CN109667854B - friction brake - Google Patents
friction brake Download PDFInfo
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- CN109667854B CN109667854B CN201811560885.5A CN201811560885A CN109667854B CN 109667854 B CN109667854 B CN 109667854B CN 201811560885 A CN201811560885 A CN 201811560885A CN 109667854 B CN109667854 B CN 109667854B
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- friction
- elastic component
- steel sheet
- plate
- driving cylinder
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- 229910000831 Steel Inorganic materials 0.000 claims abstract description 101
- 239000010959 steel Substances 0.000 claims abstract description 101
- 230000008859 change Effects 0.000 claims description 8
- 238000006073 displacement reaction Methods 0.000 claims description 8
- 230000005540 biological transmission Effects 0.000 claims description 6
- 230000000712 assembly Effects 0.000 claims 1
- 238000000429 assembly Methods 0.000 claims 1
- 230000009471 action Effects 0.000 description 11
- 230000006872 improvement Effects 0.000 description 8
- 230000004308 accommodation Effects 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000007547 defect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000000758 substrate Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
- F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
- F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/02—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
- F16D65/095—Pivots or supporting members therefor
- F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2121/00—Type of actuator operation force
- F16D2121/02—Fluid pressure
- F16D2121/04—Fluid pressure acting on a piston-type actuator, e.g. for liquid pressure
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
The invention relates to a friction brake, comprising a mounting seat for connecting with equipment; the driving cylinder body and the piston are arranged in the mounting seat, and a pressure source inlet is formed in the driving cylinder body and the piston; the friction assembly is arranged between the driving cylinder body and the hollow through shaft tube and positioned at one end of the piston, the friction assembly comprises a friction plate connected to the driving cylinder body, a friction steel plate connected to the hollow through shaft tube, and a gap is reserved between the friction plate and the friction steel plate in a relative arrangement; the first elastic component and the second elastic component are arranged on two sides of the friction plate, the first elastic component is fixed on the mounting seat, the second elastic component is fixed on the driving cylinder body, and the friction plates of the first elastic component and the second elastic component are balanced in stress so as to limit the friction plate; the third elastic component and the fourth elastic component are arranged on two sides of the friction steel sheet and are fixed on the hollow through shaft tube, and the third elastic component and the fourth elastic component enable the friction steel sheet to be stressed and balanced so as to limit the friction steel sheet.
Description
Technical Field
The invention relates to the field of brakes, in particular to a friction brake.
Background
Referring to fig. 1, a prior art friction brake is schematically illustrated. Fig. 2 is an enlarged schematic view of the portion a in fig. 1 under normal operation. Fig. 3 and 4 are enlarged schematic diagrams of two types of false brakes in the centrifugal force working condition of the portion a in fig. 1. As shown in fig. 1, a multi-disc normally closed friction brake for industrial transmission field on the market now comprises: the mounting substrate 10a and the mounting side plate 11a are connected to a mounting bracket or a device by bolts to fix the friction brake. The driving cylinder 20a connected to the mounting base plate 10a by bolts and the piston 30a provided in the driving cylinder 20a, the piston 30a and the driving cylinder 20a being combined to form a cylinder form. The driving cylinder 20a is provided with a pressure source inlet and a pressure source outlet.
The friction assembly 40a is provided at one end of the driving cylinder 20a, and the friction assembly 40a is composed of a friction plate 410a, a friction steel plate 420a and a return spring 430 a. The friction component transmits torque by pressing the friction plate and the friction steel plate against each other. The drive cylinder 20a is connected to the friction plate 410a of the friction pack 40a by a spline on which the friction pack 40a can slide in the axial direction.
A driving spring 50a connected to the piston 30a, the driving spring 50a being disposed opposite to the friction member 40 a. The driving spring 50a is provided with a plurality of holes for mounting the driving spring 50a, and driving force is provided to the piston 30a through the driving spring 50 a.
The hollow through shaft tube 60a provided inside the driving cylinder 20a and connected to the friction assembly 40a is externally machined with a spline, and the hollow through shaft tube 60a is connected with the friction steel sheet 420a of the friction assembly 40a through the spline. The hollow through shaft tube 60a forms a space for installation of a transmission power shaft, which is inserted into the hollow through shaft tube 60a and connected to the driving cylinder 20a through a flat key.
The principle of the friction brake is as follows: after the friction brake is fixedly mounted to the apparatus, the transmission power shaft is mounted into the hollow through shaft tube 60a while the friction brake is in a braking state.
When a pressure source (such as compressed air and pressure oil) is introduced from a pressure source inlet and outlet of the driving cylinder 20a, the driving cylinder 20a is limited and fixed, so that the piston 30a in the driving cylinder 20a can only be forced to move to the right in the axial direction, after the piston 30a is pushed, the friction plate 410a in the friction assembly 40a can be separated from the friction steel plate 420a under the action of the return spring 430a, the braking state is relieved, and the hollow through shaft tube 60a rotates freely along with the transmission power shaft. When the pressure source is unloaded from the inlet and outlet of the driving cylinder 20a, the piston 30a moves axially leftwards under the action of the driving spring 50a, compresses the friction assembly 40a, and restores the braking state.
Referring to fig. 2, under normal working conditions, the theoretical distribution states of the friction plate 410a and the friction steel plate 420a of the friction assembly 40a under the condition of opening the brake are that the gaps between adjacent plates are uniform, and the adjacent plates are not contacted with each other, so that no friction moment exists. Therefore, the brake is not problematic to use under normal working conditions, and is also a very mature product in the market.
However, when a brake is selected for a centrifuge device under certain special working conditions, the action direction is almost universal according to the device due to the centrifugal force. Unlike the brake in the normal operation condition, the brake is kept in the off state, i.e., the friction plate 410a and the friction steel plate 420a are kept in the off state without being in contact with each other.
As shown in connection with fig. 3 and 4, the direction of centrifugal force is simulated from right to left. As shown in fig. 3, under a special condition, if the centrifugal force is large enough to exceed the spring deformation force of the return spring 430a, the friction plate 410a and the friction steel plate 420a move along the spline and are mutually pressed, and the mistaken combination is generated to cause mistaken braking, so that equipment and personnel are damaged.
As shown in fig. 4, if the spring deformation force can overcome the centrifugal force, the centrifugal force borne by the friction plates 410a is in a superposition state, so that a non-uniform gap is generated between the friction plates 410a and the right side of the friction steel plate 4210a, and since the return spring is not arranged between the friction steel plates 420a, the left side of the friction steel plate 420a is tightly attached to the friction plates 410a, and the false brake is caused by the false combination, so that equipment and personnel are endangered.
Disclosure of Invention
The invention aims to overcome the defects of the prior art, provides a friction brake and solves the problem that the friction plate and the friction steel sheet are easy to be combined by mistake under the action of centrifugal force to cause the false braking of the brake in the prior art.
The technical scheme for achieving the purpose is as follows:
the present invention provides a friction brake comprising:
the mounting seat is used for connecting with equipment;
the driving cylinder body is arranged on the mounting seat, the piston is arranged in the driving cylinder body, the piston and the driving cylinder body form a cylinder, and the driving cylinder body and the piston form a pressure source inlet;
the hollow through shaft tube is arranged in the driving cylinder body, and a space for installing a driving power shaft is formed in the hollow through shaft tube;
the friction assembly is arranged between the driving cylinder body and the hollow through shaft tube and is positioned at one end of the piston, the friction assembly comprises at least one friction plate and at least one friction steel sheet, one end of the friction plate is connected with the driving cylinder body, one end of the friction steel sheet is connected with the hollow through shaft tube, and the friction plate and the friction steel sheet are oppositely arranged and a space is reserved between the friction plate and the friction steel sheet;
the first elastic component and the second elastic component are arranged on two opposite sides of the friction plate and are telescopic, one end of the first elastic component is fixed on the mounting seat, one end of the second elastic component is fixed on the driving cylinder body, and the friction plate is balanced in stress through the first elastic component and the second elastic component so as to limit the friction plate; and
the third elastic component and the fourth elastic component are arranged on two opposite sides of the friction steel sheet and are telescopic, the third elastic component and the fourth elastic component are fixed on the hollow through shaft tube, and the friction steel sheet is balanced in force through the third elastic component and the fourth elastic component so as to limit the friction steel sheet.
A further improvement of the friction brake according to the invention is that the axial displacement of the friction plate and the friction steel plate is smaller than the predetermined distance between the friction plate and the friction steel plate.
A further improvement of the friction brake of the present invention is that,
the sum of the change value of the deformation force of the first elastic component and the change value of the deformation force of the second elastic component is equal to the centrifugal force of the friction plate, so that the friction plate keeps balanced in stress;
and the sum of the change value of the deformation force of the third elastic component and the change value of the deformation force of the fourth elastic component is equal to the centrifugal force of the friction steel sheet, so that the friction steel sheet is kept in force balance.
A further improvement of the friction brake of the present invention is that,
the first elastic assembly includes:
one end of the first sleeve is fixed on the mounting seat; and
the first spring is inserted into the first sleeve and abuts against one side of the friction plate;
the second elastic assembly includes:
a second sleeve with one end fixed to the driving cylinder; and
and the second spring is inserted into the second sleeve and abuts against the other side of the friction plate.
A further improvement of the friction brake of the present invention is that,
the third elastic assembly includes:
one end of the third sleeve is fixed on the hollow through shaft tube; and
the third spring is inserted into the third sleeve and abuts against one side of the friction steel sheet;
the fourth elastic assembly includes:
a fourth sleeve with one end fixed on the mounting seat; and
and the third spring is inserted into the fourth sleeve and abuts against the other side of the friction steel sheet.
A further improvement of the friction brake of the present invention is that,
the first elastic components are uniformly distributed along the circumferential direction of the friction plate.
The second elastic components are uniformly distributed along the circumferential direction of the friction plate.
A further improvement of the friction brake of the present invention is that,
the plurality of the third elastic components are uniformly distributed along the circumferential direction of the friction steel sheet.
The number of the fourth elastic components is multiple, and the fourth elastic components are uniformly distributed along the circumferential direction of the friction steel sheet.
A further improvement of the friction brake of the present invention is that,
the outside of hollow logical central siphon is formed with confession the third accommodation groove that the third elastic component set up and confession the fourth accommodation groove that the fourth elastic component set up, the fourth accommodation groove with the third accommodation groove sets up relatively.
A further improvement of the friction brake of the present invention is that,
the friction assembly comprises a plurality of friction plates and a plurality of friction steel plates which are oppositely arranged;
the first elastic component or the second elastic component which is abutted against one surface of one friction plate adjacent to the corresponding friction plate penetrates through the corresponding friction plate;
the third elastic component or the fourth elastic component which is abutted against one surface of one friction steel sheet adjacent to the corresponding friction steel sheet penetrates through the corresponding friction steel sheet.
The friction brake has the beneficial effects that:
the friction brake effectively solves the problems of false braking and the like caused by mutual adhesion of the friction plate and the friction steel sheet in the friction assembly under the action of external forces such as centrifugal force in any direction in a rotating mechanism such as centrifugal machine equipment and the like, and protects equipment and personal safety. The invention can be extended to solve the problems of false braking and the like caused by mutual adhesion of the friction plate and the friction steel sheet in the friction component of the friction brake of the high-speed rail linear motion under the action of any directional external force such as a rocket.
Drawings
Fig. 1 is a schematic view of a prior art friction brake.
Fig. 2 is an enlarged schematic view of the portion a in fig. 1 under normal operation.
Fig. 3 and 4 are enlarged schematic diagrams of two types of false brakes in the centrifugal force working condition of the portion a in fig. 1.
Fig. 5 is a schematic view of a friction brake of the present invention.
Fig. 6 is an enlarged schematic view of section B of the friction brake of the present invention.
Fig. 7 is an enlarged schematic view of section C of the friction brake of the present invention.
Fig. 8 is an enlarged schematic view of a portion D of fig. 7.
Detailed Description
The invention will be further described with reference to the drawings and the specific examples.
Referring to fig. 5, a schematic diagram of a friction brake of the present invention is shown. Referring to fig. 6, an enlarged schematic view of section B of the friction brake of the present invention is shown. Referring to fig. 7, an enlarged schematic view of section C of the friction brake of the present invention is shown. As shown in connection with fig. 5 to 7, the friction brake of the present invention includes:
a mounting base 10 for connection to equipment;
a driving cylinder body 20 arranged in the mounting seat 10 and a piston 21 arranged in the driving cylinder body 20, wherein the piston 21 and the driving cylinder body 20 form a cylinder form, and the driving cylinder body 20 and the piston 21 form a pressure source inlet;
a hollow through shaft tube 30 provided in the driving cylinder 20, wherein a space for installing a transmission power shaft is formed inside the hollow through shaft tube 30;
the friction assembly 40 is arranged between the driving cylinder 20 and the hollow through shaft tube 30 and is positioned at one end of the piston 21, the friction assembly 40 comprises at least one friction plate 41 and at least one friction steel sheet 42, one end of the friction plate 41 is connected with the driving cylinder 20, one end of the friction steel sheet 42 is connected with the hollow through shaft tube 30, and the friction plate 41 and the friction steel sheet 42 are oppositely arranged and a space is reserved between the friction plate 41 and the friction steel sheet 42;
the first elastic component 50 and the second elastic component 60 are arranged on two opposite sides of the friction plate 41 and are telescopic, one end of the first elastic component 50 is fixed on the mounting seat 10, one end of the second elastic component 60 is fixed on the driving cylinder body 20, and the friction plate 41 is balanced in stress through the first elastic component 50 and the second elastic component 60 so as to limit the friction plate 41; and
the third elastic component 70 and the fourth elastic component 80 are arranged on two opposite sides of the friction steel sheet 42 and are telescopic, the third elastic component 70 and the fourth elastic component 80 are fixed on the hollow through shaft tube 30, and the friction steel sheet 42 is balanced in force through the third elastic component 70 and the fourth elastic component 80 so as to limit the friction steel sheet 42.
Referring to fig. 8, an enlarged schematic view of section D of fig. 8 is shown as a preferred embodiment of the friction brake of the present invention. As shown in fig. 5 to 8, the axial displacement of the friction plate 41 and the friction steel plate 42 is smaller than the predetermined distance between the friction plate 41 and the friction steel plate 42. Specifically, in the initial state, a space is left between the friction plate 41 and the friction steel sheet 42, and in the brake-off state, axial displacement may exist between the friction plate 41 and the friction steel sheet 42 under the centrifugal force, and when the axial displacement between the friction plate 41 and the friction steel sheet 42 is smaller than the space left between the friction plate 41 and the friction steel sheet 42 in the initial state, a distance still exists between the friction plate 41 and the friction steel sheet 42 without bonding, so that false braking can be prevented. Therefore, in order to prevent the friction plate 41 and the friction steel plate 42 from being mutually attached under the action of centrifugal force, it is necessary to ensure that the axial displacement of the friction plate 41 and the friction steel plate 42 does not exceed the original reserved distance, so that the problem of false braking caused by the mutual attachment of the friction plate 41 and the friction steel plate 42 under the action of centrifugal force can be prevented.
As a preferred embodiment of the friction brake of the present invention, as shown in connection with figures 5 to 8,
the sum of the variation of the deformation force of the first elastic member 50 and the variation of the deformation force of the second elastic member 60 is equal to the centrifugal force of the friction plate 41, so that the friction plate 41 maintains the force balance;
the sum of the variation of the deformation force of the third elastic member 70 and the variation of the deformation force of the fourth elastic member 80 is equal to the centrifugal force of the friction steel sheet 42, so that the friction steel sheet 42 is kept in force balance.
As a preferred embodiment of the friction brake of the present invention, as shown in connection with figures 5 to 8,
the first elastic member 50 includes:
a first sleeve 51 having one end fixed to the mount 10; and
a first spring 52 inserted into the first sleeve 51 and abutting against one side of the friction plate 41;
the second elastic member 60 includes:
a second sleeve 61 having one end fixed to the driving cylinder 20; and
and a second spring 62 inserted in the second sleeve 61 and abutting against the other side of the friction plate 41.
As a preferred embodiment of the friction brake of the present invention, as shown in connection with figures 5 to 8,
the third elastic member 70 includes:
a third sleeve 71 having one end fixed to the hollow through-shaft tube 30; and
a third spring 72 inserted in the third sleeve 71 and abutting against one side of the friction steel plate 42;
the fourth elastic member 80 includes:
a fourth sleeve 81 having one end fixed to the mount; and
a fourth spring 82 inserted in the fourth sleeve 81 and abutting against the other side of the friction steel plate 42.
As a preferred embodiment of the friction brake of the present invention, as shown in connection with figures 5 to 8,
the first elastic members 50 are provided in plurality and are uniformly arranged along the circumferential direction of the friction plate 41.
The second elastic members 60 are provided in plurality and are uniformly arranged along the circumferential direction of the friction plate 41.
As a preferred embodiment of the friction brake of the present invention, as shown in connection with figures 5 to 8,
the third elastic members 70 are uniformly arranged in the circumferential direction of the friction steel plate 42.
The fourth elastic members 80 are uniformly arranged in the circumferential direction of the friction steel plate 42.
As a preferred embodiment of the friction brake of the present invention, as shown in connection with figures 5 to 8,
the hollow through-shaft tube 30 is formed with a third accommodating groove for the third elastic component 70 and a fourth accommodating groove for the fourth elastic component 80, and the fourth accommodating groove and the third accommodating groove are disposed opposite to each other.
As a preferred embodiment of the friction brake of the present invention, as shown in connection with figures 5 to 8,
the friction assembly 40 comprises a plurality of friction plates 41 and a plurality of friction steel plates 42 which are oppositely arranged;
the first elastic component 50 or the second elastic component 60 abutting against one surface of the friction plate 41 adjacent to the corresponding friction plate penetrates through the corresponding friction plate 41;
the third elastic component 70 or the fourth elastic component 80 abutting against one surface of a friction steel sheet adjacent to the corresponding friction steel sheet 42 is penetrated through the corresponding friction steel sheet 42.
Specifically, as shown in connection with fig. 5 to 8, in the present embodiment, the friction assembly 40 includes four friction plates 41 and three friction steel plates 42. The simulated centrifugal force direction is laterally to the left.
In the following analysis of the leftmost friction plate 41, the first elastic member 50 provides a pre-compression force to the left side of the friction plate 41, and the second elastic member 60 provides a pre-compression force to the right side of the friction plate 41. The second elastic component 60 is correspondingly penetrated through the through holes of the remaining three friction plates 41 positioned on the right side of the leftmost friction plate 41 and then connected with the driving cylinder body through bolts so as to overcome the axial force. When the friction brake is in the brake-off state, the pre-pressure of the first elastic component 50 acting on the left side of the friction plate 41 is equal to the pre-pressure of the second elastic component 60 acting on the right side of the friction plate 41, and the pre-pressure is opposite in direction, so that the axial stress of the friction plate 41 is balanced, and the axial position of the friction plate 41 is locked.
The friction steel sheet 42 located at the leftmost side is analyzed as follows: the third spring assembly 70 provides a pre-compression force against the left side of the friction steel plate 42. The third spring 72 of the third elastic assembly 70 is mounted in the third sleeve 71, the right side of the third sleeve 71 is abutted against the spline left side surface of the hollow shaft sleeve, and the left side of the third sleeve 71 is locked by a clamp spring mounted on the hollow shaft sleeve. The fourth elastic member 80 provides a pre-pressing force to the right side surface of the friction steel plate 42. The fourth spring 82 is installed in the fourth sleeve 81, the fourth sleeve 81 passes through the through holes on the other two friction steel sheets 42 positioned on the right, the left side of the fourth sleeve 81 is abutted against the right side surface of the spline of the hollow shaft sleeve, and the right side of the fourth sleeve 81 is locked by the snap springs installed on the hollow shaft sleeve. When the brake is in the brake-off state, the pre-pressure of the third elastic component 70 on the left side of the friction steel sheet 42 is equal to the pre-pressure of the fourth elastic component 80 on the right side of the friction steel sheet 42, and the directions are opposite, so that the axial stress of the friction steel sheet 42 is balanced, and the axial position of the friction steel sheet 42 is locked.
The friction steel plates 42 of the remaining friction plates 41 are disposed in the same manner, and the description thereof will not be repeated.
The friction plate 41 in the initial state receives the pre-pressing force of the first elastic assembly 50 and the second elastic assembly 60, and the pre-pressing forces of the two sides are balanced; in the operating state of the device, centrifugal force moves the friction plate 41 to the left by delta from right to left, and simultaneously the first elastic component 50 continues to compress and the deformation force rises; the deformation amount of the second elastic component 60 is reduced, the deformation force is reduced, and by controlling the rigidity of the first elastic component 50 and the second elastic component 60, the sum of the rising amount of the deformation force of the first elastic component 50 and the falling amount of the deformation force of the second elastic component 60 is equal to the centrifugal force generated by the friction plate 41, so that the forces on two sides of the friction plate 41 are balanced continuously.
In the brake-off state, the friction plate 41 and the friction steel plate 42 are spaced from each other, and in order to prevent the friction plate 41 and the friction steel plate 42 from being mutually attached under the centrifugal force, it is necessary to ensure that the axial displacement of the friction plate 41 and the friction steel plate 42 does not exceed the original reserved spacing.
Similarly, by controlling the rigidity of the elastic components at two sides, the other friction plates and the friction steel plates are independently designed, and the structural requirement can be met under the action of centrifugal force and under the condition that the axial displacement is smaller than the reserved distance between the friction plates and the friction steel plates, the forces at two sides of the friction plates and the friction steel plates reach an equilibrium state.
The friction brake has the beneficial effects that:
the friction brake effectively solves the problems of false braking and the like caused by mutual adhesion of the friction plate and the friction steel sheet in the friction assembly under the action of external forces such as centrifugal force in any direction in a rotating mechanism such as centrifugal machine equipment and the like, and protects equipment and personal safety. The invention can be extended to solve the problems of false braking and the like caused by mutual adhesion of the friction plate and the friction steel sheet in the friction component of the friction brake of the high-speed rail linear motion under the action of any directional external force such as a rocket.
The present invention has been described in detail with reference to the embodiments thereof, and one skilled in the art can make various modifications to the invention based on the above description. Accordingly, certain details of the illustrated embodiments are not to be taken as limiting the invention, which is defined by the appended claims.
Claims (10)
1. A friction brake, comprising:
the mounting seat is used for connecting with equipment;
the driving cylinder body is arranged on the mounting seat, the piston is arranged in the driving cylinder body, the piston and the driving cylinder body form a cylinder, and the driving cylinder body and the piston form a pressure source inlet;
the hollow through shaft tube is arranged in the driving cylinder body, and a space for installing a transmission power shaft is formed in the hollow through shaft tube;
the friction assembly is arranged between the driving cylinder body and the hollow through shaft tube and is positioned at one end of the piston, the friction assembly comprises at least one friction plate and at least one friction steel sheet, one end of the friction plate is connected with the driving cylinder body, one end of the friction steel sheet is connected with the hollow through shaft tube, and the friction plate and the friction steel sheet are oppositely arranged and a space is reserved between the friction plate and the friction steel sheet;
the first elastic component and the second elastic component are arranged on two opposite sides of the friction plate and are telescopic, one end of the first elastic component is fixed on the mounting seat, one end of the second elastic component is fixed on the driving cylinder body, and the friction plate is balanced in stress through the first elastic component and the second elastic component so as to limit the friction plate; and the third elastic component and the fourth elastic component are arranged on two opposite sides of the friction steel sheet and are telescopic, the third elastic component and the fourth elastic component are fixed on the hollow through shaft tube, and the friction steel sheet is balanced in force through the third elastic component and the fourth elastic component so as to limit the friction steel sheet.
2. The friction brake of claim 1 wherein the axial displacement of said friction plate and said friction steel plate is less than the reserved spacing of said friction plate from said friction steel plate.
3. The friction brake of claim 1 wherein the sum of the magnitude of the change in the deformation force of the first resilient assembly and the magnitude of the change in the deformation force of the second resilient assembly is equal to the centrifugal force of the friction plate so that the friction plate remains in force balance;
and the sum of the change value of the deformation force of the third elastic component and the change value of the deformation force of the fourth elastic component is equal to the centrifugal force of the friction steel sheet, so that the friction steel sheet is kept in force balance.
4. The friction brake of claim 1 wherein said first resilient assembly comprises:
one end of the first sleeve is fixed on the mounting seat; and
the first spring is inserted into the first sleeve and abuts against one side of the friction plate;
the second elastic assembly includes:
a second sleeve with one end fixed to the driving cylinder; and a second spring inserted into the second sleeve and propped against the other side of the friction plate.
5. The friction brake of claim 1 wherein said third resilient assembly comprises:
one end of the third sleeve is fixed on the hollow through shaft tube; the third spring is inserted into the third sleeve and abuts against one side of the friction steel sheet;
the fourth elastic assembly includes:
a fourth sleeve with one end fixed on the mounting seat; and
and the third spring is inserted into the fourth sleeve and abuts against the other side of the friction steel sheet.
6. The friction brake of claim 1 wherein said first spring assembly is a plurality of spring assemblies uniformly disposed about a circumference of said friction plate,
the second elastic components are uniformly distributed along the circumferential direction of the friction plate.
7. The friction brake according to claim 1, wherein the third elastic members are provided in plural numbers and are uniformly arranged along the circumferential direction of the friction steel plate,
the number of the fourth elastic components is multiple, and the fourth elastic components are uniformly distributed along the circumferential direction of the friction steel sheet.
8. The friction brake of claim 1 wherein said mounting base defines a first receiving recess in which said first resilient assembly is disposed;
the driving cylinder body is provided with a second accommodating groove for the second elastic component to be arranged.
9. The friction brake as defined in claim 1, wherein a third receiving groove in which the third elastic member is disposed and a fourth receiving groove in which the fourth elastic member is disposed are formed at an outer portion of the hollow through-tube, the fourth receiving groove and the third receiving groove being disposed opposite to each other.
10. The friction brake of claim 1 wherein said friction pack includes a plurality of oppositely disposed friction plates and a plurality of friction steel plates;
the first elastic component or the second elastic component which is abutted against one surface of one friction plate adjacent to the corresponding friction plate penetrates through the corresponding friction plate;
the third elastic component or the fourth elastic component which is abutted against one surface of one friction steel sheet adjacent to the corresponding friction steel sheet penetrates through the corresponding friction steel sheet.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811560885.5A CN109667854B (en) | 2018-12-20 | 2018-12-20 | friction brake |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811560885.5A CN109667854B (en) | 2018-12-20 | 2018-12-20 | friction brake |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109667854A CN109667854A (en) | 2019-04-23 |
| CN109667854B true CN109667854B (en) | 2024-02-13 |
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| CN201811560885.5A Active CN109667854B (en) | 2018-12-20 | 2018-12-20 | friction brake |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110060560B (en) * | 2019-04-26 | 2021-09-14 | 重庆科创职业学院 | Automobile brake system teaching simulation equipment |
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| US4316530A (en) * | 1978-09-07 | 1982-02-23 | Itt Industries, Inc. | Floating caliper disc brake |
| JPH0625632U (en) * | 1992-09-07 | 1994-04-08 | 日信工業株式会社 | Disk brake retainer and pad spring for vehicles |
| CN103498882A (en) * | 2013-10-22 | 2014-01-08 | 中国北方车辆研究所 | Brake for automatic transmission |
| CN207111767U (en) * | 2017-05-31 | 2018-03-16 | 山东农业大学 | A kind of plate piston efficient hydraulic brake |
| CN108779820A (en) * | 2016-04-13 | 2018-11-09 | 威伯科欧洲有限责任公司 | Disk brake, in particular for the disk brake of commercial car |
| CN209414462U (en) * | 2018-12-20 | 2019-09-20 | 上海韩东机械科技有限公司 | Friction brake |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4065178B2 (en) * | 2002-10-24 | 2008-03-19 | 株式会社エフ・シー・シー | Multi-plate friction clutch |
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2018
- 2018-12-20 CN CN201811560885.5A patent/CN109667854B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4316530A (en) * | 1978-09-07 | 1982-02-23 | Itt Industries, Inc. | Floating caliper disc brake |
| JPH0625632U (en) * | 1992-09-07 | 1994-04-08 | 日信工業株式会社 | Disk brake retainer and pad spring for vehicles |
| CN103498882A (en) * | 2013-10-22 | 2014-01-08 | 中国北方车辆研究所 | Brake for automatic transmission |
| CN108779820A (en) * | 2016-04-13 | 2018-11-09 | 威伯科欧洲有限责任公司 | Disk brake, in particular for the disk brake of commercial car |
| CN207111767U (en) * | 2017-05-31 | 2018-03-16 | 山东农业大学 | A kind of plate piston efficient hydraulic brake |
| CN209414462U (en) * | 2018-12-20 | 2019-09-20 | 上海韩东机械科技有限公司 | Friction brake |
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| CN109667854A (en) | 2019-04-23 |
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