EP3194782A2

EP3194782A2 - Scroll compressor

Info

Publication number: EP3194782A2
Application number: EP15760194.9A
Authority: EP
Inventors: Dimitri Gossen; Muzaffer Ceylan
Original assignee: Bitzer Kuehlmaschinenbau GmbH and Co KG
Current assignee: Bitzer Kuehlmaschinenbau GmbH and Co KG
Priority date: 2014-09-17
Filing date: 2015-09-09
Publication date: 2017-07-26
Anticipated expiration: 2035-09-09
Also published as: EP3540229A1; EP3194782B1; US10634141B2; US20200217319A1; CN106795768A; US20170184107A1; WO2016041824A3; WO2016041824A2; EP3540229B1; CN106795768B; CN110925196A; US11396877B2; DE102014113435A1

Abstract

The invention relates to a compressor which comprises: a compressor housing; a scroll compressor unit having a first, stationary compressor body and a second compressor body which can be moved relative to the stationary compressor body, the first and second scroll ribs in the form of an involute engaging with each other and forming compressor chambers when the second compressor body is moved on an orbital path relative to the first compressor body; an axial guide, which supports the movable compressor body counter to movements in a direction parallel to a center axis of the stationary compressor body and guides it in a direction transverse to the center axis when there is movement; a drive motor, which drives an eccentric drive for the scroll compressor unit and has a catch driven by the drive motor and orbiting on a path about a center axis of a drive shaft, said catch interacting with a catch receptacle on the second compressor body; and a coupling which prevents the second compressor body from rotating about itself. The aim of the invention is to provide an improved compressor which is as light-weight and compact as possible and therefore can be used for example in the field of vehicle technology. The compressor body base, which carries the scroll rib of the second compressor body, is supported by the axial guide on an axial support surface such that the axial support surface lies on a sliding body so as to slide transversely to the center axis, said sliding body in turn being supported by a carrier element arranged in the compressor housing so as to slide transversely to the center axis.

Description

COMPRESSOR

The invention relates to a compressor comprising a compressor housing, a compressor unit arranged in the scroll 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 rib 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 supporting the movable compressor body against movements in the direction parallel to a center axis of the stationary compressor body and moving in the direction transverse to the central axis, a drive motor which has an eccentric drive for the scroll compressor unit driving one of the

Drive motor driven and on a path around a central axis of the drive shaft rotating cam has, which cooperates with a cam receiver of the second compressor body,

and a self-rotation of the second compressor body preventing clutch.

Such compressors are known in the art.

In these compressors there is a requirement to build them as easily and compactly as possible to use them, for example, in vehicle technology.

This object is achieved according to the invention in a compressor of the type described above in that the axial guide supports a compressor body base supporting the spiral rib of the second compressor body to an axial support surface, that the Axialstützfläche transverse to the central axis slidably rests on a slider, which in turn is supported slidably transverse to the central axis on a carrier element arranged in the compressor housing.

The advantage of the solution according to the invention is to be seen in the fact that provided by the between the Axialstützfläche the compressor body base and the support member on the compressor housing sliding body on the one hand optimally supported the second compressor body and on the other hand to wear wear, as arranged between the Axialstützfläche and the support member Slider opens the possibility to provide an optimal lubricant supply.

Theoretically, the slider could be either one-dimensionally movable relative to the compressor body base or relative to the carrier member.

It is particularly favorable if the sliding body is movable in two dimensions relative to the compressor body base and relative to the carrier element.

Thereby, a sufficient lubrication of the support between the Axialstützfläche and the slider and the slider and the support member in a simple manner and reliably realized.

Particularly suitably, the mobility of the slider can be realized when the slider is guided by a two-dimensional guide with play relative to the compressor body base or relative to the carrier element.

Through the leadership with game can be realized in a simple manner, the two-dimensional mobility of the slider and set in terms of the approved extent. For example, it can be determined by the guide with play that the slider relative to the compressor base or relative to the carrier element can perform a limited Führungsorbitalbewegung.

The orbital movement is expediently defined by a Führungsorbitalradius which is smaller than the compressor orbital radius of the movable compressor body. For example, the guide orbital radius for the slider is at values equal to 0.5 times the compressor orbital radius. It is better if the guide orbital radius values are 0.3 times the compressor orbital radius or less, more preferably 0.2 times the compressor orbital radius or less.

To obtain a minimum lubrication, the guide orbital radius is 0.01 times the compressor orbital radius or more, 0.05 times the compressor orbital radius or more.

Regarding the training of leadership with game so far, no details have been made.

Thus, an advantageous solution provides that the guide has a first guide element which is arranged on the sliding body and has a second guide body element which is connected either to the compressor body base or to the carrier element.

With regard to the design of the guide elements a variety of ways are conceivable.

It is particularly favorable if the guide with play as guide elements has a guide pin and a guide recess which cooperates with the guide pin and which are movable relative to one another two-dimensionally by engaging the guide recess in the guide recess Guide pin is movable within the guide recess due to its relative to the diameter of the guide recess of smaller diameter.

With regard to the design of the Axialstützfläche a variety of implementation options are conceivable.

For example, it is conceivable to assemble the axial support surface of individual partial surfaces, which are arranged on the second compressor body.

These partial surfaces can then be arranged in different regions of the second compressor body.

However, in order to achieve optimum support, lubrication and guidance, it is preferably provided that the axial support surface is designed as an annular surface running around the center axis of the movable compressor body.

Such an annular surface allows a reliable, uniform and secure support of the second compressor body and at the same time a structure of a homogeneous lubricating film, for the guiding properties and the

Wear resistance is very important.

The Axialstützfläche could be supported on individual surface areas of the slider.

It is particularly favorable, however, if the axial support surface is supported on an annular surface of the sliding body which revolves around the center axis.

Preferably, the annular surface of the slider is dimensioned so that it is larger than the annular surface of the Axialstützfläche, so that the Axialstützfläche is always supported in the orbiting movement of the second compressor body over its entire surface on the annular surface of the slider. In order to ensure an optimal supply of lubricant for a lubricant film between the axial support surface and the sliding body, it is preferably provided that a peripheral surface adjoins the axial support surface radially outboard and / or radially inward, which recesses relative to a plane in which the axial support surface extends runs.

A particularly favorable solution provides that the edge surface directly adjoins the Axialstützfläche, and thus extends to the plane in which extends the Axialstützfläche, and then with increasing

Distance from the axial support surface at an increasing distance from the plane in which extends the Axialstützfläche. By such, for example, stepped or wedge-shaped course of the edge surface, the supply of lubricant to the Axialstützfläche is favored from an outer side thereof ago.

The supply of lubricant between the axial support surface and the sliding body can also be further promoted by the fact that the axial support surface and / or a sliding support surface carrying the axial support surface are provided with micro-depressions, for example material-related and / or incorporated and / or embossed depression structures

Take up lubricant, make it available and distribute it.

With regard to the guidance of the slider relative to the carrier element so far no further details have been made.

Thus, an advantageous solution provides that the sliding body is supported with a sliding bearing surface on the support element.

The Gleitauflagefläche could also be formed from partial surfaces. It is particularly favorable if the sliding support surface is designed as an annular surface extending around the central axis of the stationary compressor body.

Furthermore, it is preferably provided that the carrier element has a carrier surface on which the sliding body is supported by the sliding support surface.

This support surface could also be formed from individual partial surfaces.

However, it is particularly advantageous if the carrier surface is designed as a circumferential around the central axis of the stationary compressor body ring surface.

The supply of lubricant between the carrier element and the sliding body can also be further facilitated by the fact that the sliding support surface and / or a support surface carrying the sliding support surface are provided with micro-recesses, for example material-related and / or incorporated and / or embossed depression structures

Take up lubricant, make it available and distribute it.

Further, no details were given regarding the formation of the slider.

In principle, the slider could have any shape.

For manufacturing reasons, it is particularly advantageous if the sliding body is plate-shaped, in particular as an annular disc is formed.

Furthermore, no details were given regarding the choice of materials in the compressor according to the invention. Thus, an advantageous solution provides that the first stationary compressor body is made of cast steel.

Such a first compressor body made of cast steel has optimum stability and fatigue strength.

Furthermore, it is preferably provided that the second compressor body is made of an aluminum alloy, in particular of aluminum alloy casting.

The production of the second compressor body made of an aluminum alloy has the advantage that this second compressor body has a low mass, which brings particular advantages when the second compressor body to move at high speed on the orbital path around the central axis of the first compressor body around.

Furthermore, a material combination of aluminum alloy cast steel between the first and the second compressor body has the advantage of good running properties with a high fatigue strength and longevity.

With regard to the material for the sliding body, no further details were given in connection with the previous explanation of the individual embodiments.

In principle, the slider could be made of any material, which, however, should result in an optimal material pairing to the second compressor body and the support element.

It has proved to be particularly advantageous if the slider is formed of spring steel. The design of the slider made of spring steel on the one hand has the advantage that a favorable material pairing is given to the second compressor body made of aluminum, and on the other hand the advantage that thereby also an optimal material pairing can be produced to the support element.

In addition, the design of the second sliding body made of spring steel has great advantages for cost reasons, since spring steel is a cost-effective material from which the shape suitable for the slider can be produced in a simple manner by cutting or punching.

With regard to the carrier element so far no further details have been made.

The support element could be made in the simplest case of steel or from the material of the compressor housing.

However, in order to achieve high stability, it is preferably provided that the carrier element is made of sintered material, for example sintered metal.

A particularly favorable solution provides that the carrier element has a carrier surface, formed by an open-pored sintered material, on which the sliding body is supported with its sliding support surface.

Such an open-pored sintered material for forming the support surface has the great advantage that it can advantageously absorb lubricant and then also deliver it to the lubrication between the support surface and the sliding support surface.

In this case, the lubricant can be held in particular in the open pores of the sintered material, so that in a simple manner, a lubricating film between the support surface and the Gleitauflagefläche can be maintained permanently. As low, the use of sintered material has proved, which is softer than the spring steel of the sliding element, so that thus results in an advantageous for a sliding material pairing between the support member and the slider.

Alternatively or in addition to the solution described so far of the aforementioned object is in a further compressor of the beginning

described manner that the axial guide the second compressor body on a thrust formed by this Axialstützfläche transverse to the central axis slidably supported and that the Axialstützfläche is formed by a spiral rib carrying the compressor body base.

Such a solution is particularly advantageous in terms of manufacture, since no separate part for the formation of the support surface is required, but the support surface itself can be formed by the compressor body base.

In particular, it is advantageous if the driver receptacle is integrated in the compressor body base, so that no further part is required for this purpose.

Preferably, the cam receiver is arranged in the direction parallel to the central axis of the movable compressor body without supernatant to the support surface on the compressor body base, so that the force acting on the Mitnehmeraufnahme forces when driving the second compressor body in the direction parallel to the central axis seen between the support surface and the spiral ribs on the second compressor body act and thus the forces acting on the second compressor body during operation of the scroll compressor unit tilting moments are kept small. Alternatively or in addition to the embodiments described so far, it is provided for the solution of the above-mentioned object in a further compressor that the self-rotation preventing coupling at least two coupling element sets, comprising at least two coupling elements comprises.

Such a coupling can be realized in various ways. In order to achieve an advantageous support of the second compressor body relative to the compressor housing with such a coupling, it is preferably provided that one of the coupling elements on the

Compressor body base is held.

Furthermore, it is preferably provided that one of the coupling elements is held on the carrier unit.

In this case, therefore, the coupling element sets are arranged and formed so that they directly between the carrier unit and the

Compressor body base of the second compressor body are effective, so that a compact design can be realized.

In order to improve the guidance of the second compressor body relative to the compressor housing by the clutch, it is preferably provided that the self-rotation preventing clutch has more than two coupling element sets.

With regard to the coupling element sets themselves, no further details have been given so far.

Thus, an advantageous solution that the coupling element sets are arranged around the central axis of the orbital path around at equal angular intervals. With regard to the design of the coupling elements themselves so far no details have been made.

Thus, an advantageous solution provides that one of the coupling elements is formed by a pin body.

Furthermore, it is advantageously provided that one of the coupling elements is designed as a cylindrical receptacle.

A further advantageous solution provides that one of the coupling elements is designed as arranged in the cylindrical receptacle annular body.

Preferably, it is provided that the annular body loose, that is with game, sitting in the cylindrical receptacle and thus can move relative to the cylindrical receptacle.

Such a design of the coupling element sets has the great advantage that on the one hand ensure optimum lubrication and on the other hand allow a low-noise movement of the second compressor body relative to the first compressor body, since in each of the coupling element sets two damping lubricant films are present, namely on the one hand, a lubricant film between the pen body and the annular body and on the other hand, a lubricant film between the annular body and the cylindrical receptacle, in which the annular body is arranged.

With regard to the arrangement of the coupling element sets relative to the slider so far no further details have been made.

In principle, the slider and the coupling element sets could be arranged separately.

For example, the slider could extend outside the coupling element sets, or vice versa. It is advantageous if the coupling element sets pass through the sliding body, so that thereby lubricant can be transported between the sliding body and the coupling element sets, in particular if the coupling element sets pass through openings in the sliding body.

In order to optimally lubricate in particular the coupling element sets, it is preferably provided that the compressor body base of the second

Compressor body is provided with pockets which have the cylindrical receptacles of the coupling element sets facing openings.

Such pockets with the cylindrical receptacles facing openings have the advantage that it is entrained by these lubricants in the orbiting movement of the second compressor body base and thus lubricant can always be transported to the cylindrical receptacles.

The effect of the pockets is particularly favorable if the openings of the pockets are each overlappingly positionable with two cylindrical receptacles arranged successively in the direction of rotation, that is to say that in this case the openings of the pockets have an angular extent such that they are in the orbiting movement of the pockets Compressor body base in each rotational position in each case two pockets can connect to each other and thus can advantageously transport lubricant from a cylindrical receptacle to the other cylindrical receptacle.

The features of the inventive solution described in connection with the previous embodiments are particularly advantageous when the central axis of the stationary compressor body is lying.

A lying course of the central axis of the stationary compressor body means that the central axis runs during operation of the compressor according to the invention approximately parallel to a horizontal, wherein Under the term "approximately parallel" is to be understood that the angle between the central axis and the horizontal when using the compressor according to the invention in the normal operating state is a maximum of 30 °, more preferably a maximum of 20 °.

Furthermore, in the solution according to the invention is also advantageously provided that the drive shaft of the drive motor is substantially horizontal, with the same conditions apply to the angle between the central axis of the drive shaft and a horizontal as for the

Alignment of the center axis of the stationary compressor body relative to the horizontal.

For the above-mentioned object, it is also advantageous if the compressor housing is made of an aluminum alloy in order to build the compressor of the invention as possible to save weight.

In addition, the compressor also has a better resistance to external weather conditions.

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 an inventive

compressor;

Figure 2 is a longitudinal section through the compressor according to the invention, in a plane passing through a central axis of a stationary compressor body sectional plane. 3 shows a cross section through a spiral compressor unit in the region of the intermeshing spiral ribs and a representation of an orbital path of the movable spiral rib relative to the stationary spiral rib.

4 shows an enlarged longitudinal section according to FIG. 2 in the region of the movable compressor body and an axial guide for the movable compressor body;

5 shows a further enlarged section through a partial region of the axial guide in the region of a guide with clearance for a sliding body of the axial guide;

Fig. 6 is a plan view of the axial guide with the slider and a supporting this support member; Fig. 7 is a perspective view of the axial guide together

Clutch elements of a clutch to prevent self-rotation comprising a plurality of coupling element sets;

Fig. 8 is a plan view of one of the spiral rib opposite

Flat side of the movable compressor body;

Fig. 9 to

Fig. 14 is a schematic representation of the interaction of the

Coupling element sets of the self-rotation preventing coupling;

Fig. 15 is a section along line 15-15 in Fig. 4 and FIG. 16 is a section along line 16--16 in FIG. 15th An in Fig. 1 illustrated embodiment of a designated as a whole with 10 compressor according to the invention for a gaseous medium, in particular a refrigerant comprises a designated as a whole with 12 compressor housing, which has a first end housing portion 14, a second end housing portion 16 and between the end housing sections 14 and 16th arranged intermediate section 18 has.

As shown in Fig. 2, in the first housing portion 14 a designated as a whole with 22 spiral compressor unit is provided which a first 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 compression chambers 42 to form, in which a compression of the gaseous medium, for example, refrigerant, characterized in that the second compressor body 26 with its central axis 46 about a central axis 44 of the first compressor body 24 on a Orbitalbahn 48 moves with a Verdichterorbitalbahnradius VOR, wherein the volume of the compression chambers 42 is reduced and finally compressed gaseous medium exits through a central outlet 52, while aspirated gaseous medium by circumferentially opening compressor chambers radially outwardly relative to the central axis 44 is sucked. 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 direction perpendicular to the central axis 46 extending plane.

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 an integrally formed on the front-side cover portion 74 cylindrical annular portion 76, which in turn with a ring projection 78 in an end sleeve 82 of the intermediate portion 18 forming central housing body 84 engages, wherein the central housing body 84 is closed on a side opposite the first housing body 72 side by a second housing body 86 which forms an inlet chamber 88 for the gaseous medium.

The first housing body 72 encloses with the cylindrical ring portion 76 a receptacle 92 for the scroll compressor unit 22, which has a bearing surface 94 for the compressor body base 32 of the first compressor body 24.

In particular, the first compressor body 24 is fixed immovably in the receptacle 92 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 relative to the central axis 44 in the axial direction by a whole 96, which guides the compressor body base 36 on a flat side 98 facing away from the spiral rib 38, specifically in the region of an axial support surface 102, so that the compressor body base 36 of the second compressor body 26 is stationary relative to the stationary one

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.

For this purpose, as shown in FIG. 4, the axial guide 96 formed by a support member 112, which is in particular made of an open-pore sintered material and having an axial support surface 102 facing support surface 114, on which but not the compressor body base 36 rests with the Axialstützfläche 102, but on which a as a whole 116 denoted in particular plate-shaped slider 116 rests with a sliding bearing surface 118, wherein the slider 116 with a Gleitauflagefläche 118 opposite Gleitstützfläche 122 supports the Axialstützfläche 102 against movements parallel to the central axis 44 but slidably supported 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, 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

To improve the lubrication, for example, the Gleitstützfläche 122 and the Gleitauflagefläche 118 of the slider 116 are provided with recesses 123, in particular micro-recesses, which form receptacles for a lubricant and contribute to the distribution of the lubricant, such as

by way of example in FIG. 6 in conjunction with the Gleitstützfläche 122 shown.

To the limited two-dimensional mobility of the slider 116 parallel to a plane perpendicular to the central axis 44 plane E relative to

Specify support member 112, the slider 116 is guided by a designated as a whole with 132 guide with play relative to the support member 112, wherein the guide with game 132 provided in the slider 116

Guide recess 134 includes, which has a diameter DF, and a 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 FOR, with which the slider 116 can perform an orbiting movement relative to the carrier element 112.

In order to build up a sufficient lubricating film between the axial support surface 102 of the compressor body base 36 and the Gleitstützfläche 122 of the slider 116 and the support surface 114 and the Gleitauflagefläche 118 ensure that the support member 112 is provided with radially outer pockets 142 which extend below an outer edge portion 144 of the slider 116 and thus facilitate access of lubricant in a gap 146 between the support surface 114 and the Gleitauflagefläche 118.

Further, the gap 146 due to the movement of the slider 116 with the Führungsorbitalradius FOR relative to the support member 112 is similar to the operation of a hydrodynamic bearing with a

Lubricating film 147 filled.

For a stable lubricating film 146, it is sufficient for the guide orbital radius FOR to be 0.01 times the compressor orbital radius VOR or more, in particular, 0.05 times the compressor orbital radius VOR or more.

In particular, the guide orbital radius FOR is 0.3 times the

Compressor orbital radius PRE or less, more preferably 0.2 times the compressor orbital radius BEFORE or less.

Furthermore, due to the fact that the carrier element 112 at least in the region of the support surface 114 of an open-pore sintered material

In addition, improved lubrication is ensured by the fact that lubricant enters into the pores of the carrier element 112 and is thus available over the pores of the carrier element 112 in the region of the carrier surface 114 for building up the lubricant film 147 in the intermediate space 146.

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 Gleitauflagefläche 118 is a smooth Federstahloberfläche, the formation of the lubricant film 147 in the intermediate space 146 is additionally promoted. Furthermore, the material combination of open-pore sintered material, which is softer in the region of the carrier surface 114 than spring steel, and the spring steel in the region of the sliding support surface 118 due to the wear resistance advantageous endurance properties.

In order to further assure the build up of lubricating film 149 of lubricant in a space 148 between the sliding support surface 122 and the axial support surface 102, the compressor body base 36 is disposed in a radially outboard and a radially inward edge region 152 having a relative to the axial support surface 102 inclined and opposite axial support surface 102, recessed extending edge surface 154 which, together with the sliding support surface 122 leads to a wedge-shaped radially outwardly or radially inwardly opening gap 158, which facilitates the access of lubricant to the intermediate space 148.

As shown in Figs. 4, 6, 7 and 8, the Axialstützfläche 102 and the cooperating Gleitstützfläche 122 and the support surface 114 and the cooperating Gleitauflagefläche 118 are all disposed radially outside of several coupling element sets 162, which are at equal radial distances from the central axis 44 and at equal angular intervals circumferentially about the central axis 44 are arranged and together form a coupling 164 which prevents self-rotation of the second movable compressor body 26.

Each of these coupling element sets 162 comprises, as shown in FIGS. 4, 6 to 8, as a 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 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) 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, that, as shown in Figs. 9 to 14, each one of

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 direction of rotation next coupling element set 162 changes. Due to the fact that each coupling element set 162 three

Clutch elements 172, 182 and 192 and in particular an annular body 184 between the respective pin body 174 and the respective receptacle 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 adequate 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 196 of Recording 194.

One possibility envisages that the coupling element sets 162 pass through the sliding body 116, in particular the pin bodies 174 penetrate through openings 198 (FIG. 7) of the sliding body 116, whereby lubricant from the

Lubricating films 147 and 149 can be supplied to the coupling element sets 162.

To aid in lubrication, in the compressor body base 36, as in Figs. 8 and 15, between the first coupling elements 172 receiving bores 202 pockets 204 are provided, which in the compressor body base 36 bounding flat side 98 have an opening 206 having such an angular extent with respect to the center axis 46 of the compressor body base 36 that these, as in Fig. 15

shown, in individual rotational positions with two in the direction of rotation

successive recordings 194 of the coupling element sets 162 may overlap, so that the pockets 204 are capable of one

Lubricant exchange between successive Kupplungselementen- sets 162 to effect and thus allow a uniform supply of lubricant all coupling element sets 162.

Preferably, the pockets 204 are arranged to extend around either side of a geometric arc 208 about the central axis 46, which intersects the holes 202 in the center to always achieve optimum overlap with the receptacles 194.

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 gravitational direction forms a lubricant bath 210 from which swirled lubricant in operation while being received and distributed in the manner described.

The drive of the movable compressor body 24 is effected by a drive motor designated as a whole by 212, which in particular has a stator 214 held in the central housing body 84 and a rotor 216 arranged inside the stator 214, which is arranged on a drive shaft 218 which is coaxial with the central axis 44 of the stationary compressor body 24 extends.

The drive shaft 218 is mounted on the one hand in a bearing unit 222 arranged between the drive motor 212 and the spiral compressor unit 22 and in the central housing body 84 and on the other hand in a bearing unit 224 which is arranged on a side of the drive motor 212 opposite the bearing unit 222. The bearing unit 224 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, in this case aspirated medium, in particular the refrigerant, flows through the electric motor 212 in the direction of the bearing unit 222, flows around the latter and then flows in the direction of the spiral compressor unit 22.

The drive shaft 218 drives, via an eccentric drive designated as a whole by 232, the movable compressor body 26, which moves in an orbiting manner about the central axis 44 of the stationary compressor body 24.

The eccentric drive 232 in particular comprises an eccentric pin 234 held in the drive shaft 218, which moves a driver 236 on an orbital path about the central axis 44, which is rotatably mounted on the eccentric pin 234 and in turn is rotatably mounted in a pivot bearing 238, the pivot bearing 238 a Turning the driver 236 relative to the movable compressor body 26 allowed.

The driver 236 is relative to the eccentric pin 234 and relative to

Mitnehmeraufnahme 242 limited rotation and allows adjustment of the radius of the orbital movement of the movable compressor body 26 to hold the spiral ribs 34 and 38 in abutment with each other.

For receiving the pivot bearing 238, as shown in FIGS. 2, 4 and 16, the second compressor body 26 is provided with a driver receptacle 242, which receives the pivot bearing 238.

The driver receptacle 242 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, as viewed axially through the axial guide 96 in the direction of the central axis 44 between the driver receptacle 242 and the electric motor 212 on the Axialstützfläche 102 and guided transversely to the central axis 44 movable is

Claims

claims

Comprising 1. compressor

a compressor housing (12),

a in the compressor housing (12) arranged scroll 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), formed in the form of a Kreisvolvente first and second spiral ribs (34, 38) intermesh to form compression chambers (42) when the second compressor body (26) is moved relative to the first compressor body (24) on an orbital track (48), an axial guide (96) defining the movable compressor body (26 ) is supported against movements in the direction parallel to a central axis (44) of the stationarily arranged compressor body (24) and leads in the direction transverse to the central axis (44),

a drive motor (212) which drives an eccentric drive (232) for the scroll compressor unit (22) which has a driver (236) driven by the drive motor (212) and rotating on a track about a central axis (44) of a drive shaft (218), which cooperates with a driver receptacle (242) of the second compressor body (26),

and a clutch (164) preventing self-rotation of the second compressor body (26),

characterized in that the axial guide (96) supports a compressor body base (36) of the second compressor body (26) supporting the spiral rib (38) on an axial support surface (102) such that the axial support surface (102) slides transversely to the center axis (44) on a sliding body (116) rests, which in turn is transverse to the central axis (64) slidably supported on a in the compressor housing (12) arranged support member (112).

2. A compressor according to claim 1, characterized in that the sliding body (116) relative to the compressor body base (36) and relative to the carrier element (112) is two-dimensionally movable.

3. A compressor according to claim 1 or 2, characterized in that the sliding body (116) by a two-dimensional guide with play (132) relative to the compressor body base (36) and / or relative to the carrier element (112) is movably guided.

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

Guide (132) includes a first guide member (134) disposed on the slider (116) and a second guide member (136) connected to either the compressor body base (36) or to the support member (112).

5. A compressor according to claim 3 or 4, characterized in that the guide with game (132) as Führungslemente a guide pin (136) and with the guide pin (136) cooperating guide recess (134) which are two-dimensionally movable relative to each other.

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

in that the axial support surface (102) is designed as an annular surface that runs around a central axis (46) of the movable compressor body (26).

7. A compressor according to any one of the preceding claims, characterized

in that the axial support surface (102) is supported on an annular surface of the sliding body (116) running around the central axis (44).

8. A compressor according to one of the preceding claims, characterized in that on the axial support surface (102) radially outboard and / or radially inwardly an edge surface (154) of the second compressor body base (36) connects, relative to a plane in which the Axialstützfläche (102) extends, extends back.

9. A compressor according to one of the preceding claims, characterized in that the sliding body (116) is supported with a sliding bearing surface (118) on the carrier element (112).

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

in that the carrier element (112) has a carrier surface (114) on which the sliding body (116) is supported by the sliding support surface (118).

11. A compressor according to any one of the preceding claims, characterized

characterized in that the sliding body (116) is plate-shaped,

in particular as an annular disc is formed.

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

characterized in that the first stationary compressor body (24) is made of cast steel.

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

characterized in that the second compressor body (26) made

Aluminum alloy is made.

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

characterized in that the sliding body (116) is formed of spring steel.

15. A compressor according to any one of the preceding claims, characterized in that the carrier element (112) is formed of sintered material.

16. A compressor according to claim 15, characterized in that the carrier element (112) has a support surface (114) formed by an open-pored sintered material on which the sliding body (116) with its sliding support surface (118) is supported.

17. A compressor according to the preamble of claim 1 or any one of the preceding claims, characterized in that the axial guide (96) the second compressor body (26) on a axial support surface formed by this (102) transversely to the central axis (44) slidably supported and that the axial support surface (102) is formed by a compressor body base (36) of the second compressor body (26) carrying the spiral rib (38).

18. A compressor according to claim 15, characterized in that the

Cam receiver (242) in the compressor body base (34) is integrated.

19. A compressor according to claim 18, characterized in that the

Carrier receptacle (242) in the direction parallel to the central axis (44) without overhang to the support surface (102) on the compressor body base (36) is arranged.

20. A compressor according to the preamble of claim 1 or any one of the preceding claims, characterized in that the self-rotation preventing coupling (164) at least two

Coupling element sets (162) comprising at least two

Coupling elements (172, 182, 192), comprising.

21. A compressor according to claim 20, characterized in that one of the coupling elements (172) on the compressor body base (36) is held.

22. A compressor according to claim 20 or 21, characterized in that one of the coupling elements (192) is held on the carrier unit (112).

23. A compressor according to any one of claims 20 to 22, characterized in that the self-rotation preventing coupling (164) has more than two coupling element sets (162).

24. A compressor according to claim 23, characterized in that the coupling element sets (162) about the central axis (44) of the orbital path (48) are arranged at equal angular intervals around.

25. A compressor according to any one of claims 20 to 24, characterized in that one (172) of the coupling elements by a pin body (174) is formed.

26. A compressor according to any one of claims 20 to 25, characterized in that one (192) of the coupling elements as a cylindrical receptacle (194) is formed.

27. A compressor according to any one of claims 20 to 26, characterized in that one (182) of the coupling elements as in the cylindrical receptacle (194) arranged annular body (184) is formed.

28. A compressor according to claim 27, characterized in that the annular body (184) loosely in the cylindrical receptacle (194) sits.

29. A compressor according to the preamble of claim 1 or any one of the preceding claims, characterized in that the compressor body base (36) of the second compressor body (26) with pockets (204) is provided, the cylindrical receptacles (194) of the coupling element sets (162 ) facing openings (206).

30. A compressor according to claim 29, characterized in that the openings (206) of the pockets (204) with two successively arranged in Umiaufrichtung cylindrical receptacles (194) are overlapping positionable.

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

characterized in that the central axis (44) of the stationary compressor body (24) extends lying.

32. A compressor according to any one of the preceding claims, characterized in that a drive shaft (218) of the drive motor (212) extends lying.

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

characterized in that the compressor housing (12) consists of a

Aluminum alloy is.