Construction machine and hydraulic suspension system thereof

Abstract

The application discloses an engineering machine and a hydraulic suspension system thereof, and belongs to the field of engineering machines. The hydraulic suspension system comprises an oil tank, a hydraulic pump, a first suspension oil cylinder, a second suspension oil cylinder and a reversing valve. The hydraulic pump is used for pumping hydraulic medium in the oil tank. The first suspension oil cylinder comprises a first cylinder body and a first piston rod. The second suspension oil cylinder comprises a second cylinder body and a second piston rod. The reversing valve has a first output port and a first input port. The first cylinder body has a first inner cavity. One end of the first piston rod is inserted into the first inner cavity to divide the first inner cavity into a first rod cavity and a first rodless cavity. The second suspension oil cylinder has a second inner cavity. One end of the second piston rod is inserted into the second inner cavity to divide the second inner cavity into a second rod cavity and a second rodless cavity. The first rodless cavity and the second rodless cavity are both communicated to the first output port. The application has the beneficial effects that the engineering machine and the hydraulic suspension system thereof are suitable for use in a complex terrain environment.

Description

Technical Field

[0001] The present application relates to the technical field of engineering machinery, and in particular to an engineering machinery and a hydraulic suspension system thereof. Background Art

[0002] Engineering machinery such as scrapers and rock drills are generally rarely equipped with hydraulic suspension systems. In addition, since the parts where the frame and the axle are connected (such as the swing frame) are located and have complex and dense components, and there is little available space, it is not appropriate to excessively increase the size of the swing frame and the frame to enhance the strength of both. This can easily lead to the entire frame and the parts connected to the axle (such as the swing frame) being broken due to insufficient load-bearing capacity when the engineering machinery is moving or working and is impacted by external loads.

[0003] In the existing oil-gas suspension hydraulic system, for example, when a single suspension cylinder is installed in the middle of the vehicle frame, when the vehicle is moving or working, if one side of the vehicle body is bumped due to uneven ground, resulting in an impact on one side of the frame, the suspension cylinder does not react sensitively to the external impact and often cannot buffer the external impact in time, and the frame still bears a large external impact.

[0004] Another example is a solution in which a suspension cylinder is provided on each side of the frame, and the two suspension cylinders work independently of each other. However, the external impacts brought about by the complex outdoor environment such as mining and exploration in which engineering machinery is working are frequent and severe, and the inherent load generated by its own weight is generated. Moreover, engineering machinery is generally a large vehicle, and the load brought about by its own weight on the suspension cylinder is greater than that of a family car. When the external impact on one side of the frame of the engineering machinery is too large, the suspension cylinder on that side and the accumulator connected to the suspension cylinder are often unable to bear the high-intensity impact, resulting in failure of the suspension system. In order to improve the load-bearing capacity of the suspension system, the size specifications of the accumulator and the suspension cylinder are increased, but this is not applicable to engineering machinery due to the limited installation space on the frame. Due to the complexity of the frame structure of the engineering machinery itself and the working environment in which it is located, the current hydraulic suspension system is difficult to adapt to use on engineering machinery.

[0005] In related art, Chinese patent publication CN216518915U discloses a load-adjustable hydraulic suspension system and construction machinery. This system utilizes an accumulator connected to dual suspension cylinders to improve the suspension system's sensitivity to external impacts. However, the related art does not address the technical issue of hydraulic suspension systems being unsuitable for use on construction machinery due to its inherent structure and the complex working environment in which they operate. Summary of the Invention

[0006] The content of this application is used to briefly introduce concepts that will be described in detail in the detailed description section below. The content of this application is not intended to identify key features or essential features of the technical solution for which protection is sought, nor is it intended to limit the scope of the technical solution for which protection is sought.

[0007] In order to solve the technical problems mentioned in the above background technology section, some embodiments of the present application propose an engineering machine and a hydraulic suspension system thereof.

[0008] As a first aspect of the present application, some embodiments of the present application provide a hydraulic suspension system, including: an oil tank, a hydraulic pump, a first suspension cylinder, a second suspension cylinder and a reversing valve; wherein the oil tank is used to store the hydraulic medium of the hydraulic suspension system; the hydraulic pump is used to pump the hydraulic medium in the oil tank; the first suspension cylinder includes a first cylinder body connected to the hydraulic pump and a first piston rod slidingly connected to the first cylinder body; the second suspension cylinder includes a second cylinder body connected to the hydraulic pump and a second piston rod slidingly connected to the second cylinder body; the reversing valve has a first output port and a first input port connected to the hydraulic pump to connect the first output port to the hydraulic pump when the first input port and the first output port are connected.

[0009] The first cylinder body has a first inner cavity for accommodating hydraulic medium; one end of the first piston rod is inserted into the first inner cavity to separate the first inner cavity into a first rod chamber and a first rodless chamber; the second suspension oil cylinder has a second inner cavity for accommodating hydraulic medium; one end of the second piston rod is inserted into the second inner cavity to separate the second inner cavity into a second rod chamber and a second rodless chamber; the first rodless chamber and the second rodless chamber are both connected to the first output port so that the hydraulic pump can pump hydraulic medium into the first rodless chamber and the second rodless chamber when the first output port is connected to the hydraulic pump.

[0010] Furthermore, the hydraulic suspension system further includes: an energy storage device; wherein the energy storage device is used to store at least part of the hydraulic medium pumped by the hydraulic pump to the first output port.

[0011] Furthermore, the energy storage device includes: a first accumulator and a second accumulator; wherein, the first accumulator is connected to the first rodless chamber; the second accumulator is connected to the second rodless chamber; the hydraulic suspension system also includes: a pressure relief valve; wherein, the pressure relief valve is connected between the oil tank and the first accumulator or / and the oil tank and the second accumulator to connect the first accumulator and / or the second accumulator to the oil tank when the pressure relief valve is triggered.

[0012] Furthermore, a pressure relief valve is connected between the first accumulator and the second accumulator to connect the first accumulator and the second accumulator to the oil tank when the pressure relief valve is triggered; the hydraulic suspension system also includes: a shuttle valve; wherein the shuttle valve has a first discharge port connected to the first accumulator, a second discharge port connected to the second accumulator, and a total discharge port connected to the pressure relief valve to connect the first accumulator and the second accumulator to the pressure relief valve when the shuttle valve is triggered.

[0013] Furthermore, the hydraulic suspension system also includes: a first one-way valve, a second one-way valve, a first safety valve and a second safety valve; wherein the first one-way valve is arranged between the first rodless chamber and the first output port to connect the first output port with the first rodless chamber when triggered; the second one-way valve is arranged between the second rodless chamber and the first output port to connect the first output port with the second rodless chamber when triggered; the first safety valve has a first pressure relief output port and a first pressure relief input port connected to the first rodless chamber to connect the first rodless chamber with the first pressure relief output port when triggered; the second safety valve has a second pressure relief output port and a second pressure relief input port connected to the second rodless chamber to connect the second rodless chamber with the second pressure relief output port when triggered.

[0014] The first pressure relief output port is connected to the second one-way valve so that the first rodless chamber can be connected to the second rodless chamber through the first safety valve and the second one-way valve when the first safety valve is triggered; the second pressure relief output port is connected to the first one-way valve so that the second rodless chamber can be connected to the first rodless chamber through the second safety valve and the first one-way valve when the second safety valve is triggered.

[0015] Furthermore, the first safety valve has: a first type of spring and a first control port; wherein the first type of spring provides a first type of elastic force to the valve core of the first safety valve so that the valve core of the first safety valve tends to slide to a position where the first safety valve is not triggered; the first control port is connected to the first rodless chamber and the valve core of the first safety valve so that when the hydraulic pressure of the hydraulic medium in the first rodless chamber exceeds a first threshold value, the valve core of the first safety valve slides and the first safety valve is triggered.

[0016] Furthermore, the second safety valve has: a second type of spring and a second control port; wherein the second type of spring provides a second type of elastic force to the valve core of the second safety valve so that the valve core of the second safety valve tends to slide to a position where the second safety valve is not triggered; the second control port is connected to the second rodless chamber and the valve core of the second safety valve so that when the hydraulic pressure of the hydraulic medium in the second rodless chamber exceeds a second threshold value, the valve core of the second safety valve slides and the second safety valve is triggered.

[0017] Furthermore, the ratio of the first threshold to the second threshold ranges from 0.9 to 1.1.

[0018] Furthermore, the reversing valve includes an electromagnetic reversing valve; the hydraulic suspension system also includes: a control terminal, a first type of sensor and a second type of sensor; wherein the control terminal is used to send a control signal to the electromagnetic reversing valve to control the connection between the first input port and the first output port; the first type of sensor is arranged in the first oil cylinder to send a first type of position signal containing position information of the first piston rod relative to the first cylinder body to the control terminal; the second type of sensor is arranged in the second oil cylinder to send a second type of position signal containing position information of the second piston rod relative to the second cylinder body to the control terminal; the control terminal responds to the first type of position signal and / or the second type of position signal, and sends a control signal to the control terminal.

[0019] As a second aspect of the present application, some embodiments of the present application provide an engineering machinery comprising the aforementioned hydraulic suspension system.

[0020] The beneficial effect of the present application is to provide an engineering machine and a hydraulic suspension system thereof suitable for use in complex terrain environments.

[0021] More specifically, some embodiments of the present application may have the following specific beneficial effects:

[0022] The hydraulic suspension system of the present application uses a reversing valve to charge the first and second suspension cylinders. This allows the dual suspension cylinders to enhance the hydraulic suspension system's sensitivity to external impacts when installed on construction machinery. Furthermore, the first and second cylinders are interconnected, enabling either suspension cylinder to engage the other when subjected to an impact. This enhances the hydraulic suspension system's load-bearing capacity without increasing the size of the individual suspension cylinders, making the hydraulic suspension system suitable for installation on construction machinery and use in complex outdoor construction sites.

[0023] By setting the first safety valve and the second safety valve, the first suspension cylinder or the second suspension cylinder is connected to each other after it is subjected to load so that the hydraulic pressure of the hydraulic medium in the first rodless chamber or the second rodless chamber is higher than a preset threshold value to avoid failure of a suspension cylinder subjected to a higher load. When the hydraulic pressure of the hydraulic medium in each suspension cylinder is lower than the threshold value, each suspension cylinder works independently to reduce the possibility of frequent vibration of the construction machinery due to frequent sliding of the piston rods corresponding to the two suspension cylinders after the suspension system is installed on the construction machinery, so as to further enable the hydraulic suspension system to be adapted for use in outdoor construction sites with complex environments. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The drawings constituting a part of this application are used to provide a further understanding of this application and make other features, purposes and advantages of this application more apparent. The drawings and descriptions of the exemplary embodiments of this application are used to explain this application and do not constitute an improper limitation on this application.

[0025] In addition, throughout the drawings, the same or similar reference numerals represent the same or similar elements. It should be understood that the drawings are schematic and that the elements and components are not necessarily drawn to scale.

[0026] In the attached figure:

[0027] Figure 1 is an overall schematic diagram of a hydraulic suspension system according to an embodiment of the present application;

[0028] Figure 2 yes Figure 1 The structural diagram of the first safety valve in the hydraulic suspension system shown in FIG.

[0029] Figure 3 yes Figure 1 A schematic structural diagram of the second safety valve in the hydraulic suspension system shown;

[0030] Figure 4 yes Figure 1 The structural diagram of the reversing valve in the hydraulic suspension system shown in FIG.

[0031] Figure 5 yes Figure 1 A partial enlarged view of point A in the middle.

[0032] The meaning of the reference numerals in the accompanying drawings:

[0033] 100. Hydraulic suspension system;

[0034] 101. Fuel tank;

[0035] 102. Hydraulic pump;

[0036] 103, first suspension cylinder; 103a, first cylinder body; 103b, first piston rod; 103c, first inner cavity; 103d, first rod cavity; 103e, first rodless cavity;

[0037] 104, second suspension cylinder; 104a, second cylinder body; 104b, second piston rod; 104c, second inner cavity; 104d, second rod cavity; 104e, second rodless cavity;

[0038] 105, reversing valve; 105a, first output port; 105b, first input port; 105c, second output port; 105d, first reversing electromagnet; 105e, second reversing electromagnet; 105f, first reversing spring; 105g, second reversing spring; 105h, second input port;

[0039] 106. First one-way valve;

[0040] 107. Second one-way valve;

[0041] 108, first safety valve; 108a, first pressure relief output port; 108b, first pressure relief input port; 108c, first type spring; 108d, first control port; 108e, first drain control port;

[0042] 109, second safety valve; 109a, second pressure relief output port; 109b, second pressure relief input port; 109c, second type spring; 109d, second control port; 109e, second drain control port;

[0043] 110, control terminal;

[0044] 111, first type sensor; le

[0045] 112, second type sensor;

[0046] 113, energy storage device; 113a, first accumulator; 113b, second accumulator;

[0047] 114, pressure relief valve;

[0048] 115, shuttle valve; 115a, first drain port; 115b, second drain port; 115c, total drain port;

[0049] 200, hydraulic actuator. DETAILED DESCRIPTION

[0050] Embodiments of the present disclosure will be described in more detail with reference to the drawings. Although certain embodiments of the present disclosure are shown in the drawings, it is understood that the present disclosure can be embodied in various forms and should not be interpreted as being limited to the embodiments set forth herein. Rather, these embodiments are provided so that the present disclosure can be more thoroughly and completely understood. It should be understood that the drawings of the present disclosure are only for illustrative purposes and are not intended to limit the scope of protection of the present disclosure.

[0051] It should also be noted that, for ease of description, only parts related to the present application are shown in the drawings. The embodiments in the present disclosure and the features in the embodiments can be combined with each other without conflict.

[0052] It should be noted that the modification of "one" or "multiple" mentioned in the present disclosure is illustrative rather than limiting, and those skilled in the art should understand that, unless otherwise explicitly indicated in the context, it should be understood as "one or more".

[0053] The present disclosure will be described in detail below with reference to the drawings and in conjunction with embodiments.

[0054] Reference Figures 1 to 5The hydraulic suspension system 100 provided by the application comprises an oil tank 101, a hydraulic pump 102, a first suspension oil cylinder 103, a second suspension oil cylinder 104 and a reversing valve 105.

[0055] The oil tank 101 is used for storing the hydraulic medium of the hydraulic suspension system 100, and the hydraulic medium is generally hydraulic oil. The hydraulic pump 102 is used for pumping the hydraulic medium in the oil tank 101. The hydraulic pump 102 is connected to a power source such as an electric motor or an engine, and thus works under the drive of the power source to pump the hydraulic medium stored in the oil tank 101. The first suspension oil cylinder 103 comprises a first cylinder body 103a connected to the hydraulic pump 102 and a first piston rod 103b in sliding connection with the first cylinder body 103a. The second suspension oil cylinder 104 comprises a second cylinder body 104a connected to the hydraulic pump 102 and a second piston rod 104b in sliding connection with the second cylinder body 104a. The reversing valve 105 has a first output port 105a and a first input port 105b connected to the hydraulic pump 102, so that the first output port 105a is in communication with the hydraulic pump 102 when the first input port 105b and the first output port 105a are in communication.

[0056] The hydraulic pump 102 is controlled by the reversing valve 105 to be in communication with the first suspension oil cylinder 103 and the second suspension oil cylinder 104. When the hydraulic pump 102 is in communication with the first output port 105a, the hydraulic pump 102 works to pump the hydraulic medium to the first suspension oil cylinder 103 and the second suspension oil cylinder 104, so as to charge the two hydraulic suspension oil cylinders. After the charging is completed, the first input port 105b and the first output port 105a are disconnected by controlling the reversing valve 105, so that each suspension oil cylinder can be kept in the charging state. Thus, after the hydraulic suspension system 100 is assembled on the engineering machinery, the suspension oil cylinder can buffer the impact of external load by the change of the internal hydraulic medium pressure when it bears the impact of external load, so as to make the engineering machinery run stably.

[0057] Specifically, the first cylinder body 103a has a first inner cavity 103c containing the hydraulic medium. The first piston rod 103b is inserted into the first inner cavity 103c to divide the first inner cavity 103c into a first rod cavity 103d and a first rodless cavity 103e. The second suspension oil cylinder 104 has a second inner cavity 104c containing the hydraulic medium. The second piston rod 104b is inserted into the second inner cavity 104c to divide the second inner cavity 104c into a second rod cavity 104d and a second rodless cavity 104e. The first rodless cavity 103e and the second rodless cavity 104e are in communication with the first output port 105a, so that the hydraulic pump 102 pumps the hydraulic medium into the first rodless cavity 103e and the second rodless cavity 104e when the first output port 105a is in communication with the hydraulic pump 102.

[0058] When the hydraulic suspension system 100 is assembled on the engineering machine, the two suspension oil cylinders are respectively installed on both sides of the vehicle body, and the piston rods of the two suspension oil cylinders are installed on one of the vehicle axle and the vehicle frame, and the corresponding cylinder bodies are installed on the other one of the vehicle axle and the vehicle frame. When the suspension oil cylinders are subjected to external load impact, the piston rods have a tendency to slide towards the corresponding rodless cavity end close to the corresponding cylinder body. When the first output port 105a and the first input port 105b are disconnected, the first rodless cavity 103e and the second rodless cavity 104e can be communicated.

[0059] In this way, when one of the suspension oil cylinders bears a larger load, hydraulic medium can be delivered to the rodless cavity of the other suspension oil cylinder, so as to reduce the hydraulic pressure in the rodless cavity of the suspension oil cylinder bearing a larger load. Through the linkage of the two suspension oil cylinders, the load bearing capacity of the hydraulic suspension system 100 is enhanced.

[0060] Especially, for example, when the engineering machine travels on uneven ground and one side of the vehicle body contacts a ground protrusion, the horizontal position of the side of the vehicle frame is pulled up, the hydraulic pressure in the rodless cavity of the suspension oil cylinder installed on the side is increased, and hydraulic medium can be delivered to the rodless cavity of the suspension oil cylinder installed on the other side of the vehicle body, so that the piston rod of the suspension oil cylinder on the other side of the vehicle body can slide to enable the side of the vehicle frame to also be lifted up, and the components such as the cab installed on the vehicle frame can be stabilized.

[0061] Optionally, the first suspension oil cylinder 103 and the second suspension oil cylinder 104 can be single-acting oil cylinders or double-acting oil cylinders. However, when the double-acting oil cylinders are selected, the first rod cavity 103d and the second rod cavity 104d are communicated to the oil tank 101.

[0062] It should be noted that although the above scheme can achieve the purpose of buffering impact, when the engineering machine travels in a rugged environment, the vehicle body on both sides receives frequent external impact. If the first suspension oil cylinder 103 and the second suspension oil cylinder 104 always remain in a linkage state, the cab installed on the vehicle frame will be frequently lifted and lowered to stabilize the balance, which will cause the driver to feel uncomfortable.

[0063] To solve the above problems, specifically referring to Figures 1 to 3 , the hydraulic suspension system 100 further comprises a first one-way valve 106, a second one-way valve 107, a first safety valve 108, and a second safety valve 109.

[0064] The first one-way valve 106 is arranged between the first rodless cavity 103e and the first output port 105a to communicate the first output port 105a and the first rodless cavity 103e when triggered. The second one-way valve 107 is arranged between the second rodless cavity 104e and the first output port 105a to communicate the first output port 105a and the second rodless cavity 104e when triggered.

[0065] More specifically, when the first input port 105b and the first output port 105a are connected, causing the hydraulic pump 102 to pump hydraulic medium to the first output port 105a, the first and second one-way valves 106 and 107 are hydraulically driven and triggered, thereby causing the hydraulic medium to flow into the first and second rodless chambers 103e and 104e, thereby filling the two suspension cylinders. Alternatively, when the second suspension cylinder 104 is subjected to an external impact, causing the hydraulic pressure in the second rodless chamber 104e to increase, the first and second one-way valves 106 and 107 are hydraulically driven and triggered, and when the first suspension cylinder 103 is subjected to an external impact, causing the hydraulic pressure in the first rodless chamber 103e to increase, the second and second one-way valves 107 and 107 are hydraulically driven and triggered, thereby achieving linkage between the first and second suspension cylinders 103 and 104.

[0066] The first safety valve 108 has a first pressure relief output port 108a and a first pressure relief input port 108b communicating with the first rodless chamber 103e so that the first rodless chamber 103e is connected to the first pressure relief output port 108a when triggered. The second safety valve 109 has a second pressure relief output port 109a and a second pressure relief input port 109b communicating with the second rodless chamber 104e so that the second rodless chamber 104e is connected to the second pressure relief output port 109a when triggered.

[0067] Specifically, the first pressure relief output port 108a is connected to the second one-way valve 107 so that when the first safety valve 108 is triggered, the first rodless chamber 103e is communicated to the second rodless chamber 104e through the first safety valve 108 and the second one-way valve 107. The second pressure relief output port 109a is connected to the first one-way valve 106 so that when the second safety valve 109 is triggered, the second rodless chamber 104e is communicated to the first rodless chamber 103e through the second safety valve 109 and the first one-way valve 106.

[0068] In this way, after the two suspension cylinders are filled with fluid, the two suspension cylinders will only be linked when the first safety valve 108 or the second safety valve 109 is triggered, which can reduce the frequency of height adjustment of the engineering machinery's cab and reduce the driver's discomfort.

[0069] More specifically, refer to Figure 1 and Figure 2The first safety valve 108 includes a first-type spring 108c and a first control port 108d. The first-type spring 108c provides a first-type elastic force to the valve core of the first safety valve 108, causing the valve core of the first safety valve 108 to slide to a position where the first safety valve 108 is not triggered. The first control port 108d connects to the first rodless chamber 103e and the valve core of the first safety valve 108. This allows the valve core of the first safety valve 108 to slide and trigger the first safety valve 108 when the hydraulic pressure of the hydraulic medium in the first rodless chamber 103e exceeds a first threshold. Specifically, when the first suspension cylinder 103 is impacted by an external force, causing the hydraulic pressure of the hydraulic medium in the first rodless chamber 103e to rise and exceed the first threshold, the first safety valve 108 is triggered.

[0070] Accordingly, reference Figure 1 and Figure 3 The second safety valve 109 has a second spring 109c and a second control port 109d. The second spring 109c provides a second elastic force to the valve core of the second safety valve 109, causing it to slide to a position where the second safety valve 109 is not triggered. The second control port 109d connects to the second rodless chamber 104e and the valve core of the second safety valve 109. This allows the valve core of the second safety valve 109 to slide and trigger the second safety valve 109 when the hydraulic pressure of the hydraulic medium in the second rodless chamber 104e exceeds a second threshold. Specifically, the first safety valve 108 is triggered only when the hydraulic pressure of the hydraulic medium in the second rodless chamber 104e rises and exceeds the first threshold due to an external impact on the second suspension cylinder 104.

[0071] With this solution, if the impact on the construction machinery during travel and operation is insufficient to trigger the first safety valve 108 or the second safety valve 109, the two suspension cylinders can operate independently to provide shock absorption for the vehicle body. However, if the impact is excessive enough to trigger the first safety valve 108 or the second safety valve 109, the two suspension cylinders will then be linked. This linkage is adaptively adjusted based on the impact, eliminating the need for manual intervention. This makes it more suitable for cushioning construction machinery operating in complex environments.

[0072] Specifically, for different types and specifications of construction machinery, the inherent loads imposed on the vehicle frame and axle due to their own weight are different, and therefore the corresponding first and second threshold values ​​should also be selected differently. If the values ​​of the first and second thresholds are too small, it is easy to cause the first suspension cylinder 103 and the second suspension cylinder 104 to frequently interact with each other, affecting the driving experience. If the values ​​of the first and second thresholds are too large, the first and second suspension cylinders 103 and 104 will not be able to interact with each other. Therefore, the specific values ​​of the first and second thresholds should be adaptively adjusted according to different construction machinery so that the above-mentioned hydraulic suspension system 100 can more stably perform its buffering function.

[0073] Optionally, the ratio of the first threshold to the second threshold ranges from 0.9 to 1.1. More specifically, when the ratio of the first threshold to the second threshold is 1, that is, when the first threshold is equal to the second threshold, the triggering conditions of the first safety valve 108 and the second safety valve 109 are the same, making it less likely that both suspension cylinders will fail due to excessive load impact.

[0074] Specifically, the reversing valve 105 includes an electromagnetic reversing valve 105. That is, the reversing valve 105 is an electromagnetic reversing valve 105. The hydraulic suspension system 100 also includes: a control terminal 110, a first type of sensor 111, and a second type of sensor 112. Among them, the first type of sensor 111 is arranged on the first oil cylinder to send a first type of position signal containing position information of the first piston rod 103b relative to the first cylinder body 103a to the control terminal 110. The second type of sensor 112 is arranged on the second oil cylinder to send a second type of position signal containing position information of the second piston rod 104b relative to the second cylinder body 104a to the control terminal 110. The first type of sensor 111 and the second type of sensor 112 can be displacement sensors, distance measuring sensors, etc. For example, the TemposonicsR series displacement sensor products produced by MTS can be used, which monitor the position of the corresponding piston rod relative to the corresponding cylinder body and send corresponding position signals to the control terminal 110. The control terminal 110 may be a PLC, a control chip, etc., which responds to the first type position signal and / or the second type position signal and sends a control signal to the control terminal 110. The control terminal 110 is used to send a control signal to the electromagnetic reversing valve 105 to control the communication between the first input port 105b and the first output port 105a.

[0075] During filling, the control terminal 110 connects the first input port 105b and the second input port 105h of the solenoid reversing valve 105, allowing the hydraulic pump 102 to pump hydraulic medium into the two suspension cylinders. The positions of the two piston rods relative to their respective cylinder bodies are detected by the first and second sensors 111 and 112. When filling is complete, the piston rods slide to a preset position relative to the cylinder bodies. The position signals sent by the two sensors to the control terminal 110 cause the control terminal 110 to control the first input port 105b and the first output port 105a of the solenoid reversing valve 105, completing the filling of the first and second suspension cylinders 103 and 104. The preset positions vary for different types and models of construction machinery and can be adjusted based on actual operational needs, for example, by adjusting the mounting positions of the two sensors on the corresponding suspension cylinders. This allows the hydraulic suspension system 100 to be adapted to different types and specifications of construction machinery.

[0076] Specifically, refer to Figure 1 and Figure 4 The solenoid reversing valve 105 further includes a second output port 105c. Second output port 105c is connected to the oil tank 101. When the first and second output ports 105a, 105c are connected, the first output port 105a is connected to the oil tank 101, allowing the hydraulic medium within the first and second rodless chambers 103e, 104e to flow back into the oil tank 101. Consequently, after the corresponding piston rod slides downward and away from the corresponding rodless chamber due to buffering external impact, the hydraulic medium within the rodless chamber flows back into the oil tank 101, returning the piston rod to a predetermined position.

[0077] More specifically, the electromagnetic reversing valve 105 comprises a first reversing electromagnet 105d, a second reversing electromagnet 105e, a first reversing spring 105f, and a second reversing spring 105g. The control terminal 110 controls the power on and off of the first and second reversing electromagnets 105d, 105e. The first and second reversing electromagnets 105d, 105e provide a magnetic force that moves the valve core of the electromagnetic reversing valve 105. The first reversing spring 105f provides an elastic force to the valve core of the electromagnetic reversing valve 105, cooperating with the first reversing electromagnet 105d to connect or disconnect the first input port 105b with the first output port 105a. The second reversing spring 105g provides an elastic force to the valve core of the electromagnetic reversing valve 105, cooperating with the second reversing electromagnet 105e to connect or disconnect the first output port 105a with the second output port 105c.

[0078] Using the above solution, during filling, the first reversing solenoid 105d is energized to move the valve core of the reversing solenoid valve, connecting the first input port 105b with the first output port 105a, allowing the hydraulic pump 102 to fill the two suspension cylinders. When filling is complete, the second reversing solenoid 105e is de-energized, disconnecting the first input port 105b from the second output port 105c. To drain the two suspension cylinders, the second reversing solenoid 105e is energized, connecting the first output port 105a with the second output port 105c. After the first safety valve 108 or the second safety valve 109 is triggered, the first rodless chamber 103e or the second rodless chamber 104e is connected to the oil tank 101, draining the corresponding suspension cylinders.

[0079] Optionally, the first safety valve 108 further has a first discharge control port 108e. The second safety valve 109 further has a second discharge control port 109e. Correspondingly, the solenoid reversing valve 105 further has a second input port 105h. The first discharge control port 108e is connected to the valve core of the first safety valve 108. The second discharge control port 109e is connected to the valve core of the second safety valve 109. The second input port 105h is connected to the first discharge control port 108e and the second discharge control port 109e. When the second input port 105h is connected to the first input port 105b, the hydraulic pump 102 can pump hydraulic medium to the first discharge control port 108e and the second discharge control port 109e, thereby triggering the first safety valve 108 and the second safety valve 109.

[0080] In this way, when the second reversing solenoid 105e is energized, the valve core of the first safety valve 108 and the valve core of the second safety valve 109 slide under the push of the hydraulic medium pumped by the hydraulic pump 102, that is, the first safety valve 108 and the second safety valve 109 are triggered, and the hydraulic medium in the first rodless chamber 103e and the second rodless chamber 104e is able to flow back to the oil tank 101, thereby realizing the discharge of the two suspension cylinders.

[0081] By adopting the above scheme, the first sensor, the second sensor, the control terminal 110, the first reversing electromagnet 105d and the second reversing electromagnet 105e are coordinated to realize the filling and discharging control of the first suspension cylinder 103 and the second suspension cylinder 104, so that the two suspension cylinders can automatically reset after the corresponding piston rods move due to external impact.

[0082] Specifically, the hydraulic suspension system 100 further includes an energy storage device 113. The energy storage device 113 is used to store at least a portion of the hydraulic medium pumped by the hydraulic pump 102 to the first output port 105a. This allows the hydraulic medium to be delivered to the first and second suspension cylinders 103, 104 after the hydraulic pump 102 stops pumping the hydraulic medium. More specifically, the energy storage device 113 includes a first accumulator 113a and a second accumulator 113b. The first accumulator 113a is connected to the first rodless chamber 103e, and the second accumulator 113b is connected to the second rodless chamber 104e. The first accumulator 113a is connected between the first one-way valve 106 and the first rodless chamber 103e. When the first suspension cylinder 103 is subjected to an external impact, it can push part of the hydraulic medium in the first rodless chamber 103e into the first accumulator 113a. After the external impact is weakened, the hydraulic medium can be replenished into the first rodless chamber 103e through the first accumulator 113a. Correspondingly, the second accumulator 113b is connected between the second one-way valve 107 and the second rodless chamber 104e.

[0083] By adopting the above scheme, within the load range of the two accumulators, that is, when the hydraulic pressure of the hydraulic medium in the first rodless chamber 103e is lower than the first threshold, or when the hydraulic pressure of the hydraulic medium in the second rodless chamber 104e is lower than the second threshold, the corresponding piston rod can be reset after being subjected to external impact through the two accumulators.

[0084] To facilitate maintenance of the hydraulic suspension system 100, the hydraulic suspension system 100 further includes a pressure relief valve 114. The pressure relief valve 114 is connected between the oil tank 101 and the first accumulator 113a and / or the second accumulator 113b. When the pressure relief valve 114 is triggered, the first accumulator 113a and / or the second accumulator 113b are connected to the oil tank 101. This allows the hydraulic medium within the first accumulator 113a, the first suspension cylinder 103, the second accumulator 113b, and the second suspension cylinder 104 to flow back to the oil tank 101 during maintenance, thereby reducing maintenance risks. A pressure relief valve 114 can be provided between the first accumulator 113a and the oil tank 101, and between the second accumulator 113b and the oil tank 101, respectively, to relieve pressure from both accumulators.

[0085] To further facilitate maintenance, in a preferred solution, a pressure relief valve 114 is connected between the first accumulator 113a and the second accumulator 113b so that when the pressure relief valve 114 is triggered, the first accumulator 113a and the second accumulator 113b are connected to the oil tank 101, that is, the first accumulator 113a and the second accumulator 113b are connected to the oil tank 101 through the same pressure relief valve 114, so that the pressure of the two accumulators is relieved by controlling the pressure relief valve 114.

[0086] At the same time, the hydraulic suspension system 100 further includes a shuttle valve 115. Figure 5 The shuttle valve 115 has a first drain port 115 a communicating with the first accumulator 113 a, a second drain port 115 b communicating with the second accumulator 113 b, and a total drain port 115 c communicating with the pressure relief valve 114, so that the first accumulator 113 a and the second accumulator 113 b can be connected to the pressure relief valve 114 when the shuttle valve 115 is triggered.

[0087] In this way, the pressure relief valve 114 is provided to facilitate maintenance, and the shuttle valve 115 is provided to allow the two accumulators to be spaced apart during normal use, thereby preventing the first suspension cylinder 103 and the second suspension cylinder 104 from being connected to each other through the first accumulator 113a and the second accumulator 113b during normal use.

[0088] Specifically, the pressure relief valve 114 can be a solenoid valve or a manual valve. To facilitate maintenance when the engineering machinery is stopped, the pressure relief valve 114 is preferably a manual valve.

[0089] Specifically, a constant-pressure variable displacement pump can be used as the hydraulic pump 102. This constant-pressure variable displacement pump can adaptively adjust the flow rate of the hydraulic medium flowing to the first input port 105b, as well as parameters such as the hydraulic pressure, to ensure stable operation of the first suspension cylinder 103. Constant-pressure variable displacement pumps are commercially available, and their structure and principles are not further described here.

[0090] Some embodiments of the present application further provide an engineering machine, which is integrated with the aforementioned hydraulic suspension system 100, so that the engineering machine can be buffered when subjected to external load impact, thereby reducing the possibility of damage and fracture of the frame and axle.

[0091] It should be noted that when the hydraulic suspension system 100 is integrated into the engineering machinery, the hydraulic pump 102 of the hydraulic suspension system 100 can also be connected to hydraulic actuators 200 such as hydraulic cylinders and hydraulic motors on the engineering machinery to pump hydraulic medium to various hydraulic actuators 200 on the engineering machinery, thereby driving the corresponding hydraulic actuators to work.

[0092] It should be noted that the aforementioned engineering machinery may be equipment such as scrapers, rock drilling rigs, hydraulic down-the-hole drills, etc. These equipment should be regarded as examples of engineering machinery, and engineering machinery does not include only these equipment.

[0093] The above description is only an illustration of some preferred embodiments of the present disclosure and the technical principles used. Those skilled in the art should understand that the scope of the invention involved in the embodiments of the present disclosure is not limited to the technical solutions formed by the specific combination of the above-mentioned technical features, but should also cover other technical solutions formed by any combination of the above-mentioned technical features or their equivalent features without departing from the above-mentioned inventive concept. For example, the above-mentioned features are replaced with (but not limited to) technical features with similar functions disclosed in the embodiments of the present disclosure.

Claims

1. A hydraulic suspension system comprising: an oil tank for storing hydraulic medium of the hydraulic suspension system; a hydraulic pump, configured to pump the hydraulic medium in the oil tank; Its characteristics are: The hydraulic suspension system further comprises: a first suspension oil cylinder comprising a first cylinder body connected to the hydraulic pump and a first piston rod slidably connected to the first cylinder body; a second suspension oil cylinder comprising a second cylinder body connected to the hydraulic pump and a second piston rod slidably connected to the second cylinder body; a reversing valve having a first output port and a first input port connected to the hydraulic pump so as to connect the first output port to the hydraulic pump when the first input port and the first output port are in communication; Wherein, the first cylinder body has a first inner cavity for accommodating the hydraulic medium; one end of the first piston rod is inserted into the first inner cavity to divide the first inner cavity into a first rod chamber and a first rodless chamber; the second suspension oil cylinder has a second inner cavity for accommodating the hydraulic medium; one end of the second piston rod is inserted into the second inner cavity to divide the second inner cavity into a second rod chamber and a second rodless chamber; the first rodless chamber and the second rodless chamber are both connected to the first output port so that the hydraulic pump pumps the hydraulic medium into the first rodless chamber and the second rodless chamber when the first output port is connected to the hydraulic pump; The hydraulic suspension system further comprises: a first one-way valve disposed between the first rodless chamber and the first output port to connect the first output port with the first rodless chamber when triggered; a second one-way valve disposed between the second rodless cavity and the first output port to communicate the first output port with the second rodless cavity when triggered; a first safety valve having a first pressure relief output port and a first pressure relief input port communicating with the first rodless chamber so as to connect the first rodless chamber with the first pressure relief output port when triggered; a second safety valve having a second pressure relief output port and a second pressure relief input port communicating with the second rodless chamber so as to connect the second rodless chamber with the second pressure relief output port when triggered; wherein the first pressure relief output port is connected to the second one-way valve so that when the first safety valve is triggered, the first rodless chamber is communicated to the second rodless chamber through the first safety valve and the second one-way valve; and the second pressure relief output port is connected to the first one-way valve so that when the second safety valve is triggered, the second rodless chamber is communicated to the first rodless chamber through the second safety valve and the first one-way valve; The first safety valve has a first control port connected to the first rodless chamber and the valve core of the first safety valve, so that when the hydraulic pressure of the hydraulic medium in the first rodless chamber exceeds a first threshold, the valve core of the first safety valve slides to trigger the first safety valve; The second relief valve has a second control port connected to the second rodless chamber and the valve core of the second relief valve so that the valve core of the second relief valve slides and the second relief valve is triggered when the hydraulic pressure of the hydraulic medium in the second rodless chamber exceeds a second threshold.

2. The hydraulic suspension system according to claim 1, characterized in that: The hydraulic suspension system further comprises: An energy storage device is used to store at least part of the hydraulic medium pumped by the hydraulic pump to the first output port.

3. The hydraulic suspension system according to claim 2, characterized in that: The energy storage device comprises: a first accumulator in communication with the first rodless chamber; a second accumulator in communication with the second rodless chamber; The hydraulic suspension system further comprises: A pressure relief valve is connected between the oil tank and the first accumulator or / and between the oil tank and the second accumulator to connect the first accumulator or / and the second accumulator to the oil tank when the pressure relief valve is triggered.

4. The hydraulic suspension system according to claim 3, characterized in that: The pressure relief valve is connected between the first accumulator and the second accumulator to connect the first accumulator and the second accumulator to the oil tank when the pressure relief valve is triggered; The hydraulic suspension system further comprises: A shuttle valve has a first drain port communicating with the first accumulator, a second drain port communicating with the second accumulator, and a total drain port communicating with the pressure relief valve so as to connect the first accumulator and the second accumulator to the pressure relief valve when the shuttle valve is triggered.

5. The hydraulic suspension system according to claim 1, characterized in that: The first safety valve further has a first type of spring, which provides a first type of elastic force to the valve core of the first safety valve so that the valve core of the first safety valve tends to slide to a position where the first safety valve is not triggered.

6. The hydraulic suspension system according to claim 1, characterized in that: The second safety valve further has a second type of spring, which provides a second type of elastic force to the valve core of the second safety valve so that the valve core of the second safety valve tends to slide to a position where the second safety valve is not triggered.

7. The hydraulic suspension system according to claim 6, characterized in that: The ratio of the first threshold to the second threshold ranges from 0.9 to 1.

1.

8. The hydraulic suspension system according to claim 1, characterized in that: The reversing valve includes an electromagnetic reversing valve; The hydraulic suspension system further comprises: a control terminal, configured to send a control signal to the electromagnetic reversing valve to control the communication between the first input port and the first output port; a first type of sensor, disposed on the first suspension cylinder, for sending a first type of position signal containing position information of the first piston rod relative to the first cylinder body to the control terminal; a second type of sensor, disposed on the second suspension cylinder, for sending a second type of position signal containing position information of the second piston rod relative to the second cylinder body to the control terminal; The control terminal responds to the first type of position signal and / or the second type of position signal and sends the control signal to the control terminal.

9. An engineering machine, characterized in that: Comprising the hydraulic suspension system according to any one of claims 1 to 8.

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