CA1174616A - Actuating device for a clutch - Google Patents
Actuating device for a clutchInfo
- Publication number
- CA1174616A CA1174616A CA000394128A CA394128A CA1174616A CA 1174616 A CA1174616 A CA 1174616A CA 000394128 A CA000394128 A CA 000394128A CA 394128 A CA394128 A CA 394128A CA 1174616 A CA1174616 A CA 1174616A
- Authority
- CA
- Canada
- Prior art keywords
- valve
- clutch
- return
- pressure
- return valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/14—Fluid pressure control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D48/04—Control by fluid pressure providing power assistance
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0209—Control by fluid pressure characterised by fluid valves having control pistons, e.g. spools
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A hydraulic actuating device for disengaging a clutch engaged by spring force contains a valve arrangement which enables disengagement to be effected even if the drive motor is at a standstill and no pump energy is available. The valve arrangement controlling the disengaging operation and compris-ing a blocking position, a through-flow position and a control position, may be moved into an overtravel position by a rod movable via the clutch pedal. The overtravel position is felt as pressure point on the clutch pedal. In the process, the valve arrangement mechanically pushes open a return valve via a supporting piston whereby the return valve connects a pres-sure reservoir with a servomotor of the clutch.
A hydraulic actuating device for disengaging a clutch engaged by spring force contains a valve arrangement which enables disengagement to be effected even if the drive motor is at a standstill and no pump energy is available. The valve arrangement controlling the disengaging operation and compris-ing a blocking position, a through-flow position and a control position, may be moved into an overtravel position by a rod movable via the clutch pedal. The overtravel position is felt as pressure point on the clutch pedal. In the process, the valve arrangement mechanically pushes open a return valve via a supporting piston whereby the return valve connects a pres-sure reservoir with a servomotor of the clutch.
Description
~174616 This invention relates to an actuating device for opening a clutch closed by a force. It particularly relates to an actuating device for hydraulically opening a clutch closed by spring force, of a particular type which include an oil supply unit and a valve unit.
An actuating device for opening a clutch closed by spring force is known from Offenlegungsschrift 26 36 982. In this device a valve unit in the form of a 2/2-way-magnetic valve is fitted into the feed line leading from the oil supply unit to the operating cylinder. From a line section situated between the magnetic valve and the operating cylinder a return line branches off into which is fitted a further 2/2-way-magnetic valve. In order to disengage the clutch while the motor is running and the pump is being driven, the magnetic valve fitted into the feed line is switched into a through-flow position II and the magnetic valve fitted into the return line is switched into a blocking position I. The hydraulic oil flowing into the servo-motor thus disengages the clutch thrust plate via a lever against a spring force. When the motor is at a standstill, disengaging of the clutch gives rise to difficulties insofar as on the one hand the pump does not supply any hydraulic energy, and as on the other hand the drive line is tensioned with a gear inserted. It is therefore not possible, in par-ticular on truck gearboxes, to take the gear out without dis-engaging the clutch. For this reason the oil supply unit of the known actuating device additionally contains a pressure reservoir which supplies the hydraulic energy for disengaging when the motor is at a standstill. With this arrangement the change-over of the two magnetic valves has to be effected in such a way that the magnetic valve controlling the return line is switched into the blocking position I, before the mag-netic valve controlling the feed line and thereby the pressure ~k 1~74616 reservoir is switched into the through-flow position II. This switching sequence must be adhered to under all circumstances in order to avoid emptying of the pressure reservoir. With the known actuating device an operationally safe change-over of the magnetic valves for the purpose of disengaging while the motor is at a standstill is therefore not as yet possible.
It is an object of the present invention to provide an actuating device for disengaging the clutch with the motor while at a standstill, which is inexpensive to construct and which ensures high operational safety. With such arrangement, the control section of the actuating device may be designed in such a way that operating problems are avoided.
In one aspect of the present invention, there is provided an actuating device for hydraulically opening a clutch closed by spring force, of the type having: an oil supply unit comprising a tank, a pump, a pressure reservoir and a return valve cooperating with the pressure reservoir which is connected with a feed line; a valve unit with a blocking position I and a through-flow position II for con-trolling a servomotor which is inserted between the feed line and a return line; characterized in that: (a) the valve unit comprises a pressure regulating valve with a control position III situated between the blocking position I and the through-flow position II; (b) a branch line leading to the servomotor and which is connected to the feed line; (c) a spring acting upon a control piston of the valve unit and which is supported against a rod connected with a clutch pedal; (d) a return valve connected to the branch line and associated with the valve unit, whereby the return valve acts as unblocking valve for the pressure reservoir, and (e) the rod comes to rest against the control piston in an overtravel position following upon the blocking position I and moves the return valve into 1~46~,6 the opening position.
According to the present invention the valve unit for disengaging the clutch and the return valve connecting the pressure reservoir with the clutch when the motor is at a standstill are arranged in the same axis inside a common hous-ing. When the valve unit is moved via a hydraulically operable rod past the blocking position I into an overtravel position, the valve unit comes to rest against a supporting piston which, in turn, comes to rest against the return valve. After over-coming a pressure point the return valve is pushed open. The energy stored in the pressure reservoir is thus available in the operating cylinder for disengaging. The fact that unblock-ing of the return valve is effected by mechanical coupling results in high operational safety of the actuating device.
With this arrangement it is advantageous that the reservoir pressure responsible for the pressure point ~ears upon the return valve. Overcoming this pressure point at the clutch pedal signals to the driver the use of the pressure reservoir.
Also, due to using a seat valve as return valve, the pressure reservoir is leakproof to a very high degree~
The use of a pressure-regulating valve in the ac-tuating device also has the advantage of providing for sensi-tive metering of the clutch pressure during normal vehicle operation.
The invention is illustrated by way of example in the accompanying drawing wherein:
Figure 1 is a hydraulic schematic of the actuating device according to the present invention; and Figure 2 is a simplified section through the valve arrangement defined by the chain-dotted line in Figure 1.
As shown in Fig. 1 the oil supply unit of the ac-tuating device comprises an oil tank 1, a filter 2, a pump 3 ~746~6 and a pressure reservoir 4. The pump 3 is connected via a feed line 5 with a valve unit 6 shaped as pressure-regulating valve. In relation to a return line 7 the valve unit 6 has a blocking position I, a through-flow position II and a control position III. ~he return line leads to the gearbox lubrication via an oil cooler 8. From there the oil is returned to the tank 1.
A branch line 10 of the feed line 5 is connected with a servomotor 11 of a clutch 12. In the same axis as the valve unit 6 a return valve 13 is provided acting as unblock-ing valve for the pressure reservoir 4. Via the return valve 13 the pressure reservoir 4 may be connected with the branch line 10. The branch line 10 is also connected with the return line 7 via a pressure limiting valve 14.
As is recognisable from Fig. 2 the valve unit 6 is adjustable via a master cylinder 16, a link line 17 and a slave cylinder 18, when the clutch pedal 15 is depressed. A
piston 20 in the slave cylinder 18 presses via a rod 21 against a spring 22. This spring 22 is supported via a spring plate 23 against a control piston 25 of the valve unit 6, whereby the control piston is vable in a housing bore 24. A collar 19 of the rod 21 extends into a bore of the piston 25. A
re-adjusting spring 26 presses against the rod 21. The con-trol piston 25 has a control edge 27 which may disconnect an annular groove 5A connected to the feed line 5 from an annular groove 7A connected to the return line 7. In the housing bore 24 a supporting piston 28 and a piston 30 of the return valve 13 are arranged in the same axis with the control piston 25.
The return valve 13, being a seat valve, is provided with a seating edge 31 and a sealing cone 32. The hydraulic oil advanced by the pump 3 via a feed line 5 acts upon one face 33 of the supporting piston 28 as well as upon the face 34 of the ~.~74616 piston 30 facing the supporting piston. With a full reservoir 4 the reservoir pressure bears upon a larger face 35 so that the piston 30 remains in the closing position shown. The suE)porting piston 28 has a shoulder 37 which when the piston 6 i.s ved into the overtravel position, rests against a cup spring 36.
Referring now to operation of the present device.
According to Fig. 1 and 2 the clutch 12 is closed by spring force and the hydraulic oil delivered by the pump 3 may flow via the valve unit 6 which is in through-flow position II to the return line 7 and thus to the gearbox lubrication. There-fore, pressure cannot build up either in the branch line 10 or in the servomotor 11.
If the clutch shall be disengaged while the motor is running, the pump 3 is driven, the driver operates the clutch pedal 15 within the control position III. This has the effect, due to the hydraulic force introduced at the master cylinder 16, that the piston 20 of the slave cylinder 18 is moved upwards and the tension of spring 22 is increased via the rod 21. As a result the flow cross-section to the annular groove 7A determined by the control edge 27 of the control piston 25 is reduced. In order to keep the control edge 27 open, the pump 3 is now required to exert more pressure corres-ponding to the force of the spring 22 upon the face 33 of the supporting piston 28. The force resulting from the pump pres-sure and the spring force are thus equal during activation of the clutch. The pressure increased in this way is effective via the branch line 10 in the servomotor 11 causing the clutch 12 to open.
When the motor is at a standstill the pump 3 is not driven, disengaging may be effected as follows: As the clutch pedal 15 is depressed the control piston 25 is placed into 117~G16 blocking position I by the force of the spring 22. Due to the absence of pump pressure on the face 33 of the supporting piston 28 the control edge 27 completely closes the annular groove 7A connected with the return line 7. The shoulder 37 of the supporting piston 28 now comes to rest against the cup spring 36, and simultaneously the face 33 comes to rest against the piston 30 of the return valve 13. To open the piston 30, the force of the reservoir pressure upon the face 35 and the force of the cup spring 36 must be overcome. This additional force out of pressure and cup spring is distinctly felt as pressure point in the overtravel position on the clutch pedal 15. To overcome this force, the rod 21 presses with the collar 19 directly against the control piston 25 so that the unblocking force is transmitted to the piston 30 of the return valve 13 by a mechanical coupling. Once the piston 30 has been pushed open the servomotor 11 is moved into the 'disengage' position by the reservoir pressure.
It is also possible to dimension the diameter of the piston 30 such that a sufficiently large unblocking force is generated solely via the face 35 acted upon by the reservoir pressure. In this case the cup spring 36 may be omitted.
. . .
An actuating device for opening a clutch closed by spring force is known from Offenlegungsschrift 26 36 982. In this device a valve unit in the form of a 2/2-way-magnetic valve is fitted into the feed line leading from the oil supply unit to the operating cylinder. From a line section situated between the magnetic valve and the operating cylinder a return line branches off into which is fitted a further 2/2-way-magnetic valve. In order to disengage the clutch while the motor is running and the pump is being driven, the magnetic valve fitted into the feed line is switched into a through-flow position II and the magnetic valve fitted into the return line is switched into a blocking position I. The hydraulic oil flowing into the servo-motor thus disengages the clutch thrust plate via a lever against a spring force. When the motor is at a standstill, disengaging of the clutch gives rise to difficulties insofar as on the one hand the pump does not supply any hydraulic energy, and as on the other hand the drive line is tensioned with a gear inserted. It is therefore not possible, in par-ticular on truck gearboxes, to take the gear out without dis-engaging the clutch. For this reason the oil supply unit of the known actuating device additionally contains a pressure reservoir which supplies the hydraulic energy for disengaging when the motor is at a standstill. With this arrangement the change-over of the two magnetic valves has to be effected in such a way that the magnetic valve controlling the return line is switched into the blocking position I, before the mag-netic valve controlling the feed line and thereby the pressure ~k 1~74616 reservoir is switched into the through-flow position II. This switching sequence must be adhered to under all circumstances in order to avoid emptying of the pressure reservoir. With the known actuating device an operationally safe change-over of the magnetic valves for the purpose of disengaging while the motor is at a standstill is therefore not as yet possible.
It is an object of the present invention to provide an actuating device for disengaging the clutch with the motor while at a standstill, which is inexpensive to construct and which ensures high operational safety. With such arrangement, the control section of the actuating device may be designed in such a way that operating problems are avoided.
In one aspect of the present invention, there is provided an actuating device for hydraulically opening a clutch closed by spring force, of the type having: an oil supply unit comprising a tank, a pump, a pressure reservoir and a return valve cooperating with the pressure reservoir which is connected with a feed line; a valve unit with a blocking position I and a through-flow position II for con-trolling a servomotor which is inserted between the feed line and a return line; characterized in that: (a) the valve unit comprises a pressure regulating valve with a control position III situated between the blocking position I and the through-flow position II; (b) a branch line leading to the servomotor and which is connected to the feed line; (c) a spring acting upon a control piston of the valve unit and which is supported against a rod connected with a clutch pedal; (d) a return valve connected to the branch line and associated with the valve unit, whereby the return valve acts as unblocking valve for the pressure reservoir, and (e) the rod comes to rest against the control piston in an overtravel position following upon the blocking position I and moves the return valve into 1~46~,6 the opening position.
According to the present invention the valve unit for disengaging the clutch and the return valve connecting the pressure reservoir with the clutch when the motor is at a standstill are arranged in the same axis inside a common hous-ing. When the valve unit is moved via a hydraulically operable rod past the blocking position I into an overtravel position, the valve unit comes to rest against a supporting piston which, in turn, comes to rest against the return valve. After over-coming a pressure point the return valve is pushed open. The energy stored in the pressure reservoir is thus available in the operating cylinder for disengaging. The fact that unblock-ing of the return valve is effected by mechanical coupling results in high operational safety of the actuating device.
With this arrangement it is advantageous that the reservoir pressure responsible for the pressure point ~ears upon the return valve. Overcoming this pressure point at the clutch pedal signals to the driver the use of the pressure reservoir.
Also, due to using a seat valve as return valve, the pressure reservoir is leakproof to a very high degree~
The use of a pressure-regulating valve in the ac-tuating device also has the advantage of providing for sensi-tive metering of the clutch pressure during normal vehicle operation.
The invention is illustrated by way of example in the accompanying drawing wherein:
Figure 1 is a hydraulic schematic of the actuating device according to the present invention; and Figure 2 is a simplified section through the valve arrangement defined by the chain-dotted line in Figure 1.
As shown in Fig. 1 the oil supply unit of the ac-tuating device comprises an oil tank 1, a filter 2, a pump 3 ~746~6 and a pressure reservoir 4. The pump 3 is connected via a feed line 5 with a valve unit 6 shaped as pressure-regulating valve. In relation to a return line 7 the valve unit 6 has a blocking position I, a through-flow position II and a control position III. ~he return line leads to the gearbox lubrication via an oil cooler 8. From there the oil is returned to the tank 1.
A branch line 10 of the feed line 5 is connected with a servomotor 11 of a clutch 12. In the same axis as the valve unit 6 a return valve 13 is provided acting as unblock-ing valve for the pressure reservoir 4. Via the return valve 13 the pressure reservoir 4 may be connected with the branch line 10. The branch line 10 is also connected with the return line 7 via a pressure limiting valve 14.
As is recognisable from Fig. 2 the valve unit 6 is adjustable via a master cylinder 16, a link line 17 and a slave cylinder 18, when the clutch pedal 15 is depressed. A
piston 20 in the slave cylinder 18 presses via a rod 21 against a spring 22. This spring 22 is supported via a spring plate 23 against a control piston 25 of the valve unit 6, whereby the control piston is vable in a housing bore 24. A collar 19 of the rod 21 extends into a bore of the piston 25. A
re-adjusting spring 26 presses against the rod 21. The con-trol piston 25 has a control edge 27 which may disconnect an annular groove 5A connected to the feed line 5 from an annular groove 7A connected to the return line 7. In the housing bore 24 a supporting piston 28 and a piston 30 of the return valve 13 are arranged in the same axis with the control piston 25.
The return valve 13, being a seat valve, is provided with a seating edge 31 and a sealing cone 32. The hydraulic oil advanced by the pump 3 via a feed line 5 acts upon one face 33 of the supporting piston 28 as well as upon the face 34 of the ~.~74616 piston 30 facing the supporting piston. With a full reservoir 4 the reservoir pressure bears upon a larger face 35 so that the piston 30 remains in the closing position shown. The suE)porting piston 28 has a shoulder 37 which when the piston 6 i.s ved into the overtravel position, rests against a cup spring 36.
Referring now to operation of the present device.
According to Fig. 1 and 2 the clutch 12 is closed by spring force and the hydraulic oil delivered by the pump 3 may flow via the valve unit 6 which is in through-flow position II to the return line 7 and thus to the gearbox lubrication. There-fore, pressure cannot build up either in the branch line 10 or in the servomotor 11.
If the clutch shall be disengaged while the motor is running, the pump 3 is driven, the driver operates the clutch pedal 15 within the control position III. This has the effect, due to the hydraulic force introduced at the master cylinder 16, that the piston 20 of the slave cylinder 18 is moved upwards and the tension of spring 22 is increased via the rod 21. As a result the flow cross-section to the annular groove 7A determined by the control edge 27 of the control piston 25 is reduced. In order to keep the control edge 27 open, the pump 3 is now required to exert more pressure corres-ponding to the force of the spring 22 upon the face 33 of the supporting piston 28. The force resulting from the pump pres-sure and the spring force are thus equal during activation of the clutch. The pressure increased in this way is effective via the branch line 10 in the servomotor 11 causing the clutch 12 to open.
When the motor is at a standstill the pump 3 is not driven, disengaging may be effected as follows: As the clutch pedal 15 is depressed the control piston 25 is placed into 117~G16 blocking position I by the force of the spring 22. Due to the absence of pump pressure on the face 33 of the supporting piston 28 the control edge 27 completely closes the annular groove 7A connected with the return line 7. The shoulder 37 of the supporting piston 28 now comes to rest against the cup spring 36, and simultaneously the face 33 comes to rest against the piston 30 of the return valve 13. To open the piston 30, the force of the reservoir pressure upon the face 35 and the force of the cup spring 36 must be overcome. This additional force out of pressure and cup spring is distinctly felt as pressure point in the overtravel position on the clutch pedal 15. To overcome this force, the rod 21 presses with the collar 19 directly against the control piston 25 so that the unblocking force is transmitted to the piston 30 of the return valve 13 by a mechanical coupling. Once the piston 30 has been pushed open the servomotor 11 is moved into the 'disengage' position by the reservoir pressure.
It is also possible to dimension the diameter of the piston 30 such that a sufficiently large unblocking force is generated solely via the face 35 acted upon by the reservoir pressure. In this case the cup spring 36 may be omitted.
. . .
Claims
1. An actuating device for hydraulically opening a clutch closed by spring force, of the type having: an oil supply unit comprising a tank (1), a pump (3), a pressure reservoir (4) and a return valve (13) cooperating with the pressure reservoir which is connected with a feed line (5):
a valve unit (6) with a blocking position I and a through-flow position II for controlling a servomotor 111) which is inserted between the feed line 15) and a return line (7);
characterized in that: (a) the valve unit 16) comprises a pressure regulating valve with a control position III situated between the blocking position I and the through-flow position II, (b) a branch line (10) leading to the servomotor (11) and which is connected to the feed line (S), (c) a spring (22) acting upon a control piston (25) of the valve unit (6) and which is supported against a rod (21) connected with a clutch pedal (15); (d) a return valve (13) connected to the branch line (10) and associated with the valve unit (6), whereby the return valve acts as unblocking valve for the pressure reservoir (4), and (e) the rod (21) comes to rest against the control piston (25) in an overtravel position following upon the blocking position I and moves the return valve (13) into the opening position.
a valve unit (6) with a blocking position I and a through-flow position II for controlling a servomotor 111) which is inserted between the feed line 15) and a return line (7);
characterized in that: (a) the valve unit 16) comprises a pressure regulating valve with a control position III situated between the blocking position I and the through-flow position II, (b) a branch line (10) leading to the servomotor (11) and which is connected to the feed line (S), (c) a spring (22) acting upon a control piston (25) of the valve unit (6) and which is supported against a rod (21) connected with a clutch pedal (15); (d) a return valve (13) connected to the branch line (10) and associated with the valve unit (6), whereby the return valve acts as unblocking valve for the pressure reservoir (4), and (e) the rod (21) comes to rest against the control piston (25) in an overtravel position following upon the blocking position I and moves the return valve (13) into the opening position.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DEP3105239.8-21 | 1981-02-13 | ||
| DE19813105239 DE3105239C2 (en) | 1981-02-13 | 1981-02-13 | Actuating device for a clutch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1174616A true CA1174616A (en) | 1984-09-18 |
Family
ID=6124790
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000394128A Expired CA1174616A (en) | 1981-02-13 | 1982-01-14 | Actuating device for a clutch |
Country Status (5)
| Country | Link |
|---|---|
| CA (1) | CA1174616A (en) |
| DE (1) | DE3105239C2 (en) |
| FR (1) | FR2500094A1 (en) |
| GB (1) | GB2093143B (en) |
| SE (1) | SE8200868L (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3422153A1 (en) * | 1984-06-14 | 1985-12-19 | Alfred Teves Gmbh, 6000 Frankfurt | SERVO POWER REINFORCEMENT DEVICE |
| DE3900987A1 (en) * | 1989-01-14 | 1990-07-26 | Bosch Gmbh Robert | Fluid-actuated transmission clutch |
| FR2848505B1 (en) * | 2002-12-12 | 2005-12-23 | Peugeot Citroen Automobiles Sa | CLUTCH CONTROL DEVICE AND CORRESPONDING MOTOR VEHICLE |
| DE112014000470A5 (en) * | 2013-01-18 | 2015-09-24 | Schaeffler Technologies AG & Co. KG | Fluidic system and method for driving a clutch device |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1180970A (en) * | 1956-08-13 | 1959-06-10 | Gen Motors Corp | Control device for motor vehicle power transmission mechanism |
| DE1167193B (en) * | 1958-12-23 | 1964-04-02 | Zahnradfabrik Friedrichshafen | Device for controlling the engagement and disengagement of a clutch of a motor vehicle actuated by pressure medium |
| GB1019729A (en) * | 1964-10-21 | 1966-02-09 | Cessna Aircraft Co | A combination fluid displacing master cylinder and flow control valve |
| US3348644A (en) * | 1965-07-19 | 1967-10-24 | Twin Disc Clutch Co | Control for a power drive system and including shift-restricting inhibitors for a reversible transmission |
| DE2132144B2 (en) * | 1971-06-29 | 1973-09-27 | Voith Getriebe Kg, 7920 Heidenheim | Hydrodynamic vehicle drive, in particular for a forklift |
| GB1425917A (en) * | 1972-08-19 | 1976-02-25 | Solartron Electronic Group | Rms converter |
| GB1459419A (en) * | 1973-01-22 | 1976-12-22 | Automotive Prod Co Ltd | Clutch operating mechanisms for motor vehicles |
| JPS585338B2 (en) * | 1975-04-14 | 1983-01-31 | 株式会社小松製作所 | Kutsusakutsumikomishiyariyou |
| DE2604608A1 (en) * | 1976-02-06 | 1977-08-11 | Hengstler Hydraulik | Hydraulic actuator for friction clutch - has pressure relief control and valves with pneumatic pressure store to facilitate gradual clutch engagement |
| US4036342A (en) * | 1976-06-28 | 1977-07-19 | Towmotor Corporation | Inching valve with means preventing high pressure inching |
| US4093051A (en) * | 1976-08-02 | 1978-06-06 | Allis-Chalmers Corporation | Hydraulic control system for power shift transmission |
-
1981
- 1981-02-13 DE DE19813105239 patent/DE3105239C2/en not_active Expired
- 1981-12-08 GB GB8136918A patent/GB2093143B/en not_active Expired
-
1982
- 1982-01-14 CA CA000394128A patent/CA1174616A/en not_active Expired
- 1982-02-11 FR FR8202390A patent/FR2500094A1/en not_active Withdrawn
- 1982-02-12 SE SE8200868A patent/SE8200868L/en not_active Application Discontinuation
Also Published As
| Publication number | Publication date |
|---|---|
| DE3105239A1 (en) | 1982-09-02 |
| GB2093143A (en) | 1982-08-25 |
| SE8200868L (en) | 1982-08-14 |
| DE3105239C2 (en) | 1982-12-02 |
| GB2093143B (en) | 1984-12-05 |
| FR2500094A1 (en) | 1982-08-20 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEC | Expiry (correction) | ||
| MKEX | Expiry |