Refrigerant compressor unit

Abstract

In order to make a refrigerant compressor unit as light and compact as possible, so that it can be used as a transcritical CO2 compressor, it is proposed that the cylinder head be made of an iron-containing cast material and that the housing sleeve, the compressor housing section and a cylinder housing block accommodating the cylinders as well as the motor housing section form a single part, in particular made of lightweight material.

Description

[0001] The invention relates to a refrigerant compressor unit comprising a housing with an end-closed housing sleeve, wherein the housing sleeve comprises a compressor housing section in which at least two cylinders, each with a piston arranged therein, and a drive chamber with drive units arranged therein and driven by a drive shaft are arranged, wherein the housing sleeve comprises a motor compartment with an electric motor arranged therein that drives the drive shaft, wherein a valve plate covering the cylinders is arranged on the housing sleeve, which carries a cylinder head on its side opposite the cylinders, in which at least one inlet chamber and at least one outlet chamber are arranged.

[0002] Such refrigerant compressor units are known from the prior art.

[0003] However, the problem with these is to build them as light and compact as possible, but in such a way that they can be used especially as transcritical CO2 compressors.

[0004] This problem is solved according to the invention in a refrigerant compressor unit of the type described above by the fact that the cylinder head is made of an iron-containing cast material and that the housing sleeve with the compressor housing section and a cylinder housing block receiving the cylinders as well as the motor housing section form a one-piece part, in particular made of lightweight material.

[0005] The advantage of the solution according to the invention is that it makes it possible, on the one hand, to give the cylinder head the necessary stability, especially in the case of application as a transcritical CO2 compressor, and on the other hand, to manufacture the other components of the refrigerant compressor unit from material with the lowest possible specific weight, in particular lightweight material.

[0006] In particular, such compressors can be advantageously used in refrigeration systems for all types of transport applications, for example, vehicles for road and / or rail and / or aviation.

[0007] Regarding the design of the cylinder head, a wide variety of solutions are conceivable.

[0008] One solution proposes that the cylinder head be made from a cast material containing an iron-carbon alloy.

[0009] Another possibility is that the cylinder head is made of cast steel.

[0010] Another alternative possibility is that the cylinder head is made of cast iron.

[0011] In the case of manufacturing the cylinder head from cast iron, there are also further modifications.

[0012] One solution involves making the cylinder head from cast iron with graphite.

[0013] The graphite could be present as lamellar graphite.

[0014] However, for the stability of the cylinder head under high loads, it has proven particularly advantageous if the cylinder head is made of cast iron with spheroidal graphite or vermicular graphite.

[0015] Furthermore, the lightweight material used for the housing sleeve was not specified in more detail.

[0016] One advantageous solution provides that the housing sleeve, together with the compressor housing section, the cylinder housing block and the motor housing section, is made of light metal, in particular aluminum.

[0017] It is particularly advantageous if the housing sleeve with the compressor housing section, the cylinder housing block and the motor housing section is made of an aluminum alloy with silicon, as this provides good stability despite its low specific weight.

[0018] In order to be able to advantageously form the cylinders into the housing sleeve in the cylinder housing block, it has proven useful if the housing sleeve, together with the compressor housing section, the cylinder housing block and the engine housing section, is manufactured as a casting, especially from light metal casting.

[0019] A particularly advantageous arrangement with regard to the possibility of providing an installation position with cylinders aligned transversely to the vertical direction provides that the cylinders are arranged successively in a series direction, wherein the series direction is in particular parallel to the drive shaft.

[0020] To save weight and especially to improve thermal expansion behavior, it has proven advantageous to provide separate recesses in the cylinder housing block in addition to the cylinders.

[0021] No further details were given regarding the design of the housing sleeve.

[0022] One advantageous solution provides that the housing sleeve has end-end mounting openings which are closed with housing covers.

[0023] The end-side mounting openings thus allow easy access to the installation of the drive units with the drive shaft into the drive compartment on the one hand, and easy access to the installation of the electric motor into the engine compartment on the other.

[0024] No further information was provided regarding the case covers.

[0025] One advantageous solution is to also make the housing covers out of light metal, especially aluminum.

[0026] In order to make the housing as compact and space-saving as possible, and thus also to save weight, an advantageous solution is to have the housing covers curved in order to give them sufficient stability with the lowest possible weight.

[0027] In particular, it is provided that one of the housing covers has a concave shape extending into the housing sleeve.

[0028] Furthermore, it is advantageously provided that one of the housing covers has a bulge that curves away from the housing sleeve.

[0029] In this case, the bulge can be used to increase the space required in the housing sleeve, especially the motor compartment, for the installation of components such as the electric motor.

[0030] In this case, for example, it is provided that one of the housing covers is equipped with at least one contact insert for making electrical connections, so that the space required for this contact insert and the electrical connections can also be formed by the curvature of the housing cover itself.

[0031] Furthermore, it is expediently provided that one of the housing covers is equipped with a refrigerant connection in order to easily supply refrigerant to the housing.

[0032] In particular, the connections in the housing covers make it possible to avoid arranging them in the housing sleeve, thus preventing the connections from impairing the structure of the housing sleeve and consequently its stability.

[0033] Regarding the further development of the housing sleeve, it is advantageous if the housing sleeve is provided with an intermediate wall integrally molded onto it and separating the drive compartment from the engine compartment.

[0034] Such a partition wall, molded in one piece onto the housing sleeve, stabilizes the housing sleeve in a simple way and creates the possibility of further stabilizing the housing sleeve in a weight-saving manner by means of the shape of this partition wall, for example by means of struts extending away from it.

[0035] In particular, in this case a bearing section for the drive shaft passing through the partition wall is provided.

[0036] No further details have been provided regarding the design of the cylinder head.

[0037] One advantageous solution involves the cylinder head having a high-pressure refrigerant connection, allowing the cylinder head to be directly connected to the high-pressure line. This prevents the heat-sensitive lightweight material of the housing from coming into contact with the hot, high-pressure compressed refrigerant.

[0038] In an advantageous embodiment, it is further provided that the cylinder head has a connection for low-pressure refrigerant.

[0039] In order to optimally cool the engine compartment, it is preferably provided that the engine compartment and in particular the electric motor are permeated by aspirated refrigerant, so that sufficient cooling of the electric motor is easily achievable.

[0040] Furthermore, the refrigerant flowing through the engine compartment is preferably fed through a channel to a through-opening in the valve plate in order to allow it to enter the intake chamber in the cylinder head.

[0041] In particular, it is provided that the refrigerant enters an inlet chamber of the cylinder head after cooling the electric motor.

[0042] Preferably, the channel supplying the refrigerant to the valve plate is formed into the intermediate wall of the housing sleeve.

[0043] In order to additionally create the possibility of maintaining the drive compartment at the pressure of the refrigerant flowing through the engine compartment, it is preferably provided that the channel is connected to a channel leading to the drive compartment.

[0044] In particular, in the case of a two-stage refrigerant compressor unit, it is provided that the cylinder housing block has at least one cylinder for compressing refrigerant from low pressure to medium pressure and at least one cylinder for compressing refrigerant from medium pressure to high pressure.

[0045] In the simplest case, the cylinder head can be designed such that it has an inlet chamber for refrigerant at low pressure, an outlet chamber for refrigerant at medium pressure, an inlet chamber for refrigerant at medium pressure and an outlet chamber for refrigerant at high pressure.

[0046] In this design, the cylinders are also arranged consecutively in a row to allow for the possibility of aligning the cylinders transversely to a vertical direction.

[0047] To ensure the safe operation of the refrigerant compressor unit in a refrigerant circuit, the cylinder head is provided with a pressure relief valve connected to the outlet chamber for refrigerant compressed at high pressure.

[0048] To avoid conditions with overpressure of the supplied refrigerant on the low-pressure side as well, for example during standstill phases, it is expedient to provide the cylinder head with a pressure relief valve connected to the inlet chamber.

[0049] To reduce the installation height of the refrigerant compressor unit according to the invention, it is advantageously provided that the cylinder housing block is arranged on the housing sleeve in an operating position or installation position such that the cylinders extend transversely to a vertical direction.

[0050] In particular, it is provided that the pistons move in a direction of movement in the cylinders that is transverse to the vertical direction, in particular at an angle between 70° and 110° to the vertical direction.

[0051] To further optimize the installation situation, it is provided that the housing is arranged in an operating position or installation position such that the cylinder housing block, the valve plate and the cylinder head are arranged relative to the housing sleeve in a direction transverse to a vertical direction on one side of the housing sleeve.

[0052] In order to obtain favorable lubrication in the drive chamber of the compressor housing section, it is provided that a lubricant bath forming in this chamber lies vertically below the cylinders and at a distance from them, so that the pistons also move above the lubricant bath.

[0053] To ensure a sufficiently good distribution of the lubricant, a lubricant delivery unit is provided in the compressor housing section, which takes lubricant from the engine compartment and feeds it to the lubricant bath in the compressor housing section.

[0054] Furthermore, it is preferably provided that the housing is provided with at least two mounting points that allow the housing to be mounted in such a way that the cylinder housing block, the valve plate and the cylinder head are arranged on one side of the housing sleeve in a direction transverse to a vertical direction relative to the housing sleeve.

[0055] The mounting points can, in principle, be located on the housing covers.

[0056] However, it is advantageous if the mounting points are located on the housing sleeve.

[0057] Furthermore, it is preferably provided that mounting rails are arranged on the mounting points, allowing mounting on a mounting surface. The mounting surface can, for example, be an approximately horizontal or an approximately vertical mounting surface.

[0058] Alternatively or additionally, in a refrigerant compressor unit of the type described above, it is provided that the stator is mounted in the motor housing section by means of support elements inserted into the motor housing section, which on the one hand bear against a stator receiving surface of the motor housing section and on the other hand encompass the stator inserted into the support elements on its outside, in particular over at least three quarters of its circumference and support it spring-elastically relative to the stator receiving surface.

[0059] The advantage of this solution lies in the fact that the spring-elastic support of the stator relative to the stator mounting surface allows for the compensation of diameter variations in the stator mounting surface of the lightweight motor housing section, while simultaneously ensuring that the stator is always centered within the motor housing section. This is because the surrounding support elements, which provide spring-elastic support to the stator mounting surface, are located on opposite sides of the stator between the stator and the motor housing section, thus keeping the stator centered relative to the motor housing section in the event of both thermally induced and pressure-induced diameter changes.

[0060] This has the advantage that the gap between the stator and the rotor can be kept as small as possible, thus enabling high efficiency of the electric motor.

[0061] The spring-like load-bearing elements can be designed in a wide variety of ways. For example, the load-bearing elements can be elastic bands.

[0062] A particularly advantageous solution provides that the support elements have spring-elastic bodies which are dimensioned so that they are in an elastically deformed state in all operating conditions of the motor housing section occurring during the operation of the refrigerant compressor, that is, that in no operating condition do the spring-elastic bodies enter the range of plastic deformation, which would cause the elastic properties of the spring-elastic bodies to change.

[0063] In particular, it is advantageously provided that the support elements are arranged around the stator and support the stator several times on opposite sides of the rotor axis relative to the stator mounting surface of the motor housing section, in order to achieve a uniform, spring-elastic positioning of the stator acting on it from all sides.

[0064] Furthermore, it is preferably provided that the support elements have elastic bodies arranged at defined angular intervals around the rotor axis.

[0065] For example, this solution also enables cooling of the electric motor by allowing refrigerant to flow between the stator mounting surface and the outside of the stator and through the support elements parallel to the rotor axis.

[0066] In particular, the elastic bodies are positioned relative to each other on the stator mounting surface by a band material that positions them relative to each other and circulates around the stator.

[0067] A particularly simple design of the elastic bodies involves molding them into the band material.

[0068] One particularly advantageous solution involves the band material being designed as a ring-like clip with open ends, so that it can be easily deformed for assembly in the motor housing section and thus, in particular, inserted into a motor housing section made of light metal without producing chips.

[0069] A particularly simple implementation of the spring-elastic bodies provides that they have flank areas running at an acute angle to the outside of the stator and / or to the stator mounting surface between foot areas and support areas, the former of which are located on the outside of the stator and the latter on the stator mounting surface.

[0070] Such flank areas running obliquely towards the outside of the stator and / or towards the stator mounting surface allow a spring-elastic movement of the support areas relative to the foot areas, without the foot areas or support areas moving in a circular direction around the stator, since the spring-elastic movement primarily takes place in the flank areas.

[0071] A particularly advantageous solution provides that the spring-elastic bodies are successively molded into a spring-elastic strip material, so that successive support areas abut an outside of the stator or the stator mounting and successive foot areas abut the stator mounting surface or the outside of the stator, that is, that the support areas and the foot areas are arranged successively in a circumferential direction around the stator and thus the spring-elastic support of the stator relative to the stator mounting surface takes place essentially around the entire stator.

[0072] Furthermore, it has proven advantageous if the spring-elastic bodies are located between edge regions arranged around the stator and the support regions are connected to the edge regions via flank regions running at an acute angle to the outside of the stator and / or to the stator receiving surface.

[0073] This solution, through these flank areas, particularly in addition to the flank areas connecting the support areas with the foot areas, provides advantageous elastic support of the support areas relative to the edge areas, and furthermore, such flank areas, through their action as an insertion ramp, allow the stator to be inserted into the support elements already resting on the stator mounting surface, with the insertion of the stator taking place parallel to the rotor axis of the electric motor.

[0074] Preferably, in this solution, the support areas are located on the outside of the stator or the stator mounting surface, and the edge areas are located on the stator mounting surface or the outside of the stator.

[0075] In particular, the support elements designed according to one or more of the features described above enable a decoupling of the stator and the housing sleeve, whereby on the one hand the support elements can be mounted in the housing sleeve without chips and on the other hand the stator can be mounted without chips, in particular via the flank areas designed as insertion ramps, by pushing it in and dismantling it by pulling it out, whereby the stator deforms the spring-elastic elements when being pushed in.

[0076] In particular, if the support elements described above are not ring-shaped closed elements, but rather enclose the stator but have ends that can be positioned at a distance from each other around the circumference, the support elements can be used simply and without damaging the housing sleeve by means of appropriate elastic deformation to reduce the outer contour.

[0077] This is particularly advantageous if the housing sleeve is made of light metal, preferably aluminum, or aluminum casting.

[0078] Regarding the design of the supporting elements themselves, no further details have been given in connection with the previous explanation of the solution according to the invention.

[0079] One advantageous solution is to have the supporting elements made of a spring-elastic material, in particular spring steel.

[0080] Particularly when the support elements are made of spring-elastic material, the stator can be inserted into or pulled out of the support elements without producing chips.

[0081] Furthermore, no information has yet been provided on how the support elements are positioned in the engine housing section.

[0082] One advantageous solution for achieving a defined relative position of the support elements is to position support elements arranged successively in the direction of the rotor axis at a distance from each other in the motor housing section by means of a spacer element.

[0083] Preferably, the spacer element rests against the stator mounting surface of the motor housing section in the same way as the support elements and holds the support elements at the distance specified by the length of the spacer element in the direction of the rotor axis.

[0084] In particular, the spacer element also rests against the stator receiving surface, encompassing the entire stator.

[0085] In order to be able to align at least one of the support elements with respect to its position in the motor housing section in a defined manner relative to the stator receiving surface, it is preferably provided that at least one of the support elements is positioned with respect to its position in the motor housing section by a step adjoining the stator receiving surface, namely by positioning the support element at least with one side against the step.

[0086] Furthermore, it is expediently provided that the refrigerant compressor is designed for CO2 as the refrigerant and thus a high pressure to be generated is above 80 bar and a medium pressure to be generated, depending on the embodiment, is above 40 bar.

[0087] The foregoing description of solutions according to the invention thus includes in particular the various combinations of features defined by the embodiments numbered below: 1. Refrigerant compressor unit (10), comprising a housing (12) with an end-closed housing sleeve (16), wherein the housing sleeve (16) comprises a compressor housing section (26) in which at least two cylinders (42, 44, 46) each have a piston (62, 64, 66) arranged therein, and a drive chamber (38) with drive units (92, 94, 96) arranged therein and driven by a drive shaft (70) are arranged, wherein the housing sleeve (16) comprises a motor compartment (158) with an electric motor (170) arranged therein, which drives the drive shaft (70), wherein a valve plate (120) covering the cylinders (42, 44, 46) is arranged on the housing sleeve (16), which carries a cylinder head (140) on its side opposite the cylinders (42, 44, 46), in which at least one inlet chamber (142) and at least one outlet chamber (144) are arranged,wherein the cylinder head (140) is made of an iron-containing cast material and wherein the housing sleeve (16), with the compressor housing section (26) and a cylinder housing block (40) accommodating the cylinders (42, 44, 46) as well as the motor housing section (28) form a single-piece part, in particular made of lightweight material. 2. Refrigerant compressor unit according to embodiment 1, wherein the cylinder head (140) is made of a cast material comprising an iron-carbon alloy. 3. Refrigerant compressor unit according to embodiment 1 or 2, wherein the cylinder head (140) is made of cast steel. 4. Refrigerant compressor unit according to embodiment 1 or 2, wherein the cylinder head (140) is made of cast iron. 5. Refrigerant compressor unit according to embodiment 4, wherein the cylinder head (140) is made of cast iron containing graphite. 6. Refrigerant compressor unit according to embodiment 5,wherein the cylinder head (140) is made of spheroidal graphite or vermicular graphite cast iron. 7. Refrigerant compressor unit according to one of the preceding embodiments, wherein the housing sleeve (16) with the compressor housing section (26), the cylinder housing block (40) and the motor housing section (28) is made of light metal, in particular aluminum. 8. Refrigerant compressor unit according to one of the preceding embodiments, wherein the housing sleeve (16) with the compressor housing section (26), the cylinder housing block (40) and the motor housing section (28) is made of an aluminum casting alloy with silicon. 9. Refrigerant compressor unit according to one of the preceding embodiments, wherein the housing sleeve (16) with the compressor housing section (26), the cylinder housing block (40) and the motor housing section (28) is a casting, in particular made of light metal casting.10. Refrigerant compressor unit according to one of the preceding embodiments, wherein the cylinders (42, 44, 45) are arranged successively in a series direction (48) in the cylinder housing block (40), which in particular runs parallel to the drive shaft (70). 11. Refrigerant compressor unit according to one of the preceding embodiments, wherein the cylinder housing block (40) has, in addition to the cylinders (42, 44, 45), recesses (312, 314, 316, 318, 322) separate from them. 12. Refrigerant compressor unit according to one of the preceding embodiments, wherein the housing sleeve (16) has mounting openings (21, 23) at its ends, which are closed with housing covers (22, 24). 13. Refrigerant compressor unit according to embodiment 12, wherein the housing covers (22, 24) are made of light metal, in particular aluminum. 14. Refrigerant compressor unit according to embodiment 12 or 13, wherein the housing covers (22,24) are curved. 15. Refrigerant compressor unit according to one of embodiments 12 to 14, wherein one of the housing covers (22) has a concavity (36) extending into the housing sleeve (16). 16. Refrigerant compressor unit according to one of embodiments 12 to 15, wherein one of the housing covers (24) has a bulge (286) curving away from the housing sleeve (16). 17. Refrigerant compressor unit according to one of embodiments 12 to 16, wherein one of the housing covers (24) is provided with at least one contact insert (252) for the passage of electrical connections (264). 18. Refrigerant compressor unit according to one of the preceding embodiments, wherein one of the housing covers (24) is provided with a refrigerant connection (278). 19. Refrigerant compressor unit according to one of the preceding embodiments,wherein the housing sleeve (16) is provided with an intermediate wall (156) integrally formed with it and separating the drive compartment (38) from the engine compartment (158). 20. Refrigerant compressor unit according to embodiment 19, wherein a bearing section (164) for the drive shaft (17) passing through the intermediate wall (156) is provided. 21. Refrigerant compressor unit according to one of the preceding embodiments, wherein the cylinder head (140) has a high-pressure connection (304, 304') for refrigerant. 22. Refrigerant compressor unit according to one of the preceding embodiments, wherein the cylinder head (140) has a connection (306') for refrigerant at low pressure. 23. Refrigerant compressor unit according to one of the preceding embodiments, wherein the engine compartment (158) is traversed by aspirated refrigerant. 24. Refrigerant compressor unit according to embodiment 23.wherein the refrigerant flowing through the engine compartment (158) is supplied through a channel (292) to a through-opening (294) in the valve plate (120). 25. Refrigerant compressor unit according to embodiment 23 or 24, wherein the refrigerant, after cooling the electric motor (170), enters an inlet chamber (142) of the cylinder head (140). 26. Refrigerant compressor unit according to embodiment 24 or 25, wherein the channel (292) is formed in the partition wall (156). 27. Refrigerant compressor unit according to one of embodiments 24 to 26, wherein the channel (292) is connected to a channel (296) leading to the drive compartment (28). 28. Refrigerant compressor unit according to one of the preceding embodiments, wherein the cylinder block (40) has at least one cylinder (42',44') for compressing refrigerant from low pressure to medium pressure and at least one cylinder (46') for compressing refrigerant from medium pressure to high pressure. 29. Refrigerant compressor unit according to embodiment 28, wherein the cylinder head (140) has an inlet chamber (142'a) for refrigerant at low pressure, an outlet chamber (144'a) for refrigerant at medium pressure, an inlet chamber (142'b) for refrigerant at medium pressure, and an outlet chamber (144'b) for refrigerant at high pressure. 30. Refrigerant compressor unit according to one of the preceding embodiments, wherein the cylinder head (140) is provided with a pressure relief valve (302) connected to the outlet chamber (144) for refrigerant compressed at high pressure. 31. Refrigerant compressor unit according to one of the preceding embodiments,wherein the cylinder head (140) is provided with a pressure relief valve (300) connected to the inlet chamber (142). 32. Refrigerant compressor unit according to one of the preceding embodiments, wherein the cylinder housing block (40, 40') is arranged on the housing sleeve (16) such that the cylinders (42, 44, 46, 42', 44', 46') extend transversely to a vertical direction (348). 33. Refrigerant compressor unit according to one of the preceding embodiments, wherein the housing (12) is arranged in an operating position such that the cylinder housing block (40, 40'), the valve plate (120), and the cylinder head (140) are arranged relative to the housing sleeve (16) in a direction transversely to a vertical direction (348) on one side of the housing sleeve (16). 34. Refrigerant compressor unit according to one of the preceding embodiments,wherein a lubricant bath (352) forming in the drive chamber (38) of the compressor housing section (26) is arranged in a vertical direction (348) below the cylinders (42, 44, 46) and at a distance from them. 35. Refrigerant compressor unit according to one of the preceding embodiments, wherein a lubricant supply unit (354) is provided in the compressor housing section (26), which receives lubricant from the motor chamber (158) and supplies it to the lubricant bath (352) in the compressor housing section (26). 36. Refrigerant compressor unit according to one of the preceding embodiments, wherein the housing (12) is provided with at least two mounting bosses (332, 334, 336) which allow the housing (12) to be mounted such that the cylinder housing block (40),The valve plate (120) and the cylinder head (140) are arranged on one side of the housing sleeve relative to the housing sleeve (16) in a direction transverse to a vertical direction (348). 37. Refrigerant compressor unit according to embodiment 35, wherein the mounting attachments (332, 334, 336) are arranged on the housing sleeve (16). 38. Refrigerant compressor unit (10) according to one of the preceding embodiments, wherein the stator (172) is mounted in the motor housing section (28) by means of support elements (192, 194) inserted into the motor compartment (158), which on one side bear against a stator receiving surface (184) of the motor housing section (28) and on the other hand encompass the stator (172) inserted into the support elements (192, 194) on its outer side (182) and support it springily relative to the stator receiving surface (184). 39. Refrigerant compressor unit according to embodiment 38, wherein the support elements (192, 194) have spring-elastic bodies (202) which are dimensioned such thatthat they are in an elastically deformed state in all operating conditions of the motor housing section (28) occurring during the operation of the refrigerant compressor (10). 40. Refrigerant compressor unit according to embodiment 38 or 39, wherein the support elements (192, 194) are arranged extending around the stator (172) and support the stator (172) multiple times on opposite sides of the rotor axis (178) relative to the stator receiving surface (184) of the motor housing section (28). 41. Refrigerant compressor unit according to embodiment 39 or 40, wherein the support elements (192, 194) have elastic bodies (202) arranged around the rotor axis (178) at defined angular intervals. 42. Refrigerant compressor unit according to one of the preceding embodiments,wherein the elastic bodies (202) are positioned relative to each other by a strip material (208) which positions them relative to each other and circulates around the stator (172). 43. Refrigerant compressor unit according to embodiment 42, wherein the elastic bodies (202) are formed in the strip material (208). 44. Refrigerant compressor unit according to embodiment 42 or 43, wherein the strip material (208) is formed as a ring-like clip with open ends (210). 45. Refrigerant compressor unit according to one of the preceding embodiments, wherein the spring-elastic bodies (202) extend at an acute angle to the outside (182) of the stator (172) and / or to the stator receiving surface (184) between foot regions (228) and support regions (222), the one of which bears against the outside (182) of the stator (172) and the other against the stator receiving surface (184), flank regions (224, 226, 234,236). 46. Refrigerant compressor unit according to one of the preceding embodiments, wherein the spring-elastic bodies (202) are successively molded into a spring-elastic strip material (208), such that successive support areas (222) bear against an outer surface (182) of the stator (172) or against the stator receiving surface (184) and successive foot areas (228) bear against the stator receiving surface (184) or the outer surface (182) of the stator (172). 47. Refrigerant compressor unit according to one of the preceding embodiments, wherein the spring-elastic bodies (202) are located between edge regions (212, 214) arranged circumferentially around the stator (172) and the support regions (222) are connected to the edge regions (212, 214) via flank regions (234, 236) extending at an acute angle to the outer surface (182) of the stator (172) and / or to the stator mounting surface (184). 48. Refrigerant compressor unit according to embodiment 47.wherein, on the one hand, the support areas (222) are located on the outside (182) of the stator (172) or the stator receiving surface (184), and on the other hand, the edge areas (212, 214) are located on the stator receiving surface (184) or the outside (182) of the stator (172). 49. Refrigerant compressor unit according to one of the preceding embodiments, wherein the support elements (192, 194) are made of a spring-elastic material, in particular spring steel. 50. Refrigerant compressor unit according to one of the preceding embodiments, wherein support elements (192, 194) arranged successively in the direction of the rotor axis (178) are positioned at a distance from one another in the motor housing section (28) by means of a spacer element (244). 51. Refrigerant compressor unit according to one of the preceding embodiments,wherein one of the support elements (192) is positioned with respect to its position in the motor housing section (28) by a step (146) adjoining the stator mounting surface (184). 52. Refrigerant compressor unit according to one of the preceding embodiments, wherein the refrigerant compressor unit is designed for CO₂ as the refrigerant.

[0088] Further features and advantages of the invention are the subject of the following description and the graphic representation of some exemplary embodiments.

[0089] The drawing shows: Fig. 1 a section along line 1-1 in Fig. 2 by a first embodiment of a refrigerant compressor unit according to the invention; Fig. 2 an enlarged view of the section according to Fig. 1 in the area of ​​the cylinder housing block 40; Fig. 3 a sectional view along line 3-3 in Fig. 1 by the first embodiment of the refrigerant compressor unit according to the invention, viewed in the direction of arrow A; Fig. 4 a partial schematic representation of a stator bearing in a motor housing section; Fig. 5 a perspective view of one of the support elements of the stator bearing; Fig. 6 a section along line 6-6 in Fig. 4 ; Fig. 7 a schematic longitudinal section along line 7-7 in Fig. 8 by the first embodiment of the refrigerant compressor unit and an inlet chamber to illustrate the refrigerant flow in the first embodiment of the refrigerant compressor unit according to the invention; Fig. 8 a sectional view along line 8-8 through the cylinder head in Fig. 7 looking in the direction of arrow B; Fig. 9 a schematic longitudinal section along line 9-9 in Fig. 8 by the first embodiment of the refrigerant compressor unit according to the invention in the area of ​​the outlet chamber; Fig. 10 a top view of the housing sleeve in the direction of arrow C in Fig. 11 ; Fig. 11 a longitudinal section along line 11-11 in Fig. 10 through the housing sleeve of a variant of the first embodiment; Fig. 12 a perspective overall view of the first embodiment of the refrigerant compressor unit according to the invention in an installation position; Fig. 13 a perspective overall view according to Fig. 12 of the first embodiment of the refrigerant compressor unit according to the invention in the installed position with the associated mounting elements; Fig. 14 a section along line 14-14 in Fig. 12 ; Fig. 15 a schematic longitudinal section along line 15-15 in Fig. 16 and similar Fig. 7 by a second embodiment of the refrigerant compressor unit according to the invention, designed as a two-stage compressor; Fig. 16 a schematic representation similar Fig. 8 by the second embodiment of the refrigerant compressor unit according to the invention and Fig. 17 a schematic longitudinal section along line 17-17 in Fig. 16 similar Fig. 9 by the second embodiment of the refrigerant compressor unit according to the invention.

[0090] A in Fig. 1 The illustrated embodiment of a refrigerant compressor unit 10 according to the invention comprises a total housing 12, which has a housing sleeve 16 extending in the direction of a central axis 14, extending from a front cover 22 closing a front mounting opening to a rear cover 24 closing a rear mounting opening.

[0091] The front cover 22 is followed by a compressor housing section 26, which is followed by a motor housing section 28 that extends to the rear cover 24.

[0092] The front cover 22 preferably rests on one end face 32 of the housing sleeve 16 and engages behind a front cylindrical surface 34 of the housing sleeve 16 which adjoins the end face 32 and extends coaxially to the central axis 14.

[0093] Furthermore, the front cover 22 forms a concavity 36 located within the cylinder surface 34, which engages in a working space arranged in the compressor housing section 26, so that a significant area of ​​the concavity 36 extends from the front face 32 into the drive chamber 38 and is partially offset from the front face 32 in the direction of the drive chamber 38.

[0094] Furthermore, a cylinder housing block 40 is arranged in the compressor housing section 26, which is arranged, for example, on one side of the central axis 14 and is integrally formed on the housing sleeve 16, and forms, for example, at least two, preferably three cylinders 42, 44, 46, which are arranged successively in the cylinder housing block 40 in a series direction 48 parallel to the central axis 14.

[0095] Preferably, the cylinder housing block 40 is made of the same material as the entire housing sleeve 16 and is integrally formed onto or formed in the housing sleeve 16, wherein the cylinder housing block 40 extends radially to the housing sleeve 16 from an outer surface 52 in the direction of the central axis 14 to an inner surface 54 over at least one guide length of the cylinders 42, 44, 46.

[0096] The cylinder housing block 40 limits the drive space 38 provided in the compressor housing section 26 with its inner side 54.

[0097] In cylinders 42, 44, 46, pistons 62, 64, 66 are movably guided, each having eccentrics 72, 74, 76 mounted on a common drive shaft 70, which each drive connecting rods 82, 84, 86 via the eccentrics 72, 74, 76, so that the eccentrics 72, 74, 76 and the connecting rods 82, 84, 86 form drive units 92, 94, 96 for the respective pistons 62, 64, 66 in order to move them in the cylinders 42, 44, 46 ( Fig. 1 and Fig. 2 ).

[0098] The guidance of the pistons 62, 64, 66 in the respective cylinders 42, 44, 46 could on the one hand be directly via guide surfaces 102, 104 and 106, formed by the cylinder housing block 40 itself.

[0099] In this case, however, a coating of the guide surfaces 102, 104, 106 is advantageous, which reduces wear of the material of the cylinder housing block 40.

[0100] Preferably, however, cylinder liners 112, 114, 116 are inserted into the cylinder housing block, which are made of a more wear-resistant material than the material of the cylinder housing block 40 and each have a collar 113, 115, 117, which each sits in a receptacle 107, 109, 111 of the cylinder block 40 adjacent to the outer surface 52 of the cylinder block 40.

[0101] Preferably, however, the cylinder housing block 40 is made of the same material as the housing sleeve 16 and in particular is integrally formed on the housing sleeve 16, wherein the housing sleeve 16 is made of aluminum, preferably of an aluminum casting alloy with silicon, for example AlSi9MgKT6, for reasons of weight saving.

[0102] Therefore, with regard to the material of the housing sleeve 16 and the cylinder housing block 40 formed on it, no consideration needs to be given to the wear resistance in the area of ​​the cylinders 42, 44, 46, since the wear resistance for the guidance of the pistons 62, 64, 66 can be ensured by the cylinder bushings 112, 114, 116 inserted into the cylinder housing block 40.

[0103] The individual cylinders, 42, 44, 46 are closed off by a valve plate 120 which rests on the outside 52 of the cylinder housing block 14 and seals against it. The valve plate also secures the cylinder liners 112, 114, 116 by pressing on their collars 113, 115, 117 in the receptacles 107, 109, 111 and, in particular, seals against the respective collars 113, 115, 117.

[0104] As in Fig. 2 and 3As shown, inlet valves 122, 124, 126 are arranged on the valve plate on the side of the cylinders 42, 44, 46, and exhaust valves 132, 134, 136 are arranged on a side facing away from the cylinders 42, 44, 46 for the respective cylinders 42, 44, 46.

[0105] The valve plate 120 is covered on a side facing away from the cylinders 42, 44, 46 by a cylinder head 140, which is sealed on the valve plate 120 and has an inlet chamber 142 opposite the inlet valves 122, 124, 126 and an outlet chamber 144 accommodating the outlet valves 132, 134, 136, wherein preferably the volume of the outlet chamber 144 is larger than that of the inlet chamber in order to obtain a larger damping volume for pulsations in the area of ​​the exiting refrigerant.

[0106] Preferably, the valve plate 120 is made of steel.

[0107] Since, particularly when CO2 is used as a refrigerant, the cylinder head 140 is exposed to high pressures, pressure pulsations and temperatures, and thus an intermediate wall 146 between the inlet chamber 142 and the outlet chamber 144 as well as outer walls 148 of the same are subjected to large mechanical and thermal loads and must in particular ensure a tight seal with the valve plate 140, the cylinder head is preferably made of a cast material comprising an iron-carbon alloy.

[0108] For example, the casting material can be cast steel.

[0109] However, it is preferred if the casting material of the cylinder head 140 is cast iron.

[0110] In this process, a cast iron containing graphite, in particular a cast iron containing spheroidal graphite or vermicular graphite, is preferred.

[0111] The drive shaft 70, which carries the eccentrics 72, 74, 76, is supported on one side in the front cover 22, in particular in a bearing receptacle 152, which is arranged on a side of the indentation 36 facing the drive chamber 38 and receives an end section of the drive shaft 70 engaging in the bearing receptacle 152.

[0112] Furthermore, the drive shaft extends through the drive chamber 38 to an intermediate wall 156 of the housing sleeve 16, which is arranged between the drive chamber 38 and a motor chamber 158 formed in the housing sleeve 16.

[0113] In the area of ​​the intermediate wall 156, the drive shaft 70 is also supported in a bearing section 162 of the drive shaft 70 which passes through the intermediate wall 156, wherein the intermediate wall 156 forms a bearing bushing 164 for supporting the bearing section 162.

[0114] The drive chamber 38 is thus limited in the direction of the central axis 14 of the housing sleeve 16 on the one hand by the front cover 22 and on the other hand by the intermediate wall 156, so that between these a drive section 166 of the drive shaft 70, which carries the eccentrics 72, 74, 76, extends into the drive chamber 38.

[0115] In the motor housing section 28 of the housing sleeve 16, an electric motor designated as a whole by 170 is arranged, which has a stator 172 that is arranged in a rotationally fixed manner in the motor compartment 158 ​​and has a rotor 174 that is arranged in a rotationally fixed manner on a rotor carrier section 176 extending into the motor compartment 158 ​​following the bearing section 162.

[0116] As in Fig. 1 As shown, an electric motor 170 is arranged in the motor compartment 158 ​​of the overall housing 12, located on a side of the partition wall 156 opposite the drive compartment 38. The motor 170 has a stator 172, which is mounted in the motor housing section 28 in a rotationally fixed manner, and a rotor 174, which is enclosed by the stator 172 and sits on a rotor carrier section 176 of the drive shaft 70, which is rotatable about a rotor axis 178, so that the rotor 174 is able to drive the drive shaft 70 via the rotor carrier section 176 and thus also the pistons 62, 64, 66 via the drive units 92, 94, 96.

[0117] A gap 173 is formed between the rotor 174 and the stator 172.

[0118] The stator 172 is preferably mounted in the motor housing section 28 as shown in Fig. 4 , 5 and 6represented by support elements 192 and 194 effective between an outer surface 182 of the stator 172 and a stator receiving surface 184 of the motor housing section 28, which are spring-elastically deformable in the radial direction to the rotor axis 178 and support the stator 172 relative to the stator receiving surface 184.

[0119] Preferably each of the support elements comprises 192, 194 as for example in Fig. 5 and 6 shown, in the radial direction to the rotor axis 178, spring-elastic deformable bodies 202, which, for example, support the stator 172 on the outside 182, and, viewed in the direction of the rotor axis 178, retaining elements 204 and 206 arranged on both sides of the spring-elastic deformable bodies 202 and connecting the elastic bodies 202 to each other, which are supported on the stator receiving surface 184 of the motor housing section 28.

[0120] However, it is also possible that the retaining elements 204 and 206 are supported on the outside 182 of the stator 172 and the elastically deformable bodies 202 are supported on the stator receiving surface 184 of the motor housing section 28.

[0121] As in Fig. 5 and 6 As exemplified in connection with the support element 192, these support elements 192, 194 can be realized by a strip material 208 in the form of an annular clip with spaced-apart ends 210, the edge regions 212 and 214 of which form the retaining elements 204 and 206, and in the central region 216 of which the elastically deformable bodies 202 are formed by structures embossed in the strip material 208, which rise between the edge regions 212 and 214 and form support regions 222, which abut the outer surface 182 of the stator 172 and extend via rising surfaces that support it at an acute angle. Fig. 5 flank areas 224 and 226 extending in the direction of rotation around the rotor axis 178 are connected to foot areas 228 which abut the stator mounting surface 184, and are also connected in the direction parallel to the rotor axis 178 via flank areas 234 and 236 extending at an acute angle to the supporting stator mounting surface 184 to the edge areas 212 and 214 which also abut the stator mounting surface 184.

[0122] By forming the support elements 192, 194 from a strip material 208 with ends 210 spaced apart from each other, they can be inserted into the stator receiving surface 184 without chips.

[0123] In particular, the flank areas 234 and 236 form insertion ramps that allow for chip-free assembly or disassembly of the stator 172.

[0124] Preferably, the support elements 192, 194 allow the mounting of the "hard" stator 172 in the "soft" motor housing section 28 if the latter is made of light metal, in particular aluminum, without causing damage to the motor housing section 28. The same applies when replacing the electric motor 102.

[0125] Furthermore, in this case too, the design of the housing sleeve 16 with a cross-sectional shape that is as circular and cylindrical as possible is advantageous, since in this case too the forces required to accommodate the electric motor 170 and the pressure forces in the motor housing section 28 can be optimally absorbed, in particular without any significant radial widening of the motor housing section 28, so that precise support of the electric motor 102 by the support elements 192 and 194 is possible.

[0126] Due to the gently sloping surface supporting it, in Fig. 6 The spring-elastic deformation of the deformable bodies 202 occurs primarily in the flank regions 224, 226 and 234 and 236, as shown in the figure above the stator mounting surface 184 and the flank regions 224 and 226 as well as 234 and 236. Fig. 5 The flank areas 224 and 226 are shown with dashed lines.

[0127] Preferably, the spring-elastic bodies 202 are designed such that they accommodate all variations of the radial distance RA ( Fig. 6 ) between the outer surface 182 of the stator 172 and the stator receiving surface 184 by elastic deformation, without plastic deformations occurring in the area of ​​the elastic bodies 202, in particular the flank areas 224, 226 and 234 and 236.

[0128] This makes it possible to keep the stator 172 coaxial with the rotor axis 178 at all times, regardless of the thermal and / or pressure-related radial expansion of the motor housing section 28 and the thermally induced radial expansion of the stator 172.

[0129] Such pressure-induced radial expansions of the engine housing section 22 occur in particular because the engine compartment 158 ​​is under pressure and the housing sleeve 16 of the overall housing 12 is made of light metal.

[0130] In addition to the pressure load on the motor housing section 28, there is also a thermal expansion depending on the operating state of the stator 172 and the motor housing section 28.

[0131] Since all such deformations, which result in a change in the radial distance RA, are absorbed by the spring-elastic bodies 202 in the form of purely elastic deformations, an optimally small gap 173 between the rotor 174 and the stator 172 can be maintained regardless of the operating state of the refrigerant compressor.

[0132] Because all elastic elements 202 are arranged, for example, in a strip material 208 and are held in their positions relative to each other by the retaining elements 204 and 206, the retaining elements 204 and 206 can lie almost completely around the stator 172 in planes perpendicular to the rotor axis 178 and thereby hold the elastic elements 202 in defined positions relative to the outside 182 of the stator 172 and to the stator receiving surface 184.

[0133] For the exact positioning of the support elements 192 and 194 in the motor housing section 28, a step 242 is preferably provided following the rotor mounting surface 184 on a side facing the drive chamber 22, which runs around the rotor axis 178 and serves to position one of the support elements 192 facing the drive chamber 38.

[0134] In order to position the second support element 194 exactly relative to the first support element 192, it would in principle be conceivable to also provide a step in the motor housing section 28, but this would mean a further weakening of the wall thickness of the motor housing section 22.

[0135] For this reason, the space between load-bearing elements 192 and 194 is as shown in Fig. 4 As shown, a spacer element 244 is provided, which, for example, rests against the retaining elements 206 and 204 of the support element 194 and 192 respectively, thus specifying the exact position of the second support element 194 relative to the first support element 192.

[0136] The spacer element 244 is designed, for example, to rest against the stator mounting surface 184 of the motor housing section 22 and to partially or completely enclose the rotor axis 178 in order to keep the support elements 192 and 194 positioned relatively precisely over their entire course around the rotor axis 178.

[0137] For example, the support elements 192, 194 and / or the spacer element 244 are formed by ring-shaped sheet metal elements, in particular made of strip material 208, with ends 210 spaced apart from each other, which tend to widen in the radial direction, so that these sheet metal elements automatically attach to the stator receiving surface 184 and are fixed by friction.

[0138] This allows the support elements 192, 194 and, if applicable, the spacer element 244 to be inserted into the stator mounting surface 184 without producing chips.

[0139] For the electrical supply of the electric motor 170, a contact insert 252 is preferably provided in the rear cover 24, which receives electrical contact elements 254 that are passed through the rear cover 24 ( Fig. 1 ).

[0140] On a side facing away from the motor compartment 158, a contact plug 256 can be attached to the contact insert 252, via which all contact elements 254 included in the contact insert 252 are connected to a power source or converter 268.

[0141] Furthermore, the rear cover contains 24 ( Fig. 1 A second contact insert 262 is provided, which has additional electrical contact elements 264. Preferably, these additional contact elements 264 serve to establish electrical connections with sensors arranged in the overall housing 12, for example pressure sensors 272, and / or temperature sensors 274 and / or speed sensors 276, which serve to monitor the compressor function and the motor function, so that preferably an electrical supply line to all sensors serving the compressor function and / or the motor function and arranged in the overall housing 12 is provided via the contact insert 262 and a contact plug 266.

[0142] However, it is also possible to provide all electrical contact elements 254 and 264 in a correspondingly complex contact insert and a correspondingly designed contact plug.

[0143] Furthermore, the rear cover contains 24 ( Fig. 1 ) also the refrigerant connection 278 is provided, through which refrigerant under low pressure can be supplied directly to the engine compartment 158, on a side opposite the drive compartment 38, which flows through the electric motor 170, cools it and then enters the inlet chamber 142.

[0144] The rear cover 24 also rests against an end face 282 formed by the housing sleeve 16 and engages in a cylindrical inner surface 284 of the housing sleeve 16.

[0145] For optimal space utilization, the rear cover 24 is provided with a bulge 286 extending outwards from the front face 282 and is thus able to accommodate parts of winding heads 288 of the stator 172 and thus enable a compact design of the housing 12.

[0146] The routing of the refrigerant in the embodiment of the refrigerant compressor according to the invention described above can be particularly advantageously illustrated by the schematic representations of the refrigerant compressor as shown. Fig. 1 in the Fig. 7 bis 9 describe.

[0147] As in Fig. 7 As shown, the refrigerant to be compressed enters the motor compartment 158 ​​through the refrigerant connection 278 and flows on the one hand through the gap 173 between the stator 172 and the rotor 174 and on the other hand along the outside 182 of the stator 172 and the stator receiving surface 184 of the motor housing section 28 along the outside of the stator 172 in the direction of the partition 156 between the drive compartment 38 and the motor compartment 158 ​​and then via a channel 292 provided in the partition 156 in the direction of the valve plate, passes through an access opening 294 in the valve plate 120 and then enters the inlet chamber 142 of the cylinder head 140.

[0148] In addition, the refrigerant flows from channel 292 via channel 296 into drive chamber 38 to keep it at low pressure.

[0149] This inlet chamber of the cylinder head 140 is associated with a pressure relief valve 300 provided on the cylinder head 140, which is able to relieve an overpressure occurring in the inlet chamber 142.

[0150] The refrigerant is then drawn in from the inlet chamber 142 by the pistons 62, 64, 66 moving in the cylinders 42, 44, 46 and compressed, so that the refrigerant then enters the outlet chamber 144 through the outlet valves 132, 134 and 136.

[0151] The outlet chamber 144 is also assigned a pressure relief valve 302 in order to relieve any overpressure that may occur in the outlet chamber 144.

[0152] The refrigerant, which then collects in the outlet chamber 144 and is compressed to high pressure, then exits the cylinder head 140 via a high-pressure connection 304 and is discharged from it.

[0153] In one variant of the first embodiment, illustrated in the Fig. 10 and 11 In the cylinder housing block 40V, recesses 312, 314, 316 and 318 are arranged on opposite sides of the cylinders 42, 44, 46 which are arranged consecutively in the series direction 48.

[0154] Furthermore, a recess 322 extending transversely to the row direction 48 is arranged, particularly on a side facing the motor housing section 28.

[0155] Preferably, all recesses 312, 314, 316 and 318 extend from the outer surface 52 into the cylinder housing block 40V and run without contact to the cylinders 42, 44, 46 up to a base that closes off the recesses 312, 314, 316, 318, 322 in the area near the inner surface 54 of the cylinder housing block 40V.

[0156] The recesses 312, 314, 316, 318, 322 allow for a reduction in weight and also improve, in particular, the behavior during thermal expansion.

[0157] The recesses 312, 314, 316, 318 and 322 are covered by the valve plate and, with the exception of recess 312, are closed by it.

[0158] The recess 312 is arranged such that the channel 292 opens into it and the channel 296 runs from it into the working chamber 38, while the valve plate 120 has the access opening 294, so that the recess 312 is supplied with refrigerant at low pressure.

[0159] Furthermore, the respective collars 113, 115, 117 of the cylinder liners 112, 114 and 116 are preferably designed such that their areas extending transversely to the row direction 48 have a larger extent than their areas running parallel to the row direction 48.

[0160] Regarding the further features of the variant of the first embodiment, full reference is made to the preceding description of the first embodiment.

[0161] As in the Fig. 12 bis 14 The first embodiment of the refrigerant compressor unit 10 according to the invention, in particular according to the variant thereof, is shown in the housing sleeve 16, which is provided near the front cover 22 and the rear cover 24 with mounting projections 332, 334, 336, which enable the refrigerant compressor unit 10 to be mounted on a wide variety of mounting surfaces.

[0162] Thus, the mounting units 332 and 334 allow the fixing of retaining rails 342 and 344 for mounting on a substantially horizontal mounting surface 346, whereby a substantially horizontal orientation is understood to mean a orientation of the mounting surface 346 of plus / minus 20° relative to the horizontal.

[0163] Preferably, the compressor unit according to the invention is installed in such a mounting position that the cylinder head 140 together with the cylinder housing block 40 extends transversely to the housing sleeve 16 in a vertical direction 348, preferably approximately parallel to the mounting surface 346, so that an advantageous mounting position of the refrigerant compressor unit 10 is achieved, in which the maximum height of the refrigerant compressor unit 10 above the mounting surface 346 is defined by the maximum height of the housing sleeve 16 above the mounting surface 346.

[0164] Preferably, in this installation position, the cylinders 42, 44, 46 run transversely to the vertical direction 348 and the pistons 62, 64, 66 also move transversely to the vertical direction 348, for example in a direction of movement which forms an angle between 70° and 110° with the vertical direction 348.

[0165] Alternatively, instead of using the mounting attachments 332 and 334, it is also possible to use the mounting attachments 334 and 336 for mounting on a mounting surface running approximately parallel to the vertical direction, whereby the height of the refrigerant compressor unit in the vertical direction 348 is also defined by the maximum diameter of the housing sleeve 16.

[0166] When installed in this position, the lubricant bath 352 is located in the drive chamber 38 such that in the vertical direction 348 it lies below the pistons 62, 64, 66, in the illustrated case the piston 66, and also below the position of the cylinders 42, 44, 46, so that the lubricant bath 352 does not impair the compressor operation ( Fig. 14 ).

[0167] This is made possible in particular by the fact that all cylinders 42, 44, 46 are arranged consecutively in the row direction 48.

[0168] Furthermore, a lubricant delivery unit 354 is arranged such that a lubricant extraction element 356, for example also comprising a check valve, opens into the engine compartment 158 ​​at a point on the bottom side, for example in a vertical direction 348, in order to take in lubricant from the engine compartment 158 ​​at this point and supply it to an ejector 358, arranged in the drive compartment 38 and supplied by lubricant from the area of ​​the bearing bushing 164 for the drive shaft 70, which feeds the lubricant into an outlet line 358 in the engine compartment 38, the outlet 362 of which is preferably located in a vertical direction 348 above the lubricant bath 352.

[0169] Such a lubricant delivery unit is described, for example, in DE 22 50 947 A, to which reference is made with regard to further details.

[0170] In a second embodiment, shown in the Fig. 15 bis 17 The refrigerant compressor unit is basically identical in construction to the first embodiment; however, cylinders 42' and 44' serve only to compress the low-pressure refrigerant provided at low pressure via a low-pressure port 306' in the cylinder head 140, so that the refrigerant entering the inlet chamber 142'a is compressed by the pistons 62' and 64' in the cylinders 42' and 44' to a medium pressure, at which point the refrigerant enters the outlet chamber 144'a, leaves the outlet chamber 144'a via a medium-pressure port 308' and, if necessary after cooling, is supplied to the motor compartment 158 ​​via the refrigerant port 278, flows around the electric motor 170 on the one hand between rotor 174 and stator 172 and on the other hand on the outside of the stator 172 and enters a channel 292 in the partition wall 156.which on the one hand leads to the valve plate 20 and the passage 294 in the valve plate 20 and thus into an inlet chamber 142'b for intermediate pressure.

[0171] From this inlet chamber 142'b, the refrigerant is drawn in by the piston 66' in the cylinder 46', which draws the refrigerant supplied at medium pressure from the medium pressure inlet chamber 142'b, compresses it to high pressure and supplies it to the outlet chamber 144'b, from which it then exits via the high pressure port 304'.

[0172] Preferably, the channel 292 is also opened through the channel 298 towards the drive chamber 38, so that the drive chamber 38 can advantageously be kept at medium pressure and thus the pressure differences acting on the pistons 62' and 64' and 66' can be kept lower.

[0173] In a variant of the second embodiment, the cylinder housing block 40' is also provided with the recesses 312, 314, 316, 318, 322, so that in this respect reference can be made to the description of the variant of the first embodiment with the Fig. 10 and 11 Reference is made to this.

[0174] Furthermore, in the second embodiment in particular, mounting attachments corresponding to mounting attachments 332, 334, 336 are also provided, in the same manner as in the Fig. 12 bis 14 shown, so that retaining rails 342 and 344 can also be used for mounting on a substantially horizontal mounting surface 346 as in the first embodiment.

[0175] Such an assembly is feasible due to the cylinders 42', 44', 46' being arranged successively in the 48' direction, whereby the lubricant bath 352 is then, as in Fig. 14 shown, also in the vertical direction 348 below the directions of movement of the pistons 62', 64' and 66' and the cylinders 42', 44' and 46', and a surface 353 of the lubricant bath 352 is arranged at a distance from these, as shown in Fig. 14 illustrated in connection with the first embodiment.

[0176] Furthermore, as in the first embodiment, a lubricant delivery unit 354 is also provided, with reference also made to the descriptions of the first embodiment in connection with Fig. 14 Reference is made to this.

Claims

1. Refrigerant compressor unit (10), comprising a housing (12) with a housing sleeve (16) closed at the end, wherein the housing sleeve (16) comprises a compressor housing section (26) in which at least two cylinders (42, 44, 46) each having a piston (62, 64, 66) arranged therein and a drive chamber (38) with drive units (92, 94, 96) arranged therein and driven by a drive shaft (70) are arranged, wherein the housing sleeve (16) comprises a motor chamber (158) with an electric motor (170) arranged therein, driving the drive shaft (70), wherein a valve plate (120) covering the cylinders (42, 44, 46) is arranged on the housing sleeve (16), which valve plate carries a cylinder head (140) on its side opposite the cylinders (42, 44, 46), in which at least one inlet chamber (142) and at least one outlet chamber (144) are arranged, characterized in thatthe cylinder head (140) is made of a cast material comprising iron and that the housing sleeve (16), with the compressor housing section (26) and a cylinder housing block (40) receiving the cylinders (42, 44, 46) as well as the motor housing section (28) form a one-piece part, in particular made of lightweight material.

2. Refrigerant compressor unit according to claim 1, characterized in that the cylinder head (140) is made of a cast material comprising an iron-carbon alloy and / or that in particular the cylinder head (140) is made of cast steel, and / or that in particular the cylinder head (140) is made of cast iron, and / or that in particular the cylinder head (140) is made of cast iron with graphite, in particular that the cylinder head (140) is made of cast iron with spheroidal graphite or vermicular graphite.

3. Refrigerant compressor unit according to one of the preceding claims, characterized in thatthe housing sleeve (16) with the compressor housing section (26), the cylinder housing block (40) and the motor housing section (28) is made of light metal, in particular of aluminum.

4. Refrigerant compressor unit according to one of the preceding claims, characterized in that the housing sleeve (16) with the compressor housing section (26), the cylinder housing block (40) and the motor housing section (28) is made of a cast aluminum alloy with silicon.

5. Refrigerant compressor unit according to one of the preceding claims, characterized in that the housing sleeve (16) with the compressor housing section (26), the cylinder housing block (40) and the motor housing section (28) is produced as a cast part, in particular from light metal casting.

6. Refrigerant compressor unit according to one of the preceding claims, characterized in thatin the cylinder housing block (40) the cylinders (42, 44, 45) are arranged one after the other in a row direction (48), which runs in particular parallel to the drive shaft (70).

7. Refrigerant compressor unit according to one of the preceding claims, characterized in that the cylinder housing block (40) has, in addition to the cylinders (42, 44, 45), separate recesses (312, 314, 316, 318, 322).

8. Refrigerant compressor unit according to one of the preceding claims, characterized in thatthe housing sleeve (16) has assembly openings (21, 23) at the end which are closed with housing covers (22, 24), in particular that the housing covers (22, 24) are made of light metal, in particular of aluminum, and / or that in particular the housing covers (22, 24) are curved, and / or that in particular one of the housing covers (22) has a curvature (36) extending into the housing sleeve (16), and / or that in particular one of the housing covers (24) has a curvature (286) curving away from the housing sleeve (16).

9. Refrigerant compressor unit according to claim 8, characterized in that one of the housing covers (24) is provided with at least one contact insert (252) for carrying out electrical connections (264).

10. Refrigerant compressor unit according to one of the preceding claims, characterized in that one of the housing covers (24) is provided with a refrigerant connection (278).

11. Refrigerant compressor unit according to one of the preceding claims, characterized in that the housing sleeve (16) is provided with an intermediate wall (156) which is formed integrally thereon and separates the drive chamber (38) from the motor chamber (158), and in particular a bearing section (164) for the drive shaft (17) passing through the intermediate wall (156) is provided in the intermediate wall (156).

12. Refrigerant compressor unit according to one of the preceding claims, characterized in that the cylinder head (140) has a high-pressure connection (304,304') for refrigerant.

13. Refrigerant compressor unit according to one of the preceding claims, characterized in that the cylinder head (140) has a connection (306') for low-pressure refrigerant.

14. Refrigerant compressor unit according to one of the preceding claims, characterized in thatthe engine compartment (158) is flowed through by sucked-in refrigerant, in particular that the refrigerant flowing through the engine compartment (158) is supplied through a channel (292) to a passage opening (294) in the valve plate (120), and / or that in particular the refrigerant enters an inlet chamber (142) of the cylinder head (140) after cooling the electric motor (170) and / or that in particular the channel (292) is formed in the intermediate wall (156) and / or that in particular the channel (292) is connected to a channel (296) leading to the drive chamber (28).

15. Refrigerant compressor unit according to one of the preceding claims, characterized in thatthe cylinder housing block (40) has at least one cylinder (42', 44') for compressing refrigerant from low pressure to medium pressure and at least one cylinder (46') for compressing refrigerant from medium pressure to high pressure, in particular that the cylinder head (140) has an inlet chamber (142'a) for refrigerant at low pressure, an outlet chamber (144'a) for refrigerant at medium pressure, an inlet chamber (142'b) for refrigerant at medium pressure and an outlet chamber (144'b) for refrigerant at high pressure.

16. Refrigerant compressor unit according to one of the preceding claims, characterized in that the cylinder head (140) is provided with a pressure relief valve (302) connected to the outlet chamber (144) for high-pressure compressed refrigerant.

17. Refrigerant compressor unit according to one of the preceding claims, characterized in that the cylinder head (140) is provided with a pressure relief valve (300) connected to the inlet chamber (142).

18. Refrigerant compressor unit according to one of the preceding claims, characterized in thatthe cylinder housing block (40, 40') is arranged on the housing sleeve (16) in such a way that the cylinders (42, 44, 46, 42', 44', 46') extend transversely to a vertical direction (348) and / or that in particular the housing (12) is arranged in an operating position such that the cylinder housing block (40, 40'), the valve plate (120) and the cylinder head (140) are arranged on one side of the housing sleeve (16) relative to the housing sleeve (16) in a direction transverse to a vertical direction (348) and / or that in particular a lubricant bath (352) forming in the drive chamber (38) of the compressor housing section (26) is arranged in the vertical direction (348) below the cylinders (42, 44, 46) and at a distance therefrom and / or that in particular a lubricant feed unit is arranged in the compressor housing section (26) (354) is provided, which receives lubricant from the engine compartment (158) and supplies it to the lubricant bath (352) in the compressor housing section (26).

19. Refrigerant compressor unit according to one of the preceding claims, characterized in that the housing (12) is provided with at least two mounting lugs (332, 334, 336) which allow mounting of the housing (12) in such a way that the cylinder housing block (40), the valve plate (120) and the cylinder head (140) are arranged on one side of the housing sleeve relative to the housing sleeve (16) in a direction transverse to a vertical direction (348), in particular that the mounting lugs (332, 334, 336) are arranged on the housing sleeve (16).

20. Refrigerant compressor unit (10) according to one of the preceding claims, characterized in thatthe stator (172) is mounted in the motor housing section (28) by means of support elements (192, 194) inserted into the motor compartment (158), which on the one hand bear against a stator receiving surface (184) of the motor housing section (28) and on the other hand enclose the stator (172) inserted into the support elements (192, 194) on its outer side (182) and resiliently support it relative to the stator receiving surface (184), in particular that the support elements (192, 194) have resilient bodies (202) which are dimensioned such that they are in an elastically deformed state in all operating states of the motor housing section (28) occurring during operation of the refrigerant compressor (10) and / or that in particular the support elements (192, 194) are arranged extending around the stator (172) and support the stator (172) on opposite sides the rotor axis (178) is supported several times relative to the stator receiving surface (184) of the motor housing section (28),and / or that in particular the support elements (192, 194) have elastic bodies (202) arranged at defined angular intervals around the rotor axis (178).

21. Refrigerant compressor unit according to one of the preceding claims, characterized in thatthe elastic bodies (202) are positioned relative to one another by a strip material (208) which positions them relative to one another and encircles the stator (172), in particular that the elastic bodies (202) are formed into the strip material (208) and / or that in particular the strip material (208) is designed as a ring-like clasp with open ends (210), and / or that in particular the support elements (192, 194) are formed from a resilient material, in particular spring steel, and / or that in particular the resilient bodies (202) have flank regions extending at an acute angle to the outer side (182) of the stator (172) and / or to the stator receiving surface (184) between foot regions (228) and support regions (222), some of which bear against the outer side (182) of the stator (172) and the others against the stator receiving surface (184). (224, 226, 234,236) and / or that in particular the resilient bodies (202) are successively formed into a resilient band material (208) so that successive support regions (222) abut an outer side (182) of the stator (172) or the stator receiving surface (184) and successive foot regions (228) abut the stator receiving surface (184) or the outer side (182) of the stator (172) and / or that in particular the resilient bodies (202) are located between edge regions (212, 214) arranged circumferentially around the stator (172) and the support regions (222) are connected to the edge regions (212, 214) are connected, in particular, on the one hand, the support areas (222) on the outside (182) of the stator (172) or the stator receiving surface (184) and, on the other hand, the edge areas (212,214) against the stator receiving surface (184) or the outer side (182) of the stator (172).

22. Refrigerant compressor unit according to claim 20 or 21, characterized in that support elements (192, 194) arranged one after the other in the direction of the rotor axis (178) are positioned at a distance from one another in the motor housing section (28) by a spacer element (244), in particular one of the support elements (192) being positioned with regard to its position in the motor housing section (28) by a step (146) adjoining the stator receiving surface (184).

23. Refrigerant compressor unit according to one of the preceding claims, characterized in that the refrigerant compressor unit is designed for CO2 as a refrigerant.

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