JPH0293161A - Controller for transmission - Google Patents

Abstract

PURPOSE:To prevent the breakage of a dog clutch by installing a selector valve for the interlocking with the dog clutch and supplying a hydraulic pressure into a low clutch at an advance position or retreat position of the dog clutch and suspending the supply of the hydraulic pressure at an intermediate position. CONSTITUTION:A selector valve 502 is interlocked with a dog clutch 52 for carrying out the selection between the advance state and retreat state of a gear transmission path, and when the dog clutch 52 is at an advance position or retreat position, a hydraulic pressure is supplied into a low clutch 44, and at the intermediate position between the advance position and retreat position, the supply of the hydraulic pressure is suspended. Therefore, when the dog clutch 52 is to be switched, the hydraulic pressure supply stop state to the low clutch 44 is generated by the action of the selector valve 502, and the low clutch 44 is released, and the dog clutch can be switched in the state where no load operates. Therefore, the generation of the trouble such as breakage of the dog clutch by an impact force can be prevented.

Description

[Detailed description of the invention] (b) Industrial application field The present invention relates to a control device for a transmission.

(b) Prior art As a conventional transmission control device, for example, Japanese Patent Laid-Open No. 63-7
There is one shown in Publication No. 4735.

The transmission shown here has a V-belt continuously variable transmission mechanism and a gear transmission mechanism, and is configured to transmit rotational force through either one depending on operating conditions.

V when starting or when relatively large driving force is required.
A belt-type continuously variable transmission mechanism is used, and a gear transmission mechanism is used under operating conditions that require a relatively small driving force, such as when traveling at high speeds. A transmission path of the V-belt type continuously variable transmission mechanism is provided with a starting clutch and a dog clutch for switching forward and backward. When the start clutch is engaged and the dog clutch is switched to the forward drive side, the transmission path is placed in the forward drive state, and when the start clutch is engaged and the dog clutch is switched to the reverse drive side, the transmission path is placed in the reverse drive state.

(C) Problem to be solved by the invention However, in the conventional transmission control device described above, the starting clutch and the dog clutch for switching forward/backward are configured to be able to operate completely independently. If a situation occurs in which hydraulic pressure is supplied to the starting clutch while the dog clutch is being operated, the driving force or human power will be applied to the dog clutch, and there is a possibility that the dog clutch will be damaged. The present invention aims to solve these problems.

(d) Means for Solving the Problems The present invention links a switching valve that controls the supply of hydraulic pressure to the low clutch to utilize the gear transmission path with the dog clutch, so that during switching of the dog clutch, the hydraulic pressure is applied to the low clutch. The above problem is solved by preventing the supply of. That is, the transmission control device according to the present invention includes a gear transmission path that transmits rotational force through gears and a V-belt continuously variable transmission mechanism between the human power shaft (14) and the output shaft (46). A transmission having a V-belt transmission path that transmits rotational force in a gear ratio range smaller than the minimum gear ratio of the gear transmission path, and when transmitting rotational force through the gear transmission path, The low clutch (44) is engaged, and the high clutch (60) is engaged when transmitting rotational force via the V-belt transmission path, and the dog clutch (52) is engaged to switch the gear transmission path between forward and reverse states. ), and is provided with a switching valve (502) that operates in conjunction with a dog clutch, and when the dog clutch is in the forward or reverse position, the switching valve switches to the low clutch. It is characterized in that it is configured to supply hydraulic pressure to the low clutch and to stop supplying hydraulic pressure to the low clutch when the dog clutch is in an intermediate position between a forward position and a reverse position.

The switching valve can have the following configuration, for example. That is, the spool (518) of the switching valve and the piston (504) for switching the dog clutch are integrated, and a forward hydraulic chamber (508) and a reverse hydraulic chamber (510) are provided on both sides of the piston, respectively. The forward hydraulic chamber is connected to the forward pressure hydraulic passage (142) that outputs hydraulic pressure only when the manual valve (104) is in the forward position, and the reverse hydraulic chamber is connected to the forward pressure hydraulic passage (142) when the manual valve (104) is in the reverse position. The spool of the switching valve is connected to the reverse pressure oil passage (138) that outputs hydraulic pressure only when the forward hydraulic pressure chamber is in the position where the piston and the spool of the switching valve stroke in one direction. When the piston and the spool of the switching valve are stroked in the other direction by the hydraulic pressure acting on the reverse hydraulic chamber, the forward pressure oil passage and the low clutch are communicated with each other. Ru. Note that the symbols in parentheses indicate corresponding members in the embodiments described later.

(e) Operation When the dog clutch is in the forward or reverse position, hydraulic pressure is supplied to the low clutch. As a result, the rotational force is transmitted through the gear transmission path,
The gear transmission path is in a forward or reverse state depending on the position of the dog clutch. However, when switching the dog clutch, the supply of hydraulic pressure to the low clutch is stopped due to the action of the switching valve. Therefore, the low clutch is released, and the dog clutch is switched in a state where no load is applied. This can prevent problems such as damage to the dog clutch due to impact force.

(F) Embodiment FIGS. 2 and 3 show a transmission to which the present invention is applied. A torque converter 12 is connected to an output shaft 10a of the engine 10. The torque converter 12 includes a pump impeller 12a, a turbine runner 12b, and a stator 1.
2c, and a lock-up clutch 12d that can connect or disconnect the pump impeller 12a and the turbine runner 12b. Torque converter 1
Two turbine runners 12b are connected to the drive shaft 14. A drive pulley 16 is provided on the drive shaft 14.

The drive pulley 16 includes a fixed conical member 18 fixed to the drive shaft 14 and a V-shaped pulley groove formed by opposing the fixed conical member 18 .
The movable conical member 22 is movable in the axial direction of the drive shaft 14 by hydraulic pressure applied to the drive shaft 14. The drive pulley 16 is coupled to a driven pulley 26 by a belt 24 in a transmission manner. The driven pulley 26 is connected to the driven shaft 28
fixed conical member 30 fixed to fixed conical member 3;
The movable conical member 34 is arranged opposite to the movable conical member 34 and forms a V-shaped boob groove, and is movable in the axial direction of the driven shaft 28 by the hydraulic pressure acting on the driven pulley cylinder chamber 32. These drive pulleys 16, belt 24
and the driven pulley 26 constitute a belt type continuously variable transmission mechanism. The maximum reduction ratio of the belt type continuously variable transmission mechanism is set smaller than the reduction ratio between the forward drive shaft side gear 42 and the forward output shaft side gear 48, which will be described later. A hollow shaft 36 is rotatably supported on the outer periphery of the drive shaft 14, and a reverse drive shaft gear 38 and a forward drive shaft gear 42 are rotatably provided on the outer periphery of the hollow shaft 36. . Forward drive shaft side gear 42 and reverse drive shaft side gear 38
can be selectively connected to the hollow shaft 36 by a dog clutch 52 so as to rotate together with the hollow shaft 36. The drive shaft 14 and the hollow shaft 36 can be connected or disconnected from each other by a low clutch 44. A forward output shaft gear 48 is connected to an output shaft 46 arranged parallel to the drive shaft 14 via a one-way clutch 40, and a reverse output shaft gear 50 is provided to rotate together with the output shaft 46. .

The forward output shaft gear 48 is the same as the forward drive shaft gear 4 described above.
2 and is constantly engaged. The reverse output shaft side gear 50 is
It always meshes with a reverse idler gear 56 that rotates integrally with a reverse idler shaft 54 that is rotatably provided.

The reverse idler gear 56 is the reverse drive shaft side gear 3 described above.
8 are always engaged. In addition, in FIG. 2, all the members cannot be shown on the same cross section, so the reverse idler shaft 54 and the reverse idler gear 56 are shown by broken lines, but they are actually shown in FIG. 3. They are in such a positional relationship. Further, for the same reason, the distance between the axes, the diameter of the gear, etc. are not necessarily shown accurately in FIG. 2, and it is necessary to refer to FIG. 3 for these details. The driven shaft 28 described above is provided with a forward driven shaft side gear 58.

The driven wheel 28 and the forward driven shaft side gear 58 can be connected or disconnected from each other by a high clutch 60. The forward driven shaft gear 58 always meshes with the reverse output shaft gear 50 (in FIG. 2, the forward driven shaft gear 58 and the reverse output shaft gear 50 are shown for convenience of illustration). Although it looks like they are not interlocking, they are actually interlocking with each other as shown in Figure 3). The forward driven shaft gear 58 and the reverse output shaft gear 50 have the same diameter. A reduction gear 62 is provided on the output shaft 46 so as to rotate together with the output shaft 46, and the reduction gear 62 and the final gear 64 are always in mesh with each other. The final gear 64 is provided with a differential mechanism 66. That is, a pair of pinion gears 68 and 70 are provided to rotate together with the final gear 64, and the pinion gears 68 and 70 and the pair of side gears 72 and 74
The side gears 72 and 74 are connected to drive shafts 76 and 78, respectively.

By releasing the low clutch 44 and the high clutch 60, the transmission of the rotational force of the drive shaft 14 to the output shaft 46 is interrupted, resulting in a neutral state.

Note that the dog clutch 52 may be placed in either the forward position (F position) or the reverse position (R position).

In the case of running conditions that require a relatively large driving force, such as when starting or climbing, the dog clutch 52 is set to the F position and the low clutch 44 is engaged. high clutch 60
is in the free state. In this state, the rotational force of the output shaft 10a of the engine 10 is transmitted to the drive shaft 14 via the torque converter 12, and further transmitted from the drive shaft 14 to the hollow shaft 36 via the engaged low clutch 44. The rotational force of the hollow shaft 36 is transmitted to the forward drive shaft side gear 42 via the dog clutch 52, and from the forward drive shaft side gear 42 to the forward output shaft side gear 48 meshing therewith.

Since the forward output shaft gear 48 is connected to the output shaft 46 via the one-way clutch 40 so as to rotate together with the output shaft 46, rotational force is transmitted to the output shaft 46. Next, the rotational force is transmitted to the differential mechanism 66 via the reduction gear 62 and the final gear 64, and the differential mechanism 66 distributes the rotational force to the drive shafts 76 and 78 to drive wheels (not shown). When transmitting the rotational force as described above, the rotational force is not transmitted through the V-belt type continuously variable transmission mechanism, but is transmitted via the gear mechanism. The rotational force is increased by the reduction ratio between the forward drive shaft side gear 42 and the forward output shaft side gear 48, and thereby a large driving force can be obtained.

Next, when operating conditions are reached that require a relatively small driving force, the high clutch 60 may be engaged from the above-mentioned state. As a result, rotational force is transmitted via the V-belt type continuously variable transmission mechanism. That is, the rotational force of the drive shaft 14 is transmitted to the driven shaft 28 via the drive pulley 16, the belt 24, and the driven pulley 26, and is further transmitted to the forward driven gear 58 via the high clutch 60 in the engaged state. communicated. Since the forward driven shaft side gear 58 meshes with the reverse output shaft side gear 50, rotational force is transmitted to the output shaft 46, and further rotational force is transmitted to the drive shafts 76 and 78 as in the case described above. . In this case, the output shaft 46 rotates at a higher speed than the forward output shaft side gear 48, so the one-way clutch 40 becomes idling. Therefore, the low clutch 44 can remain engaged. As mentioned above, since the rotational force is transmitted by the V-belt type continuously variable transmission mechanism, the drive pulley 1
By adjusting the V-shaped groove spacing of the driven pulley 26 and the driven pulley 26, the gear ratio can be changed continuously.

When the vehicle transmission is placed in the reverse state, the following operations are performed. That is, the dog clutch 52 is switched to the R position so that the reverse drive shaft side gear 38 rotates together with the hollow shaft 36, the low clutch 44 is engaged, and the high clutch 60 is released. In this state, drive shaft 1
4 is transmitted to the output shaft 46 via the low clutch 44, the hollow shaft 36, the dog clutch 52, the reverse drive shaft gear 38, the reverse idler gear 56, and the reverse output shaft gear 50. Since the reverse idler gear 56 is interposed in the power transmission path, the rotation direction of the output shaft 46 is reversed from that in the above case.

This allows the vehicle to travel backwards.

Next, a control device for controlling this transmission will be explained. The control device includes an oil pump 10 as shown in FIG.
1, line pressure regulation valve 102, manual valve 104, speed change control valve 106, regulation pressure switching valve 108, speed change motor 110,
It is composed of a shift command valve 111, a shift operation mechanism 112, a throttle valve 114, a constant pressure regulating valve 116, a solenoid valve 118, a torque converter pressure regulating valve 120, a lock-up control valve 122, a dog clutch drive cylinder 500, a switching valve 502, etc. . Below, a dog clutch drive cylinder 500 and a switching valve 502 that are directly related to the present invention will be mainly described.
will be explained, and the explanation of other items will be omitted. It should be noted that the configuration of the parts whose explanation is omitted is the same as that shown in, for example, Japanese Patent Laid-Open No. 105351/1983.

The dog clutch drive cylinder 500 includes a piston 504
and a spring 506. A forward hydraulic chamber 508 is formed on the upper side of the piston 504 in the figure, and a reverse hydraulic chamber 510 is formed on the opposite side. The forward hydraulic chamber 508 is connected to the forward pressure hydraulic passage 142 via a one-way orifice 512. Further, the reverse hydraulic chamber 510 is connected to the reverse pressure oil passage 138 via a one-way orifice 514. A spring 506 presses the piston 504 downward in the figure. A drive rod 516 is provided integrally with the piston 504. The drive rod 516 is connected to the dog clutch 52. That is, when the drive rod 516 moves upward in FIG. 1, the dog clutch 52 is in the R position, and conversely, when the drive rod 516 moves downward in FIG. 1, the dog clutch 52 is in the F position.

A midway portion of the drive rod 516 is configured as a spool 518 of the switching valve 502. Spool 518 has two lands 518a and 518b. These two lands 518a and 518b and the small diameter portion between them allow the oil passage 138 and the oil passage 520 to communicate with each other when the spool 518 is moved upward in the figure (left half state).
Conversely, when the spool 518 is moved downward in the figure (the state in the right half of the figure), the oil passage 142 communicates with the oil passage 520. The oil passage 520 communicates with the low clutch 44.

Note that the high clutch 60 is supplied with the same hydraulic pressure as the drive pulley cylinder chamber 20 from the oil passage 176.

Next, the operation of this embodiment will be explained.

When the spool 136 of the manual valve 104 is switched from the N position to the forward position D or L position, hydraulic pressure is output to the forward pressure oil passage 142.

When the spool 518 of the switching valve 502 is in the state shown in the right half of the figure, that is, when the drive rod 516 is moving the dog clutch 52 to the F position, the forward pressure oil passage 14
2 oil pressure immediately passes through the oil passage 520 to the low clutch 44.
supplied to

This causes the gear mechanism to move forward. Note that when the drive rod 516 is in the R position, that is, the spool 51
8 is in the state shown in the left half of the figure, the oil pressure in the forward pressure oil passage 142 is not immediately supplied to the oil passage 520, and the oil pressure in the forward pressure oil passage 142 is first applied to the one-way orifice 512. The hydraulic pressure is supplied to the hydraulic chamber 508 for turning, thereby pushing the piston 504 downward in the figure. By doing this, at the same time as the drive rod 516 switches to the F position, the forward pressure oil passage 142 and the oil passage 520 communicate with each other, and the low clutch 4
Hydraulic pressure is supplied to 4. Therefore, when the dog clutch 52 is in the R position or the intermediate position, the low clutch 44
Hydraulic pressure is not supplied from the forward pressure oil passage 142.

Therefore, the switching operation of the dog clutch 52 is not performed while the low clutch 44 is engaged. In addition,
The same effect as described above can be obtained also when the manual valve 104 is switched from the R position to the R position or the L position. When the manual valve 104 is in the R position, the reverse pressure oil passage 143 is connected to the oil chamber 51.
0, the piston 504 is in the left half state in the figure, and when the manual valve 104 is switched to the D position or L position from this state, the hydraulic pressure in the reverse pressure oil passage 143 is discharged, and the piston 504 is in the left half state in the figure. Hydraulic pressure is supplied to the pressure oil passage 142 . In this case, the oil pressure in the oil chamber 510 is discharged relatively quickly, and on the other hand, the oil pressure flows into the oil chamber 508 under the orifice effect of the one-way orifice 512, so that the piston 504
The moving speed is the same when the manual valve 104 is switched from the N position to the forward position and when it is switched from the R position to the forward position.

Even when the manual valve 104 is switched to the R position, basically the same effect as described above can be obtained. That is, the drive rod 51
6 is in the left half of the figure, that is, when the dog clutch 52 is in the R position, the hydraulic pressure in the reverse pressure oil passage 138 immediately acts on the low clutch 44 via the oil passage 520.

Further, when the drive rod 516 is in the right half in the figure, that is, when the dog clutch 52 is in the F position, the hydraulic pressure of the reverse pressure oil passage 138 acts on the oil chamber 510, and the piston 5
04 is switched from the state in the right half of the figure to the state in the left half.

At the same time, hydraulic pressure is supplied to the low clutch 44. Therefore, also in this case, the low clutch 44 is engaged after the dog clutch 52 is switched. Therefore, the dog clutch 52 is never switched during power transmission.

(g) As described in detail, according to the present invention, the switching valve that controls the supply of hydraulic pressure to the low clutch is linked with the dog clutch, so that when switching of the dog clutch is completed, Therefore, it is possible to prevent problems such as impact force being applied during switching of the dog clutch.

[Brief explanation of the drawing]

FIG. 1 is a diagram showing a control device for a transmission according to the present invention, FIG. 2 is a schematic diagram of the transmission, and FIG. 3 is a diagram showing the positional relationship of the shafts of the transmission. 14... Drive shaft (input shaft), 44. Low clutch, 46... Output shaft, 52... Dog clutch, 60... High clutch, 500... Dog clutch drive cylinder, 502... Switching valve, 504・
... Piston, 512.514 ... One-way orifice, 516 ... Drive rod, 518 ... Spool, 1
38... Reverse pressure oil passage, 142... Forward pressure oil passage, 50
8... Oil chamber for forward movement, 510... Oil chamber for reverse movement.

Claims (1)

[Claims] 1. A gear transmission path that transmits rotational force between the input shaft and the output shaft via gears, and a V-belt type continuously variable transmission mechanism that transmits rotational force from the minimum gear ratio of the gear transmission path. A transmission having a V-belt transmission path that transmits rotational force in a region with a small gear ratio, and a low clutch is engaged when transmitting rotational force through the gear transmission path, and the V-belt transmission path In a transmission control device where a high clutch is engaged when transmitting rotational force through a dog clutch, and a dog clutch is used to switch the gear transmission path between forward and reverse states, a switching valve that works with the dog clutch is used. The switching valve supplies hydraulic pressure to the low clutch when the dog clutch is in the forward or reverse position, and supplies hydraulic pressure to the low clutch when the dog clutch is in the intermediate position between the forward and reverse positions. A control device for a transmission, characterized in that it is configured to stop supplying hydraulic pressure to a clutch. 2. The spool of the switching valve and the piston for switching the dog clutch are integrated, and a forward hydraulic chamber and a reverse hydraulic chamber are provided on both sides of the piston, respectively.
The forward hydraulic chamber is connected to the forward pressure hydraulic path that outputs hydraulic pressure only when the manual valve is in the forward position, and the reverse hydraulic chamber outputs hydraulic pressure only when the manual valve is in the reverse position. The spool of the switching valve is connected to the reverse pressure oil passage, and when the piston and the spool of the switching valve stroke in one direction due to the hydraulic pressure acting on the forward hydraulic chamber, the spool of the switching valve connects the forward pressure oil passage and the low clutch, 2. The transmission control device according to claim 1, wherein the transmission control device is configured to communicate the reverse pressure oil passage with the low clutch when the piston and the spool of the switching valve are stroked in the other direction by the hydraulic pressure acting on the reverse hydraulic chamber. 3. The forward pressure oil passage is provided with a forward side one-way orifice that generates an orifice effect when hydraulic pressure is supplied to the forward hydraulic chamber, but does not generate an orifice effect when the hydraulic pressure in the forward hydraulic chamber is discharged. The reverse pressure oil path is provided with a one-way orifice on the reverse side that generates an orifice effect when hydraulic pressure is supplied to the reverse hydraulic chamber, but does not generate an orifice effect when the hydraulic pressure in the reverse hydraulic chamber is discharged. 3. The transmission control device according to claim 2, wherein: