EP3194782B1 - Scroll compressor - Google Patents

Description

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, which has a driven by the drive motor and rotating on a path about a central axis of the drive shaft driver t, which cooperates with a driver receiving the second compressor body,
and a self-rotation of the second compressor body preventing clutch.

Such compressors are known in the art.

In the pamphlets EP 2 012 015 A1 and EP 2 012 016 A1 a scroll compressor with movable cylindrical sliding bodies is disclosed.

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 sliding body, which in turn is supported slidably transverse to the central axis on a carrier element arranged in the compressor housing, and that the Axialstützfläche is supported on a circumferential surface about the central axis of the sliding body.

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.

According to the invention, the Axialstützfläche is supported on a circumferential surface about the central axis of the sliding surface.

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.

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 then be realized if the slider by a two-dimensional guide with Game is performed 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 values of the guide orbital radius 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, more preferably 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 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 advantageous if the guide with play as guide elements has a guide pin and a guide pin cooperating with the guide, which are two-dimensionally movable relative to each other that the engaging in the guide recess guide pin within the guide recess due to its lower on the diameter of the guide recess Diameter is movable.

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, which is very important for the guiding properties and the wear resistance.

The Axialstützfläche could be supported on individual surface areas 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 connects directly to the Axialstützfläche, and thus extends to the plane in which extends the Axialstützfläche, and then with increasing distance from the Axialstützfläche in increasing distance from the plane in which the axial support surface extends. 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 lubricant supply between the Axialstützfläche and the slider can also be further favored by the fact that the Axialstützfläche and / or the Axialstützfläche bearing Gleitstützfläche with microwells, for example, material-related and / or incorporated and / or embossed well structures are provided which receive lubricant available hold and distribute.

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 microwells, for example material-conditioned and / or machined and / or embossed depression structures, which receive lubricant hold and distribute.

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 above-described solution of the aforementioned object is provided in a further compressor of the type described above, that the axial guide slidably supports the second compressor body on an axial support surface formed by this axial axis and that the Axialstützfläche by a spiral rib carrying the compressor body base is formed.

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.

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 is held on the compressor body base.

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

In this case, thus, the coupling element sets are arranged and formed so as to be effective directly between the support unit and the compressor body base of the second compressor body, so that a compact structure 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 inventive solution 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 central 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.

Fig. 1

eine perspektivische Darstellung eines erfindungsgemäßen Kompressors;

Fig. 2

einen Längsschnitt durch den erfindungsgemäßen Kompressor, und zwar in einer durch eine Mittelachse eines stationären Verdichterkörpers verlaufenden Schnittebene;

Fig. 3

einen Querschnitt durch eine Spiralverdichtereinheit im Bereich der ineinandergreifenden Spiralrippen und eine Darstellung einer Orbitalbahn der bewegbaren Spiralrippe relativ zur stationären Spiralrippe;

Fig. 4

einen vergrößerten Längsschnitt gemäß Fig. 2 im Bereich des bewegbaren Verdichterkörpers und einer Axialführung für den bewegbaren Verdichterkörper;

Fig. 5

einen noch weiter vergrößerten Schnitt durch einen Teilbereich der Axialführung im Bereich einer Führung mit Spiel für einen Gleitkörper der Axialführung;

Fig. 6

eine Draufsicht auf die Axialführung mit dem Gleitkörper und einem diesen tragenden Trägerelement;

Fig. 7

eine perspektivische Darstellung der Axialführung mitsamt Kupplungselementen einer Kupplung zur Verhinderung einer Selbstdrehung umfassend eine Vielzahl von Kupplungselementensätzen;

Fig. 8

eine Draufsicht auf eine der Spiralrippe gegenüberliegende Flachseite des bewegbaren Verdichterkörpers;

Fig. 9 bis Fig. 14

eine schematische Darstellung des Zusammenwirkens der Kupplungselementensätze der die Selbstdrehung verhindernden Kupplung;

Fig. 15

einen Schnitt längs Linie 15-15 in Fig. 4 und

Fig. 16

einen Schnitt längs Linie 16-16 in Fig. 15.

In the drawing show:

Fig. 1

a perspective view of a compressor according to the invention;

Fig. 2

a longitudinal section through the compressor according to the invention, in a running through a central axis of a stationary compressor body sectional plane;

Fig. 3

a cross section through a scroll compressor unit in the region of the intermeshing spiral ribs and an illustration of an orbital path of the movable spiral rib relative to the stationary spiral rib;

Fig. 4

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;

Fig. 5

a still further enlarged section through a portion of the axial guide in the region of a guide with clearance for a sliding body of the axial guide;

Fig. 6

a plan view of the axial guide with the slider and a supporting this support member;

Fig. 7

a perspective view of the axial guide together with coupling elements of a clutch for preventing self-rotation comprising a plurality of coupling element sets;

Fig. 8

a plan view of the spiral rib opposite flat side of the movable compressor body;

FIG. 9 to FIG. 14

a schematic representation of the interaction of the coupling element sets of the self-rotation preventing coupling;

Fig. 15

a section along line 15-15 in Fig. 4 and

Fig. 16

a section along line 16-16 in Fig. 15 ,

An in Fig. 1 illustrated embodiment of a designated as a whole with 10 inventive compressor 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 a disposed between the end housing portions 14 and 16 Intermediate section 18 has.

As in Fig. 2 1, in the first housing section 14, there is provided a scroll compressor unit 22 designated as a whole which has a first compressor housing 24, in particular in the first housing section 14, and a second compressor housing 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 above which a second spiral rib 38 rises.

The compressor bodies 24 and 26 are arranged relative to each other so that the spiral ribs 34, 38 mesh with each other as in FIG Fig. 3 illustrated, 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 an orbital path 48 with a compressor orbital trajectory radius 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, in the region of an axial support surface 102, such that the compressor body base 36 of the second compressor body 26 is relative to the first compressor body stationarily positioned in the compressor housing 12 24 and in the direction parallel to the central axis 44 is supported such that the Axialdichtelemente 58 remain on the bottom surface 64 and not lift off this, while the compressor body base 36 with the Axialstützfläche 102 can move transversely to the central axis 44 slidably relative to the axial guide 96.

For this, as in Fig. 4 illustrated, the axial guide 96 formed by a support member 112 which is in particular made of an open-pore sintered material and having a the 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 as a whole with 116 denoted in particular plate-shaped slider 116 rests with a Gleitauflagefläche 118, wherein the sliding body 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.

Thus, an axial movement of the second compressor body 26 is prevented 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, as exemplified in Fig. 6 shown in connection with the sliding support surface 122.

In order to specify the limited two-dimensional mobility of the slider 116 parallel to a plane perpendicular to the central axis 44 plane E relative to the 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, the guide with game 132 a in the slider 116 provided guide recess 134 which has a diameter DF, and comprises 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 in which the sliding body 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, due to the movement of the slider 116 with the guide orbital radius FOR relative to the support member 112, the clearance 146 is filled with a lubricating film 147 similar to the operation of a hydrodynamic bearing.

For a stable lubricating film 147, 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, VOR or less, more preferably 0.2 times the compressor orbital radius VOR or less.

Furthermore, due to the fact that the carrier element 112 is made of an open-pore sintered material 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 over the pores of the carrier element 112 in the region of Carrier surface 114 is available for the construction of the lubricating 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 in the Fig. 4 . 6 . 7 and 8th 12, axial support surface 102 and cooperating sliding support surface 122 and support surface 114 and cooperating sliding surface 118 are all disposed radially outwardly of a plurality of coupling element sets 162 which are equally spaced radially from center axis 44 and at equal angular intervals about the central axis 44 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 in FIGS Fig. 4 . 6 to 8 illustrated, as a first coupling element 172 a pin body 174 which has a cylindrical surface 176 and engages with this cylindrical 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 designed as a receptacle 194 provided in the carrier element 112 for the annular body 184 and which has a cylindrical inner wall surface 196.

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, like in the Fig. 9 to 14 in each case one of the coupling element sets 162 is effective to prevent the self-rotation of the second movable compressor body 26, wherein, for example, in six coupling element sets 162 after passing through an angular range of 60 °, the effectiveness of each coupling element set 162 of a coupling element set 162 to the coupling element set next 162 in the direction of rotation replaced.

Due to the fact that each coupling element set 162 has three coupling elements 172, 182 and 192 and in particular a ring body 184 between the respective pin body 174 and the respective receptacle 194 is effective, on the one hand the wear resistance of the coupling element sets 162 is improved, on the other hand, the lubrication improved in the same area and in addition also reduces the noise generated by the coupling element sets 162, which results from the change of effectiveness of one 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 openings 198 (FIG. Fig. 7 ) of the slider 116, whereby lubricant from the lubricating films 147 and 149 the coupling element sets 162 can be supplied.

To aid in lubrication are in the compressor body base 36 as in the Fig. 8 and 15 shown, 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 successive recordings 194 of the coupling element sets 162 in the direction of rotation may overlap, so that the pockets 204 are capable of causing a lubricant exchange between successive coupling element sets 162 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 concept of the 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 body 24 and 26 are normally lying, that is at a maximum angle of 30 ° to a horizontal, extending 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 the operation and is 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 the movable compressor body 26 via an eccentric drive designated as a whole by 232, which moves in an orbiting manner around 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 rotary bearing 238, wherein the pivot bearing 238 a Turning the driver 236 relative to the movable compressor body 26 allowed.

The follower 236 is limitedly rotatable relative to the eccentric pin 234 and relative to the cam receiver 242 and allows for adjustment of the radius of orbital movement of the movable compressor body 26 to hold the spiral ribs 34 and 38 in abutment with each other.

To accommodate the pivot bearing 238 is, as in the Fig. 2 . 4 and 16 illustrated, the second compressor body 26 is provided with a driver receptacle 242 which receives the pivot bearing 238.

The cam receiver 242 is set back relative to the flat side 98 of the compressor body base 36 and thus 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 (15)

1. A compressor, including
   a compressor housing (12),
   a scroll compressor unit (22) that is arranged in the compressor housing (12) and has a first, stationary compressor body (24) and a second compressor body (26) that is movable in relation to the stationary compressor body (24), whereof first and second scroll vanes (34, 38), in the shape of a circle involute, engage in one another to form compressor chambers (42) when the second compressor body (26) is moved in relation to the first compressor body (24) on an orbital path (48),
   an axial guide (96) that supports the movable compressor body (26) to prevent movements in the direction parallel to a centre axis (44) of the stationary compressor body (24) and, in the event of movements, guides it in the direction transverse to the centre axis (44),
   a drive motor (212) that drives an eccentric drive (232) for the scroll compressor unit (22), wherein the eccentric drive (232) has an entrainer (236) that is driven by the drive motor (212), that revolves on a path about a centre axis (44) of a drive shaft (218) and that cooperates with an entrainer receptacle (242) in the second compressor body (26),
   and a coupling (164) that prevents the second compressor body (26) from rotating freely,
   characterised in that the axial guide (96) supports a compressor body base (36), which carries the scroll vane (38), of the second compressor body (26) against an axial support face (102), in that the axial support face (102) abuts a sliding body (116) such that it is slidable transversely to the centre axis (44), the sliding body (116) for its part being supported, such that it is slidable transversely to the centre axis (64), on a carrier element (112) that is arranged in the compressor housing (12), and in that the axial support face (102) is supported on an annular face of the sliding body (116) that surrounds the centre axis (44).
2. A compressor according to claim 1, characterised in that the sliding body (116) is movable in two dimensions, in relation to the compressor body base (36) and in relation to the carrier element (112).
3. A compressor according to claim 1 or 2, characterised in that the sliding body (116) is movably guided in a two-dimensional guidance with play (132) in relation to the compressor body base (36) and/or in relation to the carrier element (112).
4. A compressor according to claim 3, characterised in that the guide (132) has a first guiding element (134) that is arranged on the sliding body (116) and a second guiding element (136) that is either connected to the compressor body base (36) or to the carrier element (112).
5. A compressor according to claim 3 or 4, characterised in that the guidance with play (132) has, as the guiding elements, a guide pin (136) and a guide recess (134) that cooperates with the guide pin (136), and these are movable in two dimensions in relation to one another.
6. A compressor according to one of the preceding claims, characterised in that the axial support face (102) takes the form of an annular face surrounding a centre axis (46) of the movable compressor body (26).
7. A compressor according to one of the preceding claims, characterised in that the axial support face (102) is adjoined, radially outwardly and/or radially inwardly, by an edge face (154) of the second compressor body base (36) that is set back in relation to a plane in which the axial support face (102) extends.
8. A compressor according to one of the preceding claims, characterised in that the sliding body (116) is supported against the carrier element (112) by means of a sliding bearing face (118) and in that in particular the carrier element (112) has a carrier face (114) against which the sliding body (116) is supported by means of the sliding bearing face (118).
9. A compressor according to one of the preceding claims, characterised in that the sliding body (116) takes a plate-like form, in particular as an annular disc.
10. A compressor according to one of the preceding claims, characterised in that the first, stationary compressor body (24) is made from cast steel.
11. A compressor according to one of the preceding claims, characterised in that the second compressor body (26) is made from aluminium alloy.
12. A compressor according to one of the preceding claims, characterised in that the sliding body (116) is made from spring steel.
13. A compressor according to one of the preceding claims, characterised in that the carrier element (112) is made from sintered material, in that in particular the carrier element (112) has a carrier face (114) formed by an open-pored sintered material, on which the sliding body (116) is supported by means of its sliding bearing face (118).
14. A compressor according to one of the preceding claims, characterised in that the axial guide (96) supports the second compressor body (26) against an axial support face (102) that is formed by the latter such that it is slidable transversely in relation to the centre axis (44), and in that the axial support face (102) is formed by a compressor body base (36) of the second compressor body (26) that carries the scroll vane (38).
15. A compressor according to claim 13, characterised in that the entrainer receptacle (242) is integrated in the compressor body base (36), and in that in particular the entrainer receptacle (242) is arranged on the compressor body base (36) such that it does not project beyond the support face (102) in the direction parallel to the centre axis (44).

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