KR101920781B1 - A Heat Pump System for Providing Highly Heated Steam - Google Patents

A Heat Pump System for Providing Highly Heated Steam Download PDF

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Publication number
KR101920781B1
KR101920781B1 KR1020150078322A KR20150078322A KR101920781B1 KR 101920781 B1 KR101920781 B1 KR 101920781B1 KR 1020150078322 A KR1020150078322 A KR 1020150078322A KR 20150078322 A KR20150078322 A KR 20150078322A KR 101920781 B1 KR101920781 B1 KR 101920781B1
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South Korea
Prior art keywords
flash tank
refrigerant
steam
heat exchanger
temperature
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KR1020150078322A
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Korean (ko)
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KR20160142907A (en
Inventor
장기창
김기봉
박성룡
백영진
나호상
이길봉
조준현
박윤철
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한국에너지기술연구원
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B3/00—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F25B41/04—
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/03—Oil level
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

The present invention relates to a heat pump system capable of supplying high temperature steam at a temperature of 120 ° C or more, and a method of supplying high temperature steam using the system.
The present invention relates to an evaporator for evaporating a refrigerant by receiving heat from a heat source, a compressor for compressing a refrigerant in a vapor phase evaporated in the evaporator, and a high-temperature A heat pump including a condenser; A flash tank in which the refrigerant is condensed in the high temperature condenser and the steam to which the divergent heat is transferred is introduced; And a heat exchanger provided in the flash tank and adapted to partially reheat steam in the flash tank by flowing a portion of the refrigerant compressed by the compressor at a high temperature and a high pressure.
Further, the present invention provides a method for producing steam, comprising: evaporating a refrigerant by receiving heat from a heat source; compressing the evaporated gaseous phase refrigerant; generating steam by heat to liquefy and dissipate the compressed high temperature and high pressure gaseous refrigerant; Introducing the steam into the flash tank; And supplying a portion of the compressed high-temperature and high-pressure refrigerant to a heat exchanger in the flash tank to thereby secondarily heat the steam in the flash tank.

Figure R1020150078322

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a heat pump system for providing high temperature steam,

The present invention relates to a heat pump system, and more particularly, to a heat pump system capable of supplying high temperature steam of 120 ° C or higher and a method of supplying high temperature steam using the same.

A technique of generating steam by using a heat pump is being used. This is a method of converting water into steam through heat exchange in a high-temperature condenser.

Steam, or steam, is being used in industrial processes quite often. However, the conventional heat pump system has a problem in that it can not supply high temperature steam. Therefore, there is a limit to use the heat pump system for industrial use as a method of generating steam using the heat pump system.

Japanese Patent Publication No. 4972421 Japanese Patent Publication No. 5593902 Japanese Patent Publication No. 5593906

SUMMARY OF THE INVENTION It is an object of the present invention to provide a heat pump system capable of providing high temperature steam and a method for supplying high-energy steam using the same.

According to an aspect of the present invention, there is provided a refrigerator comprising: an evaporator that receives heat from a heat source to evaporate a refrigerant; a compressor that compresses a refrigerant in a vapor phase evaporated in the evaporator; A heat pump including a high-temperature condenser that liquefies and dissipates heat;

 A flash tank in which the refrigerant is condensed in the high temperature condenser and the steam to which the divergent heat is transferred is introduced; And

 And a heat exchanger installed in the flash tank and reheating steam in the flash tank by a part of refrigerant compressed by the compressor at a high temperature and a high pressure.

The heat pump may further include a receiver that temporarily mists the refrigerant in the liquid phase condensed in the high temperature condenser.

The refrigerant passed through the heat exchanger may be introduced into the receiver by bypassing the high temperature condenser.

The heat exchanger may be disposed above the inflow portion of the steam introduced into the flash tank.

The heat exchanger may be a coil type.

A drain portion for discharging condensed water generated in the flash tank may be provided below the steam inlet portion of the flash tank.

The flash tank may further include a level gauge for measuring the level of the condensed water.

When the level of the condensed water measured by the level gauge exceeds the reference level, the condensed water can be discharged through the drain portion.

The amount of the refrigerant flowing into the heat exchanger of the flash tank may be determined based on at least one of the pressure in the flash tank and the steam temperature.

The higher the pressure in the flash tank, the smaller the amount of refrigerant supplied to the heat exchanger in the flash tank.

The higher the steam temperature in the flash tank, the smaller the amount of refrigerant supplied to the heat exchanger in the flash tank.

The refrigerant temperature T1 at the inlet of the heat exchanger of the flash tank is compared with the refrigerant temperature T2 at the outlet of the heat exchanger so that the larger the difference between the two temperatures T1-T2 is, the greater the amount of refrigerant supplied is. The amount of refrigerant supplied can be reduced.

The amount of the refrigerant supplied to the heat exchanger can be adjusted through the automatic valve on the receiver side.

A cover plate may be provided between the heat exchanger in the flash tank and the inflow portion of the steam to remove condensed water in the steam and uniformly distribute the flow of the steam.

At least a part of the outer peripheral surface of the cover plate can be supported by the inner wall of the flash tank.

 A drain can be formed on the outer circumferential surface of the cover plate so that the condensed water removed from the steam can flow down to the bottom of the flash tank.

The cover plate may be inclined so as to gradually decrease from the central portion toward the outer peripheral surface.

A drain can be formed at the center of the cover plate so that the condensed water removed from the steam can flow down to the bottom of the flash tank.

The cover plate may be inclined so as to gradually decrease from the outer circumferential surface toward the central portion.

The inclination may be 1 to 3 degrees.

The surface of the cover plate may be polished.

 The flash tank may further include a safety valve that is opened when the pressure of the steam rises to a predetermined pressure or higher.

The safety valve may be installed above the heat exchanger.

 The pressure of the steam can be measured by a pressure sensor installed above the heat exchanger.

The refrigerant may be R-245fa.

According to another aspect of the present invention, there is provided a method of generating steam by heat from a heat source to evaporate the refrigerant, compress the evaporated gaseous refrigerant, liquefy the gaseous refrigerant at a high temperature and pressure, step;

Introducing the steam into the flash tank;

And supplying a portion of the compressed high-temperature and high-pressure refrigerant to a heat exchanger in the flash tank to secondarily heat the steam in the flash tank.

The water level of the condensed water generated in the flash tank is measured and the condensed water can be drained when the water level exceeds the reference water level.

The amount of the refrigerant supplied to the heat exchanger is reduced as the pressure in the flash tank is increased, and the amount of the refrigerant supplied to the heat exchanger is increased as the pressure in the flash tank is lower.

 The amount of the refrigerant supplied to the heat exchanger is decreased as the temperature T3 of the steam in the flash tank is higher and the amount of the refrigerant supplied to the heat exchanger is increased as the temperature of steam in the flash tank is lower.

 The refrigerant temperature T1 at the inlet of the heat exchanger of the flash tank is compared with the refrigerant temperature T2 at the outlet of the heat exchanger to increase the amount of refrigerant supplied as the difference between the two temperatures T1-T2 increases, The amount of refrigerant supplied can be increased.

When the pressure of the steam of the flash tank rises to a predetermined pressure or higher, the steam can be released to the outside of the flash tank.

The refrigerant may be R-245fa.

According to the present invention, high-temperature steam can be supplied with a simple structure.

The above and other objects, features and advantages of the present invention will be more apparent from the following detailed description taken in conjunction with the accompanying drawings, in which: FIG.

FIG. 1 is a schematic view showing the overall structure of a heat pump system according to an embodiment of the present invention,
2 and 3 are a plan view and a side view of an embodiment of a cover plate installed in a flash tank of a heat pump system according to an embodiment of the present invention,
4 and 5 are a plan view and a side view of an embodiment of a cover plate installed in a flash tank of a heat pump system according to another embodiment of the present invention,
Figure 6 is the pressure-enthalpy curve of R-245fa.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

It is to be understood that the present invention is not limited to the disclosed embodiments, but may be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, It is provided to inform.

FIG. 1 is a schematic view showing the overall structure of a heat pump system according to an embodiment of the present invention.

[Structure of Heat Pump]

The heat pump system of the present invention is for supplying high temperature steam of 120 degrees Celsius or more, and R-245fa may be used as a refrigerant of the heat pump. The pressure-enthalpy curve of R-245fa is as shown in FIG.

The heat pump (10) comprises an evaporator (11) for absorbing external heat to evaporate the refrigerant, a compressor (12) for compressing the refrigerant at high temperature and low pressure evaporated in the evaporator, a condenser A receiver 16 in which the refrigerant liquefied in the high temperature condenser 14 is stored and an expansion valve 19 for expanding the refrigerant in the receiver 16 to low pressure. The refrigerant having passed through the expansion valve (19) flows into the evaporator (11) again.

The evaporator 11 absorbs heat energy from an external heat source, and such external heat source may be wasted hot water. The temperature of the waste heat discharged after high temperature steam is usually used in the industrial field may be about 65 degrees Celsius, but it is variable depending on the use of steam in the industrial field.

The refrigerant vaporized in the evaporator 11 is compressed by the compressor 12 to be a gas of high temperature and high pressure. In the present invention, the refrigerant of a high temperature and high pressure compressed in the compressor is branched into a heat exchanger 18 The steam in the flash tank 30 is heated once more. Then, the refrigerant branched by the heat exchanger 18 flows into the receiver 16.

That is, some of the high-temperature and high-pressure refrigerant from the compressor flows through the high-temperature condenser 14 to the receiver, and the remaining portion flows to the receiver 16 via the heat exchanger 18. On the other hand, as will be described later, the refrigerant flow path through the heat exchanger 18 is not always open, but the flow rate of the refrigerant may be adjusted as necessary to prevent flow. The flow rate of the refrigerant is regulated by the automatic valve 19.

Water stored in the flash tank (30) flows into the high temperature condenser (14) to perform heat exchange with the high temperature and high pressure refrigerant. Accordingly, the water flowing from the flash tank 30 through the drain 34 flows into the flash tank 30 as steam.

[Structure of Flash Tank]

At the bottom of the flash tank (30), water is stored. The water stored in the bottom of the flash tank 30 may be supplied from the outside as needed. A drain portion 34 is connected to the bottom surface of the flash tank 30, and the drain portion is connected to the high temperature condenser 14 described above. Therefore, the water at the bottom of the flash tank enters the high temperature condenser through the drain portion, exchanges heat with the refrigerant, is vaporized into steam, and flows back into the inlet portion 32 on the middle side of the flash tank.

The steam that has flowed from the high temperature condenser 14 to the inflow portion 32 again flows into the flash tank 30 through the inlet 32 and then flows back to the bottom of the flash tank 30. [ Also, some of the steam that has flowed into the flash tank through the inlet portion is also liquefied again, and water can be dropped to the bottom of the flash tank.

The flash tank has a level gauge (42) to constantly monitor the level inside the flash tank. When the water level inside the flash tank is too high, the drain portion 34 is opened to allow water in the flash tank to enter the high temperature condenser 14.

The level gauge 42 may perform an operation to replenish the water when the water level inside the flash tank is too low. Also, the water to be supplemented may not be supplied directly to the inside of the flash tank but may be supplied in such a manner as to join the pipe of the drain portion 34. [ Because the water to be supplemented is relatively low in temperature, it may be more desirable to be fed to the inlet of the water of the hot condenser 14 rather than to the flash tank to maintain a high temperature environment.

A cover plate (50) is installed in the flash tank (30) at an upper portion of the inflow part (32). FIGS. 2 and 3 are a plan view and a side view of an embodiment of a cover plate installed in a flash tank of a heat pump system according to an embodiment of the present invention, and FIGS. 4 and 5 show another embodiment according to the present invention, A plan view and a side view of an embodiment of a cover plate installed in a flash tank of a pump system.

Referring to FIGS. 2 and 4, the cover plate 50 is provided with a porous portion 54. The replenishment unit 54 functions to disperse the steam evenly when the water vapor introduced into the flash tank through the inlet unit rises in the flash tank. This is for better heat exchange between the heat exchanger 18 and water vapor, which will be described later.

The outer peripheral surface of the cover plate 50 is fixed to the inner peripheral surface of the flash tank. As shown in FIG. 3, the cover plate 50 may be in the form of a cap having the highest center and a lower height toward the outer periphery, or a funnel shape having the lowest center and the height increasing toward the outer periphery as shown in FIG. The inclination angle a may be approximately 1 to 3 degrees. If the angle of inclination is too large, the dispersing function of water vapor is deteriorated. If the inclination angle is too small, some of the water vapor is again liquefied, and water formed on the cover plate 50 accelerates the liquefaction of water vapor.

As shown in FIG. 2, the cover plate of the cap shape of FIG. 3 has a drainage passage 52 formed on the outer circumference thereof. The drainage channel may be in the form of a groove as shown. Accordingly, the water formed on the cover plate in the form of a hat can be moved to the edge and fall downward through the drainage path (52).

The funnel-shaped cover plate of FIG. 5 has a drainage passage 52 formed at the center thereof as shown in FIG. The drain can be a circular hole as shown. Accordingly, the water formed on the cover plate in the form of a hat can be moved to the center and fall downward through the drainage path (52).

Described level gauge 42 and inlet 32 are located below the cover plate.

On the cover plate 50, the heat exchanger 18 described above is located. The heat exchanger (18) functions to reheat steam in the flash tank by introducing the high-temperature and high-pressure gas-phase refrigerant from the compressor. The refrigerant flowing out of the heat exchanger moves to the receiver. The heat exchanger 18 may be of a coil type so as to be more advantageous for heat exchange with water vapor.

As described above, since the heat exchanger 18 is configured to reheat water vapor, if the steam temperature in the flash tank is high enough to reheat the steam, it is possible to control the refrigerant not to flow through the heat exchanger, The amount of the refrigerant flowing into the heat exchanger may be adjusted. The flow interruption or the flow rate of the refrigerant can be controlled by the automatic valve 19.

There may be a pressure in the flash tank as a control factor for controlling flow of the refrigerant or regulating the flow rate. A pressure sensor 44 is installed in the flash tank to constantly monitor the internal pressure. A high pressure in the flash tank may mean that the temperature of the water vapor in the flash tank is higher. Therefore, according to the embodiment of the present invention, the amount of the refrigerant flowing into the heat exchanger decreases as the pressure inside the flash tank increases, and the amount of the refrigerant flowing into the heat exchanger increases as the pressure inside the flash tank decreases.

Other control factors that control the flow of the refrigerant or adjust the flow rate may be the temperature in the flash tank. In this case, the higher the temperature inside the flash tank, the smaller the amount of refrigerant flowing into the heat exchanger, and the lower the temperature inside the flash tank, the more the amount of refrigerant flowing into the heat exchanger can be controlled.

Further, as another control factor for controlling the flow of the refrigerant or controlling the flow rate, the refrigerant temperature T1 of the refrigerant inlet portion of the heat exchanger 18 and the refrigerant temperature T2 of the refrigerant outlet portion of the heat exchanger 18 may be used. That is, the refrigerant temperature (T1) at the inlet of the heat exchanger in the flash tank is compared with the refrigerant temperature (T2) at the outlet of the heat exchanger, and the difference between the two temperatures (T1-T2) is larger than the temperature difference between the refrigerant and the water vapor It can be said that it is necessary to increase the flow amount of the refrigerant in order to further increase the temperature of the steam. On the contrary, the fact that the difference (T1-T2) between the two temperatures is small means that the heat exchange is small and the heat exchange occurs little because the temperature difference between the refrigerant and the water vapor is small, and it can be judged that the flow amount of the refrigerant may be reduced. Therefore, the larger the difference between the two temperatures (T1-T2), the greater the amount of refrigerant supplied, and the smaller the temperature difference, the smaller the amount of refrigerant supplied.

A pressure sensor 44 is installed on the upper part of the heat exchanger of the flash tank to constantly monitor the pressure inside the flash tank. When the internal pressure is excessively high, some of the water vapor is released through the safety valve 46 installed on the flash tank Thereby preventing breakage or explosion of the flash tank.

The flash tank heat exchanger is provided with a discharge valve 36 on the upper part thereof to control the amount of steam supplied to the industrial site.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is to be understood that the scope of the invention is not limited to the disclosed exemplary embodiments. It is obvious that a transformation can be made. Although the embodiments of the present invention have been described in detail above, the effects of the present invention are not explicitly described and described, but it is needless to say that the effects that can be predicted by the configurations should also be recognized.

10: Heat pump
11: Evaporator
12: Compressor
14: High temperature condenser
16: Receiver
17: Expansion valve
18: Heat exchanger
19: Automatic valve
30: Flash tank
32:
34: drain part
36: Discharge valve
42: Level gauge
44: Pressure sensor
46: Safety valve
50: Cover plate
52: drainage
54: Pure study

Claims (33)

A condenser for compressing the refrigerant in the gas phase evaporated in the evaporator, and a high-temperature condenser for liquefying the gaseous refrigerant of high temperature and pressure compressed in the compressor and for radiating heat, including an evaporator for receiving heat from the heat source to evaporate the refrigerant, A heat pump;
A flash tank in which the refrigerant is condensed in the high temperature condenser and the steam to which the divergent heat is transferred is introduced; And
And a heat exchanger provided in the flash tank and adapted to reheat steam in the flash tank by allowing a part of the refrigerant of a high temperature and pressure compressed in the compressor to flow into the flash tank,
Wherein the amount of the refrigerant flowing into the heat exchanger of the flash tank is determined based on at least one of the pressure in the flash tank and the steam temperature.
The method according to claim 1,
Wherein the heat pump further comprises a receiver for temporarily misting the condensed liquid refrigerant in the high temperature condenser.
The method according to claim 1,
And the refrigerant passed through the heat exchanger bypasses the high temperature condenser.
The method of claim 2,
Wherein the refrigerant passed through the heat exchanger bypasses the high temperature condenser and flows into the receiver.
The method according to claim 1,
Wherein the heat exchanger is disposed above the inflow portion of the steam introduced into the flash tank.
The method according to claim 1,
Wherein the heat exchanger is a coil type.
◈ Claim 7 is abandoned due to registration fee. The method according to claim 1,
Wherein a drain portion for discharging the condensed water generated in the flash tank is provided below the steam inlet portion of the flash tank.
◈ Claim 8 is abandoned due to the registration fee. The method of claim 7,
Wherein the flash tank further comprises a level gauge for measuring the level of the condensed water.
◈ Claim 9 is abandoned upon payment of registration fee. The method of claim 8,
And the condensate is discharged through the drain when the level of the condensate measured by the level gauge exceeds the reference level.
delete The method according to claim 1,
And the amount of the refrigerant supplied to the heat exchanger in the flash tank decreases as the pressure in the flash tank increases.
The method according to claim 1,
And the amount of the refrigerant supplied to the heat exchanger in the flash tank decreases as the steam temperature in the flash tank increases.
The method of claim 12,
The refrigerant temperature T1 at the inlet of the heat exchanger of the flash tank is compared with the refrigerant temperature T2 at the outlet of the heat exchanger so that the larger the difference between the two temperatures T1-T2 is, the greater the amount of refrigerant supplied is. And the amount of the refrigerant supplied is reduced.
The method of claim 12,
And the amount of refrigerant supplied to the heat exchanger is regulated through an automatic valve on the receiver side.
The method of claim 5,
Wherein a cover plate is installed between the heat exchanger in the flash tank and the inflow portion of the steam to remove condensed water in the steam and uniformly distribute the flow of the steam.
16. The method of claim 15,
And at least a part of an outer peripheral surface of the cover plate is supported by the inner wall of the flash tank.
16. The method of claim 15,
Wherein a drainage passage is formed on an outer peripheral surface of the cover plate so that condensed water removed from the steam can flow down to the bottom of the flash tank.
18. The method of claim 17,
Wherein the cover plate is tilted so as to gradually decrease from a central portion toward an outer peripheral surface.
16. The method of claim 15,
And a drain is formed at a central portion of the cover plate so that condensed water removed from the steam can flow down to the bottom of the flash tank.
The method of claim 19,
Wherein the cover plate is tilted so as to gradually decrease from an outer circumferential surface toward a central portion.
◈ Claim 21 is abandoned due to registration fee. The method according to claim 18 or 20,
Wherein the inclination angle is 1 DEG to 3 DEG.
16. The method of claim 15,
Wherein a surface of the cover plate is polished.
The method according to claim 1,
Wherein the flash tank further includes a safety valve that is opened when the pressure of steam rises to a predetermined pressure or higher.
◈ Claim 24 is abandoned due to registration fee. 24. The method of claim 23,
Wherein the safety valve is installed above the heat exchanger.
◈ Claim 25 is abandoned due to registration fee. 24. The method of claim 23,
Wherein the pressure of the steam is measured by a pressure sensor installed above the heat exchanger.
The method according to claim 1,
And the refrigerant is R-245fa.
Generating steam by heat generated by heat from the heat source to evaporate the refrigerant, compressing the evaporated gaseous refrigerant, and liquefying and diffusing the compressed high-temperature and high-pressure gaseous refrigerant;
Introducing the steam into the flash tank; And
And supplying a portion of the compressed high-temperature and high-pressure refrigerant to a heat exchanger in the flash tank to secondarily heat the steam in the flash tank,
The amount of the refrigerant flowing into the heat exchanger of the flash tank for supplying a portion of the compressed high-temperature and high-pressure refrigerant to the heat exchanger in the flash tank to secondarily heat the steam in the flash tank is preferably at least And the steam is supplied to the steam generator.
◈ Claim 28 is abandoned due to registration fee. 28. The method of claim 27,
Wherein the water level of the condensed water generated in the flash tank is measured and the condensed water is drained when the water level exceeds the reference water level.
◈ Claim 29 has been abandoned due to registration fee. 28. The method of claim 27,
A high-temperature steam supply method for reducing the amount of refrigerant supplied to the heat exchanger as the pressure in the flash tank is higher and increasing the amount of refrigerant supplied to the heat exchanger as the pressure in the flash tank is lower
◈ Claim 30 has been abandoned due to registration fee. 28. The method of claim 27,
Wherein the amount of the refrigerant supplied to the heat exchanger is decreased as the temperature T3 of steam in the flash tank is higher and the amount of refrigerant supplied to the heat exchanger is increased as the temperature of steam in the flash tank is lower.
◈ Claim 31 is abandoned upon payment of the registration fee. 28. The method of claim 27,
The refrigerant temperature T1 at the inlet of the heat exchanger of the flash tank is compared with the refrigerant temperature T2 at the outlet of the heat exchanger to increase the amount of refrigerant supplied as the difference between the two temperatures T1-T2 increases, A method for supplying high-temperature steam to increase the amount of refrigerant to be supplied.
◈ Claim 32 is abandoned due to registration fee. 28. The method of claim 27,
Wherein the steam is discharged to the outside of the flash tank when the pressure of the steam of the flash tank rises to a predetermined pressure or higher.
◈ Claim 33 is abandoned due to registration fee. 28. The method of claim 27,
Wherein the refrigerant is R-245fa.
KR1020150078322A 2015-06-03 2015-06-03 A Heat Pump System for Providing Highly Heated Steam KR101920781B1 (en)

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KR101895383B1 (en) 2017-06-26 2018-09-05 서울대학교산학협력단 Steam generating heat pump system
KR101987884B1 (en) * 2018-03-02 2019-06-11 한국에너지기술연구원 Integrated Steam Heat PumpSystem for Making Steam Directly and by Using Flash Tank
KR102074711B1 (en) * 2018-06-18 2020-02-07 주식회사 엔박 a steam generator using air compressing cooling heat
CN116163958A (en) * 2023-01-13 2023-05-26 上海诺通新能源科技有限公司 Vapor compressor system and control method thereof

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