CN217926572U - Hydraulic control system and hydraulic lifting device - Google Patents

Abstract

The hydraulic control system and the hydraulic lifting device of the utility model comprise a pressure relay and an explosion-proof valve; the pressure relay oil port is connected to a pressure measuring point of the hydraulic control system to monitor whether the pressure measuring point of the hydraulic control system is in pressure loss or not, and a pressure loss signal is automatically sent out when the pressure measuring point of the hydraulic control system is in pressure loss; the explosion-proof valve is connected in series with the hydraulic cylinder oil delivery port, monitors whether the hydraulic cylinder is in pressure loss or not and automatically handles when the hydraulic cylinder is in pressure loss. The utility model discloses can solve the not enough problem of current decompression anomaly monitoring technology monitoring result timeliness reliability.

Description

Hydraulic control system and hydraulic lifting device

Technical Field

The present disclosure relates to hydraulic control systems and hydraulic lifting devices, and particularly to a hydraulic control system and a hydraulic lifting device for vertical material conveying or vertical material transfer.

Background

The hydraulic control system is widely applied to the fields of industrial production and logistics, so that automatic heavy-load or medium-load operation is realized. The hydraulic lifting device based on the hydraulic control system is also widely applied to the fields of industrial production and logistics, so that automatic vertical material conveying or vertical transfer operation is realized.

For a hydraulic control system and a hydraulic lifting device, a hydraulic loop is easy to have the phenomenon that the oil supply pressure or the oil return pressure of a hydraulic execution module is seriously low, namely the hydraulic loop loses pressure and is abnormal, so that the hydraulic loop cannot drive the hydraulic execution module to normally move.

In the prior art, a pressure relay or an explosion-proof valve can be adopted for monitoring the pressure loss abnormity of the hydraulic circuit. However, the pressure relay or the explosion-proof valve in the prior art often only adopts one of the pressure relays or the explosion-proof valves, only partial pressure loss abnormity can be monitored, the pressure loss abnormity occurring in the actual operation of the hydraulic control system or the hydraulic lifting device is difficult to be monitored timely and accurately, the hydraulic circuit is easy to be monitored to be free of pressure loss or still normal when the pressure loss abnormity occurs in the hydraulic circuit, the problem of insufficient reliability of the timeliness of the monitoring result exists, the pressure loss abnormity of the hydraulic circuit is not easy to be monitored and dealt with timely, and the safety, the usability and the intelligent level of the hydraulic control system are not easy to improve.

Disclosure of Invention

Some embodiments of the present disclosure provide a hydraulic control system and a hydraulic lifting device, which can solve the problem of insufficient timeliness and reliability of a monitoring result of an existing pressure loss anomaly monitoring technology, so as to improve the safety, usability and intelligent level of the hydraulic control system and the hydraulic lifting device.

In one aspect of the present disclosure, a hydraulic control system is provided, including a hydraulic control module and a hydraulic execution module; the hydraulic control module comprises a hydraulic pump station, a hydraulic control assembly and a pressure loss monitoring assembly; the hydraulic execution module comprises a hydraulic cylinder; the hydraulic control assembly comprises an electromagnetic valve group; the pressure loss monitoring assembly comprises a pressure relay and an explosion-proof valve; the pressure relay oil port is connected to a pressure measuring point of the hydraulic control system to monitor whether the pressure measuring point of the hydraulic control system is in pressure loss or not, and a pressure loss signal is automatically sent out when the pressure measuring point of the hydraulic control system is in pressure loss; the explosion-proof valve is connected in series with the oil conveying port of the hydraulic cylinder, monitors whether the hydraulic cylinder is in decompression state or not and automatically handles when the hydraulic cylinder is in decompression state.

In some embodiments, the set pressure threshold of the pressure relay is not lower than the action pressure value of the pressure relay in the simulated pressure loss state.

In some embodiments, the hydraulic pump station comprises a hydraulic oil tank, a motor and a gear pump; the motor drives the impeller of the gear pump to rotate, so that the hydraulic oil in the hydraulic oil tank has enough pressure and is output to the hydraulic control assembly to drive the hydraulic cylinder to move.

In some embodiments, the pressure relay is connected in parallel to the output of the hydraulic control assembly and monitors the output of the hydraulic control assembly for a loss of pressure.

In some embodiments, the pressure relay oil measurement port is communicated with the three-way joint and is connected in parallel with the control assembly oil outlet pipe through the three-way joint, and the pressure relay oil measurement port is arranged at the output end of the hydraulic control assembly.

In some embodiments, the hydraulic control system gradually increases the set pressure threshold of the pressure relay from a zero position until the pressure relay acts and automatically sends out a pressure loss signal in a simulated pressure loss state, and the set pressure threshold when the pressure relay acts and sends out the signal in the simulated pressure loss state is an action pressure value of the pressure relay in the simulated pressure loss state.

In some embodiments, the set pressure threshold value of the pressure relay for automatically sending out the pressure loss signal is not higher than 1.5 times of the action pressure value of the pressure relay in the simulated pressure loss state.

In some embodiments, the output end of the explosion-proof valve is directly communicated with the oil delivery port of the hydraulic cylinder, and the input end of the explosion-proof valve is communicated with the oil inlet pipe of the hydraulic cylinder.

In some embodiments, when the hydraulic oil pressure at the input end of the explosion-proof valve is lower than the hydraulic oil pressure at the output end of the explosion-proof valve and the absolute value of the hydraulic oil pressure difference at the input end and the output end of the explosion-proof valve exceeds the set pressure difference threshold value of the explosion-proof valve, the explosion-proof valve acts and automatically and unidirectionally blocks the oil way.

In some embodiments, the set pressure difference threshold of the explosion-proof valve acting and automatic one-way blocking oil circuit is not lower than the absolute value of the pressure difference of hydraulic oil at the input end and the output end of the explosion-proof valve in the moving process of the hydraulic cylinder and not lower than M times of the absolute value of the pressure difference of the explosion-proof valve acting in a leakage-breaking and pressure-loss state, wherein M is more than or equal to 1 and more than or equal to 0.5.

In some embodiments, the set pressure difference threshold of the explosion-proof valve action and automatic one-way blocking oil circuit is not higher than N times of the absolute value of the pressure difference of the explosion-proof valve action in a leakage-breaking and pressure-loss state, wherein N is more than or equal to 1.

In some embodiments, the hydraulic control system gradually reduces the set pressure difference threshold value of the explosion-proof valve from the highest value in the leakage and pressure loss state until the explosion-proof valve can act and automatically block the oil way in a one-way mode, and the set pressure difference threshold value of the explosion-proof valve at the moment is the action pressure difference absolute value of the explosion-proof valve in the leakage and pressure loss state.

In some embodiments, the hydraulic control assembly further comprises a first check valve; the input end of the first one-way valve is communicated with the oil outlet of the gear pump, the output end of the first one-way valve is directly or indirectly communicated with the hydraulic cylinder, and hydraulic oil output by the gear pump can flow to the hydraulic cylinder through the first one-way valve.

In some embodiments, the hydraulic control assembly further comprises a manual reversing valve; the manual reverse valve forms a branch and is connected with a branch formed by the electromagnetic valve group in parallel; the input end of the manual reversing valve is communicated with an execution module connecting port A of the electromagnetic valve group, and the output end of the manual reversing valve is indirectly communicated with the hydraulic oil tank.

In some embodiments, the hydraulic control assembly further comprises a throttle valve; the choke valve set up in between electromagnetism valves and the hydraulic tank, the input of choke valve with the hydraulic oil backward flow mouth R of electromagnetism valves directly or indirectly communicates, the output of choke valve with the hydraulic tank intercommunication.

In some embodiments, the hydraulic control assembly further comprises a second one-way valve; the input end of the second one-way valve is communicated with the output end of the first one-way valve, and the output end of the second one-way valve is communicated with the hydraulic cylinder; the second one-way valve forms a branch and is connected with the branch formed by the electromagnetic valve group in parallel.

In some embodiments, the hydraulic control assembly further comprises a relief valve; the input end of the overflow valve is respectively communicated with the output end of the first one-way valve and the input end of the second one-way valve through a three-way joint, and the output end of the overflow valve is indirectly communicated with the hydraulic oil tank.

In some embodiments, the voltage loss monitoring assembly further comprises a voltage loss warning device; the pressure loss alarm device is arranged on the hydraulic pump station or beside the control button of each floor.

In one aspect of the present disclosure, a hydraulic lifting device is provided, comprising a hydraulic lifting module and any one of the aforementioned hydraulic control systems.

In some embodiments, the hydraulic lift module comprises a fixed frame, a vehicle, and a vehicle track; the fixed frame comprises a main upright post and an auxiliary upright post; the carrier track fixed connection in fixed frame, the carrier is provided with the carrier pulley, carrier pulley roll connection in the carrier track to make the carrier along the carrier track is at upper and lower direction rectilinear motion.

In some embodiments, the hydraulic lift module further comprises a transmission mechanism; the transmission mechanism comprises a hanging chain, a chain wheel cross beam assembly and a chain wheel track; the hydraulic cylinder drives the carrier to lift through a chain wheel transmission mechanism formed by the hanging chain and the chain wheel.

In some embodiments, the hoist chain comprises a hoist chain first fixed point and a hoist chain second fixed point; the carrier comprises a carrier panel and a carrier guardrail; the first fixed point of the sling chain is fixedly connected with the main beam of the fixed frame, and the second fixed point of the sling chain is fixedly connected with the bottom of the carrier panel.

In some embodiments, the second fixing point of the suspension chain is directly and fixedly connected to the bottom of the carrier panel, and a connecting rod is not arranged between the second fixing point of the suspension chain and the carrier panel.

In some embodiments, the carrier track is a main column of the fixed frame, or/and the sprocket track is an auxiliary column of the fixed frame.

Therefore, according to the embodiment of the disclosure, the hydraulic control system and the hydraulic lifting device have better sensitivity and reliability of no-pressure monitoring, and meanwhile, false no-pressure alarm and delay of no-pressure monitoring can be reduced most effectively, and automatic accurate monitoring and automatic effective disposal of abnormal no-pressure can be realized, so that the safety, usability and intelligent level of the hydraulic control system or the hydraulic lifting device can be improved better.

The advantages and other aspects of the disclosure will become apparent from the following detailed description of the embodiments, taken in conjunction with the accompanying drawings.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate some embodiments of the disclosure and together with the description, serve to explain the principles of the disclosure.

The present disclosure may be understood more clearly from the following detailed description, taken with reference to the accompanying drawings.

Fig. 1 is a schematic diagram showing the general configuration of an embodiment of the hydraulic control system of the present invention.

Fig. 2 is a schematic diagram of the overall structure of an embodiment of the hydraulic lifting device of the present invention.

Fig. 3 is a partial structural schematic diagram of the hydraulic lifting device shown in fig. 2.

Fig. 4 is a schematic diagram of the overall structure of the hydraulic lifting device shown in fig. 2.

Fig. 5 is a schematic cross-sectional structure view of a section B-B of the hydraulic lifting device shown in fig. 4.

FIG. 6 is a schematic diagram of a two-position, three-way solenoid valve of the hydraulic control system of FIG. 1.

Fig. 7 is a schematic diagram showing the overall configuration of an embodiment of the hydraulic control system according to the present invention.

Fig. 8 is a schematic diagram showing the overall configuration of an embodiment of the hydraulic control system according to the present invention.

It should be understood that the dimensions of the various parts shown in the figures are not drawn to scale. Further, the same or similar reference numerals denote the same or similar components.

Included in the drawings are:

a hydraulic control system 100; a ground surface 200; a hydraulic lift device 300; a floor 400;

a hydraulic control module 10;

a hydraulic pump station 11; a hydraulic oil tank 111; a motor 112; a gear pump 113; a filter device 114;

a hydraulic control assembly 12; a solenoid valve group 121; a first check valve 122; a second check valve 123; a throttle valve 124; an overflow valve 125; a manual reversing valve 126;

a voltage loss monitoring component 13; a pressure relay 131; a no-voltage warning device 132; an explosion-proof valve 133;

the hydraulic auxiliaries 14; a three-way joint 141; a control assembly flowline 142;

a hydraulic execution module 20;

a hydraulic cylinder 21; a hydraulic cylinder inlet pipe 22;

a hydraulic lifting module 30;

a hoist chain 31; a catenary first fixed point 311; a catenary second fixed point 312;

a sprocket 32; a fixed frame 33;

a carrier 34; a carrier panel 341; a carrier guardrail 342;

a sprocket cross member assembly 35; the sprocket cross member 351; a sprocket mount 352; a sprocket guide pulley 353;

a sprocket track 36; a carrier rail 37.

Detailed Description

Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative and is in no way intended to limit the disclosure, its application, or uses. The present disclosure may be embodied in many different forms and is not limited to the embodiments described herein. These embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art. It should be noted that: the relative arrangement of parts and steps, the composition of materials, numerical expressions and numerical values set forth in these embodiments are to be construed as merely illustrative, and not as limitative, unless specifically stated otherwise.

The use of "first," "second," and similar terms in this disclosure is not intended to indicate any order, quantity, or importance, but rather are used to distinguish one element from another. The word "comprising" or "comprises", and the like, means that the element preceding the word covers the element listed after the word, and does not exclude the possibility that other elements are also covered. "upper", "lower", "left", "right", "front", "rear/end", and the like are used merely to indicate relative positional relationships, and when the absolute position of the object being described is changed, the relative positional relationships may also be changed accordingly.

The use of "input", "output" and similar terms in this disclosure is for convenience only, and is used primarily to distinguish between different components and is not limited to a mere input function or output function, and thus, the "input" may have an output function and the "output" may have an input function.

In the present disclosure, when a specific device is described as being located between a first device and a second device, there may or may not be intervening devices between the specific device and the first device or the second device. When a particular device is described as being coupled to another device, it can be directly coupled to the other device without intervening devices or can be directly coupled to the other device with intervening devices.

All terms (including technical or scientific terms) used in this disclosure have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure belongs, and also have the same (or substantially the same) technical meaning as the actual function or meaning of the technical term in the prior art document, unless otherwise specifically defined. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.

Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate.

The inventors have found that it is difficult for those skilled in the art to accurately monitor, find, or handle various kinds of pressure loss abnormalities in a timely manner because the pressure relay or the explosion-proof valve cannot be selected accurately to monitor the pressure loss, and the pressure relay and the explosion-proof valve cannot be set appropriately at their respective pressure measurement points and set thresholds (the pressure value of the hydraulic oil causing the operation of the pressure relay or the explosion-proof valve, the set threshold of the pressure relay being a set pressure threshold described below, and the set threshold of the explosion-proof valve being a set differential pressure threshold described below).

Through system analysis and research, the inventor makes technical progress in the aspects of understanding of the pressure loss abnormity, selection of a pressure loss monitoring tool, setting of a pressure measuring point, setting of a threshold value and the like compared with the prior art.

First, recognizing understanding aspects, the present disclosure provides the following technical content: the hydraulic control system and the hydraulic lifting device are easy to have various pressure loss abnormalities and mainly comprise two types, namely load loss and oil circuit breakage, wherein the former type causes the oil return pressure of a hydraulic loop to a hydraulic execution module to be sharply reduced due to the fact that a load is clamped or acted by other acting force during traveling, and the latter type causes the hydraulic oil pressure in the hydraulic loop and a hydraulic cylinder to be sharply reduced due to the fact that an oil pipe is broken or a joint is leaked, and the two pressure loss phenomena can cause the hydraulic oil pressure to be sharply reduced, so that various dangerous accidents are easy to occur. Before the present disclosure, it was difficult for those skilled in the art to systematically and comprehensively recognize and understand various pressure loss anomalies and their causes, and thus it was difficult to correctly select monitoring tools and methods for pressure loss anomalies, and it was difficult to effectively solve the problems of timely and reliable monitoring and timely and correct disposal of pressure loss anomalies.

Secondly, in the aspect of selecting a pressure loss monitoring tool, the following technical scheme is provided in the disclosure: aiming at the voltage loss abnormity caused by load loss, a pressure relay is adopted for voltage loss monitoring, so that a control device or a control circuit can obtain a voltage loss signal quickly, and the quick response and disposal of the whole hydraulic lifting device are facilitated; aiming at the pressure loss abnormity caused by oil circuit leakage, the explosion-proof valve is adopted for pressure loss monitoring and disposal, which is beneficial to rapidly and accurately monitoring the oil circuit leakage and rapidly disposing the local oil circuit leakage. Before the present disclosure, a person in the art often monitors only one type of voltage loss abnormality, there is a possibility of selecting a monitoring tool and a monitoring method by mistake, and moreover, the two types of voltage loss abnormality monitoring requirements cannot be met at the same time, so that the problems of timeliness and reliability of voltage loss abnormality monitoring are difficult to be solved effectively.

Thirdly, in the aspect of setting pressure measuring points, the present disclosure provides the following technical solutions: for a pressure relay, a pressure measuring point is arranged at the output end of a hydraulic control assembly (mainly comprising various hydraulic valves, joints for connecting the hydraulic valves, oil pipes and the like), or is arranged at the front end pipe orifice of an oil outlet pipe of the control assembly; to the explosion-proof valve, the pressure measuring point is arranged at the hydraulic cylinder oil port, namely, the output end of the explosion-proof valve is directly communicated with the hydraulic cylinder oil delivery port, and the input end of the explosion-proof valve is communicated with the hydraulic cylinder oil inlet pipe. Before the present disclosure, it was difficult for those skilled in the art to find a correct pressure measurement point, and it was impossible to accurately monitor various kinds of pressure loss abnormalities in time by a pressure relay or an explosion-proof valve, and it was easy to monitor that the hydraulic circuit was not or still normal when the pressure loss abnormality occurred in the hydraulic circuit.

Fourthly, in the aspect of setting the threshold value, the present disclosure provides the following technical solutions: setting a pressure threshold value of a pressure relay not lower than an action pressure value of the pressure relay in a simulated voltage loss state, wherein the simulated voltage loss state is an artificial voltage loss state of a use site; and for the explosion-proof valve, setting a pressure difference threshold value not lower than the absolute value of the pressure difference of hydraulic oil at the input end and the output end of the explosion-proof valve in the moving process of the hydraulic cylinder and not lower than M times of the absolute value of the action pressure difference of the explosion-proof valve in a leakage-breaking and pressure-loss state, wherein M is more than or equal to 1 and more than or equal to 0.5. Before the disclosure, a set threshold is usually set at will by an operator according to experience or feeling, and a corresponding optimal set threshold cannot be reasonably set according to the actual situation of a hydraulic control system or a hydraulic lifting device on site, so the set threshold is often higher or lower, which causes adverse consequences that either no pressure loss is frequently mistaken as abnormal pressure loss or abnormal pressure loss is frequently missed as no pressure loss, and the like, so that a pressure relay or an explosion-proof valve cannot timely and accurately monitor various abnormal pressure loss, easily monitor that the hydraulic circuit is not or still normal when abnormal pressure loss occurs in the hydraulic circuit, or frequently mistaken pressure loss is not detected as abnormal pressure loss, and has the problem of unreliable monitoring results when the monitoring results are not timely.

In order to solve the problem that the monitoring result of the hydraulic circuit pressure loss abnormality is not timely and reliable enough, and timely handle or control the pressure loss abnormality, so as to improve the safety, usability and intelligent level of a hydraulic control system or a hydraulic lifting device, as shown in fig. 1, a hydraulic control system 100 of one embodiment of the present disclosure includes a hydraulic control module 10 and a hydraulic execution module 20; the hydraulic control module 10 comprises a hydraulic pump station 11, a hydraulic control assembly 12 and a pressure loss monitoring assembly 13; the hydraulic execution module 20 comprises a hydraulic cylinder 21; the hydraulic control assembly 12 comprises a solenoid valve group 121; the pressure loss monitoring assembly 13 comprises a pressure relay 131 and an explosion-proof valve 133; an oil measuring port of the pressure relay 131 is connected to a pressure measuring point of the hydraulic control system 100 to monitor whether the pressure measuring point of the hydraulic control system 100 is in pressure loss or not, and a pressure loss signal is automatically sent out when the pressure measuring point of the hydraulic control system 100 is in pressure loss; the explosion-proof valve 133 is connected in series with the oil delivery port of the hydraulic cylinder 21, monitors whether the hydraulic cylinder 21 is under pressure loss, and automatically handles the pressure loss when the hydraulic cylinder 21 is under pressure loss.

Because hydraulic control system 100 is provided with pressure relay 131 and explosion-proof valve 133 simultaneously, can monitor two kinds of decompression of load losing load and oil circuit hourglass simultaneously, therefore decompression monitoring's reliability is higher, can not appear only monitoring a decompression and the not enough problem of decompression monitoring result reliability that leads to, also can deal with two kinds of decompressions more safely more intelligent more timely simultaneously. Moreover, because the explosion-proof valve 133 is connected in series to the oil delivery port of the hydraulic cylinder 21, the hydraulic control system 100 is more reasonable in the way of pressure loss monitoring, so that the reliability and timeliness of pressure loss monitoring can be better improved, and the beneficial effects thereof will be further explained below.

In some embodiments, the hydraulic pumping station 11 comprises a hydraulic oil tank 111, a motor 112 and a gear pump 113. The gear pump 113 is directly connected with the hydraulic oil tank 111 or indirectly connected through an oil pipe, and the motor 112 is connected with the gear pump 113; the inside hydraulic oil that holds of hydraulic tank 111 has the right amount of hydraulic oil confession the gear pump 113 extraction and pressure boost, simultaneously, hydraulic oil tank 111 can retrieve hydraulic oil. The motor 112 drives the impeller of the gear pump 113 to rotate, so that the hydraulic oil in the hydraulic oil tank 111 has sufficient pressure and is output to the hydraulic control assembly 12, and then the hydraulic execution module 20 is driven to move.

In some embodiments, the hydraulic pump station 11 further comprises a filter device 114.

In some embodiments, the filtering device 114 is disposed between the hydraulic oil tank 111 and the gear pump 113. After impurities in the hydraulic oil tank 111 are filtered by the filter device 114, the hydraulic oil enters the gear pump 113.

In other embodiments, the output of the gear pump 113 is provided with a filtering device 114. Gear pump 113's input is followed hydraulic tank 111 extracts hydraulic oil (gear pump 113 with can set up between the hydraulic tank 111 filter equipment 114 is in order further to filter impurity), the hydraulic oil output after 113's output will pressurize extremely filter equipment 114, after filter equipment 114 filters impurity, clear hydraulic oil gets into hydraulic control subassembly 12. This embodiment filters out new contaminants (e.g., debris) generated during high speed rotation of the gear pump 113 impeller, thereby most effectively ensuring that no or sufficiently low contaminants are present in the hydraulic control assembly 12.

In some embodiments, the hydraulic control assembly 12 may change the direction of the flow of hydraulic oil to change or control the direction of movement of the piston rod of the hydraulic cylinder 21.

In some embodiments, the hydraulic control assembly 12 effects a change in hydraulic oil flow direction through the solenoid valve block 121.

In some embodiments, as shown in fig. 6, the solenoid valve set 121 is a two-position three-way solenoid valve, and includes a hydraulic oil input port P, a hydraulic oil return port R, and an actuator module connection port a. The working position 1 when the electromagnetic valve group 121 is powered off is a one-way channel in which the hydraulic oil input port P points to the execution module connection port a, hydraulic oil can only flow from the hydraulic oil input port P to the execution module connection port a, and cannot flow from the execution module connection port a to the hydraulic oil input port P, at this time, the gear pump 113 outputs pressurized hydraulic oil to the hydraulic oil input port P, and the pressurized hydraulic oil enters the hydraulic execution module 20 through the execution module connection port a, so that a piston rod of the hydraulic cylinder 21 extends out, and the hydraulic cylinder 21 is driven to move forward; the working position 2 when the electromagnetic valve group 121 is powered on is a one-way channel of the execution module connecting port a pointing to the hydraulic oil return port R, at this time, hydraulic oil can only flow back to the hydraulic oil tank 111 from the execution module connecting port a through the hydraulic oil return port R, so that the piston rod of the hydraulic cylinder 21 retracts, and the hydraulic cylinder 21 is driven to move reversely.

In some embodiments, to simplify the structure of the solenoid valve assembly 121, reduce the cost, and facilitate maintenance, repair, and replacement, as shown in fig. 7, the hydraulic control assembly 12 further includes a first check valve 122, and the solenoid valve assembly 121 is a two-position two-way solenoid valve. The input end of the first check valve 122 is communicated with the oil outlet of the gear pump 113, the output end of the first check valve 122 is communicated with the hydraulic cylinder 21, the hydraulic oil output by the gear pump 113 flows to the output end of the first check valve 122 through the input end of the first check valve 122 and then flows to the hydraulic cylinder 21, and cannot flow back to the input end of the first check valve 122 from the output end of the first check valve 122, at this time, the gear pump 113 outputs the pressurized hydraulic oil to the hydraulic execution module 20 through the first check valve 122, so that the piston rod of the hydraulic cylinder 21 extends out, and the hydraulic cylinder 21 is driven to move in the forward direction. In some embodiments, the solenoid valve set 121, which is a direct-acting two-position two-way solenoid valve, includes only a hydraulic oil return port R and an execution module connection port a, where the working position 1 when the solenoid valve set 121 is powered off is a two-way cut-off channel, or a one-way channel from the hydraulic oil return port R to the execution module connection port a (from the execution module connection port a to the hydraulic oil return port R is cut off); the working position 2 when the electromagnetic valve group 121 is powered on is a one-way channel from the execution module connector A to the hydraulic oil return port R, and hydraulic oil can flow back to the hydraulic oil tank 111 from the execution module connector A through the hydraulic oil return port R, so that the piston rod of the hydraulic cylinder 21 retracts to drive the hydraulic cylinder 21 to move reversely.

To simplify the hydraulic circuit, in some embodiments, the output end of the first check valve 122 and the actuator module connection port a of the solenoid valve set 121 communicate with the hydraulic actuator module 20 through a three-way joint.

In some embodiments, to control the rate of reverse movement of the hydraulic cylinder 21, the hydraulic control assembly 12 further includes a throttle valve 124. The throttle valve 124 is arranged between the electromagnetic valve group 121 and the hydraulic oil tank 111, the input end of the throttle valve 124 is directly or indirectly communicated with the hydraulic oil return port R of the electromagnetic valve group 121, and the output end of the throttle valve 124 is communicated with the hydraulic oil tank 111, so that hydraulic oil flows back to the hydraulic oil tank 111 after the flow of the hydraulic oil is regulated by the throttle valve 124 from the execution module connecting port A, and the speed regulation of the reverse movement of the hydraulic cylinder 21 is realized.

In some embodiments, to increase ease of operation, or to implement a manual reversing function for the hydraulic cylinder 21 when the hydraulic cylinder 21 cannot be reversed electrically, the hydraulic control assembly 12 further includes a manual reversing valve 126, as shown in FIG. 1. The manual reversing valve 126 forms a branch and is connected in parallel with the branch formed by the solenoid valve assembly 121. In some embodiments, the branch formed by the solenoid valve assembly 121 may be a branch formed by connecting the solenoid valve assembly 121 and the throttle valve 124 in series, or a branch formed by the solenoid valve assembly 121 alone.

In some embodiments, as shown in fig. 1, an input end of the manual reversing valve 126 is communicated with the execution module connection port a of the solenoid valve group 121 through a three-way joint, and an output end of the manual reversing valve 126 is communicated with the hydraulic oil return port R of the solenoid valve group 121 or the output end of the throttle valve 124 through a three-way joint so as to be communicated with the hydraulic oil tank 111. In some embodiments, the throttle valve 124 is replaced by a speed regulating valve, which has both the flow rate regulating function and the pressure regulating function of the throttle valve 124, and can automatically compensate the influence of load change, so that the pressure difference between the input end and the output end of the throttle valve 124 is a constant value, and further the influence of load change on the flow rate is eliminated, so that the reverse motion of the hydraulic cylinder 21 is smoother, and the reverse motion of load change can be more adapted.

In some embodiments, as shown in FIG. 1, the hydraulic control assembly 12 further includes a second check valve 123. The input end of the second check valve 123 is communicated with the output end of the first check valve 122, and the output end of the second check valve 123 is communicated with the hydraulic cylinder 21. The second check valve 123 forms a branch, and is connected in parallel with the branch formed by the solenoid valve set 121, and also connected in parallel with the branch formed by the manual reverse valve 126.

In some embodiments, as shown in fig. 1, to prevent accidents or hazards caused by too high a pressure of hydraulic oil in the hydraulic control assembly 12, the hydraulic control assembly 12 further includes a relief valve 125. In order to save cost, reduce the number of overflow valves 125 and three-way joints and the installation workload, and improve the system reliability, the input end of the overflow valve 125 is respectively communicated with the output end of the first check valve 122 and the input end of the second check valve 123 through three-way joints, and the output end of the overflow valve 125 is communicated with the output end of the manual reversing valve 126 and the output end of the throttle valve 124 through three-way joints (when the throttle valve 124 is not provided, the output end of the overflow valve 125 is communicated with the hydraulic oil return port R of the solenoid valve group 121) and is further communicated with the hydraulic oil tank 111. When the hydraulic oil pressure at the input end of the relief valve 125 exceeds a set safety value, the relief valve 125 discharges the hydraulic oil to the hydraulic oil tank 111, thereby reducing the hydraulic oil pressure at the input end of the relief valve 125.

In some embodiments, as shown in fig. 1, an input end of the second check valve 123 is respectively communicated with an output end of the first check valve 122 and an input end of the relief valve 125 through a three-way joint. The output end of the second check valve 123 is respectively communicated with the execution module connection port a of the solenoid valve set 121 and the input end of the manual reverse valve 126 through a three-way joint, and further communicated with the hydraulic cylinder 21. The introduction of the second check valve 123 can prevent hydraulic oil from directly flowing back to the overflow valve 125 from the hydraulic cylinder 21, and is also beneficial to simplifying the structure and design, thereby realizing the modular design, cost reduction and reliability improvement of the hydraulic control assembly 12.

In some embodiments, the hydraulic control module 10 further includes a hydraulic accessory 14. The hydraulic accessories 14 include a three-way joint 141 and a control assembly flowline 142.

In some embodiments, the hydraulic implement module 20 also includes a cylinder inlet 22. The rear end pipe orifice of the hydraulic cylinder oil inlet pipe 22 is communicated with the oil delivery port of the hydraulic cylinder 21, and the front end pipe orifice of the hydraulic cylinder oil inlet pipe 22 is communicated with the output end of the hydraulic control assembly 12 or the control assembly oil outlet pipe 142.

The input end of the first check valve 122 can be directly communicated with the oil outlet of the gear pump 113, and can also be indirectly communicated through an oil pipe.

The output of the first check valve 122 communicates with other components of the hydraulic control assembly 12 via the three-way connection 141 (or the like). In this case, the input of the first check valve 122 is the input of the hydraulic control assembly 12.

The output end of the hydraulic control assembly 12 is communicated with the front end pipe orifice of the control assembly oil outlet pipe 142 through the three-way joint 141 (or the like), and hydraulic oil is output to the front end pipe orifice of the control assembly oil outlet pipe 142 through the hydraulic control assembly 12, flows to the rear end pipe orifice of the control assembly oil outlet pipe 142, and is then output to the front end pipe orifice of the hydraulic cylinder oil inlet pipe 22. For convenience, the front end port of the control assembly outlet line 142 is referred to as the output end of the hydraulic control assembly 12.

The output end of the first check valve 122 may be directly connected to the three-way joint 141, the front end of the control assembly outlet pipe 142 may be connected to the three-way joint 141, the solenoid valve block 121 may be connected to the throttle valve 124, and the three-way joint 141 may be connected to other devices, or may be indirectly connected through an oil pipe.

In some embodiments, the output end of the second check valve 123 is connected to the front end of the control module outlet pipe 142 through the three-way joint 141 (or the like), and the rear end of the control module outlet pipe 142 is directly or indirectly connected to the cylinder inlet pipe 22 and thus to the cylinder 21.

In some embodiments, the hydraulic oil has sufficient pressure under the action of the gear pump 113, and then flows through the first check valve 122 and the second check valve 123 in sequence to the control assembly outlet pipe 142, and then enters the hydraulic cylinder 21 through the cylinder inlet pipe 22 to drive the hydraulic cylinder 21 to move forward.

In some embodiments, the set pressure threshold value of the pressure relay 131 automatically sending the no-voltage signal is not lower than the action pressure value of the pressure relay 131 in the simulated no-voltage state, which is an artificial no-voltage state at the use site.

In some embodiments, the pressure relay 131 includes an oil measuring port, a manual knob, an elastic element, and a switch assembly; the manual knob adjusts the set pressure threshold of the pressure relay 131 by adjusting the stress of an elastic element; the oil measuring port is communicated with a pressure measuring point, so that hydraulic oil enters the pressure relay 131 through the pressure measuring point and the oil measuring port; when the pressure of the hydraulic oil at the pressure measuring point is lower than the set pressure threshold, the elastic element drives the switch assembly to act, so that the switch assembly is switched on, and the pressure relay 131 automatically sends out a pressure loss signal.

In some embodiments, the pressure relay 131 is specifically configured as described in patent document CN202110522413.6, and accordingly, the oil measuring port, the manual knob, the elastic element and the switch assembly of the pressure relay 131 refer to "oil port 2", "pressure adjusting knob 3", "pressure spring 303" and "movable contact 9" of the patent document, respectively.

In some embodiments, the pressure relay 131 is specifically configured as described in patent document CN 202121105493.7.

In some embodiments, the simulated pressure loss state and the artificial pressure loss state in the use site refer to a state in which the pressure of the hydraulic control system or the hydraulic lifting device at the pressure measurement point is zero, which is generated by artificial measures in the actual application site of the hydraulic control system or the hydraulic lifting device at the pressure measurement point.

In some embodiments, in a simulated voltage loss state, the set pressure threshold of the pressure relay 131 is gradually adjusted and increased from zero until the pressure relay 131 stops adjusting and increasing when the pressure relay 131 operates and automatically sends a voltage loss signal, and the set pressure threshold of the pressure relay 131 in the simulated voltage loss state at this time is an operation pressure value of the pressure relay in the simulated voltage loss state.

In some embodiments, there may be multiple simulated pressure loss states in the hydraulic control system or the hydraulic lifting device where the pressure measurement point is located, where the simulated pressure loss state with the lowest operation pressure value should be selected, and accordingly, the set pressure threshold is not lower than the operation pressure value of the pressure relay 131 in the simulated pressure loss state with the lowest operation pressure value. As a preferred embodiment, the set pressure threshold is equal to the operating pressure value of the pressure relay 131 in the simulated no-voltage state with the lowest operating pressure value, and at this time, the false alarm and the false alarm can be reduced to the maximum extent, and the no-voltage abnormality can be monitored most timely and accurately.

In addition, the inventor unexpectedly finds that different hydraulic control systems or hydraulic lifting devices have large individual differences due to machining errors, assembly errors, mechanical friction and the like, so that the action pressure values of the pressure relay 131 in the simulated decompression state have large individual differences, therefore, the simulated decompression state is limited to a use site instead of setting a uniform set pressure threshold value before delivery, the individual difference problem can be avoided, each hydraulic control system or hydraulic lifting device can find the optimal set pressure threshold value of the pressure relay 131, and the decompression abnormity can be monitored most timely and accurately.

In order to further improve the timeliness and reliability of the abnormal monitoring of the pressure loss, the pressure measuring point of the pressure relay 131 is arranged at the output end of the hydraulic control assembly, or is arranged at the front end pipe orifice of the oil outlet pipe of the control assembly.

The inventor finds that when the pressure measuring point of the pressure relay 131 is arranged at a certain node in the hydraulic control assembly, and when the pressure loss abnormality occurs at any point from the node of the hydraulic control assembly to the output end of the hydraulic control assembly, the monitoring result of the pressure relay 131 still has no pressure loss, because the pressure between the node of the hydraulic control assembly and the hydraulic pump station is always in a stable oil pressure state; when setting up pressure relay 131's pressure measurement point in hydraulic control assembly's input, when arbitrary node took place the decompression unusual in the control assembly, pressure relay 131's monitoring result still for not having the decompression because this moment often is in the oil pressure steady state between hydraulic control assembly input to the hydraulic power unit. The pressure measuring point of the pressure relay 131 is arranged at the output end of the hydraulic control assembly or at the front end pipe orifice of the oil outlet pipe of the control assembly, and the optimal pressure measuring point is set, so that the occurrence probability of missed report can be reduced to the maximum extent, and the accuracy of monitoring the abnormal pressure loss is improved.

The operating pressure value of the pressure relay 131 in the simulated pressure loss state is specifically described below in conjunction with the hydraulic control system 100 according to an embodiment of the present disclosure.

In some embodiments, the pressure relay 131 is connected in parallel to the output of the hydraulic control assembly 12 and monitors the output of the hydraulic control assembly 12 for a loss of pressure.

In some embodiments, as shown in fig. 1, the pressure relay 131 port communicates with a tee 141 (or the like) and is connected in parallel to the control assembly outlet line 142 via the tee 141 (or the like).

In some embodiments, as shown in fig. 8, the oil measurement port of the pressure relay 131 is disposed at the output end of the hydraulic control assembly 12, so that the oil pressure at the output end of the hydraulic control assembly 12 is directly monitored, the sensitivity and reliability of the pressure loss monitoring are optimal, and the false alarm of the pressure loss can be prevented to the maximum extent.

The set pressure threshold of the pressure relay 131 means that the pressure relay 131 acts and automatically sends out a pressure loss signal when the hydraulic oil pressure of an oil measuring port (i.e. a monitoring point) of the pressure relay 131 is lower than or equal to the set pressure threshold.

In some embodiments, the set pressure threshold of the pressure relay 131 is set or adjusted by a manual knob or adjusting nut.

The simulated no-pressure state refers to a state in which the hydraulic control system 100 artificially sets an external force to counteract the inertia force and the resistance force of the vehicle during the vehicle driving process through the hydraulic cylinder 21 during no-load traveling (the traveling direction is the traveling direction in which the average value of the pressure of the hydraulic oil in the cylinder of the hydraulic cylinder 21 is the lowest) after the field installation and debugging is finished or before the vehicle is put into use in a formal mode, so that the driving force of the hydraulic cylinder 21 is zero (i.e., approaches zero), and the pressure of the hydraulic oil in the cylinder of the hydraulic cylinder 21 is zero (i.e., approaches zero). The approach to zero means that the driving force of the hydraulic cylinder 21 is not higher than one percent of the rated driving force of the hydraulic cylinder 21, or means that the pressure of hydraulic oil in the hydraulic cylinder 21 is not higher than one percent of the rated pressure of hydraulic oil in the hydraulic cylinder 21.

In some embodiments, the driving force of the hydraulic cylinder 21 can be close to zero by manually setting an external force to counteract the inertia force and the resistance force of the vehicle traveling through a baffle, a stop block or a support frame.

The action pressure value refers to that, when the hydraulic control system 100 is in a simulated pressure loss state, the set pressure threshold of the pressure relay 131 is gradually increased from a zero position through a manual knob or an adjusting nut until the pressure relay 131 acts and automatically sends a pressure loss signal, and the set pressure threshold (equal to a hydraulic oil pressure value of a monitoring point of the pressure relay 131) when the pressure relay 131 acts and sends the signal in the simulated pressure loss state is the action pressure value of the pressure relay 131 in the simulated pressure loss state.

In some embodiments, the pressure loss monitoring assembly 13 further includes a burst valve 133.

In some embodiments, the explosion-proof valve 133 is connected in series with the oil delivery port of the hydraulic cylinder 21 and monitors whether the oil delivery port of the hydraulic cylinder 21 is depressurized.

In some embodiments, as shown in fig. 1 or fig. 8, the output end of the explosion-proof valve 133 is directly connected to the hydraulic cylinder 21 oil delivery port or indirectly connected to the hydraulic cylinder 21 oil delivery port through an oil pipe, and the input end of the explosion-proof valve 133 is connected to the hydraulic cylinder oil inlet pipe 22. When the hydraulic oil pressure at the input end of the explosion-proof valve 133 is lower than the hydraulic oil pressure at the output end of the explosion-proof valve 133 and the absolute value of the pressure difference between the hydraulic oil at the input end of the explosion-proof valve 133 and the pressure difference at the output end of the explosion-proof valve 133 exceeds the set pressure difference threshold value (absolute value, the same applies below) of the explosion-proof valve 133, the explosion-proof valve 133 acts and automatically and unidirectionally blocks an oil path, so that the hydraulic oil cannot flow from the oil delivery port of the hydraulic cylinder 21 to the input end of the explosion-proof valve 133 through the output end of the explosion-proof valve 133 and further flows to the oil inlet pipe 22 of the hydraulic cylinder, thereby preventing the hydraulic oil from continuously flowing from the oil delivery port of the hydraulic cylinder 21 to the oil inlet pipe 22 of the hydraulic cylinder during pressure loss, preventing the reverse traveling and possible accidents or losses of the hydraulic cylinder 21, and realizing the automatic monitoring and disposal of the pressure loss of the oil delivery port of the hydraulic cylinder 21.

Because the output end of the explosion-proof valve 133 is directly communicated with the oil delivery port of the hydraulic cylinder 21, and whether the oil delivery port of the hydraulic cylinder 21 loses pressure relative to the oil inlet pipe 22 of the hydraulic cylinder is directly monitored, once the pressure in the cylinder 21 relative to the oil inlet pipe 22 of the hydraulic cylinder is lost, the explosion-proof valve 133 can immediately sense that the pressure in the cylinder 21 relative to the oil inlet pipe 22 of the hydraulic cylinder is lost, almost no delay is caused, the sensitivity and the reliability are optimal, and the pressure loss of the hydraulic cylinder 21 can be monitored timely and accurately to the greatest extent and the automatic processing with the highest speed and the lowest delay can be realized. Particularly, the oil delivery port of the hydraulic cylinder 21 is directly connected with the output end of the explosion-proof valve 133, so that the risk of oil path leakage does not exist, the condition that the hydraulic pressure of the oil delivery port of the hydraulic cylinder 21 is lower than that of the oil inlet pipe 22 of the hydraulic cylinder does not need to be monitored or considered, the explosion-proof valve 133 only needs to automatically block the oil path in a one-way mode, does not need to automatically block the oil path in a two-way mode, the cost is reduced, and the reliability is improved.

The set pressure difference threshold (which is an absolute value of the pressure difference) of the anti-explosion valve 133 means that the anti-explosion valve 133 operates and automatically and unidirectionally blocks the oil path when the absolute value of the hydraulic oil pressure difference at the monitoring point of the anti-explosion valve 133 (i.e., the absolute value of the hydraulic oil pressure difference at the input end and the output end of the anti-explosion valve 133) is higher than or equal to the set pressure difference threshold.

In some embodiments, the set differential pressure threshold of the explosion-proof valve 133 is set or adjusted by a manual knob or adjusting nut.

In some embodiments, the set pressure difference threshold of the anti-explosion valve 133 acting and automatically blocking the oil path in one way is not less than the absolute value of the pressure difference of the hydraulic oil at the input end and the output end of the anti-explosion valve 133 in the forward traveling process of the hydraulic cylinder 21, not less than the absolute value of the pressure difference of the hydraulic oil at the input end and the output end of the anti-explosion valve 133 in the reverse traveling process of the hydraulic cylinder 21, not less than the absolute value of the pressure difference of the hydraulic oil at the input end and the output end of the anti-explosion valve 133 in the manual reverse traveling process of the hydraulic cylinder 21, and not less than M times of the absolute value of the pressure difference of the action of the anti-explosion valve 133 in a leakage and pressure loss state, wherein 1 is not less than M and not less than 0.5.

Considering various influence factors in actual operation, such as abrasion problem, hydraulic oil pressure change and the like, the set pressure difference threshold of the anti-explosion valve 133 acting and automatically blocking the oil way in one way can be higher than the absolute value of the action pressure difference of the anti-explosion valve 133 in a leakage-breaking and pressure-loss state but not higher than N times (N is more than or equal to 1) of the absolute value of the action pressure difference of the anti-explosion valve 133 in the leakage-breaking and pressure-loss state.

The absolute value of the action pressure difference of the explosion-proof valve 133 in the leakage-breaking decompression state is not less than the absolute value of the pressure difference of hydraulic oil at the input end and the output end of the explosion-proof valve 133 in the forward advancing process of the hydraulic cylinder 21, is not less than the absolute value of the pressure difference of hydraulic oil at the input end and the output end of the explosion-proof valve 133 in the reverse advancing process of the hydraulic cylinder 21, and is not less than the absolute value of the pressure difference of hydraulic oil at the input end and the output end of the explosion-proof valve 133 in the manual reverse advancing process of the hydraulic cylinder 21.

Preferably, M is 0.5, 0.6, 0.7, 0.8, 0.9 or 0.95. The N is preferably 1.05, 1.1, 1.15, 1.2, 1.25, 1.3 or 1.5.

The leakage-breaking pressure-loss state refers to that after field installation and debugging of the hydraulic control system 100 are finished or before the hydraulic control system is put into use formally, a three-way joint is arranged between the input end of the explosion-proof valve 133 and the hydraulic cylinder oil inlet pipe 22 and is communicated with a standard test pipe, the input end of the standard test pipe is communicated with the input end of the explosion-proof valve 133 and the hydraulic cylinder oil inlet pipe 22 through the three-way joint, the output end of the standard test pipe is connected with a pluggable plug (the pipe orifice of the standard test pipe can be completely plugged before being pulled out to prevent hydraulic oil from flowing out, and the standard test pipe can quickly leak oil after being pulled out), and the pluggable plug is manually and quickly pulled out (the speed is not lower than 0.2 m/s) in the no-load reverse advancing process of the hydraulic cylinder 21 driving carrier, so that the pressure difference of the hydraulic oil at the input end of the explosion-proof valve 133 is greatly increased, and the hydraulic control system 100 is in the leakage-breaking pressure-loss state of oil leakage of the leakage-way. In a leakage and pressure loss state, the output end of the standard test tube is aligned to a clean oil storage barrel or other containers to recover and reuse hydraulic oil. In a leakage-breaking and pressure-loss state, the pluggable plug can be inserted into the output end of the standard test tube (for example, the pluggable plug is inserted into the standard test tube in a wedge-shaped interference mode or a thread spiral mode) to prevent hydraulic oil from flowing out continuously.

The absolute value of the operating pressure difference refers to that the set pressure difference threshold of the anti-explosion valve 133 is gradually reduced from the highest value by a manual knob or an adjusting nut until the anti-explosion valve 133 can act and automatically and unidirectionally block the oil passage when the pluggable plug is quickly pulled out, and at this time, the set pressure difference threshold of the anti-explosion valve 133 (equal to the absolute value of the pressure difference of hydraulic oil at the input end and the output end of the anti-explosion valve 133 at this time) is the absolute value of the operating pressure difference of the anti-explosion valve 133 in the leakage-breaking pressure-loss state. In order to accurately obtain the absolute value of the action pressure difference, after the pluggable plug is inserted into the output end of the standard test tube each time, the hydraulic control system 100 is operated to make the carrier move forward for a distance L (the distance is not less than the actual distance of the carrier moving backward after the pluggable plug is pulled out), and then move backward for the same distance L in a no-load manner, so that the oil pressure in the hydraulic cylinder 21 is basically the same when the pluggable plug is pulled out each time.

In some embodiments, to simplify the operation and improve the convenience of debugging the device, the aperture of the output end of the standard test tube is smaller than the inner diameter of the hydraulic cylinder oil inlet tube 22, and the cross-sectional area of the circular hole at the output end of the standard test tube is M times of the cross-sectional area of the circular hole at the inner wall of the hydraulic cylinder oil inlet tube 22. At this time, an operator only needs to make the set pressure difference threshold of the anti-explosion valve 133 act and automatically blocking the oil passage in one way equal to the absolute value of the action pressure difference of the anti-explosion valve 133 in a leakage and pressure loss state, that is, when the cross-sectional area of the circular hole at the output end of the standard test tube is M times of the cross-sectional area of the circular hole at the inner wall of the hydraulic cylinder oil inlet tube 22, the set pressure difference threshold of the anti-explosion valve 133 is gradually reduced from the highest value through a manual knob or an adjusting nut until the anti-explosion valve 133 can act and automatically block the oil passage in one way when the pluggable plug is rapidly pulled out, and at this time, the set pressure difference threshold of the anti-explosion valve 133 is the final set pressure difference threshold of the anti-explosion valve 133.

In some embodiments, considering various factors in actual operation, such as wear problems, variation in the running resistance, and the like, the set pressure threshold value of the pressure relay 131 automatically sending the pressure loss signal is not higher than 1.5 times or 1.2 times of the action pressure value of the pressure relay 131 in the simulated pressure loss state. Preferably, the set pressure threshold value of the pressure relay 131 for automatically sending the pressure loss signal is not higher than 1.1 times of the operating pressure value of the pressure relay 131 in the simulated pressure loss state.

As shown in fig. 2, a hydraulic lift apparatus 300 according to an embodiment of the present disclosure includes a hydraulic lift module 30 and any one of the hydraulic control systems 100 described above.

In some embodiments, the hydraulic lift module 30 includes a fixed frame 33, a vehicle 34, and a vehicle rail 37. The carrier rail 37 is fixedly connected to the fixing frame 33, and the carrier 34 is provided with a carrier pulley, which is connected to the carrier rail 37 in a rolling manner, so that the carrier 34 moves linearly in the vertical direction along the carrier rail 37. The fixing frame 33 includes a main column and an auxiliary column.

In some embodiments, the hydraulic lift module 30 further includes a transmission mechanism.

In some embodiments, the drive mechanism includes a catenary 31, a sprocket 32, a sprocket cross-beam assembly 35, and a sprocket track 36. The hydraulic cylinder 21 indirectly drives the carrier 34 to realize the lifting function through a chain wheel transmission mechanism formed by the hanging chain 31 and the chain wheel 32.

In some embodiments, the hoist chain 31 includes a hoist chain first fixed point 311 and a hoist chain second fixed point 312.

In some embodiments, the vehicle 34 includes a vehicle panel 341 and a vehicle guardrail 342. A sliding door is arranged on the front side of the carrier panel 341, so that articles or goods can conveniently enter and exit; a carrier guardrail 342 is arranged on the rear side of the carrier panel 341 to completely close the rear side of the carrier panel 341 so as to prevent the articles or goods from moving out; the left and right sides of the carrier panel 341 are also provided with carrier guardrails 342, respectively, to completely close the left and right sides of the carrier panel 341, respectively, to prevent the removal of the articles or goods.

In some embodiments, the first attachment point 311 of the hoist chain is fixed to the fixed frame 33 and the second attachment point 312 of the hoist chain is fixed to the carrier 34.

In some embodiments, as shown in fig. 2 and 4, in order to save the amount of the suspension chain 31, reduce the length of the suspension chain 31, improve the reliability of the suspension chain 31, and ensure the convenience of operation and the efficiency of article entering and exiting of the hydraulic lifting device 300, the first fixing point 311 of the suspension chain is fixedly connected to the main beam of the fixing frame 33, and the second fixing point 312 of the suspension chain is fixedly connected to the bottom of the carrier panel 341. The vertical position (i.e., the height direction position) of the main beam of the fixed frame 33 depends on the upper and lower limit positions of the vehicle lifting/lowering section, generally near the middle of the fixed frame 33 in the height direction.

In some embodiments, second fixing point 312 of the sling chain is directly fixed to the bottom of carrier panel 341, and no connecting rod is provided between second fixing point 312 of the sling chain and carrier panel 341, so that the space of carrier panel 341 is large enough, but the distance between fixing frame 33 and carrier panel 341 is small.

In some embodiments, a connecting rod is disposed between the second fixing point 312 of the sling chain and the carrier panel 341, one end of the connecting rod is fixedly connected to the bottom of the carrier panel 341, the other end of the connecting rod is fixedly connected to the second fixing point 312 of the sling chain, the length of the connecting rod is adjustable, so that the distance between the second fixing point 312 of the sling chain and the carrier panel 341 is adjustable, and although the distance between the connecting rod and the fixing frame is small, the distance between the carrier 34 and the fixing frame 33 is larger, so as to prevent the carrier 34 and the fixing frame 33 from touching or being jammed.

In some embodiments, as shown in FIG. 5, the sprocket cross member assembly 35 includes a sprocket cross member 351, a sprocket mount 352, and a sprocket guide pulley 353. The sprocket fixing frame 352 is fixedly coupled to the sprocket cross member 351.

In some embodiments, as shown in fig. 3, 4 and 5, the sprocket 32 is rotatably fixedly coupled to the sprocket cross member assembly 35, and in particular, the sprocket 32 is rotatably fixedly coupled to the sprocket mount 352.

In some embodiments, the sprocket cross member assembly 35 comprises two sprocket guide pulleys 353 and a plurality of sprocket fixing brackets 352, and the two sprocket guide pulleys 353 are fixedly connected to two ends of the sprocket cross member 351 respectively, and the plurality of sprocket fixing brackets 352 are located between the two sprocket guide pulleys 353.

In some embodiments, the sprocket cross member assembly 35 includes two sprocket mounts 352, each sprocket mount 352 being located between the two sprocket guide pulleys 353.

In some embodiments, the two sprocket fixing frames 352 are symmetrically arranged on both sides of the hydraulic cylinder 21 along the length direction of the sprocket cross beam 351.

In some embodiments, the sprocket guide pulley 353 is connected to the sprocket rail 36 in a rolling manner, so that the sprocket beam 351 and the sprocket fixing frame 352 move linearly in the vertical direction along the sprocket rail 36, and the moving direction of the sprocket beam 351 and the driving force direction of the hydraulic cylinder 21 are always parallel without deviation or inclination, thereby maintaining the running smoothness and force balance of the sprocket driving mechanism (including the suspension chain 31 and the sprocket 32), and reducing the movement resistance and the fluctuation of the resistance.

In some embodiments, the hydraulic lifting module 30 includes two sets of the sprocket beam assemblies 35 and two sets of the hydraulic cylinders 21, forming two sets of hydraulic lifting units, which are respectively disposed on the left and right sides of the fixed frame 33 (corresponding to the left and right sides of the carrier panel 341), and each set of hydraulic lifting units includes one set of the sprocket beam assemblies 35, one set of the hydraulic cylinders 21, two sprockets 32, and two suspension chains 31. Accordingly, each set of hydraulic lifting units includes two of the sprocket tracks 36, two of the sprocket guide pulleys 353, and two of the sprocket mounts 352.

In some embodiments, as shown in fig. 3 and 4, the carrier rail 37 is a main column of the fixed frame 33 for simplifying the structure and manufacturing process, reducing the cost, reducing the system weight, facilitating transportation and installation, and improving the structural strength and safety. In some embodiments, the fixing frame 33 includes four main columns, each main column is the carrier rail 37, the carrier rail 37 is made of i-steel or U-shaped channel steel, and in this case, the carrier rail 37 is used as the main column of the fixing frame 33, which not only saves materials, but also makes the structure compact, and also unexpectedly increases the strength of the columns of the fixing frame 33 and the structural stability and safety of the fixing frame 33.

Similarly, in some embodiments, as shown in fig. 3 and 4, the sprocket track 36 is an auxiliary pillar of the fixing frame 33, the sprocket track 36 is fixedly connected to the main beam of the fixing frame 33, and the sprocket track 36 is made of an i-steel or U-shaped channel steel, so as to further stabilize the structure and safety of the fixing frame 33, and further reduce the cost and the weight of the system.

In some embodiments, the hydraulic control system 100 further includes a control circuit comprising a PLC logic control.

In some embodiments, the loss of voltage monitoring assembly 13 further includes a loss of voltage warning device 132. When the PLC logic control device receives a voltage loss signal from the pressure relay 131, the voltage loss alarm device 132 automatically alarms to remind an operator of the voltage loss of the hydraulic system.

In some embodiments, the pressure loss warning device 132 is disposed on the hydraulic pump station 11, and when the PLC logic control device receives a pressure loss signal sent by the pressure relay 131, it generates a warning bell or a voice broadcast of the pressure loss to alert an operator that the hydraulic system is in pressure loss. In some embodiments, the hydraulic pump station 11 is fixedly connected to the ground 200.

In some embodiments, the voltage loss alarm device 132 is disposed near the control panel or the control button of each floor 400, and when the PLC logic control device receives the voltage loss signal sent by the pressure relay 131, the PLC logic control device generates a sound such as a warning bell or a voice broadcast of the voltage loss, or sends a warning light or a warning text or a warning symbol to remind an operator of the voltage loss of the hydraulic system. At this time, various alarms of the voltage loss alarm device 132 are easier to warn or inform operators of the voltage loss condition, which is beneficial for the operators to find the voltage loss condition in time, thereby disposing and reducing the loss in time.

The control circuit and its PLC logic control device, electrical signal connection, signal transmission, etc. of the present disclosure all adopt the prior art or the existing product, and the rest is the same as the prior art or the existing product except for a small amount of adaptive local adjustment caused by the foregoing technical solution, and will not be described in detail herein.

When the operator presses the forward travel button or the up button, the solenoid valve block 121 is in the working position 1 state when the power is off, the motor 112 drives the impeller of the gear pump 113 to rotate, so that the hydraulic oil in the hydraulic oil tank 111 has sufficient pressure and is output to the hydraulic control module 12, the hydraulic control module 12 can enable the hydraulic oil to flow to the hydraulic cylinder 21 and then drive the hydraulic cylinder 21 to move forward, at this time, the execution module connection port a to the hydraulic oil return port R channel of the solenoid valve block 121 is in a cut-off state, and the hydraulic oil cannot flow from the execution module connection port a to the hydraulic oil return port R to the hydraulic oil tank 111. When an operator presses a reverse travel button or a down button, the solenoid valve group 121 is in a working position 2 state when power is supplied, a channel from an execution module connection port a of the solenoid valve group 121 to a hydraulic oil return port R is in a conducting state, hydraulic oil can flow back to the hydraulic oil tank 111 from the execution module connection port a through the hydraulic oil return port R, so that a piston rod of the hydraulic cylinder 21 retracts to drive the hydraulic cylinder 21 to move in a reverse direction, at this time, the hydraulic control assembly 12 stops a passage through which hydraulic oil flows to the hydraulic cylinder 21 (as described above, the passage is stopped by a check valve or the stop channel of the solenoid valve group 121), and hydraulic oil cannot flow to the hydraulic cylinder 21 through the hydraulic control assembly 12.

When the pressure relay 131 monitors that the output end of the hydraulic control assembly 12 is in a voltage loss state (the pressure of the hydraulic oil at the output end of the hydraulic control assembly 12 is lower than or equal to the set pressure threshold of the pressure relay 131), the pressure relay 131 acts and automatically sends a voltage loss signal, when the PLC logic control device receives the voltage loss signal sent by the pressure relay 131, the electromagnetic valve group 121 is powered off, the electromagnetic valve group 121 is in a working position 1 state when the power is off, the motor 112 and the hydraulic pump station 11 stop working, an execution module connector a of the electromagnetic valve group 121 is in a cut-off state to a hydraulic oil return port R channel, hydraulic oil cannot flow back to the hydraulic oil tank 111 from the execution module connector a to the hydraulic oil return port R, the hydraulic cylinder 21 is prevented from continuously moving and keeping the current position, so that accidents or losses are avoided, and automatic monitoring and automatic disposal of the voltage loss of the hydraulic control assembly 12 are realized. Meanwhile, the voltage loss alarm device 132 generates an alarm or warning to remind an operator to check and remove the voltage loss fault.

When the decompression fault is relieved, the pressure relay 131 monitors that the output end of the hydraulic control assembly 12 is not decompressed (the hydraulic oil pressure at the output end of the hydraulic control assembly 12 is higher than the set pressure threshold value of the pressure relay 131), the PLC logic control device cannot receive a decompression signal sent by the pressure relay 131, the solenoid valve group 121 is powered on, the solenoid valve group 121 is in a 2-state working position when powered on, hydraulic oil can flow back to the hydraulic oil tank 111 from the execution module connector A to the hydraulic oil return port R, the hydraulic cylinder 21 continues to advance, and meanwhile, the decompression alarm device 132 stops alarming or warning, and the system returns to normal.

When the explosion-proof valve 133 monitors that the hydraulic cylinder 21 oil delivery port is under pressure loss (the absolute value of the pressure difference of the hydraulic oil at the hydraulic cylinder 21 oil delivery port is higher than or equal to the set pressure difference threshold of the explosion-proof valve 133), the explosion-proof valve 133 acts and automatically blocks the oil path in a one-way manner, thereby preventing the continuous leakage of the hydraulic oil, reducing the leakage loss of the hydraulic oil, preventing accidents, and realizing the automatic monitoring and automatic disposal of the pressure loss at the hydraulic cylinder 21 oil delivery port.

When the absolute value of the pressure difference of the hydraulic oil at the oil delivery port of the hydraulic cylinder 21 is lower than the set pressure difference threshold of the anti-explosion valve 133, and when the anti-explosion valve 133 monitors that the oil delivery port of the hydraulic cylinder 21 is not decompressed, the anti-explosion valve 133 is restored and automatically switches on an oil path, so that the hydraulic control system 100 is restored to normal.

It is obvious to those skilled in the art that the pressure relay 131 is usually regarded as a zero-pressure state after the pressure loss, and therefore, it is easy to think that the pressure threshold of the pressure relay 131 is set to zero or close to zero. However, in actual tests and actual conditions, the inventor finds that when the hydraulic control module 10 loses pressure, the hydraulic oil pressure at the monitoring point is still higher than zero pressure, even has a non-negligible pressure, so that the pressure relay 131 in the actual conditions still cannot automatically act and automatically sends out a pressure loss signal when the hydraulic control module 10 loses pressure, the hydraulic control system 100 still continues to operate, various dangerous accidents and losses are easily caused, and the pressure loss monitoring sensitivity and reliability of the pressure relay 131 are limited. This decompression monitoring subassembly 13 of this disclosure especially pressure relay 131 has better decompression monitoring sensitivity and reliability, simultaneously, also can the most effective reduction decompression misstatement and decompression monitoring delay, can realize the unusual automatic accurate monitoring of decompression and automatic effective processing, therefore can improve hydraulic control system or hydraulic pressure elevating gear's security, ease for use and intelligent level better.

The structural members related to the embodiments of the present disclosure may be made of carbon steel, light metal materials such as aluminum alloy, aluminum magnesium alloy, and the like, and plastics with satisfactory strength may also be used.

The fixed connection or fixed installation or fixation referred to in the embodiments of the present disclosure generally refers to any suitable or feasible manner such as screw connection, integrated structure designed and manufactured integrally, welding, riveting, hole-shaft fit connection, bonding, binding connection, etc., unless otherwise specified. The bearing and the associated embodiments or embodiments of the bearing cap are described in the prior art and in the customary manner and are not described in detail nor are they provided with the drawings.

The outsourcing or other prior art involved in embodiments of the present disclosure, in the particular implementation used in connection with embodiments of the present disclosure, may involve adaptation of some parameters, structures, dimensions, procedures, etc., such modifications may be readily apparent to those skilled in the art, and may be readily made without the intent of describing particular embodiments.

The contents and embodiments not described in detail in the embodiments of the present disclosure can be directly embodied by referring to the prior art documents and products disclosed for sale or use, or have been used routinely by those skilled in the art or widely known by those skilled in the art, and the present disclosure only describes the main difference between the technical scheme of the present disclosure and the prior art for convenience of understanding the fundamental principle and gist of the present disclosure due to cost, effort, legal regulation and the like.

It should be understood that various forms of the flows shown above may be used, with steps reordered, added, or deleted. For example, the steps described in the present disclosure may be executed in parallel, sequentially, or in different orders, as long as the desired results of the technical solutions disclosed in the present disclosure can be achieved, which is not limited herein.

It should also be understood that, in the embodiments of the present disclosure, the sequence numbers of the above-mentioned processes do not mean the execution sequence, and the execution sequence of each process should be determined by its function and inherent logic, and should not constitute any limitation on the implementation process of the embodiments of the present disclosure.

Thus, various embodiments of the present disclosure have been described in detail. Some details that are well known in the art have not been described in order to avoid obscuring the concepts of the present disclosure. Those skilled in the art can now fully appreciate how to implement the teachings disclosed herein, in view of the foregoing description.

Although some specific embodiments of the present disclosure have been described in detail by way of example, it should be understood by those skilled in the art that the foregoing examples are for purposes of illustration only and are not intended to limit the scope of the present disclosure. It will be understood by those skilled in the art that various changes may be made in the above embodiments or equivalents may be substituted for elements thereof without departing from the scope and spirit of the present disclosure. The scope of the present disclosure is defined by the appended claims.

Claims (25)

1. The hydraulic control system is characterized by comprising a hydraulic control module and a hydraulic execution module; the hydraulic control module comprises a hydraulic pump station, a hydraulic control assembly and a pressure loss monitoring assembly; the hydraulic execution module comprises a hydraulic cylinder; the hydraulic control assembly comprises an electromagnetic valve group; the pressure loss monitoring assembly comprises a pressure relay and an explosion-proof valve; the pressure relay oil port is connected to a pressure measuring point of the hydraulic control system to monitor whether the pressure measuring point of the hydraulic control system is in pressure loss or not, and a pressure loss signal is automatically sent out when the pressure measuring point of the hydraulic control system is in pressure loss; the explosion-proof valve is connected in series with the hydraulic cylinder oil delivery port, monitors whether the hydraulic cylinder is in pressure loss or not and automatically handles when the hydraulic cylinder is in pressure loss.

2. The hydraulic control system of claim 1, wherein the set pressure threshold of the pressure relay is not lower than an actuation pressure value of the pressure relay in a simulated no-pressure condition.

3. The hydraulic control system of claim 1, wherein the hydraulic pump station comprises a hydraulic oil tank, a motor, and a gear pump; the motor drives the impeller of the gear pump to rotate, so that the hydraulic oil in the hydraulic oil tank has enough pressure and is output to the hydraulic control assembly to drive the hydraulic cylinder to move.

4. The hydraulic control system of claim 1, wherein the pressure relay is connected in parallel to the output of the hydraulic control assembly and monitors the output of the hydraulic control assembly for a loss of pressure.

5. The hydraulic control system of claim 4, wherein the pressure relay oil measurement port is connected to the tee joint and connected to the control module oil outlet pipe in parallel through the tee joint, and the pressure relay oil measurement port is disposed at an output end of the hydraulic control module.

6. The hydraulic control system according to claim 2, wherein the hydraulic control system gradually increases the set pressure threshold of the pressure relay from a zero position in a simulated decompression state until the pressure relay acts and automatically sends out a decompression signal, and the set pressure threshold when the pressure relay acts and sends out the signal in the simulated decompression state is an action pressure value of the pressure relay in the simulated decompression state.

7. The hydraulic control system of claim 2, wherein the set pressure threshold for the pressure relay to automatically signal a loss of pressure is no more than 1.5 times the operating pressure value of the pressure relay in the simulated loss of pressure condition.

8. The hydraulic control system of claim 1, wherein an output end of the explosion-proof valve is directly communicated with an oil delivery port of the hydraulic cylinder, and an input end of the explosion-proof valve is communicated with an oil inlet pipe of the hydraulic cylinder.

9. The hydraulic control system according to claim 1, wherein when the hydraulic oil pressure at the input end of the explosion-proof valve is lower than the hydraulic oil pressure at the output end of the explosion-proof valve and the absolute value of the hydraulic oil pressure difference at the input end and the output end of the explosion-proof valve exceeds a set pressure difference threshold value of the explosion-proof valve, the explosion-proof valve acts and automatically and unidirectionally blocks the oil path.

10. The hydraulic control system of claim 9, wherein the set differential pressure threshold of the explosion-proof valve acting and automatically blocking the oil circuit in one way is not lower than the absolute value of the hydraulic oil pressure difference at the input end and the output end of the explosion-proof valve in the advancing process of the hydraulic cylinder and not lower than M times of the absolute value of the pressure difference of the explosion-proof valve acting in a leakage-breaking and pressure-loss state, wherein 1 is not less than M and not less than 0.5.

11. The hydraulic control system according to claim 9, wherein the set differential pressure threshold value of the explosion-proof valve operating and automatically blocking the oil passage in one way is not higher than N times of the absolute value of the differential pressure of the explosion-proof valve operating in a leakage-proof and pressure-loss state, wherein N is greater than or equal to 1.

12. The hydraulic control system according to claim 11, wherein the hydraulic control system gradually reduces the set differential pressure threshold value of the explosion-proof valve from the highest value in the leakage-pressure-loss state until the explosion-proof valve can act and automatically block the oil passage in one way, and the set differential pressure threshold value at the moment of the explosion-proof valve is the absolute value of the action differential pressure of the explosion-proof valve in the leakage-pressure-loss state.

13. The hydraulic control system of claim 3, wherein the hydraulic control assembly further comprises a first check valve; the input end of the first check valve is communicated with the oil outlet of the gear pump, the output end of the first check valve is directly or indirectly communicated with the hydraulic cylinder, and hydraulic oil output by the gear pump can flow to the hydraulic cylinder through the first check valve.

14. The hydraulic control system of claim 13, wherein the hydraulic control assembly further comprises a manual reversing valve; the manual reverse valve forms a branch and is connected with a branch formed by the electromagnetic valve group in parallel; the input end of the manual reversing valve is communicated with an execution module connecting port A of the electromagnetic valve group, and the output end of the manual reversing valve is indirectly communicated with the hydraulic oil tank.

15. The hydraulic control system of claim 3, wherein the hydraulic control assembly further comprises a throttle valve; the choke valve set up in between electromagnetism valves and the hydraulic tank, the input of choke valve with the hydraulic oil backward flow mouth R intercommunication of electromagnetism valves, the output of choke valve with the hydraulic tank intercommunication.

16. The hydraulic control system of claim 13, wherein the hydraulic control assembly further comprises a second one-way valve; the input end of the second one-way valve is communicated with the output end of the first one-way valve, and the output end of the second one-way valve is communicated with the hydraulic cylinder; the second one-way valve forms a branch and is connected with the branch formed by the electromagnetic valve group in parallel.

17. The hydraulic control system of claim 16, wherein the hydraulic control assembly further comprises a relief valve; the input end of the overflow valve is respectively communicated with the output end of the first one-way valve and the input end of the second one-way valve through a three-way joint, and the output end of the overflow valve is indirectly communicated with the hydraulic oil tank.

18. The hydraulic control system of claim 3, wherein the pressure loss monitoring assembly further comprises a pressure loss warning device; and the pressure loss alarm device is arranged on the hydraulic pump station or beside the control button of each floor.

19. A hydraulic lifting device comprising a hydraulic lifting module and a hydraulic control system as claimed in any one of claims 1 to 18.

20. The hydraulic lift apparatus of claim 19, wherein said hydraulic lift module comprises a fixed frame, a vehicle and a vehicle rail; the fixed frame comprises a main upright post and an auxiliary upright post; the carrier track fixed connection in fixed frame, the carrier is provided with the carrier pulley, carrier pulley roll connection in the carrier track to make the carrier along the carrier track is at upper and lower direction rectilinear motion.

21. The hydraulic lift apparatus of claim 20, wherein said hydraulic lift module further comprises a transmission mechanism; the transmission mechanism comprises a hanging chain, a chain wheel cross beam assembly and a chain wheel track; the hydraulic cylinder drives the carrier to lift through a chain wheel transmission mechanism formed by the lifting chain and the chain wheel.

22. The hydraulic lift apparatus of claim 21, wherein the hoist chain includes a hoist chain first fixed point and a hoist chain second fixed point; the carrier comprises a carrier panel and a carrier guardrail; the first fixed point of the sling chain is fixedly connected with the main beam of the fixed frame, and the second fixed point of the sling chain is fixedly connected with the bottom of the carrier panel.

23. The hydraulic lift apparatus of claim 22, wherein the second attachment point of the lift chain is directly fixedly attached to the bottom of the vehicle deck, and no connecting rod is disposed between the second attachment point of the lift chain and the vehicle deck.

24. The hydraulic lift apparatus of claim 20, wherein the vehicle track is a main column of the fixed frame.

25. The hydraulic lift apparatus of claim 21 wherein said sprocket track is an auxiliary post of said fixed frame.

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