CN117325597A - Industrial and mining vehicle and hydraulic suspension system thereof - Google Patents
Industrial and mining vehicle and hydraulic suspension system thereof Download PDFInfo
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- CN117325597A CN117325597A CN202311243283.8A CN202311243283A CN117325597A CN 117325597 A CN117325597 A CN 117325597A CN 202311243283 A CN202311243283 A CN 202311243283A CN 117325597 A CN117325597 A CN 117325597A
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- expansion
- suspension system
- valve
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- 239000000725 suspension Substances 0.000 title claims abstract description 129
- 238000005065 mining Methods 0.000 title claims abstract description 35
- 239000011229 interlayer Substances 0.000 claims abstract description 6
- 238000006073 displacement reaction Methods 0.000 claims description 21
- 230000001960 triggered effect Effects 0.000 claims description 14
- 238000004891 communication Methods 0.000 claims description 11
- 230000001105 regulatory effect Effects 0.000 claims description 4
- 238000000034 method Methods 0.000 claims description 3
- 238000005192 partition Methods 0.000 claims description 3
- 238000005086 pumping Methods 0.000 claims description 3
- 230000004888 barrier function Effects 0.000 abstract description 8
- 230000009286 beneficial effect Effects 0.000 abstract description 2
- 239000003921 oil Substances 0.000 description 28
- 230000004308 accommodation Effects 0.000 description 6
- 230000003139 buffering effect Effects 0.000 description 4
- 238000007599 discharging Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005553 drilling Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000011435 rock Substances 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 230000003044 adaptive effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000005007 materials handling Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 239000002352 surface water Substances 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
- B60G11/26—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
- B60G11/26—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs
- B60G11/265—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs hydraulic springs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
- B60G17/0408—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics details, e.g. antifreeze for suspension fluid, pumps, retarding means per se
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
- B60G17/0416—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics regulated by varying the resiliency of hydropneumatic suspensions
- B60G17/0424—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics regulated by varying the resiliency of hydropneumatic suspensions by varying the air pressure of the accumulator
Abstract
The application discloses industrial and mining vehicle and hydraulic suspension system thereof, wherein hydraulic suspension system includes: the device comprises an oil tank, a hydraulic pump, a suspension oil cylinder, an energy accumulator, an air storage tank and a switch valve; the suspension oil cylinder comprises a piston rod and a cylinder body connected with the hydraulic pump; the energy accumulator is used for adjusting the pressure of the hydraulic medium in the cylinder body; the cylinder body is internally provided with an accommodating space for accommodating the hydraulic medium; the piston rod is inserted into the accommodating space; the accumulator comprises: a housing and a barrier; the shell is provided with an air pressure cavity and a hydraulic pressure cavity; the interlayer is movably arranged between the air pressure cavity and the hydraulic cavity; the air storage tank is provided with at least one first-type expansion cavity communicated with the air pressure cavity; the switch valve is provided with a first expansion interface communicated with the first expansion cavity and an expansion input interface communicated with the air pressure cavity. The beneficial point of the application lies in: the hydraulic suspension system of the industrial and mining vehicle is characterized in that the buffer capacity of the energy accumulator is changed, so that the energy accumulator can be suitable for severe road conditions.
Description
Technical Field
The application relates to the technical field of general machinery, in particular to an industrial and mining vehicle and a hydraulic suspension system thereof.
Background
Engineering machines such as material handling machines, rock drilling rigs, and scraper trucks, and mining machines often need to travel in areas with poor road conditions such as pits, rough terrain, and severe surface water accumulation, and particularly for material handling machines, often need to travel over long distances and have a higher probability of traveling in areas with poor road conditions. While the existing hydraulic suspension system can buffer the impact of external force on the vehicle, but lacks a convenient and effective adjusting mode to meet the demands of various working conditions, and the energy accumulator of the hydraulic suspension system has limited capacity of buffering external pressure and is limited by manufacturing and assembly cost and limitation on the liquid charging and discharging time of the energy accumulator, so that the buffer capacity of the energy accumulator is difficult to be enhanced by integrating an oversized energy accumulator on the vehicle, and the existing hydraulic suspension system is difficult to adapt to the use demands of severe road conditions.
In the related art, chinese patent publication No. CN110077192B discloses a semi-active hydro-pneumatic suspension system with adjustable rigidity and a method for controlling the same, which changes the rigidity of the hydro-pneumatic suspension system by adjusting the inflation pressure of the accumulator in real time. However, the related art does not provide any technical teaching for how to solve the technical problem that the buffer capacity of the accumulator is limited, so that the accumulator is difficult to adapt to the use requirement of severe road conditions.
Disclosure of Invention
The content of the present application is intended to introduce concepts in a simplified form that are further described below in the detailed description. The section of this application is not intended to identify key features or essential features of the claimed subject matter, nor is it intended to be used to limit the scope of the claimed subject matter.
Some embodiments of the present application provide an industrial and mining vehicle and a hydraulic suspension system thereof that address the technical issues mentioned in the background section above.
As a first aspect of the present application, some embodiments of the present application provide a hydraulic suspension system comprising: the hydraulic system comprises an oil tank, a hydraulic pump, a suspension oil cylinder, an energy accumulator, an air storage tank and a switching valve.
The oil tank is used for storing hydraulic medium; the hydraulic pump is used for pumping the hydraulic medium stored in the oil tank to an oil way of the hydraulic suspension system; the suspension cylinder comprises a cylinder body connected with the hydraulic pump for receiving the hydraulic medium pumped by the hydraulic pump and a piston rod connected with the cylinder body in a sliding manner; the energy accumulator is used for adjusting the pressure of the hydraulic medium pumped by the hydraulic pump received by the cylinder body; the cylinder body is internally provided with an accommodating space for accommodating hydraulic medium pumped by the hydraulic pump; one end of the piston rod is inserted into the accommodating space to partition the accommodating space into a rodless cavity and a rod cavity; the other end of the piston rod penetrates out of the accommodating space from the rod cavity; the rodless cavity is connected to the hydraulic pump; the accumulator is communicated to the rodless cavity.
The accumulator comprises: a housing and a barrier; the shell is provided with an air pressure cavity and a hydraulic cavity communicated with the rodless cavity; the interlayer is movably arranged between the air pressure cavity and the hydraulic cavity so as to bias the interlayer and compress the volume of the air pressure cavity when the hydraulic medium in the rodless cavity flows into the hydraulic cavity; the air storage tank is provided with at least one first type expansion cavity communicated with the air pressure cavity; the switch valve is provided with a first expansion interface communicated with the first expansion cavity and an expansion input interface communicated with the air pressure cavity so as to enable the first expansion cavity to be communicated with the air pressure cavity when the first expansion interface is communicated with the expansion input interface.
In one embodiment, the air reservoir further has: a second type expansion chamber; the switching valve further has: a second expansion interface; the second type of expansion cavity is communicated with the rodless cavity through a switch valve; the second expansion interface is connected to the second expansion chamber to enable the second expansion chamber to be communicated to the air pressure chamber when the second expansion interface is communicated with the expansion input interface.
In one embodiment, the on-off valve is configured as a solenoid valve; the valve core of the electromagnetic valve is provided with at least a communication position relative to the valve block of the electromagnetic valve so that the capacity expansion input interface is simultaneously communicated with the first capacity expansion cavity and the second capacity expansion cavity when the valve core of the electromagnetic valve is at the communication position.
In one embodiment, the ratio of the volume of the first expansion chamber to the volume of the second expansion chamber ranges from 0.8 to 1.2.
In one embodiment, the hydraulic suspension system further comprises: barometer and air supply device; the air pressure gauge is used for detecting whether the air pressure in the first expansion cavity and/or the second expansion cavity is at a preset value or not; the air supply device is used for inputting air into the first expansion cavity and/or the second expansion cavity so as to enable the air pressure in the first expansion cavity and/or the second expansion cavity to reach a preset value; the air supply device is connected to the first expansion cavity and/or the second expansion cavity through an air supply pipeline; the barometer is connected to the air supply line.
In one embodiment, the hydraulic suspension system further comprises: a master control electromagnetic valve and a safety valve; the master control electromagnetic valve is provided with a hydraulic input interface connected with the hydraulic pump and a hydraulic output interface connected with the rodless cavity, so that the hydraulic pump is communicated with the rodless cavity through the hydraulic input port and the hydraulic output port when triggered; the relief valve has a pressure relief input port connected to the rodless chamber and a pressure relief output port connected to the oil tank to enable the rodless chamber to communicate to the oil tank through the pressure relief input port and the pressure relief output port when triggered.
In one embodiment, the safety valve is configured as an electromagnetic reverse-proportion overflow valve.
In one embodiment, the hydraulic suspension system further comprises: a controller and a displacement sensor; the controller is electrically connected to the master control electromagnetic valve and the electromagnetic type inverse proportion overflow valve to control whether the master control electromagnetic valve and the electromagnetic type inverse proportion overflow valve are triggered or not when the controller works; the displacement sensor is used for sending a displacement signal containing the position information of the piston rod relative to the cylinder body; the displacement sensor is fixedly connected to the suspension cylinder; the controller is electrically connected with the displacement sensor so that the controller receives the displacement signal to work.
In one embodiment, the hydraulic suspension system further comprises: a pressure sensor; wherein the pressure sensor is connected to the rodless cavity to detect the magnitude of the hydraulic pressure in the rodless cavity; wherein, pressure sensor constitutes power connection with the controller.
In one embodiment, the hydraulic suspension system further comprises: an electromagnetic proportional pressure reducing valve; the electromagnetic proportional pressure reducing valve is provided with a pressure reducing input port connected with the hydraulic input interface and a pressure reducing output port connected with the rodless cavity, so that the hydraulic input interface is communicated with the rodless cavity through the pressure reducing input port and the pressure reducing output port when triggered.
As a second aspect of the present application, some embodiments of the present application provide an industrial and mining vehicle including any one of the hydraulic suspension systems described above.
The beneficial effects of this application lie in: the hydraulic suspension system of the industrial and mining vehicle is characterized in that the buffer capacity of the energy accumulator is changed, so that the energy accumulator can be suitable for severe road conditions.
More specifically, some embodiments of the present application may have the following specific benefits:
according to the hydraulic suspension system, after the air storage tank is communicated to the energy accumulator by the switch valve, the compressible allowance of air in the energy accumulator is increased, which is equivalent to changing the buffering capacity of the energy accumulator, so that the energy accumulator can buffer larger impact force, and the piston rod of the suspension oil cylinder can move relative to the cylinder body more easily, so that the rigidity of the hydraulic suspension system is changed. The provision of the on-off valve allows the accumulator to be used as is generally conventional in the art. Therefore, the buffer capacity of the energy accumulator can be adjusted according to road conditions, and the rigidity of the hydraulic suspension system can be further adjusted, so that mechanical equipment carrying the hydraulic suspension system can be suitable for different road conditions, and the hydraulic suspension system can be stably used under severe road conditions in the background art.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, are included to provide a further understanding of the application and to provide a further understanding of the application with regard to the other features, objects and advantages of the application. The drawings of the illustrative embodiments of the present application and their descriptions are for the purpose of illustrating the present application and are not to be construed as unduly limiting the present application.
In addition, the same or similar reference numerals denote the same or similar elements throughout the drawings. It should be understood that the figures are schematic and that elements and components are not necessarily drawn to scale.
In the drawings:
FIG. 1 is an overall schematic of a particular embodiment of a hydraulic suspension system according to one embodiment of the present application;
FIG. 2 is a schematic illustration of another embodiment of a hydraulic suspension system according to one embodiment of the present application with the on-off valve in the connected position;
FIG. 3 is a schematic diagram of the control valve assembly of FIG. 1;
fig. 4 is a schematic diagram of a particular embodiment of a hydraulic suspension system integrated into a mining transportation truck according to one embodiment of the present application.
Meaning of the reference numerals in the drawings:
100. a hydraulic suspension system;
110. an oil tank;
120. a hydraulic pump;
130. a suspension cylinder; 131. a cylinder; 131a, an accommodation space; 131b, rodless cavity; 131c, having a rod cavity; 132. a piston rod; 133. a displacement sensor; 134. a pressure sensor;
140. a control valve group; 141. a master control electromagnetic valve; 141a, hydraulic input interface; 141b, a hydraulic output interface; 142. a safety valve; 142a, pressure relief input port; 142b, pressure relief output port; 143. an electromagnetic proportional pressure reducing valve; 143a, a reduced pressure input port; 143b, a reduced pressure output port;
150. an accumulator; 151. a housing; 151a, pneumatic chamber; 151b, hydraulic chamber; 151c, a ventilation interface; 152. an interlayer;
160. a gas storage tank; 161. a first type expansion chamber; 162. a second type expansion chamber; 163. an air pressure gauge;
170. a switch valve; 171. a first expansion interface; 172. a capacity expansion input interface; 173. a second expansion interface;
180. a gas supply device;
190. and a controller.
Detailed Description
Embodiments of the present disclosure will be described in more detail below with reference to the accompanying drawings. While certain embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure may be embodied in various forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete. It should be understood that the drawings and embodiments of the present disclosure are for illustration purposes only and are not intended to limit the scope of the present disclosure.
It should be noted that, for convenience of description, only the portions relevant to the present application are shown in the drawings. Embodiments of the present disclosure and features of embodiments may be combined with each other without conflict.
It should be noted that references to "one", "a plurality" and "a plurality" in this disclosure are intended to be illustrative rather than limiting, and those of ordinary skill in the art will appreciate that "one or more" is intended to be understood as "one or more" unless the context clearly indicates otherwise.
The present disclosure will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.
Referring to fig. 1-4, a hydraulic suspension system 100 of the present application may be integrated for use on work machines and mining machines (hereinafter collectively referred to as "industrial and mining vehicles") including, but not limited to, materials handling machines, rock drilling rigs, scraper trucks, and the like. The hydraulic suspension system 100 includes: the hydraulic system comprises an oil tank 110, a hydraulic pump 120, a suspension cylinder 130, a control valve bank 140 and an accumulator 150.
The oil tank 110 is used for storing a hydraulic medium, and the hydraulic medium is preferably hydraulic oil. When the hydraulic suspension system 100 is integrated in a mining vehicle, hydraulic medium in the oil tank 110 may be delivered to hydraulic actuators such as an on-vehicle oil cylinder and a hydraulic motor through a pipeline to drive each hydraulic actuator to work. The hydraulic pump 120 is used to pump the hydraulic medium stored in the oil tank 110 to the oil path of the hydraulic suspension system 100, and the hydraulic pump 120 may be further used to pump the hydraulic medium stored in the oil tank 110 to other vehicle-mounted hydraulic actuators.
The suspension cylinder 130 includes a cylinder block 131 connected to the hydraulic pump 120 to receive the hydraulic medium pumped by the hydraulic pump 120, and a piston rod 132 slidably connected to the cylinder block 131. The control valve block 140 is used for controlling the on-off of the oil path between the hydraulic pump 120 and the cylinder block 131. The accumulator 150 is used to regulate the pressure of the hydraulic medium pumped by the hydraulic pump 120 received by the cylinder 131.
Specifically, the cylinder block 131 has an accommodating space 131a inside which the hydraulic medium pumped by the hydraulic pump 120 is accommodated. One end of the piston rod 132 is inserted into the accommodation space 131a to partition the accommodation space 131a into a rodless chamber 131b and a rod chamber 131c. The other end of the piston rod 132 passes through the accommodation space 131a from the rod chamber 131c, and the rod-less chamber 131b is connected to the oil tank 110 through the control valve group 140 to control the on-off of the oil passage between the rod-less chamber 131b and the oil tank 110 through the control valve group 140. The accumulator 150 communicates with the rodless chamber 131b. The rodless chamber 131b is connected to the hydraulic pump 120, i.e. the hydraulic pump 120 is able to pump hydraulic medium into the rodless chamber 131b. Specifically, the rodless chamber 131b is connected to the hydraulic pump 120 through the control valve block 140 to achieve charge and discharge control of the suspension cylinder 130 and the accumulator 150 using the control valve block 140.
In this way, the hydraulic suspension system 100, when integrated into an industrial and mining vehicle, enables the end of the piston rod 132 to be connected to one of the frame and the body of the industrial and mining vehicle, while the cylinder 131 is connected to the other of the frame and the body of the industrial and mining vehicle, so as to achieve a basic function of damping the hydraulic suspension system 100 by using the hydraulic medium in the accommodation space 131a and the accumulator 150 to buffer external impact during traveling of the industrial and mining vehicle.
More specifically, the accumulator 150 includes: a housing 151 and a barrier 152. The housing 151 has a pneumatic chamber 151a and a hydraulic chamber 151b in communication with the rodless chamber 131b, and the accumulator 150 has a vent port 151c in communication with the pneumatic chamber 151a to regulate the air pressure in the pneumatic chamber 151a under the action of an external air source. The barrier 152 is movably disposed between the pneumatic chamber 151a and the hydraulic chamber 151b to bias the barrier 152 and compress the volume of the pneumatic chamber 151a when the hydraulic medium in the rod-less chamber 131b flows into the hydraulic chamber 151 b. The barrier 152 includes, but is not limited to, a form of an air bag, a piston plate, etc., so that when an external impact is applied to the piston rod 132, the hydraulic medium in the rodless chamber 131b can flow into the hydraulic chamber 151b, the hydraulic medium biases the barrier 152 to increase the air pressure in the air pressure chamber 151a, and when the external impact is weakened, the air in the air pressure chamber 151a can bias the barrier 152 to return the hydraulic medium in the hydraulic chamber 151b to the rodless chamber 131b, thereby realizing the function of buffering the external impact by the suspension cylinder 130.
To make the stiffness of the hydraulic suspension system 100 adjustable, defining the hydraulic suspension system 100 further includes: the air tank 160 and the on-off valve 170.
Wherein the air tank 160 has at least one expansion chamber 161 of the first type communicating with the air pressure chamber 151a. The switching valve 170 has a first expansion port 171 communicating with the first expansion chamber and a expansion input port 172 communicating with the pneumatic chamber 151a to communicate the first-type expansion chamber 161 with the pneumatic chamber 151a when the first expansion port 171 communicates with the expansion input port 172.
By adopting the above scheme, when the industrial and mining vehicle integrated with the hydraulic suspension system 100 is used under different road conditions, the switch valve 170 can be controlled to select whether the first expansion cavity is communicated with the air pressure cavity 151a or not, so that the compressible quantity of air in the air pressure cavity 151a is regulated, and the resistance received when the piston rod 132 of the suspension cylinder 130 moves is changed, thus the telescopic quantity of the piston rod 132 when the piston rod 132 bears external impact is controlled, and the effect of regulating the rigidity of the hydraulic suspension system 100 is achieved. By this technical effect, the industrial and mining vehicle with the integrated hydraulic suspension system 100 can be adapted to travel under different road conditions.
Compared with the scheme of adopting a plurality of accumulators 150 to adjust the buffering capacity of the hydraulic suspension system 100, the hydraulic suspension system 100 can be adjusted in rigidity under the condition that the liquid filling and discharging time of the hydraulic cavity 151b of the accumulator 150 is not basically influenced, so that the hydraulic suspension system 100 is more suitable for being used under severe road conditions.
Specifically, the air tank 160 further has: a second type of flash chamber 162. The on-off valve 170 further has: and a second expansion interface 173. The second type expansion chamber 162 is connected to the rodless chamber 131b through the on-off valve 170. The second expansion port 173 is connected to the second expansion chamber to communicate the second expansion chamber to the pneumatic chamber 151a when communicating with the expansion input port 172. That is, the second type expansion chamber 162 may also be utilized to adjust the amount of compressibility of the gas in the pneumatic chamber 151a. In this way, a stepped adjustment of the stiffness of hydraulic suspension system 100 may be achieved with each expansion chamber.
It should be noted that, in this embodiment, the first type expansion chamber 161 and the second type expansion chamber 162 of the air tank 160 are used as an example to perform the step adjustment on the rigidity of the hydraulic suspension system 100, and it should not be considered that the air tank 160 cannot be provided with more expansion chambers, or that a plurality of independent air tanks 160 cannot be provided to implement the step adjustment on the rigidity of the hydraulic suspension system 100.
In an alternative embodiment, referring to FIG. 1, the on-off valve 170 may be configured as a manual valve. At this time, a corresponding operation handle, an operation button, etc. may be further provided in the cab of the industrial and mining vehicle to control the manual switching valve 170, thereby adjusting the on-off between the first type expansion chamber 161/the second type expansion chamber 162 and the air pressure chamber 151a.
In an alternative embodiment, referring to FIG. 2, to further adapt hydraulic suspension system 100 for use in rough road conditions, on-off valve 170 is configured as a solenoid valve. Namely, the electromagnetic control mode is adopted to automatically complete the on-off between the first type expansion cavity 161/the second type expansion cavity 162 and the air pressure cavity 151a.
At this time, the spool of the solenoid valve has at least a communication position with respect to the valve block of the solenoid valve so that the expansion input port 172 is simultaneously communicated to the first expansion chamber and the second expansion chamber when the spool of the solenoid valve is in the communication position. That is, the solenoid valve can control the first-type expansion chamber 161 and the second-type expansion chamber 162 to be synchronously communicated to the pneumatic chamber 151a, so as to fully utilize the volumes of the first-type expansion chamber 161 and the second-type expansion chamber 162 to adjust the rigidity of the hydraulic suspension system 100.
In the above scheme, if the valve core of the electromagnetic valve is adopted to simultaneously connect the first type expansion chamber 161 and the second type expansion chamber 162 to the air pressure chamber 151a when the valve core is at the connection position, it is preferable that the volumes of the first type expansion chamber 161 and the second type expansion chamber 162 are consistent, so that the variation of the compressible amount of the air in the air pressure chamber 151a between each "gear" is more balanced when the rigidity of the hydraulic suspension system 100 is adjusted in steps. Considering other factors such as manufacturing errors, optionally, the ratio of the volume of the first expansion cavity to the volume of the second expansion cavity ranges from 0.8 to 1.2, so that the rigidity of the hydraulic suspension system 100 can be changed relatively smoothly between gears while the hydraulic suspension system is convenient to manufacture.
In the related art, the air pressure in the air pressure chamber 151a of the accumulator 150 is generally charged with air having an air pressure value reaching a threshold value before the hydraulic suspension system 100 is normally used. In this application, in order to make the hydraulic suspension system 100 operate relatively stably during the rigid adjustment process, the ratio of the preset value of the air pressure in the air tank 160 to the air pressure threshold value in the air pressure chamber 151a of the accumulator 150 should be in the range of 0.9 to 1.1, so that the air pressure in the air pressure chamber 151a does not suddenly change when the air pressure chamber 151a is connected to the first type expansion chamber 161 and the second type expansion chamber 162, which would affect the stable operation of the hydraulic suspension system 100.
Optionally, the air pressure in the air storage tank 160 may be filled with air in advance before the device is put into use, so that the air pressures in the first type expansion chamber 161 and the second type expansion chamber 162 reach a preset value.
In another alternative embodiment, hydraulic suspension system 100 further includes: a barometer 163 and an air supply 180. The barometer 163 is configured to detect whether the air pressure in the first expansion chamber and/or the second expansion chamber is at a preset value. The gas supply device 180 is configured to supply gas to the first expansion chamber and/or the second expansion chamber so that the gas pressure in the first expansion chamber and/or the second expansion chamber reaches a preset value. The air supply device 180 may be a vehicle-mounted air compressor, a pressure vessel connected to the air compressor, etc., and is connected to the first expansion chamber and/or the second expansion chamber through an air supply pipeline, so that air is input into the air storage tank 160 during operation to enable the air pressure in the air storage tank 160 to reach a preset value. The barometer 163 may be a commercially available electronic barometer 163 that is connected to a gas supply line to detect the air pressure within the reservoir 160 when the gas supply 180 is supplying gas to the reservoir 160 and the hydraulic suspension system 100 is operating properly.
Thus, when the air pressure in the air tank 160 decreases due to long-term use or equipment failure, the air pressure in the air tank 160 is regulated by the air supply device 180 and the air pressure gauge 163, and the hydraulic suspension system 100 can be stably operated.
Specifically, to implement charge and discharge control of the accumulator 150 and the suspension cylinder 130, referring to fig. 3, the control valve group 140 includes: a pilot solenoid valve 141 and a relief valve 142.
Wherein the master solenoid valve 141 has a hydraulic input port 141a connected to the hydraulic pump 120 and a hydraulic output port 141b connected to the rodless chamber 131b to allow the hydraulic pump 120 to communicate to the rodless chamber 131b through the hydraulic input port and the hydraulic output port when triggered. The relief valve 142 has a relief input port 142a connected to the rodless chamber 131b and a relief output port 142b connected to the tank 110 to allow the rodless chamber 131b to communicate to the tank 110 through the relief input port 142a and the relief output port 142b when triggered. Namely, the hydraulic charge and discharge control of the accumulator 150 and the suspension cylinder 130 is realized by the actions of the master control solenoid valve 141 and the relief valve 142. The relief valve 142 may be a relief valve to allow the hydraulic pressure in the suspension cylinder 130 to be too high so that the accumulator 150 may be opened to allow the hydraulic medium in the rodless chamber 131b to flow back to the oil tank 110, thereby ensuring the safety of the hydraulic suspension system 100.
More specifically, to accommodate use in rough terrain, the relief valve 142 is configured as an electromagnetic reverse-proportional relief valve, and the subject matter of this application does not relate to improvements in the electromagnetic reverse-proportional relief valve itself, the structure and principles of which are not repeated here.
Since the vehicle requires the relief valve 142 to function as a set relief valve most of the time when the hydraulic suspension system 100 is used in rough terrain, the accumulator 150 and the suspension cylinder 130, and the piping connected therebetween, are protected. While the vehicle is adjusting the height of the vehicle, the relief valve 142 is needed as an adjustable relief valve for relief, which results in less working time. The use of an electromagnetic reverse-proportion overflow valve here allows the use of the valve as a safety valve most of the time (for example when driving and the electromagnetic reverse-proportion overflow valve is not powered). When the height of the vehicle body is adjusted, the safety valve 142 is powered to release pressure according to the environment of the vehicle and the road surface, and the oil in the rodless cavity of the suspension cylinder 130 is discharged to reduce the height of the vehicle body.
The diaphragm 152 of the accumulator 150 and the piston rod 132 of the suspension cylinder 130 move more frequently than when used on flat road surfaces, and thus it is also necessary to control the charging and discharging of the accumulator 150 and the suspension cylinder 130 more frequently. By adopting the above scheme, when the relief valve 142 is used for discharging the suspension cylinder 130 and the accumulator 150, the characteristic of the oil pressure in the pipeline can be stabilized by using the electromagnetic inverse proportion overflow valve, so that the hydraulic suspension system 100 can stably work when being used under severe terrain.
Specifically, hydraulic suspension system 100 further includes: a controller 190 and a displacement sensor 133. Wherein the controller 190 is electrically connected to the main control solenoid valve 141 and the electromagnetic type inverse proportion overflow valve to control whether both are triggered in operation. The controller 190 may be a programmable logic controller 190, a control chip, or the like integrated on an industrial and mining vehicle. The displacement sensor 133 is used for sending out a displacement signal containing information about the position of the piston rod 132 relative to the cylinder 131. The displacement sensor 133 is commercially available, and for example, a model RHM0295MP121S3B6105 displacement sensor from Metts (MTS) is available. The displacement sensor 133 is fixedly connected to the suspension cylinder 130. The controller 190 is electrically connected to the displacement sensor 133, so that the controller 190 receives the displacement signal to operate. Namely, the position of the piston rod 132 relative to the cylinder body 131 is controlled by the cooperation of the controller 190 and the displacement sensor 133, and the length of the piston rod 132 extending out of the accommodating space 131a is adjusted by the cooperation of the master control electromagnetic valve 141 and the electromagnetic inverse proportion overflow valve, namely, the amount of hydraulic medium filled in the hydraulic cavity 151b of the accumulator 150 and the rodless cavity 131b of the suspension cylinder 130 is controlled.
In this way, the reservoir 160 can be used to adjust the stiffness of the hydraulic suspension system 100 when used in rough terrain. The position of the piston rod 132 relative to the cylinder 131 can also be adjusted by using the master electromagnetic valve 141 and the electromagnetic inverse proportion overflow valve, that is, the height position of the center of gravity of the industrial and mining vehicle integrated with the hydraulic suspension system 100 is adjusted, so that when the industrial and mining vehicle passes through a wading section, the height position of the body of the industrial and mining vehicle can be adjusted, the industrial and mining vehicle can smoothly pass through the wading section, and the adaptability of the industrial and mining vehicle to severe road conditions is further improved.
In one embodiment, hydraulic suspension system 100 further includes: a pressure sensor 134. Wherein a pressure sensor 134 is connected to the rodless chamber 131b to detect the magnitude of the hydraulic pressure within the rodless chamber 131b. The pressure sensor 134 is in electrical communication with the controller 190. Pressure sensor 134 is commercially available, and may be, for example, a Danfoss company pressure sensor model 063G 1158. By providing the pressure sensor 134, the hydraulic pressure of the hydraulic medium in the suspension cylinder 130 can be fed back to the controller 190, and the controller 190 can be used to control the electromagnetic type inverse proportion reducing valve 143, so as to control the filling pressure of the rodless cavity of the suspension cylinder 130.
More specifically, the control valve block 140 further includes: electromagnetic proportional pressure reducing valve 143. Wherein the electromagnetic proportional pressure reducing valve 143 has a pressure reducing input port 143a connected to the hydraulic pressure input port 141a and a pressure reducing output port 143b connected to the rodless chamber 131b so that the hydraulic pressure input port 141a communicates to the rodless chamber 131b through the pressure reducing input port 143a and the pressure reducing output port 143b when triggered. It is contemplated that hydraulic pump 120 may be capable of pumping hydraulic medium to other on-board hydraulic actuators when hydraulic suspension system 100 is integrated with an industrial and mining vehicle, where the operating hydraulic pressure of the other on-board actuators is different from suspension cylinders 130. By providing the electromagnetic proportional pressure reducing valve 143, when the hydraulic medium is pumped to the suspension cylinder 130 by the master control electromagnetic valve 141, the electromagnetic proportional pressure reducing valve 143 can be triggered, so that the hydraulic pressure of the hydraulic medium pumped to the rodless cavity 131b is relatively stable, and the stability of the hydraulic suspension system 100 is further ensured.
When the hydraulic suspension system 100 is integrated in an industrial and mining vehicle, the arrangement of the components of the hydraulic suspension system 100 may be adaptively adjusted according to the type, model, etc. of the industrial and mining vehicle.
One possible embodiment of the hydraulic suspension system 100 when installed in a mining transportation truck is described below. It should be noted that this description should be taken as an illustration of the adaptive adjustments that can be made when hydraulic suspension system 100 is integrated with a mining transportation truck, and should not be taken as if hydraulic suspension system 100 could be integrated with a mining transportation truck only in this manner, nor should hydraulic suspension system 100 be considered to be integrated with a mining transportation truck only.
Referring to fig. 4, in one particular embodiment, four suspension cylinders 130 are provided on the mining haul truck, one on each side and front and rear of the vehicle. Wherein a cylinder body 131 of the suspension cylinder 130 is connected to a vehicle body, and an end of a piston rod 132 extending out of the accommodation space 131a is connected to a vehicle frame to which wheels are mounted, so that the vehicle body can move relative to the vehicle frame. The rodless chambers 131b of the two suspension cylinders 130 located on both sides of the rear portion of the vehicle are connected to the same accumulator 150, and the rodless chambers 131b of the two suspension cylinders 130 located on both sides of the front portion of the vehicle are connected to the other accumulator 150. And both accumulators 150 are connected to the same reservoir 160. Correspondingly, an electromagnetic switch valve 170 is arranged between the air storage tank 160 and the two accumulators 150.
The air storage tank 160 is provided with two expansion chambers which can be communicated to one of the accumulators 150 through one of the electromagnetic switch valves 170, and two other expansion chambers which are communicated to the other accumulator 150 through the other electromagnetic switch valve 170, so as to realize the step adjustment of the rigidity of the accumulator 150. The electromagnetic switch valve 170 is a three-position four-way valve.
The suspension cylinder 130 employs a single-acting cylinder, i.e., the rodless chamber 131b of the suspension cylinder 130 is connected to the hydraulic pump 120/tank 110 through the control valve block 140, while the rod chamber 131c is connected to the tank 110 through a pipe.
The oil inlet of the hydraulic pump 120 is connected to the oil tank 110 to draw hydraulic medium from the oil tank 110. The oil outlet of the hydraulic pump 120 is connected to the hydraulic input port 141a of the master solenoid valve 141. The hydraulic output port 141b of the master control solenoid valve 141 is communicated to the rodless chamber 131b through the electromagnetic proportional pressure reducing valve 143, so that the hydraulic pump 120 pumps hydraulic medium to the rodless chamber 131b of the suspension cylinder 130 and the hydraulic chamber 151b of the accumulator 150 when the master control solenoid valve 141 and the electromagnetic proportional pressure reducing valve 143 are triggered, and charging of the suspension cylinder 130 and the accumulator 150 is achieved.
The hydraulic chamber 151b of the accumulator 150 and the rodless chamber 131b of the suspension cylinder 130, which is in communication with the accumulator 150, are connected to the same electromagnetic inverse proportion overflow valve through a pipeline, so that when the electromagnet of the electromagnetic inverse proportion overflow valve is powered on or the hydraulic pressure in the rodless chamber 131b of the suspension cylinder 130 is too high, the rodless chamber 131b is communicated to the oil tank 110, and the drainage of the suspension cylinder 130 and the accumulator 150 is realized.
The outlet port of hydraulic pump 120 is also connected by piping to other on-board hydraulic actuators to pump hydraulic medium to each on-board hydraulic actuator.
The foregoing description is only of the preferred embodiments of the present disclosure and description of the principles of the technology being employed. It will be appreciated by those skilled in the art that the scope of the invention in the embodiments of the present disclosure is not limited to the specific combination of the above technical features, but encompasses other technical features formed by any combination of the above technical features or their equivalents without departing from the spirit of the invention. Such as the above-described features, are mutually substituted with (but not limited to) the features having similar functions disclosed in the embodiments of the present disclosure.
Claims (11)
1. A hydraulic suspension system comprising:
the oil tank is used for storing hydraulic medium;
the hydraulic pump is used for pumping the hydraulic medium stored in the oil tank to an oil way of the hydraulic suspension system;
a suspension cylinder including a cylinder body connected to the hydraulic pump to receive a hydraulic medium pumped by the hydraulic pump and a piston rod slidably connected to the cylinder body;
an accumulator for regulating the pressure of the hydraulic medium pumped by the hydraulic pump received by the cylinder;
wherein, the cylinder body is internally provided with an accommodating space for accommodating the hydraulic medium pumped by the hydraulic pump; one end of the piston rod is inserted into the accommodating space to partition the accommodating space into a rodless cavity and a rod-provided cavity; the other end of the piston rod penetrates out of the accommodating space from the rod cavity; the rodless cavity is connected to the hydraulic pump; the energy accumulator is communicated to the rodless cavity;
the method is characterized in that:
the accumulator includes:
a housing having a pneumatic chamber and a hydraulic chamber in communication with the rodless chamber;
the interlayer is movably arranged between the air pressure cavity and the hydraulic cavity so as to bias the interlayer and compress the volume of the air pressure cavity when the hydraulic medium in the rodless cavity flows into the hydraulic cavity;
the hydraulic suspension system further includes:
the air storage tank is provided with at least one first-type expansion cavity communicated with the air pressure cavity;
the switch valve is provided with a first expansion interface communicated with the first expansion cavity and an expansion input interface communicated with the air pressure cavity, so that the first expansion cavity is communicated with the air pressure cavity when the first expansion interface is communicated with the expansion input interface.
2. The hydraulic suspension system of claim 1 wherein:
the air storage tank further has:
the second type of expansion cavity is communicated with the rodless cavity through the switch valve;
the on-off valve further has:
and the second expansion interface is connected to the second expansion cavity so that the second expansion cavity is communicated with the air pressure cavity when the second expansion interface is communicated with the expansion input interface.
3. The hydraulic suspension system of claim 2 wherein:
the switching valve is configured as a solenoid valve; the valve core of the electromagnetic valve is provided with at least a communication position relative to the valve block of the electromagnetic valve, so that the capacity expansion input interface is simultaneously communicated with the first capacity expansion cavity and the second capacity expansion cavity when the valve core of the electromagnetic valve is positioned at the communication position.
4. A hydraulic suspension system according to claim 3, wherein:
the ratio of the volume of the first expansion cavity to the volume of the second expansion cavity is in the range of 0.8 to 1.2.
5. The hydraulic suspension system of claim 2 wherein:
the hydraulic suspension system further includes:
the barometer is used for detecting whether the air pressure in the first expansion cavity and/or the second expansion cavity is at a preset value or not;
the gas supply device is used for inputting gas into the first expansion cavity and/or the second expansion cavity so as to enable the gas pressure in the first expansion cavity and/or the second expansion cavity to reach the preset value;
wherein the air supply device is connected to the first expansion cavity and/or the second expansion cavity through an air supply pipeline; the barometer is connected to the air supply line.
6. The hydraulic suspension system according to any one of claims 1 to 5 wherein:
the hydraulic suspension system further includes:
a master control solenoid valve having a hydraulic input port connected to the hydraulic pump and a hydraulic output port connected to the rodless chamber to allow the hydraulic pump to communicate to the rodless chamber through the hydraulic input port and the hydraulic output port when triggered;
the safety valve is provided with a pressure relief input port connected with the rodless cavity and a pressure relief output port connected with the oil tank, so that the rodless cavity is communicated to the oil tank through the pressure relief input port and the pressure relief output port when triggered.
7. The hydraulic suspension system of claim 6 wherein:
the safety valve is configured as an electromagnetic reverse-proportion overflow valve.
8. The hydraulic suspension system of claim 7 wherein:
the hydraulic suspension system further includes:
the controller is electrically connected to the master control electromagnetic valve and the electromagnetic inverse proportion overflow valve to control whether the master control electromagnetic valve and the electromagnetic inverse proportion overflow valve are triggered or not when working;
the displacement sensor is used for sending out a displacement signal containing the position information of the piston rod relative to the cylinder body;
wherein the displacement sensor is fixedly connected to the suspension cylinder; the controller is electrically connected with the displacement sensor so that the controller receives the displacement signal to work.
9. The hydraulic suspension system of claim 8 wherein: .
A pressure sensor connected to the rodless chamber to detect a magnitude of hydraulic pressure within the rodless chamber;
wherein, pressure sensor with the controller constitutes power connection.
10. The hydraulic suspension system of claim 6 wherein:
the hydraulic suspension system further includes:
the electromagnetic proportional pressure reducing valve is provided with a pressure reducing input port connected with the hydraulic input interface and a pressure reducing output port connected with the rodless cavity, so that the hydraulic input interface is communicated with the rodless cavity through the pressure reducing input port and the pressure reducing output port when triggered.
11. An industrial and mining vehicle, characterized in that:
a hydraulic suspension system comprising any one of claims 1 to 10.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311243283.8A CN117325597A (en) | 2023-09-25 | 2023-09-25 | Industrial and mining vehicle and hydraulic suspension system thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311243283.8A CN117325597A (en) | 2023-09-25 | 2023-09-25 | Industrial and mining vehicle and hydraulic suspension system thereof |
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| Publication Number | Publication Date |
|---|---|
| CN117325597A true CN117325597A (en) | 2024-01-02 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311243283.8A Pending CN117325597A (en) | 2023-09-25 | 2023-09-25 | Industrial and mining vehicle and hydraulic suspension system thereof |
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| Country | Link |
|---|---|
| CN (1) | CN117325597A (en) |
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2023
- 2023-09-25 CN CN202311243283.8A patent/CN117325597A/en active Pending
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