CN104160180A - Hydraulically actuated continuously variable transmission for a vehicular drive line provided with an engine - Google Patents
Hydraulically actuated continuously variable transmission for a vehicular drive line provided with an engine Download PDFInfo
- Publication number
- CN104160180A CN104160180A CN201180076133.1A CN201180076133A CN104160180A CN 104160180 A CN104160180 A CN 104160180A CN 201180076133 A CN201180076133 A CN 201180076133A CN 104160180 A CN104160180 A CN 104160180A
- Authority
- CN
- China
- Prior art keywords
- line
- pump
- transmission fluid
- main
- hydraulic
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- 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
- F16H61/0025—Supply of control fluid; Pumps therefore
- F16H61/0031—Supply of control fluid; Pumps therefore using auxiliary pumps, e.g. pump driven by a different power source than the engine
-
- 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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
- F16H57/0446—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control the supply forming part of the transmission control unit, e.g. for automatic transmissions
-
- 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
-
- 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
- F16H61/66—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 continuously variable gearings
- F16H61/662—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 continuously variable gearings with endless flexible members
- F16H61/66272—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 continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing
-
- 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
- F16H2061/0037—Generation or control of line pressure characterised by controlled fluid supply to lubrication circuits of the gearing
-
- 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
- F16H61/66—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 continuously variable gearings
- F16H61/662—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 continuously variable gearings with endless flexible members
- F16H2061/66286—Control for optimising pump efficiency
-
- 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
- F16H2312/00—Driving activities
- F16H2312/14—Going to, or coming from standby operation, e.g. for engine start-stop operation at traffic lights
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Transmission Device (AREA)
- Control Of Fluid Gearings (AREA)
Abstract
A continuously variable transmission (1) for transmitting a driving force of an engine (VE) to a load (DW) to be driven, in particular in a vehicular drive line, provided with two hydraulic pumps (10, 11) for realising a pressurised supply of hydraulic transmission fluid for the actuation of the transmission (1), whereof a first pump (10) is driven by the engine (VE) and whereof a second pump (11) is driven by an electric motor independently from the engine (VE), and with a main hydraulic line (13), an auxiliary hydraulic line (15) and a line pressure valve (14) that control a pressure (Pline) in the main line (13) by allowing a surplus of transmission fluid to flow from the main line (13) into the auxiliary line (15), wherein the first pump (10) is connected to the main line (13) and wherein the second pump (11) is connected to the auxiliary line (15).
Description
Technical field
The present invention relates to the stepless speed variator that a kind of preamble as claimed in claim 1 limits.Such stepless speed variator is totally known, and EP0798492A1 as open in for example European patent is described, and conventionally in passenger vehicle power train, is applied between motor and its driving wheel.
Background technique
Known stepless speed variator, it can be multiple known type, the gear ratio providing can control to the arbitrary value in the variator ratio range that described speed changer covers by its electro-hydraulic actuating system.Except described gear ratio, control, the actuating system of speed changer is also controlled the moment of torsion that can transmit by speed changer.In addition,, except gear ratio is controlled and moment of torsion is controlled this two function of tonic chords, described actuating system is also moved so-called speed changer slave function, and it at least comprises the opening and closing of lubricated and its clutch of speed changer conventionally.
Conventionally, the control of the gear ratio of the actuating system of speed changer and speed change moment of torsion are controlled the maximum fluidity that these two main actuation function require hydraulic transmission fluid under maximal pressure level.Although high-pressure horizontal itself such in known speed changer can be without being implemented and controlling to difficulty especially, particularly the large flow of the transmission fluid under such high-pressure horizontal brings high request to layout and/or the assembly of the electro-hydraulic actuating system of speed changer.When the oil hydraulic pump of actuating system by wherein apply speed changer power train engine mechanical while driving, this high request just has problem especially, this be due to: when pump is only driven by minimally, even under low engine speed, this pump also must provide required transmission fluid flow.Therefore, this known Engine Driven Pump is designed to have sizable stroke capacity, so that enough flows of transmission liquid to be also provided under described low engine speed.Therefore,, under high engine speed, too much transmission fluid circulates by known Engine Driven Pump and produces unnecessary loss in efficiency.
Therefore common improvement target is, the flow by reduction especially for the required transmission fluid of described two main actuation function of actuating system, improves transmission efficiency.The design that this improved target is for example revised speed changer by its applied stress level of further increase and the mode described by above-mentioned European patent is carried out.Rear one open according to this, by the so-called V angle that limit and between the Cone Disc of belt wheel, side of rotating band, by routine value 22.0 degree from it, be effectively reduced to the value in 9.1 and 19.3 scopes between spending.
In fact, it is very successful that the required gear ratio with bootup window of the system that activated and moment of torsion are controlled the known improvement effect that reduces transmission fluid flow of these two main actuation function, to such an extent as to the secondary actuation function of actuating system becomes the limiting factor of the bottom line demand pumping capacity bottom line demand of oil hydraulic pump (for) of transmission fluid flow in some transmission design.
Summary of the invention
One object of the present invention is to make known transmission further optimizing aspect the efficiency of its whole efficiency and the special electro-hydraulic actuating system at it.
According to the present invention, the electro-hydraulic actuating system that two oil hydraulic pumps are provided by providing this target realizes, wherein, one is driven by vehicle motor, and another is by motor (being independent of vehicle motor) electric drive, and by arranging that as following claim 1 electro-hydraulic actuating system realizes.
According to electro-hydraulic actuating system of the present invention, can under three kinds of patterns, operate, that is:
(i) by electric drive pump (being totally independent of vehicle motor) for its advocate peace secondary actuation function both hydraulic fluid is provided,
(ii) or by electric drive pump for it is secondary, drive function that hydraulic fluid is provided, and provide hydraulic fluid by Engine Driven Pump for two main actuation function described in it,
(iii) or by Engine Driven Pump for its advocate peace secondary actuation function both hydraulic fluid is provided.
In electro-hydraulic actuating system according to the present invention, at the transmission fluid underfed providing by Engine Driven Pump, to carry out under the serviceability of the secondary actuation function of advocating peace, electric actuation pump can be activated thinks that secondary actuation function provides other speed change flow quantity.At this, by effectively separated, give described two main actuation function and supply with to the transmission fluid of secondary actuation function, can advantageously make desired the comparing under obviously lower stress level of electric drive pump and described two main actuation function operate.Therefore, electric drive pump can be designed efficiently and move, and be optimised for and be only used to the secondary actuation function of actuating system that transmission fluid is provided, and the design of Engine Driven Pump can be optimised for only for two main actuation function described in it.In transmission design according to the present invention, low (or lower) fluid flow demand of described two main actuation function can be fully utilized to optimize design and the efficiency of Engine Driven Pump.
According to the attendant advantages of electro-hydraulic actuating system of the present invention, be that vehicle motor can be closed in for example hybrid vehicle powertrain systems and/or the vehicle with so-called start-stop engine control, thereby Engine Driven Pump is completely not driven.Under this rear one " start-stop " operational condition, the hydraulic fluid that electric drive pump provides is not only for the secondary actuation function of actuating system, but also for described two main actuation function of actuating system.It should be noted that this rear functional and operation of actuating system, known just as prior art, for example in German patent application DE-A-4134268, be described.
Accompanying drawing explanation
Now according to accompanying drawing, further illustrate the present invention, wherein:
Fig. 1 is the schematic diagram for the treatment of improved stepless speed variator of prior art;
Fig. 2 shows the novel hydraulic pressure configuration according to speed changer of the present invention, and
Fig. 3 shows three operator schemes of transmission configuration novel in Fig. 2.
Embodiment
In the accompanying drawings, the corresponding corresponding technical functionality of same reference character or structure, determine as the case may be.
Fig. 1 has schematically shown known stepless speed variator 1, such as the stepless speed variator 1 being conventionally applied in the power train of passenger car between motor VE and its driving wheel DW.Known speed changer comprises: mechanical system MS, for realizing and change input shaft 2 and the gear ratio between output shaft 3 and the speed change torque ratio of speed changer 1; With electro-hydraulic actuating system AS, for the control of speed changer 1 (that is, the slave function of advocating peace of speed changer 1).These function of tonic chords of speed changer 1 are the control of the control of gear ratio and/or torque ratio and the moment of torsion that transmits between its input and output axle 2,3 by speed changer 1.Actuating system AS controls a plurality of other or secondary actuation function AAF-I, the AAF-II of speed changer 1 conventionally, conventionally at least comprise moving member initiatively lubricate AAF-I with for being connected rotatably or disconnecting the actuation function AAF-II of the driveline clutch of vehicle motor VE and driving wheel DW.
In this specific illustrated examples, the mechanical system MS of known speed changer 1 comprises flexible-belt 4, and its winding is separately positioned on two transmission pulley 5 and 6 on the input shaft 2 of speed changer 1 and axle 3.Belt wheel 5 and 6 comprises respectively two pulley sheaves, for what frictionally coordinate with this dish, is with 4 effective conical contact surface is provided.Under the impact of each corresponding belt wheel 5 or 6 the pulley sheaves hydraulic pressure in the hydraulic pressure cavity 7 or 8 of piston-and-cylinder assembly that puts on this corresponding belt wheel 5 or 6, be urged toward each other.By apply input tape wheel pressure Pin and apply output pulley pressure P out in output pulley pressure chamber 8 in input tape wheel pressure chamber 7 simultaneously, with 4 not only in tension between belt wheel 5,6, moment of torsion can be transmitted between the input shaft 2 of speed changer 1 and output shaft 3, but also take certain radial position between the pulley sheaves of each belt wheel 5,6, this radial position represents and provides certain gear ratio of speed changer 1.
Output pulley pressure P in and output pulley pressure P out control by actuating system AS, and in the case, thereby control, gear ratio is controlled and speed change moment of torsion is controlled this two main actuation function.In order to carry out this two main actuation function, actuating system AS is provided with the ECU (Electrical Control Unit) (not shown) based on a plurality of input signals, produce in known manner the output signal for the operation of two belt wheel pressure valve 23 and 27, thereby in input tape wheel pressure chamber 7 and output pulley pressure chamber 8, pressure P in, Pout are set respectively.
Known actuating system AS is also provided with two oil hydraulic pumps 10 and 11 to introduce hydraulic transmission fluid and this transmission fluid is pumped in the main hydraulic pipe line 13 of actuating system AS from reservoir 12, and described main hydraulic pipe line 13 is connected to described two pressure valve 23 and 27.Stress level in this main line 13 or loine pressure Pline therefore should be always at least equally high with the peak in input tape wheel pressure Pin and output pulley pressure P out.Loine pressure Pline sets by means of line pressure valve 14, and described valve 14 also operates by the ECU (Electrical Control Unit) (not shown) of actuating system AS.
Line pressure valve 14 is imported any residue transmission fluid into secondary hydraulic pipe line 15 from main line 13.Therefore force value in this looped pipeline road 15 or secondary stress Paux can set lower than loine pressure Pline and by means of secondary pressure valve 16 always.Secondary pressure valve 16 can be controlled to set constant secondary stress Paux passively, yet in the embodiment who describes at present, this valve 16 also operates by the ECU (Electrical Control Unit) (not shown) of actuating system AS.When the transmission fluid providing from this looped pipeline road 15 is provided, described secondary actuation function AAF-I and the AAF-II of speed changer 1 are operated and are controlled by actuating system AS.At least, in this example in known actuating system AS, secondary pressure valve 16 is sent the too much transmission fluid of any residue reservoir 12 back to from looped pipeline road 15.In this rear one side, it should be noted that, in the secondary actuation function of advocating peace described in actuating system AS or the transmission fluid using by the secondary actuation function of advocating peace described in actuating system AS after this use, also return to reservoir 12, thereby the hydraulic unit of actuating system AS forms closed circuit, and transmission fluid at least circulates by pump 10,11 at speed changer 1 run duration in this closed circuit.
In this known actuating system AS, the first pump 10 in two oil hydraulic pumps 10,11 is mechanically driven by vehicle motor VE, thereby the flow of the transmission fluid being provided by this first pump 10 is determined by (rotation) speed of vehicle motor VE (bent axle).In addition, the second pump 11 in two oil hydraulic pumps 10,11 is electrically driven (operated), by the motor that is independent of vehicle motor VE, is driven.Therefore the second pump 11 can start on demand and start to variable degree, particularly when during the dynamic operation of the mechanical system MS of speed changer 1 or when vehicle motor VE and the first pump 10 shutdown.Unidirectional or safety check 17,18 is arranged between each pump 10,11 and main line 13, and transmission fluid flows back to reservoir 12 from main line 13 through these corresponding pumps 10,11 when preventing that in pump 10,11 any is shut down.
As already mentioned in preface part, the whole efficiency that this known speed changer 1 has had, particularly compares with more traditional transmission design only with Engine Driven Pump 10.Yet according to the present invention, even if the transmission design herein in Fig. 1 still can be modified aspect whole speed change efficiency, its transmission design after improving schematically shows in Fig. 2.
Fig. 2, the speed changer 1 of wherein describing, corresponding with speed changer 1 known in Fig. 1 haply, yet, there are two serious differences.The first difference is the second pump in described two oil hydraulic pumps 10,11, is the looped pipeline road 15 that electric drive pump 11 is connected to (that is, transmission fluid being pumped to) actuating system AS.In addition, the first pump, be described two main actuation function (even when low engine speed) that the pumping capacity of Engine Driven Pump 10 can be designed to be suitable for actuating system AS, needn't consider otherwise can additionally be required the pumping capacity for secondary actuation function AAF-I, AAF-II.
This first difference (being the structure characteristic that electric drive pump 11 is connected to looped pipeline road 15 (being the downstream of line pressure valve 14)) therefore advantageously realizes the raising of transmission efficiency by reducing the pumping capacity of Engine Driven Pump 10.
The second difference according between speed changer 1 known in speed changer 1 of the present invention and Fig. 1 of Fig. 2 is that bypass hydraulic pipe line 20 is arranged between main line 13 and looped pipeline road 15, thereby bypass line pressure valve 14, described bypass line 20 comprises another safety check 21, and described bypass line 20 is parallel to line pressure valve 14.Described another safety check 21 of bypass line 20 is assembled into: make transmission fluid be allowed to the 15 inflow main lines 13 (as long as secondary stress Paux is higher than loine pressure Pline) from looped pipeline road, but along contrary direction, do not flow.Therefore, electric drive pump 11 still can by transmission fluid is not only provided to and for described secondary actuation function AAF-I, the AAF-II of the actuating system AS of speed changer 1, but also provide to and control and speed change moment of torsion is controlled two main actuation function described in this for its gear ratio, to support Engine Driven Pump 10.
In conjunction with the first above-mentioned difference, this second difference (being about to the structure characteristic that looped pipeline road 15 is connected to described bypass line 20 and described another safety check 21 of main line 13) therefore advantageously allows vehicle motor to close down in known manner in the operating process of speed changer 1.
Fig. 2 can operate by three kinds of different modes according to electro-hydraulic actuating system AS of the present invention, respectively as shown in Fig. 3 A, 3B and 3C.In these Fig. 3 A, 3B and 3C, actuating system AS by from or by electric drive pump 11, provide the part of transmission fluid or parts to represent with thick dashed line, and actuating system AS by from or by Engine Driven Pump 10, provide the part of transmission fluid or parts with heavy line table not.
In the first operator scheme of electro-hydraulic actuating system AS, as shown in Figure 3A, only has Engine Driven Pump 10 at pumping transmission fluid.That is to say, the flow of the transmission fluid being produced by Engine Driven Pump 10 is enough to make actuating system AS can carry out gear ratio and moment of torsion is controlled these two main actuation function " MAF " and its any secondary actuation function " AAF ".In this first operator scheme, electric drive pump 11 quilts are for stopping using completely or at least can being stopped using completely.
In the second operator scheme of electro-hydraulic actuating system AS, as shown in Figure 3 B, Engine Driven Pump 10 and electric drive pump 11 are at pumping transmission fluid.That is to say, the underfed of the transmission fluid being produced by Engine Driven Pump 10 is also to carry out the secondary actuation function " AAF " of actuating system AS completely outside two the main actuation function " MAF " carrying out actuating system AS.In this second operator scheme, electric drive pump 11 is activated to produce the additional flow of transmission fluid so that actuating system AS also can carry out its secondary actuation function " AAF " completely.
In the 3rd operator scheme of electro-hydraulic actuating system AS, as shown in Figure 3 C, vehicle motor and Engine Driven Pump 10 are deactivated and only have electric drive pump 11 at pumping transmission fluid.That is to say, electric drive pump 11 is activated so that the flow of consequent transmission fluid is enough to make actuating system AS can carry out its gear ratio and moment of torsion is controlled these two main actuation function " MAF " and any secondary actuation function " AAF " thereof.
The invention is not restricted to example discussed above, but additionally contain various modifications and improvement that it may not depart from the scope of the present invention being limited by all structure characteristics shown in specification, accompanying drawing and accompanying drawing and claim.
Claims (3)
1. one kind for transferring to the driving force of motor (VE) stepless speed variator (1) of load to be driven (DW), particularly in vehicle transmission system, described stepless speed variator (1) is provided with two oil hydraulic pumps (10, 11) to discharge the forced feed of hydraulic transmission fluid, carry out the actuating for speed changer (1), wherein, the first pump (10) drives by motor (VE) and the second pump (11) drives by being independent of the motor of motor (VE), described stepless speed variator (1) is also provided with main hydraulic pipe line (13), secondary hydraulic pipe line (15) and line pressure valve (14), described line pressure valve (14) is controlled the pressure (Pline) main line (13) by making unnecessary transmission fluid flow to looped pipeline road (15) from main line (13), wherein, the first pump (10) is connected to main line (13), it is characterized in that, the second pump (11) is connected to looped pipeline road (15).
2. stepless speed variator according to claim 1 (1), it is characterized in that, the bypass hydraulic pipe line (20) with safety check (21) is arranged between main line (13) and looped pipeline road (15), this safety check (21) is arranged as: make transmission fluid flow process bypass line (20) to main line (13) from looped pipeline road (15), and can stop the reverse flow of transmission fluid.
3. stepless speed variator according to claim 1 and 2 (1), it is characterized in that, the operation of speed changer comprises that gear ratio is controlled and speed changer driving torque is controlled these two main transformer speed actuation function (MAF) and one or more secondary shift actuation functions (AAF), for example lubricated and/or speed change clutch is controlled, two main transformer speed actuation function (MAF) are implemented as uses the transmission fluid of introducing from main line (13), and described one or more secondary shift actuation functions (AAF) are implemented as the transmission fluid using from looped pipeline road (15) introducing.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/EP2011/006599 WO2013097880A1 (en) | 2011-12-29 | 2011-12-29 | Hydraulically actuated continuously variable transmission for a vehicular drive line provided with an engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104160180A true CN104160180A (en) | 2014-11-19 |
Family
ID=45464499
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180076133.1A Pending CN104160180A (en) | 2011-12-29 | 2011-12-29 | Hydraulically actuated continuously variable transmission for a vehicular drive line provided with an engine |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN104160180A (en) |
| WO (1) | WO2013097880A1 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108006209A (en) * | 2017-03-29 | 2018-05-08 | 长城汽车股份有限公司 | Double clutch automatic speed changing case cooling and lubricating hydraulic control system and vehicle |
| CN109386610A (en) * | 2017-08-10 | 2019-02-26 | 本田技研工业株式会社 | Hydraulic control device |
| CN109595321A (en) * | 2018-12-30 | 2019-04-09 | 芜湖万里扬变速器有限公司 | Pure electric vehicle stepless speed variator system |
| WO2019166046A1 (en) * | 2018-02-28 | 2019-09-06 | Schaeffler Technologies AG & Co. KG | Switching assembly for adjusting a first pulley set and a second pulley set of a cone pulley traction mechanism transmission |
| CN110578796A (en) * | 2018-06-08 | 2019-12-17 | 舍弗勒技术股份两合公司 | Hydraulic system |
| CN112789432A (en) * | 2018-08-31 | 2021-05-11 | 邦奇动力有限责任公司 | Hydraulic control circuit for continuously variable transmission, and method for controlling clamping force of continuously variable transmission |
| CN114761710A (en) * | 2019-12-05 | 2022-07-15 | 罗伯特·博世有限公司 | Hydraulic unit for continuously variable transmission for electric vehicle application and continuously variable transmission equipped with hydraulic unit |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015125718A1 (en) * | 2014-02-20 | 2015-08-27 | ジヤトコ株式会社 | Hydraulic control device and method for controlling same |
| JP6277918B2 (en) * | 2014-09-16 | 2018-02-14 | トヨタ自動車株式会社 | Vehicle hydraulic control device |
| DE102016204399A1 (en) * | 2016-03-17 | 2017-09-21 | Zf Friedrichshafen Ag | Hydraulic system for a transmission of a motor vehicle |
| SE541602C2 (en) * | 2017-05-05 | 2019-11-12 | Scania Cv Ab | A lubrication system for a gearbox arranged in a vehicle |
| CN113544413A (en) | 2019-03-06 | 2021-10-22 | 罗伯特·博世有限公司 | Method for operating an electric vehicle powertrain with a continuously variable transmission |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20050263352A1 (en) * | 2004-05-26 | 2005-12-01 | Winfried Fideler | Hydraulic circuit for oil supply of an automatic, particularly a stepped automatic transmission for motor vehicles |
| JP2007247910A (en) * | 2007-07-02 | 2007-09-27 | Honda Motor Co Ltd | Hydraulic pressure supply device |
| EP1865236A1 (en) * | 2006-06-09 | 2007-12-12 | Robert Bosch Gmbh | Hydraulically actuated continuously variable transmission for a vehicular drive line provided with an internal combustion engine |
| CN101290064A (en) * | 2007-04-20 | 2008-10-22 | 丰田自动车株式会社 | Oil supply system for vehicle |
| DE102008035142A1 (en) * | 2007-08-07 | 2009-02-12 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydraulic arrangement for an automatic transmission |
| US20090232673A1 (en) * | 2005-03-22 | 2009-09-17 | Zf Friedrichshafen Ag | Method and device for controlling the oil supply of an automatic gearbox and a starting element |
| CN101925762A (en) * | 2007-12-28 | 2010-12-22 | 罗伯特·博世有限公司 | Automatic transmission provided with hydraulically assisted clutch and method for operating the same |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4134268C2 (en) | 1990-10-29 | 2001-05-17 | Volkswagen Ag | Drive arrangement for a motor vehicle |
| JP3660047B2 (en) | 1996-03-27 | 2005-06-15 | 本田技研工業株式会社 | Metal V belt type continuously variable transmission |
-
2011
- 2011-12-29 CN CN201180076133.1A patent/CN104160180A/en active Pending
- 2011-12-29 WO PCT/EP2011/006599 patent/WO2013097880A1/en active Application Filing
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20050263352A1 (en) * | 2004-05-26 | 2005-12-01 | Winfried Fideler | Hydraulic circuit for oil supply of an automatic, particularly a stepped automatic transmission for motor vehicles |
| US20090232673A1 (en) * | 2005-03-22 | 2009-09-17 | Zf Friedrichshafen Ag | Method and device for controlling the oil supply of an automatic gearbox and a starting element |
| EP1865236A1 (en) * | 2006-06-09 | 2007-12-12 | Robert Bosch Gmbh | Hydraulically actuated continuously variable transmission for a vehicular drive line provided with an internal combustion engine |
| CN101290064A (en) * | 2007-04-20 | 2008-10-22 | 丰田自动车株式会社 | Oil supply system for vehicle |
| JP2007247910A (en) * | 2007-07-02 | 2007-09-27 | Honda Motor Co Ltd | Hydraulic pressure supply device |
| DE102008035142A1 (en) * | 2007-08-07 | 2009-02-12 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydraulic arrangement for an automatic transmission |
| CN101925762A (en) * | 2007-12-28 | 2010-12-22 | 罗伯特·博世有限公司 | Automatic transmission provided with hydraulically assisted clutch and method for operating the same |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108006209A (en) * | 2017-03-29 | 2018-05-08 | 长城汽车股份有限公司 | Double clutch automatic speed changing case cooling and lubricating hydraulic control system and vehicle |
| CN108006209B (en) * | 2017-03-29 | 2019-12-13 | 长城汽车股份有限公司 | Double-clutch automatic gearbox cooling and lubricating hydraulic control system and vehicle |
| US11255423B2 (en) | 2017-03-29 | 2022-02-22 | Great Wall Motor Company Limited | Dual-clutch automatic transmission cooling and lubrication hydraulic control system and vehicle |
| CN109386610A (en) * | 2017-08-10 | 2019-02-26 | 本田技研工业株式会社 | Hydraulic control device |
| WO2019166046A1 (en) * | 2018-02-28 | 2019-09-06 | Schaeffler Technologies AG & Co. KG | Switching assembly for adjusting a first pulley set and a second pulley set of a cone pulley traction mechanism transmission |
| CN111566391A (en) * | 2018-02-28 | 2020-08-21 | 舍弗勒技术股份两合公司 | Switching assembly for adjusting a first disk set and a second disk set of a conical disk transmission |
| CN111566391B (en) * | 2018-02-28 | 2022-05-13 | 舍弗勒技术股份两合公司 | Switching assembly for adjusting a first disk set and a second disk set of a conical disk transmission |
| CN110578796A (en) * | 2018-06-08 | 2019-12-17 | 舍弗勒技术股份两合公司 | Hydraulic system |
| CN112789432A (en) * | 2018-08-31 | 2021-05-11 | 邦奇动力有限责任公司 | Hydraulic control circuit for continuously variable transmission, and method for controlling clamping force of continuously variable transmission |
| CN109595321A (en) * | 2018-12-30 | 2019-04-09 | 芜湖万里扬变速器有限公司 | Pure electric vehicle stepless speed variator system |
| CN114761710A (en) * | 2019-12-05 | 2022-07-15 | 罗伯特·博世有限公司 | Hydraulic unit for continuously variable transmission for electric vehicle application and continuously variable transmission equipped with hydraulic unit |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2013097880A1 (en) | 2013-07-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104160180A (en) | Hydraulically actuated continuously variable transmission for a vehicular drive line provided with an engine | |
| CN101544217B (en) | Hydraulic control system for multi-mode hybrid transmission and method of regulating the same | |
| CN102165222B (en) | Power transmitting device and vehicle having power transmitting device mounted thereon | |
| CN101549687B (en) | Hydraulic control system for multi-mode hybrid transmission and method of regulating the same | |
| US6805647B2 (en) | Hybrid electric vehicle auxiliary oil pump | |
| CN108626366B (en) | Cooling and lubrication system for an automatic transmission including a three-way solenoid actuated valve | |
| CN103443509B (en) | The hydraulic control device of stepless speed variator | |
| CN103671894A (en) | Hydraulic pressure supply system of automatic transmission | |
| CN100538125C (en) | The apparatus and method of reducing engine load at stop | |
| US20180135743A1 (en) | Multi-pressure hydraulic control system for a continuously variable automatic transmission | |
| JP6427471B2 (en) | Hydraulic circuit and control device therefor | |
| CN102767618A (en) | Transmission of a motor vehicle, having an input shaft and an output shaft | |
| CN103477120B (en) | Variable v-belt drive | |
| CN108027056B (en) | The coast stop control method and control device of vehicle | |
| JP6190858B2 (en) | Hydraulic circuit control device | |
| US20090038305A1 (en) | Hydraulic system for an automatic transmission | |
| JP2011196390A (en) | Hydraulic device of automatic transmission | |
| US20180087661A1 (en) | Multi-pressure hydraulic control system for a step-gear automatic transmission | |
| CN100378374C (en) | Hydrodynamic actuating device for construction machines | |
| EP2626596A1 (en) | Hydraulic control device for winding transmission device | |
| CN1275813C (en) | Power transmission device | |
| US20180100577A1 (en) | Multi-pressure hydraulic control system for a dual clutch automatic transmission | |
| US20120297758A1 (en) | Large Displacement Variator | |
| BE1023733B9 (en) | HYDRAULIC SYSTEM | |
| CN201081010Y (en) | Metal strips type stepless speed changer hydraulic actuator |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20141119 |