CN117605719A - Tandem type hydraulic pressurizing system - Google Patents
Tandem type hydraulic pressurizing system Download PDFInfo
- Publication number
- CN117605719A CN117605719A CN202311558108.8A CN202311558108A CN117605719A CN 117605719 A CN117605719 A CN 117605719A CN 202311558108 A CN202311558108 A CN 202311558108A CN 117605719 A CN117605719 A CN 117605719A
- Authority
- CN
- China
- Prior art keywords
- pressure
- cylinder
- boost
- control valve
- directional control
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000005070 sampling Methods 0.000 claims description 6
- 208000019595 distal arthrogryposis type 1A Diseases 0.000 claims description 3
- 208000037748 distal type 1A arthrogryposis Diseases 0.000 claims description 3
- 238000002637 fluid replacement therapy Methods 0.000 claims 1
- 239000012530 fluid Substances 0.000 abstract description 7
- 230000001502 supplementing effect Effects 0.000 abstract description 7
- 230000009471 action Effects 0.000 abstract description 5
- 239000003921 oil Substances 0.000 description 19
- 238000000034 method Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- 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
-
- 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
- F15B19/005—Fault detection or monitoring
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
Abstract
The invention is suitable for the field of hydraulic systems, and discloses a serial hydraulic pressurizing system, which comprises a pressure source, a direction control valve and at least two pressurizing cylinders which are sequentially connected in series, wherein the inner cavity of each pressurizing cylinder is divided into a low-pressure cavity, an annular cavity and a high-pressure cavity; the final output cylinder of the system is only one stage, the number of the ultrahigh-pressure fluid supplementing valves, the ultrahigh-pressure isolating valves and the unloading valves can be greatly reduced or eliminated, and the leakage point, the cost and the action control difficulty of the pressurizing system can be effectively reduced.
Description
Technical Field
The invention relates to the field of hydraulic systems, in particular to a serial hydraulic pressurizing system.
Background
At present, the pressure of a common oil pump is below 40MPa, and when the working pressure exceeds 35MPa, a booster cylinder is basically adopted to reach the required pressure. The highest pressure output of the conventional pressure cylinder for oil pressure is 100-150 MPa (limited by the viscosity change of the oil pressure); the maximum water or water-soluble medium can reach more than 400MPa, and is mainly used in the ultra-high pressure internal high pressure forming process.
The output volume of each booster cylinder is fixed, and when the diameter of the piston of the low-pressure cavity and the diameter of the piston rod are determined, the stroke of the booster cylinder determines the final volume of the booster cylinder; the higher the pressure required to be output by the booster cylinder, the larger the booster ratio (the area of the piston of the low-pressure cavity is the area of the piston rod), the smaller the effective diameter of the piston rod and the smaller the output volume on the premise of the same diameter of the piston of the low-pressure cavity. For example, the diameter of the piston of the low-pressure cavity is 280mm, the pressurizing ratio is 4:1, the effective diameter of the piston rod is 140mm, and when the stroke is 500mm, the output volume of the pressurizing cylinder is about 7.7L; when the supercharging ratio is increased to 10:1, the effective diameter of the piston rod is reduced to about 88, and when the strokes are the same, the output volume is 3L.
With the development of industry, large-tonnage high-pressure presses and parts formed by internal high pressure are increasingly required in the market, and when a single pressure cylinder cannot meet the use requirement, a plurality of pressure cylinders are generally adopted to jointly output to ensure the output volume requirement.
The existing multi-booster cylinder combination method adopts an isobaric same-level parallel connection or high-low pressure step-by-step parallel connection system. The boost output of each of the cylinders of the parallel-connected boost system is relatively independent and only contributes to a smaller pressure output volume than the cylinder itself. In contrast, for a cylinder, a high boost output means that the boost ratio is large, that is, the diameter of the piston rod is relatively small, the output volume is small, for example, when the highest pressure reaches more than 200MPa, the output volume of the high-pressure end of a single cylinder is generally less than 3L (calculated by the low pressure of 20MPa, the boost ratio is more than 10:1), when the volume output is to be increased, the stroke of the cylinder with the highest pressure output is required to be greatly increased, the volume of the cylinder is required to be geometrically increased, especially when the volume requirement is more than 8L, the number of cylinders is required to be increased and the stroke of the cylinder is required to be increased simultaneously, the total volume of the combination of the cylinders with the high pressure level alone becomes huge, the connection mode is also complicated, and the overall cost is high.
Accordingly, there is a need for improvement and development in the art.
Disclosure of Invention
The invention aims to provide a serial hydraulic pressurizing system, wherein the final output cylinder only has one stage, the number of ultrahigh-pressure fluid supplementing valves, isolating valves and unloading valves can be greatly reduced or eliminated, and the leakage point, cost and action control difficulty of the pressurizing system can be effectively reduced.
In order to achieve the above purpose, the invention provides the following scheme:
the utility model provides a tandem type hydraulic pressure booster system, includes pressure source, pneumatic cylinder and directional control valve, the pneumatic cylinder is provided with two at least, two more the pneumatic cylinder is established ties in proper order, the pneumatic cylinder includes cylinder, piston and piston rod, the piston sets up the tip of piston rod, the piston with the piston rod sets up in the cylinder, and will the inner chamber of cylinder is divided into low pressure chamber, annular chamber and high pressure chamber, adjacent two among the pneumatic cylinder, the high pressure chamber of preceding stage pneumatic cylinder is connected with the low pressure chamber of succeeding stage pneumatic cylinder, and the quantity of directional control valve is unanimous with the quantity of pneumatic cylinder, the pressure source is connected with the proportional pressure valve, the pressure source is connected with the low pressure chamber of each pneumatic cylinder respectively, just all be provided with directional control valve between the low pressure chamber of pressure source and each pneumatic cylinder, all be provided with the hydraulically controlled check valve between the non-first stage pneumatic cylinder, the annular chamber of non-first stage pneumatic cylinder is connected with corresponding directional control valve respectively with corresponding directional control valve, and the hydraulic control check valve is connected with the high pressure pipe on the hydraulic pressure pipe, the last stage pneumatic cylinder is connected with the high pressure pipe.
Preferably, the two pressure cylinders are respectively a first pressure cylinder and a second pressure cylinder, the two direction control valves are respectively a first direction control valve and a second direction control valve, the pressure source, the first direction control valve and the low pressure cavity of the first pressure cylinder are sequentially connected, the annular cavity of the first pressure cylinder is connected with the first direction control valve, the pressure source, the second direction control valve, the hydraulic control check valve and the low pressure cavity of the second pressure cylinder are sequentially connected, the annular cavity of the second pressure cylinder is respectively connected with the second direction control valve and the hydraulic control check valve, and the high pressure cavity of the second pressure cylinder is connected with a fluid supplementing pipeline.
Preferably, the first booster cylinder is a medium pressure booster cylinder, and the second booster cylinder is a high pressure booster cylinder.
Preferably, the supercharging ratio of the first supercharging cylinder is 3:1, and the supercharging ratio of the second supercharging cylinder is 4:1.
Preferably, the serial hydraulic pressure booster system further comprises a sampling circuit, the sampling circuit comprises a plurality of pressure sensors, a plurality of multi-channel current amplifiers, an analog-to-digital converter and a reference power supply, the pressure sensors are respectively connected with the input ends of the proportional pressure valves and the high-pressure cavities of the booster cylinders of all stages in a one-to-one correspondence mode, the multi-channel current amplifiers and the analog-to-digital converter are respectively provided with a plurality of input ends and output ends, the output ends of each pressure sensor are respectively connected with the plurality of input ends of the analog-to-digital converter in a one-to-one correspondence mode, the output ends of the analog-to-digital converter are connected with the input ends of the multi-channel current amplifiers in a one-to-one correspondence mode, and the reference power supply is connected with the power supply input ends of the analog-to-digital converter.
Preferably, the pressure sensor is of the type KS-N-E-E-B25D-M-V or PT9551.
Preferably, the multichannel current amplifier is of the model YH-DA1A-2 or RW-AMP-01.
Preferably, the analog-to-digital converter is of the type H3U or CP1H.
The series hydraulic supercharging system provided by the invention has the following advantages,
the first hydraulic pressurizing system and the serial hydraulic pressurizing system comprise at least two pressurizing cylinders which are sequentially connected in series, the tail end pressurizing cylinder is a final pressure output cylinder, namely, the final output cylinder of the serial hydraulic pressurizing system is only one stage, the number of ultrahigh pressure fluid supplementing valves, isolating valves and unloading valves can be greatly reduced or canceled, compared with the two-stage pressurizing cylinder high-pressure ends of a high-low pressure parallel system, the ultrahigh pressure one-way valve isolating is required to be arranged, the ultrahigh pressure unloading valve is also required to be arranged at the high-pressure stage pressurizing cylinder high-pressure end, the serial hydraulic pressurizing system can be canceled, the leakage point, the cost and the action control difficulty of the pressurizing system can be effectively reduced, meanwhile, the final output cavity is only one stage, and the utilization rate can be improved to 100%.
The second, the boost ratio product of the boost ratio of the serial hydraulic boost system etc. boost cylinders at each level, therefore, the boost ratio of the boost cylinders at each level can make the boost system reach a larger boost ratio under the smaller condition, when the boost ratio of the boost cylinders is smaller, the diameter of the piston rod of the boost cylinder is not too small, and the volume of the terminal boost cylinder is easily promoted by increasing the stroke.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings may be obtained according to the structures shown in these drawings without inventive effort for a person skilled in the art.
Fig. 1 is a schematic structural diagram of a tandem hydraulic supercharging system according to an embodiment of the present invention.
Reference numerals illustrate:
10. a pressure source; 20. a first booster cylinder; 30. a second booster cylinder; 31. a cylinder; 32. a piston; 33. a piston rod; 34. a low pressure chamber; 35. an annular cavity; 36. a high pressure chamber; 40. a first direction control valve; 50. a second directional control valve; 60. a proportional pressure valve; 70. a hydraulically controlled one-way valve; 80. a fluid supplementing pipeline; 90. an ultrahigh pressure one-way valve.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
It should be noted that all directional indicators (such as up, down, left, right, front, and rear … …) in the embodiments of the present invention are merely used to explain the relative positional relationship, movement conditions, etc. between the components in a specific posture (as shown in the drawings), and if the specific posture is changed, the directional indicators are correspondingly changed.
It will also be understood that when an element is referred to as being "mounted" or "disposed" on another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present.
Furthermore, the description of "first," "second," etc. in this disclosure is for descriptive purposes only and is not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In addition, the technical solutions of the embodiments may be combined with each other, but it is necessary to base that the technical solutions can be realized by those skilled in the art, and when the technical solutions are contradictory or cannot be realized, the combination of the technical solutions should be considered to be absent and not within the scope of protection claimed in the present invention.
As shown in fig. 1, a tandem hydraulic boosting system according to an embodiment of the present invention.
Referring to fig. 1, the tandem hydraulic pressure boosting system of the embodiment of the invention includes a pressure source 10, a pressure boosting cylinder and a directional control valve, the pressure boosting cylinder is provided with at least two pressure boosting cylinders, the two pressure boosting cylinders are sequentially connected in series, the pressure boosting cylinder includes a cylinder barrel 31, a piston 32 and a piston rod 33, the piston 32 is arranged at the end part of the piston rod 33, the piston 32 and the piston rod 33 are arranged in the cylinder barrel 31, the inner cavity of the cylinder barrel 31 is divided into a low pressure cavity 34, an annular cavity 35 and a high pressure cavity 36, the high pressure cavity 36 of the front stage pressure boosting cylinder is connected with the low pressure cavity 34 of the rear stage pressure boosting cylinder, the number of the directional control valves is consistent with that of the pressure boosting cylinders, the pressure source 10 is connected with the proportional pressure valves 60, the pressure source 10 is respectively connected with the low pressure cavities 34 of each pressure boosting cylinder, the direction control valves are respectively arranged between the pressure source 10 and the low pressure cavities 34 of each pressure boosting cylinder, the hydraulic control check valves 70 are respectively arranged between the pressure source 10 and the non-front stage pressure boosting cylinder, the annular cavity 35 is connected with the corresponding directional control valve 35, the annular cavity 35 of the non-front stage pressure boosting cylinder is connected with the corresponding directional control valve, the annular cavity 35 is connected with the corresponding directional control valve, the non-stage pressure control valve 80, the non-stage pressure boosting valve is connected with the hydraulic pressure pipe 80, the non-stage pressure control valve is connected with the hydraulic pressure valve 80, and the pressure pipe is connected with the hydraulic pressure valve 80.
Specifically, the annular chamber 35 of the non-primary booster cylinder is connected to the control oil passage of the pilot operated check valve 70.
The supercharging system of this embodiment can use terminal pneumatic cylinder alone, also can link to use, when the terminal pneumatic cylinder alone is used, through with terminal pneumatic cylinder's direction control valve supply oil to terminal pneumatic cylinder's low pressure chamber 34, when needs high pressure ratio, through the linkage oil supply of each stage pneumatic cylinder, be fit for the pressure output of superhigh pressure stage.
The final pressure output cylinder is the final pressure output cylinder, all stages of pressure cylinders respectively control the front and back actions through corresponding direction control valves, all stages of pressure cylinders share one proportional pressure valve 60 to ensure pressure input, and a hydraulic control one-way valve 70 is arranged between the low pressure cavity 34 of the non-first stage pressure cylinder and the direction control valve to automatically isolate the influence of pressure generated when the non-first stage pressure cylinder acts on the corresponding direction control valve.
As an illustration, the tandem hydraulic pressure boost system of this embodiment includes two boost cylinders sequentially connected in series, namely, a first boost cylinder 20 and a second boost cylinder 30, two directional control valves are correspondingly provided, namely, a first directional control valve 40 and a second directional control valve 50, the pressure source 10, the first directional control valve 40 and the low pressure chamber 34 of the first boost cylinder 20 are sequentially connected, the annular chamber 35 of the first boost cylinder 20 is connected with the first directional control valve 40, the pressure source 10, the second directional control valve 50, the hydraulic control check valve 70 and the low pressure chamber 34 of the second boost cylinder 30 are sequentially connected, the annular chamber 35 of the second boost cylinder 30 is respectively connected with the second directional control valve 50 and the hydraulic control check valve 70, and the high pressure chamber 36 of the second boost cylinder 30 is connected with the fluid supplementing pipe 80.
Specifically, the annular chamber 35 of the second booster cylinder 30 is connected to the control oil passage of the pilot operated check valve 70.
In the present embodiment, the first booster cylinder 20 is a medium-pressure booster cylinder, and the second booster cylinder 30 is a high-pressure booster cylinder. The ratio of the first and second cylinders 20, 30 is typically between 3:1 and 5:1, and > 5:1 may be used if desired.
It will be appreciated that the junction of first and second cylinders 20, 30 is at a medium-high pressure (typically below 80 MPa), and that both the piping and valve components are easier and less expensive to implement than ultra-high pressure grade (typically above 150 MPa) components. Meanwhile, except for the final pressure output cavity (such as the high-pressure cavity 36 of the second booster cylinder 30) which may be oil or other mediums, hydraulic oil is communicated in the other cavities, so that the area range contacted with other mediums is effectively controlled and reduced, the loss of working elements is reduced, and the use cost is reduced.
In the present embodiment, the area of the low pressure chamber 34 of the first booster cylinder 20 is S 3 The area of the high-pressure chamber 36 of the first cylinder 20 is shown as S 4 Indicating the area S of the low pressure chamber 34 of the second booster cylinder 30 1 Indicated by S, the area of the high pressure chamber 36 of the second booster cylinder 30 is 2 And (3) representing.
When the second booster cylinder 30 is used alone, the pressure source 10 supplies oil to the low pressure chamber 34 of the second booster cylinder 30 through the second directional control valve 50 at a boost ratio S 1 :S 2 Is suitable for outputting the pressure at the stage below the medium and high pressure (generally below 60-80 MPa); when a high supercharging ratio is required, the second supercharging cylinder 30 is supplied with oil through the first supercharging cylinder 20, at which time the supercharging ratio is (S 3 :S 4 )*(S 1 :S 2 ) Is suitable for pressure output in the ultra-high pressure stage.
It will be appreciated that when the first pressure cylinder 20 is switched to supply oil to the low pressure chamber 34 of the second pressure cylinder 30, the pressure source 10 supplies oil to both the low pressure chamber 34 of the first pressure cylinder 20 and the low pressure chamber 34 of the second pressure cylinder 30, and when the pressure of the low pressure chamber 34 of the second pressure cylinder 30 > the pressure output by the pressure source 10 after being regulated by the proportional pressure valve 60, the hydraulic control check valve 70 automatically cuts off, so that the pressure output of the second pressure cylinder 30 is maintained stable.
By way of illustration, assuming a boost ratio of 3:1 for the first boost cylinder 20, 4:1 for the second boost cylinder 30, a total maximum boost ratio of 12:1, a piston 32 diameter of the first boost cylinder 20 and a piston 32 diameter of the second boost cylinder 30 of 280mm, a piston rod 33 diameter of the second boost cylinder 30 of 140mm, and a final pressure output volume of about 7.7L at 500mm of travel; assuming that the input pressure is 20MPa, when the pressure output is less than or equal to 80MPa, the oil pump directly supplies oil to the second booster cylinder 30, when the pressure output is more than 80MPa, the pressure source 10 supplies oil to the first booster cylinder 20, the second booster cylinder 30 is subjected to secondary booster after boosting, and the maximum output pressure is 240MPa; regardless of where the second boost cylinder 30 is to switch the first boost cylinder 20 to supply oil, the remaining volume of the high pressure chamber 36 of the second boost cylinder 30 can be used in the subsequent boost process, without unreasonable pressure and output volume distribution; when the first booster cylinder 20 supplies oil to the low pressure cavity 34 of the second booster cylinder 30, the oil pressure of the low pressure cavity 34 of the second booster cylinder 30 is about 20MPa, the low pressure cavity 34 of the first booster cylinder 20 and the low pressure cavity 34 of the second booster cylinder 30 can be simultaneously supplied by the pressure source 10 in the switching oil supply stage, the stability of the output pressure of the second booster cylinder 30 is maintained, and the high and low pressure parallel type booster cylinders are maintained, and the pressure output of the two-stage booster cylinders firstly drops and rises due to the large difference of the boost ratio during switching, so that the switching pressure greatly fluctuates.
The tandem hydraulic booster system of the embodiments of the present invention has the following advantages,
the first hydraulic pressurizing system and the serial hydraulic pressurizing system comprise at least two pressurizing cylinders which are sequentially connected in series, the tail end pressurizing cylinder is a final pressure output cylinder, namely, the final output cylinder of the serial hydraulic pressurizing system is only one stage, the number of ultrahigh pressure fluid supplementing valves, isolating valves and unloading valves can be greatly reduced or canceled, compared with the two-stage pressurizing cylinder high-pressure ends of a high-low pressure parallel system, the ultrahigh pressure one-way valve 90 is required to be arranged for isolating, the ultrahigh pressure unloading valve is also required to be arranged at the high-pressure end of the high-pressure stage pressurizing cylinder, the serial hydraulic pressurizing system can be canceled, the leakage point, the cost and the action control difficulty of the pressurizing system can be effectively reduced, meanwhile, the final output cavity is only one stage, and the utilization rate can be improved to 100%.
The boost ratio of the boost cylinders of each level such as the boost ratio of the second and serial hydraulic boost systems is multiplied, so that the boost ratio of the boost cylinders of each level can be increased to a larger boost ratio under the condition that the boost ratio of the boost cylinders of each level is smaller, when the boost ratio of the boost cylinders is smaller, the diameter of a piston rod 33 of the boost cylinder is not too small, and the volume of the tail end boost cylinder is easily increased in a stroke increasing mode.
Referring to fig. 1, in some embodiments, the tandem hydraulic booster system further includes a sampling circuit (not shown) including a pressure sensor (voltage type or current type) (not shown), a multi-channel current amplifier (not shown), an analog-to-digital converter (not shown), and a reference power supply (not shown), the pressure sensor is provided with a plurality of pressure sensors, the plurality of pressure sensors are respectively connected with an input end of the proportional pressure valve 60 and a high-pressure chamber 36 of each stage of booster cylinder in a one-to-one correspondence manner, the multi-channel current amplifier and the analog-to-digital converter are respectively provided with a plurality of input ends and output ends, the output end of each pressure sensor is respectively connected with the plurality of input ends of the analog-to-digital converter in a one-to-one correspondence manner, the output end of the analog-to-digital converter is connected with the input end of the multi-channel current amplifier in a one-to-one correspondence manner, the reference power supply is connected with the power supply input end of the analog-to-digital converter, the output end of the multi-channel current amplifier is connected with the input end of the proportional pressure valve 60, the input pressure of the pressure source 10 and the output pressure of each stage of booster cylinders are obtained through the setting sampling circuit, then the opening degree of the proportional pressure valve 60 is regulated according to the target output pressure and the input pressure of the pressure source 10, accurate pressure regulation can be realized through digital processing and control, and flexible parameter adjustment and optimization can be carried out according to actual requirements. Meanwhile, due to the characteristic of digital control, remote monitoring and control can be realized, and the convenience and operability of the system are improved.
It will be appreciated that the pressure sensor is of the voltage or current type, and that when the pressure sensor is of the voltage type, the reference power source is a voltage source, and when the pressure sensor is of the current type, the reference power source is a current source.
Alternatively, the pressure sensor (voltage type) is model KS-N-E-E-B25D-M-V or PT9551.
Alternatively, the multi-channel current amplifier is model YH-DA1A-2 or RW-AMP-01.
Optionally, the analog-to-digital converter is of the type H3U or CP1H.
The foregoing description is only of the preferred embodiments of the present invention and is not intended to limit the scope of the invention, and all equivalent structural changes made by the description of the present invention and the accompanying drawings or direct/indirect application in other related technical fields are included in the scope of the invention.
Claims (8)
1. The utility model provides a serial-type hydraulic pressure booster system, its characterized in that includes pressure source, pneumatic cylinder and directional control valve, the pneumatic cylinder is provided with two at least, two more the pneumatic cylinder is established ties in proper order, the pneumatic cylinder includes cylinder, piston and piston rod, the piston sets up the tip of piston rod, the piston with the piston rod sets up in the cylinder, and will the inner chamber of cylinder is divided into low pressure chamber, annular chamber and high pressure chamber, in two adjacent pneumatic cylinders, the high pressure chamber of preceding stage pneumatic cylinder is connected with the low pressure chamber of succeeding stage pneumatic cylinder, and the quantity of directional control valve is unanimous with the quantity of pneumatic cylinder, the pressure source is connected with proportional pressure valve, the pressure source is connected with the low pressure chamber of each pneumatic cylinder respectively, just all be provided with directional control valve between the low pressure chamber of pressure source and each pneumatic cylinder, all be provided with the pilot operated check valve between the pneumatic cylinder and the non-first stage pneumatic cylinder, the annular chamber of non-first stage pneumatic cylinder is connected with corresponding directional control valve, and the annular chamber of non-first stage pneumatic cylinder is connected with corresponding directional control valve respectively with the directional control valve and the last stage pneumatic cylinder and the hydraulic pressure control valve, the hydraulic pressure valve is connected with the high-pressure valve on the hydraulic pressure pipe.
2. The tandem hydraulic pressure boost system of claim 1, wherein the number of boost cylinders is two, and the number of directional control valves is first directional control valve and second directional control valve, and the pressure source, the first directional control valve and the low pressure chamber of first boost cylinder are connected in proper order, and the annular chamber of first boost cylinder is connected with the first directional control valve, and the pressure source, the second directional control valve, the hydraulically controlled check valve and the low pressure chamber of second boost cylinder are connected in proper order, and the annular chamber of second boost cylinder is connected with the second directional control valve and hydraulically controlled check valve respectively, and the high pressure chamber of second boost cylinder is connected with the fluid replacement pipeline.
3. The tandem hydraulic boost system of claim 2, wherein the first boost cylinder is a medium pressure boost cylinder and the second boost cylinder is a high pressure boost cylinder.
4. The tandem hydraulic charging system of claim 3, wherein the boost ratio of the first boost cylinder is 3:1 and the boost ratio of the second boost cylinder is 4:1.
5. The serial hydraulic boosting system according to claim 1, further comprising a sampling circuit, wherein the sampling circuit comprises a pressure sensor, a multi-channel current amplifier, an analog-to-digital converter and a reference power supply, the pressure sensor is provided with a plurality of pressure sensors, the pressure sensors are respectively connected with the input end of the proportional pressure valve and the high-pressure cavity of each stage of booster cylinder in a one-to-one correspondence manner, the multi-channel current amplifier and the analog-to-digital converter are respectively provided with a plurality of input ends and output ends, the output end of each pressure sensor is respectively connected with the plurality of input ends of the analog-to-digital converter in a one-to-one correspondence manner, the output end of the multi-channel current amplifier is connected with the input end of the proportional pressure valve, and the reference power supply is connected with the power supply input end of the analog-to-digital converter.
6. The tandem hydraulic booster system of claim 5, wherein the pressure sensor is of the type KS-N-E-B25D-M-V or PT9551.
7. The tandem hydraulic boosting system according to claim 5, wherein said multi-channel current amplifier is model number YH-DA1A-2 or RW-AMP-01.
8. The tandem hydraulic boosting system according to claim 5, wherein said analog-to-digital converter is of the type H3U or CP1H.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311558108.8A CN117605719B (en) | 2023-11-21 | 2023-11-21 | Tandem type hydraulic pressurizing system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311558108.8A CN117605719B (en) | 2023-11-21 | 2023-11-21 | Tandem type hydraulic pressurizing system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN117605719A true CN117605719A (en) | 2024-02-27 |
| CN117605719B CN117605719B (en) | 2024-10-15 |
Family
ID=89945631
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311558108.8A Active CN117605719B (en) | 2023-11-21 | 2023-11-21 | Tandem type hydraulic pressurizing system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN117605719B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117605718A (en) * | 2023-11-21 | 2024-02-27 | 佛山市康思达液压机械有限公司 | Variable boost ratio hydraulic boost system and control method |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20040129255A1 (en) * | 2003-01-08 | 2004-07-08 | Stuhldreher Mark Spencer | Hydraulically intensified high pressure fuel system for common rail application |
| KR20090038560A (en) * | 2007-10-16 | 2009-04-21 | 강원대학교산학협력단 | With the raising pressure pump the wheel washing system which uses raising pressure pump |
| CN201501119U (en) * | 2009-09-10 | 2010-06-09 | 郑州人造金刚石及制品工程技术研究中心有限公司 | A continuous pressurizing hydraulic control system of cubic press pressurizer |
| WO2012143601A1 (en) * | 2011-04-21 | 2012-10-26 | Wärtsilä Finland Oy | Fluid system and internal combustion engine |
| US20130098628A1 (en) * | 2011-10-19 | 2013-04-25 | Cameron International Corporation | Subsea pressure reduction system |
| US20160354962A1 (en) * | 2014-03-11 | 2016-12-08 | Shao-Yang Hung | Two-stage hydraulic booster device for a mold functional component |
| CN106449872A (en) * | 2016-09-28 | 2017-02-22 | 安徽鼎晖新能源科技有限公司 | Automatically controlled CIGS flexible battery piece cutting mechanism |
| CN106523323A (en) * | 2015-09-11 | 2017-03-22 | 自贡通达机器制造有限公司 | Hydraulic main unit cylinder without piston rod for connection and hydraulic compressor |
| CN217107617U (en) * | 2021-12-27 | 2022-08-02 | 常州合卓机电科技有限公司 | Novel pressure boost return circuit |
-
2023
- 2023-11-21 CN CN202311558108.8A patent/CN117605719B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20040129255A1 (en) * | 2003-01-08 | 2004-07-08 | Stuhldreher Mark Spencer | Hydraulically intensified high pressure fuel system for common rail application |
| KR20090038560A (en) * | 2007-10-16 | 2009-04-21 | 강원대학교산학협력단 | With the raising pressure pump the wheel washing system which uses raising pressure pump |
| CN201501119U (en) * | 2009-09-10 | 2010-06-09 | 郑州人造金刚石及制品工程技术研究中心有限公司 | A continuous pressurizing hydraulic control system of cubic press pressurizer |
| WO2012143601A1 (en) * | 2011-04-21 | 2012-10-26 | Wärtsilä Finland Oy | Fluid system and internal combustion engine |
| US20130098628A1 (en) * | 2011-10-19 | 2013-04-25 | Cameron International Corporation | Subsea pressure reduction system |
| US20160354962A1 (en) * | 2014-03-11 | 2016-12-08 | Shao-Yang Hung | Two-stage hydraulic booster device for a mold functional component |
| CN106523323A (en) * | 2015-09-11 | 2017-03-22 | 自贡通达机器制造有限公司 | Hydraulic main unit cylinder without piston rod for connection and hydraulic compressor |
| CN106449872A (en) * | 2016-09-28 | 2017-02-22 | 安徽鼎晖新能源科技有限公司 | Automatically controlled CIGS flexible battery piece cutting mechanism |
| CN217107617U (en) * | 2021-12-27 | 2022-08-02 | 常州合卓机电科技有限公司 | Novel pressure boost return circuit |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117605718A (en) * | 2023-11-21 | 2024-02-27 | 佛山市康思达液压机械有限公司 | Variable boost ratio hydraulic boost system and control method |
Also Published As
| Publication number | Publication date |
|---|---|
| CN117605719B (en) | 2024-10-15 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN117605719B (en) | Tandem type hydraulic pressurizing system | |
| SU665788A3 (en) | Method and apparatus for control of the system of at least two series-arranged cylinders | |
| CN112797037B (en) | Continuous pressurization system with adjustable pressurization rate and control method thereof | |
| CN108331589A (en) | A kind of shield machine propulsion energy-saving control system | |
| CN109958674B (en) | Automatic compensation control device and method for back pressure of push shovel of compression type garbage truck | |
| CN109175183B (en) | Hybrid power hydraulic transmission system and method of large-scale swage hydraulic press | |
| CN106627541B (en) | Active hydraulic braking system of automobile | |
| WO2019184098A1 (en) | High-efficiency transmission free forging hydraulic machine and operation method therefor | |
| CN109248981B (en) | Accumulator flow and pressure dynamic compensation control system | |
| CN205298095U (en) | Supercharged oil cylinder | |
| CN201313410Y (en) | Hydraulic control device with groups of hydraulic cushions working integrally of hydraulic machine | |
| CN212225635U (en) | Pressurizing oil cylinder | |
| CN104819840A (en) | Dual-pressurization cylinder test bench | |
| CN111255755A (en) | Energy accumulator pressure dynamic adjusting system and method based on gas-liquid linkage cylinder | |
| CN117605718A (en) | Variable boost ratio hydraulic boost system and control method | |
| CN207226900U (en) | A kind of servo bracing members prestressing force classification application system of frequency control | |
| CN221683301U (en) | Double-acting hydraulic control reciprocating supercharger | |
| CN217271085U (en) | Main jacking oil cylinder accelerating device of spiral pipe jacking machine | |
| CN213775871U (en) | Ultrahigh pressure boosting oil cylinder | |
| CN205937256U (en) | Shunt booster in step | |
| CN219035175U (en) | Supporting promotion of moving workbench presss from both sides tight oil piping system | |
| CN209838823U (en) | Oil cylinder with built-in quick and pressurizing functions | |
| CN220302436U (en) | Logistics trailer lifting synchronous hydraulic system | |
| CN109268340B (en) | Matrix type multipath input/output integrated control valve block | |
| CN109854952B (en) | Gas pressure adjusting method |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant |