US20230150470A1 - Spindle drive, actuator assembly, and method for producing a spindle drive - Google Patents
Spindle drive, actuator assembly, and method for producing a spindle drive Download PDFInfo
- Publication number
- US20230150470A1 US20230150470A1 US17/984,689 US202217984689A US2023150470A1 US 20230150470 A1 US20230150470 A1 US 20230150470A1 US 202217984689 A US202217984689 A US 202217984689A US 2023150470 A1 US2023150470 A1 US 2023150470A1
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- US
- United States
- Prior art keywords
- spindle
- contact surface
- spindle nut
- spindle drive
- pressure
- Prior art date
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Classifications
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- 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
- B60T13/746—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 and mechanical transmission of the braking action
-
- 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
- B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
- B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
- B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
- B60T1/065—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels employing disc
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
- F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
- F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
- F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
- F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
- F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
- F16D55/28—Brakes with only one rotating disc
-
- 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
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
- F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
- F16D65/095—Pivots or supporting members therefor
- F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
- F16D65/0971—Resilient means interposed between pads and supporting members or other brake parts transmitting brake actuation force, e.g. elements interposed between brake piston and pad
-
- 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
- F16D65/00—Parts or details
- F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
- F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
- F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2121/00—Type of actuator operation force
- F16D2121/18—Electric or magnetic
- F16D2121/24—Electric or magnetic using motors
-
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2200/00—Materials; Production methods therefor
- F16D2200/0004—Materials; Production methods therefor metallic
-
- 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
- F16D2250/00—Manufacturing; Assembly
- F16D2250/0061—Joining
-
- 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
- F16D2250/00—Manufacturing; Assembly
- F16D2250/0061—Joining
- F16D2250/0076—Welding, brazing
Definitions
- the disclosure relates to a spindle drive for an actuator assembly of a vehicle brake, in particular for an electromechanically actuated brake, and to an actuator assembly with a spindle drive and to a method for producing a spindle drive.
- Two friction linings can be applied to a brake rotor by an actuating carriage in order to actuate an electromechanical vehicle brake.
- the actuating carriage contacts the back plate of a brake lining.
- an application force may occur only locally in the region of the contact surface between the actuating carriage and the back plate of the brake lining.
- the disclosure discusses an arrangement to achieve a qualitatively uniform distribution of the application force between a brake lining and the brake rotor.
- a spindle drive for a vehicle brake with a spindle and a spindle nut mounted on the spindle, forms an actuating carriage that can be displaced between a retracted and an extended position in order to place a brake lining against a brake rotor.
- the spindle nut has a pressure-distributing element at an end of the spindle nut which is dose to the brake lining, and a contact surface of the pressure-distributing element which faces away from the spindle is continuously or discontinuously annular.
- the application force when the brake lining is applied to the brake rotor is transmitted to a brake lining less punctually than in the case of a round circular surface. This is caused by the fact that the contact surface is shifted away from a centre of the brake lining by the annular shape.
- the application force is thus distributed particularly uniformly over the whole or almost the whole surface of the brake lining, as a result of which a braking procedure can be particularly effective.
- the brake lining becomes worn uniformly, as a result of which consistent braking behaviour is ensured in the long term.
- a distribution of pressure between the friction lining and the brake disc as occurs in the case of hydraulic dual-piston brake calipers can be generated by the spindle drive according to the disclosure.
- the annular contact surface can be continuously or discontinuously circular, oval or elliptical when viewed from the front.
- the shape of the annular contact surface can be adapted to the size of the brake disc and to a desired pressure distribution.
- the pressure-distributing element has a frustoconical projecting collar which ends at the contact surface and widens out from an axial end of the spindle nut to the brake lining.
- the circumference of the contact surface is consequently greater than the circumference of the spindle nut, as a result of which the application force is distributed over as large as possible an area with at the same time a compact structure of the spindle drive.
- the pressure-distributing element has the same diameter as the spindle nut at its end connected to the spindle nut.
- the cross-section of the collar preferably merges from a circular cross-section into an oval or elliptical cross-section.
- the contact surface can have at least one depression, viewed in a side view.
- the pressure-generating element is not in contact with the back plate of the brake lining even when the brake lining is applied such that a discontinuously annular contact surface results by virtue of the depression.
- the distribution of the application force can consequently be influenced in a more targeted fashion.
- the depression is arranged in particular in the region of the co-vertices.
- the pressure-distributing element is in contact with the back plate of the brake lining in the region of the vertices.
- the contact surface is consequently on average shifted as far away from a centre of the brake lining as is advantageous with respect to the distribution of the application force.
- the contact surface runs at an angle to a friction surface of the brake lining, in particular wherein two regions of the contact surface which are situated circumferentially opposite each other have opposite inclinations.
- the regions of the contact surface which are situated opposite each other are preferably inclined towards the centre.
- the contact surface is roof-shaped when viewed from the side. The elasticity of the pressure-distributing element is compensated by a contact surface inclined to the friction surface or by a region of the contact surface with an opposite inclination.
- the inclined regions are deformed elastically by the resulting pressure in such a way that the contact surface is oriented parallel to the brake lining or the angle at which the contact surface runs parallel to the brake lining is reduced.
- the contact surface thus runs in an unstressed state at an angle to the friction surface of the brake lining.
- the pressure-distributing element is preferably made from metal and press-fitted or welded to the spindle nut.
- the pressure-generating element can also merge integrally into the spindle nut.
- the pressure-distributing element has a cylindrical centring extension which sits in a recess of the spindle nut.
- the spindle drive is preferably supported on an axial bearing in the brake caliper via the spindle, wherein the contact surface of the axial bearing with the spindle is a conical surface.
- the axial bearing is bevelled at its contact surface with the spindle.
- the spindle drive is preferably a ball screw.
- balls transmit the force between the spindle and the spindle nut. By virtue of the rolling movement of the balls, friction and wear are reduced in a ball screw.
- At least one cut-out which leads to a thread of the spindle and which forms a mounting opening for the balls of the spindle drive, is present in a circumferential wall of the spindle nut. Simple mounting of the balls is consequently possible even in the case of a spindle nut which is closed on one side.
- the disclosure also discusses an actuator assembly for a vehicle brake, with a brake lining, a brake rotor and a spindle drive.
- the pressure-distributing element is arranged at an end of the spindle nut which faces the brake lining and the contact surface of the pressure-distributing element is in contact with a back plate of the brake lining in an extended position of the spindle nut and applies the brake lining to the brake rotor.
- the application force is consequently distributed particularly uniformly over the whole or almost the whole surface of the brake lining.
- balls are inserted into a thread of the spindle, and in a following step the pressure-distributing element is fastened to the spindle nut.
- the pressure-distributing element is press-fitted onto the spindle nut and is secured against rotation by a knurled joint or is welded.
- the balls can be mounted as in a conventional ball screw by the pressure-distributing element being fastened to the spindle nut after the balls have been inserted into the thread.
- the balls can be mounted in the threads and ball returns of the spindle nut by a cylindrical rod being pushed gradually into the latter. The balls are secured against falling out by the cylindrical rod in the spindle nut.
- the spindle is then twisted into the spindle nut at one end of the latter and the cylindrical rod is thus pushed out of the nut at the other end.
- the pressure-distributing element is manufactured as a single piece with the spindle nut, wherein at least one cut-out, which leads to a thread of the spindle, is present in a circumferential wall of the spindle nut, and wherein the balls of the spindle drive are blown into the thread by compressed air through the cut-out.
- the balls are arranged, for example, in a mounting tube which is plugged into the cut-out and to which compressed air is applied in order to blow the balls into the thread.
- FIG. 1 shows an actuator assembly according to the disclosure for a vehicle brake with a spindle drive according to the disclosure in a view in section
- FIG. 2 shows a drive assembly of the actuator assembly from FIG. 1 ,
- FIG. 3 shows the spindle drive from FIG. 1 in a perspective view
- FIG. 4 shows the spindle drive from FIG. 1 in a further perspective view
- FIG. 5 shows the spindle drive from FIG. 1 in a side view
- FIG. 6 shows the spindle drive from FIG. 1 with a brake lining in a side view
- FIG. 7 shows a spindle drive according to the disclosure according to a further exemplary arrangement in a perspective view
- FIG. 8 shows the spindle drive from FIG. 7 in a view in partial section
- FIG. 9 shows a further spindle drive according to the disclosure in a perspective view.
- FIG. 1 shows an actuator assembly 10 as part of an electromechanical vehicle brake.
- the actuator assembly 10 comprises a control assembly 12 which can be mounted as a separate subunit, and a drive assembly 14 which can be mounted as a separate subunit (see FIG. 2 ).
- control assembly 12 and the drive assembly 14 are arranged in a common housing 16 .
- the housing 16 comprises an essentially sleeve-shaped housing base part 18 and a housing cover 20 by which the housing base part 18 is tightly closed in the mounted state.
- the housing cover 20 is also essentially shell-shaped.
- Both the housing base part 18 and the housing cover 20 are produced from plastic material.
- the housing 16 as a whole is thus made from plastic material.
- the actuator assembly 10 furthermore comprises a brake caliper 15 in which a gap 17 is formed for a brake rotor 19 , i.e. a brake disc.
- the housing 16 is pushed partially onto the brake caliper 15 with its end close to the brake caliper 15 .
- the drive assembly 14 comprises a support assembly 22 which has a plate-like frame part 24 , as can be seen particularly well in FIG. 2 .
- a first fastening interface 26 at which an electric motor 28 is fastened in the exemplary arrangement illustrated, is provided on the plate-like frame part 24 .
- the electric motor 28 is connected captively to the frame part 24 via the first fastening interface 26 .
- the frame part 24 absorbs the forces of the electric motor 28 and holds the latter.
- the electric motor 28 fastened to the frame part 24 such that is centred with respect to a centre axis 34 of the first fastening interface 26 .
- an anti-rotation device 36 is provided in the form of an anti-rotation depression which is designed to prevent the electric motor 28 from rotating relative to the frame part 24 .
- An output gear wheel 40 is arranged on an output shaft 38 of the electric motor 28 , as shown in FIG. 2 , in order to impart torque to the drive assembly 14 .
- journal 42 on which in the exemplary arrangement illustrated a gear wheel 44 is mounted which meshes with the output gear wheel 40 , is provided on the frame part 24 .
- a receiving space 46 for a planetary gear stage 48 is provided on the frame part 24 .
- a centre axis 50 of the receiving space 46 is here arranged essentially parallel to the centre axis 34 of the first fastening interface 26 .
- a reinforcing part 52 is moreover fastened on the frame part 24 in such a way that it spans the end of the receiving space 46 axially with respect to the centre axis 50 .
- the reinforcing part 52 is essentially cross-shaped.
- a bearing point 54 for a gear wheel 56 arranged coaxially with respect to the planetary gear stage is provided on the reinforcing part 52 .
- the gear wheel 56 meshes with the gear wheel 44 .
- a gear train 58 is consequently formed by the gear wheel 44 and the gear wheel 56 , the output gear wheel 40 acting as its input member.
- the gear wheel 56 is moreover formed integrally with a sun gear 60 (see FIG. 1 ) of the planetary gear stage 48 . In this way, the gear train 58 and the planetary gear stage 48 are coupled drivingly.
- the planetary gear stage 48 moreover comprises a ring gear 62 which runs essentially along an inner circumference of the receiving space 46 (see FIG. 1 ).
- a total of three planetary gears 64 are provided drivingly between the sun gear 60 and the ring gear 62 , as can be seen in FIG. 2 . They are mounted rotatably on a planet carrier 66 .
- the planet carrier 66 here represents an output element of the planetary gear stage 48 .
- the gear train 58 and the planetary gear stage 48 are also referred to together as a gear unit 67 .
- the frame part 24 furthermore has a second fastening interface 68 which is designed for fastening a guide part 70 , held therein, for a spindle drive 72 .
- the guide part 70 is a bearing sleeve which is held in the brake caliper 15 .
- the bearing sleeve is press-fitted in the brake caliper or is welded to the latter.
- a centre axis of the second fastening interface 68 here coincides with the centre axis 50 of the receiving space 46 and for this reason is provided with the same reference numeral.
- the second fastening interface 68 has an anti-rotation geometry 74 , for example a splined shaft geometry, which runs circumferentially around the centre axis 50 .
- a complementary anti-rotation geometry 82 is provided at that end of the guide part 70 which is to be coupled to the second fastening interface 68 such that the guide part 70 can be pushed along the centre axis 50 into the anti-rotation geometry 74 of the second fastening interface 68 and held there non-rotatably in a form-fitting fashion.
- the anti-rotation geometry is likewise a splined shaft geometry.
- the spindle drive 72 is accommodated inside the guide part 70 .
- spindle 84 which is configured in the present case as a ball screw.
- the spindle 84 is here connected non-rotatably to the planet carrier 66 via the toothed section 86 .
- the spindle drive 72 can thus be driven by the electric motor 28 .
- the electric motor 28 is coupled to the spindle drive 72 drivingly via the gear train 58 and the planetary gear stage 48 .
- a spindle nut 88 which is configured as a piston and forms an actuating carriage for a brake lining, is mounted on the spindle 84 .
- Rotation of the spindle 84 thus causes the spindle nut 88 to be shifted axially along the centre axis 50 .
- the spindle nut 88 is here guided along the centre axis 50 directly on a running surface 90 , wherein the running surface 90 is formed by an inner side of the guide part 70 .
- the running surface 90 corresponds essentially to a cylindrical surface forming the inner circumference of the guide part 70 .
- the spindle nut 88 is guided linearly displaceably in the guide part 70 .
- the guide part 70 is open towards the gap 17 such that the spindle nut 88 can move into the gap 17 .
- the spindle nut 88 is moreover prevented from rotating relatively about the centre axis 50 by an anti-rotation device 92 which is designed as a slot on the guide part 70 .
- an anti-rotation element 94 which engages in the slot (see FIG. 1 ) is attached to the spindle nut 88 .
- the anti-rotation element 94 is a radial extension.
- the spindle nut 88 serves to apply a first brake lining 96 of a brake caliper assembly 98 to the brake rotor 19 .
- the first brake lining 96 can be moved actively onto a brake rotor 19 by the actuator assembly 10 .
- the spindle nut 88 is transferred selectively into an extended position, which is associated with the application of the first brake lining 96 to the brake rotor 19 , by the electric motor 28 via the gear train 58 , the planetary gear stage 48 and the spindle drive 72 .
- spindle nut 88 can be moved in the same way by operation of the electric motor 28 into a retracted position which is associated with lifting the first brake lining 96 and the second brake lining 102 off the brake rotor 19 .
- the spindle drive 72 is supported on an axial bearing 104 in the brake caliper 15 via the spindle 84 .
- the axial bearing 104 is supported on a wall 105 which is formed integrally with the guide part 70 and which runs transversely to a direction of movement of the spindle nut 88 .
- the wall 105 is a radially inward facing flange.
- a contact surface 106 which is in contact with the spindle 84 , of the axial bearing 104 is a conical surface.
- the axial bearing 104 is a rolling bearing, in particular a needle bearing.
- the actuator assembly 10 is designed so that it is not self-locking, such that the spindle nut 88 also shifts back automatically into the retracted position by virtue of elasticities inherent in the system when it is no longer actively forced into the extended position by the electric motor 28 .
- a spindle drive according to a first arrangement will be described below in detail with the aid of FIGS. 3 to 6 , in particular the spindle drive 72 of the actuator assembly 10 shown in FIG. 1 .
- the spindle nut 88 has a pressure-distributing element 108 at an end of the spindle nut 88 which is close to the brake lining 96 .
- the pressure-distributing element 108 is, for example, made from metal.
- the pressure-distributing element 108 is manufactured separately from the spindle nut 88 and press-fitted or welded to the spindle nut 88 .
- the pressure-distributing element 108 preferably has a cylindrical centring extension 110 which sits in a recess 112 of the spindle nut 88 (see FIG. 1 ).
- the pressure-distributing element 108 forms a sealing cap for the spindle nut 88 .
- the pressure-distributing element 108 can also merge into the spindle nut 88 as a single piece.
- the spindle nut 88 with the integrated pressure-distributing element 108 can be produced in this case as a milled or cast part.
- a contact surface 114 facing away from the spindle 84 , of the pressure-distributing element 108 is annular (see FIG. 4 ). To be more precise, the annular contact surface 114 is oval when viewed from the front. An elliptical or circular contact surface 114 , designed as a ring, is, however, also conceivable.
- the contact surface 114 of the pressure-distributing element 108 is in contact with a back plate 115 (see FIG. 6 ) of the brake lining 96 and applies the brake lining 96 to the brake rotor 19 .
- the contact surface 114 is in particular discontinuously annular, which is explained in more detail below.
- the pressure-distributing element 108 has a frustoconical projecting collar 116 .
- the collar 116 widens out towards the brake lining 96 and ends at the contact surface 114 .
- the contact surface 114 consequently has a larger external circumference than the spindle nut 88 , in particular an external circumference which is larger by at least 50%.
- the cross-section of the collar 116 merges from a circular cross-section into an oval cross-section.
- the collar 116 has, at the end fastened to the spindle nut 88 , the same diameter as the spindle nut 88 .
- a diameter of the collar 116 at its base is the same size as an average diameter of the spindle nut 88 or as a diameter at a circumferential surface of the recess 112 .
- the circumference of the contact surface 114 is consequently greater than the circumference of the spindle nut 88 .
- the depression 18 is formed in particular when the pressure-distributing element 108 is attached to the spindle nut 88 .
- the contact surface 114 has two depressions 122 when viewed from the side.
- the discontinuously annular form of the contact surface 114 which has already been mentioned above is obtained by the depressions 122 . There is in particular no contact of the pressure-distributing element 108 with the back plate 115 of the brake lining 96 in the region of the depressions 122 .
- the contact surface 114 thus comprises two ring segments 124 .
- the depression 122 is arranged in the region of the co-vertices 125 .
- the contact surface 114 is thus in contact with the back plate 115 of the brake lining 96 in the region of the vertices 126 .
- the ring segments 124 of the contact surface 114 run at an angle a to a friction surface 117 of the brake lining 96 .
- two regions of the contact surface 114 which are situated opposite each other at the circumference, to be more precise the two ring segments 124 formed by the depressions 122 have opposite inclinations.
- the ring segments 124 are inclined towards the centre of the pressure-distributing element 108 such that the contact surface 114 is roof-shaped when viewed from the side.
- a pressure-distributing element 108 is provided on the spindle nut 88 , improved distribution of the application force in the brake lining is achieved such that the brake lining 96 is deformed as little as possible when acted upon by the spindle nut 88 or the pressure-distributing element 108 and is consequently applied to a large area of a brake disc of the brake rotor 19 .
- the contact surface 114 is not oval and instead is circular. Moreover, there are no depressions 122 .
- the contact surface 114 is flat in FIGS. 7 to 8 .
- the spindle drive 72 illustrated in FIGS. 7 to 8 is suited in particular for combination with smaller brake linings than the spindle drive 72 illustrated in FIGS. 1 to 6 .
- FIG. 9 shows a further spindle drive 72 according to the disclosure.
- the spindle drive 72 illustrated in FIG. 9 differs from the spindle drive illustrated in FIGS. 7 and 8 in that at least one cut-out 130 , which leads to a thread 132 of the spindle 84 , is present in a circumferential wall 128 of the spindle nut 88 .
- the cut-out 130 forms in particular a mounting opening for the balls 134 of the spindle drive 72 .
- the spindle drive 72 according to FIGS. 3 to 6 and 7 to 8 can optionally likewise have a cut-out 130 in the circumferential wall 128 of the spindle nut 88 .
- the cut-out 130 enables mounting of the spindle drive 72 when the pressure-distributing element 108 forms a single piece with the spindle nut 88 or when the pressure-distributing element 108 has been connected to the spindle nut 88 before the spindle nut 88 is mounted on the spindle 84 .
- the balls 134 of the spindle drive 72 can be blown through the cut-out 130 into the thread 132 by compressed air.
- the balls 134 are, for example, arranged in a mounting tube 136 which is pushed into the cut-out and to which compressed air is applied in order to blow the balls into the thread.
- the mounting tube 136 preferably has a curve.
- the ball return can be integrated into the spindle nut 88 or into the spindle 84 .
- a ball return integrated into the spindle 84 is provided with individual ball recirculation functionality.
- a cut-out 130 is provided as a mounting opening for each individual ball recirculation.
- the cut-outs 130 can be closed with a cover once the mounting is complete.
- the balls 134 can also be inserted into the thread 132 of the spindle 84 , and in a subsequent step the pressure-distributing element 108 is fastened to the spindle nut 88 ,
- a rod which serves as a mounting aid, can be pushed gradually into the spindle nut 88 , wherein the balls 134 are mounted in the threads of the spindle nut 88 .
- the balls 134 are secured against falling out during mounting by virtue of being covered by the cylindrical rod.
- the spindle 84 can then be screwed into the spindle nut 88 , wherein the rod is pushed out of the spindle nut 88 .
- the pressure-distributing element 108 can be fastened to the spindle nut 88 .
- the pressure-distributing element 108 can be press-fitted to the spindle nut 88 and secured against rotation by a knurled joint.
- the pressure-distributing element 108 can also be welded to the spindle nut 88 .
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Abstract
A spindle drive for an actuator assembly of a vehicle brake is provided, with a spindle and a spindle nut mounted on the spindle, which forms an actuating carriage which can be displaced between a retracted and an extended position in order to apply a brake lining against a brake rotor. The spindle nut has a pressure-distributing element at an end of the spindle nut which is close to the brake lining, and a contact surface of the pressure-distributing element which faces away from the spindle is continuously or discontinuously annular. Furthermore, an actuator assembly with a spindle drive is provided. In addition, a method for producing a spindle drive is provided.
Description
- This application claims priority to German Priority Application No. 102021129963.2, filed Nov. 17, 2021, the disclosure of which is incorporated herein by reference in its entirety.
- The disclosure relates to a spindle drive for an actuator assembly of a vehicle brake, in particular for an electromechanically actuated brake, and to an actuator assembly with a spindle drive and to a method for producing a spindle drive.
- Two friction linings can be applied to a brake rotor by an actuating carriage in order to actuate an electromechanical vehicle brake. For this purpose, the actuating carriage contacts the back plate of a brake lining.
- However, an application force may occur only locally in the region of the contact surface between the actuating carriage and the back plate of the brake lining.
- The disclosure discusses an arrangement to achieve a qualitatively uniform distribution of the application force between a brake lining and the brake rotor.
- As discussed herein, a spindle drive for a vehicle brake, with a spindle and a spindle nut mounted on the spindle, forms an actuating carriage that can be displaced between a retracted and an extended position in order to place a brake lining against a brake rotor. The spindle nut has a pressure-distributing element at an end of the spindle nut which is dose to the brake lining, and a contact surface of the pressure-distributing element which faces away from the spindle is continuously or discontinuously annular.
- By virtue of a continuously or discontinuously annular contact surface, the application force when the brake lining is applied to the brake rotor is transmitted to a brake lining less punctually than in the case of a round circular surface. This is caused by the fact that the contact surface is shifted away from a centre of the brake lining by the annular shape. The application force is thus distributed particularly uniformly over the whole or almost the whole surface of the brake lining, as a result of which a braking procedure can be particularly effective. In addition, the brake lining becomes worn uniformly, as a result of which consistent braking behaviour is ensured in the long term.
- In particular, a distribution of pressure between the friction lining and the brake disc as occurs in the case of hydraulic dual-piston brake calipers can be generated by the spindle drive according to the disclosure.
- The annular contact surface can be continuously or discontinuously circular, oval or elliptical when viewed from the front. As a result, the shape of the annular contact surface can be adapted to the size of the brake disc and to a desired pressure distribution.
- According to an exemplary arrangement, the pressure-distributing element has a frustoconical projecting collar which ends at the contact surface and widens out from an axial end of the spindle nut to the brake lining. The circumference of the contact surface is consequently greater than the circumference of the spindle nut, as a result of which the application force is distributed over as large as possible an area with at the same time a compact structure of the spindle drive. In particular, the pressure-distributing element has the same diameter as the spindle nut at its end connected to the spindle nut.
- Starting from the axial end of the spindle nut, the cross-section of the collar preferably merges from a circular cross-section into an oval or elliptical cross-section. As a result, if it is produced separately from the spindle nut, the pressure-distributing element can be connected simply to the spindle nut, When the pressure-distributing element and the spindle nut are manufactured integrally, such a design is likewise advantageous for manufacturing reasons because there is a gradual transition from the spindle nut to the pressure-distributing element.
- The contact surface can have at least one depression, viewed in a side view. In the region of the depression, the pressure-generating element is not in contact with the back plate of the brake lining even when the brake lining is applied such that a discontinuously annular contact surface results by virtue of the depression. The distribution of the application force can consequently be influenced in a more targeted fashion.
- In the case of an oval or elliptical contact surface, the depression is arranged in particular in the region of the co-vertices. As a result, the pressure-distributing element is in contact with the back plate of the brake lining in the region of the vertices. The contact surface is consequently on average shifted as far away from a centre of the brake lining as is advantageous with respect to the distribution of the application force.
- According to an exemplary arrangement, the contact surface runs at an angle to a friction surface of the brake lining, in particular wherein two regions of the contact surface which are situated circumferentially opposite each other have opposite inclinations. The regions of the contact surface which are situated opposite each other are preferably inclined towards the centre. In particular, the contact surface is roof-shaped when viewed from the side. The elasticity of the pressure-distributing element is compensated by a contact surface inclined to the friction surface or by a region of the contact surface with an opposite inclination. As a result, when the pressure-distributing element is forced towards the back plate of a brake lining in order to apply the brake lining to a brake rotor, the inclined regions are deformed elastically by the resulting pressure in such a way that the contact surface is oriented parallel to the brake lining or the angle at which the contact surface runs parallel to the brake lining is reduced. The contact surface thus runs in an unstressed state at an angle to the friction surface of the brake lining.
- The pressure-distributing element is preferably made from metal and press-fitted or welded to the spindle nut. The pressure-generating element can also merge integrally into the spindle nut. In the case of two-part manufacture, the pressure-distributing element has a cylindrical centring extension which sits in a recess of the spindle nut.
- The spindle drive is preferably supported on an axial bearing in the brake caliper via the spindle, wherein the contact surface of the axial bearing with the spindle is a conical surface. As a result, the axial bearing is bevelled at its contact surface with the spindle. By virtue of the bevel, the axial bearing can absorb not only axial forces but also a certain amount of transverse force.
- The spindle drive is preferably a ball screw. In a ball screw, balls transmit the force between the spindle and the spindle nut. By virtue of the rolling movement of the balls, friction and wear are reduced in a ball screw.
- According to an exemplary arrangement, at least one cut-out, which leads to a thread of the spindle and which forms a mounting opening for the balls of the spindle drive, is present in a circumferential wall of the spindle nut. Simple mounting of the balls is consequently possible even in the case of a spindle nut which is closed on one side.
- The disclosure also discusses an actuator assembly for a vehicle brake, with a brake lining, a brake rotor and a spindle drive. The pressure-distributing element is arranged at an end of the spindle nut which faces the brake lining and the contact surface of the pressure-distributing element is in contact with a back plate of the brake lining in an extended position of the spindle nut and applies the brake lining to the brake rotor. As has already been described in connection with the spindle drive according to the disclosure, the application force is consequently distributed particularly uniformly over the whole or almost the whole surface of the brake lining.
- According to a method, in a first step, balls are inserted into a thread of the spindle, and in a following step the pressure-distributing element is fastened to the spindle nut. In particular, the pressure-distributing element is press-fitted onto the spindle nut and is secured against rotation by a knurled joint or is welded. The balls can be mounted as in a conventional ball screw by the pressure-distributing element being fastened to the spindle nut after the balls have been inserted into the thread. To be precise, the balls can be mounted in the threads and ball returns of the spindle nut by a cylindrical rod being pushed gradually into the latter. The balls are secured against falling out by the cylindrical rod in the spindle nut. The spindle is then twisted into the spindle nut at one end of the latter and the cylindrical rod is thus pushed out of the nut at the other end.
- According to a further method, the pressure-distributing element is manufactured as a single piece with the spindle nut, wherein at least one cut-out, which leads to a thread of the spindle, is present in a circumferential wall of the spindle nut, and wherein the balls of the spindle drive are blown into the thread by compressed air through the cut-out. In this case, the advantage is obtained that the pressure-generating element does not need to be fastened subsequently to the spindle.
- The balls are arranged, for example, in a mounting tube which is plugged into the cut-out and to which compressed air is applied in order to blow the balls into the thread.
- Further advantages and features of the disclosure emerge from the following description and from the attached drawings to which reference is made. In the drawings:
-
FIG. 1 shows an actuator assembly according to the disclosure for a vehicle brake with a spindle drive according to the disclosure in a view in section, -
FIG. 2 shows a drive assembly of the actuator assembly fromFIG. 1 , -
FIG. 3 shows the spindle drive fromFIG. 1 in a perspective view, -
FIG. 4 shows the spindle drive fromFIG. 1 in a further perspective view, -
FIG. 5 shows the spindle drive fromFIG. 1 in a side view, -
FIG. 6 shows the spindle drive fromFIG. 1 with a brake lining in a side view, -
FIG. 7 shows a spindle drive according to the disclosure according to a further exemplary arrangement in a perspective view, -
FIG. 8 shows the spindle drive fromFIG. 7 in a view in partial section, and -
FIG. 9 shows a further spindle drive according to the disclosure in a perspective view. -
FIG. 1 shows anactuator assembly 10 as part of an electromechanical vehicle brake. - The
actuator assembly 10 comprises acontrol assembly 12 which can be mounted as a separate subunit, and adrive assembly 14 which can be mounted as a separate subunit (seeFIG. 2 ). - The
control assembly 12 and thedrive assembly 14 are arranged in a common housing 16. - The housing 16 comprises an essentially sleeve-shaped housing base part 18 and a housing cover 20 by which the housing base part 18 is tightly closed in the mounted state.
- In the exemplary arrangement illustrated, the housing cover 20 is also essentially shell-shaped.
- Both the housing base part 18 and the housing cover 20 are produced from plastic material. The housing 16 as a whole is thus made from plastic material.
- The
actuator assembly 10 furthermore comprises abrake caliper 15 in which agap 17 is formed for abrake rotor 19, i.e. a brake disc. The housing 16 is pushed partially onto thebrake caliper 15 with its end close to thebrake caliper 15. - The
drive assembly 14 comprises asupport assembly 22 which has a plate-like frame part 24, as can be seen particularly well inFIG. 2 . - A
first fastening interface 26, at which anelectric motor 28 is fastened in the exemplary arrangement illustrated, is provided on the plate-like frame part 24. - To be more precise, the
electric motor 28 is connected captively to theframe part 24 via thefirst fastening interface 26. Theframe part 24 absorbs the forces of theelectric motor 28 and holds the latter. - The
electric motor 28 fastened to theframe part 24 such that is centred with respect to acentre axis 34 of thefirst fastening interface 26. - In addition, an
anti-rotation device 36 is provided in the form of an anti-rotation depression which is designed to prevent theelectric motor 28 from rotating relative to theframe part 24. - An
output gear wheel 40 is arranged on anoutput shaft 38 of theelectric motor 28, as shown inFIG. 2 , in order to impart torque to thedrive assembly 14. - Furthermore, a
journal 42, on which in the exemplary arrangement illustrated a gear wheel 44 is mounted which meshes with theoutput gear wheel 40, is provided on theframe part 24. - Moreover, a receiving
space 46 for aplanetary gear stage 48 is provided on theframe part 24. - A
centre axis 50 of the receivingspace 46 is here arranged essentially parallel to thecentre axis 34 of thefirst fastening interface 26. - A reinforcing
part 52 is moreover fastened on theframe part 24 in such a way that it spans the end of the receivingspace 46 axially with respect to thecentre axis 50. - In the exemplary arrangement illustrated, the reinforcing
part 52 is essentially cross-shaped. - In addition, a
bearing point 54 for agear wheel 56 arranged coaxially with respect to the planetary gear stage is provided on the reinforcingpart 52. - The
gear wheel 56 meshes with the gear wheel 44. - A
gear train 58 is consequently formed by the gear wheel 44 and thegear wheel 56, theoutput gear wheel 40 acting as its input member. - The
gear wheel 56 is moreover formed integrally with a sun gear 60 (seeFIG. 1 ) of theplanetary gear stage 48. In this way, thegear train 58 and theplanetary gear stage 48 are coupled drivingly. - The
planetary gear stage 48 moreover comprises aring gear 62 which runs essentially along an inner circumference of the receiving space 46 (seeFIG. 1 ). - In the exemplary arrangement illustrated, a total of three
planetary gears 64 are provided drivingly between thesun gear 60 and thering gear 62, as can be seen inFIG. 2 . They are mounted rotatably on aplanet carrier 66. - The
planet carrier 66 here represents an output element of theplanetary gear stage 48. - The
gear train 58 and theplanetary gear stage 48 are also referred to together as agear unit 67. - The
frame part 24 furthermore has asecond fastening interface 68 which is designed for fastening aguide part 70, held therein, for aspindle drive 72. - In the exemplary arrangement, the
guide part 70 is a bearing sleeve which is held in thebrake caliper 15. For example, the bearing sleeve is press-fitted in the brake caliper or is welded to the latter. - A centre axis of the
second fastening interface 68 here coincides with thecentre axis 50 of the receivingspace 46 and for this reason is provided with the same reference numeral. - The
second fastening interface 68 has an anti-rotation geometry 74, for example a splined shaft geometry, which runs circumferentially around thecentre axis 50. - A
complementary anti-rotation geometry 82 is provided at that end of theguide part 70 which is to be coupled to thesecond fastening interface 68 such that theguide part 70 can be pushed along thecentre axis 50 into the anti-rotation geometry 74 of thesecond fastening interface 68 and held there non-rotatably in a form-fitting fashion. The anti-rotation geometry is likewise a splined shaft geometry. - The
spindle drive 72 is accommodated inside theguide part 70. - It comprises a
spindle 84 which is configured in the present case as a ball screw. - The
spindle 84 is here connected non-rotatably to theplanet carrier 66 via thetoothed section 86. - The
spindle drive 72 can thus be driven by theelectric motor 28. In detail, theelectric motor 28 is coupled to thespindle drive 72 drivingly via thegear train 58 and theplanetary gear stage 48. - A
spindle nut 88, which is configured as a piston and forms an actuating carriage for a brake lining, is mounted on thespindle 84. - Rotation of the
spindle 84 thus causes thespindle nut 88 to be shifted axially along thecentre axis 50. - The
spindle nut 88 is here guided along thecentre axis 50 directly on a runningsurface 90, wherein the runningsurface 90 is formed by an inner side of theguide part 70. The runningsurface 90 corresponds essentially to a cylindrical surface forming the inner circumference of theguide part 70. In other words, thespindle nut 88 is guided linearly displaceably in theguide part 70. - The
guide part 70 is open towards thegap 17 such that thespindle nut 88 can move into thegap 17. - The
spindle nut 88 is moreover prevented from rotating relatively about thecentre axis 50 by ananti-rotation device 92 which is designed as a slot on theguide part 70. For this purpose, ananti-rotation element 94 which engages in the slot (seeFIG. 1 ) is attached to thespindle nut 88. In the exemplary arrangement, theanti-rotation element 94 is a radial extension. - The
spindle nut 88 serves to apply afirst brake lining 96 of abrake caliper assembly 98 to thebrake rotor 19. As a result, thefirst brake lining 96 can be moved actively onto abrake rotor 19 by theactuator assembly 10. - In detail, the
spindle nut 88 is transferred selectively into an extended position, which is associated with the application of thefirst brake lining 96 to thebrake rotor 19, by theelectric motor 28 via thegear train 58, theplanetary gear stage 48 and thespindle drive 72. - Because of the reaction forces acting inside the
actuator assembly 10 and thebrake caliper assembly 98, asecond brake lining 102 is consequently also applied to thebrake rotor 19. - It should be understood that the
spindle nut 88 can be moved in the same way by operation of theelectric motor 28 into a retracted position which is associated with lifting thefirst brake lining 96 and thesecond brake lining 102 off thebrake rotor 19. - The
spindle drive 72 is supported on anaxial bearing 104 in thebrake caliper 15 via thespindle 84. - Specifically, in the exemplary arrangement, the
axial bearing 104 is supported on awall 105 which is formed integrally with theguide part 70 and which runs transversely to a direction of movement of thespindle nut 88. In the exemplary arrangement, thewall 105 is a radially inward facing flange. - A
contact surface 106, which is in contact with thespindle 84, of theaxial bearing 104 is a conical surface. As a result, transverse forces, which occur in particular when thebrake lining 96 is applied to thebrake rotor 19, can be absorbed by theaxial bearing 104 and be absorbed by thebrake caliper 15 via theguide part 70. - The
axial bearing 104 is a rolling bearing, in particular a needle bearing. - In the present case, the
actuator assembly 10 is designed so that it is not self-locking, such that thespindle nut 88 also shifts back automatically into the retracted position by virtue of elasticities inherent in the system when it is no longer actively forced into the extended position by theelectric motor 28. - A spindle drive according to a first arrangement will be described below in detail with the aid of
FIGS. 3 to 6 , in particular the spindle drive 72 of theactuator assembly 10 shown inFIG. 1 . - The
spindle nut 88 has a pressure-distributingelement 108 at an end of thespindle nut 88 which is close to thebrake lining 96. - The pressure-distributing
element 108 is, for example, made from metal. - In the exemplary arrangement, the pressure-distributing
element 108 is manufactured separately from thespindle nut 88 and press-fitted or welded to thespindle nut 88. In this case, the pressure-distributingelement 108 preferably has acylindrical centring extension 110 which sits in arecess 112 of the spindle nut 88 (seeFIG. 1 ). - In the case of two-part manufacture, the pressure-distributing
element 108 forms a sealing cap for thespindle nut 88. - The pressure-distributing
element 108 can also merge into thespindle nut 88 as a single piece. Thespindle nut 88 with the integrated pressure-distributingelement 108 can be produced in this case as a milled or cast part. - A
contact surface 114, facing away from thespindle 84, of the pressure-distributingelement 108 is annular (seeFIG. 4 ). To be more precise, theannular contact surface 114 is oval when viewed from the front. An elliptical orcircular contact surface 114, designed as a ring, is, however, also conceivable. - In an extended position of the
spindle nut 88, thecontact surface 114 of the pressure-distributingelement 108 is in contact with a back plate 115 (seeFIG. 6 ) of thebrake lining 96 and applies thebrake lining 96 to thebrake rotor 19. - In the arrangement according to
FIGS. 3 to 6 , thecontact surface 114 is in particular discontinuously annular, which is explained in more detail below. - The pressure-distributing
element 108 has afrustoconical projecting collar 116. - Starting from an axial end of the
spindle nut 88, thecollar 116 widens out towards thebrake lining 96 and ends at thecontact surface 114. Thecontact surface 114 consequently has a larger external circumference than thespindle nut 88, in particular an external circumference which is larger by at least 50%. - In the exemplary arrangement, starting from the axial end of the
spindle nut 88, the cross-section of thecollar 116 merges from a circular cross-section into an oval cross-section. - As can be seen particularly well in
FIG. 1 , thecollar 116 has, at the end fastened to thespindle nut 88, the same diameter as thespindle nut 88. To be more precise, a diameter of thecollar 116 at its base is the same size as an average diameter of thespindle nut 88 or as a diameter at a circumferential surface of therecess 112. The circumference of thecontact surface 114 is consequently greater than the circumference of thespindle nut 88. - There is a clearance between the
collar 116 and an end side of thespindle nut 88 such that acircumferential depression 118 is formed for receiving aseal 120. Such a clearance can be obtained simply by an appropriate dimensioning of therecess 112. - The depression 18 is formed in particular when the pressure-distributing
element 108 is attached to thespindle nut 88. - As can be seen in
FIGS. 5 and 6 , which each show thespindle drive 72 in a side view, thecontact surface 114 has twodepressions 122 when viewed from the side. - The discontinuously annular form of the
contact surface 114 which has already been mentioned above is obtained by thedepressions 122. There is in particular no contact of the pressure-distributingelement 108 with theback plate 115 of thebrake lining 96 in the region of thedepressions 122. Thecontact surface 114 thus comprises tworing segments 124. - In the case of an oval or
elliptical contact surface 114, thedepression 122 is arranged in the region of the co-vertices 125. Thecontact surface 114 is thus in contact with theback plate 115 of thebrake lining 96 in the region of thevertices 126. - As can be seen in
FIG. 5 , thering segments 124 of thecontact surface 114 run at an angle a to afriction surface 117 of thebrake lining 96. In particular, two regions of thecontact surface 114 which are situated opposite each other at the circumference, to be more precise the tworing segments 124 formed by thedepressions 122, have opposite inclinations. Specifically, thering segments 124 are inclined towards the centre of the pressure-distributingelement 108 such that thecontact surface 114 is roof-shaped when viewed from the side. - Because a pressure-distributing
element 108 is provided on thespindle nut 88, improved distribution of the application force in the brake lining is achieved such that thebrake lining 96 is deformed as little as possible when acted upon by thespindle nut 88 or the pressure-distributingelement 108 and is consequently applied to a large area of a brake disc of thebrake rotor 19. - A further spindle drive 72 according to the disclosure, which can likewise be used in the
actuator assembly 10 shown inFIG. 1 , is illustrated inFIGS. 7 to 8 . - The same reference numerals are used below for the same structures with the same functions which are known from the above arrangement and reference is made in this respect to the preceding explanations, wherein the differences in the respective arrangements are discussed below in order to prevent repetitions.
- In the arrangement of the
spindle drive 72 illustrated inFIGS. 7 to 8 , thecontact surface 114 is not oval and instead is circular. Moreover, there are nodepressions 122. - In particular, the
contact surface 114 is flat inFIGS. 7 to 8 . - The
spindle drive 72 illustrated inFIGS. 7 to 8 is suited in particular for combination with smaller brake linings than thespindle drive 72 illustrated inFIGS. 1 to 6 . -
FIG. 9 shows a further spindle drive 72 according to the disclosure. - The
spindle drive 72 illustrated inFIG. 9 differs from the spindle drive illustrated inFIGS. 7 and 8 in that at least one cut-out 130, which leads to athread 132 of thespindle 84, is present in acircumferential wall 128 of thespindle nut 88. - The cut-out 130 forms in particular a mounting opening for the
balls 134 of thespindle drive 72. - The
spindle drive 72 according toFIGS. 3 to 6 and 7 to 8 can optionally likewise have a cut-out 130 in thecircumferential wall 128 of thespindle nut 88. - The cut-out 130 enables mounting of the
spindle drive 72 when the pressure-distributingelement 108 forms a single piece with thespindle nut 88 or when the pressure-distributingelement 108 has been connected to thespindle nut 88 before thespindle nut 88 is mounted on thespindle 84. - The
balls 134 of thespindle drive 72 can be blown through the cut-out 130 into thethread 132 by compressed air. - The
balls 134 are, for example, arranged in a mountingtube 136 which is pushed into the cut-out and to which compressed air is applied in order to blow the balls into the thread. The mountingtube 136 preferably has a curve. - The ball return can be integrated into the
spindle nut 88 or into thespindle 84. - For example, a ball return integrated into the
spindle 84 is provided with individual ball recirculation functionality. In this case, a cut-out 130 is provided as a mounting opening for each individual ball recirculation. - The cut-
outs 130 can be closed with a cover once the mounting is complete. - In a first step the
balls 134 can also be inserted into thethread 132 of thespindle 84, and in a subsequent step the pressure-distributingelement 108 is fastened to thespindle nut 88, In this case, a rod, which serves as a mounting aid, can be pushed gradually into thespindle nut 88, wherein theballs 134 are mounted in the threads of thespindle nut 88. Theballs 134 are secured against falling out during mounting by virtue of being covered by the cylindrical rod. Thespindle 84 can then be screwed into thespindle nut 88, wherein the rod is pushed out of thespindle nut 88. Afterwards, the pressure-distributingelement 108 can be fastened to thespindle nut 88. - Regardless of whether the pressure-distributing
element 108 is fastened to thespindle nut 88 before or after theballs 134 are mounted, the pressure-distributingelement 108 can be press-fitted to thespindle nut 88 and secured against rotation by a knurled joint. The pressure-distributingelement 108 can also be welded to thespindle nut 88.
Claims (18)
1. A spindle drive for an actuator assembly of a vehicle brake, the spindle drive including a spindle and a spindle nut mounted on the spindle that forms an actuating carriage that can be displaced between a retracted and an extended position in order to apply a brake lining against a brake rotor, wherein the spindle nut has a pressure-distributing element at an end of the spindle nut that is close to the brake lining, and wherein a contact surface of the pressure-distributing element that faces away from the spindle is continuously or discontinuously annular.
2. The spindle drive according to claim 1 , wherein the annular contact surface is at least one of continuously or discontinuously circular, oval, or elliptical when viewed from the front.
3. The spindle drive according to claim 1 , wherein the pressure-distributing element has a frustoconical projecting collar that ends at the contact surface and widens out from an axial end of the spindle nut to the brake lining.
4. The spindle drive according to claim 3 , wherein, starting from the axial end of the spindle nut, the cross-section of the collar merges from a circular cross-section into an oval or elliptical cross-section.
5. The spindle drive according to claim 1 , wherein the contact surface has at least one depression, viewed in a side view.
6. The spindle drive according to claim 5 , wherein, in the case of an oval or elliptical contact surface, the depression is arranged in the region of the co-vertices.
7. The spindle drive according to claim 1 , wherein the contact surface runs at an angle to a friction surface of the brake lining, wherein two regions of the contact surface that are situated circumferentially opposite each other have opposite inclinations.
8. The spindle drive according to claim 1 , wherein the pressure-distributing element is made from metal and press-fitted or welded to the spindle nut, or in that the pressure-distributing element merges into the spindle nut as a single piece.
9. The spindle drive according to claim 1 , wherein the spindle drive is supported on an axial bearing in the brake caliper via the spindle, wherein the contact surface of the axial bearing with the spindle is a conical surface.
10. The spindle drive according to claim 1 , wherein the spindle drive is a ball screw.
11. The spindle drive according to claim 1 , wherein at least one cut-out, which leads to a thread of the spindle and which forms a mounting opening for the balls of the spindle drive, is present in a circumferential wall of the spindle nut.
12.-14. (canceled)
15. An actuator assembly for a vehicle brake, the actuator assembly including:
a brake lining,
a brake rotor, and
a spindle drive, the spindle drive including with a spindle and a spindle nut mounted on the spindle that forms an actuating carriage that can be displaced between a retracted and an extended position in order to apply a brake lining against a brake rotor, wherein the spindle nut has a pressure-distributing element at an end of the spindle nut that is close to the brake lining, wherein a contact surface of the pressure-distributing element that faces away from the spindle is continuously or discontinuously annular, wherein the pressure-distributing element is arranged at an end of the spindle nut that faces the brake lining and the contact surface of the pressure-distributing element is in contact with a back plate of the brake lining in an extended position of the spindle nut and applies the brake lining to the brake rotor.
16. The actuator assembly according to claim 15 , wherein the annular contact surface is at least one of continuously or discontinuously circular, oval, or elliptical when viewed from the front.
17. The actuator assembly according to claim 15 , wherein the pressure-distributing element has a frustoconical projecting collar that ends at the contact surface and widens out from an axial end of the spindle nut to the brake lining.
18. The actuator assembly according to claim 17 , wherein, starting from the axial end of the spindle nut, the cross-section of the collar merges from a circular cross-section into an oval or elliptical cross-section.
19. The actuator assembly according to claim 15 , wherein the contact surface has at least one depression, viewed in a side view.
20. The actuator assembly according to claim 15 , wherein the contact surface runs at an angle to a friction surface of the brake lining, wherein two regions of the contact surface that are situated circumferentially opposite each other have opposite inclinations.
Applications Claiming Priority (2)
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DE102021129963 | 2021-11-17 | ||
DE102021129963.2 | 2021-11-17 |
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US17/984,689 Pending US20230150470A1 (en) | 2021-11-17 | 2022-11-10 | Spindle drive, actuator assembly, and method for producing a spindle drive |
US17/988,837 Pending US20230151864A1 (en) | 2021-11-17 | 2022-11-17 | Brake actuator unit and electromechanical brake |
US17/988,805 Pending US20230150471A1 (en) | 2021-11-17 | 2022-11-17 | Vehicle brake actuator and electromechanical brake |
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US17/988,837 Pending US20230151864A1 (en) | 2021-11-17 | 2022-11-17 | Brake actuator unit and electromechanical brake |
US17/988,805 Pending US20230150471A1 (en) | 2021-11-17 | 2022-11-17 | Vehicle brake actuator and electromechanical brake |
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US (3) | US20230150470A1 (en) |
CN (3) | CN116136240A (en) |
DE (3) | DE102022119397A1 (en) |
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US11994184B2 (en) * | 2022-01-13 | 2024-05-28 | Hl Mando Corporation | Brake assembly with telescopic multiple ball screw mechanism |
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DE19740867A1 (en) | 1997-09-16 | 1999-03-18 | Itt Mfg Enterprises Inc | Electromechanically operated disc brake for cars |
DE59907116D1 (en) | 1998-03-05 | 2003-10-30 | Continental Teves Ag & Co Ohg | ACTUATING UNIT FOR AN ELECTROMECHANICALLY OPERATED DISC BRAKE |
NL1011142C2 (en) | 1999-01-27 | 2000-07-31 | Skf Eng & Res Centre Bv | Compact actuator. |
DE10146779A1 (en) | 2001-09-22 | 2003-04-17 | Bosch Gmbh Robert | Electromechanical brake |
WO2005124180A1 (en) | 2004-06-15 | 2005-12-29 | Pbr Australia Pty Ltd | Actuating mechanism and brake assembly |
DE102007042654A1 (en) | 2007-09-10 | 2009-03-12 | Schaeffler Kg | Ball screw for use with brake for adjusting brake shoes, has ball channel that is finite, so that balls are movable back and forth between ends along ball channel, where ends of channel are formed by closure part attached at spindle nut |
DE102008062180B4 (en) | 2008-03-01 | 2019-03-28 | Continental Teves Ag & Co. Ohg | Combined vehicle brake with electromechanically actuated parking brake |
DE102009036884A1 (en) | 2009-08-10 | 2011-05-19 | Schaeffler Technologies Gmbh & Co. Kg | Ball screw, with axially supported threaded spindle |
DE102011005517A1 (en) | 2011-03-14 | 2012-09-20 | Continental Teves Ag & Co. Ohg | Electromechanical actuator for motor vehicle braking system, has acoustic decoupling which is provided between transmission and separate transmission element |
US9752634B2 (en) | 2012-11-21 | 2017-09-05 | Advics Co., Ltd. | Electric vehicle braking device |
JP6579853B2 (en) | 2015-08-04 | 2019-09-25 | Ntn株式会社 | Electric brake device |
CN113039373B (en) | 2018-11-15 | 2023-06-02 | 汉拿万都株式会社 | Stepped piston with oversized foot for disc brake |
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2022
- 2022-08-02 DE DE102022119397.7A patent/DE102022119397A1/en active Pending
- 2022-08-02 DE DE102022119395.0A patent/DE102022119395A1/en active Pending
- 2022-08-02 DE DE102022119399.3A patent/DE102022119399A1/en active Pending
- 2022-10-12 CN CN202211245517.8A patent/CN116136240A/en active Pending
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US20230150471A1 (en) | 2023-05-18 |
DE102022119399A1 (en) | 2023-05-17 |
CN116136240A (en) | 2023-05-19 |
US20230151864A1 (en) | 2023-05-18 |
DE102022119397A1 (en) | 2023-05-17 |
CN116136241A (en) | 2023-05-19 |
CN116136243A (en) | 2023-05-19 |
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