Ultrahigh pressure hydraulic pump and hydraulic system based on pressure flow automatic closed loop control

Abstract

The application relates to an ultrahigh-pressure hydraulic pump based on pressure flow automatic closed-loop control and a hydraulic system. The ultrahigh-pressure hydraulic pump based on pressure flow automatic closed-loop control comprises a pump core, a plunger assembly, an inner cam ring, a one-way valve assembly, an oil control assembly and a closed-loop adjusting assembly, realizes compatibility of ultrahigh pressure and wide-range flow regulation, and through mechanical linkage of the closed-loop adjusting assembly and the oil control assembly, the pressure feedback of the total high-pressure oil cavity is ingeniously converted into real-time regulation of the opening degree of an oil inlet hole, wide-range on-demand regulation of the oil inlet amount can be realized under 70MPa-120MPa or even higher pressure. The oil suction amount is automatically reduced at low load, energy waste caused by large oil leakage of a traditional hydraulic system through an overflow valve is avoided, energy consumption is obviously reduced, economic operation of 'on-demand oil supply' is realized, oil temperature rise caused by long-term large flow overflow can be avoided, damage of high temperature to sealing elements and moving pairs is avoided, the oil inlet amount is accurately matched with the output amount, forces of core components are more stable, and reliability is higher.

Description

Technical Field

[0001] This invention relates to the field of hydraulic pump technology, and in particular to an ultra-high pressure hydraulic pump and hydraulic system based on automatic closed-loop control of pressure and flow. Background Technology

[0002] As the core power component of a hydraulic system, the performance of the hydraulic pump directly determines the operational stability and efficiency of the entire hydraulic system. Due to its inherent advantages such as high dynamic ratio and fast response speed, hydraulic technology has been widely used in fields such as engineering machinery, aerospace, shipbuilding, and heavy equipment.

[0003] In recent years, with the continuous improvement of my country's industrial level, the application scenarios of hydraulic systems have become increasingly complex and extreme. In special applications such as large mold clamping, heavy material testing, and aerospace actuators, not only is it required that the hydraulic system have a huge output force, but it is also necessary to strictly control the weight of the whole machine. This has directly driven the demand for ultra-high pressure hydraulic systems. The rated working pressure of the system has developed from the traditional 31.5 MPa and 70 MPa to 120 MPa and even higher levels.

[0004] However, achieving compatibility between ultra-high pressure and wide-range flow regulation within the design framework of traditional hydraulic pumps has always been a technical challenge. Hydraulic pumps are classified into two categories based on whether their output flow is adjustable: fixed-displacement pumps and variable-displacement pumps. Fixed-displacement pumps have no adjustable flow or very limited adjustment range, while traditional variable-displacement pumps have limited adjustment ranges due to their variable mechanism, making it difficult to adapt to the flow requirements of equipment under wide load variations. When the equipment operates under low load, because the flow cannot be precisely controlled, excess flow can only be discharged through the pressure relief valve. The hydraulic pump always operates at full load, generating unnecessary energy consumption. At the same time, this "full load output, partial flow usage" working mode causes a large amount of hydraulic power to be converted into heat energy, resulting in a sharp increase in system oil temperature. Long-term high-flow overflow and high-temperature operation will accelerate the oxidation and deterioration of hydraulic oil, damage seals and precision moving parts, significantly reduce the service life and reliability of the hydraulic pump and the entire hydraulic system, and increase equipment maintenance costs. Summary of the Invention

[0005] Therefore, it is necessary to provide an ultra-high pressure hydraulic pump and hydraulic system with a simple structure, capable of stable operation in ultra-high pressure environments, and with a wide range of flow regulation capabilities, so as to achieve on-demand oil supply and reduce energy consumption, based on pressure and flow automatic closed-loop control.

[0006] An ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow, comprising: The pump core has a plunger hole and an oil inlet hole communicating with the plunger hole on its circumferential side wall and end face wall, respectively; the pump core also has a total high-pressure oil chamber and an oil control hole communicating with the oil inlet hole; a high-pressure channel is provided between the plunger hole and the total high-pressure oil chamber; A plunger assembly includes a plunger structure and a hydraulic elastic element; the plunger structure is slidably and sealingly mounted in the plunger bore; the hydraulic elastic element provides an elastic force to drive the plunger structure to slide in a direction away from the high-pressure channel; the plunger bore is defined as a pressure boosting chamber in the cavity between the plunger structure and the high-pressure channel. The inner cam ring has an inner wall with an alternating concave and convex inner cam surface; the pump core is disposed inside the inner cam ring; the plunger structure abuts against the inner cam surface; the inner cam ring and the pump core are capable of relative rotation. A one-way valve assembly is installed in the high-pressure channel; the one-way valve assembly is configured to open in the forward direction when the oil pressure in the booster chamber exceeds a preset pressure value, allowing the oil in the booster chamber to be discharged through the high-pressure channel into the total high-pressure oil chamber, and to close in the reverse direction when the oil pressure in the booster chamber exceeds a preset pressure value. An oil control component is slidably and sealed within the oil control hole. A closed-loop regulating assembly includes a cylinder body, a double-ended piston with a large piston section and a small piston section at each end, an adjusting elastic element, and a linkage mechanism. The large and small piston sections are both slidably and sealed within the cylinder body to form a large-end oil chamber and a small-end oil chamber within the cylinder body. The end face area of ​​the large piston section is larger than that of the small piston section. The adjusting elastic element provides an elastic force to drive the double-ended piston to slide along the small-end oil chamber towards the large-end oil chamber. Both the large-end and small-end oil chambers are connected to a total high-pressure oil chamber. The double-ended piston is linked to the oil control assembly via the linkage mechanism. The dual-headed piston can reciprocate within the cylinder in response to changes in the oil pressure within the main high-pressure oil chamber, thereby driving the oil control assembly to reciprocate within the oil control hole to adjust the size of the oil inlet hole.

[0007] A hydraulic system includes a drive source and an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow as described above; the drive source is drivenly connected to the inner cam ring and is used to drive the inner cam ring to rotate relative to the pump core.

[0008] The aforementioned ultra-high pressure hydraulic pump and hydraulic system based on pressure-flow closed-loop control achieves compatibility between ultra-high pressure and wide-range flow regulation. With each rotation of the inner cam ring relative to the pump core, the plunger structure, in cooperation with the oil-pressurizing elastic element and the inner cam surface, can achieve multiple oil supplies, resulting in high-flow, ultra-high pressure output. Through the mechanical linkage of the closed-loop adjustment component and the oil control component, the pressure feedback of the total high-pressure oil chamber is cleverly converted into real-time adjustment of the inlet opening. This allows for wide-range, on-demand adjustment of the oil inlet volume at pressures of 70MPa to 120MPa or even higher, overcoming the limitations of traditional pumps with fixed flow rates or small adjustment ranges. The oil inlet volume automatically matches the load demand, automatically reducing the oil suction volume under low loads, avoiding energy waste caused by excessive oil leakage through the relief valve in traditional hydraulic systems, significantly reducing energy consumption, and achieving economical "on-demand oil supply" operation. Simultaneously, it avoids oil temperature rise caused by long-term high-flow overflow, preventing damage to seals and moving parts from high temperatures. Furthermore, the precise matching of the oil inlet volume with the output volume reduces pressure shocks and vibrations, making the core components more stable under stress and increasing reliability. The pressure feedback and flow regulation functions are integrated into one unit, eliminating the need for complex external control valve groups. Its small size and light weight make it ideal for special applications requiring high output force and lightweight operation. Employing pure mechanical hard feedback closed-loop control, it eliminates electrical signal delay, providing instantaneous adjustment during pressure fluctuations. The hydraulic system remains stable on the preset pressure-flow characteristic curve, achieving high-precision automatic and stable control. Attached Figure Description

[0009] Figure 1 This is a schematic diagram of the structure of an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow according to an embodiment of the present invention; Figure 2 for Figure 1 The figure shows a cross-sectional view of an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow. Figure 3 for Figure 1 The diagram shows the structure of the pump core in an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow. Figure 4 for Figure 3 A cross-sectional view of the pump core shown; Figure 5 for Figure 1 The diagram shows the structure of the inner cam ring in an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow. Figure 6 for Figure 1 The diagram shows the installation status of the cylinder, double-ended piston, lever, and ball joint structure in an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow. Figure 7 for Figure 1 The diagram shows the structure of the linkage mechanism in an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow. Figure 8 for Figure 1 The diagram shows the structure of the guide seat in an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow. Figure 9 for Figure 1 The diagram shows the structure of the roller in an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow. Figure 10 for Figure 1 The image shows a cross-sectional view of the sealing ball seat in an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow.

[0010] Reference numerals: 10. Ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow; 100. Pump core; 110. Piston bore; 120. Oil inlet; 130. Main high-pressure oil chamber; 140. Oil control hole; 150. High-pressure channel; 160. Annular groove; 170. Mounting groove; 180. Mounting groove; 200. Piston assembly; 210. Piston structure; 211. Piston body; 212. Guide seat; 2121. Pressure groove; 213. Roller; 2131. Weight reduction through hole; 220. Oil pressure elastic element; 300. Inner cam ring; 310. Inner cam surface; 311. Protruding part; 312. Concave part; 400. One-way valve assembly; 410. Sealing ball seat; 411. Oil drain hole; 4 111. Oil inlet; 4112. Oil outlet; 420. Sealing ball; 430. Oil outlet elastic element; 440. Threaded fastener; 441. Inner hole; 500. Oil control assembly; 510. Oil control tappet; 520. Oil control elastic element; 600. Closed-loop adjustment assembly; 610. Cylinder block; 611. Large end oil chamber; 612. Small end oil chamber; 620. Double-ended piston; 621. Large piston section; 622. Small piston section; 630. Adjustment elastic element; 640. Linkage mechanism; 641. Linkage ring; 6411. Curved groove; 6412. Actuating part; 6413. Cam ring body; 6414. Actuating block; 650. Actuating lever; 660. Ball head structure; 700. Pressure boosting chamber; 800. Support component. Detailed Implementation

[0011] To facilitate understanding of the present invention, a more complete description will be given below with reference to the accompanying drawings. Preferred embodiments of the invention are shown in the drawings. However, the invention can be implemented in many different forms and is not limited to the embodiments described herein. Rather, these embodiments are provided to provide a thorough and complete understanding of the disclosure of the invention.

[0012] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used herein in the description of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0013] When describing positional relationships, unless otherwise specified, when an element is referred to as being "on" another element, it may be directly on the other element or there may be intermediate elements. It is also understood that when an element is referred to as being "between" two elements, it may be the only one between the two elements, or there may be one or more intermediate elements.

[0014] When using the terms “including,” “having,” and “comprising” as described herein, another component may be added unless explicitly qualifying terms such as “only,” “consisting of,” etc. are used. Unless otherwise stated, singular terms may include plural forms and should not be construed as having a quantity of one.

[0015] This invention provides an ultra-high pressure hydraulic pump and hydraulic system based on automatic closed-loop control of pressure and flow. The hydraulic system includes a drive source and an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow. The drive source powers the ultra-high pressure hydraulic pump to provide pressurized oil to the hydraulic system. The drive source can be an electric motor, an internal combustion engine, a starter motor, etc.

[0016] Appendix Figure 1 The structure of an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow is shown in one embodiment of the present invention. Figure 2 The internal structure of an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow is shown in one embodiment. For ease of explanation, the accompanying drawings only show structures relevant to embodiments of the present invention.

[0017] Please see Figure 1 and Figure 2 In a preferred embodiment of the present invention, the ultra-high pressure hydraulic pump 10 based on automatic closed-loop control of pressure and flow includes a pump core 100, a plunger assembly 200, an inner cam ring 300, a one-way valve assembly 400, an oil control assembly 500, and a closed-loop adjustment assembly 600.

[0018] Please refer to the following: Figure 3 and Figure 4The pump core 100 has a plunger hole 110 and an oil inlet hole 120 communicating with the plunger hole 110 on its circumferential side wall and end face wall, respectively. The pump core 100 also has a total high-pressure oil chamber 130 and an oil control hole 140 that communicates with the oil inlet hole 120. A high-pressure channel 150 is provided between the plunger hole 110 and the total high-pressure oil chamber 130.

[0019] The plunger assembly 200 includes a plunger structure 210 and a hydraulic resilient element 220. The plunger structure 210 is slidably mounted in the plunger bore 110. The hydraulic resilient element 220 provides an elastic force to drive the plunger structure 210 to slide in a direction away from the high-pressure channel 150. The cavity in the plunger bore 110 between the plunger structure 210 and the high-pressure channel 150 is defined as a pressurization chamber 700.

[0020] Please refer to the following: Figure 5 The inner wall of the inner cam ring 300 has a ring of alternating concave and convex inner cam surfaces 310. The inner cam surfaces 310 have alternating protruding portions 311 and concave portions 312, and there are multiple of each. To achieve optimal oil supply effect and obtain greater oil supply pressure and quantity, more specifically, the number of protruding portions 311 and concave portions 312 of the inner cam surfaces 310 is 8. Of course, in other embodiments, the number of protruding portions 311 and concave portions 312 of the inner cam surfaces 310 can also be 6, 10, or other numbers. The pump core 100 is disposed within the inner cam ring 300. The plunger structure 210 abuts against the inner cam surface 310. That is, the plunger structure 210 abuts against the inner cam surface 310 under the elastic force of the oil pressure elastic element 220. The inner cam ring 300 and the pump core 100 can rotate relative to each other.

[0021] The one-way valve assembly 400 is installed in the high-pressure channel 150. The one-way valve assembly 400 is configured to open in the forward direction when the oil pressure in the pressure chamber 700 exceeds a preset pressure value, allowing the oil in the pressure chamber 700 to be discharged through the high-pressure channel 150 into the main high-pressure oil chamber 130, and to close in the reverse direction when the oil pressure in the pressure chamber 700 exceeds a preset pressure value.

[0022] Please refer to the following: Figure 6The oil control assembly 500 is slidably and sealed within the oil control port 140. The closed-loop adjustment assembly 600 includes a cylinder body 610, a double-ended piston 620 with a large piston portion 621 and a small piston portion 622 at each end, an adjusting elastic element 630, and a linkage mechanism 640. Both the large piston portion 621 and the small piston portion 622 are slidably and sealed within the cylinder body 610, forming a large-end oil chamber 611 and a small-end oil chamber 612 within the cylinder body 610. The end face area of ​​the large piston portion 621 is larger than that of the small piston portion 622. The adjusting elastic element 630 provides an elastic force to drive the double-ended piston 620 to slide from the small-end oil chamber 612 towards the large-end oil chamber 611. Both the large-end oil chamber 611 and the small-end oil chamber 612 are connected to the main high-pressure oil chamber 130. The double-ended piston 620 is linked to the oil control assembly 500 via the linkage mechanism 640.

[0023] The dual-ended piston 620 can reciprocate within the cylinder 610 in response to changes in oil pressure within the main high-pressure oil chamber 130, thereby driving the oil control assembly 500 to reciprocate within the oil control hole 140 to adjust the size of the oil inlet hole 120. That is, by reciprocating within the oil control hole 140, the oil control assembly 500 can completely, partially, or completely open the oil inlet hole 120, thus changing the effective flow area of ​​the oil inlet hole 120 and adjusting its size.

[0024] In the hydraulic system, the drive source is connected to the inner cam ring 300. The drive source drives the inner cam ring 300 to rotate relative to the pump core 100. As the inner cam ring 300 rotates, the inner cam surface 310 undulates to drive the plunger structure 210 to reciprocate within the plunger bore 110.

[0025] Of course, in other embodiments, the drive source can also be connected to the pump core 100 for driving the pump core 100 to rotate relative to the inner cam ring 300.

[0026] The inner cam surface 310 has alternating concave and convex shapes, resulting in multiple undulations. Therefore, when the inner cam ring 300 rotates one revolution relative to the pump core 100, it can drive the plunger structure 210 to reciprocate multiple times within the plunger hole 110, thereby achieving multiple oil supply and thus realizing high-flow-rate ultra-high-pressure output.

[0027] Through the mechanical linkage of the closed-loop regulating component 600 and the oil control component 500, the pressure feedback of the main high-pressure oil chamber 130 is cleverly converted into real-time adjustment of the opening of the oil inlet 120. When the required flow rate of the hydraulic system changes, the oil pressure in the main high-pressure oil chamber 130 fluctuates accordingly. The double-ended piston 620 utilizes the difference in the area of ​​its two ends (the end face area of ​​the large piston part 621 is larger than the end face area of ​​the small piston part 622) to generate a change in the hydraulic resultant force. In conjunction with the adjusting elastic element 630, the double-ended piston 620 is precisely driven to slide back and forth in the cylinder 610, thereby precisely driving the oil control component 500 to slide. This allows for precise adjustment of the oil inlet volume by adjusting the size of the oil inlet 120, thus achieving flow output across the entire range from 0 to maximum flow. This purely mechanical-hydraulic closed-loop structure enables the hydraulic pump to maintain a pressure of 70MPa to 120MPa or even higher while changing the oil inlet volume over a wide range according to load requirements, thereby breaking through the technical bottleneck of fixed flow rate or extremely small adjustment range in traditional hydraulic pumps.

[0028] Addressing the pain point of "full-load overflow during low-load overflow" mentioned in the background art, this invention achieves automatic matching of oil intake volume with load demand. When the equipment is under low load and the flow rate needs to be reduced, the pressure in the main high-pressure oil chamber 130 increases. In response to this pressure change, the double-ended piston 620 moves along the direction from the large-end oil chamber 611 to the small-end oil chamber 612, thereby driving the oil control component 500 to move towards the main high-pressure oil chamber 130, increasing the shielding of the oil inlet 120 and automatically reducing the oil intake volume. When the equipment load increases and the flow rate needs to be increased, the oil pressure in the main high-pressure oil chamber 130 decreases. In response to this pressure change, the double-ended piston 620 moves along the direction from the small-end oil chamber 612 to the large-end oil chamber 611 under the action of the adjusting elastic element 630, thereby driving the oil control component 500 to move away from the main high-pressure oil chamber 130, reducing the shielding of the oil inlet 120 and automatically increasing the oil intake volume. In this way, the output flow of the hydraulic pump is precisely matched with the load demand. This design fundamentally avoids the energy loss caused by the large amount of overflow through the pressure relief valve in the traditional hydraulic system, so that the hydraulic system function is used efficiently, energy consumption is significantly reduced, and the economical operation of "supplying oil on demand" is achieved.

[0029] Because the aforementioned hydraulic system eliminates the possibility of long-term, high-flow overflow, the temperature rise of the hydraulic fluid inside the system is effectively suppressed. Lower oil temperature means that the hydraulic oil viscosity remains good, making it less prone to oxidation and deterioration. This also reduces thermal damage and wear on precision parts such as seals and moving parts (e.g., check valve assembly 400, plunger structure 210). Furthermore, since the oil control assembly 500 directly adjusts the size of the oil inlet 120, the amount of oil drawn into the plunger structure 210 each time is closer to the actual discharge volume. This reduces pressure shocks caused by repeated compression and expansion of excess oil, resulting in more stable force distribution and more reliable operation of core moving parts such as the pump core 100 and inner cam ring 300, significantly extending the service life of the entire hydraulic pump.

[0030] By integrating pressure feedback and flow regulation functions into a single unit, the aforementioned ultra-high pressure hydraulic pump 10, based on automatic closed-loop control of pressure and flow, eliminates the need for additional complex external control valve groups and sensors, unlike traditional variable displacement systems that require complex external proportional or servo valves. This highly integrated structure allows the ultra-high pressure hydraulic pump 10 to achieve ultra-high pressure and a wide range of variable displacement functions while maintaining a very small size and weight. This perfectly meets the specific requirements of "high output force and light weight" in the background technology, and is suitable for special application scenarios with stringent requirements for high output force and light weight.

[0031] Employing a purely mechanical hard feedback closed-loop control system, the dual-headed piston 620 directly senses the real-time pressure of the main high-pressure oil chamber 130 and instantaneously drives the oil control component 500 to actuate via the linkage mechanism 640. Compared to an electronic control system, this method avoids the time delay between signal acquisition, processing, amplification, and actuator action, resulting in extremely fast pressure-flow response. Furthermore, because the end-face area ratio of the large piston section 621 and the small piston section 622 is fixed, and in conjunction with the pre-pressure of the adjusting elastic element 630, the hydraulic system can always remain stable on the set pressure-flow characteristic curve, achieving high-precision automatic and stable control without manual intervention.

[0032] In addition, in different hydraulic systems, the operating pressure of the equipment may be in different pressure ranges. In this case, the pressure requirements during operation can be met by designing different end face area ratios of the large piston section 621 and the small piston section 622, and by selecting different stiffness coefficients of the adjusting elastic element 630.

[0033] Please refer to it again. Figure 1 and Figure 3 In some embodiments, the oil inlet 120 is a triangular hole. The width of the triangular hole gradually decreases along the axial direction of the control hole 140 in the direction from the plunger hole 110 toward the high-pressure channel 150. Compared with traditional circular or elliptical holes, setting the oil inlet 120 as a triangular hole allows the oil control assembly 500 to achieve linear adjustment when reciprocating within the control hole 140, thus providing more precise control of the oil quantity, which is especially beneficial for stability under low oil quantity conditions. Moreover, the gradually tapering sharp edges of the triangular hole throttle the flow, making the pressure change of the plunger assembly 200 more gradual during the pre-stroke and return phases. Therefore, setting the oil inlet 120 as a triangular hole can significantly reduce noise and vibration.

[0034] Please see Figure 1 , Figure 2 and Figure 7In some embodiments, the linkage mechanism 640 includes a linkage ring 641. The inner wall of the linkage ring 641 has an axially extending curved groove 6411. Therefore, the extending direction of the curved groove 6411 is consistent with the axial direction of the linkage ring 641. The linkage ring 641 is rotatably mounted on the end face wall of the pump core 100, which has an oil inlet hole 120. A toggle part 6412 is provided on the linkage ring 641. A lever 650, movably connected to the toggle part 6412, is provided on the double-ended piston 620. The oil control assembly 500 includes an oil control tap 510 and an oil control elastic element 520. The oil control tap 510 is slidably mounted within the oil control hole 140 and abuts against the inner wall of the curved groove 6411. The oil control elastic element 520 provides an elastic force to drive the oil control tap 510 to move towards the curved groove 6411. Thus, the oil-controlling tappet 510 is held against the inner wall of the curved groove 6411 by the elastic force of the oil-controlling elastic element 520.

[0035] Therefore, when the dual-ended piston 620 moves within the cylinder 610 in response to changes in oil pressure within the main high-pressure oil chamber 130, it actuates the linkage ring 641 via the lever 650. At this time, the inner wall of the curved groove 6411 drives the oil control tappet 510 to slide within the oil control hole 140, thereby adjusting the effective flow area of ​​the oil inlet hole 120 and achieving precise adjustment of the oil intake. By configuring the linkage mechanism 640 as a linkage ring 641 with a curved groove 6411, precise oil volume adjustment is achieved while simplifying the structure of the linkage mechanism 640. This facilitates further miniaturization and weight reduction of the ultra-high-pressure hydraulic pump 10 based on automatic closed-loop control of pressure and flow, resulting in a simpler structure.

[0036] Of course, in other embodiments, the linkage mechanism 640 can also be a crank-connecting rod mechanism, a sine mechanism, a spiral groove mechanism, a gear and rack planetary mechanism, etc., as long as it can drive the oil control tappet 510 to slide synchronously in the oil control hole 140 when the double-headed piston 620 reciprocates in the cylinder 610.

[0037] Furthermore, in some embodiments, the linkage ring 641 is provided with an actuating groove serving as an actuating part 6412. A ball-head structure 660 is formed at the end of the lever 650 away from the double-ended piston 620. The ball-head structure 660 is rotatably clamped within the actuating groove. The cross-section of the actuating groove can be a closed contour (e.g., circular, square, etc.) or an open groove (e.g., U-shaped groove, trapezoidal groove, rectangular groove, etc.). The ball-head structure 660 can be an independent structure fixed to the lever 650 by welding or other means, or it can be an integral structure formed onto the lever 650 by machining or other means. Thus, simply inserting the ball-head structure 660 into the actuating groove achieves a movable connection between the lever 650 and the actuating part 6412, making the assembly and disassembly of the lever 650 and the linkage ring 641 convenient and quick. Moreover, as the double-ended piston 620 reciprocates within the cylinder 610, the ball head structure 660 rotates synchronously within the actuating groove. This ensures a reliable connection between the lever 650 and the linkage ring 641, while also ensuring that the linkage ring 641 has a large rotational stroke, thereby ensuring that the oil control tappet 510 can reliably adjust the oil inlet hole 120.

[0038] Of course, in other embodiments, the actuating part 6412 may also be other structures that can be movably connected to the lever 650 and drive the linkage ring 641 to rotate when the double-headed piston 620 moves. For example, the actuating part 6412 is located in an arc-shaped groove or arc-shaped guide rail formed on the linkage ring 641, and one end of the lever 650 is slidably mounted on the arc-shaped groove or arc-shaped guide rail.

[0039] Furthermore, in some embodiments, two support members 800 are circumferentially spaced on the end face wall of the pump core 100 where the oil inlet hole 120 is provided. Both ends of the cylinder body 610 are fixedly connected to the support members 800 respectively. A toggle block 642 is provided on the linkage ring 641. A toggle groove is formed on the toggle block 642. The toggle block 642, while ensuring a reliable connection between the lever 650 and the linkage ring 641, can reduce the thickness of the linkage ring 641, which is beneficial for further miniaturization and weight reduction of the ultra-high pressure hydraulic pump 10 based on automatic closed-loop control of pressure and flow.

[0040] Of course, in other embodiments, the actuating groove can also be formed directly on the pump core 100.

[0041] Of course, in other embodiments, the cylinder body 610 can be directly mounted on the pump core 100, or it can be fixed on the pump core 100 by other support structures, or it can be mounted on other stationary structures other than the pump core 100.

[0042] Please refer to it again. Figures 1 to 3Furthermore, in some embodiments, an annular groove 160 is formed on the end face wall of the pump core 100 where the oil inlet hole 120 is located. The oil control hole 140 is located inside the pump core 100 and communicates with the annular groove 160. The linkage ring 641 is rotatably installed in the annular groove 160. When installing the linkage ring 641, it is only necessary to place it into the annular groove 160 and make the oil control tap 510 abut against the inner wall of the curved groove 6411, which is convenient and simple to install. Moreover, the annular groove 160 limits the position of the linkage ring 641 on the end face wall of the pump core 100, avoids the probability of the linkage ring 641 wobbling left and right when rotating, improves the rotational stability of the linkage ring 641, improves the accuracy of the oil inlet hole 120 size adjustment, and further improves the accuracy of the oil inlet volume adjustment.

[0043] Furthermore, in some embodiments, there are multiple plunger holes 110, high-pressure channels 150, oil inlets 120, oil control holes 140, plunger assemblies 200, one-way valve assemblies 400, oil control assemblies 500, and curved grooves 6411. The multiple plunger holes 110 and multiple oil inlets 120 are spaced apart circumferentially along the pump core 100 and are radially distributed with the central axis of the pump core 100 as the center. One end of each of the multiple oil inlets 120 is connected to a corresponding plunger hole 110. The multiple oil control holes 140 are cross-connected to each of the multiple oil inlets 120.

[0044] Multiple plunger structures 210 are respectively and correspondingly slidably installed in multiple plunger holes 110, and each abuts against the inner cam curved surface 310. Multiple one-way valve assemblies 400 are respectively and correspondingly installed in multiple high-pressure channels 150. Multiple oil control taps 510 are respectively and correspondingly slidably installed in multiple oil control holes 140, and each abuts against the inner wall of multiple curved grooves 6411.

[0045] When the inner cam ring 300 rotates relative to the pump core 100, multiple plunger structures 210 reciprocate within their respective plunger holes 110. Each plunger structure 210 reciprocates multiple times for each rotation of the inner cam ring 300. This means that each rotation of the inner cam ring 300 results in multiple oil supplies from the multiple plunger structures 210. This further increases the oil supply pressure of the ultra-high pressure hydraulic pump 10 based on automatic closed-loop control of pressure and flow, achieving ultra-high pressure and ultra-large flow oil supply.

[0046] When the pressure in the main high-pressure oil chamber 130 changes, the double-ended piston 620 responds to the pressure change and drives multiple oil control tappets 510 to move in their respective oil control holes 140 through the linkage ring 641, so as to simultaneously adjust the opening of multiple oil inlet holes 120 and realize the rapid adjustment of oil intake.

[0047] Further, in some embodiments, the plunger structure 210 includes a plunger body 211, a guide seat 212, and a roller 213. The plunger body 211 is slidably mounted in the plunger bore 110. The hydraulic elastic element 220 acts on the plunger body 211 to provide an elastic force that drives the plunger body 211 to slide in a direction away from the high-pressure channel 150. The guide seat 212 is slidably mounted in the plunger bore 110 and abuts against the end face of the plunger body 211 away from the high-pressure channel 150. The roller 213 is located at the end of the guide seat 212 away from the plunger body 211 and rolls in contact with the inner cam surface 310. The cavity in the plunger bore 110 between the plunger body 211 and the high-pressure channel 150 is defined as a booster chamber 700.

[0048] The roller 213 is rotatable relative to the guide seat 212 and is held against the inner cam surface 310 by the elastic force of the hydraulic elastic element 220. Therefore, when the inner cam ring 300 rotates relative to the pump core 100, the piston structure 210 moves on the inner cam surface 310 by the roller 213 rolling on the inner cam surface 310, making the movement of the piston structure 210 on the inner cam surface 310 smoother and more flexible, thereby improving the smoothness and reliability of oil supply from the ultra-high pressure hydraulic pump 10 based on automatic closed-loop control of pressure and flow.

[0049] Of course, in other embodiments, the plunger structure 210 may consist only of the plunger body 211, in which case the plunger body 211 is slidably abutted against the inner cam surface 310.

[0050] Please refer to the following: Figure 8 Furthermore, in some embodiments, the inner wall of the plunger bore 110 has an installation groove 170 at the edge away from the high-pressure channel 150. A pressure groove 2121 is formed on the end face of the guide seat 212 opposite to the plunger body 211. The guide seat 212 is slidably mounted in the installation groove 170. The roller 213 is rotatably pressed into the pressure groove 2121 and is partially located within the installation groove 170. The installation groove 170 can be a single type of groove, such as a circular groove or a rectangular groove, or it can be a combination of grooves, such as a groove structure formed by superimposing rectangular and circular grooves (i.e., a rectangular groove is formed in the area where a circular groove is formed, while retaining the characteristics of both rectangular and circular grooves).

[0051] Thus, when installing the plunger structure 210, it is only necessary to insert the plunger body 211 into the plunger hole 110, then insert the guide seat 212 into the mounting groove 170, and then use the elastic force of the hydraulic elastic element 220 to press the roller 213 between the inner wall of the pressure groove 2121 and the inner cam surface 310, and ensure that part of the roller 213 is located in the mounting groove 170, which makes the disassembly and assembly of the plunger structure 210 more convenient and quick, and significantly improves the assembly efficiency of the plunger structure 210.

[0052] Furthermore, when the roller 213 is pressed between the inner wall of the roller groove 2121 and the inner cam surface 310, part of the roller 213 is located in the mounting groove 170, so as to use the mounting groove 170 to axially limit the roller 213 and improve the structural stability of the roller 213 after assembly.

[0053] Of course, in other embodiments, the roller 213 can also be rotatably mounted on the guide seat 212 via a shaft or the like.

[0054] Please refer to the following: Figure 9 Furthermore, in some embodiments, the end face of the roller 213 is provided with a plurality of weight-reducing through holes 2131 spaced apart. These multiple weight-reducing through holes 2131 can be multiple through holes of the same diameter, multiple through holes with partially the same diameter, or multiple through holes of different diameters. The multiple weight-reducing through holes 2131 enable the roller 213 to achieve a lighter weight, thereby allowing the plunger structure 210 to achieve higher speed and acceleration within the plunger bore 110.

[0055] Please refer to it again. Figure 2 and Figure 10 In some embodiments, the one-way valve assembly 400 includes a sealing ball seat 410, a sealing ball 420, and an oil outlet elastic element 430. The sealing ball seat 410 is placed within the high-pressure channel 150. An oil drain hole 411 is provided on the sealing ball seat 410. The oil drain hole 411 has an oil inlet 4111 near the booster chamber 700 and an oil outlet 4112 near the main high-pressure oil chamber 130. The sealing ball 420 is disposed on the oil outlet 4112 side of the sealing ball seat 410. The oil outlet elastic element 430 is used to drive the sealing ball 420 to press against the oil outlet 4112 of the sealing ball seat 410 to form a seal. When the sealing ball 420 presses against the oil outlet 4112 under the action of the oil outlet elastic element 430, the sealing ball 420 can form a one-way seal on the oil outlet 4112. When the pressure of the oil in the pressurization chamber 700 acting on the sealing ball 420 exceeds the preset pressure value (i.e., the opening pressure value), the sealing ball 420 will overcome the elastic force of the oil pressure elastic element 220 and retract towards the total high-pressure oil chamber 130 to open the oil outlet 4112. At this time, the high-pressure oil in the pressurization chamber 700 can be discharged from the oil outlet 4112 and then discharged into the total high-pressure oil chamber 130 through the high-pressure channel 150. Conversely, when the pressure of the oil in the pressurization chamber 700 acting on the sealing ball 420 is insufficient to open the chamber, the sealing ball 420 will remain tightly sealed with the oil outlet 4112, forming a reverse closure.

[0056] Specifically, as the inner cam ring 300 rotates, the plunger structure 210 moves within the plunger hole 110 to close the oil inlet 120. If the plunger structure 210 continues to move from the concave portion 312 of the inner cam surface 310 to the convex portion, high pressure will be formed in the booster chamber 700. Under the action of the hydraulic pressure difference between the two sides, the sealing ball 420 overcomes the elastic force of the oil outlet elastic element 430 and opens the oil passage. When the plunger structure 210 moves from the convex portion to the concave portion 312 of the inner cam surface 310, the plunger structure 210 slides in the direction away from the high pressure channel 150 under the action of the pressure elastic element 220. The volume of the booster chamber 700 increases, and the oil pressure in the booster chamber 700 is less than the oil pressure in the high pressure channel 150. Under the action of the hydraulic pressure difference between the two sides and the elastic force of the oil outlet elastic element 430, the sealing ball 420 will maintain a tight fit with the oil outlet 4112, forming a reverse closure.

[0057] Furthermore, in some embodiments, a mounting groove 180 is formed circumferentially on the inner wall of the high-pressure channel 150 near the end of the booster chamber 700. A sealing ball seat 410 is disposed within the mounting groove 180. A threaded fastener 440 is threadedly connected to the mounting groove 180 to confine the sealing ball seat 410 to the bottom of the mounting groove 180. The threaded fastener 440 has an inner hole 441 for communicating with the booster chamber 700 and the oil drain hole 411. Thus, by tightening the threaded fastener 440, the sealing ball seat 410 can be pressed tightly within the mounting groove 180; when the oil control assembly 500 needs to be removed, only the threaded fastener 440 needs to be unscrewed, and the sealing ball seat 410, sealing ball 420, and oil outlet elastic element 430 can be removed sequentially, improving the ease of disassembly and assembly of the oil control assembly 500.

[0058] In order to ensure that the sealing ball 420 can accurately and reliably seal the oil outlet 4112, in some embodiments, the oil outlet 4112 of the sealing ball seat 410 is further provided in an outwardly expanding conical shape.

[0059] It should be noted that the oil-pressing elastic element 220, the oil-discharging elastic element 430, and the oil-controlling elastic element 520 involved in the above embodiments can all be cylindrical springs, variable diameter springs, rubber-metal composite springs, etc.

[0060] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0061] The embodiments described above are merely illustrative of several implementations of the present invention, and while the descriptions are specific and detailed, they should not be construed as limiting the scope of the invention patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this application, and these all fall within the protection scope of the present invention. Therefore, the protection scope of this invention patent should be determined by the appended claims.

Claims

1. An ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow, characterized in that, include: The pump core has a plunger hole and an oil inlet hole communicating with the plunger hole on its circumferential side wall and end face wall, respectively; the pump core also has a total high-pressure oil chamber and an oil control hole communicating with the oil inlet hole; a high-pressure channel is provided between the plunger hole and the total high-pressure oil chamber; A plunger assembly includes a plunger structure and a hydraulic elastic element; the plunger structure is slidably and sealingly mounted on the plunger bore; the hydraulic elastic element provides an elastic force to drive the plunger structure to slide in a direction away from the high-pressure channel. The plunger orifice between the plunger structure and the high-pressure channel is defined as a pressurization chamber; The inner cam ring has an inner wall with an alternating concave and convex inner cam surface; the pump core is disposed inside the inner cam ring; the plunger structure abuts against the inner cam surface; the inner cam ring and the pump core are capable of relative rotation. A one-way valve assembly is installed in the high-pressure channel; the one-way valve assembly is configured to open in the forward direction when the oil pressure in the booster chamber exceeds a preset pressure value, allowing the oil in the booster chamber to be discharged through the high-pressure channel into the total high-pressure oil chamber, and to close in the reverse direction when the oil pressure in the booster chamber exceeds a preset pressure value. An oil control component is slidably and sealed within the oil control hole. A closed-loop regulating assembly includes a cylinder body, a double-ended piston with a large piston section and a small piston section at each end, an adjusting elastic element, and a linkage mechanism. The large and small piston sections are both slidably and sealed within the cylinder body to form a large-end oil chamber and a small-end oil chamber within the cylinder body. The end face area of ​​the large piston section is larger than that of the small piston section. The adjusting elastic element provides an elastic force to drive the double-ended piston to slide along the small-end oil chamber towards the large-end oil chamber. Both the large-end and small-end oil chambers are connected to a total high-pressure oil chamber. The double-ended piston is linked to the oil control assembly via the linkage mechanism. The dual-headed piston can reciprocate within the cylinder in response to changes in the oil pressure within the main high-pressure oil chamber, thereby driving the oil control assembly to reciprocate within the oil control hole to adjust the size of the oil inlet hole.

2. The ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow as described in claim 1, characterized in that, The oil inlet is a triangular hole; the width of the triangular hole gradually decreases along the axial direction of the oil control hole in the direction from the plunger hole to the high-pressure channel.

3. The ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow as described in claim 1, characterized in that, The linkage mechanism includes a linkage ring; the inner wall of the linkage ring is provided with a curved groove extending along the axial direction; the linkage ring is rotatably mounted on the end wall of the pump core where the oil inlet hole is provided; the linkage ring is provided with a toggle part; the double-headed piston is provided with a lever that is movably connected to the toggle part; The oil control assembly includes an oil control pusher and an oil control elastic element; the oil control pusher is slidably installed in the oil control hole and abuts against the inner wall of the curved groove; the oil control elastic element is used to provide an elastic force to drive the oil control pusher to move in the direction toward the curved groove.

4. The ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow as described in claim 3, characterized in that, The linkage ring is provided with a toggle groove as the toggle part; the end of the lever away from the double-ended piston is formed with a ball head structure; the ball head structure is rotatably clamped in the toggle groove.

5. The ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow as described in claim 4, characterized in that, Two support members are arranged circumferentially on the end face wall of the pump core where the oil inlet hole is located; both ends of the cylinder are fixedly connected to the support members respectively; a toggle block is provided on the linkage ring; a toggle groove is formed on the toggle block.

6. The ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow as described in claim 3, characterized in that, An annular groove is formed on the end face wall of the pump core where the oil inlet is located; the oil control hole is located inside the pump core and communicates with the annular groove; the linkage ring is rotatably installed in the annular groove. And / or, there are multiple plunger holes, high-pressure channels, oil inlets, oil control holes, plunger assemblies, one-way valve assemblies, oil control assemblies, and curved grooves; the multiple plunger holes and multiple oil inlets are all spaced apart circumferentially along the pump core; one end of each of the multiple oil inlets is connected to a corresponding one-to-one connection with the multiple plunger holes; the multiple oil control holes are cross-connected to the multiple oil inlets in a corresponding one-to-one connection. The plurality of plunger structures are respectively sealed and slidably installed in the plurality of plunger holes, and all abut against the inner cam surface; the plurality of one-way valve assemblies are respectively installed in the plurality of high-pressure channels; the plurality of oil control tappets are respectively sealed and slidably installed in the plurality of oil control holes, and abut against the inner wall of the plurality of curved grooves.

7. The ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow as described in claim 3, characterized in that, The plunger structure includes a plunger body, a guide seat, and rollers; the plunger body is slidably mounted in the plunger bore; the hydraulic elastic element acts on the plunger body to provide an elastic force that drives the plunger body to slide in a direction away from the high-pressure channel; the guide seat is slidably mounted in the plunger bore and abuts against the end face of the plunger body away from the high-pressure channel; the rollers are located at the end of the guide seat away from the plunger body and roll in contact with the inner cam surface; the plunger bore, the cavity between the plunger body and the high-pressure channel, is defined as the booster chamber.

8. The ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow as described in claim 7, characterized in that, The inner wall of the plunger hole has an installation groove at the edge away from the high-pressure channel. The end face of the guide seat opposite to the plunger body is formed with a pressure groove; the guide seat is slidably installed in the mounting groove; the roller is rotatably pressed into the pressure groove and is partially located in the mounting groove. And / or, the end face of the roller is provided with a plurality of weight-reducing through holes spaced apart.

9. The ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow as described in claim 1, characterized in that, The one-way valve assembly includes a sealing ball seat, a sealing ball, and an oil outlet elastic element; the sealing ball seat is placed inside the high-pressure channel; the sealing ball seat is provided with an oil drain hole; the oil drain hole has an oil inlet near the booster chamber and an oil outlet near the main high-pressure oil chamber; the sealing ball is disposed on the oil outlet side of the sealing ball seat; the oil outlet elastic element is used to drive the sealing ball to press against the oil outlet of the sealing ball seat to form a seal.

10. The ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow according to claim 9, characterized in that, The high-pressure channel has a circumferentially formed mounting groove on the inner wall near the booster chamber end; the sealing ball seat is disposed in the mounting groove; a threaded fastener is threadedly connected to the mounting groove to restrict the sealing ball seat to the bottom of the mounting groove; the threaded fastener has an inner hole for communicating with the booster chamber and the oil drain hole; And / or, the oil outlet of the sealing ball seat is provided in an outwardly expanding conical shape.

11. A hydraulic system, characterized in that, It includes a drive source and an ultra-high pressure hydraulic pump based on automatic closed-loop control of pressure and flow as described in any one of claims 1 to 10; the drive source is connected to the inner cam ring for driving the inner cam ring to rotate relative to the pump core.

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