CN114483826A - Push type brake and rotary workbench using same - Google Patents

Push type brake and rotary workbench using same Download PDF

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Publication number
CN114483826A
CN114483826A CN202011266186.7A CN202011266186A CN114483826A CN 114483826 A CN114483826 A CN 114483826A CN 202011266186 A CN202011266186 A CN 202011266186A CN 114483826 A CN114483826 A CN 114483826A
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CN
China
Prior art keywords
brake
braking
brake disc
piston
housing
Prior art date
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Pending
Application number
CN202011266186.7A
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Chinese (zh)
Inventor
卓文恒
张耀仁
张宇荣
李俊霖
黄立文
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Hiwin Technologies Corp
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Hiwin Technologies Corp
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Priority to CN202011266186.7A priority Critical patent/CN114483826A/en
Publication of CN114483826A publication Critical patent/CN114483826A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0033—Fully-enclosing housings
    • 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
    • F16D2121/04—Fluid pressure acting on a piston-type actuator, e.g. for liquid pressure

Abstract

The invention provides a thrust brake, which comprises an annular shell, wherein a brake disc, a brake piston, a plurality of brake parts and a brake release piston are arranged in the annular shell. When only the brake piston receives fluid action, axial thrust can be exerted on the brake disc, the brake disc is kept at a braking position under the combined action of the brake piston and the braking elements, when only the brake piston is released, reverse thrust can be exerted on the brake disc, the brake disc is kept at the brake releasing position, once the fluid action received by the brake piston fails, the brake disc can still generate a braking effect through the acting force of the braking elements, so that the safety of the operation process is improved, in addition, the thrust type brake is in a modular design, and the convenience of assembly and disassembly can be improved. In addition, the invention also provides a rotary worktable using the push type brake.

Description

Push type brake and rotary workbench using same
Technical Field
The present invention relates to a brake device, and more particularly, to a thrust brake and a rotary table using the same.
Background
In order to prevent the rotating shaft from rotating after machining, a set of brakes is usually configured to apply braking force to the stationary rotating shaft, so that the rotating shaft is kept stable in a stationary state. However, the conventional brake cannot provide braking force for the rotating shaft under special conditions (such as power failure without warning or broken pipeline), which not only easily causes damage to the machine tool, but also may endanger the safety of surrounding personnel.
Under the conditions of shutdown or standby, etc., the normally closed hydraulic brake device disclosed in CN 210024594U utilizes the elastic forces of multiple springs to urge the piston to press down, so as to make the brake device in a hugging state and lock the spindle, thereby preventing the spindle from rotating. When the brake is released, the hydraulic oil is used for reversely pushing the piston, so that the brake device is in a released state, and the main shaft can normally run at the moment. However, in the above-mentioned patent documents, the whole device lacks a modular design, the relevant parts need to be assembled individually, and therefore it is rather inconvenient in terms of maintenance and adjustment, and the braking force provided by means of a plurality of springs alone is very limited, and it is difficult to adapt to a spindle of a large size.
The dividing plate disclosed in TW M359398 uses the spindle of the pneumatic cylinder to push the hydraulic oil in the oil chamber, so that the hydraulic oil enters between the piston chassis and the piston plate through the oil path, and further pushes the piston plate and the large brake disc to generate axial displacement, so that the large brake disc and the small brake disc are in frictional contact, thereby limiting the rotation of the main shaft and the disc surface. On the contrary, when the mandrel of the pneumatic cylinder is retracted, the front end surface of the piston disc is propped against by the elastic components, so that the large brake disc is separated from the small brake disc, and the main shaft and the disc surface can rotate. However, in the above patent documents, the whole device also lacks a modular design, and the related parts need to be assembled separately, so it is inconvenient in maintenance and adjustment, and in addition, the large brake disk and the small brake disk use the elastic restoring force of a plurality of elastic components to achieve the braking releasing effect, but the elastic components may be subjected to elastic fatigue after a period of use, so that the large brake disk and the small brake disk are not separated and a part of the large brake disk and the small brake disk still keep contact, so that the problem of abrasion may occur.
Disclosure of Invention
The invention mainly aims to provide a thrust brake which can achieve the effect of normally closed braking so as to improve the safety in operation and has the advantage of modularization.
To achieve the above objective, the thrust brake of the present invention comprises an annular housing, a brake disc, a brake piston, a brake release piston, and a plurality of braking members. The brake disc is arranged in the annular shell and can move between a braking position and a braking releasing position, and the brake disc is provided with a first surface and a second surface back to the first surface; the brake piston is arranged in the annular shell and is abutted against the first surface of the brake disc, and can apply a first axial thrust to the brake disc under the action of a first fluid; the braking-releasing piston is arranged in the annular shell and is abutted against the second surface of the brake disc, and can apply second axial thrust to the brake disc under the action of second fluid; the braking elements are arranged in the annular shell and are positioned on the same side of the brake disc with the brake piston so as to constantly apply third axial thrust to the brake disc.
In view of the above, when the brake piston is not acted by the first fluid and the brake release piston is not acted by the second fluid, a third axial thrust exerted by the braking elements on the brake disc holds the brake disc in the braking position, when the brake piston is acted upon by the first fluid but the de-brake piston is not acted upon by the second fluid, the first axial thrust applied to the brake disc by the brake piston and the third axial thrust applied to the brake disc by the brake elements jointly hold the brake disc in the braking position, when the brake piston is not acted upon by the first fluid but the de-brake piston is acted upon by the second fluid, the second axial thrust applied to the brake disc by the brake-releasing piston overcomes the third axial thrust applied to the brake disc by the braking elements to hold the brake disc in the braking-releasing position. In other words, the thrust brake of the present invention utilizes the design of the brake piston and the brake release piston, and only the first fluid and the second fluid are respectively introduced into the brake piston and the brake release piston, so that the brake disc can generate the braking effect and the brake release effect.
Optionally, the first surface of the brake disc has a positioning convex portion, one side of the brake piston facing the brake disc has a positioning concave portion, and the positioning convex portion of the brake disc is embedded in the positioning concave portion of the brake piston, so that the position of the brake disc can be fixed.
Optionally, the annular housing has a first housing and a second housing disposed on the first housing, the braking piston and the braking elements are disposed in the first housing, the braking-releasing piston is disposed in the second housing, and the brake disc is disposed between the first housing and the second housing.
Optionally, the first housing has a first ring groove for receiving the brake piston and a first fluid inlet hole communicating with the first ring groove, the first fluid reaching the first ring groove from the first fluid inlet hole and then applying a force to the brake piston, and the second housing has a second ring groove for receiving the unbraker piston and a second fluid inlet hole communicating with the second ring groove, the second fluid reaching the second ring groove from the second fluid inlet hole and then applying a force to the unbraker piston.
Optionally, a side of the first housing facing the second housing further has a plurality of first receiving grooves surrounding the first ring groove, the first surface of the brake disc has a plurality of second receiving grooves, and the braking element is disposed between one of the first receiving grooves and one of the second receiving grooves that are opposite to each other.
Optionally, each of the braking members is a compression spring or is formed of a first magnet and a second magnet. If the first axial pushing force is formed by the elastic force generated by each braking member, if the second axial pushing force is formed by the elastic force generated by each braking member, and if the second axial pushing force is formed by each braking member, the opposite ends of the first magnet and the second magnet have opposite polarities, so that the magnetic repulsion force generated by the first magnet and the second magnet forms the third axial pushing force.
In addition, the invention also provides a rotary workbench using the thrust brake, which comprises a machine table, a rotating shaft and a working disc. The rotating shaft is rotatably arranged through the machine table and is connected with the working disc through the front end of the rotating shaft, and the outer peripheral surface of the front end of the rotating shaft is provided with a convex ring part; the thrust brake is locked on the machine table by the annular shell and is penetrated by the front end of the rotating shaft, when the brake disc is located at the braking position, the brake disc is pressed against the convex ring part of the rotating shaft, so that the rotating shaft generates a braking effect, and when the brake disc is located at the braking position, the brake disc is far away from the convex ring part of the rotating shaft, so that a gap is generated between the brake disc and the convex ring part.
Therefore, the thrust brake is in a modular design, does not need to be fixed with the rotating shaft, can improve the assembly convenience, and can be conveniently detached from the machine table for adjustment and maintenance.
Optionally, the protruding ring portion of the rotating shaft is locked with a braking plate, the inner periphery of the braking disc is provided with a braking portion, and when the braking disc is located at the braking position, the braking disc is pressed against the braking plate by the braking portion.
Optionally, when the annular housing is assembled to the machine platform, the brake disc is held at the braking-off position by the fourth axial thrust, so as to protect contact surfaces of the annular housing and the machine platform from being damaged due to mutual collision.
Optionally, an air passage is formed inside the rotating shaft, and when the annular housing is assembled to the machine, air is filled into the air passage, so that the air applies the fourth axial thrust to the brake disc.
The detailed structure, characteristics, assembly or use of the thrust brake and the rotary table using the same according to the present invention will be described in the following detailed description of the embodiments. However, it should be understood by those skilled in the art that the detailed description and specific examples, while indicating the specific embodiment of the invention, are intended for purposes of illustration only and are not intended to limit the scope of the invention.
Drawings
Fig. 1 is a perspective view of a thrust brake of embodiment 1 of the present invention;
fig. 2 is an exploded perspective view of a thrust brake according to embodiment 1 of the present invention;
FIG. 3 is an end view of the thrust brake of embodiment 1 of the present invention;
FIG. 4 is a cross-sectional view taken along line 4-4 of FIG. 3;
FIG. 5 is a cross-sectional view taken along line 5-5 of FIG. 3;
FIG. 6 is a cross-sectional view taken along line 6-6 of FIG. 3;
fig. 7 is a perspective view of a rotary table to which a thrust brake of embodiment 1 of the present invention is applied;
FIG. 8 is a partial exploded perspective view of FIG. 7;
fig. 9 is a partial sectional view of a rotary table to which a thrust brake of embodiment 1 of the present invention is applied, mainly showing a brake disc in a braking position;
FIG. 10 is a view similar to FIG. 9, and primarily showing the brake rotor in an unbraked position;
fig. 11 is an exploded perspective view of a thrust brake of embodiment 2 of the present invention;
fig. 12 is a sectional view of a thrust brake of embodiment 2 of the invention;
fig. 13 is a partial cross-sectional view of a rotary table to which a thrust brake of embodiment 2 of the present invention is applied, mainly showing a brake disk in a braking position;
FIG. 14 is an illustration as in FIG. 13, showing primarily the brake rotor in a de-braking position;
fig. 15 is a partial sectional view of a rotary table to which a thrust brake of embodiment 1 of the present invention is applied, mainly showing gas applying a fourth axial thrust to a brake disc.
The reference numbers illustrate:
10-a thrust brake; 12-a first fluid; 14-a second fluid; 20-an annular housing; 22-a screw; 30-a first housing; 32-a first shaft hole; 34-a first ring groove; 36-a first vessel; 38-a first fluid input aperture; 40-a second housing; 42-second shaft hole; 44-a second ring groove; 46-a second fluid input aperture; 50-a brake disc; 51-a first surface; 52-a second surface; 53-positioning protrusions; 54-a second vessel; 55-a brake part; p1-braking position; p2-brake release position; 60-a brake piston; 62-a positioning recess; 64-brake release piston; 66-a stop member; 70-rotating the worktable; 71-a machine table; 72-a rotating shaft; 74-a collar portion; 75-a working plate; 76-brake plate; 77-screw; 78-the airway; 80-a brake member; 82-a first magnet; 84-a second magnet; f1 — first axial thrust; f2 — second axial thrust; f3-third axial thrust; f4-fourth axial thrust.
Detailed Description
Applicants first describe herein, throughout this specification, including the examples and claims that follow, directional terms are used with respect to the drawings. Next, in the embodiments and the drawings to be described below, the same component numbers denote the same or similar components or structural features thereof.
Referring to fig. 1 and 2, a thrust brake 10 according to embodiment 1 of the present invention includes an annular housing 20, a brake disc 50, a brake piston 60, a brake release piston 64, and a plurality of braking elements 66.
The annular housing 20 has a first shell 30 and a second shell 40, and the first shell 30 and the second shell 40 are fastened together by screws 22. The first shell 30 has a first shaft hole 32 penetrating through the inner and outer side surfaces, as shown in fig. 2 and 3, the inner side surface of the first shell 30 (i.e. the side surface facing the second shell 40) has a first ring groove 34 surrounding the first shaft hole 32 and a plurality of first accommodating grooves 36 (here, 16, but not limited thereto) surrounding the first ring groove 34; the second housing 40 has a second shaft hole 42 penetrating through the inner and outer sides, the second shaft hole 42 communicating with the first shaft hole 32, the second shaft hole 42 having a larger diameter than the first shaft hole 32, and the inner side of the second housing 40 (i.e., the side facing the first housing 30) having a second ring groove 44 surrounding the second shaft hole 42. In addition, as shown in fig. 2 and 5, the first casing 30 has a first fluid inlet hole 38 communicating with the first annular groove 34 on the outer periphery thereof, and as shown in fig. 2 and 6, the second casing 40 has a second fluid inlet hole 46 communicating with the second annular groove 44 on the outer periphery thereof.
The brake disc 50 is disposed between the first casing 30 and the second casing 40 and has a first surface 51 facing the first casing 30 and a second surface 52 facing the second casing 40, wherein the first surface 51 has an annular positioning protrusion 53 and a plurality of second receiving grooves 54 (16 in this case, but not limited thereto) surrounding the positioning protrusion 53. Further, the brake disk 50 has a braking portion 55 on the inner peripheral edge thereof, and the braking portion 55 of the brake disk 50 protrudes from the second shaft hole 42 in the radial direction of the second shaft hole 42 (as shown in fig. 4).
The brake piston 60 is embedded in the first annular groove 34 of the first housing 30 and abuts against the first surface 51 of the brake disc 50, and when the first fluid 12 (here, gas, although liquid may be used, but not limited to gas) is introduced into the first fluid inlet hole 38, as shown in fig. 5, the brake piston 60 is acted by the first fluid 12 to apply a first axial thrust F1 to the brake disc 50. In addition, the inner side surface of the brake piston 60 (i.e., the side surface facing the brake disk 50) has a positioning concave portion 62, and the brake piston 60 is fitted to the positioning convex portion 53 of the brake disk 50 with the positioning concave portion 62 so that the two can maintain a fixed relative position.
The unbraking piston 64 is embedded in the second annular groove 44 of the second housing 40 and adjacent to the second surface 52 of the brake disc 50, and when the second fluid 14 (here, gas, although liquid may be used, and not limited to gas) is introduced into the second fluid inlet hole 46, as shown in fig. 6, the unbraking piston 64 is acted by the second fluid 14 to apply a second axial thrust F2 to the brake disc 50.
Each stop 66 is a compression spring in this embodiment. The braking elements 66 are disposed between the first receiving grooves 36 and the second receiving grooves 54 in a one-to-one manner, as shown in fig. 2 and 4, one end of each braking element 66 abuts against the end wall of the first receiving groove 36, and the other end abuts against the end wall of the second receiving groove 54, so that the braking elements 66 apply a third axial thrust F3 to the brake disc 50 by their own elastic force.
Referring to fig. 7 and 8, a rotary table 70 is shown, which includes a table 71, a shaft 72 and a working plate 75. The rotating shaft 72 is rotatably disposed through the machine base 71 and connected to the working plate 75 at a front end thereof, so that the rotating shaft 72 can drive the working plate 75 to rotate together with a workpiece (not shown) to be processed fixed on the working plate 75 under the driving of a power source (such as a motor) disposed in the machine base 71, thereby processing the workpiece to be processed. In addition, as shown in fig. 9 and 10, the front end of the rotating shaft 72 has a protruding ring portion 74, and the rotating shaft 72 is locked with a braking plate 76 for receiving the braking disc 50 at the protruding ring portion 74.
When the thrust brake 10 of the present invention is used in conjunction with the rotary table 70, the working disc 75 is first removed, the annular housing 20 is then sleeved on the front end of the rotating shaft 72, the annular housing 20 and the machine table 71 are locked together by the screws 77, and finally the working disc 75 is reinstalled, so that the assembly of the thrust brake 10 of the present invention is completed.
In actual operation, the first fluid 12 is introduced into the first fluid inlet 38 (as shown in fig. 5), so that the brake piston 60 applies the first axial thrust F1 to the brake disc 50 under the action of the first fluid 12, and the braking elements 66 apply the third axial thrust F3 to the brake disc 50 constantly by using their own elastic force, so that the first axial thrust F1 applied to the brake disc 50 by the brake piston 60 and the third axial thrust F3 applied to the brake disc 50 by the braking elements 66 will hold the brake disc 50 at the braking position P1 shown in fig. 9, and the brake disc 50 will press the braking plate 76 by the braking portion 55, and since the braking plate 76 is fixed with the raised ring portion 74 of the rotating shaft 72, the rotating shaft 72 can generate a braking effect.
It should be added that, in order to make the brake disc 50 provide complete braking force to the rotating shaft 72, when the brake disc 50 is located at the braking position P1 shown in fig. 9, the first axial thrust F1 needs to be greater than or equal to the third axial thrust F3, and further, the following relations are satisfied between the first axial thrust F1 and the third axial thrust F3, where F3 ≦ F1, and F1 ≦ a1 xf 1, where a1 is the area (in mm) of the brake piston 60 (in mm)2) F1 is the force provided by the first fluid 12 to the brake piston 60 (assumed here to be 0.6N/mm)2)。
On the contrary, if the rotating shaft 72 is allowed to operate normally, the first fluid 12 is stopped from flowing into the first fluid inlet hole 38, so as to release the first axial thrust F1 applied to the brake disc 50 by the brake piston 60, the second fluid 14 is then introduced into the second fluid inlet 46 (as shown in fig. 6), such that the de-brake piston 64 applies a second axial thrust F2 to the brake disc 50 under the action of the second fluid 14, and since the brakes 66 still apply a third axial thrust F3 to the brake disc 50, when the second axial thrust F2 applied to the brake disc 50 by the brake release piston 64 overcomes the third axial thrust F3 applied to the brake disc 50 by the braking members 66, the brake disc 50 is maintained at the braking release position P2 shown in fig. 10, and the braking portion 55 of the brake disc 50 is separated from the braking plate 76 to generate a gap therebetween, so that the rotating shaft 72 can operate normally.
It should be added that when the brake disc 50 is located at the braking release position P2 shown in fig. 10, the second axial thrust F2 needs to be greater than the third axial thrust F3, and further, the relationship between the two is F3<F2, F2 ═ a2 xf 2, where a2 is the area (in mm) of the unbraking piston 642) F2 is the force provided by the second fluid 14 to the de-brake piston 64 (assumed here to be 0.6N/mm)2) When the safety factor ρ is set to 1.2, the above formula may be further modified so that F3 × ρ is F2 is a2 × F2, and then F2 is 0.6 and ρ is 1.2, which are substituted into the modified formula, thereby obtaining the safety factor ρ of 1.2
Figure BDA0002776199340000071
The relational expression (c) of (c).
In case of failure of the first fluid 12 and the second fluid 14 due to a special condition (e.g. no power failure or broken pipeline), although the brake piston 60 cannot apply the first axial thrust F1 to the brake disc 50, the brake disc 50 can still be maintained at the braking position P1 shown in fig. 9 by the third axial thrust F3 provided by the braking elements 66, so that the rotating shaft 72 can achieve the effect of safe shutdown. In other words, under normal conditions, the brake piston 60 and the braking elements 66 provide complete braking force to the brake disc 50, so that the brake disc 50 is reliably kept at the braking position P1 shown in fig. 9, and if the brake piston 60 and the brake release piston 64 fail, the braking force provided by the braking elements 66 can still keep the brake disc 50 at the braking position P1 shown in fig. 9, thereby achieving the effect of normally closed braking, and further improving the safety of operation.
On the other hand, instead of using the elastic force as the third axial pushing force F3, the stopper may use the magnetic repulsive force as the third axial pushing force F3. More specifically, as shown in fig. 11 and 12, each braking member 80 is composed of a first magnet 82 and a second magnet 84, the first magnet 82 is disposed in the first accommodating groove 36 of the first housing 30, the second magnet 84 is disposed in the second accommodating groove 54 of the brake disc 50, and the opposite ends of the first magnet 82 and the second magnet 84 have opposite polarities, so that the magnetic repulsion generated between the first magnet 82 and the second magnet 84 forms the third axial pushing force.
Thereby, when the first fluid 12 is introduced into the first fluid inlet hole 38, the first axial thrust F1 applied to the brake disc 50 by the brake piston 60 and the third axial thrust F3 applied to the brake disc 50 by the braking elements 80 will jointly hold the brake disc 50 at the braking position P1 shown in fig. 13, so that the brake disc 50 provides a braking effect on the rotating shaft 72.
On the contrary, if the rotating shaft 72 is allowed to normally operate, the first fluid 12 is firstly stopped to be introduced into the first fluid inlet hole 38 to release the first axial thrust F1 applied to the brake disc 50 by the brake piston 60, and then the second fluid 14 is introduced into the second fluid inlet hole 46 to allow the brake piston 64 to apply the second axial thrust F2 to the brake disc 50 under the action of the second fluid 14, and since the braking elements 80 still apply the third axial thrust F3 to the brake disc 50, when the second axial thrust F2 applied to the brake disc 50 by the brake piston 64 overcomes the third axial thrust F3 applied to the brake disc 50 by the braking elements 80, the brake disc 50 can be pushed to the brake release position P2 shown in fig. 14, so that the rotating shaft 72 normally operates.
In case of failure of the supply of the first fluid 12 and the second fluid 14 due to a special condition (such as no power failure or broken pipeline), the braking disc 50 can still be kept in the braking position P1 shown in fig. 13 by the third axial thrust F3 provided by the braking elements 80, so as to achieve the effect of normally closed braking.
Finally, it should be added that, no matter which braking elements 66 and 80 are used, in order to protect the contact surface between the brake disc 50 and the rotating shaft 72 from being damaged due to mutual collision when the thrust brake 10 of the present invention is assembled on the machine platform 71, the fourth axial thrust F4 may be applied to the brake disc 50 during the assembly process, so that the brake disc 50 is maintained at the braking release position P2 shown in fig. 15 until the assembly is completed. The fourth axial thrust F4 can be provided by the braking-off piston 64, or a gas passage 78 can be formed inside the rotating shaft 72, as shown in fig. 15, and then the gas passage 78 is filled with gas, so that the gas forms a gas curtain at the contact surface of the two and provides the fourth axial thrust F4 at the same time.
As described above, in the thrust brake 10 of the present invention, the brake piston 60 and the brake release piston 64 are designed such that the brake disc 50 can generate the braking effect and the brake release effect by only passing the first fluid 12 and the second fluid 14 through the brake piston 60 and the brake release piston 64, respectively. In addition, in the event of failure of the brake piston 60, by the design of the braking elements 66 and 80, partial braking force can still be provided to the brake disc 50, so that the brake disc 50 is kept at the braking position P1, so as to achieve the effect of normally closed braking, thereby improving the safety in operation. In addition, the thrust brake 10 of the present invention is designed in a modularized manner, and when the thrust brake is used in cooperation with the rotary worktable 70, the thrust brake does not need to be fixed with the rotating shaft 72, so that the assembly convenience can be improved, and in addition, the whole thrust brake 10 can be conveniently detached from the machine table 71, so as to be convenient for adjustment and maintenance.

Claims (10)

1. A thrust brake, comprising:
an annular housing;
the brake disc is movably arranged in the annular shell between a braking position and a braking releasing position and is provided with a first surface and a second surface back to the first surface;
the brake piston is arranged in the annular shell, abuts against the first surface of the brake disc and can apply a first axial thrust to the brake disc under the action of a first fluid;
the braking-off piston is arranged in the annular shell and is adjacent to the second surface of the braking disc, and can apply a second axial thrust to the braking disc under the action of a second fluid; and
the braking parts are arranged in the annular shell and are positioned on the same side of the braking disc with the braking piston, and the braking parts are used for constantly applying a third axial thrust to the braking disc;
wherein, when the brake piston is not acted by the first fluid and the brake release piston is not acted by the second fluid, a third axial thrust exerted by the braking elements on the brake disc holds the brake disc in the braking position, when the brake piston is acted upon by the first fluid and the de-brake piston is not acted upon by the second fluid, the first axial thrust applied to the brake disc by the brake piston and the third axial thrust applied to the brake disc by the brake elements jointly hold the brake disc in the braking position, when the brake piston is not acted on by the first fluid and the brake release piston is acted on by the second fluid, the second axial thrust applied to the brake disc by the brake-releasing piston overcomes the third axial thrust applied to the brake disc by the braking elements to hold the brake disc in the braking-releasing position.
2. The thrust brake of claim 1, wherein the first surface of the brake disc has a positioning protrusion, the brake piston has a positioning recess on a side facing the brake disc, and the positioning protrusion of the brake disc is fitted into the positioning recess of the brake piston.
3. The thrust brake of claim 1, wherein said annular housing has a first housing and a second housing disposed in said first housing, said brake piston and said braking members being disposed in said first housing, said brake release piston being disposed in said second housing, said brake disc being disposed between said first housing and said second housing.
4. The thrust brake of claim 3, wherein a side of the first housing facing the second housing has a first annular groove in which the brake piston is disposed, and the outer periphery of the first housing has a first fluid inlet hole communicating with the first annular groove, a side of the second housing facing the first housing has a second annular groove in which the brake piston is disposed, and the outer periphery of the second housing has a second fluid inlet hole communicating with the second annular groove.
5. The thrust brake of claim 4, wherein said first housing further has a plurality of first receiving grooves surrounding said first ring groove on a side surface facing said second housing, said first surface of said brake disc has a plurality of second receiving grooves, each of said braking members is a compression spring and is received in one of said first receiving grooves, one end of each of said braking members abuts against an end wall of one of said first receiving grooves, and the other end of each of said braking members abuts against an end wall of one of said second receiving grooves, such that said elastic force generated by each of said braking members forms said third axial thrust.
6. The push-type brake of claim 4, wherein the first housing further has a plurality of first receiving grooves surrounding the first ring groove on a side surface of the second housing, the first surface of the brake disc has a plurality of second receiving grooves, each of the braking members has a first magnet and a second magnet, the first magnet is disposed in the first receiving groove, the second magnet is disposed in the second receiving groove, and opposite ends of the first magnet and the second magnet have opposite polarities, such that the magnetic repulsion force generated between the first magnet and the second magnet forms the third axial pushing force.
7. A rotary table, comprising:
a machine table;
the rotating shaft is rotatably arranged in the machine table in a penetrating way, and the outer peripheral surface of the rotating shaft is provided with a convex ring part;
a working disk connected with the front end of the rotating shaft to make the working disk rotate synchronously with the rotating shaft; and
the thrust brake of any one of claims 1 to 6, wherein the annular housing is disposed on the machine platform and penetrated by a front end of the rotating shaft, when the brake disc is located at the braking position, the brake disc is pressed against the protruding ring portion of the rotating shaft, and when the brake disc is located at the braking release position, the brake disc is away from the protruding ring portion of the rotating shaft, so that a gap is formed between the brake disc and the protruding ring portion of the rotating shaft.
8. The rotary worktable of claim 7, wherein the raised ring of the rotating shaft is locked with a braking plate, and the inner periphery of the braking plate has a braking portion, so that when the braking plate is at the braking position, the braking plate is pressed against the braking plate by the braking portion.
9. The rotary worktable of claim 7 or 8, wherein the brake disc is held in the braking-released position by a fourth axial thrust when the annular casing is assembled to the machine.
10. The rotary worktable according to claim 9, wherein the rotating shaft has an air passage therein, and when the annular casing is assembled to the worktable, the air passage is filled with a gas so that the gas applies the fourth axial thrust to the brake disk.
CN202011266186.7A 2020-11-13 2020-11-13 Push type brake and rotary workbench using same Pending CN114483826A (en)

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4263991A (en) * 1977-05-27 1981-04-28 Lambert Brake Company Combined failsafe and service brake
CN101033783A (en) * 2006-03-08 2007-09-12 哈尔德克斯制动产品股份公司 Disk brake
DE102007053325A1 (en) * 2007-11-08 2009-05-20 Agco Gmbh Brake mechanism i.e. wet brake, for use in tractor, has service brake piston chamber exerting pushing force on annular piston in same direction as immobilizing force to press fixed and rotating brake disks against each other to apply brake
CN104114395A (en) * 2012-01-03 2014-10-22 Pmppro-Mec股份公司 Motor-reducer with integrated brake and inverter for direct transmission to the wheel of an electrically driven vehicle
CN104884844A (en) * 2012-12-19 2015-09-02 泛博制动国际有限公司 Planet carrier for an electromechanical actuator of a parking brake, actuator and assembly methods
WO2016101072A1 (en) * 2014-12-27 2016-06-30 Kinetics Drive Solutions Inc. Improved cooling system for multi-disc brake assembly

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4263991A (en) * 1977-05-27 1981-04-28 Lambert Brake Company Combined failsafe and service brake
CN101033783A (en) * 2006-03-08 2007-09-12 哈尔德克斯制动产品股份公司 Disk brake
DE102007053325A1 (en) * 2007-11-08 2009-05-20 Agco Gmbh Brake mechanism i.e. wet brake, for use in tractor, has service brake piston chamber exerting pushing force on annular piston in same direction as immobilizing force to press fixed and rotating brake disks against each other to apply brake
CN104114395A (en) * 2012-01-03 2014-10-22 Pmppro-Mec股份公司 Motor-reducer with integrated brake and inverter for direct transmission to the wheel of an electrically driven vehicle
CN104884844A (en) * 2012-12-19 2015-09-02 泛博制动国际有限公司 Planet carrier for an electromechanical actuator of a parking brake, actuator and assembly methods
WO2016101072A1 (en) * 2014-12-27 2016-06-30 Kinetics Drive Solutions Inc. Improved cooling system for multi-disc brake assembly

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