radial compressor

Abstract

Radial compressor (10) with: a slow-moving wave (11); a ring element (62) which rotates when the slow-running shaft (11) rotates, wherein the ring element (62) has an annular section (64); a fast-moving wave (12) located within the annular section (64); a roller (71) arranged between the annular section (64) and the fast-running shaft (12) to contact the annular section (64) and the fast-running shaft (12); a wheel (52) which rotates integrally with the fast-running shaft (12); an electric motor (13) that rotates the slowly running shaft (11); a tubular housing (20) which a speed-increasing chamber (S2) that accommodates the ring element (62), the roller (71) and part of the high-speed shaft (12) and stores oil, a motor chamber (S1) that accommodates the electric motor (13), and a partition wall (24) aligned in the radial direction of the tubular housing (20), which axially separates the speed increaser chamber (S2) and the motor chamber (S1), characterized by a partition wall (90) having a disk-shaped intermediate body (91) oriented radially in the direction of the tubular housing (20), which is arranged axially in the speed-increasing chamber (S2) between the ring element (62) and the partition wall (24), and a plate-shaped projection (92) that projects in a thickness direction of the intermediate body (91); and an inlet channel (98) which directs oil in a stirring area (96) to a bearing area (97), wherein the stirring area (96) in the speed increaser chamber (S2) includes an area between the intermediate body (91) and the projection (92) of the partition wall (90) and the ring element (62), and the bearing area (97) in the speed increaser chamber (S2) includes an area between the intermediate body (91) of the partition wall (90) and the partition wall (24) and an area between the projection (92) of the partition wall (90) and a speed increaser housing (23).

Description

Technical field

[0001] The present disclosure relates to a radial compressor equipped with a speed increaser. State of the art

[0002] A radial compressor equipped with a speed booster is disclosed in JP 2016-186238 A. The speed booster comprises an annular element, a high-speed shaft, rollers, and a speed booster chamber. The annular element rotates when a low-speed shaft rotates. The high-speed shaft is located inside the annular element. The rollers are positioned between the annular element and the high-speed shaft and contact both. The speed booster chamber houses the annular element, the high-speed shaft, and the rollers.

[0003] In the speed increaser, oil must be supplied to the contact sections between the rollers and the ring element, and between the rollers and the high-speed shaft, to limit wear and seizing at these contact points. The compressor described above includes a bearing chamber, separate from the speed increaser chamber, which stores oil. The compressor uses a pump to supply oil to the bearing chamber of the speed increaser chamber. The oil supplied to the speed increaser chamber is stirred by the rotation of the ring element.

[0004] Since the compressor described above has its bearing chamber on the outer circumferential surface of the housing, the compressor is relatively large. To limit the increase in compressor size, the speed increaser chamber can be used as the bearing chamber. However, in this case, the ring element is immersed in the oil stored in the speed increaser chamber. This increases the stirring resistance during rotation of the ring element and thus reduces the efficiency of the speed increaser. Furthermore, DE 10 2018 104 247 A1 discloses a centrifugal compressor with an electric motor coupled to a low-speed shaft, an impeller, and a speed transmission device or speed increaser. Summary

[0005] Therefore, one objective of the present disclosure is to provide a radial compressor that reduces the stirring resistance during the rotation of the ring element.

[0006] This summary is intended to introduce, in a simplified form, a selection of concepts that are further described in detail below. This summary is not intended to identify key features or essential characteristics of the claimed subject matter, nor is it intended to serve as an aid in determining the scope of protection of the claimed subject matter.

[0007] In a general design, a radial compressor is provided, comprising a slow-running shaft, an annular element, a fast-running shaft, a roller, an impeller, an electric motor, a tubular housing, a partition, and an inlet channel. The annular element rotates when the slow-running shaft rotates. The annular element has an annular section. The fast-running shaft is located within this annular section. The roller is positioned between the annular section and the fast-running shaft to make contact between them. The impeller rotates integrally with the fast-running shaft. The electric motor rotates the slow-running shaft. The tubular housing includes a speed-boosting chamber, a motor chamber, and a partition. The speed-boosting chamber contains the annular element, the roller, and a portion of the fast-running shaft, and holds oil.The motor chamber houses the electric motor. The partition separates the speed-increasing chamber and the motor chamber. The partition is located in the speed-increasing chamber between the ring element and the partition. The inlet channel directs oil through a stirring zone to a bearing zone. The stirring zone comprises an area in the speed-increasing chamber between the partition and the ring element. The bearing zone comprises an area in the speed-increasing chamber between the partition and the partition.

[0008] Other features and aspects will become clear from the following detailed description, drawings, and claims. Brief description of the characters Fig. Figure 1 is a cross-sectional view showing a radial compressor according to an exemplary embodiment. Fig. Figure 2 is an enlarged cross-sectional view showing the speed increaser. Fig. Figure 3 is a cross-sectional view along line 3-3 in Fig. 1. Fig. Figure 4 is a perspective exploded view of part of the speed increaser housing and the partition.

[0009] Throughout the drawings and detailed descriptions, the same reference symbols denote the same elements. The drawings may not be to scale, and the relative size, proportions, and representation of elements in the drawings may be exaggerated for clarity, illustration, and convenience. Detailed description

[0010] This description assumes a comprehensive understanding of the described methods, devices, and / or systems. Modifications and equivalents of the described methods, devices, and / or systems are self-evident to a person skilled in the art. Sequences of operations are exemplary and can be modified, as is self-evident to a person skilled in the art, with the exception of operations that necessarily occur in a certain order. Descriptions of functions and constructions that are well known to a person skilled in the art may be omitted.

[0011] Exemplary embodiments can take various forms and are not limited to the examples described. However, the examples described are complete and convey to a person skilled in the art the entire scope of protection of the disclosure.

[0012] In the following, a radial compressor 10 according to an exemplary embodiment is described with reference to the Fig. 1, Fig. 2, Fig. 3 to Fig. 4 described. The radial compressor 10 of the present embodiment includes a speed increaser 60. The radial compressor 10 is mounted on a fuel cell vehicle (FCV) which uses a fuel cell as its power source. The radial compressor 10 supplies air, which is a fluid, to the fuel cell.

[0013] As in Fig. As shown in Figure 1, the radial compressor 10 comprises a slow-running shaft 11, a fast-running shaft 12, an electric motor 13 that rotates the slow-running shaft 11, a speed increaser 60 that increases the speed of the slow-running shaft 11 and transmits the rotation to the fast-running shaft 12, and an impeller 52 that compresses air as the fast-running shaft 12 rotates. The slow-running shaft 11 and the fast-running shaft 12 are made of metal. For example, the shafts 11 and 12 are made of iron or an iron alloy.

[0014] The radial compressor 10 comprises a housing 20, which accommodates the slow-running shaft 11, the fast-running shaft 12, the electric motor 13, and a speed increaser mechanism 61, which forms part of the speed increaser 60. The housing 20 is tubular. The housing 20 forms the outer shell of the radial compressor 10.

[0015] The housing 20 comprises a motor housing 21, a speed booster housing 23, and a compressor housing 50. The motor housing 21 accommodates the electric motor 13. The speed booster housing 23 accommodates the speed booster mechanism 61. The compressor housing 50 has an intake opening 50a through which air is drawn in. The housing 20 has, as end faces in the axial direction of the housing 20, a first end face 20a and a second end face 20b, which is located on the opposite side of the first end face 20a. The intake opening 50a is provided at the first end face 20a of the housing 20. The compressor housing 50, the speed booster housing 23, and the motor housing 21 are arranged in this order in the axial direction of the housing 20, looking from the intake opening 50a. In the present embodiment, the speed increaser mechanism 61 and the speed increaser housing 23 form the speed increaser 60.

[0016] The motor housing 21 is tubular and has a base 22. The outer surface of the base 22 of the motor housing 21 forms the second end surface 20b of the housing 20. The speed increaser housing 23 comprises a main body 25, which is tubular and has a base 24, and a termination section 26. The termination section 26 is located on the side opposite the base 24 in the axial direction of the main body 25. The termination section 26 is tubular and has a base 26a.

[0017] The motor housing 21 and the speed increaser housing 23 are coupled together, with the open end of the motor housing 21 abutting the base 24 of the main body 25. The inner surface of the motor housing 21 and a base surface 24a of the base 24, which faces the motor housing 21, define a motor chamber S1, which accommodates the electric motor 13. The slow-running shaft 11 is accommodated in the motor chamber S1, with its axis of rotation coinciding with the axial direction of the housing 20.

[0018] The slow-running shaft 11 is rotatably supported by the housing 20. The radial compressor 10 includes a first bearing 31. The first bearing 31 is located in the base 22 of the motor housing 21. The slow-running shaft 11 includes a first end section 11a and a second end section 11b on the side opposite the first end section 11a. The first end section 11a of the slow-running shaft 11 is rotatably supported by the first bearing 31.

[0019] The base 24 of the main body 25 has a shaft entry hole 27 through which the second end section 11b of the slow-running shaft 11 is inserted. A portion of the slow-running shaft 11 projects through the shaft entry hole 27 into the speed-increasing chamber 23. The shaft entry hole 27 is slightly larger than the second end section 11b of the slow-running shaft 11. A second bearing 32 and a first sealing element 33 are arranged in the shaft entry hole 27. The second bearing 32 rotatably supports the second end section 11b of the slow-running shaft 11. The first sealing element 33 seals the gap between the shaft entry hole 27 and the second end section 11b of the slow-running shaft 11. The first sealing element 33 is located closer to the motor chamber S1 than the second bearing 32. The first sealing element 33 prevents oil from flowing into the motor chamber S1 from the speed increaser chamber 23.

[0020] The electric motor 13 comprises a rotor 41, which is attached to the slow-running shaft 11, and a stator 42. The stator 42 is located outside the rotor 41 and is attached to the inner circumferential surface of the motor housing 21. The stator 42 has a cylindrical core 43 and a coil 44 wound around the core 43. Current flowing through the coil 44 causes the rotor 41 and the slow-running shaft 11 to rotate integrally.

[0021] The speed increaser housing 23 is assembled such that the open end of the main body 25 and the open end of the end section 26 abut each other. In this state, the inner surface of the end section 26 and the inner surface of the main body 25 define a speed increaser chamber S2, which accommodates the speed increaser mechanism 61 and holds oil. Thus, the base 24 of the main body 25 acts as a partition separating the speed increaser chamber S2 from the motor chamber S1.

[0022] The base 26a of the end section 26 has an end section through-hole 28. The high-speed shaft 12, which forms part of the speed increaser mechanism 61, is guided through the end section through-hole 28. A portion of the high-speed shaft 12 projects through the end section through-hole 28 into the compressor housing 50. A second sealing element 34 is provided in the end section through-hole 28. The second sealing element 34 prevents oil from flowing from the speed increaser housing 23 into the compressor housing 50.

[0023] The compressor housing 50 is tubular. The compressor housing 50 has a compressor through-hole 51, which extends axially through the compressor housing 50. The compressor housing 50 has two end faces in the axial direction: a first end face 50b and a second end face 50c, which is located on the side opposite the first end face 50b. The first end face 50b of the compressor housing 50 forms the first end face 20a of the housing 20. The opening of the compressor through-hole 51, which is located near the first end face 50b of the compressor housing 50, serves as the intake opening 50a.

[0024] The compressor housing 50 and the end section 26 are assembled such that the second end face 50c of the compressor housing 50 abuts an end face 26c of the end section 26 opposite the open end. In this configuration, the inner surface of the compressor through-hole 51 and the end face 26c of the end section 26 define an impeller chamber S3 that accommodates the impeller 52. The intake port 50a is connected to the impeller chamber S3. The compressor through-hole 51 has a constant diameter in the axial direction from the intake port 50a to a central position. The compressor through-hole 51 is in the shape of a truncated cone, the diameter of which increases stepwise in the axial direction from the central position towards the end section 26. Thus, the impeller chamber S3, which is defined by the inner surface of the compressor through-hole 51, generally has the shape of a truncated cone.

[0025] The impeller 52 is cylindrical and has a diameter that gradually decreases from a proximal end surface 52a to a distal end surface 52b.

[0026] The impeller 52 has an inlet hole 52c, which extends in the direction of the impeller's axis of rotation. The high-speed shaft 12 is guided through the inlet hole 52. The impeller 52 is attached to the high-speed shaft 12 such that the portion of the high-speed shaft 12 projecting into the compressor through-hole 51 is inserted into the inlet hole 52. The impeller 52 thus rotates integrally with the high-speed shaft 12. When the high-speed shaft 12 rotates, the impeller 52 also rotates, compressing the air drawn in through the intake opening 50a.

[0027] The radial compressor 10 also includes a diffuser flow path 53, into which the air compressed by the impeller 52 flows, and a discharge chamber 54, into which the air that has flowed through the diffuser flow path 53 flows. The diffuser flow path 53 is continuous with the open end of the compressor housing 50, which faces the end section 26. The diffuser flow path 53 is a path defined by the end surface 26c of the end section 26 and the surface of the end section 26 opposite the end surface 26c. The diffuser flow path 53 is arranged in the radial direction of the high-speed shaft 12 outside the impeller chamber S3 and has an annular shape to surround the impeller 52 (the impeller chamber S3). The discharge chamber 54 is arranged in the radial direction of the fast-running shaft 12 outside the diffuser flow path 53 and has a ring shape.The impeller chamber S3 is connected to the discharge chamber 54 via the diffuser flow path 53. The air compressed by the impeller 52 flows through the diffuser flow path 53 to be further compressed before being discharged through the discharge chamber 54.

[0028] The speed increaser 60 will now be described. The speed increaser 60 of the present embodiment is of the type of traction drive (a friction roller type).

[0029] As in Fig. As shown in Figure 2, the speed increaser mechanism 61 of the speed increaser 60 includes a ring element 62, which is coupled to the second end section 11b of the slow-running shaft 11. The ring element 62 includes a disk-shaped base plate 63, which is coupled to the second end section 11b of the slow-running shaft 11, and an annular section 64. The annular section 64 extends from the base plate 63 in a direction away from the slow-running shaft 11. The inner diameter of the annular section 64 is larger than the diameter of the second end section 11b of the slow-running shaft 11.

[0030] The annular section 64 has two insertion holes 64h. The insertion holes 64h are located on opposite sides of the annular section 64 in the radial direction. The insertion holes 64h are through holes that extend in the thickness direction through the annular section 64 at an end section near the base plate 63. The insertion holes 64h are separated by 180° in the circumferential direction of the annular section 64. The base plate 63 has two insertion sections 63f, each of which is inserted into the two insertion holes 64h. The base plate 63 engages with the annular section 64 by the insertion of the two insertion sections 63f into the two insertion holes 64h.

[0031] The ring element 62 is coupled to the slow-running shaft 11 such that the rotation axis direction of the base plate 63 (the rotation axis direction of the ring element 62) and the rotation axis direction of the slow-running shaft 11 coincide. The rotation axis direction of the annular section 64 also coincides with the rotation axis direction of the slow-running shaft 11. The two insertion sections 63f of the base plate 63 are each inserted into the two insertion holes 64h to allow the annular section 64 to rotate integrally with the base plate 63. The ring element 62 thus rotates when the slow-running shaft 11 rotates.

[0032] Part of the high-speed shaft 12 is located within the annular section 64. The speed-increasing mechanism 61 includes three rollers 71. The three rollers 71 are arranged between the annular section 64 and the high-speed shaft 12 so that the annular section 64 and the high-speed shaft 12 are in contact. The three rollers 71 have the same shape. Each roller 71 has a columnar roller section 72, a columnar first projection 73, and a columnar second projection 74. The roller section 72 includes, as end faces in the direction of rotation, a first end face 72a and a second end face 72b. The first projection 73 projects from the first end face 72a of the roller section 72. The second projection 74 projects from the second end face 72b of the roller section 72.The rotation axis direction of the roller section 72, the rotation axis direction of the first projection 73 and the rotation axis direction of the second projection 74 are identical.

[0033] As in Fig. As shown in Figure 4, the diameter of each roller section 72 is larger than the diameter of the high-speed shaft 12. The axis of rotation of the roller section 72 also coincides with the axis of rotation of the high-speed shaft 12. The rollers 71 are arranged separately from one another in the circumferential direction of the high-speed shaft 12. The rollers 71 are made of metal. For example, the rollers 71 are made of iron or an iron alloy, which is the same metal as that of the high-speed shaft 12.

[0034] As in Fig. As shown in Figure 2, the annular section 64 has an annular projection 64f, which projects from the inner circumferential surface of the annular section 64 towards the three rollers 71. The projection 64f has a semicircular cross-section that is convex inwards in the radial direction of the annular section 64. That is, the cross-section of the projection 64f has a contour line that extends along an arc. As shown in Fig. As shown in Figure 2, the three rollers 71 touch the elevation 64f of the annular section 64 and the outer circumferential surface of the fast-running shaft 12.

[0035] As in Fig. As shown in Figure 2, a section of the annular section 64, corresponding to the protrusion 64f, is a thickness section 64d, which is thicker than the other sections. The thickness section 64d has a higher strength than the other sections. This limits radial outward deformation of the annular section 64 due to the reaction force resulting from the contact between the protrusion 64f and the three rollers 71. The thickness section 64d is located within the inner circumferential surface of the end section 26.

[0036] As in the Fig. 2 and Fig. As shown in Figure 3, the speed increaser mechanism 61 includes a support element 80, which interacts with the end section 26 to rotatably support the rollers 71. The support element 80 is arranged within the annular section 64. The support element 80 comprises a disc-shaped support base plate 81, which is slightly smaller than the annular section 64, and three column elements 82 that project from the support base plate 81. The support base plate 81 is positioned opposite the bottom 26a of the end section 26 in the direction of rotation of the roller sections 72. The three column elements 82 project from a surface 81a opposite the support base plate 81, which faces the bottom 26a of the end section 26, towards the bottom 26a of the end section 26.The three column elements 82 are arranged to fill the three cavities, each of which is defined by the inner circumferential surface of the annular section and the outer circumferential surfaces of two adjacent roller sections 72.

[0037] Each column element 82 has a screw insertion hole 84 through which a screw 83 is inserted. The base 26a of the end section 26 has screw holes 85 at positions corresponding to the screw insertion holes 84. The screw holes 85 are connected to the screw insertion holes 84. Each column element 82 is arranged such that the screw insertion hole 84 and the screw hole 85 are continuous relative to each other and the distal end face of the column element 82 abuts the base 26a of the end section 26. In this state, each column element 82 is fastened to the end section 26 by inserting a screw 82 through the screw insertion hole 84 and the screw hole 85 and tightening the screw 83 in the screw hole 85.

[0038] As in Fig. As shown in Figure 2, the speed increaser 60 includes first roller bearings 76 and second roller bearings 77, which rotatably support the rollers 71. The first roller bearings 76 are arranged in the end section 26. The second roller bearings 77 are arranged in the support base plate 81. Each roller 71 is supported by the first roller bearing 76 and the second roller bearing 77, positioned between the end section 26 and the support base plate 81.

[0039] As in Fig. As shown in Figure 3, the rollers 71, the ring element 62, and the high-speed shaft 12 are combined with the roller sections 72 that press against the high-speed shaft 12 and against the annular section 64. The high-speed shaft 12 is rotatably supported by the three roller sections 72. The contact section between the outer circumferential surface of each roller 72 and the projection 64f of the annular section 64 is referred to as an annular contact section Pa. The contact section between the outer circumferential surface of each roller section 72 and the outer circumferential surface of the high-speed shaft 12 is referred to as a shaft-side contact section Pb. A compressive load is applied to the annular contact sections Pa and the shaft-side contact sections Pb. Each of the contact sections Pa, Pb extends in the direction of rotation of the roller sections 72.

[0040] As in Fig. As shown in Figure 1, the high-speed shaft 12 has two flanges 12a, which are arranged at positions spaced apart from each other in the direction of rotation of the high-speed shaft 12. Each roller section 72 is held between the flanges 12a. Therefore, the high-speed shaft 12 is held in such a way that its position in the direction of rotation is not displaced. That is, the high-speed shaft 12 and the roller sections 72 are held in such a way that their relative positions do not change. The speed-increasing chamber S2 accommodates the ring element 62, the three rollers 71, and a portion of the high-speed shaft 12.

[0041] As in the Fig. 2 and Fig. As shown in Figure 3, the majority of the inner circumferential surface of the main body 25 is an arcuate surface 251, which extends along the outer circumferential surface of the annular section 64. The other portion of the inner circumferential surface of the main body 25, besides the arcuate surface 251, is a convex surface 252, which bulges outwards from the arcuate surface 251. Furthermore, a majority of the inner circumferential surface of the end section 26 is an arcuate surface 261, which, viewed in the axial direction of the end section 26, extends along the outer circumferential surface of the annular section 64. The other portion of the inner circumferential surface of the end section 26, besides the arcuate surface 261, is a convex surface 262, which extends outwards from the arcuate surface 261. The edge of the arc-shaped surface 261 on the open side of the end section 26 extends along the arc-shaped surface 251 of the main body 25.The edge of the curved surface 262 on the open side of the end section 26 also extends along the curved surface 252 of the main body 25.

[0042] As in Fig. As shown in Figure 2, a discharge channel 65 is defined between an end surface 64a of the annular section 64 on the open side and the bottom 26a of the end section 26 by means of the speed increaser 60 attached to the end section 26. The discharge channel 65 connects the inside and the outside of the annular section 64.

[0043] As in Fig. As shown in Figure 1, the radial compressor 10 includes an oil supply mechanism 100, which is configured to supply oil to the speed increaser mechanism 61. The oil supply mechanism 100 includes a pump 101 and an oil flow path 102 and operates the pump 101 to circulate oil through the speed increaser chamber S2 via the oil flow path 102.

[0044] The pump 101 is provided in the base 22 of the motor housing 21. The pump 101 of the present embodiment is of the positive displacement type. The pump 101 includes a receiving section 103 provided in the base 22 and a rotating body 104. The first end section 11a of the slow-running shaft 11 is coupled to the rotating body 104.

[0045] The engine housing 21 has a first oil channel 111 and a second oil channel 112, which are part of the oil flow path 102. The first oil channel 111 has a first end section that opens to the receiving section 103. The first oil channel 111 also has a second end section that opens at the end surface 21a at the open end of the engine housing 21. Specifically, the second end section of the first oil channel 111 opens in a section that contacts the bottom surface 24a. The second oil channel 112 has a first end section that opens to the receiving section 103. The second oil channel 112 also has a second end section that opens at the end surface 21a of the engine housing 21. Specifically, the second end section of the second oil channel 112 opens in a section that contacts the bottom surface 24a.

[0046] The main body 25 has a third oil channel 113 and a fourth oil channel 114, which are part of the oil flow path 102. The third oil channel 113 and the fourth oil channel 114 open in the axial direction of the main body 25 at opposite end faces. The third oil channel 113 has a first end section that opens at a position in the end face of the main body 25 facing the first oil channel 111. The first end section of the third oil channel 113 is connected to the first oil channel 111. The fourth oil channel 114 has a first end section that opens at a position in the end face of the main body 25 facing the second oil channel 112. The first end section of the fourth oil channel 114 is connected to the second oil channel 112.

[0047] The end section 26 has two fifth oil channels 115, which are part of the oil flow path 102. Each fifth oil channel 115 has a first end section that opens at a position in the open end face of the end section 26, facing the third oil channel 113. The first end section of each fifth oil channel 115 is connected to the third oil channel 113. Each fifth oil channel 115 has a second end section that opens at a position in the base 26a, facing the column element 82.

[0048] The column element 82 has two sixth oil channels 116, which are part of the oil flow path 102. Each sixth oil channel 116 has a first end section that opens at a position on the end face of the column element 82 facing one of the fifth oil channels 115. The first end section of the sixth oil channel 116 is connected to the fifth oil channel 115. Each sixth oil channel 116 has a second end section that opens at a position on the outer circumferential surface of the column element 82 facing the roller section 72. Although not shown, the fifth oil channels 115 and the sixth oil channels 116 both branch off from the third oil channel 113. The sixth oil channels 116 are provided in two of the three column elements 82 to supply oil to the ring element 62.

[0049] The end section 26 has a seventh oil channel 117, which is part of the oil flow path 102. The seventh oil channel 117 has a first end section that opens at a position in the open end surface of the end section 26 facing the fourth oil channel 114. The seventh oil channel 117 has a second end section that opens in the curved surface 262 of the end section 26. The second end section of the seventh oil channel 117 is an oil discharge hole 117a, which discharges oil from the speed-increasing chamber S2 onto the outside of the speed-increasing chamber S2. Thus, the inner circumferential surface of the housing 20 has the oil discharge hole 117a, which discharges oil from the speed-increasing chamber S2 onto the outside of the speed-increasing chamber S2.

[0050] As in Fig. As shown in Figure 2, the radial compressor 10 is used with the portion of the speed increaser housing 23 that is connected to the vertically downward-oriented seventh oil channel 117. Thus, the convex surface 252 of the main body 25 and the convex surface 262 of the end section 26 are located at the lowest vertical section. The oil discharge hole 117a is arranged to point vertically upwards. In the speed increaser chamber S2, oil is stored under its own weight in a portion connected to the oil discharge hole 117a.

[0051] The base 24 of the main body 25 has an oil supply channel 118, which branches off from the third oil channel 113 to supply oil to a portion of the shaft entry hole 27 between the first sealing element 33 and the second bearing 32. The oil supply channel 118 has a first end section that opens to the third oil channel 113. The oil supply channel 118 has a second end section that opens to a portion of the shaft entry hole 27 between the first sealing element 33 and the second bearing 32.

[0052] When pump 101 is operating, oil flows through the oil channels in the following order: seventh oil channel 117, fourth oil channel 114, second oil channel 112, intake section 103, first oil channel 111, third oil channel 113, fifth oil channel 115, and sixth oil channel 116. The oil flowing into the sixth oil channel 116 is directed into the ring element 62 to lubricate the rollers 71. The oil in the ring element 62 is discharged from the ring element 62 through the discharge channel 65. The oil discharged onto the outside of the ring element 62 is stored in the speed-increasing chamber S2.

[0053] Part of the oil flowing through the third oil channel 113 flows into the oil supply channel 118. The oil flowing through the oil supply channel 118 is supplied to a part of the shaft entry hole 27 between the first sealing element 33 and the second bearing 32 to lubricate the first sealing element 33 and the second bearing 32.

[0054] When each roller 71 rotates, a thin film of solidified oil (elastohydrodynamic lubrication (EHL)) is present at the annular contact section Pa and the shaft-side contact section Pb. The outer circumferential surface of the roller section 72 and the inner circumferential surface of the annular section 64 are in contact with each other via an intervening thin film of oil, and the outer circumferential surface of the high-speed shaft 12 and the outer circumferential surface of the roller section 72 are also in contact with each other via an intervening thin film of solidified oil. The rotational force of each roller 71 is transmitted to the high-speed shaft 12 via the thin film of solidified oil provided between the outer circumferential surface of the high-speed shaft 12 and the outer circumferential surface of the roller section 72, causing the high-speed shaft 12 to rotate. The annular section 64 rotates at the same speed as the low-speed shaft 11.The rollers 71 rotate at a higher speed than the slow-running shaft 11. Furthermore, the fast-running shaft 12, which has a smaller diameter than the roller sections 72, rotates at a higher speed than the roller sections 72. As described above, the speed increaser 60 causes the fast-running shaft 12 to rotate at a higher speed than the slow-running shaft 11.

[0055] As in Fig. As shown in Figure 4, the radial compressor 10 includes an intermediate wall 90, which is arranged between the ring element 62 in the speed-increasing chamber S2 and the base 24 of the main body 25. The intermediate wall 90 includes a thin, disk-shaped intermediate body 91 and a thin, plate-shaped projection 92, which projects from a portion of the outer circumference of a first end surface 911 of the intermediate body 91. The direction of projection of the projection 92 from the intermediate body 91 coincides with the thickness direction of the intermediate body 91.

[0056] The intermediate body 91 has a circular insertion hole 91a in its central section. The insertion hole 91a receives an end section of the slow-running shaft 11, which is guided through the shaft insertion hole 27 and projects into the speed increaser housing 23. The intermediate body 91 has two screw-receiving recesses 91b in the first end face 911 at positions around the insertion hole 91a. The screw-receiving recesses 91b are recessed in a direction opposite to the projection direction of the projection 92. Thus, sections on the first end face 911 of the intermediate body 91 corresponding to the screw-receiving recesses 91b are recessed. In contrast, the sections on a second end face 912 of the intermediate body 91 corresponding to the screw-receiving recesses 91b project by the amount corresponding to the recessed amount of the screw-receiving recesses 91b.Each screw receptacle 91b has a screw through hole 91c at its base.

[0057] As in Fig. As shown in Figure 2, the main body 25 has cylindrical projections 94 which extend from the base 24 and are located around the shaft entry hole 27. A screw 93 is guided through each screw through-hole 91c of the intermediate body 91 and screwed into the corresponding projection 94, so that the intermediate wall 90 is attached to the base 24 of the main body 25. The plane direction of the intermediate body 91 is orthogonal to the axial direction of the main body 25. The projection direction of the projection 92 from the intermediate body 91 coincides with the axial direction of the main body 25.

[0058] As in Fig. As shown in Figure 4, an outer circumferential surface 91d of the intermediate body 91 includes a first arcuate surface 911d and a second arcuate surface 912d, which extend along the arcuate surface 251 of the main body 25. The first arcuate surface 911d and the second arcuate surface 912d are tangent to the arcuate surface 251 of the main body 25. The circumferential length of the first arcuate surface 911d is longer than the circumferential length of the second arcuate surface 912d. In particular, the circumferential length of the first arcuate surface 911d is not shorter than twice the circumferential length of the second arcuate surface 912d. The projection 92 is located in the circumferential direction of the intermediate body 91 between the first arcuate surface 911d and the second arcuate surface 912d.

[0059] The outer circumferential surface 91d of the intermediate body 91 includes a first connecting surface 913d and a second connecting surface 914d. The first connecting surface 913d connects a first end section in the circumferential direction of the first arcuate surface 911d and the projection 92. The second connecting surface 914d connects a first end section in the circumferential direction of the second arcuate surface 912d and the projection 92.

[0060] The intermediate body 91 includes a cutout 95 in a portion of its outer circumference. The cutout 95 comprises a first cutout surface 95a, a second cutout surface 95b, and a third cutout surface 95c. The first cutout surface 95a extends radially inward in the intermediate body 91 from a second end section in the circumferential direction of the first arcuate surface 911d. The second cutout surface 95b extends radially inward in the intermediate body 91 from a second end section in the circumferential direction of the second arcuate surface 912d. The third cutout surface 95c connects the end section of the first cutout surface 95a on the side opposite the first arcuate surface 911d with the end section of the second cutout surface 95b on the side opposite the second arcuate surface 912d. The third cutout surface 95c extends along the arcuate surface 251 of the main body 25.

[0061] The circumferential length of the third cutout surface 95c is essentially the same as the circumferential length of the first arcuate surface 911d. Thus, the circumferential length of the third cutout surface 95c is longer than the circumferential length of the second arcuate surface 912d and not shorter than twice the circumferential length of the second arcuate surface 912d. The third cutout surface 95c is separated from the arcuate surface 251 of the main body 25. The third cutout surface 95c is arranged such that the insertion hole 91a is located in the radial direction of the intermediate body 91 between the third cutout surface 95c and the projection 92.

[0062] The projection 92 is arranged in the radial direction of the annular section 64 between the annular section 64 and the set consisting of the curved surface 252 of the main body 25 and the curved surface 262 of the end section 26. Thus, the cutout 95 is positioned further away from the curved surface 252 of the main body 25 than the projection 92 and vertically above the projection 92.

[0063] The projection 92 comprises a first plate section 92a, which has a curved plate shape, and a second plate section 92b, which has a flat plate shape. The first plate section 92a is continuous with the first connecting surface 913d. The second plate section 92b is continuous with the second connecting surface 914d. The end section of the first plate section 92a, which is on the opposite side of the first connecting surface 913d, is continuous with the end section of the second plate section 92b, which is on the opposite side of the second connecting surface 914d. The length of the first plate section 92a in the projection direction from the intermediate body 91 is the same as the length of the second plate section 92b in the projection direction from the intermediate body 91. The thickness of the first plate section 92a is equal to the thickness of the second plate section 92b.

[0064] As in Fig. As shown in Figure 2, the end section of the second plate section 92b is located on the side opposite the intermediate body 91 in the radial direction of the annular section 64, in a position overlapping the oil discharge hole 117a. Accordingly, the projection 92 is arranged in the radial direction of the annular section 64 between the inner circumferential surface of the speed increaser housing 23 and the annular section 64, and in a position opposite the oil discharge hole 117a.

[0065] In the speed increaser chamber S2, the area defined in the axial direction of the annular section 64 between the intermediate body 91 and the ring element 62, and in the radial direction of the annular section 64 between the projection 92 and the ring element 62, is designated as a stirring area 96. Furthermore, in the speed increaser chamber S2, the area defined in the axial direction of the annular section 64 between the intermediate body 91 and the base 24 of the main body 25, and in the radial direction of the annular section 64 between the projection 92 and the inner circumferential surface of the speed increaser housing 23, is designated as a bearing area 97.

[0066] The stirring area 96 is connected to the bearing area 97 via the cavity between the cutout 95 and the arcuate surface 251 of the main body 25 in the axial direction of the annular section 64 between the intermediate body 91 and the base 24 of the main body 25. Thus, the cavity between the cutout 95 and the arcuate surface 251 of the main body 25 forms an inlet channel 98, which directs oil in the stirring area 97 to the bearing area 97 in the axial direction of the annular section 64 between the intermediate body 91 and the base 24 of the main body 25.

[0067] The arcuate surface 261 of the end section 26 is an inclined surface such that, in the radially outward direction of the annular section 64, it is increasingly separated from the annular section 64 as the distance to the intermediate body 91 decreases. The arcuate surface 261 of the end section 26 forms part of the stirring area 96 on the inner circumferential surface of the speed increaser housing 23. A portion of the arcuate surface 26a of the end section 26 lies opposite the inlet channel 98 in the axial direction of the speed increaser housing 23. The inclination angle of the arcuate surface 261 of the end section 26 is greater than the angle of inclination required for manufacturing the end section 26 using a mold.

[0068] As in the Fig. 2 and Fig. As shown in Figure 3, the speed increaser housing 23 includes a locking projection 99. The locking projection 99 extends from the arcuate surface 261 of the end section 26 towards the annular section 64. The locking projection 99 is located opposite the inlet channel 98 in the axial direction of the speed increaser housing 23. As shown in Fig. As shown in Figure 2, the locking projection 99 has a distal end surface located in the projecting direction from the arcuate surface 261. The distal end surface is inclined such that, in the radially outward direction of the annular section 64, it is increasingly separated from the annular section 64 as the distance to the intermediate body 91 decreases. The distal end surface of the locking projection 99 is flat. The locking projection 99 has two side surfaces on the sides opposite the arcuate surface 261 in the circumferential direction. The side surfaces are flat and parallel to each other. The locking projection 99 is located outside the thickness section 64d of the annular section in the radial direction of the annular section 64.

[0069] The operation of the present embodiment will now be described.

[0070] When the ring element 62 rotates, the annular section 64 lifts and stirs the oil in the stirring area 96 in the speed increaser chamber S2. As the oil in the stirring area 96 is stirred by the ring element 62, the centrifugal force of the ring element 62 propels the oil outwards in the radial direction of the annular section to collide with the inner circumferential surface of the speed increaser housing 23. In particular, the thick section 64d of the annular section 64 lifts a larger quantity of oil in the stirring area 96 than the other sections of the annular section 64. Consequently, a large quantity of oil collides with the arcuate surface 261 of the end section 26 at the thick section 64d of the annular section 64.

[0071] As described above, the arcuate surface 261 of the end section 26 is inclined such that, in the radially outward direction of the annular section 64, it is increasingly separated from the annular section 64 as the distance to the intermediate body 91 decreases. Thus, the oil that collects on the arcuate surface 261 of the end section 26 is guided through the arcuate surface 261 of the end section 26 toward the intermediate body 91. The oil, having been guided through the arcuate surface 261 of the end section 26 toward the intermediate body 91, flows along the arcuate surface 251 of the main body 25 and is then directed to the bearing area 97, which is located in the axial direction of the annular section 64 between the intermediate body 91 and the base 24 of the main body 25, in order to be stored in the bearing area 97.The oil stored in bearing area 97 is unlikely to be stirred by the rotation of the ring element 62. This reduces the absolute amount of oil stirred by the ring element 62. Consequently, the stirring resistance during the rotation of the ring element 62 is reduced.

[0072] When the oil is stirred in the stirring area 96, the centrifugal force of the ring element 62 continues to propel the oil outwards in the radial direction of the annular section 64. A portion of the oil rotates along with the annular section 64 on its radial outer surface due to the rotation of the ring element 62. Specifically, the oil rotates with the annular section 64 in the cavity between the outer circumferential surface of the annular section 64 and the set of arcuate surfaces 251 of the main body 25 and arcuate surfaces 261 of the end section 26. Consequently, the oil flows as indicated by arrows R3. Fig. 3 indicated, towards the curved surface 252 of the main body 25 and the curved surface 262 of the end section 26. The oil can thus collide with the parts surrounding the oil discharge hole 117a at the curved surface 262 of the end section 26.

[0073] As described above, the projection 92 is arranged in the radial direction of the annular section 64 between the annular section 64 and the set consisting of the curved surface 252 of the main body 25 and the curved surface 262 of the end section 26. The projection 92 is located in a position opposite the oil discharge hole 117a in the radial direction of the annular section 64. Consequently, the oil first collides with the parts around the oil discharge hole 117a on the curved surface 262 of the end section 26 and is then flung onto the parts around the oil discharge hole 117a in the curved surface 262, as indicated by arrows R3 in Figure 1. Fig.3 indicated. The oil then collides with the projection 92 and is flung back to be discharged through the oil discharge hole 117a onto the outside of the speed-increasing chamber S2. Thus, the oil does not rotate together with the annular section 64 on the radial outside of the annular section 64 after impacting the parts around the oil discharge hole 117a. This reduces the absolute quantity of oil stirred by the ring element 62. Consequently, the stirring resistance during the rotation of the ring element 62 is further reduced.

[0074] Additionally, the locking projection 99 extends from the arcuate surface 261 of the end section 26 towards the annular section 64. Although the oil rotates along with the annular section 64 on the radial outer surface of the annular section 64 due to the rotation of the annular element 62, the oil therefore collides with the locking projection 99 to flow along the locking projection 99 towards the intermediate body 91. The oil is then guided in the axial direction of the annular section 64 between the intermediate body 91 and the base 24 of the main body 25 to the bearing area 97. This further reduces the absolute quantity of oil stirred by the annular element 62 and thus further reduces the stirring resistance during the rotation of the annular element 62.

[0075] The oil is supplied from the oil supply channel 118 to a portion of the shaft entry hole 27 between the first sealing element 33 and the second bearing 32. The oil then lubricates the first sealing element 33 and the second bearing 32 before flowing out of the bearing area 97 via the cavity between the second bearing 32 and the slow-running shaft 11. Thus, the oil that contributes to the lubrication of the first sealing element 33 and the second bearing 32 and flows into the speed-increasing chamber S2 does not enter the stirring area 96. Therefore, the absolute quantity of oil stirred by the ring element 62 is not increased, and the stirring resistance during rotation of the ring element 62 is reduced.

[0076] The embodiment described above has the following advantages. (1) The partition 90 is arranged in the speed-increasing chamber S2 between the ring element 62 and the base 24 of the main body 25. Furthermore, the radial compressor 10 includes the inlet channel 98, which directs the oil in the agitation zone 96 to the bearing zone 97. When the oil in the agitation zone 96 is agitated by the rotation of the ring element 62, the centrifugal force of the ring element 62 propels the oil outwards in the radial direction of the annular section 64 to collide with the inner circumferential surface of the speed-increasing housing 23. A portion of the oil that strikes the inner circumferential surface of the speed-increasing housing 23 flows towards the partition 90 and is guided via the inlet channel 98 into the bearing zone 97. The oil stored in bearing area 97 is unlikely to be stirred by the rotation of ring element 62. This reduces the absolute quantity of oil stirred by ring element 62.As a result, the stirring resistance is reduced during the rotation of the ring element 62. (2) When the oil in the stirring area 96 is stirred by the ring element 62, the centrifugal force of the ring element 62 throws the oil outwards in the radial direction of the annular section 64. A portion of the oil rotates along with the annular section 64 on its radial outer surface due to the rotation of the ring element 62. At this point, the oil may collide with the parts surrounding the oil discharge hole 117a on the inner circumferential surface of the speed increaser housing 23. As described above, the projection 92 is arranged in the radial direction of the annular section 64 between the inner circumferential surface of the speed increaser housing 23 and the annular section 64. The projection 92 is positioned opposite the oil discharge hole 117a in the radial direction of the annular section 64.Thus, the oil first collides with the particles around the oil discharge hole 117a on the inner circumferential surface of the speed increaser housing 23 and is then flung onto the particles around the oil discharge hole 117a on the inner circumferential surface of the speed increaser housing 23. Afterward, the oil collides with the projection 92 and is flung back to be discharged through the oil discharge hole 117a onto the outside of the speed increaser chamber S2. Therefore, the oil does not rotate with the annular section 64 on the radial outside of the annular section 64 after impacting the particles around the oil discharge hole 117a on the inner circumferential surface of the speed increaser housing 23. This reduces the absolute quantity of oil stirred by the annular element 62. Consequently, the stirring resistance during the rotation of the annular element 62 is further reduced. (3) The arcuate surface 261 of the end section 26 forms part of the agitation zone 96 on the inner circumferential surface of the speed-increasing housing 23. The arcuate surface 261 is an inclined surface such that, in the radially outward direction of the annular section 64, it is increasingly separated from the annular section 64 as the distance to the intermediate body 91 decreases. The arcuate surface 261 also faces the inlet channel 98 in the axial direction of the speed-increasing housing 23. With this configuration, the oil, which is flung outward in the radial direction of the annular section 64 by the rotation of the ring element 62, collides with the arcuate surface 261 and is then guided by the arcuate surface 261 toward the intermediate wall 90.This allows the oil in the stirring area 96 to be easily guided via the inlet channel 98 to the bearing area 97, thus further reducing the absolute quantity of oil stirred by the ring element 62. As a result, the stirring resistance during the rotation of the ring element 62 is further reduced. (4) The speed increaser housing 23 includes a locking projection 99. The locking projection 99 extends from the arcuate surface 261 of the end section 26 towards the annular section 64 and is located opposite the inlet channel 98 in the axial direction of the speed increaser housing 23. Although the oil rotates on the radial outside of the annular section 64 along with the annular section 64 due to the rotation of the annular element 62, the oil therefore collides with the locking projection 99 to flow along the locking projection 99 towards the intermediate wall 90. The oil is then guided via the inlet channel 98 towards the bearing area 97. This further reduces the absolute quantity of oil stirred by the annular element 62. As a result, the stirring resistance during the rotation of the annular element 62 is further reduced. (5) The base 24 of the main body 25 has the oil supply channel 118, which supplies oil to a portion of the shaft entry hole 27 between the first sealing element 33 and the second bearing 32. The oil is supplied to a portion of the shaft entry hole 27 between the first sealing element 33 and the second bearing 32. Then, before flowing towards the bearing area 97, the oil lubricates the first sealing element 33 and the second bearing 32 via the cavity between the second bearing 32 and the slow-running shaft 11. Thus, the oil that contributes to the lubrication of the first sealing element 33 and the second bearing 32 and flows into the speed-increasing chamber S2 does not flow into the stirring area 96. Therefore, the absolute quantity of oil stirred by the ring element 62 is not increased. Consequently, the stirring resistance during the rotation of the ring element 62 is reduced. (6) When the stirring resistance is reduced during the rotation of the ring element 62, as described above, stirring of the oil in the speed-increasing chamber S2 is suppressed. This reduces the amount of air trapped in the oil due to stirring. As a result, the amount of oil contributing to the lubrication of the rollers 71 is increased.

[0077] The embodiment described above can be modified as described below. The embodiment described above and the following modifications can be combined as long as the combined modifications remain technically consistent.

[0078] The partition wall 90 does not necessarily have to have the projection 92.

[0079] The inlet channel 98 can be a through hole extending through the intermediate body 91.

[0080] The circumference of the cutout 95 provided in the outer circumference of the intermediate body can be changed as required.

[0081] The arc-shaped surface 261 of the end section 26 does not necessarily have to be an inclined surface, but can also be an inner circumferential surface that extends in the axial direction of the speed increaser housing 23.

[0082] The projection 92 can as a whole have a curved plate shape extending in the circumferential direction of the annular section 64.

[0083] The first plate section 92a of the projection 92 does not necessarily have to have a curved plate shape, but can also have a flat plate standard.

[0084] The first plate section 92a and the second plate section 92b need not be continuous with respect to each other. In this case, the projection 92 includes a first plate section 92a and a second plate section 92b, which are discontinuous.

[0085] The distal end surface of the locking projection 99 need not necessarily be configured such that, in the radially outward direction of the annular section 64, the distal end surface is increasingly separated from the annular section 64 as the distance to the intermediate body 91 decreases. Instead, the distal end surface can be a flat surface extending in the axial direction of the speed increaser housing 23.

[0086] The locking projection 99 does not necessarily have to protrude from the arcuate surface 261. The locking projection 99 can also be omitted from the speed increaser housing 23.

[0087] The pump 101 does not necessarily have to be contained within the radial compressor 10. For example, an external pump located outside the radial compressor 10 can also be used.

[0088] The number of roles, 71, can be changed to four or five, for example.

[0089] The speed increaser 60 can use a wedge effect. In this case, at least one of the rollers is a movable roller that is moved by the rotation of the ring element 62.

[0090] The radial compressor 10 can be used in any suitable device to compress any type of fluid. For example, the radial compressor 10 can be used in an air conditioning system to compress a refrigerant fluid. Furthermore, the radial compressor 10 can be mounted on any structure other than a vehicle.

[0091] Various modifications to the form and details of the foregoing examples may be made without departing from the spirit and scope of the claims and their equivalents. The examples serve only for descriptive purposes and not for limitation. Descriptions of features in each example are deemed applicable to similar features and aspects in other examples. Appropriate results may be obtained by performing sequences in a different order and / or by combining components differently in a described system, architecture, device, or circuit and / or by replacing or supplementing them with other components or their equivalents. The scope of the disclosure is defined not by the detailed description but by the claims and their equivalents. All variations within the scope of the claims and their equivalents are contained in this disclosure.

Claims

[1] Radial compressor (10) with: a slow-moving wave (11); a ring element (62) which rotates when the slow-running shaft (11) rotates, wherein the ring element (62) has an annular section (64); a fast-moving wave (12) located within the annular section (64); a roller (71) arranged between the annular section (64) and the fast-running shaft (12) to contact the annular section (64) and the fast-running shaft (12); a wheel (52) which rotates integrally with the fast-running shaft (12); an electric motor (13) that rotates the slowly running shaft (11); a tubular housing (20) which a speed-increasing chamber (S2) that accommodates the ring element (62), the roller (71) and part of the high-speed shaft (12) and stores oil, a motor chamber (S1) that accommodates the electric motor (13), and a partition (24) aligned in the radial direction of the tubular housing (20), which axially separates the speed increaser chamber (S2) and the motor chamber (S1), includes characterized by a partition wall (90) having a disk-shaped intermediate body (91) oriented radially in the direction of the tubular housing (20), which is arranged axially in the speed-increasing chamber (S2) between the ring element (62) and the partition wall (24), and a plate-shaped projection (92) that projects in a thickness direction of the intermediate body (91); and an inlet channel (98) which directs oil in a stirring area (96) to a bearing area (97), wherein the stirring area (96) in the speed increaser chamber (S2) includes an area between the intermediate body (91) and the projection (92) of the partition wall (90) and the ring element (62), and the bearing area (97) in the speed increaser chamber (S2) includes an area between the intermediate body (91) of the partition wall (90) and the partition wall (24) and an area between the projection (92) of the partition wall (90) and a speed increaser housing (23). [2] Radial compressor (10) according to claim 1, wherein an inner circumferential surface of the housing (20) has an oil discharge hole (117a) that discharges oil in the speed increase chamber (S2) onto an outer surface of the speed increase chamber (S2), the partition wall (90) includes the axially extending projection (92), and the projection (92) is arranged in a radial direction of the annular section (64) between the inner circumferential surface of the housing (20) and the annular section (64) and at a position opposite the oil discharge hole (117a). [3] Radial compressor (10) according to claim 1 or 2, wherein at least part of a section of an inner circumferential surface of the housing (20) that forms the stirring area (96) is an inclined surface (261), the inclined surface (261) is inclined such that the inclined surface (261) is increasingly spaced away from the annular section (64) in a radially outward direction of the annular section (64) as the distance to the partition wall (90) decreases, and the inclined surface (261) is opposite the inlet channel (98) in an axial direction of the housing (20). [4] Radial compressor (10) according to any one of the preceding claims 1 to 3, wherein the housing (20) includes a locking projection (99), and the locking projection (99) extends from a part of an inner circumferential surface of the housing (20), on which the stirring area (96) is formed, towards the annular section (64), and wherein the locking projection (99) is opposite the inlet channel (98) in an axial direction of the housing (20). [5] Radial compressor (10) according to any one of the preceding claims 1 to 4, wherein the partition (24) has a shaft entry hole (27) through which the slow-running shaft (11) is inserted, a bearing (32) and a sealing element (33) are arranged in the shaft entry hole (27), the bearing (32) rotatably supports the slow-running shaft (11), the sealing element (33) seals a gap between the shaft entry hole (27) and the slow-running shaft (11), the sealing element (33) is located closer to the motor chamber (S1) than the bearing (32), and the partition (24) has an oil supply channel (118) which supplies oil to a part of the shaft entry hole (27) between the sealing element (33) and the bearing (32). [6] Radial compressor (10) according to any one of the preceding claims, characterized by , that the inlet channel (98) is formed by a radial gap between the housing (20) and the intermediate wall (90) or a through hole in the intermediate body (91) of the intermediate wall (90) at a point which is radially opposite the stirring area (96).

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