A hydraulically driven lubrication plunger pump with continuous oil supply capability

Abstract

This invention discloses a hydraulically driven lubricating piston pump with continuous oil supply capability, relating to the field of piston pump technology. The lubricating piston pump consists of two piston cylinders PL1 and PL2, a shuttle valve SV, an electro-proportional directional valve EV, a pressure reducing valve PR, a damping valve DP, two manual shut-off valves CT1 and CT2, and four check valves CV1, CV2, CV3, and CV4. This hydraulically driven lubricating piston pump with continuous oil supply capability connects the two sets of large and small chambers of the two piston cylinders via an X-shaped pipeline. Thus, when one piston is in an oil suction state, the other piston is necessarily in an oil discharge state, ensuring a continuous flow of lubricating oil at the discharge port A, and vice versa. Through the combined use of the four check valves, the pumping process becomes a continuously supplying flow process, solving the problem of insufficient forward thrust and poor lubrication caused by intermittent oil supply.

Description

Technical Field

[0001] This invention relates to the field of piston pump technology, specifically to a hydraulically driven lubricated piston pump with continuous oil supply capability. Background Technology

[0002] Lubrication plays a crucial role in the operation and maintenance of mechanical equipment. Improving the performance and reliability of the lubrication system is extremely important. In the design and use of the lubrication system, the design of lubrication components, especially the lubrication pumps that are directly driven by the lubrication medium, is of central importance. Currently, the main types of lubrication pumps include manual lubrication pumps, electric lubrication pumps, pneumatic lubrication pumps, and hydraulic lubrication pumps. These lubrication pumps have diverse drive methods and numerous specifications, but the basic structure of most lubrication pumps is that of a plunger type. They rely on the change of plunger volume to achieve oil suction and discharge. This type of plunger lubrication pump has a wide range of media applicability and can drive various grades and specifications of lubricating oils and greases. It has a large flow range, covering lubrication flow requirements of 60-600 mL / min. In particular, its ability to build centralized lubrication makes it widely used in various industrial fields such as machine tools, wind power, rail transportation, and even new energy vehicles. Hydraulic-driven lubrication pumps are also gaining increasingly widespread application due to their ease of automation and intelligentization.

[0003] Existing hydraulically driven lubrication pumps all employ a single plunger and two check valves (one for suction and one for discharge) as their pumping mechanism. Figure 1 As shown, its specific working mechanism is as follows: When solenoid valve Y165 is de-energized, the hydraulic oil in the large chamber of the plunger cylinder flows out through the spring position of the solenoid valve and returns to the return port (T port) pipeline system. Meanwhile, the small chamber of the plunger cylinder, being directly connected to the high-pressure port (P port), directly receives high-pressure oil, driving the plunger to retract. The volume of the plunger cylinder expands, the pressure decreases, and suction is generated. Through the one-way valve CT4, oil is drawn in from the suction port (S port). When the plunger reaches the bottom of the cylinder, completing its stroke, solenoid valve Y165 is energized, and the large (rodless) plunger cylinder... Both the large and small (rod-mounted) chambers are pressurized with oil simultaneously. Under the same pressure, because the area of ​​the large chamber is larger than that of the small chamber, the thrust of the large chamber is greater than that of the small chamber, pushing the plunger upward. The lubricating oil is discharged outward through the one-way valve CT3, thus supplying oil to each lubrication point. However, when the plunger cylinder draws oil, it cannot continuously supply oil to each lubrication point, so the oil supply can only be intermittent. The oil at the front lacks continuous thrust, and the forward momentum in slender pipelines or lubrication points is insufficient, which can easily form obstructions in the pipeline. The amount of lubricating oil cannot be accurately controlled, resulting in an unsuitable amount of lubricating oil, affecting the formation of the lubricating oil film, and causing poor lubrication problems. Moreover, it is inconvenient to adjust and cannot meet the needs of modern equipment automation and intelligence. Summary of the Invention

[0004] To address the shortcomings of existing technologies, this invention provides a hydraulically driven lubricating piston pump with continuous oil supply capability, thus solving the problems mentioned in the background section.

[0005] To achieve the above objectives, the present invention provides the following technical solution: a hydraulically driven lubricating plunger pump with continuous oil supply capability, wherein the lubricating plunger pump consists of two plunger cylinders PL1 and PL2, a shuttle valve SV, an electro-proportional directional valve EV, a pressure reducing valve PR, a damper DP, two manual shut-off valves CT1 and CT2, and four check valves CV1, CV2, CV3, and CV4. The two plunger cylinders PL1 and PL2 are the actuators, and the two sets of large and small chambers of the two plunger cylinders are connected by an X-shaped pipeline, i.e., the small chamber of plunger cylinder PL1 is connected to the large chamber of plunger cylinder PL2, and vice versa. The electro-proportional directional valve EV is the control element, the four check valves CV1, CV2, CV3, and CV4 are auxiliary actuators, the shuttle valve SV and the pressure reducing valve PR are auxiliary control elements, and the damper DP and the two manual shut-off valves CT1 and CT2 are maintenance elements.

[0006] Furthermore, the inner cavity of the plunger cylinder is divided into two diameter dimensions, with the larger diameter cavity being the large cavity and the smaller diameter cavity being the small cavity.

[0007] Furthermore, the hydraulically driven lubrication plunger pump with continuous oil supply capability includes the following operating steps:

[0008] Step 1: When the electro-proportional directional valve EV is de-energized, the valve core moves upward under the spring force and operates in the de-energized state. The high-pressure oil output by the hydraulic pump is supplied to the small chamber of the piston cylinder PL1 through the pressure reducing valve PR and the electro-proportional directional valve EV. At this time, the large chamber of the piston cylinder PL2 is connected to the oil filling port of the electro-proportional directional valve EV. The oil in its chamber returns to the oil tank through the pipeline to unload. The piston moves downward under the pressure of the oil in the small chamber. The volume of the piston cylinder PL1 expands and the pressure decreases, forming a suction force. Through the check valve CV3, the oil is drawn in from the oil suction port, i.e., port S.

[0009] Step 2: When the high-pressure oil enters the small chamber of the plunger cylinder PL1, it will also enter the large chamber of the plunger cylinder PL2 simultaneously. The high-pressure oil pushes the plunger in the plunger cylinder PL2 upward, and discharges the lubricating oil in the cylinder through the one-way valve CV2 and port A.

[0010] Furthermore, the hydraulically driven lubrication plunger pump with continuous oil supply capability also includes the following operating steps:

[0011] Step 3: When the plunger in plunger cylinder PL1 moves down to the bottom, the volume of plunger cylinder PL1 expands to its maximum, and plunger cylinder PL1 draws in lubricating oil to its maximum value during the stroke. At the same time, the plunger in plunger cylinder PL2 rises to the top, and the volume of plunger cylinder PL2 is compressed to its minimum, expelling all the lubricating oil in plunger cylinder PL2. That is, the plunger in plunger cylinder PL1 moves to the bottom dead center of the stroke, and at the same time, the plunger in plunger cylinder PL2 moves to the top dead center of the stroke. At this time, the electro-proportional directional valve EV is energized, and the valve core moves down under the action of electromagnetic attraction and operates at the positive potential.

[0012] Furthermore, the hydraulically driven lubrication plunger pump with continuous oil supply capability also includes the following operating steps:

[0013] Step 4: High-pressure hydraulic oil, energized by the electro-proportional directional valve EV, enters the large chamber of piston cylinder PL1, pushing the piston in PL1 upward. This causes the previously drawn-in lubricating oil to be discharged through port A via check valve CV4. At port A, the lubricating oil discharged from the two piston cylinders merges. Simultaneously, since the two sets of large and small chambers X of the two piston cylinders are connected, high-pressure oil also enters the small chamber of piston cylinder PL2. The piston in piston cylinder PL2 is pushed downward by the oil, continuously expanding the volume of piston cylinder PL2 and creating suction within the chamber. This suction draws in lubricating oil through check valve CV1. Piston cylinder PL1 discharges lubricating oil outward, while piston cylinder PL2 draws in lubricating oil inward, until the piston in piston cylinder PL1 reaches the top dead center of its stroke and the piston in piston cylinder PL2 reaches the bottom dead center of its stroke.

[0014] Furthermore, the hydraulically driven lubrication plunger pump with continuous oil supply capability also includes the following operating steps:

[0015] Step 5: When the two plungers reach their respective stroke dead ends, the electro-proportional directional valve EV is de-energized, the valve core returns to the spring position, and the high-pressure oil re-enters the small chamber of plunger cylinder PL1 and the large chamber of plunger cylinder PL2 to start a new round of oil circulation and pumping.

[0016] Furthermore, the cylinder bodies of the plunger cylinders PL1 and PL2 are welded with a first flange, and the first flange is fixed to a second flange by bolts on the side, and the inner diameter of the second flange is larger than the inner diameter of the first flange.

[0017] Furthermore, a plunger is provided through the inner diameter of the first flange, and the plunger includes a rod and a piston. The end of the rod is threadedly connected to the piston, and the end of the rod away from the piston is connected to an eccentric wheel through a connecting rod. The eccentric wheel is connected to the output end of the motor.

[0018] Furthermore, the outer wall of the rod is fitted with a corrugated sleeve, and the two ends of the corrugated sleeve are fixedly connected to the inner side of the second flange and the piston surface by bolts, respectively.

[0019] Furthermore, a ring-shaped movable ball is embedded in the inner diameter of the second flange, and a groove adapted to the movable ball is opened on the surface of the rod body, and the length of the groove is adapted to the stroke of the piston. An injection port is opened on the outer side of the second flange, and the injection port is connected to the embedded cavity of each movable ball through a pipe channel opened inside the second flange. An inlet and outlet air duct is also provided on the outer side of the second flange, and a wind speed detection sensor is provided on the outer surface of the inlet and outlet air duct. Moreover, the air circulation channel inside the inlet and outlet air duct is connected to the inside of the corrugated sleeve.

[0020] This invention provides a hydraulically driven lubrication plunger pump with continuous oil supply capability, which has the following beneficial effects:

[0021] 1. This hydraulically driven lubricating piston pump with continuous oil supply capability connects two sets of large and small chambers of two piston cylinders through an X-shaped pipeline. This transforms the intermittent oil suction and pumping process of a single piston into a continuous flow process. Thus, when one piston is in the suction state, the other piston is necessarily in the discharge state, ensuring a continuous flow of lubricating oil at discharge port A. Conversely, the suction state is also continuous, maintaining a constant suction state. This is because when one piston is in the discharge state, the other is necessarily in the suction state. Furthermore, the combined use of four check valves ensures that the suction and discharge of the two pistons do not interfere with each other, allowing them to complete independently while cooperating with each other. This transforms the pumping process into a continuous flow process, solving the problem of insufficient thrust and poor lubrication caused by intermittent oil supply, resulting in insufficient forward momentum in the pipeline or lubrication point.

[0022] 2. This hydraulically driven lubricated plunger pump with continuous oil supply capability features movable balls in the inner diameter of the second flange that roll along the grooves on the surface of the rod, which reciprocates at high frequency, during piston movement. This transforms sliding friction into rolling friction, significantly reducing friction. Furthermore, the bellows sleeve extends and retracts with the piston movement, ensuring that the inner diameter of the second flange is always enclosed within the bellows sleeve and not connected to the cylinder cavity, thus guaranteeing a sealing effect. The extension and retraction of the rod does not require sliding contact with the sealing ring, preventing wear and leakage caused by long-term friction while maintaining a tight seal. The pump also monitors the exhaust air velocity generated by the bellows sleeve's extension and retraction in real time to determine its status. When the velocity falls below a threshold, the pump alerts the operator to replace the bellows sleeve promptly, preventing long-term deformation and fatigue that could damage the seal. Additionally, lubricating oil can be periodically injected through the inlet. As the movable balls roll, the oil adheres to their surfaces and is then deposited onto the moving grooves, effectively ensuring the stability and smoothness of the pump plunger's movement. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the principle of an existing single-plunger pump;

[0024] Figure 2 This is a schematic diagram of the principle of the electro-proportional directional valve EV of a hydraulically driven lubricating piston pump with continuous oil supply capability under the de-energized state.

[0025] Figure 3 This is a schematic diagram of the principle of the electro-proportional directional valve EV of a hydraulically driven lubricating piston pump with continuous oil supply capability under the energized state.

[0026] Figure 4 This is a cross-sectional view of the cylinder block of a hydraulically driven lubricating piston pump with continuous oil supply capability according to the present invention.

[0027] Figure 5 This is a schematic diagram of the bellows sleeve structure of a hydraulically driven lubricating plunger pump with continuous oil supply capability according to the present invention.

[0028] Figure 6 This is a schematic diagram of the second flange structure of a hydraulically driven lubricating plunger pump with continuous oil supply capability according to the present invention.

[0029] Figure 7 This invention relates to a hydraulically driven lubricating piston pump with continuous oil supply capability. Figure 6 Enlarged structural diagram at point A in the middle. Detailed Implementation

[0030] The embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and examples. The following examples are for illustrative purposes only and should not be construed as limiting the scope of the invention.

[0031] like Figures 2-3 As shown, the present invention provides a technical solution: a hydraulically driven lubricating plunger pump with continuous oil supply capability. The lubricating plunger pump consists of two plunger cylinders PL1 and PL2, a shuttle valve SV, an electro-proportional directional valve EV, a pressure reducing valve PR, a damping valve DP, two manual shut-off valves CT1 and CT2, and four check valves CV1, CV2, CV3, and CV4. The two plunger cylinders PL1 and PL2 are the actuators. The two sets of large and small chambers of the two plunger cylinders are connected by an X-shaped pipeline, i.e., the small chamber of plunger cylinder PL1 is connected to the large chamber of plunger cylinder PL2, and vice versa. The electro-proportional directional valve EV is the control element, the four check valves CV1, CV2, CV3, and CV4 are auxiliary actuators, the shuttle valve SV and the pressure reducing valve PR are auxiliary control elements, and the damping valve DP and the two manual shut-off valves CT1 and CT2 are maintenance elements. The inner cavity of the plunger cylinder is divided into two diameter dimensions, with the larger diameter cavity being the large cavity and the smaller diameter cavity being the small cavity.

[0032] Step 1: When the electro-proportional directional valve EV is de-energized, the valve core moves upward under the spring force and operates in the de-energized state. The high-pressure oil output by the hydraulic pump is supplied to the small chamber of the piston cylinder PL1 through the pressure reducing valve PR and the electro-proportional directional valve EV. At this time, the large chamber of the piston cylinder PL2 is connected to the oil filling port of the electro-proportional directional valve EV. The oil in its chamber returns to the oil tank through the pipeline to unload. The piston moves downward under the pressure of the oil in the small chamber. The volume of the piston cylinder PL1 expands and the pressure decreases, forming a suction force. Through the check valve CV3, the oil is drawn in from the oil suction port, i.e., port S.

[0033] Step 2: When the high-pressure oil enters the small chamber of the plunger cylinder PL1, it will also enter the large chamber of the plunger cylinder PL2 simultaneously. The high-pressure oil pushes the plunger in the plunger cylinder PL2 upward, and discharges the lubricating oil in the cylinder through the one-way valve CV2 and port A.

[0034] Step 3: When the plunger in plunger cylinder PL1 moves down to the bottom, the volume of plunger cylinder PL1 expands to its maximum, and plunger cylinder PL1 draws in lubricating oil to its maximum value during the stroke. At the same time, the plunger in plunger cylinder PL2 rises to the top, and the volume of plunger cylinder PL2 is compressed to its minimum, expelling all the lubricating oil in plunger cylinder PL2. That is, the plunger in plunger cylinder PL1 moves to the bottom dead center of the stroke, while the plunger in plunger cylinder PL2 moves to the top dead center of the stroke. At this time, the electro-proportional directional valve EV is energized, and the valve core moves down under the action of electromagnetic attraction and operates at the positive potential.

[0035] Step 4: High-pressure hydraulic oil is energized by the electro-proportional directional valve EV and enters the large chamber of piston cylinder PL1, pushing the piston in piston cylinder PL1 to move upward. The lubricating oil drawn in earlier is discharged through port A via check valve CV4. At port A, the lubricating oil discharged from the two piston cylinders merges. At the same time, since the two sets of large and small chambers X of the two piston cylinders are connected, high-pressure oil is also synchronously introduced into the small chamber of piston cylinder PL2. The piston in piston cylinder PL2 is pushed downward by the oil, and the volume of piston cylinder PL2 continuously expands, forming a suction force in the chamber. The lubricating oil is drawn in through check valve CV1. Piston cylinder PL1 discharges lubricating oil outward, and piston cylinder PL2 draws in lubricating oil inward, until the piston in piston cylinder PL1 reaches the top dead center of its stroke and the piston in piston cylinder PL2 reaches the bottom dead center of its stroke.

[0036] Step 5: When the two plungers reach their respective stroke dead ends, the electro-proportional directional valve EV is de-energized, the valve core returns to the spring position, and the high-pressure oil re-enters the small chamber of plunger cylinder PL1 and the large chamber of plunger cylinder PL2 to start a new round of oil circulation and pumping.

[0037] Based on the above description, this invention connects the two sets of large and small chambers of two plunger cylinders through an X-shaped pipeline, transforming the existing intermittent oil suction and pumping process of a single plunger into a continuous flow process. Thus, when one plunger is in the oil suction state, the other plunger is necessarily in the oil discharge state, ensuring a continuous flow of lubricating oil at the discharge port A. Conversely, the same applies to the oil suction state, maintaining a continuous oil suction state. This is because when one plunger is in the oil discharge state, the other is necessarily in the oil suction state. Furthermore, the combined use of four one-way valves ensures that the oil suction and discharge of the two plungers do not interfere with each other, allowing them to complete independently while cooperating with each other. This transforms the oil pumping process into a continuous flow process, solving the problem of insufficient forward thrust and poor lubrication caused by intermittent oil supply.

[0038] like Figures 4-7 As shown, the cylinder bodies 1 of plunger cylinders PL1 and PL2 are welded with a first flange 2, and a second flange 3 is fixed to the first flange 2 by bolts on its side. The inner diameter of the second flange 3 is larger than that of the first flange 2. A plunger passes through the inner diameter of the first flange 2, and the plunger includes a rod 4 and a piston 5. The end of the rod 4 is threadedly connected to the piston 5, and the end of the rod 4 away from the piston 5 is connected to an eccentric wheel through a connecting rod. The eccentric wheel is connected to the output end of the motor. A bellows sleeve 6 is fitted on the outer wall of the rod 4, and the two ends of the bellows sleeve 6 are fixed to the inner side of the second flange 3 and the surface of the piston 5 by bolts, respectively. Next, a movable ball 7 is embedded in the inner diameter of the second flange 3 in an annular shape. The end of the rod 4 is threadedly connected to the piston 5. The surface of the rod 4 is provided with a groove 8 that is adapted to the movable ball 7, and the length of the groove 8 is adapted to the stroke of the piston 5. The end of the rod 4 is threadedly connected to the piston 5. The outer side of the second flange 3 is provided with an injection port 9, and the injection port 9 is connected to the embedded cavity of each movable ball 7 through a pipe diameter channel opened inside the second flange 3. The end of the rod 4 is threadedly connected to the piston 5. The outer side of the second flange 3 is also provided with an inlet and outlet air duct 10, and the outer surface of the inlet and outlet air duct 10 is provided with a wind speed detection sensor 11. Moreover, the air circulation channel inside the inlet and outlet air duct 10 is connected to the inside of the corrugated sleeve 6.

[0039] The specific operation is as follows: In existing plunger pumps, the plunger rod 4 is prone to frequent sliding friction with the sealing ring in the plunger hole on the surface of the cylinder 1 due to its extension and retraction, which leads to severe wear of the sealing ring and leakage of fluid inside the cavity. In this invention, when the rod 4 and piston 5 move, the movable ball 7 in the inner diameter of the second flange 3 rolls along the sliding groove 8 on the surface of the rod 4, which moves at a high frequency. This transforms sliding friction into rolling friction, thereby greatly reducing friction. At the same time, since the outer wall of the rod 4 is fitted with a bellows sleeve 6, and the two ends of the bellows sleeve 6 are fixedly connected to the inner side of the second flange 3 and the surface of the piston 5 by bolts, the bellows sleeve 6 extends and retracts with the rod 4 when the piston moves. This keeps the inner diameter of the second flange 3 inside the bellows sleeve 6, so that it is not connected to the inner cavity of the cylinder 1, thus ensuring the sealing effect.

[0040] Simultaneously, as the bellows sleeve 6 expands and contracts, it draws in and discharges outside air along the inside of the inlet and outlet air duct 10. The wind speed during exhaust is monitored in real time by the wind speed detection sensor 11. Based on the constant expansion and contraction of the rod body 4 and the bellows sleeve 6 remaining intact, the wind speed during exhaust remains constant. If the wind speed during exhaust is detected to drop beyond the threshold, it indicates that the bellows sleeve 6 has undergone deformation fatigue damage. At this time, the pump oil operation is immediately notified. By disassembling the second flange 3 and extending the rod body 4, the connection points at both ends of the bellows sleeve 6 can be exposed. Thus, a new bellows sleeve 6 can be quickly replaced by removing and installing bolts. This operation method facilitates the replacement of a new bellows sleeve 6 used for sealing.

[0041] Furthermore, a fixed amount of lubricating oil is periodically injected into the injection port 9. The lubricating oil flows along the internal pipe diameter channel of the second flange 3 to the embedded cavity of each movable ball 7. As the movable ball 7 rolls, it can attach lubricating oil to its surface and attach it to the moving slide groove 8, thereby lubricating the rolling of the movable ball 7 and the extension and retraction of the rod 4 to maintain smooth operation.

[0042] Based on the above description, when the rod 4 and piston 5 perform piston movement, the movable ball 7 in the inner diameter of the second flange 3 rolls along the groove 8 on the surface of the rod 4, which reciprocates at a high frequency. This transforms sliding friction into rolling friction, thereby greatly reducing friction. Furthermore, the bellows sleeve 6 extends and retracts with the piston movement, ensuring that the inner diameter of the second flange 3 is always enclosed within the bellows sleeve 6 and not connected to the inner cavity of the cylinder 1, thus guaranteeing a sealing effect. Therefore, the extension and retraction of the rod 4 does not require sliding contact with the sealing ring, thus ensuring a tight seal. In the case of sealing, long-term friction causes wear and leakage problems. The exhaust wind speed generated by the expansion and contraction of the bellows sleeve 6 is monitored in real time to determine the real-time status of the bellows sleeve 6. When the wind speed is lower than the threshold, the staff is prompted to replace the bellows sleeve 6 in time to avoid long-term deformation fatigue and damage to the bellows sleeve 6, which would affect the sealing performance. Moreover, lubricating oil can be injected periodically through the injection port 9. As the moving ball 7 rolls, the lubricating oil can be attached to its surface and then to the moving slide groove 8, thereby effectively ensuring the stability and smoothness of the pump body plunger movement.

[0043] The embodiments of the present invention are given for illustrative and descriptive purposes only, and are not intended to be exhaustive or to limit the invention to the forms disclosed. Many modifications and variations will be apparent to those skilled in the art. The embodiments were chosen and described in order to better illustrate the principles and practical application of the invention, and to enable those skilled in the art to understand the invention and to design various embodiments with various modifications suitable for a particular purpose.

Claims

1. A hydraulic drive lubricated piston pump with continuous oil supply capability, characterized in that: The lubricating plunger pump is composed of two plunger cylinders PL1 and PL2, a shuttle valve SV, an electric proportional reversing valve EV, a pressure reducing valve PR, a damper DP, two manual cut-off valves CT1 and CT2, and four check valves CV1, CV2, CV3 and CV4, wherein the two plunger cylinders PL1 and PL2 are execution elements, two groups of large and small cavities of the two plunger cylinders are connected through an X-shaped pipeline, i.e. the small cavity of the plunger cylinder PL1 is connected with the large cavity of the plunger cylinder PL2, and the large cavity of the plunger cylinder PL1 is connected with the small cavity of the plunger cylinder PL2, the electric proportional reversing valve EV is a control element, the four check valves CV1, CV2, CV3 and CV4 are auxiliary execution elements, the shuttle valve SV and the pressure reducing valve PR are auxiliary control elements, and the damper DP and the two manual cut-off valves CT1 and CT2 are maintenance elements. The input end of the electric proportional reversing valve EV is connected with the output end of the pressure reducing valve PR, the input end of the pressure reducing valve PR is connected with the output end of a hydraulic pump, the output oil paths of the electric proportional reversing valve EV are respectively connected with the small cavity and the large cavity of the plunger cylinder PL1, and the oil return port of the electric proportional reversing valve EV is connected with an oil tank through a pipeline; one end of the check valve CV1 is connected with the oil tank, and the other end of the check valve CV1 is respectively connected with the check valve CV2, the plunger cylinder PL2 and the manual cut-off valve CT1; one end of the check valve CV3 is connected with the oil tank, and the other end of the check valve CV3 is connected with the check valve CV4, the plunger cylinder PL1 and the manual cut-off valve CT2; the other end of the check valve CV2 is connected with a discharge port A, and the other end of the check valve CV4 is connected with the discharge port A; the shuttle valve SV is connected with the small cavity and the large cavity of the plunger cylinder PL1; one end of the damper DP is connected with the manual cut-off valves CT1 and CT2, and the other end of the damper DP is connected with the input end of the pressure reducing valve PR.

2. A hydraulic drive lubricating piston pump with continuous oil supply capability according to claim 1, characterized in that: The inner cavity of the plunger cylinder is divided into two cavities with different diameters, wherein the cavity with a larger diameter is a large cavity, and the cavity with a smaller diameter is a small cavity.

3. The hydraulic driven lubrication piston pump with continuous oil supply capacity according to claim 1, characterized in that: The hydraulic lubricating plunger pump with continuous oil supply capacity comprises the following working step processes: Step one: the electric proportional reversing valve EV is powered off, the valve core moves upward under the action of the spring thrust, works in the power-off position, and high-pressure oil output by a hydraulic pump is supplied to the small cavity of the plunger cylinder PL1 through the pressure reducing valve PR and the electric proportional reversing valve EV; at this time, the large cavity of the plunger cylinder PL2 is connected with the oil inlet of the electric proportional reversing valve EV, and the oil in the cavity is returned to the oil tank through a pipeline to unload; the plunger moves downward under the action of the oil pressure in the small cavity, the volume of the plunger cylinder PL1 expands, the pressure decreases, and suction is formed, and oil is sucked into the suction port S through the check valve CV3; Step two: when the high-pressure oil enters the small cavity of the plunger cylinder PL1, the high-pressure oil also enters the large cavity of the plunger cylinder PL2 at the same time, the high-pressure oil pushes the plunger in the plunger cylinder PL2 to move upward, and the lubricating oil in the cylinder is discharged through the check valve CV2 and the discharge port A.

4. The hydraulic driving lubricating plunger pump with continuous oil supply capacity according to claim 3, characterized in that: The hydraulic lubricating plunger pump with continuous oil supply capacity further comprises the following working step processes: Step three: when the plunger in the plunger cylinder PL1 is lowered to the bottom, the volume of the plunger cylinder PL1 expands to the maximum, the plunger cylinder PL1 absorbs lubricating oil to the maximum value in the stroke, and the plunger in the plunger cylinder PL2 is lifted to the top, the volume of the plunger cylinder PL2 is compressed to the minimum, and all the lubricating oil in the plunger cylinder PL2 is discharged, that is, the plunger in the plunger cylinder PL1 runs to the lower stop point of the stroke, and the plunger in the plunger cylinder PL2 runs to the upper stop point of the stroke; at this time, the electric proportional directional valve EV is powered on, and the spool is lowered under the action of electromagnetic attraction and works in the powered position.

5. A hydraulic drive lubrication piston pump with continuous oil supply capability according to claim 4, characterized in that: The hydraulic drive lubricating plunger pump with continuous oil supply capability further comprises the following working step process: Step four: high-pressure hydraulic oil enters the large cavity of the plunger cylinder PL1 from the powered position of the electric proportional directional valve EV, pushes the plunger in the plunger cylinder PL1 upward, discharges the lubricating oil absorbed before through the one-way valve CV4 and port A, and discharges the lubricating oil from the two plunger cylinders through port A, and at the same time, the small cavity of the plunger cylinder PL2 is also filled with high-pressure oil due to the connection of the two groups of cavities X of the two plunger cylinders, the plunger in the plunger cylinder PL2 is pushed downward by the oil, the volume of the plunger cylinder PL2 continuously expands, a suction force is formed in the cavity, the lubricating oil is sucked in through the one-way valve CV1, the lubricating oil is discharged out of the plunger cylinder PL1, and the lubricating oil is sucked into the plunger cylinder PL2, until the plunger in the plunger cylinder PL1 runs to the upper stop point of the stroke, and the plunger in the plunger cylinder PL2 runs to the lower stop point of the stroke.

6. A hydraulic driving lubricating plunger pump with continuous oil supply capacity according to claim 5, characterized in that: The hydraulic drive lubricating plunger pump with continuous oil supply capability further comprises the following working step process: Step five: after the two plungers respectively reach the stop points of the strokes, the electric proportional directional valve EV is de-energized, the spool works in the spring position again, high-pressure oil enters the small cavity of the plunger cylinder PL1 and the large cavity of the plunger cylinder PL2 again to start a new cycle of oil absorption and pumping.

7. A hydraulic driven lubrication piston pump with continuous oil supply capacity according to claim 6, characterized in that: The first flange (2) is welded at the end of the cylinder body (1) of the plunger cylinder PL1 and the second flange (3) is fixed on the side of the first flange (2) through bolts, and the inner diameter of the second flange (3) is larger than that of the first flange (2).

8. A hydraulic driving lubricating plunger pump with continuous oil supply capacity according to claim 7, characterized in that: The plunger is arranged in the inner diameter of the first flange (2), and the plunger comprises a rod body (4) and a piston (5), the end of the rod body (4) is threadedly connected with the piston (5), one end of the rod body (4) away from the piston (5) is connected with an eccentric wheel through a connecting rod, and the eccentric wheel is connected to the output end of the motor.

9. The hydraulic driven lubrication piston pump with continuous oil supply capacity according to claim 8, characterized in that: The outer wall of the rod body (4) is sleeved with a bellows sleeve (6), and the two ends of the bellows sleeve (6) are fixedly connected to the inner side of the second flange (3) and the surface of the piston (5) through bolts.

10. The hydraulic drive lubrication piston pump with continuous oil supply capacity according to claim 9, characterized in that: The inner diameter of the second flange (3) is annularly embedded with movable balls (7), the surface of the rod body (4) is provided with sliding grooves (8) matched with the movable balls (7), the length of the sliding grooves (8) is matched with the stroke of the piston (5), the outer side of the second flange (3) is provided with an injection inlet (9), the injection inlet (9) is communicated with the embedding cavities of the movable balls (7) through the pipe diameter channel provided in the inner part of the second flange (3), the outer side of the second flange (3) is further provided with an air inlet and outlet cylinder (10), the outer surface of the air inlet and outlet cylinder (10) is provided with a wind speed detection sensor (11), and the air circulation channel in the air inlet and outlet cylinder (10) is communicated with the inner part of the bellows sleeve (6).

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