KR101262927B1 - Apparatus for dual heat pump - Google Patents

Abstract

PURPOSE: A binary heat pump device is provided to improve stability and heating efficiency of products by controlling a compressed capacity ratio between low-temperature and high-temperature side compressors in a binary refrigerating cycle. CONSTITUTION: An outlet of a high-temperature side compressor(220) is alternately connected to an inlet of a hot water heat exchanger(222) and an inlet of a hot gas defrosting heat exchanger(224) by electronic valve control. A low-temperature side outlet of a binary heat exchanger(211) is alternately connected to an inlet of a low-temperature side evaporator(217) and an inlet of a defrost compensation heat exchanger(215) by the electronic valve control. When an outlet of a high-temperature side compressor is connected to the inlet of the hot gas defrosting heat exchanger for defrosting, the low-temperature side outlet of the binary heat exchanger is connected to the inlet of the defrost compensation heat exchanger by the electronic valve control.

Description

Dual heat pump device {apparatus for dual heat pump}

The present invention relates to a heat pump apparatus, and more particularly, to a binary heat pump apparatus which improves the stability and heating efficiency of a product by adjusting the compression capacity ratio of the low temperature side and the high temperature side compressors in a binary refrigeration cycle.

In general, a binary refrigeration cycle is a refrigeration system using refrigerants having different boiling points. Here, the refrigerant changes phase from liquid to gas or gas to liquid before and after the boiling point.

At this time, it is divided into a low temperature side using a low temperature refrigerant to boil at low temperature and a high temperature side using a high temperature refrigerant to boil smoothly at a relatively high temperature, the evaporation of the high temperature refrigerant and the condensation of the low temperature refrigerant in one cascade heat exchanger It is provided to wake up. Therefore, even when the outside air temperature is low in winter, the refrigerant discharge gas temperature at the high temperature side can be maintained at a constant high temperature over 100 ° C., which is effective for producing hot water.

On the other hand, the conventional heat pump device is configured to vary the compressor capacity of the low temperature side and the high temperature side, the low temperature side compressor capacity and the high temperature side compressor capacity was fixed in a ratio of 0.7: 1. Accordingly, in the cold season of less than -15 ℃ in winter, there is a problem that the evaporation efficiency is reduced in the cascade heat exchanger due to the low capacity of the low-temperature compressor to reduce the hot water production efficiency.

On the other hand, if the compressor capacity of the low temperature side and the high temperature side is configured identically, if the temperature rises to the image during the transition season, the high expansion temperature of the low temperature side low temperature refrigerant causes excessive condensation load and pressure and overloads the compressor. There was a problem that breakage or durability is significantly reduced.

In addition, since the conventional air heat exchanger acts as a condenser in the cooling or defrosting mode, a refrigeration cycle is formed even when not used in the simultaneous heating and cooling mode, but the circulation pipe of the low temperature refrigerant is piped to the air heat exchanger, thereby reducing the circulation amount of the low temperature refrigerant. Due to the unstable cycle, overcompression or overheating occurs and there is a serious problem that the welded portion of the refrigerant circulation pipe is broken.

Korean Patent Publication No. 2003-0071607

In order to solve the above problems, it is a problem to provide a binary heat pump device that improves the stability and heating efficiency of the product by adjusting the compression capacity ratio of the low-temperature and high-temperature compressor in the binary refrigeration cycle.

In order to solve the above problems, the present invention comprises a low temperature side refrigeration cycle and a high temperature side refrigeration cycle, the low temperature side condenser and the high temperature side evaporator comprising a dual heat exchanger coupled to heat exchange with each other, the high temperature side Compressor discharge end is provided to be alternately connected by inlet end of hot water defrost heat exchanger arranged to heat hot water in hot water tank and inlet end of hot gas defrost heat exchanger arranged to exchange heat with low temperature side evaporator for defrost. The low temperature side discharge end of the binary heat exchanger is alternately connected to the low temperature side evaporator inlet end and the defrost compensation heat exchanger inlet end arranged to exchange heat with cold water by the solenoid valve control, and the high temperature side compressor discharge end for defrosting. The low temperature of the binary heat exchanger when connected to the inlet of the hot gas defrost heat exchanger The side discharge end is provided with a dual heat pump apparatus characterized in that the solenoid valve is controlled to be connected to the inlet end of the defrost compensation heat exchanger.

Here, some of the refrigerant flowing into any one of the low temperature side evaporator inlet end and the defrosting compensation heat exchanger inlet end connected to the low temperature side discharge end of the binary heat exchanger is supplied to a heat recovery heat exchanger connected to the low temperature side discharge end of the binary heat exchanger. Is preferred.

Then, when the first solenoid valve provided to connect the high temperature side compressor discharge end and the hot water heat exchanger inlet end is opened, the third solenoid valve provided to connect the low temperature side discharge end of the binary heat exchanger to the heating expansion side is interlocked to open. Preferably, the solenoid valve is controlled.

At this time, when the second solenoid valve provided to connect the high temperature side compressor discharge end and the inlet end of the hot gas defrost heat exchanger is opened, the fourth solenoid valve provided to connect the low temperature side discharge end of the binary heat exchanger and the defrost expansion side is interlocked. Preferably, the solenoid valve is controlled to open.

On the other hand, the low-temperature and high-temperature compressor capacity of the low-temperature and high-temperature side refrigeration cycle is composed of a ratio of 1.4 ~ 1.6: 1, by detecting the external temperature, if the detected external temperature is above the predetermined temperature the low temperature refrigerant It is preferable to control the low temperature side evaporator to lower the boiling point of the low temperature side compressor to prevent overcompression of the low temperature side compressor.

Through the above solution, the binary heat pump apparatus according to the present invention provides the following effects.

First, the high temperature refrigerant discharged from the high temperature shaft compressor is circulated alternately with the hot water heat exchanger and the hot gas defrost heat exchanger, and the low temperature refrigerant is compensated for the defrost when the high temperature refrigerant is circulated to the hot gas defrost heat exchanger. Interlocked control to circulate to the heat exchanger, defrost the low-temperature side evaporator with the high-temperature refrigerant, but the low-temperature refrigerant is circulated to compensate for the heat of evaporation of the high-temperature refrigerant in the two-way heat exchanger, so that the heat source of the high-temperature refrigerant is supplied smoothly defrost As a result, the heating down time is reduced, thereby improving the heating efficiency of the product.

Second, the low temperature refrigerant is condensed and discharged in the binary heat exchanger, it is expanded in the heat recovery expansion can be evaporated in the heat recovery exchanger provided to circulate geothermal to waste water heat, thereby reducing the power consumption of the low temperature side evaporator of the product Efficiency can be improved.

Third, the temperature ratio of the low temperature side compressor and the high temperature side compressor is 1.4 to 1.6: 1, so that a sufficient heat source for evaporation of the high temperature refrigerant is supplied from the binary heat exchanger in a cold winter season to improve the heating efficiency of the product. In addition, by controlling the low temperature side evaporator to prevent overcompression of the low temperature side compressor according to an external temperature, it is possible to prevent the overload of the low temperature side compressor to improve the safety of the product.

1 is a block diagram of a binary heat pump apparatus according to an embodiment of the present invention.
Figure 2 is a flow chart showing the defrosting operation of the binary heat pump apparatus according to an embodiment of the present invention.
Figure 3 is a block diagram of a binary heat pump apparatus according to a second embodiment of the present invention.
Figure 4 is a block diagram of a binary heat pump apparatus according to a third embodiment of the present invention.

Hereinafter, a binary heat pump apparatus according to a preferred embodiment of the present invention with reference to the accompanying drawings will be described in detail. Here, the dual heat pump device is a heating and cooling device capable of simultaneously heating and cooling by supplying a large amount of hot water and cold water in a bathroom, a jjimjilbang, a hot water swimming pool, etc., but with high thermal efficiency.

1 is a block diagram of a binary heat pump apparatus according to an embodiment of the present invention.

As shown in FIG. 1, the binary heat pump apparatus 100 according to an exemplary embodiment of the present invention includes a low temperature side compressor 10, a binary heat exchanger 11, a low temperature side evaporator 17, and a defrost compensation heat exchanger 15. , A high temperature side compressor 20, a hot water heat exchanger 22, and a hot gas defrost heat exchanger 24.

Here, the binary heat pump apparatus 100 is composed of a low temperature side refrigeration cycle using a low temperature refrigerant that boils at a relatively low temperature and a high temperature side refrigeration cycle using a high temperature refrigerant that is boiled at a relatively high temperature. For example, as the low temperature refrigerant, R-410a which is a mixed refrigerant of HFC series in which R-32 and R-125 are mixed at a composition ratio of 50:50 may be used, and R-410a is -51 ° C at 1 atmosphere. Has a boiling point of. As the high temperature refrigerant, R-134a of HFC series may be used, and the R-134a has a boiling point of -26 ° C at 1 atmosphere.

Meanwhile, the low temperature side compressor (10) serves to circulate the refrigerant by compressing the low temperature refrigerant of low temperature and low pressure introduced from the low temperature side evaporator (17) in the low temperature side refrigeration cycle into a gas of high temperature and high pressure. Will be

In addition, the binary heat exchanger 11 is coupled such that the condenser in the low temperature side refrigeration cycle and the evaporator in the low temperature side refrigeration cycle exchange heat. At this time, the low temperature refrigerant compressed to high temperature and high pressure in the low temperature side compressor 10 is condensed into liquid while supplying heat to the high temperature refrigerant of the high temperature side refrigeration cycle from the binary heat exchanger 11.

In addition, the low temperature side evaporator 17 cools the surroundings by supplying ambient heat to the low temperature refrigerant through which the pressure and the temperature decrease through the heating expansion side 16 and vaporizing.

On the other hand, during the cooling operation to create the cooling water for cooling or defrost operation to remove the frost of the low-temperature side evaporator 17, the low temperature refrigerant condensed in the binary heat exchanger 11 flows into the defrost compensation heat exchanger (15). do. At this time, the defrost compensation heat exchanger 15 takes the heat of the water supplied and the low temperature refrigerant evaporates.

In addition, the high temperature side compressor 20 compresses the high temperature refrigerant into a gas of high temperature and high pressure. Here, the high temperature refrigerant of low temperature and low pressure evaporated in the binary heat exchanger 11 in the high temperature side refrigeration cycle is compressed into a gas of high temperature and high pressure in the high temperature shaft compressor 20, so that the hot water heat exchanger 22 or the hot gas. Circulated to the defrost heat exchanger (24).

On the other hand, during heating or hot water generation, the high temperature refrigerant compressed by the high temperature side compressor 20 flows into the hot water heat exchanger 22. At this time, the hot water circulated in the hot water heat exchanger 22 in the hot water tank 23 supplies heat generated by the condensation of the hot refrigerant.

In the defrosting operation, the high temperature refrigerant compressed by the high temperature side compressor 20 is supplied to the hot gas defrost heat exchanger 24 through a defrost hot gas supply line 109, and thus the low temperature side evaporator 17. The formation of frost or frost will be removed.

On the other hand, the discharge end of the high-temperature refrigerant compressed by the high-temperature side compressor 20 is discharged to the low-temperature side evaporator for the inlet and defrost of the hot water heat exchanger 22 arranged to heat the hot water of the hot water tank (23) 17) and the inlet end of the hot gas defrost heat exchanger 24 disposed to exchange heat with the solenoid valve control is provided to be alternately connected to each other.

Here, when the hot water of the hot water tank 23 is heated, the first solenoid valve 21 provided to open and close the pipe between the hot end compressor 20 discharge end and the hot water heat exchanger 22 inlet end is opened, and the defrost In operation, the second solenoid valve 21a provided to open and close the pipe between the discharge end of the high temperature shaft compressor 20 and the inlet end of the hot gas defrost heat exchanger 24 is opened.

In this case, when the first solenoid valve 21 is opened, the second solenoid valve 21a is closed when the first solenoid valve 21 is opened, and the first solenoid valve 21 is opened when the second solenoid valve 21a is opened. ) Is preferably closed. Accordingly, the piping of the high temperature refrigerant is opened in one direction, and the refrigerant circulation due to the compression of the high temperature side compressor 20 may be smoothly performed.

In addition, the solenoid valve control is driven when heating or hot water heating is required according to a user's input to perform the operation of opening the first solenoid valve 21, and defrosting required state according to an external temperature and a heating operation time. It is preferable to automatically perform the operation of closing the first solenoid valve 21 and opening the second solenoid valve 21a.

At this time, the solenoid valve control is performed when the first solenoid valve 21 provided to connect the high temperature side compressor 20 discharge end and the hot water heat exchanger inlet end 22 is opened, and the binary heat exchanger 11 has a low temperature side discharge end. The third solenoid valve provided to be connected to the heating expansion valve 16 is connected to open.

In detail, when the heating or hot water heating operation is performed, the low temperature side refrigeration cycle includes a low temperature side compressor (10), an oil separator (10a), a binary heat exchanger (11), a receiver (12), a heating expansion valve (16), and a low temperature side. It has a circulation structure consisting of an evaporator 17 and a liquid separator 19.

The high temperature side refrigeration cycle includes a high temperature side compressor (20), an oil separator (20a), a hot water heat exchanger (22), a fluid receiver (25), a high temperature expansion valve (27), a binary heat exchanger (11), and a liquid separator (29). It has a circulation structure composed of).

At this time, the high temperature refrigerant compressed by the high temperature shaft compressor 20 moves from the discharge end of the high temperature shaft compressor 20 to the inlet end of the hot water heat exchanger 22 via an oil separator 20a. In the hot water heat exchanger 22, a pipe through which the hot refrigerant flows and a pipe through which hot water to be heated flow are disposed adjacent to each other so that the high temperature refrigerant is condensed, and the heat generated by the condensation is transferred to the hot water. Is heated.

In addition, the heat transfer to the hot water and the condensed high-temperature refrigerant is moved to the inlet end of the binary heat exchanger 11 through the receiver 25. Here, the high temperature refrigerant expands in the high temperature expansion side 27 to become a low temperature low pressure liquid state, and absorbs heat of the low temperature refrigerant in the binary heat exchanger 11 to evaporate to a gas state.

At this time, the sixth solenoid valve 26 provided in the pipe connected to the hot expansion valve at the discharge end of the hot water heat exchanger 22 and the discharge end of the hot gas defrost heat exchanger 24 operates the high temperature side compressor 20. It is preferable to open automatically according to.

The high temperature refrigerant evaporated in the binary heat exchanger 11 is introduced into the high temperature side compressor 20 through the liquid separator 29 to circulate.

Here, looking at the circulation of the low temperature refrigerant that transfers heat to the high temperature refrigerant in the binary heat exchanger (11), the low temperature refrigerant is condensed in the binary heat exchanger (11) to dissipate heat. In this case, the pipe through which the low temperature refrigerant flows and the pipe through which the high temperature refrigerant flows are preferably disposed adjacent to each other to facilitate heat exchange, and are formed of a material such as copper having high thermal conductivity.

The low temperature refrigerant condensed is introduced into the low temperature side evaporator 17 through the receiver 12 at the low temperature side discharge end of the binary heat exchanger 11. Here, the third solenoid valve 13 provided to open and close the pipe between the discharge end of the binary heat exchanger 11 and the heating expansion side 16 is opened, and the pipe between the discharge end of the binary heat exchanger 11 and the defrost expansion side 14 is opened. It is preferable that the fourth solenoid valve 13a provided to open and close is closed.

Thus, the condensed low temperature refrigerant expands to low temperature and low pressure at the heating expansion side 16 and absorbs ambient heat as it enters the low temperature side evaporator 17 and vaporizes.

In addition, the low temperature refrigerant having a temperature rise to a predetermined level is introduced into the low temperature compressor 10 through the liquid separator 19 and circulated.

Here, the third solenoid valve 13 provided between the discharge end of the binary heat exchanger 11 and the inlet end of the low temperature side evaporator 17 and between the discharge end of the binary heat exchanger 11 and the inlet end of the defrost compensation heat exchanger 15. Fourth solenoid valve (13a) provided in is preferably opened and closed alternately with each other, it can be opened at the same time as needed.

That is, during heating or hot water heating, the third solenoid valve 13 is opened so that the low temperature refrigerant evaporates in the low temperature side evaporator 17 to absorb external heat, and is generated in the low temperature side evaporator 17. During the defrosting operation to remove frost or frost, the defrost compensation heat exchanger 15 is introduced into and evaporated. At this time, in the defrost compensation heat exchanger (15), the low temperature refrigerant is evaporated through heat absorption by exchanging heat with cold water.

In addition, during cooling, the defrost compensation heat exchange 15 may be used to generate cooling water. At this time, when the coolant is excessively generated, it is preferable to control the refrigerant circulation by opening the third solenoid valve 13 which opens and closes the pipe between the binary heat exchanger 11 and the low temperature side evaporator 17.

Of course, the third solenoid valve 13 and the fourth solenoid valve 13a are solenoid valve controlled so that the third solenoid valve 13 is opened and the fourth solenoid valve 13a is opened during heating or cornice heating. In the defrosting operation, the fourth solenoid valve 13a is opened and the third solenoid valve 13 is automatically controlled to close.

Meanwhile, the low temperature side compressor 10 and the high temperature side compressor 20 capacities of the low temperature side and the high temperature side refrigeration cycles are preferably in a ratio of 1.4 to 1.6: 1.

When the cold outside temperature is -15 ° C or lower during winter, the low temperature refrigerant passing through the heating expansion side 16 is discharged to -22 ° C to maintain a 7 ° C difference in evaporation temperature from the outside air, which is evaporated at -51 ° C. Since it is a refrigerant, the low temperature side evaporator 17 absorbs external air heat sufficiently to completely evaporate the refrigerant.

In addition, the low temperature side compressor 10 is configured such that the capacity ratio with the high temperature side compressor 20 is 1.4 to 1.6: 1, and the high temperature side is compressed since the evaporated refrigerant is sufficiently compressed and sent to the binary heat exchanger 11. It is possible to increase the temperature of hot water stored in the hot water tank 23 by sufficiently endotherm in the refrigeration cycle.

In detail, in order to facilitate the evaporation of the high temperature refrigerant exchanged in the hot water heat exchanger 22, the temperature of the low temperature refrigerant exchanged with the high temperature refrigerant in the binary heat exchanger 11 is very important.

The binary heat exchanger 11 in the high temperature side refrigeration cycle in winter is to evaporate the high-temperature refrigerant passing through the high-temperature expansion valve 27 to about 5 ℃, the high temperature refrigerant is about 10 ℃ to the temperature of about 10 ℃ It is sucked into the side compressor 20 and compressed to be heat-exchanged with the hot water of the hot water tank 23 in the hot water heat exchanger 22 and condensed, and then expands through a high temperature expansion valve 27 that is a throttling device through the receiver 25. When the pressure is lowered, a continuous cycle in which the binary heat exchanger 11 is sucked back into the high temperature side compressor 20 through an evaporation process is formed. Accordingly, the hot water may be heated to 65 ℃ ~ 70 ℃ can be stored in the hot water tank (23).

In this case, when the compression capacity of the low temperature side compressor 10 is insufficient, the high efficiency of the high temperature refrigerant through the low temperature refrigerant cannot be evaporated smoothly, thereby lowering the heating efficiency. When the capacity ratio of the low temperature side compressor and the high temperature side compressor is 1: 1, the COP (coefficient of performance) representing the performance of the refrigerator is 2.52, and the capacity ratio of the low temperature side compressor and the high temperature side compressor is 1.5: 1. In this case, it can be seen from the experimental result that the COP is 2.75 or more.

On the other hand, if the detected external temperature is greater than a predetermined temperature by detecting the external temperature to control the low-temperature side evaporator 17 to lower the boiling point of the low-temperature refrigerant to prevent over-compression of the low-temperature compressor (10). For example, at an external temperature of 10 ° C. or higher of the season, the low temperature refrigerant absorbs a lot of heat in the low temperature side evaporator 17 due to the high temperature difference.

In this case, the low temperature refrigerant requires a lot of force for compression as compared to when it has a low heat amount, the overload of the low temperature compressor 10 may occur. Therefore, when the external temperature is equal to or higher than the predetermined temperature, the low speed refrigerant is controlled to absorb proper heat by limiting the rotation speed of the pen of the low temperature storage evaporator 17.

Outside temperature
(℃) Evaporation temperature
(℃) Evaporative heat
(Kw) Power
(Kw) Refrigerant volume
(%) Discharge heat before improvement
(Kcal / h) Discharge heat after improvement
(Kcal / h) 11 7.2 10.4 0.8 32.5 25500 31300 6 1.3 10.42 1.2 42.5 26000 31300 One -4.2 10.5 1.3 54 27000 31300 -7.8 -9 10.52 1.3 65 28000 31300 -11.5 -14 10.53 1.4 82 29000 31300 -14 -21 10.53 1.6 100 31300 31300

Table 1 shows the actual calorific value of the heating cycle in winter, when the compressor capacity of the low temperature side and the high temperature side is equally configured to 1.5: 1, and the number of rotations of the pen of the low temperature side evaporator 17 is changed to the outside temperature. It shows the operation characteristics of.

As can be seen in Table 1, prior to improvement, the discharge heat is rapidly reduced toward room temperature when the number of rotations of the low temperature side evaporator 17 is maintained the same regardless of the external temperature, whereas the efficiency is lowered. When the boiling point of the low-temperature refrigerant is adjusted by adjusting the number of rotations of the evaporator 10, it can be seen that the amount of discharged heat remains the same regardless of the external temperature change.

In addition, since the required power decreases as the number of rotations of the low-temperature side evaporator 17 decreases toward room temperature, the discharge heat is the same as that of winter, and thus the heat can be increased while reducing power consumption during the season.

2 is a flowchart illustrating a defrosting operation of a binary heat pump apparatus according to an exemplary embodiment of the present invention.

As shown in FIG. 2, the binary heat pump apparatus 100 is provided to perform a defrosting operation for removing frost or frost from the low temperature side evaporator 17.

Here, when the high temperature side compressor 20 discharge end is connected to the inlet end of the hot gas defrost heat exchanger 24 for defrosting, the low temperature side discharge end of the binary heat exchanger 11 is the defrost compensation heat exchanger 15. The solenoid valve is controlled to be connected to the inlet end.

When frost or frost occurs in the low temperature side evaporator 17 during the heating operation in winter, the low temperature side evaporator 17 prevents pen rotation of the low temperature side evaporator 17 or the endotherm of the low temperature refrigerant, thereby reducing the heating efficiency. A series of operations is performed to defrost the evaporator 17.

When the high temperature side compressor 20 is driven for heating operation or hot water heating (s10), the sixth solenoid valve 26 and the first solenoid valve 21 are opened, and the second solenoid valve 21a is opened. Is closed so that the hot refrigerant may be circulated to the hot water heat exchanger 22.

Meanwhile, the low temperature side compressor 10 compresses and discharges the low temperature refrigerant to transfer heat from the binary heat exchanger 11 to the high temperature refrigerant. At this time, the third solenoid valve 13 is opened and the fourth solenoid valve 13a is closed to evaporate the low temperature refrigerant in the low temperature side evaporator 17.

Accordingly, the high temperature refrigerant and the low temperature refrigerant are circulated through the compression, condensation, expansion, and evaporation steps, and the heat generated in the condensation of the high temperature refrigerant is transferred to the hot water in the hot water heat exchanger 22. . In addition, the heat generated in the condensation step of the low temperature refrigerant is used as a heat source for evaporation of the high temperature refrigerant in the binary heat exchanger (11).

On the other hand, when the external temperature is less than the predetermined defrost temperature (s20) by comparing whether the heating operation time is more than the predetermined defrost required time (s30) it is determined whether defrost operation is necessary. For example, the predetermined defrost temperature is preferably set by automatically calculating the time of occurrence of frost or frost in the cold operation in the test operation result, and generating an automatic defrost operation control algorithm according to the calculated result.

As a result of the test operation, there is much humidity between 0 ° C and 7 ° C, and there is a lot of dropping, so that the operation efficiency of the low-temperature side evaporator is lowered. It has been shown that defrosting is required to operate.

Accordingly, the automatic defrosting control algorithm performs the defrosting operation when the external temperature is 9 ° C. or lower, when the low temperature side evaporator outlet temperature is −1 ° C. or lower, and the deviation between the refrigerant temperature before evaporation and the refrigerant temperature after evaporation is 3 ° C. or higher. It can be provided to operate. In addition, it is preferable that the defrosting operation is operated in accordance with time during the heating operation corresponding to the external humidity.

At this time, if the external humidity is more than 35%, every 90 minutes of heating operation, if the external humidity is more than 45%, every 70 minutes of heating operation, if the external humidity is more than 55%, every 50 minutes of heating operation, if the external humidity is more than 65%, heating operation Every 45 minutes, if the external humidity is 70% or higher, every 38 minutes of heating operation, if the external humidity is 75% or higher, every 33 minutes of the heating operation, if the external humidity is 80% or higher, every 25 minutes of the heating operation, if the external humidity is 85% or higher, Every 22 minutes of the heating operation, if the external humidity is 90% or more, the defrosting operation may be set to operate every 20 minutes of the heating operation.

According to the automatic defrosting operation control algorithm, the low temperature side evaporator can prevent the low temperature side compressor from being overloaded and stop the heating operation due to a drop in the low temperature side evaporator, thereby improving the safety of the product.

That is, when the outside temperature is 8 ° C. or less in the cold weather in winter, when the heating operation time and the external humidity are measured, it is determined that the defrosting operation is necessary according to the corresponding defrosting automatic control algorithm.

And, if it is determined that defrosting operation is necessary (s40), the binary heat pump apparatus 100 stops heating operation and performs a series of operations for defrosting operation.

First, the defrosting operation may be performed in 160 seconds according to a preset setting value. At this time, the pen of the low temperature side evaporator 17 and the low temperature side compressor 10 are stopped for 40 seconds. This is to prevent the circulation of the low temperature refrigerant for efficient defrosting operation since the low temperature refrigerant circulates, and thus absorbs external heat from the low temperature side evaporator 17.

Then, the low temperature side compressor 10 is operated after 40 seconds and the low temperature refrigerant is circulated to the defrost compensation heat exchanger 15 to circulate to the high temperature side compressor 20 and the hot gas defrost heat exchanger 24. The high temperature is supplied to the high temperature refrigerant.

Accordingly, since the high temperature refrigerant is supplied with continuous heat, the defrosting operation is completed in only 160 seconds according to a predetermined set value, and the defrosting is completed, and all the devices are normally operated to produce hot water. Therefore, the defrosting operation due to the high temperature refrigerant at high temperature can shorten the defrost time and prevent energy loss.

In detail, the solenoid valve control in the defrosting operation as described above is as follows.

In order to circulate the high temperature refrigerant to the hot gas defrost heat exchanger 24 provided in the low temperature side evaporator, the first solenoid valve 21 is closed and the second solenoid valve 21a is opened (s50). Accordingly, the high temperature refrigerant compressed by the high temperature side compressor 20 flows into the hot gas defrost heat exchanger 24 to supply heat to the low temperature side evaporator 17 to perform defrosting. At this time, the hot gas defrost heat exchanger 24 and the low temperature side evaporator 17 is preferably provided integrally or adjacently.

That is, when the second solenoid valve 21a provided to connect the discharge end of the high temperature side compressor 20 and the inlet end of the hot gas defrost heat exchanger 24 is opened, the low temperature side discharge end and the defrost side of the binary heat exchanger 11 are opened. The solenoid valve is controlled to open the fourth solenoid valve 13a provided with the expansion valve 14 connected thereto.

The hot gas defrost heat exchanger 24 and the low temperature side evaporator 17 may be formed of a tube coil. Further, the heat of the high temperature refrigerant circulated to the tubular coil of the hot gas defrost heat exchanger 24 is preferably indirectly transferred to the tubular coil of the low temperature side evaporator 17.

On the other hand, if the defrosting operation time is more than the preset defrosting compensation time (s60), the low-temperature compressor (10) is driven to lock the third solenoid valve 13 and open the fourth solenoid valve (13a). Driven.

In detail, the preset defrosting compensation time is preferably set to about 120 seconds. When the high temperature refrigerant is circulated for about 40 seconds without receiving the condensation heat of the low temperature refrigerant from the binary heat exchanger 11, the heat source in the binary heat exchanger 11 is insufficient due to vaporization of the high temperature refrigerant.

Therefore, the low-temperature refrigerant is circulated to supply the heat source to the binary heat exchanger 11 for fast defrosting to smooth evaporation and endotherm of the high-temperature refrigerant. At this time, when the low temperature refrigerant evaporates in the low temperature side evaporator 17, since defrosting becomes difficult due to the continuous temperature drop of the low temperature side evaporator 17, the third solenoid valve 13 is closed and the fourth solenoid valve is closed. 13a is opened so that the low temperature refrigerant is circulated to the defrost compensating heat exchanger 15.

Here, the low temperature refrigerant is expanded at the defrost expansion side 14 to endotherm in the defrost compensation heat exchanger 15 to evaporate, and a water supply pipe is connected to the defrost compensation heat exchanger 15 to evaporate the heat source of the low temperature refrigerant. To supply.

On the other hand, when the defrosting operation time is more than the predetermined defrosting operation time (s80), the binary heat pump device completes the defrosting operation and drives to generate heating or hot water (s90). At this time, the predetermined defrosting operation time is preferably set to about 160 seconds.

As such, the high temperature refrigerant compressed by the high temperature side compressor 20 is supplied to the hot gas defrost heat exchanger 24 through the defrost hot gas supply line 109 to defrost the low temperature side evaporator 17. However, by continuously supplying a heat source for the evaporation of the high-temperature refrigerant defrosting operation is made quickly and efficiently, the heating efficiency of the product can be improved.

3 is a block diagram of a binary heat pump apparatus according to a second embodiment of the present invention.

As shown in FIG. 3, in the second embodiment, since the basic configuration except for the heat recovery heat exchanger 233 is the same as the above-described embodiment, detailed description of the same configuration will be omitted.

Here, the heat recovery heat exchanger 233 is provided to supply the evaporative heat of the low-temperature refrigerant using geothermal heat or waste water heat, when the geothermal heat is used to embed the heat recovery heat exchanger 233 in the basement and the waste water heat When using, it is preferable to provide a pipe through which the sewage of the bath is circulated in the heat recovery heat exchanger 233 to supply the evaporative heat of the low temperature refrigerant.

At this time, some of the refrigerant introduced into any one of the inlet end of the low-temperature side evaporator 217 and the defrosting compensation heat exchanger (15 of FIG. 1) connected to the low-temperature side outlet of the binary heat exchanger 211 is the binary heat exchanger. It is supplied to a heat recovery heat exchanger 233 connected to the low temperature side outlet end of 211.

In detail, the low temperature refrigerant is condensed in the binary heat exchanger 211 to transfer heat to the high temperature refrigerant, and discharged to the low temperature side discharge end of the binary heat exchanger 211. The low temperature refrigerant is circulated through the receiver 212 to the low temperature side evaporator 217 for evaporation.

Here, the third solenoid valve 213 is closed by the solenoid valve control, and the fifth solenoid valve 231 provided in the pipe connecting the low temperature side discharge end of the binary heat exchanger 211 and the heat recovery expansion valve 232 is opened. Opening the low temperature refrigerant may be circulated to the heat recovery heat exchanger 233.

Through this, since the evaporative heat of the low temperature refrigerant can be supplied through geothermal heat or waste water heat, the power of the low temperature side evaporator 217 can be reduced, thereby improving product efficiency. Of course, the third solenoid valve 213 and the fifth solenoid valve 231 may be alternately opened and closed, but when the evaporation heat source is insufficient according to the supply amount of geothermal or wastewater heat, the low temperature side evaporator 217 may be used. In order to supply heat to the low temperature refrigerant, it is preferable to simultaneously open or periodically open and close alternately.

4 is a block diagram of a binary heat pump apparatus according to a third exemplary embodiment of the present invention.

As shown in FIG. 4, in the third embodiment, the basic configuration except for the production of cold water through the heat recovery heat exchanger 333 and the defrost compensation heat exchanger 315 is the same as that of the above-described embodiment, so that specific configuration of the same configuration Description is omitted.

Here, the low temperature refrigerant is condensed in the binary heat exchanger 311 to transfer heat to the high temperature refrigerant, discharged to the low temperature side discharge end of the binary heat exchanger 311 and passes through the receiver 312.

At this time, the third solenoid valve 313 is provided such that the low temperature refrigerant is circulated to the low temperature side evaporator 317, and the fourth solenoid valve 313a is the low temperature refrigerant to the defrost compensation heat exchanger 315. Is provided to be circulated, the fifth solenoid valve 331 is provided so that the low-temperature refrigerant is circulated to the heat recovery heat exchanger (333).

The defrosting compensating heat exchanger 315 discharges the pipes circulated into the defrost compensating heat exchanger 315 in the cold water tank 330 in which cold water for cooling is stored, and the low temperature side discharge pipe of the binary heat exchanger 311. A pipe through which the low temperature refrigerant is circulated is provided.

In detail, the hot water refrigeration cycle is intermittently operated or stopped so that hot water in the hot water tank 323 is maintained in the summer season, so that the cold side refrigeration cycle can be actively switched to cooling. .

In order to produce cold water for a cooling operation, the low temperature refrigerant compressed by the low temperature side compressor 310 is condensed in the binary heat exchanger 311. At this time, the heat of condensation may be transferred to the high temperature refrigerant and used to produce hot water.

The low temperature refrigerant circulates through the receiver 312 to the low temperature side evaporator 317, the heat recovery heat exchanger 333, and the defrosting compensation heat exchanger 315. The third solenoid valve 313 and the fifth solenoid valve 331 are closed, and the fourth solenoid valve 313a is opened.

In addition, as the fourth solenoid valve 313a is opened, the low temperature refrigerant expands at the defrost expansion side 314 to circulate the defrost compensation heat exchanger 315 to heat heat of cold water circulated in the cold water tank 330. It is taken away to cool the cold water and vaporize it.

As such, the cold water is stored in the cold water tank 330 by the circulation of the low temperature refrigerant and used for cooling. In this case, the high temperature refrigerant may be circulated to the hot water heat exchanger 322 or the hot gas defrost heat exchanger 324.

When hot water is required, the first solenoid valve 321 is opened to circulate to the hot water heat exchanger 322, and when the hot water is not needed, the second solenoid valve 321a is opened to open the hot gas defrost heat exchanger ( 324 preferably. At this time, the high temperature refrigerant is deprived of heat and condensed by external air supplied from a pen in the hot gas defrost heat exchanger 324, and is expanded in the high temperature expansion side 326 via a receiver 325 to expand the binary heat exchanger. To 311) and evaporate.

As such, it is possible to produce cold water for cooling and hot water for heating at the same time, to prevent overload of the product at the same time when cooling and hot water, such as a season, can improve the efficiency of the product by reducing power consumption.

As described above, the present invention is not limited to the above-described embodiments, but may be modified and implemented by those skilled in the art without departing from the scope of the claims of the present invention. Such modifications are within the scope of the present invention.

100, 200, 300: binary heat pump device 10,210,310: low temperature side compressor
20,220,320: high temperature side compressor 11,211,311: binary heat exchanger
16,216,316: heating expansion valve 13,213,313: third solenoid valve
13a, 213a, 313a: Fourth solenoid valve 14,214,314: Defrost expansion valve
15,215,315 Defrost compensation heat exchanger 17,217,317 Low temperature side evaporator
21,221,321: first solenoid valve 21a, 221a, 321a: second solenoid valve
22,222,322: hot water heat exchanger 23,223,323: hot water tank
109,209,309: Defrost hot gas supply line 330: Cold water tank
24,224,324: hot gas defrost heat exchanger 233,333: heat recovery heat exchanger

Claims (5)

In the two-sided heat pump device comprising a low-temperature side refrigeration cycle and a high-temperature side refrigeration cycle, the low-temperature side condenser and the high-temperature side evaporator coupled to each other heat exchange.
The high temperature compressor discharge end is alternately connected to the inlet end of the hot water heat exchanger arranged to heat the hot water of the hot water tank and the inlet end of the hot gas defrost heat exchanger arranged to exchange heat with the low temperature side evaporator for defrosting. Equipped,
The low temperature side discharge end of the binary heat exchanger is alternately connected to the low temperature side evaporator inlet end and the defrost compensation heat exchanger inlet end arranged to exchange heat with cold water by an electromagnetic valve control.
Binary heat pump device characterized in that the solenoid valve is controlled to be connected to the inlet end of the defrost compensation heat exchanger when the high temperature side compressor discharge end is connected to the inlet end of the hot gas defrost heat exchanger for defrosting . The method of claim 1,
Some of the refrigerant introduced into any one of the low temperature side evaporator inlet end and the defrosting compensation heat exchange inlet end connected to the low temperature side discharge end of the binary heat exchanger is supplied to a heat recovery heat exchanger connected to the low temperature side discharge end of the binary heat exchanger. Dual heat pump device. The method of claim 1,
When the first solenoid valve provided to connect the high temperature side compressor discharge end and the hot water heat exchanger inlet end is opened, the solenoid valve is opened so that a third solenoid valve provided to connect the low temperature side discharge end of the binary heat exchanger and the heating expansion valve is interlocked. Dual heat pump device characterized in that the controlled. The method of claim 1,
When the second solenoid valve provided to connect the high temperature compressor discharge end and the inlet end of the hot gas defrost heat exchanger is opened, the fourth solenoid valve provided to connect the low temperature side discharge end of the binary heat exchanger and the defrost expansion side is interlocked to open. Dual heat pump device characterized in that the solenoid valve controlled. The method of claim 1,
The low-temperature and high-temperature compressor capacity of the low-temperature and high-temperature side refrigeration cycle is composed of 1.4 ~ 1.6: 1 ratio,
And sensing the external temperature and controlling the low temperature side evaporator to lower the boiling point of the low temperature refrigerant to prevent overcompression of the low temperature side compressor when the detected external temperature is greater than or equal to a predetermined temperature.

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