CN110696796A - Double-relay valve of full hydraulic braking system - Google Patents
Double-relay valve of full hydraulic braking system Download PDFInfo
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- CN110696796A CN110696796A CN201911131018.4A CN201911131018A CN110696796A CN 110696796 A CN110696796 A CN 110696796A CN 201911131018 A CN201911131018 A CN 201911131018A CN 110696796 A CN110696796 A CN 110696796A
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- valve
- valve body
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- sleeve
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
- B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
- B60T13/12—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid
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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
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
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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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
- F16K11/20—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by separate actuating 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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
- F16K31/1221—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston one side of the piston being spring-loaded
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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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
- F16K31/1225—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston with a plurality of pistons
Abstract
The invention discloses a double relay valve of a full hydraulic brake system, which comprises a cover plate, a pressure plate, a first valve body and a second valve body which are sequentially arranged from left to right, wherein the cover plate, the pressure plate and the first valve body are fixedly connected, and the first valve body and the second valve body are fixedly connected; the brake pressure is improved through the rapid reaction of the relay valves, and then the brake pressure is transmitted into the brake mechanism, so that the brake can obtain corresponding brake pressure and flow as required, and the problems that the brake pressure is insufficient due to pressure drop caused by overlong pipelines, the brake delay is delayed, and the driving safety is influenced are solved.
Description
Technical Field
The invention relates to the technical field of relay valves, in particular to a double-relay valve of a full hydraulic braking system.
Background
The mining dump truck has the advantages of high operation efficiency, relatively low operation cost and the like, and is widely applied to large-scale surface mine transportation operation. However, the mining dump truck has a large dead weight, a large weight after full load, which can reach several hundred tons, and a high traveling speed, which can reach about 60km/h, and has a severe traveling environment and road conditions and frequent braking, so that the braking system of the dump truck is required to be very safe and reliable, and the traditional air brake system can not meet the use requirements at all.
The full hydraulic braking system has the advantages of high braking pressure, high response speed, more reliable braking effect and the like due to the use of a main engine power source, is widely applied to wheel type engineering machinery at present, and is the best choice for the mining dump truck due to the use of the full hydraulic braking system. However, the mining dump truck is large in size and long in distance from a cab to each hub, when full hydraulic braking is adopted, pressure from a brake pedal (or a handle) to a brake actuating mechanism is reduced due to overlong pipelines, so that the braking force is insufficient, braking delay is generated, and the driving safety is influenced.
Disclosure of Invention
In view of the above, the invention provides a double relay valve of a full hydraulic braking system, which adopts different relay valves, and rapidly reacts through the relay valves, so that the braking pressure is improved and then transmitted into a braking mechanism, a brake can obtain corresponding braking pressure and flow according to requirements, the problems that the pressure is too long and pressure drop causes insufficient braking force and braking delay to influence driving safety are avoided, and the double relay valve has the advantages of high safety coefficient, low cost and rapid response.
On one hand, the invention provides a double relay valve of a full hydraulic brake system, which comprises a cover plate, a pressure plate, a first valve body and a second valve body which are sequentially arranged from left to right, wherein the cover plate, the pressure plate and the first valve body are fixedly connected, and the first valve body and the second valve body are fixedly connected;
the valve comprises a first valve body, a second valve body, a first valve core, a second valve core, a first spring, a second spring and a sleeve, wherein two main cavity holes are formed in the first valve body, a valve sleeve, a spring seat, the first spring, the second spring and the sleeve are arranged in one main cavity hole, one end of the valve sleeve is connected with a pressing plate, the other end of the valve sleeve is connected with one end of the spring seat through the first valve core, the other end of the spring seat is connected with the sleeve through a push rod plunger, the push rod plunger is arranged in an inner hole of the sleeve, the first spring and the second spring are coaxially sleeved on the spring seat, the radial diameter of the second spring is larger than that of the first spring, the first valve core is arranged in the valve sleeve, the; the two main cavities are arranged in the same way as the one main cavity;
be provided with control oil duct PX on the second valve body, the push rod plunger with control oil duct PX communicates with each other, has seted up B1 mouth and P1 mouth on the valve barrel of one of them main cavity downthehole installation, has seted up B2 mouth and P1 mouth on the valve barrel of two of them downthehole installations of main cavity, the T mouth has been seted up to the inside of first valve body: when the P1 port enters pressure oil, the B1 port and the B2 port are communicated with the T port respectively; when the control oil passage PX enters pressure oil, the port B1 and the port B2 are respectively communicated with the port P1 and are not communicated with the port T.
Furthermore, the double relay valve of the full hydraulic braking system further comprises a first O-shaped sealing ring and a rectangular sealing ring, the rectangular sealing ring is arranged on the annular contact surface of the pressure plate and the first valve body, and the first O-shaped sealing ring is arranged on the annular contact surface of the second valve body and the first valve body.
Furthermore, a first annular sealing groove is formed in a contact surface, connected with the first valve body, of the sleeve, and a second O-shaped sealing ring and a first check ring are arranged in the first annular sealing groove.
Furthermore, the valve sleeve is at least provided with two shoulders with different excircle sizes along the radial direction, each shoulder is provided with a second annular sealing groove, and each second annular sealing groove is provided with a third retaining ring and a fourth O-shaped sealing ring.
Further, the sectional areas of the second valve core and the push rod plunger are set to be different in proportion according to the braking force.
Further, the inner portions of two of the main cavity holes and the inner portion of one of the main cavity holes are arranged symmetrically with respect to an axis of the first valve body extending in the left-right direction.
Furthermore, an annular groove a is formed in the pressure plate, and is used for communicating the left cavity d of the valve sleeves installed in the two main cavity holes and communicating with an oil drainage hole L formed in the first valve body, and the oil drainage hole L is communicated with the T port.
Furthermore, the first valve core arranged in one of the main cavity holes is provided with an oil hole c and an inner cavity B1, the first valve core arranged in the two main cavity holes is provided with an oil hole c and an inner cavity B2, and pressure oil of the ports B1 and B2 respectively enters the inner cavities B1 and B2 of the first valve core through the oil hole c.
Furthermore, the double relay valve of the full hydraulic braking system further comprises a first screw and a second screw, the second valve body is connected to the first valve body through the first screw, and the cover plate and the pressure plate are connected to the first valve body through the second screw.
Further, the full hydraulic braking system double relay valve further comprises a first spring washer and a second spring washer: the first spring washer is fixedly arranged on the right end face of the second valve body through a first screw; and the second spring washer is fixedly arranged on the left end surface of the cover plate through a second screw.
The invention provides a double relay valve of a full hydraulic brake system, which comprises a cover plate, a pressure plate, a first valve body, a second valve core, a first valve core, a third spring, a spring seat, a first spring, a second spring, a push rod plunger piston, a sleeve, a second valve body and a valve sleeve.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
fig. 1 is a schematic structural diagram of a dual relay valve of a full hydraulic brake system according to an embodiment of the present invention;
fig. 2 is a schematic diagram of a dual relay valve of a full hydraulic brake system according to an embodiment of the present invention.
Wherein: 1-cover plate, 2-pressure plate, 3-first valve body, 4-second valve core, 5-first valve core, 6-third spring, 7-spring seat, 8-first spring, 9-second spring, 10-push rod plunger, 11-sleeve, 12-first plug, 13-first screw and 14-first spring washer, 15-a second plug, 16-a second valve body, 17-a first O-shaped sealing ring, 18-a second O-shaped sealing ring, 19-a first retainer ring, 20-a third O-shaped sealing ring, 21-a second retainer ring, 22-a fourth O-shaped sealing ring, 23-a third retainer ring, 24-a valve sleeve, 25-a fifth O-shaped sealing ring, 26-a rectangular sealing ring, 27-a second screw and 28-a second spring washer.
Detailed Description
It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict. The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
In the present invention, the terms "left", "right", "top", "bottom", "inner", "outer", "upper", "lower", etc. indicate orientations or positional relationships based on those shown in fig. 1, and are only for convenience of describing the present invention and simplifying the description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and thus should not be construed as limiting the scope of the present invention; meanwhile, the terms "first" and "second" are mainly used to distinguish different components, but do not specifically limit the components.
Fig. 1 is a schematic structural diagram of a double relay valve of a full hydraulic brake system according to an embodiment of the present invention.
Fig. 2 is a schematic diagram of a dual relay valve of a full hydraulic brake system according to an embodiment of the present invention.
As shown in fig. 1 and fig. 2, a full hydraulic brake system double relay valve is provided with a cover plate 1, a pressure plate 2, a first valve body 3 and a second valve body 16 from left to right in sequence, the cover plate 1, the pressure plate 2 and the first valve body 3 are fixedly connected, and the first valve body 3 and the second valve body 16 are fixedly connected: specifically, two main cavity holes are arranged in the first valve body 3, a valve sleeve 24, a spring seat 7, a first spring 8, a second spring 9 and a sleeve 11 are arranged in one main cavity hole, the left end of the valve sleeve 24 is connected with the pressure plate 2, the right end of the valve sleeve is connected with the left end of the spring seat 7 through the first valve core 5, the right end of the first valve core 5 is preferably clamped at the left end of the spring seat 7, the right end of the spring seat 7 is connected with the sleeve 11 through a push rod plunger 10, meanwhile, the push rod plunger 10 is arranged in an inner hole of the sleeve 11, the first spring 8 and the second spring 9 are coaxially sleeved on the spring seat 7, the second spring 9 is used for limiting, the radial diameter of the second spring is larger than that of the first spring 8, the first valve core 5 is arranged in the valve sleeve 24, a second valve core 4 and a third spring 6 are arranged in an inner cavity of the first valve core 5, the third spring 6 is used for resetting, the other end of the spring is contacted with a third spring 6; the two main cavities are arranged in the same way as the main cavity, namely, a valve sleeve 24, a spring seat 7, a first spring 8, a second spring 9, a sleeve 11, a first valve core 5, a push rod plunger 10, a second valve core 4 and a third spring 6 are also arranged in the two main cavities, and the components are arranged in the same way as the components of the main cavity; meanwhile, a control oil duct PX is arranged on the second valve body 16, the push rod plunger 10 is communicated with the control oil duct PX, a B1 port and a P1 port are formed in the valve sleeve 24 arranged in one main cavity, a B2 port and a P1 port are formed in the valve sleeve 24 arranged in two main cavities, and a T port is formed in the first valve body 3: when the P1 port enters pressure oil, the B1 port and the B2 port are communicated with the T port respectively; when the control oil passage PX enters pressure oil, the port B1 and the port B2 are respectively communicated with the port P1 and are not communicated with the port T. Preferably, the inner portions of two of the main bores and the inner portion of one of the main bores are symmetrically arranged with respect to an axis of the first valve body 3 extending in the left-right direction in the present invention. The sectional areas of the second spool 4 and the plunger 10 are set to be different in proportion according to the magnitude of the braking force.
In a further technical scheme, the double relay valve of the full hydraulic brake system further comprises a first screw 13, a first spring washer 14, a second screw 27 and a second spring washer 28, the second valve body 16 is connected to the first valve body 3 through the first screw 13, the first spring washer 14 is fixedly arranged on the right end face of the second valve body 16 through the first screw 13, meanwhile, the cover plate 1 and the pressure plate 2 are connected to the first valve body 3 through the second screw 27, and the second spring washer 28 is fixedly arranged on the left end face of the cover plate 1 through the second screw 27. Preferably, the length of the first screw 13 is greater than the extent of the second screw 27. It should be noted that a plurality of plugs are disposed on the second valve body 16 for plugging the redundant pipe openings in the second valve body 16, specifically, the bottom of the second valve body 16 is disposed with the first plug 12, and the right end surface thereof is disposed with the second plug 15.
Meanwhile, in order to improve the sealing performance of the double relay valve, as shown in fig. 1, the double relay valve of the full hydraulic brake system further includes a first O-ring 17, a rectangular seal ring 26, a second O-ring 18 and a first retainer ring 19, the rectangular seal ring 26 is disposed on an annular contact surface of the pressure plate 2 and the first valve body 3, the first O-ring 17 is disposed on an annular contact surface of the second valve body 16 and the first valve body 3, and the second O-ring 18 and the first retainer ring 19 are mounted in a first annular seal groove disposed on a contact surface of the sleeve 11 connected to the first valve body 3.
In a preferred embodiment of the present invention, at least two shoulders with different sizes of outer circles are radially disposed on the valve sleeve 24, each shoulder is provided with a second annular seal groove, and each second annular seal groove is provided with a third retaining ring 23 and a fourth O-ring 22 for preventing pressure oil from permeating through a contact surface between the valve sleeve 24 and the valve body 3.
In addition, as shown in fig. 1, the pressure plate 2 is provided with an annular groove a for communicating the left cavity d of the valve sleeves 24 installed in the two main cavity holes, and communicating with an oil drain hole L provided on the first valve body 3, the oil drain hole L communicating with the T port; meanwhile, as shown in fig. 1, the first valve core 5 disposed in one of the main cavity holes is provided with an oil hole c and an inner cavity B1, the first valve core 5 disposed in the two main cavity holes is provided with an oil hole c and an inner cavity B2, and the pressure oil of the B1 and B2 respectively enters the inner cavities B1 and B2 of the first valve core 5 through the oil hole c.
The working principle of the relay valve of the full hydraulic braking system is briefly described as follows: : when pressure oil enters the port P1, all the components are kept at the middle position, the pressure oil P1 is stopped at the outer side of the large valve core 5, the ports B1 and B2 of the working ports are communicated with the port T, the brake actuating mechanism is in a pressure relief state, and the brake mechanism does not work; when pressure oil enters a PX control port, the push rod plunger 10 starts to move under the action of the pressure oil and transmits the force to the first valve core 5 through the first spring 8, the first valve core 5 moves leftwards, when the first valve core 5 moves to a P1 port pressure connection position (namely when a throttling port on the first valve core 5 is connected with a P1 port), ports B1 and B2 and a T port are cut off in advance, the pressure oil of the P1 port cut off at the outer side of the first valve core 5 enters ports B1 and B2, the pressure oil of the ports B1 and B2 enters inner cavities B1 and B2 of the first valve core 5 through an oil hole c on the first valve core 5, so that the rightward force generated by the first valve core 5 is balanced with the PX force transmitted on the second valve body 16, and the pressure oil starts to be output by B1 and B2; meanwhile, the annular groove a is formed in the pressure plate 2, the cavity d on the left side of the valve sleeve 24 is communicated with an oil drainage hole L formed in the first valve body 3, leakage oil generated by matching the first valve core 5, the second valve core 4 and the valve sleeve 24 can be communicated with an L port through the groove a, the leakage oil is discharged into the T port, the pressure of the cavity on the left sides of the second valve core 4 and the first valve core 5 is kept to be zero, and accurate control of pressure and flow is guaranteed.
In addition, it should be mentioned that in the present invention, the output pressure of ports B1 and B2 can be amplified or reduced in proportion to the PX input pressure, and is linearly proportional to the PX input pressure signal, and at the same time, the diameter of the cross section of the first valve spool 5 can be set, so that the braking is fast and response is realized without delay through the difference of the braking flow of the hydraulic oil input ports B1 and B2 from port P1, and the requirements of different pressures required by the front and rear wheels due to different braking torques are met.
In conclusion, the invention quickly responds through the relay valve, proportionally and quickly transmits high-pressure large-flow brake hydraulic oil to the front brake and the rear brake, adopts different relay valves according to different brake pressures of the front wheel and the rear wheel, improves the brake pressure proportion and then transmits the brake pressure proportion into the brake mechanism, so that the brakes can obtain corresponding brake pressure and flow according to requirements, avoids the problem that the brake force is insufficient due to pressure drop caused by overlong pipelines in a brake system, influences the driving safety, can convert the brake pressure according to requirements, meets the requirements that the front wheel and the rear wheel use different pressures due to different brake torques, and has the advantages of high safety factor, low cost and quick response.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (10)
1. The double relay valve of the full hydraulic brake system is characterized by comprising a cover plate (1), a pressure plate (2), a first valve body (3) and a second valve body (16) which are sequentially arranged from left to right, wherein the cover plate (1), the pressure plate (2) and the first valve body (3) are fixedly connected, and the first valve body (3) and the second valve body (16) are fixedly connected;
the valve is characterized in that two main cavity holes are formed in the first valve body (3), a valve sleeve (24), a spring seat (7), a first spring (8), a second spring (9) and a sleeve (11) are installed in one main cavity hole, one end of the valve sleeve (24) is connected with the pressing plate (2), the other end of the valve sleeve is connected with one end of the spring seat (7) through a first valve core (5), the other end of the spring seat (7) is connected with the sleeve (11) through a push rod plunger (10), the push rod plunger (10) is arranged in an inner hole of the sleeve (11), the first spring (8) and the second spring (9) are coaxially sleeved on the spring seat (7), the radial diameter of the second spring (9) is larger than that of the first spring (8), the first valve core (5) is installed in the valve sleeve (24), a second valve core (4) and a third spring (6) are arranged in an inner cavity of the first valve core (5), one end of the second valve core (4) is abutted against the pressure plate (2), and the other end of the second valve core is contacted with the third spring (6); the two main cavities are arranged in the same way as the one main cavity;
the second valve body (16) is provided with a control oil channel PX, the push rod plunger (10) is communicated with the control oil channel PX, a B1 port and a P1 port are formed in a valve sleeve (24) arranged in one main cavity hole, a B2 port and a P1 port are formed in the valve sleeve (24) arranged in two main cavity holes, and a T port is formed in the first valve body (3): when the P1 port enters pressure oil, the B1 port and the B2 port are communicated with the T port respectively; when the control oil passage PX enters pressure oil, the port B1 and the port B2 are respectively communicated with the port P1 and are not communicated with the port T.
2. The double relay valve of full hydraulic brake system according to claim 1, further comprising a first O-ring (17) and a rectangular seal (26), wherein the rectangular seal (26) is disposed on the annular contact surface of the pressure plate (2) and the first valve body (3), and the first O-ring (17) is disposed on the annular contact surface of the second valve body (16) and the first valve body (3).
3. The double relay valve of full hydraulic brake system according to claim 2, wherein the contact surface of the sleeve (11) with the first valve body (3) is provided with a first annular sealing groove, and the second O-ring (18) and the first retainer ring (19) are arranged in the first annular sealing groove.
4. The dual relay valve of full hydraulic brake system as recited in claim 3, wherein said valve housing (24) is provided with at least two shoulders having different outer circumferences along a radial direction, each of said shoulders is provided with a second annular sealing groove, and each of said second annular sealing grooves is provided with a third retainer ring (23) and a fourth O-ring (22).
5. The dual relay valve of full hydraulic brake system as claimed in claim 1, wherein the cross sectional area of the second spool (4) and the plunger (10) are sized to be differently proportional according to the magnitude of braking force.
6. The double relay valve of full hydraulic brake system according to any one of claims 1 to 5, wherein the internal arrangement of two of the main bores and the internal arrangement of one of the main bores are arranged symmetrically with respect to an axis of the first valve body (3) extending in the left-right direction.
7. The double relay valve of a full hydraulic brake system as recited in claim 6, wherein the pressure plate (2) is provided with an annular groove a for communicating the left cavity d of the valve sleeve (24) installed in the two main cavity holes and communicating with an oil drainage hole L provided on the first valve body (3), and the oil drainage hole L is communicated with the T port.
8. The double relay valve of the full hydraulic brake system according to claim 7, wherein the first valve core (5) disposed in one of the main cavity holes is provided with an oil hole c and an inner cavity B1, the first valve core (5) disposed in the two main cavity holes is provided with an oil hole c and an inner cavity B2, and pressure oil of the ports B1 and B2 respectively enters the inner cavities B1 and B2 of the first valve core (5) through the oil hole c.
9. The double relay valve of full hydraulic brake system according to claim 1, further comprising a first screw (13) and a second screw (27), wherein the second valve body (16) is connected to the first valve body (3) by the first screw (13), and the second screw (27) connects the cover plate (1) and the pressure plate (2) to the first valve body (3).
10. The dual relay valve of full hydraulic brake system as claimed in claim 9, further comprising a first spring washer (14) and a second spring washer (28): the first spring washer (14) is fixedly arranged on the right end face of the second valve body (16) through a first screw (13); and the second spring washer (28) is fixedly arranged on the left end surface of the cover plate (1) through a second screw (27).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911131018.4A CN110696796A (en) | 2019-11-19 | 2019-11-19 | Double-relay valve of full hydraulic braking system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911131018.4A CN110696796A (en) | 2019-11-19 | 2019-11-19 | Double-relay valve of full hydraulic braking system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110696796A true CN110696796A (en) | 2020-01-17 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911131018.4A Pending CN110696796A (en) | 2019-11-19 | 2019-11-19 | Double-relay valve of full hydraulic braking system |
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| Country | Link |
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| CN (1) | CN110696796A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113753011A (en) * | 2021-09-14 | 2021-12-07 | 青岛纳惟信动力科技有限公司 | Hydraulic control parallel two-way hydraulic power brake valve |
-
2019
- 2019-11-19 CN CN201911131018.4A patent/CN110696796A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113753011A (en) * | 2021-09-14 | 2021-12-07 | 青岛纳惟信动力科技有限公司 | Hydraulic control parallel two-way hydraulic power brake valve |
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