CN210240418U - Variable-suspension balancing oil cylinder control valve group, system and engineering machinery - Google Patents
Variable-suspension balancing oil cylinder control valve group, system and engineering machinery Download PDFInfo
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- CN210240418U CN210240418U CN201921000625.2U CN201921000625U CN210240418U CN 210240418 U CN210240418 U CN 210240418U CN 201921000625 U CN201921000625 U CN 201921000625U CN 210240418 U CN210240418 U CN 210240418U
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Abstract
The utility model provides a variable balanced hydro-cylinder valve unit, system and engineering machine tool that hangs. The control valve group of the balancing oil cylinder comprises an electro-hydraulic proportional pressure reducing valve and a hydraulic control one-way valve, an oil outlet of the electro-hydraulic proportional pressure reducing valve is communicated with an oil cavity of the balancing oil cylinder, an oil inlet of the hydraulic control one-way valve is communicated with an oil outlet of the electro-hydraulic proportional pressure reducing valve and used for controlling oil to flow to the balancing oil cylinder from the electro-hydraulic proportional pressure reducing valve, and a pilot oil way of the hydraulic control one-way valve is communicated with an oil inlet of the. The balance oil cylinder control system comprises a balance oil cylinder control valve group, the engineering machinery comprises the balance oil cylinder control system, and the balance oil cylinder control system is simple in control structure, low in cost and excellent in suspension rigidity adjusting characteristic.
Description
Technical Field
The utility model relates to a hang and adjust technical field, especially relate to a balanced hydro-cylinder valve unit, system and engineering machine tool that variably hangs.
Background
The walking comfort of the road vehicle is particularly important, and the quality of the damping performance is an important consideration standard of the walking comfort. The wheel excavator is a special engineering machine capable of running on a road, the walking comfort and the safety of the wheel excavator are one of important indexes considering the performance of the wheel excavator, and the wheel excavator mainly controls the operation of a balance oil cylinder by a balance oil cylinder control valve, so the working performance of the balance oil cylinder control valve is particularly important.
Because the rigidity provided by the balance oil cylinder control valve for the suspension system in the prior art is certain, when a road surface is bumpy, the walking vibration of the wheel excavator is very large, the damping effect is poor, and the driving comfort is poor.
SUMMERY OF THE UTILITY MODEL
Not enough to prior art, the utility model aims to provide a variable balanced hydro-cylinder valve unit, system and engineering machine tool that hangs to solve current engineering machine tool be difficult to reach good balanced technical problem driving comfort and security.
Therefore, the purpose of the utility model is realized by the following technical scheme:
variable balanced hydro-cylinder valve unit that hangs includes:
the oil pressure behind the valve of the electro-hydraulic proportional pressure reducing valve can be proportionally adjusted by the current input to the electro-hydraulic proportional pressure reducing valve, and an oil outlet of the electro-hydraulic proportional pressure reducing valve is communicated with an oil cavity of the balance oil cylinder;
and an oil inlet of the hydraulic control one-way valve is communicated with an oil outlet of the electro-hydraulic proportional pressure reducing valve and used for controlling oil to flow from the electro-hydraulic proportional pressure reducing valve to the balance oil cylinder, and a pilot oil way of the hydraulic control one-way valve is communicated with an oil inlet of the electro-hydraulic proportional pressure reducing valve and used for controlling the opening and closing of the hydraulic control one-way valve.
As a further optional scheme of the variably suspended balance cylinder control valve group, the variably suspended balance cylinder control valve group includes a plurality of the hydraulic control check valves, each of the hydraulic control check valves is connected in parallel to a pressure regulating oil path where the electro-hydraulic proportional pressure reducing valve is located, and the balance cylinders correspond to the hydraulic control check valves one to one.
As a further optional scheme of the variable-suspension control valve group for the balance oil cylinder, a switch valve is arranged between an oil inlet of the electro-hydraulic proportional pressure reducing valve and the actuating oil way, and the switch valve is used for controlling the on-off of the electro-hydraulic proportional pressure reducing valve and the actuating oil way.
As a further optional scheme of the variably suspended balance oil cylinder control valve group, the balance oil cylinder control valve group further comprises an integrated valve block, the electro-hydraulic proportional pressure reducing valve and the hydraulic control one-way valve are inserted into the integrated valve block, and an actuating oil port, a low-pressure oil port and an actuating oil port are formed on the integrated valve block;
the actuating oil port is communicated with an oil inlet of the electro-hydraulic proportional pressure reducing valve and a pilot oil path of the hydraulic control one-way valve, the low-pressure oil port is communicated with an oil return port of the electro-hydraulic proportional pressure reducing valve, and the actuating oil port is communicated with an oil outlet of the hydraulic control one-way valve.
As the further extension to above-mentioned technical scheme, the utility model also provides a variable balanced hydro-cylinder control system who hangs, including the balanced hydro-cylinder valve unit that controller and foretell variable hang, the controller be used for adjust to the variable input current who hangs balanced hydro-cylinder valve unit.
As a further alternative of the variable suspension balancing cylinder control system, the variable suspension balancing cylinder control system further includes a sensor electrically connected to the controller, the sensor is configured to sense a road surface bump condition, and the controller controls the current input to the electro-hydraulic proportional pressure reducing valve according to the road surface bump condition.
As a further optional solution of the variable suspension balancing cylinder control system, the sensor is a vibration sensor provided on a main machine on which the balancing cylinder is mounted.
As a further alternative of the variable suspension balancing cylinder control system, the sensor is a pressure sensor for sensing an oil pressure of an oil chamber of the balancing cylinder.
As a further optional solution of the variable suspension balancing cylinder control system, the variable suspension balancing cylinder control system further includes a control element electrically connected to the controller, and the control element is configured to adjust a current input by the controller to the electro-hydraulic proportional pressure reducing valve.
As the further extension to above-mentioned technical scheme, the utility model also provides an engineering machine tool, it includes chassis, balanced hydro-cylinder and foretell variable balanced hydro-cylinder control system who hangs, the variable balanced hydro-cylinder control system who hangs with balanced hydro-cylinder intercommunication, balanced hydro-cylinder connects on the chassis.
Compared with the prior art, the utility model discloses a variable balanced hydro-cylinder valve unit, system and engineering machine tool that hangs have following beneficial effect at least:
the pressure of the balance oil cylinder can be adjusted by arranging the electro-hydraulic proportional pressure reducing valve, the suspension rigidity is adjusted, the driving road condition and the working condition can be adjusted in an adaptive mode, the balance oil cylinder is enabled to have good self-locking performance by arranging the hydraulic control one-way valve, the quick response characteristic is achieved during pressure adjustment, the control structure is simple, the cost is low, and the excellent suspension rigidity adjusting characteristic is achieved.
In order to make the aforementioned objects, features and advantages of the present invention more apparent and understandable, the following embodiments are described in detail with reference to the accompanying drawings.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention, and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without inventive efforts.
Fig. 1 shows a schematic diagram of a variable-suspension balancing cylinder control valve group provided in embodiment 1 of the present invention;
figure 2 shows the relationship between the degree of road jounce and the desired suspension stiffness in example 1 of the present invention;
fig. 3 shows the relationship between the output pressure and the suspension stiffness of the electro-hydraulic proportional pressure reducing valve in embodiment 1 of the present invention;
fig. 4 shows the relationship between the output pressure of the electro-hydraulic proportional pressure reducing valve and the road condition jolting degree in embodiment 1 of the present invention;
fig. 5 shows the relationship between the control current and the output pressure of the electro-hydraulic proportional pressure reducing valve in embodiment 1 of the present invention;
fig. 6 shows the relationship between the control current of the electro-hydraulic proportional pressure reducing valve and the road condition jolting degree in embodiment 1 of the present invention;
fig. 7 shows an effect diagram of the suspension pressure when the balance cylinder control valve group with variable suspension is adopted in embodiment 1 of the present invention.
Description of the main element symbols:
100-balancing oil cylinder control valve group; 110-electro-hydraulic proportional pressure reducing valve; 120-a pilot operated check valve; 121-pilot oil circuit; 130-a switch valve; 140-an integrated valve block; 141-actuating oil port; 142-a low pressure oil port; 143-an execution oil port; 200-balance oil cylinder; 300-actuating oil path.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary only for the purpose of explaining the present invention, and should not be construed as limiting the present invention.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", and the like, indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be construed as limiting the present invention.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless specifically limited otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," and "fixed" are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.
In the present application, unless expressly stated or limited otherwise, the first feature may be directly on or directly under the second feature or indirectly via intermediate members. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.
Example 1
As shown in fig. 1, the present embodiment provides a variable suspension balancing cylinder control valve group, hereinafter referred to as "balancing cylinder control valve group 100" for short. The balance oil cylinder 200 is used as a providing component of suspension pressure, and the rigidity/hardness of the suspension is adjusted by adjusting the pressure of the balance oil cylinder 200, so that the comfort and the safety of driving are adjusted and selected.
The balancing cylinder control valve group 100 comprises an electro-hydraulic proportional pressure reducing valve 110 and a pilot operated check valve 120. The post-valve oil pressure of the electro-hydraulic proportional pressure reducing valve 110 can be proportionally adjusted by the current input thereto, and thus the post-valve pressure of the electro-hydraulic proportional pressure reducing valve 110 is adjusted by adjusting the current input to the electro-hydraulic proportional pressure reducing valve 110, that is, the output pressure of the electro-hydraulic proportional pressure reducing valve 110 is proportionally adjusted by the magnitude of the input current. The oil outlet of the electro-hydraulic proportional pressure reducing valve 110 is communicated with the oil cavity of the balance oil cylinder 200, so that the oil cavity pressure of the balance oil cylinder 200 can be adjusted by adjusting the pressure behind the electro-hydraulic proportional pressure reducing valve 110.
An oil inlet of the hydraulic control check valve 120 is communicated with an oil outlet of the electro-hydraulic proportional pressure reducing valve 110 to control oil to flow from the electro-hydraulic proportional pressure reducing valve 110 to the balance cylinder 200, and a pilot oil path 121 of the hydraulic control check valve 120 is communicated with an oil inlet of the electro-hydraulic proportional pressure reducing valve 110 to control opening and closing of the hydraulic control check valve 120. The pilot oil path 121 of the hydraulic control check valve 120 is communicated with the high-pressure port of the electro-hydraulic proportional pressure reducing valve 110, the oil inlet of the hydraulic control check valve 120 is connected with the low-pressure port of the electro-hydraulic proportional pressure reducing valve 110, and it is ensured that when the electro-hydraulic proportional pressure reducing valve 110 is opened, the opening pressure of the hydraulic control check valve 120 is always greater than the circulation pressure, so that the oil inlet and the oil outlet of the hydraulic control check valve 120 can be bidirectionally circulated.
Fig. 2 shows a relationship between a road bumping degree and a desired suspension stiffness, fig. 3 shows a relationship between an output pressure of the electro-hydraulic proportional pressure reducing valve 110 and a suspension stiffness, fig. 4 shows a relationship between an output pressure of the electro-hydraulic proportional pressure reducing valve 110 and a road bumping degree, fig. 5 shows a relationship between a control current and an output pressure of the electro-hydraulic proportional pressure reducing valve 110, fig. 6 shows a relationship between a control current of the electro-hydraulic proportional pressure reducing valve 110 and a road bumping degree, and fig. 7 shows an effect diagram of a suspension pressure when the balancing cylinder control valve group 100 is adopted.
The current input to the electro-hydraulic proportional pressure reducing valve 110 can adjust the opening degree of the electro-hydraulic proportional pressure reducing valve 110, so that the electro-hydraulic proportional pressure reducing valve 110 has different throttle areas and thus different pressure losses. Since the pressure of the front valve/the pressure of the oil inlet of the electro-hydraulic proportional pressure reducing valve 110 are constant, different pressure losses are adjusted, so that different pressures of the back valve/the pressure of the oil outlet are achieved. The larger the opening degree of the electro-hydraulic proportional pressure reducing valve 110 is, the smaller the pressure loss is, and the smaller the opening degree is, the larger the pressure loss is.
The electro-hydraulic proportional pressure reducing valve 110 is conventional and includes a valve spool, a valve stem, a spring, and an electromagnet. The valve core is inserted in the valve cavity, the valve rod is connected to the valve cavity, a spring is arranged in the valve rod and pushes against the end face of the valve core, and the electromagnet is a coil type electromagnet and is sleeved on the valve rod. Under the normal state, the spring pushes the valve core to be in the closing position, the electromagnet provides magnetic force for the valve core when being electrified, the valve core is driven to move towards the opening position, meanwhile, the valve core compresses the spring, and the spring generates elastic restoring force along with the electromagnetic force to balance. The magnitude of the electromagnetic force on the electromagnet is proportional to the current, the magnitude of the electromagnetic force is proportional to the compression amount of the spring, and the magnitude of the electromagnetic force is the magnitude of the elastic force generated on the spring, so that the pressure fluctuation after the valve is balanced with the spring force, that is, the electromagnetic force, and thus the pressure after the valve of the electro-hydraulic proportional pressure reducing valve 110 can be proportionally controlled by controlling the current input to the electro-hydraulic proportional pressure reducing valve 110. Meanwhile, the spring has a good response characteristic and can push the valve core to a corresponding position in time along with the change of electromagnetic force, so that the electro-hydraulic proportional pressure reducing valve 110 has different throttling areas.
As described above, the current input to the electro-hydraulic proportional pressure reducing valve 110 can be continuously adjusted, so that the pressure behind the electro-hydraulic proportional pressure reducing valve 110 can be continuously adjusted, and the pressure adjustment of the electro-hydraulic proportional pressure reducing valve 110 is a stepless adjustment. When the device is used, a plurality of adjusting nodes can be arranged for step adjustment, for example, pressures of 5Mpa, 10Mpa and 15Mpa are provided for determining, and servo continuous adjustment can be carried out according to actual road conditions.
The pilot-controlled check valve 120 has a good response speed/opening speed, and can be quickly opened when the pressure on the pilot oil path 121 meets the opening pressure of the pilot-controlled check valve, so that the electro-hydraulic proportional pressure reducing valve 110 is bidirectionally communicated with the balance oil cylinder 200, the electro-hydraulic proportional pressure reducing valve 110 provides working pressure for the balance oil cylinder 200, and the rigidity of the balance oil cylinder 200 can be adjusted by adjusting the pressure behind the electro-hydraulic proportional pressure reducing valve 110. The electro-hydraulic proportional pressure reducing valve 110 is communicated with a rodless cavity of the balance oil cylinder 200 through a hydraulic control one-way valve 120, and provides pressure for a piston rod of the balance oil cylinder 200, so that suspension rigidity is provided.
The balancing cylinder control valve group 100 includes a plurality of hydraulic control check valves 120, each hydraulic control check valve 120 is connected in parallel to the pressure regulating oil path where the electro-hydraulic proportional pressure reducing valve 110 is located, and the balancing cylinders 200 correspond to the hydraulic control check valves 120 one by one. The oil inlet of each pilot-controlled check valve 120 is connected in parallel behind the valve of the electro-hydraulic proportional pressure reducing valve 110, and the pilot oil path 121 of each pilot-controlled check valve 120 is connected in parallel in front of the valve of the electro-hydraulic proportional pressure reducing valve 110.
In this embodiment, the balancing cylinder control valve group 100 includes two hydraulic control check valves 120, and each hydraulic control check valve 120 is communicated with a balancing cylinder 200. When the working oil is introduced into the oil inlet of the electro-hydraulic proportional pressure reducing valve 110, the pilot oil path 121 of the hydraulic control check valve 120 controls the hydraulic control check valve 120 to open, the two balance oil cylinders 200 are communicated with each other, and the pressures of the two balance oil cylinders 200 are equal and equal to the pressure behind the electro-hydraulic proportional pressure reducing valve 110.
Further, a switch valve 130 is arranged between an oil inlet of the electro-hydraulic proportional pressure reducing valve 110 and the operating oil path 300, and the switch valve 130 is used for controlling the on-off of the electro-hydraulic proportional pressure reducing valve 110 and the operating oil path 300. The on-off valve 130 may be a manual valve or a solenoid valve. The on/off of the on/off valve 130 is controlled to control the presence or absence of the hydraulic oil input. When the switching valve 130 is turned off, and no operating oil is input to the electro-hydraulic proportional pressure reducing valve 110 and the pilot check valve 120, the pilot check valve 120 is not opened, the balance cylinder 200 is locked, and the balance cylinder 200 has a large rigidity. When the switching valve 130 is opened, working oil is input to the electro-hydraulic proportional pressure reducing valve 110 and the pilot check valve 120, and the pilot check valve 120 is opened, so that the pressure of the balance cylinder 200 can be adjusted by the electro-hydraulic proportional pressure reducing valve 110.
It should be noted that the above-mentioned operating oil path 300 may be an oil path connected to a hydraulic system of a host machine to which the balanced valve control valve set is applied, and can provide a stable pressure, which is greater than the pilot opening pressure of the pilot check valve 120, and the pressure provided by the electro-hydraulic proportional pressure reducing valve 110 is not greater than the pressure; the actuation oil path 300 may be the actuation pressure provided by the oil pump, and at this time, the on-off valve 130 may be omitted, and the pressure regulating function of the balancing oil cylinder 200 may be selected directly by controlling the start and stop of the oil pump.
The balancing cylinder control valve group 100 can be integrated on a valve block as a plug-in type multi-way valve. The balancing cylinder control valve group 100 further includes an integration valve block 140, the electro-hydraulic proportional pressure reducing valve 110 and the hydraulic control check valve 120 are inserted into the integration valve block 140, and an actuating oil port 141, a low pressure oil port 142 and an actuating oil port 143 are formed on the integration valve block 140. The actuating oil port 141 is communicated with an oil inlet of the electro-hydraulic proportional pressure reducing valve 110 and the pilot oil path 121 of the hydraulic control check valve 120, the low pressure oil port 142 is communicated with an oil return port of the electro-hydraulic proportional pressure reducing valve 110, and the execution oil port 143 is communicated with an oil outlet of the hydraulic control check valve 120.
The electro-hydraulic proportional pressure reducing valve 110 and the hydraulic control one-way valve 120 can be cartridge valves, threads are directly arranged on the valve body, threaded holes are formed in the integrated valve block 140, and therefore the integrated valve block 140 is directly screwed on, and the end face of the integrated valve block 140 can also be connected with the integrated valve block through bolts. The working oil port 141 is communicated with the working oil path 300, so that the working oil path 300 is communicated with the oil inlet of the electro-hydraulic proportional pressure reducing valve 110 and the pilot oil path 121 of the pilot operated check valve 120. The low pressure port 142 communicates with a low pressure oil path, typically a tank, communicating the return oil of the electro-hydraulic proportional pressure reducing valve 110 to the tank. The execution oil port 143 communicates with the balance cylinder 200, so that the balance cylinder 200 communicates with an oil outlet of the pilot operated check valve 120. The number of the execution oil ports 143 may be multiple, and corresponds to the number of the balance cylinders 200, and a spare execution oil port 143 may be reserved for communicating with more balance cylinders 200 or communicating with other execution components.
As described above, the balance cylinder control valve group 100 is integrated into the integrated valve block 140, so that the assembly and disassembly can be more convenient, a host machine to which the balance cylinder control valve group 100 is applied does not need to be modified, the integrated valve block 140 is directly fixed on the host machine, and the actuation oil path 300, the oil tank and the balance cylinder 200 are connected to corresponding oil ports of the integrated valve block 140 through oil pipes.
Example 2
The present embodiment provides a variable suspension balancing cylinder control system, hereinafter simply referred to as "balancing cylinder control system". The balance cylinder control system comprises a controller and the balance cylinder control valve group 100 in embodiment 1, wherein the controller is used for adjusting the control current of the balance cylinder control valve group 100, namely adjusting the control current of an electro-hydraulic proportional pressure reducing valve 110 in the balance cylinder control valve group 100. When the balancing cylinder control valve group 100 further includes the on-off valve 130, the controller is also used to control the on-off current of the on-off valve 130.
In this embodiment, the balancing cylinder control system further includes a sensor electrically connected to the controller, the sensor is configured to sense a road surface jolt condition, and the controller controls a current input to the electro-hydraulic proportional pressure reducing valve 110 according to the road surface jolt condition, thereby implementing servo adjustment of suspension stiffness. When the road surface is bumpy, the output pressure of the electro-hydraulic proportional pressure reducing valve 110 can be reduced, the rigidity of the balance oil cylinder 200 is reduced, and the driving comfort is improved; when the road surface is flat, the output pressure of the electro-hydraulic proportional pressure reducing valve 110 can be increased, the rigidity of the balance oil cylinder 200 is increased, and the driving safety is improved; when the main machine applied to the balance cylinder control system needs to work besides running, when the main machine works, the output pressure of the electro-hydraulic proportional pressure reducing valve 110 can be further adjusted or the switch valve 130 is closed, so that the balance cylinder 200 has higher rigidity, and the stability of the main machine in a working mode is ensured.
In the present embodiment, the sensor is a pressure sensor for sensing the oil pressure of the oil chamber of the balancing cylinder 200. The pressure sensor can be communicated with an oil path between the balance oil cylinder 200 and the hydraulic control one-way valve 120, and represents the road bumping condition in the form of stress of the balance oil cylinder 200. The more bumpy the road surface is, the larger the pressure sensed by the pressure sensor is, and the output pressure of the electro-hydraulic proportional pressure reducing valve 110 can be correspondingly reduced; the flatter the road surface, the less pressure the pressure sensor senses, and the output pressure of the electro-hydraulic proportional pressure reducing valve 110 can be correspondingly increased.
In another embodiment, the sensor may be a vibration sensor disposed on a host machine carried by the balancing cylinder 200, and the pitching condition of the road surface is represented in the form of host machine vibration. The more bumpy the road surface is, the larger the vibration sensed by the vibration sensor is; the flatter the road surface, the less vibration the vibration sensor senses.
In another embodiment, the balancing cylinder control system further includes a control element electrically connected to the controller, and the control element is configured to adjust the current input by the controller to the electro-hydraulic proportional pressure reducing valve 110. The control element can be a hardware key, a knob, a rocker, a handle and the like arranged on a host machine applied to the balance oil cylinder control system, and can also be a key on a software control interface. The driver can manually control the output pressure of the electro-hydraulic proportional pressure reducing valve 110 through the control element according to the actual road condition, if the control element is a key, the number of the key is multiple, each key represents different adjusting pressure, and the key can also comprise a '+' key and a '-' key, and the magnitude of the adjusting pressure is adjusted through adding and subtracting; if the control piece is a knob, a rocker, a handle and the like, the pressure can be adjusted in a stepped mode or continuously.
Example 3
The embodiment provides an engineering machine, which comprises a chassis, a balance cylinder 200 and a balance cylinder control system in the embodiment 2, wherein the balance cylinder control system is communicated with the balance cylinder 200, the balance cylinder 200 is connected to the chassis, and the balance cylinder 200 is used as a suspension for adjusting the hardness of the chassis.
The working machine, which is used as a main machine of the balance cylinder control system, is generally a wheel type working machine, such as a wheel excavator, a wheel loader, a wheel dozer, a wheel transporter, etc.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
Although embodiments of the present invention have been shown and described, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art without departing from the scope of the present invention.
Claims (10)
1. Variable balanced hydro-cylinder valve unit that hangs, its characterized in that includes:
the oil pressure behind the valve of the electro-hydraulic proportional pressure reducing valve can be proportionally adjusted by the current input to the electro-hydraulic proportional pressure reducing valve, and an oil outlet of the electro-hydraulic proportional pressure reducing valve is communicated with an oil cavity of the balance oil cylinder;
and an oil inlet of the hydraulic control one-way valve is communicated with an oil outlet of the electro-hydraulic proportional pressure reducing valve and used for controlling oil to flow from the electro-hydraulic proportional pressure reducing valve to the balance oil cylinder, and a pilot oil way of the hydraulic control one-way valve is communicated with an oil inlet of the electro-hydraulic proportional pressure reducing valve and used for controlling the opening and closing of the hydraulic control one-way valve.
2. The variably suspended control group of balancing cylinders according to claim 1, wherein the variably suspended control group of balancing cylinders comprises a plurality of said pilot operated check valves, each of said pilot operated check valves being connected in parallel to a pressure regulating circuit in which said electro-hydraulic proportional pressure reducing valve is located, said balancing cylinders corresponding to said pilot operated check valves one-to-one.
3. The variably-suspended balance cylinder control valve group according to claim 1, wherein a switch valve is arranged between an oil inlet of the electro-hydraulic proportional pressure reducing valve and the actuating oil path, and the switch valve is used for controlling the on-off of the electro-hydraulic proportional pressure reducing valve and the actuating oil path.
4. The variably suspended balance cylinder control valve group according to claim 1, further comprising an integration valve block, wherein the electro-hydraulic proportional pressure reducing valve and the hydraulic control check valve are inserted into the integration valve block, and an actuating oil port, a low pressure oil port and an actuating oil port are formed on the integration valve block;
the actuating oil port is communicated with an oil inlet of the electro-hydraulic proportional pressure reducing valve and a pilot oil path of the hydraulic control one-way valve, the low-pressure oil port is communicated with an oil return port of the electro-hydraulic proportional pressure reducing valve, and the actuating oil port is communicated with an oil outlet of the hydraulic control one-way valve.
5. A variable suspension balancing cylinder control system, characterized in that it comprises a controller for regulating the input current to the variable suspension balancing cylinder control valve group and a variable suspension balancing cylinder control valve group according to any of claims 1-4.
6. The variable suspension balancing cylinder control system according to claim 5, further comprising a sensor electrically connected to the controller, the sensor sensing a road surface bump condition, and the controller controlling the current input to the electro-hydraulic proportional pressure reducing valve according to the road surface bump condition.
7. The variably suspended counterbalance cylinder control system of claim 6, wherein the sensor is a vibration sensor provided on a host machine on which the counterbalance cylinder is mounted.
8. The variably suspended counterbalance cylinder control system of claim 6, wherein the sensor is a pressure sensor for sensing an oil pressure of an oil chamber of the counterbalance cylinder.
9. The variable suspension balancing cylinder control system of claim 5, further comprising a control member electrically connected to the controller, the control member being configured to adjust the current input by the controller to the electro-hydraulic proportional pressure relief valve.
10. Engineering machinery, characterized by comprising a chassis, a balancing cylinder and a variably suspended balancing cylinder control system according to any one of claims 5 to 9, the variably suspended balancing cylinder control system being in communication with the balancing cylinder, the balancing cylinder being connected to the chassis.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921000625.2U CN210240418U (en) | 2019-06-28 | 2019-06-28 | Variable-suspension balancing oil cylinder control valve group, system and engineering machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921000625.2U CN210240418U (en) | 2019-06-28 | 2019-06-28 | Variable-suspension balancing oil cylinder control valve group, system and engineering machinery |
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| CN210240418U true CN210240418U (en) | 2020-04-03 |
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| CN201921000625.2U Active CN210240418U (en) | 2019-06-28 | 2019-06-28 | Variable-suspension balancing oil cylinder control valve group, system and engineering machinery |
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| CN (1) | CN210240418U (en) |
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