KR100794271B1 - Heat pump system that use duality compression type - Google Patents

Abstract

A heat pump system in the dual compression structure is provided to utilize compressors for high and low temperatures independently from each another for carrying out cooling/heating operation according to refrigerant characteristics, thereby achieving optimum operation of the compressors and local cooling/heating operation, and generating hot water during the cooling/heating operation. A heat pump system in the dual compression structure includes a refrigerant cycle part of low temperature(10) for inducing refrigerant flow of low temperature, and a refrigerant cycle part of high temperature(20) for inducing refrigerant flow of low temperature. The high and low temperature refrigerant cycle parts are formed independently from each other, and operate complementarily with each other. The high and low temperature refrigerant cycle parts are connected to a refrigerant-exclusive heat exchanger(30) for carrying out heat exchange of different two kinds of refrigerant. The heat exchanger is connected to the high and low temperature refrigerant cycle parts by a circulation line(40). The circulation line has a variable refrigerant line part(50) for circulating liquid refrigerant of high temperature generated in the high temperature refrigerant cycle part therein or controlling refrigerant flow sequence to circulate the refrigerant to the heat exchanger in the case of hot water generation.

Description

Heat pump system that use duality compression type

1 is a heat pump and system for a heating and cooling system employing a conventional one-stage compression method.

2 is a system diagram of winter heating and hot water supply operation system of a heat pump and a system using a binary compression method according to an embodiment of the present invention.

3 is an enlarged view of a variable refrigerant line unit showing an enlarged circulation process of a high temperature side refrigerant during hot water supply as a partial enlarged view of FIG. 2 according to an embodiment of the present invention;

Figure 4 is a system diagram during the summer cooling center operation of the heat pump and the system using a binary compression method as an embodiment of the present invention.

FIG. 5 is an enlarged view of a variable refrigerant line unit illustrating an enlarged circulation process of a high temperature side refrigerant during a cooling center operation as a partial enlargement of FIG. 4 as an embodiment of the present invention; FIG.

* Description of the symbols for the main parts of the drawings

10; Low temperature refrigerant cycle unit 11; First compressor

12; First condenser 13; 1st expansion valve

14; First evaporator 20; High Temperature Refrigerant Cycle

21; Second compressor 22; 2nd condenser

23; Second expansion valve 24; 2nd evaporator

30; Heat exchanger 40; Circulation line

50; Variable refrigerant line unit 100; Heat storage tank

200; A cold storage tank 300; Hot water tank

400; Make-up tank

The present invention relates to a heat pump system for cooling and heating, and more particularly, to a heat pump system using a dual compression method in which a compressor is divided into a low temperature and a high temperature as a dual compression method to perform a cooling and heating operation suitable for refrigerant characteristics. It is about.

In general, the heat pump system, as shown in Figure 1 attached to the refrigerant consists of the flow of the compressor (1) → condenser (2) → expansion valve (3) → evaporator (4) → compressor (1).

At this time, the compressor 1 compresses the low temperature gas of low temperature introduced from the evaporator 4 and heats it up to a high temperature high pressure gas to send it to the condenser 2, and the condenser 2 is introduced from the compressor 1. The high temperature high pressure gas and the hot water flowing from the hot water tank is heated to heat up, and the high temperature high pressure gas is converted into a medium temperature liquid refrigerant and sent to the expansion valve (3).

 In general, the condenser (2) uses a shell-and-tube type that is strong in pressure because high-temperature, high-pressure gas and hot water are heat-exchanged, but a plate-type heat exchange method is also available.

Next, the expansion valve (3) expands the medium-temperature liquid refrigerant flowing from the condenser (2) is converted into a low-temperature refrigerant and then supplied to the evaporator (4),

The evaporator (4) is a low-temperature refrigerant flowing through the expansion valve (3) in the condenser (2) to produce a low-temperature cold water by heat exchange with the cold water tank and the water pipe circulated, the evaporator (4) has an internal configuration of the condenser Similar to (2), shell-and-tube or plate heat exchangers may be used.

However, while the conventional heat pump system has the same basic cycle as the refrigerator and the condensate temperature of the refrigerator is 32 ° C. to 37 ° C., the heat pump has a compressor 1 and a condenser 2 so as to produce hot water of 50 ° C. or more. However, this results in a high discharge gas temperature from the compressor 1, thereby increasing the high pressure, increasing the compression ratio, increasing the power consumption, and increasing the oil carbonization phenomenon, thereby shortening the compressor life.

In addition, the heat pump adopts a compression method of a screw or scroll, which is durable at high pressure, in place of the turbo compressor 1, in particular, a heater that requires intensive hot water. Since the condensate gas temperature rises in order to increase the condensation temperature, the liquid refrigerant temperature passing through the condenser 2 is also formed high, so that the temperature of the liquid refrigerant passing through the expansion valve 3 increases, thereby reducing the evaporation efficiency. Since the cold water temperature is increased, when cold and hot water are used at the same time, there is a disadvantage in that the overall COP is reduced but the equipment is badly operated.

In addition, most of the heat pump refrigerants currently used use R22. The refrigerant of R22 has good low temperature characteristics, but at a high temperature, the pressure rises rapidly and the power consumption is excessive. If the operation is longer than that, there is a problem that the service life of the compressor 1 is shortened rapidly.

In addition, when operating the heat storage tank (7) and the cold storage tank (8) to which the hot water pump (5) and the cold water pump (6) is connected for the heat storage operation, the heat storage tank (7) if the production hot water temperature is low Larger and higher production cold water temperature leads to a larger cold storage tank (8), which inevitably leads to a larger load facility (AHU, FCU), which is a structural problem that makes normal heating and cooling impossible when utilizing existing load facilities. There is this.

Accordingly, the present invention has been made to solve the above-mentioned conventional problems, and by developing a heat pump that is capable of cooling and heating operation suitable for refrigerant characteristics by dividing the compressor into low temperature and high temperature as a binary compression method, each compressor is Operation is possible in the best condition, and the heat exchange function between refrigerants is added according to the operating conditions to produce high quality cold water and hot water by maximizing the efficiency of each other, and low temperature or high temperature for local cooling and heating depending on the season. As it is designed to operate independently, the operation cost can be eliminated according to the entire operation, and the cooling and heating can be partially performed even if a problem such as a compressor occurs. User's economical efficiency (investment cost and Operating cost), by improving the response to load fluctuations and by extending the service life of the equipment, greatly improving and supplementing the shortcomings of the existing heat pump to spread the supply, absorbing the economic burden of rising oil prices, and reducing the consumption of fossil energy. It is an object of the present invention to provide a heat pump system using a binary compression method to contribute to pollution prevention.

The heat pump system using the present dual compression method invented to achieve the above object, the low temperature refrigerant cycle unit for inducing a low temperature refrigerant flow; A high temperature refrigerant cycle unit configured to be independent of the low temperature refrigerant cycle unit and induce high temperature cold flow; The low-temperature and high-temperature refrigerant cycle unit is configured to be connected to a refrigerant heat exchanger having a complementary function by heat-exchanging two kinds of refrigerants having different characteristics from each other. And the heat exchanger are connected by a circulation line, but the circulation line itself circulates the high temperature liquid refrigerant generated in the high temperature refrigerant cycle unit, and during the production of hot water, the refrigerant flow order is freely adjusted to be circulated to the refrigerant heat exchanger. Variable refrigerant line unit; It characterized in that the configuration.

According to another aspect, the low-temperature refrigerant cycle unit, the first compressor for compressing the low-temperature low-pressure gas generated in the first evaporator to be described later to increase the high-temperature high-pressure gas; A first condenser for first warming up the hot water circulated in the heat storage tank by using the high pressure gas heated at the first compressor and then converting the high temperature and high pressure gas into a high temperature liquid refrigerant; A first expansion valve for expanding the medium-temperature liquid refrigerant passing through the heat exchanger and converting the medium-temperature liquid refrigerant into a low temperature liquid refrigerant; A first evaporator for lowering the cold water temperature circulated from the cold storage tank by using the low temperature liquid refrigerant passing through the first expansion valve and evaporating the liquid refrigerant to low temperature low pressure gas by using heat absorbed from the cold water; It includes.

According to another aspect, the high temperature refrigerant cycle unit, a second compressor to be described later to compress the low-temperature low-pressure gas generated in the second evaporator and the heat exchanger to discharge the high-temperature compressed gas; By using the high-temperature high-pressure gas introduced from the second compressor, the hot water firstly heated up by the first condenser included in the low-temperature refrigerant cycle unit is secondly heated to a higher temperature, and the high-temperature high-pressure gas is heated to a high temperature liquid. A second condenser for phase converting into a refrigerant; A second expansion valve for expanding a high temperature liquid refrigerant converted from the second condenser to a low temperature liquid refrigerant or expanding a medium temperature liquid refrigerant through a second evaporator; Cooling the circulating water with a low temperature liquid refrigerant converted from the second expansion valve to serve as an evaporator for cold water production, or by heating the high temperature liquid refrigerant without passing through the second expansion valve with hot water circulated from the hot water tank to raise the temperature A second evaporator functioning as a heat exchanger (condenser); It includes.

According to another aspect, the heat exchanger is characterized in that the operation of the heat exchanger and the evaporator is selectively made in accordance with the change of the role of the second evaporator to enable the production of cold water or hot water according to the season and operating conditions.

According to another aspect, the circulation line is a first circulation line connecting the second compressor and the second condenser, a second circulation line connecting the second compressor and the heat exchanger, connecting the second condenser and the second evaporator A third circulation line, a fourth circulation line connecting the hot water passing through the first condenser to be circulated to the second condenser, a fifth circulation line having a high temperature water passing through the second condenser and a fourth circulation line and a branching line, and A sixth circulation line connecting the first compressor and the first condenser, a seventh circulation line connecting the first compressor and the first evaporator, an eighth circulation line connecting the first condenser and the heat exchanger, the heat exchanger and the first A ninth circulation line connecting an evaporator and having a first expansion valve installed thereon, and a tenth circulation line connecting the heat exchanger and a second evaporator and having a second expansion valve and a variable refrigerant line installed thereon And an eleventh circulation line connecting the third and ten circulation lines in parallel.

According to another aspect, the first condenser is connected to the heat storage tank through a twelfth circulation line, the first evaporator is connected to the heat storage tank through a plurality of fourteen circulation lines, the second evaporator is a plurality of It is characterized in that the connection to the hot water supply tank and the supplemental water tank through the thirteenth circulation line.

According to yet another aspect, the variable refrigerant line unit,

In order to circulate the high temperature liquid refrigerant flowing from the second condenser into the second evaporator and the second expansion valve so that the second evaporator included in the high temperature refrigerant cycle part functions as a heat exchanger and an evaporator, cold water may be produced in the second evaporator. In this case, the high temperature liquid refrigerant is circulated through the second expansion valve to the evaporator, and when producing hot water, the high temperature liquid refrigerant passing through the second evaporator is configured to have a refrigerant flow that circulates through the second expansion valve to the refrigerant heat exchanger. It features.

According to yet another aspect, the variable refrigerant line unit,

A first 3-way control valve configured in a third circulation line and configured to circulate a high temperature liquid refrigerant flowing from the second condenser to a second expansion valve or a second evaporator by selecting a supply path;

The second control of the three-way method is configured in the tenth circulation line, and the opening direction is determined by the second expansion valve or the second evaporator according to the opening direction of the first control valve to determine the direction of the refrigerant circulated to the heat exchanger. valve; And,

When forming a parallel line of multiple stages in the tenth circulation line is formed in the parallel line, so as to change the high-temperature liquid refrigerant passing order made between the first and second evaporators according to the opening direction of the first and second control valves. Directional first to fourth check valves for preventing reverse flow; It includes.

According to another aspect, the fifth circulation line comprises a 2-way first and second flow path determining valves for determining the flow path of the hot water according to the hot water temperature and operating conditions generated in the first and second condensers. It is done.

According to another aspect, the first flow path valve is closed only when hot water is not needed or when low temperature hot water is used, and the hot water passing through the first condenser is reheated through the second condenser to produce hot water. When the temperature of the hot water is less than the set temperature, the opening angle is proportionally controlled by the temperature sensor so as to adjust the hot water temperature while increasing or decreasing the circulation flow rate of the hot water.

According to another aspect, the second flow path determination valve is closed control when producing hot water, and when hot water is not needed or low temperature, such as summer, open control so that the hot water is purified through the heat storage tank without passing through the second condenser. Characterized in that made.

According to another aspect, the tenth circulation line is opened in the direction of the second compressor to guide the low-temperature low-pressure gas heat exchanged in the second evaporator to the second compressor without passing through the heat exchanger in seasons when high temperature water is not needed. In the heating season in which high temperature water is required, a third control valve of 3-way type is opened to the heat exchanger to evaporate the hot water for hot water supplied from the second evaporator and the medium temperature liquid refrigerant exchanged with the heat exchanger.

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

FIG. 2 is a schematic diagram illustrating a winter use of a heat pump system using a binary compression method according to an embodiment of the present invention, and FIG. 3 is an enlarged view of the circulation process of the high-temperature refrigerant during hot water supply as a partial enlargement of FIG. 4 is an enlarged view of a variable refrigerant line unit, and FIG. 4 is a system system diagram during a summer cooling center operation of a heat pump and a system using a dual compression method as an embodiment of the present invention, and FIG. 5 is an embodiment of the present invention. As an enlarged view, the enlarged view of the variable refrigerant line portion showing the circulation process of the high-temperature refrigerant during the cooling center operation is shown.

2 to 5, the heat pump system using the dual compression method according to an embodiment of the present invention, the low temperature refrigerant cycle unit 10, the high temperature refrigerant cycle unit 20, heat exchanger 30, circulation line 40, and a variable refrigerant line unit 50.

The low temperature coolant cycle unit 10 induces a low temperature coolant flow and includes a first compressor 11, a first condenser 12, a first expansion valve 13, and a first evaporator 14.

The first compressor 11 is configured to compress the low temperature gas of low temperature generated by the first evaporator 14 to increase the temperature of the high pressure gas to a high pressure gas, and then supply the same to the first condenser 12. In consideration of the operating conditions of the first evaporator 14 in which the condensation temperature of the condenser 12 is relatively lower than that of the second condenser 22 and the cold water temperature is to be lowered, R410 refrigerant or R410, which is excellent in low temperature characteristics, is selected. Composed of screw type compressor.

The first condenser 12 uses a high pressure gas of a high temperature heated from the first compressor 11 to firstly warm up the hot water circulated in the heat storage tank 100 (for example, 50 ° C. to 55 ° C.). It is configured to phase convert the high pressure gas into liquid refrigerant of high temperature (eg, 60 ° C.), and the heat exchange method uses a shell and tube heat exchanger in consideration of high temperature and high pressure characteristics.

The first expansion valve 13 is configured to expand the medium-temperature liquid refrigerant having passed through the heat exchanger 30 into a low-temperature liquid refrigerant and to supply it to the first evaporator 14.

The first evaporator 14 heat-exchanges the low-temperature liquid refrigerant converted from the first expansion valve 13 and the circulating water of medium temperature (eg, 15 ° C) circulated in the storage tank 200 to form cold water (eg, 5 ° C). ), And evaporate the liquid refrigerant absorbing the heat of the cold water to supply low temperature low pressure gas to the first compressor (11), wherein the high temperature liquid refrigerant supplied with the heat exchanger (30) By primary cooling in the) it is possible to improve the evaporation efficiency of the low temperature liquid refrigerant.

The high temperature refrigerant cycle unit 20 is a cycle independent of the low temperature refrigerant of the low temperature refrigerant cycle unit 10, the second compressor 21, the second condenser 22, the second expansion valve 23, and the second evaporator. (24).

The second compressor 21 compresses the low temperature gas of the low temperature generated by the second evaporator 24 and the heat exchanger 30 to increase the temperature of the high pressure compressed gas to the second condenser 22. It is configured to supply high temperature hot water while producing high temperature hot water, and to produce high temperature water over 65 ℃ to solve the problems such as overheating of the motor due to oil carbonization and excessive power consumption. It consists of a screw-type compressor using R134a gas.

The second condenser 22 is primarily heated by the first condenser 11 included in the coolant cycle unit 10 at a low temperature by using a high temperature high pressure gas heated from the second compressor 21 (eg; 55 ℃) hot water is heated to higher temperature (eg 55 ℃ → 65 ℃), and high temperature gas is converted into high temperature liquid refrigerant.The heat exchange method is characterized by high pressure and high temperature. In consideration of the shell and tube (Shell and Tube) type.

The second expansion valve 23 expands the high temperature liquid refrigerant (eg, 70 ° C.) converted from the second condenser 22 to a low temperature liquid refrigerant and supplies the same to the second evaporator 24. It is composed.

The second evaporator 24 cools the circulating water to a predetermined temperature (eg, 10 ° C. or less) with a low temperature liquid refrigerant converted from the second expansion valve 23, and then circulates it to the first evaporator 14. After the evaporation of the liquid refrigerant to a low temperature low-pressure gas, it is configured to supply it to the heat exchanger (30), wherein the second evaporator (24) is a high-temperature liquid refrigerant during the production of winter hot water to the second expansion valve (23) It is introduced without passing through, and the liquid refrigerant is also converted into a low-temperature liquid refrigerant through the second expansion valve 23 after heating the hot water to serve as an evaporator to supply to the heat exchanger (30), when cooling It is composed of a plate with good thermal conductivity because it produces cold water and hot water during heating.

That is, the second evaporator 24 is configured to operate as a heat exchanger when producing hot water and to operate as an evaporator when producing cold water.

The heat exchanger 30 exchanges the high temperature liquid refrigerant flowing from the first condenser 12 and the low temperature low pressure gas or the low temperature liquid refrigerant circulated by the second evaporator 24 with the medium temperature liquid refrigerant to evaporate it. Or configured to be heated.

That is, the heat exchanger 30 uses a plate-shaped heat exchanger, the high temperature liquid refrigerant at 60 ° C. flowing from the first condenser 12 and the low temperature low pressure gas or non-evaporation gas flowing from the second evaporator 24. The resultant liquid refrigerant is overheated through heat exchange to be supplied to the second compressor 21 to increase the discharge gas of the second compressor 21, while lowering the liquid refrigerant temperature sent to the first expansion valve 13 to expand the liquid refrigerant. And it is possible to increase the evaporation effect, it is configured to produce a low cold water temperature.

At this time, the heat exchanger 30 is the operation of the evaporator when the second evaporator 24 serves as a heat exchanger in winter to produce hot water through a high temperature liquid refrigerant.

The circulation line 40, as well as the heat exchanger 30, of the first and second compressors 11 and 21, the first and second condensers 12, 22, 22, and the first and second expansion valves constituting a double structure ( 13) 23 and the first and second evaporators 14 and 24 are connected to each other to form the first to fourteenth circulation lines L1, L2, L3, L4, L5, L5 ', L6, L7, and L8. , L9, L10, L11, L11 ', L11 ", L12, L13, L13', L14, L14 ').

The first circulation line (L1) is configured to connect the second compressor 21 and the second condenser 22, the second circulation line (L2) is the second compressor 21 and the heat exchanger (30). It is configured to connect).

The third circulation line L3 is configured to connect the second condenser 22 and the second evaporator 24, and the fourth circulation line L4 is the first and second condensers 12 and 22. Are connected in series, the fifth circulation line (L5) is branched from the fourth circulation line (L4) and connected to the second condenser (22), the branch line connected to the heat storage tank (100) L5 ') is configured.

At this time, the third circulation line (L3) is variable to circulate by selecting the supply path of the high-temperature liquid refrigerant flowing from the second condenser 22 to the second expansion valve (23) or the second evaporator (24) The 3-way first control valve V3 included in the refrigerant line unit 50 is installed.

In the fifth circulation line L5, the first and second flow paths are determined as a 2-way method for determining the flow path of the hot water according to the hot water temperature and operating conditions generated by the first and second condensers 12 and 22. The valves V1 and V2 are installed.

The sixth circulation line (L6) is configured to connect the first compressor 11 and the first condenser 12, the seventh circulation line (L7) is the first compressor (11) and the first evaporator. 14, the eighth circulation line L8 is configured to connect the first condenser 12 and the heat exchanger 30.

The ninth circulation line L9 is provided with a first expansion valve 13 and is configured to connect the heat exchanger 30 and the first evaporator 14.

The tenth circulation line (L10) is provided with a second expansion valve 23, consisting of a parallel line of the multi-stage connecting the heat exchanger 30 and the second evaporator 24, on the parallel line of the multi-stage First to fourth check valves C1 and C2 for preventing the non-return flow included in the variable refrigerant line part 50 so as to change the high-temperature liquid refrigerant passing order between the second condenser and the second evaporator 24. C3 and C4 are installed.

At this time, the opening direction is determined by the second expansion valve 23 or the second evaporator 24 according to the opening direction of the first control valve V3 in the tenth circulation line L10 and circulated to the heat exchanger 30. The second evaporator 24 may be used in the 3-way type second control valve V4 included in the variable refrigerant line unit 50 to determine the direction of the refrigerant, as well as in the season (eg, summer) when high temperature water is not required. Hot water is opened in the direction of the second compressor 21 to guide the low-temperature gas of the low-temperature heat exchanged to the second compressor 21, the hot water supplied from the second evaporator 24 in the season (eg, winter) when hot water is required A third control valve V5 of 3-Way type, which is opened in the direction of the heat exchanger 30 to evaporate the liquid refrigerant heat-exchanged with the hot water, is installed.

The eleventh circulation lines L11, L11 ′, and L11 ″ are configured to connect the third and ten circulation lines L3 and L10 in parallel.

The twelfth circulation line L12 is configured to connect the first condenser 12 with the heat storage tank 100, and the thirteenth circulation line L13 and L13 'connects the second evaporator 24 to the heating and cooling system. It is configured to connect to the tank 300 and the make-up water tank 400, the 14th circulation line (L14, L14 ') is configured to connect the first evaporator 14 and the cold storage tank (200).

Referring to Figures 2 to 5 attached to the operation according to the embodiment of the present invention configured as described above are as follows.

First, when operating the high-temperature heat pump system of the dual compression method in the winter through the accompanying Figures 2 and 3, low-temperature low-pressure gas generated in the first evaporator 14 included in the low-temperature refrigerant cycle unit 10 is circulated It enters the 1st compressor 11 via the line L7.

Then, the first compressor 11 compresses the low temperature low pressure gas into the high temperature high pressure gas and discharges it to the first condenser 12 through the sixth circulation line L6.

At this time, the first condenser 12 heats up the warm water of a predetermined temperature (eg, 50 ° C.) flowing from the heat storage tank 100 through the circulation line L12 using the high pressure gas (eg, 55 ° C.). By discharging to the second condenser 22 included in the high temperature refrigerant cycle unit 20 through the circulation line (L4), the high-temperature gas is phase-converted to a liquid refrigerant of high temperature (for example, 60 ℃). .

Next, the low pressure gas of the low temperature generated by the second evaporator 24 is introduced into the second compressor 21 included in the high temperature refrigerant cycle unit 20 through the circulation line L2.

The second compressor 21 compresses the low pressure gas at low temperature to compress the high pressure gas at high temperature and discharges the low pressure gas to the second condenser 22 through the circulation line L1.

Then, the second condenser 22 is heated to the second temperature to a higher temperature to a higher temperature by using the high temperature high pressure gas heated as described above by the first condenser 11 (eg, 55 ℃) (E.g., 55 deg. C to 65 deg. C), and converts the high temperature high pressure gas into a high temperature liquid refrigerant.

At this time, the first and second condensers 12 and 22 are connected to the circulation line L4, and the second and second condensers 22 are provided with a circulation line (V1) and V2 having the first and second flow path determination valves V1 and V2. While L5 is connected, one end of the circulation line L5 is connected to the circulation line L4, while the branch line L5 'is connected to the heat storage tank 100 at the circulation line L5. Bar,

The first flow path determination valve (V1) is the hot water passing through the first condenser 12 is reheated through the second condenser 22 to produce a high temperature water temperature of the hot water is set by a temperature sensor (not shown) The opening angle is proportionally controlled to increase or decrease the circulation flow rate of the hot water when the temperature is lower than the temperature of the hot water, and the hot water temperature is adjusted. The second flow path determination valve V2 is closed.

Then, the hot water heated at the second condenser 22 (65 ° C) is heated through the circulation line L5 and the branch line L5 'by the opening control of the first flow path determination valve V1 (100). ) The supply is made and heating is performed.

In addition, when the high-temperature heat pump system of the binary compression method is operated in the winter, the high temperature liquid refrigerant having a phase change in the first condenser 12 is introduced into the heat exchanger 30 through the circulation line (L8), The high temperature liquid refrigerant having the phase change in the second condenser 22 flows into the second evaporator 24 from the opening direction of the first 3-way control valve V3.

At this time, since the second evaporator 24 operates as a heat exchanger (two-stage condenser) in the winter, the second evaporator 24 in the second evaporator 24, the replenishment water flowing from the replenishment tank 400 through the circulation line (L13 '). After the heat exchange using the high temperature liquid refrigerant to produce hot water it is supplied to the hot water supply tank 300 through the circulation line (L13).

In addition, the high temperature liquid refrigerant heat-exchanged in the second evaporator 24 passes through the second check valve C2 having the directivity included in the variable refrigerant line part 50 in a state where phase change is made to medium temperature liquid refrigerant. The flow is guided to the heat exchanger 30 through the circulation line (L10) is converted to a low-temperature liquid refrigerant in the second expansion valve (23) through the third check valve (C3) again.

At this time, the second and third control valves V4 and V5 of the 3-way type are installed in the circulation line L10, and the circulation lines L10 are provided in the second and third control valves V4 and V5. Another circulation line (L11 ') (L11 ") branching from is connected,

The opening direction of the second and third control valves V4 and V5 is determined in the direction of the heat exchanger 30 when heating and hot water supply are performed in winter.

Therefore, the heat exchanger 30 heat-exchanges the high temperature liquid refrigerant discharged from the first condenser 12 through the circulation line L8 with the medium temperature liquid refrigerant, and then converts it into the first expansion valve (L9). 13), the low-temperature liquid refrigerant flowing through the second expansion valve 23 is converted into low-temperature gas of low temperature, and then supplied to the second compressor 21 through the circulation line L2. will be.

At this time, in the first expansion valve 13, after converting the medium-temperature liquid refrigerant into a low-temperature liquid refrigerant to supply the low-temperature refrigerant to the first evaporator 14,

In the first evaporator 14, the low temperature liquid refrigerant is evaporated to be phase converted into a low temperature low pressure gas and then supplied to the first compressor 11 through a circulation line L7.

Therefore, this heat pump is substantially separated from two completely independent refrigerant cycles and related elements equipment, but the heat transfer continuously moves from the low temperature cycle (Cycle) to the high temperature cycle, or from the high temperature cycle to the low temperature cycle. . As such, the heat is moved around the heat exchanger 30.

On the other hand, when operating the high-temperature heat pump system of the dual compression method in the summer through the accompanying Figures 4 and 5, the low-temperature low-pressure gas generated in the first evaporator 14 included in the low-temperature refrigerant cycle unit 10 is circulated It is discharged to the first compressor 11 through the line L7.

Then, the first compressor 11 heats up the low temperature low pressure gas to a high temperature high pressure gas and discharges it to the first condenser 12 through the sixth circulation line L6.

At this time, the first condenser 12 heats up hot water at a predetermined temperature (eg, 40 ° C.) flowing from the heat storage tank 100 through the circulation line L12 using the high temperature high pressure gas (eg, 45 ° C.). By discharging to the second condenser 22 included in the high temperature refrigerant cycle unit 20 through the circulation line (L4), the high-temperature high-pressure gas is phase-converted to a high temperature liquid refrigerant.

Next, a low temperature low pressure gas generated from the second evaporator 24 is introduced into the second compressor 21 included in the high temperature refrigerant cycle unit 20 through the circulation line L2.

The second compressor 21 compresses the low pressure gas at low temperature to increase the high pressure gas at high temperature, and then discharges the low pressure gas to the second condenser 22 through the circulation line L1.

Then, the second condenser 22 is heated to a higher temperature to a higher temperature to a higher temperature by the first condenser 12 by the first condenser 12 using a high temperature high pressure gas heated as described above. (E.g., 50 deg. C to 65 deg. C), the high pressure gas is converted into a high temperature liquid refrigerant.

At this time, the first and second condensers 12 and 22 are connected to the circulation line L4, and the second and second condensers 22 are provided with a circulation line (V1) and V2 having the first and second flow path determination valves V1 and V2 installed therein. While L5 is connected, one end of the circulation line L5 is connected to the circulation line L4, while the branch line L5 'is connected to the heat storage tank 100 at the circulation line L5. Bar,

The first flow path determination valve (V1) is closed control during the summer operation, the second flow path determination valve (V2) is the opening control, while the heat storage tank 100 is not the high-temperature water of the second temperature, the primary The heated warm water (eg, 50 ° C.) is supplied through the circulation line L5 and the branch line L5 '.

In addition, when the high-temperature heat pump system of the dual compression method is operated in the summer, the high temperature liquid refrigerant (eg, 60 ° C.) in which the phase change is made in the first condenser 12 is performed through the circulation line L8. ) And the high temperature liquid refrigerant having a phase change in the second condenser 22 is first checked from the opening direction of the first 3-way control valve V3 through the circulation line L11-> L10. It is converted into a low temperature liquid refrigerant through the second expansion valve 23 via the valve C1, and the flow is guided to the second evaporator 24 via the fourth fourth check valve C4.

The second evaporator 24 uses the low temperature liquid refrigerant to cool the cold water at a predetermined temperature (eg, 15 ° C.) flowing through the circulation line (L13) from the cold storage tank 200 (eg, 5 ° C.). After the heat exchange with cold water of the) is supplied to the cold storage tank 200 again through the circulation line (L13 ') it is possible to supply the cold water.

The low-temperature liquid refrigerant heat-exchanged in the second evaporator 24 is a phase change of low-temperature low-pressure gas, and when the high-temperature water is not needed, the opening directions of the second and third control valves V4 and V5 are not included. Is supplied to the second compressor 21 via the circulation line (L3-> L11 "-> L2) immediately without passing through the heat exchanger 30, and when the high temperature water is needed, the third control valve (V5). The supply is made to the heat exchanger 30 by the opening direction of), and the subsequent operation is the same as in FIG.

As described above, since the dual compression method of the present invention operates the compressor appropriately for the characteristics of the refrigerant by distinguishing the low temperature and the high temperature, there is no problem in producing cold water and high temperature water, and the equipment COP can also be increased. .

In addition, since the binary compression method of the present invention uses a 134a refrigerant having good high temperature characteristics in a high temperature compressor, even when operating a high condensation gas temperature, its compression performance is superior to that of R22 or 410 in terms of high pressure or power consumption, and equipment life is high. Shortening and unstable operation can be eliminated, and the low temperature evaporator evaporates by recovering the high temperature liquid refrigerant heat flowing into the evaporator from the low temperature condenser, as well as producing stable high temperature water by reheating the 55 ° C water through the low temperature condenser in the high temperature condenser. By improving the efficiency, it is possible to produce cold water below 5 ° C., while producing high temperature water at 65 ° C.

In addition, the dual compression method of the present invention sets the condensed water temperature low during the operation of the cooling center to produce a cold water temperature, as well as to produce cold water by operating only a low-temperature compressor, by separating the dualized refrigeration cycle low temperature and Cold water is produced in each of the high temperature evaporator, while condenser is used jointly to reduce the power consumption of the compressor while lowering the set temperature of hot water.

In addition, the dual compression method of the present invention is to supply cold and hot water at the same time through the operation of the dual system when cold water and hot water in the transition season, as well as to produce only hot water and hot water for the winter season condenser of high temperature It is possible to produce hot water and hot water by recovering the high temperature liquid refrigerant through the high temperature evaporator without going through a high temperature expansion valve, and to recover the low temperature condensation heat from the heat exchanger, thereby increasing the compression efficiency of the high temperature compressor. will be.

In addition, the binary compression method of the present invention can obtain the effect of preventing the deterioration of equipment efficiency due to overcooling by increasing the cold water set temperature even when the use of cold water at low temperature in winter.

In addition, the binary compression method of the present invention can increase the hot water produced by 10 ℃-15 ℃ or more compared to the existing equipment, while reducing the volume of the heat storage tank by more than 20%, cold water is also produced at a low temperature to store a large amount of heat in the cold storage tank In addition, it is possible to produce economical operation and construction cost savings, such as being able to produce and store a large amount of calories with inexpensive late night electricity.

In addition, the binary compression method of the present invention increases the hot water temperature produced, even when used in conjunction with the existing load equipment to enable stable cooling and heating without modifying the load equipment (AHU, FCU, floor heating) its application width In addition, it can be used without additional boilers in the process hot water or hot water facility of the production plant, and in the case of new construction, it reduces the construction cost by reducing the pipe diameter and the pump capacity. You can get the effect.

In addition, the binary compression method of the present invention partially performs cooling and heating to provide stability of a preliminary concept against failure, and performs only a low temperature or a high temperature cycle without operating the entire system while performing seasonal local cooling and heating. By operating it, it is possible to obtain the effect of preventing the economic loss due to full operation.

The present invention is not limited to the above-described specific preferred embodiments, and various modifications can be made by any person having ordinary skill in the art without departing from the gist of the present invention claimed in the claims. Of course, such changes will fall within the scope of the claims.

Claims (12)

A low temperature refrigerant cycle unit for inducing low temperature refrigerant flow; A high temperature refrigerant cycle unit configured to be independent of the low temperature refrigerant cycle unit and induce high temperature cold flow; Redundant configuration The low temperature and high temperature refrigerant cycle unit is configured to connect the heat exchanger having a complementary function by heat-exchanging two kinds of refrigerant having different characteristics, The redundant low temperature and high temperature refrigerant cycle unit and the heat exchanger are connected by a circulation line, and the circulation line itself circulates the high temperature liquid refrigerant generated in the high temperature refrigerant cycle unit, and when producing hot water, the refrigerant heat exchanger. A variable refrigerant line portion for freely adjusting the refrigerant flow order to circulate with air; Heat pump system using a binary compression method, characterized in that the configuration. The low temperature refrigerant cycle unit of claim 1, A first compressor for compressing the low temperature low pressure gas generated in the first evaporator to be described later and raising the high temperature high pressure gas; A first condenser for first warming up the hot water circulated in the heat storage tank by using the high pressure gas heated at the first compressor and then converting the high temperature and high pressure gas into a high temperature liquid refrigerant; A first expansion valve for expanding the medium-temperature liquid refrigerant passing through the heat exchanger and converting the medium-temperature liquid refrigerant into a low temperature liquid refrigerant; And, A first evaporator for lowering the cold water temperature circulated from the cold storage tank by using the low temperature liquid refrigerant passing through the first expansion valve and evaporating the liquid refrigerant to low temperature low pressure gas by using heat absorbed from the cold water; Heat pump system using a binary compression method characterized in that it comprises a. The method of claim 1, wherein the high temperature refrigerant cycle unit, A second compressor for compressing a low temperature low pressure gas generated in the second evaporator and the heat exchanger to be described later and discharging the high temperature compressed gas; By using the high-temperature high-pressure gas introduced from the second compressor, the hot water firstly heated up by the first condenser included in the low-temperature refrigerant cycle unit is secondly heated to a higher temperature, and the high-temperature high-pressure gas is heated to a high temperature liquid. A second condenser for phase converting into a refrigerant; A second expansion valve for expanding a high temperature liquid refrigerant converted from the second condenser to a low temperature liquid refrigerant or expanding a medium temperature liquid refrigerant through a second evaporator; And, Cooling the circulating water with a low temperature liquid refrigerant converted from the second expansion valve to serve as an evaporator for cold water production, or by heating the high temperature liquid refrigerant without passing through the second expansion valve with hot water circulated from the hot water tank to raise the temperature A second evaporator functioning as a heat exchanger (condenser); Heat pump system using a binary compression method characterized in that it comprises a. The method of claim 3, wherein the heat exchanger is selectively operated in a heat exchanger or an evaporator when the second evaporator is changed to an evaporator or a heat exchanger so that cold water or hot water can be produced according to seasons and operating conditions. Heat pump system using the dual compression method characterized in that. According to claim 1, wherein the circulation line, A first circulation line connecting the second compressor and the second condenser; A second circulation line connecting the second compressor and the heat exchanger; A third circulation line connecting the second condenser and the second evaporator; A fourth circulation line connecting the hot water passing through the first condenser to be circulated to the second condenser; A fifth circulation line having hot water passing through the second condenser and a fourth circulation line and a branching line; A sixth circulation line connecting a first compressor and the first condenser; A seventh circulation line connecting the first compressor and the first evaporator; An eighth circulation line connecting the first condenser and a heat exchanger; A ninth circulation line connecting the heat exchanger and the first evaporator and having a first expansion valve installed on the line; A tenth circulation line connecting the heat exchanger and the second evaporator and having a second expansion valve and a variable refrigerant line unit installed on the line; And, An eleventh circulation line connecting the third and ten circulation lines in parallel; Heat pump system using a binary compression method, characterized in that comprising a. 6. The second and second flow path determination valves V1 and V2 of claim 5, wherein the fifth circulation line determines the flow path of the hot water according to the hot water temperature and operating conditions generated in the first and second condensers. Heat pump system using a binary compression method, characterized in that the configuration. The method of claim 6, wherein the first flow path determining valve is closed only when high temperature water is not required or when low temperature hot water is used, and the hot water passing through the first condenser is reheated through the second condenser to produce hot water. And an opening angle is proportionally controlled by a temperature sensor to adjust the hot water temperature while increasing or decreasing the circulation flow rate of the hot water when the temperature of the hot water is lower than the set temperature. The method of claim 6, wherein the second flow path determination valve is closed control when producing hot water, and when hot water is used, such as summer, which does not need or low temperature, the hot water does not pass through the second condenser and is controlled to open to the heat storage tank. Heat pump system using a binary compression method characterized in that is made. According to claim 5, The 10th circulation line is opened in the direction of the second compressor to guide the low-temperature low-pressure gas heat exchanged in the second evaporator to the second compressor without passing through the heat exchanger in the season that does not need hot water, In the heating season where hot water is needed, the two-way compression is characterized by constituting a third 3-way control valve opened in the direction of the heat exchanger to evaporate the hot water for hot water supplied from the second evaporator and the medium temperature liquid refrigerant exchanged with the heat. Heat pump system using the method. The method of claim 5, The first condenser is connected to the heat storage tank through the branch line and the twelfth circulation line, The first evaporator is connected to the cold storage tank through a plurality of fourteen circulation lines, The second evaporator is connected to the hot water supply tank and the replenishment water tank through a plurality of thirteenth circulation lines. The method of claim 5, wherein the variable refrigerant line portion, The second evaporator, which is included in the high temperature refrigerant cycle unit and connected to the third circulation line, functions as a heat exchanger and an evaporator, thereby removing the high temperature liquid refrigerant flowing from the second condenser connected to the third circulation line. In a second expansion valve connected to the second evaporator and the tenth circulation line, In the case of producing cold water in the second evaporator, the high temperature liquid refrigerant is circulated to the evaporator through the second expansion valve, and in the case of hot water production, the high temperature liquid refrigerant passing through the second evaporator is circulated to the refrigerant heat exchanger through the second expansion valve. Heat pump system using a binary compression method, characterized in that configured to have a refrigerant flow. The method of claim 11, wherein the variable refrigerant line portion, A first 3-way control valve configured in the third circulation line and configured to circulate a high-temperature liquid refrigerant flowing from the second condenser to a second expansion valve or a second evaporator by selecting a supply path; The second three-way method is configured in the tenth circulation line, and the opening direction is determined by the second expansion valve or the second evaporator according to the opening direction of the first control valve to determine the direction of the refrigerant circulated to the heat exchanger. Control valve; And, When forming a parallel line of multiple stages in the tenth circulation line is formed in the parallel line, so as to change the high-temperature liquid refrigerant passing order made between the first and second evaporators according to the opening direction of the first and second control valves. Directional first to fourth check valves for preventing reverse flow; Heat pump system using a binary compression method characterized in that it comprises a.

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