WO2010081743A1 - Aktuierungsanordnung - Google Patents
Aktuierungsanordnung Download PDFInfo
- Publication number
- WO2010081743A1 WO2010081743A1 PCT/EP2010/000277 EP2010000277W WO2010081743A1 WO 2010081743 A1 WO2010081743 A1 WO 2010081743A1 EP 2010000277 W EP2010000277 W EP 2010000277W WO 2010081743 A1 WO2010081743 A1 WO 2010081743A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- hydraulic
- actuating unit
- pump
- hydraulic actuating
- Prior art date
Links
- 239000012530 fluid Substances 0.000 claims abstract description 27
- 230000008878 coupling Effects 0.000 claims description 18
- 238000010168 coupling process Methods 0.000 claims description 18
- 238000005859 coupling reaction Methods 0.000 claims description 18
- 238000000034 method Methods 0.000 claims description 10
- 230000002457 bidirectional effect Effects 0.000 claims description 2
- 238000011144 upstream manufacturing Methods 0.000 claims 1
- 230000005540 biological transmission Effects 0.000 description 11
- 230000008901 benefit Effects 0.000 description 7
- 238000012546 transfer Methods 0.000 description 7
- 230000002349 favourable effect Effects 0.000 description 5
- 238000003860 storage Methods 0.000 description 4
- 238000013461 design Methods 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- 230000004913 activation Effects 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 238000009530 blood pressure measurement Methods 0.000 description 1
- 210000000078 claw Anatomy 0.000 description 1
- 230000001447 compensatory effect Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000009969 flowable effect Effects 0.000 description 1
- 238000012432 intermediate storage Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
- B60K23/08—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles
-
- 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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/348—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed
- B60K17/35—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed including arrangements for suppressing or influencing the power transfer, e.g. viscous clutches
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
- B60K23/08—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles
- B60K23/0808—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles for varying torque distribution between driven axles, e.g. by transfer clutch
-
- 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
- F16D48/0206—Control by fluid pressure in a system with a plurality of fluid-actuated clutches
-
- 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
- F16D2048/0227—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices
- F16D2048/0233—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices by rotary pump actuation
- F16D2048/0245—Electrically driven rotary pumps
- F16D2048/0248—Reversible rotary pumps, i.e. pumps that can be rotated in the two directions
-
- 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
- F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
- F16D2048/0281—Complex circuits with more than two valves in series or special arrangements thereof not provided for in previous groups
-
- 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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/102—Actuator
- F16D2500/1026—Hydraulic
-
- 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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/302—Signal inputs from the actuator
- F16D2500/3024—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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
- F16D2500/70402—Actuator parameters
- F16D2500/7041—Position
Definitions
- the invention relates to a hydraulic arrangement for actuating a clutch in the drive train of a motor vehicle.
- the hydraulic arrangement can be used to actuate a connection clutch for on-demand connection of a secondary drive axle to a permanently driven primary drive axle.
- Such drive systems which enable switching from a two-wheel drive to a four-wheel drive, are also referred to as on-demand or hang-on systems.
- a torque transmission mechanism with a pump, a pressure accumulator and a plurality of hydraulically actuated clutches is known.
- the pressure accumulator is filled.
- the couplings can be acted upon with hydraulic pressure from the pressure accumulator.
- a drive unit with two friction clutches with hydraulic actuator is known.
- the two friction clutches are connected to one another via a short-circuit line with a safety valve.
- the pressure in the first clutch decreases, the hydraulic fluid can flow to the second clutch.
- the first clutch is opened and the second clutch is closed.
- the hydraulic system comprises a pump, which is driven by a drive shaft of the motor vehicle and which has a hydraulic see pressure generated to actuate a piston-cylinder unit.
- the piston-cylinder unit serves to actuate a friction clutch with which a secondary drive axle in the drive train of the motor vehicle can be switched on.
- the hydraulic assembly may include a pressure accumulator that can be charged by the pump and that can generate a relatively large volume flow for pressurizing the piston-cylinder unit.
- the drive assembly includes a transfer case that distributes torque introduced by a motor to a first drive axle and a second drive axle, and a longitudinal drive shaft that is in torque flow between the transfer case and the second drive axle.
- a first coupling at the first end of the longitudinal drive shaft and a second coupling at the second end of the longitudinal drive shaft In the closed state of the two clutches, torque is transmitted to the shiftable second drive axle. In the open state of the two clutches, the longitudinal drive shaft is decoupled with all rotating components of the engine and the second drive axle, so that it stands still.
- DE 10 2004 033 439 B4 discloses a drive train for a motor vehicle having a friction clutch for transmitting torque and having an actuator arrangement for actuating the friction clutch.
- the actuator assembly includes a first pump designed to close the friction clutch quickly with little effort, and a second pump designed to operate the friction clutch with a large force at a low lift.
- the two pumps have different hydraulic ratios.
- the present invention has for its object to provide an actuation arrangement for actuating at least two clutches in the drive train of a motor vehicle, which has a low switching time and allows a sensitive control. Furthermore, the object is to propose a drive arrangement for the drive train of a motor vehicle, which allows a fast connection and sensitive control of a switchable drive axle. The invention tion is also the object of proposing a method for connecting a drive axle in the drive train of a motor vehicle, which allows a low switching time.
- a first solution consists in an actuation arrangement for connecting a drive axle in the drive train of a motor vehicle, comprising a pump for generating a hydraulic pressure; a pressure accumulator which can be filled by the pump with hydraulic fluid to generate a pre-pressure; a first hydraulic actuating unit for actuating a first clutch in the drive train of the motor vehicle; a second hydraulic actuating unit for actuating a second clutch in the drive train of the motor vehicle; wherein at least one of the two first or second hydraulic actuating units can be acted upon by the pressure accumulator with hydraulic pressure, and, after the at least partial emptying of the pressure accumulator, additionally acted upon by the pump, wherein the associated first or second clutch is actuated in the closing direction.
- the pump is designed in particular as a bidirectional pump which can be actuated in a first conveying direction and an opposite second conveying direction. It is provided that upon actuation of the pump in the first conveying direction of the pressure accumulator can be filled with hydraulic fluid, while actuation of the pump in the second conveying direction at least one of the two clutches in the closing direction is actuated.
- the advantage is that the Aktu réellesanssen meets in a favorable manner, the demand for a short switching time for connecting the secondary drive train with a sensitive control of the torque to be transmitted to the secondary drive axle.
- the pressure accumulator is charged by the pump, whereby a hydraulic pre-pressure is generated.
- hydraulic fluid is pumped from the accumulator into the hydraulic system, wherein one or both of the actuating units are acted upon.
- This emptying of the pressure accumulator takes place abruptly, that is, it is pressed in a short time, a relatively large volume flow in the hydraulic system for actuating the first and second clutch.
- at least one of the two actuating units is activated, preferably at de operating units.
- the actuating units of the first solution are designed such that the associated clutch is acted upon in the closing direction by application of hydraulic pressure. Another advantage of the present actuator arrangement is that it is enabled in the event of failure of the hydraulic system, which is also referred to as a fail-safe function.
- the delivery volume of the pressure accumulator is preferably designed so that in the completely deflated state, the clutch release clearance in the at least one clutch is at least largely bypassed.
- clutch clearance is the way to understand the two relatively rotatable coupling parts can be moved against each other without torque between the two coupling parts is transmitted.
- the pressure accumulator is particularly dimensioned so that the volume flow is sufficient to fully actuate the first hydraulic actuator unit and the second hydraulic actuator unit to actuate so far that the clearance of the second clutch is reduced to a desired amount. Through the pressure accumulator is achieved in an advantageous manner that this clutch clearance is pushed out relatively quickly from the respective clutch. Subsequent to the emptying of the pressure accumulator, a sensitive control can then take over the demand-related adjustment of the torque by corresponding activation of the associated actuation unit.
- both the first and the second hydraulic actuating unit can be acted upon by the pressure accumulator with hydraulic pressure. In this way it is ensured that both clutches are switched approximately simultaneously.
- the actuation of the two actuation units takes place in dependence on the driving situation by appropriate control of valves. It is generally conceivable that both clutches are switched simultaneously. Depending on the design of the clutches, it is also conceivable that one of the two actuating units is acted upon by a small time advance to close the associated clutch in time before the other.
- the hydraulic actuation unit which defines the amount of torque transmitted to the secondary drive axle is pressurized by the pump as required with hydraulic pressure. beat.
- the pump allows a sensitive control of the actuator unit and thus also an adjustment of the torque transmitted to the secondary axle. This has a favorable effect on the driving stability of the motor vehicle.
- a second solution consists in an actuation arrangement for connecting a drive axle in the drive train of a motor vehicle, comprising a pump for generating a hydraulic pressure; a first hydraulic actuating unit, which can be acted upon by the pump against a counterforce with hydraulic pressure, wherein a pre-pressure in the first hydraulic actuating unit can be stored, with which a first clutch in the drive train of the motor vehicle is held in an open position; a second hydraulic actuating unit, which can be acted upon by the pre-pressure stored in the first hydraulic actuating unit; and, which can also be acted upon by the pump with hydraulic pressure, wherein a second clutch for transmitting a torque in the drive train of the motor vehicle is closed by acting on the second hydraulic actuating unit.
- the counterforce which acts against the hydraulic pressure of the pump, is preferably generated by an elastic element, for example a spring.
- the peculiarity of the second solution is that the first hydraulic actuator performs two functions, namely the application of the first clutch and the application of the second clutch.
- the first actuating unit can store hydraulic pressure and, to that extent, can also be referred to as an actuating pressure accumulator unit.
- a hydraulic pre-pressure is generated in the first actuating unit, with which the first clutch is held in the open position.
- the admission pressure is used to pressurize the second hydraulic actuation unit. Both the first and the second clutch are closed.
- the advantage is that by the hydraulic pre-pressure of the spring-loaded first actuating unit, a fast closing of the second actuating unit takes place. This is achieved by a relatively large volume flow. A sensitive regulation of the over- carrying torque of the second clutch can then be done by the pump.
- the first and the second hydraulic actuator are designed so that the maximum of the first hydraulic actuator to the second hydraulic actuator unit flowable volume flow is so large that the clutch release clearance of the second clutch is at least largely bridged.
- This offers the advantage that the clutch clearance is bridged quickly by the relatively large volume flow, so that the setting of the transferable to the secondary drive axle torque can be made quickly.
- the maximum actuating stroke which can be generated by emptying the first hydraulic actuating unit on the second hydraulic actuating unit approximates the clutch clearance of the second clutch, in particular corresponds approximately to the clutch clearance. This results in a particularly fast connection of the second clutch. A sensitive needs-based control of the clutch torque is then adjusted by means of the pump.
- the pump is preferably drivable by means of an electric motor, that is, by adjusting the current, the flow rate of the pump is infinitely variable.
- the pump is preferably designed in the form of a two-way pump. Upon actuation of the pump in a first conveying direction, the first hydraulic actuating unit is acted upon. In this case, the second hydraulic actuating unit preferably remains unactuated or is emptied in the opening direction of the second clutch. In this way it is achieved that both clutches are opened in the first conveying direction. Upon actuation of the pump in an opposite second conveying direction, the second hydraulic actuating unit is acted upon, wherein the first hydraulic actuating unit remains unencumbered.
- the first hydraulic actuating unit and the second hydraulic actuating unit are preferably connected to one another via a connecting channel, which comprises at least one valve for opening and closing. By opening the at least one valve, hydraulic fluid is conveyed from the first hydraulic actuating unit to the second hydraulic actuating unit.
- a multi-way valve is arranged between the pump and the two actuating units so that this connects the first actuating unit mutually with the pump or the second actuator unit.
- a check valve is further arranged, which prevents the backflow of the oil from the first actuating unit. Thereby, the pump can be switched off after filling the first operating unit without the first operating unit emptied.
- a first valve is arranged between the pump and the first actuating unit, and a second valve is arranged between the pump and the second actuating unit.
- two further check valves connect the two pump sides with the reservoir, so that the pump can suck in oil in both directions if necessary from the reservoir.
- the valves are controlled, for example, by means of an electronic control unit, which regulates the driving dynamics of the motor vehicle.
- the input signal for the control unit may be the pressure measured in the line to the second actuating unit.
- a pressure sensor is preferably provided.
- the first hydraulic actuating unit comprises a piston-cylinder unit which has an accumulator function.
- the first hydraulic actuating unit comprises a first spring which acts against the pressure force of the pump, the piston of the piston-cylinder unit.
- the first Coupling is acted upon by the first spring in the closing direction.
- the piston By generating a hydraulic pressure, the piston is moved in the direction of the spring, so that the spring biases the piston.
- the piston By opening a valve, the piston is pressed by the spring in the closing direction of the first clutch, the chamber of the piston 5 cylinder unit is suddenly emptied.
- the first clutch is closed.
- the hydraulic fluid in the chamber is conveyed to the second actuating unit, so that the second clutch is at least partially closed.
- the first hydraulic actuator comprises a second spring which acts on the piston of the piston-cylinder unit against the pressure force of the pump, wherein the second spring has a lower spring stiffness than the first spring.
- the second spring may be axially supported on a support surface of the piston-cylinder unit according to a first possibility, that is, the first and the second spring
- the first clutch is preferably designed in the form of a lockup clutch, wherein the lockup clutch between an open position in which no torque transfer bar, and a closed position in which the full torque is transmitted, is switchable.
- a lock-up clutch a toothed clutch or a dog clutch may be mentioned here.
- a so-called Sperrsynchronisiertechnik can be designed as a lock-up clutch.
- the second clutch is preferably designed in the form of a friction clutch, wherein the transmittable by the friction clutch torque is variably controllable by the pump.
- the switching order is preferably such that first the lock-up clutch is switched, and then the torque transmission is adjusted by means of the friction clutch. In this case, the clutch torque of the friction clutch can be adjusted continuously.
- a third hydraulic actuator unit for actuating a third clutch is provided.
- the third clutch is designed in particular in the form of a lock-up clutch, which serves to lock a differential gear.
- the solution of the above object further consists in a drive arrangement for a motor vehicle with a permanently driven first drive axle and a switchable as needed second drive axle, wherein a drive train for driving the second drive axle has a first clutch and a second clutch, wherein for actuating the first and second Clutch an Aktu- michsan extract is provided according to one of the above embodiments.
- the advantage of the drive arrangement according to the invention is that it can be quickly switched from a two-wheel drive mode to a four-wheel drive mode as needed.
- the permanently driven drive axle is the front axle and the drive axle which can be engaged as required is the rear axle of the motor vehicle.
- the second clutch can be arranged, for example, coaxially to the axis of rotation of a rear differential, which is particularly advantageous insofar as the angle drive for driving the rear differential is also stationary when the rear axle is switched off.
- the second clutch may also be arranged coaxially to a longitudinal drive shaft or a shaft section of the longitudinal drive shaft of the motor vehicle.
- the first clutch is preferably arranged in the torque flow between a front axle differential and an angle drive, which serves for branching the torque from the front axle to the longitudinal drive shaft.
- the permanently driven drive axle is the rear axle, and the front axle is switched on by means of the actuation arrangement if required.
- the solution of the above object is further in a method for connecting a drive axle in the drive train of a motor vehicle by means of an actuator assembly, wherein the Aktu istsanssen comprises the following components: a pump for generating a hydraulic pressure; a pressure accumulator which can be filled by the pump with hydraulic fluid to generate a pre-pressure; a first hydraulic actuating unit for actuating a first clutch in the drive train of the motor vehicle, wherein the first hydraulic actuating unit can be acted upon hydraulically by the pressure accumulator or forms the pressure accumulator; and a second hydraulic actuating unit for actuating a second clutch in the drive train of the motor vehicle, wherein the second hydraulic actuating unit is hydraulically acted upon by the pressure accumulator; comprising the steps of: filling the pressure accumulator with hydraulic fluid by means of the pump, wherein a hydraulic pre-pressure is generated, and at least partially emptying the pressure accumulator, wherein the first clutch for transmitting a torque is completely closed and the second clutch is at least partially
- This method applies to both of the above solutions as well as their preferred embodiments. This allows a short switching time, since the stored admission pressure in the pressure accumulator is used both to close the first clutch and to at least partially close the second clutch. It is understood that all of the embodiments or operating modes described in connection with the abovementioned actuation arrangements can be transferred to the method according to the invention.
- the first and the second friction clutch are actuated upon application of the respectively associated actuating unit with hydraulic fluid from the pressure accumulator in the closing direction.
- the first clutch is opened against a spring force when the associated first actuating unit is pressurized. By releasing the hydraulic pressure from the first actuating unit, hydraulic fluid flows from the first actuating unit to the second actuating unit, wherein the first and the second clutch are closed.
- the second hydraulic actuating unit for actuating the second clutch after the complete emptying of the pressure accumulator by means of the pump is required applied with hydraulic pressure.
- the pump operates bidirectionally, wherein the filling of the pressure accumulator takes place by operating the pump in a first conveying direction, and wherein the loading of the second hydraulic actuating unit takes place by actuating the pump in an opposite second conveying direction.
- FIG. 1 shows a hydraulic actuation arrangement according to the invention in a first embodiment
- FIG. 2 shows a hydraulic actuation arrangement according to the invention in a second embodiment
- FIG. 3 shows a hydraulic actuation arrangement according to the invention in a third embodiment
- FIG. 4 shows a hydraulic actuation arrangement according to the invention in a fourth embodiment
- FIG. 5 shows a hydraulic actuation arrangement according to the invention in a fifth embodiment
- FIG. 6 shows a hydraulic actuation arrangement according to the invention in a sixth embodiment
- FIG. 7 shows a drive arrangement with a hydraulic actuation arrangement according to the invention according to one of the FIGS. 1 to 6 in a first embodiment
- FIG. 8 shows a drive arrangement with a hydraulic actuation arrangement according to the invention according to one of the figures 1 to 6 in a second embodiment
- FIG. 10 shows a drive arrangement with a hydraulic actuation arrangement according to the invention according to one of the figures 1 to 6 in a fourth embodiment.
- FIG. 1 shows a hydraulic actuation arrangement 2 according to the invention for actuating a first clutch 3 and a second clutch 4 in the drive train of a motor vehicle.
- the first clutch 3 and the second clutch 4 are used for connecting a secondary drive axle (not shown here) to a permanently driven primary drive axle as required.
- the torque transmission is interrupted on the secondary drive axle.
- a portion of the drive train lying in the torque flow between the two clutches is decoupled from the permanently driven first drive axle and from the shiftable second drive axle. In this case, the portion lying between the two drive axles of the drive train is stationary, so that friction losses, which arise due to rotational movements of all rotating components, are reduced.
- the hydraulic arrangement 2 comprises a first hydraulic actuating unit 5, which preferably comprises a piston-cylinder unit 6 with a hydraulic chamber 7 and a control piston 8 which is slidably received in the hydraulic chamber 7.
- the adjusting piston 8 is sealed by means of a ring seal, which is seated in a circumferential groove of the actuating piston 8, relative to the cylinder wall and serves to actuate a sliding sleeve 9, which can actuate the first clutch 3.
- the shift sleeve 9 can be converted into a first shift position, in which the first clutch is fully open, so that no torque is transmitted, as well as in a second shift position, in which the first clutch is completely concluded for the transmission of torque.
- the loading of the first clutch 3 in the closing direction is represented by an arrow.
- the shift sleeve is acted upon by a first spring 11 against the Aktu réelleskraft the piston-cylinder unit 6, which is axially supported relative to a stationary member 12.
- the standing component 12 may be, for example, the gear housing of an angle drive, which is also referred to as "Power Transfer Unit” or “Power Takeoff Unit” (PTU).
- the hydraulic actuator assembly 2 further comprises a second hydraulic actuator unit 13, which preferably also with a piston-cylinder unit a hydraulic chamber 14 and a slidably in the hydraulic chamber 14 einitzenden actuating piston 15 comprises.
- the second clutch 4 is preferably designed in the form of a friction clutch which controls the adjustment of the torque to be transmitted between an open position in which no torque is transmitted, and a closed position in which the maximum torque is transmitted, is variably controllable.
- a hydraulic pump 16 In order to generate a hydraulic pressure on the first hydraulic actuating unit 5 or the second hydraulic actuating unit 13, a hydraulic pump 16 is provided.
- the hydraulic pump 16 is connected via a connecting channel 17 to a pressure accumulator 18.
- a check valve 19 In the connecting channel 17, a check valve 19 is provided, which prevents the pump 16 is switched off, hydraulic fluid from the pressure accumulator 18 back to the second actuating unit 13 and into the reservoir 10 flows.
- the pressure accumulator 18 comprises a storage chamber 20 which is connected via the connecting channel 17 with the pump 16. When the pump 16 is actuated, this hydraulic fluid conveys into the storage chamber 20 against the force of the spring means 22.
- the pressure accumulator 18 is connected via a connecting line 24 with the first hydraulic actuation unit 5, wherein in the line 24, a valve 25 is arranged.
- the valve 25 is preferably designed in the form of a switching valve.
- the first hydraulic actuator 5 is connected to the pressure accumulator 18, so that the chamber 7 of the pressure accumulator 18 is filled with hydraulic fluid.
- the piston 8 is moved against the force of the spring 11 to close the associated first clutch 3.
- the chamber 7 is connected to the reservoir 10 for discharging the hydraulic fluid.
- the first clutch 3 is acted upon by the spring 11 in the opening direction, so that the torque flow to the second drive axle is interrupted. In this case, hydraulic fluid escapes from the chamber 7 into the reservoir 10.
- the pressure accumulator 18 is further connected via a connecting line 26 with the second hydraulic raulischen actuating unit 13, wherein in the connecting line 26, a further valve 27 is provided.
- the valve 27 is preferably designed as a switching valve, which is switchable to a first position in which the second hydraulic actuating unit 13 is connected to the pressure accumulator 18, and in a second switching position in which the connecting line 26 is interrupted. If the valve 27 is switched to the first position, then the chamber 14 of the second actuating unit 13 is filled by the pressure accumulator 18 with hydraulic fluid until the pressure accumulator 18 is emptied.
- the piston 15 acts on the second clutch 4 in the closing direction, so that torque is transmitted to the secondary drive axle.
- the circuit of the first valve 25 for actuating the first actuating unit 5 and the second valve 27 for actuating the second actuating unit 13 takes place as required by appropriate control by means of an electronic control unit which controls the driving dynamics of the motor vehicle or the torque transmission to the drive axles. It is favorable for a fast coupling of the secondary drive train, when the two valves 25, 27 are switched in about the same time. A certain offset timing may be advantageous to ensure that first one of the two clutches is securely closed before the other clutch 4 is switched on.
- the delivery volume of the pressure accumulator 18 is preferably designed so that in the fully deflated condition, the first clutch 3 is fully closed and that the clearance in the second clutch 4 is bridged at least for the most part. In this way, it is achieved that after unlocking the valve 27, the coupling clearance is pressed out relatively quickly from the second clutch by means of the pressure accumulator 18.
- a particularly fast connection of the second drive axle is made possible when the volume flow of the pressure accumulator 18 is sufficient to completely close the first clutch 3 and to largely bridge the clutch clearance from the second clutch 4.
- the pump 16 is then connected, which takes over the need-based adjustment of the torque by sensitive control.
- the hydraulic pump 16 is drivable by means of an electric motor 21, that is, by adjusting the current, the flow rate of the pump 16 is infinitely variable.
- the pump 16 can deliver hydraulic fluid in two directions of rotation.
- the suction side of the pump 16 can be connected to the hydraulic chamber 14 of the second actuating unit 13 or to the reservoir 10.
- the hydraulic fluid in the hydraulic chamber 14 of the second actuating unit 13 is conveyed via a line 38 into the pressure accumulator 18.
- the second clutch 4 is fully opened and in the accumulator 18, a hydraulic pre-pressure is built up. If the hydraulic chamber 14 is pumped empty, further hydraulic fluid is conveyed out of the reservoir 10 through a second line 39 into the pressure accumulator 18. In the second line 39, a further check valve 19 and a filter is provided.
- the first clutch 3 is held by the spring 11 in the open position.
- hydraulic fluid is sucked through the conduit 40 from the reservoir 10 and conveyed through the line 38 to the second actuator unit 13, so that the second clutch 4 is acted upon accordingly.
- the first hydraulic actuating unit 5 is already transferred by the emptying of the pressure accumulator 18 in the closed position, in which the first clutch 3 is closed to transmit torque. That is, in the second rotational direction, only the second actuating unit 13 and thus the associated second clutch 4 is actuated. This allows a sensitive adjustment of the transferable to the secondary drive axle torque.
- the design of the hydraulic pump can be chosen arbitrarily; examples For example, vane pumps, gear pumps or piston pumps can be used.
- the pump 16 can deliver in two directions.
- the control of the electric motor 21 via an electronic control unit, which regulates the distribution of torque on the drive axles or their wheels.
- the pressure measured at the second operating unit 13 is used as an input to the control unit.
- a pressure sensor 31 is provided, which is connected to the control unit.
- Figure 2 shows a hydraulic actuator assembly according to the invention in a second embodiment, which corresponds to that of Figure 1 in large parts.
- the same or corresponding components are provided with the same reference numerals.
- the peculiarity of the present embodiment lies in the fact that the first hydraulic actuating unit 5 serves firstly for actuating the first clutch 3 and secondly as an accumulator for generating a pre-pressure with which the second hydraulic actuating unit 13 can be acted upon.
- the piston 8 By filling the hydraulic chamber 7 of the piston-cylinder unit 6, the piston 8 is moved to the right, wherein the shift sleeve 9 is axially displaced against the force of the first spring 11 in the opening direction of the first clutch 3.
- In fully filled state of the hydraulic chamber 7 is shift sleeve 9 in its final position, wherein the first clutch 3, which is actuated by the shift sleeve 9, is fully open, d. H. no torque is transmitted to the secondary drive axle.
- a multi-way valve 25 is arranged between the pump 16 and the two actuator units 5, 13 so as to connect the first actuator unit 5 to either the pump 16 or the second actuator unit 13. Furthermore, a check valve 19 is arranged between the pump 16 and the first actuation unit 5, which prevents the return flow of the oil from the first actuation unit 5.
- the multi-way valve 25 is transferred to a first switching position, so that the pump 16 is connected via the connecting channels 17 and 24 with the first hydraulic actuating unit 5, wherein the pump 16 is driven in a first rotational direction , If the secondary second drive axle to be switched, the multi-way valve 25 is transferred to the second switching position, which is shown here.
- the hydraulic chamber 7 of the first hydraulic operating unit 5 is connected to the hydraulic chamber 14 of the second hydraulic operating unit 13 via the connecting passages 24 and 26.
- the piston 8 of the first actuating unit 5 is acted upon by the spring 11 to the left, whereby hydraulic fluid flows through the channels 24 and 26 in the hydraulic chamber 14 of the second actuator unit 13.
- the shift sleeve is moved to the left, whereby the first clutch 3 is completely closed.
- the first clutch 3 is preferably designed in the form of a lock-up clutch. A particularly smooth switching is guaranteed if the two relatively rotatable coupling parts are synchronized before the non-rotatable connection.
- a Sperrsynchronisierkupplung can be used as the first clutch 3.
- the first clutch 3 can also be designed in the form of a friction clutch, in particular a friction disk clutch.
- the second clutch 4 is preferably designed in the form of a friction clutch, which has a certain axial clearance. Only after the release of the clearance from the friction clutch does this begin to transmit a torque from the clutch input part to the clutch output part.
- the volume of the first hydraulic chamber 7 in relation to the volume of the second hydraulic chamber 14 is adjusted so that by completely emptying the first hydraulic chamber 7, the clearance from the second clutch 4 is at least largely squeezed out.
- acting as an accumulator first hydraulic see actuation unit 5 when the multi-way valve 25 is in the second switching position, a closing of the second clutch 4.
- a relatively large volume flow is promoted in a very short time, so that the clearance of the second clutch 4 is overcome relatively quickly. In this way results a total of a short switching time for closing the second clutch. 4
- the pump 16 starts.
- the pump 16 rotates in the opposite direction of rotation, when filling the first hydraulic actuator unit 5.
- the pump 16 then takes over the promotion of a hydraulic flow in the hydraulic chamber 14.
- the pump 16 is driven by the electric motor 21, so that the adjustment of the current strength, the delivery volume of the pump 16 can be controlled as needed.
- FIG. 3 shows a hydraulic actuation arrangement according to the invention in a third embodiment, which largely corresponds to that of FIG. In this respect, reference may be made to the above description in terms of similarities. The same or corresponding components are provided with the same reference numerals.
- the difference of the present embodiment is that the check valve 19 and the multi-way valve 25 of Figure 2 here by a first switching valve 27 and a second switching valve 27 'are replaced.
- the switching valves 27, 27 ' which are preferably of the same design, can each be converted into a first switching position, in which the associated actuating unit 5, 13 is connected to the pump 16, and into a second switching position, in which the respective connecting channel 24, 26 is interrupted.
- the functionality is the same as in the embodiment according to FIG. 2.
- FIG. 4 shows a hydraulic actuation arrangement according to the invention in a fourth embodiment, which largely corresponds to that of FIG.
- the first hydraulic actuating unit 5 comprises a second spring 28 which acts on the piston 8 of the piston-cylinder unit 6 against the pressure force of the pump 16.
- the second spring 28 is preferably dimensioned so that it has a lower spring stiffness than the first spring 11. It can be seen that the second spring 28 is axially supported on a support surface 32 of the piston-cylinder unit 6. This results in a parallel connection of the first and the second spring 11, 28, so that the spring forces add up during the relaxation of the first spring 11.
- the operation is such that by first transferring the valve 25 into the illustrated switching position, the first spring 11 acts on the sliding sleeve 9 in the direction of the piston-cylinder unit 6. In this case, the rod 29 with the piston 8 in abutment. Has the shift sleeve 9 reaches an end position, which is formed for example by an end stop 41, the second spring 28 pushes the piston 8 further in the direction of the chamber 7. There is thus a stepped admission of the second actuator 13 with hydraulic pressure, that is second actuating unit 13 is initially applied quickly over a long distance; This is followed by a gentler application, so that the point of contact of the second clutch 4, from which torque is transmitted, is approached more sensitively.
- FIG. 5 shows a hydraulic actuation arrangement according to the invention in a fifth embodiment, which largely corresponds to that of FIG. In this respect, reference may be made to the above description with regard to the similarities. The same or corresponding components are provided with the same reference numerals.
- first and second springs 11, 28 are arranged in series connection instead of in parallel.
- the second spring 28 is indirectly supported axially on the first spring 11.
- Indirect support means in the context that the second spring 28 via a support surface 32 of the piston rod 29 against the switching element 30 and is axially supported over this against the first spring 11.
- FIG. 6 shows a hydraulic actuation arrangement according to the invention in a sixth embodiment, which largely corresponds to that of FIG. In this respect, reference may be made to the above description in terms of similarities. The same or corresponding components are provided with the same reference numerals.
- the present embodiment is characterized in that in addition to the first and second actuator unit 5, 13 for actuating the first and second clutch 3, 4, a further, third hydraulic actuator unit 33 for actuating a third clutch 34 is provided.
- the third operating unit 33 is arranged parallel to the second operating unit 13.
- the associated third clutch 34 which is preferably designed in the form of a friction clutch, serves to lock a differential in the second drive axle.
- a third valve 35 is provided, which is designed in particular in the form of a proportional valve or pressure control valve and thus allows a continuous application of the third actuating unit 33.
- the third actuating unit 33 also comprises a piston-cylinder unit with a piston 36 and a cylinder chamber 37.
- the control is preferably such that the pump 16, after closing the first clutch 3 and after at least partially closing the second clutch 4 by pressure discharge of the first actuating unit 5, the further pressurization takes over.
- the pump 16 can adjust both the clutch torque of the second clutch 4 as a function of the driving dynamics of the motor vehicle variably and steplessly.
- the setting of the locking torque on the third clutch 34 is also infinitely variable and is accomplished by appropriate control of the valve 35.
- FIGS. 7 to 10 Various embodiments of drive arrangements are shown in FIGS. 7 to 10, each of which can be equipped with one of the abovementioned inventive actuation arrangements according to one of FIGS. 1 to 6.
- FIGS. 7 to 10 will initially be described together in terms of their similarities.
- a drive arrangement 42 for a multi-axle driven motor vehicle is shown schematically.
- the drive unit 43, a first drive train 44 for driving a first drive axle 45 and a second drive train 46 for driving a second drive axle 47 can be seen from the motor vehicle.
- the drive unit 43 comprises an internal combustion engine 48, a clutch 49 and a manual transmission 50 via which torque is introduced into the first and the second drive train 44, 46. It is understood that the drive unit can also be any other drive, such as an electric motor.
- a transfer case 52 For splitting the torque generated by the drive unit on the first and the second drive train 44, 46, a transfer case 52 is provided.
- the transfer case 52 preferably comprises a differential gear having an input part and three output parts which have a balancing effect with each other.
- the input part of the differential gear is designed as a differential cage 53, which is driven by the drive unit 43.
- a rotatably connected to the differential carrier 53 ring gear is provided which is in meshing engagement with a gear of the gearbox 50.
- the first drive train 44 is basically formed by the differential cage 53, which transmits the torque via in the differential carrier 53 rotatably mounted and together with this about the rotation axis A rotating differential wheels on the first and second output part.
- the first and the second output part of the differential gear are designed in the form of side shaft wheels, which mesh with the differential wheels.
- the side-shaft gears are each rotatably connected to an associated side shaft 54, 55, via which the torque introduced is transmitted to the associated wheels 56, 57.
- the third output part is drive-connected to the second drive train 46, the second drive train 46 being switchable on demand to the first drive train 44 for transmitting a torque to the second drive axle 47.
- the third output part is formed by a free end of the differential cage 53, which is non-rotatably connected to an input part of the second drive train 46.
- the second drive train 46 includes in series the following components which are drivingly connected to each other for transmitting a torque: a first clutch 3, a first angle drive 58, a longitudinal drive shaft 59, a second angle drive 60, a second clutch 4 and a second axle differential 62, the Driving the second axis 47 is used. It is understood that the above order of the modules is not mandatory.
- the first clutch in the torque flow can in principle also be arranged behind the first angle drive.
- the first clutch 3 which is shown here only schematically, comprises an input part 63, which is indirectly connected to the drive unit 43, in particular via the differential carrier 53. Further, the first clutch 3 comprises an output part 64, opposite to the input part 63 can be connected and disconnected. The output part 64 is connected to the input shaft 65 of the angle drive 58 to introduce torque into the angle drive 58 for driving the second drive axle 47. It can be seen that the input shaft 65 of the angle drive 58 is arranged coaxially to the axis of rotation A, around which also the differential carrier 53 rotates. In this case, the input shaft 65 is designed as a hollow shaft and rotatably arranged on the side shaft 55.
- the input shaft 65 is in turn rotatably connected to a ring gear 66 which is in meshing engagement with a bevel gear to drive the longitudinal drive shaft 59 rotationally.
- the input shaft 65 of the first angle drive 58 is rotatably mounted about the axis of rotation A by means of first and second bearing means 67, 67 '.
- the bearing means 67, 67 ' are preferably designed in the form of rolling bearings, with other types of bearings, such as plain bearings, are not excluded.
- the longitudinal drive shaft 59 which is shown here only schematically, is preferably designed in the form of a multi-part shaft having a first shaft portion and a second shaft portion connected thereto non-rotatably.
- a not shown here intermediate joint and a Intermediate storage be provided. It can be seen that the front shaft portion by means of two bearing means 68, 68 'is rotatably mounted, and that the rear shaft portion by means of further bearing means 69, 69' is rotatably mounted about a rotational axis B.
- the second angle drive 60 includes a drive pinion and a hereby meshing ring gear as output.
- the ring gear is rotatably connected to an input part 72 of the second clutch 4.
- An output part 73 of the second clutch 4 is non-rotatably connected to the differential carrier 74 of the rear axle differential 62 to transmit torque thereon.
- the Deutschenachsdifferential 62 includes in addition to the differential carrier 74 here unspecified differential wheels, which rotate together with the differential carrier 74 about the axis of rotation C, and two meshing with the differential gears side gears, which are rotatably connected to the side shafts 75, 76 of the motor vehicle. At the ends of the side shafts 75, 76 are the rear wheels 77, 78. It can be seen that the coupling part 72 by means of bearing means 79, 79 'is rotatably mounted about the axis of rotation C, which are preferably designed in the form of rolling bearings.
- the peculiarity of the present drive arrangements is that by means of the first clutch 3 and the second clutch 4, the front angle drive 58, the longitudinal drive shaft 59 and the rear angle drive 60 with opened first and second clutch, 3, 4 can be switched off. In this deactivated state, said assemblies and the associated components are stationary, so that power losses due to drag torque and friction are reduced. This in turn causes a reduced fuel consumption for the driving states in which only the first drive axle 45 is driven and the second drive axle 47 runs along torque-free.
- the first clutch 3 is preferably designed in the form of a clutch.
- a clutch is understood to be a clutch in which the input side 63 can be separated from the output side 64.
- the input side 63 and the output side 64 of the clutch by positive engagement mit- connected to each other.
- claw clutches or toothed clutches may be mentioned.
- Particularly favorable for driving comfort is the use of clutches that make a synchronization between the input side and the output side before switching.
- Sperrlosynchronisierkupplitch called, as they are used in manual transmissions.
- the second clutch 4 is preferably designed in the form of a force-locking friction clutch, in particular in the form of a Reiblamellenkupplung.
- the friction clutch comprises an outer disk carrier as an input part 72, with the outer disk rotatably and axially displaceably connected, and an inner disk carrier as the output part 73, with the inner disk rotatably and axially slidably connected.
- the friction clutch is closed by axial loading of the disk set consisting of the outer disks and the inner disks by means of the second actuation unit 13, and rotational speed equalization takes place between the input part 72 and the output part 73.
- the first clutch 3 and the second clutch 4 are opened so that all the drive components resting in the torque flow between these two clutches 3, 4 are stopped. In this driving condition, power losses due to drag torque and friction are minimized.
- the shift clutch 3 is actuated, wherein initially a rotational speed equalization of the two clutch parts 63, 64 takes place. Then the clutch 3 can be completely closed without switching noises, so that the longitudinal drive shaft 59 is connected to the torque transmission to the second drive axle 47.
- the second clutch 4 is coaxial with the axis of rotation C of the differential gear 62.
- the clutch input member 72 is rotatably connected to the ring gear and the clutch output member 73 is rotatably connected to the differential carrier 74.
- the second clutch 4 is open, the clutch input part 72 and the components of the second angle drive 60 are stationary, that is, they do not perform any rotational movement.
- the embodiment of Figure 8 is characterized in that the second clutch 4, which is also preferably designed in the form of a friction clutch, coaxial with a side shaft 75 of the second drive axle 47 is arranged.
- the clutch input part 72 is rotatably connected to a side gear of the differential gear 62.
- the clutch output member 73 is rotatably connected to the associated side shaft 75.
- the second clutch 4 is disposed within the longitudinal drive shaft 59, for example between a first shaft portion and a second shaft portion of the longitudinal drive shaft 59.
- the clutch input portion 72 is rotatably connected to the first shaft portion, while the clutch output member 73 rotatably with the second shaft portion connected is.
- the clutch output member 73 rotates and all components behind it in the torque flow, while the clutch input member 72 and all lying in the torque flow between this and the first clutch 3 components are stationary.
- FIG. 10 shows a further embodiment of a drive arrangement according to the invention, which largely corresponds to that of FIG. In this respect, reference is made to the above description in terms of similarities.
- a third clutch 34 is provided in addition to the first and second clutch 3, 4, a third clutch 34 is provided.
- the present Aktu istsan Aunt 2 is configured according to Figure 6, which includes a third actuator unit 33.
- the third clutch 34 which is shown here only schematically, is preferably designed in the form of a friction clutch, which allows a variable adjustment of the locking torque.
- the third clutch 34 is operatively inserted between the differential carrier 74 and a side shaft 76, so that it can prevent a compensatory movement between the two side-shaft gears.
- a first coupling member 80 is rotatably connected to the differential carrier 74, while the second coupling member 81 is rotatably connected to the side shaft 76.
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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KR1020117019195A KR101313991B1 (ko) | 2009-01-19 | 2010-01-19 | 작동 장치, 작동 장치를 구비한 구동 장치 및 작동 장치에 의해 구동 차축을 접속하기 위한 방법 |
JP2011545698A JP5254470B2 (ja) | 2009-01-19 | 2010-01-19 | 作動装置 |
US13/145,069 US8739953B2 (en) | 2009-01-19 | 2010-01-19 | Actuating assembly |
CN201080013537.1A CN102387931B (zh) | 2009-01-19 | 2010-01-19 | 促动组件 |
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DE102009005410A DE102009005410B4 (de) | 2009-01-19 | 2009-01-19 | Aktuierungsanordnung und Verfahren zum Zuschalten einer Antriebsachse im Antriebsstrang eine Kraftfahrzeugs sowie Antriebsanordnung |
DE102009005410.3 | 2009-01-19 |
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PCT/EP2010/000277 WO2010081743A1 (de) | 2009-01-19 | 2010-01-19 | Aktuierungsanordnung |
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US (1) | US8739953B2 (de) |
JP (1) | JP5254470B2 (de) |
KR (1) | KR101313991B1 (de) |
CN (1) | CN102387931B (de) |
DE (1) | DE102009005410B4 (de) |
WO (1) | WO2010081743A1 (de) |
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DE102014105160A1 (de) | 2014-04-11 | 2015-10-15 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Kupplungsanordnung und Verfahren zu deren Betätigung |
DE102014105168A1 (de) | 2014-04-11 | 2015-10-15 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Kupplungsanordnung, Antriebsstrang und Kupplungsbetätigungsverfahren |
KR20160015932A (ko) * | 2014-08-01 | 2016-02-15 | 현대오트론 주식회사 | 페일세이프 밸브를 이용한 클러치 제어 방법 및 장치 |
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WO2005064187A1 (de) * | 2003-12-09 | 2005-07-14 | Gkn Driveline International Gmbh | Hydrauliksystem für zwei lamellenkupplungen |
WO2006007086A1 (en) | 2004-06-18 | 2006-01-19 | Magna Powertrain Usa, Inc. | Low power hydraulic clutch actuation systems |
DE102004033439B4 (de) | 2004-07-08 | 2006-11-23 | Getrag Driveline Systems Gmbh | Antriebsstrang für ein Kraftfahrzeug |
WO2006128637A1 (de) | 2005-05-31 | 2006-12-07 | Magna Powertrain Ag & Co. Kg | Reibungskupplung mit hydraulischem aktuator und antriebseinheit mit mindestens einer solchen |
DE102007063360A1 (de) | 2007-12-28 | 2009-07-02 | Gkn Driveline International Gmbh | Hydraulikanordnung für eine kraftbetätigte Stelleinheit |
DE102008037886A1 (de) | 2008-08-15 | 2010-02-25 | Gkn Driveline International Gmbh | Antriebsanordnung für ein mehrachsgetriebenes Kraftfahrzeug |
Cited By (6)
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KR20190059985A (ko) * | 2011-02-23 | 2019-05-31 | 섀플러 테크놀로지스 아게 운트 코. 카게 | 클러치의 작동을 위한 유압 장치 |
KR102198076B1 (ko) * | 2011-02-23 | 2021-01-05 | 섀플러 테크놀로지스 아게 운트 코. 카게 | 클러치의 작동을 위한 유압 장치 |
EP2587085A1 (de) * | 2011-10-26 | 2013-05-01 | GETRAG Getriebe- und Zahnradfabrik Hermann Hagenmeyer GmbH & Cie KG | Kraftfahrzeugantriebsstrang und Hydraulikkreis dafür |
CN103104699A (zh) * | 2011-11-14 | 2013-05-15 | 通用汽车环球科技运作有限责任公司 | 具有自动发动机停止-起动蓄能器的变速器液压控制系统 |
CN106870599A (zh) * | 2015-12-14 | 2017-06-20 | 舍弗勒技术股份两合公司 | 用于以液压操纵方式进行离合器致动的操纵模块 |
WO2022207079A1 (de) | 2021-03-30 | 2022-10-06 | Gkn Automotive Limited | Kupplungsanordnung |
Also Published As
Publication number | Publication date |
---|---|
US8739953B2 (en) | 2014-06-03 |
DE102009005410A1 (de) | 2010-07-29 |
JP2012515110A (ja) | 2012-07-05 |
JP5254470B2 (ja) | 2013-08-07 |
CN102387931B (zh) | 2015-05-13 |
KR101313991B1 (ko) | 2013-10-01 |
DE102009005410B4 (de) | 2012-04-12 |
KR20110106451A (ko) | 2011-09-28 |
CN102387931A (zh) | 2012-03-21 |
US20110284337A1 (en) | 2011-11-24 |
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