US20020079172A1 - Disc brake caliper with integral parking brake - Google Patents
Disc brake caliper with integral parking brake Download PDFInfo
- Publication number
- US20020079172A1 US20020079172A1 US09/746,326 US74632600A US2002079172A1 US 20020079172 A1 US20020079172 A1 US 20020079172A1 US 74632600 A US74632600 A US 74632600A US 2002079172 A1 US2002079172 A1 US 2002079172A1
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- Prior art keywords
- clutch
- piston
- thrust
- housing
- thrust pin
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- 230000007246 mechanism Effects 0.000 claims abstract description 15
- 238000006073 displacement reaction Methods 0.000 claims abstract description 3
- 239000012530 fluid Substances 0.000 description 6
- 238000013519 translation Methods 0.000 description 3
- 239000002783 friction material Substances 0.000 description 2
- 230000000717 retained effect Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000010348 incorporation Methods 0.000 description 1
- 230000001939 inductive effect Effects 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Images
Classifications
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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
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2121/00—Type of actuator operation force
- F16D2121/02—Fluid pressure
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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
- 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
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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
- F16D2125/00—Components of actuators
- F16D2125/02—Fluid-pressure mechanisms
- F16D2125/06—Pistons
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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
- 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
- F16D2125/36—Helical cams, Ball-rotating ramps
Definitions
- the present invention relates to vehicle brakes, and in particular, to a disc brake caliper integrating a parking brake therein.
- the present invention relates to vehicle brakes, and in particular, to a disc brake caliper integrating a parking brake therein.
- a disc brake operates on the principal of hydraulically actuating a piston in a caliper to force opposing brake pads against parallel faces of a rotor attached to the rotating wheel.
- Such a configuration is generally shown in FIG. 1.
- the prior art parking brake and caliper combination comprises a caliper housing 91 having an internal cavity 100 within which piston 92 is acted upon by brake fluid to translate piston 92 with respect to caliper housing 91 .
- a threaded pin extends through caliper housing 91 and into cavity 100 and piston 92 .
- the shaft of threaded pin 93 incorporates high-lead external threads 94 upon which is received a threaded sleeve 95 having mating high-lead internal threads.
- a roller clutch 96 is positioned around the exterior of threaded sleeve 95 such that when pin 93 is rotated by lever 99 , the high-lead threads cause sleeve 95 to rotate with pin 93 until roller clutch engages an outer wall of sleeve 95 and an inner wall of piston 92 to rotationally lock in place sleeve 95 with respect to piston 92 .
- the caliper includes a caliper housing defining a cavity therein and a piston axially translatable within the cavity and having an internal bearing surface. At least one brake pad is affixed to either the piston or the caliper housing.
- a parking brake mechanism is mounted within the cavity and is interposed between a portion of the housing and the piston.
- the parking brake mechanism includes a thrust pin substantially axially aligned with the piston and rotatable within the housing.
- a first radial clutch is engageable with the thrust pin, and a second axial clutch is operable upon the piston. Rotation of the thrust pin in a first direction causes engagement of the first radial clutch and of the second axial clutch causing axial displacement of the piston. Rotation of the thrust pin in an opposite direction causes disengagement of the first and said second clutches.
- FIG. 1 Another aspect of the current invention is a parking brake mechanism for a disc brake caliper of the type having a caliper housing defining a piston cavity.
- the parking brake mechanism includes a piston defining a central cavity at one end thereof and further including a bearing surface.
- a thrust pin having a cylindrical shank at one end and a thrust shoulder at an opposite end has at least a portion of the shank received in the piston cavity.
- a first radial clutch extends about the thrust pin shank and is interposed between the piston and the thrust shoulder.
- a second axial clutch is operable by the radial clutch and is proximate to the piston-bearing surface.
- FIG. 1 is a perspective view of a disc brake caliper and disc pads in engagement with a brake rotor.
- FIG. 2 is an elevational sectional view of a portion of the caliper showing a prior art parking brake utilizing high-lead threads.
- FIG. 3 is an elevational view of a disc brake caliper embodying an integral parking brake of the present invention.
- FIG. 4 is a cross-sectional view of the roller clutch taken along the lines 4 - 4 of FIG. 3.
- FIG. 5 is an exploded clamshell perspective of the parking brake assembly within the disc brake caliper housing.
- FIG. 6 is a cross-sectional view of the opposing ball ramps taken along line 6 - 6 of FIG. 5.
- FIG. 1 shows a general perspective view of a disc brake showing a disc brake caliper 20 incorporating one of the preferred embodiments of the present invention and supporting opposing brake pads 22 and 24 against wheel brake rotor 26 .
- Lever 28 provides mechanical actuation of the parking brake integral to caliper 20 .
- FIG. 3 discloses in elevation a partial section view of a brake caliper 20 incorporating one of the embodiments of the present invention illustrating the arrangement of the parking brake elements within caliper housing 30 .
- Piston 32 is slideably engaged within cavity 36 of caliper housing 30 .
- Piston 32 is axially translatable from left to right and right to left with the application of or release of pressurized brake fluid through brake fluid inlet 34 .
- pressurized brake fluid is introduced from a brake master cylinder (not shown) at a different location on the vehicle and interconnected with the brake caliper by at least one fluid transmission line (also not shown) installed at inlet 34 .
- a parking brake mechanism is also integrated within cavity 36 of housing 30 to provide a safety back-up in case of failure of the brake fluid pressurization system or alternatively to be used to engage the brake pads 22 and 24 on rotor 26 when the vehicle is parked.
- Cavity 36 is sealed from the surrounding ambient pressure with piston seal 38 and thrust pin seal 40 .
- Thrust pin 42 extends from an exterior of caliper housing 30 into cavity 36 .
- Pin 42 has attached to the end protruding from caliper housing 30 , parking brake actuation lever 28 for providing a torquing force about a longitudinal axis of pin 42 .
- Pin 42 includes an integral thrust shoulder 44 which bears upon a rightmost wall of cavity 36 through thrust bearing 46 .
- Thrust bearing 46 can be of a relatively thin non-compressible, low friction material such as Teflone or some other such low friction material.
- Pin 42 further includes a hardened shank 45 that extends into stud recess 64 in stud 62 .
- Stud 62 is affixed to the interior most portion of piston 32 or, alternatively, can be an integral unitary feature of piston 32 .
- roller clutch 48 that extends about the periphery of hardened shank 45 .
- Roller clutch 48 is of a standard roller clutch design which is well known in the art and here comprises a clutch housing 50 including about an inner periphery a plurality of ramped recesses 52 as further shown in cross section in FIG. 4.
- a roller pin 54 is retained in each of the ramped recesses 52 such that when hardened shank 45 of thrust pin 42 is rotated counter-clockwise with respect to clutch housing 50 (as viewed in FIG. 4) rollers 54 begin rolling along ramp recesses 52 .
- Pins 54 roll until they are snugly wedged between housing 50 and hardened shank 45 thereby inducing clutch housing 50 to also rotate in a counter-clockwise direction in concert with further counter-clockwise rotation of pin 42 .
- clutch housing 50 also includes three ramped thrust surfaces 68 equally spaced about clutch housing bearing face 51 at the left end of clutch housing 50 .
- Clutch housing ramped thrust surfaces 68 partially receive therein one ball 60 within each ramp 68 .
- Ramps 68 vary in depth from shallow at one end to a deeper dimension at an opposite end.
- the clutch housing bearing face 51 is retained proximate to the piston bearing face 63 of stud 62 in piston 32 by retainer 56 .
- Retainer 56 is engaged in clutch housing retainer groove 70 and stud retainer groove 72 and is constructed such that retainer 56 permits minor axial translation of clutch housing 50 with respect to stud 62 .
- Piston bearing face 63 on stud 62 includes stud ramps 66 which are configured to receive a portion of balls 60 therein when retainer 56 retains clutch housing 50 in proximate axial position to stud 62 .
- Stud ramps 66 are oppositely configured from ramped thrust surfaces 68 in such a manner that when pin 42 is rotated to engage roller clutch 48 , clutch housing 50 is rotated in like manner with respect to stud 62 .
- clutch housing 50 rotates in direction A with respect to stud 62 and stud 62 rotates in direction B with respect to clutch housing 50
- ball 60 is rolled along respective ramped surfaces 66 and 68 . This respective rotation causes ball 60 to roll to the shallow portions of ramps 66 and 68 , thereby mechanically forcing piston 32 axially to the left.
- Such axial translation of piston 32 then applies the desired clamping force to brake pads 22 and 24 to provide a braking force to brake rotor 26 .
- piston 32 axially adjusts within cavity 36 to maintain brake pads 22 and 24 in a desired spatial relationship proximate to rotor 26 to minimize pad travel when braking is desired.
- retainer 56 As the self-adjustment feature of piston 32 translates to the left within cavity 36 , retainer 56 , by reason of its engagement in grooves 70 and 72 , also translates roller clutch 48 along hardened shank 45 .
- the axial translation of roller clutch 48 along shank 45 over time does not affect the operation of roller clutch 48 because the outer periphery of shank 45 is diametrically uniform along the entire shank.
- Actuation lever 28 is typically activated through a mechanical linkage to a vehicle operator accessible control.
- an electric motor (not shown) can be coupled to pin 42 through a gearbox to transfer the rotary motion of the electric motor to the necessary torque required to actuate the parking brake.
- Such electric motors and gearboxes are well known in the art and the coupling of such an electric motor and gearbox are well within the skill of one practiced in the art.
- the chosen gearbox interfacing between the motor and pin 42 is constructed such that the back drive efficiency of the gearbox is less than 50% meaning that a reverse torque applied to pin 42 from the braking resistance of the wheels is insufficient to induce a reverse operation of the gearbox and electric motor until the electric motor is selectively reversed.
Abstract
Description
- The present invention relates to vehicle brakes, and in particular, to a disc brake caliper integrating a parking brake therein.
- The present invention relates to vehicle brakes, and in particular, to a disc brake caliper integrating a parking brake therein.
- A disc brake operates on the principal of hydraulically actuating a piston in a caliper to force opposing brake pads against parallel faces of a rotor attached to the rotating wheel. Such a configuration is generally shown in FIG. 1. It is also known in the art to incorporate a parking brake within the caliper, and such a prior
art parking brake 90 is shown in FIG. 2. The prior art parking brake and caliper combination comprises acaliper housing 91 having aninternal cavity 100 within whichpiston 92 is acted upon by brake fluid to translatepiston 92 with respect tocaliper housing 91. A threaded pin extends throughcaliper housing 91 and intocavity 100 andpiston 92. The shaft of threadedpin 93 incorporates high-leadexternal threads 94 upon which is received a threadedsleeve 95 having mating high-lead internal threads. Aroller clutch 96 is positioned around the exterior of threadedsleeve 95 such that whenpin 93 is rotated bylever 99, the high-lead threads causesleeve 95 to rotate withpin 93 until roller clutch engages an outer wall ofsleeve 95 and an inner wall ofpiston 92 to rotationally lock inplace sleeve 95 with respect topiston 92. Oncesleeve 95 is rotationally locked in place with respect topiston 92, the high-lead threads 94 ofpin 93drive sleeve 95 andpiston 96 to the left thereby forcing opposing brake pads against the brake rotor to prevent rotation of the wheel and thereby providing the parking brake function. Thrust washer 97 andretainer 98 maintainsleeve 95 in a relatively constant axial relationship with respect topiston 92. As the brake pads wear,piston 92 self adjusts to the left and thrust washer 97 correspondingly forces sleeve 95 to the left along the high-lead threads 94 ofpin 93 whenroller clutch 96 is disengaged. - Incorporation of this configuration for a parking brake in a disc brake caliper poses some problems such as the threads becoming worn or jammed with respect to each other. These problems can potentially result in the failure of the parking brake to engage or the failure of the parking brake to disengage. Additionally, the use of high-lead threads to induce the compression of the opposing brake pads upon the brake rotor is relatively inefficient thereby requiring a significant torquing force to be applied to
pin 93 to affect the required force of the brake pads against the brake rotor. Thus, there is a need for a disc brake caliper incorporating an integrated parking brake of greater reliability that further requires a lower torquing force applied to the parking brake to affect the braking function. - One aspect of the present invention is a disc brake caliper with an integral parking brake. The caliper includes a caliper housing defining a cavity therein and a piston axially translatable within the cavity and having an internal bearing surface. At least one brake pad is affixed to either the piston or the caliper housing. A parking brake mechanism is mounted within the cavity and is interposed between a portion of the housing and the piston. The parking brake mechanism includes a thrust pin substantially axially aligned with the piston and rotatable within the housing. A first radial clutch is engageable with the thrust pin, and a second axial clutch is operable upon the piston. Rotation of the thrust pin in a first direction causes engagement of the first radial clutch and of the second axial clutch causing axial displacement of the piston. Rotation of the thrust pin in an opposite direction causes disengagement of the first and said second clutches.
- Another aspect of the current invention is a parking brake mechanism for a disc brake caliper of the type having a caliper housing defining a piston cavity. The parking brake mechanism includes a piston defining a central cavity at one end thereof and further including a bearing surface. A thrust pin having a cylindrical shank at one end and a thrust shoulder at an opposite end has at least a portion of the shank received in the piston cavity. A first radial clutch extends about the thrust pin shank and is interposed between the piston and the thrust shoulder. A second axial clutch is operable by the radial clutch and is proximate to the piston-bearing surface.
- These and other features, advantages and objects of the present invention will be further understood and appreciated by those skilled in the art by reference to the following specification, claims, and appended drawings.
- FIG. 1 is a perspective view of a disc brake caliper and disc pads in engagement with a brake rotor.
- FIG. 2 is an elevational sectional view of a portion of the caliper showing a prior art parking brake utilizing high-lead threads.
- FIG. 3 is an elevational view of a disc brake caliper embodying an integral parking brake of the present invention.
- FIG. 4 is a cross-sectional view of the roller clutch taken along the lines4-4 of FIG. 3.
- FIG. 5 is an exploded clamshell perspective of the parking brake assembly within the disc brake caliper housing.
- FIG. 6 is a cross-sectional view of the opposing ball ramps taken along line6-6 of FIG. 5.
- For purposes of description herein, the terms “upper”, “lower”, “right”, “left”, “rear”, “front”, “vertical”, “horizontal”, and derivatives thereof shall relate to the invention as oriented in FIG. 3. However, it is to be understood that the invention may assume various orientations and step sequences, except where expressly specified to the contrary. It is also to be understood that the specific devices and processes illustrated in the attached drawings, and described in the following specification are simply exemplary embodiments of the inventive concepts defined in the appended claims. Hence, specific dimensions and other physical characteristics relating to the embodiments disclosed herein are not to be considered as limiting, unless the claims expressly state otherwise.
- Turning to the drawings, FIG. 1 shows a general perspective view of a disc brake showing a
disc brake caliper 20 incorporating one of the preferred embodiments of the present invention and supportingopposing brake pads wheel brake rotor 26.Lever 28 provides mechanical actuation of the parking brake integral tocaliper 20. - FIG. 3 discloses in elevation a partial section view of a
brake caliper 20 incorporating one of the embodiments of the present invention illustrating the arrangement of the parking brake elements withincaliper housing 30. Piston 32 is slideably engaged withincavity 36 ofcaliper housing 30. Piston 32 is axially translatable from left to right and right to left with the application of or release of pressurized brake fluid throughbrake fluid inlet 34. In normal operation, to activate thedisc brake caliper 20, pressurized brake fluid is introduced from a brake master cylinder (not shown) at a different location on the vehicle and interconnected with the brake caliper by at least one fluid transmission line (also not shown) installed atinlet 34. When the brake system is depressurized, such as when the operator removes pressure from the brake pedal, the pressure incavity 36 returns to ambient thereby releasing the pressure ofbrake pads rotor 26. As a safety measure, a parking brake mechanism is also integrated withincavity 36 ofhousing 30 to provide a safety back-up in case of failure of the brake fluid pressurization system or alternatively to be used to engage thebrake pads rotor 26 when the vehicle is parked.Cavity 36 is sealed from the surrounding ambient pressure withpiston seal 38 andthrust pin seal 40. -
Thrust pin 42 extends from an exterior of caliper housing 30 intocavity 36.Pin 42 has attached to the end protruding fromcaliper housing 30, parkingbrake actuation lever 28 for providing a torquing force about a longitudinal axis ofpin 42.Pin 42 includes anintegral thrust shoulder 44 which bears upon a rightmost wall ofcavity 36 through thrust bearing 46. Thrust bearing 46 can be of a relatively thin non-compressible, low friction material such as Teflone or some other such low friction material.Pin 42 further includes a hardenedshank 45 that extends intostud recess 64 instud 62. -
Stud 62 is affixed to the interior most portion ofpiston 32 or, alternatively, can be an integral unitary feature ofpiston 32. Immediately to the left ofthrust shoulder 44 isroller clutch 48 that extends about the periphery of hardenedshank 45.Roller clutch 48 is of a standard roller clutch design which is well known in the art and here comprises aclutch housing 50 including about an inner periphery a plurality of rampedrecesses 52 as further shown in cross section in FIG. 4. Aroller pin 54 is retained in each of the rampedrecesses 52 such that when hardenedshank 45 ofthrust pin 42 is rotated counter-clockwise with respect to clutch housing 50 (as viewed in FIG. 4)rollers 54 begin rolling alongramp recesses 52.Pins 54 roll until they are snugly wedged betweenhousing 50 and hardenedshank 45 thereby inducingclutch housing 50 to also rotate in a counter-clockwise direction in concert with further counter-clockwise rotation ofpin 42. - Turning now to FIG. 5,
pin 42 androller clutch 48 are shown in an exploded configuration. In the preferred embodiment,clutch housing 50 also includes three rampedthrust surfaces 68 equally spaced about clutchhousing bearing face 51 at the left end ofclutch housing 50. Clutch housing ramped thrustsurfaces 68 partially receive therein oneball 60 within eachramp 68.Ramps 68 vary in depth from shallow at one end to a deeper dimension at an opposite end. The clutchhousing bearing face 51 is retained proximate to thepiston bearing face 63 ofstud 62 inpiston 32 byretainer 56.Retainer 56 is engaged in clutchhousing retainer groove 70 andstud retainer groove 72 and is constructed such thatretainer 56 permits minor axial translation ofclutch housing 50 with respect tostud 62.Piston bearing face 63 onstud 62 includes stud ramps 66 which are configured to receive a portion ofballs 60 therein whenretainer 56 retainsclutch housing 50 in proximate axial position tostud 62. - Stud ramps66 are oppositely configured from ramped
thrust surfaces 68 in such a manner that whenpin 42 is rotated to engageroller clutch 48,clutch housing 50 is rotated in like manner with respect tostud 62. As further shown in FIG. 6, whenclutch housing 50 rotates in direction A with respect tostud 62 andstud 62 rotates in direction B with respect toclutch housing 50,ball 60 is rolled along respective rampedsurfaces ball 60 to roll to the shallow portions oframps piston 32 axially to the left. Such axial translation ofpiston 32 then applies the desired clamping force tobrake pads rotor 26. - As
brake pads piston 32 axially adjusts withincavity 36 to maintainbrake pads rotor 26 to minimize pad travel when braking is desired. As the self-adjustment feature ofpiston 32 translates to the left withincavity 36,retainer 56, by reason of its engagement ingrooves roller clutch 48 along hardenedshank 45. The axial translation ofroller clutch 48 alongshank 45 over time does not affect the operation of roller clutch 48 because the outer periphery ofshank 45 is diametrically uniform along the entire shank. -
Actuation lever 28 is typically activated through a mechanical linkage to a vehicle operator accessible control. Alternatively, an electric motor (not shown) can be coupled to pin 42 through a gearbox to transfer the rotary motion of the electric motor to the necessary torque required to actuate the parking brake. Such electric motors and gearboxes are well known in the art and the coupling of such an electric motor and gearbox are well within the skill of one practiced in the art. Ideally, the chosen gearbox interfacing between the motor andpin 42 is constructed such that the back drive efficiency of the gearbox is less than 50% meaning that a reverse torque applied to pin 42 from the braking resistance of the wheels is insufficient to induce a reverse operation of the gearbox and electric motor until the electric motor is selectively reversed. - The above description is considered that of the preferred embodiments only. Modifications of the invention will occur to those skilled in the art and to those who make or use the invention. Therefore, it is understood that the embodiments shown in the drawings and described above are merely for illustrative purposes and are not intended to limit the scope of the invention, which is defined by the following claims as interpreted according to the principals of patent law, including the doctrine of equivalents.
Claims (19)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US09/746,326 US6422354B1 (en) | 2000-12-21 | 2000-12-21 | Disc brake caliper with integral parking brake |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US09/746,326 US6422354B1 (en) | 2000-12-21 | 2000-12-21 | Disc brake caliper with integral parking brake |
Publications (2)
Publication Number | Publication Date |
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US20020079172A1 true US20020079172A1 (en) | 2002-06-27 |
US6422354B1 US6422354B1 (en) | 2002-07-23 |
Family
ID=25000348
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US09/746,326 Expired - Lifetime US6422354B1 (en) | 2000-12-21 | 2000-12-21 | Disc brake caliper with integral parking brake |
Country Status (1)
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US (1) | US6422354B1 (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2004099645A1 (en) * | 2003-05-09 | 2004-11-18 | Lucas Automotive Gmbh | Hydraulically actuated vehicle brake |
US20060124407A1 (en) * | 2004-12-09 | 2006-06-15 | Akebono Brake Industry Co., Ltd. | Disc brake actuating apparatus with parking-brake operating mechanism |
US20090145671A1 (en) * | 2007-01-05 | 2009-06-11 | Irobot Corporation | Robotic Vehicle with Dynamic Range Actuators |
WO2011000867A1 (en) * | 2009-06-30 | 2011-01-06 | Continental Teves Ag & Co. Ohg | Caliper of a disk brake |
US20140124307A1 (en) * | 2011-03-18 | 2014-05-08 | Robert Bosch Gmbh | Power tool braking device |
EP2787240A1 (en) * | 2013-04-02 | 2014-10-08 | Kone Corporation | A brake and an elevator |
US20150203170A1 (en) * | 2012-09-28 | 2015-07-23 | Honda Motor Co., Ltd. | Brake caliper |
CN112334677A (en) * | 2018-06-26 | 2021-02-05 | 日立汽车系统株式会社 | Disc brake |
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FR2828538B1 (en) * | 2001-08-08 | 2003-10-24 | Bosch Gmbh Robert | BRAKE CYLINDER WITH REDUCED DIMENSIONS AND MECHANICAL AND HYDRAULIC OPERATION, AND MOTOR VEHICLE BRAKE COMPRISING SUCH A CYLINDER |
JP3934095B2 (en) * | 2003-09-09 | 2007-06-20 | 本田技研工業株式会社 | Radial mount type disc brake |
US20050217949A1 (en) * | 2004-04-06 | 2005-10-06 | Makoto Ohta | Disc brake caliper with parking input mechanism |
US20050226719A1 (en) * | 2004-04-07 | 2005-10-13 | Sun Sung-Wei | Built-up guide flow fan device |
US7510062B2 (en) * | 2005-11-14 | 2009-03-31 | Illinois Tool Works Inc. | Rotary damper |
JP2010505072A (en) * | 2006-09-27 | 2010-02-18 | コンティネンタル・テーベス・アクチエンゲゼルシヤフト・ウント・コンパニー・オッフェネ・ハンデルスゲゼルシヤフト | Combination vehicle brake with electromechanically operable parking brake and transmission device for converting rotational motion into translational motion |
JP5532246B2 (en) * | 2010-09-30 | 2014-06-25 | 日立オートモティブシステムズ株式会社 | Thrust generator, disc brake and stabilizer |
FR2999257B1 (en) * | 2012-12-12 | 2015-01-02 | Chassis Brakes Int Bv | "DISC BRAKE WITH PARKING BRAKE, MECHANICAL PUSH ASSEMBLY, AND MOUNTING METHOD" |
US10184536B2 (en) | 2016-09-23 | 2019-01-22 | Akebono Brake Industry Co., Ltd. | Brake piston |
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US3788430A (en) * | 1971-08-17 | 1974-01-29 | Gmc Co | Disc brake actuator |
JPS594571B2 (en) * | 1975-12-17 | 1984-01-30 | 住友電気工業株式会社 | Disc brake no. |
US3991859A (en) * | 1976-02-27 | 1976-11-16 | General Motors Corporation | Adjusting mechanism for a disc brake caliper assembly |
US4022300A (en) * | 1976-08-19 | 1977-05-10 | Dayton-Walther Corporation | Mechanical disc brake |
DE3405027A1 (en) * | 1984-02-13 | 1985-08-14 | Alfred Teves Gmbh, 6000 Frankfurt | Actuating device for a friction brake |
US4620617A (en) * | 1985-02-04 | 1986-11-04 | Rockwell International Corporation | Automatic brake adjuster |
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Cited By (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2004099645A1 (en) * | 2003-05-09 | 2004-11-18 | Lucas Automotive Gmbh | Hydraulically actuated vehicle brake |
US20060054431A1 (en) * | 2003-05-09 | 2006-03-16 | Lucas Automotive Gmbh | Hydraulically actuable vehicle brake |
US7370735B2 (en) | 2003-05-09 | 2008-05-13 | Lucas Automotive Gmbh | Hydraulically actuable vehicle brake |
US20060124407A1 (en) * | 2004-12-09 | 2006-06-15 | Akebono Brake Industry Co., Ltd. | Disc brake actuating apparatus with parking-brake operating mechanism |
US7490703B2 (en) * | 2004-12-09 | 2009-02-17 | Akebono Brake Industry Co., Ltd. | Disc brake actuating apparatus with parking-brake operating mechanism |
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US20150203170A1 (en) * | 2012-09-28 | 2015-07-23 | Honda Motor Co., Ltd. | Brake caliper |
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US9862569B2 (en) | 2013-04-02 | 2018-01-09 | Kone Corporation | Brake and an elevator |
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