EP3491245A1

EP3491245A1 - Compressor

Info

Publication number: EP3491245A1
Application number: EP16748088.8A
Authority: EP
Inventors: Dimitri Gossen
Original assignee: Bitzer Kuehlmaschinenbau GmbH and Co KG
Current assignee: Bitzer Kuehlmaschinenbau GmbH and Co KG
Priority date: 2016-07-27
Filing date: 2016-07-27
Publication date: 2019-06-05
Anticipated expiration: 2036-07-27
Also published as: CN109312745B; US20190170139A1; EP3491245B1; CN109312745A; US11326593B2; WO2018019372A1

Abstract

The invention relates to a compressor comprising a compressor housing; a scroll compressor unit which is arranged in the compressor housing and comprises a first stationary compressor body and a second compressor body that can be moved relative to the stationary compressor body; an eccentric drive for the scroll compressor unit, said drive having a driver which is driven by a drive motor and a driver which circulates about the central axis of a driveshaft on an orbital path; and an orbital path balancing mass which counteracts an imbalance due to the compressor body moving on the orbital path. The aim of the invention is to improve such a compressor such that the long-term stability of the driver guidance in the driver receiving area can be ensured even at high rotational speeds. This is achieved in that the orbital balancing mass is coupled to the eccentric drive such that the mass moves on the orbital path in a manner corresponding to the movement of the driver but is uncoupled with respect to the transmission of tilting moments to the driver.

Description

COMPRESSOR

The invention relates to a compressor, comprising a compressor housing, a arranged in the compressor housing volute compressor unit with a first, stationary compressor body and a second, movable relative to the stationary compressor body movable compressor body, which formed in the form of a Kreisvolvente first and second spiral ribs mesh to form compressor chambers when the second compressor body is moved relative to the first compressor body on an orbital track, an axial guide which moves the movable one

Compressor body against movements in the direction parallel to a central axis of the stationarily arranged compressor body is supported and at

Movements in the direction transverse to the central axis leads, an eccentric drive for the scroll compressor unit, one of a drive motor

driven and a circulating on the orbital path around the central axis of a drive shaft driver, which in turn cooperates with a driver receiving the second compressor body, an imbalance by the moving on the orbital path moving compressor body orbital path compensation mass and a self-rotation of the second compressor body preventing clutch.

Such compressors are known in the art.

A drive motor for such a compressor can be operated variable in number of revolutions, for example by means of an inverter, or at a constant speed. In these compressors is - especially at high speeds, which may be, for example, more than 6,000 revolutions per minute - the problem that the leadership of the driver in the driver receiving, has low long-term stability, especially if in the driver receiving a roller bearing, such as a cylindrical roller bearing, the Storage of the driver is provided.

The invention is therefore an object of the invention to improve a compressor of the generic type such that even at high speeds, the long-term stability of the leadership of the driver can be ensured in the driver seat.

This object is achieved in a compressor of the type described above according to the invention that the Orbitalbahnausgleichsmasse is coupled to the eccentric drive so that they are in accordance with the

Movement of the driver moves on the orbital track, but is decoupled with respect to the transmission of tilting moments on the driver.

The solution according to the invention is therefore based on the knowledge unknown from the prior art that in the known solutions with a rigid connection of the driver and Orbitalbahnausgleichsmasse at high speeds the Orbitalbahnausgleichsmasse with high tilting moments acts on the driver and thus the storage of the driver in the driver , Especially if this is done by a roller bearing, such as a cylindrical roller bearing, is exposed to high wear, since such bearings are exposed to occurring tilting moments increased wear.

The solution of the invention now solves the problem existing in the known solutions of acting on the driver with overturning orbital trajectory compensation by decoupling the driver of the Orbitalbahnausgleichsmasse such that it can no longer act with significant tilting moments on the driver. With regard to the guidance of the Orbitalbahnausgleichsmasse no further details were given.

In principle, it would be conceivable to support and guide the orbital path compensation mass relative to the drive shaft by means of a bearing element provided on the drive shaft.

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

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 Orbitalbahnausgleichsmasse so that it follows the orbital path of the driver to the

required mass balance due to the eccentricity of the orbital path of the driver to cause the drive shaft, without that a transfer of overturning moments of the Orbitalbahnausgleichsmasse takes place on the driver.

Alternatively or additionally, the object mentioned in the present invention is also achieved in that the orbital path compensation mass engages with a guide body on the eccentric drive pin, in particular is rotatably mounted on this.

In this case, a particularly simple connection between the Orbitalbahnausgleichsmasse and the Exzenterantriebszapfen can be produced.

Preferably, for this purpose, the guide body is firmly connected to the Orbitalbahnausgleichsmasse. It is particularly favorable if the eccentric drive pin passes through a pin receptacle of the guide body.

A structurally particularly favorable solution provides that the orbital track compensation mass is guided on the drive shaft by means of a guide body cooperating with the drive shaft.

This solution provides an additional relief of the eccentric drive pin, characterized in that now still an additional guide of the guide body is possible relative to the drive shaft.

Thus, the action of the eccentric drive pin on the guide body essentially serves to move the guide body with the orbital track balancing mass so that the orbital track balancing mass follows the orbital track of the driver and produces the required mass balance.

In particular, it is expedient for the orbital path compensation mass to be guided by the guide body acting on the drive shaft on a path which runs in a web plane which runs parallel to an alignment plane extending perpendicular to the center axis of the drive shaft.

This is achieved by the interaction between the guide body and the drive shaft that possibly occurring tilting moments are transmitted from the Orbitalbahnausgleichsmasse means of the guide body on the drive shaft and thus produce substantially no tilting moments acting on the eccentric drive shaft.

The leadership of the guide body on the drive shaft can be in

realize a wide variety of ways. A favorable solution provides that 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 and also with regard to the leadership of the guide body stable solution provides that the provided on the drive shaft alignment surface is an end face of the drive shaft.

Furthermore, the guide body can be optimally supported on the alignment surface when the guide body is arranged over the alignment surface.

With regard to the arrangement of the guide body, it is also favorable for reasons of space, when the guide body between the alignment surface of the drive shaft and the driver is arranged.

In this case, despite the provision of the guide body, it is possible to make the eccentric drive spatially small.

It is particularly advantageous if the guide body is plate-shaped, that is to say in the direction of the center axes, a dimension which is as small as possible transversely to the central axis, relative to its extent.

In order to ensure the guidance of the guide body by the drive shaft and to ensure in particular in all possible operating conditions is preferably provided that the guide body is guided relative to the drive shaft by an axial guide. In particular, the axial guide is designed so that this

Guide surface of the guide body holds in contact with the alignment surface of the drive shaft to ensure a sufficiently precise guidance of the guide body and thus the Orbitalbahnausgleichsmasse relative to the drive shaft.

The axial guide can be designed in different ways.

Preferably, the axial guide is formed so that it is a guide body on one of the guide surface opposite side

comprises acting element.

Such an element may be formed in a variety of ways.

In particular, it is provided that the element is a screw head of an engaging in the drive shaft screw.

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

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

For example, the axial guidance can be achieved by means of a screw engaging on the drive shaft and / or a collar on the eccentric drive pin and / or a pin formed on the drive shaft

Realize circlip. Furthermore, in order to make it possible for the guide body and the orbital track compensation mass to be able to align relative to the eccentric drive pin in accordance with the respective imbalance, it is preferably provided that the guide body is rotatable to a limited extent relative to the eccentric drive pin.

By such a limited rotation on the one hand ensures that the orientation of the guide body and thus the Orbitalbahnausgleichsmasse relative to the Exzenterantriebszapfen within a permissible

Twist, for example, at standstill of the compressor remains, but on the other hand, however, the guide body with the Orbitalbahnausgleichsmasse has the possibility according to the by the movement of the

Tailored on the orbital track generated unbalance to counteract this as well 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 limiting unit can be realized by independent elements.

A particularly favorable embodiment of the movement-limiting unit provides that the first movement-limiting unit by an on

Guide body or the drive shaft held stopper body and a stop body receiving and arranged on the drive shaft or the guide body recess is formed. A particularly advantageous solution provides, however, that the movement limiting unit is realized by the elements of the axial guide, so that the axial guide on the one hand causes the movement of the guide body in the axial direction, that is, in the direction of the central axes of either the drive shaft or the second movable compressor body and on the other hand simultaneously serves as a movement limiting unit.

Furthermore, it is favorable if the orbital path compensation mass on a side opposite the eccentric drive pin is perpendicular to the

Mass balance level and through the center axis of the drive shaft

extending geometric transverse plane is arranged.

Alternatively or in addition to the above-described features of a solution according to the invention provides a further solution of the above task that the Exzenterantriebszapfen is fixedly disposed in the drive shaft and engages in a drive pin receiving in the driver so that the driver by the action of the eccentric drive pin on this within the Drive pin receptacle is driven.

In this case, it is particularly advantageous if the eccentric drive pin and the drive pin receptacle cooperate in a contact region which is penetrated by a median plane which is perpendicular to the central axis of the movable second compressor body and in the direction of the central axis of a centrally acting between the second compressor body and the driver pivot bearing runs for the driver and that there is a gap between the eccentric drive pin and the drive pin receptacle on both sides of the contact area.

Alternatively, the position of the median plane can also be defined by the fact that it runs centrally perpendicular to the eccentric pin axis and in the direction of the eccentric pin axis through the pivot bearing for the driver. This solution has the great advantage that the eccentric drive pin acts with its the driver on the orbital motion moving force as close to this center plane of the pivot bearing and thus causes the

Force of the eccentric drive pin does not lead to acting on the driver tilting moments, which in turn have a reduction in the stability of the pivot bearing for the driver result.

It is particularly advantageous if the eccentric drive pin and the drive pin receiving cooperate in a central portion of the drive pin receiving, wherein in particular the central portion is defined by the fact that it is penetrated by the median plane.

In particular, it is provided that the drive pin receptacle in the central portion has a smaller diameter, than in both sides of the central portion lying and each forming a gap end portions of the drive pin receptacle.

Preferably, it is provided that the central portion of the drive pin receiving a maximum of half, more preferably more than a third, the extension of the drive pin receiving in the direction of

Eccentric pin axis expands.

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

This ensures that the contact area in which the

Eccentric drive pin acts on the drive pin receiving, is located as close to the center plane. Alternatively or in addition to the solutions described above, provides a particularly favorable solution that the Orbitalbahnausgleichsmasse is coupled by means of a coupling body with the driver for rotational drive by the driver in a rotational movement of the same about the Exzenterantriebszapfen.

The advantage of this solution is thus to be seen in the fact that so that the Orbitalbahnausgleichsmasse is always aligned so that they through

Arrangement and orientation of the driver conditional eccentric movement of the movable compressor body together with the driver and the

Mitnehmeraufnahme compensates.

This can be realized in a particularly simple manner by virtue of the fact that the coupling body is effective between the guide body and the driver.

In this case, the coupling body is preferably arranged fixed to one of the guide body and driver and engages in a recess in the other of the guide body and driver.

Preferably, it is provided that the coupling body is arranged with play in the recess.

Such a game is advantageously provided when both the guide body with the Orbitalbahnausgleichsmasse and the driver are each rotatably arranged to Exzenterantriebszapfen and thus the coupling body at a distance from the Exzenterantriebszapfen

is to be arranged so that a lack of play between the coupling body and the recess thus an overdetermination of the connection between the position of the coupling body and the recess would have relative to the Exzenterantriebszapfen result.

The proposed game thus avoids overdetermination and also serves to facilitate lubrication. In this case, in particular, the coupling body and the recess are arranged so that the coupling body abuts in normal operation of the compressor to a portion of a wall surface of the recess and consequently without an overdetermined positioning of the coupling body and

Recess nevertheless exists a defined orientation of the orbital track mass relative to the driver.

A particularly advantageous solution provides that the coupling body is designed as a coupling pin with which can be realized in a simple manner the connection for rotational drive between the Orbitalbahnausgleichsmasse and the driver.

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

To avoid that over the coupling pin tilting moments act on the driver is preferably provided that the coupling pin and the recess cooperate in a contact area, which is penetrated by a median plane perpendicular to the pin axis of the coupling pin and in the direction of the coupling pin centered between the second compressor body and the driver effective pivot bearing for the driver runs, and that there is a gap between the coupling pin and the recess on both sides of the contact region.

Thus, in the same way as in the drive of the driver by the Exzenterantriebszapfen 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 portion of the recess. This can be realized, for example, simply by the fact that the

Recess in the central portion has a smaller diameter than in the lying on either side of the central portion and each forming a gap end portions of the recess.

With regard to the extension of the

Related to the above statements no closer

Comments made.

It is preferably provided that the central portion of the recess extends over a maximum of half 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 central section differ by a maximum of a factor of 2 in terms of their extent in the direction of the journal axis.

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

It is particularly advantageous in this context if the coupling body also represents a mass balancing body. With this solution, in particular the conditional by the Exzenterantriebszapfen and asymmetric to the mass balance level unbalance of the Exzenterantriebszapfen can compensate in a simple manner and thus improve the smoothness of the compressor. Thus, an advantageous solution that the Exzenterantriebszapfen and the coupling body are arranged on opposite sides of a mass balance plane to compensate in addition to the coupling of the Orbitalbahnausgleichsmasse with the driver even the conditional by the Exzenterantriebszapfen unbalance and to improve the smoothness.

With regard to the course of the mass balance level, no further details have been provided so far.

Thus, an advantageous solution provides that the mass balance plane through the central axis of the drive shaft and the central axis of the orbiting

movable compressor body runs through and is precisely defined by these two central axes in their position and orientation.

In order to achieve the greatest possible smoothness, it is preferably provided that the coupling body has a mass which deviates from the mass of the eccentric drive spigot by a maximum of 20%, more preferably a maximum of 10% in order to achieve the greatest possible compensation of the imbalance caused by the eccentric drive spigot ,

Furthermore, it is preferably provided that the coupling body in

Essentially the same mass, in particular the same mass as the eccentric drive pin has.

In order to provide the same as possible with respect to the distribution of mass as the eccentric drive pin, it is preferably provided that the coupling body is designed as a mass balance pin. With respect to the arrangement of the axes of the mass balance pin and the eccentric drive pin is preferably provided that a pin axis of the mass balance pin is arranged at the same distance from the mass balance plane, such as an eccentric pin axis of the eccentric drive pin.

Furthermore, as far as the alignment of the axes is concerned, no further details have been given so far.

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

Furthermore, it is particularly advantageous if the pin axis of the mass balance pin and the eccentric pin axis of the eccentric pin extend parallel to the mass balance plane.

With regard to the arrangement of the mass balance pin, no further details have been given so far.

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

A particularly favorable solution provides that the mass balance pin is held on the guide body of the Orbitalbahnausgleichsmasse and thus moved with this and is aligned relative to the Exzenterantriebszapfen.

In the case of the formation of the mass balance body as a mass balance pin is further preferably provided that the mass balance pin engages in the recess provided in the driver. In the context of the solution according to the invention were no detailed

Information on the total carried out balancing described.

In particular, it is provided that the orbital track compensation mass described above is arranged symmetrically to the mass balance plane and thus does not cause unbalanced imbalance to the mass balance plane.

A particularly favorable solution further provides that the orbital track compensation mass is arranged on a side of the eccentric drive pin and the mass balance body opposite a perpendicular to the mass balance plane and extending through the central axis of the drive shaft geometric transverse plane.

With regard to a further unbalance compensation, in particular the drive shaft, no further details have been made in connection with the solutions described so far.

Thus, an advantageous solution provides that the drive shaft has a section facing the compressor, which faces a compressor

Imbalance compensation mass and the eccentric drive pin carries and in particular the mass balance body and the Orbitalbahnausgleichmasse leads.

Preferably, the imbalance compensation mass is arranged between a rotor of the drive motor and a front bearing unit on the drive shaft.

Furthermore, provides a favorable solution that the drive shaft a

Compressor facing away portion which carries a compressor imposing imbalance compensation mass. Also in this imbalance compensation mass is preferably provided that this is arranged between the rotor of the drive motor and a rear bearing unit of the drive shaft.

Preferably, it is also provided in these imbalance compensation masses, which are arranged on the drive shaft, that they are also formed and arranged symmetrically to the mass balance plane.

Further features and advantages of the invention are the subject of the following description and the drawings of some

Embodiments.

In the drawing show:

Fig. 1 is a perspective view of a first embodiment of a compressor according to the invention;

Fig. 2 is a longitudinal section along line 2-2 in Fig. 4;

3 is a schematic illustration of interdigitated spiral ribs and the orbital motion of one of the spiral ribs and a representation of the orbital path of the movable spiral rib relative to the stationary spiral rib.

Fig. 4 is a section along line 4-4 in Fig. 2;

Fig. 5 is a section along line 5-5 in Fig. 2;

6 is an enlarged view of a region A in FIG. 5;

Fig. 7 is a section along line 7-7 in Fig. 2; 8 is an exploded view of a cooperation between an eccentric drive pin of an orbital path compensation mass and a driver in the compressor according to the invention;

9 is a schematic geometric representation of the relative position of

Central axes of the compressor body and an eccentric pin axis;

Figure 10 is a plan view of a guide body with the Orbitalbahnausgleichsmasse in its position on the drive shaft with the guide body by cross-eccentric drive pin.

11 is an enlarged section along line 11-11 in FIG. 4;

Fig. 12 is a section along line 12-12 in Fig. 11 only with

Representation of the imbalance compensation mass and the guide body;

13 is a section similar to FIG. 12 when the first movement limitation unit is active;

14 shows a section along line 14-14 in the region of a cam receiver of the movable compressor body with a driver in FIG. 11 in the position according to FIG. 12; FIG.

FIG. 15 shows a section similar to FIG. 14 in the position according to FIG. 13; FIG.

16 is an enlarged section along line 16-16 in FIG. 4 by one

Mass balance pin;

Fig. 17 is a side view of a drive shaft with that of this

driven driver;

18 is an enlarged section along line 18-18 in FIG. 4 through a

second embodiment of a compressor according to the invention; 19 shows a section similar to FIG. 11 through a third embodiment of a compressor according to the invention and

Fig. 20 is a section similar to Fig. 11 by a fourth embodiment of a compressor according to the invention.

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

As shown in FIG. As shown in FIGS. 2 to 7, in the first housing section 14 there is provided, as a whole, a spiral compressor unit 22, which has a first one in the compressor housing 12, in particular in the first

Housing portion 14, stationary arranged compressor body 24 and a second relative to the stationary arranged compressor body 24 movable compressor body 26 has.

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

The compressor bodies 24 and 26 are arranged relative to one another such that the spiral ribs 34, 38 engage in one another, as shown in FIG. 3, between at least one, preferably a plurality of compressor chambers 42 to form, in which a compression of the gaseous medium, for example of refrigerant, takes place in that the second compressor body 26 with its center axis 46 is moved about a central axis 44 of the first compressor body 24 on an orbital path 48 having a compressor orbital trajectory VOR, wherein the volume of the compression chambers 42 is reduced and ultimately compressed gaseous medium exits through a central outlet 52 (FIG. 2) while gaseous medium being aspirated is sucked radially outwardly relative to the central axis 44 by circumferentially opening compressor chambers 42.

The sealing of the compression chambers 42 relative to each other also takes place, in particular, in that the spiral ribs 34, 38 are provided at the end with axial sealing elements 54 and 58 which abut sealingly against the respective bottom surface 62, 64 of the respective other compressor body 26, 24, the bottom surfaces 62 , 64 are formed by the respective compressor body base 36 and 32 and lie in a plane perpendicular to the central axis 44, respectively.

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

The sleeve body 82 encloses the scroll compressor unit 22, whose first compressor body 24 is connected to the compressor body base 32

molded support fingers 92 on a contact surface 94 in the housing body 72 is supported. In particular, the first compressor body 24 is fixed immovably in the housing body 72 against all movements parallel to the support surface 94.

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

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 relative to the central axis 44 in the axial direction by an axial guide as a whole 96, which the compressor body base 36 at one of Spiral rib 38 facing away from bottom 98, in the region of an axial support surface 102, supports and guides, so that the compressor body base 36 of the second compressor body 26 relative to the stationary in the

Compressor housing 12 positioned first compressor body 24 and is supported in the direction parallel to the central axis 44 such that the Axialdichtelemente 58 remain on the bottom surface 64 and not lift from this, while the compressor body base 36 with the Axialstützfläche 102 transversely to the central axis 44 slidably relative to the axial guide 96 can move (Figures 2 and 4).

For this purpose, as shown in FIG. 2, the axial guide 96 is formed by a carrier element 112 which has a carrier surface 114 facing the axial support surface 102 (FIGS. 2, 5) but on which the compressor body base 36 does not rest with the axial support surface 102 on which a slider plate 116, which is designated as a whole by 116 and in particular plate-shaped, rests with a sliding support surface 118, wherein the sliding body 116 with one of the sliding support surface 118 opposite Gleitstützfläche 122 (Figures 2 and 5), the Axialstützfläche 102 (Figures 2 and 4) against movements but supported slidably with respect to movements transverse to the central axis 44 leads. This prevents an axial movement of the second compressor body 26 in the direction of the central axis 44, a movement in a plane transversely,

in particular perpendicular to the central axis 44, however, allows.

The axial guide 96 according to the present invention provides that upon movement of the second compressor body 26 on the orbital path 48 about the central axis 44 of the first compressor body 24 on the one hand, the second compressor body 26 with the compressor body base 36 and the Axialstützfläche 102 moves relative to the slider 116 On the other hand, on the other hand, the sliding body 116 in turn moves relative to the support member 118.

Thus, a sliding between the compressor body base 36 and the slider 116 by a movement of the Axialstützfläche 102 relative to the Gleitstützfläche 122 of the slider 116 takes place and also occurs a sliding of the Gleitauflagefläche 118 of the slider 116 relative to the support surface 114 of the support member 112nd

In order to predetermine the limited two-dimensional movability of the sliding body 116 parallel to a plane perpendicular to the central axis 44 relative to the carrier element 112, the sliding body 116 is provided by a device shown in FIG. 5 and 6 shown and designated as a whole with 132 guide with play relative to the support member 112, wherein the guide with game 132 includes a sliding body 116 provided in the guide recess 134 which includes a

Diameter DF, as well as an anchored in the support member 112 guide pin 136 whose diameter DS is smaller than the diameter DF, so that half of the difference DF-DS defines a Führungsorbitalradius with which the slider 116 is an orbiting movement relative to the support member 112th can perform. The movements of the slider 116 is a structure of a

sufficient lubricating film between the Axialstützfläche 102 of the compressor body base 36 and the Gleitstützfläche 122 of the slider 116 and the support surface 114 and the Gleitauflagefläche 118th

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, 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, in addition, improved lubrication is ensured by lubricant entering the pores of the carrier element 112 and thus via the surface structures of the carrier element 112 in FIG Area of the support surface 114 is available for the construction of the lubricating film in the intermediate space.

Characterized in that the sliding body 116 itself is formed as a plate-shaped, annular part made of spring steel and thus the support surface 114 facing the sliding support surface 118 is a smooth Federstahloberfläche, the formation of the lubricating film is additionally promoted.

Furthermore, the material pairing of the aluminum alloy, which is softer in the region of the support surface 114 as spring steel, and the spring steel in

Area of Gleitauflagefläche 118 due to the wear resistance advantageous endurance properties.

In the solution according to the invention, the support member 112 is not only provided with the support surface 114 on which the slider 116 rests, but also with the support surfaces 94 on which the support fingers 92 of the first compressor body 24 are supported. This makes it possible to determine the position of the first compressor body 24 and the position of the second compressor body 26 in the direction of the central axis 44 relative to each other by suitable design of the support member 112, in particular by a single surface of the support member 112, which both the support surface 114 as also includes the bearing surfaces 94 takes place.

Further, as shown in Figs. 2 and 4 to 6, the rotationally fixed fixing of the support fingers 92 relative to the support member 112 by both the support member 112 and the support fingers 92 passing through positioning pins 142nd

The support member 112 is further arranged both axially in the direction of the central axis 44 and against rotational movements about the central axis 44 fixed in the housing body 72.

To further assure 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 recessed in a radially inward edge region 152 and in a radially outward edge region 154 having a tapered relative to the axial support surface 102 and opposed to the axial support surface 102 Edge surface 156 and 158 provided, which leads together with the Gleitauflagefläche 122 to a wedge-shaped radially outwardly or radially inwardly opening gap, which facilitates the access of lubricant.

Further, the structure of the lubricating film between the Gleitstützfläche 122 and the Axialstützfläche 102 is promoted by the fact that the Gleitstützfläche 122 and the Axialstützfläche 102, in the overlap region in which they cooperate as contiguous, that is in the direction of rotation U order the central axis and in their entire radial extent uninterrupted annular surfaces 124 and 126 are formed, wherein in particular the annular surface 126 of the Axialstützfläche 102 extends from an inner contour IK with a radius IR thereof up to an outer contour AK, wherein the radius IR less than two-thirds of an outer radius AR.

Further, the annular surface 124 of the Gleitstützfläche 122 is dimensioned so that the annular surface 126 of the Axialstützfläche 102 always rests fully on all relative movements to the Gleitstützfläche 122 on this.

As shown in FIGS. 2 to 6, the Axialstützfläche 102 and the cooperating with this Gleitstützfläche 122 and the support surface 114 and the cooperating Gleitauflagefläche 118 are all radially within a plurality of coupling element sets 162 having coupling 164, which at equal radial distances from the central axis 44 and at equal angular intervals in the circumferential direction U are arranged about the central axis 44 and together form a coupling 164, which prevents a self-rotation of the second movable compressor body 26.

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

The second coupling element 182 is formed by an annular body 184 having a cylindrical inner surface 186 and a cylindrical outer surface 188 which are coaxial with each other.

This second coupling element 182 is guided in a third coupling element 192, which is provided as one provided in the carrier element 112

Receiving 194 is formed for the annular body 184 and which has a cylindrical inner wall surface 196. 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 inevitably smaller than the diameter DRA of the cylindrical outer surfaces 188 of the annular body 184, wherein also the diameter DRI of the cylindrical Inner surface 186 is larger than a diameter DSK of the cylindrical lateral surface 176 of the pin body 174th

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

By sizing the orbital radius OR of the coupling element sets 162 to be slightly larger than the compressor orbital trajectory 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 each case one of the coupling element sets 162 is effective to prevent the self-rotation of the second movable compressor body 26, wherein, for example, with six coupling element sets 162 after passing through an angular range of 60 °, the effectiveness of each coupling element set 162 of a coupling element set 162 to the coupling element set next in the direction of rotation 162nd replaced.

Due to the fact that each coupling element set 162 three

Coupling elements 172, 182 and 192 and in particular an annular body 184 between the respective pin body 174 and the respective

Recording 194 is effective, on the one hand, the wear resistance of

Improved coupling element sets 162, on the other hand, the lubrication improved in the same area and also reduces the noise generated by the coupling element sets 162, which results from the change of effectiveness of a coupling element set 162 to the other coupling element set 162. It is particularly essential that the coupling element sets 162 undergo sufficient lubrication, in particular lubrication between the cylindrical surface 176 of the pin body 174 and the cylindrical inner surface 186 of the ring body 184 and lubrication between the cylindrical outer surface 188 of the ring body 184 and the cylindrical inner wall surface 196th the recording 194.

For optimal lubrication of the coupling element sets 162 are the

Receivers 194 in the support member 112 in the axial direction open on both sides, wherein the annular body 184 are held by their on the second compressor body 26 opposite sides by a radially inwardly projecting stop member 198.

In addition, further through holes 202, 204 are provided in the support member 112, the passage of lubricant and

allow ingested refrigerant.

To accommodate the coupling elements 172 embodied as pin bodies 174, the compressor body base 36 is provided with star-shaped projections 212 extending radially outwards, which engage in intermediate spaces 214 between supporting fingers 92 which follow each other in a direction of rotation U about the center axis 44, so that the coupling elements 172 likewise engage in these Gaps 214 are located and thus within the housing body 72 in the largest possible radial distance from the central axis 44 are arranged (Fig. 7).

This predetermined by the greatest possible radial distance of the coupling elements 172 positioning the coupling element sets 162 in a radial distance as possible from the central axis 44 has the advantage that due to the large lever arm acting on the coupling element sets 162 forces can be kept as small as possible , which has a positive effect on the component dimensioning. The inventive concept of the lubrication of the axial guide 96 and the coupling element sets 162 is particularly advantageous if the center axes 44 and 46 of the compressor body 24 and 26 lying normally, that is a maximum of an angle of 30 ° to a horizontal run, in the compressor housing 12, in particular in the region of the first housing body 72 at a lowermost position in the direction of gravity lubricant bath 210 forms, from the lubricant in operation

whirled up and thereby absorbed and distributed in the manner described.

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

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

is arranged.

The compressor-remote storage unit 234 is mounted, for example, in the second housing body 86, which closes the central housing body 84 on a side opposite the first housing body 72 side. Of the inlet chamber 88 formed by the second housing body 86 thereby sucked medium, in particular the refrigerant flows through the

Drive motor 222 in the direction of the compressor facing bearing unit 232, flows around this and then flows in the direction of the scroll compressor unit 22nd

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

The eccentric drive 242 comprises, in particular, an eccentric drive pin 244 held in the drive shaft 228, which moves a carrier 246 on the orbital path 48 about the central axis 44, which in turn rotatably engages about an eccentric pin axis 245 in a drive journal receptacle 247 in the driver 246 by rotatably receiving the eccentric drive pin 244 the eccentric drive pin 244 is mounted and also rotatably about the central axis 46 of the orbiting movable compressor body 26 rotatably mounted in a pivot bearing 248, in particular designed as a fixed bearing Wälzkörperlager, wherein the pivot bearing 248, a rotation of the driver 246 relative to the orbiting movable compressor body 26 to the Center axis 46 allowed, as shown in FIG. 7 and 8 shown.

For receiving the pivot bearing 248, as shown in FIGS. 11, the second compressor body 26 is provided with an integrated catch receptacle 249 which receives the pivot bearing 248.

The driver receptacle 249 is relative to the flat side 98 of the

The compressor body base 36 is reset and thus arranged integrated in the compressor body base 36, so that the forces acting on the movable compressor body 26 driving forces on one of the spiral rib 38 side facing the Flat side 98 of the compressor body base 36 are effective and thus drive with low tilting moment the movable compressor body 26, viewed axially through the axial guide 96 in the direction of the central axis 44 between the Mitnehmeraufnahme 249 and the drive motor 222 on the Axialstützfläche 102 and guided transversely to the central axis 44 movable is.

In the solution according to the invention, the cam receiver 249, as shown in FIGS. 2 and 11 surrounded by the radial direction to the central axis 46 outer Axialstützfläche 102 and the Axialstützfläche 102 is in turn of the radial direction to the central axis 44 outer coupling element sets 162 of the self-rotation surrounded by the second compressor body 26 preventing coupling 164.

Due to the rotatability of the carrier 246 about the eccentric pin axis 245 and about the center 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 one

Compressor body 26, and thus also the central axis 46, each so far away from the central axis 44 can move away radially outwardly that the spiral ribs 34, 38 abut each other and the compressor chambers 42 close tight.

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 greater than the intended Verdichterorbitalradius VOR, that is, the distance of the center axes 44 and 46 from each other, and so large that the eccentric pin axis 245 outside of a through the two center axes 44th and 46 through

extending center axis ME and opposite to a direction of rotation D of the drive shaft 228 at a distance therefrom (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, a force FA, which relative to the central axis 46 of the driver 246 acting on the central axis 46 and the driver 246th together with the movable one

Compressor body 26 radially to the central axis 44 outwardly moving force FC leads, in the through the central axis 44 and the central axis 46th

extending center axis plane ME acts, and to which a force acting tangentially to the orbital path 48 FO, which moves the driver 246 together with the movable compressor body 26 on the orbital path 48 about the central axis 44 (Fig. 9).

The center axis ME defined by the central axes 44 and 46 represents a plane of symmetry to a system formed by the mass of the drive shaft 228 and the mass of the movable compressor body 26 together with the mass of the driver 246 and is also referred to as the mass balance plane ME.

For mass balance, an orbital path compensation mass 252 is additionally provided, which is the imbalance by the on the orbital path 48

moving compressor body 26 counteracts and this as possible

is compensated, wherein the orbital path compensation mass 252 is formed and arranged symmetrically to the mass balance plane ME, as shown in Fig. 10.

In this case, the orbital path compensation mass 252 lies, in particular, on a side of the eccentric drive pin 244 facing away from a perpendicular to the mass balance plane ME and through the central axis 44 extending transverse plane QE.

In contrast to solutions known from the prior art, the orbital path compensation mass 252 is not held on the driver 246 but is mounted with a guide body 254 on the drive shaft 228, in particular on the eccentric drive pin 244. For this purpose, the guide body 254 comprises a pin receptacle 256 which passes through the eccentric drive pin 244 in order to rotatably receive the bearing body 254 about the eccentric pin axis 245.

Further, the guide body 254 is slidably guided on an alignment surface 262 of the drive shaft 224 facing the alignment surface 262 on a guide surface 264 of the guide body 254 facing the alignment surface 262 parallel to an alignment plane 266 running perpendicular to the center axis 44 of the drive shaft 228 on an alignment surface 266 facing the drive shaft 228, so that during all rotational movements about the eccentric pin axis 245, the parallel alignment of the guide body 245 to the alignment plane 266 is maintained and thus the orbital path compensation mass 252 moves on a path 268 about the drive shaft 228, which runs in a parallel to the alignment plane 266 web plane 269.

The advantage of this solution is the fact that the orbital path equalization mass 252 is 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 the leadership of the guide body 254 relative to

Drive shaft 228 already largely avoided the transmission of tilting moments of the guide body 254 on the eccentric drive pin 244.

In order to hold the guide surface 264 in abutment with the end face 262, an axial guide 272 is provided for the guide body 254 relative to the drive shaft 228, which is formed in a first embodiment as a screw 274 having a recess or an opening 276 of the guide body 254 with a Shank portion 278 interspersed, with a Threaded portion 282 in line with the central axis 44 coaxial threaded bore 284 engages in the drive shaft 228 and with a screw head 286 the opening 276 on a driver 246 facing side 287 of the guide body 254 overlaps the guide body 254 by means of the guide surface 264 in contact with the alignment surface 262nd to keep.

In this case, 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 of orbital track balancing mass 252 and guide body 254 about the eccentric pin axis

244 is possible, as shown in Fig. 13.

Thus, the recess or opening 276 and the shaft portion 278 of the screw 274 form a first movement limiting unit 288 for the relative movement of the guide body 254 to the drive shaft 228.

The movement limiting unit 288 preferably allows relative rotation of the guide body 254 relative to the eccentric drive pin axis

245 in the range of at least ± 1 ° (angle degree) to a maximum of ± 3 ° (angle degree) even better than ± 2 ° (angle degree) to allow for a tolerance compensation when the orbital alignment 252 has a tendency to adjust so that the best possible Orbital mass equalization takes place.

In order to ensure a rotational drive between the Orbitalbahnausgleichsmasse 252 and the relative to the Exzenterantriebszapfen 244 rotatable driver 246 is provided as a coupling body, a coupling pin 292 which is fixedly arranged 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 receives the coupling pin 292 with play, thereby rotating the driver 246 about the eccentric pin axis 245 to

Avoiding a tolerance sensitive and possibly also overdetermined connection of the driver 246 rotatable by the one hand precise bearing of the driver 246 relative to the Exzenterantriebszapfen 244 and the additional connection of the driver 246 with the coupling pin 292, which in turn is also rotatably mounted about the Exzenterantriebszapfen 244 to achieve.

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

The mass not taken into account in the mass balance described above is the mass of the eccentric drive pin 244, which is arranged asymmetrically with respect to the mass balance plane ME and in particular leads to oscillations at high rotational speeds of the drive shaft 228.

For this reason, in addition to the engaging in the drive shaft 228 eccentric drive pin 244 still arranged on the guide body 254 coupling pin 292 as mass balance body (Fig. 8), which is arranged on the guide body 254 on a the Exzenterantriebszapfen 244 opposite side of the mass balance plane ME (Fig. 10) and thus together with the eccentric drive pin 244 in turn leads to a mass balance plane ME at least approximately symmetrical mass distribution. Preferably, a trunnion axis 294 of the coupling pin 292 and the eccentric pin axis 245 are arranged mirror-symmetrically with respect to the mass balance plane ME, and also preferably the eccentric drive pin 244 and the coupling pin 292 have approximately the same mass (FIG. 10).

For example, the fixation of the coupling pin 292 takes place at the

Guide body 254 characterized in that the coupling pin 292 passes through a receiving bore 312 in the guide body 254 and is fixed in this by a press fit.

For axially fixing the position of the coupling pin 292 on the guide body 254, the coupling pin 292 is still provided with a head 314 which rests on a side of the guide body 254 facing away from the driver 246 (FIG. 16).

For further mass balance, the drive shaft 228 is still provided with a compressor-facing imbalance compensation mass 322 and a compressor imbalance compensation mass 324 (FIGS. 2 and 17).

The compressor-facing imbalance compensation mass 322 is preferably between the drive motor 222 and the compressor-facing bearing unit 232 on a compressor-facing portion 326 of the drive shaft 228 and radially within winding heads 332 of a stator winding

it is located on the same side of the transverse plane QE as the orbital alignment mass 252 and is arranged symmetrically to the mass balance plane ME.

The compressor imbalance balancing mass 324 is preferably located on a compressor facing away portion 328 of the drive shaft 228 and between the drive motor 222 and the compressor facing away from storage unit 234, as well as radially within winding heads 334 of the stator winding. 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 integrally formed on the drive shaft 228, which engages with a shaft portion 344 the opening 276 of the guide body 254 and a securing ring 346 carries, which the aperture 276 is arranged radially overlapping on the driver 246 side facing 287 and thus the guide body 254 in the same manner as the screw head 286 positioned so that the guide surface 264 is held on the alignment surface 262 in abutment.

Thus, the shaft portion 344 also cooperates with the aperture 276 and forms the first movement limiting unit 288 '.

All other features of the second embodiment are identical to those of the first embodiment, so that in this respect to the

Embodiments of the first embodiment is fully incorporated by reference.

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

In the second embodiment, the first movement limiting unit 288 "is further formed by the head 314 of the mass balance pin 292, which mates with play in an end recess or recess 362 in the drive shaft 228. Thus, by the relative dimension of the head 314 and the recess 362 limited rotation of the guide body 254 relative to the drive shaft 228 set. Incidentally, all other elements of the third embodiment are identical to those of the first embodiment, so that in this respect the comments on the first embodiment can be fully incorporated by reference.

In a fourth embodiment of the solution according to the invention, shown in FIG. 20, an interaction of the eccentric drive pin 244 with the drive pin receptacle 247 "'only in a central portion 372 thereof, which is so arranged in the direction of the eccentric pin axis 245 in the drive pin receptacle 247' 'that this from a direction perpendicular to a central axis 46 of the movable second compressor body 26 or perpendicular to the eccentric pin axis 245 extending center plane 374 of the pivot bearing 248, which is located centrally between the end face 376 and 378, is cut.

The central portion 372 has an extension in the direction of the eccentric pin axis 245 which corresponds to a maximum of half, more preferably a maximum of one third of the extension of Antrisbszapfenaufnahme in this direction.

End sections 382 and 384 of the drive pin receptacle 247 '', whose diameter is greater than that of the middle section 372 and which extend in the direction of the eccentric pin axis 245 approximately with the same extent, which means that in particular the end sections 382, 384, are arranged on both sides of the middle section 372 differ by less than a factor of 2 in their extension, so that in the region thereof in each case a gap 386, 388 between the end portions 382 and 384 and the eccentric drive pin 244 remains. Thus, the eccentric drive pin 244 acts in this embodiment, the driver 246 only in the central portion 372 and thus only in the region of the median plane 374, so that thereby the pivot bearing 248 by the action of the Exzenterantriebszapfens 244 and the driver 246 experiences no tilting moments.

In the same way, the recess 296 "'for receiving the

Coupling pin 292 formed so that the coupling pin 292 in a central portion 392 of the extension 296 '' 'acts on this, wherein the central portion 392 has a similar or comparable extent in the direction of the pin axis 294 as the central portion 372 of the drive pin receptacle 247' '.

Further, both sides of the central portion 392 end portions 394 and 396 of the recess 296 '' are provided, whose diameter is greater than that of the central portion 392, so that also between the

End sections 394 and 396 column 402 and 404 form.

The end portions 394 and 396 extend in the direction of the journal axis 294 approximately the same extent as the end portions 382 and 384, so that relative to the central portion 392 are the same relations as between the central portion 372 and the end portions 382 and 384th

Thus, the coupling pin 292 acts in this embodiment, the driver 246 also only in the central portion 392 and thus only in the region of the median plane 374, so that by the coupling pin 292 also no overturning moment acts on the driver 246. This ensures in this embodiment that the pivot bearing 248, even if in the drive shaft 228 tilting moments occur and should be transmitted through the Exzenterantriebszapfen 244 and even if through the guide body 254 with the Orbitalausgleichsmasse 252 tilting moments occur and should be transmitted through the coupling pin 292 , Can rotate substantially free of such tilting moments and thus undergoes no Kippmomentbedingte reduction its life.

Claims

P A T E N T A N S P R E C H E

A compressor comprising a compressor housing (12), one in the

Compressor housing (12) arranged spiral compressor unit (22) having a first stationary arranged compressor body (24) and a second relative to the stationary arranged compressor body (24) movable compressor body (26) whose formed in the form of a Kreisvolvente first and second spiral ribs (34, 38) interlock with formation of compression chambers (42), when the second

Compressor body (26) relative to the first compressor body (24) on an orbital path (48) is moved, an axial guide (96) which the movable compressor body (26) against movements in the direction parallel to a central axis (44) of the stationarily arranged

Compressor body (24) supported and when moving in the direction transverse to the central axis (44), an eccentric (242) for the scroll compressor unit (22), one of a drive motor (222) and driven on the orbital path (48) around the Central axis (44) of a drive shaft (228) rotating cam (246), which in turn cooperates with a cam receiver (249) of the second compressor body (26), an unbalance by the on the orbital track (48) moving compressor body (26) counteracting Orbitalbahnausgleichsmasse (252) and a self-rotation of the second compressor body (26) preventing clutch (164),

characterized in that the orbital path compensation mass (252) is coupled to the eccentric drive (242) so as to move on the orbital path (48) in accordance with the movement of the follower (246) but decoupled from the driver (246) with respect to the transmission of overturning moments is. 2. A compressor according to claim 1, characterized in that the orbital track balancing mass (252) by a between the

Driver (246) and the drive shaft (228) acting eccentric drive pin (244) on the orbital track (48) is guided.

3. A compressor according to the preamble of claim 1 or any one of the preceding claims, characterized in that the Orbitalbahnausgleichsmasse (252) with a guide body (254) on the Exzenterantriebszapfen (244) engages, in particular rotatably mounted on this.

4. A compressor according to claim 3, characterized in that the

Guide body (254) is firmly connected to the Orbitalbahnausgleichsmasse.

5. A compressor according to claim 3 or 4, characterized in that the eccentric drive pin (244) passes through a pin receptacle (256) of the guide body (254).

6. Compressor according to one of the preceding claims, characterized

in that the orbital path compensation mass (252) is guided on the drive shaft (228) by means of a guide body (254) cooperating with the drive shaft (228).

7. A compressor according to claim 6, characterized in that the

Orbitalbahnausgleichsmasse (252) is guided by the on the drive shaft (228) engaging the guide body (254) on a track (268) extending in a web plane (269) which is parallel to a perpendicular to the central axis (44) of the drive shaft (228)

extending alignment plane (266) extends. 8. A compressor according to claim 6 or 7, characterized in that the guide body (254) with a guide surface (264) on an alignment surface (262) of the drive shaft (288) is guided.

9. A compressor according to claim 8, characterized in that on the drive shaft (228) provided alignment surface (262) is an end face of the drive shaft (228).

10. A compressor according to claim 8 or 9, characterized in that the guide body (254) is arranged over the alignment surface (262).

11. A compressor according to any one of claims 6 to 10, characterized in that the guide body (254) between the alignment surface (262) of the drive shaft (228) and the driver (246) is arranged.

12. A compressor according to any one of claims 3 to 11, characterized in that the guide body (254) is plate-shaped.

13. A compressor according to any one of claims 6 to 12, characterized in that the guide body (254) relative to the drive shaft (228) by an axial guide (272) is guided.

14. A compressor according to claim 13, characterized in that the

Axial guide (272) the guide surface (264) of the guide body (254) in abutment against the alignment surface (262) of the drive shaft (228) holds.

15. A compressor according to claim 13 or 14, characterized in that the axial guide (272) comprises a guide body (254) on one of the guide surface (264) opposite side acting element (286, 346, 352). 16. A compressor according to claim 15, characterized in that the element is a screw head (286) in the drive shaft (228) engaging screw (274).

17. A compressor according to claim 15, characterized in that the element is a relative to the drive shaft (228) fixed retaining ring (346).

18. A compressor according to claim 15, characterized in that the element is a on the eccentric drive pin (244) arranged projection (352).

19. A compressor according to any one of claims 6 to 18, characterized in that the guide body (254) relative to the Exzenterantriebszapfen (244) is limited rotation.

20. A compressor according to claim 19, characterized in that

between the drive shaft (228) and the guide body (254) a first movement limiting unit (288) is effective.

21. A compressor according to claim 20, characterized in that the first movement limiting unit (288) allows free rotation of the guide body (254) relative to the drive shaft in the range of 0.5 ° (angle degree) to 5 ° (angular degree).

22. A compressor according to claim 20 or 21, characterized in that the first movement limiting unit (288) by an am

Guide body (254) or the drive shaft (228) held

Stop body (314, 278, 342) and a stop body (314, 278, 342) receiving and on the drive shaft (228) and the guide body (254) arranged recess (362, 276) is formed. 23. A compressor according to any one of claims 6 to 22, characterized in that between the drive shaft (228) and the guide body (254) a first movement limiting unit (288) is effective, which a limited free rotation of the guide body (254) about an eccentric pin axis ( 245) allows.

24. Compressor according to one of the preceding claims, characterized

characterized in that the orbital path compensation mass (252) is arranged symmetrically to a mass balance plane (ME) passing through the central axis (44) of the drive shaft (228) and the central axis (46) of the movable second compressor body (26).

25. A compressor according to claim 24, characterized in that the

Orbitalbahnausgleichsmasse (252) on a the eccentric drive pin (244) opposite side of a perpendicular to the mass balance plane (ME) and through the central axis (44) of the drive shaft (228) extending geometric transverse plane (QE) is arranged.

26. A compressor according to the preamble of claim 1 or any one of the preceding claims, characterized in that the Exzenterantriebszapfen (244) in the drive shaft (228) is arranged tightly and in a drive pin receptacle (247) in

Driver (246) intervenes.

27. A compressor according to claim 26, characterized in that the eccentric drive pin (244) and the drive pin receptacle (247) in a contact region (372) cooperate, of a perpendicular to the central axis (46) of the movable second compressor body (26) and in the direction of Central axis (46) centrally one between the second compressor body (26) and the driver

(246) effective pivot bearing (248) for the driver (246)

extending median plane (374) is penetrated and that on both sides of the contact region (372) there is a gap (386, 388) between the eccentric drive pin (244) and the drive pin receptacle (247).

28. A compressor according to claim 26 or 27, characterized in that the eccentric drive pin (244) and the drive pin receptacle

(247) in a central portion (372) of the drive pin receptacle (247) cooperate.

29. A compressor according to any one of claims 26 to 28, characterized in that the drive pin receptacle (247) in the central portion (372) has a smaller diameter than in both sides of the central portion (372) lying and in each case a gap (386, 388) forming end portions ( 382, 384) of the drive pin receptacle (247).

30. A compressor according to any one of claims 27 to 29, characterized in that the central portion (372) of the drive pin receptacle (247) extends over a maximum of half the extent of the drive pin receptacle (247) in the direction of the eccentric pin axis (245).

31. A compressor according to claim 30, characterized in that the

on both sides of the central portion (372) arranged end portions (382, 384) differ in terms of their extent in the direction of the eccentric pin axis (245) a maximum of a factor of 2. 32. A compressor according to the preamble of claim 1 or any one of the preceding claims, characterized in that the orbital path compensation mass (252) by means of a coupling body (292) with the driver (246) for rotational driving through the

Driver (246) is coupled to the eccentric drive pin (244) during a rotational movement of the driver (246).

33. A compressor according to claim 32, characterized in that the coupling body (292) between the guide body (254) and the driver (246) is effective.

34. A compressor according to claim 32 or 33, characterized in that the coupling body (292) on one of guide body (254) and driver (246) is fixedly arranged and in a recess (296) in the other of guide body (254) and driver (246) intervenes.

35. Compressor according to one of claims 32 to 34, characterized in that the coupling body (292) with play in the

Recess (296) is arranged.

36. Compressor according to one of claims 32 to 35, characterized in that the coupling body (292) is designed as a coupling pin.

37. Compressor according to one of the preceding claims, characterized

in that the coupling pin (292) is fixedly arranged on the guide body and engages in the recess (296) in the driver (246). Compressor according to claim 37, characterized in that the coupling pin (292) and the recess (296) cooperate in a contact region (392) extending from one perpendicular to the pin axis (294) of the coupling pin (292) and in the direction of the pin axis (294). centrally of a between the second compressor body (26) and the driver (246) effective pivot bearing (248) for the

Carrier (246) extending median plane (374) is interspersed and that on both sides of the contact region (392) there is a gap (402, 404) between the coupling pin (292) and the recess (296).

A compressor according to claim 37 or 38, characterized in that the coupling pin (292) and the recess (296) cooperate in a central portion (392) of the recess (296).

Compressor according to claim 37 to 39, characterized in that the recess (296) in the central portion (392) has a smaller diameter than lying on both sides of the central portion (392) and in each case a gap (402, 404) forming end portions (394, 396) the recess (296).

Compressor according to claim 39 or 40, characterized in that the central portion (392) of the recess (296) expands a maximum of half the extent of the recess (296) in the direction of the pin axis (294).

Compressor according to claim 41, characterized in that on both sides of the central portion (392) arranged end portions (394, 396) differ in terms of their extension in the direction of the pin axis (294) a maximum of a factor of 2. 43. A compressor according to the preamble of claim 1 or any one of the preceding claims, characterized in that the eccentric drive (242) driving the driver (246)

Eccentric drive pin (244) and a the Orbitalbahnausgleichs- mass (252) with the driver (246) coupling coupling body (292).

44. A compressor according to claim 43, characterized in that the coupling body (292) also represents a mass balancing body.

45. A compressor according to claim 44, characterized in that the eccentric drive pin (244) and the coupling body (292) on opposite sides of a mass balance plane (ME) are arranged.

46. A compressor according to claim 45, characterized in that the mass balance plane (ME) passes through the central axis (44) of the drive shaft (228) and the central axis (44) of the orbiting movable compressor body.

47. A compressor according to any one of claims 44 to 46, characterized in that the coupling body (292) has a mass which deviates from the mass of the Exzenterantriebszapfens (244) by a maximum of 20%.

48. A compressor according to any one of claims 44 to 47, characterized in that the coupling body (292) has substantially the same mass as the eccentric drive pin (244).

49. Compressor according to one of claims 44 to 48, characterized in that the coupling body is designed as a mass balance pin (292). 50. A compressor according to claim 49, characterized in that a pin axis (294) of the mass balance pin (292) at the same distance from the mass balance plane (ME) is arranged as an eccentric pin axis (245) of the eccentric drive pin.

51. A compressor according to claim 50, characterized in that the

Pin axis (294) of the mass balance pin (292) in

Substantially parallel to the eccentric pin axis (245) of the eccentric drive pin (244) extends.

52. Compressor according to one of claims 49 to 51, characterized in that a pin axis (294) of the mass balance pin (292) and the eccentric pin axis (245) of the eccentric drive pin (244) parallel to the mass balance plane (ME).

53. A compressor according to any one of claims 44 to 52, characterized in that the Orbitalbahnausgleichsmasse (252) on a the eccentric drive pin (244) and the mass balance body (254) opposite side of a perpendicular to the mass balance plane (ME) and through the central axis (44) of the Drive shaft (228)

extending geometric transverse plane (QE) is arranged.

54. Compressor according to one of the preceding claims, characterized

characterized in that the drive shaft (228) has a compressor-facing portion (275) which carries a compressor-facing imbalance compensation mass (272) and the eccentric drive pin (244) and in particular the mass balance body (292), and the Orbitalbahnausgleichsmasse (252) leads.

55. Compressor according to claim 54, characterized in that the

Compressor facing balancing mass (272) between a rotor (226) of the drive motor (222) and a front bearing unit (232) on the drive shaft (228) is arranged. 56. Compressor according to one of the preceding claims, characterized in that the drive shaft (228) has a compressor-facing portion (278) carrying a compressor imbalance balancing mass (274).

57. A compressor according to claim 56, characterized in that the

Compressor unbalanced balancing mass (274) between the rotor (226) of the drive motor (222) and a rear bearing unit (234) of the drive shaft (228) is arranged.