JP3052716B2 - Friction wheel type continuously variable transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a friction wheel type continuously variable transmission.

[0002]

2. Description of the Related Art A conventional friction wheel type continuously variable transmission is disclosed in Japanese Patent Application Laid-Open No. 2-163562. The friction wheel type continuously variable transmission shown in the figure includes a support shaft protruding from the end of the counter shaft onto the center shaft, an intermediate collar fitted to the outer periphery of the support shaft via a one-way clutch, and an intermediate collar. Further, a bushing collar fitted to the outer periphery so as to be relatively rotatable is provided. A pair of friction plates, which are serrated and fitted to the intermediate collar, are in contact with both ends of the bushing collar, and a biasing force of a spring acts on the friction plate in a direction to press the bushing collar. Further, an arm protrudes from the outer periphery of the bushing collar, and the arm abuts on a spool of the switching valve. The one-way clutch idles when the countershaft rotates forward, that is, when it moves forward, and is locked when it rotates reversely, that is, when it moves backward. Therefore, when the countershaft rotates forward, the one-way clutch idles, and no rotational force is transmitted to the bushing collar.
The spring is set at the forward position by the urging force of the spring.
When the counter shaft rotates in the reverse direction, the one-way clutch is locked, and the rotation of the support shaft is transmitted to the intermediate collar. As the bushing collar is pressed by the friction plate biased by the spring,
The rotation of the intermediate collar is transmitted. As a result, the arm rotates and presses the spool, so that the spool is set to the position at the time of reverse travel. When the bushing collar has completely moved the spool to the reverse position, it overcomes the frictional force of the friction plate and is rotated relative to the intermediate collar.

[0003]

However, in the above-mentioned conventional friction wheel type continuously variable transmission, the rotation of the intermediate collar is transmitted to the bushing collar by the pinching of the friction plate by the urging force of the spring, and the arm is used for the transmission. Since the mechanism presses the spool, there is a problem that the friction plate wears due to friction with the bushing collar.
Also, to improve friction plate wear,
When the biasing force of the spring is reduced, the force by which the bushing collar clamps the friction plate is reduced. There is a problem that it becomes impossible to press the button. Further, in order to transmit the rotation of the support shaft to the intermediate collar, a one-way clutch or the like is required, so that there is a problem that the number of parts is large. The present invention is to solve such a problem.

[0004]

According to a first aspect of the present invention, there is provided a friction wheel type continuously variable transmission, wherein a drive gear which rotates integrally with an intermediate shaft, rotates integrally with a collar fitted on an outer periphery of the intermediate shaft, and drives the same. The gear is engaged with a sensor gear having a different number of teeth, and by the difference in the number of teeth, the intermediate shaft and the collar are rotated relative to each other, and a predetermined length is determined from the axial direction of the elongated hole formed in the axial direction of the intermediate shaft and the collar. A sliding hole formed by tilting the angle,
The above problem is solved by guiding a pin penetrating through a long hole and a smooth hole to move the pin in the axial direction, and switching the switching valve between a forward state and a backward state. That is, the friction wheel type continuously variable transmission according to the present invention includes the input disk (12, 16).
And the output disks (14, 18) and the output disk (1
4, 18), and a friction roller (3) disposed in a toroidal groove formed by the two disks so as to make frictional contact with the two disks.
0, 36) and a friction roller (3
0, 36), a shift control device (160, 170) for controlling a gear ratio by controlling a contact position between the two disks, and a forward / reverse switching mechanism (13) provided on the input side of the friction vehicle speed change mechanism.
Forward / backward detection means (90) for determining whether the vehicle is in a forward state or a reverse state; and a shift control device (160,
And a switching valve (80) capable of switching the forward / reverse control state of (170) by moving the spool (82).
Is coupled to a driven gear (64) meshed with the driving gear (60), rotates integrally with the driven gear (64), and has a hollow intermediate portion in which a first elongated hole (212) is formed in the axial direction. The shaft (62) and the outer periphery of the intermediate shaft (62) are rotatably fitted to each other, and the first slot (212)
A collar (202) formed with a second elongated hole (210) inclined at a predetermined angle with respect to the axial direction at a position corresponding to the above, and frictionally coupled so as to be integrally rotatable with the collar (202); (60), the sensor gear (20) having a number of teeth different from the number of teeth of the driven gear.
6), a plunger (200) that is axially movably fitted in the hollow portion of the intermediate shaft (62), and is fixed to the plunger and has a second slot (210) in the collar (202).
The intermediate shaft (62) and the collar (202 ) are inserted into the first elongated hole (212) of the intermediate shaft (62) and rotate by a rotation angle corresponding to the difference in the number of teeth between the driven gear and the sensor gear (64, 206). And a pin (204) that can move in the axial direction by relative rotation of the switching valve (80) and the pin (204) of the forward / reverse detecting means (90).
By pressing the plunger (200) based on the axial movement of the spool, the spool (82) interposed in the switching valve (80) moves, thereby switching to one of the forward state and the reverse state. It is characterized by the following. Also,
The friction wheel type continuously variable transmission according to the second aspect is characterized in that the collar (2)
The 02) is formed a flange portion (202a) is, on the outer peripheral portion of the collar (202), the flange portion (20
2a) and opposite way disc spring (208) is pivotally supported, the sensor gear (206), a flange portion (20
2a ) and a disc spring (208) for squeezing and supporting the collar (202). In addition, the code | symbol in a parenthesis shows the corresponding member of the Example mentioned later.

[0005]

[Action] friction wheel continuously variable transmission according to claim 1, during forward
Alternatively, in either one of the control states during the reverse drive , the pin and the plunger are connected to the first elongated hole of the intermediate shaft and the second elongated hole of the collar.
It is located at one end farthest from the slotted switching valve.
Therefore, the pin is in a state of not pressing the spool of the switching valve. From the above state, the intermediate shaft 62 is rotated in a predetermined direction. As a result, the driven gear rotates integrally with the intermediate shaft, but the sensor gear engaged with the driven gear rotates at a lower rotation speed than the driven gear due to the difference in the number of teeth from the driven gear. This allows for a while
Since the intermediate shaft and the collar rotate relative to each other, the pin located at one end of the first elongated hole of the intermediate shaft and the second elongated hole of the collar gradually rotates with the rotation of the collar. It moves with the plunger to the other end closest to the switching valve of the second elongated hole. Thus, pin through the plunger, so to press the spool of the switching valve, switching valve and the other
Control state.

[0006]

FIG. 1 is a skeleton diagram showing a friction wheel type continuously variable transmission. The torque converter 12 to which the rotational force is input from the crankshaft 72 of the engine has a pump impeller 12a, a turbine runner 12b, a stator 12c, and a lock-up clutch 12d. Lock-up clutch 12
d is an apply-side oil chamber 12e and a release-side oil chamber 12f.
The pump impeller 12a and the turbine runner 12b can be mechanically connected or disconnected according to the hydraulic pressure. The turbine shaft 26 that rotates integrally with the turbine runner 12 b of the torque converter 12 is connected to the forward / reverse switching mechanism 13. The forward / reverse switching mechanism 13 includes the planetary gear mechanism 17, a forward clutch 40, and a reverse brake 42.
The planetary gear mechanism 17 includes a sun gear 19, a pinion carrier 25 having two pinion gears 21 and 23, and an internal gear 27. The pinion gears 21 and 23 having the same diameter mesh with each other, and the pinion gear 21 meshes with the internal gear 27,
The pinion gear 23 meshes with the sun gear 19. The sun gear 19 is connected so as to always rotate integrally with the turbine shaft 26. The pinion carrier 25 can be connected to the turbine shaft 26 by a forward clutch 40. Further, the internal gear 27 can be fixed to the casing 11 by a reverse brake 42. Pinion carrier 2
5 is always connected to the transmission shaft 37 to the continuously variable transmission mechanism.

A first continuously variable transmission mechanism (friction vehicle transmission mechanism) 22 is provided downstream of the forward / reverse switching mechanism 13 in the casing 11.
And a second continuously variable transmission mechanism 24. These are the input shaft 1 connected so as to rotate integrally with the transmission shaft 37.
0 are arranged in parallel. The first continuously variable transmission mechanism 22 has a first input disk 12, a first output disk 14, and a pair of first friction rollers 30 for transmitting a rotational force between the two. The contact surfaces of the first input disk 12 and the first output disk 14 with the first friction roller 30 are toroid surfaces. By changing the contact state between the first input disk 12 and the first output disk 14, the rotation speed ratio between the first input disk 12 and the first output disk 14 can be continuously changed. The second continuously variable transmission mechanism 24 also includes a second input disk 16 similar to the first continuously variable transmission mechanism 22,
It has an output disk 18 and a pair of second friction rollers 36. However, the arrangement of the second input disk 16 and the second output disk 18 is opposite to that of the first continuously variable transmission mechanism 22. The first input disk 12 is supported on the outer periphery of the input shaft 10 via a ball spline 50. A cam flange 52 is arranged on the back side of the first input disk 12. A cam roller 54 is provided on the cam surfaces of the cam flange 52 and the first input disk 12 facing each other.
Is provided. The cam surface and the cam roller 54 are shaped so as to generate a force for pressing the first input disk 12 toward the first output disk 14 when the first input disk 12 and the cam flange 52 rotate relative to each other. A loading cam 66 is constituted by the cam flange 52, the first input disk 12, and the cam roller 54. The second input disk 16 of the second continuously variable transmission mechanism 24 is also connected to the input shaft 10 via a ball spline 56. The second input disk 16 is constantly receiving a force directed to the second output disk 18 by the disc spring 58. The first output disk 14 of the first continuously variable transmission mechanism 22 and the second output disk 18 of the second continuously variable transmission mechanism 24 are rotatably supported on the input shaft 10. A drive gear 60 is provided so as to rotate integrally with the first output disk 14 and the second output disk 18. The drive gear 60 meshes with a driven gear 64 that is coupled to one end of an intermediate shaft 62 disposed parallel to the input shaft 10 so as to rotate integrally therewith. A gear 67 integrally formed on the other end of the intermediate shaft 62 is provided with an idler gear 6.
9 and a gear 71 integral with the output shaft 70.

FIG. 2 shows a shift control section of the friction wheel type continuously variable transmission. The first friction roller 30 and the second friction roller 36
Hydraulic actuator 15 provided corresponding to these
The rotating shafts 150a, 152a, 154a and 15 which are moved in the vertical direction by 0, 152, 154 and 156.
6a, eccentric shafts 150b, 152b, 154b and 15
It is rotatably mounted via 6b. Rotating shaft 150a,
The first friction roller 30 and the second friction roller 36 can be inclined by moving the 152a, 154a and 156a in the vertical direction. At this time, the rotating shaft 150
a, 152a, 154a, and 156a are rotated when the first friction roller 30 and the second friction roller 36 are tilted by being moved up and down. Therefore, since the amount of inclination of the first friction roller 30 and the second friction roller 36 is determined by the amount of movement of the hydraulic actuators 150, 152, 154, and 156, the rotation axes 150a, 152
a, 154a and 156a. Hydraulic actuators 150, 152, 15
The movement amounts of the first and second control valves (shift control device) 160 and the second control valve (shift control device) 17 that are operated when the vehicle moves forward and backward, respectively.
0, the first and second control valves 160 and 17
And a switching valve 80 for switching 0.
The first and second control valves 160 and 170 are
Drive rods 162 and 172 rotated by step motors 161 and 171, and sleeves 163 and 173.
Spools 164 and 174 fitted to the inner diameters of the sleeves 163 and 173;
Springs 165 and 175 for pressing the spring 74 in the opposite direction to the step motors 161 and 171, respectively. The drive rods 162 and 172 have threaded portions 162a and 172a formed at the distal ends, and are formed on the sleeves 163 and 173.
a and 173a. Sleeves 163 and 1
A groove is formed in the outer periphery of 73 in the axial direction, and pins 166 and 176 are fitted in this groove. Thus, the sleeves 163 and 173 cannot rotate but can move in the axial direction. Also, the rotation shafts 150a, 152 are provided at the ends of the spools 164, 174 on the side opposite to the side where the springs 165, 175 are provided.
a, 154a and 156a are converted into axial movement amounts through the precess cams 167 and 177 and links 167a and 177a, and the axial movement amounts are introduced as feedback amounts. Has become. That is, the rotating shafts 150a, 152a, 15
4a and 156a is proportional to the amount of inclination of the first friction roller 30 and the second friction roller 36,
Feeding back the rotation amounts of the first friction roller 30 and the second friction roller 50a, 152a, 154a and 156a
The amount of inclination of the friction roller 36 is fed back. In addition. The rotation shafts on which the precess cams 167 and 177 are mounted may share one rotation shaft without being different rotation shafts. The spools 164 and 174 are provided with two land portions 164a and 164b, and 174a and 174b, respectively.
64a and 164b, and 174a and 174b, as the spools 164 and 174 move, the introduction port 16
8 and 178 to the first port 1
68a and 178a and second ports 168b and 178
b. The switching valve 80 includes a spool 82 that is slidably fitted in a valve body 81. The spool 82 is pressed to the left in the drawing via a spring 83 and the left end of the spool 82 in the drawing. , A switching signal is input via forward / reverse detection means 90 (see FIG. 3). The valve body 81 has an inlet port 1 for the first and second control valves 160 and 170.
68 and 178, ports 81a, 81b, 81c, 81d, 81e and 81f connected to the first ports 168a and 178a and the second ports 168b and 178b, respectively.
52, 154 and 156, the first control valve 16
Ports 81g and 81h for supplying hydraulic pressure controlled by the zero or second control valve 170 are formed, and a line pressure port 81i is further formed.
A line pressure in which the discharge pressure from the hydraulic pump 84 is regulated via a regulator valve 85 is introduced into the line pressure port 81i. Hydraulic actuators 150, 15
In 2, 154 and 156, an upper chamber A and a lower chamber B are respectively constituted by pistons. When a higher oil pressure is supplied to the upper chamber A than to the lower chamber B, the rotating shaft 150a,
152a, 154a and 156a are moved downward. Conversely, when a higher oil pressure is supplied to the lower chamber B than to the upper chamber A, the rotating shafts 150a, 152a, 154a and 15
6a is moved upward. On the other hand, the hydraulic actuators 150 and 152 of the first friction roller 30 and the hydraulic actuators 154 and 156 of the second friction roller 36 respectively have one upper chamber A and the other lower chamber B, and one lower chamber B and the other upper chamber. The side chamber A crosses and communicates with each other, and the hydraulic actuators 150 and 154 and the hydraulic actuators 152 and 156 are driven in opposite directions. Hydraulic actuators 150 and 154
And the lower chambers B of the hydraulic actuators 152 and 156 are connected to the port 81g via the circuit 86, and the lower chamber B of the hydraulic actuators 150 and 154 and the upper chamber A of the hydraulic actuators 152 and 156 are connected to each other. , A circuit 87 and a port 81h.
The spool 82 of the switching valve 80 is set at the upper half position in the drawing in the forward state, and the line pressure port 81i and the port 8
1a, 81e, 81g, 81c, and 81h are respectively connected. The line pressure is the first control valve 1
It is supplied to 60 inlet ports 168. First and second ports 168a and 168 of first control valve 160
The hydraulic pressure generated in 8b is supplied to hydraulic actuators 150, 152, 154 and 156 via circuits 86 and 87, respectively. In this state, the ports 81b, 81d, and 81f communicating with the second control valve 170 are all shut off. On the other hand, in reverse
The spool 82 of the switching valve 80 is set at the lower half position in the figure, and the ports 81b, 81d, and 81f that communicate with the second control valve 170 are ports 81i, respectively.
81g and 81h, the line pressure is supplied to the introduction port 178 of the second control valve 170, and the hydraulic pressure generated at the first and second ports 78a and 78b is supplied to the hydraulic actuator via the circuits 86 and 87. 150, 152, 154 and 156. In this state, all the ports 81a, 81c and 81e communicating with the first control valve 160 are shut off.

FIG. 3 shows forward / backward detecting means 90. The forward / reverse detection means 90 includes an intermediate shaft 62, a plunger 200,
A collar 202 having a flange portion 202a;
4 and a sensor gear 206. The intermediate shaft 62 is hollow, and the plunger 200
Are movably inserted in the axial direction. A collar 202 is fitted on the outer periphery of the intermediate shaft 62 so as to be movable in the circumferential direction. As shown in FIG. 4, the collar 202 is formed with a second elongated hole 210 that is inclined upward and leftward in FIG. 4 with respect to the axial direction. In the intermediate shaft 62, a first elongated hole 212 extending in the axial direction is formed at a position corresponding to the second elongated hole 210 of the collar 202, as shown in FIG. As shown in FIG.
A pin 204 that is guided by these and is movable in the axial direction is inserted into the elongated hole 210 and the first elongated hole 212 of the intermediate shaft 62, thereby moving the collar 202 in the circumferential direction with respect to the intermediate shaft 62. Is regulated. The pin 204 is fixed by being pressed into a pin hole 214 formed in the plunger 200 , and the tip of the plunger 200 is connected to the spool 82 of the switching valve 80. A sensor gear 206 is fitted around the outer periphery of the collar 202. The sensor gear 206 is pressed against the flange 202 a of the collar 202 by a disc spring 208.
As a result, the sensor gear 206 frictionally couples with the collar 202, and while no more than a predetermined sliding force acts on the collar 202,
It can rotate integrally with the collar 202 by friction. The sensor gear 206 is meshed with the drive gear 60 together with the driven gear 64. Sensor gear 206 is driven gear 64
The number of teeth is slightly larger than that.

Next, the operation of this embodiment will be described.
At the time of forward movement, as shown in FIG. 6, the pin 204 is connected to the first elongated hole 212 of the intermediate shaft 62 and the second elongated hole 2 of the collar 202.
10 is located at the right end in FIG. 6, and accordingly, the plunger 200 is also positioned as shown in the lower half of FIG.
It is located at the middle right end. Therefore, since the pin 204 does not press the spool 82 of the switching valve 80, the switching valve 80 is in the forward state shown in the lower half of FIG. The intermediate shaft 62 is rotated in the direction of the arrow in FIG. As a result, the driven gear 64 rotates integrally with the intermediate shaft 62, but the sensor gear 206 meshing with the driving gear 60 has a slightly larger number of teeth than the driven gear 64, and thus has a lower rotation speed than the driven gear 64. Rotate. As a result, the intermediate shaft 62 and the collar 202 rotate relatively for a while, so that the first elongated hole 2
12 and the pin 204 located at the right end in FIG. 6 of the second elongated hole 210 of the collar 202, as shown in FIG.
7 gradually moves to the left end in FIG. 7 of the first elongated hole 212 of the intermediate shaft 62 and the second elongated hole 210 of the collar 202. At this time, the plunger 200 moves to the left in FIG. 3 integrally with the pin 204, and enters the state shown in the upper half of FIG. As a result, the pin 204 is moved via the plunger 200 to the spring 8 of the switching valve 80.
Since the spool 82 is pressed against the elastic force of No. 3, the switching valve 80 is in the state of reverse movement shown in the upper half of FIG. 3. When the pin 204 moves to the left end in FIG. 7, the sensor gear 206 causes the disc gear 208 and the collar 20 to move.
2, and acts as a backlash-less gear from here on, and the drive gear 60 and the driven gear 64
The hitting noise between gears when they are engaged with each other is reduced. In the above embodiment, the number of teeth of the sensor gear 206 is larger than the number of teeth of the driven gear 64. However, the present invention is not limited to this. The number of teeth of the sensor gear may be smaller than the number of teeth of the driven gear. . In this case, the inclination direction of the second long hole of the collar is
It is formed in the opposite direction to the above embodiment.

[0011]

According to the friction wheel type continuously variable transmission according to the first aspect, the collar is fitted to the outer periphery of the intermediate shaft so as to be relatively rotatable, and the first elongated hole extending in the axial direction is provided on the intermediate shaft. Are formed at respective positions corresponding to the elongated holes with second elongated holes inclined at a predetermined angle from the axial direction. The first and second elongated holes are guided relative to each other by the relative rotation of the first and second elongated holes and move in the axial direction. Insert a possible pin, engage a drive gear that rotates integrally with the intermediate shaft, and a sensor gear that rotates together with the collar and that has a different number of teeth from the drive gear. The collar and the collar are relatively rotated to move the pin in the axial direction, and press the spool of the switching valve via the plunger to switch between the forward state and the reverse state. For this reason, since a large frictional force does not occur between the pin and the first and second elongated holes, wear of the pin, the collar, and the intermediate shaft can be reduced. As a result, the durability of the forward / backward detecting means is improved, and the switching valve can be switched reliably. Further, since there is no need to provide a one-way clutch or the like, the number of parts can be reduced. Further, since the sensor gear functions as a backlash-less gear, it is possible to prevent the gears from hitting each other due to the transmission of the driving force by the gears. Also,
According to the friction wheel type continuously variable transmission according to the second aspect, in addition to the above effects, when the sensor gear is frictionally coupled to the collar, the sensor gear is clamped and supported by the flange portion provided on the collar and the disc spring. Therefore, an increase in the axial dimension can be suppressed to a minimum.

[Brief description of the drawings]

FIG. 1 is a skeleton diagram of a friction wheel type continuously variable transmission.

FIG. 2 is a layout diagram of a shift control main part.

FIG. 3 is a cross-sectional view showing forward / backward detection means.

FIG. 4 is a view showing a second elongated hole of a collar.

FIG. 5 is a view showing a first elongated hole of an intermediate shaft.

FIG. 6 is a diagram showing a state near a collar fitted to an intermediate shaft.

FIG. 7 is a view showing a moving state of a pin.

[Explanation of symbols]

 12 First input disk 13 Forward / reverse switching mechanism 14 First output disk 16 Second input disk 18 Second output disk 30 First friction roller 36 Second friction roller 62 Intermediate shaft 64 Follower gear 80 Switching valve 90 Forward / reverse detection means 160 First control valve (transmission control device) 170 Second control valve (transmission control device) 200 Plunger 202 Collar 204 Pin 206 Sensor gear 210 Second elongated hole 212 First elongated hole

Claims (2)

(57) [Claims] An input disk (12, 16), an output disk (14, 18), a drive gear (60) that rotates integrally with the output disk (14, 18), and a toroid formed by the disks. A friction wheel transmission mechanism having friction rollers (30, 36) arranged in frictional contact with both disks in a groove of a shape, and controlling the contact position of the friction rollers (30, 36) with both disks to change the speed. Transmission control devices (160, 17) for controlling the ratio
0), forward / reverse switching mechanism (13) provided on the input side of the friction vehicle transmission mechanism, forward / backward detection means (90) for determining whether the vehicle is in a forward state or a reverse state, and a shift control device. A switching valve (80) capable of switching the forward / backward control state of (160, 170) by moving the spool (82); and a friction wheel type continuously variable transmission, comprising: The driven gear (6) meshed with the drive gear (60)
4), and rotates integrally with the driven gear (64), and has a hollow intermediate shaft (62) in which the first elongated hole (212) is formed in the axial direction. A collar (202) that is rotatably fitted and has a second slot (210) formed at a position corresponding to the first slot (212) and inclined at a predetermined angle with respect to the axial direction; 202), and the sensor gear (20) having a number of teeth different from the number of teeth of the driven gear and being engaged with the drive gear (60).
6), a plunger (200) which is axially movably fitted into the hollow portion of the intermediate shaft (62), and is fixed to the plunger, and has a second elongated hole (210) of the collar (202); 62) Insert into the first slot (212)
And the driven gear and the sensor gear (6
A pin (204) that is movable in the axial direction by the relative rotation of the intermediate shaft (62) and the collar (202) by a rotation angle corresponding to the difference in the number of teeth (4, 206). The switching valve (80) is provided with a plunger (20) based on the axial movement of the pin (204) of the forward / reverse detecting means (90).
0), the spool (82) interposed in the switching valve (80) moves, thereby switching to one of a forward state and a reverse state. transmission. 2. A collar (202a) is formed on the collar (202), and a flange (202) is formed on the outer periphery of the collar (202).
A disc spring (208) is axially supported so as to oppose a), and the sensor gear (206) has a flange portion (202a).
2. The friction wheel type continuously variable transmission according to claim 1, wherein the friction wheel is continuously supported by the pinion and the disc spring (208) to frictionally engage with the collar (202).