JPH0338463B2 - - Google Patents

Description

Detailed Description of the Invention (Industrial Application Field) The present invention provides a V-shaped or
A type of belt-type vehicle that stretches a belt with a trapezoidal cross section and changes the rotational speed ratio between two variable pulley shafts by changing the radial position of the point where the belt contacts each variable pulley. The present invention relates to an automatic transmission using a step-change transmission.

(Prior art) Conventionally, fixed flanges were fixed to the input shaft connected to the prime mover and the output shaft connected to the driven part, and movable flanges were provided on both shafts so as to be slidable in the axial direction. A primary pulley is formed on the side, and a secondary pulley is formed on the output shaft side, a V-belt is stretched across both pulleys, and the movable flanges on both shafts are moved toward the corresponding fixed flange. Continuously variable transmissions that are biased by the force of a spring or the like are known.

Then, a metal block having an inclined side surface corresponding to the conical engagement surfaces of the fixed flange and the movable flange constituting the pulley is connected to a large number of connected engagement surfaces using a metal belt inserted into a slit opened in the side surface. With the development of synchronizing belts, it became possible to increase the durability of continuously variable transmissions.The movable flanges of each of the above pulleys were pressed toward the fixed flanges by a hydraulic servo to increase the transmitted torque, resulting in high output. Attempts have been made to use it as a continuously variable transmission in a vehicle equipped with a prime mover.

The continuously variable transmission is equipped with a fluid transmission device, and the rotation generated by the engine is transmitted to the continuously variable transmission via the fluid transmission device. The fluid transmission device includes a fluid coupling that only transmits torque and a torque converter that amplifies the torque.However, there is a need to reduce the transmitted torque of the belt, so a fluid coupling that does not amplify the torque is sometimes used. many.

The fluid coupling has a pump impeller, a turbine runner, and a direct coupling clutch, and the rotation generated by the engine is transmitted to the pump impeller to form a fluid swirl, which rotates the turbine runner. and is transmitted to the input shaft.

(Problems to be Solved by the Invention) However, in the belt type continuously variable automatic transmission having the above configuration, the input shaft for inputting torque to the continuously variable transmission is directly supported by the impeller hub of the pump impeller. Therefore, the support part is often located behind the input shaft, that is, on the side away from the engine.

In that case, the center of rotation of the turbine runner will be located at a location that protrudes forward from the support portion, and the turbine runner will be in a cantilever supported state. Therefore, a "wandering" phenomenon occurs in the turbine runner, causing interference between the turbine runner and the impeller case and between the turbine runner and the damper, resulting in a loss of durability of the turbine runner.

In addition, in the belt type continuously variable automatic transmission having the above configuration, an oil passage for engaging the direct coupling clutch;
Oil passage for releasing the direct coupling clutch, oil passage for supplying lubricating oil, brake for the forward/reverse switching mechanism,
It is necessary to form various oil passages such as an oil passage for supplying servo oil to the clutch and an oil passage for supplying servo oil to the movable pulley, but it is necessary to form these oil passages in the input shaft or intermediate shaft. As a result, the diameter of each shaft hole oil passage becomes small, making it impossible to secure a sufficient amount of oil.

In this case, there may be a delay in the operation of the direct coupling clutch, forward/reverse switching mechanism, and continuously variable transmission, and each element may overheat due to lack of lubrication.

The present invention solves the above-mentioned problems of the conventional belt-type continuously variable transmission, suppresses interference occurring between the turbine runner and the impeller case, and between the turbine runner and the damper, and improves the durability of the turbine runner. Another object of the present invention is to provide a belt-type continuously variable automatic transmission that enables quick operation of a direct coupling clutch, forward/reverse switching mechanism, and continuously variable transmission, and provides good lubrication.

(Means for Solving the Problems) In order to solve the above problems, the present invention provides a pump impeller that is connected to the output side of the prime mover and receives the torque generated by the prime mover, and a pump impeller that is connected to the output side of the prime mover and receives the torque generated by the prime mover. , a turbine runner that receives the torque of the pump impeller via fluid, and a turbine runner that is detachably disposed between the pump impeller and the turbine runner;
A fluid coupling is provided which has a locking device which, when engaged, connects the output side of the prime mover directly to the turbine runner, via which the input shaft is connected to the output side of the prime mover.

An intermediate shaft is supported concentrically and rotatably relative to the input shaft, one end of which is supported concentrically and rotatably relative to the input shaft, and the other end rotatably supported by the housing.

A sleeve is disposed between the input shaft and the hub of the pump impeller, and a sliding bearing is disposed inside the front end of the sleeve, and a pair of seal rings is disposed inside the rear end.

An output shaft is disposed parallel to the input shaft and the intermediate shaft, a fixed flange is fixed concentrically to the intermediate shaft, a movable flange is provided to be slidable in the axial direction with respect to the fixed flange, and a primary pulley is provided. is configured. Further, a fixed flange is fixed concentrically to the output shaft, and a movable flange is provided to be slidable in the axial direction with respect to the fixed flange, thereby forming a secondary pulley.

A belt is stretched between the primary pulley and the secondary pulley, and by changing the effective drive radius position for both pulleys, the rotational speed ratio between the intermediate shaft and the output shaft can be changed.

Further, a forward/reverse switching mechanism is provided between the input shaft and the intermediate shaft to switch the direction of rotation between the two shafts.

Furthermore, an oil pump is disposed on a separation wall between the fluid coupling and the forward/reverse switching mechanism and is rotatably driven by a prime mover, and an oil pump is connected to the oil pump through an oil hole formed in the sleeve. It is formed between the input shafts and is sealed with a sliding bearing at the front and a seal ring at the rear.
and a lockup release pressure supply oil passage that communicates with the input shaft shaft hole passage through an oil hole formed in the input shaft, and a lockup connection that is formed between the sleeve and the hub of the pump impeller and communicates with the oil pump. It has a joint pressure supply oil passage and an intermediate shaft hole passage that communicates with the oil pump through the pair of seal rings and supplies oil to the forward/reverse switching mechanism.

The input shaft is supported at two points via the front end of the sleeve and the front end of the intermediate shaft, and is rotatably supported at the front end of the sleeve near the rotation center of the turbine runner.

In addition, the oil supplied to the forward/reverse switching mechanism is
It is supplied to the planetary gear or frictional engagement element of the forward/reverse switching mechanism.

Inside the input shaft, there is a shaft hole oil passage for supplying lock-up release oil, inside the intermediate shaft there is a shaft hole oil passage for supplying servo oil pressure for the movable flange, and inside the intermediate shaft there is a shaft hole oil passage for supplying oil for lock-up release. Shaft hole oil passages for supplying oil are arranged independently, and the shaft hole oil passages are arranged on the same line within the input shaft and the intermediate shaft.

(Operation and Effects of the Invention) According to the present invention, the sleeve is disposed between the hub of the pump impeller and the input shaft as described above,
The input shaft is supported at two points, one of which is rotatably supported by the sleeve near the rotation center of the turbine runner.

Therefore, the center of rotation of the turbine runner and the support portion of the input shaft coincide, resulting in a stable support state. Therefore, the "wandering" phenomenon does not occur in the turbine runner, and there is no interference between the turbine runner and the impeller case and between the turbine runner and the damper, improving the durability of the turbine runner.

A seal ring is provided between the input shaft and the sleeve for separately supplying oil supplied from the oil pump to the forward/reverse switching mechanism and for lock-up release, and a seal ring is provided between the input shaft and the sleeve. A sliding bearing is provided to support the lock-up, and the lock-up release oil passage is formed between the seal ring and the sliding bearing, and the oil supplied to the forward/reverse switching mechanism is supplied to the forward/reverse switching mechanism. Since the lubricant is supplied to the planetary gear or frictional engagement element of the lubricant, there is no need to form a special oil passage for supplying oil, and the size of the belt-type continuously variable transmission can be reduced.

A shaft hole oil passage for supplying lock-up release oil in the input shaft, a shaft hole oil passage for supplying servo oil pressure for the movable flange in the intermediate shaft, and oil for the forward/reverse switching mechanism in the intermediate shaft. The shaft hole oil passages for supplying the oil are arranged independently, and the shaft hole oil passages are arranged on the same line in the input shaft and the intermediate shaft, so that each of the shaft hole oil passages The diameter can be increased. Therefore, the responsiveness can be improved when the lockup is released, when the movable flange is moved, when the forward/reverse switching mechanism is switched, etc.

(Example) Hereinafter, the belt type continuously variable automatic transmission of the present invention will be described in detail with reference to the drawings.

FIG. 1 is a schematic diagram of a belt-type continuously variable automatic transmission according to an embodiment of the present invention, FIG. 2 is a sectional view thereof, and FIG. 3 is a sectional view of a main part.

In the figure, the output shaft of a prime mover 1 is connected to a pump impeller 3 of a fluid coupling 2, and the torque generated by the prime mover 1 is transmitted to the pump impeller 3. As the pump impeller 3 rotates, the torque is transmitted to the turbine runner 4 via fluid, and is sent to the input shaft 7 of the transmission connected to the turbine runner 4. A lock-up device is disposed between the pump impeller 3 and the turbine runner 4 in a detachable manner. Therefore, the piston 5 is slidable relative to the turbine runner 4 or the input shaft 7.
is provided, and when engaged, the friction plate 6 fixed annularly on the piston 5 and the housing are locked, and the output side of the prime mover 1 is directly connected to the turbine runner 4 side.

The transmission is a planetary gear and a belt type transmission 9
Consisting of The belt type transmission 9 includes a primary pulley 10, a secondary pulley 11, and a belt 12.
It is made up of

The primary pulley 10 has a fixed flange 14 concentrically and integrally disposed on the intermediate shaft 13 of the transmission, and a movable flange 15 disposed on the intermediate shaft 13 so as to be slidable in the axial direction thereof.

On the other hand, the secondary pulley 11 is connected to the output shaft 16
A fixed flange 17 is provided concentrically and integrally with the output shaft 16, and a movable flange 18 is provided on the output shaft 16 so as to be slidable in the axial direction thereof.

In addition, the belt 12 is attached to the primary pulley 1
A large number of metal blocks 21 are formed in the thickness direction with inclined surfaces 19 formed on both sides to engage with the V-shaped engagement surfaces of the zero and secondary pulleys 11, and slits 20 opened in the inclined surfaces. Arrange the above slit 2
Endless V bound with an endless metal band inserted into 0
It is belt-shaped (for example, JP-A-54-
This has become publicly known due to publication of No. 52253, etc. ), the belt 12 is stretched between the primary pulley 10 and the secondary pulley 11.

A cylinder 22 is fixed to the intermediate shaft 13 and is fluid-tightly engaged with an annular member 151 fixed to the outer periphery of the movable flange 15. By supplying pressure oil to the cylinder chamber 23 of the cylinder 22, the movable flange 15 A hydraulic servo is configured to slide the metal block 21 in the direction approaching the fixed flange 14, and the metal block 21 constituting the belt 12 is clamped between the movable flange 15 and the fixed flange 14. In addition, output shaft 1
6, a coil spring 25 is disposed between the movable flange 18 and a cylinder 24 that fluidly engages with the cylindrical member 181 fixed to the movable flange 18, and pressure oil is supplied to the cylinder chamber 26 of the cylinder 24. This constitutes a hydraulic servo that slides the movable flange 18 in a direction approaching the fixed flange 17 together with the biasing force of the coil spring 25, and moves the metal block 21 constituting the belt 12 between the movable flange 18 and the fixed flange 17. be clamped between.

Movable flange 15 of cylinder 22 in primary pulley 10 formed on intermediate shaft 13
The pressure receiving area on the side is made larger than the pressure receiving area on the movable flange 18 side of the cylinder 24 in the secondary pulley 11 formed on the output shaft 16.

When the pressure fluid in both cylinder chambers 23 and 26 is drained, the biasing force of the coil spring 25 acts on the secondary pulley 11 side, and the primary
Since no force acts on the pulley 10 side, the movable flange 18 of the secondary pulley 11 is close to the fixed flange 17, and the belt 12 is moved to the secondary pulley 11.
The belt 12 can be positioned diametrically outermost of the pulley 11, and in the primary pulley 10, the belt 12 can be positioned closest to the axis of the intermediate shaft 13. In this state, from the intermediate shaft 13 to the output shaft 16
The deceleration rate and torque ratio of the rotational speed transmitted to is the largest.

When the intermediate shaft 13 is connected to the input shaft 7 and pressure oil is introduced into the hydraulic servo cylinder chambers 23 and 26, the belt 12 is clamped between the fixed and movable pulleys of the primary pulley 10 and the secondary pulley 11, respectively. At the same time, the rotation of the input shaft 7 is transmitted to the output shaft 16. At this time, since the pressure receiving area on the movable flange 15 side of the primary pulley 10 is large, if the same hydraulic pressure is introduced into the cylinder chambers 23 and 26, the movable flange 15 of the primary pulley 10 will move around the belt 12 as an axis. Since the pushing force in the direction is greater than the pushing force in the axial direction of the movable flange 18 of the secondary pulley 11, the belt 12 is pushed outward in the radial direction of the intermediate shaft 13,
The effective radius that engages with the primary pulley 10 is expanded, and the effective radius that engages with the secondary pulley 11 is decreased.

In other words, continuously variable transmission is performed in which the deceleration rate of the rotational speed transmitted from the intermediate shaft 13 to the output shaft 16 is reduced and the torque ratio is reduced.

Here, the belt 12 is connected to both pulleys 10 and 11.
In order to maintain a fixed position, it is necessary to balance the pressures acting on the movable flanges 15 and 18. Therefore, the hydraulic pressure supplied to the cylinder 23 on the primary pulley 10 side is
By lowering the hydraulic pressure than the hydraulic pressure supplied to the side cylinder 26, the gear ratio (torque ratio) is maintained at a predetermined value at the above-mentioned balanced position.

A gear 27 fixed to the output shaft 16 meshes with a gear 29 on a counter shaft 28 , and a gear 291 that rotates together with the gear 29 meshes with a gear 31 provided on a housing of a differential gear device 30 . Form a reduction gear train. The rotation of the output shaft 16 is decelerated by the reduction gear train, and the rotation of the output shaft 16 is decelerated.
0 to the vehicle axles 32, 33.

The input shaft 7 and the intermediate shaft 13 are arranged concentrically within a housing 100 of the transmission, and one end of the intermediate shaft 13 is inserted into a hollow shaft 71 formed at one end of the input shaft 7 to receive input from the bush 101. The intermediate shaft 13 is supported by the shaft 7, and the other end of the intermediate shaft 13 is rotatably supported by a bearing 102 with respect to the housing 100.

The input shaft 7 has one end rotatably supported by a bearing 103 on the housing 100 at a position close to or at the same position as the bush 101 on the outer periphery of the shaft 7.

The planetary gear includes a sun gear 81 disposed concentrically with the input shaft 7 and on the hollow shaft 71, a double planetary pinion 82, a ring gear 83, and a planetary carrier 84 that rotatably supports the planetary pinion 82. Sun gear 81 is formed integrally with hollow shaft 71 , and planetary pinions 82 mesh with each other, one of which meshes with sun gear 81 and the other with ring gear 83 .

The ring gear 83 includes a drum 85 and a transmission housing 100 that are integrally fixed to the ring gear 83.
A multi-plate brake 86 is provided between the cylinder 87 and the piston 8 provided in the housing 100.
Housing 1 is activated by the hydraulic servo consisting of 8
It is controlled to be locked at 00 or to be freely rotatable.

Further, the planetary carrier 84 is spline-engaged with a hub 89 fixed to the outer circumference of the fixed flange 14 fixed to the intermediate shaft 13.
It can be rotated together with 3.

A clutch hub 72 and a hub 89 of the fixed flange 14 are provided at one end of the hollow shaft 71 of the input shaft 7.
A multi-disc clutch 90 is constructed between the
The multi-plate clutch 90 is actuated by the operation of a hydraulic servo consisting of a cylinder 91 formed by the back surface of the fixed flange 14 and the hub 89 and a piston 92 sliding in the cylinder 91.
3 is detachably connected to the input shaft 7.

As shown in FIG.
The movable flanges 15 and 18 of the secondary pulley 11 are integrally formed with cylindrical bases 152 and 182 that slide with respect to the intermediate shaft 13 and the output shaft 16, and the cylindrical bases 152 and 182 are A long groove oil passage 131 is partially in liquid-tight contact with the outer circumferential surfaces of the intermediate shaft 13 and the output shaft 16, and is partially carved in the outer circumferential surface of the intermediate shaft 13 and the output shaft 16 in the axial direction. It is supported by spheres 93 and 94 inserted in 161.

An oil passage 105 in the housing 100 is connected to the cylinder chamber 23 of the hydraulic servo of the primary pulley 10.
Pressure oil is supplied and discharged through the shaft hole oil passage 132 of the intermediate shaft 13, the oil hole 133 drilled in the intermediate shaft 13, the long groove oil passage 131, and the oil hole 153 bored in the cylindrical base 152, and The cylinder 26 of the hydraulic servo of the pulley 11 has an oil passage 10 in the housing 100.
6. Pressure oil is supplied through the shaft hole oil passage 162 of the output shaft 16, the oil hole 163 drilled in the output shaft 16, the long groove oil passage 161, and the oil hole 183 bored in the cylindrical base 182, or is discharged in the opposite direction.

Pressure oil is supplied to or discharged from a hydraulic servo cylinder 87 (FIG. 1) that operates a multi-disc brake 86 through an oil passage 107 and an oil hole 109 in the housing 100, and hydraulic pressure that operates a multi-disc clutch 90. Pressure oil is supplied to and discharged from the cylinder 91 of the servo (FIG. 1) through an oil passage 108 in the housing 100, a shaft hole oil passage 119 in the intermediate shaft 13, and an oil hole 134 drilled in the intermediate shaft 13. . Note that 99 in the figure is an embolus inserted into the shaft hole oil passages 118, 119, 132, and 162.

Note that although only an embodiment equipped with a fluid coupling is shown in the drawings, a torque converter consisting of a pump impeller, a turbine runner, and a stator supported in a housing by a one-way clutch may be used in place of the fluid coupling. In this case, as is well known, the pump impeller is connected to the output side of the prime mover, and the turbine runner is connected to the input shaft of the transmission. In addition to the fluid coupling described above, a conventional coupling such as a dry or wet clutch may be constructed between the output side of the prime mover and the input shaft.

Next, as shown in FIG. 3, a cylindrical sleeve 112 extending in the axial direction is disposed between the input shaft 7 and the impeller hub 3a of the pump impeller 3.

The sleeve 112 has its rear end connected to the housing 1.
The front end thereof extends near the rotation center of the fluid coupling 2 and is close to the hub 4a of the turbine runner 4. A sliding bearing portion, such as a bush 110, is formed between the front end of the sleeve 112 and the input shaft 7, and the input shaft 7 is rotatably supported by the sliding bearing portion. Ru.

An oil passage 107 is formed in the separation wall 100a, and an oil pump (not shown) is housed therein. The oil supplied from the oil pump flows through the oil hole 11 formed in the sleeve 112.
5. The oil is sent to the shaft hole oil passage 119 via the oil hole 201 formed in the input shaft 7.

In order to form an oil passage between the oil holes 115 and 201, a seal ring 114 is disposed between the sleeve 112 and the input shaft 7. The seal ring 114
are arranged so as to surround the oil hole 201 from both sides.

A lock-up release pressure supply oil passage 111 is formed between the seal ring 114 and the sliding bearing.
1. Oil for lockup release is supplied through the oil hole 202 and the shaft hole oil passage 118.

In addition, the sleeve 112 and the pump impeller 3
A lock-up engagement pressure supply oil passage 116 is further formed between the hubs, and oil is supplied to the inside of the fluid coupling 2 via the lock-up engagement pressure supply oil passage 116.

The shaft hole oil passages 118, 119, and 132 are arranged in a line on the same line within the input shaft 7 and the intermediate shaft 13, respectively, and are independent from each other.

4 and 5 show another embodiment in which a modification of the forward/reverse switching mechanism 8 is provided.

The gear train shown in FIG. 4 includes a sun gear 81, a double planetary pinion 82, a ring gear 83, and a planetary carrier 84 that rotatably supports the double planetary pinion 82, which are arranged concentrically on the intermediate shaft 13. Consists of planetary gears. The planetary carrier 84 is fixed to the input shaft 7, and a hydraulic servo consisting of a cylinder 91 and a piston 92 is disposed between the planetary carrier 84 and the hub 89 of the fixed flange 14. A plate clutch 90 is constructed.

In addition, the ring gear 83 and the housing 100
A multi-disc brake 86 is configured between the two, which is engaged and disengaged by the operation of a hydraulic servo consisting of a cylinder 87 and a piston 88.

In the gear train shown in FIG. 5, a sun gear 81' is disposed on a hollow shaft 71 concentrically with the input shaft 7, and at least one planetary pinion 8 meshes with the sun gear 81' and a ring gear 83'.
2' and a planetary carrier 84' that rotatably supports the planetary pinion 82'.

Hub 8 of ring gear 83' and fixed flange 14
Between 9 and 9 is a multi-disc clutch 90 that is engaged and disengaged by a hydraulic servo consisting of a cylinder 91 and a piston 92.
A cylinder 87 and a piston 8 are arranged between the planetary carrier 84' and the housing 100.
A multi-disc brake 86 is constructed which is engaged and disengaged by the operation of a hydraulic servo.

In the belt type continuously variable automatic transmission having the above configuration, the intermediate shaft 13, which is arranged on the same axis as the input shaft so as to be connected to the prime mover, has one end rotatably supported by the input shaft 7. At the same time, the other end is rotatably supported by the housing 100. A primary pulley 10 is constructed on the intermediate shaft 13 by a fixed flange 14 concentrically fixed to the shaft 13 and a movable flange 15 that is slidable in the axial direction with respect to the flange 14. The secondary pulley 11 is composed of a fixed flange 17 that is fixed concentrically and a movable flange 18 that is slidable in the axial direction with respect to the flange 17.
A belt 12 is stretched between the primary pulley 10 and the secondary pulley 11, and by changing the effective drive radius position for both pulleys 10 and 11, the rotational speed ratio between the intermediate shaft 13 and the output shaft 16 is changed. It's like this.

The input shaft 7 and the intermediate shaft 13 are made freely engageable and disengageable by a clutch 96.
A forward/reverse switching mechanism 8 such as a planetary gear is provided above, and the input side of the forward/reverse switching mechanism 8 is connected to the input shaft 7.
The output side of the forward/reverse switching mechanism 8 is connected to the intermediate shaft 1.
3, and a brake 86 for reverse operation of the forward/reverse switching mechanism 8 is formed between the constituent parts of the forward/reverse switching mechanism 8 and the housing 100. Input shaft 7 and intermediate shaft 1
By engaging the clutch 90 between 3 and releasing the operating brake 86 of the forward/reverse switching mechanism 8, the input shaft 7 and the intermediate shaft 13 are directly connected, and the drive torque of the prime mover is transferred directly from the input shaft 7 to the primary - When the clutch 90 is released to disconnect the input shaft 7 and the intermediate shaft 13 and the brake 86 is activated, the rotation on the input side is transferred to the primary through the forward/reverse switching mechanism 8.・Pulley 1
0 as a rotation in the opposite direction, the rotation is transmitted to the output shaft 16 as a rotation in the opposite direction.

Various mechanisms such as a hydraulic servo for engaging or disengaging the clutch 90 can be provided at the fixed flanges 14 and 17, so that the axial length of the input shaft 7 and the intermediate shaft 13 can be shortened. can do.

Moreover, the operating pressure oil can be directly supplied to the cylinder 91 via the shaft hole oil passage 132 of the intermediate shaft 13 and passages bored in the fixed flanges 14 and 17, and a separate hydraulic servo is installed on the outer periphery of the intermediate shaft. The configuration can be made extremely simple compared to the case where it is provided.

The forward/reverse switching mechanism 8 includes a double planetary pinion 82, a sun gear 81, and a ring gear 8.
When the reversing brake is activated, reverse rotation with the required reduction ratio is obtained, and a high-torque reverse gear can be configured as an automatic transmission for automobiles.

When the planetary gear described above is used in the forward/reverse switching mechanism 8, the sun gear 81 that engages the intermediate shaft 13 with the planetary carrier 84 that rotatably supports the double planetary pinion 82 is engaged with the input shaft 7, and the ring gear 83 to and from the housing 100 using the brake 86, the sun gear 81 can be formed integrally with the input shaft 7, and the planetary carrier 84 can be placed at a position spaced apart from the input shaft 7 in the radial direction. Therefore, an annular hub 89 is formed concentrically with the intermediate shaft 13 on the fixed flanges 14 and 17 of the primary pulley 10, and the planetary carrier 84 is spline-engaged with the annular hub 89. This makes it possible to very easily engage the output side of the planetary gear with the fixed flanges 14, 17 of the primary pulley 10, and to reduce the hydraulic pressure of the clutch 90 provided between the fixed flange and the end of the input shaft 7. The servo cylinder can be constructed using the annular hub 89 described above.

When the clutch 90 is of a multi-plate type,
By disposing a clutch hub formed at the free end of the input shaft 7 inside the annular hub 89 in the diametrical direction, a friction plate for the clutch 90 is supported between the two hubs, and the fixed flanges 14 and 17 The clutch 90 can be configured to be actuated by a hydraulic servo formed using the annular hub 89, resulting in an extremely compact structure.

Further, the input shaft 7 disposed on the same axis as the intermediate shaft 13 is formed with a hollow shaft portion, and the end portion of the intermediate shaft 13 is rotatably supported within the hollow shaft 13. By disposing the forward/reverse switching mechanism 8 on the hollow shaft portion 71 of the input shaft 7, the total axial length of the shaft including the primary pulley 10 can be shortened.

A bushing 101 that supports the intermediate shaft 13 within the hollow shaft portion 71 of the input shaft 7 is provided near the tip of the intermediate shaft 13, and a bearing 102 that supports the input shaft 7 is provided near a diametrically outward position of the bush 101. By providing the bearing 1 that supports the other end of the intermediate shaft 13
02, the intermediate shaft 13 and the input shaft 7 can be supported with respect to the housing 100 by three bearings, the axial length can be shortened, and the support structure using the bearings can be simplified.

The present invention provides an axially variable primary pulley 10 formed on the intermediate shaft 13 between the intermediate shaft 13 and the output shaft 16, an axially variable secondary pulley 11 formed on the output shaft 16, and the primary - It is spanned between the pulley 10 and the secondary pulley 11, and by changing the effective drive radius position for both pulleys 10 and 11, the rotational speed ratio between the intermediate shaft 13 and the output shaft 16 is changed steplessly. Since it is equipped with a belt type continuously variable transmission, during forward rotation, the input shaft 7 and the intermediate shaft 13
The engine is started by engaging the clutch 90 provided between the clutches and the brake 86 for operating the forward/reverse switching mechanism 8 in the case of reverse rotation, thereby continuously changing and converting the rotational speed and torque of the input shaft 7. and can be transmitted to the output shaft 16.

Note that the present invention is not limited to the above-described embodiments, and various modifications can be made based on the spirit of the present invention, and these are not excluded from the scope of the present invention.

For example, the forward/reverse switching mechanism 8 is not limited to the planetary gear shown in the figure, but may also use a gear train consisting of a combination of bevel gears known as a differential gear device, or two rotatable gears disposed on the same axis.
Of course, any known mechanism can be used as long as it is capable of causing reverse rotation between the shafts by applying a brake, and rotating together with both shafts when the brake is not activated.

[Brief explanation of the drawing]

Fig. 1 is a schematic diagram of a belt type continuously variable automatic transmission device showing an embodiment of the present invention, Fig. 2 is a sectional view of a belt type continuously variable automatic transmission device showing an embodiment of the present invention, and Fig. 3 is a main part. A sectional view, FIG. 4 is a schematic diagram of another embodiment, and FIG. 5 is a schematic diagram of another embodiment. 1... Prime mover, 2... Fluid coupling, 3...
Pump impeller, 4... Turbine runner, 7... Input shaft, 8... Forward/forward switching mechanism, 10... Primary
Pulley, 11... Secondary pulley, 12... Belt, 13... Intermediate shaft, 14, 17... Fixed flange,
15, 18...Movable flange, 16...Output shaft, 86
...Brake, 90...Clutch, 100...Housing, 111...Lockup release pressure supply oil passage, 1
18, 119, 132...Shaft hole oil passage.

Claims (1)

[Scope of Claims] 1. A pump impeller that is connected to the output side of a prime mover and receives the torque generated by the prime mover, a turbine runner that receives the torque of the pump impeller via fluid as the pump impeller rotates, and the pump impeller. a fluid coupling that is detachably disposed between the engine and the turbine runner and has a lockup device that directly connects the output side of the prime mover to the turbine runner when engaged; and a fluid coupling that is connected to the output side of the prime mover via the fluid coupling. an input shaft, an intermediate shaft disposed concentrically with the input shaft, one end of which is supported concentrically and rotatably relative to the input shaft, and the other end of which is rotatably supported by a housing;
extending between the input shaft and the hub of the pump impeller;
a sleeve provided with a sliding bearing on the inside of the front end and a pair of seal rings arranged on the inside of the rear end; an output shaft arranged parallel to the input shaft and the intermediate shaft; and a sleeve arranged concentrically with the intermediate shaft. A primary pulley consisting of a fixed fixed flange and a movable flange provided to be slidable in the axial direction with respect to the fixed flange, a fixed flange fixed concentrically to the output shaft, and a movable flange provided axially with respect to the fixed flange. A secondary pulley consisting of a movable flange that is slidably provided at a belt for converting a speed ratio; a forward/reverse switching mechanism disposed between the input shaft and the intermediate shaft for switching the direction of rotation between the two shafts; and a separation wall disposed between the fluid coupling and the forward/reverse switching mechanism;
An oil pump rotatably driven by a prime mover communicates with the oil pump through an oil hole formed in the sleeve, and is formed between the sleeve and the input shaft, and is sealed with a sliding bearing at the front and a seal ring at the rear. a lock-up release pressure supply oil passage that is connected to the shaft hole passage of the input shaft through an oil hole formed in the input shaft; and a lock-up release pressure supply oil passage that is formed between the sleeve and the hub of the pump impeller and that communicates with the oil pump. The input shaft has an oil passage for supplying lock-up engagement pressure, and a shaft hole passage of an intermediate shaft that communicates with the oil pump through the pair of seal rings and supplies oil to the forward/reverse switching mechanism. supported at two points via the front end of the sleeve and the front end of the intermediate shaft,
A belt type continuously variable automatic transmission characterized in that the front end of the sleeve is rotatably supported near the rotation center of a turbine runner. 2. Claim 1, wherein the oil supplied to the forward/reverse switching mechanism is supplied to a planetary gear or a frictional engagement element of the forward/reverse switching mechanism.
Belt-type continuously variable automatic transmission device described in . 3 A shaft hole oil passage for supplying oil for lock-up release within the input shaft, a shaft hole oil passage for supplying servo oil pressure for the movable flange within the intermediate shaft, and a forward/reverse movement switching mechanism within the intermediate shaft. The shaft hole oil passages for supplying oil to the input shaft and the intermediate shaft are independently arranged, and the shaft hole oil passages are arranged on the same line within the input shaft and the intermediate shaft. The belt type continuously variable automatic transmission device according to item 1 or 2.