CN117662559B - Hydraulic cylinder assembly, hydraulic brake device and vehicle - Google Patents
Hydraulic cylinder assembly, hydraulic brake device and vehicle Download PDFInfo
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- CN117662559B CN117662559B CN202211057424.2A CN202211057424A CN117662559B CN 117662559 B CN117662559 B CN 117662559B CN 202211057424 A CN202211057424 A CN 202211057424A CN 117662559 B CN117662559 B CN 117662559B
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- 238000007789 sealing Methods 0.000 claims description 11
- 230000000903 blocking effect Effects 0.000 claims description 9
- 238000011144 upstream manufacturing Methods 0.000 claims description 6
- 230000000694 effects Effects 0.000 abstract description 8
- 239000003921 oil Substances 0.000 description 159
- 230000001502 supplementing effect Effects 0.000 description 19
- 238000009434 installation Methods 0.000 description 8
- 230000009286 beneficial effect Effects 0.000 description 3
- 230000002708 enhancing effect Effects 0.000 description 3
- 230000004323 axial length Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 239000013589 supplement Substances 0.000 description 2
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1447—Pistons; Piston to piston rod assemblies
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
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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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Actuator (AREA)
Abstract
The disclosure relates to a hydraulic cylinder assembly, a hydraulic braking device and a vehicle, wherein the hydraulic cylinder assembly comprises a first hydraulic cylinder and a second hydraulic cylinder, the first hydraulic cylinder comprises a first cylinder body and a first piston movably mounted on the first cylinder body, the second hydraulic cylinder comprises a second cylinder body and a second piston movably mounted on the second cylinder body, the first piston is provided with a first end face and a second end face which are opposite along the moving direction of the first piston, the second piston is provided with a third end face and a fourth end face which are opposite along the moving direction of the second piston, the first end face and the inner surface of the first cylinder body jointly define a first oil cavity, a second oil cavity is arranged between the second end face and the third end face, a first through hole communicated with the first oil cavity is formed on the first cylinder body, the area of the first end face is larger than the area of the second end face, and the area of the third end face is larger than the area of the second end face. The hydraulic cylinder assembly can achieve the effect of improving the output force of the piston.
Description
Technical Field
The disclosure relates to the field of hydraulic technology, in particular to a hydraulic cylinder assembly, a hydraulic braking device and a vehicle.
Background
Currently, there are three general ways to raise the output force of the hydraulic cylinder, one is to directly increase the cross-sectional area of the piston, but this way would increase the volume of the whole device, which is difficult to achieve in the case of limited space. The second way is to simultaneously press the pistons of two or more hydraulic cylinders against the member to be pushed, but it is difficult to ensure that the extending speeds of the pistons of the plurality of hydraulic cylinders are consistent, so that uneven stress on the member to be pushed is caused. Yet another way is to arrange a plurality of hydraulic cylinders in series, with the piston of the cylinder closest to the member to be pushed against the member to be pushed, such a series of hydraulic cylinder assemblies being able to adjust the output force of the entire hydraulic cylinder assembly only by adjusting the number of hydraulic cylinders in series.
Disclosure of Invention
The disclosure provides a hydraulic cylinder assembly, a hydraulic braking device and a vehicle, so as to solve the technical problems in the related art.
To achieve the above object, according to one aspect of the present disclosure, there is provided a hydraulic cylinder assembly including a first hydraulic cylinder including a first cylinder body and a first piston movably mounted to the first cylinder body, and a second hydraulic cylinder including a second cylinder body and a second piston movably mounted to the second cylinder body;
The first piston is provided with a first end face and a second end face which are opposite along the moving direction of the first piston, the second piston is provided with a third end face and a fourth end face which are opposite along the moving direction of the second piston, the first end face and the inner surface of the first cylinder body jointly define a first oil cavity, a second oil cavity is arranged between the second end face and the third end face, and a first through hole communicated with the first oil cavity is formed in the first cylinder body;
the area of the first end face is larger than that of the second end face, and the area of the third end face is larger than that of the second end face.
Optionally, the second cylinder body is connected to the first cylinder body, a second through hole for the first piston to pass through is formed in the second cylinder body, and the second end face, the inner surface of the second cylinder body and the third end face jointly define the second oil cavity.
Optionally, at least part of the second cylinder is located in the first cylinder.
Optionally, the first cylinders are multiple, the first cylinders of the first cylinders are sequentially connected, the first through holes on the first cylinders of the first cylinders located at the head end of the first cylinders are used for being communicated with an oil supply source, the first cylinders of the first cylinders located at the tail end of the first cylinders are connected with the second cylinders, the first piston of the first cylinder located at the tail end of each adjacent two first cylinders penetrates through the first through hole on the first cylinder of the next first cylinder, the first piston of the first cylinder located at the tail end of each first cylinder penetrates through the second through hole, and the second end face of the first piston, the inner surface of the second cylinder and the third end face of the first piston jointly define the second oil cavity.
Optionally, the first cylinder body of one of the two adjacent first hydraulic cylinders is at least partially located within the first cylinder body of the other first hydraulic cylinder.
Optionally, the first piston includes the piston body and the protrusion in the piston rod of piston body, the piston rod is used for passing the second through-hole, the piston body is kept away from the terminal surface of piston rod is first terminal surface, the piston rod is kept away from the terminal surface of piston body is the second terminal surface, the piston body is close to the one end of piston rod with have first air gap between the surface of second cylinder body, be formed with on the first cylinder body with first air gap intercommunication's first air vent, be formed with on the second cylinder body intercommunication first air gap with the first oil filling hole of second oil pocket, first oil filling pipe pass first air vent with first oil filling hole and with the second oil pocket intercommunication.
Optionally, the central axis of the first vent hole and the central axis of the first oil supplementing hole are located in the same plane parallel to the moving direction of the first piston.
Optionally, a first oil supplementing port communicated with the second oil cavity is formed on the second piston;
the first oil supplementing port is provided with a first stop valve, or the first oil supplementing port is provided with a detachable first blocking piece.
Optionally, a first mounting boss is formed on the first cylinder body, a second mounting boss is formed on the second cylinder body, a first mounting hole for a fastener to pass through is formed on the first mounting boss, and a second mounting hole for the fastener to pass through is formed on the second mounting boss.
Optionally, the second end surface and the inner surface of the first cylinder body jointly define a first sub-oil cavity, the third end surface and the inner surface of the second cylinder body jointly define a second sub-oil cavity, the first sub-oil cavity is communicated with the second sub-oil cavity through a first oil delivery pipe, and the first sub-oil cavity, an oil duct inside the first oil delivery pipe and the second sub-oil cavity jointly form the second oil cavity.
Optionally, the first cylinders are sequentially connected in series through a second oil delivery pipe, the first through holes on the first cylinder body of the first cylinder located at the most upstream in the first cylinders are used for being communicated with an oil supply source, the second end faces of the first pistons of the first cylinders located at the most downstream in the first cylinders and the inner surface of the first cylinder body of the first cylinder jointly define the first sub-oil cavity, the second end faces of the first pistons of the first cylinders located at the upstream in each two adjacent first cylinders and the inner surface of the first cylinder body of the first cylinder jointly define a third oil cavity, and the third oil cavity is communicated with the first oil cavity of the first cylinder located at the downstream in each two adjacent first cylinders through the second oil delivery pipe.
Optionally, the first cylinders are multiple, the first cylinders of the first cylinders are connected in sequence, the first through holes on the first cylinders of the first cylinders located at the head end of the first cylinders are used for being communicated with an oil supply source, the second end faces of the first pistons of the first cylinders located at the tail end of the first cylinders and the inner surfaces of the first cylinders jointly define the first sub-oil cavity, and the first pistons of the first cylinders of every two adjacent first cylinders penetrate through the first through holes on the first cylinders of the next first cylinders.
Optionally, a second oil supplementing port communicated with the second sub oil cavity is formed on the second cylinder body, a second stop valve or a detachable second blocking piece is arranged at the second oil supplementing port, and/or,
The first oil delivery pipe is connected with a third oil supplementing pipe in a bypass mode, and a third stop valve is arranged on the third oil supplementing pipe.
Optionally, the areas of the first end surfaces of the plurality of first pistons are the same, and the areas of the second end surfaces of the plurality of first pistons are the same.
Optionally, the first cylinder body comprises a first cylinder groove, the first piston is installed in the first cylinder groove, the second cylinder body comprises a second cylinder groove, and the second piston is installed in the second cylinder groove;
The inner diameter of the first cylinder groove is equal to the outer diameter of the first end face, the inner diameter of the second cylinder groove is equal to the outer diameter of the third end face, the outer diameter of the first end face is equal to the outer diameter of the third end face, and the ratio of the outer diameter of the third end face to the outer diameter of the second end face is greater than or equal to 2.
Optionally, an annular groove is formed on the inner surface of the second cylinder body, an annular sealing ring is sleeved on the outer circumferential surface of the second piston, the annular sealing ring is located in the annular groove, and a chamfer is formed on the side wall, deviating from the third end face, of the annular groove.
According to another aspect of the present disclosure, there is provided a hydraulic brake device including a hydraulic cylinder assembly, a brake pad and a friction plate as described in any one of the above claims, wherein the fourth end surface of the second piston is configured to abut against the brake pad and push the brake pad to move toward the friction plate to compress the friction plate.
According to still another aspect of the present disclosure, there is provided a vehicle including the hydraulic brake device described above.
By means of the technical scheme, the area of the first end face of the first piston in the hydraulic cylinder assembly is larger than that of the second end face, and the area of the third end face of the second piston is larger than that of the second end face, so that under the condition that the pressure of hydraulic medium transmitted by the hydraulic cylinder is unchanged, the output force of the second piston is larger than that of the input force received by the first piston due to the fact that the area of the stress surface (namely the third end face) of the second piston is larger than that of the force application surface (namely the second end face) of the first piston. That is, by setting the first and second hydraulic cylinders and the area of the first end surface of the first piston to be larger than the area of the second end surface thereof, the area of the third end surface of the second piston is larger than the area of the second end surface of the first piston, an effect of increasing the output force of the pistons can be achieved.
Additional features and advantages of the present disclosure will be set forth in the detailed description which follows.
Drawings
The accompanying drawings are included to provide a further understanding of the disclosure, and are incorporated in and constitute a part of this specification, illustrate the disclosure and together with the description serve to explain, but do not limit the disclosure. In the drawings:
FIG. 1 is a schematic perspective view of a hydraulic cylinder assembly provided in an exemplary embodiment of the present disclosure;
FIG. 2 is a schematic longitudinal cross-sectional view of an exemplary hydraulic cylinder assembly provided in accordance with a first embodiment of the present disclosure;
FIG. 3 is an enlarged schematic view of a partial structure at A in FIG. 2;
FIG. 4 is a schematic cross-sectional view of a hydraulic cylinder assembly provided in an exemplary embodiment of the present disclosure;
FIG. 5 is a schematic perspective view of a first piston of a first hydraulic cylinder of a hydraulic cylinder assembly provided by an exemplary embodiment of the present disclosure;
FIG. 6 is a schematic perspective view of a second cylinder block of a second hydraulic cylinder of a hydraulic cylinder assembly provided in accordance with an exemplary embodiment of the present disclosure;
FIG. 7 is a schematic illustration of a configuration of a second piston of a second hydraulic cylinder of a hydraulic cylinder assembly provided by an exemplary embodiment of the present disclosure;
FIG. 8 is a schematic cross-sectional view of a hydraulic cylinder assembly provided by an exemplary embodiment of the present disclosure, wherein only the first piston, the second cylinder, and the second piston are shown;
FIG. 9 is a schematic cross-sectional view of a hydraulic cylinder assembly provided in accordance with another exemplary embodiment of the present disclosure;
FIG. 10 is a schematic cross-sectional view of a hydraulic cylinder assembly provided in accordance with yet another exemplary embodiment of the present disclosure;
FIG. 11 is a schematic cross-sectional view of a hydraulic cylinder assembly provided in accordance with yet another exemplary embodiment of the present disclosure;
FIG. 12 is a schematic cross-sectional view of a hydraulic cylinder assembly provided in accordance with yet another exemplary embodiment of the present disclosure;
fig. 13 is a schematic cross-sectional structure of a hydraulic cylinder assembly according to still another exemplary embodiment of the present disclosure.
Description of the reference numerals
A 100-hydraulic cylinder assembly; 1-a first hydraulic cylinder, 11-a first cylinder, 111-a first through hole, 112-a first mounting boss, 12-a first piston, 121-a first end face, 122-a second end face, 123-a piston body, 124-a piston rod, 13-a first cylinder groove, 2-a second hydraulic cylinder, 21-a second cylinder, 211-a second through hole, 212-a second mounting boss, 213-a second oil supplementing port, 214-a second stop valve, 215-a second blocking member, 216-a third oil supplementing port, 216-a third blocking valve, 218-a third blocking member, 22-a second piston, 221-a third end face, 222-a fourth end face, 23-a second cylinder groove, 3-a first oil cavity, 4-a second oil cavity, 41-a first sub oil cavity, 42-a second oil cavity, 51-a first air gap, 52-a first air gap, 53-a second air gap, 54-a second air vent, 61-a first oil supplementing hole, 62-a first oil pipe, 63-a second stop valve, 64-a second oil supplementing hole, 23-a third oil supplementing hole, 82-a third oil delivering groove, 82-a fourth oil supplementing hole, 82-a third oil supplementing hole, a third oil delivering valve, a third oil supplementing hole, a third oil pipe, a third oil sealing ring, and a fourth oil pipe, a third oil pipe, a sealing ring, and a fourth oil.
Detailed Description
Specific embodiments of the present disclosure are described in detail below with reference to the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating and illustrating the disclosure, are not intended to limit the disclosure.
In this disclosure, unless otherwise indicated, directional terms used, such as "inner and outer," refer to both inner and outer of a particular structural profile. The terms such as "first" and "second" are used merely to distinguish one element from another element and do not have order or importance. Additionally, the above-used directional terms are merely used to facilitate description of the present disclosure, and are not meant to indicate or imply that the devices or components referred to must have a particular orientation, be constructed and operate in a particular orientation, and are not to be construed as limiting the present disclosure.
As shown in fig. 1 to 13, according to an aspect of the present disclosure, there is provided a hydraulic cylinder assembly 100 including a first hydraulic cylinder 1 and a second hydraulic cylinder 2, the first hydraulic cylinder 1 including a first cylinder block 11 and a first piston 12 movably mounted to the first cylinder block 11, the second hydraulic cylinder 2 including a second cylinder block 21 and a second piston 22 movably mounted to the second cylinder block 21. The first piston 12 has a first end surface 121 and a second end surface 122 opposite in the moving direction thereof, the second piston 22 has a third end surface 221 and a fourth end surface 222 opposite in the moving direction thereof, the first end surface 121 and the inner surface of the first cylinder 11 together define a first oil chamber 3, a second oil chamber 4 is provided between the second end surface 122 and the third end surface 221, and a first through hole 111 communicating with the first oil chamber 3 is formed in the first cylinder 11. Wherein the area of the first end surface 121 is larger than the area of the second end surface 122, and the area of the third end surface 221 is larger than the area of the second end surface 122.
The working process/principle of the hydraulic cylinder assembly 100 is that when the pressure of the hydraulic medium in the first oil chamber 3 increases, the first end surface 121 of the first piston 12 receives a pushing force, and the first piston 12 moves, and the second end surface 122 of the first piston presses the hydraulic medium in the second oil chamber 4 between the second end surface 122 and the third end surface 221, thereby causing the second piston 22 to move and output a force to the outside.
By the above technical solution, since the area of the first end surface 121 of the first piston 12 is larger than the area of the second end surface 122 and the area of the third end surface 221 of the second piston 22 is larger than the area of the second end surface 122 in the hydraulic cylinder assembly 100 of the present application, under the condition that the pressure of the hydraulic medium transmitted by the hydraulic cylinder is unchanged, the output force of the second piston 22 is larger than the input force received by the first piston 12 because the area of the stress surface (i.e., the third end surface 221) of the second piston 22 is larger than the area of the force application surface (i.e., the second end surface 122) of the first piston 12. That is, by setting the first and second hydraulic cylinders 1 and 2 and the area of the first end surface 121 of the first piston 12 to be larger than the area of the second end surface 122 thereof, the area of the third end surface 221 of the second piston 22 is larger than the area of the second end surface 122 of the first piston 12, the effect of increasing the output force of the pistons can be achieved.
Compared with the mode that a plurality of hydraulic cylinders are arranged in the related art and pistons of the hydraulic cylinders are propped against the to-be-pushed piece simultaneously, the hydraulic cylinder assembly 100 provided by the disclosure is used for propping against the to-be-pushed piece with the end face being the fourth end face 222 of the second piston 22, so that the to-be-pushed piece is ensured to be uniformly stressed while the output force is ensured to be lifted, the to-be-pushed piece with smaller volume can be acted on, the situation that the to-be-pushed piece is unevenly stressed due to the fact that the pistons of the hydraulic cylinders are simultaneously acted on the to-be-pushed piece in the related art is avoided, or the situation that the pistons of the hydraulic cylinders are simultaneously propped against the to-be-pushed piece with smaller volume is difficult to realize is avoided. Compared with the mode of arranging a plurality of hydraulic cylinders in series in the related art, the mode of arranging the plurality of hydraulic cylinders in series can only be realized by increasing the number of the hydraulic cylinders in series when the output force of the whole hydraulic cylinder assembly needs to be further improved, but the effect of further improving the output force of the whole hydraulic cylinder assembly 100 can be realized by adjusting the area ratio of the third end surface 221 and the second end surface 122 on the basis of unchanged number of the hydraulic cylinders, that is, in the case of arranging the same number of the hydraulic cylinders, compared with the mode of arranging the plurality of hydraulic cylinders in series in the related art, the hydraulic cylinder assembly 100 provided by the disclosure can provide larger output force.
For the above-described effect that the area of the first end surface 121 of the first piston 12 is larger than the area of the second end surface 122 thereof, the area of the third end surface 221 of the second piston 22 is larger than the area of the second end surface 122 of the first piston 12, so that the output force of the second piston 22 is larger than the input force received by the first piston 12 can be achieved, for ease of understanding, a calculation will be described below with reference to the exemplary embodiment shown in fig. 8.
As shown in fig. 8, the area of the first end surface 121 is S 1, the area of the second end surface 122 is S 2, the area of the third end surface 221 is S 3, the input force applied to the first piston 12, that is, the force received by the first end surface 121 of the first piston 12 is F 1, the force output by the second end surface 122 of the first piston 12 is F 2, and the force received by the third end surface 221 of the second piston 22 is F 3. As can be seen from the formulas of force, pressure and area, F 1＝P1S1,F2＝P2S2,F3＝P3S3, under the condition that the pressure in the hydraulic cylinder is the same, namely P 1＝P2＝P3, the force applied by the first piston 12 is the same as the force output by the first piston 12, namely F 1＝F2, can be obtainedThat is to say that the first and second,And the force F 3 received by the second piston 22 is equal to the force F 4 output by the second piston 22, and therefore, the force output by the second piston 22In other words, the output force of the second piston 22 is equal to the ratio of the area of the third end surface 221 to the area of the second end surface 122 multiplied by the input force, and the area of the third end surface 221 is larger than the area of the second end surface 122, so that the output force of the hydraulic cylinder assembly provided by the disclosure is larger than the input force thereof, and the effect of increasing the output force can be achieved.
Alternatively, the first cylinder 11 includes a first cylinder groove 13, the first piston 12 is installed in the first cylinder groove 13, the second cylinder 21 includes a second cylinder groove 23, and the second piston 22 is installed in the second cylinder groove 23. The inner diameter of the first cylinder groove 13 is equal to the outer diameter of the first end surface 121, the inner diameter of the second cylinder groove 23 is equal to the outer diameter of the third end surface 221, the outer diameter of the first end surface 121 is equal to the outer diameter of the third end surface 221, and the ratio of the outer diameter of the third end surface 221 to the outer diameter of the second end surface 122 is greater than or equal to 2. The first cylinder 11 and the second cylinder 21 having the same inner diameter can achieve the same internal pressure, and at this time, the magnitude of the output force will increase by a power of the square of the ratio of the outer diameter of the third end surface 221 to the outer diameter of the second end surface 122.
Specifically, the output force is calculated by taking the ratio of the outer diameter of the third end surface 221 to the outer diameter of the second end surface 122 as an example of 2, where the outer diameter of the second end surface 122 is set to be D 2 and the outer diameter of the third end surface 221 is set to be D 3. By the above reasoningCan obtainIn the case where the first cylinder 11 and the second cylinder 21 have the same inner diameter (i.e., the oil pressure is the same), the output force of the second piston 22 is 4 times the input force received by the first piston 12.
It should be noted that the hydraulic cylinder assembly 100 may be applied to any suitable technical field, for example, the hydraulic cylinder assembly 100 may be applied to a hydraulic brake device of a vehicle, and it is understood that when the hydraulic cylinder assembly 100 is applied to the hydraulic brake device, the fourth end surface 222 of the second piston 22 is used to push the brake pad to move, so that the brake pad can compress the friction pad to implement braking. It will be appreciated that for the application of the hydraulic cylinder assembly 100 to a hydraulic brake device, the first cylinder block 11 may be mounted to the caliper body or may be integrally formed with the caliper body (i.e., the first cylinder block 11 is part of the caliper body or the first cylinder groove of the first cylinder block 11 is formed in the caliper body).
The first hydraulic cylinders 1 and the second hydraulic cylinders 2 mentioned above may or may not be directly connected to each other, and the number of the first hydraulic cylinders 1 may be one or more, which is not particularly limited in this disclosure.
In the case where the first and second hydraulic cylinders 1 and 2 are connected to each other, in the first embodiment provided in the present disclosure, as shown in fig. 1 to 8, the second cylinder 21 of the present disclosure may be connected to the first cylinder 11, the second cylinder 21 being formed with a second through hole 211 for the first piston 12 to pass therethrough, and the second end surface 122, the inner surface of the second cylinder 21, and the third end surface 221 together defining the second oil chamber 4. As such, when the number of the first cylinders 1 of the hydraulic cylinder assembly 100 of the present disclosure is one, and the first cylinders 11 of the first cylinders 1 and the second cylinders 21 of the second cylinders 2 are connected to each other, the integration level of the entire hydraulic cylinder assembly 100 can be made high, the volume is small, the occupied space is small, and the hydraulic cylinder assembly 100 can be installed as a whole.
In the second embodiment of the present disclosure, as shown in fig. 9, the first cylinders 1 are plural, the first cylinders 11 of the plural first cylinders 1 are sequentially connected, the first through hole 111 on the first cylinder 11 of the first cylinder 1 located at the head end among the plural first cylinders 1 is used to communicate with the oil supply source, the first cylinder 11 of the first cylinder 1 located at the tail end among the plural first cylinders 1 is connected with the second cylinder 21, the first piston 12 of the first cylinder 1 of each adjacent two first cylinders 1 passes through the first through hole 111 on the first cylinder 11 of the next first cylinder 1, the first piston 12 of the first cylinder 1 located at the tail end among the plural first cylinders 1 passes through the second through hole 211, and the second end face 122 of the first piston 12 and the inner surface and the third end face 221 of the second cylinder 21 together define the second oil chamber 4. In this way, compared to the solution in which one first hydraulic cylinder 1 is provided, the present embodiment can further raise the output force of the second piston 22.
In the case where the first hydraulic cylinder 1 and the second hydraulic cylinder 2 are not directly connected to each other, in the third embodiment of the present disclosure, as shown in fig. 11, the second end surface 122 and the inner surface of the first cylinder block 11 together define a first sub-oil chamber 41, the third end surface 221 and the inner surface of the second cylinder block 21 together define a second sub-oil chamber 42, the first sub-oil chamber 41 communicates with the second sub-oil chamber 42 through the first oil delivery pipe 81, and the first sub-oil chamber 41, the oil passage inside the first oil delivery pipe 81, and the second sub-oil chamber 42 together constitute a second oil chamber 4. In this way, the first cylinder 11 and the second cylinder 21 can be placed separately, and the second cylinder 21 can be placed at a position where the output force is required, so that the requirement for the installation space can be further reduced, and the device can be applied to a more limited installation space.
In the fourth embodiment provided in the present disclosure, as shown in fig. 12, the first cylinders 1 are plural, the first cylinders 11 of the plural first cylinders 1 are sequentially connected in series through the second oil delivery pipe 82, the first through hole 111 on the first cylinder 11 of the first cylinder 1 located furthest upstream among the plural first cylinders 1 is used for communication with the oil supply source, the second end face 122 of the first piston 12 of the first cylinder 1 located furthest downstream among the plural first cylinders 1 and the inner surface of the first cylinder 11 of the first cylinder 1 together define the first sub-oil chamber 41, the second end face 122 of the first piston 12 of the first cylinder 1 located furthest upstream among each adjacent two first cylinders 1 and the inner surface of the first cylinder 11 of the first cylinder 1 together define the third oil chamber 83, and the third oil chamber 83 is communicated with the first oil chamber 3 of the first cylinder 1 located downstream among every adjacent two first cylinders 1 through the second oil delivery pipe 82. In this way, a plurality of first hydraulic cylinders 1 can be separately placed, and the second hydraulic cylinders 2 can be placed at positions where output force is required, so that the requirement for installation space can be further reduced, and the hydraulic cylinder can be suitable for more limited installation space.
In the fifth embodiment provided in the present disclosure, as shown in fig. 13, the first cylinders 1 are plural, the first cylinders 11 of the plural first cylinders 1 are sequentially connected, the first through hole 111 on the first cylinder 11 of the first cylinder 1 located at the head end of the plural first cylinders 1 is used for communicating with the oil supply source, the second end face 122 of the first piston 12 of the first cylinder 1 located at the tail end of the plural first cylinders 1 and the inner surface of the first cylinder 11 of the first cylinder 1 together define the first sub-oil chamber 41, and the first piston 12 of the first cylinder 1 of the preceding first cylinder 1 of every two adjacent first cylinders 1 passes through the first through hole 111 on the first cylinder 11 of the following first cylinder 1. In this way, the first hydraulic cylinders 1 can be connected with each other and placed at the same position, and the second hydraulic cylinders 2 can be placed at the position where the output force is required, so that the requirement on the installation space is reduced.
Alternatively, as shown in fig. 2, 8, and 9, in the case where the second cylinder 21 is connected to the first cylinder 11, at least part of the second cylinder 21 is located inside the first cylinder 11. In this way, the axial length of the hydraulic cylinder assembly 100 can be further reduced, the overall volume of the hydraulic cylinder assembly 100 can be reduced, and the hydraulic cylinder assembly 100 can be further enabled to be suitable for a space-limited installation environment without affecting the output force.
Alternatively, in the case where the first hydraulic cylinders 1 are plural and connected to each other, as shown in fig. 9 and 13, the first cylinder block 11 of one first hydraulic cylinder 1 of the adjacent two first hydraulic cylinders 1 is at least partially located within the first cylinder block 11 of the other first hydraulic cylinder 1. In this way, the axial length of the hydraulic cylinder assembly 100 can be further reduced, and the overall volume of the hydraulic cylinder assembly 100 can be reduced.
Alternatively, as shown in fig. 2, 5 and 9, the first piston 12 may include a piston body 123 and a piston rod 124 protruding from the piston body 123, the piston rod 124 is used for passing through the second through hole 211, an end surface of the piston body 123 away from the piston rod 124 is a first end surface 121, an end surface of the piston rod 124 away from the piston body 123 is a second end surface 122, a first air gap 51 is formed between an end of the piston body 123 close to the piston rod 124 and an outer surface of the second cylinder 21, a first air vent 52 communicating with the first air gap 51 is formed on the first cylinder 11, a first oil compensating hole 61 communicating with the first air gap 51 and the second oil chamber 4 is formed on the second cylinder 21, and the first oil compensating pipe 62 passes through the first air vent 52 and the first oil compensating hole 61 and communicates with the second oil chamber 4.
In the above embodiment, the first vent hole 52 has a dual function, the first function is to make the first air gap 51 communicate with the external atmosphere through the first vent hole 52 to maintain the first air gap 51 consistent with the external atmosphere, so that the movement of the first piston 12 is not affected by the air pressure in the first air gap 51, and the second function is to be used as the penetrating hole of the first oil compensating pipe 62 to supplement the oil in the second oil cavity 4, so as to avoid the opening of the first oil compensating pipe 62 penetrating into other positions of the first cylinder 11, thereby reducing the number of openings on the first cylinder 11, and being beneficial to enhancing the structural strength of the first cylinder 11.
It will be appreciated that, as shown in fig. 2 and 9, a corresponding shut-off valve 63 may be provided on the first oil replenishment pipe 62 to shut off the first oil replenishment pipe 62 after the second oil chamber 4 is filled with the hydraulic medium, so that the second oil chamber 4 is in a sealed state.
Alternatively, as shown in fig. 2, the center axis of the first vent hole 52 and the center axis of the first oil supply hole 61 are located in the same plane parallel to the moving direction of the first piston 12. In this way, the air outlet of the first air vent 52 and the oil inlet of the first oil compensating hole 61 can reach a shorter distance, and the first oil compensating pipe 62 can directly enter the first oil compensating hole 61 in a shorter path after passing through the first air vent 52. That is, the first oil replenishment pipe 62 can be made shorter in length to shorten the oil replenishment path.
Of course, other embodiments may be used to supplement the oil in the second oil chamber 4, for example, in one embodiment of the present disclosure, as shown in fig. 10, a first oil supplementing port 71 communicating with the second oil chamber 4 is formed in the second piston 22. Wherein, the first oil supplementing port 71 is provided with a first stop valve 72, or the first oil supplementing port 71 is provided with a first detachable blocking piece 73. In this way, the second oil cavity 4 can be directly replenished with oil through the first oil replenishing port 71, and the second cylinder 21 does not need to be opened, thereby being beneficial to enhancing the structural strength and the sealing performance of the second cylinder 21.
In another embodiment of the present disclosure, as shown in fig. 11 to 13, a second oil compensating port 213 communicating with the second sub oil chamber 42 is formed on the second cylinder 21, and a second shut-off valve 214 or a detachable second blocking member 215 is provided at the second oil compensating port 213. In this way, the second sub oil chamber 42 can be replenished through the second oil replenishment port 213, and then the hydraulic oil in the second sub oil chamber 42 can be kept at the oil pressure at the time of braking through the second shutoff valve 214 or the second shutoff member 215.
As shown in fig. 12, a fourth oil compensating pipe 821 may be connected to the second oil transporting pipe 82, and a fourth stop valve 822 may be provided on the fourth oil compensating pipe 821. The second oil delivery pipe 82 can be replenished through the fourth oil replenishment pipe 821, thereby replenishing the third oil chamber 83 and the first oil chamber 3 which are communicated with the second oil delivery pipe 82, and the second oil delivery pipe 82, the first oil chamber 3, and the third oil chamber 83 can all maintain the oil pressure at the time of braking through the fourth shut-off valve 822.
Meanwhile, as shown in fig. 11 to 13, a third oil compensating pipe 811 may be connected to the first oil pipe 81, and a third stop valve 812 may be provided to the third oil compensating pipe 811. The first oil delivery pipe 81 is directly replenished with oil through the third oil replenishing pipe 811, so that the oil replenishing of the first and second oil sub-chambers 41 and 42 communicated with the first oil delivery pipe 81 is realized, and the first oil delivery pipe 81, the first and second oil sub-chambers 41 and 42 can each maintain the oil pressure at the time of braking through the third shut-off valve 812.
In the case where there are a plurality of first hydraulic cylinders 1 and are connected to each other in the above-described embodiment, in order to facilitate the replenishment of the first oil chamber 3 in at least part of the first hydraulic cylinders 1 among the plurality of first hydraulic cylinders 1, as shown in fig. 9 and 13, the piston body 123 of the first piston 12 of the preceding one of the two adjacent first hydraulic cylinders 1 and the first cylinder body 11 of the following one of the first hydraulic cylinders 1 have the second air gap 53 therebetween, the first cylinder body 11 of the preceding one of the two adjacent first hydraulic cylinders 1 is formed with the second air vent hole 54, and the first cylinder body 11 of the following one of the first hydraulic cylinders 1 is formed with the second oil compensating hole 64, and the second oil compensating pipe 65 passes through the second air vent hole 54 and the second oil compensating hole 64 to communicate with the first oil chamber 3 of the following one of the first hydraulic cylinders 1.
Alternatively, the center axis of the second vent hole 54 and the center axis of the second oil compensating hole 64 are located in the same plane parallel to the moving direction of the first piston 12 so that the second oil compensating pipe 65 passes through the second vent hole 54 and the second oil compensating hole 64.
Alternatively, in order to achieve the connection of the first cylinder 11 and the second cylinder 21 in the case where the first cylinder 11 and the second cylinder 21 are connected to each other, as shown in fig. 4, a first mounting boss 112 is formed on the first cylinder 11, a second mounting boss 212 is formed on the second cylinder 21, a first mounting hole for passing a fastener is formed on the first mounting boss 112, and a second mounting hole for passing a fastener is formed on the second mounting boss 212. In this manner, a secure mounting of the first cylinder block 11 and the second cylinder block 21 may be achieved, which is advantageous for enhancing the integrity and structural strength of the hydraulic cylinder assembly 100.
Alternatively, in the case where the first cylinder block 11 is plural and connected to each other, the plural first cylinder blocks 11 may be welded together or connected together by the plural first mounting bosses 112.
Alternatively, the first mounting hole may be a threaded hole, the second mounting hole may be a countersunk hole, and the fastener may be a countersunk bolt.
Alternatively, as shown in fig. 2 and 3, an annular groove 91 is formed on the inner surface of the second cylinder 21, an annular sealing ring 93 is sleeved on the outer peripheral surface of the second piston 22, the annular sealing ring 93 is located in the annular groove 91, and a chamfer 92 is formed on the side wall of the annular groove 91 facing away from the third end 221. In this way, on the one hand, the annular seal ring 93 can play a role in sealing a gap between the second piston 22 and the second cylinder body 21 to avoid leakage of oil in the second oil chamber 4, and on the other hand, after the second piston 22 loses pressure, the annular seal ring 93 can rebound to drive the second piston 22 to reset. Wherein the provision of chamfer 92 helps to accommodate deformed ring seal 93 and helps to increase the amount of deformation of ring seal 93, providing greater resiliency to the return of second piston 22.
In the above embodiment, the operation of the ring seal 93 is based on the principle that when the second piston 22 is pushed by the first piston 12, the ring seal 93 deforms to some extent in the movement direction of the second piston 22 along with the movement of the second piston 22. When the second piston 22 loses pressure (i.e. the first hydraulic cylinder 1 loses hydraulic pressure), the annular sealing ring 93 resumes its deformation and drives the second piston 22 to return.
In the case where there are a plurality of first hydraulic cylinders 1, the areas of the first end surfaces 121 of the plurality of first pistons 12 may be the same, and the areas of the second end surfaces 122 of the plurality of first pistons 12 may be the same. In this way, on the one hand, the control of the output force can be achieved by controlling the number of first pistons 12, which is advantageous for achieving the control of the output force, and on the other hand, for building standardized fittings, which are very convenient to process, install, replace and maintain.
According to another aspect of the present disclosure, there is provided a hydraulic brake device including the hydraulic cylinder assembly 100, a brake pad, and a friction plate as described above, the fourth end face 222 of the second piston 22 being configured to bear against the brake pad and urge the brake pad toward the friction plate to compress the friction plate.
The hydraulic brake device thus configured can provide a greater output force through the second piston 22 of the hydraulic cylinder assembly 100, thereby making the braking effect of the brake pad better. Also, the hydraulic cylinder assembly 100 of the present disclosure has a small requirement for installation space, and can be applied to a limited installation space. When the hydraulic cylinder assembly 100 is applied to a hydraulic braking device, the hydraulic cylinder assembly 100 disclosed by the disclosure can have smaller cylinder diameter and smaller number of hydraulic cylinders under the requirement of the same braking force, which is beneficial to realizing miniaturization, light weight and high efficiency of the hydraulic cylinders in the hydraulic braking device.
According to still another aspect of the present disclosure, there is provided a vehicle including the hydraulic brake device described above. The vehicle provided with the hydraulic braking device can have a more stable and strong braking effect, so that the braking safety of the vehicle can be improved.
The preferred embodiments of the present disclosure have been described in detail above with reference to the accompanying drawings, but the present disclosure is not limited to the specific details of the embodiments described above, and various simple modifications may be made to the technical solutions of the present disclosure within the scope of the technical concept of the present disclosure, and all the simple modifications belong to the protection scope of the present disclosure.
In addition, the specific features described in the foregoing embodiments may be combined in any suitable manner, and in order to avoid unnecessary repetition, the present disclosure does not further describe various possible combinations.
Moreover, any combination between the various embodiments of the present disclosure is possible as long as it does not depart from the spirit of the present disclosure, which should also be construed as the disclosure of the present disclosure.
Claims (17)
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| CN202211057424.2A CN117662559B (en) | 2022-08-31 | 2022-08-31 | Hydraulic cylinder assembly, hydraulic brake device and vehicle |
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| CN103148046A (en) * | 2013-03-14 | 2013-06-12 | 西安交通大学 | Alternating current servo direct-drive supercharged three-layer piston electrohydraulic cylinder and supercharging method |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US4471614A (en) * | 1982-06-07 | 1984-09-18 | American Standard Inc. | Hydro-pneumatic actuator with automatic slack adjuster |
| CN85103772A (en) * | 1985-05-16 | 1986-11-12 | 恩福基础理论研究有限公司 | Has the oil hydraulic cylinder that power multiplication is used |
| US6035634A (en) * | 1999-02-09 | 2000-03-14 | Latch-Tool Development Co. Llc | Compact, resistance regulated, multiple output hydraulic tool and seal valve arrangement |
| CN101092982B (en) * | 2007-07-27 | 2011-06-01 | 韩顺和 | Boosting oil cylinder |
| CN101737375A (en) * | 2009-12-31 | 2010-06-16 | 白炳生 | Top cylinder center oil-taking two-level sleeve cylinder |
| CN103671643A (en) * | 2012-09-04 | 2014-03-26 | 襄阳彼勒液压机械有限公司 | Wet type vehicle brake braking force increasing mechanism |
| CN111503088B (en) * | 2020-05-07 | 2022-04-29 | 山东万通液压股份有限公司 | Single-telescopic thrust multiplication hydraulic cylinder |
| CN111734712B (en) * | 2020-07-31 | 2025-03-21 | 中交第一航务工程局有限公司 | Two-stage booster hydraulic cylinder |
| CN216382011U (en) * | 2021-08-25 | 2022-04-26 | 油机机械工业（中国）有限公司 | Oil pressure booster for oil pressure cylinder |
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| CN103148046A (en) * | 2013-03-14 | 2013-06-12 | 西安交通大学 | Alternating current servo direct-drive supercharged three-layer piston electrohydraulic cylinder and supercharging method |
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