JP2005308063A - Belt type continuously variable transmission - Google Patents

Abstract

To reduce the size of a belt type continuously variable transmission.
SOLUTION: Two pulley shafts 51 and 61 arranged in parallel at a predetermined interval, and arranged on the pulley shafts 51 and 61 and sliding on the pulley shafts 51 and 61 in the axial direction. Movable sheaves 53, 63 to be obtained, and fixed sheaves which are arranged on the pulley shafts 51, 61 so as to face the respective movable sheaves 53, 63 and form grooves 80a, 80b between the movable sheaves 53, 63 52, 62, and the movable sheaves 53, 63 disposed opposite to each other and the belt 80 wound around the grooves 80a, 80b in the fixed sheaves 52, 62, and at least one of the movable sheave 53 and the movable sheave 53. And a movable sheave support 55 that supports the motor 550 on the other side of the grooves 80a and 80b in the movable sheaves 53 and 63. the provision d _4.
[Selection] Figure 2

Description

  The present invention relates to a belt type continuously variable transmission, and more particularly to an improvement of a belt type continuously variable transmission provided with a movable sheave sliding mechanism for sliding a movable sheave in an axial direction.

  In general, a belt-type continuously variable transmission includes two rotating shafts arranged in parallel, a primary pulley and a secondary pulley separately attached to each of the rotating shafts, and a V-shape of each of the primary pulley and the secondary pulley. And a belt wound around a groove having a shape. Here, each of the primary pulley and the secondary pulley is a vertical fixed sheave fixed to the rotary shaft (primary shaft and secondary shaft), and a vertical movable sheave that slides in the axial direction on the rotary shaft. The V-shaped groove is formed by the inclined portion of the fixed sheave and the inclined portion of the movable sheave facing each other.

  In this type of belt-type continuously variable transmission, the movable sheave is slid in the axial direction of the rotating shaft to change the V-shaped groove width, whereby each of the belt, the primary pulley, and the secondary pulley. The contact radius can be changed steplessly, whereby the gear ratio can be changed steplessly. In other words, since the ratio of the contact radius on the primary pulley side and the contact radius on the secondary pulley side becomes the gear ratio of the belt-type continuously variable transmission, this belt-type continuously variable transmission has a groove width of the primary pulley. By controlling, the gear ratio can be varied steplessly.

  Thus, conventionally, in order to change the gear ratio in a belt-type continuously variable transmission, it is necessary to slide the movable sheave in the direction of the rotation axis. Therefore, in this belt-type continuously variable transmission, the primary pulley is movable. A mechanism for sliding the sheave (movable sheave sliding mechanism) is provided. For example, as this movable sheave sliding mechanism, there is one that slides the movable sheave using the driving force of a motor such as an electric motor or a hydraulic motor, and a belt type continuously variable transmission equipped with such a movable sheave sliding mechanism. The machine is disclosed, for example, in Patent Document 1 below.

JP-A-6-249310 Special Table 2002-537529 JP-A-8-285033 Japanese Utility Model Publication No. 64-12960

  However, the movable sheave sliding mechanism disclosed in Patent Document 1 has a motor disposed at a position separated from the movable sheave, and a large number of gears that transmit the driving force of the motor to the movable sheave are interposed between the motor and the primary pulley. Therefore, it is necessary to secure these arrangement locations, and there is a disadvantage that the transmission becomes large.

  Therefore, an object of the present invention is to provide a belt type continuously variable transmission that can improve the disadvantages of the conventional example and can reduce the size of the movable sheave sliding mechanism and the transmission.

  In order to achieve the above object, according to the first aspect of the present invention, there are two pulley shafts arranged in parallel at a predetermined interval, and the pulley shafts arranged on each pulley shaft and sliding on the pulley shaft in the axial direction. A movable sheave that can move, a fixed sheave that is arranged on the pulley shaft so as to face each of the movable sheaves, and that forms a groove with the movable sheave, and each of the movable sheave and the fixed sheave arranged opposite to each other. In the belt-type continuously variable transmission provided with a belt wound around each groove, the at least one movable sheave and a motor that is a drive source of the movable sheave are integrally provided, and the motor includes the motor in the movable sheave. A movable sheave support for supporting the opposite side of the groove is provided.

  According to the first aspect of the present invention, since the motor and the movable sheave can be gathered in a compact manner, the mechanism for sliding the movable sheave can be reduced in size, thereby enabling the transmission itself to be reduced in size. become. In addition, since the tilt of the movable sheave can be suppressed by supporting the opposite side of the groove in the movable sheave with the movable sheave support portion, the belt clamping pressure on the belt can be maintained. As a result, the motor can be miniaturized, and the transmission can be further miniaturized.

  In order to achieve the above object, in the invention according to claim 2, in the belt-type continuously variable transmission according to claim 1, the movable sheave is provided with an extending portion including the motor on the opposite side of the groove, The movable sheave support portion is shaped to support a surface of the extended portion that faces the outer peripheral surface of the motor.

  According to the second aspect of the invention, not only the effect according to the first aspect can be obtained, but also the motor and the movable sheave can be arranged close to the axial direction, so that the axial direction of the transmission can be further shortened. Can be achieved.

  In order to achieve the above object, according to the third aspect of the present invention, two pulley shafts arranged in parallel at a predetermined interval, and the pulley shafts arranged on the pulley shafts and sliding on the pulley shafts in the axial direction. A movable sheave that can move, a fixed sheave that is arranged on the pulley shaft so as to face each of the movable sheaves, and that forms a groove with the movable sheave, and each of the movable sheave and the fixed sheave arranged opposite to each other. In the belt-type continuously variable transmission provided with a belt wound around each groove, at least one of the movable sheave and a motor as a drive source of the movable sheave are integrally provided, and the motor and the movable sheave are further provided. Between the motor and the motor is provided with a motion direction conversion mechanism for converting the rotational force as the driving force of the motor into the axial force and sliding the movable sheave. A relative movement / integral rotation mechanism in which the motor and the movement direction conversion mechanism component member are relatively movable in the axial direction and integrally rotatable between the movement direction conversion mechanism component member of the movement direction conversion mechanism on the side. Provided.

  According to the third aspect of the invention, the movable sheave sliding mechanism and the transmission itself can be downsized by integrating the motor and the movable sheave as in the first aspect. Furthermore, since the movement direction conversion mechanism can transmit the driving force of the motor to the movable sheave without using the gear group, the movable sheave sliding mechanism and the transmission can be further miniaturized. Since there is no drive loss in the gear group, the drive loss in the movable sheave sliding mechanism can be reduced.

  Furthermore, the reaction force of the belt clamping force applied to the belt received by the movement direction conversion mechanism is not applied to the motor by the relative movement / integral rotation mechanism, so that adverse effects such as deformation of the motor can be suppressed. For this reason, since the motor can be reduced in size, the transmission can be further reduced in size.

  In order to achieve the above object, according to a fourth aspect of the present invention, there are provided two pulley shafts arranged in parallel at a predetermined interval, and the pulley shafts arranged on the pulley shafts and slid in the axial direction on the pulley shafts. A movable sheave that can move, a fixed sheave that is arranged on the pulley shaft so as to face each of the movable sheaves, and that forms a groove with the movable sheave, and each of the movable sheave and the fixed sheave arranged opposite to each other. In the belt-type continuously variable transmission provided with a belt wound around each groove, at least one of the movable sheave and a motor with a fixed position in the axial direction as a drive source of the movable sheave are integrally provided. The rotary sheave is converted into the axial force between the motor and the movable sheave and in the vicinity of the pulley shaft of the movable sheave by sliding the movable sheave. It is provided motion direction converting mechanism for.

  According to the fourth aspect of the present invention, the movable sheave sliding mechanism and the transmission itself can be miniaturized by integrating the motor and the movable sheave as in the first aspect. Furthermore, since the movement direction conversion mechanism can transmit the driving force of the motor to the movable sheave without using the gear group, the movable sheave sliding mechanism and the transmission can be further miniaturized. Since there is no drive loss in the gear group, the drive loss in the movable sheave sliding mechanism can be reduced.

  Furthermore, since the motion direction conversion mechanism receives the reaction force of the belt clamping pressure on the belt near the highly rigid pulley shaft, adverse effects such as deformation of the motor can be suppressed. For this reason, since the motor can be reduced in size, the transmission can be further reduced in size.

  In the belt type continuously variable transmission according to the present invention, since the motor and the movable sheave are integrally provided, the movable sheave sliding mechanism can be reduced in size, thereby enabling the transmission to be reduced in size.

  Embodiments of a belt type continuously variable transmission according to the present invention will be described below in detail with reference to the drawings. The present invention is not limited to the embodiments.

  A belt type continuously variable transmission according to a first embodiment of the present invention will be described with reference to FIGS.

  First, an overall configuration of a power transmission device including a belt type continuously variable transmission according to the present invention will be described with reference to FIG.

  The power transmission device includes an internal combustion engine 10 and a transaxle 20 disposed on the output side of the internal combustion engine 10.

  As shown in FIG. 1, the transaxle 20 includes, in order from the output side of the internal combustion engine 10, a transaxle housing 21 attached to the internal combustion engine 10, a transaxle case 22 attached to the transaxle housing 21, A transaxle rear cover 23 attached to the transaxle case 22 is provided, and a housing is constituted by these.

  First, a torque converter (starting device) 30 is accommodated in the transaxle housing 21. The torque converter 30 increases the torque of the internal combustion engine 10 and transmits the torque to a belt-type continuously variable transmission 1 described later. A pump impeller 31, a turbine liner 32, a stator 33, a lock-up clutch 34, and a damper device 35 are provided. Etc.

  An input shaft 38 that is rotatable about the same axis as the crankshaft 11 of the internal combustion engine 10 is provided inside the transaxle housing 21. Here, the turbine liner 32 is attached to the end of the input shaft 38 on the internal combustion engine 10 side, and the lock-up clutch 34 is provided via the damper device 35.

  On the other hand, a front cover 37 of the torque converter 30 is connected to the end of the crankshaft 11 on the transaxle 20 side via a drive plate 12, and the pump impeller 31 is connected to the front cover 37. .

  The pump impeller 31 is disposed opposite to the turbine liner 32, and the stator 33 is disposed inside the pump impeller 31. A hollow shaft 36 is connected to the stator 33 via a one-way clutch 39, and the input shaft 38 is disposed inside the hollow shaft 36.

  Here, hydraulic oil is supplied into a casing (not shown) formed by the front cover 37 and the pump impeller 31 as described above.

  The operation of the torque converter 30 will be described below.

  First, the torque of the internal combustion engine 10 is transmitted from the crankshaft 11 to the front cover 37 via the drive plate 12. Here, when the lockup clutch 34 is released by the damper device 35, the torque transmitted to the front cover 37 is transmitted to the pump impeller 31 and circulates between the pump impeller 31 and the turbine liner 32. Torque is transmitted to the turbine liner 32 via the hydraulic oil. The torque transmitted to the turbine liner 32 is transmitted to the input shaft 38.

  Here, an oil pump (hydraulic pump) 26 shown in FIG. 1 is provided between the torque converter 30 and a forward / reverse switching mechanism 40 described later. The oil pump 26 is connected to the pump impeller 31 by a rotor 27 via a cylindrical hub 28, and a body (housing) 29 is fixed to the transaxle case 22 side. Further, the hub 28 is spline-fitted to the hollow shaft 36. With the configuration as described above, the power of the internal combustion engine 10 is transmitted to the rotor 27 via the pump impeller 31, so that the oil pump 26 can be driven.

  Next, inside the transaxle case 22 and the transaxle rear cover 23, a forward / reverse switching mechanism 40, the belt-type continuously variable transmission 1, and a final speed reducer 70 as a differential device are housed.

  First, the forward / reverse switching mechanism 40 transmits the torque of the internal combustion engine 10 transmitted to the input shaft 38 in the torque converter 30 to the primary pulley 50 of the belt-type continuously variable transmission 1 described later. The mechanism 41, the forward clutch 42, and the reverse brake 43 are comprised.

  The planetary gear mechanism 41 includes a sun gear 44, a pinion (planetary pinion) 45, and a ring gear 46.

  Here, the sun gear 44 is spline-fitted to a connecting member (not shown), and the connecting member is spline-fitted to the primary shaft 51 that is the rotation shaft of the primary pulley 50. With this configuration, the torque transmitted to the sun gear 44 is transmitted to the primary shaft 51.

  A plurality of (for example, three) pinions 42 are arranged around the sun gear 44 and meshed with the sun gear 44. Here, each pinion 42 is held by a carrier 48 that supports the pinion 42 so as to be rotatable and supports the pinion 42 so as to be integrally revolved around the sun gear 44. The carrier 48 is connected to the reverse brake 43 at its outer peripheral end.

  The ring gear 46 is engaged with each pinion 42 held by the carrier 48 and is connected to the input shaft 38 in the torque converter 30 via the forward clutch 42.

  Subsequently, the forward clutch 42 is ON / OFF controlled by the hydraulic oil supplied to the hollow portion of the input shaft 38. Here, a brake piston (not shown) is used for the ON / OFF control. During forward travel, the forward clutch 42 is turned on and the reverse brake 43 is turned off. During reverse travel, the forward clutch 42 is turned off and the reverse brake 43 is turned on.

  Next, a schematic configuration of the belt type continuously variable transmission 1 will be described.

  The belt type continuously variable transmission 1 includes a primary shaft (pulley shaft) 51 disposed concentrically with the input shaft 38 and a secondary shaft disposed in parallel with the primary shaft 51 at a predetermined interval. (Pulley shaft) 61. Here, the primary shaft 51 is rotatably supported by bearings 81 and 82 shown in FIG. 1, and the secondary shaft 61 is rotatably supported by bearings 83 and 84 shown in FIG.

  First, the primary shaft 51 is provided with a primary pulley 50 shown in FIG. The primary pulley 50 includes a fixed sheave 52 that is integrally disposed on the outer periphery of the primary shaft 51 and a movable sheave 53 that is slidable in the axial direction of the primary shaft 51.

  Here, the movable sheave 53 is splined to the primary shaft 51 by an axial spline 54 shown in FIG. A V-shaped groove 80 a is formed between the opposed surfaces of the fixed sheave 52 and the movable sheave 53.

  Further, the primary shaft 51 is provided with a movable sheave sliding mechanism 55 that slides the movable sheave 53 in the axial direction of the primary shaft 51 to approach or separate from the fixed sheave 52. Hereinafter, the movable sheave sliding mechanism 55 of the first embodiment will be described in detail.

  As shown in FIG. 2, the movable sheave sliding mechanism 55 includes a hydraulic motor 550 that is a driving source for sliding the movable sheave 53 in the axial direction of the primary shaft 51, and a driving force (rotational direction) of the hydraulic motor 550. A movement direction conversion mechanism 551 that converts a force) into a sliding force of the movable sheave 53.

  As the hydraulic motor 550 of the first embodiment, a motor having a structure in which the rotation of the outer rotor generated by the relative rotation with the inner rotor is used as a driving force is used. For example, as shown in FIG. 3, a motor shaft 550B integrally provided with first vanes (blades) 550A and 550A and a motor case serving as an outer rotor integrally provided with second vanes (blades) 550C and 550C. A so-called vane hydraulic motor with 550D is used.

  The vane hydraulic motor 550 flows hydraulic oil into first oil chambers 550E and 550E (or second oil chambers 550F and 550F) formed between the first vanes 550A and 550A and the second vanes 550C and 550C. Thus, relative rotation is generated between the inner rotor composed of the first vanes 550A and 550A and the motor shaft 550B and the outer rotor composed of the second vanes 550C and 550C and the motor case 550D.

  Here, a cylindrical first extending portion 53a is provided on the side of the movable sheave 53 opposite to the groove 80a, and the vane hydraulic motor 550 of the first embodiment includes the first extending portion. It is arranged in a cylindrical space formed by 53a and concentrically with the primary shaft 51.

  In the vane type hydraulic motor 550, the motor shaft 550B is formed in a cylindrical shape and fitted to the primary shaft 51. For this reason, the first vanes 550 </ b> A and 550 </ b> A rotate integrally with the primary shaft 51.

  The motor case 550D is fixed via a bearing 51a shown in FIG. Therefore, the motor case 550D can rotate relative to the primary shaft 51 and the first vanes 550A and 550A around the rotation axis of the primary shaft 51. The bearing 51a is positioned and fixed with respect to the primary shaft 51 by a lock nut 51b shown in FIG.

The motor case 550D is formed by fitting the open ends of two cylindrical cylinders (first and second cylinders) 550D ₁ and 550D ₂ as shown below.

The first cylinder 550D ₁ has a substantially disc-shaped bottom portion 550d ₁ through which the motor shaft 550B can be inserted, and the inner periphery of the space portion of the movable sheave 53 (right side in FIG. 2) from the periphery of the bottom portion 550d ₁ . And a cylindrical side wall portion 550d ₂ standing upright. The first cylindrical body 550D ₁ is disposed outside the space (on the left side in FIG. 2), and is fixed to the primary shaft 51 via the bearing 51a in the vicinity of the motor shaft 550B. The surface is fixed to the inner wall surface of the first extending portion 53a via the motion direction conversion mechanism 551.

The second cylindrical body 550D ₂ includes a substantially disc-shaped bottom portion 550d ₃ into which the motor shaft 550B can be inserted, and a cylindrical side wall erected from the periphery of the bottom portion 550d ₃ toward the outside of the space portion. Part 550d ₄ . The second cylinder 550D ₂ is disposed inside the space and is fixed to the first cylinder 550D ₁ with a fixing member 550E such as a screw.

Here, since the first cylinder 550D ₁ is fixed to the inner wall surface of the first extending portion 53a via the motion direction conversion mechanism 551, the side wall portion 550d ₂ where the motion direction conversion mechanism 551 does not exist and the first cylinder 550D 1 A gap is generated between the extended portion 53a and the inner wall surface. Due to this gap, the first extending portion 53a bends depending on the thickness of the first extending portion 53a, and the movable sheave 53 tilts away from the fixed sheave 52, and the belt to the belt 80 to be described later. There is a risk that the pinching pressure will decrease. In particular, the decrease in the belt clamping pressure is significant when the belt 80 has a large winding radius (when the belt 80 is positioned on the first extending portion 53a side where the rigidity of the movable sheave 53 is low).

Therefore, in the first embodiment, the first outer diameter of the side wall portion 550d ₄ of the second cylindrical body 550D ₂ is set to the extent that no friction is generated between the inner wall surface of the first extending portion 53a and relative rotation. It approaches the inner diameter of the extended portion 53a.

Accordingly, the side wall portion 550d ₄ functions as a movable sheave support portion that suppresses the bending of the first extending portion 53a. That is, the side wall portion 550d ₄ can support the inner peripheral surface of the first extending portion 53a on the back side of the movable sheave 53 (the opposite side to the groove 80a in the movable sheave 53 in the axial direction) on the outer peripheral surface. The bending of the first extending portion 53a can be suppressed, and the tilting and bending of the engaging portion of the movable sheave 53 with the belt 80 due to the reaction force of the belt clamping pressure can be suppressed. For this reason, even when the wrapping radius of the belt 80 is large, the belt clamping pressure on the belt 80 can be maintained.

Further, conventionally, the movable sheave 53 is restrained from tilting because the second extending portion 53b on the primary shaft 51 side shown in FIG. 2 in the movable sheave 53 is long, but in the second embodiment, the side wall portion 550d. _{By making 4} function as a movable sheave support portion, the second extending portion 53b can be shortened. For this reason, the vane type hydraulic motor 550 can be disposed close to the movable sheave 53, so that the axial direction of the transmission can be shortened and the size can be reduced.

Further, since it is also possible to increase the rigidity of the motor case 550D by providing the side wall portion 550d _4, first and second oil chambers 550E, it is possible to suppress the deformation of the motor case 550D by the oil pressure in the 550F . For this reason, for example, since it is possible to suppress an increase in the gap inside the motor, such as between the motor case 550D and the first vanes 550A, 550A, it is possible to increase the motor efficiency.

In the first embodiment, the side wall portion 550d ₄ that performs support on the outer peripheral side of the motor case 550D is illustrated as the movable sheave support portion for suppressing the tilt of the movable sheave 53. The part is not necessarily limited to that of the first embodiment. For example, erected a cylindrical tubular body in contact with the opposite face of the groove 80a of the movable sheave 53 from the second cylindrical body 550D ₂ bottom 550d _3, may support the movable sheave 53 by the cylindrical body .

  Next, the movement direction conversion mechanism 551 will be described.

  For example, as the motion direction conversion mechanism 551 of the first embodiment, a so-called motion screw such as a multi-thread screw or a slide screw that converts the rotational force of the motor case 550D into a force in the axial direction is used.

  This type of motion direction conversion mechanism 551 includes a cylindrical first motion direction conversion mechanism component 551a provided on the motor case 550D side and a cylindrical second motion direction conversion mechanism configuration provided on the movable sheave 53 side. It is comprised by the member 551b.

Here, the first movement direction conversion mechanism constituting member 551a of the first embodiment has a screw portion formed on the outer peripheral surface thereof, and is integrally provided on the outer peripheral surface of the side wall portion 550d ₂ of the first cylinder 550D ₁ described above. It is done. Further, the second motion direction conversion mechanism constituting member 551b of the first embodiment has a screw portion formed on the inner peripheral surface thereof, and is fitted or press-fitted into the inner wall surface of the first extending portion 53a described above. The first motion direction converting mechanism component 551a may be fixedly fitted to the outer peripheral surface of the side wall portion 550d _2, The second motion direction conversion mechanism component 551b, the first extending portion 53a It may be provided integrally on the inner wall surface.

  By providing such a movement direction conversion mechanism 551, a large thrust of the movable sheave 53 can be generated with a relatively small torque of the vane hydraulic motor 550, so that the output (torque) of the vane hydraulic motor 550 is reduced. Therefore, high efficiency can be achieved by reducing the hydraulic pressure, and the vane hydraulic motor 550 can be reduced in size (smaller diameter).

  Further, since the movement direction conversion mechanism 551 integrally rotates the motor case 550D and the movable sheave 53 in the rotation direction of the primary shaft 51, the rotation is integrally rotated to integrally rotate the vane hydraulic motor 550 together with the movable sheave 53. It also functions as a mechanism.

  The bearing 51 a and the movement direction conversion mechanism 551 constitute a relative movement mechanism that enables relative movement between the vane hydraulic motor 550 and the movable sheave 53. For example, when the motor case 550D rotates, this rotational force (torque) becomes a thrust of the vane hydraulic motor 550 for sliding the movable sheave 53 through the motion direction conversion mechanism 551. Here, the reaction force against the thrust is applied to the bearing 51a. Since the bearing 51a is fixed to the primary shaft 51, the motor case 550D does not move so much in the direction of the reaction force. 53 moves relative to the vane hydraulic motor 550 and approaches the fixed sheave 52. Thus, when the motor case 550D is rotated, the movable sheave 53 can be slid in the axial direction of the primary shaft 51.

  Moreover, since the bearing 51a is being fixed to the primary shaft 51, the reaction force with respect to the thrust of the vane type hydraulic motor 550 can be received by the primary shaft 51 via the bearing 51a. Furthermore, the relative rotation between the motor case 550D and the primary shaft 51 is limited by the stroke of the movable sheave 53 in the sliding direction. For these reasons, in the first embodiment, the reaction force is not received by the stationary system such as the transaxle case 22 and the transaxle rear cover 23, and the bearing 51a hardly rolls. Loss at 51a can be reduced.

  Here, as described above, the first vanes 550A and 550A of the vane hydraulic motor 550 rotate integrally with the primary shaft 51. Therefore, if the rotation of the vane hydraulic motor 550 is stopped, the motor case 550D is primary shaft. If the relative rotation occurs between the motor case 550D and the first vanes 550A and 550A, the primary shaft 51 rotates at a different rotational speed.

  Further, as shown in FIG. 3, the primary shaft 51 and the motor shaft 550B (or the first vanes 550A and 550A) communicate with the first oil chambers 550E and 550E, and the hydraulic oil is supplied to the first oil chambers 550E and 550E. Or supply the hydraulic oil to the second oil chambers 550F and 550F in communication with the oil passage 51c for discharging the hydraulic oil from the first oil chambers 550E and 550E and the second oil chambers 550F and 550F. An oil passage 51d for discharging hydraulic oil from the second oil chambers 550F and 550F is formed.

  As shown in FIG. 4, these oil passages 51c and 51d communicate with a transmission ratio control switching valve 56. The transmission ratio control switching valve 56 includes an oil tank OT, an oil pump ( O / P) The hydraulic oil is supplied through the OP, the oil passage 59b, the regulator valve 59, the oil passage 58a, the clamping pressure regulating valve 58, and the oil passage 56a.

  The gear ratio control switching valve 56 switches the position of the valve in which a plurality of oil passages are formed, thereby providing an oil chamber (the first oil chamber 550E, 550E or the second oil chamber 550F, which is the supply target of hydraulic oil). 550F). This switching is performed by adjusting the difference between the repulsive force of the spring disposed inside the cylinder and the pressure of the fluid such as air or hydraulic oil supplied to the inside. This is performed by a control unit (ECU).

  In the gear ratio control switching valve 56, for example, the operating oil is supplied to the first oil chambers 550E and 550E by switching the position of the valve as shown in FIG. 5-1, and the vane hydraulic motor 550 rotates in the forward direction. By switching as shown in FIG. 5B, the hydraulic oil is supplied to the second oil chambers 550F and 550F, and the vane hydraulic motor 550 is reversed.

  Further, the gear ratio control switching valve 56 supplies hydraulic oil of the same pressure to the first oil chambers 550E and 550E and the second oil chambers 550F and 550F by switching the position of the valve as shown in FIG. 5-3. . As a result, the rotation of the vane hydraulic motor 550 stops, so that the gear ratio control switching valve 56 is also used when the gear ratio is fixed.

  As described above, in the first embodiment, the vane hydraulic motor 550 and the movable sheave 53 are integrally disposed on the primary shaft 51. Therefore, the vane hydraulic motor 550 and the movable sheave 53 are connected to each other. The movable sheave sliding mechanism 55 that slides the movable sheave 53 can be reduced in size. Further, the downsizing of the movable sheave sliding mechanism 55 enables the downsizing of the belt type continuously variable transmission 1 itself. Furthermore, the use of the above-described vane hydraulic motor 550 and the provision of the above-described movement direction conversion mechanism 551 eliminates the need for a gear group for transmitting the driving force of the motor to the movable sheave 53. The sheave sliding mechanism 55 and the belt type continuously variable transmission 1 can be further reduced in size.

  Further, since the movable sheave 53 is slid using the motion direction conversion mechanism 551 as described above, the driving loss generated by the conventional gear group is eliminated, and the driving loss in the movable sheave sliding mechanism 55 is reduced. .

  Further, the primary shaft 51 according to the first embodiment is provided with a pressing mechanism that presses the movable sheave 53 against the fixed sheave 52 side to generate the belt clamping pressure in the axial direction between the fixed sheave 52 and the movable sheave 53. ing.

  This pressing mechanism is formed in the hydraulic chamber 57 shown in FIG. 4 formed between the vane type hydraulic motor 550 (motor case 550D) and the movable sheave 53, and the primary shaft 51 communicating with the hydraulic chamber 57, for example. The oil passage 51e shown in FIG. 4 and the sandwiching pressure regulating valve 58 shown in FIG. 4 communicating with the oil passage 51e are configured.

  Thus, in the first embodiment, the vane type hydraulic motor 550 (motor case 550D) constitutes a part of the hydraulic chamber 57, so that the pressing mechanism can be reduced in size, and consequently the belt type continuously variable transmission 1 Contributes to downsizing

Here, between the and the side wall portion 550d ₄ of the second cylindrical body 550D ₂ inner wall surface of the first extending portion 53a, an annular seal member 57a is disposed. In the first embodiment, the sealing member 57a is fitted into a groove formed in the outer peripheral surface of the side wall portion 550d _4. As described above, even if a gap is provided between the side wall part 550d _{4 of} the second cylinder 550D ₂ and the inner wall surface of the first extension part 53a, the second cylinder 550D ₂ and the first extension part are provided. Friction may occur when rotating relative to 53a or when moving relative to the sliding direction of the movable sheave 53. For this reason, in order to allow the hydraulic oil in the hydraulic chamber 57 to flow as lubricating oil in the meantime, the seal member 57a is preferably disposed at a position away from the hydraulic chamber 57 as shown in FIG. Improvement can be achieved.

  This pressing mechanism supplies the hydraulic pressure from the clamping pressure regulating valve 58 whose hydraulic oil supply pressure is adjusted by the electronic control unit to the hydraulic chamber 57, so that the belt is sandwiched between the fixed sheave 52 and the movable sheave 53. Pressure can be generated to prevent the belt 80 described later from slipping. The hydraulic chamber 57 is provided in series with the vane hydraulic motor 550 (motor case 550D) with respect to the axial direction of the primary shaft 51, and the movable sheave 53 is directed toward the fixed sheave 52 by the hydraulic pressure in the hydraulic chamber 57. Therefore, it is possible to reduce the output of the vane hydraulic motor 550, thereby reducing the size of the vane hydraulic motor 550 and the size of the belt type continuously variable transmission 1.

  Here, since the clamping pressure regulating valve 58 communicates with the transmission ratio control switching valve 56 described above via the oil passage 56a shown in FIG. 4, the hydraulic pressure from the clamping pressure regulating valve 58 is It is also supplied to the first oil chambers 550E and 550E and the second oil chambers 550F and 550F in the vane hydraulic motor 550 through the gear ratio control switching valve 56.

  Further, the hydraulic chamber 57 and the first and second oil chambers 550E and 550F of the vane hydraulic motor 550 are opposed to each other in the axial direction of the primary shaft 51, and the hydraulic pressure in these is the same. The internal pressure between 57 and the first and second oil chambers 550E and 550F is offset. For this reason, the wall surface of the vane type hydraulic motor 550 (motor case 550D) positioned between the hydraulic chamber 57 and the first and second oil chambers 550E and 550F can be thinned, and the weight can be reduced. Become.

  The hydraulic chamber 57 and the first and second oil chambers 550E and 550F of the vane hydraulic motor 550 include an oil passage 51e, an oil passage 56a, a gear ratio control switching valve 56, an oil passage 51c, and an oil passage 51d. Communicated through. Therefore, the hydraulic oil can be exchanged between the hydraulic chamber 57 and the first and second oil chambers 550E and 550F. This is particularly useful during a sudden deceleration downshift, and the hydraulic oil discharged from the hydraulic chamber 57 can be supplied to the second oil chambers 550F and 550F as will be described later. Can improve. Moreover, since the exchange of the hydraulic oil is made possible, the consumption amount of the hydraulic oil supplied from the oil pump OP can be reduced, and thereby the capacity of the oil pump OP can be reduced.

  Next, the secondary shaft 61 is provided with a secondary pulley 60 shown in FIG. The secondary pulley 60 includes a fixed sheave 62 that is integrally disposed on the outer periphery of the secondary shaft 61, and a movable sheave 63 that can slide in the axial direction of the secondary shaft 61. Here, the movable sheave 63 is splined to the secondary shaft 61 by an axial spline 64 shown in FIG. A V-shaped groove 80 b is formed between the opposed surfaces of the fixed sheave 62 and the movable sheave 63.

  Further, the secondary shaft 61 is provided with a pressing mechanism that presses the movable sheave 63 toward the fixed sheave 62 and generates a belt clamping pressure in the axial direction between the fixed sheave 62 and the movable sheave 63. Here, as the pressing mechanism of the first embodiment, two types of torque cam 65 and hydraulic chamber 66 are prepared.

  First, the torque cam 65 according to the first embodiment includes, for example, first and second mountain-shaped engaging portions 65a provided in a ring shape on the movable sheave 63, as shown in FIGS. 6, 7-1 and 7-2. A torque cam main body 65c having a mountain-like second engaging portion 65b facing the first engaging portion 65a, and a plurality of spherical members 65d arranged between the first and second engaging portions 65a, 65b. Composed.

  Here, the torque cam main body 65 c is fixed to the secondary shaft 61 and the movable sheave 63 by a bearing 61 a shown in FIG. 6 fixed to the secondary shaft 61 and a bearing 61 b arranged between the secondary shaft 61. Relative rotation about the rotation axis is possible.

  Thereby, for example, even if the movable sheave 63 approaches the fixed sheave 62 (in other words, even if the first engagement portion 65a is separated from the second engagement portion 65b), the torque sheave 65c and the secondary shaft 61 rotate. Since the relative rotation occurs between the movable sheave 63 and the movable sheave 63, the torque cam 65 can be changed from the state shown in FIG. 7-1 to the state shown in FIG. A surface pressure can be generated between the portion 65b and the spherical member 65d. For this reason, the second engaging portion 65b and the spherical member 65d press the first engaging portion 65a to generate a belt clamping pressure between the fixed sheave 62 and the movable sheave 63, thereby preventing the belt 80 from slipping. It becomes possible.

  Further, since the torque cam main body 65c and the movable sheave 63 rotate relative to each other, even if the torque cam main body 65c generates a thrust force on the movable sheave 63, the movable sheave 63 and the fixed sheave 62 are not twisted with each other. For this reason, the durability of the belt 80 can be improved, and the width of the transmission ratio can be increased. Further, the relative position between the primary pulley 50 and the secondary pulley 60 can be maintained at the initial set value, which contributes to improvement in durability.

  Here, the reaction force against the thrust of the torque cam 65 due to the above surface pressure can be received by the secondary shaft 61 via the bearing 61a. As described above, the reaction force is not received in the stationary system as in the case of the primary pulley 50, and the rolling of the bearing 61a hardly occurs, so that the loss of the bearing 61a can be reduced.

  Further, since the operating portion (first and second engaging portions 65a and 65b, spherical member 65d) of the torque cam 65 is disposed on the outer diameter side of the movable sheave 63, the first engaging portion 65a and the second engaging portion 65 The surface pressure between the engaging portion 65b and the spherical member 65d can be reduced.

  Subsequently, the hydraulic chamber 66 of the first embodiment is formed by a space portion on the opposite side of the groove 80 b in the movable sheave 63 and a circular member 67 concentric with the secondary shaft 61 provided on the secondary shaft 61. .

  Here, since the hydraulic chamber 66 is arranged on the inner diameter side of the movable sheave 63, the volume of the hydraulic chamber 66 can be reduced, so that the flow rate of the hydraulic chamber 66 at the time of sudden shift or the like can be reduced.

  The hydraulic chamber 66 communicates with, for example, an oil passage 61c shown in FIG. 4 formed in the secondary shaft 61, and further communicates with the clamping pressure regulating valve 58 through the oil passage 51e communicating with the oil passage 61c. doing.

  Thus, the pressing mechanism of the secondary pulley 60 constituted by the hydraulic chamber 66, the oil passage 61c, and the clamping pressure regulating valve 58 is supplied from the clamping pressure regulating valve 58 whose hydraulic oil supply pressure is adjusted by the electronic control unit. By supplying hydraulic pressure to the hydraulic chamber 66, belt clamping pressure is generated between the fixed sheave 62 and the movable sheave 63, thereby preventing the belt 80 from slipping.

  Further, even when the torque ratio is changed (when the movable sheave 63 is driven / non-driven in the secondary pulley 60) and the torque is disturbed and the thrust by the torque cam 65 cannot be obtained, the torque cam 65 is separately hydraulically independent. A desired belt clamping pressure can be generated by a pressing mechanism including an operating hydraulic chamber 66 and the like. As a result, the belt 80 can be more reliably prevented from slipping, so that reliability and drivability can be improved.

  Here, the hydraulic chamber 66 according to the first embodiment is provided with an elastic member 68 such as a coil spring having one end fixed to the wall surface of the space portion of the movable sheave 63 and the other end fixed to the circular member 67. ing.

  In the first embodiment, the torque cam 65 is set at a cam angle (for example, a non-linear cam) such that the thrust by the torque cam 65 is lower than the required thrust, and the shortage is pressed by the hydraulic chamber 66 or the like. The mechanism or / and the elastic member 68 are set to compensate. As a result, the belt 80 can be held without excessive force, so that the durability of the belt 80 can be improved, loss in the belt 80 can be reduced, and power transmission efficiency can be improved. .

  Further, the thrust corresponding to the torque when the internal combustion engine 10 is not driven may be set to be received by the pressing mechanism including the hydraulic chamber 66 or the like and / or the elastic member 68, and this may occur due to the operation of the torque cam 65. It is possible to suppress the movement of the movable sheave 63 (in other words, speed change) and keep the speed ratio constant. Further, the belt clamping pressure can be kept at a required value.

  Further, the pressing mechanism on the secondary pulley 60 side is not necessarily limited to two types as in the first embodiment, and may be one type or three or more types. In order to improve the controllability of the belt clamping pressure between the fixed sheave 62 and the movable sheave 63, it is preferable to provide at least two types of pressing mechanisms. That is, the belt clamping pressure is shared by each pressing mechanism, and at least one of them is a pressing mechanism (hydraulic chamber 66 of the first embodiment) that is operated by hydraulic pressure, thereby improving the controllability of the belt clamping pressure. Can be made.

  Next, a counter drive pinion 92 is fixed to the secondary shaft 61 on the internal combustion engine 10 side, and bearings 87 and 88 of the secondary shaft 61 are arranged on both sides of the counter drive pinion 92.

  Here, a power transmission path 90 having an intermediate shaft 91 parallel to the secondary shaft 61 is provided between the counter drive pinion 92 and a final reduction gear 70 described later. The intermediate shaft 91 is rotatably supported by bearings 85 and 86, and includes a counter driven gear 93 and a final drive pinion 94 which are engaged with the counter drive pinion 92 on the shaft.

  A parking gear 65 is disposed between the secondary pulley 60 and the transaxle rear cover 23 on the secondary shaft 61.

  Here, in the belt-type continuously variable transmission 1, the belt 80 is wound around the V-shaped grooves 80 a and 80 b of the primary pulley 50 and the secondary pulley 60. The belt 80 is an endless belt composed of a number of metal pieces and a plurality of steel rings, and the torque of the internal combustion engine 10 transmitted to the primary pulley 50 via the belt 80 is transmitted to the secondary pulley 60. Communicated.

  Next, the final reduction gear 70 will be described. The final reduction gear 70 includes a differential case 71 having a hollow inside, a pinion shaft 72, pinions 73 and 74, and side gears 75 and 76.

  First, the differential case 71 is rotatably supported by bearings 77 and 78, and a ring gear 79 meshed with the final drive pinion 94 is provided on the outer periphery thereof.

  The pinion shaft 72 is attached to the hollow portion of the differential case 71, and the pinions 73 and 74 are fixed to the pinion shaft 72.

  The side gears 75 and 76 are fixed to a drive shaft 101 (here, a front drive shaft) to which the wheel 100 is attached.

  In the transaxle case 22 configured as described above, the lubricating oil stored in the bottom (oil pan) is scraped up by the rotating ring gear 79 and transmitted to the meshing surfaces of the gears 94, 93, 92. While splattering, each component (for example, each shaft 101, 91, 61, each bearing 83-88 etc.), such as the final reduction gear 70, is lubricated, and it falls on the inner wall surface of the transaxle case 22 and falls. 51 etc. are lubricated.

  Here, each component including the belt type continuously variable transmission 1 is controlled by an electronic control unit (ECU) (not shown) based on information from various sensors. The electronic control device includes a gear ratio of the belt-type continuously variable transmission 1 according to a driving state based on data for performing the speed-change control of the belt-type continuously variable transmission 1, for example, information such as an accelerator opening degree and a vehicle speed. Data for controlling is stored in advance. Hereinafter, the operations of the movable sheave sliding mechanism 55 and the pressing mechanism (torque cam 65, hydraulic chamber 66) when controlling the gear ratio will be described in detail.

  First, the case of increasing the speed by reducing the gear ratio will be described. The electronic control unit controls the regulator valve 59, the clamping pressure regulating valve 58, and the gear ratio control switching valve 56 to cause the hydraulic oil to flow into the first oil chambers 550E and 550E, and to achieve the primary speed corresponding to the desired gear ratio. The movable sheave 53 is moved closer to the fixed sheave 52 so that the belt 50 has a winding radius of the belt 80.

  In this case, the electronic control device adjusts the valve position as shown in FIG. 5A by controlling the pressure of the working fluid of the gear ratio control switching valve 56. As a result, the hydraulic oil is supplied to the first oil chambers 550E and 550E and the hydraulic oil in the second oil chambers 550F and 550F is discharged, so that the motor case 550D of the vane hydraulic motor 550 is connected to the primary shaft 51. Relative rotation.

  The rotation of the vane hydraulic motor 550 causes the movable sheave 53 of the primary pulley 50 to approach the fixed sheave 52 via the movement direction conversion mechanism 551, and the movable sheave 63 of the secondary pulley 60 is separated from the fixed sheave 62. Thus, the gear ratio becomes small.

  At this time, since the movable sheave 63 of the secondary pulley 60 rotates together with the fixed sheave 62, the secondary shaft 61 and the bearing 61a, relative rotation occurs between the movable sheave 63 and the torque cam main body 65c. -2 to the approaching state shown in FIG. Therefore, a belt clamping pressure is generated between the fixed sheave 52 and the movable sheave 53, and the belt 80 can be prevented from slipping.

  Further, when the movable sheaves 53 and 63 slide, the hydraulic oil is supplied to the hydraulic chamber 57 of the primary pulley 50 through the oil passage 51e, and the hydraulic oil in the hydraulic chamber 66 of the secondary pulley 60 is discharged through the oil passage 61c. Is done. In the primary pulley 50, the movable sheave 53 is pressed in the sliding direction by supplying hydraulic oil to the hydraulic chamber 57, and the pressing force assists the sliding force of the movable sheave 53 by the vane hydraulic motor 550. ing. For this reason, even if the vane type hydraulic motor 550 has a low output, the movable sheave 53 can be slid sufficiently, so that a small vane type hydraulic motor 550 having a reduced output can be used.

  Since each of the oil passages 51e and the oil passages 61c communicate with each other as shown in FIG. 4, the hydraulic oil discharged from the hydraulic chamber 66 of the secondary pulley 60 is supplied to the hydraulic chamber 57 of the primary pulley 50. Further, the hydraulic oil discharged from the hydraulic chamber 66 is also supplied to the first oil chambers 550E and 550E via the gear ratio control switching valve 56. As described above, since the discharged hydraulic oil can be circulated and sent to another oil chamber, the consumption amount of the hydraulic oil can be reduced, and the capacity of the oil pump OP can be reduced.

  When the change of the gear ratio is completed as described above, the electronic control unit adjusts the valve position of the gear ratio control switching valve 56 as shown in FIG. 5-2, and the first oil chambers 550E and 550E and the second oil are adjusted. The same hydraulic pressure from the clamping pressure regulating valve 58 is applied to the chambers 550F and 550F. Accordingly, the relative rotation of the vane hydraulic motor 550 with respect to the primary shaft 51 stops, and the vane hydraulic motor 550 rotates together with the primary shaft 51 and the movable sheave 53. For this reason, since there is no rotational difference between the vane type hydraulic motor 550 and the primary shaft 51 or the movable sheave 53, it is possible to reduce loss due to unnecessary relative rotation, friction, or the like.

  Here, the hydraulic pressure from the clamping pressure regulating valve 58 is also applied to the hydraulic chamber 57 of the primary pulley 50 and the hydraulic chamber 66 of the secondary pulley 60, and for this reason, A belt clamping pressure is generated between the fixed sheave 62 and the movable sheave 63 in the secondary pulley 60 and the belt 80 can be prevented from slipping.

  Next, the case where the gear ratio is increased to reduce the speed will be described. In such a case, the electronic control device controls the regulator valve 59, the clamping pressure regulating valve 58, and the gear ratio control switching valve 56 to cause the hydraulic oil to flow into the second oil chambers 550F and 550F, thereby achieving a desired gear ratio. The movable sheave 53 is separated from the fixed sheave 52 so as to have a winding radius of the belt 80 in the corresponding primary pulley 50.

  In this case, the electronic control unit adjusts the valve position as shown in FIG. 5-3 by controlling the pressure of the working fluid of the gear ratio control switching valve 56. As a result, the hydraulic oil is supplied to the second oil chambers 550F and 550F and the hydraulic oil in the first oil chambers 550E and 550E is discharged, so that the motor case 550D of the vane type hydraulic motor 550 is connected to the primary shaft 51. Relative rotation.

  The rotation of the vane hydraulic motor 550 causes the movable sheave 53 of the primary pulley 50 to move away from the fixed sheave 52 via the movement direction conversion mechanism 551, and the movable sheave 63 of the secondary pulley 60 approaches the fixed sheave 62. As a result, the gear ratio increases.

  At this time, since the movable sheave 63 of the secondary pulley 60 rotates together with the fixed sheave 62, the secondary shaft 61 and the bearing 61a, relative rotation occurs between the movable sheave 63 and the torque cam main body 65c. -1 to the separated state shown in FIG. 7-2. Therefore, a belt clamping pressure is generated between the fixed sheave 52 and the movable sheave 53, and the belt 80 can be prevented from slipping.

  The hydraulic oil in the hydraulic chamber 57 of the primary pulley 50 is discharged through the oil passage 51e, and the hydraulic oil is supplied to the hydraulic chamber 66 of the secondary pulley 60 through the oil passage 61c. In such a case, the hydraulic oil discharged from the hydraulic chamber 57 of the primary pulley 50 is supplied to the hydraulic chamber 66 of the secondary pulley 60 and the second oil chambers 550F and 550F of the primary pulley 50. This not only reduces the capacity of the oil pump OP described above, but also supplies the hydraulic oil in the hydraulic chamber 57 to the second oil chambers 550F and 550F particularly during a sudden deceleration downshift, and immediately causes the vane hydraulic motor 550 to operate. It is also useful for improving the response of changing the gear ratio.

  The operation after changing the gear ratio is the same as that when increasing the gear ratio.

  As described above, according to the belt-type continuously variable transmission 1 of the first embodiment, the transmission can be reduced in size, and the driving loss associated with the rotation of various components can be reduced.

  Here, the secondary pulley 60 described above may be provided with a buffer mechanism 69 shown in FIGS. 8 and 9.

  The buffer mechanism 69 includes a donut-shaped outer case 691 disposed on the circular member 67 and a plate-shaped member 692 erected on the torque cam main body 65c. The outer case 691 has two hollow portions 691 a filled with a viscous fluid (for example, hydraulic oil), and rotates integrally with the circular member 67. The plate-like member 692 has a through hole (orifice) 692a formed on the surface thereof, and rotates integrally with the torque cam main body 65c.

  Here, a plate-like member 692 is arranged in each of the hollow portions 691a. When the outer case 691 and the plate-like member 692 rotate relative to each other, the plate-like member 692 moves in the hollow portion 691a. To do. A gap is provided between the end of the plate-like member 692 and the inner wall surface of the hollow portion 691a.

  As a result, the torque cam 65 is actuated when the speed ratio is changed, whereby the plate-like member 692 moves in the hollow portion 691a. At this time, resistance is generated by the viscous fluid flowing through the orifice 692a and the gap, and the relative movement between the torque cam main body 65c and the movable sheave 63 can be performed gently. For this reason, it is possible to reduce the shock when the backlash of the torque cam 65 is clogged when the gear ratio is changed (when the torque cam 65 is driven / non-driven).

  The magnitude of the resistance is adjusted by the gap between the end of the plate-like member 692 and the inner wall surface of the hollow portion 691a and the diameter of the orifice 692a.

  Further, in this buffer mechanism 69, the middle portion of the hollow portion 691a shown in FIG. 9 is wider than both end portions thereof, and the degree of buffering (buffer force) can be changed according to the gear ratio. Also good. That is, the gap between the end portion of the plate-like member 692 and the inner wall surface of the hollow portion 691a is large when the plate-like member 692 is located in the middle portion of the hollow portion 691a, and the plate-like member 692 is formed in the hollow portion 691a. A hollow portion 691a having a width changed in the circumferential direction is formed so as to become smaller as it approaches the both end portions.

  As a result, the moving speed of the plate-like member 692 is high when the plate-like member 692 is located in the middle portion of the hollow portion 691a, and becomes slower as the plate-like member 692 approaches both end portions of the hollow portion 691a. Accordingly, the degree of buffering (buffering force) can be changed according to the above, and the shock when the backlash of the torque cam 65 is clogged can be reduced. For example, drivability can be improved by setting the gap so that the buffering force is increased during downshifting.

  Here, since the movable sheave 63 is attached to the secondary shaft 61 via the spline 64, the movable sheave 63 and the fixed sheave 62 have the same rotational direction and rotational speed. Therefore, the buffer mechanism 69 is not limited to the position between the movable sheave 63 and the torque cam 65 as in the second embodiment, but may be provided on the fixed sheave 62 side. In this case, for example, the buffer mechanism 69 is provided with a rotating member (not shown) that rotates in the same manner as the torque cam main body 65c on the opposite side of the groove 80b in the fixed sheave 62, and the plate member 692 is attached to the rotating member. The outer sheave 691 may be attached to the fixed sheave 62. The rotating member may be independent of the torque cam 65, or may be extended from the torque cam main body 65c, for example.

  Next, Embodiment 2 of the belt type continuously variable transmission according to the present invention will be described with reference to FIG.

The belt-type continuously variable transmission 1 of the second embodiment integrates the second cylindrical body 550D ₂ of the motor case 550D with the motor shaft 550B to the belt-type continuously variable transmission 1 of the first embodiment described above. The difference is that the cylindrical body 550D ₁ and the second cylindrical body 550D ₂ are relatively rotated, and the other points are the same as those of the belt-type continuously variable transmission 1 of the first embodiment.

The second cylinder 550D _{2 according to} the second embodiment is integrated with the motor shaft 550B at the bottom 550d ₃ thereof, but is not fixed to the first cylinder 550D ₁ by the fixing member 550E as in the first embodiment. For this reason, the second cylinder 550D ₂ rotates together with the motor shaft 550B and relatively rotates with the first cylinder 550D ₁ .

Here, even in the second embodiment, since the motor shaft 550B is fitted to the primary shaft 51, the motor shaft 550B and the movable sheave 53 rotate integrally with the rotation of the primary shaft 51, and further this embodiment. The second cylinder 550D ₂ of Example 2 also rotates together with these. For this reason, in the second embodiment, it is not necessary to consider the friction between the second cylinder 550D ₂ and the first extending portion 53a of the movable sheave 53 as in the first embodiment.

Therefore, the side wall portion 550d ₄ of this embodiment the second cylindrical body 550D ₂ of 2, and shaped to the outer diameter of the radial inner wall and substantially equal to the first extending portion 53a, fitted on its inner wall surface To do.

Thereby, since the gap between the side wall portion 550d ₄ and the first extending portion 53a can be eliminated, the side wall portion 550d ₄ more reliably functions as the movable sheave support portion of the first extending portion 53a. It will be. For this reason, in the second embodiment, not only the effect of improving the efficiency of the motor similar to the first embodiment but also the suppression of the bending of the first extending portion 53a can be firmly established. The belt clamping pressure to the belt 80 can be maintained more reliably than in the first embodiment, and further reduction in the axial direction of the transmission can be achieved.

Here, also in the second embodiment, a hydraulic chamber 57 similar to that in the first embodiment may be provided in a space portion between the bottom portion 550d _{3 of} the second cylinder 550D ₂ and the movable sheave 53. Since the seal member 57a to be in the groove of the side wall portion 550d ₄ such a case is it is arranged, in the present second embodiment and the second cylindrical body 550D ₂ and the movable sheave 53 as has been described above is rotated integrally Wear of the seal member 57a can be suppressed.

  Next, Embodiment 3 of the belt type continuously variable transmission according to the present invention will be described with reference to FIG.

  The belt-type continuously variable transmission 1 according to the third embodiment includes a vane hydraulic motor 550 of the movable sheave sliding mechanism 55 in the belt-type continuously variable transmission 1 according to the first or second embodiment described above. The other points are the same as the belt type continuously variable transmission 1 of the first or second embodiment except that the motor 552 is changed.

  This electric motor 552 is disposed in a space portion on the opposite side of the groove 80 a in the movable sheave 53 and concentrically with the primary shaft 51, and is a three-phase AC brush 552 a connected to the battery 554 via the inverter 553. The outer rotor 552b is rotated relative to the primary shaft 51 through the bearing 552c. Here, the electric motor 552 switches between normal rotation and reverse rotation by the electronic control device controlling power supply to the three-phase AC brush 552a.

Between the outer rotor 552b of the third embodiment and the first extending portion 53a of the movable sheave 53, the movable sheave support portion that suppresses the bending of the first extending portion 53a as in the first or second embodiment. 552b ₁ is provided. For example, FIG. 11 shows an annular movable sheave having the same effect as that of the first embodiment having an outer diameter that does not cause friction between the outer peripheral surface of the outer rotor 552b and the inner wall surface of the first extending portion 53a. A support portion 552b ₁ is provided.

  Further, between the outer peripheral surface of the outer rotor 552b and the inner wall surface of the space portion in the movable sheave 53, a movement direction conversion mechanism 551 similar to that of the first embodiment or the second embodiment is provided. The movable sheave 53 can be slid in the axial direction of the primary shaft 51 by driving the electric motor 552.

  As described above, by using the electric motor 552 having the structure and arrangement as in the third embodiment, the belt-type continuously variable transmission 1 can be reduced in size and the drive loss can be reduced as in the first or second embodiment. It becomes possible to plan.

  Although not shown, even in the third embodiment, a hydraulic chamber 57 may be provided between the electric motor 552 and the movable sheave 53 as in the first or second embodiment.

  Next, Embodiment 4 of the belt type continuously variable transmission according to the present invention will be described with reference to FIG. 12 shows a state in which the movable sheave 53 is separated from the fixed sheave 52 above the central axis CL of the primary shaft 51, and the movable sheave 53 approaches the fixed sheave 52 below the central axis CL. FIG.

  The belt type continuously variable transmission 1 according to the fourth embodiment includes the motor case 550D of the vane hydraulic motor 550 and the first movement direction conversion of the movement direction conversion mechanism 551 that are integrally provided in the first or second embodiment. The mechanism constituent member 551a is divided. Except for the differences described below, the other configurations of the belt-type continuously variable transmission 1 of the fourth embodiment are the same as those of the belt-type continuously variable transmission 1 of the first or second embodiment.

  First, the vane type hydraulic motor 550 of the fourth embodiment includes a motor shaft 550B in which first vanes 550A and 550A are integrally provided, and a motor in which second vanes 550C and 550C (not shown) are integrally provided. The configuration and arrangement are the same as those of the first or second embodiment including the case 550D.

  Even in the fourth embodiment, the motor shaft 550B is fitted to the primary shaft 51, and these rotate integrally. On the other hand, the motor case 550D of the fourth embodiment is fixed to the motor shaft 550B via a bearing (not shown) and can rotate relative to the motor shaft 550B.

  Further, the motor case 550D is fixed to the inner wall surface of the first extending portion 53a of the movable sheave 53 via the movement direction changing mechanism 551 as in the first or second embodiment. Also for the movement direction conversion mechanism 551 of the fourth embodiment, a so-called movement screw constituted by the first movement direction conversion mechanism constituent member 551a and the second movement direction conversion mechanism constituent member 551b is used.

The first movement direction conversion mechanism constituting member 551a of the fourth embodiment includes a cylindrical portion 551a ₁ having a screw portion formed on the outer peripheral surface, and a first annular portion disposed on the inner side of the cylinder at one end of the cylindrical portion 551a _1. Part 551a ₂ and a second annular part 551a ₃ disposed outside the cylinder at the other end of the cylindrical part 551a ₁ . In that the first annular portion 551a _2, motor shaft 550B is inserted.

Here, the first motion direction conversion mechanism constituting member 551a and the motor case 550D can move relatively in the axial direction thereof, while being integrated with the rotation axis of the motor case 550D (the rotation axis of the primary shaft 51) as a center. Are engaged via a relative movement / integral rotation mechanism that can be rotated in a general manner. For example, as the relative movement / integral rotation mechanism of the fourth embodiment, the inner peripheral surface of the cylindrical portion 551a ₁ of the first movement direction conversion mechanism constituting member 551a and the outer peripheral surface of the motor case 550D are spline-fitted in FIG. The axial spline 551c shown is illustrated.

Also, the first motion direction conversion mechanism components 551a, at first annular portion 551a ₂ of the motor shaft 550B side, a bearing 51a ₁ shown in FIG. 12 rotatable with the primary shaft 51, rotatable with the motor shaft 550B It is fixed via a bearing 51a ₂ shown in FIG. For this reason, the first motion direction conversion mechanism constituting member 551a can rotate relative to the primary shaft 51, the motor shaft 550B, and the movable sheave 53.

Here, as shown in FIG. 12, the second annular portion 551a ₃ of the first movement direction conversion mechanism constituting member 551a contacts the inner wall surface of the first extending portion 53a of the movable sheave 53 via the seal member 57a. For this reason, the second annular portion 551a ₃ functions as a movable sheave support portion of the first extending portion 53a, like the side wall portion 550d ₄ of the second cylinder 550D ₂ in the first or second embodiment. The same effects as those of Example 1 or Example 2 are obtained.

  Subsequently, as in the first or second embodiment, the second movement direction conversion mechanism constituting member 551b of the fourth embodiment has a screw portion formed on the inner peripheral surface thereof, and the inner wall surface of the first extending portion 53a. Is fitted or press-fitted into.

  According to the fourth embodiment, in addition to the same effects as the first or second embodiment, the spline fitting is performed by forming the spline groove between the motor case 550D and the movement direction changing mechanism 551. With this simple structure, the reaction force of the belt clamping force on the belt 80 in the primary pulley 50 does not act on the vane hydraulic motor 550, so that the vane hydraulic motor 550 can be reduced in weight and size.

  That is, not only the motor case 550D but also the component parts of the vane type hydraulic motor 550 are integrated with the first movement direction conversion mechanism constituent member 551a of the movement direction conversion mechanism 551, the vane type hydraulic motor 550 is connected to the belt sandwiching mechanism. There is a possibility that the reaction force of the pressure is directly received through the movable sheave 53 and the movement direction conversion mechanism 551, and the vane hydraulic motor 550 is deformed. For this reason, in such an integrated structure, the rigidity of the vane type hydraulic motor 550 is ensured by increasing the thickness or providing ribs.

  On the other hand, by adopting a separate structure in which the vane type hydraulic motor 550 and the movement direction conversion mechanism 551 are spline-fitted as in the fourth embodiment, the movement direction conversion mechanism 551 that has received the reaction force is counteracted. Since it can be moved toward the force direction, the burden on the motor case 550D is reduced as compared with the first or second embodiment. Therefore, the thickness of the motor case 550D can be reduced and the weight thereof can be reduced, so that the vane hydraulic motor 550 can be made smaller.

  Further, the belt-type continuously variable transmission 1 can be miniaturized by reducing the size of the vane hydraulic motor 550.

  Furthermore, when the reaction force described above occurs, the movement direction conversion mechanism 551 and the vane hydraulic motor 550 can be moved relative to each other in the axial direction, thereby reducing the load on the screw portion of the movement direction conversion mechanism 551. The durability can be improved.

  Here, also in the fourth embodiment, the hydraulic chamber 57 shown in FIG. 12 may be provided between the motor case 550D and the movable sheave 53 as in the first or second embodiment.

  Although the vane type hydraulic motor 550 is illustrated in the fourth embodiment, the same configuration can be adopted for the electric motor 552 of the third embodiment.

  Next, a fifth embodiment of the belt type continuously variable transmission according to the present invention will be described with reference to FIG. 13 also shows a state in which the movable sheave 53 is separated from the fixed sheave 52 above the central axis CL of the primary shaft 51, and the movable sheave 53 approaches the fixed sheave 52 below the central axis CL. FIG.

  The belt-type continuously variable transmission 1 of the fifth embodiment is provided with the movement direction conversion mechanism 551 of the belt-type continuously variable transmission 1 of the first or second embodiment described above on the primary shaft 51 side. Except for the differences described below, the other configurations of the belt-type continuously variable transmission 1 of the fifth embodiment are the same as those of the belt-type continuously variable transmission 1 of the first or second embodiment.

  First, in the movement direction conversion mechanism 551 of the fifth embodiment, a cylindrical first movement direction conversion mechanism constituting member 551a having a screw part formed on the inner peripheral surface, and a screw part engaged with the screw part are provided on the outer peripheral surface. It is comprised with the cylindrical 2nd movement direction conversion mechanism structural member 551b formed in this.

  The second motion direction conversion mechanism constituent member 551b is spline-fitted to the outer peripheral surface of the primary shaft 51 by the spline 54 in the axial direction. In the fifth embodiment, the second movement direction changing mechanism constituting member 551b is provided integrally with the movable sheave 53. That is, the second movement direction conversion mechanism constituting member 551b of the fifth embodiment extends the second extending portion 53b of the first or second embodiment of the movable sheave 53 in the axial direction, and a screw portion on the outer peripheral surface thereof. Formed.

  Here, the first vanes 550A and 550A similar to the first embodiment or the second embodiment are integrally provided on the outer peripheral surface of the first movement direction conversion mechanism constituting member 551a. An inner rotor in the vane hydraulic motor 550 is formed.

  The vane type hydraulic motor 550 of the fifth embodiment has a motor case 550D as an outer rotor in which the inner rotor and second vanes 550C and 550C (not shown) similar to the first or second embodiment are integrally provided. It consists of.

  As shown in FIG. 13, one end of the motor case 550 </ b> D of the fifth embodiment is fitted or press-fitted to the primary shaft 51 and fixed with a lock nut 51 b, and rotates integrally with the primary shaft 51. For this reason, the motor case 550D also rotates integrally with the movable sheave 53.

Further, the first motion direction conversion mechanism constituting member 551a is fixed via bearings 51a ₁ and 51a ₂ shown in FIG. 13 which can rotate together with the motor case 550D, and is connected to the motor case 550D, the movable sheave 53 and the like. Can rotate relative to each other.

  Thus, by providing the movement direction conversion mechanism 551 on the primary shaft 51 side as in the fifth embodiment, the load on the motor case 550D can be reduced and the weight thereof can be reduced, and the size can be further reduced. .

  That is, in Example 1 or Example 2, since the reaction force of the belt clamping pressure on the belt 80 is applied to the motor case 550D via the movement direction conversion mechanism 551, the thickness of the motor case 550D is increased. Stiffness had to be secured. On the other hand, in the fifth embodiment, the reaction force is received by the motion direction conversion mechanism 551 near the highly rigid primary shaft 51, and the reaction force is not so much applied to the motor case 550D. The wall thickness can be reduced and the weight can be reduced. As a result, the vane hydraulic motor 550 can be made smaller, and the belt-type continuously variable transmission 1 can be downsized.

  Here, also in the fifth embodiment, a hydraulic chamber 57 shown in FIG. 13 may be provided between the motor case 550D and the movable sheave 53 as in the first or second embodiment.

  In the fifth embodiment, the annular member 57b shown in FIG. 13 fitted or press-fitted into the outer peripheral surface of one end on the movable sheave 53 side in the first motion direction conversion mechanism constituting member 551a is replaced with the motor case 550D and the movable sheave. The wall surface of the hydraulic chamber 57 is formed by the annular member 57b.

The annular member 57b is in contact with the inner wall surface of the first extending portion 53a of the movable sheave 53 via an annular seal member 57a disposed on the outer peripheral surface thereof. This Therefore, the annular member 57b, similar to the side wall portion 550d ₄ of the second cylindrical body 550D ₂ in Example 1 or Example 2, which functions as the movable sheave supporting portion of the first extending portion 53a.

  In this way, the hydraulic chamber 57 formed by the space surrounded by the movable sheave 53 and the annular member 57 b communicates with the screw portion of the motion direction conversion mechanism 551. For this reason, the working direction conversion mechanism 551 can be lubricated and cooled by the hydraulic oil in the hydraulic chamber 57, and the durability of the movement direction conversion mechanism 551 can be improved compared to the first or second embodiment.

  From the above, according to the fifth embodiment, not only the same effects as those of the first or second embodiment are obtained, but also the vane hydraulic motor 550 is reduced in weight and size, and further, the motion direction conversion mechanism 551 is improved. The effect of improving durability can also be achieved.

  In the fifth embodiment, the vane type hydraulic motor 550 is illustrated, but the same configuration can be adopted for the electric motor 552 of the third embodiment.

  Next, Embodiment 6 of the belt type continuously variable transmission according to the present invention will be described with reference to FIG.

  The belt-type continuously variable transmission 1 of the sixth embodiment includes the first vanes 550A and 550A of the vane-type hydraulic motor 550 provided integrally with the belt-type continuously variable transmission 1 of the fifth embodiment described above, and the movement direction conversion. The first movement direction conversion mechanism constituent member 551a of the mechanism 551 is divided. Except for the differences described below, other configurations of the belt-type continuously variable transmission 1 of the sixth embodiment are the same as those of the belt-type continuously variable transmission 1 of the fifth embodiment.

In order to adopt such a divided structure, in the sixth embodiment, a cylindrical vane holding body 551a ₁ shown in FIG. 14 is provided between the first vanes 550A and 550A and the first movement direction changing mechanism constituting member 551a. Intervene. This vane holding body 551a ₁ forms an inner rotor by integrally providing first vanes 550A and 550A similar to those of the fifth embodiment on the outer peripheral surface thereof, and second vanes 550C and 550C (not shown). Rotates relative to a motor case 550D, which is an outer rotor provided integrally therewith.

Here, the vane holder 551a ₁ is spline-fitted to the outer peripheral surface of the first movement direction conversion mechanism constituting member 551a via an axial spline 551c shown in FIG.

Further, the first movement direction conversion mechanism constituting member 551a of the movement direction conversion mechanism 551 of the sixth embodiment is fixed by a lock nut 51f via bearings 51a ₁ and 51a ₂ shown in FIG. And can rotate relative to the primary shaft 51, the motor case 550D, and the movable sheave 53. Meanwhile, the first motion direction conversion mechanism component 551a may perform the same rotation with the inner rotor formed of the vane holder 551a ₁ and the first vane 550A, and 550A.

  As described above, the moving direction conversion mechanism 551 is provided on the primary shaft 51 side by adopting a separate structure in which the vane type hydraulic motor 550 and the moving direction conversion mechanism 551 are spline-fitted as in the sixth embodiment. In addition to the effects of the fifth embodiment, the vane type hydraulic motor 550 is reduced in weight and size as in the fourth embodiment, the belt-type continuously variable transmission 1 is reduced in size, and the durability of the motion direction conversion mechanism 551 is improved. An effect can also be produced.

  Although the vane type hydraulic motor 550 is illustrated in the sixth embodiment, the electric motor 552 of the third embodiment can have the same configuration.

  In each of the first to sixth embodiments described above, the motor (vane type hydraulic motor 550 or the electric motor 552) is integrally provided on the movable sheave 53 on the primary pulley 50 side, but the present invention is not limited to this. It is not a thing. For example, the motor may be provided integrally with the movable sheave 63 on the secondary pulley 60 side, or may be provided integrally with the movable sheaves 53 and 63 of both the primary pulley 50 and the secondary pulley 60.

  As described above, the belt-type continuously variable transmission according to the present invention is useful for those equipped with a movable sheave sliding mechanism by a motor, and in particular, downsizing the movable sheave sliding mechanism and the transmission itself. Suitable for downsizing.

1 is a skeleton diagram showing an overall configuration of a power transmission device including a belt-type continuously variable transmission according to the present invention. BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows Example 1 of the belt-type continuously variable transmission which concerns on this invention, Comprising: It is explanatory drawing explaining the structure by the side of the primary pulley which comprised the hydraulic motor. It is sectional drawing of the hydraulic motor seen from the XX line | wire shown in FIG. It is explanatory drawing explaining the hydraulic circuit structure in the belt type continuously variable transmission of Example 1. FIG. It is explanatory drawing explaining operation | movement of the switching valve for gear ratio control of Example 1, Comprising: It is a figure which shows the valve position in the case of supplying hydraulic pressure to the 1st oil chamber. It is explanatory drawing explaining operation | movement of the switching valve for gear ratio control of Example 1, Comprising: It is a figure which shows the valve position in the case of supplying hydraulic pressure to the 1st and 2nd oil chamber. It is explanatory drawing explaining operation | movement of the switching valve for gear ratio control of Example 1, Comprising: It is a figure which shows the valve position in the case of supplying hydraulic pressure to a 2nd oil chamber. It is explanatory drawing explaining the structure by the side of the secondary pulley in the belt-type continuously variable transmission of Example 1. FIG. It is explanatory drawing explaining the torque cam of Example 1, Comprising: It is the figure which illustrated the case where the fixed sheave of a secondary pulley and the movable sheave are in the separated state. It is explanatory drawing explaining the torque cam of Example 1, Comprising: It is the figure which illustrated the case where the fixed sheave of a secondary pulley and the movable sheave have approached. It is another example of the secondary pulley in Example 1, Comprising: It is explanatory drawing explaining a buffer mechanism. It is sectional drawing of the buffer mechanism seen from the YY line shown in FIG. It is a figure which shows Example 2 of the belt-type continuously variable transmission which concerns on this invention, Comprising: It is explanatory drawing explaining the structure by the side of the primary pulley which comprised the hydraulic motor. It is a figure which shows Example 3 of the belt-type continuously variable transmission which concerns on this invention, Comprising: It is explanatory drawing explaining the structure by the side of the primary pulley which comprised the electric motor. It is a figure which shows Example 4 of the belt-type continuously variable transmission which concerns on this invention, Comprising: It is explanatory drawing explaining the structure by the side of the primary pulley which comprised the hydraulic motor. It is a figure which shows Example 5 of the belt-type continuously variable transmission which concerns on this invention, Comprising: It is explanatory drawing explaining the structure by the side of the primary pulley which comprised the hydraulic motor. It is a figure which shows Example 6 of the belt-type continuously variable transmission which concerns on this invention, Comprising: It is explanatory drawing explaining the structure by the side of the primary pulley which comprised the hydraulic motor.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Belt type continuously variable transmission 50 Primary pulley 51 Primary shaft 52 Fixed sheave 53 Movable sheave 53a 1st extension part 55 Movable sheave sliding mechanism 60 Secondary pulley 61 Secondary shaft 62 Fixed sheave 63 Movable sheave 80 Belt 80a, 80b V-shape Shaped groove 550 Vane type hydraulic motor 550A Vane (inner rotor side)
550B Motor shaft 550C Vane (outer rotor side)
550D Motor case 550d ₄ Movable sheave support 551 Movement direction conversion mechanism 551a First movement direction conversion mechanism component 551b Second movement direction conversion mechanism component 551c Spline 552 Electric motor 552b Outer rotor 552b ₁ Movable sheave support

Claims (4)

Two pulley shafts arranged in parallel at a predetermined interval, a movable sheave arranged on each pulley shaft and slidable on the pulley shaft in the axial direction, and opposed to each movable sheave. A fixed sheave that is arranged on the pulley shaft and forms a groove with the movable sheave, and a belt that is wound around each groove in the movable sheave and the fixed sheave arranged opposite to each other. In a step transmission,
At least one of the movable sheave and a motor as a drive source for the movable sheave are integrally provided,
A belt-type continuously variable transmission, wherein the motor is provided with a movable sheave support portion that supports an opposite side of the groove in the movable sheave. The movable sheave is provided with an extending portion that encloses the motor on the opposite side of the groove,
The belt-type continuously variable transmission according to claim 1, wherein the movable sheave support portion is formed to support a surface of the extended portion that faces the outer peripheral surface of the motor. Two pulley shafts arranged in parallel at a predetermined interval, a movable sheave arranged on each pulley shaft and slidable on the pulley shaft in the axial direction, and opposed to each movable sheave. A fixed sheave that is arranged on the pulley shaft and forms a groove with the movable sheave, and a belt that is wound around each groove in the movable sheave and the fixed sheave arranged opposite to each other. In a step transmission,
At least one of the movable sheave and a motor as a drive source for the movable sheave are integrally provided,
Provided between the motor and the movable sheave is a motion direction conversion mechanism that converts a rotational force as a driving force of the motor into a force in the axial direction to slide the movable sheave, and the motor Relative movement / integral rotation between the motor and the movement direction conversion mechanism constituting member of the movement direction changing mechanism on the motor side so that the motor and the movement direction changing mechanism constituting member can move relative to each other in the axial direction and rotate together. A belt type continuously variable transmission comprising a mechanism. Two pulley shafts arranged in parallel at a predetermined interval, a movable sheave arranged on each pulley shaft and slidable on the pulley shaft in the axial direction, and opposed to each movable sheave. A fixed sheave that is arranged on the pulley shaft and forms a groove with the movable sheave, and a belt that is wound around each groove in the movable sheave and the fixed sheave arranged opposite to each other. In a step transmission,
And at least one of the movable sheaves and a motor having a fixed position in the axial direction serving as a drive source for the movable sheaves,
A movement of sliding the movable sheave between the motor and the movable sheave and in the vicinity of the pulley shaft of the movable sheave by converting the rotational force as the driving force of the motor into the axial force. A belt type continuously variable transmission provided with a direction changing mechanism.

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