CN102483151A - Hydraulic System For Hydraulically Controlling A Dual Clutch Transmission - Google Patents
Hydraulic System For Hydraulically Controlling A Dual Clutch Transmission Download PDFInfo
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- CN102483151A CN102483151A CN2010800347233A CN201080034723A CN102483151A CN 102483151 A CN102483151 A CN 102483151A CN 2010800347233 A CN2010800347233 A CN 2010800347233A CN 201080034723 A CN201080034723 A CN 201080034723A CN 102483151 A CN102483151 A CN 102483151A
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- Prior art keywords
- valve
- hydraulic
- pressure
- speed changer
- pilot
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Classifications
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- 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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
- F16H61/0204—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
- F16H61/0206—Layout of electro-hydraulic control circuits, e.g. arrangement of valves
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- 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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
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- 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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
- F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
- F16H61/688—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive with two inputs, e.g. selection of one of two torque-flow paths by clutches
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- 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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
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- 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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
The invention relates to a hydraulic system for hydraulically controlling and supplying a transmission, in particular a dual clutch transmission, which comprises a first partial transmission and a second partial transmission, which each have a clutch, comprising: - a hydraulic energy source for supplying the hydraulic system with hydraulic energy; - a first hydraulic device for controlling the first partial transmission; - a second hydraulic device for controlling the second partial transmission. In order to provide an improved hydraulic system, a respective first control pressure and second control pressure can be set by means of the first hydraulic device and the second hydraulic device, wherein in order to engage gears of the dual clutch transmission, the respective first control pressure and the respective second control pressure can be conducted by means of a first multiplexer valve of the first hydraulic device and by means of a second multiplexer valve of the second hydraulic device to a first double surface piston of the respective hydraulic device or to a second double surface piston of the respective hydraulic device.
Description
Technical field
The present invention relates to a kind of hydraulic system that comprises the dual-clutch transmission of the first sub-speed changer that has a clutch respectively and the second sub-speed changer with hydraulic way control; Have and be used to supply with the hydraulic energy source of said hydraulic system hydraulic energy and have be used to control first hydraulic pressure installation of the first sub-speed changer and have second hydraulic pressure installation that is used to control the second sub-speed changer.
Background technique
The hydraulic system that is used for hydraulic way control and supply speed changer is known.
In automatic transmission; It is essential that oil is supplied with (having most of pumps that pump drives), the for example grading automatical speed changer of said automatic transmission, CVT speed changer or dual-clutch transmission; Has hydraulic controller; Be the actuator controller, like clutch actuator or gear shift excitation controller, and cooling/lubricant oil is supplied with.
In most cases, it is that mechanical pump drives that pump drives, and said mechanical pump drives and is connected on the internal-combustion engine.
Can replenish this in modern times in the speed changer and arrange that around the E-pump mechanical pump of (the E-motor that promptly has pump) drives.
The oil that also becomes known for speed changer and clutch actuator is not supplied with having and is leaked under the situation of mechanical pump.This moment is not because the structure (being dry clutch) of clutch needs cold oil naturally.
In the clutch of wet type operation, should suitably abandon Mechanical Driven, thereby in known system, by power-actuated pump the hydraulic power that for this reason needs is provided fully.But the running state that occur this moment is very different.Therefore the state with high volume flow demand and low-pressure demand not only is provided, the state of high pressure demand and low volume flow demand also is provided.In conventional E-motor-layout (RPM adjusts driving), this diverse boundary conditions needs very large E-motor (cost, weight, warship are loaded with power supply), in oily supply system, to show different operation states.
In the speed changer actuator, having same problem, because in gearshift procedure, must be shorter road (being that height forces down volume flow) through under low pressure one section very long road (being the high volume flow of low pressure) with from beginning synchronization onwards a section under high-drag at first.
Summary of the invention
The objective of the invention is to propose a kind of hydraulic system of improvement; Especially have as far as possible little hydraulic unit and make it possible to the clutch controlling and cool off speed changer; Said speed changer is dual-clutch transmission especially, particularly with the multifarious hydraulic unit control of smallest number and part as far as possible, in addition; Reach little energy requirement and little leakage, and/or dispose the controller that guarantees at least in part.
Said purpose solves through a kind of hydraulic system with hydraulic way control and supply speed changer; Said speed changer is dual-clutch transmission especially; Comprise the first sub-speed changer and the second sub-speed changer that have a clutch respectively; Said hydraulic system has the hydraulic energy source that is used to supply with said hydraulic system hydraulic energy; Have and be used to control first hydraulic pressure installation of the first sub-speed changer and have second hydraulic pressure installation that is used to control second speed changer; Wherein, utilize said first hydraulic pressure installation and second hydraulic pressure installation can adjust first pilot pressure and second pilot pressure respectively, wherein; In order to hang the shelves into said dual-clutch transmission, first multi-way valve that said first pilot pressure and second pilot pressure separately separately utilizes said first hydraulic pressure installation and second multi-way valve that utilizes second hydraulic pressure installation can be directed on first double-faced piston of said hydraulic pressure installation separately respectively or on second double-faced piston of said hydraulic pressure installation separately alternatively.Each said hydraulic pressure installation has two double-faced pistons, i.e. first double-faced piston and second double-faced piston.Advantageously, each hydraulic pressure installation can be controlled four shelves of total of each sub-speed changer of said dual-clutch transmission.Can utilize only two pilot pressure controls here, wherein, this can advantageously utilize the multi-way valve that correspondingly is connected in series to be switched on the surperficial piston of each pair that will control.Advantageously; Only need two two surperficial pistons of a corresponding valve control to produce first pilot pressure and second pilot pressure; Wherein, Should be controlled according to first pair of surperficial piston or second pair of surperficial piston, the said correspondingly multi-way valve of serial connection is connected alternatively or is guided said second pilot pressure to first double-faced piston of said hydraulic pressure installation separately or to second double-faced piston.
Said purpose alternatively or additionally solves through a kind of hydraulic system with hydraulic way control and supply speed changer; Said speed changer is dual-clutch transmission especially; It comprises the first sub-speed changer and the second sub-speed changer that has a clutch respectively; Said hydraulic system has the hydraulic energy source of supplying with said hydraulic system hydraulic energy; Have first hydraulic pressure installation and second hydraulic pressure installation that is used to control the second sub-speed changer that are used to control the first sub-speed changer, wherein, said hydraulic system has at least one relief valve device; Utilize said relief valve device not have pressure ground alternatively and connect at least one said hydraulic pressure installation to control the corresponding sub-speed changer of said dual-clutch transmission; Wherein, additionally utilize a blocking device of relief valve device, make two hydraulic pressure installation can remove connection at least with said hydraulic energy source.Advantageously, utilize safety valve can not have pressure ground alternatively and connect a said sub-speed changer, wherein, said another sub-speed changer is still advantageously remained valid.Advantageously, additionally can utilize said blocking device at least partly not have two hydraulic pressure installation that said sub-speed changer is connected on pressure ground alternatively., no pressure can make corresponding hydraulic tubing lay or be connected in series on the fuel tank that is conducting to said hydraulic system under connecting., disengaging can make said corresponding hydraulic tubing separately under connecting.
What in the embodiment of said hydraulic system, be provided with is that first multi-way valve of said first hydraulic pressure installation and second multi-way valve of second hydraulic pressure installation and said blocking device utilize the first pilot valve may command.Advantageously, only need a unique pilot valve control.Pilot valve can be regarded as the controllable Proportional valve of electric power, is used to form the pilot pressure of the hydraulic pressure in said multi-way valve of control and the said blocking device.
What in the further embodiment of said hydraulic system, be provided with is; In first control position of said first pilot valve; Said blocking device cuts out and said multi-way valve is not handled, and in second control position of said first pilot valve, said blocking device is opened and said multi-way valve is not handled; And in the 3rd control position of said first guiding, said blocking device is opened and said multi-way valve is handled.Advantageously, the pilot pressure that increasing or alternatively where necessary, the pilot pressure that adjustment is reducing can be adjusted in said control position; Wherein, advantageously utilize a pilot valve can adjust three Different control states, wherein; Advantageously, said first control position can be adjusted when the no current state of said pilot valve, wherein; Advantageously, when possible power failure occurring, Safety function provides through isolated said blocking device.
What in the further embodiment of said hydraulic system, be provided with is, but said first pilot valve is electric power control, in no current state, takies said first control position and along with electric current increases, takies second control position and the 3rd control position.Advantageously, in no current state, also when power failure perhaps, the hydraulic pressure installation that connects after said is by safety cut-off or hydraulic isolation.
What in the further embodiment of said hydraulic system, be provided with is that said blocking device has the locking flashboard.Advantageously, simple locking flashboard of said functional utilization particularly utilizes two parallel isolated locking flashboards of pipeline to realize.
What in the further embodiment of said hydraulic system, be provided with is; First clutch valve and the said second sub-speed changer that the said first sub-speed changer has a first clutch that is used to control the first sub-speed changer has the second clutch valve of the second clutch that is used to control the second sub-speed changer; Wherein, said clutch valve is after the blocking device downstream of said relief valve device are connected in the safety valve of said relief valve device.Advantageously, said clutch valve is tapped between said safety valve and the locking flashboard, and wherein, advantageously, although the available hydraulic energy of closing of the locking flashboard of said clutch valve is supplied with, said clutch also correspondingly can be handled.Advantageously, obtain the multistep security concept, wherein, utilize said locking flashboard, said multi-way valve can separate with said hydraulic energy source with the therefore shelves actuator of said dual-clutch transmission, wherein, when safety valve is opened, also can adjust two clutches.In addition; When the locking flashboard of a sub-speed changer of said dual-clutch transmission is opened; Also possibly also not have pressure ground and connect corresponding shelves actuator and clutch actuator, wherein, said other sub-speed changer separately keeps in full force and effect or hydraulic way ground can be adjusted.Advantageously, the possibility of minimum leakage is become be reality, this is that said multi-way valve can separate with said hydraulic energy source because handling under the situation of shelves actuator, does not also exist in said system pressure under also so has a minimal leak.
What in the further embodiment of said hydraulic system, be provided with is that said first double-faced piston is embodied as respectively with second double-faced piston has two pistons such as face such as grade of the pressure side of acting identical size in the opposite direction.Advantageously, the corresponding control of said double-faced piston can be carried out symmetrically, and is same, and pilot pressure is carried out through consistent adjustment according to the position of said multi-way valve.
What in the further embodiment of said hydraulic system, be provided with is; Said first hydraulic pressure installation and second hydraulic pressure installation have a two pressure regulator respectively, and said first pilot pressure and second pilot pressure separately can utilize said pair of pressure regulator to adjust.Advantageously, the said face piston that waits that connects behind the multi-way valve that correspondingly utilizes utilizes said pair of pressure regulator control.
What in the further embodiment of said hydraulic system, be provided with is that each said pair of pressure regulator has makes said first pilot pressure and second pilot pressure can be switched to the control position on the fuel tank.Advantageously, in this control position, also for example under the running state of said dual-clutch transmission, when it did not carry out gear shift, the said face piston that waits that connects after did not correspondingly have the connection of pressure ground, wherein, obtains minimal leak equally.
In addition, said purpose solves through a kind of dual-clutch transmission with the first sub-speed changer and second sub-speed changer, and said dual-clutch transmission is capable of using and/or with controlling in any one above-mentioned hydraulic system.It has obtained above-mentioned advantage.
Description of drawings
Obtain other advantages of the present invention, characteristic and details from following explanation, in following explanation, describe embodiment in detail with reference to accompanying drawing.Part identical, similar and/or that function is identical distributes identical reference character.
Unique Fig. 1 shows the hydraulic system with hydraulic way control and supply dual-clutch transmission.
Embodiment
Fig. 1 shows with hydraulic way control and supplies with the dual-clutch transmission 3 that only partly shows that dual-clutch transmission 3 has the first sub-speed changer 5 and the second sub-speed changer 7.First hydraulic equipment serial connection is connected in series the second sub-speed changer 7 as the part of said hydraulic system as first sub-speed changer 5, the second hydraulic equipments of the part of said hydraulic system.
Hydraulic system 1 utilizes the first power-actuated pump 9 and the second mechanically operated pump 11 to supply with hydraulic energy.Memory load valve 13 is connected in after power-actuated first pump 9.Memory load valve 13 is spring resets, and has two pressure feedback.Memory load valve 13 is used to regulate or adjust the liquid level or the memory pressure of hydraulic pressure storage 15.Therefore two one way stop peturn valves and a throttle valve are connected in after the memory load valve 13.In first on positi, as shown in Figure 1, memory load valve 13 is connected in series conducting on the direction of pressure reservoir 15, thereby pressure reservoir 15 can utilize first pump 9 to load hydraulic energy.For pressure reservoir 15 be loaded and/or after the hydraulic unit that connects have situation little or that do not have the hydraulic energy demand; Memory load valve 13 is adjusted in second on positi, wherein can guide the volume flow clutch of being carried by first pump 9 17 that is used to cool off into.The part clutch 5 and 7 of dual-clutch transmission 3 has a clutch 17 respectively.Cool stream pressure-gradient control valve 19 is connected in series clutches 17 and is connected in after the memory load valve 13, utilizes cool stream pressure-gradient control valve 19, and corresponding volume flow can preferentially flow on clutch 17 of each requires (for example manipulation) more.Therefore, cool stream pressure-gradient control valve 19 has two counteractive pressure sides, by the manipulation cylinder 21 of clutch 17 clutch control pressure is switched on the said pressure side.
Safety valve 23 is connected in after memory load valve 13 and the pressure reservoir 15.Safety valve 23 has two pressure feedback and is used for the part clutch 5 and 7 of safety cut-off dual-clutch transmission 3.In the neutral position, as shown in Figure 1, pressure reservoir 15 and the conductings of first pump 9 serial connection are on two sub-speed changers 5 and 7 of dual-clutch transmission 3.In the second other on positi, sub-speed changer 5,7 disposes first pump 9 and pressure reservoir 15 respectively alternatively, and wherein, other sub-speed changer 5,7 separately is switched on the no pressure oil tank 25 of hydraulic system 1.
The blocking device of locking flashboard 27 forms is connected in after the safety valve 23.The safety installations of locking flashboard 27 and safety valve 23 formation hydraulic systems 1.Utilize locking flashboard 27, as shown in Figure 1 in first on positi, the first sub-speed changer 5 and the second sub-speed changer 7 can be opened with pressure reservoir with first pump 9 in 15 minutes.In second on positi, they can be connected in series and be conducting on first pump 9 and the pressure reservoir 15.Advantageously, tap is used for the manipulation cylinder 21 of controlled clutch 17 in the downstream of locking flashboard 27, thereby it advantageously also can be adjusted maybe and can handle when close-lock flashboard 27.The every other function of sub-speed changer 5,7 (especially shelves final controlling element) is and the pressure reservoir 15 and first pump 9 in first on positi of locking flashboard 27 shown in Figure 1, to separate.
Handle cylinder 21 in order to control, clutch valve 29 serial connections that respectively have an electric power to handle are handled cylinder 21.Clutch valve 29 is connected in after the safety valve 23, and in the arranged downstream or the tap of locking flashboard 27, thereby the favourable property supplied with of said hydraulic energy also provides when locking flashboard 27 cuts out.
Two two pressure regulator valves 31 are connected in after the locking flashboard 27, utilize two two pressure regulator valves 31 can adjust first pilot pressure 33 and second pilot pressure 35 respectively.Two pressure regulator valves 31 have two pressure feedback, and in the neutral position pilot pressure 33 and 35 are adjusted on the fuel tank level or is placed on the fuel tank 25.In right and left on positi, to adjust on the fuel tank 25 for one in the pilot pressure 33 and 35, another is adjusted on the stress level of expectation.Advantageously, utilize the pilot pressure 33 and 35 can 4 double-faced pistons of control total, double-faced piston such as be embodied as at face piston 37.The shelves final controlling element that shows in detail that is used to handle the each several part clutch 5,7 of dual-clutch transmission 3 in face piston 37.Each sub-speed changer 5,7 has face piston 37 such as first and second, and wherein, in the sub-speed changer 5,7 one two wait between face piston 37 and the attached two pressure regulator valves 31 and connect multi-way valve 39 respectively.Each multi-way valve 39 has two on positis, and wherein, in first on positi, one is waited face piston 37 usefulness pilot pressures 33 and 35 loadings and face piston 37 such as other separately to turn on the fuel tank 25 at bilateral.Advantageously, through control multi-way valve 39 and two pressure valve 31, each sub-speed changer 5,7 carries out the control of four shelves levels of total of each sub-speed changer 5.7.
Second pump 11 of hydraulic energy source is mechanically driven by internal-combustion engine 41, internal-combustion engine 41 serial connection dual-clutch transmissions 3.Turn between the internal-combustion engine 41 and second pump 11 with the steerable clutch that maybe can connect 43 of hydraulic way.Advantageously, second pump 11 is removed connection with internal-combustion engine 41 or only under conditions of demand, is mechanically driven to practice thrift the mechanical energy of internal-combustion engine 41.Cooling equipment 45 is connected in after second pump 11.Cooling equipment 45 have cooler and with the one way stop peturn valve of cooler switched in parallel, the hydraulic medium of said one way stop peturn valve on for example can the cooler of bypass cooling equipment 45 when high reserve motion pressure head also has the hydraulic medium of cooling relatively.
Cooling fuel tap 49 is connected in after the cooling equipment 45.Cooling fuel tap 49 can obtain to amount to three on positis, wherein, in first on positi, connects a clutch 17, in second on positi, connects another clutch 17 and second pump 11, also can be imported to cool off with hydraulic medium by pump 11.In the neutral position, as shown in Figure 1, two clutches 17 and second pump were opened in 11 minutes.A corresponding surveying flow of second pump 11 is switched on the fuel tank 25.Advantageously, in this middle on positi of cooling fuel tap 49, carry out the additional cooling of hydraulic medium, for example, so that the preferred temperature in the adjustment fuel tank 25 perhaps reaches desired temperatures at fuel tank 25.
Utilize first pilot valve 51 to carry out the control of two multi-way valve 39 and locking flashboard 27 with hydraulic way.Utilize first pilot valve 51 can realize being used to controlling the pilot pressure in advance accordingly of locking flashboard 27 and multi-way valve 39.When pilot pressure in advance was zero, as shown in Figure 1, locking flashboard 27 at first cut out.First pilot valve 51 takies this on positi under no current state.Increase and during proportional risings of pilot pressure in advance, at first open locking flashboard 27 at electric current, and 9 series connection of first pump turn on pair pressure valve 31, multi-way valve 39 and etc. on the face piston 37.At this moment, multi-way valve 39 is not at first handled.At the electric current that further increases by first Proportional valve 51 and when therefore improving pilot pressure, multi-way valve 39 is final also to be connected at its second on positi, thus the face piston 37 such as corresponding other of the sub-speed changer 5,7 of may command.
Utilize second pilot valve 53 separately to carry out the essential control of two pressure valve 31 with hydraulic way.Second pilot valve 53 is Proportional valves that same electric power is handled, and adjusts each pair pressure regulator valve 31 to control in advance pilot pressure with hydraulic way.Along with the increase of electric current, can at first carry out the pressure of second pilot pressure 35 and regulate, two pilot pressures 33 and 35 no pressure connection, and, carry out the adjusting of first pilot pressure 33 along with the further increase of electric current.
Therefore, similarly, utilize the controllable pilot valve 55 of the 3rd electric power to carry out the control of safety valve 23 with hydraulic way equally.
As selection, two pressure regulators 31 also can directly be handled by ratio magnet with safety valve 23.
But the control of the clutch 43 that can connect and cooling fuel tap 49 utilizes the 4th pilot valve 57 of shared electric power control to carry out.Under the no current state of the 4th pilot valve 57, the clutch 43 that can connect is at first opened, thereby does not have mechanical energy to be delivered to second pump 11 from being used for internal combustion engine driven 41.Along with the increase of electric current, at first close the clutch 43 that to connect.Along with the further increase of electric current, can adjust the 3rd on positi of cooling fuel tap 49.This moment also can imagine the cooling fuel tap 49 alternately pulse move in second end position so that supply with two clutches, 17 corresponding cold oil volume flows thus.Can also adjust the task ratio this moment, so that for example supply with bigger cold oil volume flow to a clutch 17.
Form described shelves regulating piston in face piston 37, to handle or to hang the shelves of dual-clutch transmission 3.Each waits face piston 37 to have two pressure sides that grade is big of effect in the opposite direction.37, two controlled pressure of two face pistons such as multi-way valve 39 serial connections, the first adjustment pressure 33 is adjusted pressure 35 with second, is distributed in respectively etc. on four piston areas of total of each sub-speed changer 5,7 of face piston 37.Therefore, each multi-way valve 39 is responsible for a sub-speed changer 5,7.
Each pair pressure regulator valve 31 serial connection multi-way valve 39, two pressure regulator valves 31 can outwards be adjusted a pilot pressure 33,35 from middle position in each direction.In said neutral position, two pressure regulator valves 31 or two output terminals are switched on the fuel tank 25.Two pressure valve 31 utilize second pilot valve 53 to control in advance, but alternatively, also can directly be handled.Pilot valve 51 to 57 expression pressure regulators.
Two two pressure regulator valves 31 are connected in after the shared little locking flashboard 27, and the system pressure that locking flashboard 27 can separately be provided by first pump 9 was driven two sub-speed changers in 5,7 minutes simultaneously.
Safety valve 23 is arranged in before the locking flashboard 27.Safety valve 23 is embodied as pressure regulator, and in the neutral position, pressure regulator is connected in series two sub-speed changers 5,7 fully and is conducting to system pressure, and promptly serial connection is conducting to first pump 9.A sub-speed changer 5,7 can continue not have pressure ground from said neutral position respectively to be connected, and wherein advantageously, another 5,7 of sub-speed changer can be placed on the complete system pressure.
Advantageously, not only the locking flashboard 27, and two multi-way valve 39 are controlled with hydraulic way through the first identical pilot valve 51.In the no current state of first pilot valve 51, locking flashboard 27 and two multi-way valve 39 are latched on the reference position.Pilot pressure improves through first pilot valve in advance, thereby at first opens locking flashboard 27.As long as locking flashboard 27 is closed, advantageously, multi-way valve 39 neither be essential.Multi-way valve 39 remains in the reference position.Pilot pressure continues to improve through first pilot valve 51 in advance, makes multi-way valve 39 turn in the other link stopper.First pilot valve 51 can advantageously take the 3rd on positi, with the control locking flashboard 27 and second multi-way valve 39.
The tap that between safety valve 23 and locking flashboard 27, has clutch valve 29.Though clutch 17 can further be handled, the shelves final controlling element of dual-clutch transmission 3 can also utilize locking flashboard 27 no pressure ground to connect.Because this measure, the leakage of hydraulic system 1 can be reduced to minimum value.And a clutch 17 is not laid with should having pressure yet, yet this can advantageously utilize safety valve 23.The said leak position that only is under pressure then only is arranged on pilot valve 51 to 57 and the clutch valve 29.Advantageously, the control of dual-clutch transmission 3 can utilize lucky seven high-speed double electromagnet of pilot valve 51 to 57 and clutch valve 29.
Optional is, shown in the dotted line among Fig. 1, the 3rd pilot valve 53 is not directly to be connected after the locking flashboard 27, but directly is connected in after the safety valve 23, and this 3rd pilot valve 53 equally is tapped on the identical position as clutch 21 equally.Thus, the 3rd Proportional valve 55 can be when locking flashboard 27 cuts out application system pressure.Even locking flashboard 27 cuts out, two pressure regulator valves 31 still keep controllable, for example so that pilot pressure 33,35 turns on the fuel tank 25 jointly.
Reference numerals list
1 hydraulic system
3 dual-clutch transmissions
5 first sub-speed changers
7 second sub-speed changers
9 first pumps
11 second pumps
13 memory load valves
15 hydraulic pressure storagies
17 clutches
19 cold oils stream pressure-gradient control valve
21 handle cylinder
23 safety valves
25 fuel tanks
27 locking flashboards
29 clutch valves
31 pairs of pressure regulator valves
33 first pilot pressures
35 second pilot pressures
37 pistons such as face such as grade
39 multi-way valve
41 internal-combustion engines
43 clutches
45 cooling equipments
49 cooling fuel taps
51 first pilot valves
53 second pilot valves
55 the 3rd pilot valves
57 the 4th pilot valves
Claims (10)
1. one kind with hydraulic way control and/or supply with the hydraulic system (1) of speed changer; Said speed changer is dual-clutch transmission especially; Said speed changer comprises the first sub-speed changer (5) and the second sub-speed changer (7) that respectively has clutch (17), and said hydraulic system (1) has
-be used to supply with the hydraulic energy source of said hydraulic system (1) hydraulic energy;
-the first hydraulic pressure installation, it is used to control the said first sub-speed changer (5);
-the second hydraulic pressure installation, it is used to control the said second sub-speed changer (7);
It is characterized in that,
First pilot pressure and second pilot pressure can utilize said first hydraulic pressure installation and second hydraulic pressure installation to be adjusted respectively; Wherein, In order to hang the shelves into said dual-clutch transmission, said first pilot pressure (33) and second pilot pressure (35) separately separately utilizes first multi-way valve (3) of said first hydraulic pressure installation and utilizes second multi-way valve (39) of said second hydraulic pressure installation to be directed on first double-faced piston of hydraulic pressure installation separately respectively alternatively or on second double-faced piston of hydraulic pressure installation separately.
2. hydraulic system according to claim 1 is characterized in that,
Said hydraulic system (1) has at least one relief valve device (23; 27), utilize said relief valve device not have pressure ground alternatively and connect at least one in the hydraulic pressure installation of the corresponding sub-speed changer (5,7) be used to control said dual-clutch transmission (1); Wherein, Additionally utilize the blocking device of said relief valve device (23,27), can make two hydraulic pressure installation remove with said hydraulic energy source at least in part and connect.
3. according to any described hydraulic system in the aforementioned claim, it is characterized in that,
First multi-way valve (39) of said first hydraulic pressure installation and second multi-way valve (39) of said second hydraulic pressure installation and said blocking device first pilot valve capable of using (51) control.
4. according to any described hydraulic system in the aforementioned claim, it is characterized in that,
In first control position of said first pilot valve (51); Said blocking device cuts out and said multi-way valve (39) is not handled; In second control position of said first pilot valve (51); Said blocking device is opened and said multi-way valve (39) is not handled, and in the 3rd control position of said first pilot valve (51), said blocking device is opened and said multi-way valve (39) is handled.
5. according to any described hydraulic system in the aforementioned claim, it is characterized in that,
Said first pilot valve (51) but be electric power control, and under no current state, take said first control position, and along with the increase of electric current takies said second control position and the 3rd control position.
6. according to any described hydraulic system in the aforementioned claim, it is characterized in that,
Said blocking device has locking flashboard (27).
7. according to any described hydraulic system in the aforementioned claim, it is characterized in that,
The said first sub-speed changer (5) has the first clutch valve (29) of the first clutch (17) that is used to control the said first sub-speed changer (5); The said second sub-speed changer (7) has the second clutch valve (29) of the second clutch (17) that is used to control the said second sub-speed changer (7); Wherein, said clutch valve (29) be connected in said relief valve device in the downstream of the said blocking device of said relief valve device safety valve (23) afterwards.
8. according to any described hydraulic system in the aforementioned claim, device is characterised in that,
Said first double-faced piston is embodied as respectively with second double-faced piston has two face pistons (37) such as grade of the pressure side of acting identical size in the opposite direction,
9. according to any described hydraulic system in the aforementioned claim, it is characterized in that,
Said first hydraulic pressure installation and second hydraulic pressure installation have a two pressure regulator valve (31) respectively, and first pilot pressure (33) separately and second pilot pressure (35) can utilize said pair of pressure regulator valve adjustment.
10. according to any described hydraulic system in the aforementioned claim, it is characterized in that,
Each two pressure regulator valve (31) has makes said first pilot pressure (33) and second pilot pressure (35) can be switched to the control position on the fuel tank.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102009036427.7 | 2009-08-06 | ||
| DE102009036427 | 2009-08-06 | ||
| DE102009055900 | 2009-11-26 | ||
| DE102009055900.0 | 2009-11-26 | ||
| PCT/DE2010/000897 WO2011015182A1 (en) | 2009-08-06 | 2010-07-29 | Hydraulic system for hydraulically controlling a dual clutch transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102483151A true CN102483151A (en) | 2012-05-30 |
| CN102483151B CN102483151B (en) | 2015-05-20 |
Family
ID=43085850
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080034723.3A Expired - Fee Related CN102483151B (en) | 2009-08-06 | 2010-07-29 | Hydraulic System For Hydraulically Controlling A Dual Clutch Transmission |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN102483151B (en) |
| DE (2) | DE112010003203A5 (en) |
| WO (1) | WO2011015182A1 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103775628A (en) * | 2012-10-24 | 2014-05-07 | 福特全球技术公司 | Paths for supplying fluid to clutches of an automatic transmission |
| CN104454685A (en) * | 2014-09-28 | 2015-03-25 | 长城汽车股份有限公司 | Hydraulic control system, double-clutch transmission and automobile |
| CN104769335A (en) * | 2012-11-09 | 2015-07-08 | 大众汽车有限公司 | Hydraulic control device |
| CN105090134A (en) * | 2014-05-23 | 2015-11-25 | 大众汽车有限公司 | Hydraulic supply apparatus |
| CN105793596A (en) * | 2013-12-09 | 2016-07-20 | 舍弗勒技术股份两合公司 | Hydraulic arrangement for a dual clutch and method for actuating or cooling the dual clutch |
| CN105829777A (en) * | 2013-12-17 | 2016-08-03 | 舍弗勒技术股份两合公司 | Fluid arrangement |
| CN106468354A (en) * | 2015-08-20 | 2017-03-01 | 卡特彼勒（青州）有限公司 | Hydraulic control system for change speed gear box and machine |
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Families Citing this family (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101858431A (en) * | 2010-04-17 | 2010-10-13 | 浙江吉利汽车研究院有限公司 | Hydraulic device for gear shift of double-clutch automatic transmission |
| EP2410212B1 (en) * | 2010-07-21 | 2014-01-01 | hofer mechatronik GmbH | Hydraulic control of a dual clutch transmission |
| DE102011005284B4 (en) * | 2011-03-09 | 2021-11-04 | Zf Friedrichshafen Ag | Method for realizing sailing operation in a motor vehicle with an automatic transmission |
| DE102011005852A1 (en) * | 2011-03-21 | 2012-09-27 | Zf Friedrichshafen Ag | Method for controlling an automatic or automated switching system |
| DE102011100808A1 (en) * | 2011-05-06 | 2012-11-08 | Audi Ag | Clutch transmission, in particular dual-clutch transmission, with hydraulic actuation system |
| DE102011100836A1 (en) | 2011-05-06 | 2012-11-08 | Audi Ag | Hydraulic circuit, method of operation |
| DE102011100849A1 (en) * | 2011-05-06 | 2012-11-08 | Audi Ag | Double clutch |
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| DE102011100799B4 (en) * | 2011-05-06 | 2017-06-01 | Audi Ag | Dual-clutch transmission, method of operation |
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| CN106224538B (en) * | 2016-09-26 | 2018-03-13 | 安徽江淮汽车集团股份有限公司 | Gearbox shift control system |
| CN106151500B (en) * | 2016-09-26 | 2018-02-13 | 安徽江淮汽车集团股份有限公司 | Gear box hydraulic control system |
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| DE102022206496A1 (en) | 2022-06-28 | 2023-12-28 | Zf Friedrichshafen Ag | Method and control device for operating a hydraulic system of a transmission of a motor vehicle |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10134115A1 (en) * | 2001-07-13 | 2003-01-23 | Volkswagen Ag | Hydraulic circuit for controlling dual clutch gearbox, especially for motor vehicle, has central distributing valve device between switching cylinders and pressure valves |
| CN1696542A (en) * | 2004-05-15 | 2005-11-16 | 卢克摩擦片和离合器两合公司 | Device for controlling a plurality of hydraulic shift cylinders and hydraulic supply system |
| US20060150762A1 (en) * | 2003-04-30 | 2006-07-13 | Gunther Petrzik | Hydraulic circuit for the control of a drive train |
| CN1940332A (en) * | 2005-09-29 | 2007-04-04 | 本田技研工业株式会社 | Hydraulic control apparatus for automatic transmission |
| US20090065322A1 (en) * | 2007-07-23 | 2009-03-12 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Double-clutch transmission with a device for controlling a plurality of hydraulic shift cylinders |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005019516A1 (en) * | 2004-05-15 | 2005-12-08 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Arrangement for control of several hydraulic shift cylinders and hydraulic supply system for dual clutch operated transmission unit |
-
2010
- 2010-07-29 DE DE112010003203T patent/DE112010003203A5/en not_active Withdrawn
- 2010-07-29 WO PCT/DE2010/000897 patent/WO2011015182A1/en active Application Filing
- 2010-07-29 DE DE102010032657A patent/DE102010032657A1/en not_active Withdrawn
- 2010-07-29 CN CN201080034723.3A patent/CN102483151B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10134115A1 (en) * | 2001-07-13 | 2003-01-23 | Volkswagen Ag | Hydraulic circuit for controlling dual clutch gearbox, especially for motor vehicle, has central distributing valve device between switching cylinders and pressure valves |
| US20060150762A1 (en) * | 2003-04-30 | 2006-07-13 | Gunther Petrzik | Hydraulic circuit for the control of a drive train |
| CN1696542A (en) * | 2004-05-15 | 2005-11-16 | 卢克摩擦片和离合器两合公司 | Device for controlling a plurality of hydraulic shift cylinders and hydraulic supply system |
| CN1940332A (en) * | 2005-09-29 | 2007-04-04 | 本田技研工业株式会社 | Hydraulic control apparatus for automatic transmission |
| US20090065322A1 (en) * | 2007-07-23 | 2009-03-12 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Double-clutch transmission with a device for controlling a plurality of hydraulic shift cylinders |
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103775628A (en) * | 2012-10-24 | 2014-05-07 | 福特全球技术公司 | Paths for supplying fluid to clutches of an automatic transmission |
| CN103775628B (en) * | 2012-10-24 | 2017-05-10 | 福特全球技术公司 | Device for transmission |
| CN104769335B (en) * | 2012-11-09 | 2017-11-17 | 大众汽车有限公司 | Hydraulic control device |
| CN104769335A (en) * | 2012-11-09 | 2015-07-08 | 大众汽车有限公司 | Hydraulic control device |
| CN105793596A (en) * | 2013-12-09 | 2016-07-20 | 舍弗勒技术股份两合公司 | Hydraulic arrangement for a dual clutch and method for actuating or cooling the dual clutch |
| US10539232B2 (en) | 2013-12-17 | 2020-01-21 | Schaeffler Technologies Ag & Co. | Fluid arrangement |
| CN105829777A (en) * | 2013-12-17 | 2016-08-03 | 舍弗勒技术股份两合公司 | Fluid arrangement |
| CN105829777B (en) * | 2013-12-17 | 2018-03-06 | 舍弗勒技术股份两合公司 | Fluid assembly |
| US10018235B2 (en) | 2014-05-23 | 2018-07-10 | Volkswagen Aktiengesellschaft | Hydraulic supply apparatus |
| CN105090134B (en) * | 2014-05-23 | 2018-01-19 | 大众汽车有限公司 | Hydraulic supply unit |
| CN105090134A (en) * | 2014-05-23 | 2015-11-25 | 大众汽车有限公司 | Hydraulic supply apparatus |
| CN104454685A (en) * | 2014-09-28 | 2015-03-25 | 长城汽车股份有限公司 | Hydraulic control system, double-clutch transmission and automobile |
| CN106468354A (en) * | 2015-08-20 | 2017-03-01 | 卡特彼勒（青州）有限公司 | Hydraulic control system for change speed gear box and machine |
| CN106870599A (en) * | 2015-12-14 | 2017-06-20 | 舍弗勒技术股份两合公司 | Manipulation module for carrying out clutch actuation in hydraulic operation mode |
| WO2020043125A1 (en) * | 2018-08-28 | 2020-03-05 | 长城汽车股份有限公司 | Hydraulic control system and vehicle |
| US11441669B2 (en) | 2018-08-28 | 2022-09-13 | Great Wall Motor Company Limited | Hydraulic control system and vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102010032657A1 (en) | 2011-02-10 |
| WO2011015182A1 (en) | 2011-02-10 |
| CN102483151B (en) | 2015-05-20 |
| DE112010003203A5 (en) | 2012-05-31 |
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