JP2017180528A - Speed increaser and centrifugal compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a speed increaser capable of preferably carrying out power transmission from a ring portion to a high-speed side shaft, and a centrifugal compressor equipped with the speed increaser.SOLUTION: A speed increaser 14 is equipped with, as an article rotated with rotations of a high-speed shaft 11, a base portion 61; an annular ring portion 62 raised from the base portion 61; a high-speed shaft 12 disposed on the inside of the ring portion 62; and a first roller 71 provided between the ring portion 62 and the high-speed side shaft 12. The speed increaser 14 is equipped with a projecting portion 69 which is provided on an inner peripheral surface 63 of the ring portion 62, and projects out from the inner peripheral surface 63 toward the inner side in a diametrical direction R of the high-speed shaft 12. The first roller 71 abuts on both of the projecting portion 69 and the high-speed side shaft 12 at rest.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a speed increaser and a centrifugal compressor including the speed increaser.

  2. Description of the Related Art Conventionally, a speed increaser that transmits power of a low speed side shaft to a high speed side shaft is known (see, for example, Patent Document 1). The speed increaser described in Patent Literature 1 is configured to rotate with the rotation of the low speed side shaft, and includes a base part, an annular ring part standing from the base part, and a high speed side shaft disposed inside the ring part. And a roller provided between the ring portion and the high speed side shaft and having an outer peripheral surface that abuts both the inner peripheral surface of the ring portion and the outer peripheral surface of the high speed side shaft. The roller and the high speed side shaft are fastened by a ring portion.

  Further, in Patent Document 1, the ring portion, the roller, and the high speed side shaft rotate to correspond to the contact portion between the ring portion and the roller and the contact portion between the roller and the high speed side shaft. It is described that an oil film (elastic fluid lubricating film) is formed in a portion where power is transmitted and power is transmitted through the oil film.

JP 2003-314446 A

  In order to stably form the oil film during rotation, the contact portion between the inner peripheral surface of the ring portion and the outer peripheral surface of the roller, and the contact portion between the outer peripheral surface of the roller and the outer peripheral surface of the high-speed shaft are determined. In both cases, a certain amount of pressure is required.

  Here, since the outer peripheral surfaces of the high-speed side shaft and the roller are in contact with each other, the area of the contact portion between both tends to be small. On the other hand, since the inner peripheral surface and the outer peripheral surface are in contact with the ring portion and the roller, the area of the contact portion is likely to be larger than the area of the contact portion between the high speed side shaft and the roller. For this reason, the pressure in the contact part of a ring part and a roller tends to become small.

  In this case, for example, if the pressure at the contact portion between the ring portion and the roller is increased to increase the tightening by the ring portion, the power loss between the high speed side shaft and the roller increases or the load on the high speed side shaft increases. It becomes.

  The present invention has been made in view of the above-described circumstances, and an object thereof is a speed increaser capable of suitably performing power transmission from a ring portion to a high speed side shaft and a centrifugal compressor including the speed increaser. Is to provide.

  The speed increaser that achieves the above object is arranged to rotate with the rotation of the low speed side shaft, and is arranged inside the ring part, a plate-like base part, an annular ring part standing up from the base part, and the ring part A high speed side shaft, a convex portion provided on the inner peripheral surface of the ring portion and projecting radially inward from the inner peripheral surface of the high speed side shaft, and between the ring portion and the high speed side shaft A roller having an outer peripheral surface that is in contact with both the convex portion and the outer peripheral surface of the high-speed side shaft, and the ring portion has a tip portion that is an end portion opposite to the base portion side. The ring portion has the convex portion and the outer peripheral surface of the roller in contact with each other, so that the tip portion expands outward in the radial direction of the high-speed side shaft, and the roller extends from the convex portion. Press applied toward And a direction of is elastically deformed so as to approach the radial direction of the high speed side shaft.

  According to such a configuration, since the convex portion and the outer peripheral surface of the roller are in contact with each other, the area of the contact portion can be reduced as compared with the configuration in which the inner peripheral surface of the ring portion is in contact with the outer peripheral surface of the roller. . Thereby, the pressure in the contact location of a convex part and a roller can be enlarged. Therefore, the oil film can be formed between the convex portion and the roller during rotation with relatively small tightening.

  Further, since the convex portion is provided not on the roller but on the inner peripheral surface of the ring portion, a situation in which the area of the contact portion between the high speed side shaft and the roller is reduced by the convex portion does not occur. As a result, there is no inconvenience that the burden on the high speed side shaft is increased due to the convex portion. Accordingly, it is possible to generate an appropriate pressure at both the contact portion between the convex portion and the roller and the contact portion between the roller and the high speed side shaft. Therefore, power transmission from the ring portion to the high speed side shaft can be suitably performed.

  Here, in the configuration in which the convex portion is provided on the inner peripheral surface of the ring portion, the ring portion has its tip portion widened toward the outside in the radial direction of the high speed side shaft by the contact between the convex portion and the roller. It is elastically deformed. In this case, a pressing force including a component in the rotation axis direction of the high-speed side shaft and a drag force of the pressing force can be generated at the contact portion between the convex portion and the roller. The component in the rotational axis direction of the high-speed side shaft not only causes unnecessary loss, but can also cause misalignment of the roller and the ring portion.

  On the other hand, according to this configuration, in the state where the ring portion is elastically deformed, the direction of the pressing force approaches the radial direction of the high speed side shaft. Thereby, in the state in which the ring portion is elastically deformed, the component in the rotation axis direction becomes small. Therefore, the useless loss or the like can be suppressed.

  With respect to the speed increaser, the inner peripheral surface of the ring portion has a convex portion installation surface on which the convex portion is installed, and the convex portion installation surface has the tip portion radially outside the high speed side shaft. It is preferable that the normal direction is a surface that approaches the radial direction of the high-speed shaft by elastically deforming so as to spread toward the surface.

  According to this configuration, the direction of the pressing force can be brought close to the radial direction of the high-speed side shaft in a state where the tip end portion of the ring portion is elastically deformed so as to spread outward in the radial direction of the high-speed side shaft. Thereby, the above-described effect can be obtained with a relatively simple configuration.

About the said speed increaser, the said convex part is good in it being the cyclic | annular form extended in the circumferential direction of the said ring part.
According to such a configuration, a stable pressing force can be applied to the roller regardless of the change in the rotational position of the ring portion.

About the said speed increaser, the said convex part is good in the cross section at the time of cut | disconnecting in the direction orthogonal to the circumferential direction of the said ring part being semicircular.
According to this configuration, since the area of the contact portion between the convex portion and the outer peripheral surface of the roller can be reduced, the pressure at the contact portion can be further increased.

  A centrifugal compressor that achieves the above object includes the above-described speed increaser, an electric motor that rotates the low-speed side shaft, and an impeller attached to the high-speed side shaft.

  According to this configuration, the impeller can be rotated at a higher rotational speed than the drive rotational speed of the electric motor. And a centrifugal compressor can be operated suitably through performing power transmission from a ring part to a high-speed side shaft suitably.

  According to this invention, power transmission from the ring portion to the high speed side shaft can be suitably performed.

Sectional drawing which shows the outline | summary of a speed up gear and a centrifugal compressor typically. (A) is the 2-2 sectional view taken on the line of FIG. 1, (b) is the elements on larger scale of (a). The expanded sectional view which shows typically the circumference | surroundings of a 1st ring side contact location. The expanded sectional view which shows typically the ring part of the state which is not elastically deformed. The expanded sectional view which shows typically the ring part of the comparison object in the state which is not elastically deformed. (A) is an expanded sectional view which shows typically the ring part of the comparison object of the state which is elastically deforming, (b) is the elements on larger scale of (a). The expanded sectional view which shows typically the convex part of another example. The expanded sectional view which shows typically the convex part of another example.

  Hereinafter, an embodiment of a speed increaser and a centrifugal compressor including the speed increaser will be described. In the present embodiment, the centrifugal compressor is mounted on a fuel cell vehicle (FCV) on which a fuel cell is mounted, and is used to send air to the fuel cell. For convenience of illustration, both shafts 11 and 12 are shown in side views in FIG.

  As shown in FIG. 1, the centrifugal compressor 10 includes a low-speed side shaft 11 and a high-speed side shaft 12, an electric motor 13 that rotates the low-speed side shaft 11, and a high-speed side shaft by increasing the rotation of the low-speed side shaft 11. 12 and a compression unit 15 that compresses fluid (air in the present embodiment) by rotation of the high-speed side shaft 12. Both shafts 11 and 12 are made of, for example, metal, and more specifically, iron or an iron alloy.

  The centrifugal compressor 10 constitutes the outline of the centrifugal compressor 10, and includes a housing 20 in which both shafts 11 and 12, an electric motor 13, a speed increaser 14, and a compression unit 15 are accommodated. Yes. The housing 20 has, for example, a substantially cylindrical shape (in detail, a cylindrical shape) as a whole.

  The housing 20 includes a motor housing 21 in which the electric motor 13 is accommodated, a speed increaser housing 22 in which the speed increaser 14 is accommodated, and a compressor housing 23 in which a suction port 23a through which fluid is sucked is formed. Yes. The suction port 23 a is provided on one end surface 20 a in the axial direction of the housing 20. The compressor housing 23, the speed increaser housing 22, and the motor housing 21 are arranged in this order in the axial direction of the housing 20 when viewed from the suction port 23a. The housing 20 includes a plate 24 provided between the gearbox housing 22 and the compressor housing 23.

  Incidentally, in this embodiment, the centrifugal compressor 10 is mounted on the vehicle in a state where the axial direction of the housing 20 and the horizontal direction coincide with each other. And the up-down direction of the paper surface of FIG. 1 corresponds to the vertical direction.

  The motor housing 21 has a cylindrical shape (in detail, a cylindrical shape) having a bottom portion 21a as a whole. The outer surface of the bottom portion 21a of the motor housing 21 constitutes the other end surface 20b opposite to the one end surface 20a where the suction port 23a is located, of both end surfaces 20a and 20b in the axial direction of the housing 20. Similarly, the speed increaser housing 22 has a cylindrical shape (in detail, a cylindrical shape) having a bottom portion 22a as a whole.

  The motor housing 21 and the speed increaser housing 22 are connected in a state where the open end of the motor housing 21 is in contact with the bottom 22 a of the speed increaser housing 22. A motor housing chamber S <b> 1 in which the electric motor 13 is housed is formed by the inner surface of the motor housing 21 and the surface of the bottom 22 a of the gearbox housing 22 on the motor housing 21 side. The motor housing chamber S1 accommodates the low speed side shaft 11 in a state where the rotational axis direction of the low speed side shaft 11 and the axial direction of the housing 20 coincide.

  The low speed side shaft 11 is supported by the housing 20 in a rotatable state. Specifically, a cylindrical first boss 31 that stands up toward the gearbox housing 22 is provided on the bottom 21 a of the motor housing 21. The first boss 31 is formed to be slightly larger than the one end portion 11 a of the low speed side shaft 11. One end portion 11 a of the low speed side shaft 11 enters the first boss 31, and the low speed side shaft 11 is rotatable between the inner surface of the first boss 31 and the one end portion 11 a of the low speed side shaft 11. The 1st bearing 32 supported by is provided.

  Similarly, the bottom portion 22a of the speed increaser housing 22 has a through hole 22b formed to be slightly larger than the other end portion 11b opposite to the one end portion 11a of the low speed side shaft 11, and a peripheral edge of the through hole 22b. A cylindrical second boss 33 erected from the portion toward the motor housing 21 (specifically, the first boss 31) is provided. The other end portion 11 b of the low speed side shaft 11 enters the second boss 33, and the low speed side shaft 11 can rotate between the inner surface of the second boss 33 and the other end portion 11 b of the low speed side shaft 11. The 2nd bearing 34 supported in a state is provided. In the vicinity of the boundary between the inner surface of the through hole 22b of the speed increaser housing 22 and the inner surface of the second boss 33, an overhanging portion 35 that projects radially inward from both inner surfaces is provided. It is arranged in a region partitioned by the second boss 33 and the overhang portion 35.

  Incidentally, as shown in FIG. 1, the other end portion 11 b of the low speed side shaft 11 is inserted into the through hole 22 b of the speed increaser housing 22, and a part of the low speed side shaft 11 is located inside the speed increaser housing 22. Is arranged. Further, between the inner surface of the through hole 22b of the speed increaser housing 22 and the other end portion 11b of the low speed side shaft 11, the oil existing in the speed increaser housing 22 is restricted from flowing into the motor housing chamber S1. A seal member 36 is provided. The seal member 36 is disposed on the opposite side of the projecting portion 35 from the second bearing 34 in the region between the inner surface of the through hole 22b of the speed increasing device housing 22 and the other end portion 11b of the low speed side shaft 11. Has been.

  As shown in FIG. 1, the low speed side shaft 11 includes a positioning portion 37 that positions the low speed side shaft 11 with respect to the housing 20. The positioning portion 37 is provided on the electric motor 13 side with respect to the second bearing 34 and is fixed to the low speed side shaft 11. The positioning portion 37 has a flat ring shape extending radially outward from the outer peripheral surface of the low-speed side shaft 11. The positioning portion 37 is in contact with the second bearing 34 from the direction of the rotation axis of the low speed shaft 11. Thereby, when the force which goes to the other end part 11b from the one end part 11a is provided with respect to the low speed side shaft 11, the position shift of the low speed side shaft 11 is carried out by contact | abutting with the 2nd bearing 34 and the positioning part 37. Is regulated. The positioning part 37 corresponds to a “first positioning part”.

  The electric motor 13 includes a rotor 41 fixed to the low-speed shaft 11 and a stator 42 that is disposed outside the rotor 41 and fixed to the inner surface of the motor housing 21. The rotation axis of the rotor 41 and the center axis of the stator 42 are arranged on the same axis as the rotation axis of the low speed side shaft 11. The rotor 41 and the stator 42 are opposed to each other in the radial direction of the low speed shaft 11.

  The stator 42 includes a cylindrical stator core 43 and a coil 44 wound around the stator core 43. When the current flows through the coil 44, the rotor 41 and the low-speed side shaft 11 rotate integrally.

  The plate 24 has, for example, a disk shape having the same diameter as that of the gearbox housing 22. The plate 24 and the bottomed cylindrical gearbox housing 22 opened in one axial direction are assembled in a state where the opening end of the gearbox housing 22 and the first plate surface 24a of the plate 24 are in contact with each other. It has been. As a result, the first plate surface 24a of the plate 24 and the inner surface of the gearbox housing 22 form a gearbox S2 in which the gearbox 14 is accommodated.

  As shown in FIG. 1, the plate 24 is formed with a plate through hole 24 b into which the high speed side shaft 12 constituting a part of the speed increaser 14 can be inserted. A part of the high speed side shaft 12 is disposed in the compressor housing 23 via the plate through hole 24b.

  A seal member 50 is provided between the inner surface of the plate through hole 24 b and the high speed side shaft 12 to restrict the oil in the gearbox housing 22 from flowing into the compressor housing 23.

  The compressor housing 23 has a substantially cylindrical shape having a comp through hole 51 penetrating in the axial direction. One end surface 23b in the axial direction of the compressor housing 23 constitutes one end surface 20a in the axial direction of the housing 20, and the opening on the one end surface 23b side in the compressor through hole 51 functions as the suction port 23a.

  The compressor housing 23 and the plate 24 protrude from the other end surface 23c opposite to the one end surface 23b in the axial direction of the compressor housing 23 and the second plate surface 24c on the plate 24 opposite to the first plate surface 24a. It is assembled in a combined state. In this case, an impeller chamber S3 in which an impeller 52 serving as the compression unit 15 is accommodated is formed by the inner surface of the comp through-hole 51 and the second plate surface 24c of the plate 24. That is, the comp through hole 51 functions as the suction port 23a and functions as a partition for the impeller chamber S3. The suction port 23a and the impeller chamber S3 communicate with each other.

  Here, the compressor through-hole 51 has a constant diameter from the suction port 23 a to the midway position in the axial direction, and has a substantially truncated cone shape that gradually increases in diameter from the midway position toward the second plate surface 24 c of the plate 24. It has become. For this reason, the impeller chamber S3 defined by the inner surface of the comp through hole 51 has a substantially truncated cone shape.

  The impeller 52 has a cylindrical shape with a diameter gradually reduced from the proximal end surface 52a toward the distal end surface 52b. The impeller 52 has an insertion hole 52c that extends in the rotational axis direction of the impeller 52 and through which the high speed side shaft 12 can be inserted. The impeller 52 is attached to the high speed side shaft 12 so as to rotate integrally with the high speed side shaft 12 in a state where a portion of the high speed side shaft 12 protruding into the comp through hole 51 is inserted into the insertion hole 52c. Thereby, the impeller 52 is rotated by the rotation of the high-speed side shaft 12, and the fluid sucked from the suction port 23a is compressed.

  The centrifugal compressor 10 also includes a diffuser channel 53 into which the fluid compressed by the impeller 52 flows and a discharge chamber 54 into which the fluid that has passed through the diffuser channel 53 flows. The diffuser flow path 53 is formed by a surface that is continuous with the opening end of the compressor through hole 51 on the second plate surface 24 c side of the compressor housing 23 and faces the second plate surface 24 c, and the second plate surface 24 c of the plate 24. It is a partitioned flow path. The diffuser flow channel 53 is disposed outside the impeller chamber S3 in the radial direction R of the high-speed side shaft 12, and is formed in an annular shape (specifically, an annular shape) so as to surround the impeller 52 (and the impeller chamber S3). Yes. The discharge chamber 54 has an annular shape that is disposed on the outer side in the radial direction R of the high-speed side shaft 12 than the diffuser flow path 53. The impeller chamber S3 and the discharge chamber 54 communicate with each other through a diffuser flow path 53. The fluid compressed by the impeller 52 is further compressed by passing through the diffuser flow path 53, flows into the discharge chamber 54, and is discharged from the discharge chamber 54.

Next, the speed increaser 14 will be described.
The speed increaser 14 of the present embodiment is a so-called traction drive type (friction roller type). As shown in FIG. 1, the speed increaser 14 includes a ring member 60 connected to the other end portion 11 b of the low speed side shaft 11. The ring member 60 is made of a flexible material that can be elastically deformed. For example, the ring member 60 is made of metal or the like.

  The ring member 60 includes a plate-like (specifically disc-shaped) base portion 61 connected to the other end portion 11 b of the low-speed side shaft 11 and the base portion 61 (specifically, an edge portion of the base portion 61). And a ring portion 62 erected toward the plate 24. The base portion 61 and the ring portion 62 rotate with the rotation of the low speed side shaft 11.

  The ring portion 62 is formed in an annular shape (specifically, an annular shape) when viewed from the rotation axis direction Z of the high speed side shaft 12, and has an inner peripheral surface 63 and an outer peripheral surface 64. The ring portion 62 has a base end portion 65 that is an end portion on the base portion 61 side, and a tip end portion 66 on the side opposite to the base end portion 65. The proximal end portion 65 is a fixed end, and the distal end portion 66 is a free end capable of elastic deformation. The inner diameter of the ring portion 62 is set longer than the diameter of the other end portion 11 b of the low speed side shaft 11. It can be said that the tip portion 66 of the ring portion 62 is an end portion on the opposite side to the base portion 61 side.

  For convenience of explanation, in the following explanation, a portion having the same wall thickness (thickness) as the base end portion 65 in the ring portion 62 is referred to as a main body portion 67, and a portion between the main body portion 67 and the distal end portion 66. A portion that is continuous with both the main body portion 67 and the tip portion 66 is referred to as a continuous portion 68.

  In the present embodiment, the ring member 60 is connected to the low speed side shaft 11 so that the rotation axis of the base portion 61 (the rotation axis of the ring member 60) matches the rotation axis of the low speed side shaft 11. In this case, the rotation axis of the ring portion 62 also coincides with the rotation axis of the low speed side shaft 11. The inner diameter and outer diameter of the ring portion 62 are diameters centered on the rotation axis of the low-speed side shaft 11.

  Incidentally, if attention is paid to the fact that the ring member 60 and the low speed side shaft 11 are connected, it can be said that the positioning portion 37 that positions the low speed side shaft 11 also functions as a positioning portion of the ring member 60. . That is, it can be said that the positioning portion 37 positions the ring member 60 (ring portion 62) with respect to the housing 20 in the rotation axis direction Z of the high-speed side shaft 12.

  A part of the high speed side shaft 12 is disposed inside the ring portion 62. 2 (a) and 2 (b), the speed increaser 14 is provided between the high speed side shaft 12 and the ring portion 62, and a convex portion 69 of the ring portion 62 and a high speed are described later. A plurality of rollers 71 to 73 that come into contact with both outer peripheral surfaces 12 a of the side shaft 12 are provided. Each roller 71-73 is cylindrical. The rotation axis direction of each of the rollers 71 to 73 coincides with the rotation axis direction Z of the high speed side shaft 12. For this reason, the rotation axis direction Z of the high speed side shaft 12 can be rephrased as the rotation axis direction of the rollers 71 to 73.

  The plurality of rollers 71 to 73 are arranged side by side at a predetermined interval (for example, 120 degrees) in the circumferential direction of the high speed side shaft 12. In addition, each roller 71-73 is comprised, for example with the metal, and is specifically comprised with the same metal as the high speed side shaft 12, for example, iron or an iron alloy.

  As shown in FIGS. 1 and 2, the speed increaser 14 includes a support member 80 that rotatably supports the rollers 71 to 73 in cooperation with the plate 24. The support member 80 is disposed in the ring portion 62. The support member 80 includes a disk-shaped support base portion 81 that is formed slightly smaller than the ring portion 62, and three columnar support portions 82 to 84 erected from the support base portion 81. The support base portion 81 is disposed at a position where the base portion 61 of the ring member 60 and the plate surfaces face each other. The support base portion 81 is disposed to face the plate 24 in the rotation axis direction Z. The three support portions 82 to 84 stand up from the opposing plate surface 81a facing the first plate surface 24a of the plate 24 in the support base portion 81 toward the plate 24, and the inner peripheral surface 63 of the ring portion 62, It is formed so as to fill three spaces defined by the outer peripheral surfaces of two adjacent rollers.

  As shown in FIG. 2A, the first support portion 82 has a constant gap with respect to the inner peripheral surface 63 of the ring portion 62, the outer peripheral surface 71 a of the first roller 71, and the outer peripheral surface 72 a of the second roller 72. In the formed state, a space defined by the inner peripheral surface 63 of the ring portion 62, the outer peripheral surface 71a of the first roller 71, and the outer peripheral surface 72a of the second roller 72 is filled.

  The second support portion 83 is formed in a state where a certain gap is formed with respect to the inner peripheral surface 63 of the ring portion 62, the outer peripheral surface 72 a of the second roller 72, and the outer peripheral surface 73 a of the third roller 73. A space defined by the peripheral surface 63, the outer peripheral surface 72a of the second roller 72, and the outer peripheral surface 73a of the third roller 73 is filled.

  The third support portion 84 has a constant gap with respect to the inner peripheral surface 63 of the ring portion 62, the outer peripheral surface 71a of the first roller 71, and the outer peripheral surface 73a of the third roller 73. A space defined by the peripheral surface 63, the outer peripheral surface 71a of the first roller 71, and the outer peripheral surface 73a of the third roller 73 is filled.

  As shown in FIGS. 1 and 2A, each support portion 82 to 84 is formed with a screw hole 92 into which a bolt 91 as a fixture can be screwed. A screw hole 93 that communicates with the screw hole 92 is formed in the first plate surface 24 a of the plate 24 so as to correspond to the screw hole 92. Each support part 82-84 is arrange | positioned in the position where the screw hole 92 and the screw hole 93 were connected, and the front end surface of each said support part 82-84 faced | matched the 1st board surface 24a, In this state, the bolt 91 is screwed so as to straddle the screw hole 92 and the screw hole 93 and is fixed to the plate 24.

  The first roller 71, the second roller 72, and the third roller 73 are disposed between the plate 24 and the support base portion 81, and the first roller bearing 94 fixed to the plate 24 and the support base portion 81 The second roller bearings 95 are fixed so as to be rotatable.

  Specifically, as shown in FIG. 1, protrusions 101 and 102 protruding from both end faces are formed on both end faces in the rotation axis direction Z of the first roller 71. The protrusions 101 and 102 have a columnar shape provided at the center of the both end faces.

  A plate recess 103 that is recessed from the first plate surface 24 a is formed on the first plate surface 24 a of the plate 24. The length of the plate 24 in the radial direction of the plate recess 103 is longer than the diameter of the first protrusion 101 and shorter than the diameter of the first roller 71. A cylindrical portion 104 erected from the first plate surface 24 a is formed at the peripheral edge of the plate recess 103. The inner diameter of the cylindrical portion 104 is the same as the diameter of the plate recess 103. The first protrusion 101 is disposed in a space formed by the cylindrical portion 104 and the plate recess 103. The first roller bearing 94 is disposed between the first protrusion 101 and the inner wall of the cylindrical portion 104 and the plate recess 103, and is attached to the plate 24 in a state where the first protrusion 101 is rotatably supported. .

  In addition, a support concave portion 105 that is recessed from the counter plate surface 81 a is provided on the counter plate surface 81 a of the support base portion 81. The length of the support recess 105 in the direction intersecting the rotation axis direction Z is longer than the diameter of the second protrusion 102 and shorter than the diameter of the first roller 71. The second protrusion 102 is accommodated in the support recess 105. The second roller bearing 95 is disposed between the second protrusion 102 and the side wall of the support recess 105, and is attached to the support member 80 in a state where the second protrusion 102 is rotatably supported.

The second roller 72 and the third roller 73 are also rotatably supported by the same configuration as the first roller 71.
Here, as shown in FIG. 2A, the diameter of each of the rollers 71 to 73 (the length of each of the rollers 71 to 73 in the direction intersecting the rotation axis direction Z) is set to be longer than the diameter of the high speed side shaft 12. ing. The diameters of the rollers 71 to 73 are set to be shorter than the radius of the inner peripheral surface 63 of the ring portion 62 so that the rollers 71 to 73 can be arranged in the ring portion 62.

  Incidentally, as shown in FIG. 2A, the diameter of the first roller 71 is different from the diameters of the second roller 72 and the third roller 73. Specifically, the diameter of the first roller 71 is different from that of the second roller 71. It is set longer than the diameters of the roller 72 and the third roller 73. For this reason, the high speed side shaft 12 pressed and supported by the rollers 71 to 73 and the ring portion 62 (in other words, the low speed side shaft 11) are eccentric. Specifically, the rotation axis of the high speed side shaft 12 and the rotation axis of the ring portion 62 are deviated.

  As shown in FIG. 1, the outer peripheral surface 12 a of the high speed side shaft 12 is provided with a pair of flange portions 96 that protrude from the outer peripheral surface 12 a to the outside in the radial direction R of the high speed side shaft 12. The pair of flange portions 96 are disposed to be opposed to each other in the rotation axis direction Z. The plurality of rollers 71 to 73 are sandwiched from the rotation axis direction Z by a pair of flange portions 96. Thereby, the position shift with the high speed side shaft 12 and the some rollers 71-73 in the rotating shaft direction Z is suppressed. For example, when a thrust force in the rotation axis direction Z is generated by the rotation of the impeller 52, the impeller 52 side end surface of the first roller 71 in the rotation axis direction Z and the pair of flange portions 96 are arranged on the impeller 52 side. The flange part 96 abuts and further movement is restricted. The pair of flange portions 96 corresponds to the “second positioning portion”.

  The separation distance in the rotation axis direction Z of the pair of flange portions 96 is set slightly wider than the length of the rollers 71 to 73 in the rotation axis direction Z. For this reason, a gap into which oil can enter is formed between the flange portion 96 and the end surface in the rotation axis direction Z of the rollers 71 to 73.

  A through hole 81b that is slightly larger than the flange portion 96 is formed in the central portion of the support base portion 81, and the flange portion 96 on the base portion 61 side is disposed in the through hole 81b. Moreover, the flange part 96 arrange | positioned at the impeller 52 side is arrange | positioned in the plate through-hole 24b.

  Hereinafter, the ring part 62 which is the principal part of this case will be described with reference to FIGS. In FIG. 3, for convenience of illustration, only the contact mode between the first roller 71 and the ring portion 62 is shown, but the contact mode between the rollers 71 to 73 and the ring unit 62 is basically the same. It is. Further, in the following description, it is assumed that the shafts 11 and 12 and the rollers 71 to 73 are not rotating unless otherwise specified.

As shown in FIGS. 1 to 3, the inner peripheral surface 63 of the ring portion 62 is provided with a convex portion 69 protruding from the inner peripheral surface 63 toward the inner side in the radial direction R of the high speed side shaft 12.
As shown in FIG. 2A, the convex portion 69 has an annular shape (specifically, an annular shape) extending in the circumferential direction of the ring portion 62. As shown in FIG. 3, the convex portion 69 has a semicircular cross section when cut in a direction orthogonal to the circumferential direction of the ring portion 62. The convex part 69 and the outer peripheral surfaces 71a to 73a of the rollers 71 to 73 are in contact with each other.

  As shown in FIG. 3, the ring portion 62 has a tip portion 66 on the outer side in the radial direction R of the high-speed side shaft 12 because the convex portion 69 and the outer peripheral surfaces 71 a to 73 a of the rollers 71 to 73 are in contact with each other. It is elastically deformed so as to spread. As a result, the pressing force generated when the tip portion 66 tries to return to the ring side contact portions Pa1 to Pa3 that are the contact portions between the convex portion 69 and the outer peripheral surfaces 71a to 73a of the rollers 71 to 73. (Biasing force) F1 is applied.

  In the situation where the convex portion 69 and the outer peripheral surfaces 71a to 73a of the rollers 71 to 73 are in contact with each other, the inner peripheral surface 63 of the ring portion 62 and the outer peripheral surfaces 71a to 73a of the rollers 71 to 73 are separated from each other. doing.

  The inner peripheral surface 63 of the ring portion 62 includes a tip inner peripheral surface 63a corresponding to the tip portion 66, a main body inner peripheral surface 63b corresponding to the main body portion 67, and a convex portion installation surface 63c on which the convex portion 69 is installed. Have.

The inner peripheral surface 63b is a surface along the rotation axis direction Z of the high speed side shaft 12. That is, the inclination angle between the inner peripheral surface 63b of the main body and the rotation axis direction Z is “0” or close thereto.
The convex portion installation surface 63c is a surface that is continuous with both the tip inner peripheral surface 63a and the main body inner peripheral surface 63b. The convex portion installation surface 63 c faces the central portion in the rotation axis direction Z of the high speed side shaft 12 and the periphery thereof on the outer peripheral surfaces 71 a to 73 a of the rollers 71 to 73 and the radial direction R of the high speed side shaft 12. The convex portion installation surface 63c approaches the rotational axis direction Z by the elastic deformation of the ring portion 62 so that the tip portion 66 spreads outward in the radial direction R of the high speed side shaft 12.

  Specifically, as shown in FIG. 4, the convex portion installation surface 63 c is directed from the base end side (base portion 61 side) to the tip end side (tip portion 66 side) in a state where the ring portion 62 is not elastically deformed. It is inclined with respect to the rotation axis direction Z so as to gradually reduce the diameter. In other words, the convex portion installation surface 63c that is not elastically deformed has a predetermined inclination angle (taper angle) with respect to the rotation axis direction Z.

  On the other hand, as shown in FIG. 3, the convex portion installation surface 63 c rotates when the ring portion 62 is elastically deformed by contact between the convex portion 69 and the outer peripheral surfaces 71 a to 73 a of the rollers 71 to 73. Along the axial direction Z. Specifically, the convex portion installation surface 63c is closer to the rotational axis direction Z of the high speed side shaft 12 in a state where the ring portion 62 is elastically deformed than in a state where the ring portion 62 is not elastically deformed. In other words, the taper angle with respect to the rotation axis direction Z of the convex portion installation surface 63c in an elastically deformed state is “0” or an angle close thereto. For this reason, when the taper angle of the convex portion installation surface 63c with respect to the rotation axis direction Z is “0”, the inner diameter of the convex portion installation surface 63c is constant regardless of the rotation axis direction Z.

  That is, the convex portion installation surface 63c has a small inclination angle with respect to the rotation axis direction Z by the elastic deformation of the ring portion 62 so that the tip portion 66 spreads outward in the radial direction R of the high speed side shaft 12 (preferably Is "0"). In other words, the convex portion installation surface 63 c is a surface in which the normal direction N of the convex portion installation surface 63 c approaches (preferably coincides) with the radial direction R of the high speed side shaft 12 due to elastic deformation of the ring portion 62. It can be said.

In the present embodiment, in the state in which the ring portion 62 is elastically deformed, the convex portion installation surface 63c and the main body inner peripheral surface 63b have the same inner diameter.
Of the peripheral surface of the convex portion 69, a portion that intersects with a straight line drawn from the semicircular center M of the convex portion 69 in the normal direction N of the convex portion installation surface 63c is defined as a specific location Px. In a situation where the normal direction N of the convex portion installation surface 63c coincides with the radial direction R of the high speed side shaft 12, the convex portion 69 and the outer peripheral surfaces 71a to 73a of the rollers 71 to 73 at the specific location Px. Are in contact. That is, each ring side contact location Pa1-Pa3 and specific location Px correspond.

  And the pressing force given toward each roller 71-73 from the convex part 69 by the ring part 62 being elastically deformed so that the front-end | tip part 66 may spread toward the radial direction R outer side of the high speed side shaft 12. The direction of F1 approaches the radial direction R of the high speed side shaft 12, and preferably coincides with it. In addition, in the state in which each ring side contact location Pa1-Pa3 and specific location Px correspond, the direction of the pressing force F1 corresponds with the radial direction R of the high speed side shaft 12. FIG.

  As shown in FIG. 4, the tip inner peripheral surface 63 a is provided at a position protruding inward in the radial direction R of the high speed side shaft 12 from the main body inner peripheral surface 63 b when the ring portion 62 is not elastically deformed. And along the rotation axis direction Z. On the other hand, in the state where the ring portion 62 is elastically deformed, as shown in FIG. 3, the tip inner peripheral surface 63a is inclined so as to gradually increase in diameter toward the tip side.

  Since the tip inner peripheral surface 63a, the main body inner peripheral surface 63b, and the convex portion installation surface 63c are configured as described above, the wall thickness of the ring portion 62 differs depending on the rotation axis direction Z. Specifically, the wall thickness of the tip portion 66 of the ring portion 62 is thicker than the wall thickness of the main body portion 67.

  Further, the continuous portion 68 that is continuous with both the tip portion 66 and the main body portion 67 in the ring portion 62 has a convex portion installation surface 63c. Specifically, a portion corresponding to the continuous portion 68 in the inner peripheral surface 63 of the ring portion 62 is a convex portion installation surface 63c. The wall thickness of the continuous portion 68 gradually increases from the proximal end side of the ring portion 62 toward the distal end side. For this reason, it can be said that the convex part 69 is provided in the location where the wall thickness is thicker than the main body part 67.

  In the present embodiment, the convex portion 69 is in contact with the central portion in the rotational axis direction Z of the high speed side shaft 12 on the outer peripheral surfaces 71a to 73a of the rollers 71 to 73. However, it is not restricted to this, The contact position of the convex part 69 with respect to the outer peripheral surfaces 71a-73a of each roller 71-73 in the rotation axis direction Z is arbitrary.

  As shown in FIG. 1, some of the rollers 71 to 73 protrude beyond the ring portion 62 toward the plate 24 side. That is, a part of the outer peripheral surfaces 71 a to 73 a of the rollers 71 to 73 is not opposed to the inner peripheral surface 63 of the ring portion 62 in the radial direction R of the high speed side shaft 12 and is exposed from the ring portion 62. However, the configuration is not limited to the above configuration, and the ring portion may be configured to face the entire outer peripheral surfaces 71a to 73a of the rollers 71 to 73.

  As shown in FIG. 2A, the rollers 71 to 73, the ring member 60, and the high speed side shaft 12 are unitized in a state where the ring portion 62 is elastically deformed. The three rollers 71 to 73 are rotatably supported. In this case, each of the rollers 71 to 73 and the high speed side shaft 12 are fastened by the ring portion 62 in order to return the ring portion 62 from the elastically deformed state. For this reason, the pressing force F1 resulting from the tightening is applied to the ring side contact portions Pa1 to Pa3, which are the contact portions between the outer peripheral surfaces 71a to 73a of the rollers 71 to 73 and the convex portion 69. Similarly, as shown in FIG. 2B, the shaft side contact portions Pb1 to Pb3, which are contact points between the outer peripheral surfaces 71a to 73a of the rollers 71 to 73 and the outer peripheral surface 12a of the high speed side shaft 12, are also pressed. Pressure F2 is applied.

Here, as shown to Fig.2 (a), each ring side contact location Pa1-Pa3 is extended in the circumferential direction of the high speed side shaft 12 rather than each shaft side contact location Pb1-Pb3.
On the other hand, as shown in FIG. 1, the shaft side contact portions Pb <b> 1 to Pb <b> 3 extend in the rotation axis direction Z. On the other hand, by forming the convex portion 69, the length in the rotation axis direction Z of each ring-side contact portion Pa1 to Pa3 is set in the rotation axis direction Z of each shaft-side contact portion Pb1 to Pb3. It is shorter than the length.

  In addition, the area of each ring side contact location Pa1-Pa3 is compared with the case where the inner peripheral surface of the ring portion is formed to have the same diameter over the rotation axis direction Z of the high speed side shaft 12, As long as it approaches the area of each shaft side contact location Pb1-Pb3, it may be larger or smaller than the area of each shaft side contact location Pb1-Pb3. Moreover, the area of each ring side contact location Pa1-Pa3 and the area of each shaft side contact location Pb1-Pb3 may be the same.

  According to such a configuration, when the ring portion 62 is rotated by the rotation of the low speed side shaft 11 in a situation where the oil is sufficiently supplied to both the contact points Pa1 to Pa3, Pb1 to Pb3, the ring side contact point An oil film (elastic fluid lubrication film (EHL)) is formed at portions corresponding to Pa1 to Pa3. The portions corresponding to the ring side contact portions Pa1 to Pa3 are between the convex portion 69 and the outer peripheral surfaces 71a to 73a of the rollers 71 to 73. In this case, the convex portion 69 and the outer peripheral surfaces 71a to 73a of the rollers 71 to 73 face each other through the oil film. And the rotational force of the ring part 62 is transmitted to the rollers 71-73 via an oil film, and the rollers 71-73 rotate in the same rotation direction.

  Similarly, when the rollers 71 to 73 are rotated, the portions corresponding to the shaft side contact portions Pb1 to Pb3, more specifically, between the outer peripheral surface 12a of the high speed side shaft 12 and the outer peripheral surfaces 71a to 73a of the rollers 71 to 73, respectively. An oil film is also formed. In other words, the outer peripheral surface 12a of the high speed side shaft 12 and the outer peripheral surfaces 71a to 73a of the rollers 71 to 73 are opposed to each other through the oil film. And the rotational force of the rollers 71-73 is transmitted to the high speed side shaft 12 via an oil film, As a result, the high speed side shaft 12 will rotate. In this case, the base portion 61 and the ring portion 62 rotate at the same speed as the low speed side shaft 11, and the rollers 71 to 73 rotate at a higher speed than the low speed side shaft 11. Furthermore, the high-speed side shaft 12 having a shorter diameter than the rollers 71 to 73 rotates at a higher speed than the rollers 71 to 73.

  From the above, power is transmitted from the low speed side shaft 11 to the high speed side shaft 12 by the speed increaser 14, and the high speed side shaft 12 rotates at a higher speed than the low speed side shaft 11.

  In the present embodiment, the centrifugal compressor 10 is configured such that oil circulates in the speed increaser housing 22. Specifically, as shown in FIG. 1, an inflow port 111 into which oil flows is formed in the upper part of the speed increaser housing 22, and a drain for discharging oil is formed in the lower part of the speed increaser housing 22. An outlet 112 is formed. The oil that flows in from the inflow port 111 flows into the speed increaser 14, specifically, the ring portion 62, and is supplied to the contact portions Pa <b> 1 to Pa <b> 3 and Pb <b> 1 to Pb <b> 3. Thereafter, the oil is discharged from the discharge port 112.

  Next, the operation of this embodiment will be described with reference to FIGS. 5 and 6 are diagrams showing a ring unit 200 as a comparison target for the present case. 5 shows the ring part 200 to be compared in a state where it is not elastically deformed, FIG. 6A shows the ring part 200 in a state where it is elastically deformed, and FIG. 6B shows the ring part 200 shown in FIG. FIG.

  As shown in FIG. 5, the inner peripheral surface 201 of the ring portion 200 to be compared is a surface parallel to the rotation axis direction Z in a state where the ring portion 200 is not elastically deformed. In this case, the ring portion 200 has the tip 203 at the high-speed side shaft by the contact between the convex portion 202 provided on the inner peripheral surface 201 of the ring portion 200 and the outer peripheral surfaces 71a to 73a of the rollers 71 to 73. 12 is elastically deformed so as to spread outward in the radial direction R. Then, as shown in FIG. 6A, the inner peripheral surface 201 of the ring portion 200 is inclined with respect to the rotation axis direction Z from the tip to a portion slightly proximal to the convex portion 202.

  In such a state, as shown in FIG. 6B, the first ring-side contact location Pa1 is greatly deviated from the specific location Px. Further, the direction of the pressing force F1 is greatly inclined with respect to the radial direction R of the high speed side shaft 12. In this case, the pressing force F <b> 1 is applied from the convex portion 202 to each of the rollers 71 to 73, but the component in the radial direction R of the high speed side shaft 12 in the pressing force F <b> 1 becomes small, while the rotation axis of the high speed side shaft 12 The component in the direction Z increases. Further, a drag force is applied to the ring portion 200 from each of the rollers 71 to 73 as a reaction of the pressing force F1. In this case, the component in the radial direction R of the high speed side shaft 12 in the reaction of the pressing force F1 decreases, while the component in the rotation axis direction Z of the high speed side shaft 12 increases.

  In this respect, in this embodiment, as shown in FIG. 3, the direction of the pressing force F1 and the radial direction R of the high speed side shaft 12 approach or coincide with each other. The force in the rotation axis direction Z is not easily applied.

  According to the embodiment described above in detail, the following effects are obtained. In the following, for convenience of explanation, the relationship between the first roller 71 and the ring portion 62 among the rollers 71 to 73 will be described. However, the other rollers 72 and 73 have the same effect.

  (1) The speed increaser 14 is arranged to rotate with the rotation of the low-speed side shaft 11, and is disposed inside the ring-shaped part 62, a ring-shaped ring part 62 erected from the base part 61, and the ring part 62. And the first roller 71 provided between the ring portion 62 and the high speed side shaft 12.

  The speed increaser 14 is provided on the inner peripheral surface 63 of the ring portion 62, and includes a convex portion 69 protruding from the inner peripheral surface 63 toward the inner side in the radial direction R of the high speed side shaft 12. And the 1st roller 71 has the outer peripheral surface 71a contact | abutted to both the convex part 69 and the outer peripheral surface 12a of the high speed side shaft 12 at the time of a stationary.

  According to this configuration, the convex portion 69 and the outer peripheral surface 71a of the first roller 71 are in contact with each other, so that the inner peripheral surface of the ring portion is formed to have the same diameter along the rotation axis direction Z of the high speed side shaft 12. Compared with the case where it is made, the area of the 1st ring side contact location Pa1 can be made small. Thereby, the pressure in the 1st ring side contact location Pa1 which is a contact location of the convex part 69 and the 1st roller 71 can be enlarged. Therefore, the oil film can be formed at a portion corresponding to the first ring-side contact portion Pa1 during rotation with relatively small tightening.

Further, according to the present embodiment, it is possible to generate an appropriate pressure at both the contact points Pa1 and Pb1.
More specifically, since the high speed side shaft 12 and the first roller 71 are in contact with each other, the area of the first shaft side contact portion Pb1 tends to be small. Specifically, in the vicinity of the first shaft-side contact portion Pb1, the outer circumferential surface 71a of the first roller 71 and the outer circumferential surface 12a of the high-speed side shaft 12 have opposite directions.

  On the other hand, in the configuration in which the outer peripheral surface 71a of the first roller 71 and the inner peripheral surface 63 of the ring portion 62 are in contact with each other, the first roller 71 is in the vicinity of the first ring-side contact portion Pa1 that is the contact portion between them. The outer peripheral surface 71a and the inner peripheral surface 63 of the ring portion 62 are convex in the same direction. For this reason, the area of the 1st ring side contact location Pa1 tends to become larger than the area of the 1st shaft side contact location Pb1. That is, the pressure at the first ring side contact portion Pa1 tends to be smaller than the pressure at the first shaft side contact portion Pb1. If the pressure at the first ring-side contact point Pa1 is small, the oil film solidified at the time of rotation may not be sufficiently formed, and the power transmission from the ring part 62 to the first roller 71 may not be performed suitably. .

  On the other hand, for example, the tightening by the ring part 62 may be strengthened. However, in this case, since the pressure at the first shaft side contact portion Pb1 also increases, the power loss at the first shaft side contact portion Pb1 increases, or an excessive load is applied to the high speed side shaft 12.

  In this regard, in the present embodiment, the area of the first ring side contact portion Pa1 can be reduced by the convex portion 69, while the area of the first shaft side contact portion Pb1 is not affected by the convex portion 69. Thereby, the pressure in 1st ring side contact location Pa1 can be enlarged, without giving an excessive burden to the high speed side shaft 12. FIG. Therefore, an oil film can be suitably formed in the part corresponding to both contact locations Pa1 and Pb1 during rotation, and power transmission from the ring portion 62 to the high speed side shaft 12 can be suitably performed.

  (2) The ring part 62 has the front-end | tip part 66 on the opposite side to the base part 61 side. In the ring portion 62, the tip portion 66 expands toward the outside in the radial direction R of the high speed side shaft 12 due to the contact between the convex portion 69 and the outer peripheral surface 71 a of the first roller 71. The direction of the pressing force F <b> 1 applied toward the one roller 71 is elastically deformed so as to approach (preferably coincide with) the radial direction R of the high speed side shaft 12. In other words, the ring portion 62 is pushed in the state where the tip portion 66 is elastically deformed so as to spread outward in the radial direction R of the high speed side shaft 12 as compared with the state where the ring portion 62 is not elastically deformed. The direction of the pressure F <b> 1 is configured to approach the radial direction R of the high speed side shaft 12.

  In the configuration in which the convex portion 69 is formed on the inner peripheral surface 63 of the ring portion 62, the tip portion 66 of the ring portion 62 has a high speed side due to the contact between the convex portion 69 and the outer peripheral surface 71 a of the first roller 71. The shaft 12 is elastically deformed so as to spread outward in the radial direction R of the shaft 12. In this case, as described with reference to FIGS. 5 and 6, when the direction of the pressing force F1 is largely inclined with respect to the radial direction R of the high speed side shaft 12, the component in the rotation axis direction Z becomes large.

  In this regard, according to the present embodiment, the direction of the pressing force F1 approaches the radial direction R of the high speed side shaft 12 in consideration of the state in which the ring portion 62 is elastically deformed. Thereby, in the state in which the ring part 62 is elastically deformed, the component in the rotation axis direction Z in the pressing force F1 is reduced. Therefore, the component in the radial direction R of the high speed side shaft 12 can be increased by that amount, and through this, power transmission from the ring portion 62 to the first roller 71 can be performed more suitably.

  In addition, since the component in the rotational axis direction Z in the drag force F1 applied to the first roller 71 and the drag force F1 applied to the ring portion 62 can be reduced, the effect of (1) can be achieved. While ensuring, the position shift to the rotation axis direction Z of the 1st roller 71 and the ring part 62 can be suppressed.

  (3) Particularly, the centrifugal compressor 10 positions the rollers 71 to 73 with respect to the high-speed side shaft 12 in the rotation axis direction Z and the positioning portion 37 that positions the ring portion 62 with respect to the housing 20 in the rotation axis direction Z. A pair of flange portions 96 is provided. In such a configuration, if the component of the pressing force F1 and the drag of the pressing force F1 includes the component in the rotation axis direction Z, a force in the rotation axis direction Z is applied to the pair of flange portions 96 and the positioning portion 37. As a result, there is a concern about deterioration such as wear. On the other hand, according to this embodiment, since it can suppress that the force of the rotation axis direction Z is provided to a pair of flange part 96 and the positioning part 37, the said deterioration can be suppressed.

  (4) The inner peripheral surface 63 of the ring portion 62 has a convex portion installation surface 63c on which the convex portion 69 is installed. The convex portion installation surface 63c is elastically deformed so that the tip portion 66 of the ring portion 62 spreads outward in the radial direction R of the high speed side shaft 12, whereby the normal direction N of the convex portion installation surface 63c is changed to the high speed side shaft. It is a surface that approaches (preferably matches) 12 radial directions R. In other words, the convex portion installation surface 63c is in a state in which the tip portion 66 is elastically deformed so as to spread outward in the radial direction R of the high speed side shaft 12 rather than the state in which the ring portion 62 is not elastically deformed. The surface is configured to approach the rotation axis direction Z of the high-speed side shaft 12. According to such a configuration, the direction of the pressing force F <b> 1 is brought close to the radial direction R of the high speed side shaft 12 in a state where the distal end portion 66 is elastically deformed so as to spread outward in the radial direction R of the high speed side shaft 12. Can do. Thereby, effects (2) and the like can be obtained with a relatively simple configuration.

  (5) The convex portion 69 has an annular shape extending in the circumferential direction of the ring portion 62. Thereby, irrespective of the rotation position of the ring part 62, the stable pressing force F1 can be given with respect to the 1st roller 71, and the stable pressure is maintained in the 1st ring side contact location Pa1 through it. Can do.

  (6) The convex portion 69 has a semicircular cross section when cut in a direction orthogonal to the circumferential direction of the ring portion 62. According to such a configuration, since the area of the first ring side contact portion Pa1 can be further reduced, the pressure at the first ring side contact portion Pa1 can be further increased.

  (7) The ring part 62 includes a main body part 67 and a continuous part 68 having a wall thickness larger than that of the main body part 67. The convex portion 69 is installed on the convex portion installation surface 63 c corresponding to the continuous portion 68 in the inner peripheral surface 63 of the ring portion 62. Thereby, weight reduction of the ring part 62 can be achieved, ensuring required pressing force F1, F2.

  (8) The convex portion 69 is in contact with the central portion of the outer peripheral surface 71 a of the first roller 71 in the rotational axis direction Z of the high speed side shaft 12. As a result, it is possible to suppress the occurrence of pressure bias such that the pressure at the first shaft side contact portion Pb1 becomes larger on the other end side than on the one end side in the rotation axis direction Z.

  In addition, the load applied to both roller bearings 94 and 95 that rotatably support the first roller 71 can be made closer, and the situation in which one of the both roller bearings 94 and 95 deteriorates early is suppressed. it can.

  (9) The centrifugal compressor 10 includes an electric motor 13 that rotates the low-speed shaft 11, an impeller 52 that is attached to the high-speed shaft 12, and the speed increaser 14. Thereby, the impeller 52 can be rotated at a higher rotational speed than the drive rotational speed of the electric motor 13. And the centrifugal compressor 10 can be operated suitably through performing the power transmission from the ring part 62 to the high speed side shaft 12 suitably.

In addition, you may change the said embodiment as follows.
The convex part is not limited to a semicircular cross-sectional shape when cut in a direction orthogonal to the circumferential direction of the ring part 62. For example, as shown in FIG. 7, the convex portion 120 may have a trapezoidal cross section when cut in a direction orthogonal to the circumferential direction of the ring portion 62. In this case, the tip surface 121 of the convex portion 120 is configured such that the tip surface 121 and the outer peripheral surfaces 71a to 73a of the rollers 71 to 73 are in contact with each other in a state where the ring portion 62 is elastically deformed. Good. Specifically, as shown in FIG. 8, the distal end surface 121 of the convex portion 120 has a convex portion that gradually decreases in diameter from the proximal end side of the ring portion 62 toward the distal end side in a state where it is not elastically deformed. The taper surface may be inclined at the same inclination angle as the installation surface 63c. However, focusing on the point that the area of the contact portion can be reduced, the cross-sectional shape when cut in the direction orthogonal to the circumferential direction of the ring portion 62 is preferably semicircular rather than trapezoidal.

  In the embodiment, the convex portion 69 is an annular shape extending in the circumferential direction of the ring portion 62, but is not limited thereto. For example, the convex portion may be hemispherical. In this case, a plurality of convex portions may be provided side by side in the circumferential direction. According to such a configuration, it is possible to realize contact between the protrusions, and therefore it is possible to further reduce the area of the ring side contact portions Pa1 to Pa3.

  The convex portion installation surface 63c is a part of the inner peripheral surface 63 of the ring portion 62, but the whole may be the convex portion installation surface 63c. In short, the convex portion installation surface 63 c only needs to constitute at least a part of the inner peripheral surface 63 of the ring portion 62.

A specific configuration for positioning the ring portion 62 in the rotation axis direction Z and a specific configuration for positioning the rollers 71 to 73 in the rotation axis direction Z are arbitrary.
○ The wall thickness of the ring portion 62 may be constant. For example, the diameter corresponding to the continuous part 68 of the outer peripheral surface 64 of the ring part 62 is similarly reduced in diameter corresponding to the fact that the convex part installation surface 63c is reduced in diameter from the proximal end side toward the distal end side. Also good.

  ○ With respect to the installation position of the convex portion 69, the tip portion 66 spreads outward in the radial direction R of the high speed side shaft 12 by the contact between the convex portion 69 and the outer peripheral surfaces 71 a to 73 a of the rollers 71 to 73. What is necessary is just to be able to elastically deform and the specific position is arbitrary.

  The base part 61 and the low speed side shaft 11 may be integrally formed, and the ring part 62 may be attached to the base part 61. Moreover, the base part 61, the ring part 62, and the low speed side shaft 11 may be separate from each other and connected to each other.

○ The specific configuration for supplying oil is arbitrary. For example, an oil pump that circulates oil in the gearbox housing 22 may be provided.
The number of rollers 71 to 73 is not limited to three and is arbitrary.

A configuration in which at least one of the rollers 71 to 73 can move according to the torque of the low-speed shaft 11 may be employed.
The diameter of each roller 71-73 may be set the same. In this case, the high speed side shaft 12 and the ring member 60 (low speed side shaft 11) may be disposed on the same axis.

The specific configuration of the compression unit 15 is not limited to the configuration having the impeller 52, and may be arbitrary, for example, a vane type or a scroll type.
The target for mounting the speed increaser 14 is not limited to the centrifugal compressor 10 and is arbitrary. For example, it may be mounted on a fluid machine that does not compress fluid such as a pump.

The mounting target of the speed increaser 14 and the centrifugal compressor 10 is not limited to the vehicle and is arbitrary.
○ The application target of the centrifugal compressor 10 and the fluid to be compressed are arbitrary. For example, the centrifugal compressor 10 may be used in an air conditioner, and the fluid to be compressed may be a refrigerant.

O You may combine the said embodiment and another example suitably.
Next, a preferable example that can be grasped from the embodiment and another example will be described below.
(A) The convex portion installation surface is in a rotational axis direction of the high speed side shaft so that the diameter gradually decreases from the base portion side toward the tip portion side in a state where the ring portion is not elastically deformed. And the tip portion is elastically deformed so as to spread outward in the radial direction of the high speed side shaft, whereby the inclination angle of the high speed side shaft with respect to the rotational axis direction is reduced or the inclination angle is zero. The speed increasing device according to claim 2, wherein the speed increasing device is a surface.

  (B) a housing for housing the low speed side shaft, the high speed side shaft, the electric motor, the speed increaser, and the impeller; and positioning of the ring portion with respect to the housing in a rotation axis direction of the high speed side shaft. The centrifugal compressor according to claim 5, further comprising: a first positioning portion; and a second positioning portion that positions the roller with respect to the high speed side shaft in a rotation axis direction of the high speed side shaft.

  DESCRIPTION OF SYMBOLS 10 ... Centrifugal compressor, 11 ... Low speed side shaft, 12 ... High speed side shaft, 12a ... Outer peripheral surface of high speed side shaft, 13 ... Electric motor, 14 ... Speed increaser, 15 ... Compression part, 37 ... Positioning part, 52 ... Impeller, 60 ... Ring member, 61 ... Base part, 62 ... Ring part, 63 ... Inner peripheral surface of ring part, 63c ... Convex part installation surface, 66 ... Tip part of ring part, 69, 120 ... Convex part, 71- 73: roller, 71a to 73a ... outer peripheral surface of roller, 96 ... flange, Pa1 to Pa3 ... ring side contact location, Pb1 to Pb3 ... shaft side contact location, F1 ... pressing force.

Claims (5)

As what rotates with the rotation of the low speed side shaft, a plate-like base portion and an annular ring portion standing up from the base portion,
A high speed side shaft disposed inside the ring portion;
A convex portion provided on the inner peripheral surface of the ring portion and projecting from the inner peripheral surface toward the radially inner side of the high-speed side shaft;
A roller provided between the ring portion and the high speed side shaft, and having an outer peripheral surface that abuts both the convex portion and the outer peripheral surface of the high speed side shaft;
With
The ring part has a tip part which is an end part opposite to the base part side,
In the ring portion, since the convex portion and the outer peripheral surface of the roller are in contact with each other, the tip portion extends toward the outer side in the radial direction of the high-speed side shaft, and from the convex portion toward the roller. A speed increaser characterized in that it is elastically deformed so that the direction of the applied pressing force approaches the radial direction of the high speed side shaft. The inner peripheral surface of the ring portion has a convex portion installation surface on which the convex portion is installed,
2. The convex portion installation surface is a surface in which a normal direction approaches a radial direction of the high speed side shaft by elastically deforming the tip portion so as to spread outward in a radial direction of the high speed side shaft. Gearbox as described in   The speed increaser according to claim 1, wherein the convex portion is an annular shape extending in a circumferential direction of the ring portion.   The speed increaser according to claim 3, wherein the convex portion has a semicircular cross section when cut in a direction orthogonal to a circumferential direction of the ring portion. A speed increaser according to any one of claims 1 to 4,
An electric motor for rotating the low-speed side shaft;
An impeller attached to the high speed side shaft;
A centrifugal compressor characterized by comprising:

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