A device and method for testing the performance of a plunger pump distribution pair under simulated deep-sea working conditions

Abstract

The present invention discloses a device and method for testing the performance of a piston pump distribution pair under simulated deep-sea working conditions, comprising a fixed cylinder; a transmission part; a loading part, comprising a loading cylinder and a simulation cylinder arranged at intervals, the loading cylinder being coaxially fixed to the inner wall of the fixed cylinder; an output shaft of the transmission part passing through the inner cavity of the loading cylinder and being fixed to the simulation cylinder; a pressing force implementation part, the loading cylinder hydraulic transmission pressing force implementation part providing pressure to the simulation cylinder; a support reaction force implementation part, comprising a support seat and a distribution plate to be tested; the first end of the support seat is arranged in the fixed cylinder; the distribution plate to be tested is fixed to the end face of the first end of the support seat, and the end face of the simulation cylinder away from the loading cylinder is rotatably abutted against the outer surface of the distribution plate to be tested; an oil separator prevents mutual leakage of hydraulic oil in the loading cylinder and the distribution plate to be tested; and a torque measuring part measures the torque of the distribution plate to be tested. The present invention can simulate the actual working state of the distribution pair under deep-sea working conditions and test and evaluate the performance of the distribution pair under this state.

Description

Technical Field

[0001] The present invention relates to the technical field of hydraulic pump performance testing, and more particularly to a device and method for testing the performance of a flow distribution pair of a plunger pump under simulated deep-sea working conditions. Background Art

[0002] The deep sea holds abundant mineral and energy resources. With terrestrial resources becoming increasingly scarce, deep-sea development has garnered widespread attention worldwide. my country is also actively engaged in the research and development of full-ocean-depth submersibles. As a key power component in hydraulic transmission technology, plunger pumps, characterized by high pressure, high efficiency, and long life, are widely used in deep-sea equipment.

[0003] A plunger pump is a positive displacement pump that uses the reciprocating motion of the plunger within the cylinder bore to change the volume within the cylinder, achieving both suction and discharge of liquid. In a swash plate axial piston pump, the friction pair is the most critical component. This type of pump comprises three major friction pairs: the plunger pair (plunger and cylinder bore), the shoe pair (shoe and swash plate), and the port pair (port plate and cylinder port end face). These three friction pairs directly determine pump performance, affecting both efficiency and service life. This is also a key challenge in plunger pump design, placing high demands on component materials, structure, and processing technology. Therefore, testing each friction pair is essential to achieving high-performance plunger pump design.

[0004] The valve plate, the most critical friction pair in an axial piston pump, consists of the rotating cylinder and the valve plate. The valve plate not only distributes the flow but also supports the cylinder, maintaining force balance. During pump operation, a pair of opposing forces act between the high-speed rotating cylinder and the valve plate: a compressive force exerted on the valve plate by the high-pressure oil in the piston chamber, and a hydraulic support force exerted on the cylinder by the oil film pressure on the valve window and sealing strip. Due to the dual functions of the valve plate, a tight fit must be maintained between the valve plate end face of the cylinder and the valve plate, while also ensuring good lubrication conditions and appropriate compression and compression stresses. Current research on the valve plate primarily focuses on its frictional and lubrication characteristics and load-bearing capacity. Friction in the valve plate is typically mixed friction. The oil film thickness in this area can be considered the valve plate clearance. Increased film thickness increases leakage, reducing the pump's volumetric efficiency. Reduced film thickness leads to poor lubrication conditions, potentially leading to wear failure and plate burnout, seriously impacting the performance and service life of the piston pump.

[0005] In deep-sea operating conditions, high ambient pressures can cause deformation of hydraulic components. The density, viscosity, and temperature of the fluid vary significantly with increasing depth. These changes affect the friction, lubrication, leakage, and efficiency loss conditions of the distribution pair. Current research on distribution pair performance primarily involves constructing distribution pair performance test benches to delve into the lubrication load-bearing mechanisms and efficiency losses of the distribution pair. However, research on distribution pairs operating in deep-sea conditions remains relatively limited.

[0006] Therefore, a simple and effective test device is needed to simulate the working conditions of the flow distribution pair under deep-sea conditions and monitor them, so as to support the quantitative research of the flow distribution pair under variable sea depth conditions and provide a basis for its optimized design. Summary of the Invention

[0007] In view of this, the present invention provides a device and method for testing the performance of a piston pump distribution pair under simulated deep-sea working conditions, which can simulate the actual working state of the distribution pair under deep-sea working conditions and test and evaluate the performance of the distribution pair under this state. The actual working condition of the piston pump distribution pair is simulated by grinding a fixed distribution disc to be tested against a high-speed rotating simulated cylinder body; hydraulic clamping force and hydraulic support reaction force are applied by an independent constant pressure source, the friction and wear of the distribution pair are monitored under different clamping coefficients, and the leakage oil of the distribution pair is collected to evaluate the leakage rate; by measuring the friction torque transmitted by the rotating simulated cylinder body to the distribution disc to be tested, the mechanical efficiency loss of the distribution pair and the equivalent friction coefficient of mixed friction are indirectly calculated, thereby evaluating the change in efficiency loss of the distribution pair under variable sea depth conditions.

[0008] In order to achieve the above-mentioned purpose, the present invention adopts the following technical scheme: a performance test device of a piston pump distribution pair under simulated deep-sea working conditions, comprising a fixed cylinder, a transmission part, a loading part, a clamping force implementation part, a support and reaction force implementation part, an oil separator and a torque measuring part; the transmission part is fixed to the first end of the fixed cylinder; the loading part comprises a loading cylinder and a simulation cylinder arranged at intervals, and the loading cylinder is coaxially fixed to the inner wall of the fixed cylinder; the output shaft of the transmission part passes through the inner cavity of the loading cylinder and is fixed to the simulation cylinder; the clamping force implementation part is arranged between the loading cylinder and the simulation cylinder; the hydraulic transmission part of the loading cylinder is connected to the clamping force implementation part to provide pressure to the simulation cylinder; the support and reaction force implementation part The application part includes a support seat and a distribution disc to be tested; the first end of the support seat is located in the inner cavity of the fixed cylinder body corresponding to its second end; the distribution disc to be tested is fixed to the first end face of the support seat; the end face of the simulation cylinder body away from the loading cylinder body is rotatably abutted with the outer surface of the distribution disc to be tested; the support seat is provided with a test high-pressure oil port and a test low-pressure oil port connected to the distribution disc to be tested, and a high-pressure return oil port is provided on its first end; the oil separator is provided between the simulation cylinder body and the clamping force implementation part to prevent mutual leakage of hydraulic oil in the loading cylinder body and the distribution disc to be tested; the torque measuring part is fixed to the second end of the fixed cylinder body and is connected to the second end of the support seat by a key to measure the torque of the distribution disc to be tested.

[0009] The beneficial effect of the technical solution of the present invention is that the rotation of the simulated cylinder is driven by the transmission part, and after the hydraulic oil is introduced into the loaded cylinder, the clamping force implementation part can be driven to provide pressure for the simulated cylinder to compress the distribution disc to be tested, and the rotation of the simulated cylinder is used to rub against the distribution disc to be tested, and high-pressure hydraulic oil is introduced into the distribution disc to be tested through the support seat to simulate the actual working condition of the distribution pair of the plunger pump, and by measuring the friction torque transmitted by the rotating simulated cylinder to the distribution disc to be tested, the mechanical efficiency loss of the distribution disc to be tested and the equivalent friction coefficient of the mixed friction are indirectly calculated, so as to evaluate the change in efficiency loss of the distribution pair under variable sea depth conditions.

[0010] Preferably, the oil separator includes an oil separator ring and an oil collecting ring; both side surfaces of the oil separator ring are provided with bell mouths; the inner walls of the oil separator ring relative to the two bell mouths are respectively fixed to the outer wall of the simulation cylinder and abut against the end of the clamping force implementation part away from the loading cylinder; the outer wall of the oil collecting ring abuts against the inner wall of the fixed cylinder and covers the support seat and the outer wall of the oil separator ring corresponding to the simulation cylinder; the outer walls of the oil collecting ring and the fixed cylinder are provided with an oil collecting port connected to the inner cavity of the oil collecting ring. The oil separator ring can separate the hydraulic oil between the loading cylinder and the valve plate to be tested to prevent the hydraulic oil from flowing, and the oil collecting ring is used to collect the oil leakage of the valve plate to be tested to evaluate the leakage rate of the valve plate to be tested.

[0011] Preferably, the fixed cylinder includes a cylinder barrel and a cylinder seat; the cylinder seat is bolted to the first end of the cylinder barrel; the cylinder seat is provided with a high-pressure loading oil port and a low-pressure loading oil port that communicate with the inner cavity of the loading cylinder; the transmission unit is fixed to the end of the cylinder seat away from the cylinder barrel. High-pressure hydraulic oil is passed into the loading cylinder through the cylinder seat to provide a compressive force to the simulation cylinder.

[0012] Preferably, the reaction force implementing portion further comprises a bearing seat and a support bearing; one end of the bearing seat is bolted to the second end of the cylinder; the support bearing is embedded in the bearing seat; the outer wall of the support seat away from the end of the cylinder is press-fitted with the inner ring of the support bearing to support the support seat. The support seat is supported by the bearing seat and the support bearing, so that the support seat is stable within the inner cavity of the fixed cylinder body. The support seat is used to fix the valve plate to be tested, and the friction torque of the valve plate to be tested can be measured by simulating the rotation of the cylinder body.

[0013] Preferably, the torque measuring unit includes a mounting base and a torque sensor. The mounting base is bolted to the end of the bearing base away from the cylinder, and the torque sensor is fixed to the mounting base. The end of the support base away from the cylinder is connected to the mounting base via a key. The key connection between the support base and the mounting base can achieve fixed position, thereby achieving transmission of the valve plate torque to be measured. The torque sensor measures the torque of the mounting base to achieve measurement of the valve plate torque to be measured.

[0014] Preferably, the loading part further includes a cylinder sleeve and a loading distribution plate; the outer wall of the cylinder sleeve abuts against the inner wall of the fixed cylinder; the inner wall of the cylinder sleeve is provided with a plurality of slots; a block adapted to the slot is fixed at one end of the loading cylinder and is clamped in the cylinder sleeve; a plurality of loading waist-shaped holes are provided on the end face of the loading cylinder away from the block; a loading high-pressure waist-shaped hole and a loading low-pressure waist-shaped hole are provided on the loading distribution plate; the loading distribution plate is tightly fitted with the end of the loading cylinder away from the block. The fit between the block and the slots at different positions can adjust the number of loading waist-shaped holes and high-pressure waist-shaped holes, thereby realizing variable distribution of the loading cylinder.

[0015] Preferably, the transmission unit includes a motor, a deep groove ball bearing, and a transmission shaft; the motor is fixed to the end of the cartridge seat away from the cylinder; the outer ring of the deep groove ball bearing is embedded in the inner wall of the cartridge seat; one end of the transmission shaft is fastened to the output shaft of the motor via a coupling, and the other end passes through the cartridge seat and the inner cavity of the loading cylinder in sequence and is connected to the simulation cylinder via a key. The rotation of the simulation cylinder is driven by the motor.

[0016] Preferably, the compressive force applying portion includes a plunger, a sliding shoe, and a spring; the inner wall of the loading cylinder is provided with a plurality of plunger holes; one end of each of the plungers is inserted into the plurality of plunger holes in a one-to-one correspondence; one end of the sliding shoe is engaged with the other end of the plunger, and the other end of the sliding shoe abuts against the side end surface of the oil separator ring; the spring is sleeved on the outer walls of the sliding shoe and the plunger, with its two ends abutting against the oil separator ring and the opposite side walls of the loading cylinder. The plunger, sliding shoe, and spring together constitute the plunger sliding shoe assembly of a conventional plunger pump. By introducing hydraulic oil into the plunger hole, the plunger sliding shoe assembly can provide a compressive force to the simulation cylinder.

[0017] The present invention also provides a method for testing the performance of a plunger pump distribution pair under simulated deep-sea operating conditions. The method employs a plunger pump distribution pair performance testing device for simulating deep-sea operating conditions, as described in the aforementioned technical solution, to perform the performance test. The device also includes a temperature control module, which is connected to the inner cavity of the loading cylinder and the distribution plate to be tested via pipelines to change the viscosity of the hydraulic oil. Hydraulic oil becomes thinner when heated. Hydraulic oil with a thicker viscosity is suitable for deep-sea operating conditions, while hydraulic oil with a thinner viscosity is suitable for shallow-sea operating conditions. By varying the viscosity of the hydraulic oil through the temperature control module, hydraulic pressure and hydraulic support reaction forces are provided for different sea depths.

[0018] The loading cylinder is fed with high-pressure hydraulic oil and drives the pressing force implementation part to provide pressure to the simulation cylinder, and the test valve plate to be tested is fed with test high-pressure hydraulic oil to simulate deep-sea working conditions; the transmission part drives the simulation cylinder to rotate, and the friction torque is generated on the valve plate to be tested during the rotation of the simulation cylinder, and the mechanical efficiency loss of the valve plate to be tested and the equivalent friction coefficient of mixed friction are calculated; the oil viscosity of the test high-pressure hydraulic oil entering the valve plate to be tested is changed by the temperature control module to simulate deep-sea working conditions.

[0019] The beneficial effect of the above technical solution is that hydraulic oil of different viscosities is input into the distribution plate to be tested through the support seat and the viscosity of the hydraulic oil is changed through the temperature control module. The hydraulic oil will become thinner after heating. The hydraulic oil with high viscosity can correspond to deep-sea working conditions, and the hydraulic oil with thin viscosity corresponds to shallow-sea working conditions. The viscosity of the hydraulic oil is changed by the temperature control module to simulate the variable sea depth environment, so as to simulate the performance test of the plunger pump distribution pair under different sea depth conditions.

[0020] It can be seen from the above technical solution that compared with the prior art, the present invention discloses a device and method for testing the performance of the distribution pair of a plunger pump under simulated deep-sea working conditions, which has the following beneficial effects: 1. In the implementation method of the hydraulic clamping force, a loading cylinder and a loading distribution plate are used to implement the clamping force, which is convenient and feasible, and closer to the actual working conditions of the pump; 2. Through the special oil-isolating part design, the leakage is isolated and independently collected, avoiding cumbersome sealing measures, and the device structure is simple and more feasible; without actually measuring the oil film thickness of the distribution plate to be tested, the device can also evaluate the efficiency loss and equivalent friction coefficient of the distribution plate to be tested under different friction and lubrication conditions, different medium viscosity conditions, and different clamping coefficients, making the experiment simpler and more feasible; 3. The temperature control module tests the distribution plate to be tested by changing the viscosity of the hydraulic oil, which has a reference significance for the onshore experimental research on the efficiency loss of deep-sea plunger pumps and other components, and is convenient for simplifying the study of the efficiency evolution law under variable sea depth conditions and guiding the optimization design of deep-sea components. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are merely embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the provided drawings without paying any creative work.

[0022] Figure 1 A front cross-sectional view of the testing device provided by the present invention;

[0023] Figure 2 for Figure 1 A magnified schematic diagram of part A in FIG;

[0024] Figure 3 A top cross-sectional view of the test device provided by the present invention with the base removed;

[0025] Figure 4 A front cross-sectional view of the test device provided by the present invention with the base removed;

[0026] Figure 5 A schematic diagram of the layout of the temperature control module of the test device provided by the present invention;

[0027] Figure 6 Schematic diagram of the support structure provided by the present invention Figure 1 ;

[0028] Figure 7 Schematic diagram of the support structure provided by the present invention Figure 2 ;

[0029] Figure 8Schematic diagram of the structure of the distribution plate to be tested provided by the present invention Figure 1 ;

[0030] Figure 9 Schematic diagram of the structure of the distribution plate to be tested provided by the present invention Figure 2 ;

[0031] Figure 10 A schematic diagram of the cylinder sleeve structure provided by the present invention;

[0032] Figure 11 Schematic diagram of the loading cylinder structure provided by the present invention Figure 1 ;

[0033] Figure 12 Schematic diagram of the loading cylinder structure provided by the present invention Figure 2 ;

[0034] Figure 13 A schematic diagram of the structure of the loading distribution plate provided for the invention;

[0035] Figure 14 A schematic diagram of the cartridge seat structure provided by the present invention;

[0036] Figure 15 A schematic diagram of the oil separator structure provided by the present invention;

[0037] Figure 16 This is a schematic diagram of the transmission shaft structure provided by the present invention.

[0038] Among them: 1-fixed cylinder body; 11-cylinder; 111-cylinder drainage groove; 112-cylinder oil unloading port; 113-cylinder drainage port; 12-cylinder seat; 121-loading high-pressure oil port; 122-loading low-pressure oil port; 123-motor mounting stop groove; 124-cylinder seat drainage hole; 125-cylinder seat high-pressure area waist groove; 126-cylinder seat low-pressure area waist groove; 13-cylinder loading hydraulic pipe joint; 14-cylinder test hydraulic pipe joint; 2-transmission part; 21-motor; 22-coupling; 23-transmission shaft; 231-fixed key; 232- Drive shaft annular groove; 24-deep groove ball bearing; 3-loading part; 31-loading cylinder; 311-plunger hole; 312-block; 313-loading waist-shaped hole; 32-loading distribution plate; 321-loading waist-shaped hole in high-pressure area; 322-loading waist-shaped hole in low-pressure area; 33-cylinder sleeve; 331-slot; 34-simulated cylinder; 4-clamping force implementation part; 41-plunger; 42-slipper; 43-spring; 5-oil separator; 51-oil separator ring; 511-special-shaped hole; 52-oil collecting ring; 521-oil collecting cavity; 522-oil collecting ring drainage hole ; 53- pagoda joint; 54- measuring cylinder; 55- collecting cylinder; 6- reaction force implementation part; 61- support seat; 611- test high-pressure oil port; 612- high-pressure oil return port; 613- support seat high-pressure waist-shaped groove; 614- support seat low-pressure waist-shaped groove; 615- test low-pressure oil port; 616- support seat drainage hole; 617- support seat annular groove; 618- torque transmission boss; 619- mounting hole of the distribution plate to be tested; 62- distribution plate to be tested; 621- drainage hole of the distribution plate to be tested; 622- waist-shaped hole of the high-pressure area of ​​the distribution plate to be tested; 623- Measure the waist-shaped hole in the low-pressure area of ​​the distribution disc; 624-mounting boss of the distribution disc to be measured; 625-external sealing belt of the distribution disc to be measured; 626-inner sealing belt of the distribution disc to be measured; 63-bearing seat; 64-support bearing; 65-locking nut; 7-torque measuring part; 71-torque sensor; 72-mounting seat; 8-base; 9-temperature control module; 91-first temperature and pressure sensor; 92-second temperature and pressure sensor; 93-overflow valve; 94-first constant pressure source; 95-second constant pressure source; 96-first low-pressure feeder; 97-second low-pressure feeder. DETAILED DESCRIPTION

[0039] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0040] Example 1: The embodiment of the present invention discloses a performance test device for a piston pump distribution pair under simulated deep-sea working conditions, comprising a fixed cylinder 1, a transmission part 2, a loading part 3, a pressing force implementation part 4, a support reaction force implementation part 6, an oil separator 5 and a torque measuring part 7; the transmission part 2 is fixed to the first end of the fixed cylinder 1; the loading part 3 comprises a loading cylinder 31 and a simulation cylinder 34 arranged at intervals, and the loading cylinder 31 is coaxially fixed to the inner wall of the fixed cylinder 1; the output shaft of the transmission part 2 passes through the inner cavity of the loading cylinder 31 and is fixed to the simulation cylinder 34; the pressing force implementation part 4 is arranged between the loading cylinder 31 and the simulation cylinder 34; the hydraulic transmission part of the loading cylinder 31 is connected to the pressing force implementation part 4 to provide pressure to the simulation cylinder 34; The first end of the support seat 61 is located in the inner cavity of the fixed cylinder body 1 corresponding to its second end; the distribution disc 62 to be tested is fixed on the first end face of the support seat 61; the end face of the simulation cylinder body 34 away from the loading cylinder body 31 is rotatably abutted against the outer surface of the distribution disc 62 to be tested; a test high-pressure oil port 611 and a test low-pressure oil port 615 connected to the distribution disc 62 to be tested are provided on the support seat 61, and a high-pressure return oil port 612 is provided on its first end; the oil separator 5 is provided between the simulation cylinder body 34 and the clamping force implementation part 4 to prevent mutual leakage of hydraulic oil in the loading cylinder body 31 and the distribution disc 62 to be tested; the torque measuring part 7 is fixed on the second end of the fixed cylinder body 1 and is connected to the second end of the support seat 61 by a key to measure the torque of the distribution disc 62 to be tested.

[0041] like Figure 1 As shown in Figure 3, the hydraulic transmission pressing force implementation part of the loading cylinder is used. The pressing force implementation part can make the simulated cylinder press the distribution disc to be tested. At the same time, the distribution disc to be tested is fixed in the fixed cylinder through a support seat. Hydraulic oil is introduced into the distribution disc to be tested through the support seat, which can simulate the actual working state of the distribution pair. During the test, the distribution disc to be tested is fixed and the simulated cylinder rotates. The friction between the two occurs, which makes the distribution disc to be tested generate friction torque. The friction torque of the distribution disc to be tested is measured by the torque measuring part, and the mechanical efficiency loss of the distribution pair and the equivalent friction coefficient of mixed friction can be indirectly calculated. This is used to evaluate the change in efficiency loss of the distribution pair under deep-sea working conditions.

[0042] In this embodiment, the oil-isolating portion 5 includes an oil-isolating ring 51 and an oil-collecting ring 52; both side surfaces of the oil-isolating ring 51 are provided with bell mouths; the inner walls of the oil-isolating ring 51 relative to the two bell mouths are respectively fixed to the outer wall of the simulation cylinder 34 and abut against the end of the clamping force implementation portion 4 away from the loading cylinder 31, and the oil-isolating ring 51 is bolted and fastened to the simulation cylinder 34; the outer wall of the oil-collecting ring 52 abuts against the inner wall of the fixed cylinder 1 and is covered with a support seat 61 and the outer wall of the oil-isolating ring 51 corresponding to the simulation cylinder 34; the outer wall of the oil-collecting ring 52 and the fixed cylinder 1 are provided with an oil collecting port connected to the inner cavity of the oil-collecting ring 52.

[0043] like Figure 2 and 15As shown, the oil separator ring adopts a unique bell-mouth design. The sidewalls of the bell-mouth prevent hydraulic oil entering the valve plate under test and leaking from the loading cylinder from leaking into each other. The oil separator ring isolates and independently collects leaks, avoiding cumbersome sealing measures and simplifying the device structure for greater feasibility.

[0044] In some other specific embodiments, such as Figure 3 As shown, the clamping force implementation part 4 includes a plunger 41, a slipper 42 and a spring 43; a plurality of plunger holes 311 are provided on the inner wall of the loading cylinder 31; one end of the plurality of plungers 41 is inserted into the plurality of plunger holes 311 in a one-to-one correspondence; a spherical head is fixed to the end of the plunger 41 away from the loading cylinder 31, and a spherical groove is provided at one end of the slipper 42, and the spherical head of the plunger 41 is embedded in the spherical groove of the slipper 42. The plunger 41 and the slipper 42 form a plunger slipper assembly through spherical contact, and the end of the slipper 42 away from the spherical core groove abuts against the side end face of the oil separator 51; the spring 43 is sleeved on the outer walls of the slipper 42 and the plunger 41, and its two ends abut against the two side walls opposite to the oil separator 51 and the loading cylinder 31 respectively.

[0045] like Figure 2 and 15 As shown, the oil separator 51 has a double-flared design, with the two bell-shaped openings respectively enclosing the simulated cylinder 34 and the sliding shoe 42. This bell-shaped oil separator prevents leakage between the oil in the test valve plate 62 and the oil in the loading cylinder 31. The oil separator in this embodiment utilizes a unique bell-shaped design. The sidewalls of the bell-shaped opening prevent hydraulic oil entering the test valve plate and leaking from the loading cylinder from leaking into each other. The oil separator isolates and independently collects leaks, avoiding complex sealing measures and simplifying the device structure for greater feasibility.

[0046] The clamping force implementation part in this embodiment uses the cylinder body, distribution plate and plunger slipper assembly in the pump core of a conventional inclined plate axial piston pump for loading, which is convenient and feasible; the arrangement of the compression spring is optimized to be closer to the actual working condition of the pump.

[0047] like Figure 3 As shown, the oil collecting ring 52 is a hollow cylindrical structure, and its inner cavity is an oil collecting cavity 521. The outer wall of the oil collecting ring 52 is provided with an oil collecting ring drainage hole 522, and the outer wall of the fixed cylinder body 1 is provided with a cylinder drainage port 113 corresponding to the oil collecting ring drainage hole 522. The fixed cylinder 1 is fixed to the upper end of the base 8, and a measuring cylinder 54 is provided below the base 8 corresponding to the cylinder drainage port 113. The oil leaked from the distribution plate 62 to be tested is collected by the measuring cylinder 54 to evaluate the change in volumetric efficiency loss of the distribution plate 62 to be tested.

[0048] In order to further optimize the above technical solution, the fixed cylinder body 1 includes a cylinder barrel 11 and a cylinder seat 12; the cylinder seat 12 is bolted to the first end of the cylinder barrel 11; a loading high-pressure oil port 121 and a loading low-pressure oil port 122 connected to the inner cavity of the loading cylinder body 31 are provided on the cylinder seat 12; the transmission part 2 is fixed to the end of the cylinder seat 12 away from the cylinder barrel 11.

[0049] High-pressure hydraulic oil is injected into the plunger hole 311 of the loading cylinder 31 through the loading high-pressure oil port 121, and the pressure of the high-pressure hydraulic oil is used to push the plunger 41 so that the sliding shoe 42 can apply pressure to the simulation cylinder 34. Figure 13 As shown, the end of the cartridge seat 12 facing the cylinder barrel 11 is provided with a boss. Along the length of the boss, a waist-shaped groove 125 in the high-pressure region of the cartridge seat is provided, corresponding to the high-pressure oil loading port 121, and a waist-shaped groove 126 in the low-pressure region of the cartridge seat is provided, corresponding to the low-pressure oil loading port 122. Both the waist-shaped groove 125 and the low-pressure region of the cartridge seat are connected to the plunger hole 311. By setting up high-pressure and low-pressure regions, land-based simulation tests of the flow distribution pair performance under variable sea depth conditions were conducted.

[0050] In other specific embodiments, the transmission part 2 includes a motor 21, a deep groove ball bearing 24 and a transmission shaft 23; the motor 21 is fixed to the end of the cylinder seat 12 away from the cylinder 11; the outer ring of the deep groove ball bearing 24 is embedded in the inner wall of the cylinder seat 12; the outer wall of the transmission shaft 23 is interference fit with the inner ring of the deep groove ball bearing 24 and one end of the transmission shaft is fastened to the output shaft of the motor 21 through a coupling 22, and the other end passes through the cylinder seat 12 and the inner cavity of the loading cylinder 31 in sequence and is connected to the simulation cylinder 34 through a key.

[0051] The motor 21 is installed through the motor mounting stop groove 123 opened on the cylinder seat 12; one end of the transmission shaft 23 is connected to the motor 21 through the coupling 22, and the other end passes through the inner cavity of the loading cylinder 31 and is connected to the simulation cylinder 34 through a key. At the same time, the transmission shaft 23 and the oil separator 51 are also connected through a key, which enables the motor 21 to drive the oil separator 51 and the simulation cylinder 34 to rotate synchronously when it is running, and the other components remain stationary.

[0052] In this embodiment, the oil leaked from the loading cylinder 31 is collected as follows: the high-pressure oil flows into the plunger hole 311 through the loading high-pressure oil port 121 and the waist-shaped groove 125 in the high-pressure area of ​​the cylinder seat; the low-pressure oil flows into the plunger hole 311 through the loading low-pressure oil port 122 and the waist-shaped groove 126 in the low-pressure area of ​​the cylinder seat; a cylinder oil unloading port 112 is provided on the outer wall of the cylinder 11 corresponding to the clamping force implementation part 4, and the oil leaked from the loading cylinder 31 is collected through the cylinder oil unloading port 112.

[0053] In some other specific embodiments, a collecting cylinder 55 is provided below the base 8 relative to the cylinder oil unloading port 112 , and the oil leaked from the loading cylinder 31 flowing out of the cylinder oil unloading port 112 is collected by the collecting cylinder 55 .

[0054] In order to further optimize the above technical solution and prevent the leakage oil at the loading distribution plate 32 from axially leaking along the drive shaft 23 and the cylinder seat 12, a circle of drive shaft annular grooves 232 are opened on the drive shaft 23 in the circumferential direction, and a cylinder seat drainage hole 124 corresponding to the drive shaft annular groove 232 is opened on the convex column of the cylinder seat 12. The inner wall of the cylinder 11 is provided with a cylinder drainage groove 111 connected to the cylinder seat drainage hole 124. The leakage oil at the loading distribution plate 32 enters the cylinder seat drainage hole 124 through the drive shaft annular groove 232, is introduced into the inner cavity of the cylinder 11 through the cylinder drainage groove 111, and finally flows into the collection cylinder 55 through the cylinder oil unloading port 112 for collection.

[0055] In some other specific embodiments, a pagoda joint 53 is fixed at both the cylinder oil unloading port 112 and the cylinder drainage port 113 to facilitate the drainage of leaked oil.

[0056] In order to further optimize the above technical solution, the reaction force implementation part 6 also includes a bearing seat 63 and a support bearing 64; one end of the bearing seat 63 is bolted to the second end of the cylinder 11 away from the cylinder seat 12; the support bearing 64 is embedded in the bearing seat 63; the outer wall of the support seat 61 at one end away from the cylinder 11 is pressed tightly with the inner ring of the support bearing 64 to support the support seat 61.

[0057] like Figure 2 As shown, the bearing seat 63 is connected to the second end of the cylinder 11 relative to the cylinder seat 12 by bolts, and an angular contact thrust support bearing 64 is embedded in the bearing seat 63. The end of the support seat 61 away from the cylinder 11 is embedded in the inner ring of the support bearing 64 and fastened by a locking nut 65, so as to ensure that the support seat 61 stably supports the distribution plate 62 to be tested.

[0058] In order to further optimize the above technical solution, the torque measuring part 7 includes a mounting seat 72 and a torque sensor 71. The mounting seat 72 is bolted to the end of the bearing seat 63 away from the cylinder 11, and the torque sensor 71 is fixed on the mounting seat 72; the end of the support seat 61 away from the cylinder 11 is connected to the mounting seat 72 by a key.

[0059] like Figure 4As shown, a torque transmission boss 618 is fixed to the end of the support seat 61 away from the valve plate 62 to be tested, and a socket is provided on the end of the mounting seat 72 facing the cylinder barrel 11. The torque transmission boss 618 and the socket of the mounting seat 72 are plugged into each other. The mounting seat 72 is fixed to the bearing seat 63, and the support seat 61 is plugged into the mounting seat 72. When the simulated cylinder body 34 and the valve plate 62 to be tested are rubbed against each other, the support seat 61 has a tendency to rotate, but due to the fixed connection between the mounting seat 72 and the bearing seat 62, the support seat 61 remains stationary; the axes of the mounting seat 72 and the support seat 61 coincide with the center line of the valve plate 62 to be tested. When the simulated cylinder body 34 generates friction torque on the valve plate 62 to be tested, the friction torque can be transmitted to the mounting seat 72 and measured by the torque sensor 71.

[0060] The function of the locking nut is to circumferentially secure the support bearing and the support seat to prevent movement. This is similar to normal bearing installation methods, which include diagonal fixation and four-corner fixation. At the same time, the locking nut preloads the support bearing, regulating the clearance and improving the support bearing's load-bearing capacity. The support seat and the inner ring of the bearing have an interference fit and can rotate together. The reason the support seat cannot rotate is that it is connected to the mounting seat via a key, and the mounting seat is fixed and does not rotate. There is abutment between the two, simulating the cylinder body transmitting torque to the valve plate to be tested and the support seat, causing them to have a tendency to rotate. However, due to the fixation of the mounting seat and the bearing seat, they do not actually rotate. Therefore, the torque of the valve plate to be tested can be measured through the transmission of torque.

[0061] In order to further optimize the above technical solution, so that the transmission shaft drives the oil separator ring and the simulated cylinder body to rotate synchronously, a fixed key 231 is fixed on the end of the transmission shaft 23 away from the coupling 22; the oil separator ring 51 is bolted to the simulated cylinder body 34; and a special-shaped hole 511 adapted to the fixed key 231 is opened in the middle of the oil separator ring 51; the transmission shaft 23 passes through the inner cavity of the cylinder barrel 11 and is key-connected with the oil separator ring 51 and the simulated cylinder body 34 by means of the fixed key 231 and the special-shaped hole 511.

[0062] In this embodiment, if Figure 5As shown in Figure 8, a mounting boss 624 for the valve plate to be tested is provided in the middle of one side surface of the valve plate to be tested, and a mounting hole 619 for the valve plate to be tested that is adapted to the mounting boss 624 for the valve plate to be tested is provided at the end of the support seat 61 located in the inner cavity of the cylinder barrel 11. The valve plate to be tested 62 and the support seat 61 are fastened together by plugging the mounting boss 624 for the valve plate to be tested into the mounting hole 619 for the valve plate to be tested; the fixing key 231 sequentially penetrates the inner cavity of the loading cylinder 31, the special-shaped hole 511, the inner cavity of the simulation cylinder 34, and is connected to the simulation cylinder 34 and the oil separator. The ring 51 realizes the key connection; the outer wall of the transmission shaft 23 is provided with a convex edge, and the oil-isolating ring 51 and the simulated cylinder body 34 are limited on the rod wall between the convex edge of the transmission shaft 23 and the fixed key 231; the first end of the support seat 61 is supported in the inner cavity of the cylinder 11 by the transmission shaft 23 structure and the bearing seat 63, and there is no rigid contact between the support seat 61 and the inner wall of the cylinder 11. The clamping force of the simulated cylinder body 34 on the distribution plate 62 to be tested is borne by the support bearing 64, and the friction torque transmitted by the simulated cylinder body 34 to the distribution plate 62 to be tested can be measured by the torque measuring part 7.

[0063] like Figure 8 and 9 As shown, a waist-shaped hole 623 in the low-pressure area of ​​the distribution plate to be tested and three waist-shaped holes 622 in the high-pressure area of ​​the distribution plate to be tested are opened on the disk surface of the distribution plate 62 on the side to be tested; one waist-shaped hole 623 in the low-pressure area of ​​the distribution plate to be tested and three waist-shaped holes 622 in the high-pressure area of ​​the distribution plate to be tested are arranged radially symmetrically with respect to the distribution plate 62 on the side to be tested.

[0064] The support seat 61 is also provided with a high-pressure oil area and a low-pressure oil area corresponding to the loading cylinder 31. The high-pressure oil area on the support seat 61 corresponds to the waist-shaped hole 622 in the high-pressure area of ​​the valve plate to be tested, and the low-pressure oil area corresponds to the waist-shaped hole 623 in the low-pressure area of ​​the valve plate to be tested; Figure 1 As shown in ~3, the test high-pressure oil port 611 is connected to the waist-shaped hole 622 in the high-pressure area of ​​the distribution disc to be tested on the distribution disc to be tested 62 on the side through the high-pressure waist-shaped groove 613 of the support seat; the test low-pressure oil port 615 is connected to the waist-shaped hole 623 in the low-pressure area of ​​the distribution disc to be tested on the side distribution disc 62 through the support seat low-pressure waist-shaped groove 614 on the support seat; one end of the support seat 61 located in the cylinder 11 is provided with a high-pressure return oil port 612 connected to the oil collecting chamber 521; the outer wall of the cylinder 11 corresponding to the high-pressure return oil port 612 is fixed with a cylinder test hydraulic pipe joint 14, and the cylinder test hydraulic pipe joint 14 is connected to the high-pressure return oil port 612; the high-pressure hydraulic oil enters the waist-shaped hole 622 in the high-pressure area of ​​the distribution disc to be tested through the test high-pressure oil port 611 and the high-pressure waist-shaped groove 613 of the support seat, and then flows back to the hydraulic oil supply system through the test high-pressure return oil port 612 and the cylinder test hydraulic pipe joint 14, thereby forming a closed test high-pressure hydraulic oil circuit.

[0065] In order to further optimize the above technical solution and test the change in volumetric efficiency loss of the distribution plate to be tested, a cylinder drainage port 113 connected to the oil collecting ring drainage hole 522 is opened on the outer wall of the cylinder 11 corresponding to the distribution plate to be tested 62, and a cylinder oil unloading port 112 is opened on the side wall corresponding to the sliding shoe 42. A measuring cylinder 54 is provided below the base 8 corresponding to the cylinder oil unloading port 112, and the oil leaked from the simulated cylinder body 34 is collected through the measuring cylinder 54.

[0066] In order to further optimize the above technical solution and prevent the oil at the tested distribution disc 62 from leaking axially along the support seat 61, the outer wall of the support seat 61 located in the cylinder 11 is provided with a support seat annular groove 617, and a radial support seat drainage hole 616 is provided at its end. The annular surface of the tested distribution disc 62 is respectively fixed with an inner sealing belt 626 of the tested distribution disc and an outer sealing belt 625 of the tested distribution disc, which are spaced apart inside and outside. A distribution disc drainage hole 621 to be tested that is connected to the support seat drainage hole 616 is provided on the disk surface of the tested distribution disc 62 between the inner sealing belt 626 of the tested distribution disc and the outer sealing belt 625 of the tested distribution disc.

[0067] The leaked oil at the sealing band 626 in the distribution disc to be tested flows from the drainage hole 621 of the distribution disc to be tested through the support seat drainage hole 616 opened on the support seat and connected to it, and the leakage at the sealing band in the distribution disc to be tested is introduced into the oil collecting chamber 521; the support seat annular groove 617 is located on the side of the support seat drainage hole 616 away from the distribution disc to be tested 62, which is used to isolate the oil flowing out of the support seat drainage hole 616 from the axial leakage of the support seat 61. In this way, the oil leaked from the distribution disc to be tested 62 can be completely collected in the oil collecting chamber 521.

[0068] In this embodiment, the loading part 3 also includes a cylinder sleeve 33 and a loading distribution plate 32; the outer wall of the cylinder sleeve 33 abuts the inner wall of the fixed cylinder 1; the inner wall of the cylinder sleeve 33 is provided with a plurality of slots 331; a block 312 adapted to the slot 331 is fixed at one end of the loading cylinder 31 and is clamped in the cylinder sleeve 33; a plurality of loading waist-shaped holes 313 are provided on the end surface of the loading cylinder 31 away from the block 312; the loading distribution plate 32 is provided with loading high-pressure area waist-shaped holes 321 and loading low-pressure area waist-shaped holes 322 on both sides relative to the center thereof; there are two loading high-pressure area waist-shaped holes 321 and two loading low-pressure area waist-shaped holes 322 each and they are arranged radially symmetrically relative to the loading distribution plate 32; the loading distribution plate 32 is pressed tightly with the end of the loading cylinder 31 away from the block 312.

[0069] like Figure 9As shown in Figures 12 and 13 , four slots 331 are defined within the cylinder sleeve 33 , with each group of two slots 331 forming a group. Two latching blocks 312 are provided on the loading cylinder 31 , each of which engages with the two corresponding slots 331 in each group. By adjusting the engagement positions of the latching blocks 312 and the two groups of slots 331 , an odd or even number of loading waist-shaped holes 313 can be aligned with the loading high-pressure zone waist-shaped holes 321 , thereby varying the amount of high-pressure hydraulic oil filled in the plunger holes, thereby enabling different numbers of plunger shoe assemblies to operate.

[0070] In practice, for pumps with an odd number of plungers, the number of plunger shoe assemblies in the high-pressure zone also changes periodically during operation. For a pump with seven plungers, for example, the number of plungers switches between three and four. This device creates a variable flow distribution structure by snapping the cylinder sleeve into the loading cylinder at different locations, allowing for the selective setting of three or four plunger shoe loading.

[0071] The specific method for adjusting the number is as follows: During loading, the cylinder sleeve presses the loading cylinder body against the loading valve plate, and a retaining block is installed on the loading cylinder body and inserted into a slot in the cylinder sleeve. The loading valve plate is fastened to the support base with a pin, preventing it from rotating. The cylinder sleeve is also fastened to the cylinder barrel with bolts, also preventing it from rotating. At this point, the seven small waist-shaped holes on the loading cylinder body are uniquely positioned relative to the waist-shaped holes in the high and low pressure areas of the loading valve plate, thus determining the number of plunger shoes to be loaded.

[0072] If the number of loaded plunger shoes needs to be changed, the block on the loading cylinder needs to be pulled out from the slot on the loading sleeve, and then the loading cylinder needs to be rotated relative to the loading valve plate by an angle such as θ. Then the block on the loading cylinder needs to be re-inserted into a new set of slots on the cylinder sleeve, and finally the cylinder sleeve is tightened to complete the switching and adjustment of the number of plunger shoes. In particular, there are two sets of slots on the cylinder sleeve, such as Figure 10 As shown, the angle between the two sets of slots is also θ. The cylinder sleeve remains in a fixed position relative to the cylinder barrel; the cylinder sleeve cannot rotate. The positions of the two sets of slots correspond to the positions when three plunger shoes are loaded and four plunger shoes are loaded. This allows for variable flow distribution.

[0073] Example 2: The embodiment of the present invention discloses a method for testing the performance of a piston pump distribution pair under simulated deep-sea working conditions, and adopts a performance testing device for a piston pump distribution pair under simulated deep-sea working conditions in the above-mentioned technical scheme to perform a distribution plate performance test, and also includes a temperature control module 9. The temperature control module 9 is connected to the inner cavity of the loading cylinder 31 and the distribution plate 62 to be tested through pipelines to change the viscosity of the hydraulic oil through temperature.

[0074] like Figure 4As shown, the temperature control module 9 has two pipeline loops, corresponding to the loading cylinder 31 and the distribution plate to be tested 62 respectively; a first temperature and pressure sensor 91 and a second temperature and pressure sensor 92 are respectively provided on the two pipelines; an overflow valve 93 is also provided on the pipeline corresponding to the distribution plate to be tested 62; the two pipelines are respectively powered by a first constant pressure source 94 and a second constant pressure source 95; a first low-pressure feeder 96 and a second low-pressure feeder 97 are respectively provided on the pipelines corresponding to the low-pressure areas of the loading cylinder 31 and the distribution plate to be tested 62.

[0075] The circuit composition of the loading cylinder 31 is as follows: the high-pressure area is the first constant pressure source 94, the first temperature and pressure sensor 91, the cylinder loading hydraulic pipe joint 13 fixed at the loading high-pressure oil port 121 of the cartridge seat 12, the waist-shaped groove 125 in the high-pressure area of ​​the cartridge seat, the plunger hole 311, and the inner cavity of the loading cylinder 31; the low-pressure area is the first low-pressure feeder 96, the loading low-pressure oil port 122, the waist-shaped groove 126 in the low-pressure area of ​​the cartridge seat, and the inner cavity of the loading cylinder 31; the circuit composition of the distribution disk 62 to be tested is as follows: the high-pressure area is the second constant pressure source 95, the overflow valve 93, the second temperature and pressure sensor 92, the test high-pressure oil port 611, the support seat high-pressure waist-shaped groove 613, the high-pressure return oil port 612, the cylinder test hydraulic pipe joint 14, and the second constant pressure source 95; the low-pressure area is the second low-pressure feeder 97, the test low-pressure oil port 615, the support seat low-pressure waist-shaped groove 614, and the distribution disk 62 to be tested.

[0076] The loading cylinder 31 is fed with high-pressure hydraulic oil and drives the clamping force implementation part 4 to provide pressure to the simulation cylinder 34. The test high-pressure hydraulic oil is fed into the distribution plate 62 to simulate deep-sea working conditions. The transmission part 2 drives the simulation cylinder 34 to rotate. During the rotation of the simulation cylinder 34, a friction torque is generated on the distribution plate 62 to be tested, which can indirectly calculate the mechanical efficiency loss of the distribution plate 62 to be tested and the equivalent friction coefficient of mixed friction.

[0077] The viscosity of the test high-pressure hydraulic oil entering the test valve plate 62 is changed by the temperature control module 9 to simulate deep-sea working conditions.

[0078] High-pressure hydraulic oil is provided to the loading cylinder and the distribution disc to be tested respectively through the first constant pressure source and the second constant pressure source. The oil in the first low-pressure feeder and the second low-pressure feeder also passes through the temperature control module and enters the low-pressure area of ​​the distribution disc to be tested and the loading cylinder for lubrication.

[0079] By alternating the oil in the second constant pressure source, varying viscosities are fed to the valve plate under test to simulate varying sea depths. The alternating oil, at normal onshore temperature and pressure, has a viscosity equivalent to that at a given sea depth. The second constant pressure source varies the oil's viscosity based on the principle that low oil temperature results in high viscosity, simulating deep-sea conditions; heated oil becomes thinner and has low viscosity, simulating shallow-sea conditions. By controlling the temperature of the second constant pressure source and feeding varying viscosities to the support base, the performance of the valve plate under test can be tested under varying sea depth conditions.

[0080] When simulating the change in oil viscosity under variable sea depth conditions, the temperature of the oil supplied to the valve plate to be tested by the second constant pressure source is changed through the temperature control module, thereby changing the oil viscosity and equivalently simulating the change with sea depth.

[0081] The temperature control module, combined with the temperature and pressure sensors in the circuit, can precisely control the temperature of the oil in the pipeline during its passage. Each oil line is independently controlled without interfering with each other.

[0082] When conducting performance tests on the distribution pair of a plunger pump simulating deep-sea working conditions, the torque transmitted from the rotating simulated cylinder to the stationary distribution plate to be tested is measured to evaluate the change in mechanical efficiency loss of the distribution pair under variable sea depth conditions and the equivalent friction coefficient of the distribution pair can be calculated. By measuring the leakage oil from the distribution plate to be tested collected by the oil collecting ring, the change in volumetric efficiency loss of the distribution pair under variable sea depth conditions can be evaluated.

[0083] To further optimize this technical solution, small holes are provided in both the plunger and the slipper. This allows high-pressure oil in the plunger hole in the high-pressure area to enter the oil chamber at the bottom of the slipper, creating a hydrostatic support on the friction surface between the slipper and the oil separator. Similarly, oil in the plunger hole in the low-pressure area enters the friction surface between the slipper and the oil separator through the small holes to lubricate the friction surface, mimicking the actual operating conditions of the pump slipper pair. Therefore, while not affecting the flow distribution pair testing, this device also evaluates the friction and wear performance of the slipper pair, guiding the optimization of slipper materials and structures.

[0084] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on the differences from other embodiments. Reference can be made to the common and similar parts between the various embodiments. For the devices disclosed in the embodiments, since they correspond to the methods disclosed in the embodiments, the description is relatively simple, and the relevant parts can be referred to the method description.

[0085] The above description of the disclosed embodiments is intended to enable one skilled in the art to implement or use the present invention. Various modifications to these embodiments will be readily apparent to one skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention is not limited to the embodiments shown herein but is intended to conform to the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A device for testing the performance of a plunger pump distribution pair under simulated deep-sea working conditions, characterized in that: include: Fixed cylinder (1); A transmission part (2), the transmission part (2) being fixed to the first end of the fixed cylinder (1); A loading part (3), the loading part (3) comprising a loading cylinder (31) and a simulation cylinder (34) arranged at intervals, the loading cylinder (31) being coaxially fixed to the inner wall of the fixed cylinder (1); the output shaft of the transmission part (2) passing through the inner cavity of the loading cylinder (31) and being fixed to the simulation cylinder (34); A pressing force implementing portion (4), the pressing force implementing portion (4) being arranged between the loading cylinder (31) and the simulation cylinder (34); a hydraulic transmission portion of the loading cylinder (31) being transmission-connected to the pressing force implementing portion (4) to provide pressure to the simulation cylinder (34); A support reaction force implementation portion (6), the support reaction force implementation portion (6) comprising a support seat (61) and a distribution disc to be tested (62); the first end of the support seat (61) is located in the inner cavity of the second end of the fixed cylinder body (1); the distribution disc to be tested (62) is fixed to the first end face of the support seat (61); the end face of the simulation cylinder body (34) away from the end of the loading cylinder body (31) is rotatably abutted against the outer surface of the distribution disc to be tested (62); a test high-pressure oil port (611) and a test low-pressure oil port (615) communicating with the distribution disc to be tested (62) are provided on the support seat (61), and a high-pressure oil return port (612) is provided on the first end thereof; An oil separator (5), the oil separator (5) is provided between the simulation cylinder (34) and the pressing force implementation part (4) to prevent mutual leakage of hydraulic oil between the loading cylinder (31) and the distribution plate (62) to be tested; the oil separator (5) includes an oil separator ring (51) and an oil collecting ring (52); both sides of the oil separator ring (51) are provided with bell mouths; the inner walls of the oil separator ring (51) relative to the two bell mouths are respectively fixed to the outer wall of the simulation cylinder (34) and abut against the end of the pressing force implementation part (4) away from the loading cylinder (31); the outer wall of the oil collecting ring (52) abuts against the inner wall of the fixed cylinder (1) and covers the support seat (61) and the outer wall of the oil separator ring (51) corresponding to the simulation cylinder (34); the outer walls of the oil collecting ring (52) and the fixed cylinder (1) are provided with an oil collecting port connected to the inner cavity of the oil collecting ring (52); A torque measuring part (7) is fixed to the second end of the fixed cylinder (1) and is connected to the second end of the support seat (61) via a key to measure the torque of the valve plate (62) to be measured.

2. The device for testing the performance of a plunger pump distribution pair under simulated deep-sea working conditions according to claim 1, characterized in that: The fixed cylinder body (1) comprises a cylinder barrel (11) and a cylinder seat (12); the cylinder seat (12) is bolted to the first end of the cylinder barrel (11); a loading high-pressure oil port (121) and a loading low-pressure oil port (122) communicating with the inner cavity of the loading cylinder body (31) are provided on the cylinder seat (12); the transmission part (2) is fixed to one end of the cylinder seat (12) away from the cylinder barrel (11).

3. The device for testing the performance of a plunger pump distribution pair under simulated deep-sea working conditions according to claim 2, characterized in that: The reaction force implementing portion (6) further includes a bearing seat (63) and a support bearing (64); one end of the bearing seat (63) is bolted to the second end of the cylinder (11); the support bearing (64) is embedded in the bearing seat (63); the outer wall of the support seat (61) away from one end of the cylinder (11) is pressed into engagement with the inner ring of the support bearing (64) to support the support seat (61).

4. The device for testing the performance of a plunger pump distribution pair under simulated deep-sea working conditions according to claim 3 is characterized in that: The torque measuring part (7) comprises a mounting seat (72) and a torque sensor (71), wherein the mounting seat (72) is bolted to an end of the bearing seat (63) away from the cylinder (11), and the torque sensor (71) is fixed on the mounting seat (72); and an end of the support seat (61) away from the cylinder (11) is connected to the mounting seat (72) via a key.

5. The device for testing the performance of a plunger pump distribution pair under simulated deep-sea working conditions according to claim 1, characterized in that: The loading portion (3) further comprises a cylinder sleeve (33) and a loading distribution plate (32); the outer wall of the cylinder sleeve (33) abuts against the inner wall of the fixed cylinder (1); the inner wall of the cylinder sleeve (33) is provided with a plurality of slots (331); a clamping block (312) adapted to the slot (331) is fixed to one end of the loading cylinder (31) and is clamped in the cylinder sleeve (33); a plurality of loading waist-shaped holes (313) are provided on the end surface of the loading cylinder (31) away from the clamping block (312); a loading high-pressure zone waist-shaped hole (321) and a loading low-pressure zone waist-shaped hole (322) are provided on the loading distribution plate (32); the loading distribution plate (32) is tightly fitted with the end of the loading cylinder (31) away from the clamping block (312).

6. The device for testing the performance of a plunger pump distribution pair under simulated deep-sea working conditions according to claim 2, characterized in that: The transmission part (2) includes a motor (21), a deep groove ball bearing (24) and a transmission shaft (23); the motor (21) is fixed to one end of the cylinder seat (12) away from the cylinder (11); the outer ring of the deep groove ball bearing (24) is embedded in the inner wall of the cylinder seat (12); one end of the transmission shaft (23) is fastened to the output shaft of the motor (21) through a coupling (22), and the other end passes through the cylinder seat (12), the inner cavity of the loading cylinder (31) in sequence, and is connected to the simulation cylinder (34) through a key.

7. The device for testing the performance of a plunger pump distribution pair under simulated deep-sea working conditions according to claim 1, characterized in that: The clamping force implementing part (4) includes a plunger (41), a sliding shoe (42) and a spring (43); a plurality of plunger holes (311) are opened on the inner wall of the loading cylinder (31); one end of the plurality of plungers (41) is inserted into the plurality of plunger holes (311) in a one-to-one correspondence; one end of the sliding shoe (42) is clamped with the other end of the plunger (41), and the other end of the sliding shoe (42) is in contact with the side end face of the oil separator ring (51); the spring (43) is sleeved on the outer walls of the sliding shoe (42) and the plunger (41), and its two ends are in contact with the opposite side walls of the oil separator ring (51) and the loading cylinder (31).

8. A method for testing the performance of a plunger pump flow distribution pair under simulated deep-sea working conditions, characterized in that: The performance test of the flow distribution pair of a plunger pump is carried out according to the device for testing the performance of the flow distribution pair of a plunger pump under simulated deep-sea working conditions according to any one of claims 1 to 7. It also includes a temperature control module (9), which is connected to the inner cavity of the loading cylinder (31) and the distribution plate (62) to be tested through pipelines to change the viscosity of the hydraulic oil according to the temperature; The loading cylinder (31) is fed with high-pressure hydraulic oil and drives the pressing force implementing part (4) to provide pressure to the simulation cylinder (34), and the distribution plate (62) to be tested is fed with test high-pressure hydraulic oil to simulate deep-sea working conditions; the transmission part (2) drives the simulation cylinder (34) to rotate, and the simulation cylinder (34) generates friction torque on the distribution plate (62) to be tested during the rotation process, and the mechanical efficiency loss of the distribution plate (62) to be tested and the equivalent friction coefficient of mixed friction are calculated; The viscosity of the test high-pressure hydraulic oil entering the test distribution plate (62) is changed by the temperature control module (9) to simulate deep-sea working conditions.

Images