TRANSMISSION AND CENTRIFUGAL COMPRESSOR

Abstract

Gearbox (14), with: a gearbox housing element (22); a ring-shaped ring section (62) which is provided in the gearbox housing element (22) and rotates when a low-speed shaft (11) rotates; a high-speed wave (12) which is arranged on an inner side of the ring section (62); at least three rollers (71, 72, 73) provided between the ring section (62) and the high-speed shaft (12) and contacting both an inner circumferential surface of the ring section (62) and an outer circumferential surface of the high-speed shaft (12); and radial bearings (101, 102, 103, 104, 105, 106) with which the rollers (71, 72, 73) are rotatably mounted through the gearbox housing element (22), wherein The roles (71, 72, 73) include: a movable roller (73) which moves in a direction of rotation of the ring section (62) in response to the rotation of the ring section (62); and a fixed roller (71, 72) which is attached in such a way that it does not move in the direction of rotation of the ring section (62), the radial bearings (101, 102, 103, 104, 105, 106) include a movable bearing (103) which rotatably supports the movable roller (73), the gearbox housing element (22) includes: a first support surface (161) that contacts the movable bearing (103) to limit the movable roller (73) in a first position; and a second support surface (162) which is provided in a position spaced apart from the first support surface (161) in the direction of rotation and which contacts the movable bearing (103) in order to limit the movable roller (73) in a second position, a movement of the movable roller (73) within a range of motion from the first position to the second position is performed, and the range of motion includes a specified area in which the movable roller (73) is not supported in a radial direction of the high-speed shaft (12) by the gear housing element (22) with the movable bearing (103) in between, but is supported by being held between the ring section (62) and the high-speed shaft (12), characterized in that the gear housing element (22) has a plate section (26), The plate section (26) as surfaces defining a receiving chamber for the movable bearing (S13) which receives the movable bearing (103) includes: a floor area (151); and a receiving surface (154) extending in an axial direction of the high-speed wave (12) from the base surface (151) and including the first support surface (161) and the second support surface (162), the plate section (26) includes a plate through-hole (26c) through which the high-speed shaft (12) is guided, the receiving surface (154) has an inner opening (155) that opens inwards in the radial direction of the high-speed wave (12), the receiving chamber for the movable bearing (S13) and the plate through-hole (26c) are connected to each other through the inner opening (155), and the movable bearing (103) is partially arranged in the plate through-hole (26c).

Description

BACKGROUND area

[0001] The present disclosure relates to a gearbox and a centrifugal compressor equipped with the gearbox. Description of the state of the art

[0002] As disclosed in JP 2004-308 757, a transmission is known that transmits a driving force between a low-speed / slow-rotating shaft and a high-speed / fast-rotating shaft. The transmission disclosed in the document comprises a transmission housing, an annular ring section that rotates when a low-speed shaft rotates, a high-speed shaft arranged on the inside of the annular section, and rollers arranged between the annular section and the high-speed shaft. The rollers each have an outer circumferential surface that contacts both the inner circumferential surface of the annular section and the outer circumferential surface of the high-speed shaft. The document also discloses that at least one of the rollers is a movable roller.

[0003] The JP 2006 - 307 773 A reveals a turbocharger in which the speed of an input shaft is increased by a gearbox and transferred to an output shaft with an impeller.

[0004] JP 2017-180 791 A discloses a speed amplifier in which the oil supply is adjusted according to the load. The speed amplifier uses a ring element, a high-speed shaft, and rollers positioned between them. A movable roller is used to control the amount of oil entering the gearbox housing through an opening, thereby increasing or decreasing the oil supply depending on the load.

[0005] DE 10 2017 106 760 A1 discloses a speed increase mechanism with a rotatable circumferential wall, a high-speed shaft arranged therein, and three rolling elements. The three rolling elements are arranged in axially different positions so that their contact areas with the high-speed shaft do not overlap.

[0006] Some gearboxes include a movable bearing in which a movable roller is rotatably mounted. In this case, the movable bearing must support the movable roller in such a way that the roller can move. Therefore, the movable bearing itself can be movable.

[0007] With this design, misalignment or dimensional errors can cause the movable bearing to become stuck against the gearbox housing. In this case, the movable bearing can impede the movement of the movable roller. Furthermore, the sliding motion between the movable bearing and the gearbox housing can cause wear on components. SUMMARY

[0008] Accordingly, an objective of the present disclosure is to provide a gearbox and a centrifugal compressor / centrifugal force converter equipped with a gearbox that enables smooth / easy movement of a movable bearing.

[0009] This summary serves to present, in simplified form, a selection of concepts that are described in detail below. This summary is neither intended to identify key features or essential characteristics of the claimed subject matter, nor is it intended to be used as an aid in defining the scope of the claimed subject matter.

[0010] In a first general aspect, a transmission is provided comprising a transmission housing element, an annular ring section provided within the transmission housing element and rotating when a low-speed shaft rotates, a high-speed shaft arranged on an inner side of the ring section, at least three rollers provided between the ring section and the high-speed shaft and contacting both an inner circumferential surface of the ring section and an outer circumferential surface of the high-speed shaft, and radial bearings by which the rollers are rotatably mounted through the transmission housing element. The rollers include a movable roller that moves in the direction of rotation of the ring section in response to its rotation, and a fixed roller that is fixed / attached so that it does not move in the direction of rotation of the ring section.The radial bearings include a movable bearing that rotatably supports the movable roller. The gear housing element includes a first support surface that contacts the movable bearing to constrain the movable roller to a first position, and a second support surface located at a position spaced apart in the direction of rotation from the first support surface, which also contacts the movable bearing to constrain the movable roller to a second position. The movement of the movable roller is performed within a range of motion from the first position to the second position.The range of motion includes a specified area where the movable roller is not supported in a radial direction of the high-speed shaft by the gear housing element with the movable bearing between it, but is supported by being held between the ring section and the high-speed shaft. The gear housing element has a plate section, the plate section comprising surfaces that define a receiving chamber for the movable bearing, which receives the movable bearing: a bottom surface and a receiving side surface extending from the bottom surface in an axial direction of the high-speed shaft, comprising the first support surface and the second support surface. The plate section includes a through-hole through which the high-speed shaft passes.The receiving surface has an inner opening that opens inwards in the radial direction of the high-speed shaft. The receiving chamber for the movable bearing (S13) and the plate through-hole are connected to each other by the inner opening, and the movable bearing is partially located in the plate through-hole.

[0011] In a second general aspect, a gearbox is provided which has a gearbox housing element, an annular ring section provided in the gearbox housing element which rotates when a low-speed shaft rotates, a high-speed shaft which is arranged on an inside of the ring section, at least three rollers which are provided between the ring section and the high-speed shaft and which touch / contact both an inner circumferential surface of the ring section and an outer circumferential surface of the high-speed shaft, and roller bearings with which the at least three rollers are rotatably mounted through the gearbox housing element.The at least three rollers include at least one movable roller that moves between a first position and a second position, spaced apart from the first position in one direction of rotation of the ring section, in response to the rotation of the ring section, and at least two fixed rollers that are fixed so that they do not move in the direction of rotation of the ring section. The roller bearings have a movable bearing that rotatably supports the movable roller. The gear housing element includes, as (top) surfaces that define a receiving chamber for the movable bearing, a bottom surface and a receiving side surface extending from the bottom surface, comprising the first support surface and the second support surface. The receiving chamber for the movable bearing is arranged on an outer side of the high-speed shaft in the radial direction of the high-speed shaft.The receiving side surface has a first support surface that contacts the moving bearing to support it when the moving roller is in the first position, and a second support surface located at a position spaced rotationally from the first support surface that contacts the moving bearing to support it when the moving roller is in the second position. The receiving side surface includes a detached area located at a position separate from the moving bearing and on the outside of the moving bearing in the radial direction of the high-speed shaft. There is clearance between the detached area and the moving bearing regardless of the position of the moving bearing.

[0012] Further features and aspects will become apparent from the following detailed description, the drawings, and the claims. BRIEF DESCRIPTION OF THE FIGURES Fig. Figure 1 is a cross-sectional view that schematically shows an example of a centrifugal compressor. Fig. 2 is a cross-sectional view along line 2-2 in Fig. 1. Fig. Figure 3 is a perspective exploded view showing rollers, roller bearings, and a second part. Fig. Figure 4 is a front view showing a plate section and plate bearings. Fig. Figure 5 is a cross-sectional view along line 5-5 in Fig. 4. Fig. Figure 6 is a partially enlarged view of a third plate bearing when a third roller is in a first position. Fig. Figure 7 is a cross-sectional view along line 7-7 in Fig. 6. Fig. Figure 8 is a front view of the third plate bearing when the third roller is in an intermediate position between the first position and a second position. Fig. Figure 9 is a front view of the third plate bearing when the third roller is in the second position. Fig. Figure 10 is a front view showing a receiving chamber for the third plate bearing according to a modification. Fig. Figure 11 is a cross-sectional view along line 11-11 in Fig. 10.

[0013] In the drawings and the detailed description, the same reference numbers refer to the same elements. The drawings may not be to scale, and the relative size, proportions, and representation of the elements in the drawings may be exaggerated for the sake of clarity, illustration, and simplicity. DETAILED DESCRIPTION

[0014] This description provides a comprehensive understanding of the described methods, devices, and / or systems. Modifications and equivalents of the described methods, devices, and / or systems are obvious to a person skilled in the art. The sequence of operations is exemplary and can be modified by a person skilled in the art, except for operations that necessarily follow a specific order. Descriptions of functions and designs that are well known to a person skilled in the art may have been omitted.

[0015] Exemplary embodiments can be designed differently and are not limited to the examples described. However, the examples described are thorough and complete and convey the full scope of the disclosure to a person skilled in the art.

[0016] In this description, “at least one of A and B” should be understood to mean “only A, only B or both A and B”.

[0017] A gearbox 14 and a centrifugal compressor / centrifugal compressor / radial compressor 10 equipped with the gearbox 14 according to one embodiment are now described. The following description illustrates only one example, and the gearbox 14 and the centrifugal compressor 10 are not limited to the content of the present embodiment.

[0018] The centrifugal compressor 10 of the present embodiment is mounted on a fuel cell vehicle (FCV) equipped with a fuel cell and is used to supply air to the fuel cell.

[0019] As in Fig. As shown in Figure 1, the centrifugal compressor 10 comprises a low-speed shaft 11, an electric motor 13 that rotates the low-speed shaft 11, the gearbox 14, which includes a high-speed shaft 12 and a gearbox housing element 22, and a compression unit 15 that compresses a fluid (in the present embodiment, air) by rotating the high-speed shaft 12. The shafts 11 and 12 are, for example, made of metal. In particular, the shafts 11 and 12 are made of iron or an iron alloy.

[0020] The centrifugal compressor 10 comprises a motor housing element 21, which accommodates the electric motor 13, and a compressor housing element 23, which has an intake opening 23a. The fluid is drawn into the compressor housing element 23 through the intake opening 23a. The motor housing element 21, the compressor housing element 23, and the gearbox housing element 22 are interconnected. Specifically, the motor housing element 21 is attached to the gearbox housing element 22 from the first direction, and the compressor housing element 23 is attached to the gearbox housing element 22 from a direction opposite to the first direction. The motor housing element 21, the compressor housing element 23, and the gearbox housing element 22 work together to form the overall shape of the centrifugal compressor 10. For illustrative purposes, the motor housing element 21, the compressor housing element 23, and the gearbox housing element 22 are collectively referred to as a housing 20.

[0021] In general, the housing 20 has an essentially tubular shape (in particular, a cylindrical shape). The housing 20 accommodates the shafts 11, 12, the electric motor 13, and the compressor / compression unit 15. The housing 20 is made of aluminum, for example. However, the material of the housing 20 is not limited to this and can be any suitable material. The intake port 23a is located in the first end face 20a of the housing 20 in the axial direction.

[0022] The engine housing element 21 generally has a substantially tubular shape (in particular a cylindrical shape) and comprises a bottom section 21a. The housing 20 includes end surfaces 20a, 20b on axially opposite sides. The outer surface of the bottom section 21a of the engine housing element 21 includes a second end surface 20b, located on the side opposite the first end surface 20a, in which the intake opening 23a is provided.

[0023] The gearbox housing element 22, which represents a section of the gearbox 14, has a first part 24 and a second part 25, which are joined together in the axial direction of the housing 20. The parts 24 and 25 form a gearbox chamber S2, which accommodates various components of the gearbox 14. The gearbox chamber S2 can also be considered an interior space of the gearbox housing element 22, defined by the inner surface of the second part 25 and the inner surface of the first part 24.

[0024] In general, the first part 24 has a substantially tubular shape (in particular a cylindrical shape) and a bottom section 24a. The motor housing element 21 and the first part 24 are coupled together, with the open end of the motor housing element 21 abutting the bottom section 24a of the first part 24. The inner surface of the motor housing element 21 and the surface of the bottom section 24a of the first part 24 facing the motor housing element 21 form a motor receiving chamber S1, which accommodates the electric motor 13. The motor receiving chamber S1 accommodates the low-speed shaft 11, with the direction of rotation of the low-speed shaft 11 and the axial direction of the housing 20 being congruent.

[0025] The low-speed shaft 11 is rotatably mounted in the housing 20. In particular, the bottom section 21a of the motor housing element 21 is provided with a first shaft bearing 31, which rotatably mounts a first end section 11a of the low-speed shaft 11. Furthermore, the bottom section 24a of the first part 24 has a through-hole 24b. A second end section 11b of the low-speed shaft 11, located on a side opposite the first end section 11a, passes through the through-hole 24b. The inner surface of the through-hole 24b accommodates a second shaft bearing 32, which rotatably mounts the second end section 11b.

[0026] As in Fig. As shown in Figure 1, the second end section 11b of the low-speed shaft 11 is guided through the through-bore 24b of the first part 24, and the low-speed shaft 11 is partially located within the gearbox housing element 22 (in other words, within the gearbox chamber S2). A sealing element 33 is located between the inner surface of the through-bore 24b of the first part 24 and the second end section 11b of the low-speed shaft 11. The sealing element 33 prevents oil from flowing into the first part 24 and into the engine receiving chamber S1.

[0027] The electric motor 13, housed in the motor mounting chamber S1, comprises a rotor 41 and a stator 42. The rotor 41 is attached to the low-speed shaft 11, and the stator 42 is located on the outside of the rotor 41 and attached to the inner surface of the motor housing element 21. The axis of rotation of the rotor 41 and the central axis of the stator 42 are aligned with the axis of rotation of the low-speed shaft 11. The rotor 41 and the stator 42 are arranged opposite each other radially along the low-speed shaft 11.

[0028] The stator 42 contains a cylindrical stator core 43 and a coil 44 wound around the stator core 43. The current flowing through the coil 44 causes the rotor 41 and the low-speed shaft 11 to rotate together.

[0029] The second part 25 has a tubular shape (in particular a cylindrical shape) with a plate section 26 having a bottom section and opens towards the first part 24. The first part 24 has a tubular shape with a closed end and an opening on one side in the axial direction. The second part 25 and the first part 24 are joined together such that the open ends abut each other.

[0030] Plate section 26 includes a first plate surface 26a, which defines the gear chamber S2, and a second plate surface 26b, which is located on one side opposite the first plate surface 26a. The plate surfaces 26a and 26b intersect with the rotation axis Z of the high-speed shaft 12 (in this example, they are orthogonal to it). For clarity, the rotation axis Z of the high-speed shaft 12 is simply referred to as the rotation axis Z.

[0031] As in Fig. As shown in Figure 1, the plate section 26 of the second part 25 has a plate through-hole 26c. The high-speed shaft 12, which is a section of the gearbox 14, is guided through the plate through-hole 26c. The high-speed shaft 12 is partially located within the compressor housing element 23 through the plate through-hole 26c.

[0032] A sealing element 50a is arranged between the inner surface of the plate through-hole 26c and the high-speed shaft 12. The sealing element 50a prevents oil from flowing from the gearbox housing element 22 into the compressor housing element 23. The sealing element 50a is attached to the inner surface of the through-hole 26c of the plate in such a way that there is no gap into which oil can penetrate between the sealing element 50a and the through-hole 26c of the plate.

[0033] The high-speed shaft 12 includes a stop section 50b that abuts / adjoins the sealing element 50a. The stop section 50b has the form of a flange / shaft shoulder that projects from the high-speed shaft 12 in a radial direction R. The stop section 50b is located in the through-hole 26c of the plate. The sealing element 50a is positioned in the through-hole 26c of the plate and presses against the stop section 50b.

[0034] For clarity, the radial direction R of the high-speed wave 12 is simply referred to as radial direction R. The radial direction R coincides with the radial direction of the low-speed wave 11.

[0035] In the present embodiment, the stop section 50b and the inner surface of the through-hole 26c of the plate are spaced apart from each other in the radial direction R, so that between them, as in Fig. As shown in Figure 1, a game exists. For example, the stop section 50b and the high-speed shaft 12 are formed as a single piece. However, the configuration is not limited to this, and the stop section 50b and the high-speed shaft 12 can be provided as separate components.

[0036] The compressor housing element 23 is essentially tubular and has a compressor through-hole 51 extending in the axial direction. The compressor housing element 23 includes a first end surface 23b in the axial direction. The first end surface 23b of the compressor housing element 23 faces the first end surface 20a in the axial direction of the housing 20. The compressor through-hole 51 has an opening in the first end surface 23b. This opening serves as an intake port 23a.

[0037] The compressor housing element 23 includes a second end surface 23c, which faces the first end surface 23b of the compressor housing element 23 in the axial direction. The second plate surface 26b of the plate section 26 is located on the side opposite the first plate surface 26a. The compressor housing element 23 and the second part 25 are joined such that the second end surface 23c and the second plate surface 26b abut each other. In this case, the inner surface of the compressor through-hole 51 and the second plate surface 26b of the plate section 26 form an impeller chamber S3. The impeller chamber S3 houses an impeller 52, which serves as the compressor unit 15.

[0038] This means that the through-hole 51 of the compressor defines the impeller chamber S3 as well as the intake opening 23a. The intake opening 23a is connected to the impeller chamber S3.

[0039] That is, the compressor housing element 23 can also be considered as an element that interacts with the plate section 26 to define the impeller chamber S3, and the plate section 26 can also be considered as a wall that separates the gearbox chamber S2 and the impeller chamber S3 from each other.

[0040] The compressor through-hole 51 has a constant diameter from the intake opening 23a to an intermediate position in the axial direction. The diameter then gradually increases from the intermediate position towards the second plate surface 26b of the plate section 26, so that the compressor through-hole 51 essentially has the shape of a truncated cone. Thus, the impeller chamber S3, which is defined by the inner surface of the compressor through-hole 51, essentially has the shape of a truncated cone.

[0041] The impeller 52 is tubular and has a diameter that gradually decreases from a proximal end face 52a to a distal end face 52b. The impeller 52 has an entry hole 52c that extends in the direction of the impeller 52's axis of rotation. The high-speed shaft 12 can be guided through the entry hole 52c. The impeller 52 is attached to the high-speed shaft 12 such that it rotates together with the high-speed shaft 12, with the portion of the high-speed shaft 12 that projects into the through-hole 51 of the compressor being inserted into the entry hole 52c. As the high-speed shaft 12 rotates, the impeller 52 also rotates, thus compressing the fluid drawn in through the intake opening 23a.

[0042] The centrifugal compressor 10 also includes a diffuser channel 53, into which the fluid compressed by the impeller 52 flows, and an outlet chamber 54, into which the fluid that has passed through the diffuser channel 53 flows. The diffuser channel 53 is bounded by the second plate surface 26b of the plate section 26 and a surface of the compressor housing element 23 that faces the second plate surface 26b. In particular, the diffuser channel 53 is defined by the second plate surface 26b and a surface that is connected to the open end of the compressor through-hole 51 on the side corresponding to the second plate surface 26b. The diffuser channel 53 is arranged on the outside of the impeller chamber S3 in the radial direction R and has an annular shape (in particular a circular shape) to surround the impeller 52 (the impeller chamber S3). The outlet chamber 54 is ring-shaped and arranged on the outside of the diffuser channel 53 in radial direction R.The impeller chamber S3 and the outlet chamber 54 are connected by the diffuser channel 53. The fluid compressed by the impeller 52 flows through the diffuser channel 53 to be further compressed and flows to the outlet chamber 54 to be expelled from the outlet chamber 54.

[0043] Gearbox 14 will now be described.

[0044] The gearbox 14 of the present embodiment includes a high-speed shaft 12 and is a speed increaser that increases the rotational speed of the low-speed shaft 11 and transmits it to the high-speed shaft 12. The gearbox 14 is, for example, of the type of a traction drive (friction roller drive).

[0045] As in Fig. As shown in Figure 1, the gearbox 14 comprises a plate-shaped base section 61, which is attached to the second end section 11b of the low-speed shaft 11, and an annular section 62, which is attached to the opposite ends of the base section 61. The base section 61 and the annular section 62 are housed in the gearbox housing element 22 (in other words, in the gearbox chamber S2). The base section 61 and the annular section 62 rotate when the low-speed shaft 11 rotates.

[0046] The ring section 62 is made of metal, for example. The ring section 62 has an axial direction that coincides with the direction of the axis of rotation Z and extends from the base section 61 in the direction of the plate section 26. Viewed in the direction of the axis of rotation of the ring section 62, the ring section 62 has a ring shape (in particular a circular shape) and has an inner circumferential surface 63 and an outer circumferential surface 64. In the present embodiment, the diameter of the inner circumferential surface 63 of the ring section 62 is constant in the direction of the axis of rotation of the ring section 62 and is larger than the diameter of the second end section 11b of the low-speed shaft 11.

[0047] In the present embodiment, a ring element 60 is connected to the low-speed shaft 11 such that the axis of rotation of the base section 61 (the axis of rotation of the ring element 60) and the axis of rotation of the low-speed shaft 11 coincide. In this case, the axis of rotation of the ring section 62 also coincides with the axis of rotation of the low-speed shaft 11. The inner and outer diameters of the ring section 62 are diameters with a center point that coincides with the axis of rotation of the low-speed shaft 11.

[0048] The direction of rotation of the low-speed shaft 11, the direction of rotation Z of the high-speed shaft 12, and the direction of rotation of the ring section 62 coincide. Therefore, the direction of rotation Z of the high-speed shaft 12 can be referred to as the direction of rotation of the ring section 62 or as the direction of rotation of the low-speed shaft 11. For clarity, the direction of rotation of the ring section 62 is simply referred to as the direction of rotation M. The direction of rotation M corresponds to a circumferential direction of the high-speed shaft 12.

[0049] The high-speed wave 12 is partially located on the inside of the ring section 62. As in Fig. As shown in Figure 2, the gearbox includes 14 rollers 71 to 73, which are positioned between the high-speed shaft 12 and the ring section 62 to contact both the inner circumferential surface 63 of the ring section 62 and an outer circumferential surface 12a of the high-speed shaft 12. The rollers 71 to 73 are housed in the gearbox housing element 22 (in other words, in the gearbox chamber S2).

[0050] Rollers 71 to 73 are made of metal, for example. In particular, rollers 71 to 73 are made of the same metal as the high-speed shaft 12 and the ring element 60 (the ring section 62). For example, rollers 71 to 73 are made of iron or an iron alloy. Oil is supplied to the high-speed shaft 12, the ring section 62, and rollers 71 to 73.

[0051] The rollers 71 to 73 are columnar / cylindrical. The direction of rotation of the rollers 71 to 73 coincides with the direction of rotation Z of the high-speed shaft 12. The direction of rotation Z can therefore be referred to as the direction of rotation of the rollers 71 to 73. The rollers 71 to 73 are arranged circumferentially around the high-speed shaft 12 and surround it.

[0052] In the present embodiment, a first roller 71 and a second roller 72 of the rollers 71 to 73 are fixed rollers rotatably mounted on the gear housing element 22. The first roller 71 and the second roller 72 are mounted on the gear housing element 22 such that they do not move in the direction of rotation M, independent of the rotation of the ring section 62 (in other words, the rotation of the low-speed shaft 11). In contrast, a third roller 73 is a movable roller that moves in the direction of rotation M of the ring section 62 in response to the rotation of the ring section 62 (in other words, the rotation of the low-speed shaft 11).

[0053] As in Fig. 1 and Fig. As shown in Figure 2, the gearbox 14 includes a support element 80 which interacts with the gearbox housing element 22 (in particular the second part 25) to rotatably support / mount the rollers 71 to 73. The support element 80 is arranged within the ring section 62.

[0054] The support element 80 contains a disk-shaped base support section 81, which is slightly smaller than the ring section 62, and three support sections 82 to 84 extending from the base support section 81.

[0055] The base support section 81 is located at a position where its plate surface is opposite a plate surface of the base section 61 of the ring element 60. The base support section 81 is arranged such that it is opposite the plate section 26 in the rotational axis direction Z. The base support section 81 includes an opposing plate surface 81a, which is opposite the first plate surface 26a of the plate section 26.

[0056] The three support sections 82 to 84 extend from the opposite plate surface 81a towards the plate section 26 and occupy three spaces / places, each defined by the inner circumferential surface 63 of the ring section 62 and the outer circumferential surfaces of two adjacent rollers 71 to 73.

[0057] As in the Fig. 1 and Fig. As shown in Figure 2, the support sections 82 to 84 each have a threaded hole 92 into which a bolt 91 can be screwed. The bolt 91 acts as a fastener. The plate section 26 includes, in its first plate surface 26a, threaded holes 93 that correspond to the threaded holes 92. The threaded holes 93 are continuously connected to the threaded holes 92. The support sections 82 to 84 are arranged at positions where the threaded holes 92 and the threaded holes 93 are continuously connected to each other, and the distal end sections of the support sections 82 to 84 are adjacent to the first plate surface 26a. In this state, the bolts 91 are screwed into the threaded holes 92 and the threaded holes 93 to fasten the support sections 82 to 84 to the plate section 26.

[0058] The first roller 71, the second roller 72, and the third roller 73 are arranged between the plate section 26 and the base support section 81. The support sections 82 to 84 are configured such that the first roller 71 and the second roller 72 do not move in the circumferential direction of the ring section 62 when the ring section 62 moves, and that the third roller 73 can move in the direction of rotation M.

[0059] In particular, as in Fig. As shown in Figure 2, the first support section 82 has a first curved surface 82a, which is opposite an outer circumferential surface 71a of the first roller 71 with a first clearance Cr1 between them, and a second curved surface 82b, which is opposite an outer circumferential surface 72a of the second roller 72 with a first clearance Cr1 between them. The first curved surface 82a extends along the outer circumferential surface 71a of the first roller 71. The second curved surface 82b extends along the outer circumferential surface 72a of the second roller 72.

[0060] The second support section 83 has a third curved surface 83a, which is opposite the outer circumferential surface 72a of the second roller 72 with a first clearance Cr1 between them, and a fourth curved surface 83b, which is opposite an outer circumferential surface 73a of the third roller 73 with a second clearance Cr2 between them. The second clearance Cr2 is larger than the first clearance Cr1. The third curved surface 83a extends along the outer circumferential surface 72a of the second roller 72. The fourth curved surface 83b extends along the outer circumferential surface 73a of the third roller 73.

[0061] The third support section 84 has a fifth curved surface 84a, which is opposite the outer circumferential surface 73a of the third roller 73 with a first clearance Cr1 between them, and a sixth curved surface 84b, which is opposite the outer circumferential surface 71a of the first roller 71 with a first clearance Cr1 between them. The fifth curved surface 84a extends along the outer circumferential surface 73a of the third roller 73. The sixth curved surface 84b extends along the outer circumferential surface 71a of the first roller 71.

[0062] In the embodiment described above, the second clearance Cr2 exists between the outer circumferential surface 73a of the third roller 73 and the fourth curved surface 83b. This clearance is larger than the first clearance Cr1, allowing the third roller 73 to move in the direction of rotation M. In particular, the third roller 73 can move between a first position and a second position, which is spaced apart from the first position in the direction of rotation M. In the present embodiment, the first position is one in which the outer circumferential surface 73a of the third roller 73 and the fifth curved surface 84a are opposite each other with the first clearance Cr1 between them, and the second position is one in which the outer circumferential surface 73a of the third roller 73 and the fourth curved surface 83b are opposite each other with the first clearance Cr1 between them.

[0063] On the other hand, the first game Cr1, which is smaller than the second game Cr2, is located between the first and second rollers 71, 72 and the support sections 82 to 84. The first game Cr1 serves to prevent rollers 71, 72 from sliding on the support sections 82 to 84.

[0064] As in Fig. As shown in Figure 2, the rollers 71 to 73 are held in the radial direction R by the ring section 62 and the high-speed shaft 12 from opposite sides and pressed inwards in the radial direction R by the ring section 62. This prevents the rollers 71 to 73, including the third roller 73, from moving in the radial direction R.

[0065] The diameters of the rollers 71 to 73 (the dimensions of the rollers 71 to 73 in directions intersecting the direction of the axis of rotation Z) are set such that they are larger than the diameter of the high-speed shaft 12. The diameters of the rollers 71 to 73 are set such that they are smaller than the radius of the inner circumferential surface 63 of the ring section 62, so that the rollers 71 to 73 can be arranged in the ring section 62.

[0066] As in Fig. As shown in Figure 2, the diameter of the second roller 72 differs from the diameter of the first roller 71 and the third roller 73. In particular, the diameter of the second roller 72 is larger than the diameter of the first roller 71 and the third roller 73. Thus, the high-speed shaft 12, which is supported against the rollers 71 to 73, and the annular ring section 62 (in other words, the low-speed shaft 11) are eccentric to each other. Specifically, the axis of rotation of the high-speed shaft 12 and the axis of rotation of the annular section 62 are not aligned.

[0067] As in Fig. As shown in Figure 1, the high-speed shaft 12 has two flanges 96 extending radially outwards from the outer circumferential surface 12a in the direction R. The flanges 96 are spaced apart from each other in the direction of rotation Z and are arranged on opposite sides. The rollers 71 to 73 are held by the two flanges 96 on opposite sides in the direction of rotation Z. This limits the displacement in the direction of rotation Z between the high-speed shaft 12 and the rollers 71 to 73. For example, when a thrust force in the direction of rotation Z is generated by the rotation of the impeller 52, the end face of the first roller 71 on the side facing the impeller 52 in the direction of rotation Z and the flange 96 on the side facing the impeller 52 touch, thus restricting further movement.

[0068] The distance in the Z-direction of rotation between the flanges 96 is slightly larger than the dimensions of the rollers 71 to 73 in the Z-direction of rotation. Accordingly, there are clearances between the flanges 96 and the end faces of the rollers 71 to 73 in the Z-direction of rotation into which oil can flow.

[0069] The base support section 81 has a through hole 81b in a central section, which is slightly larger than the flanges 96. The flange 96 on the side closer to the base section 61 is located in the through hole 81b.

[0070] The flange 96 on the side facing the impeller 52 is located on the side of the stop section 50b opposite the sealing element 50a. In the present embodiment, the flanges 96 are shorter in the radial direction R than the stop section 50b.

[0071] As in the Fig. 1 and Fig. As shown in Figure 3, the centrifugal compressor 10 (in particular the gearbox 14) contains rolling bearings / roller bearings 101 to 106 which rotatably mount the rollers 71 to 73 in the gearbox housing element 22. The rolling bearings 101 to 106 are radial bearings. In the present embodiment, the rolling bearings 101 to 106 correspond to the “radial bearings”.

[0072] The rolling bearings 101 to 106 have plate bearings 101 to 103 attached to the plate section 26, and support bearings 104 to 106 attached to the support element 80 (in particular, the base support section 81). As already described, the support element 80, which has the base support section 81, is attached to the plate section 26, which is a section of the gearbox housing element 22. Thus, the support bearings 104 to 106, which are attached to the base support section 81, can be considered to be attached to the gearbox housing element 22 by the support element 80.

[0073] The plate bearings 101 to 103, for example, have a round shape. The plate bearings 101 to 103 are, for example, rolling bearings, each comprising inner rings 101a to 103a, outer rings 101b to 103b, and rolling elements 101c to 103c positioned between the inner rings 101a to 103a and the outer rings 101b to 103b. The inner rings 101a to 103a rotate relative to the outer rings 101b to 103b when the rollers 71 to 73 rotate. That is, the outer rings 101b to 103b are less likely to rotate than the inner rings 101a to 103a when the rollers 71 to 73 rotate.

[0074] The plate bearings 101 to 103 each include outer circumferential surfaces 101d to 103d. The outer circumferential surfaces 101d to 103d of the plate bearings 101 to 103 are the outer circumferential surfaces of the outer rings 101b to 103b. The outer diameter of the plate bearings 101 to 103 is the outer diameter of the outer rings 101b to 103b. The inner diameter of the plate bearings 101 to 103 is the inner diameter of the inner rings 101a to 103a. Since the design of the support bearings 104 to 106 is identical to that of the plate bearings 101 to 103, their description is omitted.

[0075] As in the Fig. 1, Fig. 3 and Fig. As shown in Figure 4, the rollers 71 to 73 each have projections 111 to 116 on their end faces opposite the axis of rotation Z. The projections are each column-shaped and located in the center of the respective end face. The projections 111 to 116 include plate projections 111 to 113, which are located on the side closer to the plate section 26, and support projections 114 to 116 on the side closer to the support base section 81. For illustrative purposes, the plate projections 111 to 113 are shown in Fig. 4 shown hatched.

[0076] The plate section 26, which is a section of the gear housing element 22, has plate bearing receiving chambers S11 to S13 that receive the plate bearings 101 to 103. The plate bearings 101 to 103 are arranged in the plate bearing receiving chambers S11 to S13, while rotatably supporting the plate projections 111 to 113. The plate projections 111 to 113 are fitted into the inner rings 101a to 103a of the plate bearings 101 to 103.

[0077] Similarly, the base support section 81 of the support element 80 has three bearing receptacles that accommodate the bearings 104 to 106. The bearings 104 to 106 are arranged in the bearing receptacles, while they rotatably support the support projections 114 to 116. Accordingly, the support projections 114 to 116 are supported on the base support section 81 by the bearings 104 to 106.

[0078] In the configuration described above, the rollers 71 to 73 are rotatably mounted on the gearbox housing element 22 by the roller bearings 101 to 106. In the present embodiment, the third plate bearing 103 corresponds to the "movable bearing", and the third plate bearing receiving chamber S13 corresponds to the "receiving chamber for the movable roller".

[0079] Next, the chambers accommodating the roller bearings 101 to 106 and the roller bearings 101 to 106 themselves are described. The structures of the support bearings 104 to 106 and the support bearing mounting chambers are identical to those of the plate bearings 101 to 103 and the plate bearing mounting chambers S11 to S13. Therefore, the structures of the plate bearings 101 to 103 and the plate bearing mounting chambers S11 to S13 are described, and a description of the support bearings 104 to 106 and the support bearing mounting chambers is omitted.

[0080] The plate bearing chambers S11 to S13 are arranged on the outside of the high-speed shaft 12 in the radial direction R of the high-speed shaft 12. In particular, the plate section 26, as already described, has the plate through-hole 26c through which the high-speed shaft 12 passes, and the plate bearing chambers S11 to S13 are arranged around the plate through-hole 26c. For example, the plate bearing chambers S11 to S13 are arranged at equal intervals (120°) around the plate through-hole 26c.

[0081] For example, in Fig. As shown in Figure 4, the plate bearing receiving chambers S11 to S13 are each continuous with the plate through-hole 26c, so that the plate bearings 101 to 103 received in the plate bearing receiving chambers S11 to S13 are partially arranged in the plate through-hole 26c. The flange 96 and the stop section 50b are located as shown in Figure 4. Fig. 5 shown, in the plate through-hole 26c at a position on the inside of the plate bearing receiving chambers S11 to S13 in the radial direction R.

[0082] Furthermore, as already described, there is a clearance between the stop section 50b and the inner surface of the plate through-hole 26c in the radial direction R, and the flange 96 is shorter than the stop section 50b in the radial direction R. Accordingly, there is clearance between the plate bearings 101 to 103 and the stop section 50b and the flange 96, so that the plate bearings 101 to 103 do not collide with the stop section 50b or the flanges 96.

[0083] Viewed in the direction of the axis of rotation Z, sections of the plate bearings 101 to 103, which are located in the plate through-hole 26c, overlap with the sealing element 50a. That is, in the present embodiment, the plate bearings 101 to 103 and the sealing element 50a are displaced relative to each other in the direction of rotation Z. Furthermore, the plate bearings 101 to 103 are arranged so that they are located relatively close to the high-speed shaft 12, so that, viewed in the direction of the axis of rotation Z, they partially overlap with the sealing element 50a. This reduces the size of the gearbox 14 in the radial direction R. In addition, at least one of the stop section 50b and the flange 96 (both in the present embodiment) is arranged between the plate bearings 101 to 103 and the high-speed shaft 12.This allows the space on the inside of the plate bearings 101 to 103 to be used effectively in the radial direction R, thereby reducing the size of the gearbox 14 in the direction of the axis of rotation Z.

[0084] The plate bearing receiving chambers S11 to S13 are now described.

[0085] As in Fig. 3 and Fig. As shown in Figure 4, plate section 26 includes plate recesses 121 to 123 in the first plate surface 26a and plate extension sections 131 to 133 extending from the first plate surface 26a. The plate bearing receiving chambers S11 to S13 are defined by the plate recesses 121 to 123 and the plate extension sections 131 to 133.

[0086] With reference to the Fig. 4 and Fig. 5 describes the first plate recess 121 and the first plate extension section 131, which define the first plate bearing receiving chamber S11.

[0087] As in Fig. As shown in Figure 4, the first plate recess 121 has the same shape as the outer shape of the first plate bearing 101. In particular, the first plate recess 121, viewed in the direction of the axis of rotation Z, has a circular shape in accordance with the disk-shaped first plate bearing 101. The diameter of the first plate recess 121 is slightly larger than the outer diameter of the first plate bearing 101. The first plate recess 121 opens into the plate through-hole 26c. The first plate recess 121 and the plate through-hole 26c are thus continuously connected.

[0088] As in the Fig. 4 and Fig. As shown in Figure 5, the first plate recess 121 contains a first bottom surface 141 and a first recess side surface 142.

[0089] In general, the first base surface 141 has a circular shape. The diameter of the first plate recess 121 can also be considered as the diameter of the first base surface 141.

[0090] In the present embodiment, the first floor surface 141 has a stepped structure. In particular, the first floor surface 141 comprises a first outer floor section 141a extending along the first recess side surface 142, and a first inner floor section 141b located on the inside of the first outer floor section 141a and recessed relative to the first outer floor section 141a.

[0091] The first outer bottom section 141a has the shape of a ring (in particular a circular shape) which has a specific first width W1 and extends in the circumferential direction of the first recess side surface 142. In other words, the first outer bottom section 141a extends from the first recess side surface 142 towards the center of the first bottom surface 141 by the first width W1. In the present embodiment, the first outer bottom section 141a has the shape of a C, which opens towards the plate through-hole 26c.

[0092] The first inner soil section 141b is surrounded by the first outer soil section 141a. The first inner soil section 141b is essentially circular when viewed in the direction of the axis of rotation Z.

[0093] In the present embodiment, the outer ring 101b of the first plate bearing 101 is supported by, as shown in Fig. As shown in Figure 5, the first outer bottom section 141a is in contact with the first outer bottom section 141a. In contrast, the inner ring 101a of the first plate bearing 101 does not contact the first outer bottom section 141a. More precisely, the inner ring 101a of the first plate bearing 101 and the first inner bottom section 141b are positioned opposite each other with a gap between them. That is, the first outer bottom section 141a of the present embodiment is a contact section that touches the outer ring 101b, but not the inner ring 101a.

[0094] In particular, the first width W1 is wider than the thickness of the outer ring 101b of the first plate bearing 101. The thickness of the outer ring 101b can also be considered as the dimension of the outer ring 101b in the radial direction. On the other hand, the first width W1 is set such that it is smaller than the total thickness of the first plate bearing 101, such that the inner edge of the first outer bottom section 141a lies on the outside of the outer circumferential surface of the inner ring 101a.

[0095] The first recess side surface 142 extends from the first base surface 141 (in particular from the first outer base section 141a) and has the shape of a C, opening towards the plate through hole 26c. The diameter of the first plate recess 121 can also be considered as the diameter of the first recess side surface 142.

[0096] The first plate extension section 131 is located at the perimeter of the first plate recess 121. The first plate extension section 131 includes a first extension side surface 143, which is connected to the first recess side surface 142. The first recess side surface 142 and the first extension side surface 143 are flush with each other.

[0097] The first plate bearing receiving chamber S11 of the present embodiment is defined by the first bottom surface 141 and a first receiving side surface 144. That is, the gearbox housing element 22 includes the first bottom surface 141 and the first receiving side surface 144 as surfaces that define the first plate bearing receiving chamber S11.

[0098] In the present embodiment, the first receiving side surface 144 is formed by the side surfaces 142 and 143. The first receiving side surface 144 extends in the direction of the axis of rotation Z from the first base surface 141. The first receiving side surface 144 has the shape of a C, which opens in the direction of the through-hole 26c of the plate. The first outer base section 141a extends along the first receiving side surface 144.

[0099] As in the Fig. 4 and Fig. As shown in Figure 5, the first receiving surface 144, viewed in the direction of the axis of rotation Z, is slightly larger than the outer circumferential surface 101d of the first plate bearing 101. The first plate bearing 101 is received in the first plate bearing receiving chamber S11 with a bearing clearance Cr11 between the first plate bearing 101 and the first receiving surface 144. The bearing clearance Cr11 is dimensioned to allow for displacement due to dimensional errors and is smaller than the first clearance Cr1. This prevents the first plate bearing 101 from moving in the direction of rotation M by contacting the first receiving surface 144. In other words, the first receiving surface 144 is considered to surround the first plate bearing 101 in order to prevent the first plate bearing 101 from moving.That is, the first plate bearing receiving chamber S11 of the present embodiment can be regarded as receiving the first plate bearing 101, whereby the first plate bearing 101 is prevented from moving in the direction of rotation M.

[0100] Since the plate recess 122 and the second plate extension section 132, which define the second plate bearing receiving chamber S12, are similar to the first plate recess 121 and the first plate extension section 131, a detailed description is omitted.

[0101] In the present embodiment, the first plate bearing 101 and the second plate bearing 102 correspond to the “fixed bearings”, and the first plate bearing receiving chamber S11 and the second plate bearing receiving chamber S12 correspond to the “fixed bearing receiving chambers”. The first bottom surface 141 corresponds to the “fixed bearing receiving bottom surface”, and the first receiving side surface 144 corresponds to the “fixed bearing receiving side surface”.

[0102] Next, with reference to the Fig. 6 to 9 describe the third plate recess 123 and the third plate extension section 133, which define the third plate bearing receiving chamber S13. Fig. Figure 6 is a front view of the third plate bearing 103 in a state in which the third roller 73 is in the first position, and Fig. Figure 7 is a cross-sectional view along line 7-7 in Fig. 6. Fig. Figure 8 is a front view of the third plate bearing 103 in a state in which the third roller 73 is in an intermediate position between the first position and the second position. Fig. Figure 9 is a front view of the third plate bearing 103 in a state in which the third roller 73 is in the second position.

[0103] As in the Fig. 6 and Fig. As shown in Figure 7, the third plate recess 123 is configured to receive the third plate bearing 103 such that the third plate bearing 103 is movable in the direction of rotation M. For example, the third plate recess 123 has an oval shape whose longitudinal direction coincides with the direction of rotation M (in other words, a tangential direction to the direction of rotation M). The third plate recess 123 opens to the plate through-hole 26c and is continuous with the plate through-hole 26c.

[0104] The third plate recess 123 contains a third bottom surface 151 and a third recess side surface 152 extending from the third bottom surface 151.

[0105] The third base surface 151 is shaped such that it has an oval form, the longitudinal direction of which coincides with the direction of rotation M. Like the third base surface 151, the third recess side surface 152 also has an oval form, the longitudinal direction of which, viewed in the direction of rotation Z, coincides with the direction of rotation M. The third recess side surface 152 does not have a completely closed ring shape, but opens towards the plate through-hole 26c.

[0106] The third plate extension section 133 is located at the perimeter of the third plate recess 123. The third plate extension section 133 includes a third extension side surface 153, which is connected to the third recess side surface 152. The third recess side surface 152 and the third extension side surface 153 are flush with each other.

[0107] The third plate bearing receiving chamber S13 of the present embodiment is defined by the third bottom surface 151 and a third receiving side surface 154. That is, the gearbox housing element 22 has the third bottom surface 151 and the third receiving side surface 154 as surfaces that define the third plate bearing receiving chamber S13.

[0108] In the present embodiment, the third receiving side surface 154 is a surface extending from the third base surface 151 in the direction of the axis of rotation Z. The third receiving side surface 154 includes the third recess side surface 152 and the third extension side surface 153. In the present embodiment, the third base surface 151 corresponds to the "base surface that defines the movable bearing receiving chamber," and the third receiving side surface 154 corresponds to the "receiving side surface that defines the movable bearing receiving chamber."

[0109] The third receiving surface 154 has an inner opening 155 that opens towards the plate through-hole 26c. Accordingly, the third receiving surface 154 does not have a completely closed ring shape, but opens inwards in the radial direction R. The inner opening 155 opens inwards in the radial direction R. The third plate bearing receiving chamber S13 and the plate through-hole 26c are connected to each other by the inner opening 155.

[0110] The third plate bearing 103 is housed in the third plate bearing receiving chamber S13 in such a way that it is movable in the direction of rotation M.

[0111] As in the Fig. 6 and Fig. As shown in Figure 9, the third receiving surface 154 includes a first support surface 161 and a second support surface 162. When the third roller 73 is in the first position, the first support surface 161 supports the third plate bearing 103. When the third roller 73 is in the second position, the second support surface 162 supports the third plate bearing 103.

[0112] When the third roller 73 is in the first position, the first support surface 161 contacts the third bearing plate 103 to support it. The first support surface 161 is, for example, a curved surface whose curvature is less than that of the outer circumferential surface 103d of the third bearing plate 103. The first support surface 161 is recessed in a direction opposite to the direction of rotation M. When the third roller 73 is in the first position, the first support surface 161 contacts the third bearing plate 103 in the direction of rotation M. This prevents the third roller 73 from moving beyond the first position in the direction opposite to the direction of rotation M. In other words, the first support surface 161 is designed to contact the third bearing plate 103 in such a way that the third roller 73 is held in the first position.

[0113] In the present embodiment, the first support surface 161 is, for example, an arcuate surface. Since the inner opening 155 is provided, the central angle of the first support surface 161 is slightly less than 180°. However, the central angle of the first support surface 161 can be changed to any angle greater or less than 180°.

[0114] The first support surface 161 includes a first inner end section 161a, which is connected to the inner surface of the plate through-hole 26c, and a first outer end section 161b, which is further away from the plate through-hole 26c (in other words, from the high-speed shaft 12) than the first inner end section 161a. In a situation where the third roller 73 is in the first position, the first outer end section 161b is arranged in a position spaced radially R away from the third plate bearing 103 and located on its outer surface.

[0115] The second support surface 162 is spaced from the first support surface 161 in the direction of rotation M. When the third roller 73 is in the second position, the second support surface 162 contacts the third plate bearing 103 to support it. The second support surface 162 is, for example, a curved surface whose curvature is less than that of the outer circumferential surface 103d of the third plate bearing 103. The second support surface 162 is recessed in the direction of rotation M. When the third roller 73 is in the second position, the second support surface 162 contacts the third plate bearing 103 from the opposite direction to the direction of rotation M. This prevents the third roller 73 from moving further in the direction of rotation M than to the first position. In other words, the second support surface 162 is designed to contact the third plate bearing 103 in such a way that the third roller 73 is held in the second position.

[0116] This means that in the present embodiment, the first support surface 161 and the second support surface 162 are opposite each other and are curved surfaces that are recessed away from each other. The third roller 73 is moved from the first position to the second position within a range of motion.

[0117] In the present embodiment, the second support surface 162 is, for example, an arcuate surface. Since the inner opening 155 is provided, the central angle of the second support surface 162 is less than 180°. However, the central angle of the second support surface 162 can be changed to any angle greater or less than 180°.

[0118] The second support surface 162 includes a second inner end section 162a, which is connected to the inner surface of the plate through-hole 26c, and a second outer end section 162b, which is further away from the plate through-hole 26c (in other words, from the high-speed shaft 12) than the second inner end section 162a. In a situation where the third roller 73 is in the second position, the second outer end section 162b is arranged in a position spaced radially R away from the third plate bearing 103 and located on its outer surface.

[0119] Due to the difference in curvature between the first support surface 161 and the outer circumferential surface 103d of the third plate bearing 103, there is a clearance in the radial direction R between the first support surface 161 and the third plate bearing 103. Likewise, there is a clearance in the radial direction R between the second support surface 162 and the third plate bearing 103.

[0120] As in the Fig. As shown in Figures 6 to 9, the gear housing element 22 has a specified space Cr12 located on the outside of the third plate bearing 103 in the radial direction R when the third roller 73 moves from the first position to the second position. In the present embodiment, the specified space Cr12 is provided within the third plate bearing receiving chamber S13.

[0121] In the present embodiment, the third receiving surface 154 includes a separated surface 163 that is separated from the third plate bearing 103 (in particular from the outer circumferential surface 103d of the third plate bearing 103). The separated surface 163 is located on the outside of the third plate bearing 103 and separated from it in the radial direction R. Specifically, the separated surface 163 is located on the outside in the radial direction R of the movement path of the third plate bearing 103 when the third roller 73 moves from the first position to the second position. The specified space Cr12 is, regardless of the position of the third plate bearing 103, a clearance between the separated surface 163 and the third plate bearing 103.In the present embodiment, the specified space Cr12 corresponds to the “clearance between the separated surface and the outer circumferential surface of the movable bearing.”

[0122] In the present embodiment, the specified space Cr12 is larger than, for example, the bearing clearance Cr11. In particular, the width W12 of the specified space Cr12 is larger than the width W11 of the bearing clearance Cr11.

[0123] The width W11 of the bearing clearance Cr11 varies depending on the displacement of the first plate bearing 101. Likewise, the width W12 of the specified space Cr12 varies depending on the position of the third plate bearing 103. In this case, the minimum value of the width W12 of the specified space Cr12 (in other words, the shortest distance between the separated surface 163 and the third plate bearing 103) is preferably greater than the maximum value of the width W11 of the bearing clearance Cr11 (the longest distance between the first plate bearing 101 and the first receiving side surface 144). However, the present disclosure is not limited to this, and the minimum value of the width W12 of the specified space Cr12 may be greater than the minimum value of the width W11 of the bearing clearance Cr11. Alternatively, the maximum value of the width W12 of the specified space Cr12 can be greater than the maximum value of the width W11 of the bearing clearance Cr11.

[0124] In the present embodiment, the separated surface 163 is located on the outside in the radial direction R of the inner opening 155 of the third receiving surface 154 with the third plate bearing 103 in between. The separated surface 163 extends in the direction in which the support surfaces 161, 162 are opposite each other (in other words, in the direction of rotation M) in order to connect the outer end sections 161b, 162b of the support surfaces 161, 162.

[0125] As previously described, the third roller 73 is held by the ring section 62 and the high-speed shaft 12 and pressed by the ring section 62 in the direction of the high-speed shaft 12. Accordingly, it is unlikely that the third roller 73 will move outwards in the radial direction R. Furthermore, the third roller 73 and the third plate bearing 103 are designed to move together. Therefore, it is unlikely that the third plate bearing 103 will move in the direction of the separated surface 163, even though the specified space Cr12 exists.

[0126] As for example in Fig. As shown in Figure 6, a section of the third plate bearing 103 is located on the inside in the radial direction R of the plate through-hole 26c through the inner opening 155. The section of the third plate bearing 103 located in the plate through-hole 26c is separated from the high-speed shaft 12, the stop section 50b, and the flanges 96. This prevents the section of the third plate bearing 103 from sliding against other components on the inside in the radial direction R.

[0127] That is, in the present embodiment, the range of movement of the third roller 73 from the first position to the second position includes a certain area in which the third roller 73 is not supported in the radial direction R by the gear housing element 22 with the third plate bearing 103 in between, but by being held between the ring section 62 and the high-speed shaft 12.

[0128] In the specified area, the specified space Cr12 exists as a clearance between the separated surface 163 and the third plate bearing 103 (in particular, the outer circumferential surface 103d of the third plate bearing 103), such that it is unlikely that the third plate bearing 103 contacts the separated surface 163. In other words, the specified area of ​​the present embodiment can be considered as an area in which the specified space Cr12 exists between the separated surface 163 and the third plate bearing 103.

[0129] As in Fig. As shown in Figure 7, the third bottom surface 151 in the present embodiment includes a stepped structure and comprises a third outer bottom section 151a extending along the third receiving side surface 154 (in particular the third recess side surface 152) and a third inner bottom section 151b located on the inside of the third outer bottom section 151a and set back with respect to the third outer bottom section 151a.

[0130] The third outer bottom section 151a has the form of a ring having a specific third width W3 and extending in the circumferential direction of the third receiving side surface 154. In other words, the third outer bottom section 151a extends from the third receiving side surface 154 by the third width W3 towards the center of the third bottom surface 151. In the present embodiment, the third outer bottom section 151a is formed such that it has the shape of an oval ring whose longitudinal direction coincides with the direction of rotation M. The third outer bottom section 151a opens towards the plate through-hole 26c.

[0131] In the present embodiment, the outer ring 103b of the third plate bearing 103 is supported by the third outer base section 151a. On the other hand, the inner running ring 103a of the third plate bearing 103 is not supported by the third outer base section 151a.

[0132] In particular, the third width W3 is wider than the thickness of the outer race 103b of the third plate bearing 103. Furthermore, the third width W3 is set such that it is shorter than the overall thickness of the third plate bearing 103, such that the inner edge of the third outer base section 151a lies on the outside of the outer circumferential surface of the inner race 103a. Accordingly, the inner race 103a of the third plate bearing 103 and the third inner base section 151b are positioned opposite each other with a clearance between them.

[0133] In the present embodiment, the third width W3 is defined to correspond to the specified space Cr12. Specifically, the third width W3 is defined to be wider than the sum of the thickness of the outer race 103b and the width W12 of the specified space Cr12. In other words, the third outer bottom section 151a extends inward from the separated surface 163 in the radial direction R by a length longer than the width W12 of the specified space Cr12 to contact the outer race 103b.

[0134] The third inner bottom section 151b is set back from the third plate bearing 103 with respect to the third outer bottom section 151a. The third inner bottom section 151b is surrounded by the third outer bottom section 151a. The third inner bottom section 151b is oval when viewed in the direction of the axis of rotation Z. The third inner bottom section 151b abuts the inner surface of the plate through-hole 26c. In the present embodiment, the third outer bottom section 151a corresponds to the "contact section" and the "outer bottom section," and the third inner bottom section 151b corresponds to the "inner bottom section."

[0135] Although not shown, the plate through-hole 26c is supplied with oil. That is, the gearbox 14 of the present embodiment includes a feed / supply mechanism that feeds oil into the plate through-hole 26c. Accordingly, the sealing element 50a is supplied with oil. The specific design of the feed mechanism is not particularly limited.

[0136] Since, as already described, the plate through-hole 26c is continuous with the plate bearing chambers S11 to S13, the oil supplied to the plate through-hole 26c is also supplied to the plate bearing chambers S11 to S13. Accordingly, oil is supplied to the plate bearings 101 to 103.

[0137] The functionality of the present embodiment will now be described.

[0138] When rollers 71 to 73 are not rotating, the third plate bearing 103 and the first support surface 161 make contact. This brings the third roller 73 into the first position. In other words, the first support surface 161 can be considered an element that positions the third roller 73 in the first position, and the first position can be considered a starting position.

[0139] On the other hand, rollers 71 to 73 rotate when the annular ring section 62 rotates during the rotation of the low-speed shaft 11. In this case, the third roller 73 moves in the direction of rotation M from the first position towards the second position. Accordingly, the third plate bearing 103 can move within the receiving chamber for the third plate bearing S13. The distance of movement of the third roller 73 varies depending on the torque. When the third roller 73 moves in the direction of rotation M, the third plate bearing 103 contacts the second support surface 162, thus positioning the third roller 73 in the second position. In other words, the second support surface 162 can be considered an element that positions the third roller 73 in the second position. When the rotation of rollers 71 to 73 stops, the third roller 73 returns to the first position.

[0140] As in the Fig. As shown in Figures 6 to 9, the range of motion of the third roller 73 from the first position to the second position includes the specified range in which the third roller 73 is not supported in the radial direction R by the gear housing element 22 with the third plate bearing 103 between it, but rather by being held between the ring section 62 and the high-speed shaft 12. Within the specified range, it is unlikely that the third plate bearing 103 and the gear housing element 22 will slide against each other.

[0141] In particular, when the third plate bearing 103 moves, when the third roller 73 moves, it is unlikely that the third plate bearing 103 and the third receiving side surface 154 (for example, the separated surface 163) will slide against each other, because of the specified space Cr12. In other words, the specified space Cr12 reduces or eliminates the sliding area between the third plate bearing 103 and the third receiving side surface 154 when the third roller 73 moves from the first position to the second position. That is, the specified space Cr12 is used to avoid or limit contact between the third plate bearing 103 and the third receiving side surface 154.

[0142] The present embodiment, which has been described above, offers the following advantages.

[0143] (1) The gearbox 14 comprises the gearbox housing element 22, the annular ring section 62, the high-speed shaft 12, the three rollers 71 to 73, and the roller bearings 101 to 106, which are radial bearings. The annular ring section 62 is arranged within the gearbox housing element 22 and is designed to rotate when the low-speed shaft 11 rotates. The high-speed shaft 12 is located on the inside of the annular section 62. The rollers 71 to 73 are arranged between the annular section 62 and the high-speed shaft 12. The rollers 71 to 73 contact both the inner circumferential surface 63 of the annular section 62 and the outer circumferential surface 12a of the high-speed shaft 12.

[0144] Rollers 71 to 73 include the third roller 73. The third roller 73 is a movable roller that moves in the direction of rotation M of the ring section 62 in response to / depending on the rotation of the ring section 62. Rollers 71 to 73 include the first roller 71 and the second roller 72. The first roller 71 and the second roller 72 are fixed rollers that do not move in the direction of rotation M of the ring section 62.

[0145] The roller bearings 101 to 106 include the third plate bearing 103. The third plate bearing 103 is a movable bearing that rotatably supports the third roller 73, which is a movable roller. The gear housing element 22 includes the first support surface 161 and the second support surface 162, which is spaced apart from the first support surface 161 in the direction of rotation M. The first support surface 161 contacts the third plate bearing 103 to constrain the third roller 73 to the first position. The second support surface 162 contacts the third plate bearing 103 to constrain the third roller 73 to the second position. The third roller 73 is moved from the first position to the second position within a range of motion.

[0146] In the configuration described above, the range of motion includes the specified area in which the third roller 73 in the radial direction R of the high-speed shaft 12 is not supported by the gear housing element 22 with the third plate bearing 103 in between, but is supported by being held between the ring section 62 and the high-speed shaft 12.

[0147] In this configuration, the range of motion from the first position to the second position includes the specified range. Therefore, when the third roller 73 moves from the first position to the second position, it is unlikely that the third plate bearing 103 and the gear housing element 22 will slide against each other. This allows for smooth movement of the third plate bearing 103 and prevents it from blocking the movement of the third roller 73 in the direction of rotation M. The configuration also limits wear caused by sliding movement between the third plate bearing 103 and the gear housing element 22.

[0148] Since the third roller 73 is supported in the specified area in the radial direction R of the high-speed shaft 12 by being held between the ring section 62 and the high-speed shaft 12, it is unlikely that the third roller 73 will be displaced in the radial direction R. Thus, it is unlikely that the high-speed shaft 12 will be displaced due to the specified area.

[0149] Furthermore, the high-speed shaft 12 is positioned by the first roller 71 and the second roller 72, which are fixed against movement in the direction of rotation. Therefore, it is unlikely that the high-speed shaft 12 will shift due to the specified space Cr12. In this way, the advantages described above are achieved while preventing any displacement of the high-speed shaft 12.

[0150] (2) The gearbox housing element 22 includes the third bottom surface 151 and the third receiving side surface 154. The third bottom surface 151 and the third receiving side surface 154 define the third plate bearing receiving chamber S13, which receives the third plate bearing 103. The third receiving side surface 154 extends from the third bottom surface 151 in the direction of the axis of rotation Z, which is the axial direction of the high-speed shaft 12, and includes the support surfaces 161, 162.

[0151] The third receiving surface 154 includes the separated surface 163, which is separated from the outer circumferential surface 103d of the third plate bearing 103. In the specified area, there is a clearance (more precisely, the specified space Cr12) between the separated surface 163 and the outer circumferential surface 103d of the third plate bearing 103.

[0152] In this configuration, the specified space Cr12, which is a clearance between the separated surface 163 and the outer circumferential surface 103d of the third plate bearing 103, prevents the separated surface 163 and the third plate bearing 103 from sliding against each other. Accordingly, the advantages described above are achieved.

[0153] (3) The first support surface 161 and the second support surface 162 are curved surfaces whose curvatures are smaller than those of the outer circumferential surface 103d of the third plate support 103. The support surfaces 161 and 162 are opposite each other. The separated surface 163 extends in the direction in which the support surfaces 161 and 162 are opposite each other and connects the first outer end section 161b, which is an end section of the first support surface 161, with the second outer end section 162b, which is an end section of the second support surface 162.

[0154] Since, in this arrangement, the first support surface 161 and the second support surface 162 are curved with a lesser curvature than the outer circumferential surface 103d of the third plate bearing 103, the radial direction R exists between the support surfaces 161, 162 and the third plate bearing 103. Accordingly, the support surfaces 161, 162 support the third plate bearing 103, even if it shifts slightly during movement.

[0155] Since the curvature of the first support surface 161 and the second support surface 162 is smaller than that of the outer circumferential surface 103d of the third plate support 103, the outer end sections 161b, 162b and the third plate support 103 are separated from each other. This separates the detached surface 163, which connects the outer end sections 161b, 162b, from the third plate support 103, thus providing the specified space Cr12. This allows the support surfaces 161, 162 to reliably support the third plate support 103 while providing the specified space Cr12.

[0156] (4) The gearbox housing element 22 includes the plate section 26, which comprises the third bottom surface 151 and the third receiving side surface 154. The plate section 26 includes the through-hole 26c through which the high-speed shaft 12 passes. The third receiving side surface 154 has the inner opening 155, which opens inwards in the radial direction R. The third plate bearing receiving chamber S13 and the plate through-hole 26c are connected to each other by the inner opening 155, and the third plate bearing 103 is partially arranged in the plate through-hole 26c.

[0157] Since the third plate bearing 103 is partially located in the plate through-hole 26c, in this configuration the third plate bearing 103 and the high-speed shaft 12 are located close together, which allows the size of the gearbox 14 to be reduced in the radial direction R. Furthermore, the section of the third plate bearing 103 located in the plate through-hole 26c does not slide on the third receiving surface 154. This prevents the third plate bearing 103 and the third receiving surface 154 from sliding against each other.

[0158] Since the third plate bearing receiving chamber S13 and the plate through-hole 26c are connected by the inner opening 155, oil can flow between them. Therefore, when oil is introduced into the through-hole 26c of the plate, some of the oil is supplied to the third plate bearing 103. This enables smooth movement of the third plate bearing 103.

[0159] (5) The roller bearings 101 to 106 include the first plate bearing 101. The first plate bearing 101 is a fixed bearing that rotatably supports the first roller 71, which is a fixed roller. The gear housing element 22 has the first plate bearing receiving chamber S11, which is a fixed bearing receiving chamber that receives the first plate bearing 101. The gear housing element 22 includes the first bottom surface 141 and the first receiving side surface 144 as surfaces that define the first plate bearing receiving chamber S11. The first receiving side surface 144 extends from the first bottom surface 141 in the direction of the axis of rotation Z. The first plate bearing 101 is accommodated in the first plate bearing receiving chamber S11 with a clearance Cr11 between the first plate bearing 101 and the first receiving side surface 144. In this design, the specified space Cr12 is larger than the clearance Cr11.

[0160] In this configuration, the initial clearance Cr1 allows the first plate bearing 101 to be received in the first plate bearing receiving chamber S11, even if the first plate bearing 101 is displaced. In this case, a section of the first plate bearing 101 can contact the first receiving side surface 144, depending on the manner in which the displacement occurs.

[0161] Since the specified space Cr12 in the present embodiment is wider than the first clearance Cr1, it is unlikely that the third plate bearing 103 will contact the third receiving side surface 154, even if the third plate bearing 103 is displaced. This reliably prevents the third plate bearing 103 and the third receiving side surface 154 from sliding against each other.

[0162] (6) The third plate bearing 103 is a rolling bearing comprising an inner ring 103a and an outer ring 103b. The inner ring 103a rotates relative to the outer ring 103b when the third roller 73 rotates. The third bottom surface 151 includes the third outer bottom section 151a, which is a contact section. The third outer bottom section 151a contacts the outer race 103b of the third plate bearing 103 but does not contact the inner race 103a of the third plate bearing 103.

[0163] In this configuration, the third plate bearing 103 is supported by the third outer bottom section 151a being brought into contact with the outer race 103b of the third plate bearing 103. The outer race 103b of the third plate bearing 103 is less likely to rotate than the inner race 103a when the third roller 73 rotates. Therefore, it is unlikely that the outer race 103b of the third plate bearing 103 and the third outer bottom section 151a will slide against each other. Since the inner race 103a of the third plate bearing 103 and the third outer bottom section 151a do not contact each other, it is also unlikely that sliding will occur. This allows the third plate bearing 103 to be supported while limiting wear from sliding.

[0164] (7) The third floor surface 151 has a stepped structure comprising the third outer floor section 151a and the third inner floor section 151b. The third outer floor section 151a extends along the third receiving side surface 154. The third inner floor section 151b is located on the inside of the third outer floor section 151a and is set back from the third outer floor section 151a.

[0165] Since the third outer bottom section 151a extends along the third receiving surface 154, in this configuration the third plate support 103 and the third outer bottom section 151a remain in contact even when the third plate support 103 moves. This allows the third plate support 103 to be supported as it moves. Because the third inner bottom section 151b is set back relative to the third outer bottom section 151a, it is unlikely that the third inner bottom section 151b will touch the third plate support 103. This prevents the third inner bottom section 151b and the third plate support 103 from sliding against each other.

[0166] (8) The centrifugal compressor 10 includes the gearbox 14, the electric motor 13, which rotates the low-speed shaft 11, and the impeller 52, which is attached to the high-speed shaft 12. In this way, the centrifugal compressor 10 achieves the advantages described above.

[0167] (9) The centrifugal compressor 10 includes the impeller chamber S3, which houses the impeller 52. The plate section 26 of the gearbox housing element 22 is used to define the impeller chamber S3. For example, the centrifugal compressor 10 includes the compressor housing element 23, which interacts with the plate section 26 to form the impeller chamber S3. The plate section 26 is a wall section that separates the gearbox chamber S2, which is the interior of the gearbox housing element 22, from the impeller chamber S3.

[0168] Since plate section 26 is also used to define the impeller chamber S3, the construction is simplified in this configuration.

[0169] In this configuration, the heat generated in the impeller 52 can be transferred to the plate section 26 and cause thermal expansion of the plate section 26. This can cause the third receiving side surface 154 to shift slightly, and this shift can have the disadvantage of hindering the movement of the third plate bearing 103, which is received in the third plate bearing receiving chamber S13.

[0170] In this respect, since the present embodiment has the specified area within the range of motion, it is unlikely that the movement of the third plate bearing 103 will be hindered, even if thermal expansion of the plate section 26 occurs. This eliminates the aforementioned disadvantage.

[0171] (10) The third plate bearing receiving chamber S13 is arranged on the outside of the high-speed shaft 12 in the radial direction R. The separated surface 163 is located on the outside of the third plate bearing 103 and separated from it in the radial direction R. The specified space Cr12 is a clearance between the separated surface 163 and the third plate bearing 103, independent of the position of the third plate bearing 103. This configuration provides advantages such as those described in point (1) above.

[0172] The embodiment described above can be modified as follows. Any combination of the embodiment described above and the following modifications is possible, provided there are no technical inconsistencies.

[0173] As in the Fig. 10 and Fig.As shown in Figure 11, a portion of the third plate extension section 133 can be cut out. For example, the third plate extension section 133 can have an outer opening 201 in an outer part in the radial direction R. The outer opening 201 is located at a position corresponding to the cut-off surface 163. Thus, in this modification, the cut-off surface 163 of the third receiving side surface 154 is formed only by the third recess side surface 152.

[0174] The separated surface 163 of this modification can also be recessed outwards in the radial direction R with respect to the support surfaces 161, 162. In this case, the third receiving surface 154 has a stepped structure between the support surfaces 161, 162 and the separated surface 163.

[0175] In this configuration, the specified space Cr12 is widened in the radial direction R. This reliably prevents the third receiving surface 154 from obstructing the movement of the third plate bearing 103.

[0176] The third plate recess 123 can be omitted. In this case, the third plate bearing receiving chamber S13 is preferably bounded by the first plate surface 26a and the third extension side surface 153 of the third plate extension section 133. In this configuration, the third extension side surface 153 forms the support surfaces 161, 162 and the separated surface 163.

[0177] In the configuration described above, the third extension side surface 153 can have an opening at a position corresponding to the separated surface 163. In this case, the separated surface 163 is not present, and the interior of the opening corresponds to the specified space Cr12. This also prevents the third plate bearing 103 and the third receiving side surface 154 from sliding against each other. The same applies to the first plate recess 121 and the plate recess 122.

[0178] The third plate extension section 133 can be omitted. In this case, the third recess side surface 152 forms the support surfaces 161, 162 and the separated surface 163. The same applies to the first plate extension section 131 and the second plate extension section 132.

[0179] The number of rollers can be any number greater than two. The number of movable rollers and the number of fixed rollers can also be changed.

[0180] The curvature of the support surfaces 161, 162 can be changed and can, for example, be the same as the curvature of the outer circumferential surface 103d of the third plate support 103.

[0181] The third floor surface 151 can have an opening at a position corresponding to the third inner floor section 151b. That is, the third floor surface 151 can only be formed by the third outer floor section 151a. The same applies to the first floor surface 141.

[0182] The third base surface 151 does not necessarily have to have a stepped structure. That is, both the inner raceway 103a of the third plate bearing 103 and the outer raceway 103b can contact the third base surface 151. The same applies to the first base surface 141.

[0183] The third plate bearing receiving chamber S13 and the plate through-hole 26c need not necessarily be continuously connected. In this case, the third receiving side surface 154 preferably includes a surface at a position located on the inside of the third plate bearing 103 and spaced radially R away from it. The same applies to the first plate bearing receiving chamber S11.

[0184] In the embodiment described above, the third outer bottom section 151a is located on the entire circumference of the third receiving surface 154. However, the third outer bottom section 151a can also be formed in a partial area of ​​the receiving surface 154. Alternatively, the third outer bottom section 151a can also be intermittent / discontinuous.

[0185] The base section 61 and the low-speed shaft 11 can be formed as a single piece. The base section 61 and the ring section 62 can also be formed as a single piece.

[0186] The specific configuration of the compressor unit 15 is not specifically limited to one with the impeller 52, but can be any type, for example a turbine wheel or a worm gear.

[0187] The gearbox 14 can be mounted on a different structure than the centrifugal compressor 10. For example, the gearbox 14 can be mounted on a fluid machine, such as a pump, that does not compress a fluid.

[0188] The gearbox 14 and the centrifugal compressor 10 can be attached to any structure other than a vehicle.

[0189] The centrifugal compressor 10 can be used in any suitable application to compress any type of fluid. For example, the centrifugal compressor 10 can be used in an air conditioning system to compress refrigerant, which is a fluid. Various modifications in form and detail can be made to the above examples without affecting the intent and scope of the claims and their equivalents. The examples serve only for description and not for limitation. Descriptions of features in each example are to be considered applicable to similar features or aspects in other examples. Suitable results can be obtained if processes are carried out in a different sequence and / or if components in a described system, architecture, device, or circuit are combined differently and / or replaced or supplemented by other components or their equivalents.The scope of disclosure is not defined by the detailed description, but by the claims and their equivalents. All variations within the scope of the claims and their equivalents are included in the disclosure.

Claims

[1] Gearbox (14), with: a gearbox housing element (22); a ring-shaped ring section (62) which is provided in the gearbox housing element (22) and rotates when a low-speed shaft (11) rotates; a high-speed wave (12) which is arranged on an inner side of the ring section (62); at least three rollers (71, 72, 73) provided between the ring section (62) and the high-speed shaft (12) and contacting both an inner circumferential surface of the ring section (62) and an outer circumferential surface of the high-speed shaft (12); and radial bearings (101, 102, 103, 104, 105, 106) with which the rollers (71, 72, 73) are rotatably mounted through the gearbox housing element (22), wherein The roles (71, 72, 73) include: a movable roller (73) which moves in a direction of rotation of the ring section (62) in response to the rotation of the ring section (62); and a fixed roller (71, 72) which is attached in such a way that it does not move in the direction of rotation of the ring section (62), the radial bearings (101, 102, 103, 104, 105, 106) include a movable bearing (103) which rotatably supports the movable roller (73), the gearbox housing element (22) includes: a first support surface (161) that contacts the movable bearing (103) to limit the movable roller (73) in a first position; and a second support surface (162) which is provided in a position spaced apart from the first support surface (161) in the direction of rotation and which contacts the movable bearing (103) in order to limit the movable roller (73) in a second position, a movement of the movable roller (73) within a range of motion from the first position to the second position is performed, and the range of motion includes a specified area in which the movable roller (73) is not supported in a radial direction of the high-speed shaft (12) by the gear housing element (22) with the movable bearing (103) in between, but is supported by being held between the ring section (62) and the high-speed shaft (12), characterized by , that the gearbox housing element (22) has a plate section (26), The plate section (26) as surfaces defining a receiving chamber for the movable bearing (S13) which receives the movable bearing (103) includes: a floor area (151); and a receiving surface (154) extending in an axial direction of the high-speed wave (12) from the base surface (151) and including the first support surface (161) and the second support surface (162), the plate section (26) includes a plate through-hole (26c) through which the high-speed shaft (12) is guided, the receiving surface (154) has an inner opening (155) that opens inwards in the radial direction of the high-speed wave (12), the receiving chamber for the movable bearing (S13) and the plate through-hole (26c) are connected to each other through the inner opening (155), and the movable bearing (103) is partially arranged in the plate through-hole (26c). [2] Gearbox (14) according to claim 1, wherein the gearbox housing element (22) includes as surfaces defining a receiving chamber for the movable bearing (S13) which receives the movable bearing (103): a floor area (151); and a receiving surface (154) extending in an axial direction of the high-speed wave (12) from the base surface (151) and including the first support surface (161) and the second support surface (162), the receiving surface (154) includes a separated surface (163) which is provided at a position separated from an outer circumferential surface of the movable bearing (103), and in the specified area there is a clearance (Cr12) between the separated surface (163) and the outer circumferential surface of the movable bearing (103). [3] Gearbox (14) according to claim 2, wherein the first support surface (161) and the second support surface (162) are curved surfaces with a curvature that is smaller than the curvature of the outer circumferential surface of the movable bearing (103), the first support surface (161) and the second support surface (162) are opposite each other, and the separated area (163) extends in a direction in which the support surfaces (161, 162) are opposite each other in order to connect an end section (161b) of the first support surface (161) and an end section (162b) of the second support surface (162). [4] Gearbox (14) according to claim 2, wherein the separated surface (163) is set back in the radial direction of the high-speed shaft (12) with respect to the support surfaces (161, 162). [5] The transmission (14) according to any one of claims 1 to 4, wherein the gearbox housing element (22) includes surfaces that define a receiving chamber for the movable bearing (S13) which receives the movable bearing (103): a floor area (151); and a receiving surface (154) extending in an axial direction of the high-speed wave (12) from the base surface (151) and comprising the first support surface (161) and the second support surface (162), the movable bearing (103) is a rolling bearing which includes: an outer ring (103b); and an inner ring (103a) which rotates relative to the outer ring (103b) when the movable roller (73) rotates, and the bottom surface (151) includes a contact section (151a) which is designed to contact the outer ring (103b) and not the inner ring (103a). [6] Gearbox (14) according to claim 5, wherein the bottom surface (151) has a stepped structure comprising: an outer ground section (151a) extending along the recording side surface (154); and an inner floor section (151b) which is arranged on an inside side of the outer floor section (151a) and is set back with respect to the outer floor section (151a), and the contact section (151a) is the outer soil section (151a). [7] Centrifugal compressor (10), with: the transmission (14) according to one of claims 1 to 6; an electric motor (13) which drives the low-speed shaft (11); and an impeller (52) which is attached to the high-speed shaft (12). [8] Centrifugal compressor (10) according to claim 7, wherein the gearbox housing element (22) includes a plate section (26), The plate section (26) as surfaces defining a receiving chamber for the movable bearing (S13) which receives the movable bearing (103) includes: a floor area (151); and a receiving surface (154) extending in an axial direction of the high-speed wave (12) from the base surface (151) and including the first support surface (161) and the second support surface (162), the centrifugal compressor (10) has a compressor housing element (23) which interacts with the plate section (26) to define an impeller chamber that accommodates the impeller (52), and the plate section (26) is a wall section that separates a gear chamber (S2), which is an interior of the gear housing element (22), and the impeller chamber (S3).

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