CN117605718A - Variable boost ratio hydraulic boost system and control method - Google Patents
Variable boost ratio hydraulic boost system and control method Download PDFInfo
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- CN117605718A CN117605718A CN202311558098.8A CN202311558098A CN117605718A CN 117605718 A CN117605718 A CN 117605718A CN 202311558098 A CN202311558098 A CN 202311558098A CN 117605718 A CN117605718 A CN 117605718A
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- 238000000034 method Methods 0.000 title claims abstract description 18
- 230000001105 regulatory effect Effects 0.000 claims abstract description 17
- 238000005070 sampling Methods 0.000 claims description 16
- 230000001276 controlling effect Effects 0.000 abstract description 4
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 229910000510 noble metal Inorganic materials 0.000 description 1
- 229910052709 silver Inorganic materials 0.000 description 1
- 239000004332 silver Substances 0.000 description 1
- 239000007779 soft material Substances 0.000 description 1
Classifications
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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
- 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
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- Fluid Mechanics (AREA)
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- General Engineering & Computer Science (AREA)
- Control Of Fluid Pressure (AREA)
Abstract
The invention is suitable for the field of hydraulic systems, and discloses a variable boost ratio hydraulic boost system and a control method, wherein the variable boost ratio hydraulic boost system comprises a first pressure source, a second pressure source and a boost cylinder, the boost cylinder comprises a cylinder barrel, a piston and a piston rod, the piston is arranged at the end part of the piston rod, the piston and the piston rod are arranged in the cylinder barrel and divide the inner cavity of the cylinder barrel into a low pressure cavity, a pressure regulating cavity and a high pressure cavity, the first pressure source is connected with the low pressure cavity through a first pipeline, a direction control valve is arranged between the first pressure source and the low pressure cavity, the first pressure source is connected with the first proportional pressure valve, the second pressure source is connected with the pressure regulating cavity through a second pipeline, the second pressure source is connected with the second proportional pressure valve, a one-way valve is arranged between the pressure regulating cavity and the direction control valve, the system realizes the variable boost ratio of the boost system through controlling the input of the first pressure source and the input of the second pressure source, and the boost ratio adjusting range is wider.
Description
Technical Field
The invention relates to the field of hydraulic systems, in particular to a variable-boost-ratio hydraulic boosting system and a control method.
Background
The boost cylinder boost ratio is generally fixed and may be referred to as a hard boost ratio. As shown in FIG. 3, S 1’ Is the effective acting area of a piston of a low-pressure input cavity, S 2’ Is delivered under high pressureThe effective acting area of the cavity-outlet pressurizing rod is calculated according to the formula P 1’ *S 1’ ＝P 2’ *S 2’ Supercharging ratio=s 1’ :S 2’ ＝P 2’ :P 1’ . Once the boost cylinder is determined, the hard boost ratio may not be changed. P (P) 2’ The minimum controllable range of (2) is P 1 Is the minimum boost ratio. Along with the development of process technology and the popularization and application of internal high-pressure forming technology, the forming pressure requirement is higher and higher, the current common requirement is more than 150-200 MPa, the supercharging ratio of a booster cylinder is more than 10:1, the adjustment dead zone of a conventional proportional pressure valve is about 2MPa, namely the minimum value of the output pressure of the booster cylinder is about 20 MPa. The influence of the pressure range on the internal high-pressure forming process of common conventional materials is not too large, but for some soft materials (such as noble metals, silver, thin-wall soft copper and the like), the initial expansion pressure is generally less than 20MPa, so that blanks are easily directly in a large deformation stage, even if a high-precision proportional pressure valve is adopted, the matching of a pressure curve and a material bulging route is difficult to ensure, the rejection rate is increased, and the production cost of products is increased.
For some composite processes, manufacturers often require output pressure control accuracy at the initial stage to be within 1MPa, and the total pressure output ranges from 10MPa to 20MPa at low pressure to more than 100MPa at high pressure. The solution at this time is to add a group of low-boost-ratio boost cylinders or find some proportional pressure valves with ultrahigh control accuracy. In either case, the equipment manufacturing cost and difficulty in controlling the pressure accuracy of the system are increased.
Accordingly, there is a need for improvement and development in the art.
Disclosure of Invention
A first object of the present invention is to provide a variable-ratio hydraulic pressure-increasing system that realizes a variable pressure-increasing ratio of the pressure-increasing system by controlling the input of the first pressure source and the input of the second pressure source, and that has a wider adjustment range of the pressure-increasing ratio.
In order to achieve the above purpose, the invention provides the following scheme:
the utility model provides a variable pressure ratio hydraulic pressure booster system, includes first pressure source, second pressure source and pneumatic cylinder, 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, pressure regulation chamber and high pressure chamber, first pressure source with the low pressure chamber passes through first pipeline connection, just first pressure source with be provided with the directional control valve between the low pressure chamber, first pressure source is connected with first proportional pressure valve, the second pressure source with pressure regulation chamber passes through the second pipeline connection, the second pressure source is connected with second proportional pressure valve, pressure regulation chamber with be provided with the check valve between the directional control valve.
Preferably, the supercharging system outputs a pressure value P 2 Is expressed as:
P 2 ＝(P 1 *S 1 -P 3 *S 3 )/S 2
wherein P is 1 Representing the input pressure value, P, of the low pressure chamber 3 Representing the input pressure value of the pressure regulating chamber S 1 Representing the area of the low pressure chamber, S 2 Represents the area of the high pressure chamber, S 3 Representing the area of the pressure regulating chamber.
Preferably, the input end of the first proportional pressure valve is provided with a first pressure sensor.
Preferably, the input end of the second proportional pressure valve is provided with a second pressure sensor.
Preferably, the output end of the high-pressure cavity is provided with a third pressure sensor.
Preferably, the input end of the first proportional pressure valve and the input end of the second proportional pressure valve are respectively connected with a sampling circuit, the sampling circuit comprises a fourth pressure sensor, a current amplifier, an analog-to-digital converter and a reference power supply, the output end of the fourth pressure sensor is connected with the input end of the analog-to-digital converter, the output end of the analog-to-digital converter is connected with the input end of the current amplifier, the reference power supply is connected with the power input end of the analog-to-digital converter, the fourth pressure sensor of the sampling circuit connected with the first proportional pressure valve is connected with the input end of the first proportional pressure valve, the output end of the current amplifier of the sampling circuit connected with the first proportional pressure valve is connected with the input end of the first proportional pressure valve, and the fourth pressure sensor of the sampling circuit connected with the second proportional pressure valve is connected with the output end of the current amplifier of the sampling circuit connected with the second proportional pressure valve is connected with the input end of the second proportional pressure valve.
A second object of the present invention is to provide a variable boost ratio hydraulic boost control method including: obtaining a function formula of an output pressure value of the supercharging system and a target output pressure value; substituting the target output pressure into a function of the output pressure value of the pressurizing system, and calculating to obtain the input pressure of the low-pressure cavity and the input pressure of the pressure regulating cavity; and adjusting the opening of the first proportional pressure valve according to the calculated input pressure of the low-pressure cavity and the pressure value of the first pressure source, and adjusting the opening of the second proportional pressure valve according to the calculated input pressure of the pressure regulating cavity and the pressure value of the second pressure source so as to enable the output pressure value of the high-pressure cavity to be equal to the target output pressure value.
Preferably, after adjusting the opening degree of the first proportional pressure valve and the opening degree of the second proportional pressure valve, further comprising: and periodically acquiring the real-time pressure of the high-pressure cavity, and finely adjusting the opening of the first proportional pressure valve and the opening of the second proportional pressure valve according to the real-time pressure of the high-pressure cavity so that the output pressure value of the high-pressure cavity is equal to the target output pressure value.
In this scheme, separate the inner chamber of pneumatic cylinder into low pressure chamber, pressure regulation chamber and high pressure chamber to be provided with the first pressure source of being connected with low pressure chamber and the second pressure source of being connected with pressure regulation chamber, under the condition of not changing the hard pressure ratio of pneumatic cylinder, add regulation pressure chamber input pressure and low pressure chamber input pressure together form soft pressure ratio through the system control, utilize soft pressure ratio to play the output pressure in actual control high pressure chamber, thereby can widen the pressure ratio adjustment scope of booster system, can realize the condition that pressure ratio is < 1 even under the condition of hard pressure ratio > > 1.
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 diagram of a variable boost ratio hydraulic boost system provided by an embodiment of the present invention;
fig. 2 is a flowchart of a variable boost ratio hydraulic boost control method provided by an embodiment of the invention.
Fig. 3 is a prior art supercharging system.
Reference numerals illustrate:
10. a first pressure source; 20. a second pressure source; 30. a pressurizing cylinder; 31. a cylinder; 32. a piston; 33. a piston rod; 34. a low pressure chamber; 35. a pressure regulating chamber; 36. a high pressure chamber; 40. a directional control valve; 50. a first proportional pressure valve; 60. a second proportional pressure valve; 70. a one-way valve; 80. a first pipe; 90. and a second pipe.
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, which is a variable boost ratio hydraulic boost system of one embodiment of the present invention.
Referring to fig. 1, the variable supercharging ratio hydraulic supercharging system of the embodiment of the present invention includes a first pressure source 10, a second pressure source 20 and a supercharging cylinder 30, the supercharging cylinder 30 includes a cylinder tube 31, a piston 32 and a piston rod 33, the piston 32 is disposed at an end of the piston rod 33, the piston 32 and the piston rod 33 are disposed in the cylinder tube 31 and divide an inner cavity of the cylinder tube 31 into a low pressure chamber 34, a pressure adjusting chamber 35 and a high pressure chamber 36, the first pressure source 10 is connected with the low pressure chamber 34 through a first pipe 80, a directional control valve 40 is disposed between the first pressure source 10 and the low pressure chamber 34, the first pressure source 10 is connected with a first proportional pressure valve 50, the second pressure source 20 is connected with the pressure adjusting chamber 35 through a second pipe 90, the second pressure source 20 is connected with a second proportional pressure valve 60, and a check valve 70 is disposed between the pressure adjusting chamber 35 and the directional control valve 40.
As can be appreciated, the boost system output pressure value P 2 Is expressed as: p (P) 2 ＝(P 1 *S 1 -P 3 *S 3 )/S 2 In which, in the process,P 1 representing the input pressure value, P, of the low pressure chamber 34 3 Representing the input pressure value of the pressure regulating chamber 35, S 1 Representing the area of the low pressure chamber 34, S 2 Representing the area of the high pressure chamber 36, S 3 Representing the area of the pressure regulating chamber 35. P (P) 3 Is a system adjustable term for a fixed booster cylinder 30 by adjusting P 1 And P 3 Can reach the pressure output P actually needed 2 . Assume that the hard boost ratio of boost cylinder 30 is 10:1, S 1 :S 2 ＝10，S 3 :S 2 When the maximum boost ratio output is required, let P be =9 3 =0, boost ratio of boost cylinder 30 is S 1 :S 2 =10:1, i.e. P 2 ＝10*P 1 The method comprises the steps of carrying out a first treatment on the surface of the When P 3 ＝P 1 When the supercharging ratio is (S 1 -S 3 ):S 2 =1:1, i.e. P 2 ＝P 1 The method comprises the steps of carrying out a first treatment on the surface of the When P 3 ＝1.1*P 1 At the time of the pressure boost ratio
＝(S 1 -1.1*S 3 ):S 2 =1:10, i.e. P 2 ＝0.1*P 1 The method comprises the steps of carrying out a first treatment on the surface of the By adjusting different P 3 The value can achieve the effect of adjusting the soft pressure ratio of the pressure cylinder 30, and the adjustment range is large, even the hard pressure ratio can be achieved>>The case of 1 realizes the case of a supercharging ratio < 1. At the moment, even if the dead zone of the conventional proportional pressure valve is 2MPa, the minimum output pressure can meet the condition that the dead zone is less than or equal to 2MPa, and the working condition requirement of the control precision within 20MPa is met.
The variable boost ratio hydraulic boost system of the embodiment of the invention divides the inner cavity of the boost cylinder 30 into the low pressure cavity 34, the pressure adjusting cavity 35 and the high pressure cavity 36, and is provided with the first pressure source 10 connected with the low pressure cavity 34 and the second pressure source 20 connected with the pressure adjusting cavity 35, under the condition that the hard boost ratio of the boost cylinder 30 is not changed, the soft boost ratio is formed by adding and adjusting the input pressure of the pressure cavity and the input pressure of the low pressure cavity 34 through the system control, the output pressure of the high pressure cavity 36 is actually controlled by utilizing the soft boost ratio, so that the boost ratio adjustment range of the boost system can be widened, and even under the condition that the hard boost ratio is >1, the boost ratio is smaller than 1.
Referring to fig. 1, in some embodiments, the input end of the first proportional pressure valve 50 is provided with a first pressure sensor (not shown), and the output pressure of the first pressure source 10 can be monitored and controlled by the first pressure sensor, so that the hydraulic system can maintain stable pressure during working, and can be regulated and controlled according to actual requirements, so as to improve the performance and reliability of the system.
Similarly, the input end of the second proportional pressure valve 60 is provided with a second pressure sensor (not shown), and the output pressure of the second pressure source 20 can be monitored and controlled by the second pressure sensor, so that the hydraulic system can be ensured to maintain stable pressure in the working process, and can be regulated and controlled according to actual requirements, so that the performance and reliability of the system are improved.
Further, the output end of the high pressure chamber 36 is provided with a third pressure sensor (not shown), by which the output pressure value of the high pressure chamber 36 (i.e. the output pressure value of the supercharging system) is monitored.
Referring to fig. 1, in some embodiments, the sampling circuit (not shown) includes a fourth pressure sensor (not shown), a current amplifier (not shown), an analog-to-digital converter (not shown) and a reference power supply (not shown), the fourth pressure sensor is connected to the input end of the first proportional pressure valve 50, the output end of the fourth pressure sensor is connected to the input end of the analog-to-digital converter, the output end of the analog-to-digital converter is connected to the input end of the current amplifier, the output end of the current amplifier is connected to the input end of the first proportional pressure valve 50, the reference power supply is connected to the power supply input end of the analog-to-digital converter, the input pressure of the first pressure source 10 is obtained by setting the sampling circuit, and then the opening degree of the first proportional pressure valve 50 is adjusted according to the target output pressure and the input pressure of the first pressure source 10. 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.
Similarly, the input end of the second proportional pressure valve 60 is also provided with a sampling circuit, which is specifically structured as described above, and is different from the point that the fourth pressure sensor is connected with the input end of the second proportional pressure valve 60, the output end of the current amplifier is connected with the input end of the second proportional pressure valve 60, the input pressure of the second pressure source 20 is obtained by setting the sampling circuit, and then the opening of the second proportional pressure valve 60 is adjusted according to the target output pressure and the input pressure of the second pressure source 20.
It will be appreciated that if the input of the first proportional pressure valve 50 is provided with a sampling circuit, no pressure sensor need be provided.
Referring to fig. 2, the embodiment of the invention further provides a variable boost ratio hydraulic boost control method, which includes:
s101, obtaining a functional formula of an output pressure value of a supercharging system and a target output pressure value;
s102, substituting the target output pressure into a function of an output pressure value of the pressurizing system, and calculating to obtain the input pressure of the low-pressure cavity 34 and the input pressure of the pressure regulating cavity 35;
s103, adjusting the opening of the first proportional pressure valve 50 according to the calculated input pressure of the low pressure chamber 34 and the calculated pressure value of the first pressure source 10, and adjusting the opening of the second proportional pressure valve 60 according to the calculated input pressure of the pressure adjusting chamber 35 and the calculated pressure value of the second pressure source 20 so that the output pressure value of the high pressure chamber 36 is equal to the target output pressure value.
Further, in order to achieve high control accuracy, to avoid that the output pressure value of the high pressure chamber 36 deviates from the target output pressure value due to the interference of the system during long-time operation, the variable boost ratio hydraulic boost control method further includes: and S104, periodically acquiring the real-time pressure of the high-pressure cavity 36, and finely adjusting the opening of the first proportional pressure valve 50 and the opening of the second proportional pressure valve 60 according to the real-time pressure of the high-pressure cavity 36 so that the output pressure value of the high-pressure cavity 36 is equal to the target output pressure value.
In this scheme, the input pressure of the low-pressure chamber 34 and the input pressure of the pressure adjusting chamber 35 are calculated according to the function formula of the output pressure value of the supercharging system and the target output pressure value, and the supercharging ratio of the supercharging system is variable by controlling the input of the first pressure source 10 and the input of the second pressure source 20, so that the supercharging ratio adjustment range of the supercharging system can be widened, and even the situation that the supercharging ratio is less than 1 can be realized under the condition that the hard supercharging ratio is > 1.
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 variable pressure ratio hydraulic pressure booster system, its characterized in that includes first pressure source, second pressure source and pneumatic cylinder, 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, pressure regulation chamber and high pressure chamber, first pressure source with the low pressure chamber passes through first pipeline connection, just first pressure source with be provided with the directional control valve between the low pressure chamber, first pressure source is connected with first proportional pressure valve, the second pressure source with pressure regulation chamber passes through second pipeline connection, the second pressure source is connected with second proportional pressure valve, pressure regulation chamber with be provided with the check valve between the directional control valve.
2. The variable boost ratio hydraulic boost system of claim 1, wherein the boost system outputs a pressure value P 2 Is expressed as:
P 2 ＝(P 1 *S 1 -P 3 *S 3 )/S 2
wherein P is 1 Representing the input pressure value, P, of the low pressure chamber 3 Representing the input pressure value of the pressure regulating chamber S 1 Representing the area of the low pressure chamber, S 2 Represents the area of the high pressure chamber, S 3 Representing the area of the pressure regulating chamber.
3. The variable boost ratio hydraulic boost system of claim 1, wherein the input of the first proportional pressure valve is provided with a first pressure sensor.
4. The variable boost ratio hydraulic boost system of claim 1, wherein the input of the second proportional pressure valve is provided with a second pressure sensor.
5. The variable boost ratio hydraulic boost system of claim 1, wherein the output of the high pressure chamber is provided with a third pressure sensor.
6. The variable boost ratio hydraulic boost system of claim 1, wherein the input of the first proportional pressure valve and the input of the second proportional pressure valve are each connected with a sampling circuit, the sampling circuits include a fourth pressure sensor, a current amplifier, an analog-to-digital converter, and a reference power source, the output of the fourth pressure sensor is connected with the input of the analog-to-digital converter, the output of the analog-to-digital converter is connected with the input of the current amplifier, the reference power source is connected with the power input of the analog-to-digital converter, the fourth pressure sensor of the sampling circuit connected with the first proportional pressure valve is connected with the input of the first proportional pressure valve, the output of the current amplifier of the sampling circuit connected with the first proportional pressure valve is connected with the input of the second proportional pressure valve, and the output of the sampling circuit connected with the second proportional pressure valve is connected with the input of the second proportional pressure valve.
7. A variable boost ratio hydraulic boost control method, characterized by comprising:
obtaining a function formula of an output pressure value of the supercharging system and a target output pressure value;
substituting the target output pressure into a function of the output pressure value of the pressurizing system, and calculating to obtain the input pressure of the low-pressure cavity and the input pressure of the pressure regulating cavity;
and adjusting the opening of the first proportional pressure valve according to the calculated input pressure of the low-pressure cavity and the pressure value of the first pressure source, and adjusting the opening of the second proportional pressure valve according to the calculated input pressure of the pressure regulating cavity and the pressure value of the second pressure source so as to enable the output pressure value of the high-pressure cavity to be equal to the target output pressure value.
8. The variable supercharging ratio hydraulic supercharging control method according to claim 7, characterized by further comprising, after adjusting the opening degree of the first proportional pressure valve and the opening degree of the second proportional pressure valve: and periodically acquiring the real-time pressure of the high-pressure cavity, and finely adjusting the opening of the first proportional pressure valve and the opening of the second proportional pressure valve according to the real-time pressure of the high-pressure cavity so that the output pressure value of the high-pressure cavity is equal to the target output pressure value.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311558098.8A CN117605718A (en) | 2023-11-21 | 2023-11-21 | Variable boost ratio hydraulic boost system and control method |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202311558098.8A CN117605718A (en) | 2023-11-21 | 2023-11-21 | Variable boost ratio hydraulic boost system and control method |
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| CN117605718A true CN117605718A (en) | 2024-02-27 |
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| CN202311558098.8A Pending CN117605718A (en) | 2023-11-21 | 2023-11-21 | Variable boost ratio hydraulic boost system and control method |
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN203532360U (en) * | 2013-11-14 | 2014-04-09 | 中联重科股份有限公司 | Hydraulic pressure boosting system |
| CN112483511A (en) * | 2020-12-08 | 2021-03-12 | 四川凌峰航空液压机械有限公司 | Variable pressure ratio hydraulic pressure boost test system |
| 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 |
| CN218717912U (en) * | 2022-11-03 | 2023-03-24 | 太原市鸿煷机械设备有限公司 | Accurate pressure control system in isostatic pressing machine pressure-increasing and pressure-reducing process |
| CN117605719A (en) * | 2023-11-21 | 2024-02-27 | 佛山市康思达液压机械有限公司 | Tandem type hydraulic pressurizing system |
-
2023
- 2023-11-21 CN CN202311558098.8A patent/CN117605718A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN203532360U (en) * | 2013-11-14 | 2014-04-09 | 中联重科股份有限公司 | Hydraulic pressure boosting system |
| CN112483511A (en) * | 2020-12-08 | 2021-03-12 | 四川凌峰航空液压机械有限公司 | Variable pressure ratio hydraulic pressure boost test system |
| 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 |
| CN218717912U (en) * | 2022-11-03 | 2023-03-24 | 太原市鸿煷机械设备有限公司 | Accurate pressure control system in isostatic pressing machine pressure-increasing and pressure-reducing process |
| CN117605719A (en) * | 2023-11-21 | 2024-02-27 | 佛山市康思达液压机械有限公司 | Tandem type hydraulic pressurizing system |
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