Device, method, braking device and vehicle for hydraulic retarder pressure control

Abstract

The application provides a hydraulic retarder pressure control device, method, braking equipment and vehicle. The device comprises a switching valve, a first switch valve and a second switch valve. The switching valve can be switched between a first opening position and a first stop position. When the switching valve is in the first opening position, the target retarder cavity is communicated with the air source. When the switching valve is in the first stop position, the target retarder cavity is communicated with the external atmosphere. The first valve port of the first switch valve is communicated with the air source, and the second valve port is communicated with the external atmosphere. The first switch valve can be switched between a second opening position and a second stop position. When the first switch valve is in the second opening position, the first valve port and the third valve port are communicated. When the first switch valve is in the second stop position, the second valve port is respectively communicated with the third valve port and the fourth valve port. The fifth valve port of the second switch valve is communicated with the third valve port, the sixth valve port is respectively communicated with the fourth valve port and the switching valve, and the sixth valve port and the fifth valve port can be communicated or isolated. The application has strong anti-pollution and low failure rate.

Description

Technical Field

[0001] This invention relates to the field of braking technology, and in particular to devices, methods, braking equipment, and vehicles for controlling the pressure of hydraulic retarders. Background Technology

[0002] Hydraulic retarders, as auxiliary braking devices for heavy-duty commercial vehicles such as heavy-duty trucks and mining trucks, play a crucial role in vehicle safety. Most domestically produced hydraulic retarders employ pneumatic control, using air to force oil from the retarder chamber into the working chamber. In other words, the greater the air pressure entering the retarder chamber, the greater the torque of the hydraulic retarder.

[0003] In existing technologies, proportional pressure valves are typically used to control air pressure. Because they operate using a pneumatic-oil system, oil-air separation is unavoidable, and oil can easily enter the valve body, causing contamination. Proportional pressure valves have poor contamination resistance and require high cleanliness of the air circuit; they are prone to malfunction when faced with oil contamination, posing safety hazards. Summary of the Invention

[0004] The hydraulic retarder pressure control device, method, braking equipment, and vehicle provided in this invention at least solve the problems of poor anti-pollution performance and high failure rate of conventional proportional pneumatic valves. By cooperating with the switching valve, the first switching valve, and the second switching valve, rapid response control of the hydraulic retarder pressure can be achieved, effectively improving the overall anti-pollution performance and reducing the failure rate.

[0005] In a first aspect, the present invention provides a device for pressure control of a hydraulic retarder, comprising: a switching valve switchable between a first open position and a first stop position; the switching valve in the first open position connects a target retarding chamber to a gas source, and the switching valve in the first stop position connects the target retarding chamber to the external atmosphere; a first switching valve including a first valve port, a second valve port, a third valve port, and a fourth valve port; the first valve port connects to the gas source, and the second valve port connects to the external atmosphere; the first switching valve is switchable between a second open position and a second stop position; the first switching valve in the second open position connects the first valve port and the third valve port... The first switching valve, located in the second stop position, connects the second valve port to the third valve port and the fourth valve port respectively; the second switching valve includes a fifth valve port and a sixth valve port; the fifth valve port is connected to the third valve port, and the sixth valve port is connected to the fourth valve port and the switching valve respectively, and the sixth valve port and the fifth valve port can be connected or disconnected; wherein, when the first switching valve is switched to the second open position and the sixth valve port and the fifth valve port are connected, the switching valve is switched to the first open position; when the first switching valve is switched to the second stop position and the sixth valve port and the fifth valve port are disconnected, the switching valve is switched to the first stop position.

[0006] In one embodiment of the present invention, the device further includes: a pressure sensor disposed at the opening of the target retardation chamber; the pressure sensor is used to detect the real-time pressure within the target retardation chamber, to emit an intake signal when the real-time pressure does not reach the target pressure range, and to emit a pressure holding signal when the real-time pressure reaches the target pressure range; a controller electrically connected to the first switching valve, the second switching valve, and the pressure sensor; the controller is used to receive the intake signal, control the first switching valve to switch to the second open position, and connect the sixth valve port and the fifth valve port; and to receive the pressure holding signal, control the first switching valve to switch to the second open position, and disconnect the sixth valve port and the fifth valve port; and to receive a stop signal, control the first switching valve to switch to the second stop position, and disconnect the sixth valve port and the fifth valve port.

[0007] In one embodiment of the present invention, the device further includes: a third switching valve electrically connected to the controller; the third switching valve includes a seventh valve port and an eighth valve port, the seventh valve port being connected to the third valve port and the fifth valve port respectively, and the eighth valve port being connected to the sixth valve port and the switching valve respectively; the eighth valve port and the seventh valve port may be connected or disconnected; the pressure sensor is further configured to transmit a micro-charging signal when the real-time pressure does not reach the target pressure range but reaches a first adjacent range; the controller is further configured to receive the micro-charging signal and control the first switching valve to switch to the second open position, disconnect the sixth valve port and the fifth valve port, and connect the eighth valve port and the seventh valve port.

[0008] In one embodiment of the present invention, the controller is further configured to receive the intake signal and control the eighth valve port and the seventh valve port to be connected; and to receive the stop signal or the pressure holding signal and control the eighth valve port and the seventh valve port to be disconnected.

[0009] In one embodiment of the present invention, multiple third switching valves are provided.

[0010] In one embodiment of the present invention, the valve port diameter of the second switching valve is smaller than the valve port diameter of the third switching valve.

[0011] In one embodiment of the present invention, the invention further includes: a fourth switching valve electrically connected to the controller; the fourth switching valve includes a ninth valve port and a tenth valve port; the ninth valve port is connected to the target retardation chamber, and the tenth valve port is connected to the external atmosphere; the tenth valve port and the ninth valve port can be connected or disconnected; the pressure sensor is further configured to emit a micro-discharge signal when the real-time pressure exceeds the target pressure range and reaches a second adjacent range; the controller is further configured to receive the micro-discharge signal and control the sixth valve port and the fifth valve port to be disconnected, and the tenth valve port and the ninth valve port to be connected.

[0012] In one embodiment of the present invention, the controller is further configured to receive one of the intake signal, the pressure holding signal and the stop signal, and control the isolation of the tenth valve port and the ninth valve port.

[0013] In one embodiment of the present invention, a safety valve is further included, which is connected to the target retardation chamber and the target atmosphere, respectively.

[0014] Secondly, the present invention also provides a method for controlling the pressure of a hydraulic retarder, applied to a hydraulic retarder pressure control device as described in any one of the above claims, comprising the steps of: controlling a first switching valve to switch to a second open position, and connecting the sixth and fifth valve ports of the second switching valve; wherein, the first switching valve includes a first valve port, a second valve port, a third valve port, and a fourth valve port; the first valve port is connected to the gas source, the second valve port is connected to the external atmosphere, and the first switching valve in the second open position connects the first valve port and the third valve port; the fifth valve port is connected to the third valve port, and the sixth valve port is connected to the fourth valve port and the switching valve respectively; the switching valve is switched to a first open position; and the target retarding chamber is connected to the gas source; or, controlling the first switching valve to switch to a second stop position, and isolating the sixth valve port and the fifth valve port; wherein, the first switching valve in the second stop position connects the second valve port to the third valve port and the fourth valve port respectively; the switching valve is switched to a first stop position; and the target retarding chamber is connected to the external atmosphere.

[0015] Thirdly, the present invention also provides a braking device, including a hydraulic retarder, an air source, and a device for controlling the pressure of the hydraulic retarder as described in any one of the above.

[0016] Fourthly, the present invention also provides a vehicle including the braking device as described in any of the preceding claims.

[0017] Compared with the prior art, the above-described technical solution of the present invention has the following advantages:

[0018] The hydraulic retarder pressure control device of this invention achieves rapid response control of the hydraulic retarder pressure through the cooperation of a switching valve, a first switching valve, and a second switching valve. The switching valves in the device are low-cost, do not experience valve core jamming, have a longer lifespan, faster response speed, and strong anti-contamination capabilities. The overall air circuit structure is simple, with exhaust mainly achieved by the switching valve, minimizing valve body contamination problems caused by oil-gas separation. This effectively reduces the device's failure rate and improves braking safety. Attached Figure Description

[0019] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this invention, illustrate exemplary embodiments of the invention and are used to explain the invention, but do not constitute an undue limitation of the invention. In the drawings:

[0020] Figure 1 This is one of the schematic diagrams of the air circuit principle of the hydraulic retarder pressure control device in a preferred embodiment of the present invention.

[0021] Figure 2This is the second schematic diagram of the air circuit principle of the hydraulic retarder pressure control device in a preferred embodiment of the present invention.

[0022] Figure 3 This is the third schematic diagram of the air circuit principle of the hydraulic retarder pressure control device in a preferred embodiment of the present invention.

[0023] The above-mentioned figures include the following reference numerals: 01, target slowing chamber; 02, air source; 10, first switching valve; 11, first valve port; 12, second valve port; 13, third valve port; 14, fourth valve port; 20, second switching valve; 21, fifth valve port; 22, sixth valve port; 30, third switching valve; 31, seventh valve port; 32, eighth valve port; 40, fourth switching valve; 41, ninth valve port; 42, tenth valve port; 50, switching valve; 51, port 1; 52, port 2; 53, port 3; 60, pressure sensor; 70, safety valve. Detailed Implementation

[0024] It should be noted that, unless otherwise specified, the embodiments and features described in the present invention can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0025] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the scope of exemplary embodiments according to the invention. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0026] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0027] This invention provides a device for controlling the pressure of a hydraulic retarder. The device is applied to braking equipment. Specifically, the device works in conjunction with the hydraulic retarder to control the air pressure of the hydraulic retarder.

[0028] The hydraulic retarder has a working chamber and a target retarding chamber 01. A rotor is housed in the working chamber, and hydraulic fluid is contained in the target retarding chamber 01. Introducing hydraulic fluid into the working chamber reduces the rotor's speed, achieving deceleration. The more hydraulic fluid introduced, the more difficult it is for the rotor to rotate, resulting in a stronger deceleration effect. The hydraulic retarder's pressure control device adjusts the amount of hydraulic fluid injected by controlling the air pressure.

[0029] Reference Figure 1 As shown, the hydraulic retarder pressure control device includes a switching valve 50, a first switching valve 10, and a second switching valve 20. The switching valve 50 can switch between a first open position and a first stop position.

[0030] The switching valve 50, located in the first open position, connects the target retardation chamber 01 and the air source 02 to achieve air intake. Then, under the action of air pressure, the oil in the target retardation chamber 01 is forced into the working chamber to achieve deceleration.

[0031] The switching valve 50, located in the first stop position, connects the target retarding chamber 01 to the external atmosphere, thus venting the air. In this way, the oil returns to the target retarding chamber 01, allowing the rotor to rotate normally.

[0032] For example, the switching valve 50 includes three valve ports and a valve core, namely port 1 51, port 2 52 and port 3 53. Port 1 51 is connected to other valve bodies, port 2 52 is connected to the target retardation chamber 01, and port 3 53 is connected to the external atmosphere.

[0033] The valve core of the switching valve 50 is driven by air pressure to move, thereby switching to the first open position, connecting port 1 51 and port 2 52, while blocking port 3 53. Alternatively, it can switch to the first stop position, connecting port 2 52 and port 3 53, while blocking port 1 51. Port 2 52 can provide air pressure feedback to port 3 53, so that when exhaust is needed, a pressure difference is generated between port 3 53 and port 1 51, thereby achieving position switching. In the attached diagram, the two ports are connected by a dashed line to illustrate this air pressure feedback.

[0034] The first switching valve 10 includes a first valve port 11, a second valve port 12, a third valve port 13, and a fourth valve port 14. The first valve port 11 is connected to an air source 02, which supplies air to the target retardation chamber 01. This air pressure then drives the oil in the target retardation chamber 01 into the working chamber to achieve deceleration. The second valve port 12 is connected to the external atmosphere. When necessary, excess gas in the target retardation chamber 01 is discharged through the second valve port 12 to reset the oil in the working chamber. The first switching valve 10 can switch between a second open position and a second stop position.

[0035] The first switch valve 10, located in the second open position, connects the first valve port 11 and the third valve port 13, while simultaneously isolating the second valve port 12 and the fourth valve port 14. At this time, the gas from the gas source 02 can pass through the first valve port 11 and the second valve port 12 in sequence, and then enter the second switch valve 20.

[0036] When the first switching valve 10 is in the second stop position, it connects the second valve port 12 to the third valve port 13 and the fourth valve port 14 respectively, while simultaneously isolating the first valve port 11 from other valve ports. At this time, gas from the gas source 02 can no longer enter the first switching valve 10, and the first port 51 of the switching valve 50 loses pressure, causing the valve core to move and block the first port 51. That is, the switching valve 50 switches to the first stop position, connecting the target slowing chamber 01 with the external atmosphere, thus achieving exhaust.

[0037] Understandably, the first switching valve 10 is a two-position four-way valve, used to switch between intake and exhaust air paths. Compared to conventional proportional valves, the first switching valve 10 is lower in cost, simplifies the overall structure, is more resistant to contamination, does not experience valve core jamming, has a longer lifespan, and a faster response time, effectively improving braking safety in emergency situations.

[0038] Preferably, the first switching valve 10 is a solenoid valve, which is in the second open position by default. When energized, it switches from the second open position to the second stop position; when de-energized, it is reset by a spring and switches from the second stop position to the second open position.

[0039] The second switching valve 20 includes a fifth valve port 21 and a sixth valve port 22. The fifth valve port 21 is connected to the third valve port 13, and the sixth valve port 22 is connected to the fourth valve port 14 and the switching valve 50, respectively. Specifically, the sixth valve port 22 is connected to the first port 51 of the switching valve 50. The sixth valve port 22 and the fifth valve port 21 can be connected or disconnected. The second switching valve 20 preferably switches synchronously with the first switching valve 10.

[0040] During operation, if the target retarding chamber 01 requires air intake, the first switching valve 10 is switched to the second open position, connecting the sixth valve port 22 and the fifth valve port 21. At this time, gas from the air source 02 can sequentially pass through the first switching valve 10 and the second switching valve 20, and enter the switching valve 50. Under the action of air pressure, the valve core of the switching valve 50 moves, connecting port 1 51 and port 2 52, and blocking port 3 53. Thus, gas from the air source 02 can enter the target retarding chamber 01, driving the oil within it into the working chamber to achieve deceleration.

[0041] If the hydraulic retarder is no longer needed for deceleration and the target retarding chamber 01 needs to be vented, the first switching valve 10 is switched to the second stop position, isolating the sixth valve port 22 and the fifth valve port 21. At this time, gas from the gas source 02 can no longer enter the first switching valve 10, and simultaneously, the first port 51 of the switching valve 50 loses pressure, causing the valve core to move and block the first port 51. That is, the switching valve 50 switches to the first stop position, connecting the target retarding chamber 01 with the external atmosphere, thus achieving venting.

[0042] Understandably, the second switching valve 20 is a two-position, two-way valve that assists the first switching valve 10 and the switching valve 50 in achieving pressure control. Compared to conventional proportional valves, the second switching valve 20 is lower in cost, effectively simplifies the overall structure, has strong resistance to contamination, does not experience valve core jamming, has a longer lifespan, and a faster response speed, effectively improving braking safety in emergency situations.

[0043] Preferably, the second switching valve 20 is configured as a solenoid valve, which by default isolates the two valve ports. When energized, the two valve ports are connected; when de-energized, it is reset by a spring, thus isolating the two valve ports.

[0044] The hydraulic retarder pressure control device of this invention, through the cooperation of switching valve 50, first switching valve 10, and second switching valve 20, can achieve rapid response control of hydraulic retarder pressure. The switching valves in the device are low-cost, do not suffer from valve core jamming, have a longer lifespan, faster response speed, and strong anti-contamination capabilities. The overall air circuit structure is simple, with exhaust mainly achieved by switching valve 50, minimizing valve body contamination problems caused by oil-gas separation. Thus, the device's failure rate can be effectively reduced, and braking safety improved.

[0045] Reference Figure 2 As shown, the hydraulic retarder pressure control device of the present invention, in some embodiments, further includes a pressure sensor 60 and a controller.

[0046] The pressure sensor 60 is installed at the opening of the target retardation chamber 01. The pressure sensor 60 is used to detect the real-time pressure inside the target retardation chamber 01. The specific pressure detection principle is existing technology and will not be described in detail here.

[0047] Pressure sensor 60 is electrically connected to the controller. If the detected real-time pressure does not reach the target pressure range, pressure sensor 60 sends an intake signal to the controller. If the detected real-time pressure reaches the target pressure range, pressure sensor 60 sends a pressure holding signal to the controller.

[0048] The target pressure range can be set according to actual needs. For example, a target pressure value can be set, and values ​​within a certain range around the target pressure value can be selected to form the target pressure range. This range can be ±5%.

[0049] The real-time pressure has not reached the target pressure range, meaning the real-time pressure value is less than the minimum value of the target pressure range. The real-time pressure has reached the target pressure range, meaning the real-time pressure value is less than or equal to the maximum value of the target pressure range and greater than or equal to the minimum value of the target pressure range.

[0050] The controller is used for each switching valve and is not shown in the attached diagram. Besides being electrically connected to the pressure sensor 60, the controller is also electrically connected to the first switching valve 10 and the second switching valve 20. It should be noted that the specific control principle between the controller and the solenoid valves is prior art and will not be elaborated further.

[0051] Specifically, the controller receives the intake signal and controls the first switching valve 10 to switch to the second open position, connecting the sixth valve port 22 and the fifth valve port 21. At this time, the air source 02 supplies air to the target deceleration chamber 01, and the oil enters the working chamber to achieve deceleration.

[0052] Simultaneously, the controller is also used to receive pressure holding signals and control the first switching valve 10 to switch to the second open position, and the sixth valve port 22 and the fifth valve port 21 to be isolated. At this time, the target slow chamber 01 is neither connected to the air source 02 nor to the external atmosphere, thus achieving pressure holding and maintaining the pressure inside the chamber.

[0053] Since the first switching valve 10 remains in the second open position, a rapid response can be achieved by adjusting the second switching valve 20 if a further increase in pressure is required. This structure effectively reduces the gas consumption of the device and avoids the disadvantage of traditional proportional valves that require frequent adjustments to the intake and exhaust to achieve stable gas pressure.

[0054] In addition, the controller is also used to receive a stop signal and control the first switching valve 10 to switch to the second stop position, and the sixth valve port 22 and the fifth valve port 21 to be isolated. At this time, the target retardation chamber 01 exhausts gas to the outside atmosphere, and the oil flows back from the working chamber to the target retardation chamber 01, stopping the deceleration.

[0055] With the cooperation of pressure sensor 60, controller and various valves, the overall control is simple and the device can achieve a fast response.

[0056] Reference Figure 2 As shown, the hydraulic retarder pressure control device of the present invention, in some embodiments, further includes a third switching valve 30. The third switching valve 30 includes a seventh valve port 31 and an eighth valve port 32. The seventh valve port 31 is connected to the third valve port 13 and the fifth valve port 21, respectively. The eighth valve port 32 is connected to the sixth valve port 22 and the switching valve 50, specifically, the eighth valve port 32 is connected to the first valve port 11 of the switching valve 50. It is understood that the second switching valve 20 and the third switching valve 30 are in parallel.

[0057] The eighth valve port 32 and the seventh valve port 31 can be connected or disconnected. Understandably, the third switching valve 30 is a two-position, two-way valve that assists the first switching valve 10, the second switching valve 20, and the switching valve 50 in achieving pressure control. Compared to conventional proportional valves, the third switching valve 30 is lower in cost, effectively simplifies the overall structure, has strong resistance to contamination, prevents valve core jamming, has a longer lifespan, and a faster response speed, effectively improving braking safety in emergency situations.

[0058] Preferably, the third switching valve 30 is configured as a solenoid valve, which by default isolates the two valve ports. When energized, the two valve ports are connected; when de-energized, it is reset by a spring, thus isolating the two valve ports.

[0059] The third switching valve 30 can switch synchronously with the first switching valve 10 and the second switching valve 20, or it can switch independently, thereby achieving degraded operation under single valve failure. This redundant design can effectively reduce the risk of overall failure caused by a single valve failure in traditional proportional valves.

[0060] Specifically, if the target deceleration chamber 01 needs air intake, the first switching valve 10 can be switched to the second open position. Simultaneously, the second switching valve 20 and the third switching valve 30 can be controlled to connect the sixth valve port 22 and the fifth valve port 21, and the eighth valve port 32 and the seventh valve port 31. At this time, the gas from the gas source 02, after passing through the first switching valve 10, can then be rapidly intaked and pressure built up through the second switching valve 20 and the third switching valve 30, increasing the pressure within the target deceleration chamber 01 and achieving deceleration.

[0061] Alternatively, only the second switching valve 20 can be controlled to connect the sixth valve port 22 and the fifth valve port 21, and disconnect the eighth valve port 32 and the seventh valve port 31. Or only the third switching valve 30 can be controlled to disconnect the sixth valve port 22 and the fifth valve port 21, and connect the eighth valve port 32 and the seventh valve port 31.

[0062] Taking the passage of gas through only the third switching valve 30 as an example, the gas from the gas source 02 can sequentially pass through the first switching valve 10 and the second switching valve 20, and then enter the switching valve 50. Under the action of air pressure, the valve core of the switching valve 50 moves, connecting port 1 51 and port 2 52, and blocking port 3 53. In this way, the gas from the gas source 02 can enter the target deceleration chamber 01, driving the oil inside into the working chamber to achieve deceleration. Compared with simultaneously opening the second switching valve 20 and the third switching valve 30, this method has a relatively smaller air intake flow rate, which can slightly increase the pressure inside the chamber and achieve fine-tuning.

[0063] In actual use, the pressure sensor 60 can be used to determine whether it is necessary to open the second switching valve 20 and the third switching valve 30 at the same time, or to open only one of them.

[0064] Specifically, when the hydraulic retarder needs to decelerate, i.e., when the target retarding chamber 01 needs to be filled with air, it needs to quickly fill with air to build up pressure. The pressure sensor 60 emits an air intake signal, and the controller and the third switching valve 30 are electrically connected. The controller simultaneously opens the first switching valve 10, the second switching valve 20, and the third switching valve 30, i.e., controls the first switching valve 10 to switch to the second open position, connects the sixth valve port 22 and the fifth valve port 21, and connects the eighth valve port 32 and the seventh valve port 31.

[0065] Under electromagnetic control, gas can pass through the first switching valve 10, the second switching valve 20 and the third switching valve 30 and then enter the switching valve 50, and then enter the target slowing chamber 01 to achieve rapid intake deceleration.

[0066] After a certain period of time, the pressure in the target retardation chamber 01 gradually increased, but it had not yet reached the target pressure range; however, it had reached the first proximity range. Understandably, the maximum value of the first proximity range is less than or equal to the minimum value of the target pressure range.

[0067] Correspondingly, when the real-time pressure does not reach the target pressure range but reaches the first adjacent range, the pressure sensor 60 emits a micro-charge signal. The controller receives the micro-charge signal and controls the first switching valve 10 to switch to the second open position, the sixth valve port 22 and the fifth valve port 21 to be isolated, and the eighth valve port 32 and the seventh valve port 31 to be connected.

[0068] Under electromagnetic control, gas can pass through the first switching valve 10 and the third switching valve 30 and then enter the switching valve 50, and then enter the target slow chamber 01, slightly increasing the pressure inside the chamber to achieve fine adjustment.

[0069] When the real-time pressure reaches the target pressure range, the pressure sensor 60 emits a pressure holding signal, the controller receives the pressure holding signal, and controls the first switching valve 10 to switch to the second open position, the sixth valve port 22 and the fifth valve port 21 to be isolated, and the eighth valve port 32 and the seventh valve port 31 to be isolated.

[0070] If the hydraulic retarder is no longer needed for deceleration and the target retarding chamber 01 needs to be vented, the first switching valve 10 is switched to the second stop position, the sixth valve port 22 and the fifth valve port 21 are disconnected, and the eighth valve port 32 and the seventh valve port 31 are disconnected. At this time, the target retarding chamber 01 is connected to the external atmosphere, thus achieving venting.

[0071] Furthermore, in some embodiments, the orifice diameter of the second switching valve 20 is smaller than that of the third switching valve 30, achieving differentiation. This allows for the selection of a suitable valve to achieve targeted air intake based on actual pressure adjustment requirements. It is understood that in some other embodiments, the orifice diameter of the third switching valve 30 may also be smaller than that of the second switching valve 20.

[0072] Reference Figure 3 As shown, in some embodiments, multiple third switching valves 30 are provided, with each valve connected in parallel, to further shorten the response time and achieve rapid air intake. Compared to directly increasing the valve body orifice diameter to accelerate the air intake speed, this method can effectively balance air intake speed and adjustment accuracy. The controller can also determine which air intake valve and the number of air intake valves to open based on changes in air pressure.

[0073] Reference Figure 2 As shown, the hydraulic retarder pressure control device of the present invention, in some embodiments, further includes a fourth switching valve 40. The fourth switching valve 40 includes a ninth valve port 41 and a tenth valve port 42. The ninth valve port 41 is connected to the target retarding chamber 01, and the tenth valve port 42 is connected to the external atmosphere. Preferably, the ninth valve port 41 is also connected to the second port of the switching valve 50, and the tenth valve port 42 is also connected to the third port of the switching valve 50.

[0074] The tenth valve port 42 and the ninth valve port 41 can be connected or disconnected. The fourth switching valve 40 serves as an exhaust valve to achieve small-scale exhaust.

[0075] Understandably, the fourth switching valve 40 is a two-position, two-way valve that assists the first switching valve 10, the second switching valve 20, and the switching valve 50 in achieving pressure control. Compared to conventional proportional valves, the fourth switching valve 40 is lower in cost, effectively simplifies the overall structure, has strong resistance to contamination, does not experience valve core jamming, has a longer lifespan, and a faster response speed, effectively improving braking safety in emergency situations.

[0076] Preferably, the fourth switching valve 40 is configured as a solenoid valve, which by default isolates the two valve ports. When energized, the two valve ports are connected; when de-energized, it is reset by a spring, thus isolating the two valve ports.

[0077] The fourth switching valve 40 can switch synchronously with the other switching valves or switch independently. Specifically, if the target retarder chamber 01 needs to be filled with air, the other switching valves can be opened, and the fourth switching valve 40 can be closed, isolating the tenth valve port 42 and the ninth valve port 41, so that gas can enter the target retarder chamber 01, causing the pressure inside the target retarder chamber 01 to increase and achieve deceleration. When the required pressure is reached and pressure needs to be maintained, the fourth switching valve 40 remains closed.

[0078] If a slight reduction in pressure is required, the second switch valve 20 and the third switch valve 30 can be closed, and the fourth switch valve 40 can be opened, so that the gas in the target slow chamber 01 can be discharged through the fourth switch valve 40.

[0079] If the hydraulic retarder is no longer needed to slow down the vehicle and the target retarding chamber 01 needs to be vented, then all the switching valves are closed to allow the target retarding chamber 01 to connect with the outside atmosphere and achieve rapid venting.

[0080] In this way, during the entire intake and exhaust process, only a portion of the gas passes through the electromagnetically controlled fourth switching valve 40 when fine-tuning the exhaust. In most cases, the gas affected by the oil does not need to pass through the solenoid valve, which minimizes the valve body contamination problem caused by oil-gas separation and reduces the failure rate of the device.

[0081] In actual use, the pressure sensor 60 can be used to determine whether the fourth switch valve 40 needs to be opened or closed.

[0082] Specifically, when the hydraulic retarder needs to decelerate, i.e., when the target retarding chamber 01 needs air intake, rapid air intake is required to build up pressure. Pressure sensor 60 emits an air intake signal. The controller is also electrically connected to the fourth switching valve 40. The controller simultaneously opens the first switching valve 10, the second switching valve 20, and the third switching valve 30, and closes the fourth switching valve 40. That is, it controls the first switching valve 10 to switch to the second open position, connects the sixth valve port 22 and the fifth valve port 21, connects the eighth valve port 32 and the seventh valve port 31, and isolates the ninth valve port 41 and the tenth valve port 42. Under electromagnetic control, gas can pass through the first switching valve 10, the second switching valve 20, and the third switching valve 30 before entering the switching valve 50, and then into the target retarding chamber 01, achieving rapid air intake and deceleration.

[0083] After a certain period of time, the pressure in the target slowing chamber 01 gradually increases, reaching the first proximity range. Correspondingly, the pressure sensor 60 emits a micro-charge signal, and the controller controls the first switching valve 10 to switch to the second open position, the sixth valve port 22 and the fifth valve port 21 to be disconnected, the eighth valve port 32 and the seventh valve port 31 to be connected, and the ninth valve port 41 and the tenth valve port 42 to be disconnected. Under electromagnetic control, gas can pass through the first switching valve 10 and the third switching valve 30, enter the switching valve 50, and then enter the target slowing chamber 01, slightly increasing the pressure inside the chamber and achieving fine-tuning.

[0084] When the real-time pressure reaches the target pressure range, the pressure sensor 60 emits a pressure holding signal. The controller receives the pressure holding signal and controls the first switching valve 10 to switch to the second open position, the sixth valve port 22 and the fifth valve port 21 to be isolated, the eighth valve port 32 and the seventh valve port 31 to be isolated, and the ninth valve port 41 and the tenth valve port 42 to be isolated.

[0085] When the real-time pressure exceeds the target pressure range and reaches the second adjacent range, the pressure sensor 60 emits a micro-discharge signal. Understandably, the maximum value of the target pressure range is less than or equal to the minimum value of the second adjacent range. The controller receives the micro-discharge signal and controls the sixth valve port 22 and the fifth valve port 21 to disconnect, the eighth valve port 32 and the seventh valve port 31 to disconnect, and the tenth valve port 42 and the ninth valve port 41 to connect.

[0086] Under electromagnetic control, the gas in the target slow-relief chamber 01 can be discharged through the fourth switching valve 40, slightly reducing the pressure inside the chamber and achieving fine-tuning. That is, the controller receives one of the following signals: air intake signal, micro-charge signal, pressure holding signal, and stop signal, and controls the isolation between the tenth valve port 42 and the ninth valve port 41.

[0087] If the hydraulic retarder is no longer needed for deceleration and the target retarding chamber 01 needs to be vented, the first switching valve 10 is switched to the second stop position, the sixth valve port 22 and the fifth valve port 21 are isolated, the eighth valve port 32 and the seventh valve port 31 are isolated, and the tenth valve port 42 and the ninth valve port 41 are isolated. At this time, the target retarding chamber 01 is connected to the external atmosphere, and the gas is vented outward through the second port 52 and the third port 53 of the switching valve 50.

[0088] In summary, when the hydraulic retarder is activated and rapid pressure build-up is required, the first switching valve 10, the second switching valve 20, and the third switching valve 30 open, while the fourth switching valve 40 closes to allow for rapid, high-flow-rate air intake. Once the target pressure range is reached, the first switching valve 10 opens, and the remaining switching valves close to maintain pressure.

[0089] When a small pressure adjustment is needed, the first switching valve 10 and the third switching valve 30 are opened, while the second switching valve 20 and the fourth switching valve 40 are closed to allow for a slight increase in intake pressure. Alternatively, the first switching valve 10 and the fourth switching valve 40 are opened, while the second switching valve 20 and the third switching valve 30 are closed to allow for a slight decrease in exhaust pressure. Of course, in some other embodiments, the first switching valve 10 and the second switching valve 20 may be opened, while the third switching valve 30 and the fourth switching valve 40 may be closed to allow for a slight increase in intake pressure.

[0090] When the air pressure reaches the target pressure range, the first switch valve 10 opens, and the second switch valve 20, the third switch valve 30 and the fourth switch valve 40 close, thus maintaining the pressure.

[0091] When the hydraulic retarder stops working and rapid venting is required, all switching valves are closed simultaneously to allow the gas in the chamber to be quickly discharged, thereby reducing the pressure.

[0092] Reference Figure 2 As shown, the hydraulic retarder pressure control device of the present invention, in some embodiments, further includes a safety valve 70, which is connected to the target retarding chamber 01 and the target atmosphere. By providing the safety valve 70, if the pressure in the target retarding chamber 01 is too high, the safety valve 70 can open, thereby connecting the target retarding chamber 01 and the target atmosphere, achieving automatic pressure relief and ensuring overall safety. Conversely, the safety valve 70 remains closed to prevent gas leakage.

[0093] This invention also provides a braking device, including a hydraulic retarder, an air source 02, and a device for controlling the pressure of the hydraulic retarder as described in any of the above embodiments. Since the braking device of this invention includes the device for controlling the pressure of the hydraulic retarder as described in the above embodiments, it also possesses all the beneficial effects described herein, and will not be repeated here.

[0094] This invention also provides a vehicle including the braking device described in any of the above embodiments. Since the vehicle of this invention includes the braking device described in the above embodiments, it also possesses all the beneficial effects described herein, which will not be repeated here.

[0095] This invention also provides a method for controlling the pressure of a hydraulic retarder, applied to the hydraulic retarder pressure control device described in any of the above embodiments. The method for controlling the pressure of a hydraulic retarder includes the following steps:

[0096] The first switching valve 10 is switched to the second open position, and the sixth valve port 22 and the fifth valve port 21 of the second switching valve 20 are connected. The first switching valve 10 includes a first valve port 11, a second valve port 12, a third valve port 13, and a fourth valve port 14. The first valve port 11 is connected to the air source 02, and the second valve port 12 is connected to the outside atmosphere. When the first switching valve 10 is in the second open position, the first valve port 11 and the third valve port 13 are connected. The fifth valve port 21 is connected to the third valve port 13, and the sixth valve port 22 is connected to both the fourth valve port 14 and the switching valve 50.

[0097] Switch valve 50 is switched to the first open position.

[0098] The target slowing chamber 01 is connected to the air source 02.

[0099] or:

[0100] The first switching valve 10 is switched to the second stop position, isolating the sixth valve port 22 and the fifth valve port 21. Specifically, when the first switching valve 10 is in the second stop position, the second valve port 12 is connected to the third valve port 13 and the fourth valve port 14, respectively.

[0101] Switching valve 50 is switched to the first stop position.

[0102] The target slowing cavity 01 is connected to the external atmosphere.

[0103] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0104] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0105] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A device for pressure control of a hydraulic retarder, characterized in that, include: The switching valve can be switched between a first open position and a first stop position; The switching valve located in the first open position connects the target retarding chamber to the air source, and the switching valve located in the first stop position connects the target retarding chamber to the external atmosphere. The first switching valve includes a first valve port, a second valve port, a third valve port, and a fourth valve port; the first valve port is connected to the gas source, and the second valve port is connected to the external atmosphere; the first switching valve can switch between a second open position and a second stop position. The first switch valve in the second open position connects the first valve port and the third valve port, and the first switch valve in the second stop position connects the second valve port to the third valve port and the fourth valve port respectively. The second switching valve includes a fifth valve port and a sixth valve port; The fifth valve port is connected to the third valve port, and the sixth valve port is connected to the fourth valve port and the switching valve respectively. The sixth valve port and the fifth valve port can be connected or disconnected. Wherein, the first switching valve is switched to the second open position, the sixth valve port and the fifth valve port are connected, so that the switching valve is switched to the first open position; The first switching valve is switched to the second stop position, and the sixth valve port and the fifth valve port are disconnected, so that the switching valve is switched to the first stop position.

2. The device for pressure control of a hydraulic retarder according to claim 1, characterized in that, Also includes: A pressure sensor is disposed at the inlet of the target retardation chamber; the pressure sensor is used to detect the real-time pressure in the target retardation chamber, to emit an intake signal when the real-time pressure does not reach the target pressure range, and to emit a pressure holding signal when the real-time pressure reaches the target pressure range. The controller is electrically connected to the first switching valve, the second switching valve, and the pressure sensor, respectively. The controller is used to receive the intake signal and control the first switching valve to switch to the second open position, connecting the sixth valve port and the fifth valve port; and to receive the pressure holding signal and control the first switching valve to switch to the second open position, disconnecting the sixth valve port and the fifth valve port; and to receive the stop signal and control the first switching valve to switch to the second stop position, disconnecting the sixth valve port and the fifth valve port.

3. The device for pressure control of a hydraulic retarder according to claim 2, characterized in that, Also includes: A third switching valve is electrically connected to the controller; the third switching valve includes a seventh valve port and an eighth valve port, the seventh valve port is connected to the third valve port and the fifth valve port respectively, and the eighth valve port is connected to the sixth valve port and the switching valve respectively; the eighth valve port and the seventh valve port can be connected or disconnected; The pressure sensor is also used to emit a micro-charging signal when the real-time pressure does not reach the target pressure range but reaches a first adjacent range. The controller is also used to receive the micro-charging signal, control the first switching valve to switch to the second open position, disconnect the sixth valve port and the fifth valve port, and connect the eighth valve port and the seventh valve port.

4. The device for pressure control of a hydraulic retarder according to claim 3, characterized in that: The controller is also configured to receive the intake signal and control the connection between the eighth valve port and the seventh valve port; and to receive the stop signal or the pressure holding signal and control the disconnection between the eighth valve port and the seventh valve port.

5. The device for pressure control of a hydraulic retarder according to claim 2, characterized in that, Also includes: The fourth switching valve is electrically connected to the controller; the fourth switching valve includes a ninth valve port and a tenth valve port. The ninth valve port is connected to the target slowing chamber, and the tenth valve port is connected to the external atmosphere; the tenth valve port and the ninth valve port can be connected or disconnected. The pressure sensor is also used to emit a micro-discharge signal when the real-time pressure exceeds the target pressure range and reaches a second adjacent range. The controller is also used to receive the micro-discharge signal and control the sixth valve port and the fifth valve port to be isolated, and the tenth valve port and the ninth valve port to be connected.

6. The device for pressure control of a hydraulic retarder according to claim 5, characterized in that: The controller is also used to receive one of the intake signal, the pressure holding signal and the stop signal, and to control the isolation of the tenth valve port and the ninth valve port.

7. The device for pressure control of a hydraulic retarder according to claim 1, characterized in that, Also includes: The safety valves are connected to the target retardation chamber and the target atmosphere, respectively.

8. A method for controlling the pressure of a hydraulic retarder, applied to the apparatus for controlling the pressure of a hydraulic retarder as described in any one of claims 1 to 7, characterized in that, Including the following steps: The first switching valve is controlled to switch to the second open position, and the sixth and fifth valve ports of the second switching valve are connected; wherein, the first switching valve includes a first valve port, a second valve port, a third valve port, and a fourth valve port; the first valve port is connected to the gas source, the second valve port is connected to the external atmosphere, and the first switching valve in the second open position connects the first valve port and the third valve port; the fifth valve port is connected to the third valve port, and the sixth valve port is connected to the fourth valve port and the switching valve respectively; Switch the valve to the first open position; The target slowing chamber is connected to the gas source; or, The first switching valve is controlled to switch to the second stop position, and the sixth valve port and the fifth valve port are isolated; wherein, the first switching valve in the second stop position connects the second valve port to the third valve port and the fourth valve port respectively; The switching valve is switched to the first stop position; The target slowing cavity is connected to the external atmosphere.

9. A braking device, characterized in that, It includes a hydraulic retarder, an air source, and a device for controlling the pressure of the hydraulic retarder as described in any one of claims 1 to 7, wherein the hydraulic retarder is provided with a target retarding chamber.

10. A vehicle, characterized in that, Includes the braking device as described in claim 9.

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