High-pressure fluid delivery pump

Abstract

A high-pressure fluid delivery pump relates to the technical field of fluid delivery equipment and comprises a plurality of machine bodies, and each machine body comprises a first end cover, a hydraulic cylinder barrel, a second end cover, a first working cylinder, a third end cover, a second working cylinder and a fourth end cover which are sequentially connected; a piston assembly is arranged in the machine body and comprises a first piston, a second piston and a third piston which are coaxially arranged at intervals, the first piston is in sealed and slidable connection with the hydraulic cylinder barrel, the second piston is in slidable and sealed connection with the first working cylinder, and the third piston is in slidable and sealed connection with the second working cylinder; the reversing valves are connected with the machine bodies in a one-to-one correspondence mode and used for controlling reciprocating reversing of the piston assemblies in the machine bodies. The timing unit comprises a servo motor, a crankshaft, a plurality of connecting rods and a plurality of sliding blocks; the timing unit controls the piston assemblies of all the machine bodies to move regularly, and instant pressure fluctuation of fluid caused by simultaneous reversing of the piston rods of all the machine bodies is avoided.

Description

Technical Field

[0001] This invention relates to the field of fluid transport equipment technology, specifically to a high-pressure fluid transport pump, which can be used for pressurizing and transporting high-pressure liquids, as well as compressing and transporting gases. Background Technology

[0002] Chinese invention patent application CN116335913A discloses a low-boost hydraulic reciprocating hydrogen compressor, which consists of a cylinder, a first hydraulic cylinder, a second hydraulic cylinder, hydrogen inlet and outlet pipelines, a nitrogen sealing and venting pipeline system, a hydraulic oil leakage monitoring pipeline system, and a hydraulic drive system. The cylinder, first, and second hydraulic cylinders are horizontally coaxially arranged; the cylinder is located in the middle, with the first and second hydraulic cylinders located on its left and right sides. Each cylinder contains a piston and piston rod, with the piston dividing the cylinder cavity into left and right cylinder chambers; both left and right cylinder chambers are connected to the hydrogen inlet and outlet pipelines. The piston rod extends through the cylinder heads at both ends of the cylinder into the first and second hydraulic cylinders, where it is securely connected to the hydraulic pistons. To achieve a low-boost, high-displacement operating mode, the inner diameter of the cylinder is 3-5 times the inner diameter of the first and second hydraulic cylinders. The reciprocating motion of the pistons in the smaller diameter hydraulic cylinders on the left and right sides drives the low-speed reciprocating motion of the piston in the larger diameter cylinder in the middle.

[0003] However, the hydrogen compressor in the aforementioned patent application has a low flow rate. If multiple such hydrogen compressors are connected in parallel, two hydrogen compressors may switch directions at the same time, which may easily cause pressure fluctuations in the compressed or transported fluid. Summary of the Invention

[0004] This invention addresses the aforementioned technical problems in the prior art by providing a high-pressure fluid transfer pump. By controlling the regular movement of the piston assemblies of each component through a timing unit, it avoids the instantaneous pressure fluctuations of the fluid caused by the simultaneous reversal of the piston rods of each component.

[0005] To achieve the above technical objectives, embodiments of the present invention provide a high-pressure fluid transfer pump, comprising:

[0006] The machine includes multiple machine bodies, each comprising a first end cap, a hydraulic cylinder, a second end cap, a first working cylinder, a third end cap, a second working cylinder, and a fourth end cap connected in sequence. A piston assembly is provided within each machine body, comprising a first piston, a second piston, and a third piston arranged coaxially and at intervals. The first piston is sealed and slidably connected to the hydraulic cylinder, the second piston is slidably and sealedly connected to the first working cylinder, and the third piston is slidably and sealedly connected to the second working cylinder.

[0007] Multiple reversing valves are connected to the machine body in a one-to-one correspondence, and are used to control the reciprocating reversing of the piston assembly in the machine body;

[0008] The system comprises multiple frequency converters, multiple motors, and multiple oil pumps. The output terminals of the motors are connected to the oil pumps via a drive connection. The oil inlets of the oil pumps are connected to the oil tank, and the oil outlets of the oil pumps are connected to the reversing valves. The frequency converters are connected to the motors via power transmission. Each frequency converter, motor, and oil pump corresponds to another motor.

[0009] Multiple displacement sensors are mounted on the first end cap, and the detection end of the displacement sensor passes through the first end cap and is connected to the piston assembly; the displacement sensor is signal-connected to the control element and is used to send displacement information of the piston assembly to the control element.

[0010] The timing unit includes a servo motor, a crankshaft, multiple connecting rods, and multiple sliders. The crankshaft includes multiple crank necks, and the crank necks, connecting rods, and sliders are connected in a one-to-one correspondence. One end of each connecting rod is pivotally connected to a crank neck, and the other end of each connecting rod is pivotally connected to a slider. The sliders are configured to move horizontally reciprocally. The timing unit also includes multiple slide bars, which are configured to move horizontally reciprocally. One end of each slide bar has a first contact portion, and the other end has a second contact portion.

[0011] When the slider is about to move to the first extreme position, it can contact the first contact part and push the slider rod to move a set distance in the first direction; when the slider is about to move to the second extreme position, it can contact the second contact part and push the slider rod to move a set distance in the second direction.

[0012] The slide rod is connected to the valve core of the reversing valve in a one-to-one correspondence, and is used to push the reversing valve to switch directions;

[0013] It also includes multiple timing displacement sensors, the detection ends of which are connected to the slider in a one-to-one correspondence, and the timing displacement sensors are used to send displacement signals of the slider to the control element;

[0014] A control element is connected to the displacement sensor for receiving the position information sent by the displacement sensor; the control element is also connected to the frequency converter for controlling the start, stop, and speed of the motor via the frequency converter; the control element is connected to the timing displacement sensor; and the control element is connected to the servo motor for controlling the crankshaft speed via the servo motor. The control element is configured to control the speed of the servo motor based on the displacement information of one of the sliders detected by the timing displacement sensor, so that the position of the slider corresponds one-to-one with the position of the piston assembly in the machine body.

[0015] In some embodiments, the set distance is the same as the sliding distance of the valve core when the reversing valve reverses.

[0016] In some embodiments, the displacement sensor includes a magnetic ring mounted on the piston assembly.

[0017] In some embodiments, the crank necks are arranged at equal intervals along the crankshaft axis and are uniformly distributed along the circumferential direction.

[0018] In some embodiments, one end of the first piston and one end of the second piston are connected by a piston rod, and the other end of the second piston is connected to the third piston by a piston rod.

[0019] In some embodiments, the inner diameter of the first working cylinder is larger than the inner diameter of the second working cylinder.

[0020] In some embodiments, the system further includes an inflow pipe, an intermediate pipe, and an outflow pipe. The inflow pipe is connected to the first working cylinder and is used to input fluid into the first working cylinder. The first working cylinder is connected to the second working cylinder via an intermediate pipe, and the second working cylinder is connected to the outflow pipe.

[0021] In some embodiments, within the first working cylinder, a first cavity is formed on one side of the second piston, and a second cavity is formed on the other side of the second piston;

[0022] It also includes a first check valve and a second check valve, the outlet of the first check valve being connected to the first cavity, for limiting the unidirectional flow of fluid from the inlet pipe to the first cavity;

[0023] The outlet of the second check valve is connected to the second cavity, which is used to limit the unidirectional flow of fluid from the inlet pipe to the second cavity.

[0024] In some embodiments, within the second working cylinder, a third cavity is formed on one side of the third piston, and a fourth cavity is formed on the other side of the third piston;

[0025] It also includes a third check valve, a fourth check valve, a fifth check valve, and a sixth check valve;

[0026] The input end of the intermediate pipeline is connected to the first cavity through a third one-way valve, which is used to limit the fluid to flow unidirectionally from the first cavity to the intermediate pipeline.

[0027] The inflow end of the intermediate pipeline is connected to the second cavity through a fourth one-way valve, which is used to limit the unidirectional flow of fluid from the second cavity to the intermediate pipeline.

[0028] The outlet end of the intermediate pipeline is connected to the third cavity through a fifth one-way valve, which is used to limit the unidirectional flow of fluid from the intermediate pipeline to the third cavity.

[0029] The outlet end of the intermediate pipeline is connected to the fourth cavity through a sixth one-way valve, which is used to limit the unidirectional flow of fluid from the intermediate pipeline to the fourth cavity.

[0030] In some embodiments, a seventh check valve and an eighth check valve are also included.

[0031] The inlet end of the outflow pipe is connected to the third chamber through a seventh one-way valve, which is used to limit the fluid to flow unidirectionally from the third chamber to the outflow pipe.

[0032] The inflow end of the outflow pipe is connected to the fourth chamber through an eighth one-way valve, which is used to limit the unidirectional flow of fluid from the fourth chamber to the outflow pipe.

[0033] One or more technical solutions provided in the embodiments of the present invention have at least the following technical effects or advantages:

[0034] This invention uses hydraulic principles to drive the piston assembly in the machine body to reciprocate. A first working cylinder and a second working cylinder are set in a machine body to achieve two-stage pressurization of the fluid.

[0035] The present invention comprises multiple machine bodies, and the control elements control the reciprocating operation of the first machine body through the first reversing valve, control the reciprocating operation of the second machine body through the second reversing valve, and control the reciprocating operation of the third machine body through the third reversing valve.

[0036] This invention, by setting a timing unit, can control the piston assemblies of each machine to change direction in a regular and sequential manner, avoiding the instantaneous impact of fluid caused by the simultaneous reversal of the piston rods of each machine. Attached Figure Description

[0037] Figure 1 This is a schematic diagram of the principle of a high-pressure fluid transfer pump according to an embodiment of the present invention.

[0038] Figure 2 This is a schematic diagram of the body arrangement structure of a high-pressure fluid transfer pump according to an embodiment of the present invention.

[0039] Figure 3 This is a schematic diagram of the structure of the high-pressure fluid transfer pump according to an embodiment of the present invention.

[0040] Figure 4 This is a schematic diagram of the pipeline connection structure in a high-pressure fluid transfer pump according to an embodiment of the present invention.

[0041] Figure 5 This is a schematic diagram of the timing unit in a high-pressure fluid transfer pump according to an embodiment of the present invention.

[0042] Figure 6This is a three-dimensional schematic diagram of the timing unit in a high-pressure fluid transfer pump according to an embodiment of the present invention.

[0043] Explanation of reference numerals in the attached figures

[0044] 1a-First machine body, 1b-Second machine body, 1c-Third machine body, 2a-First directional valve, 2b-Second directional valve, 2c-Third directional valve, 3-Control element, 4a-First frequency converter, 4b-Second frequency converter, 4c-Third frequency converter, 5a-First motor, 5b-Second motor, 5c-Third motor, 6a-First oil pump, 6b-Second oil pump, 6c-Third oil pump, 7-Oil tank, 8-Timing unit, 81-Servo motor, 82-Crankshaft, 821a-First crank journal, 821b-Second crank journal, 821c-Third crank journal, 83a - First link, 83b - Second link, 83c - Third link, 84a - First slider, 84b - Second slider, 84c - Third slider, 85a - First slide bar, 85a1 - First contact part, 85a2 - Second contact part, 85b - Second slide bar, 85c - Third slide bar, 9a - First displacement sensor, 9b - Second displacement sensor, 9c - Third displacement sensor, 901 - Magnetic ring; 10a, 10b, 10c - Overflow valve, 12a - First timing displacement sensor, 12b - Second timing displacement sensor, 12c - Third timing displacement sensor;

[0045] 101-First end cap, 102-Hydraulic cylinder barrel, 103-Second end cap, 104-Piston assembly, 1041-First piston, 1042-Second piston, 1043-Third piston, 105-First working cylinder, 106-Third end cap, 107-Second working cylinder, 108-Inflow pipe, 1081-First check valve, 1082-Second check valve, 109-Intermediate pipe, 1091-Third check valve, 1092-Fourth check valve, 1093-Fifth check valve, 1094-Sixth check valve, 110-Outflow pipe, 1101-Seventh check valve, 1102-Eighth check valve, 112-First cavity, 113-Second cavity, 114-Third cavity, 115-Fourth cavity, 116-First oil chamber, 117-Second oil chamber, 118-Fourth end cap. Detailed Implementation

[0046] Other objects and advantages of the present invention will become clear by explaining the preferred embodiments of the present application below.

[0047] like Figures 1 to 6 As shown, a high-pressure fluid transfer pump includes multiple bodies, multiple reversing valves, multiple frequency converters, multiple electric motors, and multiple oil pumps; the reversing valves are used to control the reciprocating reversal of the piston assembly inside the body; the frequency converters are electrically connected to the electric motors; and the electric motors are drive-connected to the oil pumps.

[0048] For ease of explanation, we will use three units as an example below, but the number of units can also be more, such as 4, 5, 6, etc.

[0049] like Figure 1 As shown, this embodiment includes a first body 1a, a second body 1b, and a third body 1c. The reversing valves include a first reversing valve 2a, a second reversing valve 2b, and a third reversing valve 2c. Ports A and B of the first reversing valve 2a are respectively connected to the cavities at both ends of the hydraulic cylinder in the first body 1a. The first reversing valve 2a can control the reciprocating reversing of the piston assembly in the first body 1a. Similarly, the second reversing valve 2b and the third reversing valve 2c can respectively control the reciprocating movement of the piston assemblies in the second body 1b and the third body 1c.

[0050] However, the inventors of this invention discovered during the implementation of the above technology that if the piston assemblies in the first body 1a, the second body 1b, and the third body 1c cannot sequentially change direction at uniform time intervals, it is possible for two or even three bodies to change direction simultaneously, resulting in large pressure fluctuations in the fluid being transported.

[0051] To solve the above-mentioned technical problems, the inventors of this invention designed a timing unit 8, which controls the sequential reversal of the piston assemblies of each machine body at equal time intervals, thereby effectively avoiding the problem of pressure fluctuation of the conveyed fluid caused by the simultaneous reversal of the piston assemblies of two or more machines.

[0052] Furthermore, such as Figures 2 to 4 As shown, the machine body includes a first end cap 101, a hydraulic cylinder 102, a second end cap 103, a first working cylinder 105, a third end cap 106, a second working cylinder 107, and a fourth end cap 118 connected in sequence. A piston assembly 104 is provided inside the machine body. The piston assembly 104 includes a first piston 1041, a second piston 1042, and a third piston 1043, which are coaxially arranged and spaced apart. The first piston 1041 is sealed and slidably connected to the hydraulic cylinder 102; the second piston 1042 is slidably and sealedly connected to the first working cylinder 105; and the third piston 1043 is slidably and sealedly connected to the second working cylinder 107.

[0053] Three directional control valves are provided: a first directional control valve 2a, a second directional control valve 2b, and a third directional control valve 2c. The first directional control valve 2a is connected to the first body 1a; the second directional control valve 2b is connected to the second body 1b; and the third directional control valve 2c is connected to the third body 1c. These directional control valves are used to control the reciprocating direction of the piston assembly within the body.

[0054] The system includes three frequency converters: the first frequency converter 4a, the second frequency converter 4b, and the third frequency converter 4c. It also includes three electric motors: the first electric motor 5a, the second electric motor 5b, and the third electric motor 5c. Finally, it includes three oil pumps: the first oil pump 6a, the second oil pump 6b, and the third oil pump 6c.

[0055] The output terminal of the electric motor is connected to the oil pump via a drive connection. The oil pump's inlet is connected to the oil tank, and its outlet is connected to the reversing valve. The frequency converter is connected to the electric motor via a power supply connection. The frequency converter, the electric motor, and the oil pump correspond one-to-one. An example is given using a first frequency converter 4a, a first electric motor 5a, and a first oil pump 6a. The first frequency converter 4a is connected to the first electric motor 5a via a power supply connection, and can control the start, stop, and speed adjustment of the first electric motor 5a. The output terminal of the first electric motor 5a is connected to the first oil pump 6a via a drive connection, providing power to the first oil pump 6a.

[0056] This embodiment also includes three displacement sensors: a first displacement sensor 9a, a second displacement sensor 9b, and a third displacement sensor 9c. The first displacement sensor 9a will be used as an example for explanation. Figure 3 and 4 As shown, a first displacement sensor 9a is mounted on the first end cover 101, and the detection end of the first displacement sensor 9a passes through the first end cover 101 and is connected to the piston assembly 104. The first displacement sensor 9a is signal-connected to the control element 3 and is used to send displacement information of the piston assembly to the control element 3. Further, the first displacement sensor 9a includes a magnetic ring 901 mounted on the piston assembly. The control element 3 can be, for example, a PLC.

[0057] This embodiment also includes a timing unit 8, which includes a servo motor 81, a crankshaft 82, three connecting rods and multiple sliders.

[0058] In this embodiment, as Figure 5 and Figure 6 As shown, the crankshaft 82 includes three crank necks, namely the first crank neck 821a, the second crank neck 821b, and the third crank neck 821c. The crank necks are evenly spaced along the axial direction of the crankshaft 82 and are uniformly distributed along the circumferential direction.

[0059] The three connecting links are designated as first link 83a, second link 83b, and third link 83c. The three sliders are designated as first slider 84a, second slider 84b, and third slider 84c.

[0060] The crank neck, the connecting rod, and the slider are connected in a one-to-one correspondence. Taking the first crank neck 821 as an example, one end of the first connecting rod 83a is pivotally connected to the first crank neck 821a, and the other end of the first connecting rod 83a is pivotally connected to the first slider 84a. The first slider 84a is configured to move horizontally reciprocatingly; for example, a guide shaft or guide cylinder can be used to guide the slider 84a.

[0061] The timing unit 8 also includes three sliders: a first slider 85a, a second slider 85b, and a third slider 85c. The sliders are configured to move horizontally back and forth. Taking the first slider 85a as an example, one end of the first slider 85a has a first contact portion 85a1, and the other end has a second contact portion 85a2. When the first slider 85a is about to move to a first extreme position (e.g., the left extreme position), it can contact the first contact portion 85a1, pushing the first slider 85a to move a set distance in a first direction; when the first slider 85a is about to move to a second extreme position, it can contact the second contact portion 85a2, pushing the first slider 85a to move the set distance in a second direction.

[0062] In this embodiment, the first slide rod 85a is connected to the valve core of the first directional valve 2a and is used to control the switching of the first directional valve 2a; the second slide rod 85b is connected to the valve core of the second directional valve 2b and is used to control the switching of the second directional valve 2b; the third slide rod 85c is connected to the valve core of the third directional valve 2c and is used to control the switching of the third directional valve 2c. Furthermore, the set distance is the same as the sliding distance when the valve core of the first directional valve 2a switches.

[0063] The control element 3 is connected to the first displacement sensor 9a, the second displacement sensor 9b and the third displacement sensor 9c respectively, and is used to receive the position information of each piston assembly of the machine body.

[0064] The control element 3 is connected to the first frequency converter 4a, the second frequency converter 4b and the third frequency converter 4c respectively, and is used to control the start, stop and speed of the corresponding motor through each frequency converter.

[0065] The control element 3 is signal-connected to the servo motor 81 and is used to control the rotational speed of the crankshaft 82 through the servo motor 81.

[0066] like Figure 6As shown, this embodiment also includes multiple timing displacement sensors connected to each slider in a one-to-one correspondence. Specifically, the detection end of the first timing displacement sensor 12a is connected to the first slider 84a; the detection end of the second timing displacement sensor 12b is connected to the second slider 84b; and the detection end of the third timing displacement sensor 12c is connected to the third slider 84c. Each timing displacement sensor is signal-connected to the control element 3, and is used to send the position information of each slider to the control element 3.

[0067] The working principle of the high-pressure fluid transfer pump start-up process in one embodiment of the present invention is as follows:

[0068] like Figure 5 As shown, control element 3 starts the corresponding motors 5a, 5b, and 5c through each frequency converter 4a, 4b, and 4c. The piston assemblies of each machine body 1a, 1b, and 1c move to their limit positions and remain at those limit positions. At this time, the overflow valves 10a, 10b, and 10c in the oil circuit overflow.

[0069] Control element 3 starts servo motor 81, which drives crankshaft 82 to rotate. When the first slider 84a is about to reach its rightmost limit position, it contacts the second contact part 85a2 of the first slider 85a, pushing the second slider 85a to move a set distance. At the same time, it drives the valve core of the first reversing valve 2a to move to the right, causing the first reversing valve 2a to reverse, that is, the piston assembly of the first body 1a changes its direction of movement. As crankshaft 82 continues to rotate, when the second slider 84b is about to reach its rightmost limit position, it pushes the second slider 85b to move to the right, causing the second reversing valve 2b to reverse, and thus the piston assembly of the second body 1b changes its direction of movement. Similarly, as crankshaft 82 rotates further, the third slider 84c drives the third slider 85c to move to the right, causing the third reversing valve 2c to reverse, and thus the piston assembly of the third body 1c changes its direction of movement.

[0070] The above operations completed the device startup. Next, the control element receives the signal from the first displacement sensor 9a and interacts with it. Figure 6 The position signal of the first slider 84a received by the fourth displacement sensor 12a is compared with that of the first slider 84a, and the output speed of the servo motor 81 is further adjusted so that the displacement signal of the first slider 84a detected by the fourth displacement sensor 12a matches the displacement signal of the piston assembly in the first body 1a detected by the first displacement sensor 9a.

[0071] The above operations can control the piston assembly reversal interval of each machine to be the same, which is beneficial to the regular movement of the piston assembly of each machine.

[0072] In addition, the second timing displacement sensor 12b is used to detect the position information of the second slider 84b, and the third timing displacement sensor 12c is used to detect the position information of the third slider 84c. If the piston assembly of each machine body moves at different speeds due to different internal leakage flow rates in the hydraulic system of each machine body, the control element 3 adjusts the frequency of the strain gauge corresponding to the machine body with larger internal leakage flow rates to make the piston assembly of each machine body move at the same speed.

[0073] like Figures 1 to 3 As shown, a high-pressure fluid transfer pump includes multiple bodies, multiple reversing valves, an electric motor 5, an oil pump 6, and control elements 3. The bodies include a first end cover 101, a hydraulic cylinder 102, a second end cover 103, a first working cylinder 105, a third end cover 106, a second working cylinder 107, and a fourth end cover 118 connected sequentially. A piston assembly 104 is provided within the body, comprising a first piston 1041, a second piston 1042, and a third piston 1043 coaxially and spaced apart. The first piston 1041 is sealed and slidably connected to the hydraulic cylinder 102; the second piston 1042 is slidably and sealedly connected to the first working cylinder 105; and the third piston 1043 is slidably and sealedly connected to the second working cylinder 107. The reversing valves are connected to the bodies one-to-one. The output end of the electric motor 5 is connected to the oil pump 6, the oil inlet of the oil pump 6 is connected to an oil tank 7, and the oil outlet of the oil pump 6 is connected to the reversing valves.

[0074] In this embodiment, the electric motor 5 is connected to the oil pump 6 for driving the oil pump 6 to draw hydraulic oil from the oil tank 7 and deliver it to the machine body. Figure 1 The diagram shows three units: the first unit 1a, the second unit 1b, and the third unit 1c. However, it is not limited to these three units; the number of units can also be two, four to eight, or other quantities.

[0075] The cavity inside the hydraulic cylinder 102 is divided into a first oil chamber 116 and a second oil chamber 117 by the first piston 1041. The piston assembly 104 is driven to reciprocate by alternately injecting hydraulic oil into the first oil chamber 116 and the second oil chamber 117.

[0076] In this embodiment, there are three directional control valves: a first directional control valve 2a, a second directional control valve 2b, and a third directional control valve 2c. The first directional control valve 2a is connected to the first body 1a, the second directional control valve 2b is connected to the second body 1b, and the third directional control valve 2c is connected to the third body 1c. Specifically, the P port of each directional control valve is connected to the oil outlet of the oil pump 6, the T port of the directional control valve is connected to the oil tank 7, the A port of the directional control valve is connected to the first oil chamber 116 of the hydraulic cylinder 102, and the B port of the directional control valve is connected to the second oil chamber 117 of the hydraulic cylinder 102.

[0077] In this embodiment, the control element 3 controls the reciprocating operation of the first body 1a via the first reversing valve 2a, controls the reciprocating operation of the second body 1b via the second reversing valve 2b, and controls the reciprocating operation of the third body 1c via the third reversing valve 2c. Furthermore, the control element 3 can control the first body 1a, the second body 1b, and the third body 1c to reciprocate in a regular, sequential manner.

[0078] In some embodiments, the control element 3 is signal-connected to the frequency converter 4, and the frequency converter 4 is electrically connected to the motor 5. The control element 3 controls the output speed of the motor 5 through the frequency converter 4, thereby controlling the discharge capacity of the high-pressure fluid transfer pump.

[0079] In some embodiments, displacement sensors 9a, 9b, and 9c are also included. Taking the first displacement sensor 9a as an example, the first displacement sensor 9a is mounted on the first end cover 101, and its detection end passes through the first end cover 101 and connects to the piston assembly 104. A magnetic ring 901 is mounted on the piston assembly 104. The displacement sensors can be used to determine the movement position and speed of the piston assembly 104 within each machine body.

[0080] In some embodiments, the displacement sensor 111 is signal-connected to the control element 3 and is used to send displacement information of the piston assembly 104 to the control element 3, thereby facilitating the control element 3 to control the reversing of each body and the coordinated operation between different bodies through the timing unit and the reversing valve.

[0081] In some embodiments, one end of the first piston 1041 is connected to one end of the second piston 1042 via a piston rod, and the other end of the second piston 1042 is connected to the third piston 1043 via a piston rod. The first piston 1041, the second piston 1042, and the third piston 1043 work together, and the second piston 1042 and the third piston 1043 can be driven to work synchronously by a single hydraulic cylinder, achieving dual-stage pressurization on a single machine body and increasing the fluid output pressure of the high-pressure fluid transfer pump.

[0082] In some embodiments, the inner diameter of the first working cylinder 105 is larger than the inner diameter of the second working cylinder 107. The first working cylinder 105 achieves the first pressurization of the fluid, and the second working cylinder 107 achieves the second pressurization of the fluid, thereby increasing the fluid output pressure.

[0083] In some embodiments, such as Figure 4 As shown, it also includes an inflow pipe 108, an intermediate pipe 109 and an outflow pipe 110. The inflow pipe 108 is connected to the first working cylinder 105 and is used to input fluid into the first working cylinder 105. The first working cylinder 105 is connected to the second working cylinder 107 through the intermediate pipe 109, and the second working cylinder 107 is connected to the outflow pipe 110.

[0084] In some embodiments, within the first working cylinder 105, a first cavity 112 is formed on one side of the second piston 1042, and a second cavity 113 is formed on the other side of the second piston 1042; it also includes a first check valve 1081 and a second check valve 1082, the outlet of the first check valve 1081 being connected to the first cavity 112 for limiting the unidirectional flow of fluid from the inlet pipe 108 to the first cavity 112; the outlet of the second check valve 1082 being connected to the second cavity 113 for limiting the unidirectional flow of fluid from the inlet pipe 108 to the second cavity 113.

[0085] In some embodiments, within the second working cylinder 107, a third cavity 114 is formed on one side of the third piston 1043, and a fourth cavity 115 is formed on the other side of the third piston 1043; it also includes a third check valve 1091, a fourth check valve 1092, a fifth check valve 1093, and a sixth check valve 1094; the input end of the intermediate pipeline 109 is connected to the first cavity 112 through the third check valve 1091, and the third check valve 1091 is used to limit the unidirectional flow of fluid from the first cavity 112 to the intermediate pipeline 109;

[0086] The inflow end of the intermediate pipe 109 is connected to the second chamber 113 through the fourth one-way valve 1092, which limits the unidirectional flow of fluid from the second chamber 113 to the intermediate pipe 109. The outflow end of the intermediate pipe 109 is connected to the third chamber 114 through the fifth one-way valve 1093, which limits the unidirectional flow of fluid from the intermediate pipe 109 to the third chamber 114. The outflow end of the intermediate pipe 109 is connected to the fourth chamber 115 through the sixth one-way valve 1094, which limits the unidirectional flow of fluid from the intermediate pipe 109 to the fourth chamber 115.

[0087] In some embodiments, a seventh check valve 1101 and an eighth check valve 1102 are also included. The inflow end of the outflow pipe 110 is connected to the third cavity 114 through the seventh check valve 1101, which is used to limit the unidirectional flow of fluid from the third cavity 114 to the outflow pipe 110. The inflow end of the outflow pipe 110 is connected to the fourth cavity 115 through the eighth check valve 1102, which is used to limit the unidirectional flow of fluid from the fourth cavity 115 to the outflow pipe 110.

[0088] It should be noted that the timing unit of this application can have a small size, as long as it can accommodate the detection distance of each timing displacement sensor.

[0089] The apparatus of this application has been described in detail with reference to the preferred technical solutions. However, it should be noted that, without departing from the spirit of this application, those skilled in the art can make any modifications, alterations, and variations based on the above disclosure. This application includes the above-described specific embodiments and any equivalent forms thereof.

Claims

1. A high-pressure fluid transfer pump, characterized in that, include: The machine includes multiple machine bodies, each comprising a first end cap, a hydraulic cylinder, a second end cap, a first working cylinder, a third end cap, a second working cylinder, and a fourth end cap connected in sequence. A piston assembly is provided within each machine body, comprising a first piston, a second piston, and a third piston arranged coaxially and at intervals. The first piston is sealed and slidably connected to the hydraulic cylinder, the second piston is slidably and sealedly connected to the first working cylinder, and the third piston is slidably and sealedly connected to the second working cylinder. Multiple reversing valves are connected to the machine body in a one-to-one correspondence, and are used to control the reciprocating reversing of the piston assembly in the machine body; The system comprises multiple frequency converters, multiple motors, and multiple oil pumps. The output terminals of the motors are connected to the oil pumps via a drive connection. The oil inlets of the oil pumps are connected to the oil tank, and the oil outlets of the oil pumps are connected to the reversing valves. The frequency converters are connected to the motors via power transmission. Each frequency converter, motor, and oil pump corresponds to another motor. Multiple displacement sensors are mounted on the first end cap, and the detection end of the displacement sensor passes through the first end cap and is connected to the piston assembly; the displacement sensor is signal-connected to the control element and is used to send displacement information of the piston assembly to the control element. The timing unit includes a servo motor, a crankshaft, multiple connecting rods, and multiple sliders. The crankshaft includes multiple crank necks, and the crank necks, connecting rods, and sliders are connected in a one-to-one correspondence. One end of each connecting rod is pivotally connected to a crank neck, and the other end of each connecting rod is pivotally connected to a slider. The sliders are configured to move horizontally reciprocally. The timing unit also includes multiple slide bars, which are configured to move horizontally reciprocally. One end of each slide bar has a first contact portion, and the other end has a second contact portion. When the slider is about to move to the first extreme position, it can contact the first contact part and push the slider rod to move a set distance in the first direction; when the slider is about to move to the second extreme position, it can contact the second contact part and push the slider rod to move a set distance in the second direction. The slide rod is connected to the valve core of the reversing valve in a one-to-one correspondence, and is used to push the reversing valve to switch directions; It also includes multiple timing displacement sensors, the detection ends of which are connected to the slider in a one-to-one correspondence, and the timing displacement sensors are used to send displacement signals of the slider to the control element; A control element is connected to the displacement sensor for receiving the position information sent by the displacement sensor; the control element is also connected to the frequency converter for controlling the start, stop, and speed of the motor via the frequency converter; the control element is connected to the timing displacement sensor; and the control element is connected to the servo motor for controlling the crankshaft speed via the servo motor. The control element is configured to control the speed of the servo motor based on the displacement information of one of the sliders detected by the timing displacement sensor, so that the position of the slider corresponds one-to-one with the position of the piston assembly in the machine body.

2. The high-pressure fluid transfer pump as described in claim 1, characterized in that, The set distance is the same as the sliding distance of the valve core when the reversing valve reverses.

3. The high-pressure fluid transfer pump as described in claim 1, characterized in that, The displacement sensor includes a magnetic ring mounted on the piston assembly.

4. The high-pressure fluid transfer pump as described in claim 1, characterized in that, The crank necks are evenly spaced along the crankshaft axis and uniformly distributed along the circumferential direction.

5. The high-pressure fluid transfer pump as described in claim 1, characterized in that, The first piston is connected to one end of the second piston via a piston rod, and the other end of the second piston is connected to the third piston via a piston rod.

6. The high-pressure fluid transfer pump as described in claim 5, characterized in that, The inner diameter of the first working cylinder is larger than the inner diameter of the second working cylinder.

7. The high-pressure fluid transfer pump as described in claim 6, characterized in that, It also includes an inflow pipe, an intermediate pipe, and an outflow pipe. The inflow pipe is connected to the first working cylinder and is used to input fluid into the first working cylinder. The first working cylinder is connected to the second working cylinder through an intermediate pipe, and the second working cylinder is connected to the outflow pipe.

8. The high-pressure fluid transfer pump as described in claim 7, characterized in that, Inside the first working cylinder, a first cavity is formed on one side of the second piston, and a second cavity is formed on the other side of the second piston; It also includes a first check valve and a second check valve, the outlet of the first check valve being connected to the first cavity, for limiting the unidirectional flow of fluid from the inlet pipe to the first cavity; The outlet of the second check valve is connected to the second cavity, which is used to limit the unidirectional flow of fluid from the inlet pipe to the second cavity.

9. The high-pressure fluid transfer pump as described in claim 7, characterized in that, Inside the second working cylinder, a third cavity is formed on one side of the third piston, and a fourth cavity is formed on the other side of the third piston; It also includes a third check valve, a fourth check valve, a fifth check valve, and a sixth check valve; The input end of the intermediate pipeline is connected to the first cavity through a third one-way valve, which is used to limit the fluid to flow unidirectionally from the first cavity to the intermediate pipeline. The inflow end of the intermediate pipeline is connected to the second cavity through a fourth one-way valve, which is used to limit the unidirectional flow of fluid from the second cavity to the intermediate pipeline. The outlet end of the intermediate pipeline is connected to the third cavity through a fifth one-way valve, which is used to limit the unidirectional flow of fluid from the intermediate pipeline to the third cavity. The outlet end of the intermediate pipeline is connected to the fourth cavity through a sixth one-way valve, which is used to limit the unidirectional flow of fluid from the intermediate pipeline to the fourth cavity.

10. The high-pressure fluid transfer pump as described in claim 9, characterized in that, It also includes a seventh check valve and an eighth check valve. The inlet end of the outflow pipe is connected to the third chamber through a seventh one-way valve, which is used to limit the fluid to flow unidirectionally from the third chamber to the outflow pipe. The inflow end of the outflow pipe is connected to the fourth chamber through an eighth one-way valve, which is used to limit the unidirectional flow of fluid from the fourth chamber to the outflow pipe.

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