Main / pre-boost integrated system based on dual-motion freedom piston pump

Abstract

The present invention provides a main / pre-boost integrated system, which can solve the technical problems existing in the fuel supply system of existing aircraft. The system comprises: a cooling electric pump and a dual-motion freedom piston pump main / pre-boost electric pump, which are respectively connected to the fuel tank; the electric pump comprises a second driving part and a main / pre-boost integrated dual-motion freedom piston pump, the latter comprises a reducer and a dual-motion freedom piston pump, the pump core of the dual-motion freedom piston pump adopts an upper / lower two-pump core integrated series structure, including a first and a second piston structure, the first and the second piston structures both adopt an integrated structure of a piston and a cam guide rail, the cam guide rail is located in the middle of the piston, and two sleeve structures grow symmetrically on both sides of the cam guide rail, for any sleeve structure, it comprises an outer and an inner cylinder, and a plurality of oil discharge ports and oil suction ports are respectively opened on the outer and inner cylinders in a circumferential direction; the reducer is rotatably connected to the transmission shaft assembly, and the second driving part drives the dual-motion freedom piston pump to operate through the reducer.

Description

Technical Field

[0001] The present invention belongs to the technical field of boosting, and relates to a main / pre-boosting integrated system based on a dual-motion-freedom piston pump. Background Art

[0002] Weight reduction and energy conservation are the eternal development direction of aircraft. As the main energy consumption system of aircraft, lightweight and efficient fuel supply system is crucial to reducing the weight of energy batteries and improving aircraft payload and performance indicators.

[0003] At present, the fuel supply system of an aircraft generally consists of a pre-boost electric pump, a main electric pump, a piping system, etc. The pre-boost electric pump consists of a drive motor and a centrifugal pump, and the main electric pump consists of a main drive motor and a gear pump. Figure 24 As shown in the figure, during operation, fuel is pumped from the fuel tank, pressurized by the pre-boost electric pump, and then divided into two paths. One path flows to the main boost electric pump, where it is delivered to the engine for combustion via a gear pump. The other path flows to equipment requiring cooling, where it cools the equipment before returning to the fuel tank. To maximize the efficiency of the centrifugal pump, the pre-boost electric pump typically operates at a constant, high flow rate. However, because engine fuel consumption is significantly greater than equipment cooling, and its flow rate is adjusted over a wide range depending on engine conditions, when the engine is operating at low flow (i.e., low fuel consumption), excess flow after the pre-boost pump returns to the pre-boost pump via the overflow circuit, resulting in power loss. Furthermore, as the aircraft's flight progresses, the fuel temperature in the fuel tank gradually increases, and its viscosity decreases. Under these high-temperature and high-pressure conditions, the gear pump (main pump) experiences increased internal leakage, sharply decreasing its volumetric efficiency. This reduces overall system efficiency and increases energy consumption, further impacting aircraft performance. Summary of the Invention

[0004] The present invention aims to solve at least one of the technical problems existing in the prior art.

[0005] To this end, the present invention provides a main / pre-boost integrated system.

[0006] The technical solution of the present invention is to provide a main / pre-boost integrated system, which includes a device to be cooled and an engine. In addition, the system also includes:

[0007] a fuel tank storing fuel;

[0008] The cooling electric pump and the dual-motion freedom piston pump main / pre-boost electric pump are respectively connected to the oil tank; the dual-motion freedom piston pump main / pre-boost electric pump includes a second drive unit and a main / pre-boost integrated dual-motion freedom piston pump, the main / pre-boost integrated dual-motion freedom piston pump includes a reducer and a dual-motion freedom piston pump, the dual-motion freedom piston pump includes a front end cover, a pump housing and a rear end cover, a drive shaft assembly and a pump core, the front end cover, the pump housing and the rear end cover are fixedly connected in sequence to form a pump housing structure; the pump core is arranged in the pump housing structure and is rotatably arranged on the drive shaft assembly, the pump core adopts an upper / lower two-pump core integrated series structure, the series structure includes a first piston structure and a second piston structure, the two are rotatably arranged on the drive shaft assembly at intervals along the axial direction of the drive shaft assembly. , the first piston structure and the second piston structure both adopt an integrated structure of piston and cam guide, the cam guide is located in the middle of the piston, and two sleeve structures are symmetrically grown on both sides of the cam guide, for any sleeve structure, it includes an outer cylinder and an inner cylinder located in the outer cylinder, the outer cylinder is circumferentially provided with a plurality of oil suction ports, the inner cylinder is circumferentially provided with a plurality of oil discharge ports, and any oil suction ports and any oil discharge ports are staggered; an annular cavity is formed between the outer cylinder and the inner cylinder, the annular cavities of the two sleeve structures are not connected, and the inner cylinders on both sides are connected to form an inner cavity of the piston structure; the reducer is rotatably connected to the transmission shaft assembly, and the second driving part drives the dual-motion freedom piston pump to operate through the reducer, so that the piston pump operates in a suitable working range, and the dual-motion freedom piston pump relies on its own self-priming ability to achieve fuel filling in the cavity;

[0009] In which, the system has a first oil circuit and a second oil circuit. The first oil circuit is a cooling oil circuit. The fuel in the fuel tank is transported to the cooling electric pump, which is pressurized by the cooling electric pump and transported to the equipment to be cooled. After the fuel cools the equipment to be cooled, it returns to the fuel tank; the second oil circuit is an engine oil supply and delivery circuit. The fuel in the fuel tank is transported to a dual-motion degree of freedom piston pump, which is then transported to the engine for combustion.

[0010] Furthermore, the cooling electric pump supplies the fuel flow required by the equipment to be cooled at a constant speed.

[0011] Furthermore, the cooling electric pump includes a centrifugal pump and a first driving unit, wherein the first driving unit drives the centrifugal pump to pressurize the fuel and deliver it to the equipment to be cooled.

[0012] Furthermore, the reducer housing is fixedly connected to the pump housing structure of the dual-motion freedom piston pump, the reducer housing cavity is connected to the oil cavity of the dual-motion freedom piston pump, and the structure in the reducer cavity is immersed in the fuel.

[0013] Furthermore, the output shaft of the reducer is connected to the dual-motion-freedom piston pump drive shaft assembly, and the input shaft of the reducer and the drive shaft assembly are in an "I" shape or a "T" shape.

[0014] Furthermore, the reducer is a planetary gear reducer, or the reducer is a bevel gear reducer.

[0015] Furthermore, the first driving part is a driving motor, and the second driving part is a high-speed driving motor.

[0016] Furthermore, the series structure also includes a first bushing, a second bushing and a pump core support frame. The first bushing, the first piston structure, the pump core support frame, the second piston structure, and the second bushing are coaxially arranged along the axis of the transmission shaft assembly in sequence. The first bushing and the second bushing both include a baffle and a bushing sleeve arranged on the baffle. The bushing sleeve consists of a bushing outer tube and a bushing inner tube located in the bushing outer tube. An annular cavity is formed between the bushing inner and outer tubes. The bushing sleeve is evenly distributed with multiple oil distribution ports along the circumference. Any of the oil distribution ports passes through the bushing outer tube and the bushing inner tube at the same time. The baffle has an inner hole passing through the baffle, and the inner hole is connected to the bushing inner tube to form an inner cavity of the bushing. ; The pump core support frame adopts an integrated cylinder structure, including a pump core support frame body, the pump core support frame body is fixedly connected to the pump housing, an oil discharge channel is opened inside the pump core support frame body, and a first support arm bushing assembly and a second support arm bushing assembly grow out of both ends of the pump core support frame body respectively, and the two components are arranged at a preset angle. The first support arm bushing assembly is composed of a first support arm assembly and a first bracket sleeve, and the second support arm bushing assembly is composed of a second support arm assembly and a second bracket sleeve. The first bracket sleeve and the second bracket sleeve have the same structure as the bushing sleeve, wherein the inner tube of the first bracket sleeve and the inner tube of the second bracket sleeve are both connected to the oil discharge channel to constitute the inner cavity of the pump core support frame;

[0017] Among them, the first bushing, the first piston structure and the first support arm bushing assembly cooperate with each other, the second bushing, the second piston structure and the second support arm bushing assembly cooperate with each other, the piston structure is arranged between the corresponding bushing and the support arm bushing assembly, and the inner cavities of the first bushing, the first piston structure, the pump core support frame and the second bushing are connected in sequence; the support arm assembly is fixedly connected to the baffle of the corresponding bushing, the bushing sleeve is embedded in the annular cavity of the sleeve on one side of the corresponding cam guide rail to form a closed oil chamber, and the corresponding bracket sleeve is embedded in the annular cavity of the sleeve on the other side of the cam guide rail to form another closed oil chamber, and the four closed oil chambers of the series structure perform oil suction and discharge work regularly.

[0018] Furthermore, the series structure also includes a first end cover and a second end cover, the first end cover is fixedly connected to the baffle of the first bushing, the first end cover has an inner hole passing through the first end cover and communicating with the inner hole on the baffle, the first end cover and the bushing sleeve on the baffle are respectively arranged on both sides of the baffle, the second end cover is fixedly connected to the baffle of the second bushing, and is respectively arranged on both sides of the baffle with the bushing sleeve on the baffle.

[0019] Furthermore, the piston pump also includes a first thrust bearing and a second thrust bearing, which are respectively arranged at the first end cover and the second end cover. One end of the transmission shaft assembly is matched with the first thrust bearing and is arranged in the inner hole of the first end cover. This end is the power input end, and the other end of the transmission shaft assembly is matched with the second thrust bearing.

[0020] Furthermore, in the first piston structure and the second piston structure, for any sleeve structure, a pair of oil suction ports are symmetrically opened on the outer cylinder, and a pair of oil discharge ports are symmetrically opened on the inner cylinder, and the pair of oil suction ports and the pair of oil discharge ports are orthogonally arranged; for any bushing sleeve, a pair of symmetrically arranged oil distribution ports are opened on the bushing sleeve along its circumference, and any of the oil distribution ports is composed of the oil distribution port on the outer cylinder of the bushing and the oil distribution port on the inner cylinder of the bushing, and the oil distribution port on the outer cylinder of the bushing and the oil distribution port on the inner cylinder of the bushing are arranged parallel to each other.

[0021] Furthermore, any of the oil distribution ports also extends to the free end of the corresponding sleeve.

[0022] Furthermore, the end face of the oil suction port adopts a beveled surface design, wherein the outer opening area of the oil suction port is larger than the inner opening area; and / or, the end face of the oil discharge port adopts a beveled surface design, wherein the outer opening area of the oil discharge port is larger than the inner opening area.

[0023] Furthermore, the cross-sectional area of the oil suction port is larger than the cross-sectional area of the oil discharge port.

[0024] Furthermore, a plurality of shift forks are symmetrically grown along the radial direction on the inner cavity of the piston structure, and a linear ball groove is provided on the shift fork for transmitting torque by balls.

[0025] Furthermore, a high-pressure flow channel is processed on the inner cavity wall except for the shift fork, and the high-pressure flow channel is communicated with the oil discharge port and the oil discharge flow channel.

[0026] Furthermore, the pump core support frame body is in the shape of a truncated cone, and an annular groove is provided on the circumferential side wall of the truncated cone. The annular groove is provided with a body oil discharge port and communicates with the oil discharge channel in the body. A high-pressure chamber is formed between the annular groove and the pump casing.

[0027] Furthermore, a plurality of oil passage grooves are provided on the pump core support frame body along the circumferential direction, and any of the oil passage grooves is arranged along the axial direction of the pump core support frame body and is not in communication with the oil drainage channel. The oil passage grooves are used to achieve oil flow throughout the pump casing.

[0028] Furthermore, the first support arm assembly and the second support arm assembly are both composed of two symmetrically arranged support arms; the cam guide is a double-sided cam guide; the double-sided distribution structure also includes a first roller frame assembly and a second roller frame assembly, the first roller frame assembly cooperates with the first support arm assembly and the first piston structure, the second roller frame assembly cooperates with the second support arm assembly and the second piston structure, the first roller frame assembly and the second roller frame assembly each include two groups of roller assemblies, the two groups of roller assemblies are arranged at intervals along the length direction of the corresponding support arm assembly, any of the roller assemblies includes a roller frame and a plurality of rollers, the roller frame is fixedly connected to the corresponding two support arms, and the plurality of rollers are arranged at intervals along the circumference of the roller frame on the inner wall of the roller frame, and the corresponding double-sided cam guide is clamped between the plurality of rollers of the two groups of roller assemblies, wherein, when the piston structure rotates, the rollers of the two groups of roller assemblies can respectively move circumferentially along the two sides of the double-sided cam guide.

[0029] Furthermore, the transmission shaft assembly includes an input transmission shaft, a first transmission block, a first transmission shaft, a second transmission block and a second transmission shaft connected in sequence; the two end surfaces of the first transmission block have orthogonally distributed slide grooves a and slide grooves b; the two end surfaces of the second transmission block have orthogonally distributed slide grooves c and slide grooves d; one end of the input transmission shaft is the power input end, which cooperates with the first thrust bearing, and the other end is a flat square structure c, which cooperates with the slide groove a; the first transmission shaft is arranged in the inner cavity of the first piston structure, and has a plurality of linear ball grooves parallel to the axis uniformly distributed in the circumference thereof The first transmission shaft is provided with a flat square structure a and a flat square structure b at both ends, which respectively cooperate with the slide b and the slide c; the second transmission shaft is provided in the inner cavity of the second piston structure, and has a plurality of linear ball grooves parallel to the axis, which are uniformly distributed in the circumference and are used to place balls and cooperate with the linear ball grooves of the second piston structure; one end of the second transmission shaft is also provided with a flat square structure d, which cooperates with the slide d; the other end of the second transmission shaft cooperates with the second thrust bearing;

[0030] Among them, any slide groove has multiple inner wall surfaces, some of the multiple inner wall surfaces are set as transmission surfaces, and the rest are set as non-transmission surfaces. The transmission surfaces of the two end surface slide grooves on the same transmission block are perpendicular to each other. The flat square structure a, flat square structure b, flat square structure c and flat square structure d all have transmission surfaces and non-transmission surfaces that match the corresponding slide grooves. The transmission surface of any flat square structure fits tightly with the transmission surface of the corresponding slide groove, and there is a gap between the non-transmission surface of any flat square structure and the non-transmission surface of the corresponding slide groove. During operation, the input drive shaft and the first drive shaft can slide along the normal direction of the non-transmission surface while transmitting torque through the transmission surface. The first drive shaft and the second drive shaft can also slide along the normal direction of the non-transmission surface while transmitting torque through their transmission surfaces.

[0031] Furthermore, any sliding groove is a rectangular groove, and one group of two inner wall surfaces of the rectangular groove that are arranged parallel to each other are set as transmission surfaces, and the remaining two surfaces are non-transmission surfaces.

[0032] Furthermore, the length of the transmission surface is greater than the length of the non-transmission surface.

[0033] Furthermore, any of the linear ball grooves is not fully filled with balls, and the length of the linear ball groove without balls is ΔL, ΔL=h / π, where h is the guide rail stroke of the piston pump.

[0034] Furthermore, the length of any linear ball groove is L:

[0035] L=nD+h / π

[0036] Where L is the length of the linear ball groove, D is the ball diameter, n is the number of balls, and h is the guide rail stroke.

[0037] Furthermore, the transmission shaft assembly includes:

[0038] Two transmission blocks are respectively arranged in a one-to-one correspondence with the first piston structure and the second piston structure. The transmission block is a hollow cylindrical structure with openings at both ends. A pair of inner transmission grooves are evenly opened on the inner cavity wall thereof in the circumferential direction; a pair of outer transmission grooves are evenly opened on the outer wall surface thereof in the circumferential direction. Any inner transmission groove and outer transmission groove are arranged along the length direction of the transmission block. A pair of inner transmission grooves and a pair of outer transmission grooves are arranged orthogonally. Any transmission block is arranged in the inner cavity of the corresponding piston structure, and the transmission groove on the outer side of the transmission block cooperates with the ball in the ball groove of the corresponding piston structure.

[0039] A transmission shaft, wherein a pair of shift forks are symmetrically arranged on the transmission shaft in the circumferential direction, and the shift forks are also arranged along the length direction of the transmission shaft; the transmission shaft is simultaneously arranged in the two transmission blocks, and the two transmission blocks are spaced apart along the axis direction of the transmission shaft; the inner transmission groove of any transmission block cooperates with the shift fork of the transmission shaft, and the two ends of the transmission shaft cooperate with the first thrust bearing and the second thrust bearing respectively;

[0040] A plurality of limiting parts, each of which is provided at both ends of any of the transmission blocks, and the limiting parts are also fixedly sleeved on the transmission shaft, and are used to limit the movement of the two transmission blocks along the axis of the transmission shaft;

[0041] During operation, the transmission shaft drives the two transmission blocks to rotate, and the two transmission blocks transmit torque to the first piston structure and the second piston structure through the balls, so that the first piston structure and the second piston structure rotate circumferentially.

[0042] Furthermore, the two transmission blocks, the first piston structure, the second piston structure and the transmission through-shaft are coaxially arranged; and / or the hollow cylindrical structure with openings at both ends is a hollow cylindrical structure with openings at both ends.

[0043] The beneficial effects of the present invention compared with the prior art are as follows:

[0044] (1) The main / pre-boost integrated system proposed in the present invention introduces a dual-motion free-degree piston pump with strong self-priming ability as a boost pump, which eliminates the need for the piston pump to suck in fuel for pre-boosting, thus achieving main / pre-boost integration. Compared with gear pumps and centrifugal pumps, dual-motion free-degree piston pumps have the advantage of high efficiency and can still maintain high efficiency under high temperature and high pressure conditions. Therefore, the main / pre-boost integrated piston pump has higher overall efficiency and consumes less energy than the main boost (gear pump) + pre-boost (centrifugal pump) split solution;

[0045] (2) The present invention does not require pre-pressurization of the oil suctioned by the piston pump, and the centrifugal electric pump of the present invention only needs to pressurize and deliver the fuel required for equipment cooling. Compared with the fuel flow required for engine combustion, the fuel flow required for equipment cooling is extremely small. Therefore, the power, volume, and weight of the cooling electric pump of the present invention are greatly reduced, thereby significantly reducing the weight of the entire system.

[0046] (3) The present invention uses a high-speed motor as the main pump's drive motor, which is smaller in size and weight than a low-speed motor. However, increasing the speed does not significantly reduce the weight of the oil pump. On the contrary, excessively high speeds can adversely affect the efficiency and suction characteristics of the oil pump. Therefore, a speed reducer is used to slow down the motor and drive the main pump, thereby optimizing the overall benefits of the system.

[0047] (4) The present invention connects the motor and pump via a reducer. Utilizing the reducer's diverse input and output configurations, the motor and main pump can be installed in either a straight-line configuration or a T-shaped configuration. This overall installation configuration is more flexible and can meet the installation requirements of various spatial layouts, particularly those within the confined envelope of an aircraft.

[0048] (5) The dual-motion freedom piston pump of the present invention is specially designed, wherein the piston sleeve and the double-sided guide rail of the present invention are integrated, and the rollers can be distributed on the outside of the piston sleeve, which can make full use of the axial distance of the piston, effectively shorten the axial length of the pump, reduce the volume weight of the pump, and improve the power-to-weight ratio of the pump; the piston and the bushing of the present invention are both baffle structures, and the bushing is used to replace the traditional cylinder parts. At the same time, the piston and the bushing are hollowed out in the middle and grooved circumferentially, which greatly reduces the weight of the pump; the piston and the bushing of the present invention are both baffle structures, and the integrated guide rail piston is subjected to reduced resistance during reciprocating motion, the oil stirring power loss is reduced, and the mechanical efficiency of the pump is improved; the piston of the present invention is double-sided flow distribution, and the oil suction port and the oil discharge port are distributed on different cylinders, which indirectly increases the distance between the oil ports, increases the sealing length, effectively reduces the leakage, and improves the volumetric efficiency of the pump; the piston cavity oil suction port of the present invention is arranged on the guide rail piston outer sleeve and is directly connected to the oil, and the oil can enter the piston cavity without passing through any flow channel, which effectively increases the self-priming ability of the pump. The piston of the present invention has a baffle structure. The oil entering the piston cavity has almost no circumferential rotational motion. At the same time, the axial speed of the oil is small due to the short piston stroke, the kinetic energy loss of the oil is extremely small, and the energy conversion rate of the pump is high. The piston of the present invention has a baffle structure. When the pump is at high speed, the oil can quickly follow the axial movement of the piston and fill the piston cavity in time, greatly enhancing the anti-cavitation ability of the pump. With the structure of the present invention, when the piston cavity is in the oil pressure stroke, the bushing produces a slight deformation under the action of the high-pressure oil, which reduces the gap between the bushing and the piston, reduces leakage, and improves volumetric efficiency. This gap compensation structure is also applicable at high temperatures. BRIEF DESCRIPTION OF THE DRAWINGS

[0049] The accompanying drawings are included to provide a further understanding of the embodiments of the present invention, constitute a part of the specification, illustrate the embodiments of the present invention, and together with the description, explain the principles of the present invention. Obviously, the drawings described below are only some embodiments of the present invention, and those skilled in the art can derive other drawings based on these drawings without inventive effort.

[0050] Figure 1 This is a schematic structural diagram of a dual-motion-freedom piston pump according to the present invention;

[0051] Figure 2 This is a schematic structural diagram of the pump core assembly of the present invention (stereoscopic view);

[0052] Figure 3 This is a schematic structural diagram of the pump core assembly of the present invention (exploded view);

[0053] Figure 4 This is a schematic diagram of the integrated baffle guide piston structure of the present invention;

[0054] Figure 5 for Figure 4 sectional view of

[0055] Figure 6 for Figure 4 A top view of

[0056] Figure 7 This is a schematic diagram of the positions of the crests and troughs of the guide piston guide profile;

[0057] Figure 8 This is a schematic diagram of the flow distribution principle of the present invention;

[0058] Figure 9 This is the structural diagram of the pump core support frame;

[0059] Figure 10 Schematic diagram of the roller frame;

[0060] Figure 11 This is a schematic diagram of the structure of an integrated guide rail piston with a balanced support according to the present invention;

[0061] Figure 12 Schematic diagram of the cross-torque transmission structure of the present invention (front view and cross-sectional view);

[0062] Figure 13 for Figure 12 Exploded view of;

[0063] Figure 14 Schematic diagram of the transmission surface of the transmission block of the present invention;

[0064] Figure 15 Schematic diagram of the orthogonal torque transmission structure of the present invention (front view and cross-sectional view);

[0065] Figure 16 for Figure 15 Axonometric drawing (the lower guide piston is hidden);

[0066] Figure 17 Schematic diagram of the orthogonal torque transmission structure of the present invention (top view);

[0067] Figure 18 This is a schematic diagram (stereoscopic diagram) of the transmission through-shaft structure of the present invention;

[0068] Figure 19 It is a schematic structural diagram (stereoscopic diagram) of the transmission block of the present invention.

[0069] Figure 20 Schematic diagram of the main / pre-boost integrated system (fuel supply system) of the present invention;

[0070] Figure 21 This is a schematic structural diagram of the main / pre-boost electric pump of the dual-motion freedom piston pump of the present invention;

[0071] Figure 22 The present invention is a piston pump planetary reducer assembly;

[0072] Figure 23 The invention discloses a piston pump arc cone reducer assembly.

[0073] Figure 24 This is a schematic diagram of the existing fuel supply system. DETAILED DESCRIPTION

[0074] It should be noted that, in the absence of conflict, the embodiments in this application and the features in the embodiments can be combined with each other. The technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is in no way intended to limit the present invention and its application or use. Based on the embodiments in the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present invention.

[0075] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, they indicate the presence of features, steps, operations, devices, components and / or combinations thereof.

[0076] Unless otherwise specifically stated, the relative arrangement of the parts and steps, the numerical expressions and the numerical values set forth in these embodiments do not limit the scope of the present invention. At the same time, it should be understood that, for ease of description, the sizes of the various parts shown in the drawings are not drawn according to the actual proportional relationship. The techniques, methods and equipment known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, the techniques, methods and equipment should be considered as part of the authorization specification. In all examples shown and discussed here, any specific values should be interpreted as being merely exemplary and not as limiting. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that similar numbers and letters represent similar items in the following figures, and therefore, once an item is defined in one figure, it does not need to be further discussed in subsequent figures.

[0077] like Figure 20-23As shown, in one embodiment of the present invention, a main / pre-boost integrated system is provided, which includes a device to be cooled 3' and an engine 5'. In addition, the system also includes: a fuel tank 1' (the fuel tank 1' stores fuel), a cooling electric pump 2' and a dual-motion freedom piston pump main / pre-boost electric pump 4', the cooling electric pump 2' and the dual-motion freedom piston pump main / pre-boost electric pump 4' are respectively connected to the fuel tank 1'; the dual-motion freedom piston pump main / pre-boost electric pump 4' includes a second drive unit 41' and a main / pre-boost integrated dual-motion freedom piston pump 42', the main / pre-boost integrated dual-motion freedom piston pump 42' includes a reducer 421 and a dual-motion freedom piston pump 422, the dual-motion freedom piston pump 422 includes a front end cover, a pump housing and a rear end cover, a transmission shaft assembly and a pump core, the front end cover, the pump housing and the rear end cover are sequentially fixedly connected to form a pump housing structure; the pump core is arranged in the pump housing structure and is rotatably arranged on the transmission shaft assembly, the pump core adopts an upper / lower two-pump core integrated series structure, the series structure includes a first piston structure and a second piston structure, the two are rotatably arranged on the transmission shaft assembly at intervals along the axial direction of the transmission shaft assembly, the first piston structure and the second piston structure are both piston and cam guide rail integrated Structure, the cam guide is located in the middle of the piston, and two sleeve structures are symmetrically grown on both sides of the cam guide. For any sleeve structure, it includes an outer tube and an inner tube located in the outer tube, and the outer tube is provided with a plurality of oil suction ports in the circumferential direction, and the inner tube is provided with a plurality of oil discharge ports in the circumferential direction, and any oil suction port and any oil discharge port are staggered; an annular cavity is formed between the outer tube and the inner tube, and the annular cavities of the two sleeve structures are not connected, and the inner tubes on both sides are connected to form an inner cavity of the piston structure; the reducer 421 is rotatably connected to the transmission shaft assembly, and the second driving part 41' drives the double-motion freedom piston pump 422 to operate through the reducer 421, so that the piston The piston pump operates in a suitable working range, and the dual-motion-freedom piston pump 422 relies on its own self-priming ability to fill the fuel in the cavity; wherein, the system has a first oil circuit 10' and a second oil circuit 20', the first oil circuit 10' is a cooling oil circuit, the fuel in the fuel tank 1' is transported to the cooling electric pump 2', and the cooling electric pump 2' is pressurized and transported to the device to be cooled 3', and the fuel returns to the fuel tank 1' after the device to be cooled is cooled; the second oil circuit 20' is the oil supply and delivery circuit for the engine 5', the fuel in the fuel tank 1' is transported to the dual-motion-freedom piston pump 422, and is transported by the dual-motion-freedom piston pump 422 to the engine 5' for combustion.

[0078] That is, in the embodiment of the present invention, the oil tank 1' and the cooling electric pump 2' and the dual-motion freedom piston pump 422 main / pre-boost electric pump 4' can be connected by pipelines, and the cooling electric pump 2' and the equipment to be cooled, as well as the dual-motion freedom piston pump 422 main / pre-boost electric pump 4' and the engine 5' are all connected by channel pipelines.

[0079] In this embodiment of the present invention, the electric cooling pump 2' supplies the fuel flow required by the equipment being cooled at a constant speed. This means that, because the flow and pressure required for equipment cooling are significantly lower than those required for engine combustion, the power, volume, and weight of the electric cooling pump in this embodiment are significantly reduced compared to conventional separate main / pre-boost systems. Furthermore, the dual-motion main / pre-boost electric pump adjusts its speed based on the engine's fuel flow requirements, delivering the required fuel flow to the engine for combustion.

[0080] It can be seen that in the embodiment of the present invention, since the fuel in the two oil circuits is appropriate, the power loss caused by overflow is saved and the overall efficiency is higher.

[0081] According to an embodiment of the present invention, the cooling electric pump 2' includes a centrifugal pump 21' and a first driving unit 22', wherein the first driving unit 22' drives the centrifugal pump 21' to pressurize the fuel and deliver it to the equipment to be cooled.

[0082] The dual-motion-freedom piston pump 422 of the present embodiment differs from conventional piston pumps. Its specific structure will be described in detail in the following embodiments. Furthermore, the reducer 421 of the present embodiment can directly adopt existing structures. The detailed structural components will not be elaborated here.

[0083] Specifically, the dual-motion piston pump 422 has a fuel inlet and a fuel outlet. Fuel enters the dual-motion piston pump 422 through the fuel inlet. The second drive unit 41' drives the dual-motion piston pump 422 via the reducer 421, keeping the piston pump operating within a suitable operating range to supply fuel to the engine 5'. Because the dual-motion piston pump 422 can rely on its own self-priming ability to fill the plunger cavity, there is no need for pre-pressurization equipment to pre-pressurize the oil at the piston pump's inlet.

[0084] In the embodiment of the present invention, Figure 21 As shown, the outer shell of the reducer 421 is fixedly connected to the pump housing structure of the dual-motion freedom piston pump 422, the inner cavity of the outer shell of the reducer 421 is connected to the oil cavity of the dual-motion freedom piston pump 422, the structure in the inner cavity of the reducer 421 is immersed in the fuel, and the operation process is lubricated by the fuel.

[0085] Preferably, the first driving part 22 ′ is a driving motor, and the second driving part 41 ′ is a high-speed driving motor.

[0086] In the above embodiment, the output shaft of the reducer 421 is connected to the transmission shaft assembly of the dual-motion-freedom piston pump 422, and the input shaft of the reducer 421 and the transmission shaft assembly are in an "I" shape or a "T" shape.

[0087] In other words, the orientation of the reducer input shaft and the piston pump drive shaft assembly can be adjusted through different reducer structures. The two can be arranged in a straight or T-shape, thus meeting the installation requirements of different spatial layouts, especially the confined space requirements of aircraft.

[0088] According to one embodiment of the present invention, Figure 22-23 As shown, the reducer 421 is a planetary gear reducer 421 or a bevel gear reducer 421 .

[0089] Specifically, the reducer 421 is designed as a whole with the dual-motion freedom piston pump 422. By using different reducer 421 structures, the arrangement direction of the input shaft and the pump main shaft (transmission shaft assembly) can be adjusted. For example, Figure 22 It is a planetary gear reducer consisting of an input sun gear 4211, planetary gears 4212, an internal gear 4213, and an output gear 4214. The output gear 4214 is connected to the drive shaft assembly of the dual-motion piston pump 422. Therefore, the input shaft of the dual-motion freedom main / pre-boost electric pump 4 (i.e., the input sun gear 4211 of the reducer 421) and the drive shaft assembly of the dual-motion piston pump 422 form a "straight" shape. Figure 23 This is a bevel gear reducer consisting of an input bevel gear 4215, a large bevel gear 4216, and an output shaft 4217. The output shaft 4217 is connected to the drive shaft assembly of the dual-motion piston pump 422. Thus, the input shaft of the dual-motion main / pre-boost electric pump 4 (i.e., the input bevel gear 4215 of the reducer 421) and the drive shaft assembly of the dual-motion piston pump 422 form a "T" shape. This allows for installation in various spatial configurations, particularly within the confined space of an aircraft.

[0090] like Figure 1-19 As shown, the dual-motion freedom piston pump of the embodiment of the present invention also adopts a special dual-motion freedom piston pump, and the following content will specifically introduce its structure:

[0091] like Figure 1-19As shown, in one embodiment of the present invention, a dual-motion freedom piston pump is provided, which includes: a front cover 1, a pump housing 6, a rear cover 9, a pump core and a transmission shaft assembly, wherein the front cover 1, the pump housing 6 and the rear cover 9 are sequentially fixedly connected to form a pump housing structure, the pump core is arranged in the pump housing structure, the pump core adopts an upper / lower two-pump core integrated series structure, the series structure includes a first piston structure 4 and a second piston structure 18, both of which are rotatably arranged on the transmission shaft assembly at intervals along the axial direction of the transmission shaft assembly, the first piston Structure 4 and the second piston structure 18 both adopt an integrated structure of piston and cam guide. The cam guide is located in the middle of the piston. Two sleeve structures grow symmetrically on both sides of the cam guide. For any sleeve structure, it includes an outer tube and an inner tube located inside the outer tube. A plurality of oil suction ports are opened circumferentially on the outer tube, and a plurality of oil discharge ports are opened circumferentially on the inner tube. Any oil suction port and any oil discharge port are staggered. An annular cavity is formed between the outer tube and the inner tube. The annular cavities of the two sleeve structures are not connected, and the inner tubes on both sides are connected to form an inner cavity of the piston structure.

[0092] That is, if Figure 5 As shown, the annular cavities of the two sleeve structures are not connected, which means that the two annular cavities are separated by an annular baffle 48.

[0093] Specifically, if Figures 3 to 8 As shown, the first piston structure 4 includes a first cam guide 43 and sleeve structures located on either side thereof, each comprising a first outer sleeve 41 and a first inner sleeve 42, each provided with an oil suction port and an oil discharge port. Similarly, the second piston structure 18 includes a second cam guide 181 and sleeve structures located on either side thereof, each comprising a second outer sleeve 182 and a second inner sleeve 183, each provided with an oil suction port and an oil discharge port.

[0094] In the embodiment of the present invention, the outer tube and the inner tube of the piston structure are both open structures, the inner tubes at both ends are connected, and preferably the end surfaces of the outer tube and the inner tube of the sleeve are flush.

[0095] Preferably, the outer tube and the inner tube of the piston structure are both cylindrical tubes.

[0096] In addition, those skilled in the art should understand that the rotating shaft assembly in the embodiment of the present invention is similar to the transmission shaft of an existing piston pump, which is arranged in the pump core and drives the piston structure to rotate through its rotation. The piston structure performs axial reciprocating motion under the guidance of the cam guide rail.

[0097] It can be seen that the first piston structure and the second piston structure (sleeve structure) of the embodiment of the present invention are both baffle structures, hollowed in the middle and grooved circumferentially, which greatly reduces the weight of the pump and improves the power-to-weight ratio of the pump; at the same time, the agitation effect on the oil during rotation is small, the oil agitation loss is reduced, and the mechanical efficiency is high. When the pump is at high speed, the oil can quickly follow the axial movement of the piston and fill the piston cavity in time, which greatly enhances the anti-cavitation ability of the pump; the piston has double-sided flow distribution, and the oil suction port and oil discharge port are distributed on different cylinders, which indirectly increases the distance between the oil ports, increases the sealing length, effectively reduces the leakage, and improves the volumetric efficiency of the pump. In the embodiment of the present invention, the piston cavity oil suction port is set on the outer sleeve of the piston structure. With this piston structure, the oil suction port can be directly connected to the oil, and the oil can enter the piston cavity without passing through any flow channel, which effectively increases the self-priming ability of the pump. In addition, the cam guide rails of the embodiments of the present invention are all located in the middle of the piston. Compared with the previous structure in which the guide rails and roller structures are concentrated on one side, the rollers can be distributed on the outside of the piston sleeve, which can fully utilize the axial distance of the piston, effectively shorten the axial length of the pump, and reduce the volume of the pump.

[0098] In the above embodiment, if Figure 2-3As shown, in order to achieve two-way flow distribution, the series structure also includes a first bushing 13, a second bushing 20 and a pump core support frame 16. The first bushing 13, the first piston structure 4, the pump core support frame 16, the second piston structure 18, and the second bushing 20 are coaxially arranged along the axis of the transmission shaft assembly in sequence. The first bushing 13 and the second bushing 20 both include a baffle and a bushing sleeve arranged on the baffle. The bushing sleeve consists of a bushing outer tube and a bushing inner tube located in the bushing outer tube. An annular cavity is formed between the bushing inner and outer tubes. The bushing sleeve The cylinder is evenly distributed with a plurality of oil distribution ports along the circumference, and any of the oil distribution ports passes through the outer cylinder and the inner cylinder of the bushing at the same time. The baffle has an inner hole passing through the baffle, and the inner hole is communicated with the inner cylinder of the bushing to form the inner cavity of the bushing; the pump core support frame 16 adopts an integrated cylinder structure, including a pump core support frame body 161, the pump core support frame body 161 is fixedly connected to the pump housing 6, an oil discharge channel is opened inside the pump core support frame body 161, and a first support arm bushing assembly and a second support arm bushing assembly are respectively grown at both ends of the pump core support frame body 161 , the two components are arranged at a staggered preset angle, the first support arm bushing assembly is composed of the first support arm assembly and the first bracket sleeve, the second support arm bushing assembly is composed of the second support arm assembly and the second bracket sleeve, the first bracket sleeve and the second bracket sleeve are both the same as the bushing sleeve structure, wherein the inner tube of the first bracket sleeve and the inner tube of the second bracket sleeve are both connected to the oil discharge channel to form the inner cavity of the pump core support frame 16; wherein the first bushing 13, the first piston structure 4 and the first support arm bushing assembly cooperate, the second bushing 20, the second piston structure 4 and the first support arm bushing assembly cooperate, The plug structure 18 cooperates with the second support arm bushing assembly, and the piston structure is arranged between the corresponding bushing and the support arm bushing assembly. The inner cavities of the first bushing 13, the first piston structure 4, the pump core support frame 16, and the second bushing 20 are connected in sequence; the support arm assembly is fixedly connected to the baffle of the corresponding bushing, and the bushing sleeve is embedded in the annular cavity of the sleeve on one side of the corresponding cam guide rail to form a closed oil chamber, and the corresponding bracket sleeve is embedded in the annular cavity of the sleeve on the other side of the cam guide rail to form another closed oil chamber. The four closed oil chambers in the series structure perform oil suction and discharge operations regularly.

[0099] That is, the first bushing 13, the first piston structure 4, the pump core support bracket 16, the second piston structure 18, and the second bushing 20 are sequentially arranged coaxially along the axis. The first piston structure 4 is disposed between the first bushing 13 and the first support arm bushing assembly. The first bushing 13 is fixedly connected to the first support arm assembly. The bushing sleeve of the first bushing 13 is embedded in the annular cavity of the sleeve on one side of the cam guide of the first piston structure 4, and the first bracket sleeve is embedded in the annular cavity of the sleeve on the other side, thereby forming two closed oil chambers. Similarly, the second piston structure 18, the second bushing 20, and the second support arm bushing assembly also adopt the same coordination method, thereby forming four closed oil chambers in a series structure.

[0100] Preferably, the first support arm bushing assembly and the second support arm bushing assembly are staggered at 45 degrees, that is, those skilled in the art should understand that the first support arm assembly and the second support arm assembly are staggered at 45 degrees, and the first bracket sleeve and the second bracket sleeve are also staggered at 45 degrees. This configuration can achieve pulsation-free pump output flow.

[0101] Preferably, the bushing sleeve and the bracket sleeve are both cylindrical sleeves.

[0102] Preferably, in the first piston structure 4 and the second piston structure 18, for any sleeve structure, a pair of oil suction ports are symmetrically opened on the outer tube, and a pair of oil discharge ports are symmetrically opened on the inner tube, and the pair of oil suction ports and the pair of oil discharge ports are orthogonally arranged; for any bushing sleeve, a pair of symmetrically arranged oil distribution ports are opened on the bushing sleeve along its circumference, and any of the oil distribution ports is composed of the oil distribution port on the outer tube of the bushing and the oil distribution port on the inner tube of the bushing, and the oil distribution port on the outer tube of the bushing and the oil distribution port on the inner tube of the bushing are arranged parallel to each other.

[0103] Specifically, the piston structure of the embodiment of the present invention integrates the functions of oil suction and discharge, flow distribution and transmission. Figures 3 to 8 As shown, the first piston structure 4 includes a first cam guide 43 and sleeve structures located on both sides thereof, each including a first outer tube 41 and a first inner tube 42. A pair of oil suction ports 44 and oil discharge ports 45 are orthogonally disposed on the first outer tube 41 and the first inner tube 42, respectively. Similarly, the second piston structure 18 includes a second cam guide 181 and sleeve structures located on both sides thereof, each including a second outer tube 182 and a second inner tube 183. A pair of oil suction ports and oil discharge ports are orthogonally disposed on the second outer tube 182 and the second inner tube 183, respectively.

[0104] In addition, the first bracket sleeve and the second bracket sleeve in the embodiment of the present invention have the same structure as the bushing sleeve, and will not be described in detail here.

[0105] In the above embodiment, in order to achieve better oil suction and discharge, as Figure 3 、 Figure 9 As shown, any of the oil distribution ports further extends to the free end of the corresponding sleeve.

[0106] That is, the series structure of the embodiment of the present invention is a double-sided flow distribution structure, which proposes a new baffle-type piston structure (first piston structure and second piston structure). The baffle-type piston is an integrated structure of a cam guide and a piston. The cam guide is located in the middle of the piston, and two inner and outer cylindrical sleeves grow symmetrically on both sides of the cam guide. At the same time, this structure also designs the traditional bushing structure that cooperates with the piston structure as a baffle-type bushing structure (the first bushing, the second bushing, and the first support sleeve and the second support sleeve in the embodiment of the present invention). The baffle-type bushing is nested and installed in the baffle-type piston to form a closed volume. As the closed volume increases and decreases, the piston pump can complete the expansion and compression of the fluid. Among them, a pair of oil distribution ports are respectively provided on the inner and outer sleeves of the piston structure, and the two pairs of oil distribution ports are in orthogonal positions. The oil distribution port on the outer sleeve is the oil suction port, and the oil distribution port on the inner sleeve is the oil discharge port. Two inner and outer baffles (inner and outer sleeves) grow on one side of the baffle-type bushing, and two pairs of oil grooves (oil distribution ports) are provided in parallel and centrally symmetrically. During piston pump operation, the drive shaft assembly rotates the piston structure via the torque-transmitting balls, which then complete axial reciprocating motion guided by the curved surface of the cam guide. When the suction port is connected to the oil groove on the outer baffle, the piston is in the suction stroke, with oil entering the piston cavity from the pump chamber through the suction port. When the discharge port is connected to the oil groove on the inner baffle, the piston is in the compression stroke, with fluid flowing out of the piston cavity through the discharge port.

[0107] As can be seen, in the embodiment of the present invention, the piston and double-sided guide rail are integrated to form an integrated guide rail piston, and the cam guide rail is located in the middle of the piston. Compared with the previous structure in which the guide rail and roller structure are concentrated on one side, the roller can be distributed on the outside of the piston sleeve, which can fully utilize the axial distance of the piston, effectively shorten the axial length of the pump, and reduce the volume of the pump. In addition, the piston of the embodiment of the present invention has double-sided flow distribution, and the oil suction port and oil discharge port are distributed on different cylinders, which indirectly increases the distance between the oil ports, increases the sealing length, effectively reduces leakage, and improves the volumetric efficiency of the pump. With this piston structure, the oil can enter the piston cavity directly without passing through a complex flow channel, increasing the self-priming ability of the pump; the oil enters the piston cavity with almost no circumferential rotational motion. At the same time, the axial velocity of the oil is small due to the short piston stroke, the kinetic energy loss of the oil is extremely small, and the energy conversion rate of the pump is high; at high speeds, the oil can quickly follow the axial movement of the piston and fill the piston cavity in time, greatly enhancing the anti-cavitation ability of the pump.

[0108] In the above embodiment, in order to achieve rotation, a plurality of shift forks are symmetrically extended along the radial direction on the inner cavity of the first piston structure 4 and the second piston structure 18, and a linear ball groove is provided on the shift fork for ball torque transmission.

[0109] Among them, for the cross torque transmission described below, a linear ball groove is provided on any shift fork, and for the orthogonal torque transmission described below, two linear ball grooves are provided side by side on any shift fork.

[0110] Preferably, there are two shift forks, which are symmetrically arranged.

[0111] In the above embodiment, in order to better achieve oil drainage, a high-pressure flow channel 49 is processed on the inner cavity wall except for the shift fork, and the high-pressure flow channel is communicated with the oil drain port and the oil drain flow channel.

[0112] Specifically, since the first piston structure 4 and the second piston structure 18 have the same structure, taking the first piston structure 4 as an example, Figure 4-8 As shown, a through hole is processed in the center of the first piston structure 4, and a high-pressure flow channel 49 is processed on the wall of the through hole. A first torque transmission fork 46 is processed at a position orthogonal to the high-pressure flow channel 49, and a linear ball groove a47 is provided on the first torque transmission fork 46 for the ball 15 to transmit torque.

[0113] In the above-mentioned embodiment, the oil suction port end face adopts a beveled design, wherein the outer opening area of the oil suction port is larger than the inner opening area; the oil discharge port end face adopts a beveled design, wherein the outer opening area of the oil discharge port is larger than the inner opening area. In other words, the beveled design of the oil suction and discharge port end faces effectively increases the self-priming capacity during piston rotation and reduces hydraulic losses caused by the outer diameter end face. Under high-pressure conditions, the bushing undergoes slight deformation under the action of high-pressure oil, reducing the gap between the bushing and the piston, reducing leakage, and improving volumetric efficiency.

[0114] In the above embodiment, the cross-sectional area of the oil suction port is larger than the cross-sectional area of the oil discharge port.

[0115] In this embodiment of the present invention, because the cross-sectional area of the oil suction port is larger than the oil discharge port, and the inner diameter of the outer tube is larger than that of the inner tube, the cross-sectional area of the oil suction port is larger than that of the oil discharge port. This allows the oil in the pump housing to enter the piston cavity directly through the oil suction port of the outer tube without passing through a complex flow path, further facilitating pump oil suction. Furthermore, due to the use of a baffle-type piston and bushing structure, the oil entering the piston cavity does not generate rotational motion. Instead, the oil quickly follows the axial movement of the guide piston and promptly fills the piston cavity, reducing oil churning losses while enhancing the pump's anti-cavitation capability.

[0116] Specifically, the present invention adopts an upper / lower two-pump integrated series structure, such as Figure 2 、 Figure 3As shown, the pump comprises a first bushing 13, a first piston structure 4, an integrated pump core support frame 16, a second piston structure 18, and a second bushing 20. The bushing sleeve of the first bushing 13 (composed of a first bushing outer tube 131 and a first bushing inner tube 132), the first piston structure 4, and the first support sleeve (composed of a first support outer tube 1610 and a first support inner tube 1611) are nested together to form two enclosed oil chambers. Simultaneously, the bushing sleeve of the second bushing 20 (composed of a second bushing outer tube 201 and a second bushing inner tube 202), the second piston structure 18, and the second support sleeve (composed of a second support outer tube 167 and a second support inner tube 168) are nested together to form two additional enclosed oil chambers. These four enclosed oil chambers regularly pump and discharge oil. To achieve pulsation-free pump output, the upper and lower pump cores are arranged 45° apart. The two bushings are fastened to the pump core support frame 16 via nuts, simultaneously supporting and lubricating the first and second piston structures 4 and 18. Because both the piston and bushing are baffle-type structures, the bushing replaces the traditional cylinder block. The hollow center and circumferential grooves between the two significantly reduce the pump's weight. Furthermore, when the oil enters the closed oil chamber, it is not affected by the rotation of the guide piston, generating no rotational motion. This reduces churning power losses and improves the pump's mechanical efficiency.

[0117] Because the first and second piston structures 4 and 18 share the same principles for oil suction, discharge, flow distribution, and transmission, the following uses the first piston structure 4 as an example to explain these principles. When the drive shaft assembly rotates the first piston structure 4, it reciprocates axially guided by the curved guide surface. The first piston structure 4 and first bushing 13 form a closed oil chamber. During the process of the first piston structure 4 moving from the highest point to the lowest point, the first piston structure 4 is in the oil discharge stroke, the volume of the piston chamber becomes smaller, the oil is compressed, and the oil in the piston chamber flows into the high-pressure flow channel 49 through the inner oil groove on the first bushing 13 and the oil discharge port 45 of the first piston structure 4, completing the oil discharge; during the process of the first piston structure 4 moving from the lowest point to the highest point, the first piston structure 4 is in the oil suction stroke, the volume of the piston chamber becomes larger, forming a vacuum, and the oil in the shell can be sucked into the piston chamber through the oil suction port 44 of the first piston structure 4 and the outer oil groove on the first bushing 13 without passing through a complex flow channel, completing the oil suction, and the oil suction and discharge work of the left and right piston chambers of the first piston structure 4 is performed alternately.

[0118] In the above embodiment, if Figure 9 As shown, in order to better achieve oil drainage, the pump core support frame body 161 is in the shape of a truncated cone, and an annular groove 166 is provided on the circumferential side wall of the truncated cone. The annular groove 166 is provided with a body oil discharge port 1612, which is communicated with the oil discharge channel in the body, and a high-pressure chamber is formed between the annular groove 166 and the pump housing 6.

[0119] In the above embodiment, if Figure 9 As shown, in order to achieve oil flow between the upper / second pump cores in the pump, a plurality of oil passage grooves 169 are circumferentially opened on the pump core support frame body 161. Any of the oil passage grooves 169 is arranged along the axial direction of the pump core support frame body 161 and is not connected with the oil discharge channel. The oil passage grooves 169 are used to achieve oil flow in the entire pump casing structure.

[0120] That is, when the pump core support frame 16 of the present invention is matched with the pump housing 6, the annular groove 166 on the pump core support frame body 161 is circumferentially sealed with the pump housing 6 (e.g. Figure 9 As shown, two annular sealing grooves 163 are provided on the pump core support frame body 161, distributed on both sides of the annular groove 166. Sealing rings can be placed in the sealing grooves to achieve sealing with the pump casing 6), forming a high-pressure chamber. This also divides the pump casing structure into two front and rear chambers. In order to achieve oil circulation throughout the pump, the oil discharge channel of the body can be avoided, and multiple oil grooves 169 are provided on the body to achieve circulation within the pump casing structure.

[0121] According to one embodiment of the present invention, Figure 3 、 9 As shown, the first support arm assembly and the second support arm assembly are each composed of two symmetrically arranged support arms 164. The support arms on both sides are arranged 45 degrees apart, and two mounting holes 162 are processed on the support arms 164 for mounting the roller frame 8.

[0122] In addition, the end surface of the pump core support frame body 161 is installed with a pump core support frame 16 support ear 165, preferably two evenly distributed, which are used for axial and angular positioning of the pump core and are installed in the support ear groove of the pump housing 6.

[0123] The through hole in the middle of the integrated cylinder structure of the present invention is formed through one-time processing, which ensures the coaxiality of the upper / lower pump cores, solves the problems of piston eccentric wear and adhesion caused by the misalignment of the upper / lower pump cores, and improves the working reliability of the pump.

[0124] According to one embodiment of the present invention, Figure 2 、 Figure 10 、 Figure 11As shown, the cam guide is a double-sided cam guide, and the series structure also includes a first roller frame assembly and a second roller frame assembly. The first roller frame assembly cooperates with the first support arm assembly and the first piston structure 4, and the second roller frame assembly cooperates with the second support arm assembly and the second piston structure 18. The first roller frame assembly and the second roller frame assembly each include two groups of roller assemblies, and the two groups of roller assemblies are arranged at intervals along the length direction of the corresponding support arm assembly. Any of the roller assemblies includes a roller frame and a plurality of rollers, and the roller frame is fixedly connected to the corresponding two support arms, and the plurality of rollers are arranged at intervals along the circumference of the roller frame on the inner wall of the roller frame. The corresponding double-sided cam guide is clamped between the plurality of rollers of the two groups of roller assemblies, wherein, while the piston structure rotates, the rollers of the two groups of roller assemblies can respectively move circumferentially along both sides of the double-sided cam guide.

[0125] In the embodiment of the present invention, the cam guide rail curved surface has crests and troughs, and more preferably, there are two crests and two troughs.

[0126] In the embodiment of the present invention, preferably, the roller frame is connected to the corresponding two support arms via a pin and can rotate around the pin, thereby ensuring that the two rollers on one side are always in contact with the cam guide rail and evenly sharing the axial force on the piston structure.

[0127] Specifically, the four roller assemblies of the present invention have the same structure, namely, the first, second, third and fourth roller assemblies, which all include rollers and roller frames. The structures of the first, second, third and fourth roller assemblies are described below using the first roller assembly as an example.

[0128] like Figure 10 、 11 As shown, the first roller assembly includes a first roller frame 8 and a first roller 5. Preferably, there are two first rollers 5. More preferably, the rollers utilize bolt-type needle roller bearings, evenly distributed circumferentially and bolted to positioning holes 81 of the roller frame 8. The first roller assemblies are fixedly mounted in pairs to the mounting holes 162 of the support arms 164 of the pump core support frame 16 via pins a19 (the corresponding first roller frame 8 has pin holes 83 that cooperate with the support arms 164). A zero-clearance assembly method ensures that the rollers 5 are tightly fitted to the first cam guide rail 43. The roller assembly can rotate about the pins a19, ensuring that both rollers on one side are in contact with the cam guide rail at all times, evenly sharing the axial force exerted on the guide rail piston.

[0129] Furthermore, if Figure 3As shown, the series structure also includes a first end cover 12 and a second end cover 10, the first end cover 12 is fixedly connected to the baffle of the first bushing 13, the first end cover 12 has an inner hole passing through the first end cover 12 and communicating with the inner hole on the baffle, the first end cover 12 and the bushing sleeve on the baffle are respectively arranged on both sides of the baffle, the second end cover 10 is fixedly connected to the baffle of the second bushing 20, and is respectively arranged on both sides of the baffle with the bushing sleeve on the baffle.

[0130] Furthermore, if Figure 1 As shown, the piston pump also includes a first thrust bearing 22 and a second thrust bearing 27, which are respectively disposed on the first end cap 12 and the second end cap 10. One end of the drive shaft assembly is mated with the first thrust bearing 22 and disposed within the inner hole of the first end cap 12, serving as the power input end. The other end of the drive shaft assembly is mated with the second thrust bearing 27. Two thrust bearings are disposed on the first end cap 12 and the second end cap 10 to balance the hydraulic pressure of the drive shaft assembly.

[0131] According to a preferred embodiment of the present invention, Figures 12 to 14As shown, the transmission shaft assembly adopts a cross torque transmission structure, and the transmission shaft assembly includes an input transmission shaft 11, a first transmission block 2, a first transmission shaft 3, a second transmission block 7 and a second transmission shaft 17 connected in sequence; the two end surfaces of the first transmission block 2 have orthogonally distributed slides a and slides b; the two end surfaces of the second transmission block 7 have orthogonally distributed slides c and slides d; one end of the input transmission shaft is the power input end, which cooperates with the first thrust bearing 22, and the other end is a flat square structure c, which cooperates with the slide a; the first transmission shaft 3 is arranged in the inner cavity of the first piston structure 4, and the first transmission shaft 3 is circumferentially uniformly distributed with a plurality of linear ball grooves b34 parallel to the axis, which are used to place balls 15 and cooperate with the linear ball grooves a47 of the first piston structure 4; the two ends of the first transmission shaft 3 are also respectively provided with flat square structures a and flat square structures b, which cooperate with the slide b and slide c respectively; the second transmission shaft 17 is arranged in the inner cavity of the second piston structure, and the second transmission shaft 17 is circumferentially uniformly distributed with a plurality of linear ball grooves b34 parallel to the axis The linear ball groove c174 of the axis is used to place balls and cooperates with the linear ball groove of the second piston structure 18; one end of the second transmission shaft 17 is also provided with a flat square structure d, which cooperates with the slide d; the other end of the second transmission shaft 17 cooperates with the second thrust bearing 27; wherein, any slide has multiple inner wall surfaces, part of the multiple inner wall surfaces are set as transmission surfaces, and the rest are set as non-transmission surfaces. The transmission surfaces of the two end surface slides on the same transmission block are perpendicular to each other, and the flat square structure a, flat square structure b, flat square structure c and flat square structure d all have transmission surfaces and non-transmission surfaces that cooperate with the corresponding slides. The transmission surface of any flat square structure is tightly fitted with the transmission surface of the corresponding slide, and there is a gap between the non-transmission surface of any flat square structure and the non-transmission surface of the corresponding slide. During operation, the input transmission shaft 11 and the first transmission shaft 3 can slide along the normal direction of the non-transmission surface while transmitting torque through the transmission surface. The first transmission shaft 3 and the second transmission shaft 17 can also slide along the normal direction of the non-transmission surface while transmitting torque through their transmission surfaces.

[0132] For example, if Figure 13As shown, the flat square structure c has a flat square structure c transmission surface 111 and a flat square structure c non-transmission surface 112, the flat square structure a has a flat square structure a transmission surface 31 and a flat square structure a non-transmission surface 32, and the chute b that matches the flat square structure a has a chute b transmission surface 210 and a chute b non-transmission surface 211. The flat square structure c transmission surface 111 of the input drive shaft 11 and the flat square structure a transmission surface 31 of the first drive shaft 3 are respectively closely aligned with the transmission surfaces at both ends of the first drive block 2 and are perpendicular to each other. Similarly, the flat square structure b has a flat square structure b transmission surface 33, the flat square structure d has a flat square structure d transmission surface 172 and a flat square structure d non-transmission surface 171, and the chute d of the second drive block 7 has a chute d transmission surface 72 and a chute d non-transmission surface 71. The other end of the second drive shaft 17 is provided as a smooth shaft 173, which matches the second thrust bearing 27.

[0133] That is, during operation, the input drive shaft 11 and the first drive shaft 3 transmit torque through the transmission surface while simultaneously sliding along the normal direction of the non-transmission surface, adjusting the coaxiality of the input drive shaft 11 and the first drive shaft 3 while transmitting torque and compensating for misalignment between the input drive shaft 11 and the first drive shaft 3. Similarly, the cross-shaped torque transmission structure between the first and second drive shafts 3 and 17 compensates for misalignment during processing, assembly, and operation. Therefore, the two cross-shaped torque transmission structures can reduce the coaxiality requirements between the drive shaft and the upper and lower pump cores, reduce the number of parts required for matching, improve processing and assembly processability, and significantly save money and time.

[0134] As can be seen, the present invention utilizes a drive shaft, a drive block, and straight-groove ball bearings to transmit torque, replacing the conventional through-shaft transmission structure. This decouples the rotational motion of the upper and lower drive shafts, compensating for relative displacement of the input drive shaft, the first drive shaft, and the second drive shaft during machining, assembly, and operation, while also tolerating significant radial and axial misalignment. Furthermore, the cross-shaped torque transmission structure, comprised of the drive shaft and drive block, offers advantages such as simple construction, easy installation, zero backlash, high torque, high rigidity, and high sensitivity, while significantly reducing the manufacturing costs of conventional through-shaft torque transmissions.

[0135] In the above embodiment, if Figure 13 As shown, in order to better achieve coaxiality adjustment, any sliding groove is a rectangular groove.

[0136] Preferably, one group of two inner wall surfaces of the rectangular groove that are arranged parallel to each other are set as transmission surfaces, and the remaining two surfaces are non-transmission surfaces.

[0137] In the above embodiment, in order to better transmit torque and better achieve coaxiality adjustment, the length of the transmission surface is greater than the length of the non-transmission surface.

[0138] In the above embodiment, in order to prevent the balls from escaping from the ball grooves, the cross torque transmission structure includes a plurality of limiting components, and any linear ball groove on the first transmission shaft and the second transmission shaft corresponds to a limiting component, and the limiting component is arranged in the corresponding linear ball groove to limit the balls from sliding out of the linear ball grooves.

[0139] According to one embodiment of the present invention, the limiting assembly consists of a first limiting member and a second limiting member, the first limiting member and the second limiting member are respectively arranged in the corresponding linear ball groove at intervals, and multiple balls are also arranged between the first limiting member and the second limiting member.

[0140] According to a specific embodiment of the present invention, the first limiting member and the second limiting member are both pins b14.

[0141] As can be seen, the two sets of ball grooves on the first and second transmission shafts of the present embodiment correspond to the ball grooves in the first piston structure and the inner bore of the first piston structure, respectively. Balls are placed in the ball grooves of the transmission shafts, and ball stop pins are used to limit the position of the balls. The first and second transmission shafts, through the balls, drive the first and second piston structures to rotate around the first bushing, the pump core support frame, and the second bushing. Simultaneously, the piston structures reciprocate axially under the guidance of the curved surface of the guide rail.

[0142] Furthermore, each set of linear ball grooves is evenly distributed in the circumferential direction of the corresponding transmission shaft, and all the linear ball grooves have the same length and depth.

[0143] Preferably, any of the linear ball grooves are not filled with balls, and the length of the linear ball groove without balls is ΔL=h / π, where h is the guide rail stroke. Further preferably, the length of the linear ball groove b34 and the linear ball groove c174 is L=nD+h / π, where D is the ball diameter, and n is the number of balls. The number of balls is determined based on the load-bearing capacity of the balls and the torque to be transmitted, and the specific setting is a well-known technology in the art.

[0144] Since the balls in the linear ball groove are not fully distributed, and the initial positions of the balls on each groove are inconsistent, the balls will generate a tilting torque on the drive shaft and the guide piston. This torque can be balanced by the first bushing, pump core support frame and second bushing of the piston pump.

[0145] Furthermore, the first and second transmission shafts 3 and 17, their linear ball grooves, the ball grooves within the first and second piston structures 4 and 18, the flow distribution grooves, and the profiles are all manufactured in a single clamping process. The seamless fit of the linear ball grooves within the transmission shafts and the piston structures not only ensures constant instantaneous flow in the upper and lower pump elements, but also effectively eliminates flow and pressure pulsations.

[0146] According to another preferred embodiment of the present invention, Figures 15 to 19 As shown, the transmission shaft assembly can also be designed to include two transmission blocks 25, multiple limit portions 23 and a transmission shaft 21. The two transmission blocks 25 are respectively arranged in a one-to-one correspondence with the first piston structure 4 and the second piston structure 18. The transmission block 25 is a hollow cylindrical structure with openings at both ends, and has an inner cavity 252. A pair of inner transmission grooves 253 are evenly opened on the inner cavity wall in the circumferential direction; a pair of outer transmission grooves 251 are evenly opened on the outer wall surface of the transmission block 25 in the circumferential direction, and any inner transmission groove 253 and outer transmission groove 251 are arranged along the length direction of the transmission block 25. A pair of inner transmission grooves 253 are arranged orthogonally to a pair of outer transmission grooves 251. The two transmission blocks 25 are also respectively arranged in the first piston structure 4 and the inner cavity of the second piston structure 18. The transmission groove 251 on the outer side of the transmission block 25 cooperates with the ball in the ball groove of the corresponding piston structure; a pair of shift forks 211a are symmetrically arranged on the transmission shaft 21 in the circumferential direction, and the shift forks 211a also extend along the transmission shaft. The dynamic shaft 21 is arranged in the length direction; the transmission shaft 21 is simultaneously arranged in the two transmission blocks 15, and the two transmission blocks 25 are spaced apart along the axial direction of the transmission shaft 21. The inner transmission groove 253 of any transmission block 25 cooperates with the shift fork 211a of the transmission shaft, and the two ends of the transmission shaft 21 cooperate with the first thrust bearing 22 and the second thrust bearing 27 respectively; the limiting parts 23 are distributed at both ends of any transmission block 25, and the limiting parts 23 are also fixedly sleeved on the transmission shaft 21 (that is, the limiting parts 23 cannot move along the axial direction of the transmission shaft 21, but can rotate with the transmission shaft 21), and the limiting parts 23 are used to limit the movement of the two transmission blocks 25 along the axial direction of the transmission shaft 21; wherein, during operation, the transmission shaft 21 drives the two transmission blocks 25 to rotate, and the two transmission blocks 25 transmit torque to the first piston structure 4 and the second piston structure 18 through the balls, so that the first piston structure 4 and the second piston structure 18 rotate circumferentially.

[0147] That is, the transmission shaft assembly of the present invention can also adopt an orthogonal torque transmission structure.

[0148] In the embodiment of the present invention, bearing mounting columns 210 and 212 are provided on both sides of the transmission shaft 21 , and a pair of shift forks 211 a are radially extended from the middle optical axis.

[0149] The embodiment of the present invention incorporates a transmission block between the transmission shaft and the piston. A pair of shift forks are disposed within the inner bore of the piston, each with a ball groove. A pair of shift forks are disposed on the transmission shaft. The transmission block is provided with radially orthogonal transmission grooves. The outer grooves engage with the balls in the piston fork raceways, while the inner grooves engage with the shift forks on the transmission shaft. During operation, the shaft drives the transmission block to rotate (without relative axial motion between the two). The transmission block transmits torque to the piston via the balls, causing the piston to rotate circumferentially. With this orthogonal torque transmission structure, the transmission shaft and the piston are subjected to forces in orthogonal directions, and there is no radial force component, preventing the piston from squeezing the copper bushing. Even if the transmission shaft and the first or second piston are slightly misaligned, this can be adjusted adaptively by the transmission block. This reduces the coaxiality requirements for the transmission shaft and the upper or lower pump core, reduces the number of parts required for matching, and improves the processability of processing and assembly, significantly saving money and time.

[0150] Preferably, in order to prevent the balls 26 from falling out, ball blocking blocks 24 are added to both ends of any transmission block 25 for blocking.

[0151] Preferably, the two transmission blocks 25, the piston structure and the transmission shaft 21 are coaxially arranged; and / or, the transmission block 25 is a hollow cylindrical structure with openings at both ends.

[0152] As can be seen, the dual-motion-freedom piston pump of the present invention proposes a novel baffle-type piston structure, a novel double-sided flow distribution structure, and a novel drive shaft assembly structure (a cross-torque transmission structure and an orthogonal torque transmission structure). Specifically: 1) The present invention proposes a novel baffle-type piston structure. The piston has a large outer diameter, a small inner diameter, and no inner wall. The central cylindrical surface serves as the drainage surface, and two pairs of symmetrical inlets and outlets are distributed on either side. The oil enters the piston cavity directly without passing through a complex flow channel, which increases the pump's self-priming capacity. The piston inlet and outlet end faces have a beveled design, which effectively reduces hydraulic losses caused by the outer diameter end faces during piston rotation. The oil enters the piston cavity with almost no circumferential rotational motion. At the same time, the axial velocity of the oil is low due to the short piston stroke, resulting in minimal kinetic energy loss and a high energy conversion rate for the pump. At high speeds, the oil can quickly follow the axial motion of the piston and fill the piston cavity in a timely manner, greatly enhancing the pump's anti-cavitation capability. The piston has a through hole inside, and a pair of shift forks are radially arranged along the through hole. The shift forks have four ball grooves evenly distributed on them for torque transmission. 2) The embodiment of the present invention proposes a two-way flow distribution structure, which mainly includes a two-way flow distribution integrated baffle piston, a baffle bushing, an integrated cylinder body, etc. The two-way flow distribution integrated baffle piston is an integrated structure of a cam and a piston, the cam is located in the middle of the piston, and two inner and outer cylindrical sleeves grow symmetrically on both sides of the cam. The baffle bushing is nested and installed in the baffle piston to form a closed volume. A pair of oil distribution ports are respectively provided on the sleeve and the boss, and the two pairs of oil distribution ports are in orthogonal positions. The oil distribution port on the outer sleeve is an oil suction port, and the oil distribution port on the inner sleeve is an oil discharge port. A through hole is provided in the center of the inner sleeve, and a ball groove and a high-pressure groove are orthogonally provided on the through hole. The cross torque transmission / orthogonal torque transmission structure passes through the through hole and drives the piston to rotate through the balls. The piston and double-sided guide rails are integrated to form an integrated guide rail piston, and the cam is located in the middle of the piston. Compared with the previous guide rail and roller structure concentrated on one side, the roller can be distributed on the outside of the piston sleeve, which can make full use of the axial distance of the piston, effectively shorten the axial length of the pump, and reduce the volume of the pump; the piston and sleeve are both baffle structures, and the sleeve is used to replace the traditional cylinder parts. At the same time, the piston and sleeve are hollowed out in the middle and grooved circumferentially, which greatly reduces the weight of the pump and improves the power-to-weight ratio of the pump; at the same time, the piston and sleeve are both baffle structures, which have little effect on the stirring of the oil during rotation, reduce the oil stirring loss, and have high mechanical efficiency; the piston has double-sided flow distribution, and the oil suction port and oil discharge port are distributed on different cylinders, which indirectly increases the distance between the oil ports, increases the sealing length, effectively reduces leakage, and improves the volumetric efficiency of the pump. 3) This embodiment of the present invention proposes a cross-torque transmission structure. The through-drive shaft is replaced by an upper and lower drive shaft. Transmission blocks are added between the input drive shaft and the first drive shaft, and between the first and second drive shafts. Ball bearing grooves are defined on each of the upper and lower drive shafts. A pair of shift forks, each with ball bearing grooves, are radially disposed within the piston bore.The grooves of the transmission shaft cooperate with the balls in the piston fork raceway. In order to prevent the balls in the piston raceway from falling out, two limit pins are installed on each of the upper and lower transmission shafts to seal the balls. During operation, the input transmission shaft drives the transmission block to rotate, and the transmission block drives the first transmission shaft to rotate. The first transmission shaft transmits the torque to the first piston structure through the balls, causing the piston to rotate circumferentially. At the same time, under the action of the guide rail, it reciprocates axially. The lower pump core transmits torque in the same way. When transmitting torque in this structural form, there is a certain degree of misalignment between the upper and lower pump cores and the transmission shaft, which can be adaptively adjusted by the transmission block, reducing the precision requirements for processing parts. 4) An embodiment of the present invention proposes an orthogonal torque transmission structure, in which a transmission block is added between the transmission shaft and the piston, and a pair of forks are radially arranged on the inner hole of the piston, with ball grooves on the forks. There are bearing mounting columns on both sides of the transmission shaft, and a pair of forks grow radially from the middle optical axis. Transmission grooves are arranged radially orthogonally on the transmission block. The outer groove cooperates with the balls in the piston fork raceway, and the inner groove cooperates with the fork of the transmission shaft. In order to prevent the balls in the piston raceway from falling out, blocks are added to both transmission blocks for blocking. During operation, the shaft drives the transmission block to rotate (there is no relative axial movement between the two), and the transmission block transmits torque to the piston through the balls, causing the piston to rotate circumferentially and at the same time reciprocating axially under the action of the guide rail. With the orthogonal torque transmission structure, the transmission shaft and the piston are subjected to forces in orthogonal directions, and there is no radial force component, which will not cause the piston to squeeze the copper bushing. Even if there is a small degree of misalignment between the transmission shaft and the first / second piston structure, it can be adjusted adaptively by the transmission block, thereby reducing the coaxiality requirements of the transmission shaft and the upper / lower pump core, reducing the number of parts matching processing, improving the processability of processing and assembly, and greatly saving money and time costs.

[0153] It can be seen that the present invention provides a main / pre-boost integrated system, including a fuel tank, a dual-motion freedom main / pre-boost electric pump, a cooling electric pump, pipelines and other equipment. The system has two fuel delivery routes, one of which is a dual-motion freedom main / pre-boost electric pump for boosting and delivering fuel to the engine for combustion, and the other is a cooling electric pump for boosting and delivering fuel to the equipment, cooling the equipment and returning to the fuel tank. The present invention introduces a dual-motion freedom piston pump with strong self-priming ability as a boost pump, which does not require pre-boosting for the piston pump to inhale fuel, thereby realizing the main / pre-boost integration. Compared with gear pumps and centrifugal pumps, dual-motion free piston pumps have the advantage of high efficiency and can still maintain high efficiency under high temperature and high pressure conditions. Therefore, the main / pre-boost integrated piston pump has higher overall efficiency and consumes less energy than the main boost (gear pump) + pre-boost (centrifugal pump) split solution; the present invention does not require pre-boosting or piston pump suction oil, and the centrifugal electric pump of the present invention only needs to boost and deliver the fuel required for equipment cooling. Compared with the fuel flow required for engine combustion, the fuel flow required for equipment cooling is extremely small. Therefore, the power, volume and weight of the cooling electric pump in the present invention will be greatly reduced, thereby greatly reducing the weight of the entire system. In addition, the present invention adopts a high-speed motor as the driving motor of the main pump, which has a smaller volume and weight than a low-speed motor. However, the increase in speed does not significantly reduce the weight of the oil pump. On the contrary, too high a speed will have an adverse effect on the efficiency and suction characteristics of the oil pump. Therefore, the motor is decelerated by a reducer and drives the main pump to work, so that the overall benefit of the system is optimized. The present invention also connects the motor and the pump through a reducer. By using the various input and output forms of the reducer, the motor and the main pump can be installed in an "I" shape, or the motor and the pump can be installed in a "T" shape. The overall installation form is more flexible and can meet the installation requirements of different spatial layouts, especially better adapting to the requirements of the narrow envelope space of the aircraft.

[0154] In addition, the piston sleeve and double-sided guide rail of the dual-motion freedom piston pump of the present invention are integrated, and the rollers can be distributed on the outside of the piston sleeve, which can make full use of the axial distance of the piston, effectively shorten the axial length of the pump, reduce the volume weight of the pump, and improve the power-to-weight ratio of the pump; the piston and sleeve of the present invention are both baffle structures, and the sleeve is used to replace the traditional cylinder parts. At the same time, the piston and sleeve are hollowed out in the middle and grooved circumferentially, which greatly reduces the weight of the pump; the piston and sleeve of the present invention are both baffle structures, and the integrated guide rail piston encounters less resistance during reciprocating motion, and the oil stirring power loss is reduced, thereby improving the mechanical efficiency of the pump; the piston of the present invention is distributed on both sides, and the oil suction port and the oil discharge port are distributed on different cylinders, which indirectly increases the distance between the oil ports, increases the sealing length, effectively reduces the leakage, and improves the volumetric efficiency of the pump; the piston cavity oil suction port of the present invention is arranged on the guide rail piston outer sleeve and is directly connected to the oil. The oil can enter the piston cavity without passing through any flow channel, thereby effectively increasing the self-priming ability of the pump. The piston of the present invention is a baffle-type structure, and the oil entering the piston cavity hardly has circumferential rotational motion. At the same time, the axial speed of the oil is small due to the short piston stroke, the kinetic energy loss of the oil is extremely small, and the energy conversion rate of the pump is high. The piston of the present invention is a baffle-type structure. When the pump is at high speed, the oil can quickly follow the axial motion of the piston and fill the piston cavity in time, which greatly enhances the anti-cavitation ability of the pump. With the structure of the present invention, when the piston cavity is in the oil pressure stroke, the bushing produces a slight deformation under the action of the high-pressure oil, which makes the gap between the bushing and the piston smaller, reduces the leakage, and improves the volumetric efficiency. This gap compensation structure is also applicable at high temperatures. The present invention can also achieve decoupling of the rotational motion of the two-pump core through the cross-torsion transmission / orthogonal torque transmission structure, greatly reducing the coaxiality requirements of the two-pump core, making the transmission structure simpler, and solving the problem of piston eccentric wear under high speed and high pressure caused by the different axes of the series pump core. Specifically, compared with the fork roller torque transmission structure, the orthogonal / cross torque transmission structure of the present invention has a small volume, and the torque transmission structure is arranged inside the piston, which does not affect the axial length of the pump; and the orthogonal / cross torque transmission structure of the present invention has a light weight, a short turning radius, a small moment of inertia, good start-stop performance, and good pump control performance; compared with the external fork roller torque transmission structure, the orthogonal / cross torque transmission structure of the present invention is distributed inside the piston, with extremely small oil stirring loss, and is suitable for high-speed working conditions; the orthogonal / cross torque transmission structure of the present invention realizes the decoupling of the upper and lower pump cores in rotational motion, reduces the coaxiality requirements of the upper and lower pump cores, reduces the processing accuracy requirements, reduces processing costs, and improves economic benefits.

[0155] In the description of the present invention, it should be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "horizontal, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of the present invention; the directional words "inside and outside" refer to the inside and outside relative to the outline of each component itself.

[0156] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used herein to describe the spatial positional relationship of a device or feature to other devices or features as shown in the figures. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figures. For example, if the device in the drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0157] In addition, it should be noted that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present invention.

[0158] The foregoing description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Those skilled in the art will readily appreciate that various modifications and variations of the present invention are possible. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention are intended to be within the scope of protection of the present invention.

Claims

1. A main / pre-boost integrated system, comprising a device to be cooled and an engine, characterized in that: The system further comprises: a fuel tank storing fuel; The cooling electric pump and the dual-motion freedom piston pump main / pre-boost electric pump are respectively connected to the oil tank; the dual-motion freedom piston pump main / pre-boost electric pump includes a second drive unit and a main / pre-boost integrated dual-motion freedom piston pump, the main / pre-boost integrated dual-motion freedom piston pump includes a reducer and a dual-motion freedom piston pump, the dual-motion freedom piston pump includes a front end cover, a pump housing and a rear end cover, a drive shaft assembly and a pump core, the front end cover, the pump housing and the rear end cover are fixedly connected in sequence to form a pump housing structure; the pump core is arranged in the pump housing structure and is rotatably arranged on the drive shaft assembly, the pump core adopts an upper / lower two-pump core integrated series structure, the series structure includes a first piston structure and a second piston structure, the two are rotatably arranged on the drive shaft assembly at intervals along the axial direction of the drive shaft assembly. , the first piston structure and the second piston structure both adopt an integrated structure of piston and cam guide, the cam guide is located in the middle of the piston, and two sleeve structures are symmetrically grown on both sides of the cam guide, for any sleeve structure, it includes an outer cylinder and an inner cylinder located in the outer cylinder, the outer cylinder is circumferentially provided with a plurality of oil suction ports, the inner cylinder is circumferentially provided with a plurality of oil discharge ports, and any oil suction ports and any oil discharge ports are staggered; an annular cavity is formed between the outer cylinder and the inner cylinder, the annular cavities of the two sleeve structures are not connected, and the inner cylinders on both sides are connected to form an inner cavity of the piston structure; the reducer is rotatably connected to the transmission shaft assembly, and the second driving part drives the dual-motion freedom piston pump to operate through the reducer, so that the piston pump operates in a suitable working range, and the dual-motion freedom piston pump relies on its own self-priming ability to achieve fuel filling in the cavity; In which, the system has a first oil circuit and a second oil circuit. The first oil circuit is a cooling oil circuit. The fuel in the fuel tank is transported to the cooling electric pump, which is pressurized by the cooling electric pump and transported to the equipment to be cooled. After the fuel cools the equipment to be cooled, it returns to the fuel tank; the second oil circuit is an engine oil supply and delivery circuit. The fuel in the fuel tank is transported to a dual-motion degree of freedom piston pump, which is then transported to the engine for combustion.

2. The main / pre-boost integrated system according to claim 1, characterized in that: The cooling electric pump supplies the fuel flow required by the equipment to be cooled at a constant speed.

3. The main / pre-boost integrated system according to claim 1, characterized in that: The cooling electric pump includes a centrifugal pump and a first driving unit, wherein the first driving unit drives the centrifugal pump to pressurize the fuel and deliver it to the equipment to be cooled.

4. A main / pre-boost integrated system according to any one of claims 1-3, characterized in that: The reducer housing is fixedly connected to the pump housing structure of the dual-motion freedom piston pump, the reducer housing cavity is connected to the oil cavity of the dual-motion freedom piston pump, and the structure in the reducer cavity is immersed in fuel.

5. The main / pre-boost integrated system according to claim 4, characterized in that: The output shaft of the reducer is connected to the dual-motion freedom piston pump transmission shaft assembly, and the input shaft of the reducer and the transmission shaft assembly are in an "I" shape or a "T" shape.

6. The main / pre-boost integrated system according to claim 5, characterized in that: The reducer is a planetary gear reducer, or the reducer is a bevel gear reducer.

7. The main / pre-boost integrated system according to claim 3, characterized in that: The first driving part is a driving motor, and the second driving part is a high-speed driving motor.

8. The main / pre-boost integrated system according to claim 4, characterized in that: The series structure also includes a first bushing, a second bushing and a pump core support frame, the first bushing, the first piston structure, the pump core support frame, the second piston structure, and the second bushing are coaxially arranged along the axis of the transmission shaft assembly in sequence, the first bushing and the second bushing both include a baffle and a bushing sleeve arranged on the baffle, the bushing sleeve is composed of a bushing outer tube and a bushing inner tube located in the bushing outer tube, an annular cavity is formed between the bushing inner and outer tubes, the bushing sleeve is uniformly distributed with a plurality of oil distribution ports along the circumference, any of the oil distribution ports passes through the bushing outer tube and the bushing inner tube at the same time, the baffle has an inner hole passing through the baffle, the inner hole is connected to the bushing inner tube, forming an inner cavity of the bushing; the The pump core support frame adopts an integrated cylinder structure, including a pump core support frame body, the pump core support frame body is fixedly connected to the pump housing, an oil discharge channel is opened inside the pump core support frame body, a first support arm bushing assembly and a second support arm bushing assembly grow out of both ends of the pump core support frame body, the two assemblies are staggered at a preset angle, the first support arm bushing assembly is composed of a first support arm assembly and a first bracket sleeve, the second support arm bushing assembly is composed of a second support arm assembly and a second bracket sleeve, the first bracket sleeve and the second bracket sleeve have the same structure as the bushing sleeve, wherein the inner tube of the first bracket sleeve and the inner tube of the second bracket sleeve are both connected to the oil discharge channel, forming an inner cavity of the pump core support frame; Among them, the first bushing, the first piston structure and the first support arm bushing assembly cooperate with each other, the second bushing, the second piston structure and the second support arm bushing assembly cooperate with each other, the piston structure is arranged between the corresponding bushing and the support arm bushing assembly, and the inner cavities of the first bushing, the first piston structure, the pump core support frame and the second bushing are connected in sequence; the support arm assembly is fixedly connected to the baffle of the corresponding bushing, the bushing sleeve is embedded in the annular cavity of the sleeve on one side of the corresponding cam guide rail to form a closed oil chamber, and the corresponding bracket sleeve is embedded in the annular cavity of the sleeve on the other side of the cam guide rail to form another closed oil chamber, and the four closed oil chambers of the series structure perform oil suction and discharge work regularly.

9. The main / pre-boost integrated system according to claim 8, characterized in that: The series structure also includes a first end cover and a second end cover, the first end cover is fixedly connected to the baffle of the first bushing, the first end cover has an inner hole passing through the first end cover and communicating with the inner hole on the baffle, the first end cover and the bushing sleeve on the baffle are respectively arranged on both sides of the baffle, the second end cover is fixedly connected to the baffle of the second bushing, and is respectively arranged on both sides of the baffle with the bushing sleeve on the baffle.

10. The main / pre-boost integrated system according to claim 9, characterized in that: The piston pump also includes a first thrust bearing and a second thrust bearing, which are respectively arranged at the first end cover and the second end cover. One end of the transmission shaft assembly is matched with the first thrust bearing and is arranged in the inner hole of the first end cover. This end is the power input end. The other end of the transmission shaft assembly is matched with the second thrust bearing.

11. The main / pre-boost integrated system according to claim 1, characterized in that: In the first piston structure and the second piston structure, for any sleeve structure, a pair of oil suction ports are symmetrically opened on the outer tube, and a pair of oil discharge ports are symmetrically opened on the inner tube, and the pair of oil suction ports and the pair of oil discharge ports are orthogonally arranged; for any bushing sleeve, a pair of symmetrically arranged oil distribution ports are opened on the bushing sleeve along its circumference, and any of the oil distribution ports is composed of the oil distribution port on the outer tube of the bushing and the oil distribution port on the inner tube of the bushing, and the oil distribution port on the outer tube of the bushing and the oil distribution port on the inner tube of the bushing are arranged parallel to each other.

12. The main / pre-boost integrated system according to claim 11, characterized in that: Any of the oil distribution ports further extends to the free end of the corresponding sleeve.

13. A main / pre-boost integrated system according to claim 11 or 12, characterized in that: The end face of the oil suction port adopts a beveled surface design, wherein the outer opening area of the oil suction port is larger than the inner opening area; and / or, the end face of the oil discharge port adopts a beveled surface design, wherein the outer opening area of the oil discharge port is larger than the inner opening area.

14. The main / pre-boost integrated system according to claim 13, characterized in that: The cross-sectional area of the oil suction port is larger than the cross-sectional area of the oil discharge port.

15. The main / pre-boost integrated system according to claim 8, characterized in that: A plurality of shift forks are symmetrically grown along the radial direction on the inner cavity of the piston structure, and a linear ball groove is opened on the shift fork for transmitting torque by balls.

16. The main / pre-boost integrated system according to claim 15, characterized in that: A high-pressure flow channel is processed on the inner cavity wall except the shift fork, and the high-pressure flow channel is communicated with the oil discharge port and the oil discharge flow channel.

17. The main / pre-boost integrated system according to claim 8, characterized in that: The pump core support frame body is in the shape of a truncated cone, and an annular groove is provided on the circumferential side wall of the truncated cone. The annular groove is provided with a body oil discharge port and communicates with the oil discharge channel in the body. A high-pressure chamber is formed between the annular groove and the pump casing.

18. The main / pre-boost integrated system according to claim 17, characterized in that: A plurality of oil passage grooves are provided on the pump core support frame body along the circumferential direction. Any of the oil passage grooves is arranged along the axial direction of the pump core support frame body and is not connected to the oil discharge channel. The oil passage grooves are used to achieve oil flow throughout the pump casing.

19. The main / pre-boost integrated system according to claim 15, characterized in that: The first support arm assembly and the second support arm assembly are both composed of two symmetrically arranged support arms; the cam guide is a double-sided cam guide; the series structure is a double-sided flow distribution structure, and the double-sided flow distribution structure also includes a first roller frame assembly and a second roller frame assembly, the first roller frame assembly cooperates with the first support arm assembly and the first piston structure, the second roller frame assembly cooperates with the second support arm assembly and the second piston structure, the first roller frame assembly and the second roller frame assembly each include two groups of roller assemblies, the two groups of roller assemblies are arranged at intervals along the length direction of the corresponding support arm assembly, any of the roller assemblies includes a roller frame and a plurality of rollers, the roller frame is fixedly connected to the corresponding two support arms, and the plurality of rollers are arranged at intervals along the circumference of the roller frame on the inner wall of the roller frame, and the corresponding double-sided cam guide is clamped between the plurality of rollers of the two groups of roller assemblies, wherein, when the piston structure rotates, the rollers of the two groups of roller assemblies can respectively move circumferentially along the two sides of the double-sided cam guide.

20. The main / pre-boost integrated system according to claim 15, characterized in that: The transmission shaft assembly includes an input transmission shaft, a first transmission block, a first transmission shaft, a second transmission block and a second transmission shaft connected in sequence; the first transmission block has two end surfaces with orthogonally distributed slide grooves a and slide grooves b; the second end surfaces of the second transmission block have two end surfaces with orthogonally distributed slide grooves c and slide grooves d; one end of the input transmission shaft is the power input end, which cooperates with the first thrust bearing, and the other end is a flat square structure c, which cooperates with the slide groove a; the first transmission shaft is arranged in the inner cavity of the first piston structure, and a plurality of linear ball grooves parallel to the axis are uniformly distributed on its circumference, which are used to for placing balls and cooperating with the linear ball groove of the first piston structure; the two ends of the first transmission shaft are respectively provided with a flat square structure a and a flat square structure b, which respectively cooperate with the slide groove b and the slide groove c; the second transmission shaft is arranged in the inner cavity of the second piston structure, and is circumferentially provided with a plurality of linear ball grooves parallel to the axis, which are used to place balls and cooperate with the linear ball grooves of the second piston structure; one end of the second transmission shaft is further provided with a flat square structure d, which cooperates with the slide groove d; the other end of the second transmission shaft cooperates with the second thrust bearing; Among them, any slide groove has multiple inner wall surfaces, some of the multiple inner wall surfaces are set as transmission surfaces, and the rest are set as non-transmission surfaces. The transmission surfaces of the two end surface slide grooves on the same transmission block are perpendicular to each other. The flat square structure a, flat square structure b, flat square structure c and flat square structure d all have transmission surfaces and non-transmission surfaces that match the corresponding slide grooves. The transmission surface of any flat square structure fits tightly with the transmission surface of the corresponding slide groove, and there is a gap between the non-transmission surface of any flat square structure and the non-transmission surface of the corresponding slide groove. During operation, the input drive shaft and the first drive shaft can slide along the normal direction of the non-transmission surface while transmitting torque through the transmission surface. The first drive shaft and the second drive shaft can also slide along the normal direction of the non-transmission surface while transmitting torque through their transmission surfaces.

21. The main / pre-boost integrated system according to claim 20, characterized in that: Any sliding groove is a rectangular groove, wherein a group of two inner wall surfaces of the rectangular groove arranged parallel to each other are set as transmission surfaces, and the remaining two surfaces are non-transmission surfaces.

22. A main / pre-boost integrated system according to claim 20 or 21, characterized in that: The length of the transmission surface is greater than the length of the non-transmission surface.

23. The main / pre-boost integrated system according to claim 20, characterized in that: Any of the linear ball grooves is not filled with balls, and the length of the linear ball groove without balls is , ,in is the guide rail stroke of the piston pump.

24. The main / pre-boost integrated system according to claim 23, characterized in that: The length of any linear ball groove is L: , where L is the length of the linear ball groove, D is the ball diameter, and n is the number of balls. is the guide rail travel.

25. The main / pre-boost integrated system according to claim 15, characterized in that: The transmission shaft assembly includes: Two transmission blocks are respectively arranged in a one-to-one correspondence with the first piston structure and the second piston structure. The transmission block is a hollow cylindrical structure with openings at both ends. A pair of inner transmission grooves are evenly opened on the inner cavity wall thereof in the circumferential direction; a pair of outer transmission grooves are evenly opened on the outer wall surface thereof in the circumferential direction. Any inner transmission groove and outer transmission groove are arranged along the length direction of the transmission block. A pair of inner transmission grooves and a pair of outer transmission grooves are arranged orthogonally. Any transmission block is arranged in the inner cavity of the corresponding piston structure, and the transmission groove on the outer side of the transmission block cooperates with the ball in the ball groove of the corresponding piston structure. A transmission shaft, wherein a pair of shift forks are symmetrically arranged on the transmission shaft in the circumferential direction, and the shift forks are also arranged along the length direction of the transmission shaft; the transmission shaft is simultaneously arranged in the two transmission blocks, and the two transmission blocks are spaced apart along the axis direction of the transmission shaft; the inner transmission groove of any transmission block cooperates with the shift fork of the transmission shaft, and the two ends of the transmission shaft cooperate with the first thrust bearing and the second thrust bearing respectively; A plurality of limiting parts, each of which is provided at both ends of any of the transmission blocks, and the limiting parts are also fixedly sleeved on the transmission shaft, and are used to limit the movement of the two transmission blocks along the axis of the transmission shaft; During operation, the transmission shaft drives the two transmission blocks to rotate, and the two transmission blocks transmit torque to the first piston structure and the second piston structure through the balls, so that the first piston structure and the second piston structure rotate circumferentially.

26. The main / pre-boost integrated system according to claim 25, characterized in that: The two transmission blocks, the first piston structure, the second piston structure and the transmission through-shaft are coaxially arranged; and / or the hollow cylindrical structure with openings at both ends is a hollow cylindrical structure with openings at both ends.

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