CN110778541A - Gas-liquid two-phase conversion high-energy storage density hydraulic accumulator - Google Patents
Gas-liquid two-phase conversion high-energy storage density hydraulic accumulator Download PDFInfo
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- CN110778541A CN110778541A CN201911078995.2A CN201911078995A CN110778541A CN 110778541 A CN110778541 A CN 110778541A CN 201911078995 A CN201911078995 A CN 201911078995A CN 110778541 A CN110778541 A CN 110778541A
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- gas
- temperature
- cylinder barrel
- piston
- hydraulic
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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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/04—Accumulators
- F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
- F15B1/24—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with rigid separating means, e.g. pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/042—Controlling the temperature of the fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/042—Controlling the temperature of the fluid
- F15B21/0423—Cooling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/042—Controlling the temperature of the fluid
- F15B21/0427—Heating
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids
Abstract
A gas-liquid two-phase conversion high-energy storage density hydraulic accumulator comprises a piston rod, a piston, a cylinder barrel and a temperature control device. The rod cavity is used for containing hydraulic oil, the rodless cavity is used for containing gas, a hydraulic oil port is formed in the wall of the cylinder barrel at one end of the rod cavity and connected with an external hydraulic system, the axis of the piston rod and the axis of the piston are of a hollow structure, an inflation hole is formed in one end of the piston rod extending out of the cylinder barrel, and the temperature control device is installed on the periphery of the cylinder barrel to enable the temperature of the gas in the cylinder barrel to be below the critical temperature of the gas. The gas-liquid two-phase conversion high-energy storage density hydraulic accumulator disclosed by the invention has the advantages that the charged gas is kept in a state slightly lower than the critical temperature, the gas is liquefied after being pressurized to a certain pressure, the volume is reduced, more hydraulic oil can be contained in a cylinder barrel for energy storage, the energy storage density of the accumulator is improved, the volume of the accumulator is reduced, the occupied space is saved, and the high-energy storage density hydraulic accumulator has important significance for saving the limited working space of mobile hydraulic equipment.
Description
Technical Field
The invention belongs to the field of hydraulic transmission and control, particularly relates to the field of hydraulic energy storage, and particularly relates to a gas-liquid two-phase conversion high-energy storage density hydraulic energy accumulator.
Background
A hydraulic accumulator is an energy storage device in a hydropneumatic system. The energy in the system is converted into compression energy or potential energy to be stored at a proper time, and when the system needs the energy, the compression energy or the potential energy is converted into hydraulic energy or air pressure and the like to be released, and the energy is supplied to the system again. When the system pressure is increased instantaneously, it can absorb the energy of the part to ensure the pressure of the whole system is normal.
The energy accumulator can be divided into a weight type, a spring type and a gas loading type according to the loading mode, and the gas loading type is most used at present. Gas-loaded accumulators are divided into gas-bag, gas-bottle and piston types. The piston type energy accumulator has oil-gas isolation, reliable operation and long service life, and is suitable for high-pressure and high-capacity energy storage.
The oil pressure of the existing piston type energy accumulator is equal to the gas pressure, the volume and the weight are large, the cost is also very high, along with the increase of the volume of the stored oil, the pressure is also increased, the pressure change of the stored oil is large, and the pressure change is also large when the oil is released. The existing piston type energy accumulator uses a piston to isolate oil liquid for storing energy from compressed gas, the gas is nitrogen, and the volume can be reduced only by compression and the gas cannot be liquefied. For example, if the volume of the energy storage oil is required to be 30L and the pressure variation range is 15-20MPa, the calculated required volume of the energy storage device is 190L and the external volume is 250L. If the mobile equipment uses the piston type energy accumulator to store energy, the large volume occupies large space of the mobile equipment, influences the sight line and has high cost.
Disclosure of Invention
The invention aims to provide a gas-liquid two-phase conversion high-energy storage density hydraulic energy accumulator, which reduces the volume of the prepared energy accumulator and saves the occupied working space by improving the energy storage density of the energy accumulator under the condition of meeting certain energy storage volume and pressure.
In order to achieve the above object, the technical solution of the present invention is as follows:
a gas-liquid two-phase conversion high-energy storage density hydraulic accumulator comprises a piston rod, a piston, a cylinder barrel and a temperature control device. The piston is arranged in the cylinder barrel, one end of the piston rod is fixed with the piston, the other end of the piston rod extends out of the cylinder barrel, the rod cavity is used for containing hydraulic oil, the rodless cavity is used for containing gas, a hydraulic oil port is formed in the wall of the cylinder barrel at one end of the rod cavity and used for being connected with a rod cavity and a hydraulic system outside the cylinder barrel, the axes of the piston rod and the piston are of a hollow structure, an inflation hole is formed in one end of the piston rod extending out of the cylinder barrel, and the inflation hole is communicated with the rodless cavity through the hollow. The temperature control device is arranged on the periphery of the cylinder barrel and used for regulating and controlling the temperature of the gas in the cylinder barrel so that the temperature of the gas in the cylinder barrel is below the critical temperature of the gas. When energy is stored, hydraulic oil outside the cylinder barrel enters the rod cavity through the hydraulic oil port, and when acting force of the hydraulic oil on the piston is larger than that of gas in the piston cavity on the piston, the piston compresses gas in the rodless cavity; when energy is released, the pressure of an external oil way is reduced, the acting force of gas in the rodless cavity on the piston is larger than that of hydraulic oil on the piston, the piston presses the hydraulic oil, and the hydraulic oil in the piston rod cavity is discharged from the hydraulic oil port and is supplied to an external hydraulic system for use.
Further, the temperature control device is a constant temperature device, the constant temperature device is used for keeping the temperature of the gas in the cylinder barrel at a set temperature, the set temperature is 1-2 ℃ lower than the critical temperature of the gas, and the gas can be liquefied only when the pressure of the gas is increased below the critical temperature.
Further, the constant temperature device is a heat exchanger, and when the temperature of the gas in the cylinder barrel is higher than the set temperature, cold water is introduced into the heat exchanger to dissipate the heat of the gas in the cylinder barrel; when the temperature of the gas in the cylinder barrel is lower than the set temperature, hot water is introduced into the heat exchanger to heat the gas in the cylinder barrel; when the gas temperature in the cylinder is equal to the set temperature, the heat exchanger is closed.
Further, the constant temperature device comprises a heating device and a cooling device, the heating device is a heat exchanger, the cooling device comprises a finned cooler and a cooling fan, and when the temperature of the gas in the cylinder barrel is higher than a set temperature, the cooling fan is started to blow the finned cooler to dissipate the heat of the gas in the cylinder barrel; when the temperature of the gas in the cylinder barrel is lower than the set temperature, hot water is introduced into the heat exchanger to heat the gas in the cylinder barrel; and when the temperature of the gas in the cylinder barrel is equal to the set temperature, the heating device and the cooling device are closed.
Further, the gas is CO
2Or other gases that can be liquefied and vaporized under pressure at operating temperatures.
Further, said CO
2The temperature of (a) is 29 to 31 ℃.
Compared with the prior art, the invention has the beneficial effects that:
the oil pressure of the existing piston type energy accumulator is equal to the gas pressure, the volume and the weight are large, the cost is also very high, along with the increase of the volume of the stored oil, the pressure is also increased, the pressure change of the stored oil is large, and the pressure change is also large when the oil is released. The gas-liquid two-phase conversion high-energy storage density hydraulic energy accumulator provided by the invention has the advantages that the charged gas is kept in a state slightly lower than the critical temperature, the gas is liquefied after being pressurized to a certain pressure and is changed into a liquid state, the volume is reduced, more hydraulic oil can be contained in a cylinder barrel for energy storage, the energy storage density of the energy accumulator is improved under the condition of meeting the required energy storage volume and pressure, the volume of the energy accumulator is reduced, the occupied space is saved, the cost of the energy accumulator is reduced, and the energy accumulator has important significance for saving the limited working space of mobile hydraulic equipment.
Drawings
Fig. 1 is a schematic structural diagram of a gas-liquid two-phase conversion high-energy storage density hydraulic accumulator in embodiment 1 of the present invention;
in fig. 1: 1. a piston rod; 2. a piston; 3. a cylinder barrel; 4. a heat exchanger; 5. a cooling fan; 6. a finned cooler; A. a hydraulic oil port; B. and (4) an air inflation hole.
Detailed Description
The invention is described in detail below with reference to the figures and the specific embodiments.
Example 1
As shown in figure 1, the gas-liquid two-phase conversion high-energy storage density hydraulic accumulator comprises a piston rod 1, a piston 2, a cylinder barrel 3 and a constant temperature device. Piston 2 dress is in cylinder 3, the one end of piston rod 1 and piston 2 are together fixed, the other end of piston rod 1 stretches out cylinder 3, there is the pole chamber to be used for holding hydraulic oil, no pole chamber is used for holding gas, it has hydraulic pressure hydraulic fluid port A to be located the jar bucket wall that has pole chamber one end, hydraulic pressure hydraulic fluid port A is used for being connected with pole chamber and the outside hydraulic system of cylinder, the axle center of piston rod 1 and piston 2 is hollow structure, the piston rod 1 one end that stretches out cylinder 3 has inflation hole B, inflation hole B communicates with each other through hollow structure and no pole chamber, constant temperature equipment is located cylinder 3 periphery, constant temperature equipment is used for making the gas temperature keep at the settlement temperature in the cylinder, should set for the temperature and be less than gaseous critical temperature 1 ~ 2 ℃, gaseous temperature only can liquefy below critical temperature gas pressure rise.
The thermostatic device can be a heat exchanger 4 alone, and when the temperature of the gas in the cylinder 3 is higher than the set temperature, cold water is introduced into the heat exchanger to dissipate the heat of the gas in the cylinder 3; when the temperature of the gas in the cylinder 3 is lower than the set temperature, hot water is introduced into the heat exchanger to heat the gas in the cylinder 3; when the temperature of the gas in the cylinder 3 is equal to the set temperature, the heat exchanger is turned off.
In addition, the thermostatic device can also be composed of a heating device and a cooling device, for example, the heating device is a heat exchanger 4, the cooling device comprises a finned cooler 6 and a cooling fan 5, when the temperature of the gas in the cylinder 3 is higher than the set temperature, the cooling fan 5 is started to blow the finned cooler to dissipate the heat of the gas in the cylinder, and the finned cooler 6 can increase the heat dissipation effect of the cooling fan 5; when the temperature of the gas in the cylinder 3 is lower than the set temperature, hot water is introduced into the heat exchanger 4 to heat the gas in the cylinder 3; when the temperature of the gas in the cylinder 3 is equal to the set temperature, the heating device and the cooling device are turned off.
Analyzing the stress of the piston rod 1 and the piston 2 in a steady state to obtain
In the formula:
d1-diameter (mm) of piston 2;
d2 — diameter (mm) of piston rod 1;
p 1-liquefaction pressure (MPa) of gas at set temperature;
p 2-Hydraulic oil pressure (MPa) to be stored.
According to the structure, the acting area of the hydraulic oil on the piston is smaller than that of the gas on the piston, the stored hydraulic oil pressure is higher than the critical pressure of the high-pressure gas, and the hydraulic energy storage density is higher. The diameter of the piston rod 1 is calculated according to the pressure of the hydraulic oil to be stored, the gas critical pressure and the selected diameter of the piston 2.
Before use, the gas is filled into the gas filling hole B, and the filling pressure is lower than the liquefaction pressure of the gas at the set temperature.
The liquid energy storage process is as follows:
the hydraulic oil from the outside enters the rod cavity through the hydraulic oil port A, when the downward acting force of the hydraulic oil on the piston 2 is greater than the upward acting force of the gas in the rodless cavity on the piston 2, the piston 2 moves downward, the gas in the rodless cavity is compressed, and the pressure is increased. When the gas pressure rises to the liquefaction pressure of the gas at the set temperature, the gas starts to liquefy, but the pressure is substantially constant, and the liquid converted from the gas flows into the bottom of the cylinder 3 or adheres to the inner wall of the cylinder 3. And hydraulic oil is continuously fed from the hydraulic oil port A, and the hydraulic pressure in the rod cavity is basically unchanged. If oil is continuously filled, the gas in the rodless cavity can be completely converted into liquid, and the volume of the rod cavity is the maximum volume capable of storing hydraulic oil.
The liquid energy release process is as follows:
when the pressure of the external oil way is reduced, the upward acting force of the gas in the rodless cavity on the piston 2 is larger than the downward acting force of the hydraulic oil on the piston 2, the piston 2 presses the hydraulic oil, and the hydraulic oil in the rod cavity is discharged from the hydraulic oil port A and is supplied to an external hydraulic system for use. When the pressure is lower than the vaporization pressure of the liquid, the liquid in the rodless cavity starts to vaporize, part of the liquid is converted into gas, the pressure of the gas in the rodless cavity is maintained to be basically unchanged, and the pressure of the oil discharged from the hydraulic port A is basically constant. When the liquid in the rodless chamber is totally vaporized into gas, the volume of oil discharged from the hydraulic oil port a is the maximum available oil volume.
In the process of liquid energy storage and liquid energy release, gas in the rodless cavity is in a gas-liquid two-phase transition state. Since the temperature of the gas is above its critical temperature, the pressure will not liquefy any more. Therefore, the temperature of the gas in the piston cavity is preferably slightly lower than the critical temperature of the gas, the temperature of the gas is not greatly changed, the pressure stored by the hydraulic oil is the largest under the working condition, the stored hydraulic energy is the largest under the same storage volume, and the pressure of the hydraulic oil in the storing and releasing processes is basically unchanged.
Example 2
Carbon dioxide (CO) is selected for use in this example
2) The critical temperature of the energy storage gas is about 31.2 ℃, and the critical pressure is 7.38 MPa. The liquefaction pressure is 7.05MPa when the temperature is 29 ℃; the liquefaction pressure was 7.21MPa at a temperature of 30 ℃. The temperature of the gas is required to be controlled between 29 and 31 ℃ in the working process.
If D1 is 300mm, the gas pressure p1 is 7MPa, the hydraulic oil pressure p2 is 20MPa, and D2 is 160mm as calculated from equation 1.
Through calculation, the maximum length of a piston cavity is required to be 870mm, the volume of the liquefied gas is 11L, the total volume of the energy accumulator is 82L, and the total volume of the energy accumulator is 123L when the piston rod extends out completely without hydraulic oil.
The volume of the gas-liquid two-phase conversion energy accumulator is only half of that of the existing piston type energy accumulator, the stored energy is more than that of the piston type energy accumulator, and the pressure change is small. The size and the cost of the energy accumulator are greatly reduced, and the energy accumulator has great significance for saving the limited working space of mobile hydraulic equipment.
Any gas-liquid two-phase conversion scheme, no matter which single gas or mixed gas is selected, no matter which temperature regulating device is adopted, no matter what temperature regulating device is adopted, is within the protection scope of the patent.
Claims (6)
1. A gas-liquid two-phase conversion high-energy storage density hydraulic accumulator is characterized by comprising a piston rod, a piston, a cylinder barrel and a temperature control device;
the piston is arranged in the cylinder barrel, one end of the piston rod is fixed with the piston, the other end of the piston rod extends out of the cylinder barrel, the rod cavity is used for containing hydraulic oil, the rodless cavity is used for containing gas, a hydraulic oil port is arranged on the wall of the cylinder barrel at one end of the rod cavity and is used for connecting the rod cavity with a hydraulic system outside the cylinder barrel, the axes of the piston rod and the piston are of a hollow structure, one end of the piston rod extending out of the cylinder barrel is provided with an inflation hole, and the inflation hole is communicated with the rodless cavity through the hollow structure;
the temperature control device is arranged on the periphery of the cylinder barrel and used for regulating and controlling the temperature of the gas in the cylinder barrel so that the temperature of the gas in the cylinder barrel is below the critical temperature of the gas;
when energy is stored, hydraulic oil outside the cylinder barrel enters the rod cavity through the hydraulic oil port, and when acting force of the hydraulic oil on the piston is larger than that of gas in the piston cavity on the piston, the piston compresses gas in the rodless cavity;
when energy is released, the pressure of an external oil way is reduced, the acting force of gas in the rodless cavity on the piston is larger than that of hydraulic oil on the piston, the piston presses the hydraulic oil, and the hydraulic oil in the piston rod cavity is discharged from the hydraulic oil port and is supplied to an external hydraulic system for use.
2. The hydraulic accumulator for high energy storage density through gas-liquid two-phase conversion as claimed in claim 1, wherein the temperature control device is a thermostat device for keeping the temperature of the gas in the cylinder at a set temperature 1-2 ℃ lower than the critical temperature of the gas.
3. The hydraulic accumulator of claim 2, wherein the thermostatic device is a heat exchanger, and when the temperature of the gas in the cylinder is higher than a predetermined temperature, cold water is introduced into the heat exchanger to dissipate the heat of the gas in the cylinder; when the temperature of the gas in the cylinder barrel is lower than the set temperature, hot water is introduced into the heat exchanger to heat the gas in the cylinder barrel; and when the temperature of the gas in the cylinder barrel is equal to the set temperature, closing the heat exchanger.
4. The hydraulic accumulator of claim 2, wherein the thermostat comprises a heating device and a cooling device, the heating device is a heat exchanger, the cooling device comprises a finned cooler and a cooling fan, and when the temperature of the gas in the cylinder is higher than a set temperature, the cooling fan is started to blow the finned cooler to dissipate the heat of the gas in the cylinder; when the temperature of the gas in the cylinder barrel is lower than the set temperature, hot water is introduced into the heat exchanger to heat the gas in the cylinder barrel; and when the temperature of the gas in the cylinder barrel is equal to the set temperature, the heating device and the cooling device are closed.
5. The gas-liquid two-phase conversion high energy storage density hydraulic accumulator of claim 1, wherein the gas is CO
2Or other gases that can be liquefied and vaporized under pressure at operating temperatures.
6. The gas-liquid two-phase conversion high energy storage density hydraulic accumulator of claim 1, wherein the CO is
2The temperature of (a) is 29 to 31 ℃.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911078995.2A CN110778541B (en) | 2019-11-07 | 2019-11-07 | Gas-liquid two-phase conversion high-energy storage density hydraulic accumulator |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911078995.2A CN110778541B (en) | 2019-11-07 | 2019-11-07 | Gas-liquid two-phase conversion high-energy storage density hydraulic accumulator |
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| CN110778541A true CN110778541A (en) | 2020-02-11 |
| CN110778541B CN110778541B (en) | 2022-02-08 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111765143A (en) * | 2020-07-20 | 2020-10-13 | 北京航天发射技术研究所 | High-speed actuator based on supercritical carbon dioxide |
| CN112780617A (en) * | 2021-01-25 | 2021-05-11 | 郑州东辰科技有限公司 | Carbon dioxide liquid-gas phase conversion actuator |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB647347A (en) * | 1947-07-03 | 1950-12-13 | Mini Of Supply | Improvements in or relating to energy accumulators utilising gas under pressure |
| US20110259442A1 (en) * | 2009-06-04 | 2011-10-27 | Mcbride Troy O | Increased power in compressed-gas energy storage and recovery |
| CN103518050A (en) * | 2011-01-14 | 2014-01-15 | 通用压缩股份有限公司 | Compressed gas storage and recovery system and method of operation systems |
| CN106286431A (en) * | 2016-10-18 | 2017-01-04 | 杨富刚 | A kind of energy storing structure |
| CN106763414A (en) * | 2016-12-16 | 2017-05-31 | 北京理工大学 | A kind of gas-liquid two-phase formula hydro-pneumatic spring |
-
2019
- 2019-11-07 CN CN201911078995.2A patent/CN110778541B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB647347A (en) * | 1947-07-03 | 1950-12-13 | Mini Of Supply | Improvements in or relating to energy accumulators utilising gas under pressure |
| US20110259442A1 (en) * | 2009-06-04 | 2011-10-27 | Mcbride Troy O | Increased power in compressed-gas energy storage and recovery |
| CN103518050A (en) * | 2011-01-14 | 2014-01-15 | 通用压缩股份有限公司 | Compressed gas storage and recovery system and method of operation systems |
| CN106286431A (en) * | 2016-10-18 | 2017-01-04 | 杨富刚 | A kind of energy storing structure |
| CN106763414A (en) * | 2016-12-16 | 2017-05-31 | 北京理工大学 | A kind of gas-liquid two-phase formula hydro-pneumatic spring |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111765143A (en) * | 2020-07-20 | 2020-10-13 | 北京航天发射技术研究所 | High-speed actuator based on supercritical carbon dioxide |
| CN112780617A (en) * | 2021-01-25 | 2021-05-11 | 郑州东辰科技有限公司 | Carbon dioxide liquid-gas phase conversion actuator |
| CN112780617B (en) * | 2021-01-25 | 2023-08-25 | 郑州东辰科技有限公司 | Carbon dioxide liquid-gas phase conversion actuator |
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| CN110778541B (en) | 2022-02-08 |
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