An inner curve multi-acting variable radial plunger test pump platform and test method

Abstract

The application discloses an inner curve multi-acting variable radial plunger test pump platform and a test method, and relates to the technical field of hydraulic equipment; and aims to solve the problems of the existing radial plunger test pump platform, such as insufficient compactness, low integration degree and being easily disturbed by the movement of other plunger pairs; the platform comprises a pump body, a transmission shaft is rotatably arranged in the middle of the pump body and is controlled to rotate by a prime mover; an inner flow channel stator and a rear end cover are connected through bolts, the transmission shaft penetrates through the rear end cover, the rear end cover is connected with an outer flow channel stator through bolts, the rear end cover is arranged inside one side of a plunger hole and is provided with annular oil suction and discharge cavities; an oil inlet and an oil outlet are formed in the rear end cover, the oil inlet is connected with a low-pressure oil tank, the oil outlet is connected with an energy accumulator, and finally connected with a load. The application is compact in structure design and high in integration degree; when not controlled by external signals, the application can be used as a common radial plunger pump, and has stable displacement and output pressure.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of hydraulic equipment, in particular to an inner curve multi-acting variable radial piston test pump platform and a test method. BACKGROUND

[0002] At present, with the rapid development of digital pump technology, digital pump technology has broad development prospects in the future, and the performance of the single piston of the digital radial piston pump is of great guiding significance for the flow distribution strategy and method of the whole digital pump, the piston friction pair and the lubrication and friction characteristics;

[0003] However, the existing radial piston test pump platform has the problems of insufficient structure, low integration and easy disturbance by other piston pair movements, and cannot better study the piston-roller pair in the single piston cavity, the piston pair lubrication and friction characteristics, and the force and wear of the inner curve track; and an inner curve multi-acting variable radial piston test pump platform and a test method are designed. SUMMARY

[0004] The present application aims to solve the problems of insufficient structure, low integration and easy disturbance by other piston pair movements of the existing radial piston test pump platform, and proposes an inner curve multi-acting variable radial piston test pump platform and a test method; the flow distribution strategy of the single piston and the friction and lubrication characteristics of the single piston can be studied, and the test pump platform can be used for testing and as a common radial piston pump.

[0005] The purpose of the present application can be achieved by the following technical scheme: an inner curve multi-acting variable radial piston test pump platform, comprising a pump body, a transmission shaft rotatingly installed in the middle of the pump body and controlled to rotate by a prime mover. The transmission shaft is connected with an inner curve rotor through an involute spline and drives the inner curve rotor to rotate, the rotor is composed of front and rear parts and connected by bolts to form a complete inner curve rotor; the two parts of the inner curve rotor are respectively provided with annular guide rail cavities, and the inner and outer two circles of inner curve guide rails are formed by bolt connection, which are respectively the inner circle of equal acceleration and equal deceleration inner curve guide rail and return rail, and the outer circle of equal acceleration and equal deceleration inner curve guide rail and return rail.

[0006] As a preferred embodiment of the present application, a plurality of plunger holes are arranged radially and spaced apart on the flow channel stator inside the inner curve rotor, and there are nine plunger holes in total, wherein the tenth plunger cavity is not provided, and the position of the tenth plunger hole is reserved, and the annular recess corresponding to the position of the plunger hole is provided on the annular outer wall of the assembled inner curve rotor. The nine plunger holes are all provided with plungers, the bottom of the plunger passes through the annular recess of the inner ring and is inserted into the guide rail cavity, and the insertion end of the plunger is provided with a transverse hole, a roller is rotatably arranged in the transverse hole, and when the inner curve rotor rotates with the transmission shaft, the nine rollers all make periodic rolling along the equal acceleration and equal deceleration inner curve return guide rail in the inner ring guide rail cavity, and at the same time, the head part of the plunger makes reciprocating linear motion in the corresponding plunger hole. The equal acceleration and equal deceleration inner curve guide rails and the return guide rails of the inner curve guide rails of the inner and outer rings are correspondingly distributed, the inner curve of the inner ring is at the highest point, and the inner curve of the outer ring is at the lowest point. Only one plunger is arranged in the inner curve guide rail of the outer ring, the plunger is connected by the roller and embedded in the inner curve guide rail of the outer ring, and the movement principle is consistent with that of the plunger of the inner ring. The single plunger on the inner curve guide rail of the outer ring can completely simulate the movement of the tenth plunger of the inner curve guide rail of the inner ring.

[0007] As a preferred embodiment of the present application, the inner flow channel stator is provided with an oil suction cavity and an oil discharge cavity, the outer ring is the oil suction cavity, the inner ring is the oil discharge cavity, and the oil suction and discharge flow channels are located on the same side of the flow channel stator; the oil suction cavity and the nine plunger holes in the inner flow channel stator are respectively communicated with oil suction channels, and the oil discharge cavity and the nine plunger holes in the inner flow channel stator are respectively communicated with oil discharge channels; an oil suction check valve is arranged in each oil suction channel, and an oil discharge check valve is arranged in each oil discharge channel, and the check valves are arranged in the inner flow channel stator; the oil suction and discharge flow channels of the oil suction and discharge cavities of the inner flow channel stator and the annular oil suction and discharge flow channels of the rear end cover are one-to-one corresponding.

[0008] As a preferred embodiment of the present application, the plunger located in the inner curve track of the outer ring of the inner curve rotor is provided with a separate outer flow channel and a plunger cavity, an oil suction channel is communicated between the oil suction cavity and the plunger hole, and an oil discharge channel is communicated between the oil discharge cavity and the plunger hole; an oil suction check valve is arranged in the oil suction channel, an oil discharge check valve is arranged in the oil discharge channel, a high-speed digital switch valve is arranged at the top of the plunger cavity, an insertion hole flow channel is arranged on the side corresponding to the oil suction channel for inserting and connecting a pressure sensor; one end of the valve port of the high-speed digital switch valve is communicated with the plunger cavity, and the other end is communicated with the oil suction cavity; the oil suction flow channel of the rear end cover is communicated with the plunger cavity oil suction flow channel of the outer ring plunger of the inner curve rotor, and an insertion hole flow channel is arranged at the top for inserting and connecting a pressure sensor; the oil discharge cavity and the oil discharge flow channel of the outer ring plunger are arranged vertically to the oil suction flow channel and are communicated with the oil discharge flow channel in the rear end cover, and the sealing of the oil circuit is realized through an oil plug.

[0009] As a preferred embodiment of the present application, the pump body comprises front and rear end covers and an external flow channel stator, which are rotatably mounted on the transmission shaft, and the three are fixedly connected to form an integrated body; the front end cover is internally provided with a skeleton oil seal; the rear end cover is fixedly connected with a bearing end cover, and an O-shaped sealing ring is mounted between the bearing end cover and the rear end cover.

[0010] As a preferred embodiment of the present application, an angle encoder is mounted on the tail of the transmission shaft, which is threadedly connected to the rear end cover and locked to the transmission shaft by a locking screw to rotate with the transmission shaft.

[0011] As a preferred embodiment of the present application, the inner curve guide rail is divided into an inner ring double-layer structure, and the cross section of the inner curve is an equal-acceleration and equal-deceleration inner curve, a cosine acceleration motion law inner curve, a sine acceleration motion law inner curve, a trapezoidal acceleration motion law inner curve or a parabolic acceleration motion law inner curve. The difference between the inner curves of the inner and outer rings is that the inner curve of the outer ring is rotated by 60° relative to the inner curve of the inner ring, so that when the inner curve of the inner ring is at the lowest point, the inner curve of the outer ring is at the highest point; and when the inner curve of the outer ring is at the lowest point, the inner curve of the inner ring is at the highest point.

[0012] As a preferred embodiment of the present application, the skeleton oil seal is mounted between the transmission shaft and the front end cover, the outer ring of the front tapered roller bearing is mounted inside the front end cover and the inner side of the skeleton oil seal, the inner ring of the front bearing is mounted on the transmission shaft and axially limited by the shaft shoulder on the transmission shaft and the shoulder of the front end cover, the positioning ring is embedded in the inner curve rotor and mounted between the inner curve stator and the transmission shaft; the transmission shaft is driven by the original engine through a flat key and connected with the inner curve rotor through a spline, the front end cover is fixedly connected with the external flow channel stator through screws; the rear end cover is fixedly connected with the external flow channel stator through screws, and an O-shaped ring is mounted between the rear end cover and the external flow channel stator, the inner ring of the rear bearing is mounted on the transmission shaft, and the outer ring of the rear bearing is mounted inside the rear end cover; the bearing end cover is connected with the rear end cover through screws, and an O-shaped sealing ring is mounted between the bearing end cover and the rear end cover.

[0013] As a preferred embodiment of the present application, an annular groove is formed in the inside of the rear end cover, the inner ring is an oil discharge flow channel, and the outer ring is an oil suction flow channel, which are not connected, and are connected to the annular oil suction and discharge flow channels through vertical flow channels, and oil suction and discharge ports are respectively formed on both sides of the rear end cover shell, and a vertical flow channel is separately formed on the rear end cover shell for connecting the flow channel of the external flow channel stator.

[0014] As a preferred embodiment of the present application, the internal flow channel stator is embedded in the inner curved rotor, nine plunger cavities are radially and equidistantly distributed in the internal flow channel stator, the position of the tenth plunger cavity is reserved, oil suction and discharge cavities are respectively arranged in the nine plunger cavities, the inner ring is an oil discharge flow channel, the outer ring is an oil suction flow channel, and oil suction and discharge one-way valves are respectively arranged in the oil suction and discharge cavities.

[0015] As a preferred embodiment of the present application, the inner curved rotor is installed on the transmission shaft through spline connection, the inner curved rotor is provided with two layers of inner and outer equal acceleration and deceleration inner curved guide rails, the rollers are installed on the round holes at the bottom of the plungers through gap fit of shaft holes, the rollers are fixedly installed on the rollers, the rollers and the rollers are supported by the equal acceleration and deceleration inner curved guide rails on the inner curved rotor and periodically roll on the inner curved guide rails, the bottom of the plunger is supported by the rollers and the rollers, the head of the plunger on the inner ring guide rail is installed in the plunger hole arranged in the internal flow channel stator through gap fit of shaft holes, the head of the plunger on the outer ring guide rail is separately installed in the plunger hole arranged in the external flow channel stator through gap fit of shaft holes, and the plunger head continuously performs reciprocating motion in the plunger hole with rotation of the transmission shaft; the oil suction one-way valve is embeddedly installed in the oil suction channel connected with the plunger cavity formed by the plunger and the plunger hole; the oil discharge one-way valve is embeddedly installed in the oil discharge channel connected with the plunger cavity; and the high-speed digital switch valve is separately installed in the external flow channel stator in the outer channel connected with the plunger cavity.

[0016] As a preferred embodiment of the present application, the oil suction one-way valve is opened in the positive direction when the volume of the plunger cavity increases, and low-pressure oil flows into the plunger cavity from the oil suction cavity; the oil discharge one-way valve is opened in the positive direction when the volume of the plunger cavity decreases and the extrusion pressure of the hydraulic oil increases to the opening pressure, and high-pressure oil is discharged from the plunger cavity to the oil discharge cavity through the oil discharge one-way valve; the high-speed digital switch valve is installed in the hole connected with the plunger cavity on the external flow channel stator, a hole connected with the valve port of the high-speed digital switch valve and the oil suction cavity is arranged in the external flow channel stator, an O-ring is installed on the outer edge of the hole, one end of the valve port of the high-speed digital switch valve is connected with the plunger cavity, and the other end of the valve port is connected with the oil suction cavity, the connection and disconnection between the oil suction cavity and the plunger cavity are realized by actively controlling the opening and closing of the valve port of the high-speed digital switch valve, and based on a certain control strategy, the variable displacement control and adjustment of a single plunger can be realized.

[0017] As a preferred embodiment of the present application, the rear end cover is provided with an oil suction port and an oil discharge port, in the whole hydraulic test platform, the oil suction port of the test pump is connected with a low-pressure oil tank, the oil discharge port of the test pump is connected with an accumulator, and finally connected with a load, a flow sensor and a pressure sensor are installed on the oil circuit between the accumulator and the oil discharge port of the test pump, a flow sensor is installed on the oil circuit between the accumulator and a throttle valve, the load of the test platform is simulated through the throttle valve and the oil tank, and the accumulator can provide stable flow output and pressure fluctuation for the whole test pump.

[0018] Compared with the prior art, the present application has the following beneficial effects:

[0019] 1. The inner curve multi-acting variable radial piston test pump platform can study the piston-roller pair, piston pair lubrication friction characteristics and the force and wear of the inner curve track in a single piston cavity without affecting the whole piston pump working condition.

[0020] 2. The inner curve multi-acting variable radial piston test pump platform has single-piston variable displacement adjustment, can study the variable displacement control of a single piston cavity, pressure flow regulation without affecting the whole piston pump working condition, and controls the opening and closing of a high-speed digital on-off valve based on a certain angle coding control strategy through the angle encoder at the tail of the transmission shaft, so as to obtain a general control strategy method, which has guiding significance for the control strategy of the whole piston pump.

[0021] 3. The inner curve multi-acting variable radial piston test pump platform is compact in structure design and has high integration, and can be used as an ordinary radial piston pump without external signal control, and has stable displacement and output pressure. BRIEF DESCRIPTION OF DRAWINGS

[0022] In order to facilitate the understanding of those skilled in the art, the present application will be further described below with reference to the drawings.

[0023] Figure 1 is a test pump shaft side sectional view of the present application;

[0024] Figure 2 is a test pump front sectional view of the present application;

[0025] Figure 3 is a test pump side sectional view and oil suction and discharge port schematic view of the present application;

[0026] Figure 4 is an equal acceleration and deceleration inner curve rear guide rail schematic view;

[0027] Figure 5 is an equal acceleration and deceleration inner curve front guide rail schematic view;

[0028] Figure 6 It is a schematic diagram of the test pump platform test method of the present invention.

[0029] Reference numerals: 1, transmission shaft; 2, front inner-curved rotor; 3, screw 1; 4, front end cover; 5, outer flow channel stator; 6, rear end cover; 7, rear tapered roller bearing; 8, angle encoder; 9, bearing end cover; 10, screw 2; 11, O-ring; 12, rear inner-curved rotor; 13, oil discharge chamber; 14, oil suction chamber; 15, oil suction check valve; 16, oil plug; 17, high-speed digital switching valve; 18, plunger; 19, roller; 20, pressure sensor; 21, inner flow channel stator; 22, front tapered roller bearing; 23, skeleton oil seal; 24, flat key; 25. Oil suction port; 26. Oil discharge port; 27. Oil discharge check valve; 28. Internal equal acceleration and equal deceleration curve guide rail; 29. ​​External equal acceleration and equal deceleration curve guide rail; 30. Internal equal acceleration and equal deceleration curve return guide rail; 31. External equal acceleration and equal deceleration curve return guide rail; 32. Low-pressure oil tank; 33. Outer ring plunger; 34. Inner ring plunger one; 35. Inner ring plunger two; 36. Inner ring plunger three; 37. Inner ring plunger four; 38. Inner ring plunger five; 39. Inner ring expandable plunger unit; 40. Accumulator; 41. Flow sensor; 42. Throttle valve; 43. Oil tank. DETAILED DESCRIPTION

[0030] The technical solutions of the present invention will be clearly and completely described below with reference to the embodiments. Obviously, the embodiments described are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making any creative efforts shall fall within the scope of protection of the present invention.

[0031] Example 1

[0032] See also Figures 1-6 As shown, an inner curve multi-action variable radial piston test pump platform includes a transmission shaft 1, a front inner curve rotor 2, a front end cover 4 and a skeleton oil seal 23;

[0033] The skeleton oil seal 23 is installed between the transmission shaft 1 and the front end cover 4, the transmission shaft 1 is driven by the prime mover through the flat key 24 and connected with the front inner curved rotor 2 through the spline, the front end cover 4 is fixedly installed on the outer flow channel stator 5 through the screw one 3. The front end cover 4 is supported and installed on the transmission shaft 1 by the front tapered roller bearing 22, the inner ring of the front tapered roller bearing 22 is installed on the transmission shaft 1 and axially limited by the shaft shoulder on the transmission shaft 1 and the shoulder of the front end cover 4, the rear end cover 6 is connected with the outer flow channel stator 5 through the screw one 3 and supported on the transmission shaft 1 by the rear tapered roller bearing 7, the inner ring of the rear tapered roller bearing 7 is installed on the transmission shaft 1 and axially limited by the shoulder of the rear end cover 6 and the bearing end cover 9, the bearing end cover 9 is fixedly connected on the rear end cover 6 through the screw two 10, and the O-ring 11 is installed between the bearing end cover 9 and the rear end cover 6.

[0034] The front inner curve rotor 2 is installed on the transmission shaft 1 through spline connection, the front inner curve rotor 2 is respectively provided with an inner equal acceleration and equal deceleration curve guide rail 28, an outer equal acceleration and equal deceleration curve guide rail 29, an inner equal acceleration and equal deceleration curve return guide rail 30 and an outer equal acceleration and equal deceleration curve return guide rail 31, the roller 19 is installed on the circular hole at the bottom of the plunger 18 through shaft hole gap cooperation, the roller 19 is supported by the inner equal acceleration and equal deceleration curve guide rail 28 and the outer equal acceleration and equal deceleration curve guide rail 29 on the front inner curve rotor 2 and periodically rolls on the inner equal acceleration and equal deceleration curve guide rail 28 and the outer equal acceleration and equal deceleration curve guide rail 29, the bottom end of the plunger 18 is supported by the roller 19, the head of the plunger 18 is installed in the plunger hole provided in the inner flow channel stator 21 and the outer flow channel stator 5 through shaft hole gap cooperation, with the rotation of the transmission shaft 1, the head of the plunger 18 continuously performs reciprocating motion in the plunger hole, the rear inner curve rotor 12 is supported by the transmission shaft 1 and fixedly connected with the front inner curve rotor 2 through a screw, and is limited in the axial direction by the shoulder of the front end cover 4 and the shoulder of the rear end cover 6. The rear end cover 6 is provided with an oil suction and discharge cavity flow channel separately leading to the outer flow channel stator 5, for connecting the oil suction and discharge flow channel of the outer flow channel stator 5, a hole channel connected with the pressure sensor 20 is provided at the top of the oil suction cavity flow channel of the rear end cover 6, the pressure sensor 20 is connected with the hole channel through screw connection, a hole channel of the oil plug 16 is provided at the top of the oil discharge cavity flow channel of the rear end cover 6, the oil plug 16 is connected with the hole channel through screw connection to realize oil path sealing, the oil suction check valve 15 is embeddedly installed in the oil suction cavity 14 channel connected with the plunger cavity formed by the plunger 18 and the plunger hole, the oil discharge check valve 27 is embeddedly installed in the oil discharge cavity 13 channel connected with the plunger cavity, and the high-speed digital on-off valve 17 is installed in the outer hole channel connected with the plunger cavity. One end of the valve port of the high-speed digital on-off valve 17 is connected with the plunger cavity, and the other end is connected with the oil suction cavity 14, the oil suction flow channel of the rear end cover 6 is connected with the plunger cavity oil suction flow channel of the outer circle plunger 33 of the inner curve rotor, and an insertion hole flow channel provided with an oil suction flow channel at the top is provided for inserting the pressure sensor 20; the oil discharge cavity and the oil discharge flow channel of the outer circle plunger 33 of the inner curve rotor are arranged vertically to the oil suction flow channel and are connected with the oil discharge flow channel in the rear end cover 6, and the oil path is sealed through the oil plug.

[0035] A plurality of groups of oil suction check valves 15 and oil discharge check valves 27 are respectively connected with the inner circle plungers; the inner circle plungers include an inner circle plunger one 34, an inner circle plunger two 35, an inner circle plunger three 36, an inner circle plunger four 37, an inner circle plunger five 38 and an inner circle expandable plunger unit 39.

[0036] The oil suction one-way valve 15 opens in positive direction when the plunger cavity volume increases, and low pressure oil flows into the plunger cavity from the oil suction cavity 14, the oil suction cavity 14 is formed by the annular oil suction cavity in the rear end cover 6 and the oil suction hole in the tail of the oil suction one-way valve 15 in the inner flow channel stator 21, two layers of O-rings 11 are installed between the rear end cover 6 and the inner flow channel stator 21, and the rear end cover 6 and the inner flow channel stator 21 are fixed by screw connection; the oil discharge one-way valve 27 opens in positive direction when the plunger cavity volume decreases and the hydraulic oil is extruded to increase the pressure to the opening pressure, and high pressure oil is discharged to the oil discharge cavity 13 from the plunger cavity through the oil discharge one-way valve 27, the oil discharge cavity 13 is formed by the annular oil discharge cavity in the rear end cover 6 and the oil discharge hole in the tail of the oil discharge one-way valve 27, and the oil suction cavity 14 and the oil discharge cavity 13 are connected with the oil suction port 25 and the oil discharge port 26 of the pump respectively. The high speed digital on-off valve 17 is installed in the hole communicating with the plunger cavity in the outer flow channel stator 5, the hole communicating the valve port of the high speed digital on-off valve 17 and the oil suction port 25 is formed in the outer flow channel stator 5, the O-ring 11 is installed on the outer edge of the hole, one end of the valve port of the high speed digital on-off valve 17 is connected with the plunger cavity, and the other end of the valve port is connected with the oil suction port 25, the oil suction port 25 and the plunger cavity are connected and disconnected by driving and controlling the opening and closing of the valve port of the high speed digital on-off valve 17, and based on a certain control strategy, the variable displacement control and adjustment of the pump can be realized. The hole connecting the pressure sensor 20 and the plunger cavity is formed in the outer flow channel stator 5, and the pressure sensor 20 is inserted into the hole connected with the plunger cavity through screw thread connection.

[0037] The number of the oil suction one-way valve 15 and the oil discharge one-way valve 27 is multiple, corresponding to the number of the plungers 18, and there is only one high speed digital on-off valve 17, the plungers 18 are distributed in the inner flow channel stator 21 in a radial manner, and only one plunger 18 is distributed in the outer flow channel stator 5, wherein the single plunger 18 is located at the position of the distributed plungers 18 in the inner flow channel stator 21, as shown in the figure. Figure 2 The plunger 18 is supported and driven by the inner equal acceleration and equal deceleration curve guide rail 28 and the outer equal acceleration and equal deceleration curve guide rail 29 on the front inner curve rotor 2, and is simultaneously acted on by the inner equal acceleration and equal deceleration curve return guide rail 30 and the outer equal acceleration and equal deceleration curve return guide rail 31 formed by the connection of the rear inner curve rotor 12 and the front inner curve rotor 2, so that the same plunger 18 can complete multiple oil suction and discharge reciprocating movements per revolution of the inner curve rotor.

[0038] In the whole hydraulic test platform, the oil suction port 25 of the test pump is connected with the low pressure oil tank 32, the oil discharge port of the test pump is connected with the accumulator 40, and finally connected with the load.

[0039] The working process of the application is as follows:

[0040] Driven by the prime mover, under the support of the front tapered roller bearing 22 and the rear tapered roller bearing 7, the transmission shaft 1 rotates, and the inner curved rotor is composed of the front inner curved rotor 2 and the rear inner curved rotor 12. Since the inner curved rotor and the transmission shaft 1 are connected together through the spline, the inner curved rotor will rotate together with the transmission shaft 1. The inner curved rotor has an inner equal acceleration and deceleration curve guide rail 28, an outer equal acceleration and deceleration curve guide rail 29, an inner equal acceleration and deceleration curve return guide rail 30, and an outer equal acceleration and deceleration curve return guide rail 31 on the inner side of the inner curved rotor. Due to the rotational movement of the inner equal acceleration and deceleration curve guide rail 28, the outer equal acceleration and deceleration curve guide rail 29, and the return guide rail, the roller 19 installed with the plunger 18 rolls on the inner equal acceleration and deceleration curve guide rail 28, the outer equal acceleration and deceleration curve guide rail 29, and the return guide rail, respectively, so that the plunger 18 performs periodic reciprocating motion in the plunger hole of the inner flow channel stator 21 and the outer flow channel stator 5. Under the forced driving of the inner equal acceleration and deceleration curve guide rail 28 and the outer equal acceleration and deceleration curve guide rail 29, the plunger 18 performs the oil discharge working stroke, at which time the plunger cavity volume decreases. Under the forced return action of the inner equal acceleration and deceleration curve return guide rail 30 and the outer equal acceleration and deceleration curve return guide rail 31 provided on the inner edge of the inner curved rotor, the plunger 18 that has completed the forward stroke performs the return oil suction stroke, at which time the plunger cavity volume increases.

[0041] When the plunger cavity volume increases, a local negative pressure is formed inside the plunger cavity. At this time, the oil suction one-way valve 15 is opened under the pressure difference between the external atmospheric pressure and the negative pressure inside the plunger cavity. Low-pressure oil is sucked into the plunger cavity through the oil suction port 25 and the oil suction cavity 14 of the pump and the oil suction one-way valve 15. When the plunger cavity volume decreases, the hydraulic oil inside the plunger cavity is extruded, the pressure rises, and thus the oil suction one-way valve 15 is closed. When the hydraulic oil pressure inside the plunger cavity rises to be greater than or equal to the sum of the load pressure of the pump outlet and the opening pressure of the oil discharge one-way valve 27, the oil discharge one-way valve 27 is opened, and high-pressure oil is discharged from the plunger cavity to the load circuit through the oil discharge cavity 13 and the oil discharge port 26 of the pump. The plunger 18 can complete multiple reciprocating motions and realize multiple oil suction and discharge every rotation of the inner curved rotor. With the continuous driving and rotation of the inner curved rotor on the transmission shaft 1, the multiple plungers 18 installed in the inner flow channel stator 21 in a radial radial manner and the plunger 18 separately installed in the outer flow channel stator 5 will continuously perform reciprocating motion for oil suction and discharge, thereby realizing the functions of pumping low-pressure oil and discharging high-pressure oil.

[0042] The angle encoder 8 is installed at the tail of the transmission shaft 1, which can monitor the rotation angle of the transmission shaft 1 in real time and output digital encoding signals. Through the obtained digital encoding signals, the opening and closing of the high-speed digital switch valve 17 is controlled in real time. When the high-speed digital switch valve 17 is not powered and does not work, the oil suction and discharge functions of the pump are completed by the oil suction check valve 15 and the oil discharge check valve 27. The plunger 18 in the outer flow channel stator 5 can completely simulate the movement of the plunger 18 in the inner flow channel stator 21. At this time, the pump can be used as a constant displacement pump. When it is necessary to study the influence of the high-speed digital switch valve 17 on the pressure and displacement of the single plunger 18, when the high-speed digital switch valve 17 is powered by receiving the digital signal, the valve port of the high-speed digital switch valve 17 is opened, and in the plunger cavity volume reduction plunger 18 process oil discharge stroke, the hydraulic oil in the plunger cavity will be returned to the oil suction chamber 14 of the pump through the opened valve port of the high-speed digital switch valve 17, which externally shows that the plunger cavity pressure discharge high pressure oil function fails, and the high pressure oil flow output from the oil discharge port 26 of the pump is reduced, that is, the displacement and pressure of the single plunger cavity are adjusted to a smaller level. Through the pressure sensor 20 installed inside the plunger cavity and the pressure sensor 20 between the oil suction chamber 14 and the high-speed digital switch valve 17, the pressure change is monitored in real time. At the same time, the flow sensor 41 is arranged on the oil path between the oil discharge port 26 and the accumulator 40 to monitor the flow change and the pressure sensor 20 to monitor the pressure fluctuation. The accumulator 40 is used to stabilize the flow and pressure fluctuation, so that the entire plunger pump outputs stable pressure and flow to the load. The flow sensor 41 is installed on the oil path between the accumulator 40 and the throttle valve 42, and the load of the test platform is simulated through the throttle valve 42 and the oil tank 43. The accumulator 40 can provide stable flow output and pressure fluctuation for the entire test pump.

[0043] According to the digital signal output by the angle encoder 8, based on the digital timing control strategy, the power-on and power-off state and timing of the high-speed digital switch valve 17 changing the plunger cavity can be controlled, the experimental research on the variable displacement and pressure regulation of the single plunger of the plunger pump can be completed, and the law of the universal control strategy can be obtained. The control strategy of the output flow and pressure of the entire pump is realized.

[0044] For the single plunger 18 and the roller 19 on the inner curve guide rail of the outer ring, under the normal working condition of the plunger pump, the single plunger 18 and the roller 19 can be completed without being affected by the movement of the plunger 18 and the roller 19 on the inner curve guide rail of the inner ring. The plunger-roller pair, the plunger pair lubrication friction characteristics under normal working condition and the research on the force and wear of the inner curve track are completed.

[0045] From the above structure can be seen, the application provides a kind of inner curve multi-action variable radial plunger test pump platform, with the advantages of compact structure design, high integration, while excluding other interference, without affecting the working condition of pump, independent study the plunger-roller pair in single plunger cavity, plunger pair lubrication friction characteristics and the force and wear condition of inner curve track;Single plunger variable displacement adjustment is convenient for the realization of the control strategy of digital valve;When not controlled by external signal, it can be used as ordinary radial plunger pump, and has stable displacement and output pressure.

[0046] The preferred embodiments of the application disclosed above are only used to help explain the application. The preferred embodiments do not describe all the details and limit the application to the specific embodiments. Obviously, many modifications and variations can be made according to the content of the specification. The specification selects and specifically describes these embodiments in order to better explain the principles and practical applications of the application, so that those skilled in the art can well understand and utilize the application. The application is limited by the claims and their entire scope and equivalents.

Claims

1. An inner curve multi-acting variable radial piston test pump platform, comprising a pump body, a transmission shaft is rotatably installed in the middle of the pump body and is controlled to rotate by a prime mover, characterized in that: The transmission shaft is connected with the inner curve rotor through the involute spline and drives the inner curve rotor to rotate, the inner curve rotor is composed of a front inner curve rotor and a rear inner curve rotor and is connected into a complete inner curve rotor through bolts; the front inner curve rotor and the rear inner curve rotor are respectively provided with annular guide rail cavities, and the annular guide rail cavities are connected into inner and outer two layers of curve guide rails through bolts, and the tracks of the inner and outer two layers of curve guide rails are staggered at a certain angle and are respectively an inner circle of equal acceleration and equal deceleration inner curve guide rails and return guide rails and an outer circle of equal acceleration and equal deceleration inner curve guide rails and return guide rails; The transmission shaft passes through the inner flow channel stator, the inner flow channel stator is provided with a plurality of plunger holes arranged in a radial radial manner, the annular inner wall and the outer wall of the assembled inner curve rotor are provided with annular grooves corresponding to the positions of the plunger holes, a plurality of plunger holes are provided with plungers, the bottoms of the plungers pass through the inner annular grooves and are inserted into the guide rail cavities, and the insertion ends of the plungers are provided with transverse holes; the transverse holes are rotatably provided with rollers; when the inner curve rotor rotates with the transmission shaft, the rollers reciprocatingly and periodically roll along the equal acceleration and equal deceleration inner curve return guide rails in the inner circle guide rail cavities, and the heads of the plungers reciprocatingly and linearly move in the corresponding plunger holes; the inner flow channel stator inside the inner curve rotor is provided with a plurality of plunger holes arranged in a radial radial manner, a total of nine plunger holes are provided, a tenth plunger cavity is not provided, the position of the tenth plunger hole is reserved, and only one plunger is installed in the outer layer of the inner curve guide rail, the plunger is connected by a roller and is embedded in the outer layer of the inner curve guide rail, the plunger is located at the position of the outer layer of the inner curve guide rail corresponding to the tenth plunger cavity, and when the inner curve rotor rotates with the transmission shaft, the single plunger installed in the outer layer of the inner curve guide rail reciprocatingly and linearly moves in the plunger cavity corresponding to the outer flow channel stator.

2. An inner curve multi-action variable displacement radial piston test pump platform according to claim 1, characterized in that: The pump body comprises a front end cover and a rear end cover mounted on the transmission shaft, and the outer flow channel stator is connected into a whole; the inner curve rotor is mounted between the inner flow channel stator and the outer flow channel stator, the inner flow channel stator is connected with the rear end cover through bolts; the bearing end cover is fixedly connected to the rear end cover; the shaft seal is mounted between the front end cover and the transmission shaft; The rear end cover is provided with an oil inlet and an oil outlet, the oil inlet is connected with a low-pressure oil tank, the oil outlet is connected with an accumulator, and finally connected with a load; a pressure sensor and a flow sensor are mounted at the front end of the oil circuit of the accumulator, and a flow sensor is separately mounted at the rear end of the oil circuit of the accumulator.

3. An inner curve multi-action variable displacement radial piston test pump platform according to claim 2, characterized in that: The transmission shaft passes through the rear end cover, the rear end cover is connected with the outer flow channel stator through bolts, the rear end cover is located inside one side of the plunger hole and is provided with an annular oil suction cavity and an oil discharge cavity; the oil suction cavity and the oil discharge cavity are respectively communicated with each plunger hole on the inner flow channel stator through an oil suction channel and an oil discharge channel; meanwhile, an oil suction check valve is mounted in each oil suction channel, and an oil discharge check valve is mounted in each oil discharge channel; the oil suction channel and the oil discharge channel of the plunger hole of the outer flow channel stator are separately communicated with the vertically extending annular oil suction and discharge cavity on the rear end cover; one end of the valve port of the high-speed digital on-off valve mounted on the outer flow channel stator is communicated with the plunger cavity on the outer flow channel stator, and the other end is separately communicated with the oil suction cavity on the rear end cover.

4. An inner curve multi-action variable displacement radial piston test pump platform according to claim 3, characterized in that: The rear inner curve rotor is provided with outer equal acceleration and equal deceleration curve return guide rails and inner equal acceleration and equal deceleration curve return guide rails, and the front inner curve rotor is provided with outer equal acceleration and equal deceleration curve guide rails, outer equal acceleration and equal deceleration curve return guide rails, inner equal acceleration and equal deceleration curve guide rails and inner equal acceleration and equal deceleration curve return guide rails, respectively.

5. An inner curve multi-action variable displacement radial piston test pump platform according to claim 1, characterized in that: The pressure sensor is arranged in the oil suction cavity flow channel of the rear end cover, and the pressure sensor is also arranged in the plunger cavity of the outer flow channel stator.

6. A method of testing an inner curve multi-action variable-displacement radial piston test pump, characterized by: The method is applied to the inner curve multi-acting variable radial plunger test pump platform of any one of claims 1-5, and the method comprises: Driven by the prime mover, the transmission shaft rotates under the support of the front and rear tapered roller bearings, and the inner curve rotor rotates with the transmission shaft, thereby driving the rollers installed with the plunger to roll on the inner and outer equal acceleration and equal deceleration curve guide rails and return guide rails, so that the plunger performs periodic reciprocating motion in the plunger holes of the inner and outer flow channel stators; Under the forced driving of the inner and outer equal acceleration and equal deceleration curve guide rails, the plunger performs the oil discharge working stroke, and the plunger cavity volume decreases; under the forced return action of the inner and outer equal acceleration and equal deceleration curve return guide rails formed in the inner edge of the inner curve rotor, the plunger that has completed the forward stroke immediately performs the return oil suction stroke, and the plunger cavity volume increases; When the plunger cavity volume increases, a local negative pressure is formed in the plunger cavity, and the valve port of the oil suction check valve is opened under the pressure difference between the external atmospheric pressure and the internal negative pressure of the plunger cavity, so that low-pressure oil is sucked into the plunger cavity through the oil suction port and the oil suction cavity of the pump and the oil suction check valve; when the plunger cavity volume decreases, the hydraulic oil in the plunger cavity is extruded to increase the pressure, so that the oil suction check valve is closed; when the pressure of the hydraulic oil in the plunger cavity increases to be greater than or equal to the sum of the load pressure of the pump outlet and the opening pressure of the oil discharge check valve, the oil discharge check valve is opened, and high-pressure oil is discharged from the plunger cavity to the load circuit through the oil discharge cavity and the oil discharge port of the pump; The plunger completes multiple reciprocating motions and realizes multiple oil suction and discharge every time the inner curve rotor rotates one revolution, and the multiple plungers installed in the inner flow channel stator and the plunger separately installed in the outer flow channel stator will continuously perform reciprocating motion for oil suction and discharge under the continuous driving rotation of the inner curve rotor on the transmission shaft, thereby realizing the functions of pumping low-pressure oil and discharging high-pressure oil. The angle encoder monitors the rotation angle of the transmission shaft in real time and outputs a digital encoding signal. The digital encoding signal is used to control the opening and closing of the high-speed digital switch valve in real time. When the high-speed digital switch valve is not powered, the suction and discharge functions of the pump are completed by the suction and discharge check valves. The plunger in the external flow channel stator completely simulates the movement of the plunger in the internal flow channel stator. At this time, the pump can be used as a constant displacement pump. The influence of the high-speed digital switch valve on the pressure and displacement of the single-plunger flow distribution is studied. When the high-speed digital switch valve is powered by the digital encoding signal, the valve port of the high-speed digital switch valve is opened. In the process of reducing the volume of the plunger cavity and the progress of the plunger, the hydraulic oil in the plunger cavity will be returned to the suction cavity of the pump through the opened valve port of the high-speed digital switch valve. The external performance is that the high-pressure oil function of the plunger cavity is invalid, and the high-pressure oil flow output from the discharge port of the pump is reduced. That is, the displacement and pressure of the single-plunger cavity are adjusted to a smaller level. The pressure changes are monitored in real time by the pressure sensor installed inside the plunger cavity and the pressure sensor between the suction cavity and the high-speed digital switch valve. At the same time, the flow sensor monitors the flow changes and the pressure sensor monitors the pressure fluctuations in the oil line between the discharge port and the accumulator. The accumulator stabilizes the flow and pressure fluctuations, so that the entire plunger pump outputs stable pressure and flow to the load. According to the digital encoding signal output by the angle encoder, based on the digital timing control strategy, the power-on and power-off state and timing of the high-speed digital switch valve of the plunger cavity are controlled, the experimental research on the variable displacement and pressure regulation of the single-plunger of the plunger pump is completed, and the general control strategy is obtained. The law is generalized to the research on the pressure and displacement control strategy of multiple plungers, and then the control strategy of the output flow and pressure of the entire pump is realized.

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