JP2009115265A - Belt-type continuously variable transmission and its assembly method - Google Patents

Abstract

A belt-type continuously variable transmission capable of relatively shortening the axial length of a rotating member to which a movable piece and a wall member are attached is provided.
A rotating member 22 that rotates by transmission of power, an axis A1 that is the center when the rotating member 22 rotates, and an outer circumference of the rotating member 22 that moves in a direction along the axis A1. The fixed piece 31 that cannot be moved, the movable piece 33 that is provided on the outer periphery of the rotating member 22 and that can move in the direction along the axis A 1, the hydraulic chamber 46 that is formed outside the rotating member 22, and the rotating member 22. In the belt-type continuously variable transmission including the wall member 38 that surrounds the hydraulic chamber 46 and the fixing mechanism 42 that prevents the wall member 38 from being detached from the rotating member 22, the rotating member 22 is moved along the axis A1. A hole 28 having a depth in the direction is provided, and a fixing mechanism 42 is provided in the hole 28.
[Selection] Figure 1

Description

  The present invention relates to a belt type continuously variable transmission configured to wrap a belt around a plurality of pulleys and transmit power between the pulleys, and an assembling method thereof.

  Conventionally, a power transmission path formed between a power source and a driven member is provided with a transmission. This transmission is a transmission that changes the ratio between the input rotation speed and the output rotation speed, that is, the transmission gear ratio. This transmission includes a continuously variable transmission that can change the gear ratio steplessly and a stepped transmission that can change the gear ratio stepwise. An example of this continuously variable transmission is described in Patent Document 1. Patent Document 1 describes a belt-type continuously variable transmission provided in a power transmission path from an engine to wheels. This belt type continuously variable transmission is provided in a transaxle case. The belt type continuously variable transmission has a primary shaft and a secondary shaft. The primary shaft is provided with a primary pulley, and the secondary shaft is provided with a secondary pulley. A belt is wound around the secondary pulley and the primary pulley. The primary pulley has a fixed piece and a movable piece. The fixed piece and the movable piece are configured to rotate integrally with the primary shaft. Further, the fixed piece is formed continuously on the outer peripheral side of the primary shaft, and this fixed piece is configured to be inoperable in the direction along the axis of the primary shaft.

  On the other hand, the movable piece is configured in an annular shape around the axis, and the movable piece is configured to be operable in a direction along the axis. Furthermore, a wall member is attached to the outer periphery of the primary shaft. The wall member is formed in an annular shape around the axis. A hydraulic chamber is formed between the wall member and the movable piece. Furthermore, a male screw part is formed on the outer periphery of the primary shaft, and a nut having a female screw part is provided. By tightening the nut, the movable piece is fixed to the primary shaft. Specifically, a step portion is formed on the outer periphery of the primary shaft, the inner peripheral end of the movable piece is sandwiched between the nut and the step portion, the movable piece is fixed, and the movable piece is detached from the primary shaft. It is prevented. In addition, an oil passage is formed in each of the primary shaft and the movable piece, and the oil passage communicates with the hydraulic chamber. The hydraulic pressure in the hydraulic chamber is controlled to control the thrust applied to the movable piece, that is, the thrust in the direction along the axis.

JP 2005-3035 A

  By the way, in the belt-type continuously variable transmission described in Patent Document 1, the inner peripheral end of the wall member and the nut are arranged side by side in the direction along the axis of the primary shaft. For this reason, there has been a problem that the axial length of the primary shaft becomes relatively long.

  The present invention has been made against the background of the above circumstances, and is a belt-type continuously variable transmission capable of relatively shortening the axial length of a rotating member provided with a movable piece and a wall member, and its assembly. It aims to provide a method.

  In order to achieve the above object, the invention of claim 1 is provided on a rotating member that is rotated by transmission of power, an axis that is the center when the rotating member rotates, and an outer periphery of the rotating member. And a fixed piece that does not move in the direction along the axis, a movable piece that is provided on the outer periphery of the rotating member and that can move in the direction along the axis, and is formed on the outer peripheral side of the rotating member. And a hydraulic chamber that applies thrust to the movable piece in a direction along the axis, a wall member that is provided in the rotating member and surrounds the hydraulic chamber, and the wall member is disengaged from the rotating member. In the belt-type continuously variable transmission provided with a fixing mechanism for preventing the rotation, a hole having a depth in the direction along the axis is formed in the rotating member, and the fixing mechanism is provided inside the hole. It is characterized by being Than is.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, the wall member includes an annular portion disposed outside the rotating member in a radial direction centered on the axis, and an inner periphery of the annular portion. A projecting portion that is continuous to the end and extends inward in the radial direction; and a cylindrical portion that is continuous to the inner peripheral end of the projecting portion and extends in a direction along the axis. The cylindrical portion is disposed inside the hole, and the fixing mechanism is provided between the outer peripheral surface of the cylindrical portion and the inner peripheral surface of the rotating member. It is what.

  According to a third aspect of the present invention, in addition to the configuration of the first or second aspect, an oil passage leading to the hydraulic chamber is provided between the end of the rotating member in the direction along the axis and the protruding portion. It is characterized by that.

  According to a fourth aspect of the present invention, in addition to the configuration of the first to third aspects, the fixing mechanism is a screw mechanism having a female screw portion formed on the rotating member and a male screw portion formed on the cylindrical portion. It is characterized by this.

  The invention of claim 5 has a press-fitting member inserted into the cylindrical portion in addition to the configuration of any of claims 1 to 4, and when the press-fitting member is press-fitted into the cylindrical portion. One of the male screw part and the female screw part provided in advance is pressed against the mating member, and either the male screw part or the female screw part is formed.

  According to a sixth aspect of the present invention, in addition to the configuration of the fourth or fifth aspect, the rotating member and the wall are formed between the rotating member and the cylindrical portion by a circumferential engagement force about the axis. An anti-rotation mechanism for preventing relative rotation of the member is provided.

  The invention of claim 7 is characterized in that, in addition to the structure of any of claims 2 to 6, a plug portion for closing the free end of the cylindrical portion is provided.

  According to an eighth aspect of the present invention, a rotating member made of a metal material is prepared, and a movable piece capable of moving in a direction along the axis is attached to the rotating member, and then the movable piece is attached to the rotating member. Assembly of a belt-type continuously variable transmission, in which a hydraulic chamber is formed between the wall member and a wall member made of a metal material is attached and then fixed so as to prevent the wall member from being detached from the rotating member. In the method, before attaching the wall member to the rotating member, a hole having a depth in the direction along the axis is formed in the rotating member, and an internal thread portion is formed on the inner peripheral surface of the rotating member. And a first step of forming an engagement portion projecting radially about the axis on the inner peripheral surface of the rotating member, and before attaching the wall member to the rotating member, the axis is attached to the wall member. Centered cylindrical part The second step is performed, the third step is performed subsequent to the first step and the second step, and the third step is performed after the third step of inserting the cylindrical portion of the wall member into the hole of the rotating member. In addition, a press-fitting member is press-fitted into the cylindrical portion in a direction along the axis, the cylindrical portion is pressed against the inner peripheral surface of the rotating member, and the cylindrical portion is placed outside the axis. By forming plastic deformation toward the outer periphery of the cylindrical portion, a male screw portion that meshes with the female screw portion is formed on the outer periphery of the cylindrical portion, and the rotation member and the wall member are rotated relative to each other by being engaged with the engaging portion. And a fourth step of forming an engaged portion to be prevented.

  According to the first aspect of the present invention, since the fixing mechanism is provided inside the hole of the rotating member, the wall member and the fixing mechanism can be avoided from being arranged in the direction along the axis. Therefore, the axial length of the rotating member can be relatively shortened.

  According to the invention of claim 2, in addition to obtaining the same effect as that of the invention of claim 1, a fixing mechanism is provided between the outer peripheral surface of the cylindrical portion and the inner peripheral surface of the rotating member.

  According to the invention of claim 3, in addition to obtaining the same effect as that of the invention of claim 1 or 2, an oil passage leading to the hydraulic chamber is provided between the end of the rotating member and the protrusion. . Therefore, it is not necessary to form the oil passage through the rotating member and the wall member. Therefore, it can suppress that the manufacturing cost of a rotation member and a wall member rises.

  According to the invention of claim 4, in addition to obtaining the same effect as that of any of the inventions of claims 1 to 3, it is possible to prevent the wall member from being detached from the rotating member by the screw mechanism.

  According to the invention of claim 5, in addition to obtaining the same effect as the invention of any one of claims 1 to 4, a screw mechanism is formed by press-fitting a press-fitting member inside the cylindrical portion. An increase in manufacturing cost can be suppressed.

  According to the invention of claim 6, in addition to obtaining the same effect as that of the invention of claim 4 or 5, it is possible to prevent the rotation member and the wall member from rotating relative to each other. Therefore, it is possible to prevent the screw mechanism from being loosened.

  According to the seventh aspect of the invention, the same effect as that of any of the fourth to sixth aspects can be obtained, and the free end of the cylindrical portion is closed by the plug portion. Therefore, the cylindrical portion is not easily deformed inward in the radial direction, and the durability of the screw mechanism is improved.

  According to the invention of claim 8, in the first step, before attaching the wall member to the rotating member, a hole having a depth in the direction along the axis is formed in the rotating member, An internal thread portion is formed on the peripheral surface, and an engaging portion protruding in the radial direction about the axis is formed on the inner peripheral surface of the rotating member. Further, in the second step, before the wall member is attached to the rotating member, a cylindrical portion centering on the axis is formed on the wall member. Further, following the first step and the second step, in the third step, the cylindrical portion of the wall member is inserted into the hole of the rotating member. In the fourth step after the third step, the press-fitting member is press-fitted into the cylindrical member in the direction along the axis, the cylindrical portion is pressed against the inner peripheral surface of the rotating member, and the cylindrical portion is centered on the axis. Plastic deformation toward the outside. Then, a male screw portion that meshes with the female screw portion is formed on the outer periphery of the cylindrical portion, and an engaged portion that engages with the engaging portion is formed. Thus, the screw mechanism can prevent the wall member from being detached from the rotating member. Further, the engaging portion and the engaged portion are engaged to form a rotation preventing mechanism, and relative rotation between the rotating member and the wall member is prevented. Therefore, it is possible to prevent the screw mechanism from being loosened. Furthermore, since the fixing mechanism is provided in the hole of the rotating member, it can be avoided that the inner peripheral end of the wall member and the fixing mechanism are arranged side by side in the direction along the axis. Therefore, the axial length of the rotating member can be relatively shortened.

  The present invention can be used for vehicles, machine tools, and the like. Specifically, a belt type continuously variable transmission is disposed in a power transmission path from a power source to a driven member. When the present invention is used in a vehicle, a belt-type continuously variable transmission can be disposed on a power transmission path from a driving force source to wheels (driven members). When this invention is used for a vehicle, it is possible to use at least one kind of driving force source among an engine, an electric motor, a hydraulic motor, a flywheel system and the like as a driving force source. When using a plurality of driving force sources, power is transmitted to the first power train configured to transmit a plurality of driving force sources to the same wheel, or to a different wheel for each driving force. Any of the configured second power trains may be used. The first power train is a so-called two-wheel drive vehicle, and the second power train is a four-wheel drive vehicle. The two-wheel drive vehicle may be configured such that the power of the driving force source is transmitted to either the front wheels or the rear wheels. The engine is a power unit that converts heat energy when fuel is burned into kinetic energy, and an internal combustion engine such as a gasoline engine, an LPG engine, or a methanol engine can be used as the engine. Further, the electric motor is a power device that converts electric energy into kinetic energy and outputs it, and may be either a DC motor or an AC motor. Further, as the electric motor, it is possible to use a motor / generator having both a function as a motor (power running function) and a function as a generator (regenerative function). The hydraulic motor is a power device that converts fluid energy of pressure oil into kinetic energy of a rotating member. Further, the flywheel system is a power unit that uses the inertial energy of the inertial mass as the kinetic energy of the rotating member.

  The vehicle includes a passenger car, a bus, a truck, and the like. When this invention is used for a machine tool, it is possible to arrange a belt type continuously variable transmission in a power transmission path from a power source to a workpiece or a tool (driven member). In the present invention, the rotating member is an element that transmits power, and the rotating member includes elements such as a shaft member, a connecting drum, and a gear. Further, the rotating member in the present invention means a member that can rotate, does not mean that it always rotates, and does not mean that it is currently rotating. Therefore, the rotating member can be stopped. Furthermore, a hole having a depth in the direction along the axis is formed in the rotating member. This hole may penetrate the rotating member in the direction along the axis, or may not penetrate the rotating member in the direction along the axis. The fixing mechanism according to the present invention prevents the wall member from detaching from the rotating member, specifically, the wall member and the rotating member relatively moving in the direction along the axis, and preventing the wall member from dropping from the rotating member. It is a mechanism to do.

  The wall member in this invention is a partition member that forms a hydraulic chamber in cooperation with the movable piece. Therefore, the wall member is made of a material, for example, a metal material, from which the hydraulic oil in the hydraulic chamber does not leak. The belt-type continuously variable transmission of the present invention is a transmission device in which power is transmitted between a plurality of rotating members via a belt that is an annular winding transmission member, and the rotational speed of the input member, The transmission can change the ratio with the rotation speed of the output member, that is, the gear ratio steplessly or continuously. Furthermore, when the belt type continuously variable transmission according to the present invention is mounted on a vehicle, the belt type continuously variable transmission is supported by the support mechanism. Here, the support mechanism may be a frame member or a bracket in addition to a casing or a housing that is hollow inside. Further, that the belt type continuously variable transmission is supported by the support mechanism specifically means that the rotating member is directly or indirectly supported by the support mechanism with a bearing interposed therebetween. Further, the belt used in the belt type continuously variable transmission is an endless belt, and may be either a belt that transmits power by pressing force or a belt (chain) that transmits power by pulling force.

  On the other hand, in the assembly method of the belt type continuously variable transmission, the first step and the second step may be performed in parallel, that is, at the same time, and either the first step or the second step is performed first. And other steps may be performed later.

  Next, a specific example when the belt type continuously variable transmission of the present invention is used in a vehicle will be described with reference to the drawings. FIG. 2 is a skeleton diagram showing a specific example in which a belt-type continuously variable transmission is arranged on a power transmission path from a driving force source of a vehicle to wheels. The vehicle 1 shown in FIG. 2 is provided with an engine 2 as a driving force source that generates driving force for traveling. As the engine 2, an internal combustion engine, specifically, a gasoline engine, a diesel engine, an LPG engine, or the like is used. The engine 2 is a power unit that burns fuel and outputs thermal energy as kinetic energy of the crankshaft 3. A crankshaft 3 that is an output shaft of the engine 2 is disposed in the width direction (left-right direction) of the vehicle 1. The crankshaft 3 is provided so as to be rotatable about an axis A1, and the axis A1 is disposed substantially horizontally.

  A transaxle case 4 is fixed to the outer wall of the engine 2. The transaxle case 4 has a housing 5, a casing 6, and a rear cover 7 that are divided in a direction along the axis A 1. The housing 5, the casing 6 and the rear cover 7 are all made of a metal material. Examples of the metal material include aluminum or an aluminum alloy. The housing 5, the casing 6 and the rear cover 7 are molded and processed as separate members. A casing 6 is disposed between the housing 5 and the rear cover 7 in a direction along the axis A1. The housing 5 and the casing 6 are fastened and fixed using a fixing mechanism (not shown) such as bolts and nuts. In addition, the casing 6 and the rear cover 7 are fastened and fixed using a fixing mechanism (not shown) such as bolts and nuts.

  Inside the transaxle case 4 thus configured, a fluid transmission device 8, a forward / reverse switching mechanism 9, a belt-type continuously variable transmission 10, and a differential 11 are arranged. The fluid transmission device 8, the forward / reverse switching device 9, the belt type continuously variable transmission 10 and the differential 11 are transmission devices that constitute a power transmission path from the engine 2 to the wheels 12. The wheel 12 is provided outside the transaxle case 4, and the wheel 12 is supported by a vehicle body (not shown) via a suspension device (not shown).

  A fluid transmission device 8 is disposed between the forward / reverse switching device 9 and the engine 2 in a direction along the axis A1. The fluid transmission device 8 includes a pump impeller 13 and a turbine runner 14. The pump impeller 13 and the crankshaft 3 are connected to transmit power, and the turbine runner 14 and the input shaft 15 are connected to transmit power. The input shaft 15 is disposed so as to be rotatable about the axis A1. Further, a lock-up clutch 16 that connects the pump impeller 13 and the input shaft 15 so as to be able to transmit power is provided. In the fluid transmission device 8 configured as described above, when the lock-up clutch 16 is released, power is transmitted between the pump impeller 13 and the turbine runner 14 by the kinetic energy of the fluid. Further, when the lockup clutch 16 is engaged, power is transmitted between the crankshaft 3 and the input shaft 15 by a frictional force.

  On the other hand, the forward / reverse switching device 9 is disposed between the belt-type continuously variable transmission 10 and the fluid transmission device 8 in a direction along the axis A1. In this specific example, the forward / reverse switching device 9 has a double pinion type planetary gear mechanism. The planetary gear mechanism includes a sun gear 17 that rotates integrally with the input shaft 15, a ring gear 18 that is disposed coaxially with the sun gear 17 on the outer peripheral side of the sun gear 17, and a pinion gear 19 that meshes with the sun gear 17. A pinion gear 20 meshed with the pinion gear 19 and the ring gear 18 and a carrier 21 that holds the pinion gears 19 and 20 so as to be capable of rotating and revolving are provided. And this carrier 21 and the primary shaft 22 of the belt-type continuously variable transmission 10 are connected so that power transmission is possible.

  Further, the forward / reverse switching device 9 has a switching mechanism that switches the rotation direction of the carrier 21 as an output element between forward and reverse. In this embodiment, a friction engagement device, specifically, a forward clutch 23 and a reverse brake 24 are used as the switching mechanism. The forward clutch 23 selectively connects / disconnects the input shaft 15 and the carrier 21. As the forward clutch 23, it is possible to use a hydraulic clutch that operates by hydraulic pressure, or an electromagnetic clutch that operates by electromagnetic force. Further, the reverse brake 24 can apply a braking force to the ring gear 18 to stop the ring gear 18. As the reverse brake 24, it is possible to use a hydraulic brake that operates by hydraulic pressure or an electromagnetic brake that operates by electromagnetic force.

  Next, the configuration of the belt type continuously variable transmission 10 will be described. The belt type continuously variable transmission 10 has a primary shaft 22 and a secondary shaft 25. First, the primary shaft 22 is configured to be rotatable about the axis A1. The secondary shaft 25 is provided so as to be rotatable about the axis B1. The axis A1 and the axis B1 are arranged in parallel. Further, the primary shaft 22 is provided with a primary pulley 26, and the secondary shaft 25 is provided with a secondary pulley 27.

  Here, the “first specific example” of the primary shaft 22 and the primary pulley 26 will be described with reference to FIG. Two holes 28 and 29 are formed in the primary shaft 22 at different positions in the direction along the axis A1. The two holes 28 and 29 both have a depth in the direction along the axis A1. Further, the hole 28 is formed closer to the rear cover 7 than the hole 29 in the direction along the axis A1. Further, the hole 29 is formed closer to the forward / reverse switching device 9 than the hole 28 in the direction along the axis A1. The holes 28 and 29 are both formed around the axis A1. Further, a partition wall 32 is formed between the hole 28 and the hole 29 in the direction along the axis A1. That is, the hole 28 and the hole 29 are partitioned by the partition wall 32. On the other hand, the carrier 21 has a cylindrical portion 30, and the cylindrical portion 30 is inserted into the hole 29. Specifically, the cylindrical portion 30 and the primary shaft 22 are splined or serrated and the carrier 21 and the primary shaft 22 are integrally rotated.

  A fixed piece 31 is formed continuously on the outer periphery of the primary shaft 22 configured as described above. The primary shaft 22 and the fixed piece 31 are integrally formed of a metal material. Therefore, the fixed piece 31 rotates integrally with the primary shaft 22 and cannot operate in the direction along the axis A <b> 1 with respect to the primary shaft 22. The fixed piece 31 has a flange shape that protrudes outward in the radial direction with the axis A1 as the center. Further, the fixing piece 31 is provided in the same region as the region where the hole 29 is formed in the direction along the axis A1. On the other hand, a movable piece 33 is attached to the outer periphery of the primary shaft 22. The movable piece 33 has a cylindrical portion 34 configured in a cylindrical shape, and a flange portion 35 formed continuously on the outer periphery of the cylindrical portion 34. The flange portion 35 protrudes outward in the radial direction about the axis A1. Further, an O-ring 37 is attached to the outer periphery of the flange portion 35. The cylindrical portion 34 is disposed so as to surround the primary shaft 22, and the cylindrical portion 34 and the primary shaft 22 are spline-coupled or serrated-coupled.

  Further, the movable piece 33 and the primary shaft 22 are coupled so as to rotate integrally, and the movable piece 33 and the primary shaft 22 can move relative to each other in the direction along the axis A1. In addition, the operation area of the movable piece 33 and the arrangement area of the hole 28 overlap each other in the direction along the axis A1. Further, an annular seat 36 is fixed to the end of the primary shaft 22 that is closer to the rear cover 7. The outer diameter of the sheet 36 is configured to be larger than the inner diameter of the movable piece 33. Therefore, when the movable piece 34 moves toward the left side in FIG. 1, the movable piece 34 comes into contact with the sheet 36 and the movable range of the movable piece 34 is restricted. Note that the end surface of the shaft end of the primary shaft 22 and the end surface of the sheet 36 are located on substantially the same plane. The movable piece 33 and the fixed piece 31 thus configured constitute a primary pulley 26, and a groove C <b> 1 is formed between the movable piece 33 and the fixed piece 31. Note that the primary shaft 22 and the primary pulley 33 are made of a metal material such as carbon steel or chrome steel.

  Next, a mechanism for moving the movable piece 33 in the direction along the axis A1 will be described. A cylinder 38 is provided on the primary shaft 22. The cylinder 38 is made of a metal material such as a rolled steel plate. The cylinder 38 is formed in an annular shape as a whole, and the cylinder 38 has a curved portion 39, a protruding portion 40, and a cylindrical portion 41. The bending portion 39 is disposed outside the primary shaft 22, and the bending portion 39 is bent in a substantially S shape within a plane in a direction along the axis A1. The outer portion of the curved portion 39 is disposed outside the flange portion 35 of the movable piece 33, and the O-ring 37 is in contact with the curved portion 38 to form a sealing surface. The protruding portion 40 is formed continuously at the inner peripheral end of the bending portion 39. The protruding portion 40 protrudes inward in the radial direction from the inner peripheral end of the bending portion 39. That is, the protrusion 40 has a disk shape configured in parallel with a plane perpendicular to the axis A1.

  Further, the cylindrical portion 41 is continuously formed at the inner peripheral end of the protruding portion 40. The cylindrical portion 41 extends from the inner peripheral end of the protruding portion 40 in a direction along the axis A1. The cylindrical portion 41 is disposed in the hole 28, and the outer peripheral surface of the cylindrical portion 41 and the primary shaft 22 are joined and fixed. Specifically, the cylindrical portion 41 and the primary shaft 22 are welded by electron beam welding to form the joint portion 42. Since the primary shaft 22 and the cylinder 38 are welded and fixed in this way, the primary shaft 22 and the cylinder 38 can rotate integrally, and the cylinder 38 cannot move in the direction along the axis A1. That is, the cylinder 38 is configured not to be detached from the primary shaft 22. The cylinder 38 is rotatably supported by the rear cover 7 via a bearing 43, and the primary shaft 22 is rotatably supported by the casing 6 via a bearing 44. The bearing 43 has an inner ring 61, an outer ring 62 and a rolling element 63. The inner ring 61 holds the cylinder 38. An annular holding portion 64 is formed on the inner periphery of the rear cover 7, and an outer ring 62 is press-fitted into the holding portion 64. Further, the rear cover 7 is fixed with a plate 66 for positioning and fixing the outer ring 62 to the rear cover 7 in the direction along the axis A1. The plate 66 is fixed to the rear cover 7 with bolts 65.

  A specific configuration of the protrusion 40 will be described with reference to FIG. The protrusions 40 have a waveform shape that is alternately bent in the direction along the axis A1. Even when the protruding portion 40 contacts the sheet 36, a portion where the protruding portion 40 does not contact the sheet 36, that is, a groove is formed. This groove constitutes an oil passage 45. A hydraulic chamber 46 is formed between the movable piece 33 and the bending portion 39, and an oil passage 45 communicates with the hydraulic chamber 36. Furthermore, the structure of the said cylindrical part 42 is demonstrated based on FIG. FIG. 4 is a cross-sectional view in a direction orthogonal to the axis A1. A groove is formed in the direction along the axis A <b> 1 on the outer peripheral surface of the cylindrical portion 41, and the groove constitutes an oil passage 47. A plurality of oil passages 47 are provided in the circumferential direction, and each oil passage 47 communicates with each oil passage 45.

  A joining portion 42 is formed between the oil passages 47 in the circumferential direction of the cylindrical portion 41. Further, the oil passage 47 communicates with the hole 28. Then, it is possible to supply pressure oil to the hydraulic chamber 46 via the hole 28 and the oil passages 47 and 45. In addition, the pressure oil in the hydraulic chamber 46 can be discharged to the hole 28 via the oil passages 45 and 47. In this way, the hydraulic pressure in the hydraulic chamber 46 is controlled, and the axial thrust applied to the movable piece 33 is controlled. As described above, in this specific example, the region where the joint portion 42 is formed and the region where the movable piece 33 can operate partially overlap in the direction along the axis A1. Further, a part of the arrangement region of the cylinder 38 and the whole arrangement region of the joint portion 42 overlap each other in the direction along the axis A1. Further, a cylindrical portion 53 extending toward the inside of the transaxle case 4 is formed continuously with the rear cover 7. The cylindrical portion 53 is disposed around the axis A1. The cylindrical portion 41 is disposed outside the cylindrical portion 53 in the radial direction centered on the axis A1. An O-ring 54 is disposed between the cylindrical portion 41 and the cylindrical portion 53. The O-ring 54 prevents the pressure oil in the hole 28 from leaking into the transaxle case 4 via the space between the cylindrical portion 41 and the cylindrical portion 53.

  Next, the configuration of the secondary shaft 25 and the secondary pulley 27 will be described. The secondary pulley 27 has a fixed piece 48 and a movable piece 49. The fixed piece 48 rotates integrally with the secondary shaft 25 and cannot move in the direction along the axis B1. On the other hand, the movable piece 49 is configured to rotate integrally with the secondary shaft 25 and to operate in the direction along the axis B <b> 1 with respect to the secondary shaft 25. Further, a hydraulic chamber (not shown) is provided for applying a thrust in the direction along the axis to the movable piece 49. A groove D <b> 1 is formed between the movable piece 49 and the fixed piece 48. A belt 50 is wound around the primary pulley 26 and the secondary pulley 27. The belt 50 is attached to a ring-shaped cage in a state where a plurality of elements are laminated along the circumferential direction. Further, a gear transmission 51 is provided as a transmission on the path from the secondary shaft 25 to the differential 11. Further, the wheel 12 is connected to a drive shaft 52 which is an output shaft of the differential 11.

  Next, control and operation of the power train shown in FIG. 1 will be described. For example, the driving / stopping of the engine 2 is controlled based on parameters such as the vehicle speed and the accelerator opening. When the engine 2 is in operation and the lockup clutch 16 in the fluid transmission device 8 is released, power is transmitted between the pump impeller 13 and the turbine runner 14 by the kinetic energy of the hydraulic oil. It is carried out. On the other hand, when the lockup clutch 16 is engaged, power is transmitted between the crankshaft 3 and the input shaft 15 by a frictional force. In this way, the engine torque is transmitted to the input shaft 15.

  Furthermore, control of the forward / reverse switching device 9 will be described. When the forward position is selected as the shift position, the forward clutch 23 is engaged, the reverse brake 24 is released, and the input shaft 15 and the primary shaft 22 are connected to rotate integrally. In this state, when engine torque is transmitted to the input shaft 15, the input shaft 15, the carrier 21, and the primary shaft 22 rotate integrally. On the other hand, when the reverse position is selected, the forward clutch 23 is released and the reverse brake 24 is engaged, so that the ring gear 18 is fixed. Then, the ring gear 18 becomes a reaction force element, and the carrier 21 and the primary shaft 22 rotate in a direction opposite to the rotation direction of the input shaft 15 as the input shaft 15 rotates.

  Next, control of the gear ratio and transmission torque of the belt type continuously variable transmission 10 will be described. In the belt type continuously variable transmission 10, the belt 50 is configured by laminating a plurality of elements, and the power of the primary pulley 26 is transmitted to the secondary pulley 27 by a pressing force generated between the elements. Further, by controlling the hydraulic pressure in the primary pulley 26 hydraulic chamber 46, the clamping pressure applied from the primary pulley 26 to the belt 50 is controlled, and the ratio between the rotation speed of the primary shaft 22 and the rotation speed of the secondary shaft 25, that is, The gear ratio is changed steplessly (continuously). Further, by controlling the hydraulic pressure in the hydraulic chamber (not shown) of the secondary pulley 27, the clamping pressure applied to the belt 50 from the secondary pulley 27 changes, and the transmission torque is controlled. Thus, the torque transmitted to the secondary pulley 27 is transmitted to the drive shaft 52 via the secondary shaft 25, the gear transmission 51, and the differential 11 to generate a driving force.

  In the “first specific example” shown in FIGS. 1, 2, and 3, a joint portion 42 is provided in the hole 28 of the primary shaft 22. Specifically, a part of the arrangement area of the cylinder 38 and the whole arrangement area of the joint portion 42 overlap each other in the direction along the axis A1. For this reason, it can avoid that the arrangement | positioning area | region of the cylinder 38 and the arrangement | positioning area | region of the junction part 42 are located in a line along the axis A1. Therefore, it can suppress that the axial length of the primary shaft 22 becomes relatively long in the direction along the axis A1. In the first specific example, oil passages 45 and 47 communicating with the hydraulic chamber 46 are formed between the primary shaft 22 and the cylinder 38. For this reason, it is not necessary to form the oil passage through the primary shaft 22 and the cylinder 38. Therefore, it can suppress that the manufacturing cost of the primary shaft 22 and the cylinder 38 rises. Further, the cylinder 38 is formed by pressing a metal material, and grooves that become the oil passages 45 and 47 can be formed in the cylinder 38 by a pressing process of the cylinder 38. Therefore, an increase in manufacturing cost can be further suppressed.

  Furthermore, a sensor (not shown) for detecting the rotation speed of the primary shaft 22 can be attached to the inner wall of the rear cover 7. Here, if an electromagnetic pickup type sensor is used as the sensor, it is also possible to detect the rotational speed of the primary shaft 22 by using the uneven portion formed by the side surface of the protruding portion 40 of the cylinder 38. The concavo-convex portion means a concavo-convex portion that is displaced in a direction along the axis A1. Further, the protruding portion 40 of the cylinder 38 has a wave shape, and the strength against the bending load in the direction along the axis A1 is relatively increased. For this reason, even when the hydraulic pressure of the hydraulic chamber 46 acts on the cylinder 38 and a load is applied in such a direction as to press the curved portion 39 against the rear cover 7, it is possible to suppress the cylinder 38 from being elastically deformed by the protruding portion 40. Therefore, it is possible to avoid leakage of the pressure oil in the hydraulic chamber 46 through the seal surface formed by the O-ring 37.

  The correspondence between the configuration described based on the “first specific example” and the configuration of the present invention will be described. The axis A1 corresponds to the axis in the present invention, and the primary shaft 22 is the rotating member in the present invention. The fixed piece 31 corresponds to the fixed piece in the present invention, the movable piece 33 corresponds to the movable piece in the present invention, the hydraulic chamber 46 corresponds to the hydraulic chamber in the present invention, and the cylinder 38 Corresponding to the wall member in the present invention, the joining portion 42 corresponds to the fixing mechanism in the present invention, the hole 28 corresponds to the hole in the present invention, the curved portion 39 corresponds to the annular portion of the present invention, and protrudes The portion 40 corresponds to the protruding portion of the present invention, the cylindrical portion 41 corresponds to the cylindrical portion of the present invention, and the oil passage 45 corresponds to the oil passage in the present invention.

  Next, a “second specific example” of the primary shaft 22 and the primary pulley 33 will be described with reference to FIG. In the “second specific example”, the same reference numerals as those in the first specific example are used for the same components as those in the first specific example. FIG. 5 is a cross-sectional view in the direction along the axis A1. In the second specific example, the length of the cylindrical portion 41 is longer than the cylindrical portion 41 described in the first specific example in the direction along the axis A1. In the second specific example, the free end of the cylindrical portion 41 and the primary shaft 22 are fixed by the screw mechanism 55 in the direction along the axis A1. Specifically, the screw mechanism 55 includes a female screw portion 56 formed on the inner periphery of the primary shaft 22 and a female screw portion 57 formed on the outer periphery of the cylindrical portion 41. The screw mechanism 55 fixes the cylinder 38 so as not to be detached from the primary shaft 22. That is, the primary shaft 22 and the cylinder 38 are prevented from relatively moving in the direction along the axis A1. Furthermore, in the direction along the axis A1, the region where the curved portion 38 is formed and the region where the screw mechanism 55 is formed overlap. Furthermore, in the second specific example, an oil passage 58 is provided between the screw mechanism 55 and the protruding portion 40 in the direction along the axis A1. The oil passage 58 is provided through the cylindrical portion 41 in the radial direction. A plurality of the oil passages 58 are provided in the circumferential direction around the axis A1. The oil passage 58 allows the hole 28 and the oil passage 47 to communicate with each other.

  Further, the shape of the hole 28 of the cylindrical portion 41 is a hexagon in a plane orthogonal to the axis A1. When a hexagon wrench is inserted into the hole 28 and the hexagon wrench is rotated about the axis A1, the screw mechanism 55 can be loosened or tightened. Also in the “second specific example”, the same operational effects as those of the first specific example can be obtained with respect to the same components as in the first specific example. In the second specific example, the region where the curved portion 38 is formed and the region where the screw mechanism 55 is formed overlap each other in the direction along the axis A1. For this reason, it can suppress that the primary shaft 22 becomes relatively long in the direction along the axis A1. In the second specific example, the screw mechanism 55 corresponds to the fixing mechanism of the present invention. The correspondence between the other configurations in the second specific example and the configuration of the present invention is the same as the corresponding relationship between the configuration of the first specific example and the configuration of the present invention.

  Next, a “third specific example” of the primary shaft 22 and the cylinder 38 will be described with reference to FIG. FIG. 6 is a cross-sectional view in the direction along the axis A1. In the “third specific example”, the same components as those in FIG. 5 are denoted by the same reference numerals as those in FIG. The “third specific example” is different from the second specific example in that the hole 28 formed in the primary shaft 22 penetrates the primary shaft 22 in the direction along the axis A1. For this reason, in the third specific example, the cylindrical portion 41 and the cylindrical portion 30 are disposed in the hole 28. Furthermore, in the third specific example, a plug portion 59 is formed continuously at the free end of the cylindrical portion 41. That is, the opening end of the cylindrical portion 41 is closed by the plug portion 59. The plug portion 59 has a disk shape centered on the axis A1. In the “third specific example”, the cylinder 38 is manufactured by pressing a metal material. In this way, the oil passage 60 is formed in the cylindrical portion 41. The oil passage 60 communicates with the oil passage 47 through the oil passage 58.

  In the third specific example, the same operational effects as those of the first specific example and the second specific example can be obtained with respect to the same components as those of the first specific example and the second specific example. In the third specific example, the hole 28 and the oil passage 60 are liquid-tightly partitioned by the plug portion 59. Therefore, in the third specific example, it is not necessary to provide the partition wall 32 on the primary shaft 22 as in the second specific example. For this reason, in the process of manufacturing the primary shaft 22, the hole 22 may be formed by cutting a rod-shaped workpiece from one side in the direction along the axis with a tool. Or if the fixed piece 31 is provided in the outer periphery of a tube-shaped workpiece, the primary shaft 22 can be manufactured. That is, it can suppress that the manufacturing cost of the primary shaft 22 rises. Further, since the plug portion 59 is provided, the rigidity of the cylindrical portion 41 is increased, and the durability of the male screw portion 57 is improved. The correspondence between the “third specific example” and the configuration of the present invention will be described. The plug portion 59 corresponds to the plug portion in the present invention. The correspondence between the other configurations in the third specific example and the configuration of the present invention is the same as the corresponding relationship between the configurations of the first specific example and the second specific example and the configuration of the present invention.

  Next, a “fourth example” of the primary shaft 22 and the cylinder 38 will be described with reference to FIG. In the fourth specific example, the same components as those in the third specific example are denoted by the same reference numerals as those in the third specific example. In the fourth specific example, the cylindrical portion 41 is not provided with the plug portion 59. In the fourth specific example, a hole 28 that penetrates the primary shaft 22 in the direction along the axis A <b> 1 is provided, and a cylindrical portion 41 is disposed in the hole 28. In addition to the screw mechanism 55, an anti-rotation mechanism 67 is provided at a contact portion between the cylindrical portion 41 and the primary shaft 22. The anti-rotation mechanism 67 is a mechanism that prevents the cylinder 38 and the primary shaft 22 from rotating relative to each other in the circumferential direction about the axis A1. Specifically, the primary shaft 22 and the cylindrical portion 41 are splined or serrated to form a rotation preventing mechanism 67. That is, the outer teeth 70 are formed on the outer peripheral surface of the cylindrical portion 41, and the inner teeth 69 are formed on the inner peripheral surface of the primary shaft 22. The inner teeth 69 and the outer teeth 70 are engaged to generate a circumferential engaging force. Further, a plug 68 is press-fitted and fixed in the cylindrical portion 41. The plug 68 divides the oil passage 60 in the cylindrical portion 41 and the hole 28 in a liquid-tight manner. The plug 68 is made of a metal material in a cylindrical shape. The plug 68 is made of a metal material having a hardness higher than that of the cylinder 38.

  Further, a method for assembling the belt type continuously variable transmission of the fourth specific example will be described. First, the first step will be described. This first process is a manufacturing process of the primary shaft 22, and in this first process, the primary shaft 22 in which the internal thread 69 and the internal teeth 69 are formed in the hole 28 by processing a rotating member made of a metal material. To manufacture. In the first step, the cylinder 38 is not attached to the primary shaft 22. Next, the second step will be described. This second process is a manufacturing process of the cylinder 38. The first step and the second step may be performed simultaneously or in parallel, and a time difference may be generated between the first step and the second step. In the second step, the cylinder 38 is manufactured by pressing a metal material. In the second step, the cylinder 38 is not attached to the primary shaft 22.

  Following the first step and the second step, the primary shaft 22 is arranged inside the casing 6 as shown in FIG. Thereafter, in the third step, the cylinder 38 is inserted into the casing 6, and the cylindrical portion 41 of the cylinder 38 is inserted into the hole 28 of the primary shaft 22. In the third step, the male screw 57 and the external teeth 70 are not yet formed on the outer peripheral surface of the cylindrical portion 41. In this third step, oil passages 45 and 47 are formed. A fourth step is performed after the third step. In the fourth step, the plug 68 is moved along the axis A <b> 1, and the plug 68 is press-fitted into the cylindrical portion 41. Then, the load which expands the cylindrical part 41 toward the outer side generate | occur | produces. As a result, the cylindrical portion 41 is pressed against the inner peripheral surface of the primary shaft 22 and plastically deformed, and the male screw portion 57 and the external teeth 70 are formed on the outer peripheral surface of the cylindrical portion 41.

  As described above, in the fourth step, the screw mechanism 55 in which the male screw portion 57 and the female screw portion 56 are engaged with each other and the anti-rotation mechanism 67 in which the inner teeth 69 and the outer teeth 70 are engaged are formed. . On the other hand, a unit in which the bearing 43 is attached to the rear cover 7 is assembled. This unit assembly operation may be performed in parallel with the first step to the third step, or may be performed at a different time from the first step to the third step. After the fourth step, the unit in which the bearing 43 is attached to the rear cover 7 is brought close to the casing 6, the cylinder 38 is held by the inner ring 63 of the bearing 43, and a bolt (not shown) is tightened to tighten the casing 6 and the rear cover. 7 are fixed to each other. In this way, the work of attaching the belt type continuously variable transmission 10 in the transaxle case 4, that is, the assembling work is completed.

  In the fourth specific example, when the plug 68 is press-fitted into the cylindrical portion 41 to form the screw mechanism 55 and the rotation preventing mechanism 67, the screw mechanism 55 is provided. However, there is no relative movement in the direction along the axis A1. Further, since the rotation prevention mechanism 67 is provided, the primary shaft 22 and the cylinder 38 do not rotate relative to each other about the axis A1. Therefore, even when the hydraulic pressure in the hydraulic chamber 46 acts on the cylinder 38 and a load in the direction along the axis A1 is applied to the cylinder 38, the screw mechanism 55 can be reliably prevented from loosening. The retaining function is further improved. Further, since the plug 68 is press-fitted into the inner periphery of the cylindrical portion 41, it is possible to prevent the cylindrical portion 41 from being deformed inward with the axis A1 as the center, and it is further ensured that the meshing force of the screw mechanism 55 is reduced. Can be prevented. In the fourth specific example, the same operational effects as those of the third specific example can be obtained for the same components as those of the third specific example. Here, the correspondence between the configuration of the fourth specific example and the configuration of the present invention will be described. The plug 68 corresponds to the press-fitting member of the present invention, and the anti-rotation mechanism 67 corresponds to the anti-rotation mechanism of the present invention. Correspondingly, the external tooth 69 corresponds to the engaging portion in the present invention, and the internal tooth 70 corresponds to the engaged portion in the present invention.

  Next, a “fifth specific example” of the primary shaft 22 and the cylinder 38 will be described with reference to FIG. In the fifth specific example, the same components as those in the first specific example to the fourth specific example are denoted by the same reference numerals as those in the first specific example to the fourth specific example. In the “fifth specific example”, the primary shaft 22 and the fixed piece 31 are separately formed of a metal material, and the primary shaft 22 and the fixed piece 31 are connected so as to rotate integrally. , Different from the first to fourth examples. In the “fourth specific example”, the primary shaft 22 and the fixed piece 31 are made of carbon steel, chrome steel, or the like. The primary shaft 22 has a pipe shape having a hole 28, and the primary shaft 22 and the fixed piece 31 are connected so as to rotate integrally. Further, the cylindrical portion 31 of the carrier 21 is coupled to the fixed piece 31 and the primary shaft 22 so as to rotate integrally. Further, an outward flange 71 is formed at the end of the primary shaft 22 opposite to the position where the fixed piece 31 is provided. The outward flange 71 protrudes outward in the radial direction and is provided over the entire circumference of the primary shaft 22.

  A movable piece 33 is provided between the fixed piece 31 and the outward flange 71 in the direction along the axis A <b> 1 on the outer peripheral side of the primary shaft 22. For this reason, when the movable piece 33 contacts the outward flange 71, the operation in the direction along the axis A1 is restricted. Further, the primary shaft 22 and the movable piece 38 are connected so as to be able to rotate integrally. Further, the oil passage 45 is formed between the end portion of the primary shaft 22 and the protruding portion 40 of the cylinder 38, and the oil passage 47 is formed between the cylinder 22 and the cylindrical portion 41. The configuration is the same as the specific example. Further, the point that a screw mechanism 55 serving as a retaining mechanism is provided between the primary shaft 22 and the cylindrical portion 41 is the same as the fourth specific example. Furthermore, the point that the rotation prevention mechanism 67 is provided between the cylindrical portion 41 and the primary shaft 22 is the same as the fourth specific example. Furthermore, the point that the plug 68 is press-fitted into the cylindrical portion 41 is the same as the fourth specific example.

  A method of assembling the belt type continuously variable transmission according to the “fifth example” will be described. First, the first step will be described. This first process is a manufacturing process of the primary shaft 22. In this first process, a pipe made of a metal material is processed to manufacture the primary shaft 22 in which the internal thread 56 and the internal teeth 69 are formed in the hole 28. To do. In the first step, the cylinder 38 is not attached to the primary shaft 22. In addition to the primary shaft 22, the fixed piece 31 and the movable piece 38 are manufactured, and the movable piece 38 is first attached to the outer periphery of the primary shaft 22. Thereafter, the fixed piece 31 is attached to the outer periphery of the primary shaft 22, the carrier 21 is attached to the primary shaft 22 and the fixed piece 31 so as to rotate integrally, and the primary pulley 26 is attached to the primary shaft 22. A unit is configured.

  Next, the second step will be described. This second process is a manufacturing process of the cylinder 38. The first step and the second step may be performed simultaneously or in parallel, and a time difference may occur between the first step and the second step. In the second step, the cylinder 38 is manufactured by pressing a metal material. In the second step, the cylinder 38 is not attached to the primary shaft 22. Following the first step and the second step, the unit of the primary shaft 22 and the primary pulley 26 is disposed inside the casing 6 as shown in FIG. The third step and the fourth step performed thereafter are the same as in the case of the fourth specific example, and thus description thereof is omitted. In the “fifth specific example”, the same operational effects as those of the first specific example to the fourth specific example can be obtained for the same components as those of the first specific example to the fourth specific example. Further, in the “fifth specific example”, since the primary shaft 22 is manufactured using a pipe, it is not necessary to perform cutting when the hole 28 is formed, and the manufacturing cost can be further reduced. In the power train shown in FIG. 2, the forward / reverse switching device 9 is arranged on the power transmission path from the engine 2 to the belt type continuously variable transmission 10, but from the belt type continuously variable transmission 10 to the wheels 12. The present invention can also be applied to a power train in which a forward / reverse switching device is arranged in the power transmission path. The forward / reverse switching device 9 has a planetary gear mechanism, but a parallel shaft gear type forward / backward switching device can also be used.

In the belt-type continuously variable transmission of this invention, it is sectional drawing which shows "the 1st example" of a structure of a primary shaft and a primary pulley. It is a skeleton figure which shows the power train of the vehicle which has a belt-type continuously variable transmission in this invention. It is sectional drawing of the cylinder in III-III of FIG. It is sectional drawing of the primary shaft and cylinder of FIG. FIG. 6 is a cross-sectional view showing a “second specific example” of a configuration of a primary shaft and a primary pulley in the belt-type continuously variable transmission of the present invention. FIG. 7 is a cross-sectional view showing a “third specific example” of a configuration of a primary shaft and a primary pulley in the belt-type continuously variable transmission of the present invention. In the belt-type continuously variable transmission of this invention, it is sectional drawing which shows "the 4th example" of a structure of a primary shaft and a primary pulley. It is sectional drawing which shows the assembly process of the primary shaft and primary pulley which were shown by FIG. In the belt-type continuously variable transmission of this invention, it is sectional drawing which shows the "5th example" of a structure of a primary shaft and a primary pulley. It is sectional drawing which shows the assembly process of the primary shaft shown in FIG. 9, and a primary pulley.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Belt-type continuously variable transmission, 22 ... Primary shaft, 28 ... Hole, 31 ... Fixed piece, 33 ... Movable piece, 38 ... Cylinder, 42 ... Joint part, 46 ... Hydraulic chamber, 39 ... Curved part, 40 ... Projection , 41 ... cylindrical part, 45 ... oil passage, 55 ... screw mechanism, 56 ... female screw part, 57 ... male screw part, 69 ... internal teeth, 70 ... external teeth, A1 ... axis.

Claims (8)

A rotating member that is rotated by transmission of power, an axis that becomes the center when the rotating member rotates, and a fixed piece that is provided on the outer periphery of the rotating member and does not move in a direction along the axis; A movable piece provided on the outer periphery of the rotating member and capable of moving in a direction along the axis, and a thrust formed in an outer peripheral side of the rotating member and in the direction along the axis on the movable piece. A belt-type continuously variable transmission that includes a hydraulic chamber that provides pressure, a wall member that is provided in the rotating member and surrounds the hydraulic chamber, and a fixing mechanism that prevents the wall member from being detached from the rotating member. ,
A belt-type continuously variable transmission in which a hole having a depth in a direction along the axis is formed in the rotating member, and the fixing mechanism is provided in the hole. The wall member is continuous with an annular portion disposed outside the rotating member in a radial direction centered on the axis, and an inner peripheral end of the annular portion, and extends inward in the radial direction. And a cylindrical portion that is continuous with the inner peripheral end of the protruding portion and extends in a direction along the axis, and the cylindrical portion is disposed inside the hole. Has been
The belt-type continuously variable transmission according to claim 1, wherein the fixing mechanism is provided between an outer peripheral surface of the cylindrical portion and an inner peripheral surface of the rotating member.   3. The belt-type device according to claim 1, wherein an oil passage leading to the hydraulic chamber is provided between an end portion of the rotating member in the direction along the axis and the protruding portion. Step transmission.   The belt type according to any one of claims 1 to 3, wherein the fixing mechanism is a screw mechanism having a female screw portion formed in the rotating member and a male screw portion formed in the cylindrical portion. Continuously variable transmission.   It has a press-fitting member inserted into the cylindrical part, and when the press-fitting member is press-fitted into the cylindrical part, either the male screw part or the female screw part provided in advance is pressed against the mating member The belt-type continuously variable transmission according to any one of claims 1 to 4, wherein either the male screw portion or the female screw portion is formed.   An anti-rotation mechanism is provided between the rotating member and the cylindrical portion to prevent the rotating member and the wall member from rotating relative to each other due to a circumferential engaging force centered on the axis. The belt-type continuously variable transmission according to claim 4 or 5.   The belt-type continuously variable transmission according to any one of claims 2 to 6, wherein a plug portion that closes a free end of the cylindrical portion is provided. A rotating member made of a metal material is prepared, and a movable piece that can move in the direction along the axis is attached to the rotating member, and then a hydraulic chamber is provided between the movable member and the rotating member. In a method for assembling a belt-type continuously variable transmission, which is formed and fixed so as to prevent the wall member from being detached from the rotating member after attaching a wall member made of a metal material.
Before attaching the wall member to the rotating member, a hole having a depth in the direction along the axis is formed in the rotating member, and an internal thread portion is formed on the inner peripheral surface of the rotating member, and A first step of forming an engaging portion projecting in a radial direction around an axis on an inner peripheral surface of the rotating member;
Before attaching the wall member to the rotating member, a second step of forming a cylindrical portion around the axis on the wall member;
A third step performed after the first step and the second step, and inserting the cylindrical portion of the wall member into the hole of the rotating member;
This third step is performed, and a press-fitting member is press-fitted into the cylindrical portion in a direction along the axis, and the cylindrical portion is pressed against the inner peripheral surface of the rotating member, so that the cylindrical portion is By plastically deforming toward the outside centered on the axis, a male screw part meshing with the female screw part is formed on the outer periphery of the cylindrical part, and the rotating member is engaged with the engaging part. And a fourth step of forming an engaged portion for preventing relative rotation with the wall member.

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