Hydraulic control type hydraulic reverser and system suitable for electro-hydraulic energy-regenerative suspension active damping
By employing pilot hydraulic control technology and a high-flow integrated valve core structure, combined with embedded integrated oil passages, the problem of suspension vibration energy recovery and damping under active control conditions of hydraulic commutators has been solved, achieving efficient energy recovery and damping of high-speed tracked vehicles, and improving energy utilization and vehicle reliability.
Patent Information
- Application Number
- CN202211662914.5
- Authority / Receiving Office
- CN · China
- Patent Type
- Patents(China)
- Current Assignee / Owner
- Filing Date
- 2022-12-23
- Publication Date
- 2026-02-13
- Estimated Expiration
- 2042-12-23
AI Technical Summary
Existing full-bridge or half-bridge hydraulic commutators cannot achieve selective recovery and storage of suspension vibration energy under active control conditions, and their size cannot be reduced, resulting in low energy feeding efficiency.
By adopting pilot-operated hydraulic control technology and a high-flow integrated valve core structure, the active vibration reduction and passive rectification of the hydraulic commutator are achieved by controlling the action of the active/passive switching valve in the external control oil circuit. Combined with the embedded integrated oil passage, the size is reduced and the energy feeding efficiency is improved.
It achieves efficient recovery and active vibration reduction of vibration energy of high-speed tracked vehicles on complex road surfaces, improves the energy utilization rate and vibration reduction performance of the vehicle, and reduces the size of the hydraulic commutator.
Smart Images
Figure CN116538224B_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The present application belongs to the field of hydraulic flow reversing equipment, and particularly relates to a hydraulic control type hydraulic reverser and system suitable for electro-hydraulic energy feedback suspension active damping. BACKGROUND
[0002] At present, the existing electro-hydraulic energy feedback suspension vibration energy recovery device for vehicles is mainly composed of a shock absorber, a hydraulic reverser and a hydraulic pump / motor, which are sequentially connected. The vehicle includes a connecting rod, a pull arm, a generator and a vehicle-mounted battery. The generator is connected with the vehicle-mounted battery. When the vehicle runs on a rolling off-road surface, the connecting rod connected with the wheel converts the up-down vibration of the wheel into reciprocating swing of the pull arm through the pull arm connected with the other end of the connecting rod. The reciprocating swing of the pull arm is converted into the forward / backward movement of the shock absorber through the shock absorber connected with the pull arm. Since the forward / backward movement of the shock absorber forms high / low pressure cavities with non-fixed relative positions, no matter what relative position the high / low pressure cavities are in, the hydraulic oil in the high pressure cavity can flow into the hydraulic motor after being rectified by the hydraulic reverser, drive the hydraulic motor to rotate, and then flow out of the hydraulic motor through the hydraulic reverser into the low pressure cavity, thereby providing the hydraulic motor with a stable flow of hydraulic oil, allowing the hydraulic motor to work continuously and driving the generator to rotate and generate electricity to store energy, thereby completing the recovery and storage of vibration energy of the electro-hydraulic energy feedback suspension when the vehicle runs on a rolling off-road surface. In the electro-hydraulic energy feedback suspension vibration energy recovery device, the hydraulic reverser can rectify the reciprocating flow of hydraulic oil in the high / low pressure cavities formed by the forward / backward movement of the shock absorber, so that the hydraulic oil can flow out of the hydraulic reverser after flowing through the hydraulic reverser, drive the hydraulic motor to work, and then flow into the hydraulic reverser to drive the hydraulic motor to work and drive the generator to rotate and generate electricity to store energy. Therefore, the hydraulic reverser plays a crucial role in the process of recovering vibration energy of the electro-hydraulic energy feedback suspension of the vehicle.
[0003] The existing high-speed tracked vehicle has a heavy body weight, and the driving surface is mostly rolling off-road surface. The vibration energy generated under the driving conditions of high speed and heavy load is huge. Related research shows that the energy feedback potential of high-speed tracked vehicles is 4.37 times that of wheeled vehicles. If the vibration energy can be efficiently recovered and used for active damping or stored in the storage battery to supply the vehicle-mounted electrical equipment, it will effectively improve the energy utilization efficiency of high-speed tracked vehicles and thus improve the overall performance such as the endurance of the vehicle.
[0004] The existing full-bridge or half-bridge hydraulic reverser is mainly composed of a one-way valve and a cavity corresponding to the one-way valve and a pipeline structure, is connected with high / low pressure cavities formed by the positive / negative movement of the shock absorber, and can make the reciprocating flow of the hydraulic oil formed by the high / low pressure cavities flow out and flow in in a fixed direction after being rectified by the hydraulic reverser, so as to provide the hydraulic motor with stable hydraulic oil in a flow direction, make the hydraulic motor work and then drive the generator to rotate and generate energy. At present, the active control of the high-speed tracked vehicle puts forward higher requirements for the hydraulic reverser, which requires the hydraulic reverser to not only complete the recovery of the suspension vibration energy in the passive / semi-active working condition, but also to realize the active damping of the vehicle suspension and improve the reliability of the vehicle in the active working condition, and to reduce the volume as much as possible and increase the energy feeding efficiency.
[0005] For the new requirements of the hydraulic reverser for the active control of the current high-speed tracked vehicle, the existing full-bridge or half-bridge hydraulic reverser cannot fully meet the requirements. The existing full-bridge or half-bridge hydraulic reverser can only realize the recovery of the suspension vibration energy in the passive / semi-active working condition, and cannot selectively use the suspension vibration energy for energy recovery and storage or for active damping of the vehicle suspension and improvement of the reliability by active control. Moreover, the existing full-bridge or half-bridge hydraulic reverser cannot reduce the volume due to the limitation of the one-way valve, the cavity and the pipeline structure.
[0006] Through the above analysis, the problems and defects of the prior art are:
[0007] The existing full-bridge or half-bridge hydraulic reverser cannot realize active damping, and the volume cannot be reduced, and the energy feeding efficiency is low. SUMMARY
[0008] In view of the problems of the prior art, the present application provides a hydraulic control type hydraulic reverser suitable for active damping of an electro-hydraulic energy feeding suspension.
[0009] The present application is realized in this way, a hydraulic control type hydraulic reverser suitable for active damping of an electro-hydraulic energy feeding suspension, the new hydraulic control type hydraulic reverser, in the passive / semi-active working condition, the positive / negative rotation of the vane shock absorber forms high / low pressure cavities with non-fixed relative positions, no matter what relative position the high / low pressure cavities are in, the hydraulic oil flows out along a fixed flow direction after flowing into the new hydraulic control type hydraulic reverser under the action of the high pressure cavity, pushes the hydraulic motor to work and then flows into the low pressure cavity along a fixed flow direction, realizes the directional rectification of the hydraulic oil; in the active working condition, by controlling the action of the master / passive switching valve on the external control oil way, controlling the state of the pilot oil in the external control oil way and then controlling the normally open and normally closed state of the eight valve ports of the new hydraulic control type hydraulic reverser, the new hydraulic control type hydraulic reverser is short-circuited, and the active control is realized.
[0010] Further, the new hydraulic control type hydraulic reverser controls the normally open state of four valve ports and the normally closed state of the other four valve ports among the eight valve ports of the new hydraulic control type hydraulic reverser through the pilot oil state in the external control oil circuit.
[0011] Further, when there is no pilot oil in the external control oil circuit, the new hydraulic control type hydraulic reverser realizes rectification through the reciprocating flow of the hydraulic oil in the high / low pressure cavities formed between the blade damper and the new hydraulic control type hydraulic reverser, the flow through the new hydraulic control type hydraulic reverser, the flow out along the fixed flow direction after driving the hydraulic motor, and the flow in along the fixed flow direction after the hydraulic motor works.
[0012] Further, when there is pilot oil in the external control oil circuit, the new hydraulic control type hydraulic reverser controls the positions of each control piston and spool valve in the new hydraulic control type hydraulic reverser through the pilot oil in the external control oil circuit, keeps four valve ports among the eight valve ports of the new hydraulic control type hydraulic reverser normally open and keeps the other four valve ports normally closed, and makes the new hydraulic control type hydraulic reverser short-circuit.
[0013] Further, the internal structure of the new hydraulic control type hydraulic reverser includes the new hydraulic control type hydraulic reverser valve body, spool valve one, extension spring, control piston one, large end cover, small end cover, spool valve two, compression spring, control piston two, sealing element, small valve body one, connecting element, small valve body two, and lower base.
[0014] Further, when there is no pilot oil in the external control oil circuit, the new hydraulic control type hydraulic reverser is in passive / semi-active working condition, the blade damper generates positive / negative rotation under the driving action of the up and down vibration of the negative weight wheel, and the high / low pressure cavities are formed between the blade damper and the new hydraulic control type hydraulic reverser. When the blade damper generates positive rotation (clockwise rotation) under the driving action of the up and down vibration of the negative weight wheel, the hydraulic oil in the high pressure cavity drives Figure 7 the spool valve one in the section A-A to move into the new hydraulic control type hydraulic reverser and flow out from the oil port C below the section G-G, drives the hydraulic motor to rotate, and then flows into the new hydraulic control type hydraulic reverser from the oil port A below the section G-G to drive Figure 13 the spool valve one in the section C-C to move, so that the hydraulic oil enters the low pressure cavity. Figure 13 When the blade damper generates negative rotation (counterclockwise rotation) under the driving action of the up and down vibration of the negative weight wheel, the hydraulic oil in the high pressure cavity drives Figure 9 the spool valve two in the section C-C to move into the new hydraulic control type hydraulic reverser and flow out from the oil port C below the section G-G, drives the hydraulic motor to rotate, and then flows into the new hydraulic control type hydraulic reverser from the oil port A below the section G-G to drive Figure 9 the spool valve one in the section C-C to move, so that the hydraulic oil enters the low pressure cavity. Figure 13 When the blade damper generates negative rotation (counterclockwise rotation) under the driving action of the up and down vibration of the negative weight wheel, the hydraulic oil in the high pressure cavity drives Figure 13 the spool valve two in the section C-C to move into the new hydraulic control type hydraulic reverser and flow out from the oil port C below the section G-G, drives the hydraulic motor to rotate, and then flows into the new hydraulic control type hydraulic reverser from the oil port A below the section G-G to drive Figure 7The spool valve in section A-A moves, and hydraulic oil enters the low-pressure cavity. Figure 13 The lower oil port C in section G-G flows out, and hydraulic oil flows along Figure 13 The lower oil port A in section G-G flows in, and pushes the hydraulic motor to rotate in a certain direction, which in turn drives the generator to rotate and generate energy.
[0015] Further, when the new hydraulic control hydraulic reverser is in active working condition, and there is pilot oil in the external control oil circuit, the pilot oil flows out from Figure 8 The B port in section B-B flows in and then flows along B1, B2 and B3 ports, and the pilot oil flowing in from the B2 port pushes Figure 7 The control piston one and the control piston two in section A-A move, and Figure 7 The spool valve one in section A-A is always open, and the spool valve two is always closed; the pilot oil flowing in from the B1 port pushes Figure 9 The control piston one in section C-C moves, and the valve port of the spool valve one in this section is always open; the pilot oil flowing in from the B3 port pushes Figure 9 The control piston two in section C-C moves, and the valve port of the spool valve two in this section is always closed. The new hydraulic control hydraulic reverser is thus in a short-circuit state, and hydraulic oil can freely enter and exit. The hydraulic motor is converted into a hydraulic pump under the action of the electrical control system, and supplies oil to the cavity formed between the blade damper and the new hydraulic control hydraulic reverser through the new hydraulic control hydraulic reverser. The oil supply direction of the hydraulic pump depends on the circuit signal in the electrical control system, which is generated by the vehicle detecting the road condition in the early stage to estimate the up-and-down vibration of the load wheel. The oil supply direction of the hydraulic pump is always opposite to the rotation direction of the blade damper caused by the up-and-down vibration of the load wheel. The hydraulic oil hinders the rotation of the blade damper and thus hinders the up-and-down vibration of the wheel, thereby achieving the purpose of active damping.
[0016] Another object of the present application is to provide a mechatronic energy feedback suspension system suitable for the hydraulic control hydraulic reverser of the electro-hydraulic energy feedback suspension, and the working process of the mechatronic energy feedback suspension system is as follows:
[0017] When the vehicle is running on uneven road, it is determined whether the main / passive switching valve in the external control oil circuit is in action, and whether there is pilot oil in the external control oil circuit. If the main / passive switching valve is in action, and there is pilot oil in the external control oil circuit, the new hydraulic control hydraulic reverser is in active working condition, and the new hydraulic control hydraulic reverser is in short circuit. The circuit signal generated by the vehicle detecting the road condition in the early stage is used to control whether the hydraulic pump rotates forward or reversely. After the hydraulic pump outputs hydraulic oil, the hydraulic oil freely enters and exits the new hydraulic control hydraulic reverser into the cavity formed between the blade damper and the new hydraulic control hydraulic reverser, hinders the rotation of the blade damper and thus hinders the up-and-down vibration of the wheel, and completes the active damping.
[0018] If the main / passive switching valve does not act, and there is no pilot oil in the external control oil circuit, the new type of hydraulic control hydraulic reverser is in passive / semi-active working condition, due to the up and down vibration of the load wheel, the connecting rod drives the pull arm to swing repeatedly, drives the blade damper to rotate forward / backward to form the high / low pressure cavity with non-fixed relative position, so as to generate reciprocating flow of hydraulic oil, and the reciprocating flow of hydraulic oil can flow out / in the new type of hydraulic control hydraulic reverser along the fixed direction after directional rectification, push the hydraulic motor to rotate in a fixed direction, and then drive the generator to rotate and generate electricity to store energy, and energy recovery is completed.
[0019] Another object of the present application is to provide an information data processing terminal for realizing the electromechanical hydraulic energy feedback suspension system.
[0020] Another object of the present application is to provide an application of the hydraulic control hydraulic reverser for realizing the active damping of the electromechanical hydraulic energy feedback suspension in a high-speed tracked vehicle.
[0021] In combination with the above technical solutions and the technical problems solved, the advantages and positive effects of the technical solution to be protected by the present application are analyzed from the following aspects:
[0022] Firstly, in view of the technical problems existing in the prior art and the difficulty in solving the problems, the technical solution to be protected by the present application and the results and data in the research and development process are combined to analyze in detail and profoundly how the technical solution solves the technical problems and brings some creative technical effects after solving the problems. The specific description is as follows:
[0023] The present application is based on the problem that the existing full-bridge or half-bridge hydraulic reverser cannot overcome the contradiction between the energy feedback rectification and the direct connection demand of the active damping control oil circuit of the electromechanical hydraulic energy feedback suspension, which hinders the realization of the active damping function of the electromechanical hydraulic energy feedback suspension. The pilot hydraulic control technology is used to solve the control mode switching problem of the energy feedback suspension, the large-flow integrated valve core structure is used to solve the flow and space contradiction, the embedded integrated oil channel is used to realize the integration of the energy feedback suspension function in limited space, and the hydraulic control hydraulic reverser and working system suitable for active damping of the electromechanical hydraulic energy feedback suspension are proposed. The new type of hydraulic control hydraulic reverser and working system not only can actively select to recover the vibration energy generated by the high-speed tracked vehicle during driving on complex road surface or improve the damping performance of the high-speed tracked vehicle, but also can reduce the volume of the hydraulic reverser and increase the energy feedback efficiency.
[0024] Secondly, the technical solution is regarded as a whole or from the perspective of the product, the technical effects and advantages of the technical solution to be protected by the present application are described as follows:
[0025] The application adopts pilot hydraulic control technology to solve the problem of switching of the energy feedback suspension control mode, and proposes a hydraulic control type hydraulic reverser and working system suitable for active damping of the electro-hydraulic energy feedback suspension, which can realize the active damping control function of the electro-hydraulic energy feedback suspension, and has important promoting effect on improving the damping performance and application of the electro-hydraulic energy feedback suspension.
[0026] The contradiction between the flow and the structural limitation of the electro-hydraulic energy feedback suspension circuit is solved by adopting a large-flow integrated valve core structure combined with an embedded integrated oil channel, the energy loss is small, the response is fast, and the energy feedback efficiency and the damping performance are improved synchronously.
[0027] The switching of the passive / semi-active and active control modes of the electro-hydraulic energy feedback suspension can be realized by adopting the hydraulic control pilot to simultaneously control the eight large-flow integrated valve cores of the new hydraulic control type hydraulic reverser, and the control is simple and stable.
[0028] The control oil circuit integration is realized by adopting the multi-layer arrangement and the embedded integrated oil channel which can communicate with each other, the problem of the control oil circuit arrangement in the limited space is solved, and the oil channel damping is small and the processing is convenient.
[0029] Thirdly, as the creative auxiliary evidence of the claims of the application, it is also embodied in the following important aspects:
[0030] The expected income and commercial value of the technical scheme of the application after transformation are:
[0031] The hydraulic control type hydraulic reverser and working system suitable for active damping of the electro-hydraulic energy feedback suspension can control the state of the pilot oil in the external control oil circuit by controlling the action of the main / passive switching valve in the external control oil circuit, so as to realize the switching of the passive / semi-active and active modes of the electro-hydraulic energy feedback suspension. Thus, the electro-hydraulic energy feedback suspension realizes hydraulic rectification in the passive / semi-active working condition, improves the energy feedback efficiency; realizes the bidirectional free control of the blade damper in the active working condition, and improves the damping performance. The new hydraulic control type hydraulic reverser provides technical support for the passive / semi-active / active layered control of the electro-hydraulic energy feedback suspension after transformation, and can improve the energy utilization rate and the ride smoothness of the high-speed tracked vehicle synchronously. Moreover, the new hydraulic control type hydraulic reverser system and control scheme can be applied to new energy vehicles, off-road vehicles and other civilian vehicles, improve the energy utilization rate, fuel economy and ride comfort, and has great practical value and commercial value. BRIEF DESCRIPTION OF DRAWINGS
[0032] Figure 1 is a model diagram of the hydraulic control type hydraulic reverser suitable for active damping of the electro-hydraulic energy feedback suspension provided by the embodiment of the application;
[0033] Figure 2 is a front view of the hydraulic control type hydraulic reverser suitable for active damping of the electro-hydraulic energy feedback suspension provided by the embodiment of the application;
[0034] Figure 3It is the left view of the hydraulic control type hydraulic reverser suitable for electro-hydraulic energy-regenerative suspension active damping provided by the embodiment of the application;
[0035] Figure 4 It is the plan view of the hydraulic control type hydraulic reverser suitable for electro-hydraulic energy-regenerative suspension active damping provided by the embodiment of the application;
[0036] Figure 5 It is the bottom view of the hydraulic control type hydraulic reverser suitable for electro-hydraulic energy-regenerative suspension active damping provided by the embodiment of the application;
[0037] Figure 6 It is the principle diagram of the hydraulic control type hydraulic reverser suitable for electro-hydraulic energy-regenerative suspension active damping provided by the embodiment of the application;
[0038] Figure 7 It is the A-A cross-sectional view provided by the embodiment of the application;
[0039] Figure 8 It is the B-B cross-sectional view provided by the embodiment of the application;
[0040] Figure 9 It is the C-C cross-sectional view provided by the embodiment of the application;
[0041] Figure 10 It is the D-D cross-sectional view provided by the embodiment of the application;
[0042] Figure 11 It is the E-E cross-sectional view provided by the embodiment of the application;
[0043] Figure 12 It is the F-F cross-sectional view provided by the embodiment of the application;
[0044] Figure 13 It is the G-G cross-sectional view provided by the embodiment of the application;
[0045] Figure 14 It is the flow chart of the electro-mechanical-hydraulic energy-regenerative suspension system provided by the embodiment of the application;
[0046] Figure 15 It is the model diagram of the electro-mechanical-hydraulic energy-regenerative suspension system provided by the embodiment of the application;
[0047] Figure 16 It is the simulation model diagram of the electro-mechanical-hydraulic energy-regenerative suspension system provided by the embodiment of the application;
[0048] Figure 17 (a) is the energy recovery power schematic diagram of the electro-mechanical-hydraulic energy-regenerative suspension under passive / semi-active working condition provided by the embodiment of the application, (b) is the energy recovery efficiency schematic diagram of the electro-mechanical-hydraulic energy-regenerative suspension under passive / semi-active working condition provided by the embodiment of the application;
[0049] Figure 18 is a simulation model diagram of the hydraulic control type hydraulic reverser suitable for the electro-hydraulic energy-regenerative suspension active damping provided by the embodiment of the present application;
[0050] Figure 19 (a) is a simulation verification diagram of the hydraulic pump output flow in the active condition provided by the embodiment of the present application, and (b) is a simulation verification diagram of the output rotating speed of the blade damper in the active condition provided by the embodiment of the present application;
[0051] In the figure: 101, valve body of the new hydraulic control type hydraulic reverser; 201, large end cover; 202, control piston one; 203, tension spring; 204, spool valve one; 301, large end cover; 302, control piston two; 303, compression spring; 304, spool valve two; 305, small end cover; 401, small end cover; 402, sealing element; 403, small valve body two; 404, spool valve two; 405, compression spring; 406, control piston two; 407, connecting element; 408, control piston one; 409, small valve body one; 410, spool valve one; 411, tension spring; 412, lower base; 1, new hydraulic control type hydraulic reverser; 5, spool valve one and spool valve two integration; 6, spool valve one integration; 7, spool valve two integration; 8, pull arm; 9, external control oil circuit; 10, hydraulic pump / motor. DETAILED DESCRIPTION
[0052] In order to make the purpose, technical scheme and advantages of the present application more clear, the present application is further described in detail below in combination with embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application, and are not used to limit the present application.
[0053] In order to make those skilled in the art fully understand how the present application is specifically implemented, this part is an explanation and description of the embodiments of the technical scheme of the claims.
[0054] The model diagram of the hydraulic control type hydraulic reverser 1 suitable for the electro-hydraulic energy-regenerative suspension active damping provided by the embodiment of the present application is as shown in Figure 1 , the front view is as shown in Figure 2 , the left view is as shown in Figure 3 , the top view is as shown in Figure 4 , and the bottom view is as shown in Figure 5 .
[0055] The principle diagram of the hydraulic control type hydraulic reverser 1 suitable for the electro-hydraulic energy-regenerative suspension active damping is as shown in Figure 6As shown, when the main / passive switching valve on the external control oil line 9 is not controlled to act, there is no pilot oil in the external control oil line 9, and the new hydraulic control hydraulic reverser 1 can only realize hydraulic rectification of the blade damper to the hydraulic motor 10; when the main / passive switching valve on the external control oil line 9 is controlled to act, there is pilot oil in the external control oil line 9, and 4 of the 8 valve ports in the new hydraulic control hydraulic reverser 1 are always open, and 4 of the 8 valve ports are always closed, the new hydraulic control hydraulic reverser 1 is short-circuited, and the hydraulic oil can flow freely between the blade damper and the hydraulic pump 10 through the new hydraulic control hydraulic reverser 1. Therefore, by controlling the main / passive switching valve on the external control oil line 9 to act, the pilot oil can be controlled, and then the on-off state of each valve port in the new hydraulic control hydraulic reverser 1 can be controlled, so as to achieve the purpose of actively controlling whether to realize hydraulic rectification or active damping.
[0056] In the embodiment of the present application, the internal structure of the new hydraulic control hydraulic reverser 1 is as shown in Figure 7 、 8 , 9, 10, 11, 12, 13, because the new hydraulic control hydraulic reverser 1 is a symmetrical structure, one side includes: 101, new hydraulic control hydraulic reverser valve body; 201, large end cover; 202, control piston one; 203, tension spring; 204, cone valve one; 301, large end cover; 302, control piston two; 303, compression spring; 304, cone valve two; 305, small end cover; 401, small end cover; 402, sealing element; 403, small valve body two; 404, cone valve two; 405, compression spring; 406, control piston two; 407, connecting element; 408, control piston one; 409, small valve body one; 410, cone valve one; 411, tension spring; 412, lower base.
[0057] When the new hydraulic control hydraulic reverser 1 is in passive / semi-active working condition, the main / passive switching valve on the external control oil line 9 is not actuated, and there is no pilot oil in the external control oil line 9, because the up and down vibration of the loaded wheel drives the blade damper to rotate forward / backward, so that the high and low pressure cavities are formed between the blade damper and the new hydraulic control hydraulic reverser 1. When the blade damper rotates forward (clockwise) under the driving action of the up and down vibration of the loaded wheel, the hydraulic oil in the high pressure cavity pushes Figure 7 the cone valve one in section A-A to move into the new hydraulic control hydraulic reverser 1 and flow out from the oil port C below section G-G, to push the hydraulic motor 10 to rotate, and then flow into the new hydraulic control hydraulic reverser 1 from the oil port A below section G-G, to push Figure 13 the cone valve one in section C-C to move, so that the hydraulic oil enters the low pressure cavity; when the blade damper rotates backward (counterclockwise) under the driving action of the up and down vibration of the loaded wheel, the hydraulic oil in the high pressure cavity pushes Figure 13 the cone valve one in section A-A to move into the new hydraulic control hydraulic reverser 1 and flow out from the oil port A below section G-G, to push the hydraulic motor 10 to rotate, and then flow into the new hydraulic control hydraulic reverser 1 from the oil port C below section G-G, to push Figure 9 the cone valve one in section C-C to move, so that the hydraulic oil enters the low pressure cavity; when the blade damper rotates backward (counterclockwise) under the driving action of the up and down vibration of the loaded wheel, the hydraulic oil in the high pressure cavity pushes Figure 9The spool valve two in the section C-C moves into the new hydraulic control type hydraulic commutator 1 and flows out from the Figure 13 The oil in the section G-G flows out from the oil port C, pushes the hydraulic motor 10 to rotate, and then flows out from the Figure 13 The oil in the section G-G flows into the new hydraulic control type hydraulic commutator 1 from the oil port A, pushes Figure 7 The spool valve two in the section A-A moves to make the hydraulic oil enter the low-pressure cavity. In this working condition, no matter how the blade damper rotates and what the relative positions of the high-pressure cavity and the low-pressure cavity are, the new hydraulic control type hydraulic commutator 1 can realize the purpose of hydraulic rectification, makes the hydraulic oil flow into and out of the hydraulic motor 10 in a fixed direction, pushes the hydraulic motor 10 to work stably in a fixed direction, and further drives the generator to rotate and generate energy; in the active working condition of the new hydraulic control type hydraulic commutator 1, the main / passive switching valve on the external control oil circuit 9 is in action, and when the pilot oil in the external control oil circuit 9, the pilot oil in the external control oil circuit 9 pushes Figure 7 The section A-A and Figure 9 The control piston one and two in the section C-C move to make Figure 7 The spool valve two in the section A-A is always closed, the spool valve one is always opened, the spool valve one in the section C-C is always opened, the spool valve two is always closed, and the circuit signal obtained by the early road surface detection controls the oil supply of the hydraulic pump 10 to rotate in the positive direction or the reverse direction, so that the hydraulic oil flows into the cavity between the new hydraulic control type hydraulic commutator 1 and the blade damper from the oil port A or C in the section G-G, hinders the rotation of the blade damper caused by the up-down vibration of the load wheel, and after the active damping is completed, the hydraulic oil flows out from the oil port C or A in the section G-G.
[0058] In order to prove the creativity and technical value of the technical scheme of the application, this part is an application embodiment of the technical scheme of the claim on a specific product or related technology.
[0059] The embodiment of the application further provides a mechatronic energy feeding suspension system, a flow chart as shown in Figure 14 A model diagram as shown in Figure 15 Comprises:
[0060] When the vehicle is running on uneven road, the state of the pilot oil in the external control oil circuit 9 is controlled by the action of the main / passive switching valve on the external control oil circuit 9, if so, the active working condition is carried out, the motor is controlled to rotate forward or reverse by the electrical control system, the hydraulic pump 10 is driven to rotate forward or reverse by the motor, the hydraulic pump 10 outputs hydraulic oil, the novel hydraulic control hydraulic reverser 1 is short-circuited, the hydraulic oil can freely enter and exit the cavity formed between the blade shock absorber and the novel hydraulic control hydraulic reverser 1, and the action of the blade shock absorber is hindered to complete the active damping; if not, the passive / semi-active working condition is carried out, the load wheel vibrates up and down, the connecting rod drives the pull arm to swing repeatedly, and then drives the blade shock absorber to rotate forward or reverse, the high and low pressure cavities are formed between the blade shock absorber and the novel hydraulic control hydraulic reverser 1, and the hydraulic oil reciprocating flow is generated, the hydraulic oil flows into and out of the hydraulic motor 10 after being rectified by the novel hydraulic control hydraulic reverser 1, the hydraulic motor 10 is pushed to rotate in a certain direction and drives the motor to rotate to generate electricity, and finally the electrical control system stores the electrical energy to complete the energy recovery.
[0061] It should be noted that the embodiments of the present application can be realized by hardware, software or a combination of software and hardware. The hardware part can be realized by special logic; the software part can be stored in a memory and executed by a suitable instruction execution system, such as a microprocessor or a specially designed hardware. Those skilled in the art can understand that the above-mentioned devices and methods can be realized by computer executable instructions and / or included in processor control codes, such as carrier media, such as magnetic disk, CD or DVD-ROM, programmable memory, such as read-only memory (firmware), or data carrier, such as optical or electronic signal carrier. The device of the present application and its modules can be realized by hardware circuit, such as ultra-large scale integrated circuit or gate array, semiconductor, such as logic chip, transistor, etc., or programmable hardware device, such as field programmable gate array, programmable logic device, etc., or by software executed by various types of processors, or by a combination of the above-mentioned hardware circuit and software, such as firmware.
[0062] During the development or use of the embodiments of the present application, some positive effects have been achieved, and compared with the prior art, the present application indeed has great advantages, which will be described below in combination with the data and graphs of the test process.
[0063] The simulation verification of the novel hydraulic control hydraulic reverser 1 suitable for electro-hydraulic energy feedback suspension active damping is also carried out, the simulation model of the novel hydraulic control hydraulic reverser 1 and the electro-mechanical-hydraulic energy feedback suspension active damping is established based on the AMESim software, it is verified by simulation that the passive / semi-active working condition can efficiently recover the suspension vibration energy after being rectified by the novel hydraulic control hydraulic reverser 1, and the mode switching of the novel hydraulic control hydraulic reverser 1 can be realized through the external control oil circuit 9.
[0064] According to the proposed electro-hydraulic energy-regenerative suspension working principle, an electro-hydraulic energy-regenerative suspension simulation model is built in AMESim as shown in Figure 16 Fig. 1, and the energy recovery effect of the electro-hydraulic energy-regenerative suspension system is tested under different amplitudes (represented by the blade damper rotation angle amplitude) in the passive / semi-active working condition using a 1 Hz sine input. The simulation model runs for two cycles, and the energy recovery power of the electro-hydraulic energy-regenerative suspension system is shown in Figure 17 Fig. 2(a). After rectification by the new hydraulic control type hydraulic rectifier 1, the electro-hydraulic energy-regenerative suspension can recover vibration energy at high power regardless of the clockwise or counterclockwise swing of the blade damper. As the blade damper swing angle amplitude increases from 5° to 25°, the average energy recovery power of the system increases from 273 W to 3483 W, and the energy recovery power reaches the kilowatt level. The energy recovery efficiency of the electro-hydraulic energy-regenerative suspension is shown in Figure 17 Fig. 2(b). After rectification by the new hydraulic control type hydraulic rectifier 1, the electro-hydraulic energy-regenerative suspension can recover suspension vibration energy at high efficiency. As the blade damper swing angle amplitude increases from 5° to 25°, the average energy recovery efficiency of the system decreases from 60.9% to 52.6% within one cycle, and can reach more than 50% in the low-frequency ideal working condition. The above simulation proves that after hydraulic rectification by the new hydraulic control type hydraulic rectifier 1, the electro-hydraulic energy-regenerative suspension can achieve superior energy recovery performance.
[0065] According to the working principle of the new hydraulic control type hydraulic rectifier 1 proposed in the scheme, a simulation model is built in AMESim as shown in Figure 18 Fig. 3, to verify that when the main / passive switching valve in the external control oil circuit 9 is actuated and there is pilot oil in the external control oil circuit 9, the new hydraulic control type hydraulic rectifier 1 is in the active working condition, and the blade damper can be freely controlled to rotate forward or reverse. At this time, the blade damper can be regarded as a large displacement hydraulic motor. A rotation speed signal is input to the hydraulic pump of the external control oil circuit 9 to supply oil to the control oil circuit. At this time, the new hydraulic control type hydraulic rectifier 1 is in the active working condition. The hydraulic pump output flow under the sine input rotation speed working condition is shown in Figure 19 Fig. 4(a), and the blade damper output rotation speed is shown in Figure 19 Fig. 4(b). It can be seen from Figure 16 that at this time, the blade damper can be freely controlled to rotate forward or reverse by the hydraulic pump 10, which is the active damping principle of the electro-hydraulic energy-regenerative suspension, and at this time, the blade damper action hysteresis time is 0.02 s, the hysteresis is low, and the system response speed is fast.
[0066] From the above simulation, it can be seen that the new type of hydraulic control type hydraulic commutator 1 can control the state of the pilot oil in the external control oil circuit 9 by controlling the action of the main / passive switching valve on the external control oil circuit 9, realize the free switching of passive / semi-active working condition and active working condition, and achieve the functions of realizing high-efficiency vibration energy recovery by hydraulic rectification under passive / semi-active working condition, and realizing high-performance damping by bidirectional free control under active working condition.
[0067] The above is only a specific embodiment of the present application, but the protection scope of the present application is not limited thereto, any modification, equivalent replacement and improvement within the technical range disclosed by the present application and within the spirit and principle of the present application should be covered within the protection scope of the present application.
Claims
1. A pilot operated hydraulic diverter, characterized by, The hydraulic control type hydraulic reverser is an integrated structure, and the free switching of the passive / semi-active working condition and the active working condition is controlled by the action of the main / passive switching valve on the external control oil circuit, and the normally open and normally closed states of the valve port of the hydraulic control type hydraulic reverser are controlled. The internal structure of the hydraulic control type hydraulic reverser comprises a hydraulic control type hydraulic reverser valve body, a cone valve one, a tensile spring, a control piston one, a large end cover, a small end cover, a cone valve two, a compression spring, a control piston two, a sealing element, a small valve body one, a connecting element, a small valve body two, and a lower base. When the hydraulic control type hydraulic reverser is in the passive / semi-active working condition, the main / passive switching valve on the external control oil circuit is not in action, and there is no pilot oil in the external control oil circuit, the rotation of the blade damper causes the high and low pressure cavities between the blade damper and the hydraulic control type hydraulic reverser, the high pressure cavity hydraulic oil pushes the cone valve one or the cone valve two into the hydraulic control type hydraulic reverser and flows out from the oil port C, pushes the hydraulic motor to rotate in a certain direction, and then flows back to the hydraulic control type hydraulic reverser from the oil port A, pushes the cone valve two or the cone valve one to move, so that the hydraulic oil enters the low pressure oil cavity, and the hydraulic oil flows into and out of the hydraulic control type hydraulic reverser in a certain direction, and the hydraulic motor rotates in a certain direction. When the hydraulic control type hydraulic reverser is in the active working condition, the main / passive switching valve on the external control oil circuit is in action, and there is pilot oil in the external control oil circuit, the pilot oil in the external control oil circuit flows into the oil port B, pushes the control piston one, the cone valve one, and the control piston two to move, so that one of the two valve ports is normally closed and the other is normally open, and the two valve ports are normally open and normally closed, respectively, and the motor is controlled to rotate in a certain direction by the circuit signal, so that the hydraulic pump rotates in a certain direction to supply oil, and the hydraulic oil flows into the oil port A or C and then flows out from the oil port C or A, thereby preventing the blade damper from rotating in a certain direction under the vibration transmission action of the load wheel.
2. The pilot operated hydraulic diverter as set forth in claim 1, wherein, The valve port of the hydraulic control type hydraulic reverser is controlled by the action of the main / passive switching valve on the external control oil circuit to control the normally open and normally closed states of the valve port.
3. The pilot operated hydraulic diverter as defined in claim 1, wherein, When the main / passive switching valve on the external control oil circuit is not in action and there is no pilot oil in the external control oil circuit, the hydraulic control type hydraulic reverser performs directional rectification from the damper to the hydraulic motor.
4. The pilot operated hydraulic diverter as defined in claim 1, wherein, When the main / passive switching valve on the external control oil circuit is in action and there is pilot oil in the external control oil circuit, the pilot oil in the external control oil circuit controls the normally open and normally closed states of the eight valve ports of the hydraulic control type hydraulic reverser, so that the hydraulic control type hydraulic reverser is short-circuited.
5. An electro-hydraulic energy feeding suspension system implementing the hydraulic pilot operated hydraulic diverter according to any one of claims 1-4, the electro-hydraulic energy feeding suspension system comprising: The load wheel, the connecting rod, the pull arm, the damper, the hydraulic reverser, the hydraulic pump / motor, the generator, the battery, and the electrical control system are characterized in that the working process of the electromechanical hydraulic energy feedback suspension system is as follows: When the vehicle is running on uneven road, it is judged whether the main / passive switching valve in the external control oil circuit is actioned, if the main / passive switching valve is actioned, there is pilot oil in the external control oil circuit, then the hydraulic control hydraulic reverser is in the active working condition, the hydraulic control hydraulic reverser is short circuit, the electrical control system controls the motor forward / reverse rotation, the motor drives the hydraulic pump forward / reverse rotation, after the hydraulic pump outputs hydraulic oil, the hydraulic oil freely enters and exits the chamber between the hydraulic control hydraulic reverser and the blade shock absorber, and the blade shock absorber is hindered from vibrating up and down under the action of the load wheel to complete the active damping; If the main / passive switching valve is not actioned, there is no pilot oil in the external control oil circuit, then the hydraulic control hydraulic reverser is in passive / semi-active working condition, the load wheel vibrates up and down, the connecting rod drives the pull arm to swing repeatedly, and then drives the blade shock absorber to rotate forward / reverse, the reciprocating flow of hydraulic oil is generated in the high and low pressure cavities, the hydraulic oil flows into and out of the hydraulic motor after being rectified by the hydraulic control hydraulic reverser, pushes the hydraulic motor to rotate directionally and then drives the motor to rotate to generate electricity, and finally the electrical control system stores the electrical energy to complete energy recovery.
Citation Information
Patent Citations
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