WO2015067268A1 - Hydraulikanordnung - Google Patents
Hydraulikanordnung Download PDFInfo
- Publication number
- WO2015067268A1 WO2015067268A1 PCT/DE2014/200589 DE2014200589W WO2015067268A1 WO 2015067268 A1 WO2015067268 A1 WO 2015067268A1 DE 2014200589 W DE2014200589 W DE 2014200589W WO 2015067268 A1 WO2015067268 A1 WO 2015067268A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- hydraulic
- hydrostatic
- section
- pressure
- path
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/06—Control by electric or electronic means, e.g. of fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- 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
- F16D2048/0236—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 with multiple independent pumps, e.g. one per clutch, or for supplying fluid to different systems
-
- 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
- F16D2048/0236—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 with multiple independent pumps, e.g. one per clutch, or for supplying fluid to different systems
- F16D2048/0239—One fluid source supplying fluid at high pressure and one fluid source supplying fluid at low 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
- 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
Definitions
- the invention relates to a hydraulic system for actuating at least one clutch, with a hydrostatic path between a slave cylinder and a master cylinder.
- the invention further relates to a method for actuating at least one coupling with such a hydraulic arrangement.
- Clutch actuator with a master cylinder and an axially displaceable, a pressure chamber with pressure acting piston known.
- the object of the invention is to simplify the actuation of at least one clutch with a hydrostatic path between a slave cylinder and a master cylinder.
- the object is achieved in a hydraulic arrangement for actuating at least one clutch, with a hydrostatic path between a slave cylinder and a master cylinder, characterized in that the master cylinder is designed as a hydraulic pressure booster between the hydrostatic section and a hydraulic path with a hydraulic pump actuator.
- the hydrostatic path serves to transmit an actuating force for actuating the clutch from the master cylinder by means of a static pressure to the slave cylinder.
- the actuating force is generated in the hydraulic path by the hydraulic pump actuator.
- the hydraulic pressure booster realizes an interface between the hydraulic section and the hydrostatic section in a simple manner.
- the above object is alternatively achieved in that the master cylinder as a hydraulic pressure booster between the respective hydrostatic route and in each case a hydraulic route are designed with a hydraulic pump actuator.
- the hydrostatic path serves to transmit an actuating force for actuating the clutch from the master cylinder by means of a static pressure to the slave cylinder.
- the actuating force is generated in the hydraulic path by the hydraulic pump actuator.
- the hydraulic pressure booster is easy way and realized an interface between the hydraulic route and the hydrostatic route.
- Each partial clutch of the double clutch is thus assigned a hydrostatic section and a hydraulic section with a hydraulic pump actuator. The actuation of the pump actuators can take place via separate control units or via a common control unit.
- a hydraulic arrangement for actuating a double clutch with two partial clutches each associated with a hydrostatic path between a slave cylinder and a master cylinder
- the master cylinder as a hydraulic pressure booster between the respective hydrostatic route and a hydraulic route
- a common hydraulic pump actuator and a hydraulic logic are executed.
- the hydrostatic path serves to transmit an actuating force for actuating the clutch from the master cylinder by means of a static pressure to the slave cylinder.
- the actuating force is generated in the hydraulic path by the hydraulic pump actuator.
- the hydraulic pressure booster realizes an interface between the hydraulic section and the hydrostatic section in a simple manner.
- Each partial clutch of the double clutch is assigned a hydrostatic section and a pressure booster. Hydraulic lines from the intensifiers are combined via the hydraulic logic in the common hydraulic pump actuator.
- the above object is alternatively achieved in that the master cylinder as a hydraulic pressure booster between the respective hydrostatic route and a hydraulic route a common hydraulic control unit are executed.
- the hydrostatic path serves to transmit an actuating force for actuating the clutch from the master cylinder by means of a static pressure to the slave cylinder.
- the hydraulic pressure booster realizes an interface between the hydraulic section and the hydrostatic section in a simple manner.
- the hydraulic control unit includes, for example, conventional conventional hydraulic control logic.
- Such a control logic comprises, for example, a gear pump mechanically driven by an internal combustion engine as a hydraulic pressure source or volume flow source.
- Another preferred embodiment of the hydraulic system is characterized in that the two hydraulic pressure booster are realized in separate housing parts.
- a further preferred embodiment of the hydraulic arrangement is characterized in that the two hydraulic pressure booster are realized in a common housing part.
- a further preferred embodiment of the hydraulic arrangement is characterized in that a housing of the hydraulic pressure booster or of the hydraulic pressure booster is formed from plastic.
- a further preferred embodiment of the hydraulic arrangement is characterized in that the hydraulic line with the hydraulic pump actuator is connected directly to a low-pressure side of the hydraulic pressure booster.
- a further preferred embodiment of the hydraulic arrangement is characterized in that the hydraulic pump actuator is designed as a reversing pump with opposite directions of flow.
- the reversible pump is preferably an electric motor driven hydraulic pump.
- the hydraulic pump is preferably designed as a positive displacement pump, for example as a vane pump, gear pump or piston pump.
- Another preferred embodiment of the hydraulic system is characterized in that the hydraulic path is acted upon by a low pressure, wherein the hydrostatic path is acted upon by a high pressure.
- the hydraulic path can be acted upon by a high pressure, wherein the hydrostatic path is then subjected to a low pressure.
- the low pressure is for example a pressure of about fifteen bar.
- the high pressure is for example a pressure of about forty bar.
- a further preferred exemplary embodiment of the hydraulic system is characterized in that the hydraulic pressure booster has a pressure relief port on a high-pressure side, via which the hydrostatic path in an unactuated state of the hydraulic pressure booster is connected without pressure to a fluid space located higher. that will.
- the term higher refers to the earth gravity in the installed state of the hydraulic system.
- the fluid space is represented for example by a surge tank, which is connected to the hydraulic booster.
- a further preferred embodiment of the hydraulic arrangement is characterized in that the hydraulic pressure booster is equipped with a sensor device which detects the current operating state of the hydraulic pressure booster.
- the sensor device is connected, for example via a signal line, to an electronic control unit.
- the electronic control unit is supplied in addition to a position signal of the hydraulic pressure booster alternatively or additionally, a pressure signal of the low pressure side.
- the pressure in the hydraulic path on the low pressure side is advantageously detected by a further pressure sensor.
- the electronic control unit is advantageously supplied in addition to the position signal of the hydraulic pressure booster alternatively or additionally, a pressure signal of the high pressure side.
- the pressure in the hydrostatic section or on the high pressure side of the hydraulic pressure booster is advantageously detected by a further pressure sensor.
- the position signals detected by the sensor device and the pressure signals optionally detected with at least one of the mentioned pressure sensors are used to improve the control of the pump actuator, in particular an electromotive pump drive, and thus to improve the operation of the clutch.
- the sensor device can be used to detect the position signal of the hydraulic pressure booster, since the control of the pump drive and thus the operation of the clutch is mainly influenced by the position signal. Then one or more, or all, pressure sensors can be saved.
- Another preferred embodiment of the hydraulic system is characterized in that the hydrostatic path and the hydraulic path are filled with the same hydraulic medium. As a result, the logistical effort in the manufacture and assembly of the hydraulic system can be reduced.
- a further preferred embodiment of the hydraulic system is characterized in that the hydrostatic path and the hydraulic path are filled with different hydraulic media. This provides the advantage that the optimum hydraulic medium can be selected for the two routes.
- a further preferred embodiment of the hydraulic system is characterized in that the hydraulic pressure booster has a pressure ratio of one to one. In this case, the hydraulic pressure booster is mainly used for media separation between the hydrostatic line and the hydraulic line.
- the above-mentioned object is alternatively or additionally achieved in that the coupling is hydrostatically actuated starting from the hydraulic path via the hydraulic pressure booster and the hydrostatic path.
- Figure 1 is a simplified representation of a hydraulic system according to the invention for actuating a dual clutch, comprising two partial clutches;
- Figure 2 is a similar view as in Figure 1 with only a pump actuator and a hydraulic control logic and
- Figure 3 is a similar view as in Figures 1 and 2 with a hydraulic control unit.
- FIG. 1 shows in simplified form a hydraulic arrangement 1 for actuating a double clutch 2.
- the dual clutch 2 comprises two partial clutches 10, 50. If one considers only one of the two partial clutches 10, 50, then the associated part of the hydraulic arrangement 1 can also be used alone for actuating a single clutch.
- the two partial clutches 10, 50 are hydrostatically actuated with the interposition of an actuating bearing 1 1, 51 by a slave cylinder 12, 52.
- the slave cylinder 12, 52 is hydrostatically connected to a master cylinder 15, 55 via a hydrostatic section 14, 54.
- the hydrostatic section 14, 54 can be acted upon by a high pressure of about forty bar.
- the hydraulic section 18, 58 can be acted upon with a low pressure of about fifteen bar.
- the hydraulic section 18, 58 comprises a pump actuator 20, 60.
- the pump actuator 20, 60 is designed as a reversing pump 22, 62 with opposite directions of flow.
- the re-versierpumpe 22, 62 can be driven by an electric motor 23, 63 in opposite directions of rotation.
- the electric motor 23, 63 which serves to drive the reversing pump 22, 62, is connected in terms of control to a control unit 25, 65.
- the control units 25, 65 can be combined in a common control unit.
- the control unit 25, 65 is further connected in terms of control with an optional pressure sensor 26, 66, a sensor device 28, 68 and a pressure sensor 30, 70.
- the pressure sensor 26, 66 detects the pressure on the high-pressure side of the hydraulic pressure booster 16. 56.
- the sensor device 28, 68 detects the position of a booster piston in the hydraulic pressure booster 16, 56.
- the pressure sensor 30, 70 detects the pressure in the hydraulic path 18, 58th
- the reversing pump 22, 62 is connected via a tank connection to a hydraulic medium reservoir 24, 64.
- the hydraulic pressure booster 16, 56 is connected to a container 31, 71 with hydraulic medium.
- the container 31, 71 serves to receive leakage.
- the container 31, 71 may be merged with the reservoir 24, 64.
- the hydraulic pressure booster 16, 56 is further connected to a container 32, 72.
- the container 32, 72 based on the Erdhekraft, in the installed state of the hydraulic assembly 1 above the hydraulic pressure booster 16, 56 are arranged.
- the container 32, 72 serves as a reservoir and represents a fluid chamber 33, 73 with hydraulic medium, which is acted upon by ambient pressure.
- the pressurized with low pressure hydraulic line 18, 58 with the pump actuator 20, 60 is connected directly to a low pressure side of the hydraulic pressure booster 16, 56.
- the high-pressure side of the hydraulic pressure booster 16, 56 is connected to the slave cylinder 12, 52 via the hydrostatic section 14, 54.
- the high pressure side or a high pressure chamber of the hydraulic pressure booster 16, 56 is connected without pressure to the higher fluid space 33, 73.
- the sensor device 28, 68 the current position of the booster piston in the hydraulic pressure booster 16, 56 is transmitted to the control unit 25, 65.
- the hydrostatic section 14, 54 and the hydraulic section 18, 58 are advantageously filled with the same hydraulic medium.
- the two routes 14, 54 and 18, 58 can also be filled with different hydraulic media. This provides the advantage that a hydraulic medium with the appropriate or ideal hydraulic properties can be selected for the respective route.
- the hydraulic pressure booster 16, 56 also serves for media separation.
- FIGS. 2 and 3 show similar hydraulic arrangements as in FIG. The same parts are provided with no or the same reference numerals as in Figure 1. To avoid repetition, reference is made to the preceding description of FIG. In the following, mainly the differences between the illustrated embodiments will be discussed.
- the two hydraulic lines 18, 58 are connected via a hydraulic logic 80 with a hydraulic medium reservoir 81 to a common pump actuator 82.
- the common pump actuator 82 is designed as a re-versierpumpe 83 with opposite directions of flow or directions of rotation.
- the drive of the reversing pump 83 via an electric motor 84 via an electric motor 84.
- the electric motor 84 is connected in terms of control with a common control unit 85 for both partial clutches.
- the actuating supply with hydraulic medium is realized by the hydraulic logic 80.
- the two hydraulic lines 18, 58 in contrast to the embodiment shown in Figure 2, connected to a common hydraulic control unit 90.
- the common hydraulic control unit 90 is in control with a common controller 95 for both Part couplings connected.
- the hydraulic control unit 90 is preferably a classic hydraulic control logic.
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201480060562.3A CN105705818A (zh) | 2013-11-05 | 2014-10-23 | 液压组件 |
EP14802307.0A EP3066355A1 (de) | 2013-11-05 | 2014-10-23 | Hydraulikanordnung |
JP2016550943A JP2016535224A (ja) | 2013-11-05 | 2014-10-23 | 液圧装置 |
DE112014005079.2T DE112014005079A5 (de) | 2013-11-05 | 2014-10-23 | Hydraulikanordnung |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013222434.6 | 2013-11-05 | ||
DE102013222434 | 2013-11-05 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2015067268A1 true WO2015067268A1 (de) | 2015-05-14 |
Family
ID=51947089
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2014/200589 WO2015067268A1 (de) | 2013-11-05 | 2014-10-23 | Hydraulikanordnung |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP3066355A1 (de) |
JP (1) | JP2016535224A (de) |
CN (1) | CN105705818A (de) |
DE (1) | DE112014005079A5 (de) |
WO (1) | WO2015067268A1 (de) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015204673B3 (de) * | 2015-03-16 | 2016-07-21 | Schaeffler Technologies AG & Co. KG | Hydraulikanordnung für eine hydraulisch betätigte Reibkupplung und Verfahren zum Betätigen einer hydraulisch betätigten Reibkupplung |
WO2017041804A1 (de) * | 2015-09-10 | 2017-03-16 | Schaeffler Technologies AG & Co. KG | Pumpenaktor für eine hydraulische kupplungsbetätigungsanordnung |
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 |
WO2017101932A1 (de) * | 2015-12-18 | 2017-06-22 | Schaeffler Technologies AG & Co. KG | Pumpenaktor zur kupplungs- und gangstelleraktuierung in einem getriebe eines kraftfahrzeugs |
DE102016210400B3 (de) * | 2016-06-13 | 2017-09-21 | Schaeffler Technologies AG & Co. KG | Fluidanordnung und Verfahren zur fluidischen Betätigung mindestens eines Verbrauchers |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017115453A1 (de) * | 2017-07-11 | 2019-01-17 | Schaeffler Technologies AG & Co. KG | Verfahren und System zum fluidischen Betätigen von zwei Teilkupplungen |
DE102018007461A1 (de) * | 2018-09-21 | 2020-03-26 | Fte Automotive Gmbh | Hydraulische Vorrichtung zum Kühlen von wenigstens zwei nasslaufenden Kupplungen in einem Kraftfahrzeug |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5780956A (en) * | 1980-11-10 | 1982-05-20 | Nippon Air Brake Co Ltd | Hydraulic control for anti-skid device |
GB2174161A (en) * | 1985-04-25 | 1986-10-29 | Volkswagen Ag | Hydraulic brake system for motor vehicles having an anti-skid control device |
EP1837545A1 (de) * | 2006-03-21 | 2007-09-26 | Peugeot Citroën Automobiles Sa | Kupplungshilfssystem und ein solches System umfassendes Kraftfahrzeug |
WO2011050766A1 (de) | 2009-10-29 | 2011-05-05 | Schaeffler Technologies Gmbh & Co. Kg | Hydrostatischer kupplungsaktor |
DE102011119631A1 (de) * | 2011-11-22 | 2013-05-23 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Aktuatoranordnung für einen Kraftfahrzeug-Antriebsstrang |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NO902057L (no) * | 1990-05-09 | 1991-11-11 | Kongsberg Automotive As | Kraftforsterkningsinnretning til inn- og utkobling av kjoeretoeyclutcher. |
DE102004009834A1 (de) * | 2003-03-03 | 2004-09-16 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Antriebsstrang |
DE102008056665A1 (de) * | 2007-12-11 | 2009-06-18 | Continental Teves Ag & Co. Ohg | Verfahren zur automatischen Steuerung einer Kupplung eines Kraftrades sowie Kraftrad |
-
2014
- 2014-10-23 WO PCT/DE2014/200589 patent/WO2015067268A1/de active Application Filing
- 2014-10-23 EP EP14802307.0A patent/EP3066355A1/de not_active Withdrawn
- 2014-10-23 JP JP2016550943A patent/JP2016535224A/ja active Pending
- 2014-10-23 DE DE112014005079.2T patent/DE112014005079A5/de not_active Withdrawn
- 2014-10-23 CN CN201480060562.3A patent/CN105705818A/zh active Pending
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5780956A (en) * | 1980-11-10 | 1982-05-20 | Nippon Air Brake Co Ltd | Hydraulic control for anti-skid device |
GB2174161A (en) * | 1985-04-25 | 1986-10-29 | Volkswagen Ag | Hydraulic brake system for motor vehicles having an anti-skid control device |
EP1837545A1 (de) * | 2006-03-21 | 2007-09-26 | Peugeot Citroën Automobiles Sa | Kupplungshilfssystem und ein solches System umfassendes Kraftfahrzeug |
WO2011050766A1 (de) | 2009-10-29 | 2011-05-05 | Schaeffler Technologies Gmbh & Co. Kg | Hydrostatischer kupplungsaktor |
DE102011119631A1 (de) * | 2011-11-22 | 2013-05-23 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Aktuatoranordnung für einen Kraftfahrzeug-Antriebsstrang |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015204673B3 (de) * | 2015-03-16 | 2016-07-21 | Schaeffler Technologies AG & Co. KG | Hydraulikanordnung für eine hydraulisch betätigte Reibkupplung und Verfahren zum Betätigen einer hydraulisch betätigten Reibkupplung |
WO2017041804A1 (de) * | 2015-09-10 | 2017-03-16 | Schaeffler Technologies AG & Co. KG | Pumpenaktor für eine hydraulische kupplungsbetätigungsanordnung |
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 |
CN106870599B (zh) * | 2015-12-14 | 2021-04-09 | 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 |
WO2017101932A1 (de) * | 2015-12-18 | 2017-06-22 | Schaeffler Technologies AG & Co. KG | Pumpenaktor zur kupplungs- und gangstelleraktuierung in einem getriebe eines kraftfahrzeugs |
CN108291590A (zh) * | 2015-12-18 | 2018-07-17 | 舍弗勒技术股份两合公司 | 用于在机动车的变速器中进行离合器和换挡器致动的泵致动器 |
CN108291590B (zh) * | 2015-12-18 | 2020-04-07 | 舍弗勒技术股份两合公司 | 用于在机动车的变速器中进行离合器和换挡器致动的泵致动器 |
DE102016210400B3 (de) * | 2016-06-13 | 2017-09-21 | Schaeffler Technologies AG & Co. KG | Fluidanordnung und Verfahren zur fluidischen Betätigung mindestens eines Verbrauchers |
Also Published As
Publication number | Publication date |
---|---|
CN105705818A (zh) | 2016-06-22 |
JP2016535224A (ja) | 2016-11-10 |
DE112014005079A5 (de) | 2016-08-04 |
EP3066355A1 (de) | 2016-09-14 |
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