KR101206794B1 - Heat Pump System With 2- Stage cascade Refrigeration Cycle - Google Patents

Abstract

PURPOSE: A heat pump system using a binary refrigerating cycle is provided to improve energy efficiency by respectively installing an auxiliary heat exchanger in a first stage heat pump system and a second stage heat pump system and to reduce peak load by producing cold water in summer season. CONSTITUTION: A heat pump system using a binary refrigerating cycle comprises a first stage heat pump and a second stage heat pump. A circulating line of a reservoir tank(70) is heat-exchanged with a first stage condenser(20a) or circulates hot water heated by heat-exchanging with a second stage condenser(20b) to the reservoir tank. When the outdoor temperature is over a predetermined temperature in spring, autumn, and winder, the first stage heat pump is independently operated. When the outdoor temperature is less than the predetermined temperature, the first and second stage heat pumps are simultaneously operated to generate hot water.

Description

Heat Pump System With 2-Stage Cascade Refrigeration Cycle}

The present invention adopts a dual refrigeration cycle to supply hot water during the spring season and winter season by utilizing the late night power in the late-night time zone with low general power and electric power demand, and assists each of the first stage heat pump system and the second stage heat pump system. The present invention relates to a heat pump system that improves energy efficiency by installing a heat exchanger, maintains a constant supply of hot water even when the outdoor air temperature is low in winter, and reduces the peak load in summer by producing cold water in summer.

In general, a refrigerant circulation cycle of a heat pump system includes a compressor for compressing a refrigerant gas to a condensation pressure in a state of high temperature and high pressure, a condenser for condensing the refrigerant compressed in the compressor to a liquid phase by heat radiation, and a high temperature condensed in the condenser. An expansion valve for throttling a liquid refrigerant in a high pressure state and expanding the gaseous refrigerant in a low pressure state, and cooling the air blown using latent heat of evaporation of the refrigerant while evaporating the refrigerant expanded in the expansion valve by heat exchange and Furnace to return the refrigerant gas. This heat pump system is a system in which the refrigerant is continuously phase-changed from gas to liquid and liquid to gas during a refrigerant circulation cycle, and the heating and cooling operations are switched in all directions. The heat pump generates hot water as a heating heat source. to be.

In addition, a normal heat pump is difficult to generate hot water of high temperature, and generates a small amount intermittently even if a high temperature heat source is generated. Therefore, when the outside air temperature decreases in winter, the performance decreases rapidly and the heat source temperature decreases, and the evaporation pressure and the specific volume of the compressor suction refrigerant increase, so that the compression ratio, which is the ratio of the discharge pressure of the compressor, increases, so that the compression efficiency decreases. This causes the compressor to burn out, and the condenser pressure is operated at high temperature and high pressure to make the heat source temperature high, causing the compressor to be overloaded and cause burnout. In addition, the existing heat exchanger for the superheat degree of the refrigerant vapor does not have a control function, causing the compressor motor to burn out due to excessive temperature rise of the discharge gas of the compressor, causing pyrolysis and sludge generation of the refrigerant oil, and As the specific volume is increased, the refrigerant suction amount is reduced to decrease the performance. In the conventional heat pump, as the capacity control device, the rotation speed control by the inverter, the number of cylinders of the compressor itself, and the bypass circuit inside the compressor are all. In the case of inverter control, capacity control and power saving are good, but they are expensive and there are many failures. Therefore, the number of compressor cylinders and the bypass control are available only in large refrigerators.

In the conventional heat pump system as described above, when the evaporation pressure drop and the condensation pressure rise are drastically deteriorated and the driving power of the compressor is increased, the compressor burns out and wastes energy, and when the outside air temperature decreases in winter, Low performance and high energy loss occur due to lowered volume and efficiency due to low evaporation temperature. In addition, in a typical heat pump system, when operating in one heat pump system, when the outside temperature decreases, the compression ratio, which is the ratio of the condensation pressure and the evaporation pressure, is large, which causes a decrease in compressor efficiency and performance degradation.

Registered Patent Publication No. 0639104 (October 20, 2006) Publication No. 10-2003-0031543 (2003.04.21) Publication No. 10-2010-0064751 (2010.06.15)

The present invention adopts a dual refrigeration cycle to supply hot water during the spring season and winter season by utilizing the late night power in the late-night time zone with low general power and electric power demand, and assists each of the first stage heat pump system and the second stage heat pump system. The present invention relates to a heat pump system that improves energy efficiency by installing a heat exchanger, maintains a constant supply of hot water even when the outdoor air temperature is low in winter, and reduces the peak load in summer by producing cold water in summer.

Heat pump system using a binary refrigeration cycle of the present invention comprises a first stage compressor (10a) for compressing the first refrigerant (A) at high temperature and high pressure; A first stage first condenser 20a or a first stage second condenser 200a for condensing and liquefying the first refrigerant A having a high temperature and high pressure; The first stage side heat exchanger connected to the first stage side condenser 20a or the second stage side condenser 200a to exchange heat with the low temperature low pressure refrigerant flowing from the first stage side evaporator 40a to the first stage side compressor 10a. Unit 100; A first stage expansion valve (30a) for making the first refrigerant (A) passed through the first stage side auxiliary heat exchanger unit (100) into a gas state of high temperature and low pressure; A first stage evaporator (40a) for vaporizing the first refrigerant (A) having passed through the first stage expansion valve (30a); A first stage side heat pump including a first stage side blow fan 50a of the first stage side evaporator 40a, and a second stage side compressor 10b for compressing the second refrigerant B at a high temperature and high pressure; A two-stage side condenser 20b for condensing and liquefying the first refrigerant B having a high temperature and high pressure; A two-stage loop heat sapon type auxiliary heat exchanger unit (200) connected to the two-stage side condenser (20b) to exchange heat with a low-temperature low pressure refrigerant flowing from the two-stage side evaporator (40b) to the two-stage compressor (10b); The two-stage side loop heat sapon type auxiliary heat exchanger unit 200 includes an evaporator 210, a vaporized steam flow path 220, a condensation part 230, and a liquefied vapor flow path 240 in which a third refrigerant C is circulated. A two-stage expansion valve (30b) which makes the second refrigerant (B) passed through the two-stage side loop heat sapon type auxiliary heat exchanger unit (100) into a gas state of high temperature and low pressure; It consists of a two-stage side heat pump comprising a; two-stage side evaporator (40b) for evaporating the second refrigerant (B) through the two-stage expansion valve (30b), the circulation line of the storage tank 70 is the first stage condenser The heat exchanger 20a or the second stage condenser 20b consists of a circulation line in which heated hot water is circulated to the water storage tank, and in the spring and winter, when the outside air temperature is higher than a predetermined temperature, the single stage side heat pump is operated alone. When the outside temperature is less than the predetermined temperature, the first stage side heat pump and the second stage side heat pump are characterized in that the hot water is produced at the same time.

When the outside temperature is higher than the predetermined temperature, hot water is produced without being heat-exchanged with the two-stage side condenser 20b.

In the summer, the first stage (A) flow path of the one-sided four sides (60a) is changed so that the first stage side evaporator (40a) functions as a condenser, so that the first stage side heat exchanger (20a) and the first stage side condenser-water heat exchanger (70a). It is characterized in that it is used as a cold heat source to produce cold water by heat exchange in.

A refrigerant pipe through which the second refrigerant B condensed in the second stage condenser 20b flows is located in the evaporation unit 210 of the second stage side loop heat sapon type auxiliary heat exchanger unit 200, and the third refrigerant C The second refrigerant (B) is cooled, the third refrigerant (C) is evaporated and flows to the condensation unit (230) through the vaporization steam flow path (220), and vaporizes in the second stage evaporator (40b). The refrigerant pipe through which the second refrigerant B flows is located in the condensation unit 230 of the second stage side heat exchanger subsidiary heat exchanger unit 200, and is heat-exchanged with the third refrigerant C to thereby exchange the second refrigerant B. ) Is superheated, and the third refrigerant (C) is condensed and flows through the liquefied vapor flow path 240 to the evaporator 210.

In the vaporization steam flow path 220 of the third refrigerant (C) circulation line of the two-stage side loop heatspan auxiliary heat exchanger unit 200, the vaporization steam flow path 220 is formed according to the discharge pressure of the two-stage compressor 10b. It further comprises an electric valve 221 for controlling the amount of refrigerant flowing.

The two-stage side loop heat-sponge type auxiliary heat exchanger unit 200 includes a gas storage 250 for the capacity control of the two-stage side heat exchanger and a capacity control cylinder 251 of the two-stage side heat exchanger on one side of the condenser 230. Thus, when the pressure in the evaporator 210 is high, the heat exchange area of the condensation unit is increased, and when the pressure in the evaporator 210 is low, the capacity of the second stage side heat exchanger is reduced to reduce the heat exchange area of the condenser. The cylinder 251 is characterized in that it is controlled to move.

The first stage side heat exchanger unit 100 includes an inner tube 120 through which the first refrigerant condensed in the first stage condenser 20a flows and an external tube through which the first refrigerant vaporized in the first stage side evaporator 40a flows. 130 is concentric, and made of a heat insulating cover 140 surrounding the outer tube 130, characterized in that the high-pressure liquid refrigerant and low-pressure steam refrigerant heat exchange.

The condensing pressure of the one-stage condenser 20a is installed at the inlet side of the inner tube 120 of the one-stage side heat exchanger unit 100 while reducing the pressure of the high-pressure liquid refrigerant condensed in the one-stage side condenser 20a by a predetermined pressure. It characterized in that it further comprises a pressure maintaining valve 110 to maintain.

An inlet is connected to the pipeline just before the first stage expansion valve 30a and an outlet is connected to the pipeline immediately after the first stage expansion valve 30a to store the excess first refrigerant A; The first pressure control check valve 152 and the pressure compensation tank 153 are installed in the inlet pipe of the pressure compensation tank 153 and open only when the pressure of the refrigerant liquid is higher than the predetermined pressure. It characterized in that it further comprises a pressure compensator (150) consisting of a check valve (155) for adjusting the second pressure to open only when the predetermined pressure or less.

When the outside air temperature is higher than the predetermined temperature in the spring and winter seasons, the single stage side heat pump is operated alone, and the first stage side condenser-water heat exchanger 70a is connected to the first stage side condenser 20b in the circulation line of the water storage tank 70. Heat is produced by heat exchange, and is bypassed without flowing into the two-stage condenser-water heat exchanger (70b) and introduced into the storage tank, and the outside air temperature is less than the predetermined temperature or the discharge water demand temperature of the storage tank 70 is more than the predetermined temperature. In this case, the first stage heat pump and the second stage heat pump are simultaneously operated, and the first stage condenser-water heat exchanger 70a is bypassed in the circulation line of the water storage tank 70, and the second stage condenser-water heat exchanger 70b is performed. It is characterized in that it further comprises a hot water circulation line for flowing to the second stage condenser (20b) to flow into the hot water is produced is introduced into the reservoir tank.

The present invention adopts a dual refrigeration cycle to supply hot water during the spring season and winter season by utilizing the late night power in the late-night time zone with low general power and electric power demand, and assists each of the first stage heat pump system and the second stage heat pump system. Due to the installation of a heat exchanger, the low outside air temperature prevents the refrigerant from absorbing the latent heat of evaporation sufficiently, resulting in poor evaporation, resulting in low dryness of the low pressure refrigerant, preventing compression failure by wet compression, and increasing the specific volume of the suction refrigerant This decreases the problem of not producing enough hot water, improving energy efficiency, and maintaining the hot water temperature even when the outside air temperature is low in winter, and producing cold water in summer to reduce the peak load in summer. It relates to a pump system.

1 is a hot water circulation when only the spring and winter season 1 stage heat pump driving only
2 is a hot water circulation diagram at the same time during the spring and winter seasons 1 stage side and 2 stage side heat pump
Figure 3 is a cold water circulation when driving the one-stage side heat pump for shrinkage cooling in summer
Figure 4a, b is a two-stage secondary heat exchange unit (loop thermosiphon heat exchanger) structure and operation diagram
5A and 5B show the structure of one-stage side heat exchange
6 is a refrigerant circulation diagram of the first stage side auxiliary heat exchange and the pressure compensator;

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

Looking at the heat pump system using the binary refrigeration cycle of the present invention shown in Figure 1, the first stage compressor (A) for compressing the first refrigerant (A) at high temperature and high pressure; A first stage first condenser 20a or a first stage second condenser 200a for condensing and liquefying the first refrigerant A having a high temperature and high pressure; The first stage side heat exchanger is connected to the first stage side condenser 20a or the second stage side condenser 200a to exchange heat with the low temperature low pressure refrigerant flowing from the first stage side evaporator 40a to the first stage side compressor 10a. Unit 100; A first stage expansion valve (30a) for making the first refrigerant (A) passed through the first stage side auxiliary heat exchanger unit (100) into a gas state of high temperature and low pressure; A first stage evaporator (40a) for vaporizing the first refrigerant (A) having passed through the first stage expansion valve (30a); A first stage side heat pump including a first stage side blow fan (50a) of the first stage side evaporator (40a), and a second stage side compressor (10b) for compressing the second refrigerant (B) at high temperature and high pressure; A two-stage side condenser 20b for condensing and liquefying the first refrigerant B having a high temperature and high pressure; A two-stage side loop heat sapon type auxiliary heat exchanger unit (200) connected to the two-stage side condenser (20b) to exchange heat with a low temperature low pressure refrigerant flowing from the two-stage side evaporator (40b) to the two-stage compressor (10b); The two-stage side loop heat sapon type auxiliary heat exchanger unit 200 includes an evaporator 210, a vaporized steam flow path 220, a condensation part 230, and a liquefied vapor flow path 240 in which a third refrigerant C is circulated. A two-stage expansion valve (30b) which makes the second refrigerant (B) passed through the two-stage side loop heat sapon type auxiliary heat exchanger unit (200) into a gas state of high temperature and low pressure; It consists of a two-stage side heat pump comprising a; two-stage side evaporator (40b) for evaporating the second refrigerant (B) through the two-stage expansion valve (30b), the circulation line of the storage tank 70 is the first stage condenser The heat exchanger 20a or the second stage condenser 20b consists of a circulation line in which the heated hot water is circulated to the water storage tank.

In addition, the first refrigerant A is 410A, the second refrigerant B is 134A, and the third refrigerant is ethanol.

The generated hot water is used for heating in the spring and winter seasons, and when the outside air temperature is more than 2 ℃, a predetermined temperature, by driving only the one-stage side heat pump as shown in Figure 1 to produce hot water. The hot water has a temperature range of about 50 ℃. At this time, the first check valve 71 of the hot water circulation line is opened and flows to the first stage condenser-water heat exchanger 70a so that the water in the hot water line is connected to the first refrigerant A of the condenser 20a of the first stage heat pump. The heat exchange produces hot water, and the two stage side heat pump is not driven. At this time, the hot water passing through the first stage condenser-water heat exchanger 70a does not flow into the second stage condenser-water heat exchanger 70b by opening the second check valve 72 and enters the water storage tank 70.

In addition, when the outside temperature is less than 2 ℃ or the hot water temperature to be discharged from the water storage tank 70 is 50 ℃ or more, as shown in FIG. 2, the first stage heat pump and the second stage side heat pump are simultaneously driven. At this time, the first stage check valve of the hot water circulation line of the water storage tank 70 is closed to bypass the first stage condenser-water heat exchanger 70a, and the second stage check valve 72 is closed to close the second stage condenser-water heat exchanger. The water flows to 70b and the water of the hot water line exchanges heat with the second refrigerant B of the condenser 20b of the two-stage heat pump to become hot water, and then enters the water storage tank 70. The first refrigerant A discharged from the first stage compressor 10a flows to the first stage second condenser 200a without being flowed to the first stage side condenser 20a and is heat-exchanged with the second stage side evaporator 40b. The problem that the evaporation pressure is insufficient in the evaporator 40b of the heat pump is solved.

In addition, as shown in Figure 4a, the two-stage side heat pump is connected to the two-stage condenser (20b), the two-stage side loop heat-sponge type auxiliary heat exchanged with the low-temperature low-pressure refrigerant flowing from the two-stage side evaporator (40b) to the two-stage compressor (10b) It has a heat exchanger unit 200.

The two-stage side loop heat sapon type auxiliary heat exchanger unit 200 includes an evaporator 210, a vaporized steam flow path 220, a condensation part 230, and a liquefied vapor flow path 240 in which a third refrigerant C is circulated. If you look at the operation process,

The refrigerant pipe of the second stage condenser outlet line 21b on which the second refrigerant B condensed in the second stage condenser 20b flows is the evaporation unit 210 of the second stage side heat exchanger subsidiary heat exchanger unit 200. Located in the chamber, the second refrigerant (B) is cooled and flows to the second stage expansion valve (30b) through the second stage expansion valve inlet line (22b), and the third refrigerant (C) is heat exchanged with the third refrigerant (C). ) Is vaporized and flows through the vaporization steam flow path 220 to the condensation unit 230, the second stage evaporator outlet line 41b side through which the second refrigerant B vaporized in the second stage evaporator 40b flows. A refrigerant pipe is located in the condensation unit 230 of the two-stage side loop heat sapon type auxiliary heat exchanger unit 200, and heat exchanges with the third refrigerant C so that the second refrigerant B is overheated and the two stage side compressor 10b. The inlet line 42b flows to the second stage compressor 10b, and the third refrigerant C is condensed and flows to the evaporator 210 through the liquefied vapor flow path 240.

At this time, the second stage side evaporator outlet line 41b through which the second refrigerant B vaporized in the second stage side evaporator 40b located in the condensation unit 230 of the two stage side side heat exchanger subsidiary heat exchanger unit 200 flows. When the refrigerant superheat of the refrigerant pipe is sufficient and the pressure discharged from the compressor is within the range of the normal pressure, it is necessary to block or reduce the flow of the third refrigerant C flowing in the vaporization steam flow path 220. have. As a method of controlling this, the amount of refrigerant is controlled by driving the electric valve 221 which detects the discharge pressure of the compressor and controls the amount of refrigerant flowing into the vaporization steam flow path 220.

Another method of controlling the flow of the third refrigerant (C) flowing in the two-stage side loop heatspan auxiliary heat exchanger unit (200) is shown in Figure 4b. The two-stage side loop heatsonic subsidiary heat exchanger unit 200 includes a gas storage unit 250 for adjusting the capacity of the two-stage side heat exchanger and a capacity control cylinder 251 for the two-stage side heat exchanger on one side of the condensation unit 230. When the pressure at the evaporation unit 210 of the two-stage side loop heatsonic auxiliary heat exchanger unit 200 is high, the capacity adjusting cylinder 251 located at the condensation unit 230 is moved by the pressure of the vaporized vapor refrigerant. Push back to increase the heat exchange area in the condensation unit 230 of the two-stage side loop heatsonic auxiliary heat exchanger unit 100, and in the evaporation unit 210 of the two-stage side loop heatsonic auxiliary heat exchanger unit 100. When the pressure is low, the vaporizing steam of the third refrigerant (C) is pushed to the discharge side by the pressure of the capacity adjusting cylinder 251 located in the condensation unit to the discharge side of the second stage heat exchanger auxiliary heat exchanger unit ( Heat exchange surface at condensation unit 230 of 100 A is controlled to decrease. This control method is to change the heat exchange area according to the pressure in the evaporator 210 of the subsidiary heat exchanger unit 100 and the relative pressure between the gas reservoir 250 for the capacity control of the second stage side subsidiary heat exchanger.

The first stage side heat exchanger unit 100 shown in Figure 5a, 5b is composed of a heat exchanger, a pressure maintaining valve 110 consisting of an outer tube 130, an insulating cover 140 on the outer side of the inner tube 120, If you look at how it works,

The first refrigerant (A) of medium temperature and high pressure flowing in the outlet line (21a) of the first stage condenser (20a) is introduced into the inner tube (120), and the steam refrigerant flowing in the outlet line (41a) of the first stage side evaporator (40a). Heat exchanged with the outer tube 130 into which the inlet is introduced, and the first refrigerant A having a medium temperature and high pressure flowing through the inner tube 120 flows to the inlet side line 22a of the first stage expansion valve 30a, and the outer tube ( The steam refrigerant flowing through 130 is flowed into the inlet line 42a of the first stage compressor 10a.

In addition, Figure 6 is arranged between the first stage side heat exchanger unit 100 and the first stage side condenser (20a) while maintaining the condensation pressure of the first stage side condenser (20a) to the predetermined high-pressure high-temperature liquid refrigerant to medium pressure medium temperature Pressure maintaining valve 110 for lowering the pressure is further configured. The first stage side heat exchanger unit 100 has an inner tube 120 which is continuously banded in a zigzag form to have a predetermined heat exchange length, an outer tube 130 which concentrically receives the inner tube 120, and their It is made of a heat insulating cover 140 to prevent heat loss. The outer tube 130 accommodates the inner tube 120 concentrically therein and is configured such that the cross section of the flow path is the same as the flow cross section of the evaporator 40a except for the entire cross-sectional area including the thickness of the inner pipe 120. do. The insulation cover 140 is composed of a tubular insulation material to surround the outer tube 130 itself.

The pressure maintaining valve 110 is installed at the inlet side of the inner tube 120 of the first stage side heat exchanger unit 100 to reduce the cross-sectional area of the flow path such that the refrigerant liquid condensed in the condenser 20a is not atomized. To keep the pressure of the refrigerant liquid different before and after.

The pressure compensator 150 may be provided together to maintain a constant pressure and evaporation pressure of the refrigerant liquid so as not to be affected by load variation. The pressure compensator 150 includes a pressure compensating tank 153 for storing excess refrigerant in the system, and a first pressure for guiding the extra refrigerant fluid to the pressure compensating tank 153 when the pressure of the refrigerant is higher than a predetermined set value. The control check valve 152 and the second pressure control check valve 155 for flowing out the refrigerant in the pressure compensation tank 153 when the evaporation pressure is lower than a predetermined set value. The pressure compensation tank 153 has an inlet connected to the conduit 151 immediately before the expansion valve and an outlet connected to the conduit 41a immediately after the expansion valve. The first pressure control check valve 152 is installed in the inlet conduit 151 of the pressure compensation tank 153 to open only when the pressure of the refrigerant liquid is greater than or equal to the predetermined pressure, and the second pressure control check valve 155 is pressure compensated. It is installed in the outlet duct 154 of the tank 153 and is opened only when the pressure of the expanded refrigerant is below a predetermined pressure.

As another example, a shrinkage heat method for cooling cold water by using cold water produced during a peak peak load during the summer during the peak load is stored in the storage tank.

3 shows a shrinkage heat pump for cooling cold water by only driving the one-stage side heat pump by using a late-night electric power. The first stage side heat exchanger 20a and the first stage side evaporator-water heat exchanger 70a of the circulation line of the storage tank produce cold water and are stored in the storage tank 70. If you look at how it works,

The flow direction of the first stage first refrigerant A is operated in the reverse direction of operation during heating. That is, the first refrigerant (A) of high temperature and high pressure flows from the first stage compressor (10a) to the heat exchanger (40a) to exchange heat, and then passes through the first stage expansion valve (30a) and then the first stage side secondary heat exchange unit (100) and the first stage. After passing through the pressure holding valve 110, the first stage side heat exchanger (20a) and the first stage side heat exchanger (70a) after heat exchange enters the first stage compressor (10a) inlet line.

1 and 2 shows a circulation line of the water storage tank 70 during the single stage operation or the first stage and the second stage simultaneous operation of the heat pump. Looking at the circulation line,

If the outside air temperature is higher than the predetermined temperature, the single stage side heat pump is operated alone, and the first check valve 71 is opened in the circulation line of the water storage tank 70 to the first stage side condenser-water heat exchanger 70a. Water is flowed to exchange heat with the first refrigerant (A) of the first stage condenser (20a) to produce hot water, and the second check valve (72) is opened to not flow to the second stage condenser-water heat exchanger (70b). Bypassed into the reservoir tank.

In addition, when the outside temperature is less than the predetermined temperature or the discharge water demand temperature of the water storage tank 70 is more than the predetermined temperature, the first stage side heat pump and the second stage side heat pump are simultaneously operated, and the first of the circulation lines of the storage tank 70 is operated. By closing the check valve 71, the water in the circulation line is bypassed to the first stage condenser-water heat exchanger 70a, and the second check valve 72 is closed to close the water in the circulation line to the second stage condenser-water heat exchanger. It has a hot water circulation line that flows to (70b) to heat exchange with the second refrigerant (B) of the two-stage condenser (20b) to produce hot water is introduced into the reservoir tank.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is to be understood that the invention is not limited to the disclosed exemplary embodiments. Therefore, the embodiments disclosed in the present invention are not intended to limit the technical spirit of the present invention but to describe the present invention, and the technical scope of the present invention is not limited by these embodiments. The scope of protection of the present invention should be construed according to the following claims, and all technical ideas within the scope of equivalents should be construed as falling within the scope of the present invention.

10a: single stage compressor 10b: two stage compressor
20a: 1st stage first condenser 20b: 2nd stage condenser
200a: 1st stage 2nd condenser
21a: 1st stage condenser outlet line 21b: 2nd stage condenser outlet line
22a: 1st stage expansion valve inlet line 22b: 2nd stage expansion valve inlet line
23a, 230a: condenser inlet open / close valve 24a, 240a: condenser outlet open / close valve
30a: 1st stage expansion valve 30b: 2nd stage expansion valve
40a: single stage evaporator 40b: two stage evaporator
41a: 1st stage evaporator side outlet line 41b: 2nd stage evaporator side outlet line
42a: 1st stage compressor inlet line 42b: 2nd stage compressor inlet line
50a: 1 stage blower
60a: One-sided Four Sides 60b: Two-sided Four Sides
70a: one-stage condenser-water heat exchanger 70b: two-stage condenser-water heat exchanger
70: reservoir tank 71, 72: first and second check valve
75: circulation pump
100: 1 side auxiliary heat exchange unit
110: pressure holding valve 120: inner tube
130: outer tube 140: insulation cover
150: pressure compensator 151: branch line after the first stage secondary heat exchange
152: check valve for the first pressure adjustment 153: pressure compensation tank
155: second pressure control check valve
200: 2-stage auxiliary heat exchange unit (loop thermosiphon heat exchanger)
210: evaporation section of the two-stage side heat exchanger 220: vaporization steam flow path of the two-stage side heat exchanger
221: electric valve for controlling the amount of refrigerant in the second stage side heat exchanger
230: Condensation unit of the two-stage side heat exchanger 240: Liquefied steam flow path of the two-stage side heat exchanger
250: gas storage for capacity control of two stage secondary heat exchanger
251: cylinder for capacity regulation of the second stage side heat exchanger

Claims (10)

A first stage compressor (10a) for compressing the first refrigerant (A) at high temperature and high pressure;
A first stage first condenser 20a or a first stage second condenser 200a for condensing and liquefying the first refrigerant A having a high temperature and high pressure;
The first stage side heat exchanger is connected to the first stage side condenser 20a or the second stage side condenser 200a to exchange heat with the low temperature low pressure refrigerant flowing from the first stage side evaporator 40a to the first stage side compressor 10a. Unit 100;
A first stage expansion valve (30a) for making the first refrigerant (A) passed through the first stage side auxiliary heat exchanger unit (100) into a gas state of high temperature and low pressure;
A first stage evaporator (40a) for vaporizing the first refrigerant (A) having passed through the first stage expansion valve (30a);
Consists of a one-stage side heat pump including; one-stage side blowing fan 50a of the one-stage side evaporator 40a,
A two stage compressor (10b) for compressing the second refrigerant (B) at high temperature and high pressure;
A two-stage side condenser 20b for condensing and liquefying the first refrigerant B having a high temperature and high pressure;
A two-stage side loop heat sapon type auxiliary heat exchanger unit (200) connected to the two-stage side condenser (20b) to exchange heat with a low temperature low pressure refrigerant flowing from the two-stage side evaporator (40b) to the two-stage compressor (10b);
The two-stage side loop heat sapon type auxiliary heat exchanger unit 200 includes an evaporator 210, a vaporized steam flow path 220, a condensation part 230, and a liquefied vapor flow path 240 in which a third refrigerant C is circulated. It consists of
A two-stage expansion valve (30b) for making the second refrigerant (B), which has passed through the two-stage side loop heatsonic auxiliary heat exchanger unit (200), into a gas state at high temperature and low pressure;
Consists of a two-stage side heat pump comprising a; two-stage side evaporator (40b) for evaporating the second refrigerant (B) through the two-stage expansion valve (30b),
The circulation line of the reservoir tank 70 is heat-exchanged with the first stage condenser 20a, or the hot water heated by heat exchange with the second stage condenser 20b.
In the spring and winter, when the outside air temperature is higher than the predetermined temperature, the single-stage heat pump is operated alone, and when the outside temperature is less than the predetermined temperature, the first-stage heat pump and the second-stage heat pump are operated simultaneously to produce hot water. Heat pump system using a binary refrigeration cycle. The method of claim 1,
When the outside air temperature is less than a predetermined temperature, the first stage condenser 20a and the first stage condenser-water heat exchanger 70a of the hot water circulation line are not heat-exchanged, and the second stage condenser 20b and the hot water circulation line are Heat pump system using a two-stage side condenser-water heat exchanger (70b) heat exchange to produce hot water. The method of claim 1,
In the summer season, the first stage (A) flow path of the first stage side-side (60a) is changed so that the first stage side evaporator (40a) functions as a condenser so that the first stage side heat exchanger (20a) and the first stage side condenser-water heat exchanger ( Heat pump system using a dual refrigeration cycle, characterized in that 70a) is heat exchanged to produce cold water. The method of claim 1,
A refrigerant pipe through which the second refrigerant B condensed in the second stage condenser 20b flows is located in the evaporation unit 210 of the second stage side loop heat sapon type auxiliary heat exchanger unit 200, and the third refrigerant C The second refrigerant (B) is cooled, the third refrigerant (C) is evaporated and flows to the condensation unit (230) through the vaporization steam flow path (220), and vaporizes in the second stage evaporator (40b). The refrigerant pipe through which the second refrigerant B flows is located in the condensation unit 230 of the second stage side heat exchanger subsidiary heat exchanger unit 200, and is heat-exchanged with the third refrigerant C to thereby exchange the second refrigerant B. ) Is overheated, and the third refrigerant (C) is condensed and flows to the evaporator 210 through the liquefied vapor flow path 240, the heat pump system using a two-way refrigeration cycle. 5. The method of claim 4,
In the vaporization steam flow path 220 of the third refrigerant (C) circulation line of the two-stage side loop heatspan auxiliary heat exchanger unit 200, the vaporization steam flow path 220 is formed according to the discharge pressure of the two-stage compressor 10b. Heat pump system using a binary refrigeration cycle, characterized in that it further comprises an electric valve for controlling the amount of refrigerant flowing. 5. The method of claim 4,
The two-stage side loop heatsonic subsidiary heat exchanger unit 200 includes a gas storage unit 250 for adjusting the capacity of the two-stage side heat exchanger and a capacity control cylinder 251 for the two-stage side heat exchanger on one side of the condensation unit 230. Thus, when the pressure in the evaporator 210 is high, the heat exchange area of the condensation unit is increased, and when the pressure in the evaporator 210 is low, the capacity of the second stage side heat exchanger is reduced to reduce the heat exchange area of the condenser. Heat pump system using a binary refrigeration cycle, characterized in that the cylinder 251 is controlled to move. The method according to any one of claims 1 to 3,
The first stage side heat exchanger unit 100 includes an inner tube 120 and a first stage evaporator 40a through which the first refrigerant condensed in the first stage first condenser 20a or the first stage second condenser 200a flows. The outer tube 130, the condensation of the first refrigerant flows in the condensation, and consists of a heat insulating cover 140 surrounding the outer tube 130, two-way refrigeration characterized in that the high-pressure liquid refrigerant and low-pressure steam refrigerant heat exchange Cycle heat pump system. The method of claim 7, wherein
The first stage side condenser 20a or 1 is installed at the inlet side of the inner tube 120 of the first stage side heat exchanger unit 100 and the pressure of the high pressure liquid refrigerant condensed in the first stage side condenser 20a is reduced by a predetermined pressure. Heat pump system using a two-way refrigeration cycle, characterized in that it further comprises a pressure maintaining valve (110) for maintaining the condensation pressure of the second side condenser (200a). 9. The method of claim 8,
Inlet is connected to the pipeline immediately before the first stage expansion valve (30a) and the outlet is connected to the pipeline immediately after the first stage expansion valve (30a) and the pressure compensation tank 153 for storing the first refrigerant (A) and the pressure The first pressure control check valve 152 installed in the inlet pipe of the compensation tank 153 and opened only when the pressure of the refrigerant liquid is equal to or greater than the predetermined pressure, and the evaporation pressure is installed in the outlet pipe of the pressure compensation tank 153. Heat pump system using a dual refrigeration cycle, characterized in that it further comprises a pressure compensator (150) consisting of a second pressure control check valve (155) to open only when the following. The method of claim 1,
When the outside air temperature is higher than the predetermined temperature in the spring and winter seasons, the single stage side heat pump is operated alone, and the first stage side condenser-water heat exchanger in the circulation line of the water storage tank 70 exchanges heat with the first stage side condenser 20a. Hot water is produced, bypassed without flowing into the two-stage condenser-water heat exchanger (70b) and introduced into the reservoir tank,
If the outside air temperature is lower than the predetermined temperature or the water discharge demand temperature of the water storage tank 70 is higher than the predetermined temperature, the first stage side heat pump and the second stage side heat pump are simultaneously operated, and the first stage condenser in the circulation line of the storage tank 70 The water heat exchanger 70a bypasses and flows to the two-stage condenser-water heat exchanger 70b to exchange heat with the two-stage condenser 20b so that hot water is produced and introduced into the water storage tank. Heat pump system using a binary refrigeration cycle, characterized in that.

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