EP3227587A2 - Ensemble frein de stationnement - Google Patents

Ensemble frein de stationnement

Info

Publication number
EP3227587A2
EP3227587A2 EP15794471.1A EP15794471A EP3227587A2 EP 3227587 A2 EP3227587 A2 EP 3227587A2 EP 15794471 A EP15794471 A EP 15794471A EP 3227587 A2 EP3227587 A2 EP 3227587A2
Authority
EP
European Patent Office
Prior art keywords
pressure
control
slide
valve
chamber
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.)
Withdrawn
Application number
EP15794471.1A
Other languages
German (de)
English (en)
Inventor
Markus Brandenburg
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mercedes Benz Group AG
Original Assignee
Daimler AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Daimler AG filed Critical Daimler AG
Publication of EP3227587A2 publication Critical patent/EP3227587A2/fr
Withdrawn legal-status Critical Current

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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/40—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism comprising signals other than signals for actuating the final output mechanisms
    • F16H63/48—Signals to a parking brake or parking lock; Control of parking locks or brakes being part of the transmission
    • F16H63/483—Circuits for controlling engagement of parking locks or brakes
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/34—Locking or disabling mechanisms
    • F16H63/3416—Parking lock mechanisms or brakes in the transmission
    • F16H63/3483—Parking lock mechanisms or brakes in the transmission with hydraulic actuating means

Definitions

  • the invention relates to a parking brake device for a motor vehicle.
  • the invention relates to a parking brake device for a motor vehicle, having at least one actuating unit which is provided for actuating a parking lock, and having at least one discharge slide, which has at least one pressure chamber with at least one actuation port connected to the actuation unit.
  • the emptying slide has at least one control surface associated with the pressure chamber, which serves to provide one of a
  • the emptying slide is provided to decouple the control surface assigned to the pressure chamber from the provision of the switching force in a first valve position and to use the control surface associated with the pressure chamber to provide the switching force in a second valve position. It can thereby be realized that the pressure prevailing in the pressure chamber
  • Maintaining the second valve position can be linked to different conditions from each other and in particular can be realized by different operating medium pressures. It can be realized that a first switching force for switching the second valve position during switched second valve position is replaced or supported by a second switching force, which results from the pressure space associated control surface, whereby the first switching force during switched second Valve position of the drain valve can be reduced or even dissolved. As a result, the first switching force after switching the second valve position can be used at least partially for other actuation. Due to the support of the first switching force by the second switching force, the second valve position can be maintained by an operating medium pressure which is smaller than an operating medium pressure which is necessary for switching the second valve position starting from the first valve position. It can be realized that a larger operating medium pressure is necessary for switching the second valve position than for holding the second valve position. As a result, an unwanted leaving the first valve position due to
  • Valve position can be maintained, creating a flexible operation of the
  • the pressure chamber has at least one return port and the emptying slide is provided to connect in the first valve position the control surface associated with the pressure chamber with the return port and to separate in the second valve position the control surface associated with the pressure chamber of the return port.
  • Control surface particularly simple and reliable decoupled from the provision of switching power.
  • the actuator unit may be decoupled during decoupling
  • Pressure chamber of the emptying slide is preferably connected via the return port to a pressureless resource reservoir.
  • the parking brake device has at least one parking slide, which is intended to divert an operating medium pressure for the actuating unit, wherein the pressure chamber of the emptying slide has at least one supply port which is connected to supply the pressure chamber with the diverted operating medium pressure to the parking lock slider, and wherein the emptying slide is provided for separating the control surface associated with the pressure chamber from the supply connection in the first valve position and the control surface associated with the pressure chamber in the second valve position
  • the control surface associated with the pressure chamber By connecting the control surface associated with the pressure chamber with the supply connection, the control surface associated with the pressure chamber can be used in a particularly simple and reliable manner for the provision of the switching force. Furthermore, the actuating unit can advantageously be actuated via the pressure chamber during the utilized control surface. By the valve positions of the emptying valve can also be determined whether by the
  • Parking lock slider and the drain valve can be a redundant
  • ParksperrenbetHence Trental is realized, whereby the parking brake can be particularly safe and reliable on and interpreted.
  • the parking brake can be safely and quickly inserted and the inserted state can be reliably maintained.
  • a "supply connection of the pressure chamber” should in particular be understood to mean a hydraulic or pneumatic connection which is provided for supplying the pressure space of the emptying slide with a working medium
  • Pressure chamber of the emptying slide is preferably connected via the supply connection in terms of operational resources to an equipment pressure system or connectable.
  • the pressure chamber of the emptying slide is preferably provided to the
  • the emptying slide has at least one first control chamber and a control surface assigned to the first control chamber, which are connected to the first control chamber
  • Provision of a dependent of an operating medium pressure in the first control room switching force is provided, wherein the first control space associated control surface and the pressure chamber associated control surface are aligned rectified with respect to a switching direction to each other.
  • the pressure prevailing in the pressure chamber of the emptying valve operating medium pressure with which the operation of the Parking lock provided actuator is supplied to maintain the switched by the prevailing in the first control room operating medium pressure valve position can be used.
  • the second valve position can by a first
  • valve spool movement in the same valve position.
  • the operating medium pressures acting on the control surfaces which are rectilinearly oriented with respect to the switching direction act preferably on the valve spool movement in the same valve position.
  • Control space associated control surface acts through the circuit in the second
  • Valve position additionally act on the pressure chamber associated control surface, whereby at the same operating medium pressure, a larger control surface is effective and thus results in a higher switching force at the same operating pressure. It can be realized that after switching the emptying slide in the second valve position, the pressure chamber associated control surface is effective, which can ensure that the second valve position even with pressure drop below necessary for switching the second valve position operating medium of the emptying valve in the second valve position remains switched.
  • the emptying slide is provided to connect in the first valve position only the control surface associated with the first control chamber to the parking lock slider and in the second valve position the first control chamber associated control surface and the pressure chamber associated control surface to the parking lock slide.
  • Threshold exceeds and only then via the drain valve of the Actuator is discharged when it falls below a second pressure threshold, wherein the second pressure threshold is smaller than the first pressure threshold.
  • Threshold is preferably below a smallest, during operation of the
  • Pressure threshold is preferably dimensioned so that unintentional switching of the emptying slide is prevented in the second valve position, in particular in the dynamic transition when starting the engine.
  • the emptying slide has at least one second control chamber and a control surface assigned to the second control chamber, which is provided for providing a switching force dependent on an operating medium pressure in the second control chamber, the control surface assigned to the second control chamber and the pressure chamber associated with the second control chamber Control surface are oriented with respect to a switching direction opposite to each other.
  • This can be a
  • Shifting force can be provided in the direction of the first valve position, whereby the
  • Control of the drain valve can be improved.
  • the circuit of the second valve position can be selectively prevented thereby.
  • the control surfaces which are oriented opposite to each other with respect to the switching direction, are preferably provided for valve spool movement in opposite valve positions. The operating pressures acting on the control surfaces opposing each other with respect to the switching direction act to
  • Valve slide movement preferably in opposite valve positions.
  • the parking brake device be provided for locking the actuator unit locking unit and at least one
  • Parksperrenschieber which is intended to divert in a first valve position, an operating medium pressure for the operating unit and in a second
  • Operating medium pressure can be used either to actuate the parking brake or to actuate the locking unit, creating a particularly compact
  • Parking lock device can be provided. By the valve positions of the parking lock slider can be determined whether the parking brake is to be inserted or designed.
  • the actuating unit can be performed to actuate the parking brake as a single-acting cylinder-piston unit, which is a spring force Has switching direction and an operating medium pressure-related switching direction. By switching the parking lock slider in the first valve position is the
  • Actuator preferably operated in the operating medium pressure-related switching direction, provided that the emptying slide is switched to its second valve position and the actuating unit is unlocked.
  • the actuating unit is preferably unlocked and actuated by a spring in the spring-force-induced switching direction.
  • the locking unit has an actuating-technology control and an electromagnetic control which acts in parallel to the operational-technical control.
  • a redundant unlocking of the actuating unit can be realized, so that in the event of a failure of the
  • the first valve positions are each formed as basic positions.
  • a “basic position” is to be understood in particular a valve position of a slide, which assumes the slider without concern of a control pressure, whereby the slide preferably the basic position even when standing
  • Fig. 1 is a hydraulic system of an automatic transmission, with a
  • FIG. 1 shows a hydraulic system of an automatic transmission of a motor vehicle.
  • the automatic transmission is for example as a transmission with several coupled
  • the automatic transmission can also be used, for example, as an automated change-speed gearbox, as
  • Double clutch transmission or be designed as a continuously variable transmission.
  • the hydraulic system has a main pump 10, which is driven by an internal combustion engine 1 1.
  • the main pump 10 sucks through a suction filter 12 resources from a resource reservoir 13.
  • Fig. 1 drains to a resource reservoir are shown at several points. This is to be understood that resources from these drains directly or indirectly enters the resource reservoir 13. In the resource reservoir 13, excess resources are collected.
  • the main pump 10 conveys the operating fluid into a working pressure line 14, which supplies a working pressure slide 15 with the operating medium.
  • a check valve 16 is arranged, which is designed so that the working pressure line 14
  • the operating means is designed as a transmission oil.
  • the working pressure slide 15 is designed as a normally constructed control slide, acts on the control pressure as set by a control solenoid valve working pressure 17 operating medium pressure. Together with a spring force which sets a base pressure of the working pressure, the control pressure acts against the recirculated from the working pressure line 14 working pressure. By changing the operating pressure set by the control solenoid valve working pressure 17, the level of the working pressure can be adjusted. When the working pressure reaches that of the control solenoid valve working pressure 17
  • Lubricating pressure line 18 made a connection between the working pressure line 14 and a lubricating pressure slide 19.
  • the lubricating pressure slide 19 is thus supplied with equipment only when the working pressure has reached its set by Regelmagnetventil- working pressure 17 setpoint.
  • the working pressure slide 15 thus controls the working pressure in the working pressure line 14 to the set by Regelmagnetventil- working pressure 17 setpoint.
  • the lubricating pressure slide 19 is also designed as a normally constructed control slide, acts on the control pressure as set by a control solenoid valve lubrication pressure 20 operating medium pressure.
  • the control solenoid lubrication pressure 20 may thus be referred to as a pilot valve.
  • the control pressure acts against the returned from the lubricating pressure line 18 lubricating pressure.
  • the amount of lubrication pressure can be adjusted.
  • the lubrication pressure slide 19 establishes a connection between the
  • Lubricating pressure line 18 and a return line 21 made.
  • Lubricating pressure slide 19 thus controls the lubricating pressure in the lubricating pressure line 18 to the set by the control solenoid valve lubrication pressure 20 setpoint.
  • Lubricating pressure slide 19 is designed so that the maximum required
  • Lubricating pressure is achieved at a control pressure of about 3 bar.
  • Lubricating pressure slide 19 is thus assigned an operating medium pressure range of 0 to 3 bar. If the control pressure continues to rise, so does the set
  • control solenoid valve working pressure 17 and the control solenoid valve lubrication pressure 20 are both configured as so-called direct control valves.
  • direct control valves a force acts from an electronic control device, not shown
  • Control solenoid valve working pressure 17 and the control solenoid valve lubrication pressure 20 is the working pressure in the working pressure line 14 as a supply pressure.
  • the hydraulic system can also have a connection, not shown, via which a controllable Drehmomentverteilvorides for a four-wheel drive of
  • Motor vehicle can be supplied with working pressure.
  • the hydraulic system has, in addition to the main pump 10, an additional pump 23, which is controlled by an electric motor 24 controlled by the electronic control device can be driven.
  • the auxiliary pump 23, on the one hand, the main pump 10 in situations where the delivery rate of the main pump 10 is insufficient, support, with a maximum achievable operating medium pressure of the auxiliary pump 23 is significantly lower than a maximum operating medium pressure of the main pump 10.
  • the auxiliary pump 23 a Basic supply of hydraulic system with stationary
  • Additional pump 23 also sucks on the suction filter 12 from the resource reservoir
  • Additional pump line 25 can flow into the working pressure line 14, but not vice versa.
  • the auxiliary pump 23 in the case in which the working pressure is less than its maximum achievable operating medium pressure, promote together with the main pump 10 in the working pressure line 14.
  • the auxiliary pump line 25 is also connected to an auxiliary pump slide 27.
  • a connection between the auxiliary pump line 25 and the lubricating pressure line 18 are produced, wherein between the auxiliary pump slide 27 and lubricating pressure line 18, a check valve 28 is arranged so that the resources of
  • Additional pump slide 27 can flow into the lubrication pressure line 18, but not vice versa.
  • said connection between the auxiliary pump line 25 and the lubricating pressure line 18 is interrupted, in a switched position of the auxiliary pump slide 27, said connection is made.
  • On the auxiliary pump slide 27 acts as
  • Control pressure of the working pressure in the working pressure line 14 against a spring force is designed so that the auxiliary pump slider 27 so long in the
  • auxiliary pump 23 may also support the main pump 10 when the working pressure is greater than their maximum achievable operating pressure and they therefore no longer in the working pressure line
  • the multi-plate clutches and brakes are shown schematically by gear change piston-cylinder units 35, 36, 37, 38, 39 and 40, by means of which the multi-plate clutches and brakes can be closed and opened.
  • the speed change piston-cylinder units 35, 38 and 40 are multi-disc brakes, and the speed change piston-cylinder units 36, 37 and 39 are associated with multi-plate clutches.
  • the control solenoid valves 29, 30, 31, 32, 33 and 34 are constructed identically, so that only the control solenoid valve 29 is explained in more detail.
  • the control solenoid valve 29 is also designed as a direct control valve, which is controlled by the electronic control device, not shown.
  • Gear change piston-cylinder unit 35 to which it is connected via a line 42.
  • the actuating pressure in the line 42 is returned as control pressure to the control solenoid valve 29.
  • the actuation pressure is additionally fed back to two further connections of the control solenoid valve 29.
  • the line 42 is connected via the control solenoid valve 29 to a pressure accumulator 43.
  • Via a return line 87, the control solenoid valve 29 and the control solenoid valves 30, 31, 32, 33 and 34 is connected to the resource reservoir 13.
  • Return line 87 is a spring-loaded check valve 44 is arranged.
  • Check valve 44 is arranged so that the operating fluid in the
  • the multi-plate clutches and brakes of the automatic transmission are closed and opened, allowing the individual gears to be engaged and disengaged.
  • the control solenoid valves 29, 30, 31, 32, 33 and 34 and the speed change piston-cylinder units 35, 36, 37, 38, 39 and 40 may thus be referred to as a speed change system 61. With this shown gear change system 61 a total of nine forward gears and one reverse gear can be switched.
  • the actuator 88 has a hydraulic control 89 and a parallel to the hydraulic control 89 acting electromagnetic control 90.
  • the parking lock piston 71 can be unlocked by the hydraulic driver 89 and by the electromagnetic driver 90.
  • the first control chamber 94 of the parking slide valve 91 is hydraulically connected to the control solenoid lubricant pressure 20.
  • the parking brake device 68 has a control pressure line 96 which connects the control solenoid valve lubrication pressure 20 hydraulically with the first control chamber 94 of the parking slide valve 91.
  • the operating medium set by the control solenoid valve lubrication pressure 20 prevails. print.
  • the set by the control solenoid valve lubrication pressure 20 operating medium pressure thus acts on the lubricating pressure slide 19, the centrifugal oil valve 45 and the parking brake slide 91 as the control pressure.
  • the emptying slide 100 which is arranged hydraulically displaceable. Furthermore, the emptying slide 100 has an operatively connected to the valve spool 101 spring 102, which is intended to move the valve spool 01 independently in the first valve position and thus independently switch the first valve position of the emptying slide 100.
  • the first valve position of the emptying slide 100 is formed as a basic position.
  • the emptying slide 100 has a second control chamber 105.
  • the second control chamber 105 counteracts the first control chamber 103.
  • the control spaces 103, 105 are arranged opposite to each other.
  • the second control chamber 105 acts in the same direction to the spring force of the spring
  • An operating medium pressure in the second control chamber 105 is provided to move the valve spool 101 against the operating medium pressure in the first control chamber 103 and thus from the second valve position.
  • the operating medium pressure in the second control chamber 105 is for the displacement of the valve spool 101 provided in the first valve position.
  • the second control chamber 105 can also be dispensed with.
  • the supply port 1 10 is hydraulically connected to the first control chamber 103 of the emptying slide 100.
  • the parking brake device 68 has a connecting line 1 11, which connects the first control chamber 103 and the supply port 1 10 hydraulically to the parking lock slider 91.
  • the connecting line 11 1 connects the first control chamber 103 and the pressure chamber 106 hydraulically with each other.
  • Actuator 69 hydraulically with each other.
  • the parking brake device 68 has a connecting line 12, which connects the pressure chamber 106 of the emptying slide 100 and the pressure chamber 76 of the provided for actuating the parking lock actuator unit 69 hydraulically.
  • the emptying slide 100 has a third control surface 14 which is assigned to the pressure chamber 106 provided for the operating medium supply of the actuating unit 69.
  • To form the third control surface 1 14 of the valve spool 101 is designed to limit the pressure chamber 106 stepped.
  • the valve spool 101 has surfaces facing each other which are axially delimiting the pressure chamber 06 and which differ in an efficiency provided for the provision of an axial force oriented parallel to the displacement axis.
  • the surface with the higher efficiency provided for the provision of the axial force oriented parallel to the displacement axis forms the third control surface 14.
  • the efficiency provided for the provision of the axial force oriented parallel to the displacement axis depends, in particular, on an area of the surface and / or on an angular position relative to the displacement axis.
  • the surface forming the third control surface 14 has a larger area compared to the other surface.
  • the surface forming the third control surface 14 and the other surface additionally or alternatively differ in the angular position relative to the displacement axis of the valve slide 101.
  • the surface forming the third control surface 14 and the other surface have the same surface area, wherein the surface forming the third control surface 14 is oriented perpendicular to the displacement axis and the other surface is oriented obliquely to the displacement axis.
  • the second control chamber 105 associated control surface 1 15 and the pressure chamber 106 associated control surface 1 14 act in opposite directions on the valve spool 101.
  • the second control surface 15 and the third control surface 1 14 are oppositely oriented with respect to the switching direction to each other.
  • the operating medium pressure in the pressure chamber 106 is provided to move the valve spool 101 against the spring 102 and thus from the first valve position.
  • the operating medium pressure in the pressure chamber 106 is provided for displacement of the valve spool 101 in the second valve position.
  • the switching force provided by the third control surface 1 1 is provided to assist the switching force provided by the first control surface 104, whereby the second valve position of the discharge valve 100 can be maintained by small operating pressures diverted from the parking slide valve 91.
  • the emptying slide 100 is provided to decouple in its first valve position, the third control surface 1 14 of the provision of the switching force and to use in its second valve position, the third control surface 1 14 for providing the switching force.
  • the third control surface 114 In the first valve position of the emptying slide 100, the third control surface 114 is ineffective. In the second valve position of the emptying slide 100, the third control surface 1 14 is effectively switched.
  • the emptying slide 100 connects the third control surface 1 14 hydraulically with the return port 109.
  • the emptying slide 100 connects the third control surface 1 14 hydraulically with the return port 109.
  • Actuator 69 and thus the interpretation of the parking brake is not yet possible.
  • only a first pressure threshold in the connecting line 11 1 and thus in the first control chamber 103 must be exceeded by the working pressure to the
  • Discharge slider 100 to switch from its first valve position to its second valve position and thereby release the working pressure to the parking brake piston 71. Due to the stepped version of the emptying slide 100 is after the circuit of the
  • Pressure threshold of the emptying slide 100 continues to maintain its second valve position. Only when the working pressure is significantly lower than the first pressure threshold can the emptying slide 100 switch back into its first valve position and connect the pressure chamber 76 to the working fluid reservoir 13.
  • a second pressure threshold of the working pressure, below which the emptying slide 100 switches back into the first valve position, is below a minimum working pressure that is actuated during driving, so that an unintentional pressure relief in the pressure chamber 76 and thus an undesired insertion during operation when the parking lock is designed the parking brake is prevented.
  • control solenoid valve lubrication pressure 20 is activated.
  • the parking slide valve 91 switches to its second valve position and connects the working pressure line 14 with the unlocking line 116
  • Connection line 111 and the connection line 112 are via the
  • Actuator 69 unlocked, causing the parking brake piston 71 moves due to the spring force of the spring 78 in the switching direction 75. This will engage the parking brake.
  • Equipment pressure can be prevented that the parking brake slide 91 switches to its second valve position.
  • the back pressure line 98 is useful, for example, when the operating medium pressure in the first control chamber 94 of the parking brake slide 91 is to be used in the overall control, without unintentionally the
  • the parking brake device 68 is a redundant system, which can be realized that the single-fault parking brake can always be safely inserted and / or whereby unintentional disengagement of the parking brake can be prevented. In addition, multiple redundant can be ensured that during the
  • third control surface 1 14 the switching back of the emptying slide 100 can be realized below a not reached in driving pressure threshold, without reducing the security against unintentional leaving the parking position when starting the engine 1 1.
  • first control surface 104 and the third control surface 1 14 is a high operating medium pressure for holding the parking lock and to hold the designed state of the parking brake a much smaller

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear-Shifting Mechanisms (AREA)

Abstract

La présente invention concerne un ensemble frein de stationnement (68) pour un véhicule à moteur, qui comporte au moins une unité d'actionnement (69) destinée à l'actionnement d'un frein de stationnement, et au moins un tiroir de décharge (100) comprenant au moins une chambre de pression (106) pourvue d'au moins une borne d'actionnement (108) raccordée à l'unité d'actionnement (69), le tiroir de décharge (100) comportant au moins une surface de commande (114), associée à la chambre de pression (106), qui est destinée à fournir une force de commutation en fonction d'une pression de fluide de travail dans la chambre de pression (106).
EP15794471.1A 2014-12-06 2015-11-11 Ensemble frein de stationnement Withdrawn EP3227587A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014018123.5A DE102014018123A1 (de) 2014-12-06 2014-12-06 Parksperrenvorrichtung
PCT/EP2015/002268 WO2016087018A2 (fr) 2014-12-06 2015-11-11 Ensemble frein de stationnement

Publications (1)

Publication Number Publication Date
EP3227587A2 true EP3227587A2 (fr) 2017-10-11

Family

ID=54542203

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15794471.1A Withdrawn EP3227587A2 (fr) 2014-12-06 2015-11-11 Ensemble frein de stationnement

Country Status (3)

Country Link
EP (1) EP3227587A2 (fr)
DE (1) DE102014018123A1 (fr)
WO (1) WO2016087018A2 (fr)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015214037B4 (de) * 2015-07-24 2022-08-04 Bayerische Motoren Werke Aktiengesellschaft Parksperre
DE102016210874B4 (de) 2016-06-17 2018-06-07 Audi Ag Vorrichtung zum Betätigen einer Parksperre eines Automatikgetriebes, sowie Parksperreneinrichtung für ein solches Automatikgetriebe
US10161518B2 (en) 2016-10-07 2018-12-25 GM Global Technology Operations LLC Park control system for a vehicle transmission
DE102018006097A1 (de) * 2018-08-03 2020-02-06 Fte Automotive Gmbh Parksperrenmodul zur Betätigung einer Parksperre in einem Kraftfahrzeug
DE102018214433A1 (de) * 2018-08-27 2020-02-27 Zf Friedrichshafen Ag Hydrauliksystem für ein Getriebe eines Kraftfahrzeug-Antriebsstrangs
CN110425278B (zh) * 2019-08-27 2020-09-25 宁波上中下自动变速器有限公司 一种液压式驻车执行总成及变速器
DE102020117021B4 (de) * 2020-06-29 2022-02-03 Schaeffler Technologies AG & Co. KG Parksperrenbetätigungssystem mit doppeltwirkendem Betätigungszylinder am Verriegelungselement; sowie Ansteuerungsverfahren
DE102020117020B4 (de) * 2020-06-29 2022-03-24 Schaeffler Technologies AG & Co. KG Parksperrenbetätigungssystem mit formschlüssig gehaltenem Verriegelungselement; sowie Verfahren zum Ansteuern des Parksperrenbetätigungssystems
DE102020004982A1 (de) 2020-07-15 2022-01-20 Daimler Ag Automatikgetriebe für ein Kraftfahrzeug sowie Kraftfahrzeug
DE102020126523B4 (de) 2020-10-09 2022-12-01 Schaeffler Technologies AG & Co. KG Parksperrenbetätigungssystem sowie Verfahren zum Betreiben eines Parksperrenbetätigungssystems
CN112178184B (zh) * 2020-10-15 2022-02-15 中国第一汽车股份有限公司 一种自动变速器的液压控制系统
CN112344016B (zh) * 2020-10-26 2022-01-18 中国第一汽车股份有限公司 一种应急解锁驻车锁装置及车辆
CN113357365B (zh) * 2021-05-27 2022-07-05 重庆长安汽车股份有限公司 双离合变速器的液压驻车系统及车辆
WO2023088513A1 (fr) * 2021-11-18 2023-05-25 Schaeffler Technologies AG & Co. KG Ensemble hydraulique et procédé de commande d'un ensemble hydraulique
WO2023088509A1 (fr) * 2021-11-18 2023-05-25 Schaeffler Technologies AG & Co. KG Procédé d'actionnement d'un dispositif de verrouillage de stationnement
DE102022101251B3 (de) * 2022-01-20 2023-03-09 Schaeffler Technologies AG & Co. KG Verfahren zur Ansteuerung einer Parksperrvorrichtung und Fluidversorgungsvorrichtung
DE102022101368A1 (de) 2022-01-21 2023-07-27 Schaeffler Technologies AG & Co. KG Hydraulische Baueinheit
DE102022206712A1 (de) 2022-06-30 2024-01-04 Zf Friedrichshafen Ag Parksperrensystem für ein Kraftfahrzeuggetriebe sowie Kraftfahrzeuggetriebe mit einem Parksperrensystem

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004012117B4 (de) 2004-03-12 2013-11-07 Daimler Ag Kupplungsvorrichtung
DE102008055626A1 (de) 2008-11-03 2010-05-06 Daimler Ag Getriebeeinheit
JP2011085256A (ja) * 2009-09-18 2011-04-28 Aisin Aw Co Ltd 車輌の油圧制御装置
DE102010028759A1 (de) * 2010-05-07 2011-11-10 Zf Friedrichshafen Ag Hydrauliksystem einer elektrohydraulischen Betätigungseinrichtung einer Parksperre einer Getriebeeinrichtung
DE102011105068A1 (de) * 2011-06-21 2012-07-05 Daimler Ag Kraftfahrzeugparksperrenvorrichtung mit zumindest einem Verriegelungselement
DE102011105380A1 (de) * 2011-06-22 2011-12-29 Daimler Ag Kraftfahrzeugparksperrenvorrichtung
DE102011109377A1 (de) 2011-08-04 2013-02-07 Daimler Ag Hydraulische Steuerung für ein Automatikgetriebe eines Kraftfahrzeugs
DE102011109376A1 (de) * 2011-08-04 2013-02-07 Daimler Ag Hydraulische Steuerung für ein Automatikgetriebe eines Kraftfahrzeugs
DE102012200202B4 (de) * 2012-01-09 2022-02-03 Zf Friedrichshafen Ag Hydraulische Schaltvorrichtung für ein Automatikgetriebe

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