Liquid-driven hydrogen compressor reversing control device and liquid-driven hydrogen compressor

Abstract

The utility model discloses a hydraulic drive type hydrogen compressor reversing control device and a hydraulic drive type hydrogen compressor. The reversing control device comprises a motor, a hydraulic control proportional closed pump, an electric control proportional valve set, a pressure detection module and a control module. An oil port of the hydraulic control proportional closed pump, an oil port of the electric control proportional valve group and an oil port of the compression oil cylinder are mutually connected to form a closed hydraulic system; the motor is in transmission connection with the hydraulic control proportional closed pump, the pressure detection module is connected with the control module, and the pressure detection module is used for detecting a working pressure signal of the hydraulic control proportional closed pump; the control module is connected with the electric control proportional valve group and is used for controlling the electric control proportional valve group according to the working pressure signal detected by the pressure detection module so as to control the reversing of the hydraulic control proportional closed pump and adjust the displacement of the hydraulic control proportional closed pump; and the hydraulic control proportional closed pump is used for driving the compression oil cylinder to reciprocate to continuously compress hydrogen. The reversing impact is small, the compression efficiency is high, and a hydraulic pipeline is greatly simplified.

Description

Technical Field

[0001] This application relates to the field of hydrogen compressor technology, and in particular to a reversing control device for a liquid-driven hydrogen compressor and a liquid-driven hydrogen compressor. Background Technology

[0002] A hydrogen compressor is a device that compresses and transports hydrogen by changing its volume. It is widely used in hydrogen production, pipeline transportation, and hydrogen refueling stations. Liquid-driven hydrogen compressors, with their high efficiency, large displacement, and high safety, have become key equipment in the hydrogen energy storage and transportation field. The compression cylinder of a liquid-driven hydrogen compressor is special, employing a double-piston rod cylinder. The reciprocating motion of the two piston rods alternately compresses the hydrogen in the chambers at both ends of the piston rods.

[0003] Traditional liquid-driven hydrogen compressors employ an open hydraulic system consisting of a fixed-displacement pump and a pilot-operated directional valve. The fixed-displacement pump supplies oil to the compressor cylinder via the pilot-operated directional valve, which controls the cylinder's reversing direction by changing the oil inlet and outlet directions, thus compressing hydrogen. However, liquid-driven hydrogen compressors that rely on an open hydraulic system with a fixed-displacement pump and pilot-operated directional valve suffer from problems such as large reversing impact, low compression efficiency, and complex hydraulic piping. Summary of the Invention

[0004] To address at least one of the aforementioned technical problems, this application provides a reversing control device for a liquid-driven hydrogen compressor and a liquid-driven hydrogen compressor, which features low reversing impact, high compression efficiency, and significantly simplified hydraulic piping.

[0005] The first objective of this application is to provide a reversing control device for a liquid-driven hydrogen compressor.

[0006] The first objective of this application is achieved through the following technical solution:

[0007] A reversing control device for a liquid-driven hydrogen compressor, wherein the liquid-driven hydrogen compressor includes a compression cylinder having a first oil port and a second oil port, and the reversing control device includes a motor, a hydraulically controlled proportional closed-loop pump, an electronically controlled proportional valve group, a pressure detection module, and a control module.

[0008] The oil ports of the hydraulically controlled proportional closed-loop pump, the oil ports of the electrically controlled proportional valve group, and the oil ports of the compression cylinder are interconnected to form a closed-loop hydraulic system.

[0009] The motor has its output shaft connected to the power input end of the hydraulically controlled proportional closed-loop pump to drive the hydraulically controlled proportional closed-loop pump to work.

[0010] The pressure detection module has its signal output terminal connected to the signal input terminal of the control module. The pressure detection module is used to detect the working pressure signal of the hydraulic proportional closed-loop pump and transmit the detected working pressure signal to the control module.

[0011] The control module has its signal output terminal connected to the signal input terminal of the electronically controlled proportional valve group. The control module is used to control the electronically controlled proportional valve group according to the working pressure signal detected by the pressure detection module, so as to control the reversing of the hydraulically controlled proportional closed pump and adjust the displacement of the hydraulically controlled proportional closed pump through the electronically controlled proportional valve group.

[0012] The hydraulically controlled proportional closed-loop pump is used to drive the reciprocating motion of the compression cylinder by changing the oil inlet / outlet direction and displacement to achieve continuous compression of hydrogen.

[0013] Preferably, the hydraulically controlled proportional closed-loop pump has a first drive oil port, a second drive oil port, a first control oil inlet, a second control oil inlet, and a signal oil supply port.

[0014] The electronically controlled proportional valve assembly has a first signal oil inlet, a second signal oil inlet, a first control oil outlet, a second control oil outlet, and a signal oil inlet.

[0015] The first drive port of the hydraulically controlled proportional closed-loop pump, the first signal oil inlet of the electronically controlled proportional valve group, and the first oil port of the compression cylinder are connected; the second drive port of the hydraulically controlled proportional closed-loop pump, the second signal oil inlet of the electronically controlled proportional valve group, and the second oil port of the compression cylinder are connected.

[0016] The first control oil inlet of the hydraulically controlled proportional closed-loop pump is connected to the first control oil outlet of the electronically controlled proportional valve group, and the second control oil inlet of the hydraulically controlled proportional closed-loop pump is connected to the second control oil outlet of the electronically controlled proportional valve group.

[0017] The signal oil supply port of the hydraulically controlled proportional closed-loop pump is connected to the signal oil inlet port of the electronically controlled proportional valve group.

[0018] Preferably, a high-pressure condenser is provided between the first drive port of the hydraulically controlled proportional closed-loop pump and the first port of the compression cylinder, and / or between the second drive port of the hydraulically controlled proportional closed-loop pump and the second port of the compression cylinder.

[0019] Preferably, the electronically controlled proportional valve assembly includes a proportional valve, a first one-way sequence valve, a second one-way sequence valve, and a hydraulically controlled directional valve.

[0020] The signal input terminal of the proportional valve is connected to the signal output terminal of the control module as the signal input terminal of the electronically controlled proportional valve group.

[0021] The P port of the proportional valve is connected to the signal oil inlet of the electronically controlled proportional valve assembly and the signal oil supply port of the hydraulically controlled proportional closed-loop pump. The A port of the proportional valve is connected to the P port of the hydraulically controlled directional valve.

[0022] Port A of the hydraulically controlled directional valve is connected to the first control oil outlet of the electro-hydraulic proportional valve group and the first control oil inlet of the hydraulically controlled proportional closed-loop pump, and Port B of the hydraulically controlled directional valve is connected to the second control oil outlet of the electro-hydraulic proportional valve group and the second control oil inlet of the hydraulically controlled proportional closed-loop pump.

[0023] The inlet of the first one-way sequence valve is connected to the first port of the compression cylinder as the first signal oil inlet of the electronically controlled proportional valve assembly, and the outlet of the first one-way sequence valve is connected to the first pilot control port of the hydraulically controlled directional valve.

[0024] The oil inlet of the second one-way sequence valve is connected to the second oil port of the compression cylinder as the second signal oil inlet of the electronically controlled proportional valve group, and the oil outlet of the second one-way sequence valve is connected to the second pilot control oil port of the hydraulically controlled directional valve.

[0025] Preferably, the proportional valve is a proportional pressure reducing valve.

[0026] Preferably, the hydraulic control directional valve is a pilot-operated two-position four-way hydraulic control directional valve.

[0027] Preferably, the hydraulically controlled proportional closed-loop pump includes a swashplate axial piston pump, wherein the input shaft of the swashplate axial piston pump is connected to the output shaft of the motor as the power input end of the hydraulically controlled proportional closed-loop pump, and the first suction / discharge port and the second suction / discharge port of the swashplate axial piston pump are respectively connected to the first oil port and the second oil port of the compression cylinder.

[0028] Preferably, the pressure detection module employs a dual-channel pressure sensor, and the signal output terminal of the dual-channel pressure sensor is connected to the signal input terminal of the control module.

[0029] The dual-channel pressure sensor is used to detect the pressure at the first suction / discharge port and the second suction / discharge port of the swashplate axial piston pump, and sends the larger of the two pressure values ​​as the working pressure signal of the hydraulically controlled proportional closed-loop pump to the control module.

[0030] Preferably, the control module is a microcontroller.

[0031] The second objective of this application is to provide a liquid-driven hydrogen compressor.

[0032] The second objective of this application is achieved through the following technical solution:

[0033] A liquid-driven hydrogen compressor includes the reversing control device for a liquid-driven hydrogen compressor as described in any of the first objectives above.

[0034] The beneficial effects of this application are as follows:

[0035] This application constructs a closed hydraulic system by setting up an electronically controlled proportional valve group and a hydraulically controlled proportional closed pump to form the compression cylinder of a liquid-driven hydrogen compressor. The hydraulically controlled proportional closed pump directly supplies oil to the compression cylinder. The electronically controlled proportional valve group controls the reversing and displacement adjustment of the hydraulically controlled proportional closed pump based on the working pressure signal detected by the pressure detection module. Compared with the traditional open hydraulic system composed of a fixed displacement pump and a hydraulically controlled reversing valve to control the reversing of the compression cylinder in a liquid-driven hydrogen compressor, the control device of this application avoids the hydraulic shock and energy loss that occur during the reversing process of an open hydraulic system. Therefore, the reversing shock of the hydraulic system is smaller, the hydrogen compression efficiency is higher, and the hydraulic pipeline is greatly simplified. Attached Figure Description

[0036] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0037] Figure 1 This is a schematic diagram of the reversing control device for a liquid-driven hydrogen compressor in one embodiment of this application;

[0038] Figure 2 This is a schematic diagram of the structure of a hydrogen compressor in one embodiment of this application. Detailed Implementation

[0039] To enable those skilled in the art to better understand the technical solutions in this application, the technical solutions in the embodiments of this application will be clearly and completely described below. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of the embodiments. Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0040] In the embodiments provided in this application, it should be understood that the disclosed methods and systems can be implemented in other ways. The system embodiments described below are merely illustrative. For example, the division of units and modules is only a logical functional division, and in actual implementation, there may be other division methods, such as: multiple units or modules can be combined, or integrated into another system, or some features can be ignored or not executed. In addition, the coupling, direct coupling, or communication connection between the various components shown or discussed can be through some interfaces, indirect coupling or communication connection of devices or modules, and can be electrical, mechanical, or other forms.

[0041] In addition, each functional unit in the various embodiments of this application can be integrated into a single processor, or each unit can be a separate device, or two or more units can be integrated into a single device; each functional unit in the various embodiments of this application can be implemented in hardware or in the form of hardware plus software functional units.

[0042] Those skilled in the art will understand that all or part of the steps of the following method embodiments can be implemented by program instructions and related hardware. The aforementioned program instructions can be stored in a computer-readable storage medium. When the program instructions are executed, they perform the steps of the following method embodiments. The aforementioned storage medium includes various media capable of storing program code, such as mobile storage devices, read-only memory (ROM), magnetic disks, or optical disks.

[0043] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, "a plurality of" or "several" means two or more, unless otherwise explicitly specified.

[0044] This application provides a reversing control device for a liquid-driven hydrogen compressor, such as... Figure 1 As shown, the liquid-driven hydrogen compressor includes a compression cylinder 100, which has a first oil port a1 and a second oil port a2. The reversing control device includes a motor 1, a hydraulically controlled proportional closed-loop pump 2, an electronically controlled proportional valve group 3, a pressure detection module (not shown in the figure), and a control module (not shown in the figure).

[0045] The oil ports of the hydraulically controlled proportional closed-loop pump 2, the electronically controlled proportional valve group 3, and the compression cylinder 100 are interconnected to form a closed-loop hydraulic system.

[0046] Motor 1, whose output shaft is connected to the power input end of hydraulically controlled proportional closed pump 2, so as to drive hydraulically controlled proportional closed pump 2 to work.

[0047] The pressure detection module has its signal output terminal connected to the signal input terminal of the control module. The pressure detection module is used to detect the working pressure signal of the hydraulic proportional closed pump 2 and transmit the detected working pressure signal to the control module.

[0048] The control module has its signal output terminal connected to the signal input terminal of the electronically controlled proportional valve group 3. The control module is used to control the electronically controlled proportional valve group 3 according to the working pressure signal detected by the pressure detection module, so as to control the reversing of the hydraulically controlled proportional closed pump 2 and adjust the displacement of the hydraulically controlled proportional closed pump 2 through the electronically controlled proportional valve group 3.

[0049] The hydraulically controlled proportional closed-loop pump 2 is used to continuously compress hydrogen by driving the reciprocating motion of the compression cylinder 100 by changing the oil inlet and outlet direction and displacement.

[0050] The working principle of the liquid-driven hydrogen compressor reversing control device in this embodiment is as follows:

[0051] When the liquid-driven hydrogen compressor is working, the pressure detection module detects the working pressure signal of the liquid-controlled proportional closed-loop pump 2 and transmits it to the control module. The control module controls the electronically controlled proportional valve group 3 according to the working pressure signal detected by the pressure detection module. The electronically controlled proportional valve group 3 controls the reversing of the liquid-controlled proportional closed-loop pump 2 and adjusts the displacement of the liquid-controlled proportional closed-loop pump 2. The liquid-controlled proportional closed-loop pump 2 drives the compression cylinder 100 to reciprocate by changing the oil inlet and outlet direction and displacement, thereby completing the continuous compression of hydrogen.

[0052] This embodiment of the application establishes a closed hydraulic system by setting up an electronically controlled proportional valve group 3 and a hydraulically controlled proportional closed pump 2 to form a compression cylinder 100 of a liquid-driven hydrogen compressor. The hydraulically controlled proportional closed pump 2 directly supplies oil to the compression cylinder 100. The electronically controlled proportional valve group 3 controls the reversing and displacement adjustment of the hydraulically controlled proportional closed pump 2 based on the working pressure signal detected by the pressure detection module. Compared with the traditional liquid-driven hydrogen compressor that controls the reversing of the compression cylinder 100 through an open hydraulic system composed of a fixed displacement pump and a hydraulically controlled reversing valve 34, the control device of this application avoids the hydraulic shock and energy loss that occur during the reversing process of the open hydraulic system. Therefore, the reversing shock of the hydraulic system is smaller, the compression efficiency of hydrogen is higher, and the hydraulic pipeline is greatly simplified.

[0053] Data from experimental verification and actual use testing show that the compression efficiency of a conventional liquid-driven hydrogen compressor using an open hydraulic system consisting of a fixed-displacement pump and a hydraulically controlled directional valve 34 is no higher than 65%, while the compression efficiency of the liquid-driven hydrogen compressor in this embodiment can be increased to over 80%.

[0054] In this embodiment, by controlling the displacement of the hydraulically controlled proportional closed-loop pump 2 based on the working pressure signal detected by the pressure detection module, constant power control of the hydraulically controlled proportional closed-loop pump 2 can also be achieved. This can significantly reduce the maximum power of the motor 1 and decrease the maximum power requirement of the hydraulically driven hydrogen compressor on the motor 1. For example, when the hydraulically driven hydrogen compressor of the conventional open hydraulic system composed of a fixed displacement pump and a hydraulically controlled directional valve 34 requires a maximum power of 55kW for the motor 1, the constant power control of the closed hydraulic system of this application can reduce the maximum output power of the motor 1 to only 45kW to meet the normal operation requirements of the equipment.

[0055] Specifically, such as Figure 1 As shown, in one embodiment, the hydraulically controlled proportional closed-loop pump 2 has a first drive oil port b1, a second drive oil port b2, a first control oil inlet b3, a second control oil inlet b4, and a signal oil supply port b5 connected to it.

[0056] The electronically controlled proportional valve assembly 3 has a first signal oil inlet c1, a second signal oil inlet c2, a first control oil outlet c3, a second control oil outlet c4, and a signal oil inlet c5.

[0057] The first drive oil port b1 of the hydraulically controlled proportional closed-loop pump 2, the first signal oil inlet c1 of the electronically controlled proportional valve group 3, and the first oil port a1 of the compression cylinder 100 are connected; the second drive oil port b2 of the hydraulically controlled proportional closed-loop pump 2, the second signal oil inlet c2 of the electronically controlled proportional valve group 3, and the second oil port a2 of the compression cylinder 100 are connected.

[0058] The first control oil inlet b3 of the hydraulically controlled proportional closed-loop pump 2 is connected to the first control oil outlet c3 of the electronically controlled proportional valve group 3, and the second control oil inlet b4 of the hydraulically controlled proportional closed-loop pump 2 is connected to the second control oil outlet c4 of the electronically controlled proportional valve group 3.

[0059] The signal oil supply port b5 of the hydraulically controlled proportional closed-circuit pump 2 is connected to the signal oil inlet port c5 of the electronically controlled proportional valve group 3.

[0060] In this embodiment, the hydraulically controlled proportional closed-loop pump 2 supplies oil to the signal oil inlet c5 of the electronically controlled proportional valve group 3 through the signal oil supply port b5, thereby providing control oil pressure to the electronically controlled proportional valve group 3. The electronically controlled proportional valve group 3 obtains the oil inlet / outlet direction and oil pressure of the first oil port a1 and the second oil port a2 of the compression cylinder 100 through the first signal oil inlet c1 and the second signal oil inlet c2, respectively, thereby controlling the oil inlet / outlet direction of the first control oil outlet c3 and the second control oil outlet c4 of the electronically controlled proportional valve group 3, and further controlling the oil inlet / outlet direction of the first control oil inlet b3 and the second control oil inlet b4 of the hydraulically controlled proportional closed-loop pump 2; and the control The control module controls the flow rate of the first control oil outlet c3 and the second control oil outlet c4 of the electronically controlled proportional valve group 3 based on the working pressure signal detected by the pressure detection module. This, in turn, controls the flow rate of the first control oil inlet b3 and the second control oil inlet b4 of the hydraulically controlled proportional closed pump 2. The flow direction and flow rate of the first control oil inlet b3 and the second control oil inlet b4 of the hydraulically controlled proportional closed pump 2 control the flow direction and flow rate of the first drive oil port b1 and the second drive oil port b2 of the hydraulically controlled proportional closed pump 2, thereby driving the compression cylinder 100 to reciprocate, ultimately achieving continuous compression of hydrogen.

[0061] like Figure 1 As shown, in one embodiment, a high-pressure condenser 4 is provided between the second drive port b2 of the hydraulically controlled proportional closed-loop pump 2 and the second port a2 of the compression cylinder 100.

[0062] In this embodiment, a high-pressure condenser 4 is installed at one oil port of the compression cylinder 100 to replace the flushing valve and cooling system required by the traditional closed pump system for cooling the hydraulic oil. This not only meets the cooling requirements of the hydraulic oil in the closed hydraulic system and effectively avoids overloading of the motor 1, but also effectively reduces the complexity of the entire hydraulic pipeline and the equipment cost of the liquid-driven hydrogen compressor.

[0063] like Figure 1 As shown, in one embodiment, the electronically controlled proportional valve assembly 3 includes a proportional valve 31, a first one-way sequence valve 32, a second one-way sequence valve 33, and a hydraulically controlled directional valve 34.

[0064] The signal input terminal of the proportional valve 31 is connected to the signal output terminal of the control module as the signal input terminal of the electronically controlled proportional valve group 3.

[0065] The P port of the proportional valve 31 is connected to the signal oil inlet c5 of the electronically controlled proportional valve assembly 3 and the signal oil supply port b5 of the hydraulically controlled proportional closed-circuit pump 2. The A port of the proportional valve 31 is connected to the P port of the hydraulically controlled directional valve 34.

[0066] Port A of the hydraulic directional valve 34 is connected to the first control oil outlet c3 of the electro-hydraulic proportional valve group 3 and the first control oil inlet b3 of the hydraulic proportional closed-loop pump 2. Port B of the hydraulic directional valve 34 is connected to the second control oil outlet c4 of the electro-hydraulic proportional valve group 3 and the second control oil inlet b4 of the hydraulic proportional closed-loop pump 2.

[0067] The oil inlet of the first one-way sequence valve 32 is connected to the first signal oil inlet c1 of the electronically controlled proportional valve group 3 and the first oil port a1 of the compression cylinder 100. The oil outlet of the first one-way sequence valve 32 is connected to the first pilot control oil port x1 of the hydraulically controlled directional valve 34.

[0068] The oil inlet of the second one-way sequence valve 33 is connected to the second signal oil inlet c2 of the electronically controlled proportional valve group 3 and the second oil port a2 of the compression cylinder 100. The oil outlet of the second one-way sequence valve 33 is connected to the second pilot control oil port x2 of the hydraulically controlled directional valve 34.

[0069] Specifically, in this embodiment, the proportional valve 31 is a proportional pressure reducing valve; the hydraulic control directional valve 34 is a pilot-operated two-position four-way hydraulic control directional valve 34; the hydraulic control proportional closed pump 2 includes a swashplate axial piston pump 21, the input shaft of the swashplate axial piston pump 21 is used as the power input end of the hydraulic control proportional closed pump 2 and is connected to the output shaft of the motor 1 for transmission; the first suction / discharge port d1 and the second suction / discharge port d2 of the swashplate axial piston pump 21 are respectively connected to the first oil port a1 and the second oil port a2 of the compression cylinder 100.

[0070] In this embodiment, the electronically controlled proportional valve group 3, by setting a proportional valve 31, a first one-way sequence valve 32, a second one-way sequence valve 33, and a hydraulically controlled directional valve 34, realizes the directional control and displacement control of the swashplate axial piston pump 21 in the hydraulically controlled proportional closed pump 2. The principle is as follows:

[0071] Oil enters through the first control oil inlet b3 and exits through the second suction / discharge port d2 below the swashplate axial piston pump 21. The amount of oil discharged depends on the pressure of the first control oil inlet b3. Oil enters through the second control oil inlet b4 and exits through the first suction / discharge port d1 above the swashplate axial piston pump 21. Similarly, the amount of oil discharged depends on the pressure of the second control oil inlet b4.

[0072] The proportional valve 31 controls the pressure of the first control oil inlet b3 and the second control oil inlet b4 according to the input current from the control module. This pressure value is between 0.6MPa and 1.8MPa. The required displacement is determined by the pressure of the first control oil inlet b3 or the second control oil inlet b4 obtained through the proportional valve 31. Since displacement * speed * pressure = power, the working pressure of the hydraulic proportional closed-loop pump 2 will gradually increase as the compression cylinder 100 compresses hydrogen. To ensure that the maximum power remains unchanged (i.e., constant power control), the working pressure signal of the hydraulic proportional closed-loop pump 2 is collected by the pressure detection module. By converting pressure, power, and displacement, the current input to the proportional valve 31 is determined. This current determines the displacement of the swashplate axial piston pump 21, which in turn determines the power of the motor 1. Therefore, when the pressure increases, reducing the displacement of the swashplate axial piston pump 21 can maintain the power of the motor 1 unchanged (without overload).

[0073] The working principle of the hydraulic directional valve 34 is as follows: it detects the pressure on both sides of the compression cylinder 100. When the compression cylinder 100 completes its stroke, the hydraulic system pressure will increase. When it rises to the set pressure of the one-way sequence valve, the one-way sequence valve opens and pushes the hydraulic directional valve 34 to switch, so as to complete the switching of the proportional valve 31 to supply oil to the first control oil inlet b3 or the second control oil inlet b4. This switching causes the swashplate axial piston pump 21 to switch. After the swashplate axial piston pump 21 switches, the compression cylinder 100 switches. This realizes that after the compression cylinder 100 completes its stroke in one end, the swashplate axial piston pump 21 automatically switches, so that the cylinder moves in the other direction, thus realizing the switching of the cylinder.

[0074] Specifically, the operation process of the reversing control device for the liquid-driven hydrogen compressor in this embodiment is as follows:

[0075] When the liquid-driven hydrogen compressor starts, the hydraulically controlled proportional closed-loop pump 2 supplies oil to the P port of the proportional valve 31 through the signal oil supply port b5 and the signal oil inlet port c5. The oil from the A port of the proportional valve 31 enters the P port of the hydraulically controlled directional valve 34. The oil from the B port of the hydraulically controlled directional valve 34 enters the hydraulically controlled proportional closed-loop pump 2 through the first control oil outlet c3 and the first control oil inlet b3 (the A port of the hydraulically controlled directional valve 34 returns oil). This controls the second suction / discharge port d2 of the swashplate axial piston pump 21 in the hydraulically controlled proportional closed-loop pump 2 to discharge oil (the first suction / discharge port d1 suctions oil). The oil is output from the second drive port b2, passes through the high-pressure condenser 4, and then enters the lower chamber of the compression cylinder 100 through the second port a2, driving the piston of the compression cylinder 100 to move from bottom to top, increasing the pressure in the lower chamber of the compression cylinder.

[0076] When the pressure in the lower chamber of the compression cylinder rises to the set pressure of the second one-way sequence valve 33, part of the pressure oil from the second drive port b2 enters the second pilot control port x2 of the hydraulic directional valve 34 through the second signal oil inlet c2 and the second one-way sequence valve 33. This pushes the hydraulic directional valve 34 to switch, causing the control oil from the proportional valve 31 to switch from outlet A of the hydraulic directional valve 34 to outlet C4 and inlet B4, entering the swashplate axial piston pump 21 in the hydraulic proportional closed pump 2. Oil is discharged from the first suction / discharge port d1 (oil is drawn in from the second suction / discharge port d2), and output from the first drive port b1 through the first port a1 of the compression cylinder 100 into the upper chamber of the compression cylinder 100. This drives the piston of the compression cylinder 100 to move from top to bottom, increasing the pressure in the upper chamber of the compression cylinder. This cycle repeats, driving the compression cylinder 100 to reciprocate and achieve continuous compression of hydrogen.

[0077] It should be noted that during the above-mentioned operation of the liquid-driven hydrogen compressor, the pressure detection module detects the working pressure signal of the hydraulically controlled proportional closed-loop pump 2 in real time. The control module controls the input current of the proportional valve 31 according to the working pressure signal detected by the pressure detection module, thereby controlling the flow rate of the pressure oil passing through the proportional valve 31, and then controlling the flow rate of the pressure oil entering the hydraulically controlled proportional closed-loop pump 2, so as to realize the adjustment of the displacement of the hydraulically controlled proportional closed-loop pump 2.

[0078] In one embodiment, the pressure detection module employs a dual-channel pressure sensor, with the signal output terminal of the dual-channel pressure sensor connected to the signal input terminal of the control module.

[0079] The dual-channel pressure sensor is used to detect the pressure at the first suction / discharge port d1 and the second suction / discharge port d2 of the swashplate axial piston pump 21, and sends the larger of the two pressure values ​​as the working pressure signal of the hydraulically controlled proportional closed-circuit pump 2 to the control module.

[0080] Specifically, in one embodiment, the control module employs a microcontroller. It should be noted that the control function of the control module in this embodiment only needs to control the input current of the proportional valve 31 according to a preset pressure-current matching relationship based on the detected working pressure signal. The control program that outputs the corresponding control current according to the preset pressure-current matching relationship based on the detected working pressure signal is mature prior art. Therefore, the control program executed by the control module in this application does not involve any improvement to the control method itself.

[0081] It should be noted that the specific structure and working principle of the hydraulically controlled proportional closed-loop pump 2 used in this application are existing technologies and will not be described in detail here.

[0082] like Figure 2The present application also provides a liquid-driven hydrogen compressor, including the liquid-driven hydrogen compressor reversing control device 200 in any of the above embodiments.

[0083] The liquid-driven hydrogen compressor in this embodiment includes the reversing control device of the liquid-driven hydrogen compressor in any of the above embodiments. Therefore, it has the same working principle and technical effect as the reversing control device of the liquid-driven hydrogen compressor in any of the above embodiments, and will not be described again here.

[0084] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on its differences from other embodiments. Similar or identical parts between embodiments can be referred to interchangeably. For the apparatus disclosed in the embodiments, since it corresponds to the method disclosed in the embodiments, the description is relatively simple; relevant parts can be referred to the method section.

[0085] Those skilled in the art will further recognize that the units and algorithm steps of the various examples described in conjunction with the embodiments disclosed herein can be implemented in electronic hardware, computer software, or a combination of both. To clearly illustrate the interchangeability of hardware and software, the components and steps of the various examples have been generally described in terms of functionality in the foregoing description. Whether these functions are implemented in hardware or software depends on the specific application and design constraints of the technical solution. Those skilled in the art can use different methods to implement the described functions for each specific application, but such implementation should not be considered beyond the scope of this application.

[0086] The steps of the methods or algorithms described in conjunction with the embodiments disclosed herein can be implemented directly using hardware, a software module executed by a processor, or a combination of both. The software module can be located in random access memory (RAM), main memory, read-only memory (ROM), electrically programmable ROM, electrically erasable programmable ROM, registers, hard disk, removable disk, CD-ROM, or any other form of storage medium known in the art.

[0087] The above description of the disclosed embodiments enables those skilled in the art to make or use this application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of this application. Therefore, this application is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A reversing control device for a liquid-driven hydrogen compressor, the liquid-driven hydrogen compressor comprising a compression cylinder having a first oil port and a second oil port, characterized in that, The reversing control device includes a motor, a hydraulically controlled proportional closed-loop pump, an electrically controlled proportional valve group, a pressure detection module, and a control module. The oil ports of the hydraulically controlled proportional closed-loop pump, the oil ports of the electrically controlled proportional valve group, and the oil ports of the compression cylinder are interconnected to form a closed-loop hydraulic system. The motor has its output shaft connected to the power input end of the hydraulically controlled proportional closed-loop pump to drive the hydraulically controlled proportional closed-loop pump to work. The pressure detection module has its signal output terminal connected to the signal input terminal of the control module. The pressure detection module is used to detect the working pressure signal of the hydraulic proportional closed-loop pump and transmit the detected working pressure signal to the control module. The control module has its signal output terminal connected to the signal input terminal of the electronically controlled proportional valve group. The control module is used to control the electronically controlled proportional valve group according to the working pressure signal detected by the pressure detection module, so as to control the reversing of the hydraulically controlled proportional closed pump and adjust the displacement of the hydraulically controlled proportional closed pump through the electronically controlled proportional valve group. The hydraulically controlled proportional closed-loop pump is used to drive the reciprocating motion of the compression cylinder by changing the oil inlet / outlet direction and displacement to achieve continuous compression of hydrogen.

2. The reversing control device for a liquid-driven hydrogen compressor according to claim 1, characterized in that, The hydraulically controlled proportional closed-loop pump has a first drive oil port, a second drive oil port, a first control oil inlet, a second control oil inlet, and a signal oil supply port. The electronically controlled proportional valve assembly has a first signal oil inlet, a second signal oil inlet, a first control oil outlet, a second control oil outlet, and a signal oil inlet. The first drive port of the hydraulically controlled proportional closed-loop pump, the first signal oil inlet of the electronically controlled proportional valve group, and the first oil port of the compression cylinder are connected; the second drive port of the hydraulically controlled proportional closed-loop pump, the second signal oil inlet of the electronically controlled proportional valve group, and the second oil port of the compression cylinder are connected. The first control oil inlet of the hydraulically controlled proportional closed-loop pump is connected to the first control oil outlet of the electronically controlled proportional valve group, and the second control oil inlet of the hydraulically controlled proportional closed-loop pump is connected to the second control oil outlet of the electronically controlled proportional valve group. The signal oil supply port of the hydraulically controlled proportional closed-loop pump is connected to the signal oil inlet port of the electronically controlled proportional valve group.

3. The reversing control device for a liquid-driven hydrogen compressor according to claim 2, characterized in that, A high-pressure condenser is provided between the first drive port of the hydraulically controlled proportional closed-loop pump and the first port of the compression cylinder, and / or between the second drive port of the hydraulically controlled proportional closed-loop pump and the second port of the compression cylinder.

4. The reversing control device for a liquid-driven hydrogen compressor according to claim 2, characterized in that, The electronically controlled proportional valve assembly includes a proportional valve, a first one-way sequence valve, a second one-way sequence valve, and a hydraulically controlled directional valve. The signal input terminal of the proportional valve is connected to the signal output terminal of the control module as the signal input terminal of the electronically controlled proportional valve group. The P port of the proportional valve is connected to the signal oil inlet of the electronically controlled proportional valve assembly and the signal oil supply port of the hydraulically controlled proportional closed-loop pump. The A port of the proportional valve is connected to the P port of the hydraulically controlled directional valve. Port A of the hydraulically controlled directional valve is connected to the first control oil outlet of the electro-hydraulic proportional valve group and the first control oil inlet of the hydraulically controlled proportional closed-loop pump, and Port B of the hydraulically controlled directional valve is connected to the second control oil outlet of the electro-hydraulic proportional valve group and the second control oil inlet of the hydraulically controlled proportional closed-loop pump. The inlet of the first one-way sequence valve is connected to the first port of the compression cylinder as the first signal oil inlet of the electronically controlled proportional valve assembly, and the outlet of the first one-way sequence valve is connected to the first pilot control port of the hydraulically controlled directional valve. The oil inlet of the second one-way sequence valve is connected to the second oil port of the compression cylinder as the second signal oil inlet of the electronically controlled proportional valve group, and the oil outlet of the second one-way sequence valve is connected to the second pilot control oil port of the hydraulically controlled directional valve.

5. The reversing control device for a liquid-driven hydrogen compressor according to claim 4, characterized in that, The proportional valve is a proportional pressure reducing valve.

6. The reversing control device for a liquid-driven hydrogen compressor according to claim 4, characterized in that, The hydraulic control directional valve is a pilot-operated two-position four-way hydraulic control directional valve.

7. The reversing control device for a liquid-driven hydrogen compressor according to any one of claims 1-6, characterized in that, The hydraulically controlled proportional closed-loop pump includes a swashplate axial piston pump. The input shaft of the swashplate axial piston pump is connected to the output shaft of the motor as the power input end of the hydraulically controlled proportional closed-loop pump. The first suction / discharge port and the second suction / discharge port of the swashplate axial piston pump are respectively connected to the first oil port and the second oil port of the compression cylinder.

8. The reversing control device for a liquid-driven hydrogen compressor according to claim 7, characterized in that, The pressure detection module employs a dual-channel pressure sensor, and the signal output terminal of the dual-channel pressure sensor is connected to the signal input terminal of the control module. The dual-channel pressure sensor is used to detect the pressure at the first suction / discharge port and the second suction / discharge port of the swashplate axial piston pump, and sends the larger of the two pressure values ​​as the working pressure signal of the hydraulically controlled proportional closed-loop pump to the control module.

9. The reversing control device for a liquid-driven hydrogen compressor according to any one of claims 1-6, characterized in that, The control module uses a microcontroller.

10. A liquid-driven hydrogen compressor, characterized in that, The device includes the reversing control device for a liquid-driven hydrogen compressor as described in any one of claims 1-9.

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