JPH02180336A - Belt type continuous transmission - Google Patents

Abstract

PURPOSE:To shorten the dimension in axial direction by offsetting at least one of the two countershafts to move interlockedly the rotary parts of mechanical actuators on the primary and secondary sides in a place where a gear borne by countershaft does not interfere with a structure on shaft with the other rotary part fitted viewed on the side elevation. CONSTITUTION:A primary and a secondary actuator rotary part 10b, 11b of mechanical type are moved interlockedly by a torque transmitting device 12, and movable sheaves 5b, 6b of a primary and a secondary pulley 5, 6 move in the axial direction in conjunction with each other. However a gear 20a on a countershaft 19 meshing with a gear 22'b fixed to one of the mechanical actuator rotary parts 11b shall be offset in a place where it on the side elevation does not interfere with a structure, for ex. primary pulley 5, on a shaft, for ex. the primary shaft 2, on which the other mechanical actuator 10 is fitted. This eliminates necessity for installation of any axially oriented space for gear 20a on the shaft 2, and thus the dimension in the axial direction will never increase.

Description

DETAILED DESCRIPTION OF THE INVENTION (a) Industrial field of application The present invention provides a method for attaching a belt made of metal or the like to a primary pulley and a secondary pulley consisting of a movable sheave and a fixed sheave, respectively.
It relates to a belt-type continuously variable transmission fi (CVT) that consists of a belt-type continuously variable transmission (CVT) wrapped around a belt-type continuously variable transmission (including a chain type), and more specifically, a mechanical actuator operating device such as a ball screw device that moves the movable sheaves of the primary and secondary pulleys in the axial direction. Regarding structure.

(b) Prior Art Recently, due to the demand for improved fuel consumption, automatic transmissions incorporating belt-type continuously variable transmissions have been attracting attention as automobile transmissions.

Conventionally, the present applicant applied an axial force corresponding to the transmitted torque to a pulley using a pressure regulating cam mechanism, as shown in, for example, Japanese Patent Application Laid-open No. 62-159848 and Japanese Patent Application Laid-open No. 63-158353. We devised a belt-type continuously variable transmission that uses a device to adjust the effective diameter of the pulley.

The belt-type continuously variable transmission has two gears fixed to one countershaft meshing with gears provided on the rotating parts of the primary and secondary ball screw devices, respectively, and a rotary drive device attached to the countershaft. The movable sheaves of the primary and secondary pulleys are adjusted by transmitting torque from the ball screw device and moving the ball screw device in the axial direction. Furthermore, if both the rotating sheaves of the primary and secondary pulleys are moved by the same amount in the axial direction, the amount of movement of the movable sheave will differ from the original movement of the movable sheave defined by the belt, so the ball screw device of the primary and secondary side The re-rotating section is interlocked via a non-circular gear, and the amount of movement of the movable sheave by the ball screw device is corrected to match the original amount of movement of the movable sheave.

(Problems to be Solved by the Invention) In the case of the above-mentioned one consisting of one countershaft, the gear on the countershaft that meshes with the gear provided in the rotating part of the ball screw device on the secondary pulley side is connected to the primary shaft. axially avoiding the upper components,
In side view, it is arranged so as to wrap around the component, for example, the primary pulley. For this reason, a certain amount of space is required on the primary shaft so as not to interfere with the gears on the countershaft, which is one of the causes of an increase in the axial dimension of the belt type continuously variable transmission. Even if the secondary ball screw device strokes in the axial direction, the gear must always maintain a meshing relationship with the gear fixed to the rotating part of the screw device.
The installation position of the gear is limited, so the installation position of the gear is
The position of the components on the primary shaft is also affected, resulting in a tendency for axial dimensions to increase.

In addition, if an attempt is made to make the circular and non-circular gears fixed to the countershaft smaller and more compact, the gear on the ball screw device side that meshes with the gears will be limited in diameter reduction because it is fixed to the outer periphery of the threaded part. As a result, the rotation of the countershaft increases in speed and is transmitted to the rotating part of the ball screw device, and due to the restriction that the rotation of the non-circular gear mentioned above is within one rotation, it becomes necessary to increase the lead of the ball screw device. As the number of balls in the device decreases, it becomes difficult to ensure sufficient load capacity, and therefore it is impossible to achieve compactness by reducing the gear diameter of the countershaft.

Accordingly, one object of the present invention is to provide a belt type continuously variable transmission that eliminates the above-mentioned problems by using a plurality of countershafts.

(d) Means for Solving the Problems The present invention has been made in view of the above-mentioned circumstances. For example, when shown with reference to FIGS. 1 and 2 and FIGS. Two sheets (5a), (5) supported by shafts (2), (3) and capable of relative movement in the axial direction.
b), (6a), (6b) primary pulley (
5) and secondary pulley (6), and both these pulleys (
5), a mechanical actuator (10) such as a ball screw device that moves the movable sheaves (5b), (6b) of both hoolis in the axial direction.
, (11), and a belt type continuously variable transmission (1
), the rotating parts (for example, female screw parts) (10b), (llb) of the mechanical actuators (10)', (it) on the frying and secondary sides are mutually interlocked by a torque transmission device (12), and , the torque from the rotational drive device (13) (see FIG. 3) is transmitted to the torque transmission device, and the torque transmission device (12) is connected to the gears ( 22b
), (22'b) meshing gears (21a), (20a
) supporting two countershafts (17) and (19
), and at least one countershaft (
19) supported on the counter shaft.
0a) is a component on the shaft (for example, a primary pulley) equipped with a rotating part (10b) on the side that does not mesh with the gear.
(5) It is characterized in that it is offset to a position where it does not overlap when viewed from the side.

As an example, the torque transmission device (12) includes a pair of non-circular gears (15) and (16) that mesh with each other, and the pair of non-circular gears (15) and (16) are fixed to the countershafts (17) and (19), respectively, and large gears (2
0a), (21a) and small gears (20b), (21b)
The large gear (21 or 20) of the gear unit (21 or 20) supported by one of the countershafts (17 or 19) is rotatably supported.
1a or 20a) is meshed with a gear (22b or 22'b) fixed to one rotating part (10 or 11),
The small gear (21b or 20b) is fixed to the other countershaft (19 or 17).
It meshes with a).

(E) Effect Based on the above configuration, the rotation of the primary pulley (5) is as follows:
It is transmitted to the secondary shaft (3) via the belt (7) and the secondary pulley (6). Further, the torque from the rotation drive device (13) such as an electric motor is transmitted to the primary and secondary mechanical actuators (e.g. ball screw device) (10) via the torque transmission device (12).
(11) is transmitted to the rotating parts (10b) and (llb),
Based on the rotation of these rotating parts, the mechanical actuators are moved in the axial direction to move the movable sheaves (5b) and (6b), respectively.
Move the primary and secondary pulleys (5), (
6) Change the belt effective diameter to create a belt-type continuously variable transmission!
! (1) Continuously variable speed.

At this time, the torque transmission device (12) connects both the primary and secondary mechanical actuator rotating parts (10b
), (1'lb) are interlocked, and movable sheaves (5b), (6b) of primary and secondary pulleys (5), (6)
) move axially in relation to each other, while a gear (22) fixed to one mechanical actuator rotation part (llb)
' b) The gear (20a) on the countershaft (19) meshing with the shaft (e.g. primary shaft) (2) on which the other mechanical actuator (10) is mounted
It is not necessary to overlap the upper component (for example, the primary pulley) (5) in a side view (see Fig. 7), and to provide an axial space for the gear (20a) on the shaft (2). do not have.

As an example, rotation from the rotary drive device (13) may be performed on one side (
For example, the signal is transmitted to the gear (22b) of the ball screw device (10) (on the primary side), rotates the female threaded portion (10b) multiple times, moves the movable sheave (5b) in the axial direction, and further moves the gear (2"2b). The rotation of is caused by the large gear (21a) and the small gear (2
A gear unit (21) consisting of a gear unit (21) further comprising a gear (19)
a), and is transmitted to the other countershaft (19), and in the decelerated state, the non-circular gears (16) and (17) mesh within a rotation angle of one rotation. . The rotation corrected by the non-circular gear is transmitted from one countershaft (17) to the gear (17a).
and the gear unit (20), and the gear (for example, the secondary side) of the ball screw device (11)
22'b) and rotates the female threaded portion (llb) multiple times to move the movable sheave (6b) in the axial direction.

At this time, the tooth thickness of the large gears (20a) and (21a) is increased so that the meshing relationship with the gears (22b) and (22'b) can be maintained even by the axial movement of the ball screw devices (10) and (11). Although always maintained, thickening the gear does not have the same effect on the formation (5) on the other shaft (2).

Note that the symbols in parentheses are used to contrast with the drawings to facilitate understanding, and do not limit equivalent configurations, and even if the same symbols are used, they are used as generic concepts in accordance with the scope of the claims. For reasons mentioned above, some names may be different from those of the embodiments shown below.

(F) Embodiments Hereinafter, embodiments in which the present invention is applied to an automatic continuously variable transmission for a vehicle will be described along with the drawings.

First, the outline of the present automatic continuously variable transmission will be explained in accordance with FIG. Output member 70 consisting of device 71 etc.
, a forward/reverse switching device 90 consisting of a dual planetary gear mechanism, and a starting device 100 consisting of a fluid coupling 101, a centrifugal lock-up clutch 102, and a slip clutch 103.

The planetary gear mechanism 40 has a ring gear 4
0R is interlocked with the secondary shaft 3 of the continuously variable speed bag rIt1, the carrier 40C is interlocked with the output member 70, and the sun gear 40S is connected to the row one-way clutch F and the low coast clutch F and the low-coast clutch which constitute the locking means via the transfer device 80. It is connected to the reverse brake B1 and also to the input shaft 60 via the high clutch C2.

Also, dual planetary gear mechanism 90. , the sun gear 909 is connected to the input shaft 60, and the carrier 90C
is connected to the primary shaft 2 of the continuously variable transmission 1 and to the input shaft 60 via the forward clutch C1, and the ring gear 90R is connected to the reverse brake B2.

Based on the above configuration, each clutch, brake, and one-way clutch in the present automatic continuously variable transmission A operate as shown in FIG. 5 at each position. Note that * indicates that the lock-up clutch 102 can be operated appropriately by centrifugal force.

To explain in detail, in low speed mode L in D range,
In addition to the forward clutch C1 being connected, the row one-way clutch F is activated. In this state, the rotation of the engine crankshaft is transmitted to the input shaft 60 via the lock-up clutch 102 and slip clutch 103 or via the fluid coupling 101, and further directly transmitted to the sun gear 90S of the dual planetary gear device 90. The signal is transmitted to the carrier 90C via the forward clutch C1. Therefore, the dual planetary gear machine [90 rotates integrally with the input shaft 60, transmits the forward rotation to the primary shaft 2 of the belt-type continuously variable transmission 'Ii1, and is further shifted as appropriate by the continuously variable transmission 1. Rotation is transmitted from the secondary shaft 3 to the ring gear 40R of the single planetary gear device 40. On the other hand, in this state, the sun gear 405, which is a reaction force support element that receives reaction force, is stopped by the row one-way clutch F via the transfer device 80, and therefore the rotation of the ring gear 40R is taken out from the carrier 40C as decelerated rotation. , and further reduction gear device 7
1, etc., to the axle shaft 73.

Furthermore, in high-speed mode H in the D range, the high clutch C2 is connected in addition to the forward clutch C1. In this state, as described above, the forward rotation, which has been appropriately changed in speed by the continuously variable transmission 1, is taken out from the secondary shaft 3 and input to the link gear 40R of the single planetary gear device 40.

Meanwhile, at the same time, the rotation of the input shaft 60 is transmitted to the sun gear 403 of the single planetary gear mechanism 40 via the high clutch C2 and the transfer device 80, and as a result, the torques of the -C ring gear 40R and the sun gear 40S are combined in the planetary gear mechanism 40. The signal is then output from the carrier 40C. At this time, since the rotation that resists the reaction force is transmitted to the sun gear 408 via the transfer device 80, torque circulation does not occur and the predetermined +1
. . . . . . . . . . . . . . . . . .

Then, the combined torque from the carrier 40C is transmitted to the axle shaft 73 via the reduction gear device 71 and the like.

In addition, in the operation in the D range, the one-way clutch F becomes free when reverse torque is applied (during engine braking), but in the S range, in addition to the low one-way clutch F, the low coast stage reverse brake B1 is activated.
operates and transmits power even when reverse torque is applied.

Furthermore, in the R range, the reverse brake B2 operates together with the low coast stage reverse brake B1. In this state, the rotation of the input shaft 60 is input to the belt-type continuously variable transmission 1 as reverse rotation from the carrier 90C because the ring gear 90R is fixed in the dual planetary gear mechanism 90. On the other hand, the sun gear 40S of the single planetary gear device 40 is fixed based on the operation of the low coast stage reverse brake B1, so that the reverse rotation from the continuously variable transmission device 1 is caused by the planetary gear device l? I40
It is decelerated at and taken out to the output member 7o.

Next, an embodiment embodying the present invention will be described with reference to FIG.

This continuously variable transmission A has a transmission case 25 that is divided into three parts, and an input shaft 60 and a primary shaft 2 of the continuously variable transmission 1 are rotatably supported coaxially on the case 25. The secondary shaft 3 and the gear shaft 70a of the continuously variable transmission 1 are coaxially and rotatably supported to form a second shaft. Further, on the first shaft, a starting device 100, an operating section 50 consisting of a forward clutch C1, a high clutch C2, a low coast stage reverse brake B1, a reverse brake B2, and a row one-way clutch F, and a forward/reverse switching device are configured. A dual planetary gear machine #190 and a hydraulic pump 61 are disposed, and a single planetary gear mechanism 40 is disposed on the second shaft.

The starting device 100 includes a fluid coupling 101, a lock-up clutch 102 consisting of a centrifugal clutch, and a slip clutch 103. And slip clutch 103
is a cam mechanism 105 that generates an axial force corresponding to the load torque.
The cam mechanism presses and acts on the clutch plate and disk of the slip clutch, increasing the torque capacity of the slip clutch 103 in response to an increase in load torque.

Further, a protrusion 25a protrudes from the case 25 on the engine side of the input shaft 60, and an input block block 81 of the transfer device 80 is supported by the protrusion 25a via a bearing. Further, the hub portion of the sprocket 81 is connected to the case protrusion 25a via a one-way clutch F, and the flange extending radially outward from the sprocket 81 has a flange on its inner circumferential surface. The input shaft 60 is connected via a high clutch C2 consisting of a multi-plate clutch, and the outer peripheral surface of the input shaft 60 is connected to the case 2.
A low coast stage reverse brake B1 consisting of a multi-disc brake is interposed between the brake and the brake.

A sun gear 90S (see FIG. 4) of the dual planetary gear mechanism 90 is spline-coupled to the tip of the input shaft 60, and a flange extends in the outer diameter direction. Further, the tip of the input shaft 60 is fitted and aligned with the primary shaft 2 of the belt-type continuously variable transmission 1 via a bushing, and a carrier 90C is spline-coupled to the shaft 2. A first pinion 90P1 and a second pinion 90P2 are supported on the carrier 90C, and a connecting member extends in the outer diameter direction, and the inner diameter side of the connecting member and the outer diameter side of the flange from the input shaft 60 are connected to the carrier 90C. A forward clutch C1 consisting of a multi-disc clutch is interposed between the ring gear 90R and the ring gear 90R.
A reverse brake B2 consisting of a multi-disc brake is interposed between the outer peripheral side of the support member fixing the case 25 and the case 25.

An actuator unit 51 is disposed between the low coast reverse brake B1 and high clutch C2 and the reverse brake B2 and forward clutch C1 in the operation section 50, and the actuator unit 51 is adjacent to the low coast reverse brake B1 and high clutch C2. It consists of an actuator 51a for a forward/reverse switching device and an actuator 51b for a low/high speed mode switching device, which are arranged at the same time. The actuator unit 51 has a motor for a forward/reverse switching device and a motor for a low/high speed mode switching device which are arranged at a predetermined distance in the circumferential direction, and these motors include a commutator motor, a step motor, etc. The motor is comprised of an electric motor such as a rotating magnetic field motor, a servo motor, or an ultrasonic motor, and is provided with holding means such as an electromagnetic brake to maintain the motor at a predetermined rotational position. Further, the female threaded portions of ball screw devices 52 and 53 for the forward/reverse switching device and the low/high speed mode switching device are respectively fixed to the case 25, and the male threaded portions of the ball screw devices are respectively fixed to the case 25. It meshes with the output gear of the motor via a gear, and a connecting member is connected to each male threaded portion, respectively. The connecting member connected to the ball screw device 52 for the forward/reverse switching device engages the forward clutch C1 by moving axially in one direction, and engages the reverse brake B2 by moving axially in the other direction. Furthermore, the connecting member connected to the ball screw device 53 for the low/high speed mode switching device engages the high clutch C2 by moving in the axial direction in one direction, and engages the high clutch C2 by moving in the axial direction in the other direction. Engage B1.

Further, as shown in detail in FIG. 1, the continuously variable transmission 1 includes a primary pulley 5, a secondary pulley 6, and a belt 7 wound around both pulleys, and both pulleys each have a fixed sheave 5a.

6a and movable sheaves 5b, 6b. The belt 7 has a large number of metal pieces, and these pieces come into contact with both the primary and secondary pulleys 5 and 6 in a lubricated state to transmit torque. The friction is relatively small, so that the angle of the contact surface between the bridge and the pulley is set larger than its static friction angle. That is, by moving the pulleys 5, 6 in the axial direction, the belt 7 can be moved in the radial direction. In addition, the fixed sheave 5a of the primary pulley 5
is rotatably supported by the case 25 by a roller bearing 30, and furthermore, the base end of the primary shaft 2 bulges in the outer radial direction to form a flange portion 2a,
A pressure regulating cam mechanism 9 is interposed between the flange portion 2a and the back surface of the fixed sheave 5a. And the pressure regulating cam mechanism 9
The fixed side cam portion 9a is spline-coupled to the primary shaft 2 and whose axial movement is regulated by the flange portion 2a, and the fixed-side cam portion 9a is spline-coupled to the fixed sheave 5a and is in pressure contact via a disc spring. It consists of a movable side cam part 9b and rollers interposed between both cam parts, and applies an axial force corresponding to the transmitted torque to the fixed sheave 5b. The boss portion of the fixed sheave 5a extends toward the movable sheave 5b, and its inner circumferential surface is fitted into the primary shaft 2, and its outer circumferential surface is equipped with a plurality of rows of ball spline mechanisms (linear ball bearings). A boss portion of the movable sheave 5b is supported via 21 so as to be movable only in the axial direction. That is, the movable sheave 5b is fitted into the fixed sheave boss portion only through the balls without being subjected to sliding frictional resistance.

Further, a ball screw device 10 is disposed on the back of the movable sheave 5b, and the ball screw device 10 has a male threaded portion 10.
a, a female threaded part LOb, and a ball, and is of a circulet type in which the ball is circulated in a return passage. Further, the ball screw device is composed of a single thread screw, and the female threaded portion 10b has a concave groove for about one turn and a block-type return passage, and the male threaded portion 10a is axially closer than the female threaded portion. The rear end portion is fixed to an adjusting member 26 which is restrained and supported in the axial direction and radial direction by the shoulder portion of the case 25. The adjustment member 26 moves the inner cylindrical part of the boss part of the fixed sheave 5a by means of a roller bearing 33, so that it is connected to the primary shaft 2.
The belt is supported rotatably and is engaged with the worm 34, and rotates based on the operation of the worm 34, causing the male threaded portion 10a to rotate relative to the female threaded portion 10b. The initial tension of 7 and the running center of the belt can be adjusted. Further, an automatic alignment mechanism 22 is fixed to the female screw portion 10b, and a thrust ball bearing 23 is interposed between the automatic alignment mechanism 22 and the back surface of the movable sheave 5b. The thrust bearing 23 has a large number of balls 23b held in a cage, and the balls 23b are in direct contact with a recess formed on the back surface of the movable sheave 5b, and are in contact with the movable sheave 5b. The opposite side is in contact with the race 23a. race 23
The other side surface of a has a spherical convex surface, and the spherical support surface of the self-aligning mechanism 22 is in close contact with the spherical convex surface. The spherical support surface 22a faces diagonally downward and the primary shaft 2
The self-aligning mechanism 22 includes a protrusion extending diagonally along the spherical support surface 22a, a gear 22b formed at the tip of the protrusion, and the female screw portion. 10b has a key fixing portion 22c that is integrally fixed in the rotational and axial directions. Further, an elastic spring made of a predetermined number of disc springs is provided between the support plate 35, which is prevented from moving in the axial direction by the inner race of the roller bearing 33 held by the adjustment member 31, and the back surface of the movable sheave 5b. A biasing member 36 is disposed, and the biasing member 36 carries a part of the belt clamping load, and the biasing member 36 carries a part of the belt clamping load and the ball screw device 10
and lower the supporting load of the bearing 23. Further, a flange portion 27 is fixed to the distal end of the primary shaft 2 by screw connection, and an automatic alignment mechanism 28 is fixed to the flange portion. The self-aligning mechanism 28 has a spherical support surface 28a which is a convex surface facing diagonally outward and whose focal point is located on the axial extension of the shaft 2. Furthermore, a thrust ball bearing 29 is interposed on the back surface of the self-aligning mechanism 28 and the adjustment member 32, and the bearing 2
9 has a large number of balls 29b held in a cage and one race 29a. Ball 29b is adjustment member 2
The race 29a that is in direct contact with a recess formed on the back surface of the ball 6 and the other side of the ball has a spherical concave surface that is in close contact with the spherical support surface 28a of the self-aligning mechanism 28. There is.

On the other hand, the fixed sheave 6a of the secondary pulley 6 is rotatably supported by the case 25 together with the secondary shaft 3 via a roller bearing 30', and the boss portion 6b of the movable sheave 6b.

However, a ball spline 21' similar to the aforementioned ball spline is slidably inserted into the secondary shaft 3 through only the balls.

Further, a ball screw device 11 similar to that described above is disposed on the back surface of the movable sheave 6b, and its male threaded portion 11a is fixed to an adjustment member 26' similar to the m-section member 26. The adjustment member 26' is a roller bearing 3
3' supports the secondary shaft 3, and based on the rotation of the ohm 34', the initial tension and running center line of the belt 7 can be adjusted in conjunction with the adjustment member 26 on the primary side. In addition, the female threaded portion 11b has
Similarly to the primary side, the automatic alignment mechanism 22' is fixed, and the automatic alignment mechanism 22' and the movable sheave 6
A thrust ball bearing 23' is interposed on the back surface of b. Further, a support plate 35' fixed to the shaft 3
An elastic biasing member 36' similar to that on the primary side is disposed between the movable sheave 6b and the back surface of the movable sheave 6b. Further, the secondary shaft 3 has a proximal end that is expanded in diameter and is formed with a hole 3a for receiving the gear shaft 70a, and furthermore, the end of the expanded shaft portion 3b protrudes in the outer radial direction to form a flange portion 3.
A fixed sheave 6a is fitted to the tip of the shaft 3 via a key k, and a nut 38 is screwed to prevent the fixed sheave 6a from coming off. Similarly to the primary side, a self-aligning mechanism 28' is fixed to the flange portion 3C, and has a spherical support surface 28'a which is a convex surface and whose focal point is located on the axial extension line of the shaft 3. On the back surfaces of the self-aligning mechanism 28' and the adjustment member 26', there are provided a ball 29'b that directly contacts the back surface of the member and a race 29'a that has a spherical concave surface that comes into close contact with the spherical support surface 28'a. A thrust ball bearing 29' is interposed therebetween.

In FIG. 1, the numbers 39 and 39' indicate the fixed sheaves 5a and 6 on the primary side and the secondary side.
This is a groove for detection formed at the tip of the groove 3.
The rotation speeds of the primary shaft 2 and the secondary shaft 3 are detected by being counted by the electromagnetic sensors S + and S z of 9.39, respectively.

Then, as shown in FIGS. 1 and 2 and FIGS. 6 to 8, the primary shaft 2 and the secondary shaft 3
An operating device 130 is disposed at a portion that forms a triangle. The operating device 130 has first and second countershafts 17, 19 supported by the case 25 via bearings 132, 132, . . .
The countershaft 17 has a large float 21a and a small gear 2.
A gear unit 21 having a gear 1b is rotatably supported, and a large gear 17a is integrally fixed to its tip. The second countershaft 19 also has a large gear 1.
9a is integrally fixed, and a small gear 2 is attached to the tip.
A gear unit 20 having a gear 0b and a large gear 20a is rotatably supported. Furthermore, as shown in FIG. 6, non-circular gears 15, 18 that mesh with each other are fixed to the protruding portions of both countershafts 17, 19 that protrude from the bearings 132, so that they are in a non-linear relationship with each other. These non-circular gears 15.
16 is covered with a protective cover 131 fixed to the case 25. As shown in detail in FIG. 7, the gear unit 21 rotatably supported on the first countershaft 17 has its large gear 21a meshing with the gear 22b of the primary ball screw device 10, which will be described later. The gear 136b from the electric motor 13 meshes with the large float 19a whose small gear 21b is fixed to the second countershaft 19, thereby creating a speed increasing device in the transmission path from the second countershaft 19. 12b (therefore, it constitutes a speed reduction device in the transmission path from the gear 22b of the ball screw device). Further, as shown in detail in FIG. 8, the gear unit 20 rotatably supported on the second countershaft 19 has its large float 20a meshing with the gear 22'b of the secondary ball screw assembly r111. ,
The small gear 20b meshes with the large gear 17a fixed to the first countershaft 17, and the speed increasing device 12a is connected to the transmission path from the first countershaft 17.
(Accordingly, it constitutes a reduction gear in the transmission path from the gear 22'b of the ball screw device.As shown in FIG. 1, the female threaded portion 10b of the ball screw device Ht6.tt,
The gears 22b and 22'b connected to the gears 22b and 22'b have thin teeth, and the large gears 21a and 20a of the gear unit 21.20 supported by the countershaft 17.19.
is the thin gear 22b even if the ball screw device makes a full stroke in the axial direction.

It consists of a gear with thick teeth so that it can always maintain a meshing relationship with 22'b.

In addition, as shown in detail in FIG. 8, the second countershaft 19 has a large toothed gear (20a) supported on the shaft 19 that is connected to a component on the primary shaft 2, such as the primary pulley 5. The large float (20a) is arranged offset in a non-lapping position in a side view, and therefore does not affect the axial dimension of the primary shaft 2.

On the other hand, as shown in FIGS. 3 and 9, an electric motor 13 for speed change operation is fixed outside the case 25, and the electric motor 13 is similar to the electric motor in the operation section 50 described above. , has an electromagnetic brake 145 that can hold the motor in a predetermined position when the motor is not energized.

The output gear 133 of the motor 13 is connected to the large gear 13.
5a and a small gear 135b, and a gear unit 136 having a large gear 136a and a small gear 136b.
That is, the small gear 136b meshes with the large gear 21a to transmit power.

The gears of the torque transmission device 12 and the speed reduction device 143 are made of spur gears or helical gears, and are capable of reversible transmission and highly efficient power transmission.

Further, as shown in FIG. 3, the single planetary gear mechanism 40 is disposed on a gear shaft 70a constituting a second shaft, and its ring gear 40R is connected to the flange of the secondary shaft 3 of the belt type continuously variable transmission 1. 19. A sprocket 82 is rotatably supported on the gear shaft 70a integrally with the sun gear 40S, and a pinion 4. A carrier 40C that rotatably supports the OP is fixed.

On the other hand, a silent chain 8 is connected between the sprocket 82 integrated with the sun gear 403 on the second shaft and the sprocket 81 supported by the row one-way clutch F.
3 is wound around, and these sprockets and chains constitute a transfer device 80.

Further, the gear shaft 70a integrally constitutes the output member 70 with a gear 71a, and the gear 71a meshes with a gear 71c fixed to the intermediate shaft 72. Further, a small gear 71d is formed on the intermediate shaft 72, and the gear 71d meshes with a ring gear 75a fixed to the differential gear device 75, thereby forming the speed reduction device 71. Further, left and right front axle shafts 73 extend from the differential gear device 75.

Next, the operation of this embodiment will be explained.

The rotation of the engine crankshaft is transmitted to the input shaft 60 via the fluid coupling 101 when the vehicle is started, and thereafter via the centrifugal lock-up clutch 102 and the slip clutch 103. The rotation of the input shaft 60 is controlled by an actuator 51 for the forward/reverse switching device in the operation section 50.
By operating the forward clutch C1 or reverse brake B2 based on step a, the forward/reverse switching device 90 consisting of a dual planetary gear mechanism is switched, and forward rotation or reverse rotation is transmitted to the fixed side cam portion 9a of the pressure regulating cam mechanism 9. The operation of the high clutch C2 or the low coast reverse brake B1 based on the actuator 51b for the low/high speed mode switching device in the operating section 50, and the locking/overrun of the row one way clutch F results in a single planetary gear mechanism as described above. The low-high-speed mode switching device 40 is set to low-speed mode L or high-speed mode H.
can be switched to

The torque transmitted to the fixed side cam part 9 of the pressure regulating cam mechanism 9 is transmitted to the movable sheave 5b of the primary pulley 5 via the roller and the movable side cam part 9b, and the axial force corresponding to the transmitted torque is transmitted to the movable sheave 5b of the primary pulley 5. is applied to the fixed sheave 5a, and therefore an axial force corresponding to the transmitted torque is applied to the entire associated belt type continuously variable transmission 1 via the belt 7. Further, the torque of the fixed sheave 5a is transmitted to the movable sheave 5b via the ball spline 21, and the belt 7 is held between the belts 7 by the axial force based on the pressure regulating cam mechanism 9, and the belt 7 is
is transmitted to the secondary pulley 6 via. At this time, the axial reaction force from the belt 7 acts on the fixed sheave 5a and the movable sheave 5b, and is carried by the flange portion 2a of the shaft, and the axial force from the movable sheave 5b is applied to the thrust ball bearing 23, the automatic It is carried by the flange portion 27 fixed to the shaft 2 via the alignment mechanism 22, the ball screw device 10 in a predetermined state, the adjustment member 26, the thrust ball bearing 29, and the automatic alignment mechanism 28, thereby reducing the axial force. It is received in a closed loop that acts as a tensile stress on the primary shaft 2. A part of the axial force acting on the movable sheave 5b is directly received by the shaft 2 from the back surface of the sheave via the elastic biasing member 36 and the support plate 35, and is received by the shaft 2 through the thrust bearing 23, 29 and the ball screw device T.
The axial force acting on 110 is reduced.

The torque from the belt 7 is transmitted to the secondary pulley 6, and further transmitted to the secondary shaft 3 via the key k and the ball spline 21'. At this time, similarly to the primary side, on the secondary side, the axial reaction force acting on the fixed sheave 6a is carried directly by the shaft 3 by the nut 38, and the axial reaction force acting on the movable sheave 6b is carried by the thrust ball bearing 23. ', ball screw device 11.1 joint member 26', thrust ball bearing 29
' and the flange portion 3C. Similarly, a portion of the axial force acting on the movable sheave 6b is directly received by the shaft 3 via the elastic biasing member 36' and the support plate 35'.

At this time, on the primary and secondary sides,
Even if the movable sheaves 5b, 6b become loose, the thrust ball bearings 23.
23' is automatically aligned, and the balls 23b, 23'b are automatically adjusted so as to uniformly contact the back surfaces of the movable sheaves 5b, 6b over the entire circumference. Furthermore, even if the primary or secondary pulley 2.3 is distorted with respect to the adjustment member 28.26' supported by the shoulder of the case 25, the self-alignment mechanism 28.28' will automatically align it. , balls 29b, 29'b are automatically adjusted so that they uniformly contact the rear surface of the adjusting member 26, 26' over the entire circumference.

Also, based on the speed change command from the control unit, the electric motor 13
When the gear 21a rotates, the large gear 21a loosely engaged with the first countershaft 17 via the reduction gear 143 rotates, and the gear 22b that meshes with the gear 21a rotates the self-aligning mechanism 22 and the female screw portion integrated therewith. 10b rotates. Then, the female threaded portion 10b moves in the axial direction with respect to the male threaded portion 10a whose rotation is prevented by the adjustment member 26, moves the movable sheave 5b via the thrust ball bearing 23, and rotates the primary pulley 5. Change the belt effective diameter. On the other hand, the rotation of the large gear 21a is caused by the gear unit 21
Due to the meshing of the small gear 21b and the large gear 19a, the speed is significantly reduced and transmitted to the second countershaft 19, and further transmitted to the first countershaft 17 via the non-circular gear 16.15. The rotation of the first countershaft 17 is accelerated through the large gear 17a, the small float 20b of the gear unit 20, and the large gear 20a. The signal is transmitted to gear 22'b. Due to the rotation of the gear 22'b,
The female threaded portion 11b integrated therewith rotates relative to the fixed female threaded portion 11a and moves in the axial direction, and moves the movable sheave 6b via the thrust ball bearing 23', thereby controlling the belt of the secondary pulley 6. Change the effective diameter.

At this time, although the amount of movement of the primary and secondary pulleys 5.6 and the amount of movement of the belt 7 do not correspond linearly, the difference in the amount of re-movement is corrected by the kneading transmitted through the non-circular gear 15.16. absorbed into. Also, from a structural standpoint,
The non-circular gear 15.16 is held within one rotation, but the first and second countershafts 17.19 are mutually decelerated.
By providing a non-circular gear in the non-circular gear 15.
Although the rotation of 16 is suppressed to within 1 rotation, the gears 22b and 22'b on the primary and secondary sides are linked with accelerated rotation, and the ball screw devices filo, 11 are
This makes it possible for the ball screw device to obtain a predetermined stroke with a predetermined lead. In addition, the ball screw device filo, 11 moves in the axial direction, and the gear 2 coupled to the female threaded portions 10b, llb.
Even if 2b, 22'b moves in the axial direction, the large gears 21a, 20a that mesh with the gears are made of thick gears,
The large gear 20a on the second countershaft 19 always maintains a meshing relationship, and is radially separated from components on the primary shaft 2, such as the primary shaft 5. The axial dimension of the primary shaft 5 is not affected by the presence of the primary shaft 5.

At this time, for example, when the electric motor 13 is rotated in the upshift direction of the continuously variable transmission 1, the female threaded portion 10b of the ball screw device filO on the primary side expands, and the female threaded portion 11b of the ball screw device 11 on the secondary side expands. Shrink. Then, the primary side movable sheave 5b moves in the pulley diameter expansion direction (to the right in the axial direction in the drawing) together with the female threaded portion 10b, but at this time, the boss portions of both movable sheaves 5b are subject to frictional sliding due to the ball spline 21. move in the axial direction. Moreover, the secondary side movable sheave 6b is
As the female threaded portion 11b moves, the pulley moves in the direction of diameter reduction (to the right in the axial direction in the drawing) based on the force from the belt 7 caused by the pressure regulating cam mechanism 9, but at this time, as with the primary side, the ball spline 21' allows the movable sheave 6b to move in the axial direction without any frictional sliding movement between the movable sheaves 6b. Furthermore, the primary side ball screw device 10 and the secondary side ball screw device 11 are composed of reversible transmission devices capable of converting rotational force into axial force and axial rotational force, and the female screw portions 10b of both ball screw devices, llb is interlocked by a reversible transmission device 12 consisting of a spur gear or a hesocal gear, so the axial force from the belt 7 on the secondary pulley 6 is converted and transmitted to the axial force of the primary pulley 5 via the reversible transmission device. There is. Therefore, the axial force exerted on the movable sheave 5b by the primary ball screw device 10 during gear shifting is based on the fact that there is almost no axial movement resistance of the movable sheave 5b and the reversible transmission. 7
The difference in the clamping force between the two is sufficient, the electric motor 13 needs to have a small torque capacity, and the speed can be changed at high speed, and the pressure regulating cam mechanism 9 does not require a movement resistance bone of the movable sheave 5b. , one that generates a relatively small axial force is sufficient. Note that when the electric motor 13 is rotated in the downshift direction, the secondary side ball screw device 11 expands and the Japanese pine ball screw device 10 contracts, so that a speed change operation is performed in the same manner as described above.

In addition, when the vehicle is in a high speed state, that is, the belt type continuously variable transmission 1 is in an increasing speed state, and the vehicle is suddenly stopped by applying the brakes, the belt type continuously variable transmission 1 may not be able to return to the lowest speed state. be. In this case, as described above, the ball screw device 10.11 has a relatively small lead angle, there is no sliding friction resistance of the movable sheaves 5b, 6b, and the static friction angle between the belt 7 and the pulleys 5, 6 is Since the contact angle is smaller than the contact angle, the movable sheave can be moved in the axial direction even when the belt type continuously variable transmission 1 is stopped. Therefore, even after the vehicle has stopped, the electric motor 13 continues to rotate and the movable sheave is moved. 5b and 6b in the axial direction to return the continuously variable transmission 1 to the lowest speed state.

The rotation of the primary shaft 3 is controlled by the flange portion 3.
Ring gear 4 of single planetary gear mechanism 4° from C
0R, and as described above, is simply decelerated by the planetary gear mechanism or combined with the rotation from the transfer 80 and transmitted to the gear shaft 70a. Furthermore, the rotation of the gear shaft 70a is transmitted to the differential gear device 7 via the reduction gear device 71.
5 and then to the left and right front axle shafts 73.

In the above embodiment, the belt type continuously variable transmission device 1 is applied to an automatic transmission A that switches between a low speed mode and a high speed mode by combining the single planetary gear machine fA40. It goes without saying that the present invention may be applied to other types of automatic transmissions, such as automatic transmissions combined with a step-change transmission.

Furthermore, although we have described a case in which the large float 20a that engages with the ball screw device on the secondary side is avoided in the radial direction from the components on the primary shaft 2, due to differences in the pulley layout and other components, the ball screw device on the primary side The large gear 21a meshing with the secondary shaft 2
If avoided from the above configuration, the first countershaft 1
Of course, the same application can be made by arranging 7 in an offset manner.

In addition, although an embodiment has been described in which the non-circular gears 15 and 16 are sped up and interlocked with the gears of the ball screw device, the present invention is not limited to this. The present invention can be similarly applied to pulleys with curved contact surfaces or other correction mechanisms (see, for example, Japanese Patent Application Laid-open No. 13856/1983).

(G) As described in detail of the invention, according to the present invention, the rotating parts (10
b), a countershaft (17) that interlocks (llb)
, (19), and at least one of the shafts (19) is supported by the counter shaft.
a) is the shaft (2) on which the other rotating part (10b) is attached.
) on the shaft (2) so that it does not overlap with the component (5) on the shaft (2) when viewed from the side.
20a), and the axial dimension can be shortened.

In addition, a speed increasing (
If the gear units (21) and (20) constituting the speed reduction devices (12b) and (12a) are rotatably supported, the shaft support structure of these speed increase devices becomes simple, and the rotating part (1
0b) Gears (22b) and (22'b) provided in (llb)
) The diameters of the gears (21a) and (20a) that mesh with the gears (21a) and (20a) can be reduced, and the device can be made more compact.

Furthermore, a gear (2) supported on the countershaft (19)
Even if a gear with thick teeth is used for 0a), the gear does not interfere with the component (5) on the shaft (2).
A gear (22) on the mechanical actuator side that does not affect the axial dimension and maintains a meshing relationship with the gear.
b) and (22'b) can be used with thinner teeth, making it possible to secure space for the worm gear (34) (34), etc., making it more compact, and also improving assembly performance. be able to.

[Brief explanation of the drawing]

FIG. 1 is a developed sectional view showing a belt-type continuously variable transmission according to the present invention, and FIG. 2 is a schematic diagram thereof. FIG. 3 is an overall sectional view showing an automatic transmission to which the belt-type continuously variable transmission is applied, FIG. 4 is a schematic diagram showing the outline of the automatic transmission, and FIG. 5 is each element at each position. FIG. Furthermore, Figures 6 to 9 are diagrams of each gear train seen from the rear (left side of Figure 1) of the belt type continuously variable transmission, Figure 6 is a diagram showing a non-circular gear, and Figure 7 is a diagram showing a non-circular gear. FIG. 8 is a diagram showing one speed increasing device T1 (speed reducing device fi), FIG. 8 is a diagram showing the other speed increasing device, and FIG. 9 is a diagram showing a speed reducing device from the rotary drive device. 1... Belt type continuously variable transmission yi 2... Primary shaft 3... Secondary shaft 5...
・Primary pulley 6...Secondary pulley
5a, 6a - fixed sieve, 5b. 6 b--Movable sheave, 5 at, 5 b
1, 6 b t... Boss part 7... (metal)
Belt 9...Pressure adjustment (cam) mechanism 10.1
1... Mechanical actuator (ball screw device),
10a.

Claims (1)

[Claims] 1. A primary pulley and a secondary pulley each consisting of two sheaves supported by a shaft and capable of relative movement in the axial direction, a belt wound around these two pulleys, and a movable sheave of these two pulleys. a mechanical actuator that moves in an axial direction; the mechanical actuator includes a fixed part whose rotational direction is blocked at least by a fixed member; and a rotating part; The rotating parts of both the primary and secondary mechanical actuators are interlocked by a torque transmitting device, and the torque from the rotational drive device is transmitted to the torque transmitting device, and the torque transmitting device is connected to each of the rotating parts. It has two countershafts that support gears that mesh with the provided gear, and at least one of the countershafts is mounted on a shaft that is equipped with a rotating part on the side where the gear that is supported by the countershaft does not mesh with the gear. A belt-type continuously variable transmission that is offset from the components in a position that does not overlap when viewed from the side. 2. The mechanical actuator is composed of a ball screw device, the male threaded portion of the ball screw device is connected to the fixing member immovably in the rotational and axial directions to constitute the fixing portion, and the female threaded portion is The belt type continuously variable transmission device according to claim 1, wherein the rotating portion is configured by being connected to a rotational drive device, and is screwed into the male screw portion to move in the axial direction. 3. A pair of non-circular gears that mesh with each other are interposed in the torque transmission device, and each of the pair of non-circular gears is fixed to the counter shaft, and a large gear and a small gear are respectively attached to the counter shaft. A large gear of the gear unit supported by one of the countershafts is meshed with a gear fixed to one rotating part, and a small gear of the gear unit is fixed to the other countershaft. The belt-type continuously variable transmission device according to claim 1, wherein the belt-type continuously variable transmission device is meshed with a gear that is meshed with a gear. 4. The gear provided on the rotating part is a gear with thin teeth, and the gear supported on the countershaft always maintains a meshing relationship with the gear with thin teeth even when the mechanical actuator moves in the axial direction. The belt-type continuously variable transmission according to claim 1, comprising a gear with thick teeth for holding.