GB2614917A - Linear actuator for braking systems and braking systems - Google Patents

Linear actuator for braking systems and braking systems Download PDF

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Publication number
GB2614917A
GB2614917A GB2200910.4A GB202200910A GB2614917A GB 2614917 A GB2614917 A GB 2614917A GB 202200910 A GB202200910 A GB 202200910A GB 2614917 A GB2614917 A GB 2614917A
Authority
GB
United Kingdom
Prior art keywords
nut
piston
linear actuator
spindle
ball screw
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.)
Granted
Application number
GB2200910.4A
Other versions
GB202200910D0 (en
GB2614917B (en
Inventor
Ratoi Andrei
Cirjontu Cristina
Andrei Vadeanu Victor
Ratoi Petrut
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.)
Continental Automotive Technologies GmbH
Original Assignee
Continental Automotive Technologies GmbH
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 Continental Automotive Technologies GmbH filed Critical Continental Automotive Technologies GmbH
Priority to GB2200910.4A priority Critical patent/GB2614917B/en
Publication of GB202200910D0 publication Critical patent/GB202200910D0/en
Publication of GB2614917A publication Critical patent/GB2614917A/en
Application granted granted Critical
Publication of GB2614917B publication Critical patent/GB2614917B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/74—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive
    • B60T13/745—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive acting on a hydraulic system, e.g. a master cylinder
    • 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
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
    • 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
    • F16D51/00—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like
    • F16D51/16—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as brake-shoes pivoted on a fixed or nearly-fixed axis
    • F16D51/18—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as brake-shoes pivoted on a fixed or nearly-fixed axis with two brake-shoes
    • F16D51/20—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as brake-shoes pivoted on a fixed or nearly-fixed axis with two brake-shoes extending in opposite directions from their pivots
    • F16D51/22—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as brake-shoes pivoted on a fixed or nearly-fixed axis with two brake-shoes extending in opposite directions from their pivots mechanically actuated
    • 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
    • F16D51/00—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like
    • F16D51/46—Self-tightening brakes with pivoted brake shoes, i.e. the braked member increases the braking action
    • F16D51/48—Self-tightening brakes with pivoted brake shoes, i.e. the braked member increases the braking action with two linked or directly-interacting brake shoes
    • F16D51/50—Self-tightening brakes with pivoted brake shoes, i.e. the braked member increases the braking action with two linked or directly-interacting brake shoes mechanically actuated
    • 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
    • F16D67/00—Combinations of couplings and brakes; Combinations of clutches and brakes
    • F16D67/02—Clutch-brake combinations
    • 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
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • 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
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/40—Screw-and-nut
    • 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
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H2025/204—Axial sliding means, i.e. for rotary support and axial guiding of nut or screw shaft
    • 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
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H2025/2062—Arrangements for driving the actuator
    • F16H2025/2075—Coaxial drive motors
    • F16H2025/2078—Coaxial drive motors the rotor being integrated with the nut or screw body

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Transmission Devices (AREA)

Abstract

A linear actuator 10 for a braking system (e.g. electrohydraulic brake-by-wire system), comprises an electric motor 1 with a motor housing 1.1; a piston 4 with a piston housing 5; and a ball screw drive 2 including a spindle (2.2; figs. 2-4) and a nut 2.4. The ball screw drive converts rotational motion of the rotor tube (1.2; fig. 5) of the electric motor 1 into a linear translation of the piston 4. The spindle is rotationally and axially fixed to the motor housing 1.1, and the nut 2.4 is connected to the piston 4. The spindle may be fixed to the motor housing via a tolerance ring (2.1; figs. 2-4). The nut may include slots (12; fig. 4) for guiding the nut relative to ribs (13; fig. 6) in profile pipe (1.3; figs. 5-6), and/or may include a bump element (11; fig. 4) to stop movement of the nut in the backwards direction at the end of the stroke. The nut may include a plastic sleeve (2.5; fig. 4).

Description

Description
Linear actuator for braking systems and braking systems The invention relates to a linear actuator for braking systems, comprising an electric motor, a piston, a ball screw with a spindle and a nut for converting the rotational motion of the rotor tube of the electric motor into a linear translation of said piston, a motor housing, and a piston housing. It further relates to a corresponding braking system.
In electrohydraulic braking systems, especially of brake-by-wire-type, braking pressure can be generated by an actuator without or in addition to the pressure created by muscle force of the driver. Depending on the driver braking wish and/or the desired value of the braking torque, the actuator pushes braking fluid into the brakes which are hydraulically connected to a fluid chamber of the actuator. In known braking systems, for this purpose, linear actuators with a drive train are employed.
The main components of the drive train are the electric motor, which is typically built as a BLOC motor, a piston, a ball screw for converting the rotational motion of the rotor of the motor into a linear motion of a piston, a torque support for the ball screw nut, and the piston housing. The torque support, as the naming describes, is a component used to counteract the torque of the motor to convert the rotational movement of the spindle from the ball screw into translational movement of the nut from the ball screw.
To create pressure in the braking system, a torque is applied by the motor and the rotational movement is transferred using a coupling to the spindle of the ball screw. To transform the rotational movement in translational movement, the nut of the ball screw is fixed rotationally by the torque support. The piston is fixed together with the ball screw and presents a translational movement inside the piston housing.
In the current design, an important axial length of the motor is used by the coupling of motor to ball screw and cannot be used for the stroke of the ball screw. For this reason, to ensure a certain stroke for the piston inside the piston housing, the axial length of the motor needs to be increased accordingly resulting in an increasement of packaging.
Beside this, a configuration where the spindle of the ball screw has a rotational movement and the nut translational movement, implies the need to use a different part, namely the torque support, to block rotationally the nut. This additional part also creates problems in axial length because it takes space from the available area for the translation of the nut. At the same time, the sealing frame, where the torque support is assembled, needs a complex geometry to be able to withstand the motor torque.
The document DE 10 2016 209 537 Al discloses a linear actuator with an electric motor, a ball screw and a piston. The ball screw is provided with a friction clutch, which is put over a profile tubing which is firmly connected to a nut of the ball screw. The piston is fixed to this profile tubing.
The task of the invention is to provide a technically simple and robust solution which leads to a decrease of the axial length of the drive train. Furthermore, a corresponding braking system is provided.
With respect to the linear actuator, the object is solved according to the invention in that the spindle is rotationally and axially fixed to the motor housing, whereby the nut is connected to the piston.
Preferred embodiments are described in the dependent claims and the figure description.
The invention is based on the consideration that in modern vehicles the available installation space is often small. For this reason, the axial length of the linear actuator should be as small as possible.
Applicant has recognized that these demands can be met with a design in which the spindle is fixed to the motor housing, while the nut, rotating on the spindle, is connected to the piston.
Preferably, the spindle is fixed to the motor housing with a tolerance ring arranged axially between spindle and motor housing. In this way, radial tolerance compensation and eccentricity compensation are realized. The tilting of the ball screw spindle is achieved in a dynamic way. Moreover, a low complexity of spindle and motor housing connecting interface is realized.
The nut preferably comprises a bump element. The bump element serves to stop the nut in a backward motion. No additional component is needed as the bump formed directly on the nut. The total axial length of the ball screw is reduced by integrating the feature directly into the nut. A firm and robust mechanical end stop for the "zero position" of the ball screw is provided.
Advantageously, the nut comprises a number of slots for guiding the nut. In a preferred embodiment, exactly two slots are provided radially on opposite sides of the nut, i.e., spaced by 180 degrees. The slots cand be obtained directly into the nut during the forming process of the nut. No additional process step is needed compared to the current situation where the profile pipe needs additional step to form the slots. As robust torque transfer connection is achieved which that leads to less deformations of the components in case of overload.
In the rotor tube, preferably a profiled pipe is pressed which comprises ribs which engage with said slots. The ribs fulfil a double function: they provide torque transfer and guiding for the ball screw nut.
The nut in a preferred embodiment is encompassed by a nut sleeve, which improves wear behaviour between the nut and the profile pipe for guiding and improves the NVH (Noise, Vibration, Harshness)-behaviour during the translation of the nut into the guiding. The nut sleeve is a safety component to block the balls from the ball screw to fall out from the nut.
The nut sleeve preferably is made of plastic, providing an improved wear and NVH 5 behaviour. A nut sleeve made of plastic is easy to manufacture and helps to reduce costs. In other preferred embodiment, it can be built of anti-friction materials.
In a preferred embodiment, the piston is built as a deep drawn sheet metal piston, which provides a double function, the piston and the connection to the nut. No additional tube is needed between the nut and piston to compensate the ball screw stroke. The deep drawn sheet metal piston is easy to manufacture. In other preferred embodiments, the piston can be made of plastic.
Advantageously, a piston sealing element is arranged within the piston housing.
The sealing element seals the space between the piston and the piston housing. The sealing element is preferably built as a ring, especially an 0-ring, or with a special section profile. Preferred materials are materials compatible with brake fluid like EPDM.
With respect to the braking system, the object is solved by a braking system with a linear actuator described above. In a preferred embodiment, the braking system is built as a electrohydraulic braking system with four brakes. The system can be built as a brake-by-wire system. The braking wish measured by a, preferably, redundant, pedal sensor is transmitted to the linear actuator which correspondingly builds up braking pressure.
The invention provides the following advantages. It proposes a new technical solution that improves the usage of the space inside of the drive train, reduces the number of parts and complexity which leads also to cost savings. The proposed technical solution improves the space usage inside the drive train that leads to an increasement of the working stroke in the same packaging and a cost reduction by downsizing of components. The motor torque is reduced by increasing the working stroke of the ball screw. The axial force of the ball screw is reduced, leading to a reduction of the motor housing sheet metal thickness and motor screw size.
The piston and the profile pipe used on the ball screw are only one part. A simpler sealing frame for motor without torque support interface is provided. An increased contact area for torque support that leads to a reduction of wear. Only one interface is needed with two main functions: torque support and coupling. Additionally, a simpler rotor tube inside the motor is realized.
A preferred embodiment of the invention is described in connection with a drawing in which FIG. 1 shows a linear actuator in a preferred embodiment; FIG. 2 shows an end of the spindle attached to the motor housing with a tolerance ring; FIG. 3 shows spindle and tolerance ring in an exploded view; FIG. 4 shows ball screw assembly; FIG. 5 shows the rotational-translational coupling of the linear actuator; FIG 6 shows a nut with slots; FIG. 7 shows a ball screw assembly with rotational-translational movement, and FIG. 8 shows part of the piston housing with piston and sealing element.
Same parts are labelled in all figures with identical reference numbers.
In FIG. 1, a linear actuator 10 is shown which comprises an electric motor 1 built as a BLDG (brushless DC) motor 1, a ball screw 2, a torque support 3, a piston 4, a motor housing 1.1 and a piston housing 5. The linear actuator 10 described here improves the usage of the space inside of the drive train and reduces the number of parts and complexity, which leads to cost savings. To this end, in the linear actuator shown, see also FIG. 4, a spindle 2.2 is fixed on the motor housing 1.1.A nut 2.4 of the ball screw 2 is fixed to the piston, preferably by plastic deformation, but it can also be welded, and provides a rotation-translation movement in order to transform the rotation of the rotor or rotor tube of the motor 1 into a linear displacement of piston 4. The piston 4 in a known manner thereby is moving into a pressure chamber of the linear actuator and pushes braking fluid towards the connected brakes.
As can be seen in FIGs 2 and 3, a tolerance ring 2.1 is inserted between the spindle 2.2 and the motor housing 1.1. The tolerance ring 2.1 fixes the spindle 2.2 in the housing 1.1 rotationally and axially and also allows an angular deviation for the spindle to compensate the misalignments between the components that can lead to a tilting effect of the ball screw 2.
The proposed ball screw 2, which is also shown in FIG. 4, comprises less components than the one used in known linear actuators. Moreover, the complexity of the parts used in the actuator is reduced.
As shown in FIGs 4-6, the nut 2.4 is provided with a bump 11 that together with a radial end stop 2.3 is used to stop the ball screw 2 in backwards direction at the end of the stroke. i.e., the movement of the nut 2.4 is stopped, thereby preventing a damage of components. The nut 2.4 presents two slots 12 positioned at 180 degrees one from another, whereby the slots 12 serve used for the guiding of the nut 2.4 and for the torque support. Over the nut 2.4, a plastic sleeve 2.5 is arranged. Inside of the rotor tube 1.2, a profiled pipe 1.3 is pressed. The profiled pipe 1.3 comprises two ribs 13 disposed at 180 degrees one from another that enter inside of the nut slots 12.
The plastic sleeve 2.5 has essentially two main functions. Firstly, it serves to reduce the wear for the torque support 3. Secondly, it serves to secure the caps from the nut recirculation. The piston 4 is preferably built as a deep drawn sheet metal piston 2.6 is fixed together with the nut 2.4, as seen in in FIG. 5.
During operation, for the built-up of pressure, the nut 2.4 is performing a combination of a rotational and a translation motion as displayed schematically in FIG. 7. After applying current to the BLDC motor, the torque is transmitted from the rotor tube 1.2 to the nut 2.4 through the ribs 13 of the profiled pipe 1.3 up to the slots 12 from the nut 2.4. In this way, since the spindle 2.2 is fixed rotationally and axially to the motor housing 1.1, the nut 2.4 will perform a rotational movement together with the rotor tube 1.2, and the profiled pipe 1.3, and at the same time a linear displacement inside of the profiled pipe 1.3, guided by the slots 12 from the nut 2.4 and the ribs 13 from the profiled pipe 1.3.
As displayed in FIG.8, a piston sealing 6 is provided within the piston housing 5, leading to a simpler geometric arrangement of piston 4 and sealing 6. The sealing is of ring-type. It can be built as an 0-ring or as a ring with a special section profile The sealing prevents braking fluid to leave the piston housing into the direction of the space in which the ball screw 2 is arranged and in which no braking fluid is allowed.
List of reference numerals 1 motor 1.1 motor housing 1.2 rotor tube 1.3 profiled pipe 2 ball screw 2.1 tolerance ring 2.2 spindle 2.3 radial end stop 2.4 nut 2.5 nut sleeve 2.6 deep drawn metal piston 3 torque support 4 piston piston housing linear actuator 11 bump 12 slot 13 rib

Claims (10)

  1. Patent claims 1. Linear actuator (10) for braking systems, comprising an electric motor (1), a piston (4), a ball screw (2) with a spindle (2.2) and a nut (2.4) for converting the rotational motion of the rotor tube (1.2) of the electric motor (1) into a linear translation of said piston (4), a motor housing (1.1), and a piston housing (5), characterized in that said spindle (2.2) is rotationally and axially fixed to said motor housing (1.1), whereby said nut (2.4) is connected to said piston (4).
  2. 2. Linear actuator (10) according to claim 1, whereby said spindle (2.2) is fixed to said motor housing (1.1) with a tolerance ring (2.1) arranged axially between spindle (2.2) and motor housing (1.1).
  3. 3. Linear actuator (10) according to claim 1 or 2, whereby said nut (2.4) comprises a bump element (11).
  4. 4. Linear actuator (10) according to one of the previous claims, whereby said nut (2.4) comprises a number of slots (12) for guiding said nut (2.4).
  5. 5. Linear actuator (10) according to claim 4, whereby in said rotor tube (1.2) a profiled pipe (1.3) is pressed which comprises ribs (13) which engage with said slots (12).
  6. 6. Linear actuator (10) according to one of the previous claims, whereby said nut (2.4) is encompassed by a nut sleeve (2.5).
  7. 7. Linear actuator (10) according to claim 6, whereby said nut sleeve (2.4) is made of plastic.
  8. 8. Linear actuator (10) according to one of the previous claims, whereby said piston (4) is built as a deep drawn sheet metal piston (2.6).
  9. 9. Linear actuator (10) according to one of the previous claims, whereby a piston sealing element (6) is arranged within said piston housing (5).
  10. 10. Braking system for vehicles, comprising a linear actuator (10) according to one of the previous claims.
GB2200910.4A 2022-01-25 2022-01-25 Linear actuator for braking systems and braking systems Active GB2614917B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB2200910.4A GB2614917B (en) 2022-01-25 2022-01-25 Linear actuator for braking systems and braking systems

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB2200910.4A GB2614917B (en) 2022-01-25 2022-01-25 Linear actuator for braking systems and braking systems

Publications (3)

Publication Number Publication Date
GB202200910D0 GB202200910D0 (en) 2022-03-09
GB2614917A true GB2614917A (en) 2023-07-26
GB2614917B GB2614917B (en) 2024-04-17

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ID=80507369

Family Applications (1)

Application Number Title Priority Date Filing Date
GB2200910.4A Active GB2614917B (en) 2022-01-25 2022-01-25 Linear actuator for braking systems and braking systems

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GB (1) GB2614917B (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018213527A1 (en) * 2018-08-10 2020-02-13 Continental Teves Ag & Co. Ohg Linear actuator with kinematic interface
JP2020094647A (en) * 2018-12-13 2020-06-18 日本精工株式会社 Power transmission device
JP2020094640A (en) * 2018-12-13 2020-06-18 日本精工株式会社 Power transmission device
DE102019205273A1 (en) * 2019-02-06 2020-08-06 Continental Teves Ag & Co. Ohg Pressure supply device for electro-hydraulic brake systems and brake system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018213527A1 (en) * 2018-08-10 2020-02-13 Continental Teves Ag & Co. Ohg Linear actuator with kinematic interface
JP2020094647A (en) * 2018-12-13 2020-06-18 日本精工株式会社 Power transmission device
JP2020094640A (en) * 2018-12-13 2020-06-18 日本精工株式会社 Power transmission device
DE102019205273A1 (en) * 2019-02-06 2020-08-06 Continental Teves Ag & Co. Ohg Pressure supply device for electro-hydraulic brake systems and brake system

Also Published As

Publication number Publication date
GB202200910D0 (en) 2022-03-09
GB2614917B (en) 2024-04-17

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Owner name: CONTINENTAL AUTOMOTIVE TECHNOLOGIES GMBH

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