CN114109935A - Hydraulic amplifier based on static pressure support - Google Patents
Hydraulic amplifier based on static pressure support Download PDFInfo
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- CN114109935A CN114109935A CN202111613118.8A CN202111613118A CN114109935A CN 114109935 A CN114109935 A CN 114109935A CN 202111613118 A CN202111613118 A CN 202111613118A CN 114109935 A CN114109935 A CN 114109935A
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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
- F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
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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
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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
- F15B15/1423—Component parts; Constructional details
- F15B15/1471—Guiding means other than in the end cap
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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
- F15B15/20—Other details, e.g. assembly with regulating devices
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Abstract
The invention provides a hydraulic amplifier based on static pressure support, which comprises two oil cylinders, wherein each oil cylinder comprises a cylinder barrel, a piston and a mounting floor, the piston is inserted into the cylinder barrel and is in clearance fit with the cylinder barrel, at least two static pressure bearings which are distributed up and down are arranged inside the cylinder barrel, static pressure support sealing and guiding between the cylinder barrel and the piston are realized through the static pressure bearings, the mounting bottom plate is fixedly arranged at the bottom of the cylinder barrel, a bearing cavity filled with oil is defined by the mounting bottom plate, the cylinder barrel and the piston, and the bearing cavities of the two oil cylinders are communicated through a high-pressure hose. The invention realizes the relative motion of the piston and the cylinder barrel without mechanical friction by means of the hydrostatic bearing, and realizes no leakage of the bearing cavity under the condition of no sealing by the hydrostatic bearing, thereby ensuring that the invention realizes the Pascal principle under the condition of completely not needing to supplement oil. The invention has no mechanical friction interference, thereby not generating extra disturbance and improving the sensitivity and reproducibility.
Description
Technical Field
The invention relates to the technical field of force value measurement, in particular to a hydraulic amplifier based on static pressure support.
Background
The hydraulic amplifier is based on the Pascal principle, adopts a small-load weight, and realizes the measurement of a large-load force value through hydraulic amplification. The hydraulic amplifier is suitable for the field of large force value measurement, the characteristics of large load, high precision and the like are fully utilized, but the hydraulic principle adopted by the traditional hydraulic amplifier has defects, after the oil in the bearing cavity leaks, the oil must be supplemented immediately, otherwise the Pascal principle fails, and the impact caused when the bearing cavity is supplemented with the oil tends to cause the fluctuation of the hydraulic amplifier, so that the measurement sensitivity and reproducibility are influenced.
Disclosure of Invention
The invention aims to solve the technical problem that the continuous leakage and the re-supplement of oil in a bearing cavity can cause the fluctuation of a hydraulic amplifier, and provides a hydraulic amplifier based on static pressure support.
In order to achieve the purpose, the invention adopts the following specific technical scheme:
the invention provides a hydraulic amplifier based on static pressure support, which comprises a large oil cylinder and a small oil cylinder which are amplified according to a preset proportion; the large oil cylinder comprises a large oil cylinder barrel, a large oil cylinder piston and a large oil cylinder mounting bottom plate, the large oil cylinder piston is inserted into the large oil cylinder barrel and is in clearance fit with the large oil cylinder barrel, at least two large oil cylinder hydrostatic bearings which are distributed up and down are arranged inside the large oil cylinder barrel, hydrostatic support sealing between the large oil cylinder barrel and the piston is realized through the large oil cylinder hydrostatic bearings, the large oil cylinder mounting bottom plate is fixedly mounted at the bottom of the large oil cylinder barrel, the large oil cylinder mounting bottom plate, the large oil cylinder barrel and the large oil cylinder piston enclose a large oil cylinder bearing cavity, and oil is filled into the large oil cylinder bearing cavity; the small oil cylinder comprises a small oil cylinder barrel, a small oil cylinder piston and a small oil cylinder mounting base plate, the small oil cylinder piston is inserted into the small oil cylinder barrel and is in clearance fit with the small oil cylinder barrel, at least two small oil cylinder hydrostatic bearings distributed up and down are arranged in the small oil cylinder barrel, static pressure supporting sealing between the cylinder barrel and the piston is achieved through the small oil cylinder hydrostatic bearings, the small oil cylinder mounting base plate is fixedly mounted at the bottom of the small oil cylinder barrel, the small oil cylinder mounting base plate, the small oil cylinder barrel and the small oil cylinder piston form a small oil cylinder bearing cavity, oil liquid is filled into the small oil cylinder bearing cavity, and the small oil cylinder bearing cavity is communicated with the large oil cylinder bearing cavity through a high-pressure hose.
Preferably, each large oil cylinder hydrostatic bearing comprises at least four large hydrostatic cavities which are radially and symmetrically distributed and are arranged on the inner wall of the large oil cylinder barrel, a large hydrostatic cavity restrictor is arranged at an inlet of each large hydrostatic cavity, and large hydrostatic cavity oil drainage grooves are formed in the upper side and the lower side of each large hydrostatic cavity on the inner wall of the large oil cylinder barrel.
Preferably, the large hydrostatic pocket choke is a fixed damping slit choke.
Preferably, at least one of the large cylinder hydrostatic bearings is a variable input hydrostatic bearing and the remaining large cylinder hydrostatic bearings are fixed input hydrostatic bearings.
Preferably, the large oil cylinder piston is of a hollow structure, and two ends of the large oil cylinder piston are sealed by end covers.
Preferably, each small oil cylinder hydrostatic bearing comprises at least four small hydrostatic pressure chambers which are radially and symmetrically distributed and are arranged on the inner wall of the small oil cylinder barrel, a small hydrostatic pressure chamber restrictor is arranged at an inlet of each small hydrostatic pressure chamber, and small hydrostatic pressure chamber oil drainage grooves are respectively formed in the upper side and the lower side of each small hydrostatic pressure chamber on the inner wall of the small oil cylinder barrel.
Preferably, the small hydrostatic pocket flow restrictor is a slit flow restrictor.
Preferably, at least one of the small cylinder hydrostatic bearings is a variable input hydrostatic bearing, and the remaining small cylinder hydrostatic bearings are fixed input hydrostatic bearings.
Preferably, a large oil cylinder pressure sensor is mounted on the large oil cylinder mounting base plate, and the large oil cylinder pressure sensor is used for monitoring the pressure in the large oil cylinder bearing cavity.
Preferably, a small oil cylinder pressure sensor is mounted on the small oil cylinder mounting base plate and used for monitoring the pressure in the small oil cylinder bearing cavity.
Compared with the prior art, the invention realizes the sealing and guiding of the amplifier piston rod and the amplifier cylinder body by means of the hydrostatic bearing, realizes the real-time balance of the pressure of the hydrostatic cavity and the pressure of the bearing cavity by a hydrostatic supporting gap throttling mode, ensures that the oil liquid in the bearing cavity is not leaked, realizes the Pascal principle under the condition of completely not needing to supplement the oil liquid, thereby not generating additional disturbance, improving the sensitivity and the reproducibility, realizing that the sensitivity is not more than 0.01 percent and the reproducibility is better than 0.01 percent.
Drawings
FIG. 1 is a schematic diagram of the overall structure of a hydrostatic support based hydraulic amplifier according to one embodiment of the present invention;
FIG. 2 is a schematic diagram of a large cylinder hydrostatic bearing according to one embodiment of the present invention;
fig. 3 is a schematic structural view of a hydrostatic bearing of a small cylinder according to an embodiment of the present invention.
Wherein the reference numerals include: the large-oil-cylinder barrel 110, the large-hydrostatic-pressure-cavity upper oil drainage groove 111, the large-hydrostatic-pressure-cavity lower oil drainage groove 112, the large-oil-cylinder piston 120, the large-oil-cylinder mounting base plate 130, the large hydrostatic-pressure cavity 140, the large-oil-cylinder upper hydrostatic bearing 150, the large-oil-cylinder lower hydrostatic bearing 160, the large hydrostatic-pressure-cavity restrictor 170, the large-oil-cylinder pressure sensor 180, the large-oil-cylinder bearing accommodating cavity 190, the small-oil-cylinder barrel 210, the small hydrostatic-pressure-cavity upper oil drainage groove 211, the small hydrostatic-pressure-cavity lower oil drainage groove 212, the small-oil-cylinder piston 220, the small-oil-cylinder mounting base plate 230, the small hydrostatic cavity 240, the small-oil-cylinder upper hydrostatic bearing 250, the small-oil-cylinder lower hydrostatic bearing 260, the small hydrostatic-pressure-cavity restrictor 270, the small-oil-cylinder pressure sensor 280, the small-cylinder accommodating cavity 290 and the high-pressure hose 310.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail below with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not to be construed as limiting the invention.
The hydrostatic support based hydraulic amplifier provided by the embodiments of the present invention will be described in detail below.
Fig. 1 shows an overall structure of a hydrostatic support-based hydraulic pressure amplifier according to an embodiment of the present invention.
As shown in fig. 1, an embodiment of the present invention provides a hydrostatic support-based hydraulic amplifier, including: the large oil cylinder and the small oil cylinder are amplified according to a preset proportion, the small oil cylinder is used as a loading end of the hydraulic amplifier, the large oil cylinder is used as a measuring end of the hydraulic amplifier, a weight is applied to the loading end, and the measuring end outputs a load, so that the requirement of high-force value precision measurement is met.
The large oil cylinder comprises a large oil cylinder barrel 110, a large oil cylinder piston 120 and a large oil cylinder mounting base plate 130, the large oil cylinder piston 120 is inserted into an inner hole of the large oil cylinder barrel 110, the large oil cylinder piston 120 is in clearance fit with the large oil cylinder barrel 110 in the radial direction and moves axially relative to the large oil cylinder barrel 110, the large oil cylinder mounting base plate 130 is fixedly mounted at the bottom of the large oil cylinder barrel 110 through bolts, a cavity defined by the large oil cylinder barrel 110, the large oil cylinder piston 120 and the large oil cylinder mounting base plate 130 forms a large oil cylinder bearing accommodating cavity 190, and oil is filled into the large oil cylinder bearing accommodating cavity 190.
In order to reduce the weight of the large oil cylinder piston 120, the large oil cylinder piston 120 is of a hollow structure, two ends of the large oil cylinder piston 120 are sealed by end covers, the outer surface of the large oil cylinder piston 120 is subjected to thermal spraying and polishing treatment, and the large oil cylinder piston is high in machining precision and long in service life.
The inner hole of the large oil cylinder barrel 110 is honed, and at least two large oil cylinder hydrostatic bearings which are distributed up and down are arranged in the large oil cylinder barrel 110.
Fig. 2 shows a structure of a large cylinder hydrostatic bearing according to an embodiment of the present invention.
As shown in fig. 1 and 2, the large cylinder hydrostatic bearing adopts at least four large hydrostatic chambers 140 arranged on the inner wall of the large cylinder barrel 110 in a radial symmetrical distribution, a large hydrostatic chamber restrictor 170 is respectively arranged at the inlet of each large hydrostatic chamber 140, the large hydrostatic chamber restrictor 170 can adopt a capillary restrictor, a small hole restrictor, a slit restrictor or other type restrictors, the oil flows into the large hydrostatic chamber 140 after being throttled by the large hydrostatic chamber restrictor 170, a layer of high-pressure oil film is formed between the large cylinder barrel 110 and the large cylinder piston 120, so that a hydrostatic support is formed between the large cylinder barrel 110 and the large cylinder piston 120, the relative movement between the large cylinder barrel 110 and the large cylinder piston 120 without mechanical friction is realized, thereby realizing the ultra-high-precision hydraulic amplification function, and the hydrostatic support between the large cylinder barrel 110 and the large cylinder piston 120 can resist the side load caused by installation error, it is ensured that mounting errors will not have any effect on the hydraulic amplifier.
Fig. 1 shows two large cylinder hydrostatic bearings, namely a large cylinder upper hydrostatic bearing 150 and a large cylinder lower hydrostatic bearing 160, and hydrostatic support sealing and guiding between the large cylinder barrel 110 and the large cylinder piston 120 are realized through the large cylinder upper hydrostatic bearing 150 and the large cylinder lower hydrostatic bearing 160.
An upper large static pressure cavity oil drainage groove 111 and a lower large static pressure cavity oil drainage groove 112 are formed in the upper side and the lower side of the large cylinder upper static pressure bearing 150 on the inner wall of the large cylinder barrel 110, oil in the large static pressure cavity of the large cylinder upper static pressure bearing 150 is discharged from the upper large static pressure cavity oil drainage groove 111 and the lower large static pressure cavity oil drainage groove 112 respectively, and oil in the large static pressure cavity of the large cylinder lower static pressure bearing 160 is discharged from the lower large static pressure cavity oil drainage groove 112.
At least one V-shaped damping groove is formed in the inner wall of the large oil cylinder barrel 110 and used for enhancing the sealing effect between the large oil cylinder barrel 110 and the large oil cylinder piston 120.
An oil path channel communicated with the large oil cylinder bearing cavity 190 is formed in the large oil cylinder mounting base plate 130, an oil path interface and a pressure measuring interface are further arranged on the side wall of the large oil cylinder mounting base plate 130, the oil path channel is respectively communicated with the pressure measuring interface and the oil path interface, a large oil cylinder pressure sensor 180 is mounted at the pressure measuring interface, and the large oil cylinder pressure sensor 180 is used for monitoring the pressure in the large oil cylinder bearing cavity 190.
The small oil cylinder comprises a small oil cylinder barrel 210, a small oil cylinder piston 220 and a small oil cylinder mounting base plate 230, the small oil cylinder piston 220 is inserted into an inner hole of the small oil cylinder barrel 210, the small oil cylinder piston 220 is in clearance fit with the small oil cylinder barrel 210 in the radial direction and moves axially relative to the small oil cylinder barrel 210, the small oil cylinder mounting base plate 230 is fixedly mounted at the bottom of the small oil cylinder barrel 210 through bolts, a small oil cylinder bearing cavity 290 is formed by a cavity formed by the small oil cylinder barrel 210, the small oil cylinder piston 220 and the small oil cylinder mounting base plate 230 in an enclosed mode, and oil liquid is filled into the small oil cylinder bearing cavity 290.
The inner hole of the small oil cylinder barrel 210 is honed, and at least two small oil cylinder hydrostatic bearings which are distributed up and down are arranged in the small oil cylinder barrel 210.
Fig. 3 shows a structure of a small cylinder hydrostatic bearing according to an embodiment of the present invention.
As shown in fig. 1 and 3, the small cylinder hydrostatic bearing adopts at least four small hydrostatic chambers 240 which are radially and symmetrically distributed and are arranged on the inner wall of the small cylinder barrel 210, a small hydrostatic chamber restrictor 270 is respectively arranged at the inlet of each small hydrostatic chamber 240, the small hydrostatic chamber restrictor 270 can adopt a capillary restrictor, a small hole restrictor, a slit restrictor or other restrictors, preferably a fixed damping slit restrictor, oil flows into the small hydrostatic chamber 240 after being throttled by the small hydrostatic chamber restrictor 270, a layer of high-pressure oil film is formed between the small cylinder barrel 210 and the small cylinder piston 220, a hydrostatic support is formed between the small cylinder barrel 210 and the small cylinder piston 220, the relative movement between the small cylinder barrel 210 and the small cylinder piston 220 without mechanical friction is realized, so that the ultra-high-precision hydraulic amplification function is realized, and the hydrostatic support between the small cylinder barrel 210 and the small cylinder piston 220 can resist the lateral load caused by the installation error, it is ensured that mounting errors will not have any effect on the hydraulic amplifier.
Fig. 1 shows two small cylinder hydrostatic bearings, namely a small cylinder upper hydrostatic bearing 250 and a small cylinder lower hydrostatic bearing 260, and hydrostatic support sealing between the small cylinder barrel 210 and the small cylinder piston 220 is realized through the small cylinder upper hydrostatic bearing 250 and the small cylinder lower hydrostatic bearing 260.
An upper small hydrostatic pressure cavity oil drainage groove 211 and a lower small hydrostatic pressure cavity oil drainage groove 212 are formed in the upper side and the lower side of the large cylinder hydrostatic bearing 150 on the inner wall of the small cylinder barrel 210, oil in the large hydrostatic pressure cavity of the small cylinder hydrostatic bearing 250 is discharged from the upper small hydrostatic pressure cavity oil drainage groove 211 and the lower small hydrostatic pressure cavity oil drainage groove 212 respectively, and oil in the small hydrostatic pressure cavity of the small cylinder hydrostatic bearing 260 is discharged from the lower small hydrostatic pressure cavity oil drainage groove 212.
The inner wall of the small oil cylinder barrel 210 is further provided with a V-shaped damping groove for enhancing the sealing effect between the small oil cylinder barrel 210 and the small oil cylinder piston 220.
An oil passage communicated with the small oil cylinder bearing cavity 290 is formed in the small oil cylinder mounting base plate 230, an oil passage interface and a pressure measuring interface are further arranged on the side wall of the small oil cylinder mounting base plate 230, the oil passage is respectively communicated with the pressure measuring interface and the oil passage interface, a small oil cylinder pressure sensor 280 is mounted at the pressure measuring interface, and the small oil cylinder pressure sensor 280 is used for monitoring the pressure in the small oil cylinder bearing cavity 290. The oil line interface of the small oil cylinder is connected with the oil line interface of the large oil cylinder through a high-pressure hose 310, so that the small oil cylinder bearing cavity 290 is communicated with the large oil cylinder bearing cavity 190.
The above details describe the whole hydraulic amplifier based on the static pressure support provided by the embodiment of the present invention, and the working process of the hydraulic amplifier based on the static pressure support is as follows:
two oil cylinders with the amplification ratio of 100:1 are selected, and the large oil cylinder bearing cavity 190, the small oil cylinder bearing cavity 290 and the high-pressure hose 310 are filled with oil liquid and are closed and kept. The weight is applied to the small oil cylinder serving as the loading end, the piston 220 of the small oil cylinder moves downwards, the pascal principle shows that oil in the bearing cavity 290 of the small oil cylinder flows to the bearing cavity 190 of the large oil cylinder through the high-pressure hose 310 and is loaded to the bottom surface of the piston 120 of the large oil cylinder to push the piston 120 of the large oil cylinder to move upwards, the load output by the large oil cylinder serving as the measuring end is 100 times of the load of the weight at the loading end, namely, the large load force value is measured through the small load weight, and therefore the resolution and the measuring accuracy are improved.
The working process of the large oil cylinder is as follows: the oil with fixed pressure is input to the hydrostatic bearing 150 on the large oil cylinder, the oil with fixed pressure enters the large hydrostatic chamber 140 after being throttled by the large hydrostatic chamber throttler 170, and the oil in the large hydrostatic chamber 140 is respectively discharged from the oil drainage groove 111 on the large hydrostatic chamber and the oil drainage groove 112 under the large hydrostatic chamber through the two-way throttling edge (the peripheral area of the cylinder barrel corresponding to the oil drainage groove is the throttling edge), so that fixed pressure drop is generated, and the stable operation of the hydrostatic bearing 150 on the large oil cylinder is realized. The variable-pressure oil is input into the large cylinder lower hydrostatic bearing 160, the variable-pressure oil enters the large hydrostatic chamber 140 after being throttled by the large hydrostatic chamber throttler 170, and the oil in the large hydrostatic chamber 140 is discharged from the large hydrostatic chamber lower oil drainage groove 112 through a one-way throttling edge, so that a fixed pressure drop is generated. The pressure in the large oil cylinder bearing cavity 190 is acquired in real time through the large oil cylinder pressure sensor 180, the input pressure of the hydrostatic bearing 150 on the large oil cylinder is adjusted according to the pressure in the large oil cylinder bearing cavity 190, the pressure drop of the throttler can be obtained through calculation, so that the pressure of the throttled oil can be calculated according to the pressure of the input oil and compared with the pressure in the large oil cylinder bearing cavity 190, when the two pressure values are equal, the oil throttled by the large hydrostatic cavity throttler 170 is changed into the sealing oil of the large oil cylinder bearing cavity 190, and therefore oil leakage in the large oil cylinder bearing cavity 190 is avoided. Through the normal operation of the large oil cylinder upper hydrostatic bearing 150 and the large oil cylinder lower hydrostatic bearing 160, the guiding and sealing between the large oil cylinder barrel 110 and the large oil cylinder piston 120 are ensured, and the relative movement between the two without any mechanical friction is realized. The working process of the small oil cylinder is the same as that of the large oil cylinder, and the description is omitted here.
According to the invention, the static pressure support gap throttling mode is adopted to realize the real-time balance of the pressure of the static pressure cavity and the pressure of the bearing cavity, so that no leakage of oil in the bearing cavity is ensured, and the Pascal principle is realized under the condition of completely not needing to supplement oil, thereby generating no additional disturbance, improving the sensitivity and reproducibility, and realizing that the sensitivity is not more than 0.01% and the reproducibility is better than 0.01%. And because the hydrostatic bearing makes big hydro-cylinder and little hydro-cylinder possess the ability of resisting side load, guarantee that installation error also can not have any influence to this hydraulic amplifier.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.
The above embodiments of the present invention should not be construed as limiting the scope of the present invention. Any other corresponding changes and modifications made according to the technical idea of the present invention should be included in the protection scope of the claims of the present invention.
Claims (10)
1. A hydraulic amplifier based on static pressure support is characterized by comprising a large oil cylinder and a small oil cylinder which are amplified according to a preset proportion; wherein the content of the first and second substances,
the large oil cylinder comprises a large oil cylinder barrel, a large oil cylinder piston and a large oil cylinder mounting bottom plate, the large oil cylinder piston is inserted into the large oil cylinder barrel and is in clearance fit with the large oil cylinder barrel, at least two large oil cylinder hydrostatic bearings which are distributed up and down are arranged inside the large oil cylinder barrel, the large oil cylinder hydrostatic bearings are used for realizing hydrostatic support sealing between the large oil cylinder barrel and the piston, the large oil cylinder mounting bottom plate is fixedly arranged at the bottom of the large oil cylinder barrel, the large oil cylinder mounting bottom plate, the large oil cylinder barrel and the large oil cylinder piston are enclosed to form a large oil cylinder bearing cavity, and oil is filled into the large oil cylinder bearing cavity;
the small oil cylinder comprises a small oil cylinder barrel, a small oil cylinder piston and a small oil cylinder mounting bottom plate, the small oil cylinder piston is inserted into the small oil cylinder barrel and is in clearance fit with the small oil cylinder barrel, at least two small oil cylinder hydrostatic bearings distributed from top to bottom are arranged in the small oil cylinder barrel, the small oil cylinder hydrostatic bearings are used for achieving the effect that the cylinder barrel is sealed with hydrostatic support between the pistons, the small oil cylinder mounting bottom plate is fixedly mounted at the bottom of the small oil cylinder barrel, the small oil cylinder mounting bottom plate, the small oil cylinder barrel and the small oil cylinder piston are enclosed to form a small oil cylinder bearing cavity, oil is filled into the small oil cylinder bearing cavity, and the small oil cylinder bearing cavity is communicated with the large oil cylinder bearing cavity through a high-pressure hose.
2. The hydrostatic support-based hydraulic amplifier according to claim 1, wherein each large cylinder hydrostatic bearing comprises at least four large hydrostatic chambers radially and symmetrically arranged on the inner wall of the large cylinder barrel, a large hydrostatic chamber restrictor is arranged at an inlet of each large hydrostatic chamber, and large hydrostatic chamber oil drainage grooves are respectively arranged on the upper side and the lower side of each large hydrostatic chamber on the inner wall of the large cylinder barrel.
3. The hydrostatic support-based hydraulic amplifier of claim 2, wherein the large hydrostatic cavity restrictor is a slit restrictor.
4. The hydrostatic support based hydraulic amplifier of claim 3, wherein at least one of the large cylinder hydrostatic bearings is a variable input hydrostatic bearing and the remaining large cylinder hydrostatic bearings are fixed input hydrostatic bearings.
5. The hydrostatic support based hydraulic amplifier of claim 1, wherein the large cylinder piston is a hollow structure, and both ends of the large cylinder piston are sealed by end caps.
6. The hydrostatic support-based hydraulic amplifier according to claim 1, wherein each small cylinder hydrostatic bearing comprises at least four small hydrostatic chambers radially and symmetrically arranged on the inner wall of the small cylinder barrel, a small hydrostatic chamber restrictor is arranged at an inlet of each small hydrostatic chamber, and small hydrostatic chamber oil drainage grooves are respectively arranged on the upper side and the lower side of each small hydrostatic chamber on the inner wall of the small cylinder barrel.
7. The hydrostatic support-based hydraulic amplifier of claim 6, wherein the small hydrostatic pocket choke is a fixed damping slit choke.
8. The hydrostatic support based hydraulic amplifier of claim 6, wherein at least one of the small hydro-cylinder hydrostatic bearings is a variable input hydrostatic bearing and the remaining small hydro-cylinder hydrostatic bearings are fixed input hydrostatic bearings.
9. The hydrostatic support based hydraulic amplifier of claim 1, wherein a large cylinder pressure sensor is mounted on the large cylinder mounting base plate for monitoring the pressure within the large cylinder load bearing chamber.
10. The hydrostatic support based hydraulic amplifier of claim 1, wherein a small cylinder pressure sensor is mounted on the small cylinder mounting base plate for monitoring the pressure in the small cylinder bearing cavity.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111613118.8A CN114109935A (en) | 2021-12-27 | 2021-12-27 | Hydraulic amplifier based on static pressure support |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111613118.8A CN114109935A (en) | 2021-12-27 | 2021-12-27 | Hydraulic amplifier based on static pressure support |
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| Publication Number | Publication Date |
|---|---|
| CN114109935A true CN114109935A (en) | 2022-03-01 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111613118.8A Pending CN114109935A (en) | 2021-12-27 | 2021-12-27 | Hydraulic amplifier based on static pressure support |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115931203A (en) * | 2023-03-15 | 2023-04-07 | 中机试验装备股份有限公司 | High-precision mass balance system |
| CN117526218A (en) * | 2024-01-03 | 2024-02-06 | 江苏大春电力器材有限公司 | Iron tower cable protection device of hydraulic crimping connection |
-
2021
- 2021-12-27 CN CN202111613118.8A patent/CN114109935A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115931203A (en) * | 2023-03-15 | 2023-04-07 | 中机试验装备股份有限公司 | High-precision mass balance system |
| CN117526218A (en) * | 2024-01-03 | 2024-02-06 | 江苏大春电力器材有限公司 | Iron tower cable protection device of hydraulic crimping connection |
| CN117526218B (en) * | 2024-01-03 | 2024-04-30 | 江苏大春电力器材有限公司 | Iron tower cable protection device of hydraulic crimping connection |
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