GB2100814A - Spot brake - Google Patents

Spot brake Download PDF

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Publication number
GB2100814A
GB2100814A GB08215969A GB8215969A GB2100814A GB 2100814 A GB2100814 A GB 2100814A GB 08215969 A GB08215969 A GB 08215969A GB 8215969 A GB8215969 A GB 8215969A GB 2100814 A GB2100814 A GB 2100814A
Authority
GB
United Kingdom
Prior art keywords
diaphragm
booster piston
hole
set forth
disc
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
GB08215969A
Other versions
GB2100814B (en
Inventor
Clive Anthony Barker
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
TI Interlock Ltd
Original Assignee
TI Interlock Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by TI Interlock Ltd filed Critical TI Interlock Ltd
Priority to GB08215969A priority Critical patent/GB2100814B/en
Publication of GB2100814A publication Critical patent/GB2100814A/en
Application granted granted Critical
Publication of GB2100814B publication Critical patent/GB2100814B/en
Expired legal-status Critical Current

Links

Classifications

    • 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
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • 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
    • F16D65/78—Features relating to cooling
    • F16D65/84—Features relating to cooling for disc brakes
    • F16D65/847—Features relating to cooling for disc brakes with open cooling system, e.g. cooled by air
    • 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
    • F16D2125/00—Components of actuators
    • F16D2125/02—Fluid-pressure mechanisms
    • F16D2125/14—Fluid-filled flexible members, e.g. enclosed air bladders

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Systems And Boosters (AREA)

Abstract

A spot brake including a rotor disc 13 to be braked, one or more pads 26 to be pressed against (a) working face(s) 19 of disc 13 in a direction parallel to the axis of disc rotation and mounted in respective bores 28 in (a) stator disc(s) 20, the pads being axially removable from the stator disc (20) in the said direction parallel to the axis of the disc 13; the number of pads is selected in relation to the power to be disipated. As shown, pads 26 are screwed to pieces 27 of heat-insulating material and are operated by compressed air fed to elastomeric capsules 32 retained in caps 34-the assembly 34, 32, 30, 27, 26 may be withdrawn by slackening screws 35, rotating cap 34 until ears 36 disengage screws 35 and then withdrawing assembly axially (see Figure 2). Figure 5 shows alternative pad 26. Bores 28 not containing pads 26 may have fans (54) therein for passing cooling air and further disclosure regarding cooling is found, for example, in Figures 3, 4, 5. <IMAGE>

Description

respectively. Due to their flexibility, the bellows 33 are capable of sealing the through-holes 32 without hindering the forward and rearward movement of the booster piston 2.
The superposed surfaces of the disc portion 2b of the booster piston 2 and the diaphragm 4 can be separated from each other except at the portion of the inner circumferential bead 4a and is communicated with the second working chamber B via a through-hole 34 of the diaphragm 4 through which the tie rod 11 penetrate. The through-hole 34 is defined by an annular bead 4c which is integral with the diaphragm 4 and is generally brought into intimate contact with the rear surface of the rear end portion 33b of the bellows 33 but in a detachable manner by means of an elastic member C.
The elastic member C is formed integrally so as to extend from the outer circumference of the anchor ring 5 and consists of an elastic push plate 5a that is brought into pressure contact with the rear surface of the annular bead 4c. The push plate 5a has a circular hole 35 or a U-shaped slit 35' such as shown in Figure 6, which serves as an opening to permit communication between the through-hole 34 and the second working chamber B.
As depicted in Figures 7 and 8, the elastic member C is integrally formed with the outer circumference of the anchor ring 5 so as to extend therefrom. It may be composed of a spring seat 5b disposed so as to oppose the rear surface of the annular bead 4c with a predetermined gap between them and a coiled spring 47 placed under compression between the annular bead 4c and the spring seat 5b. In this case, annular grooves 48, 49 are formed at the support portions of the annular bead 4c and spring seat 5b in order to prevent the spring 47 from falling. The spring seat 5b has a circular hole 35" of a larger diameter through which the tie rod 11 penetrates.
In order to concentrically arrange the throughhole 32 of the booster piston 2, the through-hole 34 of the diaphragm 4 and the openings 35, 35' (Figs. 1,2 and 6) or the circular hole 35" of the spring seat 5b (Figs. 7 and 8) with the tie rods 11, the following locating means are provided at the connecting portions of the front and rear shells 1 A, 1 B of the booster shell 1 , the diaphragm 4, the disc portion 2b and central boss portion 2a of the booster piston 2 and the anchor ring 5.
Namely, as shown in Figure 3, a locating slit 36 and a locating pawl 37, which are engaged with each other, are disposed at the connecting end portions of the front and rear shells 1 A and 1 B, respectively, while a locating slot 38 and a locating projection 39 for engaging with each other are disposed at the connecting portions between the rear shell 1 B and the outer circumferential bead 4b of the diaphragm 4, respectively, as shown in Figure 4. A locating recess 40 and a locating protuberance 41 to be engaged with each other are disposed on the superposed surfaces of the disc portion 2b and the diaphragm 4, respectively, as shown in Figure 1.A semi-circular locating slit 42 is formed on the outer circumference of the flange 3 of the central boss portion 2a as shown in Figure 5 and a locating ring 43 to be engaged with the slit 42 is fitted around the portion of the disc portion 2b encompassing the rear end portion 33b of the bellows. Furthermore, a locating groove 44 and a locating pawl 45 for engaging with each other are disposed at the connecting portions between the central boss portions 2a and the anchor ring 5 as shown in Figure 6. Incidentally, reference numeral 46 represents an elastic anchor pawl for anchoring the anchor ring 5 to the outer circumference of the central boss portion 2a.
In the above-described arrangement, it will now be assumed that a high vacuum pressure is accumulated in the first working chamber A and a large suction force due to the vacuum pressure acts upon the end wall of the front shell 1 A, which has especially low rigidity. This suction force is transmitted to and supported by the support wall W via the clamp plate 1 8 and the tie rods 11.
Moreover, since the end wall of the front shell 1 A is clamped and reinforced by the clamp plate 1 8 and the fitting flange 28 of the master cylinder M, it hardly undergoes inward deformation. Since the clamp plate 1 8 supports the fixed end of the return spring 19, it also transmits the resiliency of the return spring 19 to the tie rods 11 but not to the front shell 1 A.
When the booster piston 2 is operated to advance by the advancing operation of the input rod 7 through the brake pedal 8, the booster piston 2 pushes the operation piston 29 of the master cylinder M forwardly to generate oil pressure inside an oil pressure chamber not shown, thereby actuating the wheel brakes. In this case, the forward push force of the operation piston 29 acts as the forward thrust load upon the cylinder main body 27 of the master cylinder M via the oil pressure. But this load is transmitted to and supported by the support wall W via the fitting flange 28 and the tie rods 11. Accordingly, the booster shell 1 does not bear the load and can be kept from being deformed by the load.
Next, it will be assumed that no vacuum pressure exists in the vacuum supply source and hence, no vacuum pressure is accumulated in the first working chamber A. If the booster piston 2 is pushed forward by advancing the input rod 7, the second working chamber B is cut off its communication with the first working chamber A and is in turn connected to the atmosphere by the control valve (not shown) so that the air inside the first working chamber A is compressed and is about to be discharged towards the vacuum supply source from the vacuum inlet pipe 6.
However, when the pressure inside the chamber B rises and then exceeds a predetermined value due to the discharge resistance, the pressure enters between the superposed surfaces of the disc portion 2b of the booster piston 2 and the diaphragm 4 to form a gap g there, separating the annular bead 4c from the rear end 33b of the bellows 33 against the resilient push force of the push plate 5a (Fig. 2) or the resiliency of the coiled spring 47 (Fig. 7). As a result, the air inside the first working chamber A is easily exhausted into the second working chamber B under the atmospheric pressure through the gap g and the through-hole 34. For this reason, almost no discharge resistance of the air exists in the first working chamber A and hence, the booster piston 2 can be manually operated lightly.
In accordance with the present invention as described above, the anchor ring for fixing the inner circumferential bead of the diaphragm is anchored to the central boss portion of the booster piston, and those surfaces of the disc portion of the booster piston and the diaphragm which are detachably superposed on each other is communicated with the second working chamber via the through-hole of the diaphragm so that the peripheral portion of the through-hole of the diaphragm is pushed towards the disc portion of the booster piston by means of the resiliency of the elastic member.Accordingly, when the booster piston is manually operated under the state where no vacuum pressure is stored in the first working chamber, the air inside the first working chamber compressed by the advance of the booster piston can be discharged into the second working chamber through the throughhole of the diaphragm so that the manual operation can be effected lightly. Since the excessive air pressure is prevented from acting upon the diaphragm in this case, durability of the diaphragm is not damaged. In the ordinary state in which vacuum pressure is accumulated in the first working chamber, the peripheral portion of the through-hole of the diaphragm is pushed to the booster piston by means of the push force of the elastic member, thus enabling a reliable sealing of the through-hole.Hence, unnecessary leakage of the negative pressure from the first working chamber to the second working chamber can be prevented reliably.
If the elastic member is composed of the resilient push plate formed integrally with the anchor ring that is to fix the inner circumferential bead of the diaphragm to the central boss portion of the booster piston, the construction can be simplified without increasing the number of components and assembling operation also becomes easier because the push plate can be set to the predetermined position simultaneously with the fitting of the anchor ring.
Furthermore, if the elastic member is composed of the spring seat fixed to the booster piston inside the second working chamber so as to oppose the peripheral portion of the through-hole of the diaphragm and spring means compressed between the spring seat and the peripheral portion of the through-hole of the diaphragm, the air inside the first working chamber is discharged into the second working chamber through the gap defined between the disc portion of the booster piston and the diaphragm and then through the through-hole of the diaphragm in accordance with the advancing movement of the booster piston during the manual operation thereof, and the peripheral portion of the through-hole of the diaphragm comes away from the booster piston while inclining.In this case, the spring means can be freely deformed in response to the inclination of the diaphragm at any fitting position so that the diaphragm can be reliably removed from the booster piston.
CLAIMS 1. A vacuum booster device comprising: a booster shell; a booster piston axially slidably accommodated in said booster shell and having a disc portion; a diaphragm having an inner circumferential bead coupled in superposition to the rear surface of said disc portion of said booster piston and an outer circumferential bead coupled to the circumferential wall of said booster shell; said booster piston and said diaphragm together dividing the interior of said booster shell into a front side first working chamber communicated with a vacuum supply source and a rear side second working chamber selectively communicated with said first working chamber or to the atmosphere via a control valve operatively connected to an input member; tie rods extending through said booster piston and said diaphragm for connecting the front and rear walls of the said booster shell with each other;; said booster piston having through-holes through which said tie rods penetrate; and seal means disposed in said through-holes of said booster piston for sealing air-tight the space formed between said booster piston and said tie rods; and wherein an elastic member resiliently biases the peripheral portion of a through-hole of said diaphragm towards said disc portion of said booster piston, said diaphragm is at at least portions of said inner and outer circumferential beads thereof normally placed in intimate contact with said disc portion of said booster piston due to the pressure difference between said first and second working chambers, and when the internal pressure of said first working chamber becomes greater than that of said second working chamber, said diaphragm is separated from said disc portion to define a gap therebetween and simultaneously moves the peripheral portion of said through-hole thereof away from said disc portion against resiliency of said elastic member, thereby mutually communicating said first and second working chambers via the gap between said diaphragm and said disc portion and via said through-hole.
2. A device as set forth in Claim 1, wherein an anchor ring for fixing said inner circumferential bead of said diaphragm is anchored to a central boss portion of said booster piston and said elastic member is an elastic push plate integrally formed with said anchor ring.
3. A device as set forth in Claim 2, wherein said through-hole of said diaphragm is defined by an annular bead integral with said diaphragm.
4. A device as set forth in Claim 3, wherein said seal means comprises flexible bellows encompassing said tie rods and having the front end thereof fitted to said tie rods and the rear end thereof fitted into said through-hole of said booster piston, and said annular bead is resiliently pushed to the rear end of said bellows by said push plate.
5. A device as set forth in Claim 2, wherein said booster piston is provided with a locating groove formed on the outer circumference of said central boss portion thereof, and said anchor ring is provided with a locating pawl for engaging with said locating groove.
6. A device as set forth in Claim 2, wherein said push plate has an opening portion allowing communication between said through-hole of said diaphragm and said second working chamber.
7. A device as set forth in Claim 1 , wherein said elastic member comprises a spring seat fixed to said booster piston inside said second working chamber so as to face the peripheral portion of said through-hole of said diaphragm and spring means compressed between said spring seat and the peripheral portion of said through-hole of said diaphragm.
8. A device as set forth in Claim 7, wherein an anchor ring is disposed for coupling said inner circumferential bead of said diaphragm to said booster piston, and said spring seat is formed integrally with said anchor ring.
9. A vacuum booster device substantially as hereinbefore described with reference to Figures 1 to 6 or Figures 7 and 8 of the accompanying drawings.
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (1)

  1. **WARNING** start of CLMS field may overlap end of DESC **.
    4. A device as set forth in Claim 3, wherein said seal means comprises flexible bellows encompassing said tie rods and having the front end thereof fitted to said tie rods and the rear end thereof fitted into said through-hole of said booster piston, and said annular bead is resiliently pushed to the rear end of said bellows by said push plate.
    5. A device as set forth in Claim 2, wherein said booster piston is provided with a locating groove formed on the outer circumference of said central boss portion thereof, and said anchor ring is provided with a locating pawl for engaging with said locating groove.
    6. A device as set forth in Claim 2, wherein said push plate has an opening portion allowing communication between said through-hole of said diaphragm and said second working chamber.
    7. A device as set forth in Claim 1 , wherein said elastic member comprises a spring seat fixed to said booster piston inside said second working chamber so as to face the peripheral portion of said through-hole of said diaphragm and spring means compressed between said spring seat and the peripheral portion of said through-hole of said diaphragm.
    8. A device as set forth in Claim 7, wherein an anchor ring is disposed for coupling said inner circumferential bead of said diaphragm to said booster piston, and said spring seat is formed integrally with said anchor ring.
    9. A vacuum booster device substantially as hereinbefore described with reference to Figures 1 to 6 or Figures 7 and 8 of the accompanying drawings.
GB08215969A 1981-06-19 1982-06-01 Spot brake Expired GB2100814B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB08215969A GB2100814B (en) 1981-06-19 1982-06-01 Spot brake

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB8119065 1981-06-19
GB08215969A GB2100814B (en) 1981-06-19 1982-06-01 Spot brake

Publications (2)

Publication Number Publication Date
GB2100814A true GB2100814A (en) 1983-01-06
GB2100814B GB2100814B (en) 1984-12-19

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
GB08215969A Expired GB2100814B (en) 1981-06-19 1982-06-01 Spot brake

Country Status (1)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0143934A1 (en) * 1983-10-05 1985-06-12 Gustav Magenwirth GmbH &amp; Co. Hydraulic bicycle rim brake
EP0219938A1 (en) * 1985-08-30 1987-04-29 Ti Interlock Limited Brake device
AU659534B2 (en) * 1992-02-14 1995-05-18 Warner Electric Technology, Inc. Fluid operated brake device
GB2304837A (en) * 1995-09-07 1997-03-26 Automotive Products Plc A disc brake caliper arrangement

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0143934A1 (en) * 1983-10-05 1985-06-12 Gustav Magenwirth GmbH &amp; Co. Hydraulic bicycle rim brake
EP0219938A1 (en) * 1985-08-30 1987-04-29 Ti Interlock Limited Brake device
US4782922A (en) * 1985-08-30 1988-11-08 Ti Interlock Limited Brake device
AU659534B2 (en) * 1992-02-14 1995-05-18 Warner Electric Technology, Inc. Fluid operated brake device
GB2304837A (en) * 1995-09-07 1997-03-26 Automotive Products Plc A disc brake caliper arrangement

Also Published As

Publication number Publication date
GB2100814B (en) 1984-12-19

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Legal Events

Date Code Title Description
PCNP Patent ceased through non-payment of renewal fee