JP2001012599A - Lockup clutch controller for vehicular driving device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent clutch shock generated at the time of frictional clutch engaging when a gear shift operation is completed by providing an operating means for operating a lockup clutch, a means for detecting the gear shift operation of a transmission, and a control means for controlling a lockup clutch operating means. SOLUTION: This controller is composed of an internal combustion engine 2, a fluid joint 4, a frictional clutch 8, and a manual transmission 10. The fluid joint 4 is provided with a lockup clutch for directly transmitting and connecting a casing and a turbine. In the case where traveling speed of a vehicle is about 5 km/h or more, it is judged by a control means 300 that a release operation of a frictional clutch 8 is a clutch operation in a gear shift operation, and the lockup clutch is connecting controlled. Concretely, a solenoid direction control valve 67 as the lockup clutch operating means is energized. It is thus possible to prevent clutch shock generated when the gear shift operation of a vehicular driving device provided with the fluid joint is carried out.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD The present invention relates to a vehicle drive device,
More particularly, the present invention relates to a lock-up clutch control device for a vehicle drive device having a fluid coupling having a lock-up clutch.

[0002]

2. Description of the Related Art Fluid couplings have been conventionally used as power transmission couplings for ships, industrial machines, and automobiles. A vehicle drive device having a fluid coupling is disclosed, for example, in Japanese Patent Application Laid-Open No. 55-159360, in which an engine mounted on a vehicle, a fluid coupling, a friction clutch and a transmission are arranged in series. . The fluid coupling provided in such a vehicle drive device can absorb torque fluctuations and perform smooth power transmission, while the fluid coupling has an input element (pump impeller) and an output element (turbine runner). There is a problem that the power transmission efficiency is poor and the fuel efficiency is deteriorated because slip cannot be avoided between the vehicle and the vehicle. The problem due to the slip is the same in the torque converter provided in the automatic transmission. In a vehicle drive device provided with the torque converter, in order to solve the above problem, the input / output elements are directly connected under predetermined conditions. A lock-up clutch is attached.

[0003]

In a vehicle drive apparatus having a fluid coupling without a lock-up clutch disclosed in Japanese Patent Application Laid-Open No. 55-159360, the friction clutch is disengaged at the end of the gear shifting operation. When engaging, an unexpected clutch shock may occur. Also,
Even in a vehicle drive device in which the above-described lock-up clutch is attached to the fluid coupling, the clutch shock occurs if the lock-up clutch is not engaged when performing a shift operation. Hereinafter, with reference to FIG. 7, a description will be given of the operating state of each member constituting the vehicle drive device equipped with the fluid coupling at the time of shifting.

FIG. 7 shows an example of a shift at the time of upshifting. In the figure, the horizontal axis represents the elapsed time during the shift. In FIG. 7, the solid lines indicate the clutch stroke of the friction clutch,
The dotted line indicates the engine speed, the two-dot chain line indicates the clutch driven plate rotation speed of the friction clutch, and the broken line indicates the clutch drive plate rotation speed of the friction clutch. In FIG. 7, a shift operation is started at time t1 while the vehicle is running. First, the driver performs the disengagement operation of the friction clutch at time t1, and returns the accelerator pedal substantially simultaneously. As a result, the engine speed decreases as indicated by the one-dot chain line.
In this manner, when the driver performs an upshifting operation of the transmission while the engine speed is decreasing, the two-point operation is performed by the operation of the synchronization device provided in the transmission because the friction clutch is disconnected. The rotation speed of the clutch driven plate indicated by the chain line is reduced to a rotation speed corresponding to the traveling speed of the vehicle until time t2. On the other hand, when the shift-up operation of the transmission is completed, the driver starts engagement of the friction clutch at time t3, enters the half-clutch state at time t4, and at time t5, the rotational speed of the clutch driven plate and the engine rotational speed are reduced. It is determined that they match, and the friction clutch is rapidly engaged. However, the clutch drive plate of the friction clutch connected to the turbine of the fluid coupling does not decrease in rotational speed corresponding to the engine rotational speed even if the engine rotational speed decreases as described above due to its own inertial force. Therefore, the time t at which the above-described half-clutch state is established
4, there is a considerably large rotational speed difference (A) between the clutch drive plate and the clutch driven plate. For this reason, the rotation of the clutch drive plate rapidly decreases the rotation speed difference (A) from time t4 when the friction clutch is in the half-clutch state to time t5 when the friction clutch is substantially completely engaged. Unexpected clutch shock occurs.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-described circumstances, and a main technical problem thereof is that, in a drive device equipped with a fluid coupling, the occurrence of the clutch shock which occurs when a friction clutch is engaged at the end of a gearshift operation. It is an object of the present invention to provide a lock-up clutch control device for a vehicle drive device capable of preventing the occurrence of a lock.

[0006]

According to the present invention, in order to solve the above-mentioned main technical problems, an engine mounted on a vehicle, a fluid coupling operated by the engine, the fluid coupling and a transmission are provided. And a friction clutch disposed between the transmission and the transmission, wherein the fluid coupling includes a lock-up clutch, wherein a lock-up clutch operating means for operating the lock-up clutch; and A shift operation detecting means for detecting a shift operation, and a control means for controlling the lock-up clutch operating means so as to connect the lock-up clutch during a shift operation based on a detection signal from the shift operation detecting means. A lock-up clutch control device for a vehicle drive device is provided.

The speed change operation detecting means comprises clutch detecting means for detecting the engagement / disengagement of the friction clutch, and vehicle speed detecting means for detecting the traveling speed of the vehicle. The control means comprises clutch detecting means and vehicle speed detecting means. Based on the detection signal from the means, when the friction clutch is disengaged and the traveling speed of the vehicle is equal to or higher than a predetermined speed, it is determined that a shift operation is being performed.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A preferred embodiment of a lock-up clutch control device for a vehicle drive device constructed in accordance with the present invention will be described in more detail with reference to the accompanying drawings.

FIG. 1 shows an embodiment of a lock-up clutch control device in a vehicle drive device configured according to the present invention. The illustrated vehicle drive system includes an internal combustion engine 2 as a prime mover, a fluid coupling (fluid coupling) 4, a friction clutch 8, and a manual transmission 10, which are arranged in series. The internal combustion engine 2 comprises a diesel engine in the illustrated embodiment.

Next, the fluid coupling will be described with reference to FIG. The fluid coupling 4 is provided in a fluid coupling housing 40 attached to a housing 22 mounted on the diesel engine 2 by fastening means such as bolts 23. The fluid coupling 4 in the illustrated embodiment includes a casing 41, a pump 42, and a turbine 43.

A casing 41 has a bolt 44 on the outer periphery of a drive plate 44 having an inner periphery attached to the crankshaft 21 of the diesel engine 2 by bolts 24.
1, mounted by fastening means such as nut 442. A ring gear 45 for starting is engaged with the drive gear of a starter motor (not shown) on the outer periphery of the drive plate 44.

The pump 42 is disposed to face the casing 41. The pump 42 includes a bowl-shaped pump shell 421 and a plurality of impellers 422 radially arranged in the pump shell 421. The pump shell 421 is fixed to the casing 41 by welding or the like. Installed. Accordingly, the pump shell 421 of the pump 42 is connected to the crankshaft 21 via the casing 41 and the drive plate 44. For this reason, the crankshaft 21 functions as an input shaft of the fluid coupling 4.

The turbine 43 is disposed in a chamber formed by the pump 42 and the casing 41 so as to face the pump 42. The turbine 43 includes a bowl-shaped turbine shell 431 disposed to face the pump shell 421 of the pump 42, and a plurality of runners 432 radially disposed in the turbine shell 431. . The turbine shell 431 is attached to a turbine hub 47 spline-fitted to an output shaft 46 disposed on the same axis as the crankshaft 21 as the input shaft by welding or other fixing means.

The fluid coupling 4 in the illustrated embodiment has a lock-up clutch 50 for directly transmitting and connecting the casing 41 and the turbine 43. The lock-up clutch 50 includes the casing 41 and the turbine 4
3 and an outer chamber 40 between the casing 41 and the outer chamber 40.
a and between the inner chamber 40 and the turbine 43.
The clutch disk 51 for forming b is provided. The clutch disc 51 has an inner peripheral edge that is the same as that of the turbine hub 4.
7 is supported so as to be relatively rotatable and slidable in the axial direction, and a clutch facing 52 is attached to a surface facing the casing 41 on an outer peripheral portion thereof.
Further, the inner chamber 4 in the outer peripheral portion of the clutch disk 51
On the 0b side, an annular concave portion 53 is formed, and a plurality of damper springs 55 supported by support pieces 54 are arranged at predetermined intervals in the concave portion 53. On both sides of the plurality of damper springs 55, an input-side retainer 56 attached to the clutch disk 51 is provided so as to protrude therefrom, and between the damper springs 55 is attached to a turbine shell 431 of the turbine 43. The output side retainer 57 is provided to protrude.

The lock-up clutch 50 in the illustrated embodiment is configured as described above, and its operation will be described. When the pressure of the working fluid in the inside chamber 40b is higher than the pressure of the working fluid in the outside chamber 40a, that is, the working fluid supplied by the lock-up clutch operating means described later is formed by the pump 42 and the turbine 43. 4a through the inner chamber 40b to the outer chamber 40a
2, the clutch disc 51 is pressed to the left in FIG. 2, so that the clutch facing 52 attached to the clutch disc 51 is
To engage frictionally (lock-up clutch contact). Therefore, the casing 41 and the turbine 43 are directly connected to each other via the clutch facing 52, the clutch disk 51, the input side retainer 56, the damper spring 55, and the output side retainer 57. On the other hand, when the pressure of the working fluid in the outer chamber 40a is higher than the pressure of the working fluid on the inner chamber 40b side, that is, the working fluid supplied by the working fluid circulating means described later moves from the outer chamber 40a to the inner chamber 40a.
b, the clutch disc 51 is pressed to the right in FIG. 2 when circulating in the working chamber 4a formed by the pump 42 and the turbine 43, so that the clutch facing 52 mounted on the clutch disc 51
Does not frictionally engage with the casing 41 (lock-up clutch is disconnected), and therefore, the transmission connection between the casing 41 and the turbine 43 is released.

The driving device in the illustrated embodiment includes a hydraulic pump 60 as a fluid pressure source of a lock-up clutch operating means described later. The hydraulic pump 60 is mounted on the fluid coupling housing 40 by a fixing means such as a bolt 61 and is disposed on the pump housing 62. The hydraulic pump 60 is configured to be rotationally driven by a pump hub 48 attached to a pump shell 421 of the pump 42. The pump hub 48 is mounted on the cylindrical support portion 620 of the pump housing 62 which protrudes and surrounds the output shaft 46.
It is rotatably supported by zero. In addition, as shown in FIGS. 3 and 4, a working fluid passage 460 is provided in the output shaft 46 in connection with a lock-up clutch operating means described later, and the output shaft 46 and the cylindrical support 62 are provided.
A passage 461 for the working fluid is provided between the first and second passages. One end of the passage 460 communicates with the outer chamber 40a at one end thereof and opens at the left end face in the drawing of the output shaft 46, and the other end thereof communicates with a radial passage 462 opening at the outer peripheral surface of the output shaft 46. . Further, the passage 461 is configured to communicate the working chamber 4 a formed by the pump 42 and the turbine 43 with the communication hole 621 provided in the cylindrical support 620.

Next, the lock-up clutch operating means for circulating the working fluid through the fluid coupling 4 will be described with reference to FIGS. The lock-up clutch actuating means has a reserve tank 65 for containing a working fluid, and the working fluid in the reserve tank 65 is discharged to a passage 66 by the hydraulic pump 60. The working fluid discharged into the passage 66 is supplied to a passage 68 communicating with the communication hole 621 or a passage 69 communicating with the passage 462 via an electromagnetic direction control valve 67 that controls a circulation path of the working fluid. The electromagnetic direction control valve 67 is controlled by a control unit described later based on the operating state of the vehicle drive device and the traveling speed of the vehicle. When the electromagnetic direction control valve 67 is deenergized (OFF) as shown in FIG. 3, the working fluid discharged into the passage 66 is supplied to the passage 6 as indicated by an arrow.
9, passage 462, passage 460, outer chamber 40a, inner chamber 4
Ob, the working chamber 4 a formed by the pump 42 and the turbine 43, the passage 461, the communication hole 621, the passage 68, the return passage 70, the cooler 71 and the passage 72 are circulated to the reserve tank 65. When the working fluid circulates as shown by the arrow in FIG. 2, the fluid pressure of the outer chamber 40a is higher than the fluid pressure of the inner chamber 40b, so that the lock-up clutch 50 does not frictionally engage as described above (the lock-up clutch No). On the other hand, when the electromagnetic directional control valve 67 is urged (ON), the state shown in FIG. 4 is reached, and the working fluid discharged into the passage 66 passes through the passage 68, the communication hole 621, the passage 461, and the pump 42 as indicated by arrows. Working chamber 4a, inner chamber 40b, outer chamber 40 formed by turbine 43
a, passage 460, passage 462, passage 69, return passage 7
0, and is circulated to the reserve tank 65 through the cooler 71 and the passage 72. When the working fluid circulates as shown by the arrow in FIG. 4, the fluid pressure in the inner chamber 40b is higher than the fluid pressure in the outer chamber 40a, so that the lock-up clutch 5
0 is frictionally engaged as described above (lock-up clutch engagement).

In the fluid circuit in the illustrated embodiment, a relief passage 7 connecting the passage 66 and the reserve tank 65 is provided.
The relief valve 74 is provided in the relief passage 73. The relief valve 74 is set at a valve opening pressure of, for example, 6 kg / cm 2, which is a fluid pressure required for the clutch facing 52 mounted on the clutch disk 51 to be pressed by the casing 41 and frictionally engaged when the lock-up clutch is ON. Passage 6
When the working fluid pressure in 6 exceeds 6 kg / cm 2, the working fluid is returned to the reserve tank 65 via the relief passage 73.

Next, the friction clutch 8 will be described with reference to FIG. The friction clutch 8 is provided in a clutch housing 80 mounted on the fluid coupling housing 40 by bolts 81. The friction clutch 8 in the illustrated embodiment includes a clutch drive plate 82 mounted on the output shaft 46 of the fluid coupling, and the output shaft 4.
6, the input shaft 101 of the transmission 10 disposed on the same axis as the transmission 6.
And a clutch driven plate 85 attached to the clutch hub 83 and having a clutch facing 84 mounted on an outer peripheral portion thereof.
And a pressure plate 86 for pressing the clutch driven plate 85 against the clutch drive plate 82.
And a diaphragm spring 8 for urging the pressure plate 86 toward the clutch drive plate 82.
7, a release bearing 88 that engages with the inner end of the diaphragm spring 87 and operates with the middle part of the diaphragm spring 87 as a fulcrum 871, and a clutch release fork 89 that operates the release bearing 88 in the axial direction. are doing. The clutch release fork 89 includes a friction clutch operating means 90 shown in FIG.
Actuated by

The friction clutch operating means 90 in the illustrated embodiment includes a clutch pedal 91, a clutch master cylinder 92 which is operated by the clutch pedal 91 to generate hydraulic pressure, and is connected to the clutch master cylinder 92 by a hydraulic pipe 93. And a slave cylinder 94 which is operated by the hydraulic pressure generated by the clutch master cylinder 92. The piston rod 941 of the slave cylinder 94 is engaged with the end of the clutch release fork 89. In the illustrated state where the clutch pedal 91 is not depressed, the members constituting the friction clutch 8 are located in the state shown in FIG. 2, and the pressure plate 86 is moved by the spring force of the diaphragm spring 87 to the clutch drive plate 82. Pressed toward.
Therefore, the clutch facing 84 mounted on the clutch driven plate 85 is
2 and frictionally engaged (friction clutch contact), and the power transmitted to the output shaft 46 of the fluid coupling is transmitted to the input shaft 101 of the transmission 10 via the clutch drive plate 82 and the clutch driven plate 85. . When the clutch pedal 91 is depressed, the clutch master cylinder 92
When the hydraulic pressure is generated, the slave cylinder 94 operates and the release bearing 88 is moved to the left in FIG. For this reason, the diaphragm spring 87 is operated as shown by a two-dot chain line in FIG. 2, and the power transmission from the clutch drive plate 82 to the clutch driven plate 85 is cut off by releasing the pressing force on the pressure plate 86. (Friction clutch disconnected).

The vehicle drive device in the illustrated embodiment is configured as described above, and its operation will be described below. First, a case where power is transmitted by the action of the working fluid by the fluid coupling 4 will be described. In this case, the electromagnetic direction control valve 67 of the lock-up clutch operating means is used.
Is deenergized (OFF), and the working fluid is circulated in the direction indicated by the arrow in FIG. 3 as described above. In the state where the working fluid is circulated in the direction indicated by the arrow in FIG. 3, the pressure of the outer chamber 40a is higher than the pressure of the inner chamber 40b as described above, and the clutch disc 51 is moved to the right in FIGS. As a result, the clutch facing 52 mounted on the clutch disc 51 does not frictionally engage with the casing 41 (lock-up clutch is disconnected). As a result, the driving force generated on the crankshaft 21 (input shaft) of the diesel engine 2 is
As described above, the power is transmitted to the casing 41 of the fluid coupling 4 via the drive plate 44. Since the casing 41 and the pump shell 421 of the pump 42 are integrally formed, the pump 42 is rotated by the driving force. When the pump 42 rotates, the working fluid in the pump 42 flows toward the outer periphery along the impeller 422 due to centrifugal force, and flows into the turbine 43 as indicated by an arrow. The working fluid flowing into the turbine 43 flows toward the center side and is returned to the pump 42 as indicated by an arrow. As described above, the working fluid in the working chamber 4a formed by the pump 42 and the turbine 43 circulates in the pump 42 and the turbine 43, so that the driving torque of the pump 42 is transmitted to the turbine 43 through the working fluid. Is transmitted. Turbine 4
The driving force transmitted to the third side is transmitted to the output shaft 46 via the turbine shell 431 and the turbine hub 47, and further transmitted to the transmission 10 via the friction clutch 8.

Next, a state in which the lock-up clutch 50 is operated to directly connect the casing 41 and the turbine 43 to transmit the driving torque will be described. In this case, the electromagnetic direction control valve 67 of the lock-up clutch operating means is energized (ON), and the working fluid is circulated in the direction indicated by the arrow in FIG. In the state where the working fluid is circulated in the direction indicated by the arrow in FIG.
As described above, the pressure in the inner chamber 40b is higher than the pressure in the outer chamber 40a, and the clutch disc 51
At the left side, the clutch disc 51
The clutch facing 52 mounted on the casing 4
1 and frictionally engaged (lock-up clutch engagement). As a result, the casing 41, the pump 42, and the turbine 43 are directly driven by the clutch facing 52, the clutch disc 51, the input side retainer 56, the damper spring 54, and the output side retainer 57. Therefore, the crankshaft 21 of the diesel engine 2
The driving force generated on the (input shaft)
4, transmitted to the output shaft 46 via the casing 41, the lock-up clutch 50, the turbine 43, and the turbine hub 47, and further transmitted to the transmission 10 via the friction clutch 8.

Next, the lock-up clutch control device will be described with reference to FIG. The lock-up clutch control device in the illustrated embodiment includes an engine speed detection unit 2 that detects the rotation speed of the diesel engine 2.
01, clutch detecting means 202 for detecting the engagement / disengagement of the friction clutch 8, input shaft rotational speed detecting means 203 for detecting the rotational speed of the input shaft 101 of the transmission 10, and the speed position of the transmission 10. Speed detecting means 204 for detecting
And a vehicle speed detecting means 205 for detecting a running speed of the vehicle. The engine speed detecting means 201 includes, for example, a pulse generator disposed opposite to the ring gear 45, and sends a detection signal to a control means described later. In the illustrated embodiment, the clutch detecting means 202 comprises a potentiometer for detecting the operating position of the clutch release fork 89, that is, the amount of clutch engagement,
The detection signal is sent to control means described later. The input shaft rotation number detecting means 203 is composed of a pulse generator arranged opposite to the input shaft 101 of the transmission 10 and sends out a detection signal to a control means described later. Shift speed detecting means 204
Consists of a group of switches for detecting, for example, the selection and shift position of the shift lever 110, and sends out a detection signal to a control means described later. And the control means described later,
The shift speed is determined by a combination of the switches corresponding to the transmitted signal. In the illustrated embodiment, the vehicle speed detecting means 205 is composed of a pulse generator disposed opposite to the output shaft 102 of the transmission 10, and sends a detection signal to a control means described later.

The lock-up clutch control device in the illustrated embodiment has a control means 300. The control means 300 is constituted by a microcomputer, and includes a central processing unit (CPU) 301 for performing arithmetic processing according to a control program, a read-only memory (ROM) 302 for storing a control program, and a readable and writable storage for storing a calculation result and the like. Random access memory (RA
M) 303, and an input interface 304 and an output interface 305. The input interface 304 of the control means 300 thus configured
The detection signals from the engine speed detecting means 201, the clutch detecting means 202, the input shaft speed detecting means 203, the gear position detecting means 204, and the vehicle speed detecting means 205 are input to the CPU. Also, from the output interface 305,
The electromagnetic direction control valve 6 of the lock-up clutch operating means
7 to output a control signal.

The lock-up clutch control device in the illustrated embodiment is configured as described above, and the operation procedure of the control means 300 will be described below with reference to the flowchart shown in FIG. The control means 300 first checks whether or not the friction clutch 8 is disengaged based on a detection signal from the clutch detection means 202 in step S1. If the friction clutch 8 is disengaged in step S1, the control means 300 proceeds to step S2 and checks whether or not the traveling speed (V) of the vehicle is 5 km / h or more based on the detection signal from the vehicle speed detection means 205. I do. If the traveling speed (V) of the vehicle is less than 5 km / h in step S2, the control means 300 determines that the disconnection operation of the friction clutch 8 in step S1 is a clutch operation at the time of starting, and proceeds to step S3. To perform the disconnection control of the lock-up clutch 50, and return to step S1. Specifically, the disconnection control of the lock-up clutch 50 deactivates (turns off) the electromagnetic direction control valve 67 of the lock-up clutch operating means. If the traveling speed (V) of the vehicle is 5 km / h or more in step S2, the control means 300
Determines that the disengagement operation of the friction clutch 8 in step S1 is a clutch operation at the time of a shift operation, and determines in step S4
Then, the engagement control of the lock-up clutch 50 is executed. Specifically, the control means 300 biases (ON) the electromagnetic direction control valve 67 of the lock-up clutch operating means. As described above, when the friction clutch 8 is disengaged and the traveling speed (V) of the vehicle is 5 km / h or more, it is determined that a shift operation is being performed. In the illustrated embodiment, the clutch detection means 202 and the vehicle speed detection means 205 is the transmission 10
Function as shift operation detecting means for detecting the shift operation of the vehicle.

As described above, in the illustrated embodiment,
At the time of shifting operation of the transmission 10, the lock-up clutch 50
To directly connect the casing 41 and the turbine 43, it is possible to prevent the occurrence of the clutch shock at the time of a shift operation of the vehicle drive device having the fluid coupling. Hereinafter, the reason why the occurrence of the clutch shock can be prevented will be described with reference to FIG. FIG. 6 shows an example of a shift at the time of upshifting. In the figure, the horizontal axis indicates the elapsed time during the shift. In FIG. 6, the upper solid line is the disconnected / connected state of the lock-up clutch (L / U clutch) 50, the clutch stroke of the lower friction clutch 8, the chain line is the rotational speed of the engine 2, and the broken line is the friction clutch 8. The rotation speed of the clutch drive plate 82 and the two-dot chain line indicate the rotation speed of the clutch driven plate 85 of the friction clutch 8. In FIG. 6, a shift operation is started at time T1 while the vehicle is running. First, the driver performs the disengagement operation of the friction clutch 8 at time T1, and returns the accelerator pedal substantially simultaneously. As a result, the engine speed decreases as indicated by the one-dot chain line. In this manner, when the driver performs an upshift operation of the transmission 10 while the engine speed is decreasing, the operation of the synchronization device provided in the transmission 10 because the friction clutch 8 is disconnected. As a result, the rotation speed of the clutch driven plate 85 indicated by the two-dot chain line is reduced to the rotation speed corresponding to the traveling speed of the vehicle until time T3. On the other hand, as described above, at time T2 when the clutch stroke position at which the friction clutch is substantially disengaged during the disengagement operation of the friction clutch 8, the L / U clutch 50 is engaged as described above. When the L / U clutch 50 is brought into contact, the fluid coupling 4
The casing 41 and the pump 42 and the turbine 43 are directly connected and integrated, so that the clutch drive plate 82
As shown by the broken line immediately matches the engine speed. When the shift-up operation of the transmission is completed, the driver starts to connect the friction clutch 8 at time T4, enters the half-clutch state at time T5, and turns on at time T6.
It is determined that the rotational speed of the clutch driven plate 85 and the engine rotational speed coincide with each other, and the friction clutch 8 is rapidly engaged. At this time, since the rotation speed of the clutch drive plate 82 matches the engine rotation speed as described above, the rotation speeds of the clutch drive plate 82 and the clutch driven plate 85 match, and there is a difference in rotation speed between the two. Since there is no shock, no shock occurs even if the engagement is sudden. That is, by engaging the L / U clutch 50 during the gear shifting operation, the engine rotation speed and the rotation speed of the clutch drive plate 82 match, so that the rotation can be adjusted in the same manner as in a normal drive device without a fluid coupling. . Note that the L / U clutch 50 engaged during the gear shifting operation
The transmission 1 is connected to the friction clutch 8 as described later.
If the shift stage of 0 is less than the third speed, for example, the traveling speed (V) of the vehicle is less than 30 km / h, for example, or if the engine speed (R) is less than 1000 rpm, it is cut off.

Returning to the flowchart shown in FIG. 5, the description will be continued. If the friction clutch 8 is not disconnected in step S1, that is, if the friction clutch 8 is in the engaged state, the control means 300 proceeds to step S5 and performs L / U.
It is checked whether the clutch 50 is engaged. This check is made based on whether or not the electromagnetic direction control valve 67 is energized (ON) in the illustrated embodiment. If the L / U clutch 50 is engaged in step S5, the control means 300 proceeds to step S6, where the transmission 10
It is checked whether or not the shift speed is, for example, the third speed or higher. If the speed of the transmission 10 is not higher than the third speed in step S6, that is, if it is lower than the second speed, the control unit 30
In step S3, the process goes to step S3 to disconnect the L / U clutch 50. This is because, in the case of a truck or the like, the second speed is often set as the starting gear, and the driving force is large. Therefore, when the L / U clutch 50 is in the directly connected state, a shift shock occurs. L / U to prevent
The clutch 50 is disconnected.

In step S6, the transmission 1
If the 0 gear is, for example, 3rd gear or higher, the control means 300
Goes to step S7, and checks whether or not the traveling speed (V) of the vehicle is, for example, 30 km / h or more. Step S7
If the traveling speed (V) is not equal to or higher than 30 km / h, that is, is lower than 30 km / h, the control means 300
Proceeds to step S3 to disconnect the L / U clutch 50.
This is because, when the L / U clutch 50 is in the directly connected state during low-speed running, a torque fluctuation appears remarkably in response to the movement of the accelerator pedal, and a so-called jerky feeling is generated. L / U clutch 50
Refuse.

If the running speed (V) of the vehicle is, for example, 30 km / h or more in step S7, the control means 300 proceeds to step S8 to check whether or not the engine speed is, for example, 1000 rpm or more. In step S8, the engine speed (R) is 1000 rpm
If not more than m, that is, if it is less than 1000 rpm, the control means 300 proceeds to step S3 to disconnect the L / U clutch 50. This is because if the L / U clutch 50 is directly connected while the engine is running at low speed, the engine may stall.
Cut off 0.

If the L / U clutch 50 is not engaged in step S5, that is, if the L / U clutch 50 has been disengaged, the control means 300 proceeds to step S9 and sets the speed of the transmission 10 to, for example, 3 Check if it is faster or faster. If the shift stage of the transmission 10 is not higher than the third speed in step S9, the shift shock may occur if the L / U clutch 50 is directly connected as described above, so that the L / U clutch 50 is maintained in the disengaged state. Then, the process returns to step S1.

If the shift speed is higher than the third speed in step S9, the control means 300 proceeds to step S10, where the rotational difference between the pump 42 (P) and the turbine 43 (T) is 2
It is checked whether or not it is 00 rpm or less (PT ≦ 200 rpm). In step S10, the pump 42
If the rotational difference between (P) and the turbine 43 (T) is not less than 200 rpm, that is, if the rotational difference is larger than 200 rpm, a large shock will occur if the L / U clutch 50 is directly connected. Is maintained in the disconnected state, and the process returns to step S1.

In step S10, the pump 42
If the rotation difference between (P) and the turbine 43 (T) is 200 rpm or less, the control means 300 proceeds to step S11 to check whether the running speed (V) of the vehicle is, for example, 30 km / h or more. If the traveling speed (V) is not equal to or greater than 30 km / h in step S11, that is, 30 km / h
h, the L / U clutch 50 as described above.
Is directly connected, a so-called jerky feeling is generated. Therefore, the L / U clutch 50 is maintained in the disengaged state, and the process returns to step S1.

If the traveling speed (V) is 30 km / h or more in step S11, the control means 300
Goes to step S12 to check whether the engine speed (R) is, for example, 1000 rpm or more. In step S12, the engine speed (R) is 1000
If it is not more than rpm, that is, if it is less than 1000 rpm, there is a possibility that engine stall will occur if the L / U clutch 50 is directly connected. Therefore, the L / U clutch 50 is kept disconnected and the process returns to the step S1. Step S12
If the engine speed (R) is equal to or higher than 1000 rpm, the control means 300 proceeds to step S4 and performs L /
With the U-clutch 50 engaged, the process returns to step S1.

Although the present invention has been described based on the illustrated embodiment, the present invention is not limited to the embodiment, and various modifications can be made within the technical idea of the present invention. For example, in the illustrated embodiment, an example of a shift operation detecting unit that detects a shift operation of a transmission includes a clutch detecting unit that detects disconnection / engagement of a friction clutch and a vehicle speed detecting unit that detects a traveling speed of a vehicle. Although shown, for example, in a vehicle equipped with an automatic clutch, a signal from a shift instruction switch provided on a shift lever may be used.

[0035]

The lock-up clutch control device for a vehicle drive device according to the present invention is constructed as described above, and has the following operational effects.

That is, according to the present invention, in the vehicle drive device having the fluid coupling provided with the lock-up clutch, the lock-up clutch is connected at the time of gear shifting operation, so that the clutch drive plate of the friction clutch and the clutch driven Since rotation adjustment with the plate 5 can be performed in the same manner as in a normal drive device without a fluid coupling, it is possible to prevent the occurrence of clutch shock caused by a difference in rotation speed between the clutch drive plate and the clutch driven plate 5. . In addition, since it is easy to engage the friction clutch by adjusting the rotational speeds of the clutch drive plate and the clutch driven plate, wear of the clutch facing is reduced, and durability of the clutch facing is improved.

[Brief description of the drawings]

FIG. 1 is a schematic block diagram showing an embodiment of a lock-up clutch control device for a vehicle drive device configured according to the present invention.

FIG. 2 is a sectional view showing an embodiment of a vehicle drive device applied to the present invention.

FIG. 3 is an explanatory view showing an operation state of a lock-up clutch operating means provided in the vehicle drive device shown in FIG. 2, in which a lock-up clutch is disconnected.

FIG. 4 is an explanatory view showing an operation state of a lock-up clutch operation means provided in the vehicle drive device shown in FIG. 2 and showing a lock-up clutch contact state.

5 is a flowchart showing the operation of control means provided in the lock-up clutch control device of the vehicle drive device shown in FIG.

FIG. 6 is a diagram showing a clutch stroke, an engine speed, a clutch drive plate speed, and a clutch driven plate speed when a lock-up clutch is engaged during a gear shift operation by the lock-up clutch control device shown in FIG. 1;

FIG. 7 is a diagram showing a clutch stroke, an engine speed, a clutch drive plate speed, and a clutch driven plate speed during a gear shift operation in a drive device having a conventional fluid coupling.

[Explanation of symbols]

 2: Internal combustion engine 21: Crankshaft 4: Fluid coupling 40: Fluid coupling housing 41: Casing 42: Pump 421: Pump shell 422: Impeller 43: Turbine 431: Turbine shell 432: Runner 44: Drive plate 45: Ring gear 46: Output Shaft 47: Turbine hub 48: Pump hub 50: Lock-up clutch 51: Clutch disk 54: Support piece 55: Damper spring 56: Input side retainer 57: Output side retainer 60: Hydraulic pump 62: Pump housing 65: Reserve tank 67: Electromagnetic Direction control valve 71: Cooler 74: Relief valve 75: Restrictor 8: Friction clutch 80: Clutch housing 82: Clutch drive plate 83: Clutch hub 84: Clutch facing 85: Driven plate 86: Release plate 87: Diaphragm spring 88: Release bearing 89: Clutch release fork 90: Friction clutch operating means 91: Clutch pedal 92: Clutch master cylinder 94: Slave cylinder 10: Transmission 101: Transmission input shaft 102: Transmission Output shaft 110: Gear lever 201: Engine speed detecting means 202: Clutch detecting means 203: Input shaft speed detecting means 204: Gear position detecting means 205: Vehicle speed detecting means 300: Control means

Claims (2)

[Claims] 1. An engine mounted on a vehicle, a fluid coupling operated by the engine, and a friction clutch disposed between the fluid coupling and a transmission, wherein the fluid coupling locks up. In a vehicle drive device having a clutch, a lock-up clutch operating means for operating the lock-up clutch; a shift operation detecting means for detecting a shift operation of the transmission; and a detection signal from the shift operation detecting means. Control means for controlling the lock-up clutch actuating means so as to connect the lock-up clutch at the time of a gear shift operation. 2. The speed change operation detecting means comprises: clutch detecting means for detecting disconnection / engagement of the friction clutch; and vehicle speed detecting means for detecting a traveling speed of the vehicle. 2. The lock-up of a vehicle drive device according to claim 1, wherein when the friction clutch is disengaged and the running speed of the vehicle is equal to or higher than a predetermined speed, it is determined that a shift operation is being performed based on the detection signal from the vehicle speed detecting device. Clutch control unit.