A hypochlorite toothpaste

Abstract

The application relates to a hypoid tooth gas-liquid loading displacement pump and a pressure regulating and speed regulating system, which comprises a driving part, a driving part connected with a speed reducing part, first and second fixed boxes fixed on the two sides of the shell of the speed reducing part, a screw nut connected with the speed reducing part, a screw connected with the screw nut, one end of the screw extending into a first cylinder fixed in the first fixed box, the other end of the screw extending into a second cylinder fixed in the second fixed box, a boss arranged on the part of the screw nut located in the first fixed box, a thrust part arranged between the boss and the wall of the first fixed box, an anti-rotation pin fixed on the part of the screw located in the second cylinder, the anti-rotation pin being inserted into an anti-rotation groove arranged on the wall of the second cylinder, and the first cylinder being provided with an inlet and an outlet. The displacement pump has high axial force resistance, long service life and can realize large-flow and rapid loading working conditions.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of constant speed and constant pressure pump, in particular to a hypoid gear gas-liquid loading displacement pump and a pressure regulating and speed regulating system. BACKGROUND

[0002] The statements herein merely provide background information related to the present application and do not necessarily constitute the prior art.

[0003] As a kind of high-pressure plunger pump, constant speed and constant pressure pump is widely used in metering, oil development and chemical industry fields, mainly used for high-pressure fluid displacement, metering control, which can be used with laboratory instruments or devices that can simulate different conditions of formation pressure, such as fluid-structure interaction model test, fracturing and displacement test, gas-liquid injection simulation, etc., and its performance index is crucial to the research results.

[0004] At present, many constant speed and constant pressure pump devices have been developed by predecessors, and the research status is as follows:

[0005] The Chinese patent with application number 201520246488.6 discloses a transmission device of constant speed and constant pressure metering pump, which adopts worm gear transmission, the worm shaft is movably connected with the worm fixed plate, there are problems such as small worm lead, large axial force, easy damage of worm, etc., and the friction resistance between worm gear and worm during transmission is relatively large compared with other transmission modes, the transmission efficiency is low, and the liquid supply speed is slow.

[0006] The Chinese patent with application number 201920653585.5 discloses a displacement pump with constant speed and constant pressure function, which works with harmonic gear reducer and servo motor, improving the motion stability of displacement pump, but the harmonic gear reducer is not resistant to impact, and this displacement pump cannot effectively solve the impact effect of axial force on harmonic gear reducer, and it is difficult to stably pump high-precision and high-pressure fluid and gas.

[0007] Through comprehensive analysis of the above constant speed and constant pressure pump devices, the following deficiencies exist:

[0008] 1. The existing constant speed and constant pressure pump cannot avoid the impact damage of axial force on the transmission mechanism, and when pumping high-pressure fluid, the overall device often has problems such as poor pressure stability, large precision deviation, etc., and the mechanical components of the equipment are easily damaged and failed after long-term use.

[0009] 2. The existing constant speed and constant pressure pump adopts worm gear transmission, which is limited by the small worm lead, and the gas-liquid loading rate of the device is low, which is difficult to meet the large flow and rapid loading working condition. SUMMARY

[0010] The hypoid tooth gas-liquid loading displacement pump can bear the axial force impact with high capacity, is not easy to be damaged during use, has long service life, and can meet the large-flow and rapid loading working condition.

[0011] To achieve the above object, the present application adopts the following technical scheme

[0012] In the first aspect, the embodiment of the present application provides a hypoid tooth gas-liquid loading displacement pump, which comprises a driving part, the driving part is connected with a speed reduction part, the speed reduction part is fixed with a first fixed box and a second fixed box on two sides of a shell of the speed reduction part, the speed reduction part is connected with a screw nut, the screw nut is connected with a lead screw, one end of the lead screw is inserted into a first cylinder fixed in the first fixed box, the other end of the lead screw is inserted into a second cylinder fixed in the second fixed box, a boss is arranged on the part of the screw nut located in the first fixed box, a thrust part is arranged between the boss and the wall of the first fixed box, an anti-rotation pin is fixed on the part of the lead screw located in the second cylinder, the anti-rotation pin is inserted into an anti-rotation groove arranged on the wall of the second cylinder, and the first cylinder is provided with an inlet and an outlet.

[0013] Optionally, a rotating flange is arranged in the second fixed box, a rotating output part of the speed reduction part is fixed with the rotating flange, and the rotating flange is fixed with the part of the screw nut located in the second fixed box.

[0014] Further, the speed reduction part adopts a hypoid gear reducer.

[0015] In the second aspect, the embodiment of the present application provides a hypoid tooth gas-liquid loading displacement pump, which comprises a driving part, the driving part is connected with a speed reduction part, one side of a shell of the speed reduction part is fixed with a first fixed box, the speed reduction part is connected with a screw nut, the screw nut is connected with a lead screw, one end of the lead screw is inserted into a first cylinder fixed in the first fixed box, a boss is arranged on the part of the screw nut located in the first fixed box, a thrust part is arranged between the boss and the wall of the first fixed box, an anti-rotation pin is fixed on the part of the lead screw located in the first cylinder, the anti-rotation pin is inserted into an anti-rotation groove arranged on the wall of the first cylinder, and the first cylinder is provided with an inlet and an outlet.

[0016] Optionally, the speed reduction part is connected with a hypoid tooth rotating table, and the hypoid tooth rotating table is connected with the screw nut.

[0017] Optionally, the thrust part adopts a thrust bearing, the boss is provided with the thrust bearing on both sides, the inner ring of the thrust bearing on one side is fixed with one side end face of the boss, the outer ring is fixed with the inner side face of the wall of the first fixed box close to the speed reduction part, the inner ring of the thrust bearing on the other side is fixed with the other side end face of the boss, and the outer ring is fixed with the inner side face of the wall of the first fixed box away from the speed reduction part.

[0018] Optionally, the end of the lead screw extending into the first cylinder is movably connected with a clamping groove member, a sealing member is arranged between the clamping groove member and the inner cylinder surface of the first cylinder, and the clamping groove member and the inner cylinder surface of the first cylinder are sealingly and slidably connected through the sealing member.

[0019] Further, the sealing member comprises a first sealing rubber ring and a second sealing rubber ring sleeved on the outer periphery of the clamping groove member, a copper sleeve is arranged between the first sealing rubber ring and the second sealing rubber ring, one side of the second sealing rubber ring is the copper sleeve, and the other side is provided with an oil seal sleeved on the outer periphery of the clamping groove member.

[0020] Optionally, the end of the lead screw extending into the first cylinder is provided with a plug, and the clamping groove member is provided with a plug groove matched with the plug, the size of the plug groove is greater than the size of the plug, and the plug is inserted into the plug groove to movably connect the lead screw with the clamping groove member.

[0021] Optionally, the end of the anti-rotation pin is provided with a guide sliding block embedded in the anti-rotation groove.

[0022] Further, the length of the anti-rotation groove is greater than the maximum stroke distance of the lead screw.

[0023] In a second aspect, an embodiment of the present application provides a pressure and speed regulating system, comprising two sea-tooth gas-liquid loading displacement pumps according to the first aspect, wherein the inlet and outlet of one sea-tooth gas-liquid loading displacement pump are connected with a first electromagnetic pneumatic valve through a first pipeline, the inlet and outlet of the other sea-tooth gas-liquid loading displacement pump are connected with a second electromagnetic pneumatic valve through a second pipeline, and the driving components of the sea-tooth gas-liquid loading displacement pumps, the first electromagnetic pneumatic valve and the second electromagnetic pneumatic valve are connected with a control system.

[0024] Optionally, the first pipeline and the second pipeline are both provided with a pressure detection element, and the two sea-tooth gas-liquid loading displacement pumps are both provided with a displacement detection element for detecting the displacement of the lead screw, and the pressure detection element and the displacement detection element are both connected with the control system.

[0025] The beneficial effects of the present application are as follows:

[0026] 1. The sea-tooth gas-liquid loading displacement pump of the present application, the lead screw nut is provided with a boss, and a thrust piece is arranged between the boss and the wall of the first fixed box, so that the axial force generated during work is jointly borne by the lead screw nut, the thrust piece, the first fixed box and the housing of the speed reduction component, the internal transmission parts of the speed reduction component can be better protected from damage, and the stability of the displacement pump in pumping fluid is ensured.

[0027] 2. The hypoid tooth gas-liquid loading displacement pump of the present application adopts a hypoid gear reducer or a hypoid gear rotary table as a speed reduction component, has higher transmission efficiency and greater axial bearing capacity than a worm gear transmission, is not prone to damage, adopts a hypoid gear reducer in combination with a lead screw nut and a lead screw top pressure loading technology, can realize large flow rate rapid loading, improves loading efficiency, meets the requirements of large flow rate high pressure water and high gas pressure quantitative application in large scale fluid-structure coupling model tests, and has the advantages of high pressure and high precision, large flow rate adjustment range, compact structure and the like.

[0028] 3. The hypoid tooth gas-liquid loading displacement pump of the present application avoids the occurrence of jamming of a lead screw during movement of the lead screw by arranging a clamping groove component in movable connection with the lead screw.

[0029] 4. The hypoid tooth gas-liquid loading displacement pump of the present application can form multiple seals, maximally reduces the possibility of fluid leakage, and reduces situations such as leakage and slow leakage by arranging a sealing assembly composed of a first sealing ring, a copper sleeve, a second sealing ring and an oil seal. BRIEF DESCRIPTION OF DRAWINGS

[0030] The drawings accompanying the specification of the present application form a part thereof, serve to further provide a further understanding of the present application, and together with the specification explain the present application, but do not limit the present application.

[0031] Figure 1 is a schematic view of the overall structure of embodiment 1 of the present application;

[0032] Figure 2 is a schematic view of the overall structure of embodiment 1 of the present application; Figure 1

[0033] Figure 3 is a schematic view of the overall structure of embodiment 1 of the present application; Figure 2

[0034] Figure 4 is a schematic view of the overall structure of embodiment 1 of the present application; Figure 2

[0035] Figure 5 is a schematic view of the overall structure of embodiment 1 of the present application; Figure 2

[0036] Figure 6 is a schematic view of the overall structure of embodiment 2 of the present application;

[0037] Figure 7 is a schematic view of the overall structure of embodiment 2 of the present application; Figure 6

[0038] Figure 8 is a schematic view of the overall structure of embodiment 2 of the present application; Figure 6 ​​​​​​

[0039] Figure 9 For the application Figure 6 The local enlarged view of F in the application is shown in the figure.

[0040] Figure 10 The overall structure of the embodiment 3 of the application is shown in the figure.

[0041] Figure 11 The overall structure of the embodiment 4 of the application is shown in the figure. Figure 1 ;

[0042] Figure 12 The overall structure of the embodiment 4 of the application is shown in the figure. Figure 2 ;

[0043] In the figure, 1. servo motor, 2. hypoid gear reducer, 3. first fixed box, 4. first cylinder, 5. cylinder cover, 6. second fixed box, 7. second cylinder, 8. rotating flange, 9. screw nut, 10. lead screw, 11. thrust bearing, 12. anti-rotation pin, 13. anti-rotation groove, 14. deep groove ball bearing, 15. shaft end retainer, 16. positioning pin, 17. clamping groove part, 18. first sealing rubber ring, 19. second sealing rubber ring, 20. copper sleeve, 21. oil seal, 22. pressure head, 23. transparent cover plate, 24. PLC controller, 25. first electromagnetic pneumatic valve, 26. second electromagnetic pneumatic valve, 27. output interface, 28. input interface, 29. displacement detection element, 30. touch display screen, 31. pressure sensor, 32. frame box, 33. hypoid gear rotary table, 34. reducer. DETAILED DESCRIPTION

[0044] Embodiment 1

[0045] The embodiment provides a hypoid gear gas-liquid loading displacement pump, as shown in the figure, which comprises a driving part, the driving part is connected with a speed reduction part, and the speed reduction part is used for reducing the rotating speed output by the driving part. Figures 1-5

[0046] In the embodiment, the driving part adopts a servo motor 1, the speed reduction part adopts a hypoid gear reducer 2, the shell of the servo motor 1 is fixed with the shell of the hypoid gear reducer 2, the output shaft of the servo motor 1 is connected with the input shaft of the hypoid gear reducer 2, and the hypoid gear reducer 2 can be powered.

[0047] The outer shell of the hypoid gear reducer 2 is fixed with a first fixed box 3 on one side, the first fixed box 3 adopts a cubic structure, the fixed box wall of the first fixed box 3 has an opening, and the other side box wall is fixed with a first cylinder 4.

[0048] ​The first cylinder 4 includes a frustum section and a straight cylinder section, wherein the end face with smaller area of the frustum section is fixed with the straight cylinder section, the end face with larger area is connected with an embedded cover plate, the embedded cover plate is embedded in the groove of the box wall of the first fixed box, and is fixed with the box wall of the first fixed box through a plurality of bolts, so as to realize the fixation of the first cylinder and the first fixed box.

[0049] One end of the first cylinder 4 is fixed with the first fixed box 3, and the other end is provided with a cylinder cover 5, and the cylinder cover 5 is provided with an inlet and an outlet for liquid or gas to enter or flow out of the first cylinder.

[0050] The other side of the housing of the hypoid gear reducer 2 is fixed with a second fixed box 6, the box wall of the second fixed box 6 fixed with the housing of the hypoid gear reducer 2 has an opening, and the box wall of the opposite side is fixed with a second cylinder 7, the structure of the second cylinder 7 is similar to that of the first cylinder 4, the end of the second cylinder 7 with larger area of the frustum section is fixed with an embedded cover plate, the embedded cover plate is embedded in the groove of the box wall of the second fixed box 6, and is fixed with the box wall of the second fixed box 6 through a plurality of bolts, so as to realize the fixation of the second cylinder 7 and the second fixed box 6.

[0051] A rotating flange 8 is arranged in the second fixed box 6, the rotating flange 8 is connected with the output shaft of the hypoid gear reducer 2, and the hypoid gear reducer 2 can drive the rotating flange 8 to rotate around the axis thereof.

[0052] A fixed hole is arranged at the central part of the rotating flange 8, and the end of the screw nut 9 extending into the second fixed box 6 is fixed through the fixed hole, in the embodiment, the opening on the box wall of the second fixed box 6 enables the end of the screw nut 9 to extend into the second fixed box 6.

[0053] After the screw nut 9 passes through the hypoid gear reducer 2, the other end extends into the first fixed box 3, and correspondingly, the opening on the box wall of the first fixed box 3 enables the screw nut 9 to extend into the first fixed box 3.

[0054] The screw nut 9 is threadedly connected with a lead screw 10, the lead screw 10 is a ball screw, one end of the lead screw 10 is located in the first cylinder 4, and the other end is located in the second cylinder 7.

[0055] The end of the screw nut 9 extending into the first fixed box 3 is fixed with an annular boss, and a thrust piece is arranged between the boss and the two box walls of the first fixed box 3 perpendicular to the axis of the screw nut.

[0056] The thrust piece is a thrust bearing 11, the inner ring of the thrust bearing 11 on one side of the boss is fixed with the end face on one side of the boss, and the outer ring is fixed with the box wall of the first fixed box 3 close to the hypoid gear reducer 2. The inner ring of the thrust bearing 11 on the other side of the boss is fixed with the end face on the other side of the boss, and the outer ring is fixed with the box wall of the first fixed box 3 away from the hypoid gear reducer 2.

[0057] Through the thrust bearing 11, the screw nut 9 and the housing of the hypoid gear reducer 2 can jointly bear the axial load of the liquid or gas on the screw, the axial bearing capacity is larger, the internal transmission parts of the reduction part can be better protected from damage, and the stable pumping of the displacement pump is ensured.

[0058] The part of the screw 10 located in the second cylinder 7 is fixed with a rotation prevention pin 12, both ends of the rotation prevention pin 12 are inserted into the rotation prevention groove 13 formed on the wall of the second cylinder 7, the rotation prevention groove 13 is arranged along the axial direction of the second cylinder 7, and the length of the rotation prevention groove 13 is greater than the maximum stroke distance of the screw.

[0059] Through the rotation prevention pin 13, the screw 10 can be prevented from rotating around its own axis under the driving of the screw nut 9, so that the screw 10 can move linearly along its own axial direction under the action of the screw nut 9.

[0060] In order to reduce the friction between the rotation prevention pin 12 and the groove surface of the rotation prevention groove 13, the outer periphery of the end of the rotation prevention pin 12 extending into the rotation prevention groove 13 is sleeved with a guide sliding block, in the embodiment, the rotation prevention pin 12 includes three parts, the diameters of the two end parts are smaller than the diameter of the middle part, the outer periphery of the end part is sleeved with the guide sliding block, the guide sliding block adopts two deep groove ball bearings 14, the rotation prevention pin 12 contacts the groove surface of the rotation prevention groove 13 through the deep groove ball bearings 14, the friction between the rotation prevention pin 12 and the groove surface of the rotation prevention groove 13 is reduced when the rotation prevention pin 12 moves linearly, so that the screw 10 can move stably, and the stability of operation is improved.

[0061] The guide sliding block is pressed against the stepped surface formed by the smaller diameter part and the larger diameter part of the rotation prevention pin 12 by the shaft end stop washer 15.

[0062] The rotation prevention pin 12 is fixed with the screw 10 through the positioning pin 16, specifically, a channel for the rotation prevention pin 12 to pass through is formed on the screw 10, and the channel is perpendicular to the axis of the screw 10, the rotation prevention pin 16 is inserted into the channel, and a threaded hole communicating with the channel is further arranged on the screw 10, the positioning pin 16 is threadedly connected in the threaded hole, a T-shaped groove is arranged at the end of the positioning pin 16, the positioning pin can be driven to rotate by using the T-shaped groove through a tool, until the rotation prevention pin 16 is rotated to press the rotation prevention pin 12 tightly in the channel, and the fixation of the rotation prevention pin 12 and the screw 10 is realized.

[0063] The end of the screw 10 extending into the first cylinder 4 is movably connected with a clamping groove piece 17, and the clamping groove piece 17 and the cylinder cover 5 of the first cylinder 4 form a pump cavity. The clamping groove piece 17 is sealingly and slidably connected with the inner cylinder surface of the first cylinder.

[0064] In the embodiment, the first cylinder 4 and the second cylinder 7 are arranged, and the stroke of the ball screw is increased by adopting the symmetrical double-cylinder structure, the volume of the pump cavity is fully utilized, and the flow regulation range is increased.

[0065] Specifically, the end of the screw rod 10 is provided with a plug, the clamping groove member 17 is provided with a slot, the shape of the slot matches the plug, but the size is larger than the plug, the plug is inserted into the slot, and the movable connection of the screw rod 10 and the clamping groove member 17 is realized.

[0066] In the embodiment, the clamping groove member 17 is arranged to support the end of the screw rod, prevent the screw rod from being deformed too much, and ensure that the screw rod does not change in the axial direction.

[0067] The clamping groove member 17 comprises a first part, a second part and a third part arranged in sequence, the first part is provided with a slot, the diameter of the second part is larger than that of the first part and the third part, the end of the second part close to the first part is provided with an annular protrusion, and the annular protrusion is attached to the inner cylinder surface of the first cylinder 4.

[0068] The outer periphery surface of the second part and the third part is provided with a sealing assembly between the inner cylinder surface of the first cylinder.

[0069] The sealing assembly comprises a first sealing rubber ring 18, a second sealing rubber ring 19, a copper sleeve 20 and an oil seal 21 sleeved on the outer periphery of the clamping groove member. The inner annular surface of the first sealing rubber ring 18, the second sealing rubber ring 19, the copper sleeve 20 and the oil seal 21 is attached to the clamping groove member 17, and the outer annular surface is attached to the inner cylinder surface of the first cylinder 4, which is used for sealing.

[0070] In the embodiment, the first sealing rubber ring 18, the second sealing rubber ring 19 and the copper sleeve 20 are sleeved on the outer periphery of the second part of the clamping groove member 17, the first sealing rubber ring 18 is attached to the annular protrusion of the second part, and the copper sleeve 20 is arranged between the first sealing rubber ring 18 and the second sealing rubber ring 19.

[0071] The oil seal 21 is sleeved on the outer periphery of the third part and is attached to the second sealing rubber ring 19, the end of the clamping groove member 17 is fixed with a pressure head 22, and the pressure head 22 presses the oil seal 21 tightly on the stepped surface formed by the third part and the second part.

[0072] In the embodiment, the copper sleeve is arranged between the two sealing rubber rings to fix the position of the sealing rubber ring, and the copper sleeve has good wear resistance and corrosion resistance.

[0073] By arranging two sealing rubber rings, a copper sleeve 20 and an oil seal 21, the sealing performance is greatly improved, and the occurrence of liquid leakage and slow liquid leakage is reduced.

[0074] In this embodiment, both the top walls of the first fixed box 3 and the second fixed box 6 are provided with observation windows, and transparent covers 23 are provided at the observation windows. By providing transparent covers 23, the situation inside the first fixed box 3 and the second fixed box 6 can be seen, and the damage to the thrust bearing 11 or the deformation of the lead screw nut 9 can be detected in time, which is convenient for maintenance.

[0075] The working method of the displacement pump in this embodiment is as follows:

[0076] When the servo motor 1 is started, the power is transmitted to the lead screw nut 9 through the Hybo gear reducer 2 and the rotating flange 8. The lead screw nut 9 rotates with the rotating flange 8, and the anti-rotation pin 12 prevents the lead screw 10 from rotating coaxially with the lead screw nut 9, thereby converting the rotational motion of the lead screw nut 9 into the linear motion of the lead screw 10 along its own axis. The deep groove ball bearing 14 at the end of the anti-rotation pin 12 slides along the anti-rotation groove 13 to ensure that the linear motion of the lead screw 10 is smooth and the direction remains unchanged. When the lead screw 10 extends into the end of the first cylinder 4 and moves away from the cylinder head 5, the fluid enters the pump chamber from the inlet and outlet in the middle of the cylinder head 5. When the lead screw 10 moves in the opposite direction, the fluid is discharged from the pump chamber from the inlet and outlet.

[0077] In this embodiment, the constant speed and pressure of the output fluid is achieved by changing the rotational speed of the servo motor. When the pressure is too high, the servo motor 1 rotates counterclockwise, and the lead screw 10 moves away from the cylinder head 5, increasing the pump chamber volume and reducing the pressure. When the pressure is too low, the servo motor 1 rotates clockwise, and the lead screw 10 moves towards the cylinder head 5, decreasing the pump chamber volume and increasing the pressure. In constant flow mode, the servo motor 1 operates at the set rotational speed, thus ensuring a stable flow rate.

[0078] Example 2

[0079] This embodiment provides a Hypoglu gas-liquid loading displacement pump, such as... Figures 6-9 As shown, no second fixed box or second cylinder is provided. The anti-rotation pin is vertically connected to the lead screw and located inside the first cylinder. It is slidably connected to the anti-rotation groove opened in the wall of the first cylinder. The deceleration component is a reducer 34. The reducer 34 is connected to the lead screw nut through the Hypo gear rotary table 33. Other structures and working methods are the same as in Embodiment 1, and will not be described in detail here.

[0080] Example 3

[0081] This embodiment provides a voltage regulation and speed regulation system, such as Figure 10As shown, two hypochlorite tooth gas-liquid loading displacement pumps described in Embodiment 1 are included, and the two hypochlorite tooth gas-liquid loading displacement pumps described in Embodiment 1 are defined as A pump and B pump respectively, the A pump and the B pump are fixed side by side on the front side platform of the frame box 32, the servo motors of the A pump and the B pump are connected with the control system installed on the frame box, and the working of the A pump and the B pump is controlled by the control system, in this embodiment, the control system adopts a PLC controller 24.

[0082] The inlet and outlet of the A pump are connected with the first electromagnetic pneumatic valve 25 through a first pipeline, and the inlet and outlet of the B pump are connected with the second electromagnetic pneumatic valve 26 through a second pipeline, and the first electromagnetic pneumatic valve 25 and the second electromagnetic pneumatic valve 26 are installed on the frame box.

[0083] In this embodiment, the first electromagnetic pneumatic valve 25 and the second electromagnetic pneumatic valve 26 are both existing devices, having one normally open port and two other ports, the normally open port of the first electromagnetic pneumatic valve is connected with the first pipeline, and the normally open port of the second electromagnetic pneumatic valve is connected with the second pipeline.

[0084] The first pipeline and the second pipeline are both provided with a pressure detection element for detecting the pressure of the output liquid or gas, in this embodiment, the pressure detection element adopts a pressure sensor 31, the pressure sensor 31 is connected with the PLC controller 24, and the pressure information detected by the pressure sensor 31 can be transmitted to the PLC controller 24.

[0085] The first electromagnetic pneumatic valve 25 and the second electromagnetic pneumatic valve 26 are both connected with the PLC controller 24, the PLC controller 24 can control the switching of the opening and closing state of the other two ports of the electromagnetic pneumatic valve, one of the other two ports of the first electromagnetic pneumatic valve 25 and the second electromagnetic pneumatic valve 26 is used as an output port 27, and the other port is used as an input port 28 of the oil source or the gas source.

[0086] The two hypochlorite tooth gas-liquid loading displacement pumps are provided with a laser range finder on the two end side groove surfaces of the anti-rotation slot, the laser range finder is used as a displacement detection element 29 for detecting the displacement of the lead screw, and the laser range finder can detect the movement distance of the anti-rotation pin, and then obtain the displacement of the lead screw.

[0087] The frame box is also provided with a touch display screen 30, the touch display screen 30 is connected with the PLC controller, the information detected by the displacement detection element and the pressure detection element can be displayed on the display screen, and the staff can send instructions to the PLC controller through the display screen to control the working of the related equipment.

[0088] The working method of the constant speed mode of the pressure regulating and speed regulating system of this embodiment is as follows:

[0089] The constant speed working mode is set on the PLC controller, the servo motor 5 drives two hydraulic loading displacement pumps to retreat, the first electromagnetic pneumatic valve 25 and the second electromagnetic pneumatic valve 26 open two input interfaces 28 and close two output interfaces 27; after sufficient liquid absorption, the A pump starts to pump at the set speed, and the pressure sensor 31 on the first pipeline starts to monitor the A pump 9 output pressure; when the A pump stroke reaches 80% position, the laser range finder feeds back a signal to the PLC controller 24; the PLC controller 24 transmits the signal to the servo motor 1 of the A pump, the servo motor 1 drives the A pump 9 to decelerate, and the B pump servo motor 1 accelerates; the A pump servo motor 1 starts to uniformly decelerate, and the B pump servo motor 1 starts to uniformly accelerate from the static state, and the output rotation speeds of the two pump servo motors are set values. When the A pump screw rod stroke reaches 100%, the laser range finder feeds back a signal to the PLC controller 24 again, the servo motor 1 of the A pump stops moving, the B pump servo motor 1 continues to pump at the set flow rate, and when the A pump output pressure is zero, the pressure sensor 31 feeds back a signal to the PLC controller 24, and under the control of the PLC controller 24, the servo motor of the A pump drives the A pump to move, the A pump starts to absorb liquid and retreats at high speed, at this time, the output interface 27 of the first electromagnetic pneumatic valve 25 is closed, the input interface 28 is opened, the A pump retreats at a speed greater than the B pump, and after sufficient retreat, liquid is absorbed and the output pressure of the B pump is tracked, and this process is completed when the B pump reaches 80% position. When the B pump reaches 80% position, the laser range finder feeds back a signal, the B pump servo motor 1 starts to decelerate, and the A pump servo motor 1 starts to uniformly accelerate from the static state, and the output rotation speeds of the two pump servo motors 1 are set values, and when the B pump screw rod stroke reaches 100%, a signal is fed back again, the B pump servo motor 1 stops moving, the A pump pumps at the set speed, and when the B pump output pressure is zero, the pressure sensor 31 of the second pipeline feeds back the PLC controller 24, and under the control of the PLC controller 24, the servo motor of the B pump drives the B pump 10 to move, the B pump 10 starts to absorb liquid and retreats at high speed, at this time, the output interface 27 of the second electromagnetic pneumatic valve 26 is closed, the input interface 26 is opened, the B pump retreats at a speed greater than the A pump, and after sufficient retreat, liquid is absorbed and the output pressure of the A pump is tracked, and this process is completed when the A pump reaches 80% position. The constant speed continuous liquid output purpose can be achieved by entering the circulating pump state in this way.

[0090] The working method of the constant pressure mode of the pressure regulating and speed regulating system of the embodiment is as follows:

[0091] The constant pressure mode is set on the PLC controller 24, the servo motor 1 drives the double pump body to retreat to the starting position, at this time the pressure in the pump is 0, and the two electromagnetic pneumatic valves open the input interface 28 and close the output interface 27, after fully absorbing liquid, the input interface 28 is closed. The A pump is started first, the output interface 27 of the first electromagnetic pneumatic valve 25 is opened and the pump is pumped, and the pressure sensor 31 monitors the A pump output pressure in real time. When the A pump reaches 80% of the stroke position, the laser range finder feeds back the signal to the PLC controller 24, and the PLC controller 24 transmits the signal to the servo motor 1, and the servo motor 1 drives the A pump to slow down and start the pump switching work. The output interface 27 of the second electromagnetic pneumatic valve 26 is opened, and the output interface 27 of the first electromagnetic pneumatic valve 25 is closed, and the B pump provides a constant pressure power source. At this time, the A pump retreats, and when the A pump pressure is 0, the input interface 28 of the first electromagnetic pneumatic valve 25 is opened to absorb liquid (the A pump retreats faster than the B pump). When the B pump runs to 80% of the stroke position, the pump switching starts, and the process is consistent with the A pump switching to the B pump. The above process is repeated to enter the circulating pump switching state, so as to achieve the purpose of constant pressure continuous liquid output.

[0092] The system of the embodiment can also perform pulse and vibration loading, specifically:

[0093] The system can face user automatic operation, and the PLC controller 24 provides specific services, and the core service is the automatic program-controlled guide curve loading function. The user obtains information and interacts through the touch display screen. The PLC controller 24 controls the servo motor 1 to work based on the PID loading adjustment function, the power is transmitted through the speed reducer and the hypoid gear rotary table to drive the rotating disc to rotate, and then the rotating disc drives the nut to rotate synchronously. The rotation of the nut drives the screw rod to move reciprocally. The running speed of the screw rod is controlled by continuously modifying the pressure target value and the loading rate, so as to complete the program-controlled loading function. The program-controlled loading function is started after the user enters the program-controlled setting interface to edit the loading curve and confirms execution. According to the user-designed loading curve, the working pressure and the loading rate are automatically adjusted to follow the target curve designed by the user. The program-controlled curve is designed to have a periodic sine wave, a triangular wave and a square wave, a horizontal line in the constant pressure process, and a slope line with a certain slope, so as to realize pulse and vibration form loading.

[0094] Embodiment 4:

[0095] The embodiment provides a pressure and speed regulating system, as shown in Figures 11-12 The embodiment provides a pressure and speed regulating system, as shown in

[0096] The above describes the specific embodiments of the present application in combination with the drawings, but is not a limitation on the protection scope of the present application. Those skilled in the art should understand that various modifications or variations made by those skilled in the art on the basis of the technical solutions of the present application without creative labor are still within the protection scope of the present application.

Claims

1. A hypotrochoidal tooth gas-liquid loading displacement pump, characterized in that, The drive component is connected with a reduction component, the two sides of the reduction component shell are respectively fixed with a first fixed box and a second fixed box, the reduction component is connected with a screw nut, the screw nut is connected with a screw, one end of the screw extends into a first cylinder fixed in the first fixed box, the other end of the screw extends into a second cylinder fixed in the second fixed box, the part of the screw nut located in the first fixed box is provided with a boss, a thrust piece is arranged between the boss and the box wall of the first fixed box, the screw part located in the second cylinder is fixed with an anti-rotation pin, the anti-rotation pin is inserted into an anti-rotation groove arranged on the cylinder wall of the second cylinder, and the first cylinder is provided with an inlet and an outlet; The thrust piece is a thrust bearing, both sides of the boss are provided with the thrust bearing, the inner ring of the thrust bearing on one side is fixed with the side end face of the boss, the outer ring is fixed with the inner side face of the box wall of the first fixed box close to the reduction component, the inner ring of the thrust bearing on the other side is fixed with the other side end face of the boss, and the outer ring is fixed with the inner side face of the box wall of the first fixed box away from the reduction component; The end of the screw extending into the first cylinder is movably connected with a clamping groove piece, a sealing piece is arranged between the clamping groove piece and the inner cylinder surface of the first cylinder, and the sealing piece is in sealed sliding connection with the inner cylinder surface of the first cylinder, the sealing piece comprises a first sealing rubber ring and a second sealing rubber ring sleeved on the outer periphery of the clamping groove piece, a copper sleeve is arranged between the first sealing rubber ring and the second sealing rubber ring, one side of the second sealing rubber ring is provided with the copper sleeve, and the other side is provided with an oil seal sleeved on the outer periphery of the clamping groove piece; The end of the anti-rotation pin is provided with a guide sliding block, the guide sliding block is embedded in the anti-rotation groove, and the length of the anti-rotation groove is greater than the maximum stroke distance of the screw.

2. A hypercusp gas-liquid loading displacement pump as claimed in claim 1, wherein, The second fixed box is provided with a rotating flange, the rotating output component of the reduction component is fixed with the rotating flange, and the rotating flange is fixed with the part of the screw nut located in the second fixed box. Further, the reduction component adopts a hypoid gear reducer.

3. A hypotrochoidal tooth gas-liquid loading displacement pump, characterized in that, The drive component is connected with a reduction component, one side of the reduction component shell is respectively fixed with a first fixed box, the reduction component is connected with a screw nut, the screw nut is connected with a screw, one end of the screw extends into a first cylinder fixed in the first fixed box, the part of the screw nut located in the first fixed box is provided with a boss, a thrust piece is arranged between the boss and the box wall of the first fixed box, the screw part located in the first cylinder is fixed with an anti-rotation pin, the anti-rotation pin is inserted into an anti-rotation groove arranged on the cylinder wall of the first cylinder, and the first cylinder is provided with an inlet and an outlet; The thrust piece is a thrust bearing, both sides of the boss are provided with the thrust bearing, the inner ring of the thrust bearing on one side is fixed with the side end face of the boss, the outer ring is fixed with the inner side face of the box wall of the first fixed box close to the reduction component, the inner ring of the thrust bearing on the other side is fixed with the other side end face of the boss, and the outer ring is fixed with the inner side face of the box wall of the first fixed box away from the reduction component; The end of the lead screw extending into the first cylinder is movably connected with a clamping groove piece, a sealing piece is arranged between the clamping groove piece and the inner cylinder surface of the first cylinder, and the sealing piece is in sealing sliding connection with the inner cylinder surface of the first cylinder through the sealing piece, the sealing piece comprises a first sealing rubber ring and a second sealing rubber ring sleeved on the outer periphery of the clamping groove piece, a copper sleeve is arranged between the first sealing rubber ring and the second sealing rubber ring, one side of the second sealing rubber ring is the copper sleeve, and the other side is provided with an oil seal sleeved on the outer periphery of the clamping groove piece. The end of the anti-rotation pin is provided with a guide sliding block, the guide sliding block is embedded in the anti-rotation groove, and the length of the anti-rotation groove is greater than the maximum stroke distance of the lead screw.

4. A hypercycloidal tooth gas-liquid loading displacement pump according to claim 3, wherein, The speed reduction component is connected with the hypoid gear rotary table, and the hypoid gear rotary table is connected with the lead screw nut.

5. A hypercycloid gas-liquid loading displacement pump according to claim 1 or 3, wherein, The end of the lead screw extending into the first cylinder is provided with a plug, and the clamping groove piece is provided with a plug slot matched with the plug, the size of the plug slot is greater than the size of the plug, and the plug is inserted into the plug slot to movably connect the lead screw with the clamping groove piece.

6. A pressure regulating and speed regulating system comprising two hypoid gear gas-liquid loading displacement pumps according to claim 1 or claim 3, wherein the inlet and outlet of one of the hypoid gear gas-liquid loading displacement pumps are connected with a first electromagnetic pneumatic valve through a first pipeline, the inlet and outlet of the other hypoid gear gas-liquid loading displacement pump are connected with a second electromagnetic pneumatic valve through a second pipeline, and the driving component of the hypoid gear gas-liquid loading displacement pump and the first electromagnetic pneumatic valve and the second electromagnetic pneumatic valve are connected with a control system.

7. A pressure regulating and speed regulating system as claimed in claim 6, wherein The first pipeline and the second pipeline are both provided with a pressure detection element, and the two hypoid gear gas-liquid loading displacement pumps are both provided with a displacement detection element for detecting the displacement of the lead screw, and the pressure detection element and the displacement detection element are connected with the control system.

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