JP2012102774A - Belt-type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a belt-type continuously variable transmission that can be made compact in the size of a planetary gear train.SOLUTION: The belt-type continuously variable transmission 40 includes a pair of pulleys and the planetary gear train 150 which generates power which is generated after the transmission is steplessly speed-changed by a belt 140 wound to the pair of pulleys and power which is transmitted without being speed-changed, and outputs them by synthesizing them. The planetary gear train 150 includes: a sun gear 151 arranged on a transmission shaft 90; a ring gear 152 arranged on an axial line which is the same with that of the sun gear 151; a plurality of planetary gears 157, 157... engaged with the sun gear 151 and the ring gear 152; and a carrier gear 153 arranged on an axial line which is the same with that of the sun gear 151. The planetary gears 157, 157... are turnably supported by a plurality of planetary shafts 155, 155... which are turnably supported to the carrier gear 153 at their one-side ends.

Description

  The present invention relates to a technology of a belt type continuously variable transmission, and more particularly to a technology of a planetary gear mechanism that is provided in a belt type continuously variable transmission and combines power.

  Conventionally, a technology of a belt-type continuously variable transmission that transmits power by winding a belt between a pair of pulleys having variable groove widths is known.

  In addition, a technology in which the belt type continuously variable transmission is provided with a planetary gear mechanism and the power is combined in the planetary gear mechanism is also known. Specifically, the power transmitted through the pair of pulleys and the belt and the power transmitted from the engine as the driving source without passing through the pair of pulleys and the belt are combined in the planetary gear mechanism and output. Is.

  As a technique of such a planetary gear mechanism, a technique described in Patent Document 1 is known.

  The planetary gear mechanism described in Patent Document 1 includes a carrier as a member for supporting a plurality of planetary gears. However, in the planetary gear mechanism provided with such a carrier, it is necessary to secure a space for arranging the carrier, which is disadvantageous in that it is difficult to make it compact.

JP 2006-258290 A

  The present invention has been made in view of the above situation, and provides a belt-type continuously variable transmission that can achieve a compact planetary gear mechanism.

  The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described.

  That is, according to the first aspect of the present invention, the power after being steplessly shifted by the pair of pulleys and the belt wound around the pair of pulleys is transmitted without being shifted by the pair of pulleys and the belt. A belt-type continuously variable transmission having a planetary gear mechanism that combines and outputs power, the planetary gear mechanism being disposed on a shaft and a sun gear disposed on the same axis as the sun gear. A ring gear, a plurality of planetary gears meshed with the sun gear and the ring gear, and a carrier gear disposed on the same axis as the sun gear, the planetary gear having one end rotatably supported by the carrier gear. Each of the plurality of planetary shafts is rotatably supported.

  According to a second aspect of the present invention, end portions of the plurality of planetary shafts on the opposite side to the carrier gear with the planetary gear interposed therebetween are supported by a support member that is rotatably supported on the shaft.

  According to a third aspect of the present invention, the support member is formed with an oil passage through which lubricating oil supplied to the planetary shaft flows.

  According to a fourth aspect of the present invention, the carrier gear is rotatably supported by the sun gear.

  As effects of the present invention, the following effects can be obtained.

  Since the planetary gear is supported by the carrier gear for inputting or outputting power without using the carrier for supporting the planetary gear, the planetary gear mechanism can be made compact and the cost can be reduced. .

  According to the second aspect of the present invention, it is possible to reliably support the planetary gear while reducing the size of the planetary gear mechanism and to prevent the axis of the planetary gear from being inclined.

  In claim 3, the support of the planetary gear and the formation of the oil passage for supplying the lubricating oil to the planetary shaft can be realized by one member (support member), and the cost can be reduced.

  In claim 4, the planetary gear mechanism can be made compact.

1 is a side cross-sectional view showing an overall configuration of a transmission including a belt type continuously variable transmission according to an embodiment of the present invention. Side surface sectional drawing which shows the transmission input shaft etc. of a belt type continuously variable transmission. Similarly, a side sectional view showing an input pulley, a hydraulic cylinder, a hydraulic servo mechanism, and the like. The figure which shows a servo spool and a feedback spool. (A) is a perspective view, (b) is a side sectional view. Side surface sectional drawing which shows the case where the servo spool of a belt-type continuously variable transmission slides back. Similarly, side surface sectional drawing which shows the case where an input side movable sheave slides back. Similarly, side surface sectional drawing which shows the case where the pressure in the hydraulic chamber of a hydraulic cylinder falls. Similarly, side surface sectional drawing which shows the case where a servo spool slides ahead. Side surface sectional drawing which shows the mode of lubrication, such as a transmission input shaft, an input pulley, and a hydraulic cylinder. Side surface sectional drawing which shows the transmission shaft etc. of a belt-type continuously variable transmission. Similarly, side sectional view showing an output pulley, a cam mechanism, a biasing member, and the like. Similarly, a side sectional view showing a planetary gear mechanism, an output shaft, and the like. The disassembled perspective view which shows a planetary gear mechanism. Side surface sectional drawing which shows the mode of lubrication, such as an output pulley and a planetary gear mechanism. The figure which shows other embodiment of a guide member. (A) is side sectional drawing which shows a cylindrical guide member, (b) is side sectional drawing which shows a cylinder member and a piston member.

  Below, the transmission 7 which is a transmission of a work vehicle is demonstrated using FIG. The transmission 7 according to the present embodiment is described as being provided in a tractor that is an agricultural vehicle, but the present invention is not limited to this, and other vehicles such as other agricultural vehicles, construction vehicles, and industrial vehicles can be used. It can be applied in general. In the following description, the direction of arrow F in the figure is defined as the forward direction.

  The transmission 7 outputs power after shifting power from an engine (not shown) as a drive source. The transmission 7 includes a mission input shaft 20, a clutch mechanism 200, a belt type continuously variable transmission 40, an output shaft 170, a front wheel drive transmission shaft 180, a PTO brake 210, a PTO input shaft 220, a rear PTO shaft 230, and a mid PTO shaft 240. Etc.

The power from the engine is transmitted to the mission input shaft 20 and then transmitted to the belt type continuously variable transmission 40 and the PTO input shaft 220 via the clutch mechanism 200.
The power transmitted to the belt-type continuously variable transmission 40 is continuously shifted in the belt-type continuously variable transmission 40 and then transmitted to the output shaft 170 and the front wheel drive transmission shaft 180.
The power transmitted to the output shaft 170 is transmitted to a rear wheel (not shown) of the tractor via a final speed reduction mechanism (not shown).
The power transmitted to the front wheel drive transmission shaft 180 is transmitted to the front wheels (not shown) of the tractor via the front axle (not shown).
The power transmitted to the PTO input shaft 220 is transmitted to the rear PTO shaft 230 and the mid PTO shaft 240 via gears and the like.

In the transmission 7 configured as described above, the vehicle speed of the tractor can be arbitrarily adjusted by changing the gear ratio in the belt type continuously variable transmission 40.
Further, a working machine (for example, a rotary tiller or the like) coupled to the rear PTO shaft 230 and a working machine coupled to the mid PTO shaft 240 (for example, a rotary tiller device) by the power transmitted to the rear PTO shaft 230 and the mid PTO shaft 240 ( For example, a midmore can be driven.
Further, when the transmission of power from the engine to the PTO input shaft 220 is interrupted by the clutch mechanism 200, the rotation of the PTO input shaft 220 is braked by the PTO brake 210.

  The belt-type continuously variable transmission 40 can be applied to transmissions other than the transmission 7 according to this embodiment, and can be widely applied to transmissions that output power after shifting power from a drive source. is there.

  Hereinafter, each part of the belt type continuously variable transmission 40 will be described in detail with reference to FIGS. 1 to 14. The belt type continuously variable transmission 40 includes a transmission input shaft 50, an input pulley 60, a hydraulic cylinder 70, a hydraulic servo mechanism 80, a transmission shaft 90, an output pulley 100, an output member 110, a cam mechanism 120, a biasing member 130, and a belt 140. And a planetary gear mechanism 150 and the like.

The transmission input shaft 50 shown in FIGS. 1 and 2 is connected to the mission input shaft 20 and transmits power from the mission input shaft 20. The transmission input shaft 50 is a substantially cylindrical member, and is arranged with the axial direction as the front-rear direction.
An enlarged diameter portion 50a having a larger diameter than that of the other portion is formed in the middle portion before and after the transmission input shaft 50.
In the vicinity of the rear end portion of the transmission input shaft 50, the transmission input gear 51 is connected to the transmission input shaft 50 so as not to rotate relative thereto by spline fitting. The transmission input gear 51 is meshed with the gear of the clutch mechanism 200 (see FIG. 1), and the power of the mission input shaft 20 can be transmitted through the clutch mechanism 200. The method of connecting the transmission input gear 51 to the transmission input shaft 50 is not limited to the spline fitting, and the transmission input gear 51 can be formed integrally with the transmission input shaft 50 or the like.
Immediately behind the speed change input gear 51, the bearing 52 is fitted to the speed change input shaft 50. Further, the bearing 53 is fitted to the transmission input shaft 50 in front of the enlarged diameter portion 50a. The transmission 52 is rotatably supported by the transmission case 8 by supporting the bearing 52 on the transmission case 8 that houses the transmission 7 and the bearing 53 on the front case 81 described later.

  The input pulley 60 shown in FIG. 3 is a pulley that is disposed on the transmission input shaft 50 and includes a pair of sheaves. The input pulley 60 includes an input side fixed sheave 61, an input side movable sheave 63, and the like.

The input-side fixed sheave 61 is a member having a substantially cylindrical shaft tube portion and a substantially frustoconical sheave portion formed integrally with the front end of the shaft tube portion in a side sectional view. The input side fixed sheave 61 is fitted on the transmission input shaft 50 with the sheave portion disposed in front of the shaft tube portion. The front surface 61a of the sheave portion of the input side fixed sheave 61 is formed as an inclined surface whose diameter increases from the front to the rear.
On the axis of the input side fixed sheave 61, a through hole 61b that penetrates the input side fixed sheave 61 in the front-rear direction is formed. The rear end portion of the through hole 61b (specifically, the portion corresponding to the axial tube portion in the axial direction of the input side fixed sheave 61) has a reduced diameter portion 61c having a smaller diameter of the through hole 61b than the other portions. Is formed. The transmission input shaft 50 is inserted into the through hole 61b of the input side fixed sheave 61 from the front, and is press-fitted until the front surface of the reduced diameter portion 61c of the through hole 61b and the rear surface of the enlarged diameter portion 50a of the transmission input shaft 50 abut. Is done. The portion immediately behind the enlarged diameter portion 50 a of the speed change input shaft 50 and the reduced diameter portion 61 c of the input side fixed sheave 61 are fitted together by press fitting, so that the input side fixed sheave 61 is relative to the speed change input shaft 50. It is fixed so that it cannot rotate and cannot slide.

Thus, by fixing the input side fixed sheave 61 to the transmission input shaft 50 by press fitting, the manufacturing cost can be reduced as compared with the case where the input side fixed sheave 61 is fixed using a spline or serration. Further, since the backlash of the input side fixed sheave 61 and the transmission input shaft 50 can be eliminated, the change in the gear ratio of the belt-type continuously variable transmission 40 or the contact between the belt 140 and the input side fixed sheave 61 can be eliminated. A decrease in surface durability can be prevented.
Further, the input side fixed sheave 61 can be positioned with respect to the transmission input shaft 50 only by press-fitting until the reduced diameter portion 61c of the through hole 61b and the enlarged diameter portion 50a of the transmission input shaft 50 come into contact with each other. Therefore, the input side fixed sheave 61 can be easily and reliably positioned as compared with the case where the input side fixed sheave 61 is fixed to the transmission input shaft 50 using a taper.

In this embodiment, the speed change input shaft 50 and the input side fixed sheave 61 are fitted (fitted) by press fitting, but the speed change input shaft 50 such as “shrink fit” or “cool fit” is used. Any method may be used as long as the diameter is larger than the diameter of the through hole 61 b of the input side fixed sheave 61.
Further, in the present embodiment, the portion immediately behind the enlarged diameter portion 50a of the transmission input shaft 50 and the reduced diameter portion 61c of the input side fixed sheave 61 are fitted together by press fitting, but the present invention is not limited to this. is not. That is, it is possible to fit the enlarged diameter portion 50a of the transmission input shaft 50 and the portion immediately before the reduced diameter portion 61c of the input side fixed sheave 61 by press fitting. When performing this press-fitting, the diameter-reduced portion 61c of the input-side fixed sheave 61 can be slid on the transmission input shaft 50 to serve as a guide for press-fitting work.
Further, in this embodiment, the input side fixed sheave 61 is formed with a sheave portion at the front end of the shaft tube portion, but is not limited to this, and a sheave portion is formed at the rear end of the shaft tube portion. Is also possible.

  A lock nut 62 is fastened to the transmission input shaft 50 immediately behind the input side fixed sheave 61. As a result, the input-side fixed sheave 61 can be prevented from sliding backward on the transmission input shaft 50, and the input-side fixed sheave 61 can be securely fixed to the transmission input shaft 50.

The input side movable sheave 63 is a member having a substantially cylindrical shaft tube portion and a substantially frustoconical sheave portion formed integrally with the rear end of the shaft tube portion in a side sectional view. The input-side movable sheave 63 is fitted on the transmission input shaft 50 in front of the input-side fixed sheave 61 with the sheave portion disposed behind the shaft tube portion. The rear surface 63a of the sheave portion of the input side movable sheave 63 is formed as an inclined surface whose diameter increases from the rear to the front.
On the axis of the input side movable sheave 63, a through hole 63b that penetrates the input side movable sheave 63 in the front-rear direction is formed. The transmission input shaft 50 is inserted through the through hole 63b of the input side movable sheave 63 from the rear.
By arranging the front surface 61a of the input side fixed sheave 61 and the rear surface 63a of the input side movable sheave 63 to face each other on the transmission input shaft 50, a groove of the input pulley 60 is formed by the front surface 61a and the rear surface 63a. The
A sheave side groove 63c and a shaft side groove 50b are formed in the inner peripheral surface of the through hole 63b and the outer peripheral surface of the transmission input shaft 50 along the axial direction of the transmission input shaft 50, respectively. The sheave side groove 63c is formed at least from the front end of the input side movable sheave 63 (the front end of the shaft tube portion) to the middle part before and after the input side movable sheave 63. The sheave-side groove 63c and the shaft-side groove 50b are formed at three equal intervals in the circumferential direction of the inner peripheral surface of the through hole 63b and the outer peripheral surface of the transmission input shaft 50, and the steel balls 64 are formed in a pair of grooves positioned facing each other. -64 ... are arranged. As a result, the input side movable sheave 63 is supported so as to be slidable in the axial direction with respect to the transmission input shaft 50 and not to be relatively rotatable.
The intervals between the sheave side grooves 63c and the shaft side grooves 50b are not limited to equal intervals, and the numbers of the sheave side grooves 63c and the shaft side grooves 50b are not limited to the above numbers.
The input side movable sheave 63 is formed with a through hole 63d that communicates the outer peripheral surface of the shaft tube portion with the inner peripheral surface of the through hole 63b. The through hole 63d is formed at a position that does not overlap with the sheave side groove 63c formed on the inner peripheral surface of the through hole 63b.

  The hydraulic cylinder 70 is for sliding the input side movable sheave 63 on the transmission input shaft 50 in the axial direction thereof. The hydraulic cylinder 70 includes a movable cylinder case 71, a fixed cylinder case 73, and the like.

  The movable cylinder case 71 is a box-shaped member whose front part is opened. A through hole 71a is formed in the axial direction at the center of the rear surface of the movable cylinder case 71, and the shaft cylinder portion of the input movable sheave 63 is inserted through the through hole 71a.

The movable side cylinder case 71 is brought into contact with the input side movable sheave 63 in a state in which the front surface of the sheave portion of the input side movable sheave 63 and the rear surface of the movable side cylinder case 71 are brought into contact with each other by fasteners such as bolts or welding. It is fixed.
It is also possible to integrally form the movable cylinder case 71 and the input movable sheave 63 by forging or the like.

  The fixed-side cylinder case 73 is a member having a box-shaped part whose rear part is opened and an annular flange part integrally formed at the rear end of the box-shaped part. A through hole 73a is formed in the center of the front surface of the fixed cylinder case 73, and the speed change input shaft 50 is inserted through the through hole 73a. The rear portion (the flange portion) of the fixed side cylinder case 73 is inserted into the movable side cylinder case 71 from the open side (front side) of the movable side cylinder case 71. A seal member 74 is disposed between the fixed cylinder case 73 and the movable cylinder case 71.

  After the stationary cylinder case 73 is inserted into the movable cylinder case 71, a bearing 72 is fitted inside the open side (front) end of the movable cylinder case 71.

Immediately in front of the fixed cylinder case 73, the transmission input shaft 50 is inserted into the above-described bearing 53, and is supported rotatably with respect to the transmission case 8 via the bearing 53.
A lock nut 75 is fastened to the transmission input shaft 50 immediately in front of the bearing 53. Accordingly, the bearing 53 can be prevented from sliding forward, and the stationary cylinder case 73 can be prevented from sliding forward via the bearing 53. Further, the bearing 53, the fixed side cylinder case 73, the movable side cylinder case 71, the input side movable sheave 63, the belt 140, and the input side fixed sheave 61 are sandwiched by the lock nut 62 and the lock nut 75, and the torque applied to each member Can be confined between the lock nut 62 and the lock nut 75.

  As described above, the hydraulic cylinder 70 is provided on the input side movable sheave 63 of the input pulley 60. Further, in the hydraulic cylinder 70 configured as described above, a hydraulic chamber 76 is formed in a space closed by the input side movable sheave 63, the movable side cylinder case 71, the fixed side cylinder case 73, and the transmission input shaft 50.

  The hydraulic servo mechanism 80 is for controlling the operation of the input side movable sheave 63 via the hydraulic cylinder 70. The hydraulic servo mechanism 80 includes a front case 81, a servo spool 83, a feedback spool 84, a spool spring 85, and the like.

  The front case 81 is a member having a substantially rectangular parallelepiped main body portion and a disc-shaped flange portion integrally formed at the rear end of the main body portion. The front case 81 is formed with a valve chamber 81a, a bearing hole 81b, a hydraulic oil port 81c, a communication oil passage 81d, a lubricating oil port 81e, and the like.

  The valve chamber 81a is a through-hole having a circular cross section formed so as to communicate the front surface and the rear surface of the front case 81. The valve chamber 81a is formed with the axial direction as the front-rear direction. Further, the valve chamber 81 a is formed so as to overlap the input side movable sheave 63 of the input pulley 60 in a front view, that is, at a position facing the input side movable sheave 63.

  The bearing hole 81b is a through hole having a circular cross section formed so as to communicate the front surface and the rear surface of the front case 81. The bearing hole 81b is formed with the axial direction as the front-rear direction. The front end portion of the transmission input shaft 50 is inserted through the bearing hole 81b from the rear. The front end portion of the bearing hole 81b is closed by the plug 82.

The hydraulic oil port 81c is a through hole formed so as to communicate the side surface of the main body of the front case 81 and the valve chamber 81a. More specifically, the hydraulic oil port 81c communicates the side surface of the main body portion of the front case 81 and the substantially central portion in the axial direction of the valve chamber 81a. The hydraulic oil port 81c is connected to a hydraulic oil pump (not shown) by piping or the like.
The hydraulic oil port 81c only needs to communicate with the outside of the front case 81 and the valve chamber 81a, and does not limit the shape and size of the hole.

  The communication oil passage 81d is an oil passage formed to communicate the valve chamber 81a and the bearing hole 81b. More specifically, the communication oil passage 81d communicates the vicinity of the rear end portion of the valve chamber 81a and the vicinity of the rear end portion of the bearing hole 81b.

  The lubricating oil port 81e is a through hole formed so as to communicate the side surface of the main body of the front case 81 and the bearing hole 81b. More specifically, the lubricating oil port 81e communicates the side surface of the main body portion of the front case 81 and the substantially central portion in the axial direction of the bearing hole 81b. The lubricating oil port 81e is connected to a lubricating oil pump (not shown) by piping or the like.

  The servo spool 83 shown in FIGS. 3 and 4 is for switching the oil path in the hydraulic servo mechanism 80. The servo spool 83 is a substantially columnar member, and a disc-shaped flange is integrally formed at the rear end. The servo spool 83 is arranged with the axial direction as the front-rear direction. The servo spool 83 is formed with a sliding hole 83a, a first groove 83b, a second groove 83c, a first through hole 83d, a second through hole 83e, a discharge oil passage 83f, and the like.

The sliding hole 83 a is a hole having a circular cross section formed from the rear end of the servo spool 83 to the vicinity of the front end on the axis of the servo spool 83.
The first groove 83 b is formed along the outer periphery of the servo spool 83 at a substantially central portion in the axial direction of the servo spool 83. As will be described later, even when the servo spool 83 slides in the axial direction relative to the valve chamber 81a of the front case 81, the first groove 83b is always formed regardless of the sliding position of the servo spool 83. The first groove 83b is formed long in the axial direction of the servo spool 83 so as to face the hydraulic oil port 81c.
The second groove 83 c is formed along the outer periphery of the servo spool 83 behind the first groove 83 b of the servo spool 83. As will be described later, even when the servo spool 83 slides in the axial direction with respect to the valve chamber 81a of the front case 81, the second groove 83c is always formed regardless of the sliding position of the servo spool 83. The second groove 83 c is formed long in the axial direction of the servo spool 83 so as to face the communication oil path 81 d.
83 d of 1st through-holes are formed so that the 1st groove | channel 83b and the sliding hole 83a may be connected by making an axial direction orthogonal to the axial line of the servo spool 83. As shown in FIG.
The second through hole 83e is formed so that the second groove 83c and the sliding hole 83a communicate with each other with the axial direction orthogonal to the axis of the servo spool 83.
The drain oil passage 83f is an oil passage formed so as to communicate the rear end of the servo spool 83 and the sliding hole 83a. More specifically, the drain oil passage 83f communicates the rear end of the servo spool 83 with a portion behind the portion facing the second groove 83c of the sliding hole 83a.

  The outer diameter of the servo spool 83 is formed to be substantially the same as the inner diameter of the valve chamber 81a of the front case 81. The servo spool 83 is slidably inserted from the rear into the valve chamber 81a of the front case 81. The diameter of the flange portion of the servo spool 83 is formed to be larger than the diameter of the valve chamber 81a of the front case 81, and when the flange portion abuts against the front case 81, the forward sliding of the servo spool 83 is restricted at a predetermined position. Is done. The front end portion of the servo spool 83 is connected to a shift operation tool (not shown) such as a shift lever or a shift pedal, and the servo spool 83 can be slid in the front-rear direction by operating the shift operation tool. is there.

  The feedback spool 84 is for switching the oil path in the hydraulic servo mechanism 80. The feedback spool 84 is a substantially cylindrical member. The feedback spool 84 is arranged with the axial direction as the front-rear direction. The feedback spool 84 is formed with a discharge oil passage 84a, a communication groove 84b, and the like.

The drain oil passage 84 a is an oil passage formed so as to communicate the front end and the rear end of the feedback spool 84 on the axis of the feedback spool 84.
The communication groove 84 b is formed along the outer periphery of the feedback spool 84 at a substantially central portion in the axial direction of the feedback spool 84.

  The outer diameter of the feedback spool 84 is formed to be substantially the same as the inner diameter of the sliding hole 83a of the servo spool 83. The feedback spool 84 is slidably inserted into the sliding hole 83 a of the servo spool 83. As a result, the feedback spool 84 can slide in the front-rear direction with respect to the servo spool 83.

  The spool spring 85 biases the feedback spool 84 backward. The spool spring 85 is constituted by a compression coil spring. The spool spring 85 is disposed in the sliding hole 83a of the servo spool 83 and constantly urges the feedback spool 84 rearward (that is, the input side movable sheave 63 side).

  Note that the member for biasing is not limited to the compression coil spring (spool spring 85) as long as the feedback spool 84 can be biased backward.

  Since the feedback spool 84 is always urged rearward by the spool spring 85, the rear end of the feedback spool 84 is a bearing 72 (more specifically, a movable cylinder case 71 fixed to the input movable sheave 63). Is always in contact with the inner ring of the bearing 72.

  In this manner, the feedback spool 84 is not directly brought into contact with the movable cylinder case 71 but is brought into contact with the bearing 72 through the bearing 72, thereby preventing the feedback spool 84 and the movable cylinder case 71 from being worn by friction. Can do. That is, since the outer ring of the bearing 53 comes into contact with the movable cylinder case 71 and the inner ring of the bearing 53 comes into contact with the feedback spool 84, the friction between the feedback spool 84 and the movable cylinder case 71 is caused by the bearing 72. Will be reduced.

In the present embodiment, the feedback spool 84 is configured to contact the movable cylinder case 71 via the bearing 72, but the present invention is not limited to this. That is, it is possible to adopt a configuration in which the input side movable sheave 63 is brought into contact with the bearing 72 via the bearing 72 or a configuration in which the input side movable sheave 63 is directly brought into contact with the bearing 72 without going through the bearing 72.
In addition, the member interposed between the feedback spool 84 and the movable cylinder case 71 is not limited to the bearing 72, and friction between the feedback spool 84 and the movable cylinder case 71 can be reduced. Any material (for example, a member whose friction is reduced by surface processing) may be used.

  Further, a first groove 50c, a second groove 50d, a working groove 50e, a working oil passage 50f, a lubricating oil passage 50g, and a distribution oil passage 50h are formed in the transmission input shaft 50 shown in FIG.

The first groove 50 c is formed along the outer periphery of the transmission input shaft 50 in the vicinity of the front end portion in the axial direction of the transmission input shaft 50. More specifically, the first groove 50c is formed at an axial position facing the communication oil passage 81d formed in the front case 81 when the transmission input shaft 50 is inserted into the bearing hole 81b of the front case 81. Is done.
The second groove 50d is formed along the outer periphery of the transmission input shaft 50 in the vicinity of the front end in the axial direction of the transmission input shaft 50 and in front of the first groove 50c. More specifically, the second groove 50d is formed at an axial position facing the lubricating oil port 81e formed in the front case 81 when the transmission input shaft 50 is inserted into the bearing hole 81b of the front case 81. Is done.
The operation groove 50 e is formed in a part of the outer peripheral surface of the transmission input shaft 50 in the middle of the transmission input shaft 50 in the axial direction. More specifically, the operating groove 50e is formed at a position facing the through hole 63d formed in the input side movable sheave 63 when the input side movable sheave 63 is supported on the transmission input shaft 50. Even when the input-side movable sheave 63 slides in the axial direction with respect to the transmission input shaft 50, the operation groove 50e always faces the through hole 63d regardless of the sliding position of the movable sheave. The operating groove 50e is formed long in the axial direction of the transmission input shaft 50.
The hydraulic oil passage 50f is a hole formed from the front end of the speed change input shaft 50 to the substantially same position as the operation groove 50e in the axial direction. The front end portion of the hydraulic oil passage 50 f is closed by the plug 54. The hydraulic oil passage 50f communicates with the first groove 50c in the vicinity of the front end portion and the operating groove 50e in the vicinity of the rear end portion.
The lubricating oil passage 50g is a hole formed from the front end of the speed change input shaft 50 to substantially the same position as the rear end of the enlarged diameter portion 50a in the axial direction. The front end portion of the lubricating oil passage 50g is closed by the plug 55. The lubricating oil passage 50g communicates with the second groove 50d in the vicinity of the front end portion.
The distribution oil passage 50h is a through hole formed so as to communicate the outer peripheral surface of the transmission input shaft 50 and the lubricating oil passage 50g with the axial direction orthogonal to the axis of the transmission input shaft 50. More specifically, the distribution oil passage 50h is an outer peripheral surface of the enlarged diameter portion 50a of the speed change input shaft 50, and in the vicinity of the front surface 61a of the sheave portion of the input side fixed sheave 61 fixed to the speed change input shaft 50; The lubricating oil passage 50g is communicated.

  Hereinafter, a state in which the operation of the hydraulic cylinder 70 is controlled using the hydraulic servo mechanism 80 configured as described above and the input side movable sheave 63 is slid will be described.

  First, as shown in FIG. 3, the case where the servo spool 83 slides most forward with respect to the valve chamber 81a will be described.

  In this case, the input-side movable sheave 63 and the movable-side cylinder case 71 fixed to the input-side movable sheave 63 are moved forward until the front end of the shaft tube portion of the input-side movable sheave 63 contacts the fixed-side cylinder case 73. Is sliding. Further, the feedback spool 84 that comes into contact with the bearing 72 fixed to the movable cylinder case 71 from the front is pushed into the sliding hole 83a of the servo spool 83 to a predetermined position against the urging force of the spool spring 85. Held in a state.

  Here, the “predetermined position” of the feedback spool 84 is a relative position with respect to the servo spool 83, and more specifically, by the outer peripheral surface of the feedback spool 84 (specifically, the outer peripheral surface in front of the communication groove 84b). This is a position where the first through hole 83d of the servo spool 83 is closed and the discharge oil passage 83f of the servo spool 83 is closed by the outer peripheral surface of the feedback spool 84 (specifically, the outer peripheral surface behind the communication groove 84b).

  The hydraulic oil pumped from the hydraulic oil pump is supplied to the first groove 83 b of the servo spool 83 via the hydraulic oil port 81 c of the front case 81. However, the first through hole 83 d that communicates the first groove 83 b and the sliding hole 83 a is closed by the outer peripheral surface of the feedback spool 84. Therefore, the hydraulic oil supplied from the hydraulic oil pump is blocked by the feedback spool 84 and is not supplied to the hydraulic chamber 76 of the hydraulic cylinder 70.

  Further, since the input side movable sheave 63 is biased forward by the tension of a belt 140 (described later) wound around the input pulley 60, the input side movable sheave 63 and the movable side cylinder case 71 slide forward. It is held in the state.

  Next, as shown in FIG. 5, a case where the servo spool 83 is slid rearward by operating the shift operation tool will be described.

  In this case, the servo spool 83 slides rearward, whereas the feedback spool 84 is in contact with the bearing 72 and cannot slide rearward. Therefore, the feedback spool 84 slides forward relative to the servo spool 83. As a result, the communication groove 84b of the feedback spool 84 faces the first through hole 83d and the second through hole 83e of the servo spool 83, and the hydraulic oil supplied from the hydraulic oil pump to the hydraulic oil port 81c is The oil is supplied to the communication oil passage 81d through the groove 83b, the first through hole 83d, the communication groove 84b, the second groove 83c, and the second through hole 83e.

  The hydraulic oil supplied to the communication oil path 81d is further supplied to the hydraulic chamber 76 via the first groove 50c of the transmission input shaft 50, the hydraulic oil path 50f, the operating groove 50e, and the through hole 63d of the input side movable sheave 63. Supplied with. When the hydraulic oil is supplied to the hydraulic chamber 76, the pressure in the hydraulic chamber 76 increases, and the input side movable sheave 63 and the movable side cylinder case 71 are urged rearward by the pressure. The input side movable sheave 63 and the movable side cylinder case 71 urged rearward by the pressure of the hydraulic oil in this manner slide rearward against the forward urging force due to the tension of the belt 140 ( (See FIG. 6).

  Next, the case where the input side movable sheave 63 and the movable side cylinder case 71 slide rearward as shown in FIG. 6 will be described.

  When the input-side movable sheave 63 and the movable-side cylinder case 71 slide backward, the feedback spool 84 that is in contact with the bearing 72 fixed to the movable-side cylinder case 71 while being urged from the front also slides backward. To do. That is, the feedback spool 84 slides backward relative to the servo spool 83.

  When the feedback spool 84 slides to a predetermined position and the first through hole 83d of the servo spool 83 is closed again by the outer peripheral surface of the feedback spool 84, the supply of hydraulic oil to the hydraulic chamber 76 of the hydraulic cylinder 70 is completed. To do. Therefore, the input-side movable sheave 63 and the movable-side cylinder case 71 are held at the positions when the supply of hydraulic oil to the hydraulic chamber 76 is finished.

  Next, as shown in FIG. 7, the case where the hydraulic oil in the hydraulic chamber 76 of the hydraulic cylinder 70 leaks and the pressure in the hydraulic chamber 76 decreases will be described.

  When the supply of hydraulic fluid to the hydraulic chamber 76 is completed with the input-side movable sheave 63 and the movable-side cylinder case 71 sliding rearward, the input-side movable sheave 63 and the movable-side cylinder case 71 are in contact with the hydraulic chamber 76. The hydraulic oil is held at the position at the time when the supply of hydraulic oil to the end is completed. However, when the hydraulic oil in the hydraulic chamber 76 leaks little by little from the gap between the movable cylinder case 71 and the fixed cylinder case 73, the gap between the input side movable sheave 63 and the transmission input shaft 50, etc. The pressure in 76 decreases, and the input side movable sheave 63 and the movable side cylinder case 71 slide forward little by little due to the tension of the belt 140.

  When the input-side movable sheave 63 and the movable-side cylinder case 71 slide forward, the feedback spool 84 that is in contact with the bearing 72 fixed to the movable-side cylinder case 71 while being biased from the front also slides forward. To do. That is, the feedback spool 84 slides forward relative to the servo spool 83.

  When the feedback spool 84 slides forward and the communication groove 84b of the feedback spool 84 again faces the first through hole 83d and the second through hole 83e of the servo spool 83, the hydraulic oil returns to the hydraulic chamber 76 of the hydraulic cylinder 70 again. Supplied with. As a result, the input side movable sheave 63 and the movable side cylinder case 71 slide rearward (see FIG. 6).

When the feedback spool 84 slides to a predetermined position together with the input-side movable sheave 63 and the movable-side cylinder case 71 and the first through hole 83d of the servo spool 83 is closed again by the outer peripheral surface of the feedback spool 84, the hydraulic cylinder 70 The supply of hydraulic oil to the hydraulic chamber 76 ends.
In this way, the feedback spool 84 slides following the input side movable sheave 63 and the movable side cylinder case 71 and switches the oil passage communicating with the hydraulic chamber 76, whereby the input side movable sheave 63 and the movable side cylinder are switched. The case 71 can be held at a position corresponding to the sliding position of the servo spool 83.

  Next, as shown in FIG. 8, a case where the servo spool 83 is slid forward by operating the shift operation tool will be described.

  In this case, the servo spool 83 slides forward, whereas the feedback spool 84 is urged toward the bearing 72 by the spool spring 85, so that the feedback spool 84 is in contact with the bearing 72. Retained. Therefore, the feedback spool 84 slides backward relative to the servo spool 83. As a result, the communication groove 84b of the feedback spool 84 faces the second through hole 83e and the discharge oil passage 83f of the servo spool 83, and the hydraulic oil is discharged through the second groove 83c and the second through hole 83e. It becomes possible to distribute it.

  The input side movable sheave 63 and the movable side cylinder case 71 are biased forward by the tension of the belt 140. Therefore, the hydraulic oil in the hydraulic chamber 76 of the hydraulic cylinder 70 is pushed out by the input side movable sheave 63 and the movable side cylinder case 71, and the through hole 63 d of the input side movable sheave 63, the operation groove 50 e of the transmission input shaft 50, The oil path 50f, the first groove 50c, the communication oil path 81d, the second groove 83c of the servo spool 83, the second through hole 83e, the communication groove 84b of the feedback spool 84, and the discharge oil path 83f of the servo spool 83 The servo spool 83 is discharged rearward from the rear end. The hydraulic oil discharged from the rear end of the servo spool 83 can lubricate the bearing 72 fixed to the movable cylinder case 71. Further, when the hydraulic oil in the hydraulic chamber 76 is discharged, the input side movable sheave 63 and the movable side cylinder case 71 slide forward according to the urging force from the belt 140 (see FIG. 3).

  In this case, the first through hole 83d of the servo spool 83 remains closed by the outer peripheral surface of the feedback spool 84, and the hydraulic oil from the hydraulic oil pump is supplied to the hydraulic chamber 76 of the hydraulic cylinder 70. There is no.

  Next, a case where the input side movable sheave 63 and the movable side cylinder case 71 slide forward as shown in FIG. 3 will be described.

  When the input-side movable sheave 63 and the movable-side cylinder case 71 slide forward, the feedback spool 84 that is in contact with the bearing 72 fixed to the movable-side cylinder case 71 while being biased from the front also slides forward. To do. That is, the feedback spool 84 slides forward relative to the servo spool 83.

  When the feedback spool 84 slides to a predetermined position and the discharge oil passage 83f of the servo spool 83 is closed by the outer peripheral surface of the feedback spool 84, the discharge of the hydraulic oil from the hydraulic chamber 76 of the hydraulic cylinder 70 is completed. Therefore, the input side movable sheave 63 and the movable side cylinder case 71 are held at the positions at the time when the discharge of the hydraulic oil from the hydraulic chamber 76 is completed.

  As described above, the input side movable sheave 63 can be slid to a desired position by sliding the servo spool 83 to an arbitrary position. Further, the input movable sheave 63 can be held at a desired sliding position by the feedback spool 84 that slides following the input movable sheave 63.

  In the present embodiment, the input side movable sheave 63 is slid by using the hydraulic servo mechanism 80. However, the present invention is not limited to this, and an output pulley described later using the hydraulic servo mechanism 80 is used. It is also possible to have a configuration in which 100 output-side movable sheaves 103 are slid.

  Hereinafter, with reference to the arrows shown in FIG. 9, the state of lubrication of the transmission input shaft 50, the input pulley 60, the hydraulic cylinder 70, etc. in the above-described configuration will be described.

  As described above, the hydraulic oil supplied into the hydraulic chamber 76 of the hydraulic cylinder 70 passes through the clearance between the front end of the shaft tube portion of the input side movable sheave 63 and the fixed side cylinder case 73, and the shaft side groove 50 b of the transmission input shaft 50. And leaks into the sheave side groove 63 c of the input side movable sheave 63. The steel balls 64, 64... Disposed in the shaft side groove 50b and the sheave side groove 63c are lubricated by the hydraulic oil.

Further, the hydraulic oil supplied into the hydraulic chamber 76 of the hydraulic cylinder 70 is a gap between the front end of the shaft cylinder portion of the input side movable sheave 63 and the fixed side cylinder case 73, and the input side movable sheave 63 and the transmission input shaft 50. And leak out to the rear of the input side movable sheave 63. The contact surface (sliding surface) between the input side movable sheave 63 and the transmission input shaft 50 is lubricated by the hydraulic oil.
In this way, instead of providing an oil passage fixed to the transmission input shaft 50, the hydraulic oil is supplied using a gap between the input side movable sheave 63 and the transmission input shaft 50, so that the input side movable sheave 63 is Regardless of the sliding position, the input side movable sheave 63 can be properly lubricated.

  Further, the contact surface between the rear surface 63a of the sheave portion of the input side movable sheave 63 and the belt 140 described later is lubricated by the hydraulic oil leaking to the rear of the input side movable sheave 63 as described above.

  Further, during the flow of the hydraulic oil supplied from the hydraulic oil pump to the hydraulic chamber 76 of the hydraulic cylinder 70, the hydraulic oil is in contact with the valve chamber 81a of the front case 81 and the servo spool 83 (sliding surface). , And the contact surface (sliding surface) between the sliding hole 83a of the servo spool 83 and the feedback spool 84 is lubricated.

  Further, the hydraulic oil leaking into the sliding hole 83 a of the servo spool 83 through the gap between the servo spool 83 and the feedback spool 84 passes through the discharge oil passage 84 a of the feedback spool 84 and the rear end of the feedback spool 84. Discharged from. The contact surface between the feedback spool 84 and the bearing 72 is lubricated by the discharged hydraulic oil.

The hydraulic fluid pumped from the lubricating oil pump and supplied to the lubricating oil port 81e of the front case 81 is shifted through the second groove 50d, the lubricating oil passage 50g, and the distribution oil passage 50h of the transmission input shaft 50. It is supplied to the outer peripheral surface of the input shaft 50 (near the front surface 61a of the sheave portion of the input side fixed sheave 61). The contact surface between the front surface 61a of the sheave portion of the input side fixed sheave 61 and the belt 140 described later is lubricated by the supplied hydraulic oil.
In this way, for the input side fixed sheave 61 that does not slide with respect to the transmission input shaft 50, an oil passage (lubricant for supplying hydraulic oil that lubricates the front surface 61a of the sheave portion of the input side fixed sheave 61 is provided. By forming the oil port 81e, the second groove 50d of the transmission input shaft 50, the lubricating oil passage 50g, the distribution oil passage 50h, etc., the input-side fixed sheave 61 can be properly lubricated.

A transmission shaft 90 shown in FIGS. 1 and 10 transmits power from the transmission input shaft 50. The transmission shaft 90 is a substantially cylindrical member, and is arranged with the axial direction as the front-rear direction.
In the vicinity of the front end portion of the transmission input shaft 50, an enlarged diameter portion 90a having a larger diameter than that of other portions is formed.
A bearing 91 is fitted to the transmission shaft 90 in front of the enlarged diameter portion 90a. By supporting the bearing 91 on the transmission case 8, the transmission shaft 90 is rotatably supported on the transmission case 8.

  The output pulley 100 shown in FIG. 11 is a pulley that is disposed on the transmission shaft 90 and includes a pair of sheaves. The output pulley 100 includes an output side fixed sheave 101, an output side movable sheave 103, and the like.

The output side fixed sheave 101 is a member made of the same material as the input side fixed sheave 61 and formed in the same shape. That is, the output side fixed sheave 101 is a member having a substantially cylindrical shaft tube portion and a substantially frustoconical sheave portion formed integrally with the rear end of the shaft tube portion in a side sectional view. . The output side fixed sheave 101 is fitted on the transmission shaft 90 with the sheave portion disposed behind the shaft tube portion. The rear surface 101a of the sheave portion of the output side fixed sheave 101 is formed as an inclined surface whose diameter increases from the rear to the front.
On the axis of the output side fixed sheave 101, a through hole 101b that penetrates the output side fixed sheave 101 in the front-rear direction is formed. The front end portion of the through hole 101b (specifically, the portion corresponding to the axial tube portion in the axial direction of the output side fixed sheave 101) has a reduced diameter portion 101c in which the diameter of the through hole 101b is smaller than other portions. It is formed. The transmission shaft 90 is inserted into the through hole 101b of the output side fixed sheave 101 from the rear, and is press-fitted until the rear surface of the reduced diameter portion 101c of the through hole 101b and the front surface of the enlarged diameter portion 90a of the transmission shaft 90 abut. . The portion immediately before the enlarged diameter portion 90 a of the transmission shaft 90 and the reduced diameter portion 101 c of the output side fixed sheave 101 are fitted together by press fitting, so that the output side fixed sheave 101 cannot rotate relative to the transmission shaft 90. And it is fixed so that it cannot slide.

Thus, by fixing the output side fixed sheave 101 to the transmission shaft 90 by press fitting, the manufacturing cost can be reduced as compared with the case where the output side fixed sheave 101 is fixed using a spline or serration. Further, since the backlash of the output side fixed sheave 101 and the transmission shaft 90 can be eliminated, the change in the gear ratio of the belt type continuously variable transmission 40 and the contact surface between the belt 140 and the output side fixed sheave 101 can be eliminated. It is possible to prevent a decrease in durability.
Further, the output-side fixed sheave 101 can be positioned with respect to the transmission shaft 90 only by press-fitting until the reduced diameter portion 101c of the through hole 101b and the enlarged diameter portion 90a of the transmission shaft 90 come into contact with each other. Therefore, the output side fixed sheave 101 can be easily and reliably positioned as compared with the case where the output side fixed sheave 101 is fixed to the transmission shaft 90 using a taper.

In this embodiment, the transmission shaft 90 and the output side fixed sheave 101 are fitted (fitted) by press fitting, but the diameter of the transmission shaft 90 such as “shrink fit” or “cool fit” is used. May be a method of fitting using the fact that the diameter is larger than the diameter of the through hole 101b of the output side fixed sheave 101.
In the present embodiment, the portion immediately in front of the enlarged diameter portion 90a of the transmission shaft 90 and the reduced diameter portion 101c of the output side fixed sheave 101 are fitted together by press fitting, but the present invention is not limited to this. Absent. That is, the enlarged diameter portion 90a of the transmission shaft 90 and the portion immediately behind the reduced diameter portion 101c of the output side fixed sheave 101 can be fitted together by press fitting. When performing this press-fitting, the diameter-reduced portion 101c of the output side fixed sheave 101 can be slid on the transmission shaft 90 to serve as a guide for the press-fitting operation.

Immediately in front of the output-side fixed sheave 101, the transmission shaft 90 is inserted into the above-described bearing 91, and is rotatably supported with respect to the transmission case 8 via the bearing 91.
Just before the bearing 91, the lock nut 102 is fastened to the transmission shaft 90. Accordingly, the bearing 91 can be prevented from sliding forward, and the output-side fixed sheave 101 can be prevented from sliding forward via the bearing 91, so that the output-side fixed sheave 101 can be connected to the transmission shaft 90. Can be securely fixed.

The output side movable sheave 103 is a member made of the same material as the input side movable sheave 63 and formed in the same shape. That is, the output side movable sheave 103 is a member having a substantially cylindrical shaft tube portion and a substantially frustoconical sheave portion formed integrally with the rear end of the shaft tube portion in a side sectional view. . The output-side movable sheave 103 is fitted on the transmission shaft 90 behind the output-side fixed sheave 101 with the sheave portion disposed in front of the shaft tube portion. The front surface 103a of the sheave portion of the output side movable sheave 103 is formed as an inclined surface whose diameter increases from the front to the rear.
On the axis of the output side movable sheave 103, a through hole 103b that penetrates the output side movable sheave 103 in the front-rear direction is formed. The transmission shaft 90 is inserted into the through hole 103b of the output side movable sheave 103 from the front.
By arranging the rear surface 101a of the output-side fixed sheave 101 and the front surface 103a of the output-side movable sheave 103 to face each other on the transmission shaft 90, a groove of the output pulley 100 is formed by the rear surface 101a and the front surface 103a. .
A sheave side groove 103c and a shaft side groove 90b are formed in the inner peripheral surface of the through hole 103b and the outer peripheral surface of the transmission shaft 90 along the axial direction of the transmission shaft 90, respectively. The sheave side groove 103 c is formed at least from the rear end (rear end of the shaft tube portion) of the output side movable sheave 103 to the middle part before and after the output side movable sheave 103. The sheave side groove 103c and the shaft side groove 90b are formed at three positions at equal intervals in the circumferential direction of the inner peripheral surface of the through hole 103b and the outer peripheral surface of the transmission shaft 90, and the steel balls 104. 104... Are arranged. Thereby, the output side movable sheave 103 is supported so as to be slidable in the axial direction with respect to the transmission shaft 90 and not to be relatively rotatable.
The intervals between the sheave side grooves 103c and the shaft side grooves 90b are not limited to equal intervals, and the numbers of the sheave side grooves 103c and the shaft side grooves 90b are not limited to the above numbers.
The output side movable sheave 103 is formed with a through hole 103d that communicates the outer peripheral surface of the shaft tube portion with the inner peripheral surface of the through hole 103b. The through hole 103d is formed at a position that does not overlap with the sheave side groove 103c formed on the inner peripheral surface of the through hole 103b.

  As described above, the input-side fixed sheave 61 and the input-side movable sheave 63 of the input pulley 60 and the output-side fixed sheave 101 and the output-side movable sheave 103 of the output pulley 100 are shared by the same parts, so that Can be reduced, and as a result, the cost of parts can be reduced.

  The output member 110 is for transmitting the power from the cam mechanism 120 to the planetary gear mechanism 150. The output member 110 is a member having a substantially cylindrical shaft tube portion and an annular flange portion formed integrally with the front end of the shaft tube portion. A cylindrical outer guide portion 110 a is formed on the front end side of the output member 110. The outer guide portion 110a is disposed in a bottomed cylindrical shape that is disposed with the axial direction facing in the front-rear direction and the front side is open. A through hole is formed in the axial direction at the center of the rear surface of the output member 110, and a spline portion 110b is formed on the inner peripheral surface of the through hole. The output member 110 is disposed behind the output pulley 100 with the transmission shaft 90 inserted through the through hole of the output member 110.

  The cam mechanism 120 enables torque transmission between the output pulley 100 and the output member 110. The cam mechanism 120 includes a first cam 121, a second cam 122, and the like.

The first cam 121 is a substantially cylindrical member. The first cam 121 is disposed so that the axial direction is directed in the front-rear direction and the axial line coincides with the axial line of the transmission shaft 90. A through hole 121 a having a predetermined inner diameter is formed on the axis of the first cam 121. The inner diameter of the through hole 121 a of the first cam 121 is formed to be substantially the same as the inner diameter of the outer guide portion 110 a of the output member 110. A plane perpendicular to the axial direction is formed on the front surface of the first cam 121, and a plurality of surfaces that are inclined at a predetermined angle with respect to the surface orthogonal to the axial direction are formed on the rear surface of the first cam 121. The
The shaft tube portion of the output side movable sheave 103 is inserted through the through hole 121a of the first cam 121 from the front. The first cam 121 is fixed to the output side movable sheave 103 in a state where the rear surface of the sheave portion of the output side movable sheave 103 and the front surface of the first cam 121 are brought into contact with each other by a fastener such as a bolt or welding. Is done.
Note that the first cam 121 and the output-side movable sheave 103 can be integrally formed by forging or the like.

The second cam 122 is a member made of the same material as the first cam 121 and formed in the same shape. That is, the second cam 122 is disposed so that the axial direction is directed in the front-rear direction and the axial line coincides with the axial line of the transmission shaft 90. A through hole 122 a having a predetermined inner diameter is formed on the axis of the second cam 122. The inner diameter of the through hole 122a of the second cam 122 is formed to be substantially the same as the inner diameter of the outer guide portion 110a of the output member 110. On the rear surface of the second cam 122, a plane perpendicular to the axial direction is formed, and on the front surface of the second cam 122, a plurality of surfaces inclined by a predetermined angle with respect to the surface orthogonal to the axial direction are formed. The
The transmission shaft 90 is inserted into the through hole 122a of the second cam 122 from the front. The second cam 122 is fixed to the output member 110 in a state where the front surface of the output member 110 and the rear surface of the second cam 122 are brought into contact with each other by a fastener such as a bolt or welding. As a result, the rear surface of the first cam 121 and the front surface of the second cam 122 are arranged to face each other.
The second cam 122 and the output member 110 can be integrally formed by forging or the like.

  The urging member 130 urges the output side movable sheave 103 forward. The biasing member 130 is disposed in the outer guide portion 110a of the output member 110, and is configured by a plurality of disc springs 131, 131,... Arranged in the axial direction. The rear end of the biasing member 130 (the disc spring 131 disposed at the rearmost position) is in contact with the output member 110, and the front end of the biasing member 130 (the disc spring 131 disposed at the frontmost position) is interposed via the inner guide member 132. Thus, the output side movable sheave 103 is brought into contact with the rear end.

  The inner guide member 132 is a member having a cylindrical portion 132a having a substantially cylindrical shape and an annular spring receiving portion 132b integrally formed at the front end of the cylindrical portion 132a. The inner diameter of the cylindrical portion 132a is formed to be substantially the same as the outer diameter of the transmission shaft 90, and the axial length of the cylindrical portion 132a is formed to be a predetermined length. Further, the spring receiving portion 132b is formed to be orthogonal to the axial direction.

  By the urging force of the urging member 130, the output side movable sheave 103 is urged forward, that is, in a direction close to the output side fixed sheave 101.

  In this case, the inner diameter of the outer guide portion 110a of the output member 110 is formed so as to be substantially the same as the outer diameter of the biasing member 130 (the disc springs 131, 131...). Moreover, the outer diameter of the cylindrical part 132a of the inner side guide member 132 is formed so that it may become substantially the same as the inner diameter of the biasing member 130 (disc spring 131 * 131 ...). Accordingly, the disc springs 131, 131,... Arranged on the rear side of the biasing member 130 are connected to the outer guide portion 110a of the output member 110 (more specifically, the outer guide portion 110a of the output member 110 and the second guide portion 110a). The disc springs 131, 131... Which are guided by the inner peripheral surface of the cam 122 so as not to deviate from each other's axis and are arranged on the front side of the urging member 130 are mutually connected by the cylindrical portion 132 a of the inner guide member 132. It is guided so that the axis of As described above, the output side movable sheave 103 can be urged stably by preventing the axial displacement of the plurality of disc springs 131.

  Further, in the state where the output side movable sheave 103 slides most forward, the cylindrical portion 132a of the inner guide member 132 extends rearward to a position overlapping the inner peripheral surface of the second cam 122 in the axial direction. With this configuration, all the disc springs 131, 131... Constituting the urging member 130 even when the output side movable sheave 103 is slid the most forwardly, the outer guide portion 110 a of the output member 110. It can be guided by the inner peripheral surface of the second cam 122 or the cylindrical portion 132a of the inner guide member 132.

  Further, as in the present embodiment, the urging member 130 is composed of a plurality of disc springs 131, 131..., And the axial length is shorter and more compact than when a coil spring is used as the urging member. can do.

  The belt 140 shown in FIGS. 2 and 10 is wound around the groove of the input pulley 60 and the groove of the output pulley 100, and transmits the power of the input pulley 60 to the output pulley 100. The belt 140 is a metal belt including a band in which metal thin plates are stacked and a metal element. The present invention is not limited to this, and a belt made of rubber, a chain, or a resin may be used as the belt 140.

  The belt 140 wound around the groove of the input pulley 60 is clamped by the input pulley 60 when the input side movable sheave 63 is pushed toward the input side fixed sheave 61 by the hydraulic cylinder 70 with a predetermined force. The belt 140 wound around the groove of the output pulley 100 is pushed to the output pulley 100 by the output side movable sheave 103 being pushed toward the output side fixed sheave 101 side with a predetermined force by the urging force of the urging member 130. It is pinched.

The planetary gear mechanism 150 shown in FIGS. 12 and 13 is for synthesizing and outputting two powers. The planetary gear mechanism includes a sun gear 151, a ring gear 152, a carrier gear 153, planetary shafts 155, 155, connecting shafts 156, 156, planetary gears 157, 157, a support member 159, a planetary output member 163, and the like. It comprises.
In FIG. 13, detailed shapes of teeth and splines formed on each gear are omitted.

The sun gear 151 is a gear in which a spline portion 151a is formed on the outer periphery of the front end portion of the substantially cylindrical shaft tube portion, and a tooth 151b is formed on the outer periphery of the rear end portion of the shaft tube portion separated from the spline portion 151a by a predetermined distance. is there. On the axis of the sun gear 151, a through hole 151c that penetrates the sun gear 151 in the front-rear direction is formed. The transmission shaft 90 is inserted into the through-hole 151c of the sun gear 151 from the front, and the sun gear 151 is supported by the transmission shaft 90 so as to be relatively rotatable.
The spline portion 151 a of the sun gear 151 is engaged with the spline portion 110 b of the output member 110, and the sun gear 151 is rotated integrally with the output member 110.

  The ring gear 152 is a gear in which teeth 152a are formed on the inner peripheral surface of the annular member. The transmission shaft 90 is inserted into the ring gear 152 from the front, and the teeth 152a of the ring gear 152 are disposed at positions facing the teeth 151b of the sun gear 151.

The carrier gear 153 is a gear having teeth 153a formed on the outer peripheral surface of a substantially circular plate-like member. On the axis of the carrier gear 153, a through hole 153b that penetrates the carrier gear 153 in the front-rear direction is formed.
Three through holes 153c, 153c,... Having a predetermined inner diameter penetrating the carrier gear 153 in the front-rear direction are formed at equal intervals on the same circumference centered on the axis of the carrier gear 153. Similarly, three through holes 153d, 153d,... Having a predetermined inner diameter penetrating the carrier gear 153 in the front-rear direction are formed at equal intervals on the same circumference around the axis of the carrier gear 153. . The through holes 153c, 153c, ... and the through holes 153d, 153d, ... are arranged alternately on the same circumference.
The sun gear 151 supported by the transmission shaft 90 is inserted into the through hole 153b of the carrier gear 153, and the carrier gear 153 is supported by the shaft cylinder portion (front and rear halfway portion) of the sun gear 151 via the needle bearing 154 so as to be relatively rotatable. Is done.
The teeth 153 a of the carrier gear 153 are engaged with the gear of the clutch mechanism 200 provided on the mission input shaft 20, and the power of the mission input shaft 20 can be transmitted through the clutch mechanism 200.

  The planetary shafts 155, 155... Are substantially cylindrical members. The one end (front end) of the planetary shafts 155, 155,... Is fitted into the through-holes 153c, 153c, etc. of the carrier gear 153, whereby the planetary shafts 155, 155,. The The other end (rear end) of the planetary shafts 155, 155... Extends rearward.

  The connecting shafts 156, 156... Are substantially cylindrical members. The one end (front end) of the connecting shafts 156, 156... Is fitted into the through holes 153d, 153d, etc. of the carrier gear 153, whereby the connecting shafts 156, 156. The The other ends (rear ends) of the connecting shafts 156 and 156 extend rearward.

  .. Are three gears that mesh with the teeth 151b of the sun gear 151 and the teeth 152a of the ring gear 152, respectively. A through hole 157 a that penetrates the planetary gear 157 in the front-rear direction is formed on the axis of the planetary gear 157. The planetary shafts 155, 155,... Fixed to the carrier gear 153 are inserted into the through holes 157a, 157a,... Of the planetary gears 157, 157, respectively, and the planetary gears 157, 157,. ... Are supported on the planetary shafts 155,.

The support member 159 is a member having a substantially cylindrical shaft tube portion and an annular flange portion integrally formed at the front end of the shaft tube portion. A through hole 159 a that penetrates the support member 159 in the front-rear direction is formed on the axis of the support member 159.
In the flange portion of the support member 159, three through holes 159b and 159b having a predetermined inner diameter penetrating the flange portion of the support member 159 in the front-rear direction on the same circumference centered on the axis of the support member 159. Are formed at equal intervals. Similarly, in the flange portion of the support member 159, three penetrations having a predetermined inner diameter that penetrates the flange portion of the support member 159 in the front-rear direction on the same circumference centering on the axis of the support member 159. Holes 159c, 159c,... Are formed at equal intervals. The through holes 159b, 159b,... And the through holes 159c, 159c,... Are arranged alternately on the same circumference.
The transmission shaft 90 is inserted into the through-hole 159a of the support member 159, and the support member 159 is supported by the transmission shaft 90 via the bearing 160 at the rear of the planetary gears 157, 157. Immediately after the bearing 160, the lock nut 161 is fastened to the transmission shaft 90. As a result, the bearing 160 can be prevented from sliding backward.
The other ends of the planetary shafts 155, 155, ... are fitted into the through holes 159b, 159b, ... of the support member 159, respectively. The other ends of the connecting shafts 156, 156,... Are fitted in the through holes 159c, 159c,. In this way, the support member 159 is connected to the carrier gear 153 via the planetary shafts 155, 155,.
A communication member 162, which is a ring-shaped member, is interposed between the through hole 159 a of the support member 159 (more specifically, a portion corresponding to the flange portion of the support member 159) and the transmission shaft 90.

The planetary output member 163 is a box-shaped member whose front part is opened. A through hole is formed at the center of the rear surface of the planetary output member 163, and a spline portion 163a is formed in the through hole. The planetary output member 163 is disposed so as to cover the rear end portion of the transmission shaft 90 and the support member 159 from the rear of the transmission shaft 90. The vicinity of the front and rear central portion of the planetary output member 163 is supported by the transmission shaft 90 via a bearing 164 so as to be relatively rotatable. The front end of the planetary output member 163 is fastened to the ring gear 152 by bolts 165, 165... And connected to the ring gear 152 so as to be integrally rotatable.
The planetary output member 163 and the ring gear 152 can be integrally formed by forging or the like.

  The output shaft 170 is spline fitted to the spline portion 163a of the planetary output member 163. Power from the planetary output member 163 can be transmitted to the rear wheel (not shown) of the tractor and the front wheel drive transmission shaft 180 via the output shaft 170.

  Below, the structure regarding the lubrication of the transmission shaft 90, the output pulley 100, and the planetary gear mechanism 150 is demonstrated using FIG. 11 and FIG.

  The transmission shaft 90 is formed with a lubricating oil passage 90c, a distribution oil passage 90d, a cam oil passage 90e, a carrier distribution oil passage 90f, and a planetary distribution oil passage 90g.

The lubricating oil passage 90c is a hole formed from the front end of the transmission shaft 90 to the vicinity of the rear end. The lubricating oil passage 90c is connected to a lubricating oil pump (not shown) by piping or the like.
The distribution oil passage 90d is a through-hole formed so that the outer circumferential surface of the transmission shaft 90 and the lubricating oil passage 90c communicate with each other with the axial direction orthogonal to the axis of the transmission shaft 90. More specifically, the distribution oil passage 90d is the outer peripheral surface of the enlarged diameter portion 90a of the transmission shaft 90, the vicinity of the rear surface 101a of the sheave portion of the output side fixed sheave 101 fixed to the transmission shaft 90, and the lubricating oil. The road 90c is communicated.
The cam oil passage 90e is a through hole formed so as to communicate the lubricating oil passage 90c with a portion of the outer peripheral surface of the transmission shaft 90 facing the through hole 103d formed in the output side movable sheave 103. is there.
The carrier distribution oil passage 90f is a through-hole formed so that the outer circumferential surface of the transmission shaft 90 and the lubricating oil passage 90c communicate with each other with the axial direction orthogonal to the axis of the transmission shaft 90. More specifically, the carrier distribution oil passage 90f communicates the lubricating oil passage 90c with a portion of the outer peripheral surface of the transmission shaft 90 that opposes the shaft cylinder portion (front and rear halfway portion) of the sun gear 151.
The planetary distribution oil passage 90g is a through hole formed so that the outer circumferential surface of the transmission shaft 90 and the lubricating oil passage 90c communicate with each other with the axial direction orthogonal to the axis of the transmission shaft 90. More specifically, the planetary distribution oil passage 90g communicates the lubricating oil passage 90c with the outer peripheral surface of the transmission shaft 90 and the portion facing the communication member 162.

A distribution oil passage 151 d is formed in the sun gear 151.
The distribution oil passage 151d is a through hole formed so that the outer peripheral surface of the sun gear 151 and the through hole 151c are communicated with each other with the axial direction orthogonal to the axis of the sun gear 151. More specifically, the distribution oil passage 151d is the outer peripheral surface of the shaft cylinder portion (front and rear halfway portion) of the sun gear 151 and the through hole 151c, and is located at the same position in the axial direction as the carrier distribution oil passage 90f of the transmission shaft 90. It communicates with the part that becomes.

A distribution oil passage 162 a is formed in the communication member 162.
The distribution oil passage 162a is formed so as to communicate the groove formed on the inner peripheral surface of the communication member 162 and the outer peripheral surface of the communication member 162 with the axial direction being a direction perpendicular to the axis of the communication member 162. It is the oil path comprised from the through-hole made.

A distribution oil passage 159d is formed in the support member 159.
The distribution oil passage 159d is an oil passage that communicates the through hole 159a of the support member 159 with the through holes 159b, 159b,. More specifically, the distribution oil passage 159d is a groove formed on the inner peripheral surface of the through hole 159a of the support member 159 and corresponding to the flange portion of the support member 159, and the groove and the through hole 159b. -It is comprised from the through-hole formed so that 159b ... may be connected.

Lubricating oil passage 155 a is formed on planetary shaft 155.
Lubricating oil passage 155a communicates the outer peripheral surface of planetary shaft 155 with the portion facing support oil distribution passage 159d of support member 159 and the outer peripheral surface of planetary shaft 155 with the portion facing needle bearing 158. It is an oil passage.

  Below, with reference to the arrows shown in FIG. 14, the state of lubrication of the transmission shaft 90, the output pulley 100, the planetary gear mechanism 150 and the like in the above-described configuration will be described.

The hydraulic fluid pumped from the lubricating oil pump and supplied to the lubricating oil passage 90c of the transmission shaft 90 passes through the distribution oil passage 90d to the outer peripheral surface of the transmission shaft 90 (near the rear surface 101a of the sheave portion of the output side fixed sheave 101). ). The contact surface between the rear surface 101a of the sheave portion of the output side fixed sheave 101 and the belt 140 is lubricated by the supplied hydraulic oil.
Thus, for the output-side fixed sheave 101 that does not slide with respect to the transmission shaft 90, an oil passage (lubricating oil) for supplying hydraulic oil that lubricates the rear surface 101 a of the sheave portion of the output-side fixed sheave 101. The output side fixed sheave 101 can be properly lubricated by forming the passage 90c and the distribution oil passage 90d).

  The hydraulic fluid pumped from the lubricating oil pump and supplied to the lubricating oil passage 90 c of the transmission shaft 90 passes through the cam oil passage 90 e and the through-hole 103 d of the output-side movable sheave 103, and the output-side movable sheave. 103 is supplied to the outer peripheral surface of the axial tube portion 103. The contact surface between the first cam 121 fixed to the output side movable sheave 103 and the second cam 122 in contact with the first cam 121 is lubricated by the supplied hydraulic oil.

  Further, the hydraulic oil pumped from the lubricating oil pump and supplied to the lubricating oil passage 90c of the transmission shaft 90 passes through the distribution oil passage 90f for the carrier and the distribution oil passage 151d of the sun gear 151, and the shaft cylinder portion of the sun gear 151. Is supplied to the outer peripheral surface. The supplied hydraulic oil lubricates the needle bearing 154 fitted on the shaft cylinder portion of the sun gear 151.

  The hydraulic fluid pumped from the lubricating oil pump and supplied to the lubricating oil passage 90c of the transmission shaft 90 includes a planetary distribution oil passage 90g, a distribution oil passage 162a of the communication member 162, and a distribution oil passage 159d of the support member 159. And the lubricating oil passages 155a, 155a, ... of the planetary shafts 155, 155, ..., are supplied to the outer peripheral surfaces of the planetary shafts 155, 155, .... The needle bearings 158, 158... Externally fitted to the planetary shafts 155, 155... Are lubricated by the supplied hydraulic oil.

  Hereinafter, an outline of power transmission and speed change in the belt type continuously variable transmission 40 configured as described above will be described.

  When power from the engine is transmitted to the transmission input shaft 50 via the mission input shaft 20 and the clutch mechanism 200, the input pulley 60 is also rotated together with the transmission input shaft 50. When the input pulley 60 is rotated, the output pulley 100 is rotated via the belt 140. When the output pulley 100 is rotated, the first cam 121 fixed to the output pulley 100 is rotated. When the first cam 121 rotates, the rear surface (inclined surface) of the first cam 121 and the front surface (inclined surface) of the second cam 122 come into contact with each other. It is rotated. When the second cam 122 is rotated, the sun gear 151 of the planetary gear mechanism 150 is rotated via the output member 110. When the sun gear 151 is rotated, the planetary gears 157, 157... Meshed with the sun gear 151 rotate (rotate) around the planetary shafts 155, 155.

  On the other hand, the power from the engine is transmitted to the carrier gear 153 of the planetary gear mechanism 150 via the mission input shaft 20 and the clutch mechanism 200 (that is, not shifted by the input pulley 60, the output pulley 100, and the belt 140). Then, together with the carrier gear 153, planetary gears 157, 157... Supported by the carrier gear 153 rotate (revolve) around the transmission shaft 90.

  Thus, the power transmitted from the mission input shaft 20 to the planetary gear mechanism 150 via the belt 140 and the power transmitted from the mission input shaft 20 directly to the planetary gear mechanism 150 without passing through the belt 140 are the planets. Are combined by planetary gears 157, 157. The combined power is transmitted to the output shaft 170 via the ring gear 152 meshed with the planetary gears 157, 157... And the planetary output member 163.

  Further, the cam mechanism 120 can apply a forward biasing force to the output side movable sheave 103 according to the torque transmitted from the first cam 121 to the second cam 122. Specifically, twisting occurs between the first cam 121 and the second cam 122 according to the torque transmitted by the cam mechanism 120. In this case, since the rear surface (inclined surface) of the first cam 121 and the front surface (inclined surface) of the second cam 122 are in contact with each other, the first cam 121 and the second cam 122 are separated according to the contacted surface. Force is generated in the direction of The first cam 121 is moved away from the second cam 122 by the force, so that the output side movable sheave 103 is urged toward the output side fixed sheave 101. With the urging force and the urging force by the urging member 130, the belt 140 can be clamped with an appropriate force in the output pulley 100.

  When the operation of the hydraulic cylinder 70 is controlled and the input side movable sheave 63 is slid rearward, the distance between the rear surface 63a of the input side movable sheave 63 and the front surface 61a of the input side fixed sheave 61 (input pulley 60). The groove width) becomes narrower. When the groove width of the input pulley 60 is reduced, the diameter of the belt 140 wound around the input pulley 60 is increased. Since the entire length of the belt 140 is constant, when the diameter of the belt 140 wound around the input pulley 60 increases, the output-side movable sheave 103 of the output pulley 100 moves backward against the urging force of the urging member 130. By sliding, the groove width of the output pulley 100 increases, and the diameter of the belt 140 wound around the output pulley 100 decreases. As described above, the diameter of the belt 140 wound around the input pulley 60 is increased, and the diameter of the belt 140 wound around the output pulley 100 is decreased, so that the belt 140 is transmitted to the planetary gear mechanism 150. The power can be shifted to the speed increasing side.

  When the operation of the hydraulic cylinder 70 is controlled so that the hydraulic oil in the hydraulic chamber 76 can be discharged, the input-side movable sheave 63 is driven by the forward component of the tension of the belt 140 wound around the input pulley 60. Slid forward, the groove width of the input pulley 60 becomes wider. As the groove width of the input pulley 60 increases, the diameter of the belt 140 wound around the input pulley 60 decreases. Since the total length of the belt 140 is constant, when the diameter of the belt 140 wound around the input pulley 60 decreases, the output-side movable sheave 103 of the output pulley 100 slides forward due to the urging force of the urging member 130. Thus, the groove width of the output pulley 100 is narrowed, and the diameter of the belt 140 wound around the output pulley 100 is increased. By reducing the diameter of the belt 140 wound around the input pulley 60 and increasing the diameter of the belt 140 wound around the output pulley 100 in this way, the belt 140 is transmitted to the planetary gear mechanism 150 via the belt 140. The power can be shifted to the deceleration side.

  Thus, by shifting the power transmitted from the mission input shaft 20 to the planetary gear mechanism 150 via the belt 140, the power transmitted to the output shaft 170 via the planetary gear mechanism 150 is reversed from normal rotation to reverse rotation. (I.e., from forward to reverse).

As described above, the belt-type continuously variable transmission 40 according to the present embodiment is
An input pulley 60 including an input side fixed sheave 61 and an input side movable sheave 63 slidable in a direction approaching and separating from the input side fixed sheave 61, and a direction approaching and separating from the output side fixed sheave 101 and the output side fixed sheave 101. An output pulley 100 comprising a slidable output side movable sheave 103;
A belt 140 wound around the two pulleys for transmitting power from one pulley to the other;
A hydraulic cylinder 70 provided on the input-side movable sheave 63 of the input pulley 60;
A hydraulic servo mechanism 80 for controlling the operation of the hydraulic cylinder 70;
Comprising
A belt type continuously variable transmission 40 that can change speed by changing the distance between the input side fixed sheave 61 and the input side movable sheave 63;
The hydraulic servomechanism 80 is
A valve chamber 81a disposed at a position facing the input side movable sheave 63;
An oil passage that is slidably accommodated in the valve chamber 81a, is connected to a shift operation tool (not shown), and communicates with the hydraulic chamber 76 of the hydraulic cylinder 70 by sliding according to the operation of the shift operation tool. A servo spool 83 for switching between
The servo spool 83 is slidably housed, and one end of the servo spool 83 is disposed so as to contact the input side movable sheave 63 via a bearing 72 or the like. A feedback spool 84 that switches the oil passage so as to be held at a position corresponding to the position;
It comprises.
With this configuration, the belt-type continuously variable transmission 40 can be shifted with a simple configuration without using complicated electronic control. Further, the hydraulic servo mechanism 80 can be configured in a compact manner.

The feedback spool 84 is
The input side movable sheave 63 is slidable in the same direction as the sliding direction of the input side movable sheave 63 and is urged in a direction in contact with the input side movable sheave 63.

The belt-type continuously variable transmission 40 is
Between the feedback spool 84 and the input side movable sheave 63, a bearing 72 for reducing friction between the feedback spool 84 and the input side movable sheave 63 is interposed.
With this configuration, it is possible to prevent wear due to friction between the input side movable sheave 63 and the feedback spool 84.

As described above, the belt-type continuously variable transmission 40 according to the present embodiment is
The power after the stepless change by the pair of pulleys (the input pulley 60 and the output pulley 100) and the belt 140 wound around the pair of pulleys is transmitted without being changed by the pair of pulleys and the belt 140. A belt-type continuously variable transmission 40 including a planetary gear mechanism 150 that combines and outputs the power to be
The planetary gear mechanism 150 is
A sun gear 151 disposed on the transmission shaft 90;
A ring gear 152 disposed on the same axis as the sun gear 151;
A plurality of planetary gears 157, 157... Meshing with the sun gear 151 and the ring gear 152;
A carrier gear 153 disposed on the same axis as the sun gear 151;
Comprising
Planetary gears 157, 157 ...
The one end is rotatably supported by a plurality of planetary shafts 155, 155,.
With this configuration, the planetary gear mechanism 157, 157... Is supported by the carrier gear 153 for inputting power without using the carrier for supporting the planetary gears 157, 157. 150 compactness and cost reduction can be achieved.

The belt-type continuously variable transmission 40 is
The ends of the plurality of planetary shafts 155, 155,... Opposite to the carrier gear 153 across the planetary gears 157, 157 are supported by a support member 159 that is rotatably supported on the transmission shaft 90. Is.
With this configuration, it is possible to reliably support the planetary gears 157, 157... While reducing the size of the planetary gear mechanism 150, and to prevent the axis of the planetary gears 157, 157. can do.

Further, the support member 159 includes
A distribution oil passage 159d through which the lubricating oil supplied to the planetary shafts 155, 155... Flows is formed.
With this configuration, the planetary gears 157, 157... And the distribution oil passage 159d for supplying lubricating oil to the planetary shafts 155, 155. ), And cost reduction can be achieved.

The carrier gear 153 is rotatably supported by the sun gear 151.
With this configuration, the planetary gear mechanism 150 can be made compact.

As described above, the belt-type continuously variable transmission 40 according to the present embodiment is
Two shafts (transmission input shaft 50 and transmission shaft 90) arranged in parallel to each other;
An input pulley 60 having an input side fixed sheave 61 fixed to the speed change input shaft 50, and an input side movable sheave 63 supported by the speed change input shaft 50 so as to be slidable in the axial direction and not relatively rotatable;
An output pulley 100 having an output side fixed sheave 101 fixed to the transmission shaft 90, and an output side movable sheave 103 supported by the transmission shaft 90 so as to be slidable in the axial direction and non-rotatable relative to the transmission shaft 90;
A belt 140 wound around the two pulleys;
Comprising
Each of the fixed sheaves is
The through-holes (through-hole 61b and through-hole 101b) formed in the fixed sheave are fixed to the shaft so as not to be relatively rotatable by fitting to the corresponding shaft,
The reduced diameter portion (the reduced diameter portion 61c and the reduced diameter portion 101c) formed in the through hole of the fixed sheave is contacted with the enlarged diameter portion (the enlarged diameter portion 50a and the enlarged diameter portion 90a) formed on the corresponding shaft. By making contact, the position in the axial direction of the axis is determined.
With this configuration, the manufacturing cost is reduced, and the fixed sheave (the input-side fixed sheave 61 and the output-side fixed sheave 101) is easily and reliably positioned on the shaft (the transmission input shaft 50 and the transmission shaft 90). It can be carried out.

The input side fixed sheave 61 and the output side fixed sheave 101 are made of the same member.
By configuring in this way, the two fixed sheaves can be shared to reduce the component cost.

The input side movable sheave 63 and the output side movable sheave 103 are made of the same member.
With this configuration, the two movable sheaves can be shared, thereby reducing the component cost.

As described above, the belt-type continuously variable transmission 40 according to the present embodiment is
An output pulley 100 having an output side fixed sheave 101 fixed to the transmission shaft 90, and an output side movable sheave 103 supported by the transmission shaft 90 so as to be slidable in the axial direction and non-rotatable relative to the transmission shaft 90;
An output member 110 disposed on the same axis as the transmission shaft 90;
It is interposed between the output-side movable sheave 103 and the output member 110 to enable transmission of torque between the output-side movable sheave 103 and the output member 110, and to apply an axial pressing force corresponding to the torque to the output-side movable. A cam mechanism 120 applied to the sheave 103;
A biasing member 130 for biasing the output side movable sheave 103 toward the output side fixed sheave 101;
A belt type continuously variable transmission 40 comprising:
The biasing member 130 is
It is comprised by the some disc spring 131 * 131 ... arrange | positioned along with the axial direction of the transmission shaft 90 between the output side movable sheave 103 and the output member 110. As shown in FIG.
By comprising in this way, the axial direction length of the urging | biasing member 130 for urging | biasing the output side movable sheave 103 can be comprised compactly. Further, by changing any one of the plurality of disc springs 131, 131,... To a disc spring having a different spring constant, the pressing force in the axial direction can be easily performed without changing the storage shape or the spring shape. You can change the characteristics.

The belt-type continuously variable transmission 40 is
A guide member for preventing a shift of the axis of the plurality of disc springs 131, 131... Is provided.
In addition, the guide member is
A cylindrical outer guide portion 110a that is formed on the output member 110 and guides the plurality of disc springs 131, 131,.
.. Of the plurality of disc springs 131, 131... Are arranged between the disc spring 131 disposed on the most output side movable sheave 103 side and the output side movable sheave 103, and a plurality of disc springs An inner guide member 132 composed of a cylindrical portion 132a for guiding the plurality of disc springs 131, 131,.
It is comprised from.
By configuring in this way, the urging member 130 is configured in a compact manner, the axial displacement of the plurality of disc springs 131, 131... Is prevented, and the output side movable sheave 103 is urged stably. be able to.

As described above, the belt-type continuously variable transmission 40 according to the present embodiment is
An input pulley 60 having an input side fixed sheave 61 fixed to the transmission input shaft 50 and an input side movable sheave 63 supported by the transmission input shaft 50 so as to be slidable in the axial direction;
A steel ball 64 that is disposed in grooves (sheave side groove 63c and shaft side groove 50b) formed in the input side movable sheave 63 and the transmission input shaft 50 and connects the input side movable sheave 63 to the transmission input shaft 50 so as not to be relatively rotatable.・ 64 ...
A hydraulic cylinder 70 provided in the input-side movable sheave 63 to change the sliding position of the input-side movable sheave 63;
A belt 140 wound around the input pulley 60;
Comprising
Steel balls 64, 64,... Due to leakage of hydraulic oil sent from the oil passages (operating groove 50e and hydraulic oil passage 50f) formed in the transmission input shaft 50 to the hydraulic chamber 76 of the hydraulic cylinder 70. The contact surface between the input side movable sheave 63 and the transmission input shaft 50 and the contact surface between the input side movable sheave 6 and the belt 140 are lubricated.
With this configuration, the steel balls 64, 64..., The contact surface between the input-side movable sheave 63 and the transmission input shaft 50, and the contact surface between the input-side movable sheave 63 and the belt 140 are movable on the input side. Appropriate lubrication can be achieved regardless of the sliding position of the sheave 63.

The shift input shaft 50 includes
Oil passages (lubricating oil passage 50g and distribution oil passage 50h) for supplying hydraulic oil to the contact surface between the input side fixed sheave 61 and the belt 140 are formed.
With this configuration, the contact surface between the input-side fixed sheave 61 fixed to the transmission input shaft 50 and the belt 140 can be appropriately lubricated.

  In the above description, the configuration in which the outer guide portion 110a of the output member 110 and the inner guide member 132 are used as a guide member for preventing the axial displacement of the plurality of disc springs 131, 131. However, it is also possible to configure as follows.

  That is, as shown in FIG. 15 (a), it is also possible to prevent the deviation of the axes of the plurality of disc springs 131, 131... Using a substantially cylindrical guide member 133. The inner diameter of the guide member 133 is formed to be substantially the same as the outer diameter of the disc spring 131. Moreover, the longitudinal direction length of the guide member 133 is formed to a length that can cover all the plurality of disc springs 131, 131... From the outside. The disc springs 131, 131,... Can be guided from the outside by the guide member 133 configured as described above, and the deviation of the axis can be prevented.

  Further, as shown in FIG. 15B, a so-called hydraulic damper can be configured using the biasing member 130.

  A cylinder member 134 is externally fitted to the shaft tube portion of the transmission shaft 90 and the output side movable sheave 103 from the outside. Further, a piston member 135 is arranged inside the cylinder member 134 so as to divide the internal space of the cylinder member 134 into the front and the rear. Sealing members are appropriately disposed on the sliding surfaces of the cylinder member 134 and the piston member 135 to prevent the hydraulic oil from flowing out.

  The urging member 130 (the disc springs 131, 131...) Is disposed in the internal space of the cylinder member 134 and in the space behind the piston member 135 (spring chamber 136). The piston member 135 is formed with orifices 135a and 135a which are small through holes penetrating the piston member 135 in the front-rear direction. Further, the internal space of the cylinder member 134 is filled with hydraulic oil.

  The output side movable sheave 103 is in contact with the piston member 135 from the front. Further, the urging member 130 urges the piston member 135 forward. In this way, a so-called hydraulic damper can be configured by the cylinder member 134, the piston member 135, and the biasing member 130.

40 Belt type continuously variable transmission 60 Input pulley (pulley)
90 Transmission shaft (shaft)
100 output pulley (pulley)
140 Belt 150 Planetary Gear Mechanism 151 Sun Gear 152 Ring Gear 153 Carrier Gear 155 Planetary Shaft 157 Planetary Gear 159 Support Member 159d Distribution Oil Path (Oil Path)

Claims (4)

The power after steplessly shifting by the pair of pulleys and the belt wound around the pair of pulleys and the power transmitted without being shifted by the pair of pulleys and the belt are combined and output. A belt-type continuously variable transmission including a planetary gear mechanism,
The planetary gear mechanism is
A sun gear disposed on the shaft;
A ring gear disposed on the same axis as the sun gear;
A plurality of planetary gears meshing with the sun gear and the ring gear;
A carrier gear disposed on the same axis as the sun gear;
Comprising
The planetary gear is
A belt-type continuously variable transmission whose one end is rotatably supported by a plurality of planetary shafts rotatably supported by the carrier gear.   2. The belt-type continuously variable transmission according to claim 1, wherein ends of the plurality of planetary shafts on the side opposite to the carrier gear across the planetary gear are supported by a support member that is rotatably supported on the shaft. Machine. In the support member,
The belt-type continuously variable transmission according to claim 2, wherein an oil passage through which lubricating oil supplied to the planetary shaft flows is formed.   The belt-type continuously variable transmission according to any one of claims 1 to 3, wherein the carrier gear is rotatably supported by the sun gear.

Images