smaller than the diameter DF, so that half of the difference DF-DS defines a guiding orbital radius with which the sliding body 116 can carry out an orbiting movement relative to the carrier element 112.

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

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.

Furthermore, for example, due to the fact that the carrier element 112 is made of an aluminum alloy at least in the area of the carrier surface 114, improved lubrication is additionally ensured by the fact that lubricant enters the pores of the carrier element 112 and thus via the surface structures of the carrier element 112 provided, for example Area of the carrier surface 114 is available for building up the lubricating film in the gap.

Because the sliding body 116 itself is designed as a plate-shaped, annular part made of spring steel and thus the sliding support surface 118 facing the carrier surface 114 represents a smooth spring steel surface, the formation of the lubricating film is additionally promoted.

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 long-term running properties due to its wear resistance.

In the solution according to the invention, the carrier element 112 is not only provided with the carrier surface 114 on which the sliding body 116 rests, but also with the support surfaces 94 on which the support fingers 92 of the first compressor body 24 are supported.

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 suitable design of the carrier element 112, in particular by a single surface of the carrier element 112, which is both the carrier surface 114 and also includes the support surfaces 94.

Furthermore (as in Fig. 2 and 4 to 6 shown) the non-rotatable 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.

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

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 in a radially inner edge region 152 and in a radially outer edge region 154 with an inclined relative to the axial support surface 102 and set back from the axial support surface 102 Edge surface 156 or 158 is provided, which together with the sliding support surface 122 leads to a wedge-shaped gap that opens radially outwards or radially inwards, which facilitates the access of lubricant.

Furthermore, the build-up of the lubricating film between the sliding support surface 122 and the axial support surface 102 is promoted by the fact that the sliding support surface 122 and the axial support surface 102, in the overlap area in which they interact, are contiguous, that is to say in the circumferential direction U the central axis and uninterrupted annular surfaces 124 and 126 in their entire radial extent are formed, in particular the annular surface 126 of the axial support surface 102 extending from an inner contour IK with a radius IR of the same to an outer contour AK, the radius IR less than is two-thirds of an outer radius AR.

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 over its entire surface during all relative movements to the sliding support surface 122.

Like in the Fig. 2 to 6 shown, the axial support surface 102 and the sliding support surface 122 cooperating with it, as well as the support surface 114 and the sliding support surface 118 cooperating with it, all lie radially within a clutch 164 which has a plurality of coupling element sets 162, which are at equal radial distances from the central axis 44 and at equal angular distances in the direction of rotation U are arranged around the central axis 44 and together form a clutch 164, which prevents self-rotation of the second movable compressor body 26.

Each of these coupling element sets 162 includes, as shown in FIGS Fig. 2 , 6 and 7 shown, as the first coupling element 172 a pin body 174, which has a cylindrical lateral surface 176 and engages with this cylindrical lateral surface 176 in a second coupling element 182.

The second coupling element 182 is formed by an annular body 184 which has a cylindrical inner surface 186 and a cylindrical outer surface 188 which are arranged coaxially with one another.

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

In particular, a diameter DI of the inner wall surface 196 is larger than a diameter DRA of the cylindrical outer surface 188 of the ring body 184 and a diameter DRI of the cylindrical inner surface 186 is inevitably smaller than the diameter DRA of the cylindrical outer surfaces 188 of the ring body 184, whereby the diameter DRI of the cylindrical Inner surface 186 is larger than a diameter DSK of the cylindrical lateral surface 176 of the pin body 174.

Thus, each set of coupling elements 162 in turn forms an orbital guide whose maximum orbital radius OR for the orbiting movement corresponds to DI/2-(DRA-DRI)/2-DSK/2.

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 that, in each case one of the coupling element sets 162 is effective to prevent the self-rotation of the second movable compressor body 26, for example with six coupling element sets 162 after passing through an angular range of 60 °, the effectiveness of each coupling element set 162 from one coupling element set 162 to the next coupling element set 162 in the direction of rotation changes.

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, and on the other hand the lubrication in the area thereof is improved and also reduces the noise generated by the coupling element sets 162, which arises from the change in effectiveness from one coupling element set 162 to the other coupling element set 162.

It is particularly essential that the coupling element sets 162 experience sufficient lubrication, in particular lubrication between the cylindrical lateral surface 176 of the pin body 174 and the cylindrical inner surface 186 of the ring body 184 and lubrication between the cylindrical outer surface 188 of the ring body 184 and the cylindrical inner wall surface 196 of recording 194.

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, the ring bodies 184 being held on their sides facing away from the second compressor body 26 by a stop element 198 which projects radially inwards.

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

To accommodate the coupling elements 172 designed as pin bodies 174, the compressor body base 36 is provided with star-shaped extensions 212 which extend radially outwards and which engage in spaces 214 between support fingers 92 which follow one another in a direction of rotation U around the central axis 44, so that the coupling elements 172 also engage in these Intermediate spaces 214 lie and are therefore arranged within the housing body 72 at the largest possible radial distance from the central axis 44 ( Fig. 7 ).

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

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

The movable compressor body 24 is driven (as in Fig. 2 shown) by a drive motor designated as a whole by 222, for example an electric motor, which in particular has a stator 224 held in the central housing body 84 and a rotor 226 arranged within the stator 224, which is arranged on a drive shaft 228 which is coaxial with the central axis 44 the stationary compressor body 24 runs.

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

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

Medium, in particular the refrigerant, flows from the inlet chamber 88 formed by the second housing body 86 through the drive motor 222 in the direction of the bearing unit 232 facing the compressor, flows around it and then flows in the direction of the scroll compressor unit 22.

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

The eccentric drive 242 in particular includes an eccentric drive pin 244 held in the drive shaft 228, which moves a driver 246 on the orbital path 48 about the central axis 44, which in turn can be rotated about an eccentric pin axis 245 by a rotatable receptacle of the eccentric drive pin 244 in a drive pin receptacle 247 in the driver 246 the eccentric drive pin 244 is mounted and is also rotatably mounted about the central axis 46 of the orbitally movable compressor body 26 in a pivot bearing 248, in particular a rolling element bearing designed as a fixed bearing, the pivot bearing 248 allowing the driver 246 to rotate relative to the orbitally movable compressor body 26 about Center axis 46 allowed, as in Fig. 7 and 8th shown.

To accommodate the pivot bearing 248, as in the Fig. 11 shown, the second compressor body 26 is provided with an integrated driver receptacle 249, which accommodates the pivot bearing 248.

The driver receptacle 249 is set back relative to the flat side 98 of the compressor body base 36 and is thus arranged integrated in the compressor body base 36, so that the driving forces acting on the movable compressor body 26 are on a side facing the spiral rib 38 Flat side 98 of the compressor body base 36 are effective and thus drive the movable compressor body 26 with a low tilting moment, which is axially supported by the axial guide 96 in the direction of the central axis 44 between the driver receptacle 249 and the drive motor 222 on the axial support surface 102 and guided movably transversely to the central axis 44 is.

In the solution according to the invention, the driver receptacle is 249, as in the Fig. 2 and 11 shown surrounded by the axial support surface 102, which is external in the radial direction to the central axis 46, and the axial support surface 102 is in turn surrounded by the coupling element sets 162, which are external in the radial direction to the central axis 44, of the coupling 164, which prevents the self-rotation of the second compressor body 26.

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, can be variably adjusted, so that The movable compressor body 26, and thus also the central axis 46, can move radially outwards away from the central axis 44 so far that the spiral ribs 34, 38 rest against one another and seal the compressor chambers 42.

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 chosen to be larger than the intended compressor orbital radius VOR, that is, the distance of the central axes 44 and 46 from one another, and so large that the eccentric pin axis 245 is outside one through the two central axes 44 and 46 running through the central axis plane ME and opposite to a direction of rotation D of the drive shaft 228 at a distance from this ( Fig. 9 ).

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, based on the central axis 46 of the driver 246, acts on the central axis 46 and the driver 246 together with the movable compressor body 26, which leads to a force FC that moves radially outwards to the central axis 44, which acts in the central axis plane ME running through the central axis 44 and the central axis 46, and to which a force FO acts tangentially to the orbital path 48, which leads to the driver 246 together the movable compressor body 26 moves on the orbital path 48 about the central axis 44 ( Fig. 9 ).

The central axis plane ME defined by the central axes 44 and 46 represents a plane of symmetry to a system, formed from 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 a mass compensation plane ME.

For mass balancing, an orbital path balancing mass 252 is additionally provided, which counteracts the unbalance caused by the compressor body 26 moving on the orbital path 48 and compensates for this as far as possible, the orbital path balancing mass 252 also being designed and arranged symmetrically to the mass compensation plane ME, as in Fig. 10 shown.

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 which runs perpendicular to the mass balancing plane ME and through the central axis 44.

In contrast to solutions known from the prior art, the orbital orbit balancing 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.

For this purpose, the guide body 254 includes a pin receptacle 256 through which the eccentric drive pin 244 passes in order to accommodate the bearing body 254 so that it can rotate about the eccentric pin axis 245.

Furthermore, the guide body 254 is slidably guided on an alignment surface 262 of the drive shaft 228 facing it, for example on the front side of the drive shaft 228, with a guide surface 264 of the guide body 254 facing the alignment surface 262, parallel to an alignment plane 266 running perpendicular to the central axis 44 of the drive shaft 228, so that During all rotational movements about the eccentric pin axis 245, the parallel alignment of the guide body 245 to the alignment plane 266 is maintained and the orbital orbit balancing mass 252 thus moves on a path 268 around the drive shaft 228, which runs in a path plane 269 parallel to the alignment plane 266.

The advantage of this solution is that the orbital orbit balancing mass 252 can be completely decoupled from the driver 246 and is therefore no longer able to transmit tilting moments with respect to the central axes 44, 46 to the driver 246.

Rather, by guiding the guide body 254 relative to the drive shaft 228, the transmission of tilting moments from the guide body 254 to the eccentric drive pin 244 is largely avoided.

In order to hold the guide surface 264 in contact with the end face 262, an axial guide 272 is provided for the guide body 254 relative to the drive shaft 228, which in a first exemplary embodiment is designed as a screw 274 which has a recess or a breakthrough 276 in the guide body 254 with a Shaft section 278 interspersed with a Threaded section 282 engages in line with the central axis 44 coaxial threaded hole 284 in the drive shaft 228 and engages with a screw head 286 the opening 276 on a side 287 of the guide body 254 facing the driver 246 in order to bring the guide body 254 into contact with the alignment surface 262 by means of the guide surface 264 to keep.

However, 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 consisting of orbital orbit balancing mass 252 and guide body 254 about the eccentric pin axis 244 is possible, as in Fig. 13 shown.

The recess or opening 276 and the shaft section 278 of the screw 274 thus 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 a relative rotation of the guide body 254 relative to the eccentric drive pin axis 245 in the range of at least ± 1 ° (angular degree) to a maximum of ± 3 ° (angular degree), even better a maximum of ± 2 ° (angular degree) in order to enable tolerance compensation if the The aim is to adjust the orbital orbit balancing mass 252 in such a way that the orbital mass balancing is as optimal as possible.

In order to ensure rotational driving between the orbital orbit balancing mass 252 and the driver 246, which is rotatable relative to the eccentric drive pin 244, a coupling pin 292 is provided as a coupling body, which is arranged in a fixed manner on the guide body 254.

In order to realize the connection of the coupling pin 292 with the driver 246, the driver 246 is provided with a recess 296, which accommodates the coupling pin 292 with play, so that a rotational movement of the driver 246 about the eccentric pin axis 245 to avoid a tolerance-sensitive and possibly also overdetermined connection of the driver 246 rotatable by the precise mounting of the driver 246 relative to the eccentric drive pin 244 and the additional connection of the driver 246 with the coupling pin 292, which in turn is also rotatably mounted around the eccentric drive pin 244.

Preferably, the coupling pin 292 and the recess 296 are arranged so that the coupling pin 292 rests in normal operation on a portion of an inner wall surface 298 of the recess 296 that is located at the front in the direction of rotation.

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.

For this reason, in addition to the eccentric drive pin 244 engaging in the drive shaft 228, the coupling pin 292, which is firmly arranged on the guide body 254, is also used as a mass balancing body ( Fig. 8 ), which is arranged on the guide body 254 on a side of the mass compensation plane ME opposite the eccentric drive pin 244 ( Fig. 10 ) and thus together with the eccentric drive pin 244 in turn leads to a mass distribution that is at least approximately symmetrical to the mass compensation plane ME.

Preferably, a pin axis 294 of the coupling pin 292 and the eccentric pin axis 245 are arranged mirror-symmetrically to the mass compensation plane ME and, moreover, the eccentric drive pin 244 and the coupling pin 292 preferably have approximately the same mass ( Fig. 10 ).

For example, the coupling pin 292 is fixed to the guide body 254 in that the coupling pin 292 passes through a receiving hole 312 in the guide body 254 and is fixed in it by a press fit.

To axially determine the position of the coupling pin 292 on the guide body 254, the coupling pin 292 is also provided with a head 314, which rests on a side of the guide body 254 facing away from the driver 246 ( Fig. 16 ).

For further mass balancing, the drive shaft 228 is also provided with an unbalance compensation mass 322 facing the compressor and an unbalance compensation mass 324 facing away from the compressor ( Fig. 2 and 17 ).

The unbalance compensation mass 322 facing the compressor is preferably arranged between the drive motor 222 and the bearing unit 232 facing the compressor on a section 326 of the drive shaft 228 facing the compressor and radially within winding heads 332 of a stator winding, which lies on the same side of the transverse plane QE as the orbital path compensation lug 252 and is symmetrical to the mass compensation plane ME arranged.

The imbalance compensation mass 324 facing away from the compressor is preferably located on a section 328 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, as well as radially within winding heads 334 of the stator winding.

In a second embodiment of the solution according to the invention, shown in Fig. 18 , the axial guide 272 'for the guide body 254 is formed by a pin 342 formed on the drive shaft 228', which passes through the opening 276 of the guide body 254 with a shaft section 344 and carries a locking ring 346 which radially overlaps the opening 276 on the driver 246 facing side 287 is arranged and thus the guide body 254 is positioned in the same way as the screw head 286 so that the guide surface 264 is held in contact with the alignment surface 262.

The shaft section 344 therefore also interacts with the opening 276 and forms the first movement limiting unit 288'.

All other features of the second exemplary embodiment are identical to those of the first exemplary embodiment, so that full reference is made in this regard to the statements on the first exemplary embodiment.

In a third exemplary embodiment of the solution according to the invention, the axial guide 272" for the guide body 254 is formed by a projection 352, in particular a collar, which is formed on the eccentric drive pin 244" and, as in Fig. 19 shown, secures the guide body 254 against movement in the direction of the central axis 44 away from the alignment surface 262 and for this purpose, for example, engages in a recess 354 which extends into the guide body 254 from a side 287 facing the driver 246 ( Fig. 19 ).

In the third exemplary embodiment, the first movement limiting unit 288" is further formed by the head 314 of the mass balancing pin 292, which engages with play in an end-side recess or recess 362 in the drive shaft 228. The relative dimension of the head 314 and the recess 362 thus determines the limited rotatability of the guide body 254 relative to the drive shaft 228.

Otherwise, all other elements of the third exemplary embodiment are identical to those of the first exemplary embodiment, so that full reference can be made in this regard to the statements on the first exemplary embodiment.

In a fourth embodiment of the solution according to the invention, shown in Fig. 20 , the eccentric drive pin 244 interacts with the drive pin receptacle 247‴ only in a central section 372 of the same, which is arranged in the direction of the eccentric pin axis 245 in the drive pin receptacle 247‴ in such a way that it is perpendicular to a central axis 46 of the movable second compressor body 26 or vertically the central plane 374 of the pivot bearing 248, which runs to the eccentric pin axis 245 and lies centrally between its end face 376 and 378, is cut.

The middle section 372 has an extension in the direction of the eccentric pin axis 245 which corresponds to a maximum of half, even better a maximum of a third, of the extension of the drive pin receptacle 247"' in this direction.

End sections 382 and 384 of the drive pin receptacle 247' are arranged on both sides of the middle section 372, the diameter of which is larger than that of the middle section 372 and which extend in the direction of the eccentric pin axis 245 with approximately the same extent, which means that the end sections 382, 384 in particular differ in their extent by less than a factor of 2, so that in the area thereof a gap 386, 388 remains between the end sections 382 and 384 and the eccentric drive pin 244.

Thus, in this exemplary embodiment, the eccentric drive pin 244 acts on the driver 246 only in the middle section 372 and thus only in the area of the central plane 374, so that the pivot bearing 248 also does not experience any tilting moments on the driver 246 due to the action of the eccentric drive pin 244.

In the same way, the recess 296‴ for receiving the coupling pin 292 is designed so that the coupling pin 292 acts on the extension 296‴ in a middle section 392, the middle section 392 having a similar or comparable extension in the direction of the pin axis 294 as the middle section 372 of the drive pin holder 247‴.

Furthermore, end sections 394 and 396 of the recess 296' are also provided on both sides of the middle section 392, the diameter of which is larger than that of the middle section 392, so that gaps 402 and 404 are also formed between the end sections 394 and 396.

The end sections 394 and 396 extend in the direction of the pin axis 294 with approximately the same extent as the end sections 382 and 384, so that the same relationships exist relative to the middle section 392 as between the middle section 372 and the end sections 382 and 384.

Thus, in this exemplary embodiment, the coupling pin 292 also acts on the driver 246 only in the middle section 392 and thus only in the area of the central plane 374, so that no tilting moment acts on the driver 246 through the coupling pin 292.

This ensures in this exemplary embodiment that the pivot bearing 248, even if tilting moments occur in the area of the drive shaft 228 and should be transmitted through the eccentric drive pin 244 and even if tilting moments occur through the guide body 254 with the orbital balancing mass 252 and should be transmitted through the coupling pin 292 , can rotate essentially free of such tilting moments and therefore does not experience any reduction in its service life due to the tilting moment.

Claims (16)

1. A compressor, comprising a compressor housing (12), a scroll compressor unit (22) that is arranged in the compressor housing (12) and has a first, stationary compressor body (24) and a second compressor body (26) that is movable in relation to the stationary compressor body (24), of which first and second scroll vanes (34, 38), in the shape of a circle involute, engage in one another to form compressor chambers (42) when the second compressor body (26) is moved in relation to the first compressor body (24) on an orbital path (48), an axial guide (96) that supports the movable compressor body (26) to prevent movements in the direction parallel to a centre axis (44) of the stationary compressor body (24) and, in the event of movements, guides it in the direction transverse to the centre axis (44), an eccentric drive (242) for the scroll compressor unit (22), wherein the eccentric drive (242) has an entrainer (246) that is driven by a drive motor (222), that revolves on the orbital path (48) about the centre axis (44) of a drive shaft (228) and that itself cooperates with an entrainer receptacle (249) in the second compressor body (26), an orbital path compensating mass (252) that counters an unbalance caused by the compressor body (26) moving on the orbital path (48), and a coupling (164) that prevents the second compressor body (26) from rotating freely,
   characterised in that the orbital path compensating mass (252) is coupled to the eccentric drive (242) such that it moves on the orbital path (48) in a manner corresponding to movement of the entrainer (246) but is uncoupled in respect of the transmission of tilting moments to the entrainer (246), in that the orbital path compensating mass (252) is guided on the drive shaft (228) by a guide body (254) that cooperates with the drive shaft (228), in that the orbital path compensating mass (252) is guided by the guide body (254) acting on the drive shaft (228) on a path (268) that runs in a path plane (269) running parallel to an orientation plane (266) that runs perpendicular to the centre axis (44) of the drive shaft (228), in that the guide body (254) is guided on an orientation face (262) of the drive shaft (228) by a guide face (264), in that the guide body (254) is guided in relation to the drive shaft (228) by an axial guide (272), in that the axial guide (272) keeps the guide face (264) of the guide body (254) in abutment against the orientation face (262) of the drive shaft (228).
2. A compressor according to Claim 1, characterised in that the orbital path compensating mass (252) is guided on the orbital path (48) by an eccentric drive pin (244) that acts between the entrainer (246) and the drive shaft (228).
3. A compressor according to one of the preceding claims, characterised in that by way of a guide body (254) the orbital path compensating mass (252) acts on the eccentric drive pin (244), in particular being mounted rotatably thereon, in that in particular the guide body (254) is fixedly connected to the orbital path compensating mass (252), and/or in that in particular the eccentric drive pin (244) passes through a pin receptacle (256) in the guide body (254).
4. A compressor according to one of the preceding claims, characterised in that in particular the orientation face (262) provided on the drive shaft (228) is an end face of the drive shaft (228), and/or in that in particular the guide body (254) is arranged to engage over the orientation face (262), and/or in that in particular the guide body (254) is arranged between the orientation face (262) of the drive shaft (228) and the entrainer (246), and in that in particular the guide body (254) is configured to be plate-shaped.
5. A compressor according to one of the preceding claims, characterised in that in particular the axial guide (272) comprises an element (286, 346, 352) that acts on the guide body (254) on an opposite side to the guide face (264), in that in particular the element is a screw head (286) of a screw (274) engaging in the drive shaft (228), or in that in particular the element is a securing ring (346) that is fixed in relation to the drive shaft (228), or in that in particular the element is a projection (352) from the eccentric drive pin (244).
6. A compressor according to one of the preceding claims, characterised in that the guide body (254) is rotatable to a limited extent in relation to the eccentric drive pin (244), in that in particular between the drive shaft (228) and the guide body (254) there operates a first movement-limiting unit (288), in that in particular the first movement-limiting unit (288) permits free rotatability of the guide body (254) in relation to the drive shaft in the range of from 0.5° (angular degrees) to 5° (angular degrees), and/or in that in particular the first movement-limiting unit (288) is formed by an abutment body (314, 278, 342), which is held against the guide body (254) or the drive shaft (228), and a recess (362, 276) which receives the abutment body (314, 278, 342) and is arranged in the drive shaft (228) or the guide body (254).
7. A compressor according to one of the preceding claims, characterised in that a first movement-limiting unit (288) operates between the drive shaft (228) and the guide body (254) and permits limited free rotatability of the guide body (254) about an eccentric pin axis (245).
8. A compressor according to one of the preceding claims, characterised in that the orbital path compensating mass (252) is arranged symmetrically in relation to a mass compensating plane (ME) that runs through the centre axis (44) of the drive shaft (228) and the centre axis (46) of the movable second compressor body (26), in that in particular the orbital path compensating mass (252) is arranged on an opposite side, in relation to the eccentric drive pin (244), of a geometric transverse plane (QE) that runs perpendicular to the mass compensating plane (ME) and through the centre axis (44) of the drive shaft (228).
9. A compressor according to one of the preceding claims, characterised in that the eccentric drive pin (244) is arranged such that it is fixedly seated in the drive shaft (228) and engages in a drive pin receptacle (247) in the entrainer (246).
10. A compressor according to Claim 9, characterised in that the eccentric drive pin (244) and the drive pin receptacle (247) cooperate in a contact region (372) through which there passes a centre plane (374) that runs perpendicular to the centre axis (46) of the movable second compressor body (26) and in the direction of the centre axis (46), centrally with respect to a pivot bearing (248) for the entrainer (246), wherein the pivot bearing (248) operates between the second compressor body (26) and the entrainer (246), and in that on either side of the contact region (372) there is a gap (386, 388) between the eccentric drive pin (244) and the drive pin receptacle (247).
11. A compressor according to Claim 9 or 10, characterised in that the eccentric drive pin (244) and the drive pin receptacle (247) cooperate in a centre portion (372) of the drive pin receptacle (247), and/or in that in particular the drive pin receptacle (247) has a smaller diameter in the centre portion (372) than in end portions (382, 384) of the drive pin receptacle (247) lying either side of the centre portion (372) and each forming a gap (386, 388), and/or in that in particular the centre portion (372) of the drive pin receptacle (247) extends at most over half of the extent of the drive pin receptacle (247) in the direction of the eccentric pin axis (245), in that in particular the end portions (382, 384) arranged either side of the centre portion (372) differ in respect of their extent in the direction of the eccentric pin axis (245) by at most a factor of 2.
12. A compressor according to one of the preceding claims, characterised in that the orbital path compensating mass (252) is coupled by a coupling body (292) to the entrainer (246) for the purpose of rotational entrainment by the entrainer (246) when the entrainer (246) moves in rotation about the eccentric drive pin (244), in that in particular the coupling body (292) operates between the guide body (254) and the entrainer (246), and/or in that in particular the coupling body (292) is arranged such that it is fixedly seated on one of the guide body (254) and the entrainer (246) and engages in a recess (296) in the other of the guide body (254) and the entrainer (246), and/or in that in particular the coupling body (292) is arranged in the recess (296) with play, and/or in that in particular the coupling body (292) is configured as a coupling pin, in that in particular the coupling pin (292) is arranged such that it is fixedly seated on the guide body and engages in the recess (296) in the entrainer (246), in that in particular the coupling pin (292) and the recess (296) cooperate in a contact region (392) through which there passes a centre plane (374) that runs perpendicular to the pin axis (294) of the coupling pin (292) and in the direction of the pin axis (294), centrally with respect to a pivot bearing (248) for the entrainer (246), wherein the pivot bearing (248) operates between the second compressor body (26) and the entrainer (246), and in that on either side of the contact region (392) there is a gap (402, 404) between the coupling pin (292) and the recess (296), and/or in that in particular the coupling pin (292) and the recess (296) cooperate in a centre portion (392) of the recess (296), and/or in that in particular the recess (296) has a smaller diameter in the centre portion (392) than in end portions (394, 396) of the recess (296) lying either side of the centre portion (392) and each forming a gap (402, 404), and/or in that in particular the centre portion (392) of the recess (296) extends at most over half of the extent of the recess (296) in the direction of the pin axis (294), in that in particular the end portions (394, 396) arranged either side of the centre portion (392) differ in respect of their extent in the direction of the pin axis (294) by at most a factor of 2.
13. A compressor according to one of the preceding claims, characterised in that the eccentric drive (242) has the eccentric drive pin (244) that drives the entrainer (246) and a coupling body (292) that couples the orbital path compensating mass (252) to the entrainer (246), in that in particular the coupling body (292) also represents a mass compensating body, in that in particular the eccentric drive pin (244) and the coupling body (292) are arranged on mutually opposite sides of a mass compensating plane (ME), in that in particular the mass compensating plane (ME) runs through the centre axis (44) of the drive shaft (228) and the centre axis (44) of the orbitally movable compressor body, and/or in that in particular the coupling body (292) has a mass that differs from the mass of the eccentric drive pin (244) by at most 20%, in that in particular the coupling body (292) has substantially the same mass as the eccentric drive pin (244), and/or in that in particular the coupling body is configured as a mass compensating pin (292), in that in particular a pin axis (294) of the mass compensating pin (292) is arranged at the same spacing from the mass compensating plane (ME) as an eccentric pin axis (245) of the eccentric drive pin, in that in particular the pin axis (294) of the mass compensating pin (292) runs substantially parallel to the eccentric pin axis (245) of the eccentric drive pin (244), and/or in that in particular a pin axis (294) of the mass compensating pin (292) and the eccentric pin axis (245) of the eccentric drive pin (244) run parallel to the mass compensating plane (ME).
14. A compressor according to Claim 13, characterised in that the orbital path compensating mass (252) is arranged on an opposite side, in relation to the eccentric drive pin (244) and the mass compensating body (254), of a geometric transverse plane (QE) that runs perpendicular to the mass compensating plane (ME) and through the centre axis (44) of the drive shaft (228).
15. A compressor according to one of the preceding claims, characterised in that the drive shaft (228) has a compressor-facing portion (326), which carries a compressor-facing unbalance compensating mass (322) and the eccentric drive pin (244) and which in particular guides the mass compensating body (292) and the orbital path compensating mass (252), in that in particular the compressor-facing unbalance compensating mass (322) is arranged on the drive shaft (228) between a rotor (226) of the drive motor (222) and a front bearing unit (232).
16. A compressor according to one of the preceding claims, characterised in that the drive shaft (228) has a compressor-remote portion (328), which carries a compressor-remote unbalance compensating mass (324), in that in particular the compressor-remote unbalance compensating mass (324) 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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