JP2008032189A - Speed-increasing gear and reduction gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To enhance lubricating performance and cooling performance by oil in a speed-increasing gear. <P>SOLUTION: In this speed-increasing gear 20, oil injection holes 64, 65 are formed at a carrier 50 for supporting intermediate rollers 31 to 33. The oil injected from the oil injection holes 64, 65 is directly supplied to a rolling contact surface on which an output shaft 12 is brought into contact with the intermediate rollers 31 to 33 or a rolling contact surface on which an outer ring 27 is brought into contact with the intermediate rollers 31 to 33. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a speed increaser and a speed reducer.

As a speed increaser used for a supercharger or the like, as described in Patent Document 1, the input shaft is rotated by rotation of the crankshaft of the engine, and the rotation of the input shaft is increased by the speed increaser to be an output shaft. In some cases, the intake air is supercharged by the rotation of an impeller coupled to the output shaft.
JP 2003-201850

  The speed increaser described in Patent Document 1 uses a planetary friction roller mechanism, a flexible outer ring rotated by an input shaft, and a friction roller such as a sun shaft coupled to an output shaft. And a plurality of planetary rollers (intermediate rollers) interposed between the outer ring and the friction roller, and the planetary roller and the friction roller are tightened through elastic deformation of the outer ring.

  As shown in FIG. 14, the conventional speed increaser incorporates an oil pump 100 for circulating traction oil therein, and the oil pump 100 is a rotor fixed to the input shaft 101 around the input shaft 101. A plurality of vanes are provided on the outer periphery of the plate, and the vane is configured by a vane pump or the like surrounded by a base plate, a side plate, and a cam ring, and is driven by the input shaft 11 or the output shaft.

  The traction oil discharged from the oil pump 100 lubricates and cools the bearing 111 and the oil seal 112 around the input shaft 101, is drilled in the diameter direction to the axial direction of the input shaft 101, and is inserted into the hole 120 </ b> A of the carrier 120. From the oil passage 121 that opens to the shaft end surface, flows from the shaft end surface of the output shaft 103 inserted into the hole 120B of the carrier 120 to the oil passage 122 that is drilled in the axial direction, and further intersects the oil passage 122. From the distribution path 123 formed in the diameter direction of the output shaft 103, the centrifugal force accompanying the rotation of the output shaft 103 scatters and flows out to the outer peripheral side.

  The oil flowing out from the distribution path 123 that opens to the driven-side cylindrical surface of the output shaft 103 lubricates and cools the driven-side cylindrical surface of the output shaft 103 and the power transmission cylindrical surface of the intermediate roller 102.

  The oil flowing out from the distribution path 123 near both sides of the driven side cylindrical surface of the output shaft 103 lubricates and cools the thrust contact portion between both side flanges of the output shaft 103 and both end surfaces of the power transmission cylindrical surface of the intermediate roller 102. To do. The oil flowing out from the distribution path 123 intersecting the closed end side of the oil path 122 lubricates and cools the oil seal 113 around the output shaft 103.

  However, in the conventional speed increaser, oil is passed through an oil passage drilled in the output shaft, and this oil flows out by using the centrifugal force of rotation of the output shaft, and has the following problems. .

  (1) Oil is blown from the oil passage of the output shaft by the rotation of the output shaft. When the output shaft becomes high, the oil that flows out of the output shaft becomes mist-like by the rotation of the output shaft and the intermediate roller. It becomes difficult to form an oil film on the rolling contact surface where the output shaft and the intermediate roller are in contact.

  (2) Oil flows out only from the oil passage of the output shaft, and there is a limit to the amount of oil supplied.

  An object of the present invention is to improve lubrication and cooling performance with oil in a speed increaser.

  Another object of the present invention is to improve lubrication and cooling performance with oil in a reduction gear.

  According to the first aspect of the present invention, when the rotation of the input shaft is accelerated and transmitted to the output shaft, the outer ring is rotated by the input shaft and is eccentric with respect to the output shaft, and the outer peripheral surface of the output shaft. The width on the radial direction of the output shaft between the drive-side cylindrical surface and the drive-side cylindrical surface that is the inner peripheral surface of the outer ring is disposed in an annular space where the width in the radial direction of the output shaft is not the same in the circumferential direction of the output shaft. And a plurality of intermediate rollers having a driven cylindrical surface and a power transmission cylindrical surface that frictionally contacts the driven cylindrical surface, and at least one intermediate roller is disposed around the output shaft. In the speed increaser, which is a movable roller that can move in the direction and the radial direction, an oil injection hole is provided in the carrier that supports the intermediate roller, and the oil that is injected from the oil injection hole is directly connected to the output shaft and the intermediate roller. Contacting rolling surface or outside And it is obtained so as to provide the rolling contact surface of the intermediate roller is in contact.

  According to a second aspect of the present invention, in the first aspect of the present invention, the inner mounting portion of the connecting member made of a cup-like body is fixed to the input shaft, the outer mounting portion of the connecting member is fixed to the outer ring, and the connecting member A flexible membrane plate is provided between the inner mounting portion and the outer mounting portion, and the coupling member cup-shaped body covers one side of the carrier and the intermediate roller to guide the oil flow to the inner peripheral surface of the outer ring. The flow path is partitioned.

  The invention of claim 3 further includes an oil pump driven by the input shaft or the output shaft in the invention of claim 1 or 2, and the oil pump has a pump chamber formed between the rotor and the cam ring by a plate. The suction port provided in the plate is arranged inside the pump chamber in the radial direction, the inlet corner facing the suction port of the rotor is chamfered, and the discharge port provided in the plate is arranged radially outside the pump chamber. In addition, the corners of the exit facing the discharge port of the cam ring are chamfered.

  A fourth aspect of the invention is a supercharger using the speed increaser according to any one of the first to third aspects.

  According to the invention of claim 5, when the rotation of the input shaft is decelerated and transmitted to the output shaft, the outer ring which is arranged eccentrically with respect to the input shaft and rotates the output shaft, and the driving side cylinder which is the outer peripheral surface of the input shaft Between the surface and the driven cylindrical surface that is the inner peripheral surface of the outer ring is disposed in an annular space in which the width in the radial direction of the input shaft is not the same in the circumferential direction of the input shaft. And a plurality of intermediate rollers as power transmission cylindrical surfaces that are in frictional contact with the driven cylindrical surface and the driven cylindrical surface, and at least one intermediate roller is disposed in the circumferential direction of the input shaft and In a reduction gear that is a movable roller that can move in the radial direction, an oil injection hole is provided in a carrier that supports the intermediate roller, and the oil injected from the oil injection hole directly contacts the input shaft and the intermediate roller. Face or outer ring and inside Those in which the roller has to be supplied to the rolling contact surface in contact.

  According to a sixth aspect of the present invention, in the fifth aspect of the present invention, further, an inner mounting portion of a connecting member made of a cup-like body is fixed to the output shaft, and an outer mounting portion of the connecting member is fixed to an outer ring, and the connecting member A flexible membrane plate is provided between the inner mounting portion and the outer mounting portion, and the coupling member cup-shaped body covers one side of the carrier and the intermediate roller to guide the oil flow to the inner peripheral surface of the outer ring. The flow path is partitioned.

  The invention of claim 7 further comprises an oil pump driven by the input shaft or the output shaft in the invention of claim 5 or 6, wherein the oil pump comprises a plate with a pump chamber formed between the rotor and the cam ring. The suction port provided in the plate is arranged inside the pump chamber in the radial direction, the inlet corner facing the suction port of the rotor is chamfered, and the discharge port provided in the plate is arranged radially outside the pump chamber. In addition, the corners of the exit facing the discharge port of the cam ring are chamfered.

(Claim 1)
(a) An oil injection hole is provided in the carrier supporting the intermediate roller, and the oil injected from the oil injection hole directly contacts the rolling contact surface where the output shaft and the intermediate roller are in contact, or the outer ring and the intermediate roller are in contact with each other. By supplying to the rolling contact surface, the atomization of the oil hardly occurs, and the oil film formation on the rolling contact surface becomes easy. By making the oil injection direction from the oil injection hole the same direction along the rotation direction of the output shaft, the intermediate roller, and the outer ring, the oil film can be formed more reliably.

  (b) A plurality of intermediate rollers are supported in the speed increaser, and oil injection holes are provided at a plurality of locations on the carrier that are located over a wide range in the speed increaser, and a plurality of oil supply points are provided from the oil injection holes. Oil can be supplied to each of these, and the amount of oil supply can be increased.

(Claim 2)
(c) The cup-shaped body of the connecting member covered one side of the carrier and the intermediate roller, and partitioned an oil flow path for guiding the oil flow to the inner peripheral surface of the outer ring. Therefore, the oil supplied to the inside of the speed increaser is effectively guided to the rolling contact surface of the outer ring and the intermediate roller by the rotating centrifugal force of the output shaft or the like and the cup-shaped body, and the oil film is more reliably secured by the rolling contact surface. Can be formed.

(Claim 3)
(d) In the oil pump, the suction port provided in the plate was disposed radially inward from the pump chamber, and the inlet corner facing the suction port of the rotor was chamfered. Therefore, the oil suction efficiency can be improved by the centrifugal force exerted by the rotor on the oil sucked into the pump chamber from the suction port. Further, by chamfering the inlet corner portion of the rotor, the suction performance exerted by the inlet corner portion of the rotor on the oil sucked into the pump chamber from the suction port can be reduced.

  Further, the oil discharge efficiency can be improved by the centrifugal force exerted by the rotor on the oil discharged from the pump chamber to the discharge port. Further, by chamfering the outlet corner of the cam ring, the discharge resistance exerted by the outlet corner of the cam ring on the oil discharged from the pump chamber to the outlet can be reduced.

(Claim 4)
(e) The above-described (a) to (d) can be realized in the turbocharger.

(Claim 5)
(f) The carrier supporting the intermediate roller is provided with an oil injection hole, and the oil injected from the oil injection hole directly contacts the rolling contact surface where the input shaft and the intermediate roller are in contact, or the outer ring and the intermediate roller are in contact with each other. By supplying to the rolling contact surface, the atomization of the oil hardly occurs, and the oil film formation on the rolling contact surface becomes easy. By making the oil injection direction from the oil injection hole the same direction along the rotation direction of the input shaft, the intermediate roller, and the outer ring, the oil film can be formed more reliably.

  (g) A plurality of intermediate rollers are supported in the speed reducer, and oil injection holes are provided at a plurality of locations of the carrier that are located over a wide range in the speed reducer, and each of the oil supply points is provided from the oil injection holes. Oil can be supplied to the tank, and the amount of oil supply can be increased.

(Claim 6)
(h) The cup-shaped body of the connecting member covered one side of the carrier and the intermediate roller, and partitioned an oil passage for guiding the oil flow to the inner peripheral surface of the outer ring. Therefore, the oil supplied to the inside of the speed increaser is effectively guided to the rolling contact surface of the outer ring and the intermediate roller by the rotating centrifugal force of the output shaft or the like and the cup-like body, and the oil film is more reliably secured by the rolling contact surface. Can be formed.

(Claim 7)
(i) In the oil pump, the suction port provided in the plate was disposed radially inward from the pump chamber, and the inlet corner facing the suction port of the rotor was chamfered. Therefore, the oil suction efficiency can be improved by the centrifugal force exerted by the rotor on the oil sucked into the pump chamber from the suction port. Further, by chamfering the inlet corner portion of the rotor, the suction performance exerted by the inlet corner portion of the rotor on the oil sucked into the pump chamber from the suction port can be reduced.

  Further, the oil discharge efficiency can be improved by the centrifugal force exerted by the rotor on the oil discharged from the pump chamber to the discharge port. Further, by chamfering the outlet corner of the cam ring, the discharge resistance exerted by the outlet corner of the cam ring on the oil discharged from the pump chamber to the outlet can be reduced.

  1 is a cross-sectional view showing a supercharger, FIG. 2 is another cross-sectional view showing the supercharger, FIG. 3 is another cross-sectional view showing the supercharger, and FIG. 4 is another cross-sectional view showing the supercharger. 5 is a sectional view taken along line VV in FIG. 1, FIG. 6 is a sectional view taken along line VI-VI in FIG. 1, FIG. 7 is a sectional view taken along line VII-VII in FIG. 9 is an enlarged cross-sectional view of the main part of FIG. 1, FIG. 10 is a side view of the oil pump, FIG. 11 is an exploded perspective view of the oil pump, and FIG. 12 is a cross-section of the oil pump. ) Is a sectional view taken along line AA in FIG. 10, (B) is a sectional view taken along line BB in FIG. 10, FIG. 13 is a sectional view showing a conventional oil pump, and FIG. 14 is a sectional view showing a conventional example. 15 is a cross-sectional view showing the speed reducer, FIG. 16 is another cross-sectional view showing the speed reducer, FIG. 17 is another cross-sectional view showing the speed reducer, FIG. 18 is another cross-sectional view showing the speed reducer, and FIG. Is the XIX-XIX line in Fig. 15. 20 is a sectional view taken along line XX-XX in FIG. 15, FIG. 21 is a sectional view taken along line XXI-XXI in FIG. 15, FIG. 22 is a sectional view showing a connecting member, and FIG. It is a principal part expanded sectional view.

  The supercharger 10 for an automobile shown in FIGS. 1 to 7 accelerates the rotation of the input shaft 11 by the speed increaser 20 and transmits it to the output shaft 12. The input shaft 11 has a pulley driven by engine output. 13 is fixed, and an impeller 14 is provided on the output shaft 12.

  In the supercharger 10, a compressor housing 16 is fitted in a center plate 15 with an inlay and fixed. The compressor housing 16 accommodates the impeller 14 and includes a suction port 16A, a supercharging passage 16B, and a scroll 16C.

  The speed increaser 20 is a friction roller type speed increaser that uses a wedge action. The front housing 21 and the compressor housing 16 constitute an outer shell of the turbocharger, and the front housing 21 is fitted in the center plate 15 with an inlay. At the same time, the compressor housing 16 is fitted into the center plate 15 by inlay fitting.

  The speed increaser 20 penetrates and supports the input shaft 11 through the bearings 23 and 24 in the front housing 21, and surrounds the input shaft 11 by an oil seal 25 inserted at a position between the bearings 23 and 24 of the front housing 21. And the pulley 13 is fixed to the end of the input shaft 11 protruding from the front housing 11 by a bolt (or a nut) 17. The speed increaser 20 seals the periphery of the output shaft 12 with an oil seal 26 inserted into the center plate 15, and the impeller 14 is fixed to the end of the output shaft 12 with a nut 18.

  The step-up gear 20 has an outer ring 27 that is rotated by the input shaft 11. In this embodiment, the input shaft 11 and the outer ring 27 are arranged substantially coaxially, and the input shaft 11, the outer ring 27 and the output shaft 12 are arranged eccentrically. The input shaft 11 and the outer ring 27 are connected by a connecting member 28 as will be described later.

  The speed increaser 20 includes three intermediate rollers 31 in an annular space between a driven cylindrical surface 12A that is an outer peripheral surface of the output shaft 12 and a driving side cylindrical surface 27A that is an inner peripheral surface of the outer ring 27. 32 and 33 are arranged. The outer peripheral surfaces of the three intermediate rollers 31, 32, 33 are power transmission cylindrical surfaces 31A, 32A, 33A that are in frictional contact with the driven cylindrical surface 12A of the output shaft 12 and the driving cylindrical surface 27A of the outer ring 27. The

  In the present embodiment, one of the three intermediate rollers 31, 32, 33 has a larger diameter than the other two intermediate rollers 32, 33, and as a result, the driven-side cylinder of the output shaft 12. When the above-described annular space is formed between the surface 12A and the driving-side cylindrical surface 27A of the outer ring 27, the width of the annular space in the radial direction of the output shaft 12 is made the same in the circumferential direction of the output shaft 12. At least one of the three intermediate rollers 31, 32, 33, in this embodiment, the intermediate roller 33 can be moved in the circumferential direction and the radial direction of the output shaft 12 in the annular space. As a result, all the intermediate rollers 31 to 33 can be pressed against the output shaft 12 and the outer ring 27, and the rotation of the input shaft 11 and the outer ring 27 is increased through the intermediate rollers 31 to 33. Transmission to the output shaft 12 is enabled.

  As shown in FIGS. 1 to 7, the speed increaser 20 fastens the outer ring 27 to the outer periphery of all the intermediate rollers 31 to 33 in an elastically deformed state (elastically expanded state). The driving side cylindrical surface 27A) is brought into contact with the outer peripheral surface (driven side cylindrical surface 12A) of the output shaft 12 in a state of elastic tension.

  At this time, the movable roller 33 can move in the circumferential direction and the radial direction of the output shaft 12 within a range of a guide groove 34 provided in the center plate 15 and a carrier 50 described later. In a state where the springs 35 and 36 inserted into the holes provided in the center plate 15 and the carrier 50 are backed up by the caps 35A and 36A screwed to the center plate 15 and the carrier 50, the pressers 35B and 36B are The bearings 43A and 53A loaded on the both end support shafts of the movable roller 33 are pressed against. The movable roller 33 can move in the circumferential direction and the radial direction of the output shaft 12 within the range of the guide groove 34 while being urged by the springs 35 and 36.

  In the manufacturing stage of the speed increaser 20, for example, a pressing claw for gripping a workpiece of a lathe is used, and three circumferential positions of the outer ring 27 are pressed by the same number of three pressing claws as all the intermediate rollers 31 to 33. Is elastically deformed into a generally triangular shape. Thus, a diameter-reduced portion is formed in a portion corresponding to the pressing claw in the inner circumference of the outer ring 27, and a diameter-enlarged portion is formed in a portion sandwiched between adjacent reduced-diameter portions. Each of the intermediate rollers 31 to 33 is inserted, and then the outer ring 27 can be fastened to the outer periphery of all the intermediate rollers 31 to 33 by releasing the pressing by the pressing claws.

Therefore, the supercharger 10 can operate as follows (FIGS. 1 to 7).
(1) When driving force from the engine is input to the pulley 13, this driving force is transmitted from the input shaft 11 to the outer ring 27. At this time, the outer ring 27 and the output shaft 12 are eccentric as described above, and the width of the annular space in the radial direction of the output shaft 12 is not the same in the circumferential direction of the output shaft 12, so that the speed of the engine increases. When the outer ring 27 to which a large amount of power is transmitted rotates in the direction a, the movable roller 33 is in a direction in which the width of the annular space between the outer ring 27 and the output shaft 12 becomes narrower, and the wedge action acts on the movable roller 33. The large pressing force is applied between the driven cylindrical surface 12A of the output shaft 12, the driving cylindrical surface 27A of the outer ring 27, and the power transmission cylindrical surfaces 31A to 33A of the intermediate rollers 31 to 33. c. Due to this large pressing force c, a large frictional force is generated between the driven side cylindrical surface 12A of the output shaft 12, the driving side cylindrical surface 27A of the outer ring 27, and the power transmission cylindrical surfaces 31A to 33A of the intermediate rollers 31 to 33, The large driving force transmitted to the outer ring 27 is transmitted to the output shaft 12, and the output shaft 12 rotates at high speed in the direction d. Due to the high speed rotation of the output shaft 12, the impeller 14 fixed to the output shaft 12 rotates at high speed, and a large amount of air sucked from the suction port 16A of the compressor housing 16 is supercharged to the engine via the supercharging passage 16B and the scroll 16C. Is done.

  (2) When the driving force transmitted from the input shaft 11 to the outer ring 27 decreases due to the deceleration of the engine, the movable roller 33 resists the springs 35 and 36 and the annular space between the outer ring 27 and the output shaft 12 is It is a direction in which the width increases, and is displaced in the direction opposite to b which weakens the wedge action on the movable roller 33, and the driven side cylindrical surface 12A of the output shaft 12, the driving side cylindrical surface 27A of the outer ring 27, and the intermediate rollers 31 to 31. 33 to reduce the pressing force c generated between the power transmission cylindrical surfaces 31A to 33A, and to transmit power to the driven cylindrical surface 12A of the output shaft 12, the driving cylindrical surface 27A of the outer ring 27, and the intermediate rollers 31 to 33. The frictional force generated between the cylindrical surfaces 31A to 33A is reduced, the output shaft 12 is rotated at a low speed in the direction d, and the required amount of air is supercharged to the engine.

  When the driving force from the engine becomes excessive, the movable roller 33 abuts with one end groove surface (stopper surface) of the guide groove 34 in the direction b to restrict the upper limit of the pressing force c, and the speed increaser. 20 damage is prevented. When the driving force from the engine becomes excessive, the movable roller 33 abuts the other end groove surface (stopper surface) of the guide groove 34 in the direction opposite to b, and regulates the lower limit of the pressing force c. Power transmission from the shaft 11 to the output shaft 12 is maintained.

  Hereinafter, in the speed increaser 20 of the supercharger 10, (A) the connection structure of the input shaft 11 and the outer ring 27, (B) the support structure of the intermediate rollers 31 to 33, and (C) the axial position of the output shaft 12 are regulated. (D) Oil supply structure will be described.

(A) Connection Structure of Input Shaft 11 and Outer Ring 27 The speed increaser 20 connects the input shaft 11 and the outer ring 27 by a connecting member 28 as shown in FIGS. The connecting member 28 is provided between a boss-shaped inner mounting portion 28A fixed to the input shaft 11, a ring-shaped outer mounting portion 28B fixed to the outer ring 27, and the inner mounting portion 28A and the outer mounting portion 28B. And a flexible portion 28C. The flexible portion 28C is made of a flexible film plate, and its plate surface extends along the rotation direction of the input shaft 11 and the outer ring 27, and in this embodiment, extends in a continuous rotation surface shape.

  Specifically, as shown in FIG. 8, the connecting member 28 generally forms a cup-shaped body 29, an inner mounting portion 28 </ b> A is provided at the center of the bottom 29 </ b> A of the cup-shaped body 29, and the opening of the side wall 29 </ b> B of the cup-shaped body 29 is opened. The outer mounting portion 28B is provided in the portion, and the corner portion 29C where the bottom portion 29A of the cup-shaped body 29 and the side wall 29B intersect and the side wall 29B are defined as the flexible portion 28C. In the present embodiment, the corner portion 29C, the side wall 29B, and the portion of the bottom portion 29A near the corner portion 29C are set as the flexible portion 28C, and the portion near the inner mounting portion 28A of the bottom portion 29A is thicker than the flexible portion 28C. The waist strength in the axial direction of the body 29 can be ensured.

  The inner mounting portion 28 </ b> A of the connecting member 28 is screwed and fixed to the outer periphery of the shaft end portion of the input shaft 11 located inside the front housing 21. The outer mounting portion 28B of the connecting member 28 is provided with an annular thin portion 27C on the side portion on one end side in the width direction of the outer ring 27, in this embodiment, on one end side of the main body portion 27B that forms the drive side cylindrical surface 27A of the outer ring 27. Are fixed by being screwed to the outer periphery of the thick annular mounting portion 27D joined together. By fixing the connecting member 28 to the side portion of the outer ring 27, the outer diameter of the gearbox 20 is reduced. The attachment part 27D of the outer ring 27 to which the connecting member 28 is fixed is separated from the main body part 27B by the thin annular part 27C, and the main body part 27B changes the elastic deformation state with respect to the outer periphery of each of the intermediate rollers 31 to 33 to the presence of the annular attachment part 27D. Regardless, it is generally uniform in the width direction of the main body 27B. A plurality of circumferential positions of the annular thin portion 27C are provided with tool locking holes 27E for preventing the outer ring 27 from rotating when the connecting member 28 and the input shaft 11 are attached to and removed from the outer ring 27. .

According to the present embodiment, the following operational effects can be obtained.
(a) The connecting member 28 that connects the input shaft 11 and the outer ring 27 is fixed to the input shaft 11 and the outer ring 27, and there is no place to contact or separate between the input shaft 11 or the outer ring 27. Therefore, the connecting member 28 does not make a hitting sound with the input shaft 11 or the outer ring 27 and does not cause sliding wear, so that the rotational force of the input shaft 11 can be stably transmitted to the outer ring 27.

  (b) In the connecting member 28, the flexible portion 28 </ b> C provided between the inner attachment portion 28 </ b> A fixed to the input shaft 11 and the outer attachment portion 28 </ b> B fixed to the outer ring 27 is formed in the axial direction of the outer ring 27 with respect to the input shaft 11. While restricting the position, (i) the outer mounting portion 28B can flexibly follow the elastic deformation in the radial direction of the outer ring 27, and (ii) the misalignment between the input shaft 11 and the outer ring 27 can be absorbed. .

  (c) The flexible portion 28C of the connecting member 28 is made of a flexible membrane plate, and the flexible membrane plate is formed by extending the plate surface in the rotation direction of the input shaft 11 and the outer ring 27. The rotational force of the input shaft 11 can be reliably transmitted to the outer ring 27 while performing the action (b).

  (d) The connecting member 28 generally forms a cup-shaped body 29, an inner mounting portion 28 A is provided at the center of the bottom 29 A of the cup-shaped body 29, and an outer mounting portion 28 B is provided at the opening of the side wall 29 B of the cup-shaped body 29. The corner portion 29C where the bottom 29A of the cup 29 and the side wall 29B intersect, and the side wall 29B are formed as the flexible portion 28C. Accordingly, the cup-shaped body 29 has a cup-like shape while restricting the axial position of the outer ring 27 relative to the input shaft 11 to a fixed position by the balance of the overall strength of the cup-shaped body 29, particularly the waist strength of the bottom 29A around the inner mounting portion 28A. Due to the flexibility of the corner portion 29C and the side wall 29B of the body 29, the outer mounting portion 28B can be easily deformed in the radial direction and the axial direction, and (i) the outer mounting portion 28B is flexible to elastic deformation in the radial direction of the outer ring 27. (Ii) The axial misalignment between the input shaft 11 and the outer ring 27 can be absorbed.

  (e) The outer mounting portion 28B of the connecting member 28 is fixed to the side portion on one end side in the width direction of the outer ring 27, whereby the outer mounting portion 28B of the connecting member 28 is fixed to the outer peripheral portion of the outer ring 27. The outer diameter size of the gearbox 20 can be reduced as compared with that of the gearbox.

  (f) The above-described (a) to (e) can be realized in the speed increaser 20 of the supercharger 10.

(B) Support Structure of Intermediate Rollers 31-33 The speed increasing device 20 has the carrier 50 assembled to the center plate 15 and the bearings 41A, 42A, 43A loaded on the one end support shafts of the intermediate rollers 31-33. The bearings 51A, 52A, 53A loaded on the other end support shaft are supported by the bearing holes 51, 52, 53 provided in the carrier 50.

  The carrier 50 is fixed to the center plate 15 by fastening each of the three legs 54 of the carrier 50 to the center plate 15 with bolts 55. The center plate 15 is provided with a hole 15A at the center portion through which the intermediate portion of the output shaft 12 is inserted and the oil seal 26 is inserted. The carrier 50 has a hole 50A through which the end of the input shaft 11 (the inner mounting portion 28A of the connecting member 28 fixed to the input shaft 11) passes, and a hole 50B through which the end of the output shaft 12 passes through the center (covering described later). 50C) are provided eccentric to each other.

  The bearing holes 43 and 53 for supporting the bearings 41A and 53A loaded on the both end support shafts of the movable roller 33 are round holes having a larger diameter than the bearings 43A and 53A. Form.

  However, as shown in FIGS. 1 to 4, the intermediate rollers 31 to 33 are elastically supported from both directions in the axial direction when supported by the center plate 15 and the carrier 50.

  Specifically, the bearings 41A to 43A and 51A to 53A loaded on the both end support shafts of the intermediate rollers 31 to 33 are fitted into the bearing holes 41 to 43 of the center plate 15 and the bearing holes 51 to 53 of the carrier 50, respectively. (The gaps are fitted to the bearing holes 41 to 43 of the center plate 15 and the bearing holes 51 to 53 of the carrier 50 so as to be displaceable in the axial direction), and the bearings 41A to 43A and 51A to 53A are axially outward (intermediate rollers). End surfaces facing the power transmission cylindrical surfaces 31 </ b> A to 33 </ b> A opposite to the main body) are supported by the center plate 15 and the carrier 50 via leaf springs 56 and 57.

  That is, the bearings 41A to 43A loaded on one end support shafts of the intermediate rollers 31 to 33 are arranged on the closing surfaces of the closing holes 41 to 43 provided in the center plate 15 in the axial direction, as shown in FIG. It is elastically supported through 56A, leaf spring 56, and spacer 56B. Further, bearings 51A to 53A loaded on the other end support shafts of the intermediate rollers 31 to 33 are attached to a retaining ring 58 engaged with an annular groove at an opening end of the through holes 51 to 53 provided in the carrier 50 in the axial direction. As shown in FIG. 9B, it is elastically supported through a spacer 57A, a leaf spring 57, and a spacer 57B. The axial urging force exerted by the leaf springs 56 and 57 on the intermediate rollers 31 to 33 is, for example, 4.5 KGF.

According to the present embodiment, the following operational effects can be obtained.
(a) The intermediate rollers 31 to 33 are elastically supported from both axial directions. The intermediate rollers 31 to 33 are given a resilient force as a preload from both directions in the axial direction, are supported without backlash in the axial direction, and vibrations in the axial direction are attenuated by the resilient force. As a result, the durability of the bearings 41A to 43A and 51A to 53A that support the intermediate rollers 31 to 33 is improved, and the surface pressure of the rolling contact surface where the intermediate rollers 31 to 33 are in contact with the output shaft 12 and the outer ring 27 is appropriately adjusted. Can be secured.

  (b) By supporting the end surfaces of the bearings 41A to 43A and 51A to 53A loaded on the support shafts of the intermediate rollers 31 to 33 with leaf springs 56 and 57, the intermediate rollers 31 to 33 can be moved in the axial direction with a simple structure. You can keep bullets from both directions.

  (c) The above-described (a) and (b) can be realized in the speed increaser 20 of the supercharger 10.

(C) Structure for regulating the axial position of the output shaft 12 When the output shaft 12 and the intermediate rollers 31 to 33 are assembled to the center plate 15 and the carrier 50, the output shaft 12 is provided on both sides of the driven cylindrical surface 12A. The flange portions 12B, 12B regulate the axial position of the output shaft 12 with only one intermediate roller 31-33, in this embodiment sandwiching both end surfaces of the cylindrical surface 31A for power transmission of the intermediate roller 31. . At this time, the flanges 12B and 12B of the output shaft 12 form a gap G between the end faces of the power transmission cylindrical surfaces 32A and 33A of the other intermediate rollers 32 and 33.

  The flanges 12 </ b> B and 12 </ b> B of the output shaft 12 form a gap G between both end surfaces of the power transmission cylindrical surface 33 </ b> A of the movable roller 33.

According to the present embodiment, the following operational effects can be obtained.
(a) The flanges 12B on which the output shaft 12 is provided on both sides of the driven cylindrical surface 12A regulates the axial position of the output shaft 12 across only one end surface of the intermediate roller 31; A gap G was formed between both end faces of the other intermediate rollers 32 and 33. Accordingly, all of the intermediate rollers 31 to 33 are not coupled in the axial direction without gaps via the flange portion 12B of the output shaft 12, and the axial displacement and vibration do not interfere with each other. Therefore, even if one of the plurality of intermediate rollers 31 to 33 is displaced in the axial direction due to the effect of the output shaft 12 rotating at high speed or vibrates due to its own high speed rotation, Displacement and vibration do not interfere with other intermediate rollers via the flange 12B of the output shaft 12, and the durability of the speed increaser 20 can be improved.

  (b) Since the axial displacements and vibrations of the intermediate rollers 31 to 33 do not interfere with each other as described in the above (a), the intermediate rollers 31 to 33 are in contact with the output shaft 12 and the outer ring 27. Appropriate contact pressure can be ensured.

  (c) The flanges 12B provided on both sides of the driven-side cylindrical surface 12A with the output shaft 12 form a gap G between both end surfaces of the movable roller 33, so that the above-described (a), (b) In addition, the movable roller 33 can be moved smoothly.

  (d) The above-described (a) to (c) can be realized in the speed increaser 20 of the supercharger 10.

(D) Oil supply structure The speed increaser 20 includes an oil pump 60 for circulating traction oil therein. The oil pump 60 is configured by a vane pump or the like in which a plurality of vanes are provided around the input shaft 11 of the front housing 21 on the outer periphery of a rotor fixed to the input shaft 11, and the vanes are surrounded by a base plate, a side plate, and a cam ring. In this embodiment, it is driven by the input shaft 11 (the oil pump 60 may be driven by the output shaft 12).

  The traction oil discharged from the oil pump 60 lubricates and cools the bearing 24 and the oil seal 25 around the input shaft 11, is drilled in the diameter direction to the axial direction of the input shaft 11, and is inserted into the hole 50 </ b> A of the carrier 50. From the oil passage 61 opened to the shaft end surface, the oil flows from the shaft end surface of the output shaft 12 inserted into the hole 50B of the carrier 50 to the oil passage 62 drilled in the axial direction, and further intersects the oil passage 62. From the distribution path 63 formed in the diameter direction of the output shaft 12, the centrifugal force accompanying the rotation of the output shaft 12 scatters and flows out to the outer peripheral side. Oil flowing out from the distribution path 63 that opens to the driven cylindrical surface 12A of the output shaft 12 lubricates and cools the driven cylindrical surface 12A of the output shaft 12 and the power transmission cylindrical surfaces 31A to 33A of the intermediate rollers 31 to 33. The oil flowing out from the distribution path 63 near both sides of the driven cylindrical surface 12A is in thrust contact with both side flanges 12B of the output shaft 12 and both end surfaces of the power transmission cylindrical surfaces 31A to 33A of the intermediate rollers 31 to 33. Lubricate and cool the parts. The oil flowing out from the distribution path 63 intersecting the closed end side of the oil path 62 lubricates and cools the oil seal 26 around the output shaft 12. The oil that has flowed to the outer periphery of the output shaft 12 further flows in the annular space between the output shaft 12 and the outer ring 27, and the bearings 41 </ b> A to 43 </ b> A of the intermediate rollers 31 to 33, the bearings 51 </ b> A to 53 </ b> A, 27A is lubricated and cooled, and returns to the oil pump 60.

  In the speed increaser 20, the input shaft 11 and the output shaft 12 are eccentrically arranged. However, the carrier that supports the connection portion of the oil passage 61 of the input shaft 11 and the oil passage 62 of the output shaft 12 to the center plate 15. 50, the shaft end of the input shaft 11 and the shaft end of the output shaft 12 are covered with a center covering portion 50C having holes 50A and 50B through which the shaft ends are inserted in an eccentric state. The oil that flows out from the oil passage 61 of the input shaft 11 is blocked outward by the covering portion 50C to reduce leakage, and is guided to the oil passage 62 of the output shaft 12.

  The speed increaser 20 can form an oil film damper by allowing oil to enter the gap between the outer periphery of the shaft end of the input shaft 11 and the inner periphery of the hole 50A of the covering portion 50C. The different diameter step surface provided on the outer periphery of the shaft end of the input shaft 11 and the different diameter step surface provided on the inner periphery of the hole 50A of the covering portion 50C are brought into contact with each other to develop a labyrinth effect, and the outer blocking effect of the covering portion 50c. Can be strengthened.

  The speed increaser 20 can form oil film dampers by allowing oil to enter the gap between the outer periphery of the shaft end of the output shaft 12 and the inner periphery of the hole 50B of the covering portion 50C. The different diameter step surface provided on the outer periphery of the shaft end of the output shaft 12 and the different diameter step surface provided on the inner periphery of the hole 50B of the covering portion 50C are brought into contact with each other to develop a labyrinth effect, and the outer blocking effect of the covering portion 50C. Can be strengthened.

  The speed increaser 20 is provided with oil injection holes 64 and 65 communicating with the oil passage 61 in the covering portion 50 </ b> C of the carrier 50. As shown in FIGS. 1 and 5, the speed increaser 20 directly applies oil injected from the oil injection hole 64 to the driven side cylindrical surface 12 </ b> A of the output shaft 12 and the power transmission cylinders of the intermediate rollers 31 to 33. The roller 31 is jetted and supplied in the same direction as the rotation direction of the output shaft 12 and the intermediate rollers 31 to 33 to the rolling contact surface with which the surfaces 31A to 33A are in contact. As shown in FIG. 5, the speed increaser 20 directly applies the oil injected from the oil injection hole 65 to the drive side cylindrical surface 27 </ b> A of the outer ring 27 and the power transmission cylindrical surfaces 31 </ b> A to 33 </ b> A of the intermediate rollers 31 to 33. Is sprayed and supplied in the same direction as the rotation direction of the outer ring 27 and the intermediate rollers 31 to 33 with respect to the rolling contact surface.

  As shown in FIG. 1, the speed increaser 20 covers the side of one of the carrier 50 and the intermediate rollers 31 to 33 in the axial direction (on the input shaft 11 side) with the cup-shaped body 29 of the connecting member 28, and outputs the output shaft. The oil flow path 66 that guides the flow of oil flowing out from the 12 distribution paths 63 and the flow of oil injected from the oil injection holes 64 and 65 of the carrier 50 to the inner peripheral surface (drive side cylindrical surface 27A) of the outer ring 27. Partition. At this time, the aforementioned tool locking hole 27E provided in the annular thin portion 27C of the outer ring 27 is closed by an O-ring 67 loaded on the inner periphery of the annular thin portion 27C. The oil guided to the drive-side cylindrical surface 27A of the outer ring 27 by the oil passage 66 is one end to which the outer mounting portion 28B of the connecting member 28 is fixed in the width direction of the outer ring 27, as indicated by an arrow in FIG. The oil flows out from the opposite side to the inner peripheral side of the front housing 21 and returns to the oil pump 60 from an oil return port 68 provided in the front housing 21.

According to the present embodiment, the following operational effects can be obtained.
(a) The carrier 50 supporting the intermediate rollers 31 to 33 is provided with oil injection holes 64 and 65, and the oil injected from the oil injection holes 64 and 65 is directly supplied to the output shaft 12 and the intermediate rollers 31 to 33. Is supplied to the rolling contact surface where the outer ring 27 and the intermediate rollers 31 to 33 are in contact with each other, so that the oil is less likely to be atomized and the oil film can be easily formed on the rolling contact surface. By making the oil injection direction from the oil injection holes 64 and 65 the same direction along the rotation direction of the output shaft 12, the intermediate rollers 31 to 33 and the outer ring 27, an oil film can be formed more reliably.

  (b) A plurality of intermediate rollers 31 to 33 are supported in the speed increaser 20, and oil injection holes 64 and 65 are provided at a plurality of locations of the carrier 50 that are positioned over a wide range in the speed increaser 20. The oil can be supplied from the oil injection holes 64 and 65 to each of the plurality of oil supply points, and the amount of oil supply can be increased.

  (c) The cup-shaped body 29 of the connecting member 28 covers one side of the carrier 50 and the intermediate rollers 31 to 33, and defines an oil passage 66 that guides the oil flow to the inner peripheral surface of the outer ring 27. Therefore, the oil supplied to the inside of the speed increaser 20 is effectively guided to the rolling contact surface of the outer ring 27 and the intermediate rollers 31 to 33 by the rotating centrifugal force of the output shaft 12 and the like and the cup-shaped body 29, An oil film can be more reliably formed on the contact surface.

  (d) The above-described (a) to (c) can be realized in the speed increaser 20 of the supercharger 10.

  As shown in FIGS. 10 to 12, the oil pump 60 (vane pump) is provided with a plurality of vanes 72 around the input shaft 11 of the front housing 21 on the outer periphery of the rotor 71 fixed to the input shaft 11. A pump chamber 76 is formed by being surrounded by the base plate 73, the side plate 74 and the cam ring 75.

  As shown in FIG. 12A, the oil pump 60 has a suction port 77 provided in the base plate 73 disposed radially inward from the pump chamber 76 and a chamfered inlet corner 71A facing the suction port 77 of the rotor 71. To do. FIG. 13A shows a conventional structure corresponding to FIG.

  As shown in FIG. 12B, the oil pump 60 has a discharge port 78 provided in the base plate 73 arranged radially outside the pump chamber 76 and a chamfered outlet corner 75A facing the discharge port 78 of the cam ring 75. To do. FIG. 13B shows a conventional structure corresponding to FIG.

According to the present embodiment, the following operational effects can be obtained.
(a) In the oil pump 60, the suction port 77 provided in the base plate 73 is disposed radially inward from the pump chamber 76, and the inlet corner portion 71A facing the suction port 77 of the rotor 71 is chamfered. Therefore, the oil suction efficiency can be improved by the centrifugal force exerted by the rotor 71 on the oil sucked into the pump chamber 76 from the suction port 77. Further, by chamfering the inlet corner portion 71A of the rotor 71, the suction performance exerted by the inlet corner portion 71A of the rotor 71 on the oil sucked into the pump chamber 76 from the suction port 77 can be reduced.

  (b) The oil discharge efficiency can be improved by the centrifugal force exerted by the rotor 71 on the oil discharged from the pump chamber 76 to the discharge port 78. Further, by chamfering the outlet corner portion 75A of the cam ring 75, the discharge resistance exerted by the outlet corner portion 75A of the cam ring 75 on the oil discharged from the pump chamber 76 to the discharge port 78 can be reduced.

  The speed reducer 110 in FIGS. 15 to 21 decelerates the rotation of the input shaft 111 and transmits it to the output shaft 112, and can be used to decelerate the rotation of an engine, an electric motor, a hydraulic motor, or the like.

  The speed reducer 110 is a friction roller type speed reducer that uses a wedge action. The center plate 121 and the rear housing 122 form an outer shell, and the rear housing 122 is fitted to the center plate 121 by inlay fitting.

  The reducer 110 penetrates and supports the output shaft 112 in the rear housing 122 via bearings 123 and 124, and the periphery of the output shaft 112 is surrounded by an oil seal 125 inserted at a position between the bearings 123 and 124 of the rear housing 122. Seal. The reducer 110 seals the periphery of the input shaft 111 with an oil seal 126 inserted into the center plate 121.

  The reducer 110 has an outer ring 127 that rotates the output shaft 112. In this embodiment, the output shaft 112 and the outer ring 127 are arranged substantially coaxially, and the output shaft 112, the outer ring 127 and the input shaft 111 are arranged eccentrically. The output shaft 112 and the outer ring 127 are connected by a connecting member 128 as will be described later.

  The speed reducer 110 includes three intermediate rollers 131 and 132 in an annular space between a driving-side cylindrical surface 111 </ b> A that is an outer peripheral surface of the input shaft 111 and a driven-side cylindrical surface 127 </ b> A that is an inner peripheral surface of the outer ring 127. 133 are arranged. The outer peripheral surfaces of the three intermediate rollers 131, 132, and 133 are power transmission cylindrical surfaces 131A, 132A, and 133A that make frictional contact with the driving-side cylindrical surface 111A of the input shaft 111 and the driven-side cylindrical surface 127A of the outer ring 127, respectively. The

  In the present embodiment, one of the three intermediate rollers 131, 132, 133 has a larger diameter than the other two intermediate rollers 132, 133, and as a result, the driving side cylindrical surface of the input shaft 111. When the above-described annular space is formed between 111A and the driven-side cylindrical surface 127A of the outer ring 127, the width of the annular space in the radial direction of the input shaft 111 is set to be the same in the circumferential direction of the input shaft 111. Then, at least one of the three intermediate rollers 131, 132, and 133, in this embodiment, the intermediate roller 133 can be moved in the circumferential direction and the radial direction of the input shaft 111 within the annular space. As a result, all the intermediate rollers 131 to 133 can be pressed against the input shaft 111 and the outer ring 127, and the rotation of the input shaft 111 is decelerated through the intermediate rollers 131 to 133 so that the outer ring 127 and the output are output. The transmission to the shaft 112 is made possible.

  As shown in FIGS. 15 to 21, the reducer 110 fastens the outer ring 127 to the outer periphery of all the intermediate rollers 131 to 133 in an elastically deformed state (elastically expanded state), and the inner peripheral surface (covered) of the outer ring 127. The driving side cylindrical surface 127A) is brought into contact with the outer peripheral surface (driving side cylindrical surface 111A) of the input shaft 111 in a state of elastic tension.

  At this time, the movable roller 133 can move in the circumferential direction and the radial direction of the input shaft 111 within a range of a guide groove 134 provided in the center plate 121 and a carrier 150 described later. The springs 135 and 136 inserted in the holes provided in the center plate 121 and the carrier 150 are backed up by the caps 135A and 136A screwed to the center plate 121 and the carrier 150, and the pressers 135B and 136B are moved. The bearings 143A and 153A loaded on the both end support shafts of the movable roller 133 are pressed against. The movable roller 133 can move in the circumferential direction and the radial direction of the input shaft 111 within the range of the guide groove 134 while being urged by the springs 135 and 136.

  In the manufacturing stage of the speed reducer 110, for example, using a lathe work gripping claw or the like, the circumferential ring 3 position of the outer ring 127 is pressed by the same number of three pressing claws as the intermediate rollers 131 to 133, and the outer ring 127 is It is elastically deformed in a generally triangular shape. As a result, a diameter-reduced portion is formed in a portion corresponding to the pressing claw in the inner circumference of the outer ring 127, and a diameter-increased portion is formed in a portion sandwiched between adjacent reduced-diameter portions. By inserting each of the intermediate rollers 131 to 133 and then releasing the pressing by the pressing claw, the outer ring 127 can be fastened to the outer periphery of all the intermediate rollers 131 to 133.

Therefore, the speed reducer 110 can operate as follows (FIGS. 15 to 21).
(1) When a driving force from, for example, an engine is input to the input shaft 111, this driving force is transmitted from the input shaft 111 to the outer ring 127. At this time, the outer ring 127 and the input shaft 111 are eccentric as described above, and the width of the annular space in the radial direction of the input shaft 111 is not the same in the circumferential direction of the input shaft 111. When the input shaft 111 to which a large amount of power is transmitted rotates in the direction a, the movable roller 133 is in a direction in which the width of the annular space between the outer ring 127 and the input shaft 111 is reduced, and the wedge exerted on the movable roller 133. It moves in the direction b to strengthen the action, and is pressed between the driving side cylindrical surface 111A of the input shaft 111, the driven side cylindrical surface 127A of the outer ring 127, and the power transmission cylindrical surfaces 131A to 133A of the intermediate rollers 131 to 133. Force c is generated. Due to this large pressing force c, a large frictional force is generated between the driving side cylindrical surface 111A of the input shaft 111, the driven side cylindrical surface 127A of the outer ring 127, and the power transmission cylindrical surfaces 131A to 133A of the intermediate rollers 131 to 133, The large driving force transmitted to the input shaft 111 is transmitted to the outer wheel 127, and the outer wheel 127 and the output shaft 112 rotate at a reduced speed in the direction d.

  (2) When the driving force transmitted to the input shaft 111 decreases due to engine deceleration, the movable roller 133 increases the width of the annular space between the outer ring 127 and the input shaft 111 against the springs 135 and 136. Direction, which is displaced in the direction opposite to b which weakens the wedge effect on the movable roller 133, and the power of the driving side cylindrical surface 111A of the input shaft 111, the driven side cylindrical surface 127A of the outer ring 127, and the intermediate rollers 131-133. The pressing force c generated between the transmission cylindrical surfaces 131A to 133A is reduced, and the driving side cylindrical surface 111A of the input shaft 111, the driven side cylindrical surface 127A of the outer ring 127, and the power transmission cylindrical surface 131A of the intermediate rollers 131 to 133 are reduced. The frictional force generated between ˜133A is reduced, and the outer ring 127 and the output shaft 112 are decelerated and rotated in the direction d.

  When the driving force from the engine becomes excessive, the movable roller 133 abuts with one end groove surface (stopper surface) of the guide groove 134 in the direction b to limit the upper limit of the pressing force c, and the speed reducer 110. To prevent damage. When the driving force from the engine becomes too small, the movable roller 133 abuts the other end groove surface (stopper surface) of the guide groove 134 in the opposite direction to b, restricts the lower limit of the pressing force c, and inputs Power transmission from the shaft 111 to the output shaft 112 is maintained.

  Hereinafter, in the speed reducer 110, (A) a connection structure between the output shaft 112 and the outer ring 127, (B) a support structure for the intermediate rollers 131 to 133, (C) a structure for regulating the axial position of the input shaft 111, (D) The oil supply structure will be described.

(A) Connection structure of output shaft 112 and outer ring 127 The reduction gear 110 connects the output shaft 112 and the outer ring 127 by a connecting member 128 as shown in FIGS. The connecting member 128 is provided between the boss-shaped inner mounting portion 28A fixed to the output shaft 112, the ring-shaped outer mounting portion 128B fixed to the outer ring 127, and the inner mounting portion 128A and the outer mounting portion 128B. Flexible portion 128C. The flexible portion 128C is made of a flexible film plate, and its plate surface extends along the rotation direction of the output shaft 112 and the outer ring 127, and in this embodiment, extends in a continuous rotation surface shape.

  Specifically, as shown in FIG. 22, the connecting member 128 generally forms a cup-shaped body 129, an inner mounting portion 128 </ b> A is provided at the center of the bottom 129 </ b> A of the cup-shaped body 129, and the opening of the side wall 129 </ b> B of the cup-shaped body 129. An outer mounting portion 128B is provided at the portion, and a corner portion 129C where the bottom portion 129A of the cup-shaped body 129 and the side wall 129B intersect, and the side wall 129B are defined as a flexible portion 128C. In this embodiment, the corner portion 129C, the side wall 129B, and the portion of the bottom portion 129A near the corner portion 129C are set as the flexible portion 128C, and the portion near the inner mounting portion 128A of the bottom portion 129A is thicker than the flexible portion 128C. The waist strength in the axial direction of the body 129 can be secured.

  The inner mounting portion 128 </ b> A of the connecting member 128 is screwed and fixed to the outer periphery of the shaft end portion of the output shaft 112 located inside the rear housing 122. The outer mounting portion 128B of the connecting member 128 has an annular thin portion 127C on the side portion on one end side in the width direction of the outer ring 127, in this embodiment, on one end side of the main body portion 127B that forms the driven side cylindrical surface 127A of the outer ring 127. And is fixed by being screwed to the outer periphery of the thick annular mounting portion 127D coupled thereto. By fixing the connecting member 128 to the side of the outer ring 127, the outer diameter of the speed reducer 110 is reduced. The attachment portion 127D of the outer ring 127 to which the connecting member 128 is fixed is separated from the main body portion 127B by the annular thin portion 127C, and the main body portion 127B changes the elastic deformation state with respect to the outer periphery of each of the intermediate rollers 131 to 133 to the presence of the annular attachment portion 127D. Regardless, it is generally uniform in the width direction of the main body 127B. Note that a plurality of positions in the circumferential direction of the annular thin portion 127C are provided with tool locking holes 127E for preventing the outer ring 127 from rotating when the connecting member 128 and the output shaft 112 are attached to and removed from the outer ring 127. .

According to the present embodiment, the following operational effects can be obtained.
(a) A connecting member 128 that connects the output shaft 112 and the outer ring 127 is fixed to the output shaft 112 and the outer ring 127, and there is no place to contact or separate between the output shaft 112 or the outer ring 127. Therefore, the connecting member 128 does not make a hitting sound with the output shaft 112 or the outer ring 127 or slide wear, and the rotational force of the output shaft 112 can be stably transmitted to the outer ring 127.

  (b) In the connecting member 128, the flexible portion 128C provided between the inner attachment portion 128A fixed to the output shaft 112 and the outer attachment portion 128B fixed to the outer ring 127 is the axial direction of the outer ring 127 with respect to the output shaft 112. While restricting the position, (i) the outer mounting portion 128B can flexibly follow the elastic deformation in the radial direction of the outer ring 127, and (ii) the misalignment between the output shaft 112 and the outer ring 127 can be absorbed. .

  (c) The flexible portion 128C of the connecting member 128 is made of a flexible membrane plate, and the flexible membrane plate is formed by extending the plate surface in the rotation direction of the output shaft 112 and the outer ring 127. The rotational force of the output shaft 112 can be reliably transmitted to the outer ring 127 while performing the action (b).

  (d) The connecting member 128 generally forms a cup-shaped body 129, an inner mounting portion 128A is provided at the center of the bottom portion 129A of the cup-shaped body 129, and an outer mounting portion 128B is provided at the opening of the side wall 129B of the cup-shaped body 129. The corner portion 129C where the bottom portion 129A and the side wall 129B of the cup-shaped body 129 intersect and the side wall 129B are formed as a flexible portion 128C. Accordingly, the cup-shaped body 129 is cup-shaped while the axial position of the outer ring 127 relative to the output shaft 112 is restricted to a fixed position by the balance of the overall strength of the cup-shaped body 129, particularly the waist strength of the bottom 129A around the inner mounting portion 128A. The flexibility of the corner portion 129C and the side wall 129B of the body 129 makes the outer mounting portion 128B easy to deform in the radial direction and the axial direction, and (i) the outer mounting portion 128B is flexible to elastic deformation in the radial direction of the outer ring 127. (Ii) Axis misalignment between the output shaft 112 and the outer ring 127 can be absorbed.

  (e) The outer mounting portion 128B of the connecting member 128 is fixed to the side portion on one end side in the width direction of the outer ring 127, whereby the outer mounting portion 128B of the connecting member 128 is fixed to the outer peripheral portion of the outer ring 127. The outer diameter size of the speed reducer 110 can be reduced as compared with that.

  (f) In the reduction gear 110, the above (a) to (e) can be realized.

(B) Support structure for intermediate rollers 131 to 133 The speed reducer 110 has the carrier 150 assembled to the center plate 121, and bearings 141A, 142A, and 143A loaded on one end support shafts of the intermediate rollers 131 to 133 are attached to the center plate 121. The bearings 151A, 152A, and 153A loaded on the other end support shaft are supported by the bearing holes 151, 152, and 153 provided in the carrier 150 while being supported by the provided bearing holes 141, 142, and 143.

  The carrier 150 is fixed to the center plate 121 by fastening each of the three legs 154 of the carrier 150 to the center plate 121 with bolts 155. The center plate 121 is provided with a hole 121A at the center portion through which the intermediate portion of the input shaft 111 is inserted and the oil seal 26 is inserted. The carrier 150 has a hole 150A through which an end of the output shaft 112 (an inner mounting portion 128A of the connecting member 128 fixed to the output shaft 112) passes, and a hole 150B through which the end of the input shaft 111 passes through a central portion (a coating described later). 150C) are provided eccentric to each other.

  The bearing holes 143 and 153 for supporting the bearings 141A and 153A loaded on the both end support shafts of the movable roller 133 are round holes having a larger diameter than the bearings 143A and 153A. Form.

  However, as shown in FIGS. 15 to 18, the intermediate rollers 131 to 133 are elastically supported from both directions in the axial direction when supported by the center plate 121 and the carrier 150.

  Specifically, the bearings 141A to 143A and 151A to 153A loaded on the both end support shafts of the intermediate rollers 131 to 133 are fitted into the bearing holes 141 to 143 of the center plate 121 and the bearing holes 151 to 153 of the carrier 150, respectively. (A gap is fitted between the bearing holes 141 to 143 of the center plate 121 and the bearing holes 151 to 153 of the carrier 150 so as to be displaceable in the axial direction), and the outer sides of the bearings 141A to 143A and 151A to 153A in the axial direction (intermediate rollers). End surfaces facing the power transmission cylindrical surfaces 131 </ b> A to 133 </ b> A opposite to the main body) are supported by the center plate 121 and the carrier 150 via leaf springs 156 and 157.

  That is, the bearings 141A to 143A loaded on one end support shafts of the intermediate rollers 131 to 133 are arranged on the closing surfaces of the closing holes 141 to 143 provided in the center plate 121 in the axial direction, as shown in FIG. It is elastically supported via 156A, leaf spring 156, and spacer 156B. Further, bearings 151A to 153A loaded on the other end support shafts of the intermediate rollers 131 to 133 are attached to the retaining ring 158 engaged with the annular groove at the opening end of the through holes 151 to 153 provided in the carrier 150 in the axial direction. As shown in FIG. 23B, it is elastically supported through a spacer 157A, a leaf spring 157, and a spacer 157B. The axial urging force exerted by the leaf springs 156, 157 on the intermediate rollers 131-133 is, for example, 4.5 KGF.

According to the present embodiment, the following operational effects can be obtained.
(a) The intermediate rollers 131 to 133 are elastically supported from both directions in the axial direction. The intermediate rollers 131 to 133 are given a resilient force as a preload from both directions in the axial direction, are supported without backlash in the axial direction, and the vibration in the axial direction is attenuated by the resilient force. As a result, the durability of the bearings 141A to 143A and 151A to 153A that support the intermediate rollers 131 to 133 is improved, and the surface pressure of the rolling contact surface where the intermediate rollers 131 to 133 are in contact with the input shaft 111 and the outer ring 127 is appropriately adjusted. Can be secured.

  (b) The end surfaces of the bearings 141A to 143A and 151A to 153A loaded on the support shafts of the intermediate rollers 131 to 133 are supported by leaf springs 156 and 157, so that the intermediate rollers 131 to 133 can be moved in the axial direction with a simple structure. You can keep bullets from both directions.

  (c) The above-described (a) and (b) can be realized in the speed reducer 110.

(C) Structure for restricting the axial position of the input shaft 111 When the input shaft 111 and the intermediate rollers 131 to 133 are assembled to the center plate 121 and the carrier 150, the input shaft 111 is provided on both sides of the drive side cylindrical surface 111A. The flanges 111B, 111B restrict the position of the input shaft 111 in the axial direction with only one intermediate roller 131-133, in this embodiment sandwiching both end surfaces of the power transmission cylindrical surface 131A of the intermediate roller 131. At this time, the flanges 111B and 111B of the input shaft 111 form a gap G between the other intermediate rollers 132 and 133 and both end surfaces of the power transmission cylindrical surfaces 132A and 133A.
The flanges 111 </ b> B and 111 </ b> B of the input shaft 111 form a gap G between both end surfaces of the power transmission cylindrical surface 133 </ b> A of the movable roller 133.

According to the present embodiment, the following operational effects can be obtained.
(a) The flanges 111B on which the input shaft 111 is provided on both sides of the drive-side cylindrical surface 111A regulates the axial position of the input shaft 111 across the both end surfaces of the single intermediate roller 131, A gap G was formed between both end faces of the intermediate rollers 132 and 133. Accordingly, all of the intermediate rollers 131 to 133 are not coupled with no gap in the axial direction via the flange 111B of the input shaft 111, and the axial displacement and vibration do not interfere with each other. For this reason, even if one of the plurality of intermediate rollers 131 to 133 is displaced in the axial direction due to the influence of the input shaft 111 rotating at high speed or vibrates due to its own high speed rotation, Displacement and vibration do not interfere with other intermediate rollers via the flange 111B of the input shaft 111, and the durability of the speed reducer 110 can be improved.

  (b) Since the axial displacements and vibrations of the intermediate rollers 131 to 133 do not interfere with each other as described above (a), the intermediate rollers 131 to 133 are in contact with the input shaft 111 and the outer ring 127. Appropriate contact pressure can be ensured.

  (c) The flanges 111B provided with the input shaft 111 on both sides of the drive-side cylindrical surface 111A form a gap G between both end surfaces of the movable roller 133, so that the above-described (a) and (b) In addition, the movable roller 133 can be moved smoothly.

  (d) The above-described (a) to (c) can be realized in the speed reducer 110.

(D) Oil supply structure The speed reducer 110 incorporates an oil pump 160 for circulating traction oil therein. The oil pump 160 is composed of a vane pump or the like around the output shaft 112 of the rear housing 122 and provided with a plurality of vanes on the outer periphery of the rotor fixed to the output shaft 112 and surrounded by a base plate, a side plate, and a cam ring. In this embodiment, it is driven by the output shaft 112 (the oil pump 160 may be driven by the input shaft 111).

  The traction oil discharged from the oil pump 160 lubricates and cools the bearing 124 and the oil seal 125 around the output shaft 112, is drilled in the diameter direction to the axial direction of the output shaft 112, and is inserted into the hole 150 </ b> A of the carrier 150. The oil passage 161 that opens to the shaft end surface flows from the shaft end surface of the input shaft 111 inserted through the hole 150B of the carrier 150 to the oil passage 162 that is drilled in the axial direction, and further intersects the oil passage 162. From the distribution path 163 bored in the diameter direction of the input shaft 111, the centrifugal force accompanying the rotation of the input shaft 111 scatters and flows out to the outer peripheral side. The oil flowing out from the distribution path 163 opening to the drive side cylindrical surface 111A of the input shaft 111 lubricates and cools the drive side cylindrical surface 111A of the input shaft 111 and the power transmission cylindrical surfaces 131A to 133A of the intermediate rollers 131 to 133. The oil flowing out from the distribution path 163 near the both sides of the drive side cylindrical surface 111A lubricates the thrust contact portions between both side flanges 111B of the input shaft 111 and both end surfaces of the power transmission cylindrical surfaces 131A to 133A of the intermediate rollers 131 to 133. ·Cooling. The oil flowing out from the distribution passage 163 intersecting the closed end side of the oil passage 162 lubricates and cools the oil seal 126 around the input shaft 111. The oil that has flowed to the outer periphery of the input shaft 111 further flows in an annular space between the input shaft 111 and the outer ring 127, and the bearings 141A to 143A of the intermediate rollers 131 to 133, the bearings 151A to 153A, and the driven side cylinder of the outer ring 127. Lubricate and cool the surface 127A and return to the oil pump 160.

  In the reduction gear 110, the input shaft 111 and the output shaft 112 are eccentrically arranged. However, the carrier 150 that supports the connection portion of the oil passage 161 of the output shaft 112 and the oil passage 162 of the input shaft 111 to the center plate 121. , The shaft end of the output shaft 112 and the shaft end of the input shaft 111 are covered with a center covering portion 150C having holes 150A and 150B through which they are inserted in an eccentric state. The oil flowing out from the oil passage 161 of the output shaft 112 is blocked outward by the covering portion 150C to reduce leakage, and is guided to the oil passage 162 of the input shaft 111.

  The reducer 110 can form oil film dampers by allowing oil to enter the gap between the outer periphery of the shaft end of the output shaft 112 and the inner periphery of the hole 150A of the covering portion 150C. The different diameter step surface provided on the outer periphery of the shaft end of the output shaft 112 and the different diameter step surface provided on the inner periphery of the hole 150A of the covering portion 150C are brought into contact with each other to develop a labyrinth effect, and the outer blocking effect of the covering portion 150c. Can be strengthened.

  The reducer 110 can form oil film dampers by allowing oil to enter the gap between the outer periphery of the shaft end of the input shaft 111 and the inner periphery of the hole 150B of the covering portion 150C. The different diameter step surface provided on the outer periphery of the shaft end of the input shaft 111 and the different diameter step surface provided on the inner periphery of the hole 150B of the covering portion 150C are brought into contact with each other to develop a labyrinth effect, and the outer blocking effect of the covering portion 150C. Can be strengthened.

  The reduction gear 110 is provided with oil injection holes 164 and 165 communicating with the oil passage 161 in the covering portion 150 </ b> C of the carrier 150. As shown in FIGS. 15 and 19, the speed reducer 110 directly applies the oil injected from the oil injection hole 164 to the drive side cylindrical surface 111 </ b> A of the input shaft 111 and the power transmission cylindrical surface 131 </ b> A of the intermediate rollers 131 to 133. ˜133A is sprayed and supplied in the same direction as the rotation direction of the input shaft 111 and the intermediate rollers 131 to 133 with respect to the rolling contact surface. As shown in FIG. 19, the speed reducer 110 directly applies the oil injected from the oil injection hole 165 to the driven cylindrical surface 127A of the outer ring 127 and the power transmission cylindrical surfaces 131A to 133A of the intermediate rollers 131 to 133. Is sprayed and supplied in the same direction as the rotation direction of the outer ring 127 and the intermediate rollers 131 to 133 to the rolling contact surface.

  As shown in FIG. 15, the speed reducer 110 covers the side of one side (the output shaft 112 side) of the carrier 150 and the intermediate rollers 131 to 133 by the cup-shaped body 129 of the connecting member 128, and the input shaft 111. An oil passage 166 that guides the flow of oil flowing out from the distribution passage 163 and the flow of oil injected from the oil injection holes 164 and 165 of the carrier 150 to the inner peripheral surface (driven-side cylindrical surface 127A) of the outer ring 127. Partition. At this time, the aforementioned tool locking hole 127E provided in the annular thin portion 127C of the outer ring 127 is closed by an O-ring 167 loaded on the inner periphery of the annular thin portion 127C. The oil guided to the driven-side cylindrical surface 127A of the outer ring 127 by the oil passage 166 has the outer mounting portion 128B of the connecting member 128 fixed in the width direction of the outer ring 127 as indicated by an arrow in FIG. The oil flows out from the side opposite to the one end side to the inner peripheral side of the rear housing 122 and returns to the oil pump 160 from an oil return port 168 provided in the rear housing 122.

According to the present embodiment, the following operational effects can be obtained.
(a) Oil injection holes 164 and 165 are provided in the carrier 150 that supports the intermediate rollers 131 to 133, and the oil injected from the oil injection holes 164 and 165 is directly applied to the input shaft 111 and the intermediate rollers 131 to 133. Is supplied to the rolling contact surface where the outer ring 127 and the intermediate rollers 131 to 133 are in contact with each other, so that the oil is less likely to be atomized, and the oil film can be easily formed on the rolling contact surface. By setting the oil injection direction from the oil injection holes 164 and 165 to the same direction along the rotation direction of the input shaft 111, the intermediate rollers 131 to 133, and the outer ring 127, an oil film can be formed more reliably.

  (b) A plurality of intermediate rollers 131 to 133 are supported in the speed reducer 110, and oil injection holes 164 and 165 are provided at a plurality of locations on the carrier 150 that are positioned over a wide range in the speed reducer 110. Oil can be supplied from the oil injection holes 164 and 165 to each of the plurality of oil supply points, and the amount of oil supply can be increased.

  (c) The cup-shaped body 129 of the connecting member 128 covers one side of the carrier 150 and the intermediate rollers 131 to 133, and defines an oil passage 166 that guides the oil flow to the inner peripheral surface of the outer ring 127. Accordingly, the oil supplied to the inside of the speed reducer 110 is effectively guided to the rolling contact surfaces of the outer ring 127 and the intermediate rollers 131 to 133 by the rotating centrifugal force of the input shaft 111 and the like and the cup-shaped body 129, and the rolling contact Oil film can be more reliably formed on the surface.

  (d) The above-described (a) to (c) can be realized in the speed reducer 110.

  The embodiment of the present invention has been described in detail with reference to the drawings. However, the specific configuration of the present invention is not limited to this embodiment, and even if there is a design change or the like without departing from the gist of the present invention. It is included in the present invention. The oil pump 160 has the same structure as the oil pump 60 (FIGS. 10 to 12).

FIG. 1 is a sectional view showing a supercharger. FIG. 2 is another sectional view showing the supercharger. FIG. 3 is another sectional view showing the supercharger. FIG. 4 is another sectional view showing the supercharger. FIG. 5 is a cross-sectional view taken along line VV in FIG. 6 is a cross-sectional view taken along line VI-VI in FIG. FIG. 7 is a sectional view taken along line VII-VII in FIG. FIG. 8 is a cross-sectional view showing the connecting member. FIG. 9 is an enlarged cross-sectional view of the main part of FIG. FIG. 10 is a side view showing the oil pump. FIG. 11 is an exploded perspective view showing the oil pump. 12 shows a cross section of the oil pump, (A) is a cross-sectional view taken along line AA in FIG. 10, and (B) is a cross-sectional view taken along line BB in FIG. FIG. 13 is a sectional view showing a conventional oil pump. FIG. 14 is a cross-sectional view showing a conventional example. FIG. 15 is a sectional view showing the reduction gear. FIG. 16 is another cross-sectional view showing the reduction gear. FIG. 17 is another sectional view showing the reduction gear. FIG. 18 is another sectional view showing the reduction gear. FIG. 19 is a sectional view taken along line XIX-XIX in FIG. 20 is a cross-sectional view taken along line XX-XX in FIG. FIG. 21 is a sectional view taken along line XXI-XXI in FIG. FIG. 22 is a cross-sectional view showing the connecting member. FIG. 23 is an enlarged cross-sectional view of the main part of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Supercharger 11 Input shaft 12 Output shaft 12A Driven side cylindrical surface 20 Speed up gear 27 Outer ring 27A Drive side cylindrical surface 28 Connecting member 28A Inner mounting portion 28B Outer mounting portion 28C Flexible portion (flexible membrane plate)
29 Cup-shaped bodies 31 to 33 Intermediate rollers 31A to 33A Power transmission cylindrical surface 50 Carrier 60 Oil pump 64, 65 Oil injection hole 66 Oil flow path 71 Rotor 71A Inlet corner 72 Vane 73 Base plate 74 Side plate 75 Cam ring 75A Outlet angle Port 76 Pump chamber 77 Suction port 78 Discharge port 110 Reducer 111 Input shaft 111A Drive side cylindrical surface 112 Output shaft 127 Outer ring 127A Driven side cylindrical surface 128 Connecting member 128A Inner mounting portion 128B Outer mounting portion 128C Flexible portion (flexible) Membrane plate)
129 Cup-shaped bodies 131-133 Intermediate rollers 131A-133A Power transmission cylindrical surface 150 Carrier 160 Oil pumps 164, 165 Oil injection hole 166 Oil flow path

Claims (7)

When the rotation of the input shaft is increased and transmitted to the output shaft,
An outer ring that is rotated by the input shaft and is eccentric with respect to the output shaft;
An annular space between the driven cylindrical surface, which is the outer peripheral surface of the output shaft, and the driving cylindrical surface, which is the inner peripheral surface of the outer ring, in which the width in the radial direction of the output shaft is not the same in the circumferential direction of the output shaft And a plurality of intermediate rollers each having an outer peripheral surface as a driven-side cylindrical surface and a cylindrical surface for power transmission in frictional contact with the driven-side cylindrical surface,
In the speed increasing machine which is a movable roller that can move at least one or more intermediate rollers in the circumferential direction and the radial direction of the output shaft,
An oil injection hole is provided in the carrier that supports the intermediate roller, and the oil that is injected from the oil injection hole is directly contacted with the output shaft and the intermediate roller, or the outer ring and the intermediate roller are in contact with each other. A speed increaser characterized by being supplied to A flexible membrane plate is fixed between the inner mounting portion and the outer mounting portion of the connecting member by fixing the inner mounting portion of the connecting member made of a cup-like body to the input shaft, fixing the outer mounting portion of the connecting member to the outer ring. Provided,
The speed increaser according to claim 1, wherein the cup-shaped body of the connecting member covers one side of the carrier and the intermediate roller, and defines an oil passage for guiding the oil flow to the inner peripheral surface of the outer ring. It has an oil pump driven by the input shaft or the output shaft, and the oil pump closes a pump chamber formed between the rotor and the cam ring with a plate,
The suction port provided in the plate is arranged radially inside from the pump chamber, and the inlet corner facing the suction port of the rotor is chamfered,
The speed increasing device according to claim 1 or 2, wherein a discharge port provided in the plate is disposed radially outward from the pump chamber, and an outlet corner portion facing the discharge port of the cam ring is chamfered.   The supercharger using the gearbox in any one of Claims 1-3. When decelerating the rotation of the input shaft and transmitting it to the output shaft,
An outer ring arranged eccentrically with respect to the input shaft and rotating the output shaft;
An annular space between the driving-side cylindrical surface that is the outer peripheral surface of the input shaft and the driven-side cylindrical surface that is the inner peripheral surface of the outer ring, and the width in the radial direction of the input shaft is not the same in the circumferential direction of the input shaft A plurality of intermediate rollers each having an outer peripheral surface serving as a cylindrical surface for power transmission in frictional contact with the driving-side cylindrical surface and the driven-side cylindrical surface,
In a speed reducer that is a movable roller that can move at least one intermediate roller in the circumferential direction and the radial direction of the input shaft,
An oil injection hole is provided in the carrier that supports the intermediate roller, and the oil that is injected from the oil injection hole directly contacts the rolling contact surface that the input shaft and the intermediate roller contact, or the rolling contact surface that contacts the outer ring and the intermediate roller. A speed reducer characterized by being supplied to. An inner mounting portion of a connecting member made of a cup-shaped body is fixed to the output shaft, an outer mounting portion of the connecting member is fixed to an outer ring, and a flexible membrane plate is provided between the inner mounting portion and the outer mounting portion of the connecting member. Provided,
The speed reducer according to claim 5, wherein the cup-shaped body of the connecting member covers one side of the carrier and the intermediate roller, and defines an oil flow path for guiding the oil flow to the inner peripheral surface of the outer ring. It has an oil pump driven by the input shaft or the output shaft, and the oil pump closes a pump chamber formed between the rotor and the cam ring with a plate,
The suction port provided in the plate is arranged radially inside from the pump chamber, and the inlet corner facing the suction port of the rotor is chamfered,
The speed reducer according to claim 5 or 6, wherein the discharge port provided in the plate is disposed radially outward from the pump chamber, and the outlet corner facing the discharge port of the cam ring is chamfered.

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