EP3810935B1 - Scroll compresor with de-coupable orbiting counter weight - 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 which can be moved in orbit relative to the stationary compressor body, the first and second spiral ribs of which are designed in the form of a circular involute to form compressor chambers interlock 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 rotating on the orbital path around the central axis of a drive shaft and rotatably mounted relative to the drive shaft about an eccentric drive axis, which in turn interacts with a driver receptacle of the second compressor body, one of an imbalance caused by the moving on the orbital path Compressor body counteracting and also rotatably mounted around the eccentric drive axis orbital track balancing mass and a coupling that prevents the second compressor body from rotating.

Such compressors are from the prior art, for example WO 2018/019372 known.

The problem with these known compressors is to be able to control as optimally as possible the centrifugal force generated by the compressor body, which can be moved on the orbital path.

This object is achieved according to the invention by a compressor of the type described at the outset in that the driver and the orbital orbital balancing mass can be coupled to one another with a coupling unit in such a way that the coupling unit is effective when the drive shaft is rotating in a centrifugal force-coupling state in such a way that the orbital orbital balancing mass is subject to a centrifugal force of at least one Driver and the unit comprising the orbiting compressor body counteracts that the coupling unit is effective when the drive shaft is rotating in a centrifugal force decoupling state in such a way that the orbital path balancing mass does not counteract the centrifugal force of the unit comprising at least the driver and the orbiting compressor body and that the coupling unit is separated from the centrifugal force decoupling by means of a positioning device State can be converted into the centrifugal force decoupling state or vice versa.

Out of JP H09 195957 A and JP 3 467746 B2 Other scroll compressors are known in which the orbiting compressor body and/or a balancing mass are displaced relative to the axis of rotation of the drive shaft depending on the speed in order to counteract centrifugal force loads.

The advantage of the solution according to the invention can therefore be seen in the fact that it opens up the possibility of allowing the centrifugal force as such to act to its full extent or, if necessary, counteracting the centrifugal force and thus adapting the force acting on the spiral ribs radially to the central axis of the drive shaft to different operating states.

It is preferably provided that the coupling unit comprises two coupling elements, one of which is connected to the orbital orbit balancing mass and one to the driver.

Preferably, the coupling elements can be brought into the centrifugal force-coupling and centrifugal-force-decoupling states by a movement relative to one another.

The coupling elements can be connected to the orbital orbit balancing mass and the driver in a variety of ways.

For example, a movable connection would be conceivable.

A particularly advantageous solution provides that a coupling element is firmly connected to the orbital orbit balancing mass or the driver and the other coupling element is firmly connected to the driver or the orbital orbit balancing mass.

This enables a structurally very simple arrangement of the coupling elements relative to the orbital orbit balancing mass and the driver.

In principle, the coupling elements can be designed in any way.

A structurally particularly favorable solution provides that one of the coupling elements is a coupling body and another of the coupling elements is a receptacle into which the coupling body engages.

In this case, it is particularly favorable if the coupling body engages in the receptacle with play in order to be able to realize the centrifugal force coupling state and the centrifugal force decoupling state.

A particularly favorable solution provides that the coupling body in the centrifugal force-coupling state rests against a portion of the receptacle and thus interacts with the receptacle and is arranged in contactless relation to the receptacle in the centrifugal force-decoupling state, so that the coupling body and the receptacle do not interact.

The coupling body could be constructed in a variety of ways.

An advantageous solution provides that the coupling body is designed as a coupling pin.

A particularly simple implementation of the coupling unit provides that the coupling pin is connected to the orbital orbit balancing mass and engages in the receptacle connected to the driver.

In order to realize the different states of the coupling unit, it is conceivable, for example, to provide an actuator or a spring-controlled or friction-controlled drive.

It is preferably provided that the positioning device operates in a speed-controlled manner and, in particular, brings the coupling unit into the centrifugal force-decoupling state below a switching speed of the drive shaft and, above the switching speed, brings the coupling unit into the centrifugal-force-coupling state, so that the positioning device reacts only to the speed of the drive shaft either the centrifugal force-decoupling state or brings about the centrifugal force coupling state.

The positioning device can theoretically be arranged on the orbital orbit balancing mass or the driver.

A particularly favorable solution provides that the positioning device is arranged on the drive shaft.

In order to be able to realize the centrifugal force-coupling and the centrifugal-force-decoupling state of the coupling elements of the coupling unit, it is preferably provided that a positioning device allows the coupling elements to interact in the centrifugal-force-coupling state and, in the centrifugal-force-decoupling state, positions the coupling elements in a contact-free manner relative to one another and thus prevents the coupling elements from interacting.

The positioning device can be constructed in a particularly simple manner if it has a positioning body, which is guided on the drive shaft by means of a guide body with at least one component in the radial direction to the central axis and can be moved along the guide body depending on the speed.

The speed-dependent movement of the positioning body can be implemented in a variety of ways.

For example, it would be conceivable to provide separate masses that react to the speed of the drive shaft.

A structurally particularly simple solution provides that the positioning body is acted upon by means of a spring-elastic force accumulator against a centrifugal force acting on the positioning body.

This means that the positioning body itself reacts to the speed of the drive shaft in that the centrifugal force acting on it tends to move the positioning body away from the drive shaft, while the resilient energy storage counteracts this centrifugal force.

It can thus be achieved that the positioning body assumes a position close to the drive shaft up to the switching speed due to the force effect of the spring-elastic energy storage and from the switching speed onwards the centrifugal force of the positioning body overcomes the force of the spring-elastic energy storage and thus the spring-elastic energy storage moves to an increasing distance moved by the drive shaft.

In order to be able to transfer the position of the positioning body to the coupling unit, it is preferably provided that the positioning body is provided with a positioning surface which acts on the coupling unit depending on a radial position of the positioning body.

It is preferably provided that the positioning body brings the coupling unit into its centrifugal force-decoupling state in a first position which corresponds to a speed below the switching speed, and brings the coupling unit into its centrifugal force-coupling state in a position which corresponds to a speed above the switching speed.

This solution has the great advantage that at low speeds, due to the centrifugal force decoupling state of the coupling unit, the full centrifugal force of the unit consisting of compressor body and driver acts on the spiral ribs and at a speed above the switching speed, the centrifugal force of the compressor body and driver is counteracted by the orbital track balancing mass.

It is particularly expediently provided here that the positioning device can be used to bring the coupling element connected to the orbital orbit balancing mass relative to the coupling element connected to the driver into the centrifugal force-coupling or centrifugal-force-decoupling state.

In the simplest case, it is provided that the positioning device brings the orbital orbit balancing mass together with the coupling element into the centrifugal force decoupling state or the centrifugal force coupling state.

No further information has yet been provided regarding the position of the orbital orbit balancing mass in the centrifugal force coupling state and the centrifugal force decoupling state.

An advantageous solution provides that the orbital orbit balancing mass is in the centrifugal force decoupling state of the coupling unit with its center of mass at a distance from the mass compensation plane and in the centrifugal force coupling state of the coupling unit with its center of mass close to or even better in the mass balancing plane.

This solution has the great advantage that there is a slight imbalance at low speeds because the center of mass of the orbital orbit balancing mass is not in the mass balancing plane, but this unbalance is of little relevance.

In contrast, this solution has the great advantage that at higher speeds in the centrifugal force-coupling state of the coupling unit, the center of mass of the orbital orbit balancing mass is close to or preferably in the mass balancing plane and thus an optimal mass balancing is available.

In addition, the solution according to the invention provides that a first movement limiting unit is effective between the drive shaft and the orbital orbit balancing mass.

With this first limiting unit, a position range of the orbital path compensation mass relative to the drive shaft and relative to the compressor body can be specified in a simple manner.

A particularly favorable solution provides that the central axis of the drive shaft and a central axis of the movable second compressor body define a mass compensation plane running through it and that the first movement limiting unit places the orbital path compensation mass on a side opposite the eccentric drive axis of a geometrical plane running perpendicular to the mass compensation plane and through the central axis of the drive shaft Transverse plane holds.

In particular, it is preferably provided that the first movement limiting unit aligns the orbital orbit balancing mass in such a way that a center of mass thereof remains within an unbalance tolerance range extending across the mass balancing plane and on both sides thereof, so that excessive unbalances caused by the orbital orbit balancing mass can be prevented by the first movement limiting unit.

A particularly simple solution to this provides that the first movement limiting unit allows the guide body to rotate freely about the eccentric drive axis in an angular range of 0.5° (angular degrees) to 5° (angular degrees).

With regard to the implementation of the first movement limitation unit, a wide variety of possibilities are also conceivable.

An advantageous solution provides that the first movement limiting unit is supported by a first stop element held on the orbital orbit compensation element, in particular on its guide body, or on the drive shaft, and a first stop element which interacts with the first stop element, in particular receiving it, on the drive shaft or the orbital orbit compensation mass, in particular its guide body , arranged second stop element is formed.

With regard to the storage of the orbital orbit balancing mass, no further information was provided in connection with the previous description of the solution according to the invention.

An advantageous solution provides that the orbital orbit balancing mass is rotatably mounted with a guide body about the eccentric axis.

In the simplest case, the guide body is firmly connected to the orbital orbit balancing mass.

A particularly simple and robust design implementation provides that the orbital track balancing mass is rotatably mounted about the eccentric axis by an eccentric drive pin that interacts with the driver and the drive shaft.

In the simplest case it is provided that the eccentric drive pin passes through a pin receptacle of the guide body.

A further advantageous solution provides that the orbital orbit balancing mass interacts with the drive shaft by means of the guide body and is guided on the drive shaft and can therefore be guided in a defined orientation relative to 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.

In particular, it is advantageous if the orbital path 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.

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 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 preferably provided that the guide body is guided relative to the drive shaft by an axial guide.

In particular, the axial guide is designed such 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 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.

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.

A particularly advantageous solution provides that the eccentric drive has an eccentric drive pin that drives the driver and a coupling body that couples 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, 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.

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.

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 einem Mitnehmer bei dem erfindungsgemäßen Kompressor und einer Positioniervorrichtung;

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 einem den Führungskörper durchgreifendem Exzenterantriebszapfen und einem Kopplungszapfen entsprechend Linie 10-10 in Fig. 11;

Fig. 11

einen vergrößerten Schnitt längs Linie 11-11 in Fig. 10;

Fig. 12

einen Schnitt längs Linie 12-12 in Fig. 10;

Fig. 13

einen Schnitt ähnlich Fig. 10 bei aktiver erster Bewegungsbegrenzungseinheit;

Fig. 14

einen Schnitt ähnlich Fig. 10 bei inaktiver erster Bewegungsbegrenzungseinheit;

Fig. 15

einen Schnitt längs Linie 15-15 in Fig. 11 im Bereich einer Mitnehmeraufnahme des bewegbaren Verdichterkörpers mit einem Mitnehmer in einem zentrifugalkraftkoppelnden Zustand einer Kopplungseinheit;

Fig. 16

eine Darstellung ähnlich Fig. 9 zur Erläuterung der Verhältnisse gemäß Fig. 15;

Fig. 17

einen Schnitt ähnlich Fig. 15 in einem zentrifugalkraftentkoppelnden Zustand der Kopplungseinheit;

Fig. 18

eine Darstellung ähnlich Fig. 9 zur Erläuterung der Verhältnisse in Fig. 17;

Fig. 19

eine vergrößerte perspektivische Ansicht der Antriebswelle mit der Positioniervorrichtung im zusammengebauten Zustand und;

Fig. 20

einen Schnitt längs Linie 20-20 in Fig. 19.

Shown in the drawings:

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, an orbital orbit balancing mass, a driver in the compressor according to the invention and a positioning device;

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 and a coupling pin corresponding to line 10-10 in Fig. 11 ;

Fig. 11

an enlarged section along line 11-11 in Fig. 10 ;

Fig. 12

a cut along line 12-12 in Fig. 10 ;

Fig. 13

a cut similar Fig. 10 when the first movement limitation unit is active;

Fig. 14

a cut similar Fig. 10 when the first movement limitation unit is inactive;

Fig. 15

a cut along line 15-15 in Fig. 11 in the area of a driver receptacle of the movable compressor body with a driver in a centrifugal force coupling state of a coupling unit;

Fig. 16

a similar representation Fig. 9 to explain the circumstances Fig. 15 ;

Fig. 17

a cut similar Fig. 15 in a centrifugal force decoupling state of the coupling unit;

Fig. 18

a similar representation Fig. 9 to explain the conditions in Fig. 17 ;

Fig. 19

an enlarged perspective view of the drive shaft with the positioning device in the assembled state and;

Fig. 20

a cut along line 20-20 in Fig. 19 .

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 its central axis 46 about a central axis 44 of the first compressor body 24 on an orbital path 48 moves with a compressor orbital orbit radius VOR, whereby the volume of the compressor chambers 42 is reduced and ultimately compressed gaseous medium flows 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 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 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 stationary in the Compressor housing 12 positioned first compressor body 24 and is supported 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 slides transversely to the central axis 44 relative to the axial guide 96 can move ( 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, denoted 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 until 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 in the circumferential direction U around the central axis and in their entire radial extent uninterrupted annular surfaces 124 and 126 are formed, in particular the annular surface 126 of the axial support surface 102 extending from an inner contour IK with a radius IR thereof to an outer contour AK, the radius IR being less than 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, wherein in the compressor housing 12, in particular in the area of the first housing body 72, a lubricant bath 210 is formed at a point lowest in the direction of gravity, from which lubricant is whirled up during operation and 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, preferably firmly inserted therein, which moves a driver 246 on the orbital path 48 about the central axis 44, which in turn moves through a rotatable receptacle of the eccentric drive pin 244 in a drive pin receptacle 247 in the driver 246 is rotatably mounted on the eccentric drive pin 244 about an eccentric axis 245 and is also rotatably mounted about the central axis 46 of the orbiting compressor body 26 in a rotary bearing 248, in particular a rolling element bearing designed as a fixed bearing, the rotary bearing 248 allowing the driver 246 to rotate relative to the orbitally movable compressor body 26 about the central axis 46 is 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 effective on a side of the flat side 98 of the compressor body base 36 facing the spiral rib 38 and thus drive the movable compressor body 26 with a low tilting moment, which is axially supported by the axial guide 96 in the direction of the central axis 44 between the driver receptacle 249 and the drive motor 222 on the axial support surface 102 and is guided movably transversely to the central axis 44.

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 axis 245 and about the central axis 46, as in Fig. 9 shown, 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, variably adjustable, so that the movable compressor body 26, and thus also the central axis 46, respectively can move radially outwards so far from the central axis 44 that the spiral ribs 34, 38 rest against each other under force at the point of contact 322 and seal the compressor chambers 42.

For this purpose, in particular, the distance of the eccentric 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 between the central axes 44 and 46 from one another, and so large that the eccentric 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 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, the force FC moves radially outwards to the central axis 44, which is in the central axis plane ME running through the central axis 44 and the central axis 46 acts and places the spiral ribs 34, 38 against one another, and which leads to a force FO acting tangentially to the orbital path 48, which moves the driver 246 together with the movable compressor body 26 on the orbital path 48 around the central axis 44 moves in a direction of rotation D ( Fig. 9 ).

The central axis plane ME defined by the central axes 44 and 46 represents a reference plane for a system, formed from the mass of the drive elements comprising the eccentric drive 242 on the one hand and the mass of the unit 250 made up of the movable compressor body 26 together with the mass of the driver 246 and the pivot bearing 248 on the other hand , whose center of mass SOS lies in the central axis plane ME, and is also referred to as the mass balance plane ME, since all centers of mass contributing to the optimal possible mass balance should be close to or in this.

An orbital orbit balancing mass 252 ( Fig. 10 ) is provided, which counteracts the imbalance caused by the unit 250 moving on the orbital path 48 consisting of compressor body 26, driver 246 and pivot bearing 248 and compensates for it as far as possible, the orbital path balancing mass 252 with its center of mass SOAGM being arranged as close as possible to the mass compensation plane ME, as in Fig. 10 or 13 and 14 shown.

The orbital orbit balancing mass 252 lies in particular on a side of a transverse plane QE which runs perpendicular to the mass balancing plane ME and runs through the central axis 44, facing away from the eccentric drive pin 244 and the central axis 46, in particular on the opposite side.

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 on the drive shaft 228 with a guide body 254, in particular on the eccentric drive pin 244.

For this purpose, the guide body 254 includes a pin receptacle 256, which the eccentric drive pin 244 driving the driver 246 passes through in order to accommodate the bearing body 254 so that it can rotate about the eccentric 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 axis 245, the parallel alignment of the guide body 254 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 ( Fig. 10 , 11 ).

The advantage of this solution can be seen in the fact that the orbital orbit balancing mass 252 is decoupled from the driver 246 with regard to possible tilting moments 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.

To keep the guide surface 264 in contact with the end surface 262, as in Fig. 11 shown, an axial guide 272 is provided for the guide body 254 relative to the drive shaft 228, which has a projection 274 arranged on the eccentric drive pin 244, for example a collar, and which protects the guide body 254 against movement in Direction of the central axis 44 away from the alignment surface 262 and for this purpose, for example, engages in a recess 276, which extends limitedly into the guide body 254 from a side 278 of the guide body 254 facing the driver 246.

A first movement limiting unit 280 for limiting a relative movement of the guide body 254 to the drive shaft 228 in order to keep the center of mass SOAGM of the orbital orbit balancing mass 252 close to the optimal possible position for the mass balancing, that is to say at a short distance from the mass balancing plane ME, and not to have excessive deviations from the optimal position, which corresponds to a position of the center of mass SOAGM in the mass compensation plane ME, includes, as in Fig. 12 shown, a stop body 282 firmly connected to the guide body 254 and arranged at a distance from the eccentric drive pin 244, which engages in a recess 284 in the drive shaft 228, which extends from its end face 262 into the drive shaft 228 and the stop body 282 with play takes up and thus allows the guide body 254 a limited rotational work and the eccentric axis 245 relative to the drive shaft 228.

The stop body 282 is preferably designed as the head of a coupling pin 292 which passes through the guide body 252 and will be explained in more detail below and which in turn also cooperates with the driver 246.

For example, the coupling pin 292 is fixed to the guide body 254 in that the coupling pin 292 passes through a receiving hole 288 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 its head 282, which rests on a side of the guide body 254 facing away from the driver 246 ( Fig. 12 ).

The first movement limiting unit 280 preferably allows a relative rotation of the guide body 254 about the eccentric drive axis 245, which lies within an angular range of at least 2° (angular degrees), up to a maximum of 4° (angular degrees), even better a maximum of 6° (angular degrees), in order to enable tolerance compensation , whereby the orbital orbit balancing mass 252 should be aligned relative to the drive shaft 228, in particular relative to the central axis 44, in such a way that the orbital mass balancing is as optimal as possible ( Fig. 14 ).

The first movement limiting unit 280 is in particular dimensioned so that - without any additional action - the unit 260, comprising the orbital orbit balancing mass 252 and the guide body 254, the orbital orbit balancing mass 252, aligns itself in such a way that a center of mass SOAGM of the unit 260 made up of orbital orbit balancing mass 252, guide body 254 and the coupling pin 292 of a coupling unit 300 on a side of the transverse plane QE opposite the eccentric pin 244 and within a plane extending beyond the mass compensation plane ME and on both sides of the mass compensation plane ME in Fig. 13 and Fig. 14 The remaining unbalance tolerance range UWT remains, so that the possible unbalances are limited to a tolerable level.

The unit 260 consisting of the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 with the center of mass SOAGM brings about the optimal possible mass balance to the unit 250 consisting of the orbiting compressor body 26 with the pivot bearing 248 and the driver 246 with the center of mass SOS when the centers of mass are SOAGM and SOS are as close as possible to the mass balance level ME.

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, acts as a mass balancing body ( Fig. 8 ), formed and 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 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 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. 13, 14 ).

In order to have the possibility of a coupling between the orbital orbit balancing mass 252 and the driver 246 which is rotatable relative to the eccentric drive pin 244, the coupling unit 300 includes, in addition to the coupling pin 292 with its pin axis 294, a recess 296 in the driver 246 which forms a receptacle and into which the coupling pin 292 is located extends and which receives the coupling pin 292 with play, so that a second movement limiting unit is available to prevent a rotational movement of the driver 246 about the eccentric axis 245 in order to avoid a tolerance-sensitive and possibly also overdetermined connection of the driver 246 relative to the guide body 254 and thus in turn relative to the drive shaft 228 through the precise mounting of the driver 246 relative to the eccentric drive pin 244 and the additional connection of the driver 246 to the coupling pin 292, which in turn is also rotatably mounted about the eccentric drive pin 244 ( Fig. 14 ).

To realize a centrifugal force-coupling state ( Fig. 15 and 16 ) of the coupling unit 300, the coupling pin 292 and the recess 296 are arranged relative to one another in such a way that the coupling pin 292 can rest on a partial region 304 of an inner wall surface 298 of the recess 296 which is located at the front in the direction of rotation D, which makes it possible to resist the centrifugal force FZsos Unit 250, formed from the orbiting compressor body 26, the driver 246 and the pivot bearing 248, which acts in the sense of increasing the compressor orbital radius VOR in addition to the force FC and thus generates a speed-dependent contact force in a contact point 322 of the spiral ribs 34, 38 to counteract.

This is done because the coupling pin 292 rests on the front portion 304 of the recess 296 in the direction of rotation D, and thus counteracts the centrifugal force FZsos, since the unit 260 consisting of the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 296 strives to have its center of mass SOAGM to rotate in the direction of rotation D about the eccentric axis 245 (and consequently to move away from the mass compensation plane ME) while due to the centrifugal force FZsos the unit 250 consisting of the orbiting compressor body 26, the driver 246 and the pivot bearing 248 tends to move in the opposite direction to the direction of rotation D to move the eccentric axis 245 ( Fig. 16 ).

In particular, by suitable arrangement of the coupling pin 292 and the recess 296 it can be achieved that the unit 260 consisting of the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 lies with its center of mass SOAGM on a side of the transverse plane QE opposite the center of mass SOS and has the tendency to rotate in the direction of rotation D around the eccentric axis 245 ( Fig. 16 ).

The coupling pin 292 acting on the recess 296 in the partial area 304 acts - as in Fig. 16 shown - in the partial area 304, based on the eccentric axis 245, a torque generated by the force FD _SOAGM on the driver 246, which corresponds to the torque acting on the driver 246 due to the centrifugal force FZsos, also related to the eccentric axis 245 and generated by the force FDsos, counteracts and thereby reduces the centrifugal force FZsos to the centrifugal force FZR. This reduction in the centrifugal force FZsos depends on the mass in the center of mass SOAGM.

On the other hand, the above-mentioned arrangement of the coupling pin 292 and the recess 296 can ensure that the center of mass SOAGM in the centrifugal force-coupling state lies close to or preferably in the mass compensation plane ME on a side of the central axis 44 opposite the center of mass SOS, and thus essentially optimal mass balance to the unit 250 consisting of the orbiting compressor body 26, the driver 246 and the pivot bearing 248.

A realization of an in Fig. 17 and 18 The centrifugal force decoupling state of the coupling unit 300 shown occurs due to a mutual rotation of the unit 260 about the eccentric axis 245 opposite to the direction of rotation D and a displacement of the pin axis 294 opposite to the direction of rotation into a position 294e ( Fig. 17 and 18 ), so that contact between the coupling pin 292 and the recess 296 is no longer possible, and the center of mass SOAGM is at a distance from the mass compensation plane ME. Thus, the speed-dependent centrifugal force FZsos acting in the center of mass SOS is fully effective in the contact point 322 of the spiral ribs 34, 38, while the unit 260 consisting of the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 with its center of mass SOAGM relative to the drive shaft 228, as follows described in detail, the center of mass SOAGM lies on a side of the transverse plane QE opposite the center of mass SOS and at a short distance from the mass compensation plane ME.

In order to be able to utilize both the centrifugal force decoupling state of the coupling unit 300 and the centrifugal force coupling state of the coupling unit 300 in the compressor according to the invention, as in the Fig. 8 and 19 to 20 shown, on the drive shaft 228 as The entire speed-dependent positioning device, designated 332, is provided for determining or releasing the rotational positions of the unit 260 consisting of the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 relative to the drive shaft 228.

This positioning device 332 comprises a guide body 336 which can be fixed in the drive shaft 228 and extends with its central axis 334 radially to the drive shaft 228, which in the simplest case is designed as a cylindrical pin which can be fixed in a receiving bore 338 of the drive shaft 228, for example by a screw 339 passing through it is, which forms a guide surface 342 on the circumference, along which a positioning body 344 is guided movably parallel to the central axis 334 and thus radially to the drive shaft 228.

The positioning body 344 is acted upon by a spring 346, which is supported on the one hand with a radially inner end on the positioning body 344 and with a radially outer end on a stop 348, which is designed, for example, as a disk body fixed to the guide body 336 by means of the screw 339 is.

The spring 346 acts on the positioning body 344, which acts on the positioning body 344 in the direction of a radially inner stop 352, which is formed, for example, on the guide body 336.

The positioning body 344 is thus movable in a direction radial to the central axis 44 in the opposite direction to the force of the spring 346 from a position resting on the radially inner stop 352 to a position resting on the radially outer stop 348.

The spring 346 is dimensioned so that at low speeds of the drive shaft 228 the positioning body 344 rests on the radially inner stop 352 and moves away from this as the speed increases and from a defined switching speed onwards it rests on the radially outer stop 348, as shown in Fig. 17 and 15 is shown.

The positioning body 344 is preferably provided with a positioning surface 354 running obliquely to the central axis 334, which in the simplest case has a conically tapering course to the central axis 334 in the direction of the radially inner stop 352.

The positioning surface 354 of the positioning body 344 serves to influence a rotational position of the unit 260 made up of orbital path compensation mass 252 and guide body 254 together with the coupling pin 292, relative to the drive shaft 228, with a change in the rotational position by rotating the unit 260 about the eccentric drive pin 244, in particular its eccentric axis 245, is possible.

For this purpose, the guide body 254 is provided with an extension 356, on which an actuating body 358 which interacts with the positioning surface 354 is arranged ( Fig. 15 , 17 and 19 ).

The positioning body 344 is as in Fig. 17 shown, in the position in which it rests against the radially inner stop 352, the positioning surface 354 acts on the actuating body 358 with its area lying radially outer with respect to the central axis 334 and thereby places the unit 260 consisting of orbital path compensation mass 252, guide body 254 and coupling pin 292 in a rotational position about the eccentric axis 245 relative to the drive shaft 228, in which the center of mass SOAGM is at a distance from the mass compensation plane ME.

Furthermore, in this rotational position, the position of the recess 296 relative to the coupling pin 292 is such that they do not touch each other in this position of the positioning body 344, so that the unit 260 consisting of orbital orbit balancing mass 252, guide body 254 and coupling pin 292 is removed from the orbiting unit 250 Compressor body 26, the driver 246 and the pivot bearing 248 is in the centrifugal force decoupled state, and the center of mass SOS of this unit 250 is the speed-dependent centrifugal force FZsos ( Fig. 17 and 18 ) generated.

The unit 250, consisting of the orbiting compressor body 26, the driver 246 and the pivot bearing 248, thus develops the full centrifugal force FZsos at low speeds in the sense of an increase in the compressor orbital radius VOR, which together with the force FC contributes to the contact force in the contact point 322 of the spiral ribs 34, 38 ( Fig. 18 ).

Increasing the speed up to the switching speed, at which the positioning body 344 is moved radially outwards to the central axis 44 against the force of the spring 346 by the centrifugal force that increases with the speed and finally rests against the radially outer stop 348, causes the positioning surface 354 increasingly moves radially outwards and releases the actuating body 358 so that the unit 260 can pivot relative to the eccentric axis 245 in the direction of rotation D and can move until the coupling pin 292 comes to rest on the portion 304 of the wall surface 298 of the recess 296 and thus between the unit 260 made up of the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 and the unit 250 made up of the orbiting compressor body 26, the driver 246 and the pivot bearing 248, the coupling unit 300 is in the centrifugal force coupling state in which the unit 260 from the orbital orbit balancing mass 252, the guide body 254 and the coupling pin 292 counteracts and reduces the centrifugal force FZsos in the manner already described ( Fig. 16 ).

The solution according to the invention thus creates the possibility of operating the compressor in such a way that at low speeds the coupling unit 300 is in the centrifugal force decoupling state and thus the unit 250, comprising the orbiting movable compressor body 26, the driver 246 and the pivot bearing 248 with their full centrifugal force FZsos is effective, so that this centrifugal force FZsos together with the force FC, which is created by the force FA acting on the orbiting movable compressor body 26 due to the eccentric drive 242 ( Fig. 18 ), acts on the contact point 322 of the spiral ribs 34, 38 and thus keeps the spiral ribs 34, 38 in contact with the contact point 322 in order to achieve the tightest possible seal between them. In particular, there is the possibility of designing the mass of the components contributing to the unit 250 in such a way that as the speed increases, the centrifugal force FZsos generated by the unit 250 increases significantly as the speed increases in order to achieve a sufficiently large force in the contact point 322 as quickly as possible at the lowest possible speed To obtain spiral ribs 34, 38.

However, such a design would have the major disadvantage that as the speed continues to increase, the centrifugal force of the unit 250 acting in the contact point 322 of the spiral ribs 34, 38 becomes too great a force in the contact point 322 between the spiral ribs 34, 38, so that there is a danger that the spiral ribs 34, 38 in the contact point 322 are damaged and, for example, the lubricating film between them tears due to the excessive force on the spiral ribs 34, 38 in the contact point 322.

For this reason, in the solution according to the invention, as the speed increases in the transition speed range, the coupling unit 300 transitions from the centrifugal force decoupling state ( Fig. 18 ) into the centrifugal force-coupling state ( Fig. 17 ) in which the Centrifugal force FZsos generated by the unit 250 is reduced to the centrifugal force FZR by coupling the unit 250 with the unit 260, so that overall when high speeds are reached, the force between the spiral ribs 34, 38 in the contact point 322 can be limited.

The solution according to the invention thus creates, on the one hand, the advantage of achieving a sufficiently high force between the spiral ribs 34, 38 at very low speeds in the contact point 322, and on the other hand, the force in the contact point 322 between the spiral ribs at high speeds 34, 38 to a level at which no damage to the spiral ribs 34, 38 occurs.

Claims (19)

1. A compressor comprising a compressor housing (12), a scroll compressor unit (22) arranged in the compressor housing (12) with a first, stationarily-arranged compressor body (24) and a second compressor body (26) moveable relative to the stationarily-arranged compressor body (24), of which first and second spiral ribs (34, 38) having the shape of a circle involute engage in each other to form compression chambers (42), when the second compressor body (26) is moved relative to the first compressor body (24) on an orbital path (48), an axial guide (96) which supports the moveable compressor body (26) against movements in the direction parallel to a central axis (44) of the stationarily-arranged compressor body (24) and guides it upon movements in the direction transverse to the central axis (44), an eccentric drive (242) for the scroll compressor unit (22), which comprises a drive element (246) which is driven by a drive motor (222) and which rotates on the orbital path (48) around the central axis (44) of a drive shaft (228) and which is rotatably mounted relative to the drive shaft (228) about an eccentric drive axis (245), the drive element itself cooperating with a drive element receptacle (249) of the compressor body (26), an orbital path balancing weight (252) which counteracts an unbalance of the compressor body (26) moving on the orbital path (48) and which is also mounted rotatably about the eccentric axis (245), and a coupling (164) which prevents a self-rotation of the second compressor body (26),
   characterised in that the drive element (246) and the orbital path balancing element (252) are couplable to each other by means of a coupling unit (300) such that the coupling unit (300) with a rotating drive shaft (228) acts in a centrifugal force-coupling state such that the orbital path balancing weight (252) counteracts a centrifugal force (FZ_sos) of a unit (250) comprising at least the drive element (246) and the orbiting compressor body (26), in that the coupling unit (300) with a rotating drive shaft (228) acts in a centrifugal force-uncoupling state such that the orbital path balancing weight (252) does not counteract the centrifugal force (FZ_sos) of the unit (250) comprising at least the drive element (246) and the orbiting compressor body (26), and in that the coupling unit (300) is transferable by a positioning device (332) from the centrifugal-force-coupling state into the centrifugal-force-uncoupling state or vice versa.
2. A compressor according to Claim 1, characterised in that the coupling unit (300) comprises two coupling elements (292, 296) of which one is connected with the orbital path balancing weight (252) and one is connected with the drive element (246), in that in particular the coupling elements (292, 296) are moveable relative to each other into the centrifugal-force-coupling state and into the centrifugal-force-uncoupling state.
3. A compressor according to one of the preceding Claims, characterised in that one coupling element (292) is fixedly connected to the orbital path balancing weight (252) or with the drive element (246) and the other coupling element (296) is fixedly connected to the drive element (246) or the orbital path balancing weight (252) respectively.
4. A compressor according to one of the preceding Claims, characterised in that one of the coupling elements is a coupling body (292) and another of the coupling elements is a receptacle (296) into which the coupling body (292) engages, in that in particular the coupling body (292) engages in the receptacle (296) with play, in that in particular the coupling body (292) in the centrifugal-force-coupling state abuts a partial region (304) of the receptacle (296) and in the centrifugal-force-uncoupling state is arranged so as not to contact the receptacle (296).
5. A compressor according to Claim 4, characterised in that the coupling body (292) is configured as a coupling pin, in that in particular the coupling pin (292) is connected to the orbital path balancing weight (252) and engages in the receptacle (296) connected with the drive element (246)
6. A compressor according to one of the preceding Claims, characterised in that the positioning device (332) operates in speed-controlled manner and below a switching speed brings the coupling unit (300) into the centrifugal-force-uncoupling state and above the switching speed brings the coupling unit (300) into the centrifugal-force-coupling state.
7. A compressor according to one of the preceding Claims, characterised in that the positioning device (232) is arranged on the drive shaft (228).
8. A compressor according to one of the preceding Claims, characterised in that the positioning device (332) in the centrifugal-force-coupling state allows a cooperation of the coupling elements (292, 296) and in the centrifugal-force-uncoupling state positions the coupling elements (292, 296) so as not to contact each other.
9. A compressor according to one of the preceding Claims, characterised in that the positioning device (332) comprises a positioning body (344), which is guided on the drive shaft (228) by means of a guide body (336) with at least a component in the direction radial to the central axis (44) and is movable along the guide body (336) in speed-dependent manner, in that in particular the positioning body (344) is acted upon by means of a resilient energy store (346) against a centrifugal force acting upon the positioning body (344), in that in particular the positioning body (344) is provided with a positioning face (354) which acts on the coupling unit (300) in dependence upon a radial position of the positioning body (344), in that in particular the positioning body (344) in a first disposition, which corresponds to a speed below the switching speed, brings the coupling unit (300) into its centrifugal-force-uncoupling state, and in a disposition, which corresponds to a speed above the switching speed, brings the coupling unit (300) into its centrifugal-force-coupling state.
10. A compressor according to one of the preceding Claims, characterised in that by means of the positioning device (332) the coupling element (292) connected to the orbital path balancing weight (252) is movable relative to the coupling element (296) connected to the drive element (246) into the centrifugal-force-coupling state or the centrifugal-force uncoupling state, in that in particular the positioning device (332) brings the orbital path balancing weight (252) together with the coupling element (292) into the centrifugal-force-uncoupling state or into the centrifugal-force-coupling state.
11. A compressor according to one of Claims 6 to 10, characterised in that the orbital path balancing weight (252), in the centrifugal-force-uncoupling state of the coupling unit (300), is located with its centre of gravity (SOAGM) at a spacing from the weight-balancing plane (ME) and in the centrifugal-force-coupling state of the coupling unit (300) lies with its centre of gravity (SOAGM) near to or in the weight balancing plane (ME).
12. A compressor according to one of the preceding Claims, characterised in that a first movement limitation unit (280) acts between the drive shaft (228) and the orbital path balancing weight (252).
13. A compressor according to one of the preceding Claims, characterised in that the central axis (44) of the drive shaft (228) and a central axis (46) of the movable second compressor body (26) define a weight balancing plane (ME) running therethrough, and in that the first movement limitation unit (280) holds the orbital path balancing weight (252) on a side of a geometric transverse plane (QE) running perpendicularly to the weight balancing plane (ME) and through the central axis (44) of the drive shaft (228), said side being opposite to the eccentric axis (245).
14. A compressor according to Claim 12 or 13, characterised in that the first movement limitation unit (288) so orientates the orbital path balancing weight (252) that a centre of gravity (SOAGM) thereof remains within an unbalanced tolerance region extending over the weight balancing plane (ME) and at both sides thereof.
15. A compressor according to one of Claims 12 to 14, characterised in that the first movement limitation unit (280) permits a free rotatability of the guide body (254) about the eccentric axis (245) within an angular range of 0.5° (angular degree) to 5° (angular degree).
16. A compressor according to one of Claims 12 to 15, characterised in that the first movement limitation unit (280) is formed by a first stop element (282) held on the orbital path balancing weight (252), in particular on its guide body (254), or on the drive shaft (228), and a second stop element (284) cooperating with the first stop element (282), in particular receiving the first stop element, the second stop element being arranged on the drive shaft (228) or on the orbital path balancing weight (252), in particular on its guide body (254).
17. A compressor according to one of the preceding Claims, characterised in that the orbital path balancing weight (252) is rotatably mounted with a guide body (254) on the eccentric drive axis (245), or in that in particular the guide body (254) is fixedly connected to the orbital path balancing weight (252).
18. A compressor according to one of the preceding Claims, characterised in that the orbital path balancing weight (252) is rotatably mounted around eccentric drive axis (245) by an eccentric drive pin (244) cooperating with the drive element (246) and the drive shaft (228), in that in particular the eccentric drive pin (244) penetrates a pin receptacle (256) of the guide body (254).
19. A compressor according to one of the preceding Claims, characterised in the orbital path balancing weight (252) cooperates with the drive shaft (228) by means of the guide body (254) and is guided on the drive shaft (228).

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