CN1206079A - Disk brake device - Google Patents
Disk brake device Download PDFInfo
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- CN1206079A CN1206079A CN 98116356 CN98116356A CN1206079A CN 1206079 A CN1206079 A CN 1206079A CN 98116356 CN98116356 CN 98116356 CN 98116356 A CN98116356 A CN 98116356A CN 1206079 A CN1206079 A CN 1206079A
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- 238000006073 displacement reaction Methods 0.000 claims description 9
- 238000005299 abrasion Methods 0.000 abstract 1
- 238000000034 method Methods 0.000 description 11
- 210000003127 knee Anatomy 0.000 description 5
- 230000000694 effects Effects 0.000 description 3
- 239000011796 hollow space material Substances 0.000 description 3
- 238000012856 packing Methods 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 210000001138 tear Anatomy 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
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Abstract
A disk brake device includes a brake bar 3A which applies the incline force to the device during operation. A stopper 58 is formed on the lower end of the brake bar 3A and extends to the outside, a regulate bolt 56 is vertically screwed into the stopper 58. A base 59 is disposed on the bottom plate 1 and under the stopper. A pinion 61 is jointed on the top of the regulate bolt 56 by a one-way clutch 60 so as to rotate the regulate bolt 56 in the direction of fastening the bolt downwards. A rack 67 is supported by the bottom plate and engaged with the pinion to get a predetermined backlash, and extends in one swing direction of the brake bars 3A, 3B. When the disk brake is under the release status, even the brake linings 9A, 9B are abrades, an automatic brake lining regulate device 53 can regulate the brake to reduce the clearance caused by the abrasion of the brake linings 9A, 9B, the brake bars 3A, 3B can be insured at the same open position in the left and right.
Description
The present invention relates to a kind of common engineering machinery that is used for as the disk brake device on the winch.Prior art
A kind of general industrial disk brake device mechanically that is used for has been shown in JP-A-07229527.Be described with reference to appended Fig. 9 to 20 pair of so a kind of disk brake device below.
As shown in FIG., a pair of vertical braking bar 3A and 3B are arranged on the base plate 1 relative to one another, so that their ground, back that is positioned at another is on the axial D1 of vertical rotation brake puck 2, this rolling brake disk 2 is between bar 3A and 3B.The bottom of brake rod 3A and 3B pivotally is installed on a pair of mounting 4A and 4B on the base plate 1 by the horizontal axis 5A that radially extends from brake puck 2 and 5B, so that open in the vertical plane that the upper end of brake rod 3A and 3B can be extended on the axial D1 of brake puck 2 or close.
When with Fig. 9 during as a front view, each brake rod 3A and 3B form by paired header board and back plate, and this paired header board and back plate are connected with each other by a connecting rod 6A or 6B at an upper portion thereof.
Each brake rod 3A and 3B in the top and the intermediate portion between the lower end all have a horizontal axis 7A or a 7B, this horizontal axis 7A or 7B and axle 5A and 5B parallels and be on the level height with one 11 of brake puck 2 basically.Braking shoes 8A and 8B can rotate around axle 7A and 7B, so that they are laid respectively between the header board and back plate of forming brake rod 3A and 3B.Braking shoes 8A and 8B have surfaces opposite to each other, are coated with brake bush 9A and 9B on this surface respectively, so that clamp and braking brake puck 2 from relative both sides.
A 3A in the brake rod has the pivot 13 parallel with 5B with axle 5A on the part near its upper end.Pivot 13 extends through brake rod 3A and further extends rod 3A on its thickness direction.
The barrel-type casing 26 of a vertical hollow is its lower end is articulated in mounting 24 on the base plate 1 by a horizontal axis 25 that parallels with axle 5A and 5B on.By the hollow space 27 of this housing 26, the loam cake 28 of the upper end of vertical bar 29 by being installed in this housing 26 stretches out, and this bar 29 can be moved up and down.Spring 31 is housed in housing 26, and spring 31 is at loam cake 28 and be installed between the base 30 on the lower end of bar 29 so that bar 29 always is pushed downwards.
The sleeve 41 of hollow integrally is connected on the end of the sleeve 40 adjacent with brake rod 3A, and this sleeve 41 loosely is installed on the outer periphery of axle 37, so that sleeve 41 aligns with sleeve 40.Female thread 41a on the interior periphery of the external screw thread 37a on the outer periphery of axle 37 and sleeve 41 is meshed.
Threaded 42 is installed on the end away from the sleeve 41 of sleeve 40, and this threaded 42 comprises male screw portion 42a, major diameter part 42b, with part 42b adjacent small diameter portion 42c and with the part 42c adjacent male screw portion 42d adjacent with part 42a.Part 42a is screwed in the sleeve 41, and part 42b, 42c and 42d stretch out from sleeve 41 on the direction of leaving sleeve 40.
Overrunning clutch 48 is enclosed within on the small diameter portion 42c of threaded 42, and in its side adjacent with male screw portion 42d a distance piece 49 is installed.The nut 50 that is screwed on the male screw portion 42d prevents that overrunning clutch 48 and distance piece 49 are from the last slippage of the part 42c of threaded 42.
Overrunning clutch 48 can adopt the overrunning clutch of type known in the state of the art, it comprises interior ring 48a on the part 42c that directly is enclosed within threaded 42, be enclosed within outer shroud 48b and a plurality of roller 48c between ring 48a and 48b on the ring 48a.By the rotation of roller 48c on the circumference that encircles 48a and 48b, outer shroud 48b can rotate along circumference in one direction, and because roller 48c and the wedge bond of encircling 48a and 48b can prevent the direction rotation that outer shroud 48b is opposite in the circumference upper edge.
The cylinder stop ring 51 of hollow extends through quarter butt 15, so that stop ring 51 and axle 13 are parallel and can rotate with respect to quarter butt 15.Joining pin 52 extends radially and insert the hollow space 51a of stop ring 51 at its top from the outer shroud 48b of overrunning clutch 48.
The diameter of joining pin 52 be substantially stop ring 51 hollow space 51a internal diameter 1/3.When brake bush 9A and 9B were not worn, bar 14,15 and 16 swings around pivot 13 can not cause that joining pin 52 is promoted by the interior periphery of stop ring 51, and joining pin 52 can be maintained at horizontal position, shown in Figure 13 and 14.
Yet.When brake bush 9A and 9B were worn, bar 16,14 and 15 can be swung manyly, and joining pin 52 is promoted up or down by the interior periphery of stop ring 51, shown in Figure 15 and 16.
The design of overrunning clutch 48 should make that when joining pin 52 is pushed upwardly only outer shroud 48b rotates, and when joining pin 52 was pushed down, outer shroud 48b was by locking.
Therefore, connection set 34 comprises axle 37, sleeve 40 and 41 and threaded 42; Automatic wear compensation device 53 then comprises overrunning clutch 48, joining pin 52 and stop ring 51.
In the accompanying drawings, reference number 54 is represented spring pin, and this spring pin is along the radially extension of sleeve 41 and threaded 42, and sleeve 41 connected and is fixed on the threaded 42.
In above-mentioned disk brake device, when propulsion device 20 is activated when moving up bar 21, a power that makes progress is applied on the knee 16 by top 22 and axle 23.Therefore, in the process of the downward thrust of resisting spring 31 as shown in Figure 11, knee 16 is swung clockwise around pivot 13 on a direction a shown in Figure 9. Quarter butt 14 and 15 is also together swung around pivot 13 and bar 16 on this direction a clockwise.
Thus, the axle 43 of strut rail 44 is clockwise rotated by quarter butt 14 and 15 drives on direction a shown in Figure 9, makes strut rail 44 promote the axle 37 of connection sets 34 by cover 45,40 and 41 at direction b upper edge axle shown in Figure 12 12.This makes brake rod 3A and 3B open in the top.Brake rod 3B centers on an axle 5B counter-clockwise swing on direction c shown in Figure 9, and brake rod 3A centers on an axle 5A counter-clockwise swing on a direction e shown in Figure 9.The lower end surface that is connected to the adjustment bolt 10A of stopper 11A on the upper surface of base 12A and 12B and 11B and 10B defines the final open position of brake rod 3A and 3B, on make brake rod 3A and 3B stop at them the position that similarly opens on the left side and the right respectively.Therefore, the brake bush 9A of braking shoes 8A and 8B and braking surface that 9B leaves brake puck 2 and the braking of take-off the brake disk 2.
On the other hand, when propulsion device 20 was not activated, bar 16 was subjected to axle 13 counter-clockwise swings of effect in Fig. 9 of the downward thrust of spring 31, and bar 21 is moved down by axle 23.The counter-clockwise swing of the bar 16 among Fig. 9 causes quarter butt 14 and 15 also around axle 13 counter-clockwise swings, as shown in figure 12, connection set 34 is ended along the axis 12 of axle 37 and cover 40,41 and 45 in direction be pulled.Opposite with above-mentioned opening operation, this makes brake rod 3A and 3B be incorporated into together in the top.Thus, brake bush 9A and the 9B of braking shoes 8A and 8B contact with the braking surface of brake puck 2.Brake puck 2 is clamped with braking brake puck 2 from opposite end by brake bush 9A and 9B.
Interrelate with the release or the braking of 2 brakings of above-mentioned brake puck, the bar 14,15 among Fig. 9 and 16 clockwise or counter-clockwise swing so that the stop ring 51 on quarter butt 15 also move downward or upward.
When brake bush 9A and 9B are not worn, flatly and from the joining pin 52 that the outer shroud 48b radially outward of overrunning clutch 48 stretches out do not promoted by the interior periphery of stop ring 51.Therefore, shown in Figure 13 and 14, joining pin 52 is maintained at horizontal position, and automatic wear compensation device 53 is inoperative.
Yet, as brake bush 9A with 9B is worn and propulsion device 20 when not being activated, brake rod 3A and 3B under axle 5A and the 5B situation when not being worn than brake bush 9A and 9B bigger amplitude towards brake puck 2 swings.Then, each in the bar 14,15 and 16 increases around the oscillating quantity of pivot 13 swings.
For this reason, be not activated and under the situation of braking, bar 14,15 and 16 moves down with respect to pivot 13 towards propulsion device 20 sides with it, and moves up with respect to pivot 13 towards overrunning clutch 48 sides with it at propulsion device 20.Therefore, engage with joining pin 52 on the outer shroud 48b that is installed to overrunning clutch 48, the top of pin 52 is pushed upwardly, as shown in figure 15 in the minimum point on the interior periphery that is installed to the stop ring 51 on the quarter butt 15.
Therefore, outer shroud 48b is with respect to interior ring 48a counter-clockwise swing on direction g, and as shown in figure 15, and joining pin 52 tilts with respect to the center generation of the small diameter portion 42c of threaded 42.In this case, interior ring 48a does not produce swing.
On the other hand, when propulsion device 20 was activated with take-off the brake, bar 14,15 and 16 was swung clockwise around pivot 13, and as shown in Figure 9, the end that bar 15 has stop ring 51 moves down.
As a result, joining pin 52 is promoted downwards by the peak on the interior periphery of stop ring 51; But the outer shroud 48b of overrunning clutch 48 can not be with respect to interior ring 48a swing, and ring 48a and 48b be h and i swing along clockwise direction integrally, as shown in figure 16.
The integral body swing of ring 48a and 48b causes threaded 42 to be swung with identical direction with sleeve 40,41, so that the female thread of sleeve 40 is with respect to the external screw thread 37a rotation of axle 37.This makes axle 37 axially move and be drawn into sleeve 40 and 41 on the D2.Therefore, along the axis 12 of axle 37, the distance L (Fig. 9) between the center of axle 43 the center of strut rail 44 and the axle 35 of strut rail 36, promptly the effective length of connection set 34 is shortened, the gap that is produced by the wearing and tearing of brake bush 9A and 9B with automatic reduction.
Therefore, according to aforesaid disk brake device, the gap that is produced by the wearing and tearing of brake bush 9A and 9B can be reduced by automatic wear compensation device 53 continuous stepless ground, so that can access constant braking force all the time.
In aforesaid disk brake device, braking is by opening brake rod 3A in the upper end of brake rod 3A and 3B and 3B discharges, and the state of brake rod 3A and 3B is kept by the support of the lower end of the adjustment bolt 10A of stopper 11A on the upper surface that is positioned at base 12A and 12B and 11B and 10B.Therefore, when the effective length of connection set in opening operation 34 is shortened by automatic wear compensation device 53, and when the final open position of brake rod 3A and 3B closer shifted to brake puck 2, between the upper surface of the lower end of adjusting bolt 10A and 10B and base 12A and 12B, formed extra gap.Therefore because the downward force unbalance effect of spring 31, might brake rod 3A and 3B integral body tilt towards brake rod 3A.
Or rather, under an initial setting braking release situation as shown in figure 17, wherein brake bush 9A and 9B wearing and tearing as yet must be adjusted bolt 10A and 10B, so that thickness is T
AAnd T
B(T
A=T
B) brake bush 9A and the 9B clearance G that is equivalent to the effective stroke of propulsion device 20 (Fig. 9) respectively with brake puck 2 at interval
AAnd G
B, and on the left side and the right same open (G
A=G
B).In this case, when having set up clearance G
AAnd G
BAfterwards, adjust bolt 10A and 10B so that the upper surface of its following end in contact base 12A and 12B.
Therefore, under initial setting braking condition as shown in figure 18, brake bush 9A closely contacts brake puck 2 with 9B, and on the left side and the right similarly form gap S between the upper surface of the lower end of adjusting bolt 10A and 10B and base 12A and 12B respectively
AAnd S
B(S
A=S
B).
When disk brake device is is similarly worn and torn at brake bush 9A and 9B on the left side and the right, wear extent is △ T
AWith △ T
B(△ T
A=△ T
B) situation under when being used to carry out braking, adjust gap between the upper surface of the lower end of bolt 10A and 10B and base 12A and 12B because wear extent △ T
AWith △ T
BWith inclination amount △ S
AWith △ S
BAnd increased inclination amount △ S wherein
AWith △ S
BThe amount that to be brake rod 3A and 3B tilt towards brake puck 2, corresponding to from the center of axle 5A and 5B to the length H of the bar at the center of axle 7A and 7B, and changed into S respectively
A+ △ S
AAnd S
B+ △ S
B
On the other hand, when brake bush 9A and 9B were worn, automatic wear compensation device 53 was regulated connection sets 34 so that reduce distance L (effective length) between the axle 35 and 43.Under the situation that the distance L between axle 35 and 43 is lowered, the effective stroke of propulsion device 20 is identical with initial setting basically, so that discharge brake bush 9A under the situation of braking and the clearance G between 9B and the brake puck 2 when brake bush 9A and 9B are worn
A 'And G
B '(G
A '=G
B ') substantially with clearance G as shown in Figure 17 under initial setting
AAnd G
B(G
A '=G
AG
B '=G
B) identical.For this reason, even when braking is released, between the upper surface of the lower end of adjusting bolt 10A and 10B and base 12A and 12B, also maintain gap △ S
AWith △ S
BThe downward unbalanced force of spring 31 will cause that brake rod 3A and 3B tilt towards brake rod 3A around axle 5A and 5B, as shown in Figure 20.The lower end of adjusting bolt 10A contacts with the upper surface of base 12A, and the gap between the upper surface of the lower end of adjustment bolt 10A and base 12B is increased to △ S
A+ △ S
BG is changed in gap between brake bush 9A and 9B and the brake puck 2 respectively into
A+ △ G and G
B-△ G becomes uneven.
Therefore, even when carrying out when regulating with automatic wear compensation device 53 as described above with the gap that reduces automatically to produce by the wearing and tearing of brake bush 9A and 9B, if the protrusion amount of bolt 10A and 10B of adjusting is not regulated, so when braking is released, the clearance G between brake bush 9B and the brake puck 2
B-△ G just changes zero into, and G is changed in the gap between brake bush 9A and the brake puck 2
A+ G
B, so that brake bush 9B contacts brake puck 2 lopsidedly or obliquely, this is very disadvantageous.
In such disk brake device, when opening brake rod 3A and 3B in the top and during take-off the brake, brake rod 3A and 3B balance no longer on the position is unless the lower end supporting surface of the adjustment bolt 10A of stopper 11A or 11B or 10B is resisted against on the upper surface of base 12A or 12B.Therefore, correctly design philosophy is downward the thrust uneven or biasing towards brake rod 3A that makes spring 31, preferably makes the lower end abutment of adjusting bolt 10A on the upper surface of base 12A, to be stabilized in brake rod 3A under the non-braking state and the action of 3B.In example shown in the drawings, adopt common design to make the downward Driving force of spring 31 tilt towards the brake rod 3A that leaves propulsion device 20.
Yet under the position that changes spring 31, leverage 55 isostructural situations, the downward thrust of spring 31 can be setovered towards brake rod 3B.
The present invention aims to provide a kind of disk brake device, this disk brake device comprises and being arranged opposite to each other to clamp and to brake a pair of brake rod of the disk of a vertical rotation by brake bush from opposite end that described brake rod lower end can be rotated so that open or the brake puck that closes its upper end relative to base plate; This disk brake device also comprises the leverage on the upper end that is supported in this brake rod one rotationally; Be used for the connection set that the upper end with the part of this leverage and another brake rod couples together; Be used for the part of this leverage is upwards promoted so that the propulsion device that open the upper end of brake rod; Be used for when propulsion device is not activated the part of this leverage is promoted downwards so that the spring of the upper end closure of brake rod; And be used for according to the relative displacement of leverage and connection set corresponding to the wearing and tearing of brake bush automatic wear compensation device with the effective length that shortens connection set.The problem that the present invention emphasized is when braking discharges, even when the brake bush wearing and tearing, also guarantees brake rod is remained on the position of the left side and the right similarly opening reliably, and the gap that is produced by the wearing and tearing of brake bush is reduced automatically by the automatic wear compensation device.
This problem is solved in the following manner, in the opening operation of brake rod, make in its downward-sloping brake rod by the effect of spring force, have outwardly directed stopper in its underpart, this stopper has an adjustment bolt of vertically twisting within it; Base plate with base also is provided, this base be positioned at described stopper under, be used to receive a lower end of described adjustment bolt, described adjustment bolt has a small gear, this small gear is assembled to the upper end of this adjustment bolt by overrunning clutch, only can rotate on the direction of a downward clamping bolt so that adjust bolt; One tooth bar also is provided, and this tooth bar is meshed with described gear having a predetermined backlash, on a direction of the swing of brake rod, extend, and by backplanes support.
Therefore, when leverage is upwards promoted when opening the brake rod upper end by propulsion device, the brake bush of brake rod separates with brake puck and discharges braking.When propulsion device was not activated, with the brake rod closure, brake bush then clamped and brakes brake puck to leverage by spring promotion downwards.
As mentioned above, in the braking release or brake operation course of brake puck, the swing of brake rod makes the small gear of stopper move with respect to fixing tooth bar.When brake bush was not worn, the amount of each brake rod swing all was normal, and the size permission small gear of backlash and the relative displacement of tooth bar and small gear are retained as and do not rotate.
On the other hand, when brake bush weares and teares, the oscillating quantity of each brake rod increase and by the automatic wear compensation device according to the effective length that shortens connection set corresponding to the relative displacement of the wear extent leverage of brake bush and connection set.Therefore, the gap that is formed by the wearing and tearing of brake bush has automatically been reduced.Simultaneously, the relative displacement between small gear and the tooth bar has surpassed the backlash that between is provided with, and small gear then back and forth rotates with respect to tooth bar, so that adjusts bolt and only rotate off and on direction it is fastening downwards by overrunning clutch.Adjusting bolt moves down with the gap between the upper surface of the lower end that reduces to adjust bolt and base with respect to stopper.
By reducing to adjust the gap between bolt lower end and the base upper surface, the oscillating quantity of brake rod is lowered, and this oscillating quantity limits by adjusting the support of bolt lower end on base upper surface, and small gear also is lowered with respect to the amount of movement of tooth bar.When this rate of travel becomes when equaling backlash, small gear stops operating, and the oscillating quantity of brake rod becomes the oscillating quantity before the brake bush wearing and tearing.Therefore, the gap between the lower end of adjustment bolt and the upper surface of base is being carried out in the closing operation process of brake rod by spring, automatically changes back to brake bush wearing and tearing value before.
In a word, the gap that has automatically reduced to be produced by the wearing and tearing of brake bush even the effective length of brake bush wearing and tearing and connection set has been shortened by automatic brake bush wear adjustment device, the gap in the closing operation of brake rod between the upper surface of the lower end of adjustment bolt and base can automatically turn back to the size of the initial setting before the brake rod wearing and tearing.Therefore, the moving by the lower end abutment of adjusting bolt of brake rod that applies downward Driving force in opening operation thereon limits on the upper surface of base to guarantee that positively brake rod on the left side and the right are in identical open position.And, under brake release state, can prevent from brake puck, to apply the pressure of deflection, to guarantee at any time can to obtain best braking maneuver by brake bush.
With reference to the accompanying drawings to indefiniteness embodiment's of the present invention description, can more be expressly understood the present invention by following, accompanying drawing comprises:
Brief description
Fig. 1 is the front view of one embodiment of the present of invention;
Fig. 2 is the perspective view of being done along the direction II-II among Fig. 1;
Fig. 3 is a side view, shows gear and the relation of the mutual alignment between the tooth bar that one shown in Fig. 1 adjusts bolt;
Fig. 4 is a sectional view, shows to adjust the details of bolt along one of direction IV-IV shown in Fig. 3;
Fig. 5 is the operational instruction figure of small gear in the braking process before brake bush wearing and tearing;
Fig. 6 is the operational instruction figure that braked small gear in the releasing course before the brake bush wearing and tearing;
Fig. 7 is the operational instruction figure of small gear in the braking process after brake bush wearing and tearing;
Fig. 8 is the operational instruction figure that brakes small gear in the releasing course after the brake bush wearing and tearing;
Fig. 9 is the front view of prior-art devices;
Figure 10 is the sectional view that the device shown in Fig. 9 is done along direction X-X;
Figure 11 is the sectional view that the concrete layout of spring shown in Fig. 9 is shown.
Figure 12 illustrates the sectional view along the details of the automatic wear compensation device of XII-XII direction shown in Fig. 9;
Figure 13 is the automatic wear compensation device explanatory drawing in the braking process before the brake bush wearing and tearing;
Figure 14 is the automatic wear compensation device explanatory drawing in the braking releasing course before the brake bush wearing and tearing;
Figure 15 is the operational instruction figure of the automatic wear compensation device in the braking process after the brake bush wearing and tearing;
Figure 16 is the operational instruction figure that brakes the automatic wear compensation device in the releasing course after the brake bush wearing and tearing;
Figure 17 is the operational instruction figure of each brake rod in the braking process before the brake bush wearing and tearing;
Figure 18 is the operational instruction figure of each brake rod in the braking releasing course before the brake bush wearing and tearing;
Figure 19 is the operational instruction figure of each brake rod in the braking process after the brake bush wearing and tearing;
Figure 20 is the operational instruction figure that brakes each brake rod in the releasing course after the brake bush wearing and tearing.
Embodiment
Fig. 1 to Fig. 8 shows one embodiment of the present of invention, wherein with Fig. 9 to Figure 20 in identical parts represent by identical reference number.
In this embodiment, in opening operation, make the lower end of its downward-sloping brake rod 3A form outwardly directed stopper 58 by the elastic force of spring 31, the male screw portion 56b that adjusts bolt 56 vertically is screwed in it by thread bush 57.Base 59 is set on base plate 1, this base 59 be positioned at stopper 58 under so that accept to adjust a lower end of bolt 56.
As shown in Figure 4, adjusting bolt 56 upper ends has a small diameter portion 56a, and small gear 61 only can rotate it one so that adjust bolt 56 by overrunning clutch 60 assemblings thereon on the downward fastening direction.Small gear 61 is remained on therebetween from the above and below rotationally by a distance ring 63 and a thrust washer 64, and this distance ring 63 and thrust washer 64 is along adjusting the axially separated from one another by a ring 62 that is enclosed within on the small diameter portion 56a of the inside that is positioned at overrunning clutch 60 of bolts 56.Utilize set screw nut 65 to prevent small gear 61 slippages.
Overrunning clutch 60 can have identical substantially structure with the overrunning clutch 48 of automatic wear compensation device 53, as above description with reference to accompanying drawing 12.
Backlash W is set to such size, and brake rod 3A has normal oscillating quantity when brake bush 9A does not wear and tear so that allow, unless produce wearing and tearing on brake bush 9A, small gear 61 can not rotate with respect to tooth bar 67.
Compare very for a short time in the oscillating quantity of brake rod 3A lower end with the oscillating quantity of its upper end, and can equate with the aforesaid backlash W that can between small gear 61 and tooth bar 67, set.
When the leverage 55 that includes knee 16 and quarter butt 14,15 is upwards promoted when opening brake rod 3A and 3B upper end by propulsion device 20, the brake bush 9A of brake rod 3A and 3B separates with brake puck 2 with 9B, with take-off the brake.When propulsion device 20 was not activated, leverage 55 was promoted downwards by spring 31 and brake rod 3A and 3B is closed, and brake bush 9A and 9B clamp and braking brake puck 2.
As mentioned above, in the braking release or braking process on brake puck 2, the swing of brake rod 3A makes the small gear 61 of stopper 58 produce with respect to fixing tooth bar 67 and relatively moves.For example, in the brake operating that does not start propulsion device 20, small gear 61 moves towards the left side, as shown in Figure 5.Under the braking releasing orientation that propulsion device 20 is activated, small gear 61 returns mobile towards the right, as shown in Figure 6.Under the normal oscillating quantity of brake rod 3A when brake bush 9A is not worn, the relative displacement of small gear 61 and tooth bar 67 is held by backlash W and small gear 61 remains not rotary state.
On the other hand, when brake bush 9A and 9B wearing and tearing, the oscillating quantity of each brake rod 3A and 3B increases, and shorten the effective length (distance L) of connection sets 34 corresponding to the wear extent of brake bush 9A and 9B by automatic wear compensation device 53 according to the relative displacement of leverage 55 and connection set 34, so that the gap that is produced by the wearing and tearing of brake bush 9A and 9B reduces automatically.Simultaneously, the relative displacement of small gear 61 and tooth bar 67 has also surpassed the backlash W that between is provided with, and for example, under the braking state that propulsion device 20 is not activated, brake rod 3A swings towards brake puck 2 around axle 5A, its swing degree is big when not being worn than brake bush 9A, so that small gear 61 moves and clockwise rotates along a direction j with respect to tooth bar 67 to position shown in Figure 7.
In this case, suppose that the fastening direction of the adjustment bolt 56 among Fig. 7 is clockwise, small gear 61 is driven with respect to adjusting bolt 56 idle running by overrunning clutch 60.Under the brake release state that propulsion device 20 is activated, when small gear 61 moved back to displacement shown in Figure 8, small gear 61 and adjustment bolt 56 were driven by overrunning clutch 60 and together clockwise rotate on direction k and l, are tightened down so that adjust bolt 56.
As mentioned above, small gear 61 back and forth rotates with respect to tooth bar 67, and adjusts bolt 56 and only rotated off and on by overrunning clutch 60 drives on its downward fastening direction.Therefore, adjusting bolt 56 moves down with the gap between the upper surface of the lower end that reduces to adjust bolt 56 and base 59 with respect to stopper 58.
Under the situation that reduces in the gap between the upper surface of the lower end of adjusting bolt 56 and base 59, oscillating quantity by the brake rod 3A that support limited of lower end on the upper surface of base 59 that adjusts bolt 56 is reduced, and small gear 61 also is reduced with respect to moving of tooth bar 67.When such rate of travel becomes when equaling backlash, small gear 61 stops operating, and the oscillating quantity of brake rod 3A becomes the oscillating quantity before the brake bush 9A wearing and tearing.Therefore, in the closed procedure of brake rod 3A that is promoted by spring 31 and 3B, the gap between the lower end of adjustment bolt 56 and the upper surface of base 59 is automatically become again brake bush 9A wearing and tearing value before.
Therefore, according to present embodiment, as brake bush 9A with 9B is worn and shorten the effective length (distance L) of connection sets 34 and when reducing the gap that wearing and tearing produced by brake bush 9A and 9B automatically by automatic wear compensation device 53, adjust gap between the upper surface of the lower end of bolt 56 and base 59 and in the closed procedure of brake rod 3A and 3B, can automatically be changed back to initial setting up value before brake bush 9A and the 9B wearing and tearing.Therefore, the moving by the support of lower end on the upper surface of base 59 of adjusting bolt 56 of brake rod 3A that has downward Driving force to apply thereon in opening operation limits to guarantee that brake rod 3A and 3B on the left side and the right can similarly be opened.And, under brake release state, can prevent to be applied to the pressure of the deflection on the brake puck 2, thereby guarantee at any time can realize best braking by brake bush 9A or 9B.
Should be understood that the present invention is not limited to above-mentioned most preferred embodiment, can also make various changes and modifications present embodiment.For example, can adopt with illustrated embodiment in structure multiple structure and parts different with parts be used for the automatic wear compensation device.The structure of leverage and shape also are not limited to structure shown in the embodiment and shape.
The reference number explanation
1 base plate
2 brake pucks
The 3A brake bar
The 3B brake bar
The 9A brake bush
The 9B brake bush
20 propellers
31 springs
34 jockeys
53 automatic wear compensation devices
55 leverages
56 adjust bolt
58 retainers
59 bases
60 one-way clutch
61 pinions
67 tooth bars
Claims (1)
1. disk brake device comprises:
A pair of being arranged opposite to each other to pass through brake bush (9A from two opposite ends, 9B) clamp and brake the brake rod (3A of the brake puck (2) of a vertical rotation, 3B), and described brake rod (3A, 3B) lower end can be rotated so that open in the top or the brake puck that closes (2) relative to base plate (1);
Be supported on the leverage (55) on the upper end of brake rod (3A) rotationally;
The connection set (34) that the part of leverage (55) is connected with the upper end of another brake rod (3B);
This part of leverage (55) is upwards promoted to open brake rod (3A, the propulsion device of upper end 3B) (20);
Be used for propulsion device (20) when not being activated the part of leverage (55) promoted downwards with brake rod (3A, upper end 3B) is with brake rod (3A, 3B) Bi He spring (31); With
Be used for according to the relative displacement of leverage (55) and connection set (34) corresponding to brake bush (9A, wearing and tearing 9B) and shorten the automatic wear compensation device of the effective length of connection set (34);
It is characterized in that,
(3A in opening operation 3B), makes its downward-sloping brake rod (3A) lower end be formed with outwardly directed stopper (58) by the elastic force of spring (31), adjusts bolt (56) and vertically is screwed in it at brake rod;
Described base plate (1) has base (59), this base (59) be positioned at described stopper (58) under, be used to accept the lower end of described adjustment bolt (56);
Described adjustment bolt (56) has a small gear (61), this small gear (61) is sleeved on the upper end of described adjustment bolt (56) by overrunning clutch (60), so that described adjustment bolt (56) only can rotate on the direction of downward fastening described bolt; With
Tooth bar (67), this tooth bar (67) are meshed with described small gear (61) to have a predetermined backlash, and (3A extends on swaying direction 3B) this tooth bar (67), and is supported by base plate (1) at brake rod.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 98116356 CN1206079A (en) | 1997-07-23 | 1998-07-22 | Disk brake device |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP09196995/97 | 1997-07-23 | ||
| CN 98116356 CN1206079A (en) | 1997-07-23 | 1998-07-22 | Disk brake device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1206079A true CN1206079A (en) | 1999-01-27 |
Family
ID=5225027
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 98116356 Pending CN1206079A (en) | 1997-07-23 | 1998-07-22 | Disk brake device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1206079A (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100383428C (en) * | 2005-12-22 | 2008-04-23 | 江苏恒力制动器制造有限公司 | Double thrust disc and double regulating caliper type pneumatic brake device capable of self-regulating braking clearance |
| CN100423896C (en) * | 2003-07-04 | 2008-10-08 | Chr.迈尔有限公司及两合公司 | Rack and pinion gear with brake unit |
| CN100593648C (en) * | 2005-05-25 | 2010-03-10 | 克诺尔商用车制动系统有限公司 | Pneumatically and/or electromechanically operable disc brake for a utility vehicle |
| CN102770682A (en) * | 2010-02-02 | 2012-11-07 | 克诺尔-布里姆斯轨道车辆系统有限公司 | Pressure rod adjuster with threaded part mounted directly on the adjuster housing for compact brake caliper units |
| CN103597237A (en) * | 2011-06-09 | 2014-02-19 | 北京京西重工有限公司 | Pivot pad brake caliper |
| CN104632945A (en) * | 2015-02-06 | 2015-05-20 | 焦作市制动器开发有限公司 | Novel arm disc type brake |
| CN107076232A (en) * | 2014-09-17 | 2017-08-18 | 克诺尔商用车制动系统有限公司 | Disk brake for commercial car |
| CN108953421A (en) * | 2018-06-04 | 2018-12-07 | 深圳市南硕明泰科技有限公司 | A kind of symmetrical reducing type compensation brake system |
| CN111442041A (en) * | 2019-01-16 | 2020-07-24 | 庆昌产业株式会社 | Self-excited brake caliper |
| CN115720612A (en) * | 2020-04-24 | 2023-02-28 | 伏尔甘度巴西有限公司 | Electric hydraulic disc brake |
-
1998
- 1998-07-22 CN CN 98116356 patent/CN1206079A/en active Pending
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100423896C (en) * | 2003-07-04 | 2008-10-08 | Chr.迈尔有限公司及两合公司 | Rack and pinion gear with brake unit |
| CN100593648C (en) * | 2005-05-25 | 2010-03-10 | 克诺尔商用车制动系统有限公司 | Pneumatically and/or electromechanically operable disc brake for a utility vehicle |
| CN100383428C (en) * | 2005-12-22 | 2008-04-23 | 江苏恒力制动器制造有限公司 | Double thrust disc and double regulating caliper type pneumatic brake device capable of self-regulating braking clearance |
| CN102770682B (en) * | 2010-02-02 | 2016-01-06 | 克诺尔-布里姆斯轨道车辆系统有限公司 | Wear adjusters for calipers of rail vehicle disc brakes and disc brakes |
| CN102770682A (en) * | 2010-02-02 | 2012-11-07 | 克诺尔-布里姆斯轨道车辆系统有限公司 | Pressure rod adjuster with threaded part mounted directly on the adjuster housing for compact brake caliper units |
| US9416829B2 (en) | 2011-06-09 | 2016-08-16 | Beijingwest Industries Co. Ltd. | Pivot pad brake caliper |
| CN103597237B (en) * | 2011-06-09 | 2015-11-25 | 北京京西重工有限公司 | Rotary Disc Brake Caliper |
| CN103597237A (en) * | 2011-06-09 | 2014-02-19 | 北京京西重工有限公司 | Pivot pad brake caliper |
| CN107076232A (en) * | 2014-09-17 | 2017-08-18 | 克诺尔商用车制动系统有限公司 | Disk brake for commercial car |
| CN107076232B (en) * | 2014-09-17 | 2020-02-14 | 克诺尔商用车制动系统有限公司 | Disk brake for a commercial vehicle |
| US10718394B2 (en) | 2014-09-17 | 2020-07-21 | Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh | Disk brake for a utility vehicle |
| CN104632945A (en) * | 2015-02-06 | 2015-05-20 | 焦作市制动器开发有限公司 | Novel arm disc type brake |
| CN108953421A (en) * | 2018-06-04 | 2018-12-07 | 深圳市南硕明泰科技有限公司 | A kind of symmetrical reducing type compensation brake system |
| CN111442041A (en) * | 2019-01-16 | 2020-07-24 | 庆昌产业株式会社 | Self-excited brake caliper |
| CN111442041B (en) * | 2019-01-16 | 2021-09-10 | 庆昌产业株式会社 | Self-excited brake caliper |
| CN115720612A (en) * | 2020-04-24 | 2023-02-28 | 伏尔甘度巴西有限公司 | Electric hydraulic disc brake |
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