WO2014090468A1 - Getriebevorrichtung und elektromotorischer bremskraftverstärker - Google Patents
Getriebevorrichtung und elektromotorischer bremskraftverstärker Download PDFInfo
- Publication number
- WO2014090468A1 WO2014090468A1 PCT/EP2013/072122 EP2013072122W WO2014090468A1 WO 2014090468 A1 WO2014090468 A1 WO 2014090468A1 EP 2013072122 W EP2013072122 W EP 2013072122W WO 2014090468 A1 WO2014090468 A1 WO 2014090468A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pinion
- adjustable piston
- transmission device
- adjustable
- piston
- Prior art date
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
- B60T13/746—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
-
- 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
-
- 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
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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
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
- F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H1/222—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with non-parallel axes
- F16H1/225—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with non-parallel axes with two or more worm and worm-wheel gearings
-
- 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
- F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
- F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
- F16H19/04—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack
-
- 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
- F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
- F16D2125/24—Rack-and-pinion
-
- 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
- F16D2125/44—Mechanical mechanisms transmitting rotation
- F16D2125/46—Rotating members in mutual engagement
- F16D2125/52—Rotating members in mutual engagement with non-parallel stationary axes, e.g. worm or bevel gears
Definitions
- the invention relates to a transmission device. Moreover, the invention relates to an electric motor brake booster.
- the power transmission arrangement comprises a drive, a worm shaft connected to the drive, two worm wheels, which are in engagement with the worm shaft, and two pinions, which together with an associated one
- Worm wheel of the two worm wheels are rotatable.
- a double gear member having a first row of teeth and a second row of teeth, which are respectively in engagement with one of the two pinions.
- the invention provides a transmission device with the features of claim 1 and an electromotive brake booster with the features of claim 9.
- the present invention makes possible a transmission device whose static and dynamic tolerances (its tolerance chain) are not distorted
- the static tolerances can be understood to mean tolerances that arise after the gearbox assembly and / or do not change during operation of the gearbox. Such static tolerances are, for example, an angular offset between worm gear and pinion toothing and / or an axial offset between the two on the adjustable piston trained racks, which are in engagement with the two pinions. Dynamic tolerances can be understood to mean tolerances which become effective during operation of the transmission device and / or depend on an actuating travel of the transmission device. Such dynamic
- Tolerances can be, for example, concentricity deviations and pitch errors of all involved gears, worms and / or racks.
- the present invention is thus reliably suitable for eliminating functional impairments that conventionally occur on a transmission.
- two load paths are formed on the transmission device so that an advantageous power split occurs.
- the power split creates a compact gearbox that can transmit comparatively high forces.
- unwanted partial gear forces from the two intersections between the two pinions and their associated toothed racks can cancel each other out on the gear device in such a way that only a force directed in a desired adjustment direction of the adjustable piston is exerted thereon. This causes an advantageous good adjustability of the adjustable piston in the desired adjustment.
- the adjustable piston is perpendicular to the adjustment axis to a
- the adjustable piston may be floatingly guided between the first pinion and the second pinion such that between the first pinion and the first pinion
- an axial distance offset of at least ⁇ 0.3 mm is formed.
- an axial distance offset of ⁇ 0.3 mm is understood to mean that the two toothings are spaced from each other by 0.3 mm from the "starting position" of pinion teeth / rack teeth, resulting in a tooth backlash that is significantly larger than in a conventional one Gasket design with ⁇ 0.1 mm offset between the first pinion and the adjustable piston and between the second pinion and the adjustable piston be formed at least ⁇ 0.4 mm.
- the advantageous two-sided design of the comparatively large swim of the adjustable piston perpendicular to the adjustment allows the advantageous compensation of tolerances without additional components and without an additional space requirement.
- a pinion center plane is defined, which intersects the first pinion and the second pinion in the center, wherein the adjustable piston in the pinion center plane exclusively by means of a first tooth engagement of the first pinion on a first row of teeth of the adjustable piston and by means of a second tooth engagement of the second Pinion is guided floating on a second row of teeth of the adjustable piston.
- a first overlap of the first tooth engagement greater than or equal to 1 or a second overlap of the second tooth engagement can be greater than or equal to 1.
- the first overlap of the first tooth engagement may be greater than or equal to 1.05
- the second overlap of the second tooth engagement may be greater than or equal to 1.05. In this way, an overload of the teeth and a non-circular gear sequence are avoidable.
- a function of a force balance is formed on the transmission device.
- the piston designed as an adjustable piston adjustable piston in at least one inclined to the pinion center plane guide plane by means of a radial clearance in a housing bore of a
- Fig. 1 a to 1 e schematic total and partial views of an embodiment of the transmission device.
- FIG. 2a to 2c partial representations of various gear, wherein Fig. 2a shows an example of the embodiment of Fig. 1 a to 1 e and the transmission of Fig. 2b and 2c are not embodiments of the invention.
- Fig. 1 a to 1 e show schematic total and partial views of a
- the transmission device shown schematically in FIG. 1 a comprises a worm shaft 10, which can be connected to an electric motor (not shown) in such a way that the worm shaft 10 can be set into a rotational movement about a longitudinal axis of the worm shaft 10 by means of the electric motor.
- the longitudinal axis of the worm shaft 10 is aligned perpendicular to the image plane.
- the electric motor by means of which the
- Worm shaft 10 in the rotational movement about its longitudinal axis is displaceable, may be a gear own or an external electric motor.
- the transmission device has a first worm wheel 12a, which is connected via a first pinion shaft 14a with a first pinion 16a.
- a second worm wheel 12a which is connected via a first pinion shaft 14a with a first pinion 16a.
- Worm wheel 12b of the transmission device is connected to a second pinion 16b via a second pinion shaft 14b.
- Worm wheel 12b contact the worm shaft 10 in such a way that, by means of the worm shaft 10 offset into the rotational movement about its longitudinal axis, the first shaft 10 is in contact with the worm shaft 10
- Worm wheel 12a and the first pinion 16a about a common first axis of rotation 18a and the second worm wheel 12b and the second pinion 16b are rotatable about a common second axis of rotation 18b.
- the first axis of rotation 18a and the second Rotary axis 18b aligned parallel to each other.
- the first axis of rotation 18a and / or the second axis of rotation 18b may in particular be perpendicular to the longitudinal axis of the
- Worm shaft 10 to be aligned.
- the feasibility of the gear device is not limited to a particular orientation of the longitudinal axis of the worm shaft 10 or the axes of rotation 18 a and 18 b to each other.
- the transmission device also includes an adjustable piston 20 which is floatingly guided between the first pinion 16a and the second pinion 16b.
- the adjustable piston 20 is adjustable along an adjustment axis 22 by means of the first pinion 16a rotated about the first axis of rotation 18a and of the second pinion 16b rotated about the second axis of rotation 18b.
- the adjustable piston is around
- the adjustment axis 22 of the adjustable piston 20 may in particular parallel to the longitudinal axis of the
- Worm shaft 10 perpendicular to the first axis of rotation 18a and / or be aligned perpendicular to the second axis of rotation 18b.
- the adjustment axis 22 is aligned perpendicular to the image plane.
- the orientation of the adjustment axis 22 may also differ from this embodiment.
- the adjustable piston 20
- swimming path of at least 0.6 mm is adjustable.
- the adjustable piston 20 Under the aligned perpendicular to the adjustment axis 22 floating path of the adjustable piston 20 of at least 0.6 mm can be understood that between the two pinions 16a and 16b sufficient clearance is formed so that the lying at a minimum distance to the first pinion 16a adjustable Piston 20 can swim at least 0.6 mm perpendicular to the adjustment axis 22 in the direction of the second pinion 16b.
- the adjustable piston 20 lying at a minimum distance from the second pinion 16b may be movable toward the first pinion 16a perpendicular to the adjustment axis 22 about the displacement of at least 0.6 mm.
- the adjustable piston 20 is thus relatively free with respect to a perpendicular to the
- Adjustment axis 22 aligned possible adjustment of the adjustable piston 20 between the two pinions 16 a and 16 b out.
- the adjustable piston 20 perpendicular to its adjustment axis 22 of at least 0.6 mm is thus advantageously also in an operation of the transmission device in an environment with a maximum onset temperature of the transmission device and / or a presence of the adjustable piston 20 and / or the pinion 16a and 16b in contact with a liquid / air humidity for several
- the static tolerances include, for example, the tolerances of the positions of the rolling bearings 23a of the worm shaft 10 from their target positions and / or the tolerances of the positions of the rolling bearings 23b of the pinion shafts 14a and 14b from their target positions.
- the transmission device illustrated in FIG. 1a has two rolling bearings 23a for the worm shaft 10 and four rolling bearings 23b for the pinion shafts 14a and 14b.
- Dynamic tolerances can be understood to mean tolerances that take effect during operation of the transmission device.
- dynamic tolerances may depend on a travel of the transmission device.
- Such dynamic tolerances can, for example, concentricity deviations and
- the first worm wheel and the first pinion may be at a first distance from a definable center plane 24 which centrally intersects the worm shaft 10 which is (nearly) equal to a second distance of the second worm wheel 12b and the second pinion 16b from the midplane 24 is.
- Transmission device can thus be formed (almost) symmetrical with respect to the center plane 24 extending centrally through the worm shaft 10.
- the adjustable piston 20 (present in a central position between the two pinions 16a and 16b) may also be designed symmetrically with respect to the center plane 24. This ensures an advantageous power split of the power delivered by the electric motor via a first path along the first worm wheel 12a and the first pinion 16a and a second path via the second worm wheel 12b and the second pinion 16b. By virtue of this power branching, comparatively high forces can be transmitted from the electric motor to the adjustable piston 20.
- the transmission device is not limited to such a symmetrical design.
- the adjustable piston 20 is floatingly guided between the first pinion 16a and the second pinion 16b, in that a center distance offset of at least ⁇ 0.3 mm is formed between the first pinion 16a and the adjustable piston 20 and between the second pinion 16b and the adjustable piston 20.
- the advantageous swimming path of at least 0.6 mm can thus be formed via a backlash.
- the two pinions 16a and 16b are formed symmetrically with respect to their backlash. This results in an advantageous power split despite the comparatively large swimming path of the adjustable piston 20 perpendicular to its adjustment axis 22 of at least 0.6 mm.
- the adjustable piston 20 can be adjustable perpendicular to the adjustment axis 22 by a distance of at least 0.8 mm, preferably at least 0.9 mm, in particular at least 1.0 mm.
- the adjustable piston 20 is floatingly guided between the two pinions 16a and 16b such that the maximum displacement of the adjustable piston 20 perpendicular to the adjustment axis 22 is less than 1.3 mm, in particular less than 1.2 mm, preferably less than one , 1 mm, is. It is preferred for the maximum
- a pinion center plane 26 is also definable, which intersects the first pinion 16a and the second pinion 16b each centered.
- the pinion center plane 26 may be oriented perpendicular to the first axis of rotation 18a and / or the second axis of rotation 18b.
- the adjustable piston 20 in the pinion center plane 26 is exclusively by means of a first tooth engagement of the first pinion 16a on a first row of teeth (not shown) the adjustable piston 20 and by means of a second tooth engagement of the second pinion 16b on a (not outlined) second row of teeth of the adjustable piston 20 floating guided.
- This can also be described in such a way that the adjustable piston 20 in the pinion middle plane 26 is not guided, or centered, by a wall of a housing bore, but via the tooth engagements of the two pinions 16a and 16b.
- the maximum possible floating path of the adjustable piston 20 is perpendicular to its
- the maximum possible floating path of the adjustable piston 20 perpendicular to its adjustment axis 22 can thus be determined comparatively accurately in a simple manner.
- the adjustable piston 20 may also be guided via a raised contour formed on its exterior within a guide in 2-dimensions.
- a first overlap of the first tooth engagement (of the first pinion 16a on the first row of teeth of the adjustable piston 20) is greater than or equal to 1 or a second overlap of the second tooth engagement (of the second pinion 16b on the second
- first overlap of the first meshing engagement may be greater than or equal to 1.05, or the second overlap of the second meshing engagement may be greater than or equal to 1.05.
- Rows of teeth are formed. In this way can be advantageously large
- the transmission device shown in Fig. 1a is a subunit of a
- the adjustable piston 20 is formed as a booster piston (booster). Underneath may be e.g. be understood that the adjustable piston 20 can cooperate with a (not outlined) input rod that a transmitted via the input rod
- Driver braking force can be transmitted together with a force of the electric motor to at least one master cylinder piston.
- a continuous central bore 28 may be formed, through which the Input rod is feasible.
- the design of the transmission device as a subunit of an electromotive brake booster is to be interpreted only as an example.
- the formation of contact surfaces 36 on the housing bore 32 allows a reliable guidance of the amplifier piston designed as an adjustable piston 20, but is not necessary.
- FIG. 1 b the toothing forces Fr1 and Fr2 are shown, which are exerted on the adjustable piston 20 by means of the pinions 16a and 16b.
- the toothing force Fr1 can be exerted on the adjustable piston 20 by means of the first pinion 16a rotated about the first axis of rotation 18a. Accordingly, a second
- Gear force Fr2 exercisable by means of the second pinion 16b rotated about the second axis of rotation 18b on the adjustable piston 20 This can also be described in such a way that the toothing forces Fr1 and Fr2 are exerted by the tooth flanks of the pinions 16a and 16b on the contacted tooth flanks (rows of teeth) of the adjustable piston 20.
- the toothing forces Fr1 and Fr2 are aligned orthogonal to the respective tooth flanks. If the toothing forces Fr1 and Fr2 exerted on the adjustable piston 20 are the same or have the same magnitude, the components of the toothing forces Fr1 and Fr2 oriented perpendicular to the adjusting axis 22 compensate each other out.
- the toothing forces Fr1 and Fr2 add up in this case to one
- Adjustment axis 22 reliably ensured without jamming occurs.
- a force component aligned perpendicular to the adjusting axis 22 remains from the high-power side (the larger spline force Fr1 or Fr2) to the
- the adjustable piston 20 is moved by means of the perpendicular to the adjustment axis 22 aligned force component (automatically) from the high-pressure side to the low-force side. In this way (automatically) the meshing comes on the original
- the function of a force balance is formed on the transmission device. This ensures a symmetrical load distribution of the force transmitted from the motor to the adjustable piston 20 via a first load path realized by means of the first worm wheel 12a and the first pinion 16a and via a second load path passing over the second worm wheel 12b and the second pinion 16b.
- the tolerance compensation on the transmission device is explained below with reference to FIGS. 1 c to 1 e:
- the worm shaft 10 is about 0.1 mm from a central position between the two worm wheels 12 a and 12 b in the direction 40 offset.
- the longitudinal axis 42 of the worm shaft 10 thus has with respect to their dashed lines
- Rotational movement 50 of the second pinion 16 causes a (slight) displacement 52 of the adjustable piston 20 along the adjustment axis 22nd
- the (slight) displacement 52 of the adjustable piston 20 is not associated with a simultaneous rotational movement of the first pinion 16a about the first axis of rotation 18a
- the (slight) displacement 52 of the variable piston 20 results in an increase in the backlash between the first pinion 12a and the adjustable piston 20.
- the tooth engagement 54 between the first pinion 16a and the adjustable piston 20 is thus free of force.
- the toothing force Fr2 which is exerted by the second pinion 16b on the adjustable piston 20, is thus not at least partially compensated by a counterforce.
- This causes the force component, oriented perpendicular to the adjustment axis 22, of the toothing force Fr2 exerted by the second pinion 16b on the adjustable piston 20 to effect an adjustment movement of the adjustable piston 20 until an equilibrium of forces between the toothing forces Fr1 and Fr2 is again achieved.
- the above-described function of the force balance can also be used to compensate for an un mid-position of the worm shaft 10.
- Adjusting the adjustable piston 20 along its adjustment axis 22 are then executable without a terminal.
- the comparatively large displacement of at least 0.6 mm thus leads to the possibility of an axial offset of the adjustable piston 20, whereby each tolerance chain can be compensated.
- FIG. 2a to 2c show partial representations of various transmissions, wherein Fig. 2a shows an example of the embodiment of Fig. 1 a to 1 e and the transmission of Fig. 2b and 2c are not embodiments of the invention.
- An axial distance offset of ⁇ 0.4mm can be understood as meaning that the two gearings are spaced apart from each other by 0.4 mm from the "initial position" of the pinion teeth / rack teeth, resulting in an oversized backlash (in the case of a typical gear design, this is usually a center distance offset
- the expert in a transmission device also prefers the highest possible transmission ratio, which is why he often sets the diameter of the pinions 16a and 16b comparatively small compared to the diameter of the worm wheels 12a and 12b a reduction of the diameter of the pinions 16a and 16b at a (two-sided) center distance offset of ⁇ 0.4 mm to an overlap of the
- Tooth flexion stresses is connected. Although a larger diameter of the pinion 16a and 16b increases the coverage, but causes a lower translation.
- the implementation of the transmission device partially shown in Fig. 2a thus requires of the skilled person that despite a (two-sided) distance tolerance of 0.4 mm, an overlap of the meshing at least equal to 1, preferably greater than 1, guaranteed.
- Embodiment of the invention has a maximum displacement of about 0.2 mm perpendicular to an adjustment axis 22 'of its adjustable piston 20', i. one
- Gear force is transmitted from the pinion 16 'to the teeth of the associated row of teeth of the adjustable piston 20'.
- the amount of toothing force and the distance of the intersection of the force line 58 'on the tooth flanks of the tooth roots gives the torques that the teeth must withstand during operation of the transmission.
- An operation of the transmission shown in Fig. 2b causes a comparatively small tooth stress of about 70%.
- Embodiment of the invention has a maximum floating path for the adjustable piston 20 "perpendicular to its adjustment axis 22", which is 1, 3 mm.
- the center distance offset is thus ⁇ 0.65mm.
- the coverage is only at a value of 0.75.
- the adjustable piston 20 is floating between the first pinion 16a and the second pinion 16b (not shown) such that the adjustable piston 20 is adjustable perpendicular to its adjustment axis 22 by a distance of 0.8 mm is. This is by a two-sided
- Axial distance offset of ⁇ 0.4 mm realized.
- the coverage of the first meshing is maximum 1, 05. This causes the advantageous force line 58 and a
- Tooth load of 100% during operation of the transmission of Fig. 2a is guaranteed despite the comparatively large swimming distance of 0.8 mm.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Gear Transmission (AREA)
- Transmission Devices (AREA)
- Braking Systems And Boosters (AREA)
Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/650,219 US20150308527A1 (en) | 2012-12-12 | 2013-10-23 | Transmission device and electromotive brake booster |
CN201380064834.2A CN104837713B (zh) | 2012-12-12 | 2013-10-23 | 传动装置以及电动的制动力放大器 |
KR1020157015244A KR20150094627A (ko) | 2012-12-12 | 2013-10-23 | 트랜스미션 장치 및 전동식 제동력 부스터 |
JP2015545710A JP2015536278A (ja) | 2012-12-12 | 2013-10-23 | 伝動装置および電動機式のブレーキ倍力装置 |
PL412660A PL227719B1 (pl) | 2012-12-12 | 2013-10-23 | Urządzenie przekładniowe i elektromotoryczny wzmacniacz siły hamowania |
MX2015007381A MX2015007381A (es) | 2012-12-12 | 2013-10-23 | Dispositivo de transmision e intensificador electromotriz de la fuerza de frenado. |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012222949.3 | 2012-12-12 | ||
DE102012222949.3A DE102012222949A1 (de) | 2012-12-12 | 2012-12-12 | Getriebevorrichtung und elektromotorischer Bremskraftverstärker |
Publications (1)
Publication Number | Publication Date |
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WO2014090468A1 true WO2014090468A1 (de) | 2014-06-19 |
Family
ID=49448185
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2013/072122 WO2014090468A1 (de) | 2012-12-12 | 2013-10-23 | Getriebevorrichtung und elektromotorischer bremskraftverstärker |
Country Status (8)
Country | Link |
---|---|
US (1) | US20150308527A1 (de) |
JP (1) | JP2015536278A (de) |
KR (1) | KR20150094627A (de) |
CN (1) | CN104837713B (de) |
DE (1) | DE102012222949A1 (de) |
MX (1) | MX2015007381A (de) |
PL (1) | PL227719B1 (de) |
WO (1) | WO2014090468A1 (de) |
Cited By (4)
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CN110731769A (zh) * | 2019-10-31 | 2020-01-31 | 苏孟勤 | 压力传感器伸缩式快速固定架 |
US10682996B2 (en) | 2015-09-17 | 2020-06-16 | Zf Active Safety Gmbh | Electromechanical brake force booster |
US10814854B2 (en) | 2015-09-17 | 2020-10-27 | Zf Active Safety Gmbh | Assembly having a brake cylinder and an electromechanical brake booster |
US10946845B2 (en) | 2015-09-17 | 2021-03-16 | Zf Active Safety Gmbh | Electromechanical brake booster |
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FR3005295B1 (fr) * | 2013-05-03 | 2015-08-28 | Bosch Gmbh Robert | Systeme de freins a servofrein electrique |
DE102014100444B4 (de) * | 2014-01-16 | 2017-06-29 | MAQUET GmbH | Vorrichtung zum linearen Verschieben einer Patientenlagerfläche und Verfahren zur Montage einer derartigen Vorrichtung |
US9777797B2 (en) | 2014-12-01 | 2017-10-03 | Asmo Co., Ltd. | Actuator |
DE102015219505B4 (de) * | 2015-10-08 | 2019-03-07 | Bayerische Motoren Werke Aktiengesellschaft | Ritzelstartergetriebe mit korrigierter Zahnradgeometrie |
CN105667484A (zh) * | 2016-01-11 | 2016-06-15 | 清华大学 | 一种全解耦双电机驱动的线控制动*** |
AT518943B1 (de) | 2016-07-04 | 2018-08-15 | Univ Wien Tech | Elektrisches Maschinensystem |
US10281037B2 (en) * | 2016-08-09 | 2019-05-07 | Nidec Motors & Actuators (Germany) Gmbh | Device and a method for distributing torque in a worm gear assembly |
DE102017204119A1 (de) | 2017-03-13 | 2018-09-13 | Robert Bosch Gmbh | Aktor mit einer Antriebseinheit und einer Getriebeeinheit |
DE102017204114A1 (de) | 2017-03-13 | 2018-09-13 | Robert Bosch Gmbh | Antriebseinheit für einen Aktor, sowie Aktor mit einer Antriebseinheit und einer Getriebeeinheit |
CN108194596A (zh) * | 2017-12-16 | 2018-06-22 | 包炜廷 | 一种齿条传动机构 |
DE102018211443A1 (de) * | 2018-07-10 | 2020-01-16 | Robert Bosch Gmbh | Druckerzeugungsvorrichtung für ein Bremssystem eines Fahrzeugs |
KR102175273B1 (ko) * | 2019-03-29 | 2020-11-06 | 아주자동차대학 산학협력단 | 타이밍벨트 견인 구동형 액추에이터 |
CN110357009A (zh) * | 2019-08-21 | 2019-10-22 | 辽宁科技大学 | 单动力源的四点同时驱动整体式齿轮齿条升降装置 |
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- 2013-10-23 US US14/650,219 patent/US20150308527A1/en not_active Abandoned
- 2013-10-23 WO PCT/EP2013/072122 patent/WO2014090468A1/de active Application Filing
- 2013-10-23 KR KR1020157015244A patent/KR20150094627A/ko not_active Application Discontinuation
- 2013-10-23 JP JP2015545710A patent/JP2015536278A/ja active Pending
- 2013-10-23 CN CN201380064834.2A patent/CN104837713B/zh active Active
- 2013-10-23 PL PL412660A patent/PL227719B1/pl unknown
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US10682996B2 (en) | 2015-09-17 | 2020-06-16 | Zf Active Safety Gmbh | Electromechanical brake force booster |
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Also Published As
Publication number | Publication date |
---|---|
MX2015007381A (es) | 2015-09-16 |
JP2015536278A (ja) | 2015-12-21 |
PL412660A1 (pl) | 2016-07-18 |
CN104837713A (zh) | 2015-08-12 |
DE102012222949A1 (de) | 2014-06-12 |
KR20150094627A (ko) | 2015-08-19 |
US20150308527A1 (en) | 2015-10-29 |
CN104837713B (zh) | 2017-11-21 |
PL227719B1 (pl) | 2018-01-31 |
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