CN112628220A - Servo oil source of pressure testing machine - Google Patents
Servo oil source of pressure testing machine Download PDFInfo
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- CN112628220A CN112628220A CN202011510498.8A CN202011510498A CN112628220A CN 112628220 A CN112628220 A CN 112628220A CN 202011510498 A CN202011510498 A CN 202011510498A CN 112628220 A CN112628220 A CN 112628220A
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- oil
- plunger
- pump
- servo
- sliding block
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
- F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B1/16—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B1/18—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having self-acting distribution members, i.e. actuated by working fluid
- F04B1/188—Plate-like distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/28—Control of machines or pumps with stationary cylinders
- F04B1/29—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B1/295—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/12—Special measures for increasing the sensitivity of the system
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
- F15B2211/20515—Electric motor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/255—Flow control functions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7053—Double-acting output members
- F15B2211/7054—Having equal piston areas
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/75—Control of speed of the output member
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N3/00—Investigating strength properties of solid materials by application of mechanical stress
- G01N3/08—Investigating strength properties of solid materials by application of mechanical stress by applying steady tensile or compressive forces
- G01N3/10—Investigating strength properties of solid materials by application of mechanical stress by applying steady tensile or compressive forces generated by pneumatic or hydraulic pressure
- G01N3/12—Pressure testing
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Reciprocating Pumps (AREA)
Abstract
The application relates to a servo oil source of a pressure testing machine, which relates to the technical field of experimental equipment and comprises a hydraulic cylinder, a plunger pump for pumping oil of the hydraulic cylinder, a driving motor for driving the plunger pump and an oil tank for storing hydraulic oil, wherein the hydraulic cylinder is communicated with the plunger pump, the plunger pump is communicated with the oil tank and the hydraulic cylinder is communicated with the oil tank through oil pipes; the pump body is also provided with a servo control mechanism for adjusting the included angle between the axis of the swash plate and the axis of the cylinder body. This application reduces the pump oil volume of plunger pump through servo control mechanism when the pump oil volume of plunger pump needs to be reduced, and driving motor's slew velocity can remain unchanged, and then the pulsation phenomenon when having alleviateed the pump oil has improved measurement accuracy.
Description
Technical Field
The application relates to the field of experimental equipment, in particular to a servo oil source of a pressure testing machine.
Background
The pressure tester is also called an electronic pressure tester, and is mainly suitable for testing various physical and mechanical properties of materials such as rubber, plastic plates, pipes, profiled bars, plastic films, electric wires and cables, waterproof coiled materials, metal wires, cartons and the like. When the compression tester is used for testing the compression strength of an object, the extending speed of a piston rod of a hydraulic cylinder of the compression tester is required to be constant, and if the piston rod has acceleration during extending, the final measurement result is degraded.
At present, China invention application with publication number CN110987625A, whose publication number is 10.04.2020, provides an ultra-silent electro-hydraulic servo universal testing machine, which comprises a host structure, a measuring system and an electro-hydraulic servo system, wherein the host structure comprises a base and a vertically arranged rectangular testing frame vertically connected to the base in a sliding manner, the base is fixedly connected with a hydraulic cylinder for driving the testing frame to vertically slide, and the electro-hydraulic servo system provides hydraulic power for the hydraulic cylinder. The electro-hydraulic servo system comprises an oil tank, wherein a servo pump is fixedly connected with the oil tank (the servo pump controls a hydraulic pump by a servo motor and provides a power source for a hydraulic cylinder), an outlet of the servo pump is communicated with a two-position four-way electromagnetic valve which controls the hydraulic cylinder, the servo pump is electrically connected with a control module, the control module is electrically connected with a speed sensor, the control module receives a detection signal of the speed sensor and compares the detection signal with a set value, and then the control module outputs a signal to control the start and stop of the servo pump.
In view of the above-mentioned related technologies, the inventor believes that when the amount of oil pumped by the servo pump needs to be reduced, the rotation speed of the servo motor will be reduced, and at this time, the pulsation phenomenon of the servo pump will become obvious, so that the extension speed of the piston rod of the hydraulic cylinder is not constant, and the measurement accuracy is reduced.
Disclosure of Invention
When reducing the pump oil mass of oil pump, in order to alleviate pulsation phenomenon, improve measurement accuracy, this application provides a pressure testing machine's servo oil source.
The application provides a servo oil source of compression testing machine adopts following technical scheme:
a servo oil source of a pressure testing machine comprises a hydraulic cylinder, a plunger pump for pumping oil by the hydraulic cylinder, a driving motor for driving the plunger pump and an oil tank for storing hydraulic oil, wherein the hydraulic cylinder is communicated with the plunger pump, the plunger pump is communicated with the oil tank, and the hydraulic cylinder is communicated with the oil tank through oil pipes,
the plunger pump comprises a pump body, a cylinder body, an oil distribution disc, a plunger and a swash plate, wherein the cylinder body, the oil distribution disc and the swash plate are all arranged in the pump body in a penetrating manner;
the oil distribution disc is fixedly connected in the pump body, an oil inlet and an oil outlet are formed in the oil distribution disc, the oil inlet is communicated with the oil tank, and the oil outlet is communicated with the hydraulic cylinder;
the cylinder body and the oil distribution disc are coaxially arranged, one end face of the cylinder body is abutted against the oil distribution disc, and the cylinder body is rotatably connected with the pump body along the axis of the cylinder body;
the cylinder body is provided with a plurality of plunger holes for placing plungers, the axial direction of each plunger hole is parallel to the axial direction of the cylinder body, and the plunger holes are uniformly distributed along the circumferential direction of the cylinder body;
the plunger is provided with a plurality of plungers, one plunger corresponds to one plunger hole, the plunger is arranged in the plunger hole in a penetrating way,
the swash plate is arranged at one end of the cylinder body, which is far away from the oil distribution disc, and the axis of the swash plate is intersected with the axis of the cylinder body; one end of the plunger, which is far away from the oil distribution disc, is connected with the swash plate;
an output shaft of the driving motor is coaxially and fixedly connected with the cylinder body;
and the pump body is also provided with a servo control mechanism for adjusting an included angle between the axis of the swash plate and the axis of the cylinder body.
By adopting the technical scheme, when pumping oil, the driving motor drives the cylinder body to rotate, at the moment, the plunger continuously reciprocates in the plunger hole under the action of the swash plate, the hydraulic cylinder in the oil tank flows into the plunger hole from the oil inlet, and then the hydraulic oil in the plunger hole is discharged out of the plunger hole from the oil outlet, so that the oil pumping process is completed;
when the oil pumping amount of the plunger pump needs to be reduced, the servo control mechanism can adjust the swash plate to reduce an included angle between the axis of the swash plate and the axis of the cylinder body, so that the oil pumping amount of the plunger pump is reduced; because in the process of reducing the oil pumping amount of the plunger pump, the rotating speed of the driving motor can be kept unchanged, the sliding distance of the plunger in the plunger hole is reduced, and the reciprocating sliding frequency of the plunger in the plunger hole is unchanged, so that the pulsation phenomenon during oil pumping is reduced, and the measurement precision is improved.
Optionally, servo control mechanism includes servo motor, lead screw and sliding block, the sliding block with the pump body slides and is connected, the sloping cam plate rotates to be connected on the sliding block, the one end threaded connection of lead screw is in on the sliding block, the other end of lead screw rotates to be connected on the pump body, servo motor fixed connection be in on the pump body, just servo motor with screw drive connects.
By adopting the technical scheme, when the oil pumping amount of the plunger pump needs to be adjusted, the servo motor controls the lead screw to rotate, and the lead screw drives the sliding block to slide; because the swash plate rotates on the sliding block, in the sliding process of the sliding block, the included angle between the axis of the swash plate and the axis of the cylinder body can be changed, and the oil pumping amount of the plunger pump is adjusted.
Optionally, the servo oil source of the pressure testing machine further comprises a controller, a speed sensor is arranged in the cylinder body of the hydraulic cylinder, the speed sensor is in electric signal connection with the controller, and the controller is in electric signal connection with the servo motor.
By adopting the technical scheme, the speed sensor detects the extending speed of the piston rod of the hydraulic cylinder in real time, when the extending speed of the piston rod is reduced, the controller can control the servo motor to rotate, so that the included angle between the axis of the swash plate and the axis of the cylinder body is increased, the pump oil amount of the plunger pump is improved, the pressure of hydraulic oil in the hydraulic cylinder is further improved, and the extending speed of the piston rod of the hydraulic cylinder is more constant.
Optionally, the servo control mechanism further comprises an auxiliary driving component for auxiliary driving of the sliding block.
Through adopting above-mentioned technical scheme, when the servo motor drive sliding block slided, the auxiliary drive subassembly auxiliary drive sliding block slided simultaneously, has improved the reaction rate of plunger pump, the plunger pump quick adjustment oil outlet speed and the pressure of producing oil of the oil-out of being convenient for.
Optionally, an adjustment cavity is formed in the pump body, the sliding block is arranged in the adjustment cavity in a penetrating mode, the adjustment cavity of the sliding block is divided into an increment cavity and a decrement cavity, the auxiliary driving assembly comprises a first valve and a second valve, the decrement cavity is communicated with the oil outlet through the first valve, and the increment cavity is communicated with the oil tank through the second valve.
Through adopting above-mentioned technical scheme, when the pump oil volume of plunger pump needs to be reduced, first valve intercommunication oil-out and decrement chamber, second valve intercommunication oil tank and increment chamber, hydraulic oil flows into the decrement chamber through first valve from the oil-out department, and then promote the sliding block and slide, meanwhile servo motor control sliding block slides towards the same direction, hydraulic oil in the increment chamber flows into in the oil tank, so unnecessary hydraulic oil drive sliding block in usable oil outlet department, the speed that pressure reduces in oil-out department has both been improved, the required energy consumption of servo motor drive sliding block has been reduced simultaneously.
Optionally, the hydraulic cylinder is communicated with the increment cavity through a second valve, and the decrement cavity is communicated with the oil tank through a first valve.
Through adopting above-mentioned technical scheme, when the pump oil volume of needs increase plunger pump, hydraulic oil flows into the increment chamber through the second valve in following the pneumatic cylinder, and then promotes the sliding block and slides, and meanwhile servo motor control sliding block slides towards the same direction, and hydraulic oil in the decrement chamber flows into the oil case, and unnecessary hydraulic oil drive sliding block in the pneumatic cylinder so usable has both improved the rate of oil-out department pressure increase, has reduced the required energy consumption of servo motor drive sliding block simultaneously.
Optionally, the cross-section of sliding block is circular, the sealing washer has all been inlayed at sliding block length direction's both ends.
Through adopting above-mentioned technical scheme, be circular with the cross-section setting of sliding block, be convenient for inlay on the sliding block and establish the sealing washer, simultaneously because the setting of sealing washer, reduced the probability that hydraulic oil revealed from increment chamber, decrement chamber, improved the rate of oil-out department pressure variation.
Optionally, a guide block is arranged on the sliding block, a guide groove is formed in the pump body, the length direction of the guide groove is the same as the sliding direction of the sliding block, and the guide block is clamped in the guide groove.
Through adopting above-mentioned technical scheme, under the guide effect of guide block, when servo motor drive lead screw rotated, the lead screw was difficult for driving the sliding block and makes the sliding block take place relative rotation along the axle center of self and the pump body, has improved the gliding efficiency of sliding block, and then has improved the speed of oil-out department pressure variation.
Optionally, the pump body is provided with a limiting part, the limiting part can be abutted against the guide block, and when the limiting part is abutted against the guide block, the axis of the swash plate is coaxial with the axis of the cylinder body.
Through adopting above-mentioned technical scheme, when reducing the pump oil mass of plunger pump, the sliding block can produce relative slip with the pump body, and when guide block and spacing portion butt, the pump oil mass of plunger pump is zero, and under the effect of spacing portion, the sliding block just can't continue to produce relative slip with the pump body this moment, has reduced the probability of hydraulic oil refluence.
Optionally, the plunger pump further comprises a connecting plate, the connecting plate is connected with the swash plate in a coaxial rotating mode along the axis of the swash plate, a plurality of connecting blocks are connected to the connecting plate in a sliding mode along the radial direction of the connecting plate, one connecting block corresponds to one plunger, and one end, far away from the oil distribution disc, of the plunger is connected with the connecting block in a universal rotating mode.
By adopting the technical scheme, the plunger is rigidly connected with the swash plate, so that the plunger has self-absorption capacity, when the axis of the swash plate is approximately parallel to the axis of the cylinder body, the plunger pump still can keep pumping oil, and the reliability of the plunger pump when the requirement of low pumping oil quantity is small is improved.
In summary, the present application includes at least one of the following beneficial technical effects:
1. through the setting of servo control mechanism, when the pump oil volume of plunger pump needs to be reduced, reduce the contained angle between the axle center of sloping cam plate and the axle center of cylinder body through servo control mechanism, and then reduce the pump oil volume of plunger pump, and driving motor's slew velocity can remain unchanged, and then the pulsation phenomenon when having alleviateed the pump oil, has improved measurement accuracy.
2. Through the setting of auxiliary drive subassembly, when the servo motor drive sliding block slided, auxiliary drive subassembly can drive the sliding block simultaneously and slide, has reduced the resistance of sliding block, makes the plunger pump can the quick adjustment oil outlet speed and the pressure of producing oil of oil-out, has improved the reaction rate of plunger pump.
3. Through the arrangement of the connecting plate and the connecting block, rigid connection is formed between the plungers and the swash plate, when the cylinder body rotates, the plungers have a self-suction function, even if the included angle between the axis of the swash plate and the axis of the cylinder body is small, the suction force of each plunger can be still maintained, and when the oil pumping requirement of the plunger pump is low, oil can still be reliably pumped.
Drawings
FIG. 1 is a hydraulic system diagram of an embodiment of the present application;
FIG. 2 is a schematic cross-sectional view of a plunger pump according to an embodiment of the present application;
fig. 3 is an exploded view of a structure in a pump body according to an embodiment of the present application.
Description of reference numerals: 100. a hydraulic cylinder; 110. an oil cylinder; 120. a piston; 130. a piston rod; 140. a stroke pushing cavity; 150. a return cavity; 200. a plunger pump; 210. a pump body; 220. a cylinder body; 221. a plunger hole; 230. an oil distribution disc; 231. a gear lever; 232. an oil inlet; 233. an oil outlet; 240. a swash plate; 250. a plunger; 260. a connecting plate; 261. a chute; 270. connecting blocks; 300. a drive motor; 400. an oil tank; 500. a servo control mechanism; 510. a servo motor; 520. a lead screw; 530. a slider; 531. a guide block; 532. a guide groove; 533. a limiting part; 540. an increment cavity; 550. a decrement chamber; 600. an auxiliary drive assembly; 610. a first valve; 620. a second valve; 630. a third valve; 640. a pressure relief valve; 650. and (5) sealing rings.
Detailed Description
The present application is described in further detail below with reference to figures 1-3.
The embodiment of the application discloses pressure test machine's servo oil source. Referring to fig. 1, the servo oil source of the pressure tester includes a hydraulic cylinder 100 as an actuator, a plunger pump 200 for supplying hydraulic oil to the hydraulic cylinder 100, a driving motor 300 for supplying power to the plunger pump 200, and an oil tank 400 for storing hydraulic oil, and the plunger pump 200 is provided with a servo control mechanism 500 for adjusting the amount of oil pumped by the plunger pump 200.
Referring to fig. 2 and 3, the plunger pump 200 includes a pump body 210, and the pump body 210 is disposed in a hollow state. A cylinder 220 for pumping hydraulic oil penetrates through the pump body 210, the cylinder 220 is rotatably connected with the pump body 210 along the axis of the cylinder 220, and an output shaft of the driving motor 300 is in coaxial key connection with the cylinder 220.
Referring to fig. 2 and 3, the cylinder 220 is provided with a plurality of plunger holes 221 parallel to the axis thereof, each plunger hole 221 is penetrated with a plunger 250, and the plunger 250 is slidably connected with the cylinder 220 along the axial direction of the plunger hole 221. The plunger holes 221 are uniformly distributed along the circumferential direction of the cylinder 220, and the number of the plunger holes 221 is odd, in the embodiment of the present application, the number of the plunger holes 221 is five.
Referring to fig. 2 and 3, a swash plate 240 for controlling the sliding movement of the plunger 250 is further inserted into the pump body 210, and the axis of the swash plate 240 intersects with the axis of the cylinder block 220. The swash plate 240 is coaxially and rotatably connected with a connecting plate 260, a plurality of sliding grooves 261 are formed in one end face, away from the swash plate 240, of the connecting plate 260, and the sliding grooves 261 are formed in the radial direction of the connecting plate 260. All the joints on each inclined groove are provided with a connecting block 270, and the connecting block 270 slides along the length direction of the sliding groove 261 and is connected with the connecting plate 260. The end of the plunger 250 adjacent the swash plate 240 is gimbaled to a connecting block 270.
Referring to fig. 2 and 3, an oil distribution pan 230 for distributing oil is further disposed in the pump body 210, the oil distribution pan 230 is disposed coaxially with the cylinder block 220, and the oil distribution pan 230 is disposed at an end of the cylinder block 220 away from the swash plate 240. The oil distribution disc 230 is hollow, and a blocking rod 231 is integrally formed on the inner circumferential surface of the oil distribution disc 230, and the blocking rod 231 divides the cavity in the middle of the oil distribution disc 230 into an oil inlet 232 and an oil outlet 233. The stop rod 231 is perpendicular to the axis of the oil distribution plate 230, and the stop rod 231 is perpendicular to the plane where the axis of the cylinder 220 and the axis of the swash plate 240 are located.
Referring to fig. 1 and 3, an oil inlet 232 of the oil distribution plate 230 is communicated with an oil tank 400, an oil outlet 233 is communicated with the oil cylinder 110 through an auxiliary driving assembly 600, the hydraulic cylinder 100 comprises a piston 120 and a piston rod 130 of the oil cylinder 110, and the piston 120 divides the interior of the oil cylinder 110 into a push stroke cavity 140 and a return stroke cavity 150. The auxiliary drive assembly 600 includes a first valve 610 and a third valve 630, and the first valve 610 and the third valve 630 are two-position four-way solenoid valves.
Referring to fig. 1 and 3, when the first valve 610 is in the left position, the point a of the first valve 610 is communicated with the point P, the point a of the first valve 610 is also communicated with the point T, and the point B of the first valve 610 is in a closed state; when the first valve 610 is at the right position, the point a of the first valve 610 is communicated with the point P, and the point B of the first valve 610 is communicated with the point T. When the third valve 630 is in the left position, the point a of the third valve 630 is communicated with the point P, and the point B of the third valve 630 is communicated with the point T; with the third valve 630 in the right position, point a of the third valve 630 is in communication with point T, and point B of the third valve 630 is in communication with point P.
Referring to fig. 1 and 3, a point P of the first valve 610 is communicated with the oil outlet 233, a point a of the first valve 610 is communicated with a point P of the third valve 630, and a point B of the first valve 610 is communicated with the oil tank 400. The point a of the third valve 630 communicates with the push chamber 140 of the hydraulic cylinder 100, and the point B of the third valve 630 communicates with the return chamber 150.
When the first valve 610 and the third valve 630 are both located at the left position, the plunger pump 200 pumps the hydraulic oil in the oil tank 400 into the push stroke cavity 140, the hydraulic oil in the return stroke cavity 150 flows out, and the piston rod 130 of the hydraulic cylinder 100 extends out; when the first valve 610 is in the left position and the third valve 630 is in the right position, the plunger pump 200 pumps the hydraulic oil in the oil tank 400 into the return chamber 150, the hydraulic oil in the push chamber 140 flows out, and the piston rod 130 of the hydraulic cylinder 100 is retracted.
Referring to fig. 1 and 3, a point T of the third valve 630 is communicated with the second valve 620, the second valve 620 is a two-position four-way solenoid valve, the point T of the third valve 630 is communicated with a point B of the second valve 620, a point a of the second valve 620 is communicated with the oil tank 400, and the point T of the second valve 620 is also communicated with the oil tank 400. When the second valve 620 is in the left position, the point a and the point T of the second valve 620 are both in a closed state, and the point B and the point P of the second valve 620 are communicated; with the second valve 620 in the right position, point a of the second valve 620 communicates with point P and point B of the second valve 620 communicates with point T.
Referring to fig. 2 and 3, the servo control mechanism 500 includes a slide block 530 connected to the swash plate 240, a lead screw 520 for slidably moving the slide block 530, and a servo motor 510 for slidably controlling the lead screw 520. The pump body 210 is provided with an adjusting cavity, the cross section of the adjusting cavity is circular, the axis of the adjusting cavity is perpendicular to the axis of the cylinder body 220, and the axial direction of the adjusting cavity is also perpendicular to the length direction of the stop rod 231. The sliding block 530 is coaxially disposed in the adjustment cavity, and the sliding block 530 is slidably connected to the pump body 210 along the axial direction of the adjustment cavity, and the sliding block 530 divides the adjustment cavity into an increment cavity 540 and a decrement cavity 550.
Referring to fig. 2 and 3, the axis of the screw 520 is coaxial with the axis of the adjustment cavity, the screw 520 is rotatably connected to the pump body 210 along the axis thereof, and the screw 520 is further slidably connected to the sliding block 530. The servo motor 510 is fixedly connected to the outer wall of the pump body 210 by screws, and an output shaft of the servo motor 510 is coaxially and fixedly connected to the lead screw 520 by a coupling. The end of the swash plate 240 away from the connecting plate 260 is integrally formed with a universal ball, which is clamped in the sliding block 530, so that the swash plate 240 and the sliding block 530 are connected in a universal rotation manner, and the end of the swash plate 240 close to the sliding block 530 faces the decrement chamber 550.
The servo motor 510 rotates to drive the sliding block 530 to slide, when the volume of the increment cavity 540 increases and the volume of the decrement cavity 550 decreases, the included angle between the axis of the swash plate 240 and the axis of the cylinder block 220 gradually decreases, and further the flow of the plunger pump 200 is reduced; when the volume of the increment chamber 540 is decreased and the volume of the increment chamber 540 is increased, the angle between the axis of the swash plate 240 and the axis of the cylinder block 220 is gradually increased, thereby increasing the flow rate of the plunger pump 200.
Referring to fig. 1 and 2, the T point of the first valve 610 communicates with the decrement chamber 550, and the P point of the second valve 620 communicates with the increment chamber 540. When the flow rate of the plunger pump 200 needs to be reduced, the servo motor 510 controls the sliding block 530 to slide, so that the volume of the decrement chamber 550 is increased and the volume of the increment chamber 540 is reduced. When the first valve 610 is in the left position and the second valve 620 is in the right position, the excess hydraulic oil at the outlet of the plunger pump 200 flows into the decrement chamber 550 to push the sliding block 530, and the lubricating oil in the increment chamber 540 flows into the oil tank 400 through the second valve 620, so that the resistance of the sliding block 530 during sliding is reduced, and the response speed of the plunger pump 200 is improved.
When the flow rate of the plunger pump 200 needs to be increased, the servo motor 510 controls the sliding block 530 to slide, so that the volume of the decrement chamber 550 is reduced and the volume of the increment chamber 540 is increased. When the second valve 620 is in the left position and the first valve 610 is in the right position, the hydraulic oil in the return chamber 150 or the push chamber 140 of the hydraulic cylinder 100 flows into the increment chamber 540 to push the sliding block 530, and the lubricating oil in the decrement chamber 550 flows into the oil tank 400 through the first valve 610, so that the resistance of the sliding block 530 during sliding is reduced, and the response speed of the plunger pump 200 is improved.
Referring to fig. 1, a pressure relief valve 640 is further bypassed between the point P of the second valve 620 and the incremental chamber 540, and the other end of the pressure relief valve 640 communicates with the oil tank 400. When the flow rate of the hydraulic oil flowing out of the return chamber 150 or the push chamber 140 is larger than the flow rate required by the increment chamber 540, the excess hydraulic oil flows into the oil tank 400 through the relief valve 640.
Referring to fig. 2, a guide groove 532 is formed on a side wall of the adjustment cavity, and a length direction of the guide groove 532 is the same as a sliding direction of the sliding block 530; the outer peripheral surface of the slide block 530 is integrally formed with a guide block 531, and the guide block 531 is engaged with the guide groove 532. Thus, the sliding block 530 is not easily rotated relative to the pump body 210 along the axis thereof, and the response efficiency of the sliding block can be improved when the sliding block 530 is slid by the screw 520.
Referring to fig. 2, a stopper 533 is formed at an end of the guide groove 532 remote from the reducing chamber 550, and the guide block 531 may abut against the stopper 533. When the guide block 531 abuts against the stopper portion 533, the axis of the swash plate 240 is coaxial with the axis of the cylinder block 220. This reduces the probability of the slider 530 slipping excessively, and thus reduces the probability of the hydraulic oil flowing in the reverse direction.
Referring to fig. 2, the seal rings 650 are fitted to the outer circumferential surfaces of both ends of the slide block 530 in the axial direction, the outer circumferential surface of the seal ring 650 close to the increment chamber 540 abuts against the inner circumferential surface of the increment chamber 540, and the outer circumferential surface of the seal ring 650 close to the decrement chamber 550 abuts against the inner circumferential surface of the decrement chamber 550. The probability of leakage of hydraulic oil from the increment chamber 540 and the decrement chamber 550 is reduced, and the reliability of the auxiliary drive assembly 600 is improved.
The servo oil source of the pressure testing machine further comprises a controller, a speed sensor is arranged on a piston rod 130 of the hydraulic cylinder 100, the speed sensor is connected with the controller through an electric signal, and the controller is connected with the servo motor 510 through an electric signal. The speed sensor detects the extending speed of the piston rod 130 of the hydraulic cylinder 100 in real time, when the extending speed of the piston rod 130 is reduced, the controller controls the servo motor 510 to rotate, so that the included angle between the axis of the swash plate 240 and the axis of the cylinder body 220 is increased, the oil pumping amount of the plunger pump 200 is increased, the pressure of hydraulic oil in the hydraulic cylinder 100 is further increased, and the extending speed of the piston rod 130 of the hydraulic cylinder 100 is more constant.
The implementation principle of the servo oil source of the pressure testing machine is as follows:
when the piston rod 130 of the hydraulic cylinder 100 extends out, the pressure testing machine gradually applies pressure to the test block, at the moment, the extending speed of the piston rod 130 is relatively small, so that the requirement of the hydraulic cylinder 100 on the oil pumping quantity of the plunger pump 200 is small, at the moment, the servo motor 510 drives the sliding block 530 to slide, the included angle of the axis between the swash plate 240 and the cylinder body 220 is reduced, the rotating speed of the driving motor 300 is kept unchanged, the sliding distance of the plunger 250 in the plunger hole 221 is reduced, but the reciprocating sliding frequency of the plunger 250 in the plunger hole 221 is unchanged, the pulsation phenomenon during oil pumping is reduced, and the measurement accuracy is improved.
The above embodiments are preferred embodiments of the present application, and the protection scope of the present application is not limited by the above embodiments, so: all equivalent changes made according to the structure, shape and principle of the present application shall be covered by the protection scope of the present application.
Claims (10)
1. The utility model provides a servo oil supply of compression testing machine which characterized in that: comprises a hydraulic cylinder (100), a plunger pump (200) for pumping oil for the hydraulic cylinder (100), a driving motor (300) for driving the plunger pump (200) and an oil tank (400) for storing hydraulic oil, wherein the hydraulic cylinder (100) is communicated with the plunger pump (200), the plunger pump (200) is communicated with the oil tank (400), and the hydraulic cylinder (100) is communicated with the oil tank (400) through oil pipes,
the plunger pump (200) comprises a pump body (210), a cylinder body (220), an oil distribution disc (230), a plunger (250) and a swash plate (240), wherein the cylinder body (220), the oil distribution disc (230) and the swash plate (240) are arranged in the pump body (210) in a penetrating manner;
the oil distribution disc (230) is fixedly connected in the pump body (210), an oil inlet (232) and an oil outlet (233) are formed in the oil distribution disc (230), the oil inlet (232) is communicated with the oil tank (400), and the oil outlet (233) is communicated with the hydraulic cylinder (100);
the cylinder body (220) and the oil distribution disc (230) are coaxially arranged, one end face of the cylinder body (220) is abutted against the oil distribution disc (230), and the cylinder body (220) is rotatably connected with the pump body (210) along the axis of the cylinder body (220);
the cylinder body (220) is provided with a plurality of plunger holes (221) for placing plungers (250), the axial direction of each plunger hole (221) is parallel to the axial direction of the cylinder body (220), and the plunger holes (221) are uniformly distributed along the circumferential direction of the cylinder body (220);
the plunger (250) is provided with a plurality of plungers, one plunger (250) corresponds to one plunger hole (221), the plunger (250) is arranged in the plunger hole (221) in a penetrating way,
the swash plate (240) is arranged at one end of the cylinder body (220) far away from the oil distribution disc (230), and the axis of the swash plate (240) is intersected with the axis of the cylinder body (220); one end of the plunger (250) far away from the oil distribution disc (230) is connected with the swash plate (240);
an output shaft of the driving motor (300) is coaxially and fixedly connected with the cylinder body (220);
the pump body (210) is further provided with a servo control mechanism (500) for adjusting an included angle between the axis of the swash plate (240) and the axis of the cylinder body (220).
2. The servo oil source of the pressure tester according to claim 1, wherein: servo control mechanism (500) includes servo motor (510), lead screw (520) and sliding block (530), sliding block (530) with the pump body (210) slides and is connected, swash plate (240) rotate to be connected on sliding block (530), the one end threaded connection of lead screw (520) is in on sliding block (530), the other end of lead screw (520) rotates to be connected on the pump body (210), servo motor (510) fixed connection be in on the pump body (210), just servo motor (510) with lead screw (520) transmission is connected.
3. The servo oil source of the pressure tester according to claim 2, wherein: the hydraulic cylinder is characterized by further comprising a controller, wherein a speed sensor is arranged in the cylinder body (220) of the hydraulic cylinder (100), the speed sensor is in electric signal connection with the controller, and the controller is in electric signal connection with the servo motor (510).
4. The servo oil source of the pressure tester according to claim 2, wherein: the servo control mechanism (500) further comprises an auxiliary drive assembly (600) for auxiliary driving of the sliding block (530).
5. The servo oil source of the pressure tester according to claim 4, wherein: the oil pump is characterized in that an adjusting cavity is formed in the pump body (210), the sliding block (530) penetrates through the adjusting cavity, the adjusting cavity of the sliding block (530) is divided into an increment cavity (540) and a decrement cavity (550), the auxiliary driving assembly (600) comprises a first valve (610) and a second valve (620), the decrement cavity (550) is communicated with the oil outlet (233) through the first valve (610), and the increment cavity (540) is communicated with the oil tank (400) through the second valve (620).
6. The servo oil source of the pressure tester according to claim 5, wherein: the hydraulic cylinder (100) is communicated with the increment chamber (540) through a second valve (620), and the decrement chamber (550) is communicated with the oil tank (400) through a first valve (610).
7. The servo oil source of the pressure tester according to claim 5, wherein: the cross-section of sliding block (530) is circular, sliding block (530) length direction's both ends all inlay and are equipped with sealing washer (650).
8. The servo oil source of the pressure tester according to claim 7, wherein: the sliding block (530) is provided with a guide block (531), the pump body (210) is provided with a guide groove (532), the length direction of the guide groove (532) is the same as the sliding direction of the sliding block (530), and the guide block (531) is clamped in the guide groove (532).
9. The servo oil source of the pressure tester according to claim 8, wherein: the pump body (210) is provided with a limiting part (533), the limiting part (533) can be abutted against the guide block (531), and when the limiting part (533) is abutted against the guide block (531), the axis of the swash plate (240) is coaxial with the axis of the cylinder body (220).
10. The servo oil source of the pressure tester according to claim 1, wherein: plunger pump (200) still includes connecting plate (260), connecting plate (260) along the axle center of swash plate (240) with swash plate (240) coaxial rotation is connected, radially sliding along self on connecting plate (260) is connected with connecting block (270), connecting block (270) are provided with a plurality ofly, one connecting block (270) and one plunger (250) correspond, plunger (250) are kept away from the one end of joining in marriage food tray (230) with connecting block (270) universal rotation is connected.
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| CN202011510498.8A CN112628220B (en) | 2020-12-18 | 2020-12-18 | Servo oil source of pressure testing machine |
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| CN202011510498.8A CN112628220B (en) | 2020-12-18 | 2020-12-18 | Servo oil source of pressure testing machine |
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| CN112628220B CN112628220B (en) | 2023-01-03 |
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| CN112628220B (en) | 2023-01-03 |
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