CN111412675A - Ultralow-temperature water vapor capture pump pipeline system using secondary refrigerant for cold storage - Google Patents
Ultralow-temperature water vapor capture pump pipeline system using secondary refrigerant for cold storage Download PDFInfo
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- CN111412675A CN111412675A CN202010268589.9A CN202010268589A CN111412675A CN 111412675 A CN111412675 A CN 111412675A CN 202010268589 A CN202010268589 A CN 202010268589A CN 111412675 A CN111412675 A CN 111412675A
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- 239000003507 refrigerant Substances 0.000 title claims abstract description 87
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Chemical compound O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 21
- 239000007788 liquid Substances 0.000 claims abstract description 42
- 238000005057 refrigeration Methods 0.000 claims abstract description 28
- 238000009833 condensation Methods 0.000 claims abstract description 14
- 230000005494 condensation Effects 0.000 claims abstract description 14
- 238000009825 accumulation Methods 0.000 claims abstract description 8
- 239000002826 coolant Substances 0.000 claims description 13
- 238000010257 thawing Methods 0.000 claims description 13
- 238000002955 isolation Methods 0.000 claims description 11
- 238000001035 drying Methods 0.000 claims description 5
- 238000010992 reflux Methods 0.000 claims description 5
- 238000001816 cooling Methods 0.000 abstract description 14
- 238000010438 heat treatment Methods 0.000 abstract description 12
- 238000001771 vacuum deposition Methods 0.000 abstract description 6
- 238000004781 supercooling Methods 0.000 abstract description 4
- 230000002035 prolonged effect Effects 0.000 abstract description 2
- 239000003921 oil Substances 0.000 description 12
- 230000000694 effects Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 239000007791 liquid phase Substances 0.000 description 3
- 239000012808 vapor phase Substances 0.000 description 3
- 239000010687 lubricating oil Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000012071 phase Substances 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D8/00—Cold traps; Cold baffles
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- C—CHEMISTRY; METALLURGY
- C23—COATING METALLIC MATERIAL; COATING MATERIAL WITH METALLIC MATERIAL; CHEMICAL SURFACE TREATMENT; DIFFUSION TREATMENT OF METALLIC MATERIAL; COATING BY VACUUM EVAPORATION, BY SPUTTERING, BY ION IMPLANTATION OR BY CHEMICAL VAPOUR DEPOSITION, IN GENERAL; INHIBITING CORROSION OF METALLIC MATERIAL OR INCRUSTATION IN GENERAL
- C23C—COATING METALLIC MATERIAL; COATING MATERIAL WITH METALLIC MATERIAL; SURFACE TREATMENT OF METALLIC MATERIAL BY DIFFUSION INTO THE SURFACE, BY CHEMICAL CONVERSION OR SUBSTITUTION; COATING BY VACUUM EVAPORATION, BY SPUTTERING, BY ION IMPLANTATION OR BY CHEMICAL VAPOUR DEPOSITION, IN GENERAL
- C23C14/00—Coating by vacuum evaporation, by sputtering or by ion implantation of the coating forming material
- C23C14/22—Coating by vacuum evaporation, by sputtering or by ion implantation of the coating forming material characterised by the process of coating
- C23C14/56—Apparatus specially adapted for continuous coating; Arrangements for maintaining the vacuum, e.g. vacuum locks
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/06—Superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/37—Capillary tubes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
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- Chemical Kinetics & Catalysis (AREA)
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Abstract
The invention provides an ultralow-temperature water vapor capture pump pipeline system using secondary refrigerant for cold accumulation, which comprises a compressor, wherein the discharge end of the compressor is connected with an oil separator, the oil separator is respectively connected with a condensation pipeline and a hot tank pipeline through a third three-way electromagnetic valve, the free end of the condensation pipeline is connected with a second three-way valve, and the second three-way valve is connected with a main return pipe connected with the return end of the compressor. The excess cold is stored in the refrigerating medium, so that the compressor is prevented from being stopped due to low temperature and low pressure of a compressor suction port caused by supercooling of the system, the system further stably operates, and the service life of the equipment is prolonged. Under the condition of reaching the heating temperature of the same refrigeration temperature, the work load of the compressor is reduced, and the use of energy is saved. Meanwhile, the load cold trap is cooled by the liquid secondary refrigerant with high specific heat capacity, so that the cooling speed of the cold trap is increased, and the water vapor is captured more quickly, so that the working efficiency of the vacuum coating industry is improved.
Description
Technical Field
The invention relates to the field of refrigeration, in particular to an ultralow-temperature water vapor capture pump pipeline system applying secondary refrigerant for cold storage.
Background
The ultralow temperature steam entrapment pump that uses at present domestically adopts from overlapping refrigeration cycle to reduce the refrigerant to ultralow temperature, lets in the low temperature refrigerant to the load cold-trap again, after the load cold-trap cools off to the uniform temperature, can adsorb the surface of load cold-trap with the vapor in the outside cavity space of load cold-trap on to make the cavity inside obtain higher vacuum under the effect of vacuum pump. During the long-time standby operation of the capture pump equipment, the temperature at the tail end can reach-150 ℃ or even lower, and the excessively low cryogenic temperature reflects that the equipment system is in a highly supercooled state, so that the temperature and the pressure of a refrigerant entering a suction port of a compressor are excessively low. When the equipment is in a refrigeration state, a refrigerant in a low-temperature state directly contacts with the load cold trap for heat exchange, and the flow of the liquid refrigerant entering the load cold trap is not enough to quickly reduce the temperature of the load cold trap due to the change of the size and the form of the load cold trap, so that the working efficiency is influenced because the inside of a vacuum cavity cannot quickly reach a high vacuum degree in the vacuum coating industry.
Such devices have the following disadvantages:
1. the temperature of the air suction port of the compressor is too low, the probability of liquid impact of the compressor is increased, the normal and reliable operation of the compressor is not facilitated, and a large amount of frost is easily formed outside the air suction port of the compressor.
2. The equipment system is in a high supercooling state for a long time, so that the pressure at the air suction port of the compressor is low to generate low-pressure alarm, the compressor is stopped, and the service life of the equipment is shortened.
3. When the pressure of the connecting part of the load cold trap and the equipment reaches 3Mpa and the temperature of the connecting part changes between minus 150 ℃ and plus 50 ℃, the connecting part expands with heat and contracts with cold, and the refrigerant is easy to leak at the connecting part. The mixed refrigerant used by the equipment damages the balance inside the system once leakage occurs, and at the moment, the system needs to be stabilized by replacing the set of mixed refrigerant with higher cost.
4. In the heating and defrosting process of the equipment, when lubricating oil used by a compressor directly enters a load cold trap along with a refrigerant in a gaseous form, part of oil vapor is cooled in the vicinity of a refrigeration electromagnetic valve, so that the refrigeration electromagnetic valve fails.
5. In the actual use process of the equipment, the load cold trap needs to be subjected to staged refrigeration and heating, and the refrigerant brings heat back to the equipment system during heating and defrosting, so that the working load of the compressor is increased. The refrigerant entering the load cold trap mainly exists in a gas-liquid two-phase state, so that the cooling speed of the load cold trap is not enough to improve the working efficiency of the vacuum coating industry.
Disclosure of Invention
In order to solve the above-mentioned defects in the prior art, an ultralow temperature water vapor capture pump with a novel structure, high speed and efficiency is provided, the ultralow temperature water vapor capture pump using secondary refrigerant for cold storage comprises a load cold trap refrigeration pipeline, a return pipeline, a load cold trap defrosting pipeline and a load cold trap arranged in external vacuum equipment, wherein the refrigerant in the load cold trap refrigeration pipeline passes through a capillary tube, a refrigeration manual isolation valve and a refrigeration electromagnetic valve from a five-stage heat exchanger, then passes through a cold tank containing low-temperature secondary refrigerant with high specific heat capacity and exchanges heat with the secondary refrigerant in the cold tank, then flows into the return pipeline through a total return valve, the low-temperature secondary refrigerant flows out of the cold tank, then enters the load cold trap through a three-way electromagnetic valve, a circulating pump and an output electromagnetic valve, then flows back into the cold tank, the refrigerant in the defrosting pipeline enters a hot tank containing high-capacity secondary refrigerant and exchanges heat with the secondary refrigerant, and then flows into a water-cooled condenser, and the secondary refrigerant in the hot tank flows out of the hot tank, then enters the load cold trap through the three-way electromagnetic valve, the circulating pump and the output electromagnetic valve, and then flows back to the hot tank.
The technical scheme of the invention is realized as follows:
use ultra-low temperature steam entrapment pump pipe-line system of secondary refrigerant cold-storage, including the compressor, oil separator is connected to the compressor discharge end, oil separator connects condensation pipeline and hot jar pipeline respectively through a third tee bend solenoid valve, the second tee bend is connected to the condensation pipeline free end, the second tee bend be connected with the main return pipe that the compressor feed back end is connected.
As a preferred scheme of the invention, the condensing pipeline is connected with a fourth tee joint after sequentially passing through the water-cooled condenser, the drying filter, the heat regenerator, the primary vapor-liquid separator, the primary heat exchanger, the secondary vapor-liquid separator, the secondary heat exchanger, the tertiary vapor-liquid separator, the tertiary heat exchanger and the quaternary heat exchanger.
As a preferred scheme of the invention, the fourth tee is also connected with two branches;
the first branch passes through a fourth capillary tube and a fourth-stage heat exchanger and then is connected with the second tee joint;
and the second branch passes through a fifth capillary tube, a refrigeration manual isolation valve, a refrigeration electromagnetic valve, a cold tank and a total reflux manual isolation valve and then is connected with the second tee joint.
As a preferable scheme of the invention, the hot tank pipeline is connected with the discharge end of the condensation pipeline after passing through the defrosting manual isolation valve and the hot tank.
As a preferred scheme of the invention, the oil separator is connected with a first tee, and the first tee is also connected with two branches;
one branch is connected with the material return end of the compressor;
the other branch is connected with a third tee joint through a sixth capillary.
As a preferred scheme of the invention, the third tee is also connected with two branches;
one branch is connected with the gas storage tank;
the other branch is connected with the secondary gas-liquid separator after passing through the pressure relief battery valve.
As a preferable scheme of the invention, the primary gas-liquid separator is also connected with a branch which passes through the BP electromagnetic valve and the first capillary tube and is connected with a main return pipe between the primary heat exchanger and the secondary heat exchanger.
As the preferred scheme of the invention, two ends of a second capillary tube are respectively connected with the secondary gas-liquid separator and the main return pipe between the secondary heat exchanger and the tertiary heat exchanger;
two ends of a third capillary tube are respectively connected with the three-stage gas-liquid separator and the feeding end of the main return pipe.
As a preferable scheme of the invention, the cold tank is connected with three branches;
the first branch is connected with the hot tank;
the second branch is connected with a first three-way electromagnetic valve;
the third branch is connected with a second three-way electromagnetic valve;
the first three-way electromagnetic valve is connected with a pipeline which is connected with the second three-way electromagnetic valve after sequentially passing through the circulating pump, the output electromagnetic valve and the load cold trap.
As a preferable scheme of the invention, the second three-way electromagnetic valve is also provided with a branch connected with the hot tank.
Has the advantages that:
use ultra-low temperature steam entrapment pump pipe-line system of secondary refrigerant cold-storage, including the compressor, oil separator is connected to the compressor discharge end, oil separator connects condensation pipeline and hot jar pipeline respectively through a third tee bend solenoid valve, the second tee bend is connected to the condensation pipeline free end, the second tee bend be connected with the main return pipe that the compressor feed back end is connected.
The invention has the beneficial effects that in the running process of the ultralow temperature water vapor capture pump, the excessive cold energy is stored in the secondary refrigerant, so that the compressor halt caused by low temperature and pressure of the air suction port of the compressor due to supercooling of the system is avoided, the system further stably runs, and the service life of the equipment is prolonged. The mixed refrigerant is used by the ultralow-temperature water vapor trapping pump, when the pressure is too high, the refrigerant leakage is easily caused at the joint of the load cold trap and the equipment, the refrigerant leakage needs to be changed into the whole set of mixed refrigerant, the load cold trap is cooled by the secondary refrigerant, and even if the secondary refrigerant leakage is caused, the leakage problem can be solved by adding a small amount of secondary refrigerant. The load cold trap is cooled by the secondary refrigerant, so that the problem that the refrigeration electromagnetic valve fails due to the fact that part of oil vapor is cooled in the vicinity of the refrigeration electromagnetic valve when the equipment is heated and defrosted is solved. When the device heats and defrosts the load cold trap, the high-temperature high-pressure refrigerant transfers partial heat to the secondary refrigerant in the hot tank and then enters the water-cooled condenser, so that the load cold trap can be heated by the secondary refrigerant, the heat contained in the high-temperature high-pressure refrigerant entering the water-cooled condenser can be reduced, and the operation heating link of a specific compressor is omitted. Under the condition of reaching the heating temperature of the same refrigeration temperature, the work load of the compressor is reduced, and the use of energy is saved. Meanwhile, the load cold trap is cooled by the liquid secondary refrigerant with high specific heat capacity, the refrigerating capacity per unit volume of the secondary refrigerant is higher than that of the refrigerant, and the mass flow of the secondary refrigerant flowing through the load cold trap is 20-30 times of that of the refrigerant, so that the cooling speed of the cold trap is increased, and the water vapor is captured more quickly to improve the working efficiency of the vacuum coating industry.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.
FIG. 1 is a schematic view of the structure of the present invention.
In the figure, a compressor 1, an oil separator 2, a water-cooled condenser 3, a drying filter 4, a heat regenerator 5, a primary vapor-liquid separator 6, a primary heat exchanger 7, a BP solenoid valve 8, a first capillary tube 9, a secondary vapor-liquid separator 10, a secondary heat exchanger 11, a second first second capillary tube, a tertiary vapor-liquid separator 13, a tertiary heat exchanger 14, a third first fifth capillary tube, a quaternary heat exchanger 16, a fourth first capillary tube 7, a refrigeration manual isolation valve 18, a refrigeration solenoid valve 19, a fifth second capillary tube 0, a total reflux manual isolation valve 21, a cold tank 22, a first three-way solenoid valve 23, a circulating pump 24, an output solenoid valve 25, a load cold trap 26, a second three-way solenoid valve 27, a hot tank 28, a defrosting manual isolation valve 29, a third three-way solenoid valve 30, a pressure relief solenoid valve 31, an air tank 32 and a sixth third capillary tube 3 are included.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Example 1
The ultralow temperature steam trap pump can acquire ultralow temperature through self-overlapping refrigeration circulation, and can reduce the temperature of the load cold trap through the direct contact heat exchange between an ultralow temperature refrigerant and the load cold trap, so that the steam in the external cavity space of the cold trap is adsorbed on the outer surface of the cold trap, and the inside of the cavity can acquire higher vacuum degree under the action of the vacuum pump. The cold storage tank stores cold energy and cools a cold trap arranged in a vacuum coating system through the secondary refrigerant, the secondary refrigerant with low temperature and high specific heat capacity is used, and under the condition of occupying small space, the secondary refrigerant in the cold tank can store excessive cold energy generated when the ultralow temperature capture pump is standby, so that the problem of shutdown of equipment due to low-pressure alarm caused by system supercooling is avoided. Meanwhile, the specific heat capacity of the secondary refrigerant stored in the cold tank is higher, and under the condition of ensuring a certain flow, the heat absorbed from the load cold trap in unit time is much higher than that of a gas-liquid refrigerant, so that the cooling speed of the load cold trap is increased, the working efficiency of the vacuum coating machine is improved, and the power consumption is reduced.
The ultralow-temperature water vapor capture pump pipeline system applying the secondary refrigerant cold accumulation comprises a compressor 1, wherein the discharge end of the compressor 1 is connected with an oil separator 2, the oil separator is respectively connected with a condensation pipeline and a hot tank pipeline through a third three-way electromagnetic valve 30, the free end of the condensation pipeline is connected with a second three-way valve, and the second three-way valve is connected with a main return pipe connected with the return end of the compressor 1.
The condensing pipeline passes through the water-cooled condenser 3, the drying filter 4, the heat regenerator 5, the primary gas-liquid separator 6, the primary heat exchanger 7, the secondary gas-liquid separator 10, the secondary heat exchanger 11, the tertiary gas-liquid separator 13, the tertiary heat exchanger 14 and the quaternary heat exchanger 16 in sequence and then is connected with a fourth tee joint.
The fourth tee is also connected with two branches;
the first branch passes through a fourth capillary tube 17 and a fourth-stage heat exchanger 16 and then is connected with the second tee joint;
and the second branch passes through a fifth capillary tube 20, a refrigeration manual isolation valve 18, a refrigeration electromagnetic valve 19, a cold tank 22 and a total reflux manual isolation valve 21 and then is connected with the second tee joint.
The hot tank pipeline passes through a defrosting manual isolation valve 29 and a hot tank 28 and then is connected with the discharge end of the condensation pipeline.
The oil separator 2 is connected with a first tee joint, and the first tee joint is also connected with two branches;
one branch is connected with the material return end of the compressor 1;
the other branch is connected to a third tee via a sixth capillary 33.
The third tee is also connected with two branches;
one branch is connected with the air storage tank 32;
the other branch is connected with the secondary gas-liquid separator 10 after passing through the pressure relief battery valve 31.
The first-stage gas-liquid separator 6 is also connected with a branch which passes through a BP electromagnetic valve 8 and a first capillary 9 and is connected with a main return pipe between the first-stage heat exchanger 7 and the second-stage heat exchanger 11.
Two ends of a second capillary tube 12 are respectively connected with the secondary gas-liquid separator 10 and a main return pipe between the secondary heat exchanger 11 and the tertiary heat exchanger 14;
two ends of a third capillary 15 are respectively connected with the three-stage gas-liquid separator 13 and the feeding end of the main return pipe.
The cold tank 22 is connected with three branches;
the first branch is connected with the hot tank 28;
the second branch is connected with a first three-way electromagnetic valve 23;
the third branch is connected with a second three-way electromagnetic valve 27;
the first three-way solenoid valve 23 is connected to a pipeline which passes through a circulating pump 24, an output solenoid valve 25 and a load cold trap 26 in sequence and then is connected to a second three-way solenoid valve 27.
The second three-way solenoid valve 27 is also provided with a branch connected to a hot tank 28.
A high-pressure high-temperature non-azeotropic refrigerant discharged by a compressor 1 in an ultralow-temperature water vapor capture pump system is divided into two paths, wherein the first path sequentially passes through an oil separator 2, a water-cooled condenser 3, a drying filter 4, a heat regenerator 5, a primary vapor-liquid separator 6, a primary heat exchanger 7, a secondary vapor-liquid separator 10, a secondary heat exchanger 11, a tertiary vapor-liquid separator 13, a tertiary heat exchanger 14, a quaternary heat exchanger 16, a manual refrigerating isolating valve 18, a refrigerating electromagnetic valve 19, a fifth capillary tube 20, a cold tank 22 and a total reflux manual isolating valve 21 from the front to the back from the exhaust end of the compressor, and then enters an air suction port of the compressor after exchanging heat with. When the cryogenic temperature reaches a certain low temperature value, the refrigeration electromagnetic valve 19 is opened, and the cryogenic temperature value for closing the electromagnetic valve 19 is set to be higher than the opening temperature. Therefore, the cold energy generated by long-time standby is transferred to the high specific heat capacity refrigerating medium in the cold tank 22, and the system is prevented from entering a supercooled state to influence the operation of equipment.
The second path returns to the refrigerant inlet of the water-cooled condenser 3 from the exhaust end of the compressor through a third three-way electromagnetic valve 30, a defrosting manual isolating valve 29 and a hot tank 28. When the defrosting mode is started, the high-temperature and high-pressure refrigerant discharged from the exhaust port of the compressor 1 exchanges heat with the secondary refrigerant in the hot tank 28, the heat is transferred to the secondary refrigerant with high specific heat capacity, and then the secondary refrigerant enters the water-cooling condensation, so that the condition that the stability of the system is damaged due to the rise of the temperature and the pressure in the equipment system during defrosting is avoided.
The pressure relief system sequentially passes through the secondary gas-liquid separator 10, the pressure relief solenoid valve 31, the air storage tank 32 and the sixth capillary tube 33 from front to back from the inlet end, and then enters the air suction port of the compressor 1. When the refrigerating capacity in the refrigerant is absorbed by the coolant in the cold tank 22, the pressure of the refrigerant in the system increases, and when the pressure reaches a certain value, the pressure relief solenoid valve 31 is opened to temporarily store the refrigerant in the air storage tank 32. And then through a sixth capillary 33 into the system.
The first-stage gas-liquid separator 6 is connected with the first-stage heat exchanger 7 through a first capillary tube 9, the second-stage gas-liquid separator 10 is connected with the second-stage heat exchanger 11 through a second capillary tube 12, the third-stage gas-liquid separator 13 is connected with the third-stage heat exchanger 14 through a third capillary tube 15, and an outlet at one position of the fourth-stage heat exchanger 16 is connected with an inlet at one position of the fourth-stage heat exchanger 16 through a fourth capillary tube. Through the throttling and cooling effects of the capillary tube, the liquid refrigerant with lower temperature can cool the gaseous refrigerant in the mixed refrigerant until the gaseous refrigerant is liquefied.
The refrigerating medium in the cold tank 22 sequentially passes through a first three-way electromagnetic valve 23, a circulating pump 24, an output electromagnetic valve 25, a load cold trap 26 and a second three-way electromagnetic valve 27 from front to back, and then returns to the cold tank 22. When the load cold trap needs to be cooled to trap water vapor, the refrigeration mode is started, the equipment starts the refrigeration electromagnetic valve 19 and the output electromagnetic valve 25, meanwhile, the first three-way electromagnetic valve 23 and the second three-way electromagnetic valve 27 are electrified, the circulating pump 24 is started, and the ultralow-temperature secondary refrigerant enters the load cold trap 26 at a certain flow rate and cools the load cold trap 26. When the temperature required for cooling is reached, the refrigeration solenoid valve 19 is closed, and the first three-way solenoid valve 23 and the second three-way solenoid valve 27 are de-energized. The liquid secondary refrigerant with high specific heat capacity is used for cooling the load cold trap, and the temperature difference between the liquid secondary refrigerant and the load cold trap is larger during heat exchange, so that the effect of cooling the load cold trap by using the refrigerant with vapor phase and liquid phase is better than that of cooling the load cold trap by using the refrigerant with vapor phase and liquid phase, and the cooling speed of the load cold trap is higher.
The refrigerating medium in the hot tank 28 passes through the first three-way electromagnetic valve 23, the circulating pump 24, the output electromagnetic valve 25, the load cold trap 26 and the second three-way electromagnetic valve 27 in sequence from front to back, and then returns to the hot tank 28. When the load cold trap needs defrosting, the defrosting mode is started, the equipment automatically starts the output electromagnetic valve 25, meanwhile, the first three-way electromagnetic valve 23 and the second three-way electromagnetic valve 27 are powered off, the circulating pump 24 is started, and the high-temperature refrigerating medium enters the cold trap at a certain flow rate to heat the cold trap. When the defrost temperature is reached, the output solenoid valve 25 and the circulation pump 24 are closed. The liquid secondary refrigerant with high specific heat capacity is used for heating the load cold trap, and the temperature difference between the liquid secondary refrigerant and the load cold trap during heat exchange is larger, so that the effect of heating the load cold trap by using the refrigerant with vapor phase and liquid phase is better, and the heating speed of the load cold trap is higher. Meanwhile, the problem that the failure of the refrigeration electromagnetic valve is influenced by the fact that gaseous lubricating oil contained in the gaseous refrigerant enters a low-temperature region can be solved by using the secondary refrigerant with high specific heat capacity to heat the load cold trap.
When the load cold trap reaches the temperature required by cooling, the first three-way electromagnetic valve 23 is powered off, the second three-way electromagnetic valve 27 is continuously powered on in a delayed mode, and the low-temperature secondary refrigerant in the load cold trap is discharged into the cold tank 22. After the delay time is reached, the second three-way solenoid valve 27 is energized and the coolant in the cold load trap is then discharged to the heat rejection tank 28.
In the running process of the ultralow-temperature water vapor trapping pump, the heating load cold trap is cooled by introducing the secondary refrigerant instead of directly cooling the heating load cold trap by adopting the refrigerant, so that the state of the refrigerant in the system cannot fluctuate greatly, the stability and energy conservation of the system can be improved, and the cooling speed of the cold trap can be improved. The coolant, cold tanks, hot tanks, circuit control systems, coolant mass balance between the cold and hot tanks, and the manner in which the coolant is used to cool the cold traps of the heating load are critical and protected points.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (10)
1. Use ultra-low temperature steam entrapment pump pipe-line system of secondary refrigerant cold-storage, including compressor (1), its characterized in that, oil separator (2) are connected to compressor (1) discharge end, oil separator connects condensation pipeline and hot tank pipeline respectively through a third three-way solenoid valve (30), the second tee bend is connected to the condensation pipeline free end, the second tee bend be connected with the main return pipe that compressor (1) feed back end is connected.
2. The ultralow temperature water vapor capture pump pipeline system using secondary refrigerant cold accumulation as claimed in claim 1, wherein the condensing pipeline is connected with a fourth tee after passing through the water-cooled condenser (3), the drying filter (4), the heat regenerator (5), the primary gas-liquid separator (6), the primary heat exchanger (7), the secondary gas-liquid separator (10), the secondary heat exchanger (11), the tertiary gas-liquid separator (13), the tertiary heat exchanger (14) and the quaternary heat exchanger (16) in sequence.
3. The ultra-low temperature water vapor capture pump pipeline system applying coolant cold accumulation as claimed in claim 2, wherein the fourth tee further connects two branches;
the first branch passes through a fourth capillary tube (17) and a four-stage heat exchanger (16) and then is connected with the second tee joint;
and the second branch passes through a fifth capillary tube (20), a refrigeration manual isolating valve (18), a refrigeration electromagnetic valve (19), a cold tank (22) and a total reflux manual isolating valve (21) and then is connected with the second tee joint.
4. The ultra-low temperature vapor capture pump piping system using coolant cold storage according to claim 1, wherein the hot tank piping is connected to the discharge end of the condensation piping after passing through the defrosting manual isolation valve (29) and the hot tank (28).
5. The ultra-low temperature water vapor capture pump pipeline system applying the secondary refrigerant cold accumulation as claimed in claim 2, wherein the oil separator (2) is connected with a first tee, and the first tee is further connected with two branches;
one branch is connected with the feed back end of the compressor (1);
the other branch is connected with a third tee joint through a sixth capillary (33).
6. The ultra-low temperature water vapor capture pump pipeline system using coolant cold accumulation as claimed in claim 5, wherein the third tee is further connected with two branches;
one branch is connected with the air storage tank (32);
the other branch is connected with the secondary gas-liquid separator (10) after passing through a pressure relief battery valve (31).
7. The ultra-low temperature water vapor capture pump pipeline system applying the secondary refrigerant cold accumulation as claimed in claim 2, wherein the primary vapor-liquid separator (6) is further connected with a branch which passes through a BP solenoid valve (8) and a first capillary tube (9) and is connected with a main return pipe between the primary heat exchanger (7) and the secondary heat exchanger (11).
8. The ultra-low temperature water vapor capture pump pipeline system applying the secondary refrigerant cold accumulation as claimed in claim 2, wherein two ends of a second capillary tube (12) are respectively connected with the secondary vapor-liquid separator (10) and the main return pipe between the secondary heat exchanger (11) and the tertiary heat exchanger (14);
two ends of a third capillary tube (15) are respectively connected with the three-stage gas-liquid separator (13) and the feeding end of the main return pipe.
9. The ultra-low temperature water vapor capture pump piping system using coolant cold storage according to claim 3, characterized in that the cold tank (22) is connected with three branches;
the first branch is connected with a hot tank (28);
the second branch is connected with a first three-way electromagnetic valve (23);
the third branch is connected with a second three-way electromagnetic valve (27);
the first three-way electromagnetic valve (23) is connected with a pipeline which is connected with the second three-way electromagnetic valve (27) after sequentially passing through the circulating pump (24), the output electromagnetic valve (25) and the load cold trap (26).
10. The ultra-low temperature vapor capture pump piping system using coolant cold storage according to claim 9, wherein the second three-way solenoid valve (27) is further provided with a branch connected to the hot tank (28).
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| CN202010268589.9A CN111412675A (en) | 2020-04-07 | 2020-04-07 | Ultralow-temperature water vapor capture pump pipeline system using secondary refrigerant for cold storage |
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| CN202010268589.9A CN111412675A (en) | 2020-04-07 | 2020-04-07 | Ultralow-temperature water vapor capture pump pipeline system using secondary refrigerant for cold storage |
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