Combined radial plunger water hydraulic pump

Abstract

The invention discloses a combined radial plunger water hydraulic pump which comprises a hydraulic pump main body, two groups of functional units are arranged along the axial direction of the hydraulic pump main body, and four functional units in each group are respectively arranged on four side surfaces of the hydraulic pump main body. And a pump suction inlet pressurizing mechanism is arranged in a suction inlet at the tail end of the hydraulic pump main body. The functional unit is composed of a driven bevel gear module, a cam-roller transmission module comprising a plunger-cam shaft assembly, a cylinder module and a unit shell module. And runners on the unit shell and the unit cover are communicated with a liquid path on the main shell, so that flow division and flow collection of the functional unit and the pump main body part are realized. During working, a plurality of pairs of driving-driven bevel gears on the pump shaft transmit power to each functional unit, the cam, the roller, the half coupling sleeve and other components transmit the power to the plunger, and liquid suction and drainage functions are achieved through the cylinder body and the flow distribution windows in the plunger. The functional units are independently designed in structure and are very easy to disassemble and assemble; the characteristics that driving force is transmitted in the axial direction of the transmission shaft and a pressurizing mechanism is contained can allow higher working rotating speed, and the device is suitable for the working conditions that the displacement is large and water serves as a hydraulic medium.

Description

Technical Field

[0001] This invention belongs to the field of fluid transmission and control technology, and particularly relates to a combined radial plunger hydraulic pump. Background Technology

[0002] Because water, as a working medium, offers advantages such as low pollution, low cost, and better flame retardancy and safety, hydrohydraulic technology is applied in various industries including marine, shipbuilding, and coal mining. Deep-sea robotic arms, underwater robots, and seawater desalination plants all rely on deep-sea hydrohydraulic technology. Automotive cooling systems, high-pressure cleaning equipment, and hydraulic supports are also inseparable from hydrohydraulic technology. The hydrohydraulic pump, as a core component of the hydrohydraulic system, provides sufficient pressure and flow.

[0003] Existing water hydraulic pump products mainly include multi-plunger reciprocating pumps, axial piston pumps, gear pumps, and vane pumps. Among them, multi-plunger reciprocating pumps and axial piston pumps operate at high pressures. Due to the low viscosity, strong corrosiveness, and poor lubricity of water, water hydraulic pumps present a series of key technical challenges related to lubrication, sealing, wear, and corrosion. Currently, high-pressure water hydraulic pumps suffer from drawbacks such as rapid wear, frequent maintenance, and short service life, hindering the further development of water hydraulic technology. Summary of the Invention

[0004] To address the technical problems of existing high-pressure hydraulic pumps, such as rapid wear, frequent maintenance, and short service life, this invention provides a combined radial piston hydraulic pump. This invention features high operating speed, good lubrication, high mechanical efficiency, long service life, and a high-side-pressure pressure relief structure for the oil-water separation seal, making it easy to disassemble and replace.

[0005] The technical solution adopted in this invention is: A combined radial plunger hydraulic pump includes a hydraulic pump body. The hydraulic pump body (1) has a rectangular structure and multiple sets of functional units (2) are arranged axially. Each set of four functional units (2) is arranged on four sides of the hydraulic pump body (1). The functional units (2) are connected to the hydraulic pump body (1) via second-type screws (2403). Each functional unit (2) has suction and discharge ports corresponding to the flow channels on the hydraulic pump body (1) to achieve suction and discharge. In each set of four functional units (2), the plunger (2204) is in different working positions: left limit position, right limit position, middle leftward movement position, and middle rightward movement position. The positions of each set of functional units (2) are complementary to reduce flow pulsation. The hydraulic pump body (1) includes a pump shaft module (11) and a pump housing module (12). The pump shaft module (11) includes a pump shaft (1101) and a rotary oil seal (1103), two rolling bearings (1102), two drive bevel gears (1105), and a pump inlet booster mechanism (10) mounted on the pump shaft (1101). The pump housing module (12) includes a main housing (1201), a secondary housing (1202), and a pump cover (1203). Each functional unit (2) is installed on the inner holes of the four sides of the main housing (1201), and the contact surface and the flow channel are connected by a design. The seal is achieved using O-rings of type 8 (2410), type 9 (2411), and type 12 (2414); the sub-shell (1202) is connected to the main shell (1201) by bolts (1209) and is centered by a flange; the right end of the sub-shell (1202) is connected to the pump cover (1203), and the pump cover (1203) is embedded in the inner hole on the right side of the sub-shell (1202) to form a flow channel groove (12027); all contact surfaces between the main shell (1201), the sub-shell (1202), and the pump cover (1203) are sealed by O-rings of type 1 (2410), type 9 (2411), and type 12 (2414). 05) The second type of O-ring (1206) and the third type of O-ring (1212) are used for sealing; the pump shaft (1101) is installed on the main housing (1201), the left end of which contacts the right side shoulder of the main housing (1201) through the pump shaft bearing (1102), and the right side of which contacts the left side shoulder of the auxiliary housing (1202) through the pump shaft bearing (1102). Two active bevel gears (1105) are installed back to back on the pump shaft (1101); the pump inlet pressurization mechanism (10) includes a pressurization wheel (1109), which is installed in the inlet of the combined pump tail end. It is fixed to the pump shaft (1101) by a nut (1112) and located in the cavity formed by the sub-housing (1202) and the pump cover (1203); a mechanical seal device for separating the working fluid from the pump lubricating oil is provided on the left side of the booster wheel (1109). The mechanical seal device includes a mechanical seal stationary ring (1106), a mechanical seal dynamic ring (1107) and a mechanical seal retaining ring (1108). The mechanical seal stationary ring (1106) contacts the right shoulder of the sub-housing (1202), and the mechanical seal dynamic ring (1107) contacts the mechanical seal retaining ring (1108).

[0006] Furthermore, the functional unit (2) includes a driven bevel gear module (21), a cam-roller transmission module (22), a cylinder module (23), and a unit housing module (24); wherein: The driven bevel gear module (21) includes a driven bevel gear (211), steel balls (226), steel ball retaining rings (213), and a thrust combined bearing (214). The driven bevel gear (211) meshes with the driving bevel gear (1105). A camshaft (2201) is inserted into the inner hole of the driven bevel gear (211), and the semi-circular grooves (2111) evenly distributed on the inner hole of the driven bevel gear (211) and the semi-circular grooves (22011) evenly distributed on the camshaft (2201) form multiple rows of circular grooves evenly distributed along the axial direction. The steel balls 226 are embedded in the circular grooves to realize the connection between the driven bevel gear (211) and the camshaft (2201), so that the driven bevel gear (211) drives the camshaft (2201) to rotate through the steel balls (226). A ball retaining ring (213) is installed on the right end of the inner hole of the wheel (221), and is limited by a second type of elastic retaining ring (212). A limiting pin (216) is installed in the hole of the ball retaining ring (213) to limit the axial position of each row of balls (226). The back of the driven bevel gear (211) contacts the thrust combined bearing (214), which is installed in the center hole of the unit cover (2408). The shoulder of the thrust combined bearing (214) contacts the rightmost end of the unit cover (2408) to achieve axial positioning of the driven bevel gear (211). The driven bevel gear (211) is locked on one side of the center hole of the first roller frame (222) by a third type of elastic retaining ring (215), so that the first roller frame (222) is connected to the unit cover (2408). The cam-roller drive module (22) includes a plunger-camshaft assembly (220), a cam (221), rollers (227), a camshaft (2201), a cam half retainer ring (225), a half coupling sleeve (2203), a floating sleeve (2202), a first roller carrier (222), a second roller carrier (224), and a roller carrier clearance adjustment ring (223). The cam-roller drive module (22) is installed on the right side hole of the unit housing (2401). The cam (221) is connected to the camshaft (2201) by a fourth type key (2210). The first roller carrier (222) and the second roller carrier (224) are located on the cam. On both sides of (221), the first roller holder (222) and the second roller holder (224) are respectively equipped with two pairs of cylindrical rollers (227) arranged mirror-oriented relative to the cam (221). The two pairs of rollers (227) are in contact with the contours of the two end faces of the cam (221). The right end of the first roller holder (222) is in contact with the unit cover (2408). The first roller holder (222) and the second roller holder (224) are connected to the unit shell (2401) through the fifth type key (2211). The circumferential position of the two pairs of rollers (227) is fixed. When the cam (221) rotates, its contour surface is constrained by the two pairs of rollers (227), generating axial reciprocating motion. Both the cam (221) and the camshaft (2201) are provided with axial grooves (22012), and two cam half retaining rings (225) are installed in the axial grooves. The cam half retaining rings (225) are connected and positioned to the cam (221) by set screws (229) to limit the axial position of the cam (221). The plunger-camshaft assembly (220) includes a plunger (2204), a camshaft (2201), two half-coupling sleeves (2203), eight drive pins (2205), and a floating sleeve (2202). Drive pins (2205) are installed in the semi-circular grooves (22013) at the ends of the two half-coupling sleeves (2203), the semi-circular grooves (22041) at the ends of the camshaft (2201), and the plunger (2204). The floating sleeve (2202) is located outside the two half-coupling sleeves (2203), allowing the plunger (2204) and camshaft (2201) to be connected together. The plunger-camshaft assembly (220) is installed from left to right in the center hole of the second roller holder (224), the center hole of the cam (221), the center hole of the first roller holder (222), and the center hole of the driven bevel gear (211). During operation, the plunger-camshaft assembly (220), together with the cam (221) and the cam half retainer ring (225) fixed thereon, constitute the two-dimensional motion component of the functional unit. The power of the pump shaft (1101) is transmitted through the driven bevel gear module (21) to make the two-dimensional motion component of the functional unit rotate and reciprocate, thereby making the plunger (2204) rotate and reciprocate. The cylinder module (23) includes a cylinder (232), an O-ring retaining ring (233), a stop pin (237), and a plug seal (231) located on the right side of the cylinder (232). Each functional unit (2) has only one cylinder module (23). The cylinder (232) and the plug seal (231) are installed in the hole on the left side of the unit housing (2401) to realize the communication between the high and low pressure chambers of the cylinder (232) and the high and low pressure flow channels of the unit housing (2401). The two holes on the left and right sides of the unit housing (2401) are provided with shoulder holes. The shoulder holes of the unit housing (2401) block the right end of the plug seal (231) to realize the axial positioning of the cylinder (232). The plunger (2204) is inserted into the cylinder (232). 232) In the inner hole, the left end flange of the cylinder body (232) is provided with a half-pin hole (2321) for preventing rotation. The stop pin 237 is inserted into the half-pin hole (2321) to prevent the cylinder (232) from rotating in the unit housing (2401) and to ensure the relative position of the low pressure distribution window (2324) and high pressure distribution window (2325) on the cylinder body (232) and the roller (227) in the cam-roller drive module (22). The cylinder body cover (2402) is installed on the left side of the cylinder body (232) and is connected to the unit housing (2401) by screws (2403). The cylinder body cover (2402) is provided with a central blind hole. The plunger (2204) enters the central blind hole when moving axially. The unit housing module (24) includes a unit housing (2401), a cylinder head (2402), and a unit cover (2408). The unit housing (2401) is connected to the cylinder head (2402) and the unit cover (2408) by second-type screws (2403). The contact surfaces of the unit cover (2408), the cylinder head (2402), and the unit housing (2401) are sealed with sixth-type O-rings (236) and tenth-type O-rings (2412). High-pressure and low-pressure flow channels are respectively opened at the upper and lower ends of the unit housing (2401) and the unit cover (2408). The high-pressure and low-pressure flow channels of the unit housing (2401) are divided into two sections: an oblique flow channel. The high-pressure oblique flow channel is the first flow channel (24011), the DC flow channel is the second flow channel (24012); the low-pressure oblique flow channel is the third flow channel (24013), the DC flow channel is the fourth flow channel (24014); the oblique flow channels do not communicate with other components and are sealed with second-type screw plugs (2406) and third-type screw plugs (2407); the unit cover (2408) is installed on the unit shell (2401) by positioning pins (2405) to realize communication between the high and low pressure flow channels on the unit shell (2401) and the unit cover (2408), and the flow channel holes are sealed with seventh-type O-rings (2409) and eleventh-type O-rings (2413).

[0007] Furthermore, the cylinder body (232) is provided with two recessed grooves, namely a low-pressure groove (2322) and a high-pressure groove (2323). The high-pressure groove (2323) communicates with the first flow channel (24011) on the unit shell. The high-pressure groove (2323) has two mirror-oriented circular holes on the center line of the cylinder hole, forming two high-pressure distribution windows (2325) on the inner cylindrical surface of the cylinder body (232). The low-pressure groove (2322) communicates with the third flow channel (24013) on the unit housing. The cylinder low-pressure groove (2322) has two mirror-oriented circular holes on the cylinder bore centerline, forming two low-pressure distribution windows (2324) on the inner cylindrical surface of the cylinder (232). The diameter of the low-pressure distribution window (2324) is larger than the diameter of the high-pressure distribution window (2325), and the high and low-pressure distribution windows are staggered and arranged with a 90-degree phase difference. The plunger... (2204) has a flow-through inner hole on its end face. The plunger (2204) has a pair of symmetrically arranged plunger grooves (22042) in the radial direction. The plunger grooves (22042) are larger at the top and smaller at the bottom, with a trapezoidal cross-section, and communicate with the inner hole of the plunger (2204). The inner cylindrical surface of the cylinder (232), the inner hole surface of the plunger (2204), and the cylinder cover (2402) form a sealed cavity. The two radial plunger grooves (22042) of the plunger (2204) are connected to the cylinder. The four windows on (232) constitute the distribution valve port; during operation, the plunger (2204) makes periodic reciprocating motion, the sealed cavity increases or decreases, and at the same time, the plunger (2204) makes rotational motion, the low-pressure distribution window (2324) and the high-pressure distribution window (2325) open alternately, so that the sealed cavity communicates with the third flow channel (24013) and the first flow channel (24011) alternately, realizing the intake and discharge of the working medium in the functional unit (2).

[0008] Furthermore, the plug seal ring (231) divides the internal cavity of the unit housing (2401) into two parts. The cylinder module (23) on the left contains the working medium, and the unit housing (2401) on the right contains lubricating oil. The driven bevel gear module (21) and the cam-roller transmission module (22) are immersed in the lubricating oil. The end of the cylinder (232) that contacts the plug seal ring (231) communicates with two shallow grooves (2326) that are radially symmetrical to the cylinder low-pressure groove (2322). This is used to allow the working medium that leaks between the plunger (2204) and the cylinder (232) to the plug seal ring (231) to flow back into the cylinder low-pressure groove (2322), preventing the pressure on the water medium side of the plug seal ring (231) from increasing beyond its pressure resistance.

[0009] Furthermore, the driven bevel gear (211) is provided with a central hole, and a thrust combined bearing (214) is installed on the hub of the driven bevel gear (211). When the pump is working, the volume of the lubricating oil chamber in the functional unit (2) increases or decreases, and the lubricating oil in the functional unit (2) enters and exits the functional unit (2) through the gap between the central hole of the driven bevel gear (211) and the thrust combined bearing (214). The lubricating oil passing through the central hole of the driven bevel gear (211) is divided into two paths to enter and exit the interior of the functional unit (2). One is through the central hole of the camshaft (2201), and the other is through the gap between the camshaft (2201) and the steel ball groove connecting the driven bevel gear (211), as well as the gap of the thrust combined bearing (214), forming three lubricating oil channels that constitute three hydraulic resistances from small to large. And through these three lubricating oil channels, the heat in the functional unit (2) is carried into the hydraulic pump body (1).

[0010] Furthermore, the main shell (1201) has a fifth flow channel (12011), a sixth flow channel (12012), a seventh flow channel (12013), and an eighth flow channel (12014) arranged diagonally along the axial direction; each side of the main shell (1201) has a pair of high-pressure and low-pressure oblique flow channels, arranged alternately on adjacent sides, wherein the fifteenth flow channel (120111), the sixteenth flow channel (120112), the seventeenth flow channel (120113), and the eighteenth flow channel (120114) converge into the fifth flow channel (12011); the nineteenth flow channel (120121), the twentieth flow channel (120122), and the second The eleventh flow channel (120123) and the twenty-second flow channel (120124) converge into the sixth flow channel (12012); the twenty-third flow channel (120131), the twenty-fourth flow channel (120132), the twenty-fifth flow channel (120133), and the twenty-sixth flow channel (120134) converge into the seventh flow channel (12013); the twenty-seventh flow channel (120141), the twenty-eighth flow channel (120142), the twenty-ninth flow channel (120143), and the thirtieth flow channel (120144) converge into the eighth flow channel (12014), thus realizing the separation and collection of flow between the functional unit (2) and the hydraulic pump body (1); The sub-shell (1202) has a ninth flow channel (12021), a tenth flow channel (12022), an eleventh flow channel (12023), and a twelfth flow channel (12024) on its four diagonal sides. The ninth flow channel (12021) communicates with the sixth flow channel (12012); the tenth flow channel (12022) communicates with the seventh flow channel (12013). All are sealed by a type III O-ring (1212). The ninth flow channel (12021), the tenth flow channel (12022), and the twelfth flow channel (12024) are located at their respective corners. The flow channel (12022) is connected to the threaded hole to form two outlets; the eleventh flow channel (12023) is connected to the fifth flow channel (12011); the twelfth flow channel (12024) is connected to the eighth flow channel (12014), and both are sealed by the third type of O-ring (1212). The eleventh flow channel (12023) and the twelfth flow channel (12024) are connected to the flow channel groove (12027) and the central threaded hole of the pump cover (1203) to form a suction port.

[0011] Furthermore, the main housing (1201) has two oil inlets and two measuring interfaces on its four sides, which are sealed by screw plugs (1204) when not in use; the main housing (1201) is provided with countersunk holes to accommodate the head of the second type of screw (2403) on the right side of the functional unit (2); the flange has symmetrical countersunk grooves on both sides to accommodate large screws; the eleventh flow channel (12023) and the twelfth flow channel (12024) on the sub-housing (1202) are provided with a thirteenth flow channel (12025) and a fourteenth flow channel (12026) on the outside of the eleventh flow channel (12023) and the twelfth flow channel (12024), which are connected to the flow channel groove (12027) and sealed by a first type of screw plug (1211).

[0012] Furthermore, the cam (221) is a double-end-face spatial cam, and its motion law is an equal acceleration and deceleration curve from the low point to the high point. The two end face profiles of the cam (221) are "two high and two low", "three high and three low" or "four high and four low".

[0013] Furthermore, the floating sleeve (2202) is inside the center hole of the second roller holder (224) and sleeved on the outside of the two half-coupling sleeves. The inner and outer cylindrical surfaces of the floating sleeve form inner and outer sliding oil film supports through clearance fit with the outer cylindrical surface of the half-coupling sleeve and the center hole of the second roller holder, and satisfy the two-dimensional motion of the plunger-camshaft assembly.

[0014] Furthermore, the camshaft has a central through hole, an end face groove is provided on the end face where the camshaft connects with the plunger, a radial through hole is provided on the half coupling sleeve, and a shallow groove and a radial through hole are provided on the outer cylindrical surface of the floating sleeve. The lubricating oil enters the inner hole of the floating sleeve through the central hole of the camshaft, the end face groove where the camshaft connects with the plunger, and the radial through hole on the half coupling sleeve, and then enters the circumferential oil groove on the outer cylindrical surface of the floating sleeve through the radial through hole of the floating sleeve, forming a supporting oil film inside and outside the floating sleeve.

[0015] The working principle of this invention is as follows: The pump shaft rotates, and the torque is transmitted to each functional unit through the meshing of the driving bevel gear on the pump shaft and the driven bevel gear of each functional unit; the plunger-camshaft assembly, along with the cam and cam half-retaining ring fixed on it, constitutes the two-dimensional motion component of the functional unit. The torque, via the driven bevel gear module, causes the two-dimensional motion component of the functional unit to rotate and reciprocate, thereby causing the plunger to rotate and reciprocate; the through groove on the plunger and the distribution window on the cylinder form a distribution structure. When the plunger rotates, the volume of the sealed cavity continuously increases and decreases according to the movement law of the plunger, and liquid suction and discharge are realized through the distribution structure; the flow channels arranged on the main housing communicate with the flow channels on the functional units, realizing the diversion and collection of flow between the functional units and the pump body. At the same time, the booster wheel rotates with the pump shaft, and the generated centrifugal liquid flows through the flow channel groove to pressurize and transport the sucked working liquid into each functional unit.

[0016] This invention has the following advantages: For larger displacement requirements, the pump's displacement specifications can be increased by adding more functional units, forming a series of combined radial plunger hydraulic pumps. Each functional unit in the combined pump has an identical structure, the internal transmission structure of the functional units is rationally stressed, the operating speed is high, lubrication is good, mechanical efficiency is high, and service life is long. The high side pressure of the oil-water separation seal has a pressure relief structure and is easy to disassemble and replace. Because the force acting on the plunger is in the same direction as the plunger's movement, the wear between the plunger and the cylinder is small, allowing the pump to maintain a high volumetric efficiency throughout its service life. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the structure of the present invention.

[0018] Figure 2 This is a structural schematic diagram of the main body of the pump.

[0019] Figure 3 This is a structural diagram of a functional unit.

[0020] Figure 4 This is an exploded view of the cylinder block plunger module and related housing.

[0021] Figure 5 This is an exploded view of the driven bevel gear, cam-roller transmission module, and related housing.

[0022] Figure 6 This is an exploded view of the main body of the pump.

[0023] Figure 7 This is an exploded view of the pump housing module, used to illustrate the flow path.

[0024] Figure 8 This is a schematic diagram of the cylinder block.

[0025] Explanation of reference numerals in the attached drawings: 1-Hydraulic pump body; 10-Suction inlet booster mechanism; 11-Pump shaft module; 1101-Pump shaft; 1102-Pump shaft bearing; 1103-Skeleton oil seal; 1104-Type I elastic retaining ring; 1105-Driving bevel gear; 1106-Mechanical seal stationary ring; 1107-Mechanical seal moving ring; 1108-Mechanical seal retaining ring; 1109-Booster wheel; 1110-Gasket; 1111-Type I spring washer; 1112-Type I nut; 1113-Type I key; 1114-Type II key; 1115-Type III key; 12-Pump housing module; 1201-Main housing; 12011-Fifth flow channel; 120111-Fifteenth flow channel; 120112-Sixteenth flow channel; 120 113 - Seventeenth flow channel; 120114 - Eighteenth flow channel; 12012 - Sixth flow channel; 120121 - Nineteenth flow channel; 120122 - Twentieth flow channel; 120123 - Twenty-first flow channel; 120124 - Twenty-second flow channel; 12013 - Seventh flow channel; 120131 - Twenty-third flow channel; 120132 - Twenty-fourth flow channel; 120133 - Twenty-fifth flow channel; 120134 - Twenty-sixth flow channel; 12014 - Eighth flow channel; 120141 - Twenty-seventh flow channel; 120142 - Twenty-eighth flow channel; 120143 - Twenty-ninth flow channel; 120144 - Thirtieth flow channel; 1202 - Subshell; 12021 - Ninth flow channel; 12022 - Tenth flow channel 12023-Eleventh flow channel; 12024-Twelfth flow channel; 12025-Thirteenth flow channel; 12026-Fourteenth flow channel; 12027-Flow channel groove; 1203-Pump cover; 1204-Plug; 1205-Type I O-ring; 1206-Type II O-ring; 1207-Type II nut; 1208-Type II spring washer; 1209-Bolt; 1210-Type I screw; 1211-Type I plug; 1212-Type III O-ring; 2-Functional unit; 21-Bevel gear module; 211-Driven bevel gear; 2111-Driven bevel gear semi-circular groove; 212-Type II elastic retaining ring; 213-Steel ball retaining ring; 214-Thrust combined bearing; 215-Type III elastic retaining ring; 2 16-Limit pin; 22-Cam-roller drive module; 221-Cam; 22101-Cam groove; 222-Roller carrier 1; 223-Roller carrier clearance adjusting ring; 224-Roller carrier 2; 225-Cam retaining ring; 226-Steel ball; 227-Roller; 228-Roller shaft; 229-Set screw; 2210-Fourth type key; 2211-Fifth type key; 220-Plunger-camshaft assembly; 2201-Camshaft; 22011-Camshaft semi-circular groove; 22012-Camshaft groove; 22013-Camshaft end semi-circular groove; 2202-Floating sleeve; 2203-Half coupling sleeve; 2204-Plunger; 22041-Plunger semi-circular groove; 22042-Plunger through groove; 2205-Drive pin;23-Cylinder block module; 231-Plug seal ring; 232-Cylinder block; 2321-Cylinder block anti-rotation half pin hole; 2322-Cylinder block low-pressure groove; 2323-Cylinder block high-pressure groove; 2324-Cylinder block low-pressure distribution window; 2325-Cylinder block high-pressure distribution window; 2326-Cylinder block shallow groove; 233-O-ring retainer ring; 234-Type IV O-ring; 235-Type V O-ring; 236-Type VI O-ring; 237-Stop pin; 24-Unit housing module; 2401-Unit housing; 24011-First flow channel 24012 - Second flow channel; 24013 - Third flow channel; 24014 - Fourth flow channel; 2402 - Cylinder block head; 2403 - Second type screw; 2404 - Third type spring washer; 2405 - Locating pin; 2406 - Second type plug; 2407 - Third type plug; 2408 - Unit cover; 2409 - Seventh type O-ring; 2410 - Eighth type O-ring; 2411 - Ninth type O-ring; 2412 - Tenth type O-ring; 2413 - Eleventh type O-ring; 2414 - Twelfth type O-ring. Detailed Implementation

[0026] The technical solution of this invention will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this invention, not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without inventive effort are within the scope of protection of this invention.

[0027] In the description of this invention, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing the invention and simplifying the description. They do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. All orientation terms are described based on the schematic diagrams. Furthermore, the terms "first," "second," "third," "first type," "second type," and "third type" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0028] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0029] In this embodiment, the hydraulic pump body 1 can accommodate up to eight functional units 2. This embodiment is used to introduce the combined radial water hydraulic pump.

[0030] refer to Figures 1 to 8 This invention discloses a combined radial plunger hydraulic pump, comprising a hydraulic pump body 1, which has a rectangular structure and multiple sets of functional units 2 arranged axially, with each set of four functional units 2 arranged on four sides of the body 1. In each set of four functional units 2, the plunger 2204 is in different working positions: left extreme position, right extreme position, intermediate position (moving to the left), and intermediate position (moving to the right). The positions of each set of functional units 2 are complementary, thereby reducing flow pulsation.

[0031] In this embodiment, the hydraulic pump body 1 is composed of a pump shaft module 11 and a pump housing module 12. The pump shaft module 11 includes a pump shaft 1101, a rotary oil seal 1103 mounted on the pump shaft 1101, two rolling bearings 1102, two drive bevel gears 1105, and a pump inlet pressurization mechanism 10. The pump housing module 12 mainly includes a main housing 1201, a secondary housing 1202, and a pump cover 1203. Each functional unit 2 is installed on the inner holes of four sides of the main housing 1201, and the contact surface and the flow channel are sealed with O-rings 2410, 2411, and 2414. The secondary housing 1202 is connected to the main housing 1201 by a second type of nut 1207 and a bolt 1209. A second type of spring washer 1208 is installed between the second type of nut 1207 and the bolt 1209 to prevent loosening. At the same time, the secondary housing 1202 is centered by a flange. The right end of the sub-housing 1202 is connected to the pump cover 1203 by a first type of screw 1210. At the same time, the pump cover 1203 is embedded in the inner hole on the right side of the sub-housing 1202 to form a flow channel groove 12027. All contact surfaces between the main housing 1201, the sub-housing 1202 and the pump cover 1203 are sealed by O-rings 1205, 1206 and 1212.

[0032] In this embodiment, the pump shaft 1101 is mounted on the main housing 1201. Its left side contacts the right shoulder of the main housing 1201 via a pump shaft bearing 1102. A skeleton oil seal 1103 is installed in the central inner hole of the main housing 1201, with its right end contacting the left end of the pump shaft bearing 1102. The left end of the skeleton oil seal 1103 is limited by a first-type elastic retaining ring 1104. The right side of the pump shaft bearing 1102 contacts the left shoulder of the secondary housing 1202. The protruding portion of the left end of the pump shaft is connected to the motor via a third-type key 1115. Two driving bevel gears 1105 are mounted "back-to-back" on the pump shaft 1101 and connected to it via a second-type key 1114. In the pump inlet pressurization mechanism 10, the pressurization wheel 1109 is installed inside the inlet of the combined pump tail end and is connected to the pump shaft 1101 via a first type key 1113. Simultaneously, the pressurization wheel 1109 is axially fixed via a first type nut 1112. A first type spring washer 1111 is installed between the first type nut 1112 and the pressurization wheel 1109 to prevent loosening, and a gasket 1110 is also installed. The pressurization wheel 1109 is installed in the cavity formed by the sub-housing 1202 and the pump cover 1203. To achieve separation of the working fluid from the pump lubricating oil and prevent mutual leakage between the lubricating oil in the hydraulic pump body 1 and the working fluid in the inlet, the mechanical seal device is installed on the left side of the pressurization wheel. The mechanical seal stationary ring 1106 contacts the right shoulder of the sub-housing 1202, and the mechanical seal moving ring 1107 contacts the mechanical seal retaining ring 1108.

[0033] In this embodiment, the eight functional units 2 have identical structures, so only the structural features of one functional unit 2 are described: the functional unit 2 is a functional component consisting of a driven bevel gear module 21, a cam-roller transmission module 22, a cylinder module 23, and a unit housing module 24. The functional unit 2 is connected to the hydraulic pump body 1 by screws 2403, and the driven bevel gear 211 on the functional unit 2 meshes with the driving bevel gear 1105 on the pump shaft 1101 in the hydraulic pump body 1.

[0034] The driven bevel gear module 21 mainly includes a driven bevel gear 211, steel balls 226, a steel ball retaining ring 213, and a thrust combined bearing 214. A camshaft 2201 is inserted into the inner hole of the driven bevel gear 211. The semi-circular grooves 2111 evenly distributed on the inner hole of the driven bevel gear 211 and the semi-circular grooves 22011 evenly distributed on the camshaft 2201 form multiple rows of axially evenly distributed circular grooves. Steel balls 226 are embedded into these grooves, connecting the driven bevel gear 211 to the camshaft 2201, thereby causing the driven bevel gear 211 to drive the camshaft 2201 to rotate via the steel balls 226. A steel ball retaining ring 213 is installed at the right end of the inner hole of the driven bevel gear 221 and is limited by an elastic retaining ring 212. A limiting pin 216 is installed inside the hole of the steel ball retaining ring 213 to limit the axial position of each row of steel balls 226. The driven bevel gear 211 contacts the back of the thrust combined bearing 214, which is installed in the center hole of the unit cover 2408. The shoulder of the thrust combined bearing 214 contacts the rightmost end of the unit cover 2408 to achieve axial positioning of the driven bevel gear 211. The driven bevel gear 211 is locked in place on one side of the center hole of the roller frame 222 by the elastic retaining ring 215, so that the roller frame 222 and the unit cover 2408 are connected together.

[0035] In this embodiment, the cam-roller transmission module 22 mainly includes a cam 221, a roller 227, a camshaft 2201, a cam half retaining ring 225, a half coupling sleeve 2203, a floating sleeve 2202, a roller carrier 222, a roller carrier 224, and a roller carrier clearance adjustment ring 223. The cam-roller transmission module 22 is installed on the right side hole of the unit housing 2401. The cam 221 is a double-end-face spatial cam, and the end face profile of the double-end-face spatial cam is "two highs and two lows". The motion law of the cam 221 from the low point to the high point is a constant acceleration and deceleration curve. In addition, the end face profiles of the cam 221 can also be "three highs and three lows" or "four highs and four lows". The cam 221 is connected to the camshaft 2201 via a key 2210. Two roller holders are located on both sides of the cam 221. Two pairs of cylindrical rollers 227 are mounted on the roller holders 222 and 224, mirror-arranged relative to the cam 221. The two pairs of rollers 227 contact the contours of the two end faces of the cam 221, respectively. The right end of the roller holder 222 contacts the unit cover 2408. Since the two roller holders are connected to the unit cover 2401 via a key 2211, and the circumferential positions of the two pairs of rollers 227 are fixed, when the cam 221 rotates, its contour surface is constrained by the two pairs of rollers 227, resulting in axial reciprocating motion.

[0036] Both the cam 221 and the camshaft 2201 have axial grooves. Two cam half-retaining rings 225 are installed on the camshaft 2201 to limit the axial position of the cam 221. When installing the cam half-retaining rings 225, the two cam half-retaining rings 225 are first inserted radially into the grooves 22012 on the camshaft 2201. After rotating a certain angle, the threaded holes of the cam 221 and the cam half-retaining rings 225 are aligned. At this time, the two cam half-retaining rings 225 are just inserted into the grooves 22101 of the cam 221. Then, the cam half-retaining rings 225 and the cam 221 are connected and positioned by the set screws 229.

[0037] In the cam-roller transmission module 22, the plunger-camshaft assembly 220 consists of a plunger 2204, a camshaft 2201, two half-coupling sleeves 2203, eight drive pins 2205, and a floating sleeve 2202. Drive pins 2205 are installed in the semi-circular grooves 22013 and 22041 at the ends of the two half-coupling sleeves 2203, the camshaft 2201, and the plunger 2204. The floating sleeve 2202 is installed on the outside of the two half-coupling sleeves 2203, connecting the plunger 2204 and the camshaft 2201 together. The plunger-camshaft assembly 220 is installed from left to right in the center holes of the roller carrier 224, the cam 221, the roller carrier 222, and the driven bevel gear 211. During operation, the plunger-camshaft assembly 220, along with the cam 221 and cam half retainer ring 225 fixed thereon, constitutes the two-dimensional motion assembly of functional unit 1. The pump shaft 1101 drives the two-dimensional motion assembly of functional unit 2 to rotate and reciprocate via the driven bevel gear module 21, thereby causing the plunger 2204 to rotate and reciprocate.

[0038] The cylinder module 23 includes a cylinder 232, an O-ring and a retaining ring, a stop pin 237, and a plug seal 231 located on the right side of the cylinder 232. Each functional unit 2 has only one cylinder module 23. The cylinder 232 and the plug seal 231 are installed in a hole on the left side of the unit housing 2401. The unit housing 2401 has shoulders in both holes, which block the right end of the plug seal 231, achieving axial positioning of the cylinder 232. Simultaneously, a plunger 2204 is inserted into the inner hole of the cylinder 232. The flange at the left end of the cylinder 232 has an anti-rotation half-pin hole 2321. After inserting the stop pin 237, it not only prevents the cylinder 232 from rotating within the unit housing 2401 but also ensures the relative position of the distribution window on the cylinder 232 and the roller 227 in the cam-roller drive module 22. A cylinder cover 2402 is installed on the left side of the cylinder block 232 and is connected to the unit housing 2401 by screws 2403. The cylinder cover 2402 has a central blind hole, which allows the plunger 2204 to enter the hole during axial movement.

[0039] The cylinder body 232 has two cutting grooves, namely a low-pressure groove 2322 and a high-pressure groove 2323, which are separated by a fourth type of O-ring 234. The high-pressure groove 2323 communicates with the first flow channel 24011 on the unit shell. Two mirror-oriented circular holes are drilled from the high-pressure groove 2323 downwards towards the center line of the cylinder bore, forming two high-pressure distribution windows 2325 on the inner cylindrical surface of the cylinder body 232. The low-pressure groove 2322 communicates with the third flow channel 24013 on the unit shell. Two mirror-oriented circular holes are drilled from the low-pressure groove 2322 downwards towards the center line of the cylinder bore, forming two low-pressure distribution windows 2324 on the inner cylindrical surface of the cylinder body 232. The diameter of the low-pressure distribution window 2324 is larger than that of the high-pressure distribution window 2325 to reduce the liquid resistance during liquid suction. The high and low pressure distribution windows are staggered and 90 degrees out of phase. The plunger 2204 is inserted into the cylinder 232. A flow-through inner hole is opened on the end face of the plunger 2204. A pair of symmetrically arranged through grooves 22042 are opened radially on the plunger 2204. The through grooves 22042 are larger at the top and smaller at the bottom, with a trapezoidal cross-section, and communicate with the inner hole of the plunger 2204. A sealed cavity is formed between the cylindrical surface of the cylinder 232, the inner surface of the plunger 2204, and the cylinder cover 2402. The sealed cavity is separated from the high-pressure groove 2323 by the fifth type O-ring 235 and the sixth type O-ring 236. The two radial through grooves 22042 of the plunger 2204 and the four windows on the cylinder 232 constitute the flow distribution valve port. During operation, as the plunger 2204 makes periodic reciprocating motion, the sealed cavity increases or decreases. At the same time, the plunger 2204 rotates, and the low-pressure 2324 and high-pressure 2325 distribution windows open alternately, so that the sealed cavity communicates alternately with the third flow channel 24013 and the first flow channel 24011, realizing the intake and discharge of the working medium in functional unit 2.

[0040] In addition, the plug seal 231 divides the internal cavity of the unit housing 2401 into two parts. The cylinder module 23 on the left side contains the working medium, while the space inside the unit housing 2401 on the right side is filled with lubricating oil, so that the driven bevel gear module 21 and the cam-roller transmission module 22 are both immersed in the lubricating oil. The end of the cylinder 232 that contacts the plug seal 231 communicates with two radially symmetrical shallow grooves 2326 in the low-pressure groove 2322, which are used to allow the working medium that leaks between the plunger 2204 and the cylinder 232 to the plug seal 231 to flow back into the low-pressure groove 2322, preventing the pressure on the water medium side of the plug seal 231 from increasing beyond its pressure resistance.

[0041] In this embodiment, the driven bevel gear 211 has a central hole, and a thrust bearing 214 is mounted on its hub. When the pump is working, with the reciprocating motion of the plunger-camshaft assembly 220, the volume of the lubricating oil chamber in the functional unit 2 increases or decreases. The lubricating oil in the functional unit 2 enters and exits the functional unit 2 through the gap between the central hole of the driven bevel gear 211 and the thrust bearing 214. The lubricating oil passing through the central hole of the driven bevel gear 211 is divided into two paths to enter and exit the interior of the functional unit 2. One path is through the central hole of the camshaft 2201, and the other is through the gap between the camshaft 2201 and the connecting steel ball groove of the driven bevel gear 211, as well as the gap of the thrust bearing 214, forming three lubricating oil channels that constitute three hydraulic resistances from small to large. The heat in the functional unit 2 is carried into the hydraulic pump body 1 through these three lubricating oil channels.

[0042] In this embodiment, the unit housing module 24 mainly includes a cylinder cover 2402, a unit housing 2401, and a unit cover 2408. The unit housing 2401 is connected to the other two via screws 2403 and is equipped with a third type of spring washer 2404 for anti-loosening. The contact surfaces of the unit cover 2408, cylinder cover 2402, and unit housing 2401 are sealed with O-rings 236 and 2412. High-pressure and low-pressure flow channels are respectively opened at the upper and lower ends of the unit housing 2401 and unit cover 2408. The high-pressure and low-pressure flow channels of the unit housing 2401 are each divided into two sections: an oblique flow channel and a direct flow channel. The high-pressure oblique flow channel is the first flow channel 24011, and the direct flow channel is the second flow channel 24012; the low-pressure oblique flow channel is the third flow channel 24013, and the direct flow channel is the fourth flow channel 24014. The oblique flow channels do not communicate with other components, therefore they are sealed with screw plugs 2406 and 2407. The cylinder body 232 is installed in the left inner hole of the unit housing 2401, enabling communication between the high and low pressure chambers of the cylinder body 232 and the high and low pressure flow channels of the unit housing 2401. At the same time, the unit cover 2408 is installed on the unit housing 2401 through the positioning pin 2405, enabling communication between the high and low pressure flow channels on the unit housing 2401 and the unit cover 2408. The flow channel holes are sealed with O-rings 2409 and 2413.

[0043] In this embodiment, the main housing 1201 has a fifth flow channel 12011, a sixth flow channel 12012, a seventh flow channel 12013, and an eighth flow channel 12014 arranged diagonally along the axial direction. Each side of the main housing 1201 has a pair of high-pressure and low-pressure oblique flow channels, arranged alternately on adjacent sides. The fifteenth flow channel 120111, the sixteenth flow channel 120112, the seventeenth flow channel 120113, and the eighteenth flow channel 120114 converge into the fifth flow channel 12011. The nineteenth flow channel 120121, the second... The tenth flow channel 120122, the twenty-first flow channel 120123, and the twenty-second flow channel 120124 converge into the sixth flow channel 12012; the twenty-third flow channel 120131, the twenty-fourth flow channel 120132, the twenty-fifth flow channel 120133, and the twenty-sixth flow channel 120134 converge into the seventh flow channel 12013; the twenty-seventh flow channel 120141, the twenty-eighth flow channel 120142, the twenty-ninth flow channel 120143, and the thirtieth flow channel 120144 converge into the eighth flow channel 12014. Taking functional unit 2 (as shown in the diagram) as an example, the second flow channel 24012 communicates with the twenty-first flow channel 120123; the fourth flow channel 24014 communicates with the eighteenth flow channel 120114, and the flow channel holes are sealed with O-rings 2410 and 2414. Through the staggered arrangement of the flow channels, the flow channels on the two sets of functional units 2 converge to the two pairs of direct current channels 12011-12014 on the axial direction of the main housing 1201, realizing the flow separation and collection between functional unit 2 and hydraulic pump body 1. The sub-housing 1202 has a ninth flow channel 12021, a tenth flow channel 12022, an eleventh flow channel 12023, and a twelfth flow channel 12024 on its four opposite corners. Among them, the ninth flow channel 12021 communicates with the sixth flow channel 12012; the tenth flow channel 12022 communicates with the seventh flow channel 12013, both of which are sealed by O-rings 1212. At the same time, the ninth flow channel 12021 and the tenth flow channel 12022 are connected to threaded holes to form two discharge ports. The eleventh flow channel 12023 is connected to the fifth flow channel 12011; the twelfth flow channel 12024 is connected to the eighth flow channel 12014, and both are sealed by O-ring 1212. At the same time, the eleventh flow channel 12023 and the twelfth flow channel 12024 are connected to the flow channel groove 12027 and the central threaded hole of the pump cover 1203, forming a suction port.

[0044] In this embodiment, the main housing 1201 has two oil inlets and two measuring interfaces on its four sides, which are sealed by screw plugs 1204 when not in use. The main housing 1201 has countersunk holes to accommodate the head of the screw 2403 on the right side of the functional unit 2. The flange has symmetrical countersunk grooves on both sides to accommodate large screws. The eleventh flow channel 12023 and the twelfth flow channel 12024 on the sub-housing 1202 have a thirteenth flow channel 12025 and a fourteenth flow channel 12026 on their outer sides, which communicate with the flow channel groove 12027 and are sealed by screw plugs 1211.

[0045] The specific working principle of this invention is as follows: The pump shaft 1101 rotates, and the torque is transmitted to each functional unit 2 through the meshing of the active bevel gear 1105 on the pump shaft 1101 and the driven bevel gear 211 of each functional unit 2; the plunger-camshaft assembly 220 and the cam 221 and cam half retaining ring 225 fixed on it constitute the two-dimensional motion component of the functional unit 2. The torque causes the two-dimensional motion component of the functional unit 2 to rotate and reciprocate through the driven bevel gear module 21, thereby causing the plunger 2204 to rotate and reciprocate; the through groove 22042 on the plunger 2204 and the flow distribution windows 2324 and 2325 on the cylinder 232 form a flow distribution structure. When the plunger 2204 rotates, the volume of the sealed cavity continuously increases and decreases according to the movement law of the plunger 2204, and liquid suction and discharge are realized through the flow distribution structure; the flow channel arranged on the main housing 1201 communicates with the flow channel on the functional unit 2, realizing the diversion and collection of flow between the functional unit 2 and the hydraulic pump body 1. At the same time, the booster wheel 1109 rotates with the pump shaft 1101, and the generated centrifugal liquid flows through the flow channel 12027 to pressurize and deliver the sucked working liquid into each functional unit.

[0046] In some embodiments, by extending the pump body portion to increase the number of drive bevel gears on the pump shaft and correspondingly adding several sets of functional units, a radial piston hydraulic pump with a larger displacement can be assembled.

[0047] The embodiments described in this specification are merely examples of implementations of the inventive concept. The scope of protection of this invention should not be considered as limited to the specific forms stated in the embodiments. The scope of protection of this invention also extends to equivalent technical means that can be conceived by those skilled in the art based on the inventive concept.

Claims

1. A combined radial plunger hydraulic pump, comprising a hydraulic pump body, characterized in that, The hydraulic pump body (1) has a rectangular structure and multiple functional units (2) are arranged along the axial direction. Each group of four functional units (2) is arranged on the four sides of the hydraulic pump body (1). The functional units (2) are connected to the hydraulic pump body (1) by second-type screws (2403). The functional units (2) have suction and discharge ports, which correspond to the flow channels on the hydraulic pump body (1) to realize the suction and discharge of the functional units. In each group of four functional units (2), the plunger (2204) is in different working positions, namely the left limit position, the right limit position, the middle leftward movement position, and the middle rightward movement position. The positions of each group of functional units (2) are complementary to reduce flow pulsation. Among them: The hydraulic pump body (1) includes a pump shaft module (11) and a pump housing module (12). The pump shaft module (11) includes a pump shaft (1101) and a rotary oil seal (1103), two rolling bearings (1102), two drive bevel gears (1105), and a pump inlet booster mechanism (10) mounted on the pump shaft (1101). The pump housing module (12) includes a main housing (1201), a secondary housing (1202), and a pump cover (1203). Each functional unit (2) is installed on the inner holes of the four sides of the main housing (1201), and the contact surface and the flow channel are connected by a design. The seal is achieved using O-rings of type 8 (2410), type 9 (2411), and type 12 (2414); the sub-shell (1202) is connected to the main shell (1201) by bolts (1209) and is centered by a flange; the right end of the sub-shell (1202) is connected to the pump cover (1203), and the pump cover (1203) is embedded in the inner hole on the right side of the sub-shell (1202) to form a flow channel groove (12027); all contact surfaces between the main shell (1201), the sub-shell (1202), and the pump cover (1203) are sealed by O-rings of type 1 (2410), type 9 (2411), and type 12 (2414). 05) The second type of O-ring (1206) and the third type of O-ring (1212) are used for sealing; the pump shaft (1101) is installed on the main housing (1201), the left end of which contacts the right side shoulder of the main housing (1201) through the pump shaft bearing (1102), and the right side of which contacts the left side shoulder of the auxiliary housing (1202) through the pump shaft bearing (1102). Two active bevel gears (1105) are installed back to back on the pump shaft (1101); the pump inlet pressurization mechanism (10) includes a pressurization wheel (1109), which is installed in the inlet of the combined pump tail end. It is fixed to the pump shaft (1101) by a nut (1112) and located in the cavity formed by the sub-housing (1202) and the pump cover (1203); a mechanical seal device for separating the working fluid from the pump lubricating oil is provided on the left side of the booster wheel (1109). The mechanical seal device includes a mechanical seal stationary ring (1106), a mechanical seal dynamic ring (1107) and a mechanical seal retaining ring (1108). The mechanical seal stationary ring (1106) contacts the right shoulder of the sub-housing (1202), and the mechanical seal dynamic ring (1107) contacts the mechanical seal retaining ring (1108).

2. The combined radial plunger hydraulic pump as described in claim 1, characterized in that, The functional unit (2) includes a driven bevel gear module (21), a cam-roller transmission module (22), a cylinder module (23), and a unit housing module (24); wherein: The driven bevel gear module (21) includes a driven bevel gear (211), steel balls (226), steel ball retaining rings (213), and a thrust combined bearing (214). The driven bevel gear (211) meshes with the driving bevel gear (1105). A camshaft (2201) is inserted into the inner hole of the driven bevel gear (211), and the semi-circular grooves (2111) evenly distributed on the inner hole of the driven bevel gear (211) and the semi-circular grooves (22011) evenly distributed on the camshaft (2201) form multiple rows of circular grooves evenly distributed along the axial direction. The steel balls 226 are embedded in the circular grooves to realize the connection between the driven bevel gear (211) and the camshaft (2201), so that the driven bevel gear (211) drives the camshaft (2201) to rotate through the steel balls (226). A ball retaining ring (213) is installed on the right end of the inner hole of the wheel (221), and is limited by a second type of elastic retaining ring (212). A limiting pin (216) is installed in the hole of the ball retaining ring (213) to limit the axial position of each row of balls (226). The back of the driven bevel gear (211) contacts the thrust combined bearing (214), which is installed in the center hole of the unit cover (2408). The shoulder of the thrust combined bearing (214) contacts the rightmost end of the unit cover (2408) to achieve axial positioning of the driven bevel gear (211). The driven bevel gear (211) is locked on one side of the center hole of the first roller frame (222) by a third type of elastic retaining ring (215), so that the first roller frame (222) is connected to the unit cover (2408). The cam-roller drive module (22) includes a plunger-camshaft assembly (220), a cam (221), rollers (227), a camshaft (2201), a cam half retainer ring (225), a half coupling sleeve (2203), a floating sleeve (2202), a first roller carrier (222), a second roller carrier (224), and a roller carrier clearance adjustment ring (223). The cam-roller drive module (22) is installed on the right side hole of the unit housing (2401). The cam (221) is connected to the camshaft (2201) by a fourth type key (2210). The first roller carrier (222) and the second roller carrier (224) are located on the cam. On both sides of (221), the first roller holder (222) and the second roller holder (224) are respectively equipped with two pairs of cylindrical rollers (227) arranged mirror-oriented relative to the cam (221). The two pairs of rollers (227) are in contact with the contours of the two end faces of the cam (221). The right end of the first roller holder (222) is in contact with the unit cover (2408). The first roller holder (222) and the second roller holder (224) are connected to the unit shell (2401) through the fifth type key (2211). The circumferential position of the two pairs of rollers (227) is fixed. When the cam (221) rotates, its contour surface is constrained by the two pairs of rollers (227), generating axial reciprocating motion. Both the cam (221) and the camshaft (2201) are provided with axial grooves (22012), and two cam half retaining rings (225) are installed in the axial grooves. The cam half retaining rings (225) are connected and positioned to the cam (221) by set screws (229) to limit the axial position of the cam (221). The plunger-camshaft assembly (220) includes a plunger (2204), a camshaft (2201), two half-coupling sleeves (2203), eight drive pins (2205), and a floating sleeve (2202). Drive pins (2205) are installed in the semi-circular grooves (22013) at the ends of the two half-coupling sleeves (2203), the semi-circular grooves (22041) at the ends of the camshaft (2201), and the plunger (2204). The floating sleeve (2202) is located outside the two half-coupling sleeves (2203), allowing the plunger (2204) and camshaft (2201) to be connected together. The plunger-camshaft assembly (220) is installed from left to right in the center hole of the second roller holder (224), the center hole of the cam (221), the center hole of the first roller holder (222), and the center hole of the driven bevel gear (211). During operation, the plunger-camshaft assembly (220), together with the cam (221) and the cam half retainer ring (225) fixed thereon, constitute the two-dimensional motion component of the functional unit. The power of the pump shaft (1101) is transmitted through the driven bevel gear module (21) to make the two-dimensional motion component of the functional unit rotate and reciprocate, thereby making the plunger (2204) rotate and reciprocate. The cylinder module (23) includes a cylinder (232), an O-ring retaining ring (233), a stop pin (237), and a plug seal (231) located on the right side of the cylinder (232). Each functional unit (2) has only one cylinder module (23). The cylinder (232) and the plug seal (231) are installed in the hole on the left side of the unit housing (2401) to realize the communication between the high and low pressure chambers of the cylinder (232) and the high and low pressure flow channels of the unit housing (2401). The two holes on the left and right sides of the unit housing (2401) are provided with shoulder holes. The shoulder holes of the unit housing (2401) block the right end of the plug seal (231) to realize the axial positioning of the cylinder (232). The plunger (2204) is inserted into the cylinder (232). 232) In the inner hole, the left end flange of the cylinder body (232) is provided with a half-pin hole (2321) for preventing rotation. The stop pin 237 is inserted into the half-pin hole (2321) to prevent the cylinder (232) from rotating in the unit housing (2401) and to ensure the relative position of the low pressure distribution window (2324) and high pressure distribution window (2325) on the cylinder body (232) and the roller (227) in the cam-roller drive module (22). The cylinder body cover (2402) is installed on the left side of the cylinder body (232) and is connected to the unit housing (2401) by screws (2403). The cylinder body cover (2402) is provided with a central blind hole. The plunger (2204) enters the central blind hole when moving axially. The unit housing module (24) includes a unit housing (2401), a cylinder head (2402), and a unit cover (2408). The unit housing (2401) is connected to the cylinder head (2402) and the unit cover (2408) by second-type screws (2403). The contact surfaces of the unit cover (2408), the cylinder head (2402), and the unit housing (2401) are sealed with sixth-type O-rings (236) and tenth-type O-rings (2412). High-pressure and low-pressure flow channels are respectively opened at the upper and lower ends of the unit housing (2401) and the unit cover (2408). The high-pressure and low-pressure flow channels of the unit housing (2401) are divided into two sections: an oblique flow channel. The high-pressure oblique flow channel is the first flow channel (24011), the DC flow channel is the second flow channel (24012); the low-pressure oblique flow channel is the third flow channel (24013), the DC flow channel is the fourth flow channel (24014); the oblique flow channels do not communicate with other components and are sealed with second-type screw plugs (2406) and third-type screw plugs (2407); the unit cover (2408) is installed on the unit shell (2401) by positioning pins (2405) to realize communication between the high and low pressure flow channels on the unit shell (2401) and the unit cover (2408), and the flow channel holes are sealed with seventh-type O-rings (2409) and eleventh-type O-rings (2413).

3. A combined radial plunger hydraulic pump as described in claim 2, characterized in that, The cylinder body (232) is provided with two recessed grooves, namely the cylinder body low-pressure groove (2322) and the cylinder body high-pressure groove (2323). The cylinder body high-pressure groove (2323) communicates with the first flow channel (24011) on the unit shell. The cylinder body high-pressure groove (2323) has two mirror circular holes facing the center line of the cylinder body hole at an angle downwards, forming two high-pressure distribution windows (2325) on the inner cylindrical surface of the cylinder body (232). The cylinder body low-pressure groove (2322) communicates with the third flow channel (24013) on the unit shell. The cylinder body low-pressure groove (2322) has two mirror circular holes facing the center line of the cylinder body hole at an angle downwards, forming two low-pressure distribution windows (2324) on the inner cylindrical surface of the cylinder body (232). The diameter of the low-pressure distribution window (2324) is larger than the diameter of the high-pressure distribution window (2325). The high and low pressure distribution windows are staggered and arranged with a 90-degree phase difference. The plunger (22) 04) An inner flow hole is opened on the end face, and a pair of symmetrically arranged plunger grooves (22042) are opened radially on the plunger (2204). The plunger grooves (22042) are larger at the top and smaller at the bottom, with a trapezoidal cross-section, and communicate with the inner hole of the plunger (2204). The inner cylindrical surface of the cylinder (232), the inner hole surface of the plunger (2204), and the cylinder cover (2402) form a sealed cavity. The two radial plunger grooves (22042) of the plunger (2204) connect with the cylinder (232) and the cylinder cover (2402). The four windows on 32) constitute the distribution valve port; during operation, the plunger (2204) makes periodic reciprocating motion, the sealed cavity increases or decreases, and at the same time, the plunger (2204) makes rotational motion, the low-pressure distribution window (2324) and the high-pressure distribution window (2325) open alternately, so that the sealed cavity communicates alternately with the third flow channel (24013) and the first flow channel (24011), realizing the intake and discharge of the working medium in the functional unit (2).

4. A combined radial plunger hydraulic pump as described in claim 2, characterized in that, The plug seal (231) divides the internal cavity of the unit housing (2401) into two parts. The cylinder module (23) on the left contains the working medium, and the unit housing (2401) on the right contains lubricating oil. The driven bevel gear module (21) and the cam-roller transmission module (22) are immersed in the lubricating oil. The end of the cylinder (232) that contacts the plug seal (231) communicates with two shallow grooves (2326) of the cylinder low-pressure groove (2322) that are radially symmetrical. This is used to allow the working medium that leaks between the plunger (2204) and the cylinder (232) to the plug seal (231) to flow back into the cylinder low-pressure groove (2322) and prevent the pressure on the water medium side of the plug seal (231) from increasing beyond its pressure resistance.

5. A combined radial plunger hydraulic pump as described in claim 1, characterized in that, The driven bevel gear (211) is provided with a central hole, and a thrust combined bearing (214) is installed on the hub of the driven bevel gear (211). When the pump is working, the volume of the lubricating oil chamber in the functional unit (2) increases or decreases, and the lubricating oil in the functional unit (2) enters and exits the functional unit (2) through the gap between the central hole of the driven bevel gear (211) and the thrust combined bearing (214). The lubricating oil passing through the central hole of the driven bevel gear (211) is divided into two paths to enter and exit the interior of the functional unit (2). One is through the central hole of the camshaft (2201), and the other is through the gap between the camshaft (2201) and the steel ball groove connecting the driven bevel gear (211), as well as the gap of the thrust combined bearing (214), forming three lubricating oil channels that constitute three hydraulic resistances from small to large. And through these three lubricating oil channels, the heat in the functional unit (2) is carried into the hydraulic pump body (1).

6. A combined radial plunger hydraulic pump as described in claim 1, characterized in that, The main shell (1201) has a fifth flow channel (12011), a sixth flow channel (12012), a seventh flow channel (12013), and an eighth flow channel (12014) arranged diagonally along the axial direction. Each side of the main shell (1201) has a pair of high-pressure and a pair of low-pressure oblique flow channels, arranged alternately on adjacent sides. The fifteenth flow channel (120111), sixteenth flow channel (120112), seventeenth flow channel (120113), and eighteenth flow channel (120114) converge into the fifth flow channel (12011). The nineteenth flow channel (120121), twentieth flow channel (120122), and twenty-first flow channel (120124) are also present. The flow channels (120123) and 22 (120124) converge into the 6th flow channel (12012); the flow channels (120131), 24 (120132), 25 (120133), and 26 (120134) converge into the 7th flow channel (12013); the flow channels (120141), 28 (120142), 29 (120143), and 30 (120144) converge into the 8th flow channel (12014), thus realizing the separation and collection of flow between the functional unit (2) and the hydraulic pump body (1); The sub-shell (1202) has a ninth flow channel (12021), a tenth flow channel (12022), an eleventh flow channel (12023), and a twelfth flow channel (12024) on its four diagonal sides. The ninth flow channel (12021) communicates with the sixth flow channel (12012); the tenth flow channel (12022) communicates with the seventh flow channel (12013). All are sealed by a type III O-ring (1212). The ninth flow channel (12021), the tenth flow channel (12022), and the twelfth flow channel (12024) are located at their respective corners. The flow channel (12022) is connected to the threaded hole to form two outlets; the eleventh flow channel (12023) is connected to the fifth flow channel (12011); the twelfth flow channel (12024) is connected to the eighth flow channel (12014), and both are sealed by the third type of O-ring (1212). The eleventh flow channel (12023) and the twelfth flow channel (12024) are connected to the flow channel groove (12027) and the central threaded hole of the pump cover (1203) to form a suction port.

7. A combined radial plunger hydraulic pump as described in claim 1, characterized in that, The main housing (1201) has two oil inlets and two measuring interfaces on its four sides, which are sealed with plugs (1204) when not in use. The main housing (1201) has countersunk holes to accommodate the head of the second type of screw (2403) on the right side of the functional unit (2). The flange has symmetrical countersunk grooves on both sides to accommodate large screws. The eleventh flow channel (12023) and the twelfth flow channel (12024) on the sub-housing (12022) are provided with a thirteenth flow channel (12025) and a fourteenth flow channel (12026) on the outside of the eleventh flow channel (12023) and the twelfth flow channel (12024), which are connected to the flow channel groove (12027) and sealed with a first type of plug (1211).

8. A combined radial plunger hydraulic pump as described in claim 2, characterized in that, The cam (221) is a double-end-face spatial cam, and its motion law is an equal acceleration and deceleration curve from low point to high point. The two end face profiles of the cam (221) are "two high and two low", "three high and three low" or "four high and four low".

9. A combined radial plunger hydraulic pump as described in claim 2, characterized in that, The floating sleeve (2202) is inside the center hole of the second roller holder (224) and sleeved on the outside of the two half-coupling sleeves. The inner and outer cylindrical surfaces of the floating sleeve form inner and outer sliding oil film supports through clearance fit with the outer cylindrical surface of the half-coupling sleeve and the center hole of the second roller holder, and satisfy the two-dimensional motion of the plunger-camshaft assembly.

10. A combined radial plunger hydraulic pump as described in claim 5, characterized in that, The camshaft has a central through hole, and an end face groove is provided on the end face of the camshaft connected to the plunger. The half coupling sleeve has a radial through hole, and the outer cylindrical surface of the floating sleeve has a full circumferential shallow groove and a radial through hole. The lubricating oil enters the inner hole of the floating sleeve through the central hole of the camshaft, the end face groove of the camshaft connected to the plunger, and the radial through hole on the half coupling sleeve, and then enters the circumferential oil groove on the outer cylindrical surface of the floating sleeve through the radial through hole of the floating sleeve, forming a supporting oil film inside and outside the floating sleeve.

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