US3498421A - Hydraulic disk brake with mechanical actuating means - Google Patents

Hydraulic disk brake with mechanical actuating means Download PDF

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Publication number
US3498421A
US3498421A US669907A US66990767A US3498421A US 3498421 A US3498421 A US 3498421A US 669907 A US669907 A US 669907A US 66990767 A US66990767 A US 66990767A US 3498421 A US3498421 A US 3498421A
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Prior art keywords
brake
disk
piston
brakeshoe
yoke
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US669907A
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English (en)
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Siegfried Ohmayer
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Continental Teves AG and Co OHG
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Alfred Teves GmbH
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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
    • F16D55/228—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 separate actuating member for each side
    • 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
    • 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
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/54—Slack adjusters mechanical self-acting in one direction for adjusting excessive play by means of direct linear adjustment
    • 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
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F16D65/567—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • F16D2055/002—Brake calipers assembled from a plurality of parts
    • 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
    • F16D2121/02—Fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/14—Mechanical
    • 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
    • F16D2123/00—Multiple operation forces
    • 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
    • F16D2125/20—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
    • F16D2125/28—Cams; Levers with cams
    • F16D2125/32—Cams; Levers with cams acting on one cam follower
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/40—Screw-and-nut
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/007—Auxiliary mechanisms for non-linear operation

Definitions

  • My present invention relates to a disk-brake system and, more particularly, to a hydraulically actuatable disk brake with an auxiliary piston or actuating means.
  • each wheel-brake cylinder is provided with a main piston and an auxiliary piston acting jointly upon an associated brakeshoe, the two pistons being interconnected by coupling means e.g.
  • auxiliary piston may move forward independently of the main piston but an operative displacement of the latter entrains the auxiliary piston and, with it, the brakeshoe.
  • the auxiliary piston is received in a fluid chamber formed by the brakeshoe support, e.g. a yoke spanning the disk periphery as is well known per se, while the main piston moves in a cylinder of its own.
  • the working face of the main piston in its cylinder is substantially larger than the working face of the auxiliary piston in the aforementioned fluid chamber so that, if both fluid spaces are simultaneously subjected to hydraulic pressure from a common fluid source or from separate sources, these smaller auxiliary pistons will rapidly advance to urge the brakeshoe under relatively low pressure against its confronting disk surface whereas the larger main piston will lag behind, being held back by a suitable biasing force, until the brakeshoes make contact with their disks. After overcoming this biasing force, and with a delay due to an inherent lost motion of the unidirectional coupling means, the main piston will then supplement the braking force exerted by the auxiliary piston.
  • the same lost motion allows a limited reverse movement of the auxiliary piston with reference to the main piston upon a subsequent release of the hydraulic pressure, so as to facilitate the disengagement of the brakeshoe from the disk.
  • the force transmission from the main piston to the auxiliary piston takes place through the intermediary of the housing shiftably mounted on the support or yoke which defines the fluid chamber for the auxiliary piston 7 O and is connected therewith through the aforementioned unidirectional coupling means.
  • the auxiliary piston is generally mushroom-shaped so as to have a relatively wide head bearing in a stable manner upon the brakeshoe and a relatively narrow stern received in a shiftable housing.
  • a wedge member positively connected with the housing for maintaining contact therewith through the intermediary of a restoring spring, forms part of the unidirectional coupling by cooperating with a set of spherical rotary bodies which surround the stem of the auxiliary piston and are clamped between the latter and a frustoconical bore of the wedge member whenever the housing moves forwardly beyond the permissible tolerance with reference to the stem.
  • This housing also constitutes a convenient anchorage for a manually operable control member designed to displace the auxiliary piston independently of or supplementary to the action of the hydraulic control member, e.g. in response to actuation of the usual emergency-brake, parking-brake or locking-brake lever of the vehicle.
  • the main piston need not bear directly upon the housing but may be coupled therewith by way of the same control member, the latter arrangement permitting a repositioning of the main cylinder at a location remote from the auxiliary cylinder or fluid chamber so as to allow for a more effective cooling of this main cylinder.
  • the prior application provides for a pressure piston which is subjected to the primary hydraulic pressure as well as a second piston adapted to bear upon the brakeshoe over a contact area or crosssection which is less than the effective hydraulic crosssection of the power cylinder while the unidirectionally effective coupling is provided between these pistons to permit axial separation thereof in the direction of brake actuation.
  • This arrangement has, however, the disadvantage that when the pistons are mounted upon the oscillating portions of the vehicle chassis, namely the unsuspended wheel axle and nondamped structures depending from the main portion of the chassis by a torsion bar or spring suspensions, the vibrations cause an impermissible relative movement between the pressure piston and the contacting piston.
  • Another object of this invention is to provide a relatively compact brake of low volume and bulk which is easily mounted in an automotive vehicle, which can be used on the nonresiliently supported portions of the body, which is easily adjusted and which avoids the difficulties hitherto encountered with the systems previously described.
  • a mechanical drive arrangement or transmission which transfers the actuating force of the latter piston to the backing plate of the brakeshoe.
  • This mechanical drive is, according to the invention, constituted from a rack-and-pinion arrangement acting upon the piston and having a pinion connected to a threaded spindle onto which a nonrotatable, axially shiftable adjusting nut is threaded.
  • This nut has a radial contact face adapted to bear upon a backing plate of the brakeshoe.
  • FIG. 1 is an axial cross-sectional view of a hydrauli disk brake embodying this invention
  • FIG. 2 is an elevational view partly in section along the lines II-II of FIG. 1 showing the rack-and-pinion arrangement
  • FIG. 3 is an axial cross-sectional view through the yoke of a modified disk brake having means for manually actuating one of the brakeshoes;
  • FIG. 4 is an elevational view, partly broken away, of the actuating system
  • FIG. 5 is an elevational view, partly broken away of still another system embodying the invention.
  • FIG. 6 is an axial cross-sectional view through the device of FIG. 5.
  • the brake yoke is represented at 1 and is disposed along the periphery of a brake disk 2 whose braking faces 2a and 2b are respectively confronted by the brake linings 3a and 3b of a pair of brakeshoes 30 and 31 whose backing plates 4a and 4b have the linings bonded to them.
  • the yoke 1 has a flange case integrally therewith and secured to the axle-housing flange adjacent the wheel of a motor vehicle, the disk 2 being secured by conventional means to the vehicle wheel disk or its rotary axle.
  • the brake illustrated in FIGS. 1 and 2 constitutes a disk-type wheel brake of the automotive vehicle.
  • a pair of power pistons 6a and 6b are received within the wheel-brake cylinders 32a and 32b formed by the yoke 1 on opposite sides of the disk 2 such that the axis of these cylinders extends in the direction of movement of the pistons 6a and 6b and perpendicularly to the braking faces 2a and 2b of the disk. Seals 33a and 33b prevent escape of the brake fluid around the pistons 6a and 6b which they slidably engage.
  • the pistons 6a and 6b are connected each with a respective sleeve or nut 9a or 9b of the threaded-spindle means which is. axially shiftable within the piston 6a or 6b but is restrained from rotation therein.
  • the pistons 6a and 6b can be formed at 34a and 34b with concavities open in the direction of the backing plate 4a or 4b of the respective brakeshoe and of a rectangular or other polygonal cross-section for engagement with the correspondingly polygonal outer periphery of the sleeves 9a and 9b.
  • the threaded-spindle assembly comprises members 9a and 9b which constitute nuts threadedly engaging an adjusting spindle 8a and 8b extending through the respective nuts.
  • the spindles 8a and 8b are generally mushroomshaped and have axially extending shanks a and 10b passing rotatably through the respective pistons 6a and 6b and sealed relatively thereto via sealing rings 35a and 35b.
  • the members 9a and 9b bear against the backing plate 4a and 4b via relatively narrow radial contact zones over a relatively large cross-section as represented at 36a and 36b.
  • Each of the pistons 6a and 6b is also provided with a central boss 37a and 37b surrounding the axial passage 11 through which the spindles 10a and 10b extend and defining a socket 38a or 38b for the correspondingly shaped portion 39a, 39b of the adjustment member 8a or 8b.
  • the portions 38a, 39a and 38b, 39b conform to surfaces of revolution centered on the axis of the spindles so as to permit rotation of the members 8a and 8b and axial force transfer between these members and the respective pistons 6a and 6b.
  • the extremities of the shanks 10a and 10b remote from the backing plates 4a and 4b are formed as pinions whose teeth are indicated at 40a and 40b, respectively in mesh with a rack 7a or 7b constituting an actuating piston or plunger.
  • Each actuating piston as shown for the piston 7a in FIG. i2, is provided at its extremity with a pair of gland-type seals 41, 42 and along an intermediate portion, an array of axially spaced teeth 43 in mesh with the teeth 40a or 40b of the respective pinion 10a or 10b.
  • each lobe of the yoke is provided rearwardly of the respective cylinder 32a and 32b with a bore 12 slidably receiving the respective actuating piston 7a and 7b and defining therewith working chambers as represented at 15 communicating via an inlet port 44 with the hydraulic brake network which includes a master cylinder actuatable by the brake pedal and adapted to drive hydraulic fluid through the port 44 into chamber 15.
  • the pistons 6a and 6b also define respective working chambers 14a and 14b in the cylinder bores 32a and 32b which are connected to the same hydraulic network, eg via a passage 45 in each lobe of the yoke.
  • a forwardpressure valve 46 is provided in the supply line to the main piston chambers 14a and 14b and opens only upon the attainment in the transmission network of a predetermined elevated pressure to connect these chambers with the hydraulic lines which otherwise are blocked.
  • each piston 7a and 7b is shifted hydraulically prior to the pressurization of the respective main brake chamber 14a or 14b.
  • the brake yoke 1 In normal operating conditions, the brake yoke 1 is stationary while the disk 2 is rotating and the brakeshoes 30 and 31 have been thrown back from the braking faces 2a and 2b of the disk after the previous brake operation.
  • hydraulic pressure is forced through port 44 and to line 47 communicating with passage 45 and initially shifts the pistons 7a and 7b relatively to the axis of the pinions 10a and 10b in mesh therewith, thereby rotating the spindles 8a and 8b within the adjusting nuts 9a and 9b which are held against rotation.
  • the brakeshoes 30 and 31 are thus advanced axially until their linings 3a and 3b bear against the braking faces 2a and 2b of the disk 2.
  • the brake-fluid consumption is, as determined by the relatively small volume of the cylinder bores within which the auxiliary pistons 7a and 7b ride, relatively little so that the corresponding displacement of the brake pedal necessary to take up the brake play is negligible.
  • each piston 6a, 6b need undergo no significant displacement as the brake linings 3a and 3b already abut the braking faces 2a and 2b so that the elevated brake pressure immediately is translated into a friction force at the disk 2 via the spindle 8a and 8b of each piston 6a or 6b and the respective abutment nut 9a, 9b which presses against the backing plate 4a, 4b of each shoe.
  • the stroke of each piston 6a, 6b thus corresponds only to that determined by frictional wear of the brake lining 3a or 3b and the yield or distention of the support system.
  • V (a s +a s
  • a represent the cross-sectional areas of the bores 12 while s and s are the strokes of the auxiliary pistons 7a and 7b.
  • the hydraulic ratio between the master cylinder and the wheel-brake cylinder is relatively high in terms of the force applied to the latter with a relatively small total volume of brake-fluid displacement.
  • the pistons 6a and 6b do not aspirate fluid into the chambers 14a and 14b when the spindles 8a and 8b advance the nuts 9a and 9b in the direction of the disk 2.
  • the spring 16 shifts each rack-like piston 7a, 7b in the opposite direction to withdraw the nut 9a, 9b from the backing plate 4a, 4b and permit the surfaces 2a and 2b to fling the shoes 30 and 31 outwardly.
  • the rack 7a abuts the frictional member 17 directly and shifts it along the bore 12 with the hydraulic force developed by member 7a.
  • the original brake play can be restored merely by inserting a tool through the open end 12 of bore 12 to shift member 17' and the respective piston 7a or 7b in the opposite direction (arrow B) until the system once again assumes the position illustrate in FIG. 2.
  • FIGS. 3 and 4 show a modified brake system in 'which the brake disk 1 or 2 is sandwiched between a pair of brakeshoes 130 and 131 shiftable in a yoke 101 attached at 105 to the axle housing adjacent the vehicle wheel for movement toward and away from the respective braking faces 102a and 102b along the outer periphery of this disk.
  • the brakeshoes 130 and 131 have respective linings 103a and 103b confronting the braking faces 102a and 102b of the disk 102 and bonded to backing plates 104a and 104b guided in the yoke 101 in the usual manner (eg via bolts 101a interconnecting both lobes of the yoke).
  • Each yoke half is here provided with a respective nonrotatable adjustment nut 109a or which is shiftable in the direction of arrow 109a and 10%. respectively for actuation of the brake.
  • the hydraulic force necessary to actuate the brake derives from a hydraulically operable cylinder 106 independent of the yoke 101 and connected via a piston rod 106a to an actuating arm 121.
  • the actuating arm 121 has a rectangular socket 121' hugging the correspondingly shaped head 120' of an eccentric 120 journaled in the right-hand side of yoke 101.
  • a locking nut 120 clamps the actuating lever or arm 121 in place while a split ring 120a, remote from head 120, retains the eccentric shaft in the bore 101a provided therefor.
  • the shaft 120 has its eccentric portion 120b offset from the axis of rotation 120c of this shaft, the axis running parallel to the braking faces 102a, 102b of the disk, transversely of the axis of rotation of the disk 102 and perpendicularly to the direction of displacement of 109a and 10% of the brakeshoes 130, 131.
  • the ec centric portion 12% of shaft 120 bears against the pinion-forming extremity or stem 110a of a spindle 108a at the right-hand lobe of the yoke 101 and, upon rotation of the lever 121 in the clockwise sense (FIG. 3) shifts the spindle 108a and its brakeshoe 130 against the braking face 102a of the disk.
  • the reaction force developed by the shaft draws the yoke 101 which is mounted on the axle housing with freedom of limited axial movement, to the right to apply brakeshoe 131 to the other face of the disk.
  • the other lobe of yoke 101 is also provided with a spindle 108b threadedly received by the nonrotatable but axially shiftable nut 10% and bearing at 110' in a socket 101" of the yoke.
  • the spindle 108b has a toothed stern 110b forming a pinion analogous to the pinion 11011 of spindle 108a.
  • the pinions 110a and 11% of each of the brakeshoes and 131 are in mesh with respective auxiliary piston 107a and 107b slidable in respective bores 112a and 11% parallel to the braking faces 102a and 102b and perpendicular to the direction of displacement of the respective brakshoes 109a and 10%.
  • the chambers 115a and 115b of the pistons 107a and 107b are connected in the hydraulic network 147 which is pres surized by the master cylinder and delivers hydraulic fluid to the wheel-brake cylinder 106 by a valve 146 of the type described at 46 in FIGS. 1 and 2.
  • a friction member 117a and 117b is mounted in each bore 112a, 112b and serves as a seat for respective spring 116a or 116b bearing upon the piston 107a or 107b.
  • the arm 121 Upon release of the brake pressure, the arm 121 permits retraction of the threaded-spindle arrangement 108a, 109a, and 108b, 109b, the springs 116a and 116b establishing the brake play as previously described in connection with FIGS. 1 and 2.
  • FIGS. 5 and 6 show a brake yoke 201, the righthand half of which serves for mounting the yoke via lugs 205 with freedom of axial movement upon the axle housing of a motor vehicle.
  • the wheel-brake disk 202 which is secured to the wheel disk of a vehicle wheel, rotates relatively to the yoke 201 and is peripherally surrounded thereby over a sector of its path.
  • a pair of brakeshoes 230 and 231 flank the disk 202 and are guided by pins 230a and 231a in the adjusting nuts 209a and 20% of the brake-actuating system.
  • a spring clip 230' has arms 230b and 231b forming guides for the brakeshoes 230 and 231 at the upper part of the brake yoke.
  • the brakeshoes 230 and 231 have brake linings 7 203a and 203b confronting the disk 202 and bonded to backing plates 204a and 20411.
  • a pair of pistons 207a and 207b respectively displace the nut 209a, 20% to advance the brakeshoes 230 and 231 through the desired brake play.
  • the pistons 207a and 207b which are shiftable in respective bores 212a and 21% form racks meshing with pinions 210a and 210b affixed to the ends or integral with respective threaded spindles 208a and 208b.
  • the spindles are threadedly received in the nuts 209a and 20% and have shoulders 208a and 20812 respectively seated against the yoke 201 and the actuating piston 206 which is here built into the yoke 201.
  • the piston 206 defines, at the right-hand side of the yoke 201, a main working chamber 214 energizable with hydraulic fluid via the forward-pressure valve 46 previously described and is also engageable by the eccentric portion 22% of an eccentric shaft 220 whose axis runs perpendicularly to that of the spindle 20812 and the rack 20712.
  • the spindle 208b is rotatably mounted in a bore 211 of the power piston 208 which is held yialdably to the right by a stack 222 of dished-disk spring washers of the Belleville type. These springs are seated against a ring 222a which, in turn, is retained by a split ring 222b anchored in the wall of the yoke portion 201 defining the cylinder 20117.
  • the piston 207b (as illustrated in FIG.
  • the piston 207a may be connected via a rod 218 to a friction body 217 at the open end 212' of the bore 212b, the friction body being shiftable within a casing 217' against the force of restoring spring 216 in the form of a stack of Belleville washers.
  • the end 218' of the rod 218 may emerge from the casing 217 to allow the rod 218 to be forced inwardly when the device is to be reset.
  • hydraulic fluid is supplied to the bores 212a and 212k via, for example, the fitting 244, thereby shifting the rack-forming pistons 207a and 207b to rotate the spindles 208a and 208b and bring the nonrotatable nuts 209a and into axial engagement with the backing plates 204a and 204b of the respective brakeshoes and advance these brakeshoes until the brake linings 203a and 20312 engage the braking faces of the disk.
  • the rods 218 displace the friction bodies 217 (e.g. to the left in FIG.
  • the reaction force is applied to the yoke 201 which is shifted to the right to transmit force via the spindle assembly 208a and 20911 to the brakeshoe 231.
  • the total stroke is determined by the yielding of the yoke and the wear of the brakeshoes.
  • the eccentric shaft 220 is employed and is provided with an arm 221 which can be engaged by a bowden line or other flexible-cable arrangement for operation by the hand-brake lever of the vehicle.
  • lever 221 When lever 221 is rotated, the eccentric 220 shifts the piston 206 to the left and may retain it in its left-hand position as long as the flexible cable (not shown) remains tensioned.
  • a disk brake comprising a brake disk, a housing positioned along the periphery of said disk, a brakeshoe mounted in said housing for movement toward and away from said disk and engageable therewith to brake relative rotation of said housing and said disk, main actuating means for applying said brakeshoe with substantial force to said disk, and auxiliary actuating means for advancing said brakeshoe in the direction of said disk prior to the application of the brakeshoe thereagainst with substantial force
  • said auxiliary actuating means includes a hydraulically displaceable auxiliary piston mounted in said housing and shiftable therein under hydraulic pressure, and a mechanical transmission interposed between said auxiliary piston and said brakeshoe for displacing said brakeshoe upon movement of said auxiliary piston
  • said main actuating means including a cylinder, and a piston shiftable in said cylinder and having an effective area greater than the effective area of said auxiliary piston and operatively coupled with said brakeshoe for applying same against said disk, said mechanical transmission including a threaded-spindle assembly
  • said mechanical transmission further includes a pinion provided on said assembly and a rack formed on said auxiliary piston and meshing with said pinion.
  • said assembly includes a nonrotatable axially shiftable nut bearing upon said brakeshoe, and a spindle carrying said pinion and threadedly received in said nut for axially displacing same upon rotation of said spindle by said rack.
  • said friction means includes a rod extending through said bore and engaging said auxiliary piston, and a friction element mounted in said here and engaging said rod, said spring means including a spring bearing upon said element and yieldably limiting displacement thereof upon movement of said rod.
  • said friction means includes a friction element yieldably engaging the wall of said bore, said spring means being interposed between said friction element and said auxiliary piston.
  • a disk brake comprising a brake disk, a housing positioned along the periphery of said disk, a brakeshoe mounted in said housing for movement toward and away from said disk and engageable therewith to brake relative rotation of said housing and said disk, a main actuating means for applying said brakeshoe with substantial force to said disk, and auxiliary actuation means for advancing said brakeshoe in the direction of said disk prior to the application of the brakeshoe thereagainst with substantial force
  • said auxiliary actuating means includes a hydraulically displaceable auxiliary piston mounted in said housing and shiftable therein under hydraulic pressure, and a mechanical transmission interposed between said auxiliary piston and said brakeshoe for displacing said brakeshoe upon movement of said auxiliary piston
  • said main actuating mean including an eccentric mounted in said housing and rotatable about an axis transverse to the direction of displacement of said brakeshoe, and an actuating arm connected to said eccentric for rotating same.
  • a disk brake comprising a brake disk, a housing positioned along the periphery of said disk, a 'brakeshoe mounted in said housing for movement toward and away from said disk and engageable therewith to brake relative rotation of said housing and said disk, main actuating means for applying said brakeshoe with substantial force to said disk, and auxiliary actuating means for advancing said brakeshoe in the direction of said disk prior to the application of the brakeshoe thereagainst with substantial force
  • said auxiliary actuation means includes a hydraulically displaceable auxiliary piston mounted in said housing and shiftable therein under hydraulic pressure, and a mechanical transmission interposed between said auxiliary piston and said brakeshoe upon movement of said auxiliary piston, said housing being a yoke carrying a pair of brakeshoes each mounted for movement relatively to said disk and confronting respective brake faces thereof, each of said brakeshoes being provided with a respective auxiliary piston and a mechanical transmission interposed between the corresponding auxiliary piston and brakeshoe for displacing the latter
  • said mean actuating means includes an eccentric mounted in said yoke for rotation about an axis perpendicular to the axis of one of said spindles and to the direction of displacement of the corresponding auxiliary piston, and an actuating lever connected with said eccentric and coupled with said piston of said main actuating means.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
US669907A 1965-08-14 1967-09-22 Hydraulic disk brake with mechanical actuating means Expired - Lifetime US3498421A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DET0029212 1965-08-14
DET0032130 1966-09-24

Publications (1)

Publication Number Publication Date
US3498421A true US3498421A (en) 1970-03-03

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US669907A Expired - Lifetime US3498421A (en) 1965-08-14 1967-09-22 Hydraulic disk brake with mechanical actuating means

Country Status (5)

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US (1) US3498421A (OSRAM)
DE (1) DE1600142B2 (OSRAM)
FR (1) FR93027E (OSRAM)
GB (1) GB1179890A (OSRAM)
SE (1) SE350582B (OSRAM)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0260934A1 (en) * 1986-09-19 1988-03-23 LUCAS INDUSTRIES public limited company Disc brakes
WO2002014710A3 (de) * 2000-08-17 2002-05-10 Knorr Bremse Systeme Scheibenbremse mit einer nachstell-einrichtung auf jeder seite der bremsscheibe
WO2003044386A1 (de) * 2001-11-23 2003-05-30 Continental Teves Ag & Co. Ohg Schwimmsattelscheibenbremse mit vorrichtung zur lüftspieleinstellung sowie zugehöriges verfahren
WO2003067114A1 (de) * 2002-02-08 2003-08-14 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse mit elektrisch angetriebener nachstelleinrichtung
WO2003069181A1 (de) * 2002-02-13 2003-08-21 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse mit elektromotorisch angetriebener nachstellvorrichtung und verfahren zur steuerung einer scheibenbremse
EP1138971A3 (de) * 2000-03-28 2004-01-02 Siemens Aktiengesellschaft Elektromechanische Bremsvorrichtung, insbesondere für ein Kraftfahrzeug
US20050040703A1 (en) * 2001-11-16 2005-02-24 Johann Baumgartner Control method for controlling a resetting system of a disc brake and brake disc assembly
US20050077126A1 (en) * 2002-01-14 2005-04-14 Johann Baumgartner Disc brake with an adjusting system
EP1447584A3 (en) * 2003-01-31 2005-05-11 CORAM S.p.A. Hydraulically and mechanically actuated disc brake
US20080277212A1 (en) * 2005-12-08 2008-11-13 Volvo Lastvagnar Ab Service Disc Brake for a Heavy Vehicle
US20090283371A1 (en) * 2006-09-27 2009-11-19 Continental Teves Ag & Co., Ohg Combined Vehicle Brake With Electromechanically Operable Parking Brake and Gear For Converting A Rotary Movement Into A Translational Movement
CN107061559A (zh) * 2016-10-22 2017-08-18 许星星 采用新型制动材料的载重汽车盘式制动器
CN108730372A (zh) * 2018-06-04 2018-11-02 广州天下通电子商务有限公司 一种对称变径刹车系统
CN109058326A (zh) * 2018-08-13 2018-12-21 浙江零跑科技有限公司 一种设有失效驻车结构的刹车装置
US20230025413A1 (en) * 2019-12-16 2023-01-26 Bayerische Motoren Werke Aktiengesellschaft Fixed-Caliper Brake Comprising Electromechanical-Hydraulic Force Transmission
EP4578748A1 (en) * 2023-12-29 2025-07-02 Huawei Digital Power Technologies Co., Ltd. Electromechanical braking system with wear compensation and vehicle

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2600387B1 (fr) * 1986-06-23 1990-08-10 Wabco Westinghouse Systeme de frein d'immobilisation pour vehicule et etrier de frein pour un tel systeme
DE102009006259A1 (de) * 2009-01-27 2010-03-04 Daimler Ag Bremssattel

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US1886936A (en) * 1928-08-18 1932-11-08 Hydraulic Brake Co Fluid pressure operated brake mechanism
US2826277A (en) * 1956-02-13 1958-03-11 Goodyear Tire & Rubber Compound pressure cylinder for brakes

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Publication number Priority date Publication date Assignee Title
US1886936A (en) * 1928-08-18 1932-11-08 Hydraulic Brake Co Fluid pressure operated brake mechanism
US2826277A (en) * 1956-02-13 1958-03-11 Goodyear Tire & Rubber Compound pressure cylinder for brakes

Cited By (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0260934A1 (en) * 1986-09-19 1988-03-23 LUCAS INDUSTRIES public limited company Disc brakes
EP1138971A3 (de) * 2000-03-28 2004-01-02 Siemens Aktiengesellschaft Elektromechanische Bremsvorrichtung, insbesondere für ein Kraftfahrzeug
US20040026181A1 (en) * 2000-08-17 2004-02-12 Johann Baumgartner Disk brake having an adjusting system
US20040050630A1 (en) * 2000-08-17 2004-03-18 Johann Baumgartner Disk brake
WO2002014709A3 (de) * 2000-08-17 2002-06-27 Knorr Bremse Systeme Scheibenbremse mit einem synchronisierten nachstellsystem
WO2002014708A3 (de) * 2000-08-17 2002-06-27 Knorr Bremse Systeme Scheibenbremse mit einer nachstell-einrichtung auf jeder seite der bremsscheibe
US7219772B2 (en) * 2000-08-17 2007-05-22 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Disk brake with a regulating system
US7134532B2 (en) * 2000-08-17 2006-11-14 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Disk brake
WO2002014125A3 (de) * 2000-08-17 2002-05-10 Knorr Bremse Systeme Scheibenbremse mit schiebe- oder schwenksattel
WO2002014710A3 (de) * 2000-08-17 2002-05-10 Knorr Bremse Systeme Scheibenbremse mit einer nachstell-einrichtung auf jeder seite der bremsscheibe
US7121387B2 (en) 2000-08-17 2006-10-17 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Disk brake having a brake application system with a rotary lever
US20040045776A1 (en) * 2000-08-17 2004-03-11 Johann Baumgartner Disc brake comprising an adjuster module
US20040050635A1 (en) * 2000-08-17 2004-03-18 Dieter Bieker Disk brake with a regulating system
WO2002014127A3 (de) * 2000-08-17 2002-06-27 Knorr Bremse Systeme Scheibenbremse mit einem elektromotorangetriebenen nachstellsystem, und verfahren
US7086504B2 (en) 2000-08-17 2006-08-08 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Disc brake comprising an adjuster module
EP1607652A3 (de) * 2000-08-17 2006-04-26 KNORR-BREMSE SYSTEME FÜR NUTZFAHRZEUGE GmbH Elektromechanisch oder pneumatisch betätigte Scheibenbremse
CN100398864C (zh) * 2000-08-17 2008-07-02 克诺尔商用车制动系统有限公司 用于控制盘式制动器的调整系统的方法
US7032721B2 (en) * 2001-11-16 2006-04-25 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Control method for controlling a resetting system of a disc brake and brake disc assembly
US20050040703A1 (en) * 2001-11-16 2005-02-24 Johann Baumgartner Control method for controlling a resetting system of a disc brake and brake disc assembly
WO2003044386A1 (de) * 2001-11-23 2003-05-30 Continental Teves Ag & Co. Ohg Schwimmsattelscheibenbremse mit vorrichtung zur lüftspieleinstellung sowie zugehöriges verfahren
US20050077126A1 (en) * 2002-01-14 2005-04-14 Johann Baumgartner Disc brake with an adjusting system
US7240773B2 (en) 2002-01-14 2007-07-10 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Disc brake with an adjusting system
WO2003067114A1 (de) * 2002-02-08 2003-08-14 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse mit elektrisch angetriebener nachstelleinrichtung
WO2003069181A1 (de) * 2002-02-13 2003-08-21 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse mit elektromotorisch angetriebener nachstellvorrichtung und verfahren zur steuerung einer scheibenbremse
EP1447584A3 (en) * 2003-01-31 2005-05-11 CORAM S.p.A. Hydraulically and mechanically actuated disc brake
US20080277212A1 (en) * 2005-12-08 2008-11-13 Volvo Lastvagnar Ab Service Disc Brake for a Heavy Vehicle
US20090283371A1 (en) * 2006-09-27 2009-11-19 Continental Teves Ag & Co., Ohg Combined Vehicle Brake With Electromechanically Operable Parking Brake and Gear For Converting A Rotary Movement Into A Translational Movement
US8616348B2 (en) * 2006-09-27 2013-12-31 Continental Teves Ag & Co. Ohg Combined vehicle brake with electromechanically operable parking brake and gear for converting a rotary movement into a translational movement
CN107061559A (zh) * 2016-10-22 2017-08-18 许星星 采用新型制动材料的载重汽车盘式制动器
CN107061559B (zh) * 2016-10-22 2019-04-05 瑞安市寅明机车部件有限公司 采用制动材料的载重汽车盘式制动器
CN108730372A (zh) * 2018-06-04 2018-11-02 广州天下通电子商务有限公司 一种对称变径刹车系统
CN108730372B (zh) * 2018-06-04 2020-10-09 海门茂发美术图案设计有限公司 一种对称变径刹车系统
CN109058326A (zh) * 2018-08-13 2018-12-21 浙江零跑科技有限公司 一种设有失效驻车结构的刹车装置
US20230025413A1 (en) * 2019-12-16 2023-01-26 Bayerische Motoren Werke Aktiengesellschaft Fixed-Caliper Brake Comprising Electromechanical-Hydraulic Force Transmission
EP4578748A1 (en) * 2023-12-29 2025-07-02 Huawei Digital Power Technologies Co., Ltd. Electromechanical braking system with wear compensation and vehicle

Also Published As

Publication number Publication date
DE1600142A1 (de) 1970-04-02
FR93027E (fr) 1969-01-31
DE1600142B2 (de) 1974-01-24
SE350582B (OSRAM) 1972-10-30
GB1179890A (en) 1970-02-04

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