CN112049839A - Hydraulic differential hydraulic cylinder device and hydraulic loading force source system - Google Patents
Hydraulic differential hydraulic cylinder device and hydraulic loading force source system Download PDFInfo
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- CN112049839A CN112049839A CN202010941237.5A CN202010941237A CN112049839A CN 112049839 A CN112049839 A CN 112049839A CN 202010941237 A CN202010941237 A CN 202010941237A CN 112049839 A CN112049839 A CN 112049839A
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
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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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/17—Characterised by the construction of the motor unit of the straight-cylinder type of differential-piston type
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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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
Abstract
The invention discloses a hydraulic differential cylinder device and a hydraulic loading force source system, wherein the hydraulic differential cylinder device comprises: the hydraulic loading system comprises a cylinder body, a piston, a first piston rod and a second piston rod, wherein the first piston rod and the second piston rod are respectively connected with two sides of the piston, the rod diameter of the first piston rod is larger than that of the second piston rod, the piston divides the cylinder body into a first cavity and a second cavity, the first piston rod is arranged in the first cavity, the second piston rod is arranged in the second cavity, the first cavity is provided with an oil inlet, the second cavity is provided with an oil outlet which is used for being connected with a loading oil cylinder of a hydraulic loading force source system, and the oil inlet; and the output end of the driving device is connected with the first piston rod so as to drive the first piston rod to move. The hydraulic differential oil cylinder device can output a fixed flow of hydraulic oil within a certain pressure range, and when the hydraulic differential oil cylinder device is applied to a hydraulic loading force source system, the hydraulic loading force source system generates discrimination force and adjusts the discrimination force. The hydraulic loading force source system comprises the hydraulic differential oil cylinder device and has the beneficial effects.
Description
Technical Field
The invention relates to the technical field of metering and testing equipment, in particular to a hydraulic differential pressure oil cylinder device. In addition, the invention also relates to a hydraulic loading force source system comprising the hydraulic differential cylinder device.
Background
In the technical field of force value measurement and detection, a force sensor needs to be calibrated or calibrated by using a precisely controllable force source device, and currently, for a large force value measuring instrument with a measuring range exceeding 1MN, a superposed force standard machine is usually adopted to calibrate or calibrate the large force value measuring instrument internationally, namely, a calibrated reference force sensor and a measured force sensor are connected in series, and the reference force sensor and the measured force sensor which are connected in series are loaded in a mechanical or hydraulic mode.
In the prior art, a servo valve is generally utilized to unidirectionally control the hydraulic oil pump to output pressure to load the loading oil cylinder, so that the loading oil cylinder outputs a certain force value, and the force value simultaneously acts on the reference force sensor and the measured force sensor, so as to calibrate or calibrate the measured force sensor through the indicating value of the reference force sensor.
Meanwhile, in order to ensure the stability of the output force value of the loading cylinder (the output force value of the loading cylinder is detected and displayed by a reference force sensor) in consideration of system leakage, two sets of servo oil pumps (generally gear pumps) are generally adopted to form a flow difference in the prior art so as to make up for the pressure drop, namely, pressure relief, of the loading cylinder caused by leakage.
Specifically, two sets of servo oil pumps are arranged in parallel, one is rotated forward, the other is rotated backward, hydraulic oil of the two sets of servo oil pumps enters one another and flows out, a flow difference is formed, and after entering the loading oil cylinder, leakage pressure of the loading oil cylinder can be compensated instantly, namely, when a force value detected by a reference force sensor fluctuates (for example, is reduced), the flow difference is generated by controlling the two sets of servo oil pumps, the leakage pressure loss is compensated, the force value detected by the reference force sensor is recovered to a target value, and the output pressure of the loading oil cylinder is controlled to be stable in a closed loop mode.
However, when the system leakage is compensated by the method, the flow difference of the two sets of servo oil pumps is uncertain, so that the system leakage pressure can be supplemented only in a short time, and the force value detected by the reference force sensor is kept stable; and a quantitative compensation force value can not be given according to the magnitude of the pressure relief, namely, the discrimination force of the force source device and the discrimination force of the precise adjustment force source device can not be given, wherein the discrimination force is that when the initial load of the force standard machine or the force source measuring range is stable, a micro load is applied to the reference force sensor (or the serially connected force sensor to be measured), so that the output of the force sensor generates an indication value increment delta F, and the increment delta F is the discrimination force of the force standard machine.
In summary, how to provide the discriminating force of the force source device and precisely adjust the discriminating force of the force source device is a problem to be solved by those skilled in the art.
Disclosure of Invention
In view of the above, an object of the present invention is to provide a hydraulic pressure differential hydraulic cylinder device, which can output a certain flow rate of hydraulic oil within a certain hydraulic pressure range, so that when the hydraulic pressure differential hydraulic cylinder device is applied to a hydraulic loading force source system, the hydraulic loading force source system can continuously provide a quantitative discriminating force and accurately adjust the magnitude of the discriminating force.
Another object of the present invention is to provide a hydraulic loading force source system including the above hydraulic differential cylinder device, which can output a discriminating force and can precisely adjust the magnitude of the discriminating force.
In order to achieve the above purpose, the invention provides the following technical scheme:
a hydraulic differential cylinder apparatus comprising:
the hydraulic loading system comprises a cylinder body, a piston arranged in the cylinder body, and a first piston rod and a second piston rod which are respectively connected with two sides of the piston, wherein the rod diameter of the first piston rod is larger than that of the second piston rod, the piston divides the cylinder body into a first cavity and a second cavity, the first piston rod is arranged in the first cavity, the second piston rod is arranged in the second cavity, the first cavity is provided with an oil inlet, the second cavity is provided with an oil outlet which is used for being connected with a loading oil cylinder of a hydraulic loading force source system, and the oil inlet is communicated with the oil outlet through a pipeline;
and the output end of the driving device is connected with the first piston rod so as to drive the first piston rod to move.
Preferably, at least two pull rods are connected between two ends of the cylinder body.
Preferably, the driving means includes:
a power source for outputting rotational motion;
and the first piston rod is connected with a nut of the ball screw.
Preferably, the number of the ball screws is two, and the two ball screws are respectively connected with the output shaft through a transmission mechanism.
Preferably, a cross beam is connected between the nuts of the two ball screws, the cross beam is provided with a flange plate, and the first piston rod is fixedly connected with the flange plate.
Preferably, the frame for arranging the cylinder and the driving means includes:
the hydraulic cylinder comprises a top plate and a bottom plate which are arranged in parallel, wherein one end of the cylinder body is fixedly arranged on the top plate, a fixed part of a power source is fixedly arranged on the bottom plate, and two ends of a screw rod of a ball screw are respectively and rotatably connected with the top plate and the bottom plate;
a plurality of support rods connected between the top plate and the bottom plate.
Preferably, two ends of the supporting rod are respectively provided with a positioning shaft shoulder so as to respectively limit the top plate and the bottom plate; and two ends of the supporting rod respectively penetrate through the mounting holes of the top plate and the bottom plate and are locked through locking nuts.
A hydraulic loading force source system comprising:
a reference force sensor for placement in series with the load cell;
the loading oil cylinder is used for pressurizing the reference force sensor and the measured force sensor;
the oil supply system is connected with the loading oil cylinder and is used for supplying hydraulic oil to the loading oil cylinder;
the control device is respectively connected with the reference force sensor and the oil supply system;
in any of the above hydraulic differential motion cylinder devices, an oil outlet of the hydraulic differential motion cylinder device is connected to the loading cylinder, and a driving device of the hydraulic differential motion cylinder device is connected to the control device, so that the control device controls an output of the driving device according to a force value detected by the reference force sensor.
Preferably, the device further comprises a screw pump for enabling the loading oil cylinder to be rapidly loaded, the output end of the screw pump is connected with the loading oil cylinder, and the screw pump is connected with the control device.
Preferably, the method further comprises the following steps:
the pressure sensor is used for detecting the oil pressure of the loading oil cylinder and is connected with the control device, so that the control device controls the action of the screw pump according to the pressure value detected by the pressure sensor;
and/or the presence of a gas in the gas,
and the displacement sensor is used for detecting the displacement of the piston rod of the loading oil cylinder and is connected with the control device, so that the control device controls the oil supply system to be closed or opened according to a detection signal of the displacement sensor.
When the hydraulic differential oil cylinder device is applied to a hydraulic loading force source system, the first piston rod can move for a preset distance by controlling the action of the driving device of the hydraulic differential oil cylinder device, so that the hydraulic differential oil cylinder device outputs a fixed flow of hydraulic oil to the loading oil cylinder of the hydraulic loading force source system, and finally the loading oil cylinder outputs a certain identification force; in addition, the size of the discriminating force can be accurately adjusted by changing the size of the moving distance of the first piston rod.
The hydraulic loading force source system provided by the invention comprises the hydraulic differential oil cylinder device, and can continuously output the discriminating force and accurately adjust the discriminating force.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the provided drawings without creative efforts.
Fig. 1 is a schematic structural diagram of a hydraulic differential cylinder device according to an embodiment of the present invention;
FIG. 2 is a schematic view of the internal structure of FIG. 1;
fig. 3 is a schematic structural diagram of a hydraulic loading force source system according to an embodiment of the present invention.
The reference numerals in fig. 1 to 3 are as follows:
1 is a cylinder body, 11 is a piston, 12 is a first piston rod, 13 is a second piston rod, 14 is an oil inlet, 15 is an oil outlet, 16 is a pull rod, 21 is a motor, 22 is a speed reducer, 23 is a ball screw, 231 is a nut, 24 is a transmission mechanism, 25 is a cross beam, 26 is a flange plate, 27 is a transmission device, 31 is a top plate, 32 is a bottom plate, 33 is a support rod, 34 is a lock nut, 41 is a reference force sensor, 42 is a loading oil cylinder, 431 is an oil tank, 432 is an oil supply pump, 433 is an oil supply motor, 434 is a one-way valve, 435 is an electromagnetic directional valve, 436 is a throttle valve, 437 is a filter, 44 is a control device, 441 is a lower controller, 442 is an upper computer, 45 is a screw pump, 46 is a pressure sensor, 421 is a loading oil cylinder piston rod, 47 is a displacement sensor, and.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The core of the invention is to provide a hydraulic pressure differential hydraulic cylinder device which can output hydraulic oil with determined flow rate within a certain hydraulic pressure range, so that when the hydraulic pressure differential hydraulic cylinder device is applied to a hydraulic loading force source system, the hydraulic loading force source system can give quantitative discrimination force and accurately adjust the discrimination force. The invention also provides a hydraulic loading force source system comprising the hydraulic differential oil cylinder device, which can output the discrimination force and can accurately adjust the discrimination force.
Referring to fig. 1-2, fig. 1 is a schematic structural diagram of a hydraulic differential cylinder device according to an embodiment of the present invention; fig. 2 is a schematic view of the internal structure of fig. 1.
The invention provides a hydraulic differential hydraulic cylinder device, which mainly comprises a differential hydraulic cylinder and a driving device.
Specifically, the differential oil cylinder comprises a cylinder body 1, a piston 11 arranged in the cylinder body 1, and a first piston rod 12 and a second piston rod 13 which are connected with two sides of the piston 11 respectively, wherein the rod diameter of the first piston rod 12 is larger than that of the second piston rod 13, the cylinder body 1 is divided into a first cavity and a second cavity by the piston 11, the first piston rod 12 is arranged in the first cavity, the second piston rod 13 is arranged in the second cavity, the first cavity is provided with an oil inlet 14, the second cavity is provided with an oil outlet 15 which is used for being connected with a loading oil cylinder 42 of a hydraulic loading force source system, and the oil inlet 14 is communicated with the oil outlet 15 through a pipeline.
The output of the drive means is connected to the first piston rod 12 for driving the first piston rod 12 in motion.
It can be understood that, since the oil inlet 14 and the oil outlet 15 are communicated through a pipeline, that is, the first cavity and the second cavity of the differential cylinder are communicated to form a differential circuit, the oil pressure on both sides of the piston 11 is the same.
And because the rod diameter of the first piston rod 12 is larger than that of the second piston rod 13, when the driving device drives the first piston rod 12 to perform linear motion, a flow difference is generated between the first cavity and the second cavity, so that the oil outlet 15 outputs a certain flow of oil to the loading oil cylinder 42 of the hydraulic loading force source system.
For example, assume that the first piston rod 12 has a diameter d1The diameter of the second piston rod 13 is d2When the driving device drives the first piston rod 12 to move the preset distance L, the oil volume Δ V reduced by the differential cylinder is:
this is also the flow of oil from the outlet port 15 to the charging cylinder 42 of the hydraulic charging force source system.
And combining an oil volume elastic modulus formula:
it can be known that, at this time, the oil pressure increment of the hydraulic loading force source system is as follows:
wherein, V0The initial oil volume of the hydraulic loading force source system, and K is the elastic modulus of oil.
Further, according to the pascal principle, when the area of the piston 11 of the loading cylinder 42 of the hydraulic loading force source system is S, the discriminating force value Δ F output by the loading cylinder piston rod 421 is:
ΔF＝Δp×S。
therefore, when the hydraulic differential cylinder device provided by the present invention is applied to a hydraulic loading force source system, the first piston rod 12 can be moved by a predetermined distance by controlling the operation of the driving device of the hydraulic differential cylinder device, and the hydraulic differential cylinder device can output a fixed flow rate of hydraulic oil to the loading cylinder 42 of the hydraulic loading force source system, and finally the loading cylinder 42 can output a fixed discriminating force.
In addition, by changing the magnitude of the moving distance of the first piston rod 12, the magnitude of the discriminating force can be accurately adjusted.
As can be seen from the derivation process of the above formula, the larger the difference between the rod diameters of the first piston rod 12 and the second piston rod 13 is, the larger the value of the discriminating force is, and the lower the adjustment precision of the discriminating force is; it is understood that the smaller the difference in rod diameter, the smaller the value of the discrimination force, and the higher the precision of the discrimination force adjustment.
A person skilled in the art can set specific rod diameters of the first piston rod 12 and the second piston rod 13 according to actual needs, and when a rod diameter difference between the first piston rod 12 and the second piston rod 13 is small (for example, when the rod diameter difference between the first piston rod 12 and the second piston rod 13 is less than or equal to 20% of the rod diameter of the first piston rod 12), the driving device is operated to control moving amounts of the first piston rod 12 and the second piston rod 13, so that a value of an oil pressure increment Δ p can be small, and thus a discrimination value Δ F output by the loading cylinder piston rod 421 is also small, that is, a small loading force can be output under the condition that the oil pressure of the hydraulic loading force source system is extremely high, so as to continuously reproduce discrimination forces of force value points within a range of the reference force sensor 41 of the hydraulic loading force source system; meanwhile, when the discrimination force is adjusted, the discrimination force can be finely adjusted.
It can be understood that, assuming that the oil pressure in the first and second chambers is P and the diameter of the cylinder 1 is D, the pressure difference Δ F between the two sides of the differential cylinder piston 11 is0Comprises the following steps:
it can be seen that when the difference in rod diameters between the first piston rod 12 and the second piston rod 13 is small, the thrust required by the drive means acting on the first piston rod 12 will also be greatly reduced when loaded.
In addition, the specific lengths of the first piston rod 12 and the second piston rod 13 are not limited in the present invention, and can be set by those skilled in the art according to actual needs.
Since the ranges of the reference force sensor 41 and the load cell are usually large, in order to continuously reproduce the discriminating force of each force value point within the range of the reference force sensor 41 of the hydraulic loading force source system, the lengths of the first piston rod 12 and the second piston rod 13 are usually long, and in order to ensure the linearity and stability of the first piston rod 12 and the second piston rod 13, at least two pull rods 16 are connected between the two ends of the cylinder 1 on the basis of the above-mentioned embodiment.
That is, the present embodiment resists the forced deformation of the cylinder 1 by the two or more tie rods 16 to ensure the linearity of the cylinder 1, thereby ensuring the linearity and stability of the movement of the first and second piston rods 12 and 13.
Preferably, more than two tie rods 16 are symmetrically distributed about the centre line of the cylinder 1; alternatively, two or more tie rods 16 are evenly distributed along the outer periphery of the cylinder 1.
As shown in fig. 1, the number of the tie rods 16 is preferably four, and four tie rods 16 are symmetrically distributed with respect to the center line of the cylinder block 1 in pairs.
In view of convenience in connecting the pull rod 16 to both ends of the cylinder body 1, it is preferable that both ends of the cylinder body 1 are respectively provided with flanges, and both ends of the pull rod 16 are respectively fixedly connected to the flanges at both ends of the cylinder body 1.
For example, as shown in fig. 1, both ends of the pull rod 16 are respectively provided with external threads, and both ends of the pull rod 16 are respectively passed through flanges at both ends of the cylinder 1 and then locked with the flanges by first nuts.
The present invention is not limited to the specific structure of the driving device, as long as the first piston rod 12 can be driven to move linearly.
Preferably, on the basis of the above-mentioned embodiment, the driving device includes a power source and a ball screw 23, the power source is used for outputting a rotary motion, an output shaft of the power source is connected with the ball screw 23, a nut 231 of the ball screw 23 is connected with the first piston rod 12, when the power source outputs a rotary motion, a screw of the ball screw 23 is driven to rotate, so that the nut 231 of the ball screw 23 drives the first piston rod 12 to move linearly.
Preferably, the power source includes a motor 21 and a speed reducer 22, and a screw of a ball screw 23 is connected to an output shaft of the speed reducer 22.
In order to provide sufficient power to the first piston rod 12, on the basis of the above-described embodiment, the number of the ball screws 23 is two, and the two ball screws 23 are connected to the output shaft through the transmission mechanism 24, respectively.
That is, in the present embodiment, the first piston rods 12 are connected to the nuts 231 of the two ball screws 23, respectively, and the first piston rods 12 are synchronously driven to move by the nuts 231 of the two ball screws 23.
Preferably, the two ball screws 23 are disposed symmetrically with respect to the line on which the first piston rod 12 is located.
In the present embodiment, the specific structure of the transmission mechanism 24 is not limited, and the transmission mechanism 24 may be a gear transmission mechanism 24, a synchronous belt transmission mechanism 24, or the like.
Preferably, as shown in fig. 2, the transmission mechanism 24 includes three open transmission gears, that is, a driving gear and two driven gears, the driving gear is fixedly mounted on the output shaft of the power source, and the two driven gears are respectively and fixedly connected with the screws of the two ball screws 23, so that when the power source outputs a rotary motion, the driving gear can be engaged with the two driven gears respectively to realize synchronous rotation of the two screws, and the nuts 231 of the two ball screws 23 can drive the first piston rod 12 to move synchronously.
In view of the convenience of connecting the nuts 231 of the two ball screws 23 with the first piston rod 12, on the basis of the above-mentioned embodiment, the cross beam 25 is connected between the nuts 231 of the two ball screws 23, the cross beam 25 is provided with the flange 26, and the first piston rod 12 is fixedly connected with the flange 26.
That is, in the present embodiment, the first piston rod 12 is connected to the nuts 231 of the two ball screws 23 through the cross member 25, respectively.
Preferably, the flange 26 is provided in a central position of the cross beam 25.
Further preferably, the first piston rod 12 is threadedly connected to the flange 26.
In view of the fixed portion of the power source and the fixed problem of the cylinder block 1, on the basis of the above-described embodiment, the frame for arranging the cylinder block 1 and the driving device includes the top plate 31, the bottom plate 32, and the plurality of support rods 33.
Specifically, a top plate 31 and a bottom plate 32 are arranged in parallel, one end of the cylinder body 1 is fixedly arranged on the top plate 31, a fixed part of the power source is fixedly arranged on the bottom plate 32, and two ends of a screw rod of the ball screw 23 are respectively rotatably connected with the top plate 31 and the bottom plate 32; a plurality of support rods 33 are connected between the top plate 31 and the bottom plate 32, respectively.
As shown in fig. 1, the number of the support rods 33 is four, and four support rods 33 are respectively disposed at four corners of the top plate 31 and the bottom plate 32.
In view of the smoothness of the rotation of the screw of the ball screw 23, it is preferable that the corresponding positions of the top plate 31 and the bottom plate 32 are respectively provided with a fitting hole in which a bearing (for example, a tapered roller bearing) is fitted, and both ends of the screw are respectively rotatably connected to the top plate 31 and the bottom plate 32 through the bearing.
Preferably, as shown in fig. 1, a limit nut is connected to one end of the screw extending out of the top plate 31 to axially limit the screw by the limit nut.
In the present embodiment, the connection manner of the support bar 33 to the top plate 31 and the bottom plate 32 is not limited.
As a preferable scheme, on the basis of the above embodiment, two ends of the supporting rod 33 are respectively provided with a positioning shaft shoulder to respectively limit the top plate 31 and the bottom plate 32; both ends of the support rod 33 are respectively passed through the mounting holes of the top plate 31 and the bottom plate 32 and then locked by the locking nuts 34.
Referring to fig. 3, a schematic structural diagram of a hydraulic loading force source system according to an embodiment of the present invention is shown.
In addition to the above-mentioned hydraulic differential cylinder device, the present invention also provides a force source device, that is, a hydraulic loading force source system including the hydraulic differential cylinder device disclosed in the above-mentioned embodiment, the hydraulic loading force source system further includes a reference force sensor 41, a loading cylinder 42, an oil supply system, and a control device 44, etc.
Specifically, the reference force sensor 41 is used to be disposed in series with the load cell to calibrate or calibrate the load cell with the reference force sensor 41.
The loading cylinder 42 is used for pressurizing the reference force sensor 41 and the load-to-be-measured sensor, preferably, the reference force sensor 41 is arranged at the end of the loading cylinder piston rod 421, and a connecting plate 48 is arranged at the side of the reference force sensor 41 away from the loading cylinder piston rod 421, so that when loading is carried out, the connecting plate 48 abuts against the load-to-be-measured sensor to transmit output force.
The oil supply system is connected to the loading cylinder 42 so as to supply the loading cylinder 42 with hydraulic oil.
A control unit 44 is connected to the oil supply system to control the amount of oil in the system.
Meanwhile, the oil outlet 15 of the hydraulic differential cylinder device is connected with the loading cylinder 42, and the reference force sensor 41 and the driving device of the hydraulic differential cylinder device are connected with the control device 44, so that the control device 44 controls the output of the driving device according to the force value detected by the reference force sensor 41.
It should be noted that the specific structure of the oil supply system is not limited in this embodiment, and as shown in fig. 3, the oil supply system preferably includes an oil tank 431, an oil supply pump 432, an oil supply motor 433, a check valve 434, an electromagnetic directional valve 435, a throttle valve 436, a filter 437, and the like.
In the initial stage, the control device 44 controls the oil supply system to provide a certain oil pressure for the loading cylinder 42 to balance the gravity of the piston 11 of the loading cylinder 42, the reference force sensor 41, the connecting plate 48 and the like.
During loading, the control device 44 firstly controls the oil supply system to work, so that the piston 11 of the loading oil cylinder 42 and the piston rod 421 of the loading oil cylinder float to a position just contacting with the load cell, and at this time, loading is performed through the hydraulic differential oil cylinder device, that is, the control device 44 controls the driving device of the hydraulic differential oil cylinder device to act, so that the oil outlet 15 of the hydraulic differential oil cylinder device supplies hydraulic oil to the loading oil cylinder 42, and the loading oil cylinder 42 generates pressure on the reference force sensor 41 and the load cell, so as to calibrate or calibrate the load cell.
In addition, in view of the fact that the range of the load cell is usually large, in order to realize the fast loading, on the basis of the above embodiment, a screw pump 45 for fast loading the loading cylinder 42 is further included, the output end of the screw pump 45 is connected with the loading cylinder 42, and the screw pump 45 is connected with the control device 44.
That is, in this embodiment, when the piston 11 of the loading cylinder 42 and the loading cylinder piston rod 421 float to a position just about to contact the load cell, the control device 44 may control the screw pump 45 to operate, so as to compress the oil, so as to quickly raise the oil pressure in the loading cylinder 42, when the oil pressure in the loading cylinder 42 rises to a preset pressure value, the control device 44 controls the screw pump 45 to stop operating, and at this time, the control device 44 controls the hydraulic differential cylinder device to load the loading cylinder 42, so as to make the oil pressure in the loading cylinder 42 reach a target value.
In view of the convenience of control of the oil supply system and the screw pump 45, a pressure sensor 46 and a displacement sensor 47 are further included on the basis of the above-described embodiment.
Specifically, the pressure sensor 46 is used for detecting the oil pressure of the loading oil cylinder 42, and the pressure sensor 46 is connected with the control device 44, so that the control device 44 controls the action of the screw pump 45 according to the pressure value detected by the pressure sensor 46.
The displacement sensor 47 is used for detecting the displacement of the piston rod 421 of the loading oil cylinder, and the displacement sensor 47 is connected with the control device 44, so that the control device 44 controls the oil supply system to be closed or opened according to a detection signal of the displacement sensor 47.
The operation of the hydraulic loading force source system of fig. 3 will be described by way of example.
During loading, the control device 44 controls the electromagnetic directional valve 435 to be switched to the left position, and simultaneously controls the oil supply motor 433 to be opened to start injecting oil into the system, so that the piston 11 of the loading oil cylinder 42 and the piston rod 421 of the loading oil cylinder float upwards to a position just contacting with a load cell; when the displacement sensor 47 detects that the loading cylinder piston rod 421 moves to a preset position (the preset position corresponds to a position where the loading cylinder piston rod 421 floats upwards to just touch the load cell), the control device 44 controls the oil supply motor 433 to close, controls the screw pump 45 to start working, compresses oil, and quickly raises the system oil pressure, and when the pressure sensor 46 detects that the oil pressure reaches a first preset pressure value, the control device 44 controls the screw pump 45 to stop working, controls the driving device of the hydraulic differential cylinder device to start working, and starts loading by using the hydraulic differential cylinder device so as to add the system pressure to a first target value.
When unloading, the control device 44 controls the screw pump 45 to start reverse operation first, so that the volume of the oil liquid is increased, and the system pressure is rapidly reduced to a second preset pressure value, when the pressure sensor 46 detects that the pressure of the oil liquid is reduced to the second preset pressure value, the control device 44 controls the screw pump 45 to stop working, and then the control device 44 controls the driving device of the hydraulic differential oil cylinder device to work reversely, so that the hydraulic differential oil cylinder device starts unloading, the volume of the oil liquid is slightly adjusted, and the system pressure is unloaded to a second target value.
When the system is unloaded, the driving device of the hydraulic differential oil cylinder device and the screw pump 45 are controlled to stop working, the electromagnetic directional valve 435 is controlled to be switched to the right position, oil flows back to the oil tank 431 through the throttle valve 436, and finally the pressure of the system is reduced to zero, and unloading is finished.
Therefore, the hydraulic loading force source system provided by the invention adopts the screw pump 45 and the hydraulic differential oil cylinder device to be matched for loading, the influence of pressure pulsation is reduced, and the higher force value precision requirement of the system is ensured.
It should be noted that, in the above embodiments, the control device 44 preferably includes the lower controller 441 and the upper computer 442. The lower controller 441 is mainly used for acquiring signals and outputting control instructions to execution mechanisms; the upper computer 442 is mainly used to calculate an output force value to be compensated based on the detection value of the reference force sensor 41, and further calculate an output flow rate required by the hydraulic differential cylinder device.
It should be noted that the hydraulic differential cylinder device and the hydraulic loading force source system provided in the above embodiments are preferably applicable to high-pressure and ultrahigh-pressure systems, that is, the pressure of the oil is very high, so that, when a large force value is required to be output, the overall structure size of the hydraulic differential cylinder device and the hydraulic loading force source system can be prevented from being too large.
Note that the transmission 27 in fig. 3 is for convenience of illustration, and the reduction gear 22, the transmission mechanism 24, the ball screw 23, and the like in fig. 1 and 2 are collectively referred to as the transmission 27.
It is further noted that, in the present specification, relational terms such as first and second, and the like are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions.
The embodiments are described in a progressive manner in the specification, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.
The hydraulic differential cylinder device and the hydraulic loading force source system provided by the invention are described in detail above. The principles and embodiments of the present invention are explained herein using specific examples, which are presented only to assist in understanding the method and its core concepts. It should be noted that, for those skilled in the art, it is possible to make various improvements and modifications to the present invention without departing from the principle of the present invention, and those improvements and modifications also fall within the scope of the claims of the present invention.
Claims (10)
1. A hydraulic pressure differential cylinder device, comprising:
the hydraulic loading system comprises a cylinder body (1), a piston (11) arranged in the cylinder body (1), and a first piston rod (12) and a second piston rod (13) which are respectively connected with two sides of the piston (11), wherein the rod diameter of the first piston rod (12) is larger than that of the second piston rod (13), the cylinder body (1) is divided into a first cavity and a second cavity by the piston (11), the first piston rod (12) is arranged in the first cavity, the second piston rod (13) is arranged in the second cavity, the first cavity is provided with an oil inlet (14), the second cavity is provided with an oil outlet (15) connected with a loading oil cylinder (42) of a hydraulic loading force source system, and the oil inlet (14) is communicated with the oil outlet (15) through a pipeline;
the output end of the driving device is connected with the first piston rod (12) so as to drive the first piston rod (12) to move.
2. The hydraulic differential cylinder device according to claim 1, characterized in that at least two tie rods (16) are connected between the two ends of the cylinder body (1).
3. The hydraulic differential cylinder device according to claim 1, wherein the drive device includes:
a power source for outputting rotational motion;
and the ball screw (23) is connected with the output shaft of the power source, and the first piston rod (12) is connected with a nut (231) of the ball screw (23).
4. The hydraulic differential cylinder device according to claim 3, wherein the number of the ball screws (23) is two, and the two ball screws (23) are connected to the output shaft through a transmission mechanism (24), respectively.
5. The hydraulic differential cylinder device according to claim 4, characterized in that a cross beam (25) is connected between the nuts (231) of the two ball screws (23), the cross beam (25) is provided with a flange (26), and the first piston rod (12) is fixedly connected with the flange (26).
6. The hydraulic differential cylinder device as claimed in any one of claims 3 to 5, wherein the frame for arranging the cylinder block (1) and the drive means comprises:
the hydraulic cylinder comprises a top plate (31) and a bottom plate (32) which are arranged in parallel, one end of the cylinder body (1) is fixedly arranged on the top plate (31), a fixing part of a power source is fixedly arranged on the bottom plate (32), and two ends of a screw rod of a ball screw (23) are respectively in rotary connection with the top plate (31) and the bottom plate (32);
a plurality of support rods (33) connected between the top plate (31) and the bottom plate (32).
7. The hydraulic differential cylinder device according to claim 6, characterized in that the two ends of the support rod (33) are respectively provided with a positioning shoulder for respectively limiting the top plate (31) and the bottom plate (32); two ends of the supporting rod (33) penetrate through the mounting holes of the top plate (31) and the bottom plate (32) respectively and then are locked through locking nuts (34).
8. A hydraulic loading force source system, comprising:
a reference force sensor (41) for being arranged in series with the load cell;
a loading cylinder (42) for pressurizing the reference force sensor (41) and the load cell;
the oil supply system is connected with the loading oil cylinder (42) and is used for supplying hydraulic oil to the loading oil cylinder (42);
a control device (44) connected to the reference force sensor (41) and to the oil supply system, respectively;
the hydraulic differential cylinder device as claimed in any one of claims 1-7, an oil outlet (15) of said hydraulic differential cylinder device being connected to said loading cylinder (42), and a drive means of said hydraulic differential cylinder device being connected to said control means (44) so that said control means (44) controls an output of said drive means in accordance with a force value detected by said reference force sensor (41).
9. The hydraulic loading force source system of claim 8, further comprising a progressive cavity pump (45) for rapidly loading the loading cylinder (42), an output of the progressive cavity pump (45) being connected to the loading cylinder (42), the progressive cavity pump (45) being connected to the control device (44).
10. The hydraulic loading force source system of claim 9, further comprising:
the pressure sensor (46) is used for detecting the oil pressure of the loading oil cylinder (42) and is connected with the control device (44), so that the control device (44) controls the action of the screw pump (45) according to the pressure value detected by the pressure sensor (46);
and/or the presence of a gas in the gas,
and the displacement sensor (47) is used for detecting the displacement of a piston rod (421) of the loading oil cylinder and is connected with the control device (44), so that the control device (44) controls the oil supply system to be closed or opened according to a detection signal of the displacement sensor (47).
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| CN202010941237.5A CN112049839B (en) | 2020-09-09 | 2020-09-09 | Hydraulic differential hydraulic cylinder device and hydraulic loading force source system |
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| CN202010941237.5A CN112049839B (en) | 2020-09-09 | 2020-09-09 | Hydraulic differential hydraulic cylinder device and hydraulic loading force source system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112555208A (en) * | 2020-12-10 | 2021-03-26 | 重庆大学 | Hydraulic device suitable for ultrahigh pressure precision force loading and step control method |
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| CN2933840Y (en) * | 2006-06-08 | 2007-08-15 | 河南农业大学 | Double hydraulic heads piston type biomass modeling fuel machine |
| CN102177348A (en) * | 2008-08-08 | 2011-09-07 | 罗伯特·博世有限公司 | Control device, and valve arrangement having such a control device |
| CN102864778A (en) * | 2012-09-11 | 2013-01-09 | 同济大学 | Hydraulic system for hydraulic pile hammer |
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|---|---|---|---|---|
| CN2933840Y (en) * | 2006-06-08 | 2007-08-15 | 河南农业大学 | Double hydraulic heads piston type biomass modeling fuel machine |
| CN102177348A (en) * | 2008-08-08 | 2011-09-07 | 罗伯特·博世有限公司 | Control device, and valve arrangement having such a control device |
| CN102864778A (en) * | 2012-09-11 | 2013-01-09 | 同济大学 | Hydraulic system for hydraulic pile hammer |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112555208A (en) * | 2020-12-10 | 2021-03-26 | 重庆大学 | Hydraulic device suitable for ultrahigh pressure precision force loading and step control method |
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