KR20110031547A - Heat pump - Google Patents

Abstract

PURPOSE: A heat pump is provided to prevent excessive cooling operation and excessive heating operation by controlling the temperature of discharged gas. CONSTITUTION: A heat pump comprises a compressor(100), a condenser(200), a temperature sensor, an evaporator(600), a first solenoid valve(SV1), a first expansion valve, a second expansion valve, and a liquid separator(700). The condenser condenses a refrigerant compressed through the compressor. The temperature sensor senses the temperature of the refrigerant discharged from the compressor. The evaporator evaporates the refrigerant passing through the condenser. The first solenoid valve controls the amount of the refrigerant flowing into the evaporator. The first expansion valve is located between the condenser and the evaporator. The second expansion valve is located between the first solenoid valve and the evaporator. The liquid separator separates liquid refrigerant from the refrigerant passing through the evaporator.

Description

Heat Pump

The present invention relates to a heat pump. More specifically, by controlling the amount of refrigerant through controlling the temperature of the discharge gas, it is possible to increase the efficiency by preventing overcooling and overheating operation, and to solve the low pressure compensation and summer high pressure problems in winter by using the liquid heater in a parallel structure and prevent freezing. Not only does the defrosting work need to be done, but also the cold / hot function can be used at the same time, and the heat source can be hybridized to use air and other heat sources at the same time, which is advantageous in terms of equipment stability and installation cost. The present invention relates to a heat pump provided with an orifice to prevent failure of the compressor in advance and to allow a sufficient amount of gas refrigerant to be sucked into the compressor.

The heat pump is a cooling and heating device that transfers a low temperature heat source to a high temperature or a high temperature heat source to a low temperature by using heat of a refrigerant or condensation heat, and most of the heat pumps have a structure of cooling and heating at present.

Heat pumps are classified into electric and engine type according to the driving method, air heat source type, hydrothermal source type (waste heat source type), and geothermal source type depending on the heat source. In addition, according to the heat supply method is divided into heating, cooling, dehumidification and heating and cooling according to the range of hot air, cold air, hot water, cold water, pump. Geothermal source not only consumes a lot of time and money in the installation process, but also has a disadvantage of being unable to move. On the contrary, the air heat source type has an advantage of easy installation and free movement by using air, which is an environmentally friendly future energy source, and many researches on this have been made recently.

The general air heat source heat pump system has a problem in that the heating capacity of the system is drastically deteriorated because the low pressure side load (pressure) is lowered when the temperature of the external air is lowered in the heating mode, so that an frost occurs on the evaporator (outdoor heat exchanger) side. That is, in the heating mode of the heat pump, the outdoor heat exchanger acts as an evaporator, and the low-temperature low-pressure refrigerant and the external air heat exchange with each other to use the heat of the air to evaporate the refrigerant. At this time, when the temperature of the outside air is lowered, frost phenomenon occurs on the fin surface of the outdoor heat exchanger, so that the heat transfer rate is lowered, thereby lowering the load on the low pressure side, and as a result, the heating capacity is deteriorated.

In order to solve this problem, a defrosting operation to remove frost formed on the outdoor heat exchanger fin is performed. As a defrost method, flush defrost and hot gas defrost have been introduced. In the case of flush defrost, a large amount of water is consumed and heat loss occurs.In the case of hot gas defrost, high temperature and high pressure defrost occurs, causing malfunction of valves and more than 15% of heat loss. There is this. In addition, according to these methods, since the main cycle is stopped by a separate defrosting operation, there is a problem that the capacity of the device must be largely designed to reduce the uptime for heat production and to compensate for this. In addition, according to these methods, the temperature of the hot water is theoretically about 70 degrees Celsius, but as low as 45 ~ 62 degrees in actual operation, there is a problem that the actual efficiency is lower than the theory.

On the other hand, the general heat pump is inconvenient to use the hot water and cold water at the same time can not only operate the cooling or heating selectively with a single machine. In addition, the general heat pump cannot use it efficiently because it uses only a single heat source, and if the corrosive heat source including waste water or sea water is used, water can penetrate into the equipment due to breakage of the evaporator, causing a lot of repair cost. There is a problem of reduced ability. In addition, the general heat pump has a problem that energy utilization is inefficient because the condensation heat source generated for cold water production in the summer discards as a waste heat source in the atmosphere.

The present invention has been made to solve the above problems, in particular, by increasing the efficiency by preventing overcooling and overheating operation can solve the low pressure compensation and summer high pressure problems in winter, as well as no separate defrosting work, Its purpose is to provide a heat pump that can use both cold and hot functions simultaneously, use air and other heat sources simultaneously, prevent compressor failure and allow a sufficient amount of gas refrigerant to be sucked into the compressor.

Heat pump according to the present invention devised to achieve the above object is a compressor; A condenser for condensing the refrigerant compressed by the compressor; A third temperature sensor positioned between the compressor and the condenser to sense a temperature of the refrigerant discharged from the compressor; An evaporator through which the refrigerant passing through the condenser is introduced to evaporate the refrigerant; A first solenoid valve positioned between the condenser and the evaporator to control the amount of refrigerant flowing into the evaporator by being opened and closed by the first temperature sensor; A first expansion valve positioned between the condenser and the evaporator; A second expansion valve positioned between the first solenoid valve and the evaporator; And a liquid separator separating the liquid refrigerant from the refrigerant passing through the evaporator.

The third temperature sensor may close the first solenoid valve when the temperature of the refrigerant discharged from the compressor is equal to or less than a predetermined value.

The third temperature sensor may open the first solenoid valve when the temperature of the refrigerant discharged from the compressor is greater than or equal to a predetermined value.

In addition, an orifice for injecting a liquid refrigerant may be positioned between the evaporator and the liquid separator.

In addition, the rim piece is provided at the inlet side of the liquid separator pipe section for supplying a refrigerant to the liquid separator; A blocking film provided inside the pipe part; And a capillary tube formed in the blocking film to allow gas refrigerant to pass through and to spray the liquid refrigerant.

In addition, the blocking film may be formed in a concave shape with respect to the advancing direction of the refrigerant.

In addition, the barrier layer may be formed in any one of a hemispherical shape, a semi-elliptic sphere shape, a cone shape, and a truncated cone shape.

In addition, the capillary tube may be provided in plural and may have an inner diameter gradually increasing along the advancing direction of the refrigerant.

In addition, the inner peripheral surface of the capillary in the cross section including the central axis of the capillary may be inclined or curved with respect to the central axis.

In addition, the blocking film may be provided in plural to form a multilayer.

The apparatus may further include a first liquid heater configured to perform heat exchange with the refrigerant discharged from the evaporator using the refrigerant discharged from the condenser.

In addition, the refrigerant discharged from the evaporator and heat exchanged through the first liquid heater may be introduced into the liquid separator.

The apparatus may further include a second heat exchanger configured to perform heat exchange with the refrigerant discharged from the evaporator using hot water introduced from the outside.

In addition, the hot water passing through the second liquid heater may be introduced into the condenser to perform heat exchange with the refrigerant introduced from the compressor.

In addition, the first temperature sensor for sensing the temperature of the hot water flowing into the second liquid heater to control the operation of the compressor, the second temperature sensor for sensing the temperature of the hot water discharged from the condenser, and the hot water outlet side It may further include a fifth solenoid valve provided to be opened and closed by the second temperature sensor.

In addition, some of the refrigerant discharged from the evaporator may be introduced into the second liquid heater, and others may be introduced into the liquid separator.

In addition, some of the refrigerant discharged from the evaporator may be introduced into the first liquid heater, and others may be introduced into the liquid separator.

In addition, a receiver may be provided between the first liquid heater and the evaporator, and a second solenoid valve may be provided between the receiver and the liquid separator to be opened and closed by the third temperature sensor.

The apparatus may further include a pressure gauge for measuring a refrigerant pressure of the receiver, and a third solenoid valve may be provided between the receiver and the first heater to be opened and closed by the pressure gauge.

The apparatus may further include a cold water tank for introducing the refrigerant from the receiver and performing heat exchange, and then introducing the heat-exchanged refrigerant into the liquid separator, the first liquid heater, and the second liquid heater.

According to the present invention, by controlling the amount of refrigerant through controlling the temperature of the discharge gas, it is possible to increase efficiency by preventing overcooling and overheating operation, and it is possible to solve the low pressure compensation and summer high pressure problems in winter by using the liquid heater in a parallel structure and freezing phenomenon. There is no unnecessary defrost work by preventing.

In addition, according to the present invention can be used at the same time the cold / hot function, and can be used simultaneously with the air and other heat sources by hybridizing the heat source has an advantageous effect in terms of equipment stability and installation cost.

In addition, according to the present invention is provided with an orifice at the inlet of the liquid separator, there is an effect to prevent the failure of the compressor in advance and to allow a sufficient amount of gas refrigerant to be sucked into the compressor.

In addition, according to the present invention by controlling the flow rate of the hot water using the water-saving side has the effect of improving the heat exchange capacity of the condenser and control the pressure of the refrigerant.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings. First, in adding reference numerals to the components of each drawing, it should be noted that the same reference numerals are assigned to the same components as much as possible, even if shown on different drawings. In addition, in describing the present invention, when it is determined that the detailed description of the related well-known configuration or function may obscure the gist of the present invention, the detailed description thereof will be omitted. In addition, the following will describe a preferred embodiment of the present invention, but the technical idea of the present invention is not limited thereto and may be variously modified and modified by those skilled in the art.

1 is a block diagram of a heat pump according to a preferred embodiment of the present invention.

Referring to FIG. 1, the heat pump according to the preferred embodiment of the present invention may include a compressor 100, a condenser 200, a first column 300, a second column 400, a receiver 500, and an evaporator. 600 and the liquid separator 700. The heat pump may include first to third temperature sensors TH1 to TH3, first to fifth solenoid valves SV1 to SV5, pressure gauges HP1, and first to second bulge valves EX1 and EX2. And a cold water tank 800.

The compressor 100 compresses the gas refrigerant of low temperature and low pressure transferred from the liquid separator 700 to high temperature and high pressure and transfers the gas refrigerant to the condenser 200.

The condenser 200 changes the gas refrigerant of the high temperature and high pressure compressed by the compressor 100 into a liquid refrigerant of high temperature and low pressure. In addition, the condenser 200 heat-exchanges with the hot water introduced from the second liquid heater 400 by using the heat generated during the phase change, and discharges the hot water toward the hot water outlet direction.

The third temperature sensor TH3 is provided between the compressor 100 and the condenser 200 to sense the temperature of the refrigerant discharged from the compressor 100, thereby the first solenoid valve SV1 and the second solenoid valve SV2. To control the opening and closing.

Specifically, when the temperature of the refrigerant discharged from the compressor 100 is equal to or less than a predetermined value, the third temperature sensor TH3 closes the first solenoid valve SV1. When the first solenoid valve SV1 is closed, the amount of the refrigerant flowing into the evaporator 600 decreases in half, thereby increasing the temperature of the refrigerant. In addition, when the temperature of the refrigerant discharged from the compressor 100 is greater than or equal to a predetermined value, the third temperature sensor TH3 lowers the refrigerant temperature by opening the first solenoid valve SV1 to increase the amount of the refrigerant.

Since the heat pump must be able to operate four seasons, it is necessary to control the temperature of the discharge gas in both winter and summer. The temperature of the discharge gas is most sensitive to the amount of refrigerant and the amount of heat of evaporation in the cycle of the heat pump. The temperature of the discharge gas is lowered when the amount of refrigerant is high and rises when the amount of refrigerant is low. If the temperature of the discharge gas is too low, the supercooling effect is excellent, but the heating effect is lowered, and the compressor may be damaged due to liquid compression due to insufficient evaporation. On the other hand, when the temperature of the discharge gas is excessively high, oil may carbonize due to deterioration and heating of the compressor may cause insulation breakdown.

Therefore, in the present invention, the plurality of expansion valves EX1 and EX2 are used, and the first solenoid valve SV1 is opened and closed through the third temperature sensor TH3 to adjust the amount of refrigerant flowing into the evaporator 600. Through this, the temperature of the discharge gas is controlled and the efficiency of the heat pump is increased by preventing overcooling and overheating operation.

In addition, the third temperature sensor TH3 detects the temperature of the refrigerant discharged from the compressor 100 to open and close the second solenoid valve SV2. When the temperature of the coolant is higher than a predetermined temperature in the summer, the third temperature sensor TH3 opens the second solenoid valve SV2 to allow the coolant to flow from the fluid receiver 500 into the liquid separator 700, thereby discharging the discharge gas. Cool.

The liquid heaters 300 and 400 perform low pressure compensation when the pressure of the refrigerant is too low and lower it when the pressure of the refrigerant is too high, thereby maintaining a stable pressure. The first column 300 and the second column 400 has a parallel structure to prevent the freezing phenomenon by performing a low pressure compensation to maintain a predetermined or more refrigerant pressure at a low temperature (separate defrosting work is unnecessary) It solves the phenomenon that the operation of the heat pump is impossible due to the pressure drop at low temperature, and prevents the high pressure overheat operation at high temperature. In particular, by introducing hot water into the second heat exchanger 400, the low pressure compensation of the winter season can be performed more effectively.

The first heat exchanger 300 uses the refrigerant discharged from the condenser 200 to perform heat exchange with the refrigerant discharged from the evaporator 600. At this time, since the refrigerant discharged from the condenser 200 is relatively hot compared to the refrigerant discharged from the evaporator 600, the liquid refrigerant not completely evaporated among the refrigerant discharged from the evaporator 600 is evaporated by obtaining heat. As such, the refrigerant discharged from the evaporator 600 and heat-exchanged through the first liquid heater 300 flows into the liquid separator 700.

The second liquid heat generator 400 performs heat exchange with the refrigerant discharged from the evaporator 600 by using hot water introduced from the outside. At this time, since the hot water introduced from the outside (hot water tank, not shown) is relatively high temperature compared to the refrigerant discharged from the evaporator 600, the liquid refrigerant (first liquid heater not completely evaporated among the refrigerant discharged from the evaporator 600) The remaining fraction of the liquid refrigerant entering the evaporation and evaporating is evaporated by obtaining heat. Likewise, the refrigerant exchanged in this manner is introduced into the liquid separator 700. That is, some of the unevaporated liquid refrigerant discharged from the evaporator 600 flows into the second liquid heater 400, and the remainder is transferred toward the liquid separator 700. In addition, some of the unevaporated liquid refrigerant discharged from the evaporator 600 is introduced into the first liquid heater 300, the remainder is introduced into the liquid separator 700.

On the other hand, the hot water that has undergone heat exchange while passing through the second liquid heater 400 flows into the condenser 200 and discharges to the hot water tank after performing heat exchange and condensation due to the phase change of the refrigerant introduced from the compressor 100. Thereby allowing the continuous hot water to be produced continuously.

The first temperature sensor TH1 is provided at the hot water inlet side, and the second temperature sensor TH2 is provided at the hot water outlet side.

The first temperature sensor TH1 controls the operation of the compressor 100 by sensing a temperature of hot water flowing into the second liquid heater 400. Specifically, when the temperature of the hot water introduced into the second heat exchanger 400 is above a predetermined temperature (eg, 50 degrees C), heat exchange with condensation heat due to phase change in the condenser 200 may not be performed smoothly, and thus hot water production capacity. This deteriorates and the compressor 100 is overloaded. Therefore, the first temperature sensor TH1 turns off the compressor when the temperature of the hot water flowing into the second liquid heater 400 is high.

The second temperature sensor TH2 controls the opening and closing of the fifth solenoid valve SV5 by sensing the temperature of the hot water discharged from the condenser 200. The fifth solenoid valve SV5 is provided at the hot water outlet side to improve the heat exchange capacity of the condenser 200 by adjusting the flow rate of the hot water. For example, when the temperature of the hot water is above a certain temperature, the second temperature sensor TH2 closes the fifth solenoid valve SV5 to reduce the flow rate of the hot water. When the flow rate of the hot water is reduced, the phenomenon that the heat exchange capacity of the condenser 200 is lowered due to the temperature rise of the hot water is improved.

In addition, the hot water outlet side is provided with a water-saving side (WV) and a bypass (hot water passage branched below the water-saving side). When the coolant pressure drops below a predetermined value, the water-saving valve WV adjusts the pressure of the coolant through the flow rate control of the hot water. In winter, the evaporation temperature is low and the amount of refrigerant recovered is low, so the pressure of the refrigerant drops. In this case, the water-saving valve is operated to increase the flow rate of the hot water, thereby improving the heat exchange capacity of the condenser 200 and increasing the pressure of the refrigerant.

The receiver 500 is temporarily discharged from the condenser 200, the refrigerant passing through the first heater 300 is temporarily supplied to the expansion valve (SX1, SX2). A pressure gauge HP1 is provided to measure the pressure of the refrigerant flowing into the fluid receiver 500 or discharged from the fluid receiver 500. As mentioned above, the second solenoid valve SV2, which is opened and closed by the third temperature sensor TH3, is positioned between the receiver 500 and the liquid separator 700.

In addition, a third solenoid valve SV3 that is opened and closed by the pressure gauge HP1 is provided between the receiver 500 and the first heat receiver 300. The third solenoid valve SV3 is opened by the pressure gauge HP1 when the pressure of the refrigerant rises excessively in the summer, and the like, so as to lower the temperature of the hot water by cooling the heat heaters 300 and 400 and to lower the pressure of the refrigerant. do.

The expansion valves EX1 and EX2 rapidly expand the high-temperature low-pressure liquid refrigerant supplied from the receiver 500 to a low-temperature low-pressure fog state and supply them to the evaporator 600. The first expansion valve EX1 is located between the receiver 500 and the evaporator 600, and the second expansion valve EX2 is located between the first solenoid valve SV1 and the evaporator 600. At this time, the transfer path containing CH is used in the cooling cycle. Since the CH passes the refrigerant only in one direction (the lower direction in FIG. 1), the refrigerant does not flow into the transfer path including the CH in the hot water cycle. As described above, the first solenoid valve SV1 is opened and closed by the third temperature sensor TH3 to control the amount of refrigerant, thereby adjusting the temperature of the discharge gas of the compressor 100.

The evaporator 600 allows the misty refrigerant supplied from the expansion valves EX1 and EX2 to evaporate while taking away the surrounding heat. The evaporator 600 serves as a condenser in the cooling cycle.

The liquid separator 700 separates the liquid refrigerant from the refrigerant passing through the evaporator 600, so that the liquid refrigerant does not flow into the compressor 100. An orifice 710 is provided between the evaporator 600 and the liquid separator 700 to inject the liquid refrigerant.

FIG. 2 is a partial cutaway perspective view of the orifice of FIG. 1, FIG. 3 is a vertical sectional view of FIG. 2, and FIG. 4 is a plan view of FIG. 2.

The orifice 710 includes a pipe part 10, a blocking film 20, and a capillary tube 30.

The pipe part 10 is provided at the inlet side of the liquid separator 700. The pipe part 10 transfers the refrigerant of low temperature and low pressure discharged from the evaporator 600 and supplies it to the liquid separator 700. The refrigerant conveyed through the pipe part 10 includes a gaseous refrigerant sufficiently evaporated in the evaporator 600 and a liquid refrigerant not sufficiently evaporated in the evaporator 600.

The blocking film 20 is provided inside the pipe part 10. The blocking film 20 is formed in a concave shape with respect to the advancing direction (arrow) of the coolant, so that the coolant colliding with the concave surface accumulates. The blocking film 20 may be formed in a hemispherical shape as shown in FIG. 2, and although not shown, the blocking film 20 may be formed in various shapes such as a semi-elliptic shape, a cone shape, or a truncated cone shape.

The capillary tube 30 is formed in the blocking film 20 to select a refrigerant and spray a liquid refrigerant. The capillary tube 30 is provided in plural in the blocking membrane 20, so that the gas coolant is permeated and the liquid coolant is sprayed to have smaller diameter particles. That is, the gaseous refrigerant sufficiently evaporated in the evaporator 600 is allowed to pass through as it is to be sucked into the liquid separator 700, and the liquid refrigerant that is not vaporized is injected into the fine particles to form a liquid phase and a gaseous phase in the liquid separator 700. To facilitate the separation and to produce a greater amount of gaseous refrigerant. This prevents failure of the compressor 100 in advance and allows a sufficient amount of gas refrigerant to be sucked into the compressor.

In addition, the amount of refrigerant can be controlled by adjusting the number of capillaries 30.

5A and 5B are cross-sectional views illustrating another embodiment of a capillary tube.

Referring to FIGS. 5A and 5B, the capillary tube may be formed such that an inner diameter gradually increases along a direction in which the refrigerant moves (arrows).

In the case of Figure 5a, the capillary tube has an internal diameter increases at a constant rate along the direction of travel of the refrigerant. That is, in the cross section including the central axis C of the capillary tube, the inner circumferential surface of the capillary tube forms an inclined straight line (primary function) having a predetermined slope with respect to the central axis C. At this time, the capillary is formed in an approximately funnel shape.

In the case of FIG. 5B, the capillary tube has an inner diameter that increases at an increasing rate along the advancing direction of the refrigerant. That is, in the cross section including the central axis C of the capillary tube, the inner circumferential surface of the capillary tube is curved with respect to the central axis C (higher-order function, y = ax ⁿ + b). At this time, the capillary is formed in a substantially trumpet shape.

As such, the injection diameter of the liquid refrigerant may be maximized by increasing the inner diameter of the capillary tube in the advancing direction of the refrigerant.

6 is a vertical sectional view of an embodiment having a plurality of blocking films.

Referring to FIG. 6, a plurality of blocking films 20a and 20b may be provided to form a multilayer. Accordingly, the capillaries 30a and 30b also form a multilayer.

The blocking membrane 20a and the capillary tube 30a disposed in the upper portion of FIG. 6 are referred to as the primary blocking membrane 20a and the primary capillary tube 30a, respectively, and the blocking membrane 20b and the capillary tube 30b disposed in the lower portion of FIG. It is referred to as the secondary blocking film 20b and the secondary capillary tube 30b.

The refrigerant in the gaseous state is discharged through the primary capillary tube 30a after the collision with the primary blocking membrane 20a, and passes through the secondary capillary tube 30b after the collision with the secondary barrier membrane 20b. That is, the gaseous refrigerant proceeds in the direction of the liquid separator 700 without difficulty.

On the other hand, the liquid refrigerant is injected into the fine particles through the primary capillary 30a and re-injected through the secondary capillary tube 30b when a certain amount is accumulated after the impact on the primary blocking film 20a. That is, in the multilayer structure, the spray is repeatedly performed through the multilayer capillaries 30a and 30b, so that finer particles can be produced. To this end, it is preferable that the capillary diameter of the multilayer structure is reduced along the advancing direction of the refrigerant. That is, the secondary capillary 30b is preferably formed smaller than the diameter of the primary capillary 30a (in the case of the n-th capillary, the diameter of the capillary decreases as n increases).

The heat pump according to the present invention can use cooling and heating (cooling cycle and hot water cycle) at the same time. That is, the cooling cycle may be performed while the hot water cycle is in progress. The cooling cycle is carried out as follows.

The refrigerant compressed by the compressor 100 flows into the condenser 200 and then discharges into the four-way valve 4W. When the four-way valve 4W is operated, the refrigerant is conveyed toward the evaporator 600 (the condenser in the cooling cycle), condensed, and then transferred downward through the CH shown directly below the evaporator 600. At this time, when the third solenoid valve SV3 is opened, the third solenoid valve SV3 is introduced into the fourth solenoid valve SV4 through the receiver 500 through the CH. When the fourth solenoid valve SV4 is opened, the refrigerant is injected through the third expansion valve EX3 and flows into the cold water tank 800. The refrigerant evaporated while performing heat exchange with cold water in the cold water tank 800 is introduced into the compressor 100 through the liquid separator 700.

Heat pump according to the present invention can reduce the energy cost for hot water production because it utilizes in hot water production instead of discarding the condensation heat source generated for cold water production in the summer as a waste heat source in the atmosphere. In other words, when cold water and hot water are needed at the same time in summer, the heat pump can be used to produce two heat sources at the cost of producing one heat source, thereby greatly reducing energy costs.

The heat pump may reduce the efficiency decrease due to lack of heat of evaporation by using heating and cooling at the same time in the production of winter hot water. On the other hand, instead of using multiple heat sources such as geothermal heat, sea water, and river water independently in order to prevent deterioration of efficiency due to the reduction of evaporative heat during the hot water production in winter, the heat pump can use air and other heat sources simultaneously. There are various advantages in terms of stability and installation cost.

In the case of general heat pumps, waste water, seawater, and other highly corrosive heat sources cause moisture to penetrate into the equipment due to breakage of the evaporator, which incurs a lot of repair costs. As a result, the durability of the equipment is also excellent. In addition, when the evaporator is damaged, the evaporator, the compressor, and the like are often replaced, but the heat pump can be repaired and repaired at a low cost since only the damage line needs to be replaced.

The above description is merely illustrative of the technical idea of the present invention, and various modifications, changes, and substitutions may be made by those skilled in the art without departing from the essential characteristics of the present invention. will be. Accordingly, the embodiments disclosed in the present invention and the accompanying drawings are not intended to limit the technical spirit of the present invention but to describe the present invention, and the scope of the technical idea of the present invention is not limited by the embodiments and the accompanying drawings. . The protection scope of the present invention should be interpreted by the following claims, and all technical ideas within the equivalent scope should be interpreted as being included in the scope of the present invention.

The present invention relates to a heat pump, in particular, when a hybrid function using a complex heat source is required, and at the same time can be applied to a wide range such as cold / hot function.

1 is a block diagram of a heat pump according to a preferred embodiment of the present invention,

2 is a partial cutaway perspective view of the orifice of FIG.

3 is a vertical cross-sectional view of FIG.

4 is a plan view of FIG.

5a and 5b are cross-sectional views for explaining another embodiment of the capillary,

6 is a vertical sectional view of an embodiment having a plurality of blocking films.

<Description of the symbols for the main parts of the drawings>

100-Compressor 200-Condenser

300-1st column 400-2nd column

500-Receiver 600-Evaporator

700-Liquid Separator 800-Cold Water Tank

Claims (20)

compressor; A condenser for condensing the refrigerant compressed by the compressor; A third temperature sensor positioned between the compressor and the condenser to sense a temperature of the refrigerant discharged from the compressor; An evaporator through which the refrigerant passing through the condenser is introduced to evaporate the refrigerant; A first solenoid valve positioned between the condenser and the evaporator to control the amount of refrigerant flowing into the evaporator by being opened and closed by the first temperature sensor; A first expansion valve positioned between the condenser and the evaporator; A second expansion valve positioned between the first solenoid valve and the evaporator; And Liquid separator for separating the liquid refrigerant from the refrigerant passing through the evaporator Heat pump comprising a. The method of claim 1, The third temperature sensor is a heat pump, characterized in that for closing the first solenoid valve when the temperature of the refrigerant discharged from the compressor is a predetermined value or less. The method of claim 2, The third temperature sensor is a heat pump, characterized in that for opening the first solenoid valve when the temperature of the refrigerant discharged from the compressor is above a certain value. The method of claim 1, Heat pump is characterized in that between the evaporator and the liquid separator is an orifice for injecting a liquid refrigerant. The method of claim 4, wherein the orifice A pipe part provided at an inlet side of the liquid separator to supply a refrigerant to the liquid separator; A blocking film provided inside the pipe part; And Capillary tubes formed on the barrier layer for permeating gas refrigerant and injecting liquid refrigerant Heat pump comprising a. The method of claim 5, The blocking film is a heat pump, characterized in that formed in a concave shape with respect to the traveling direction of the refrigerant. The method of claim 6, The blocking film is a heat pump, characterized in that formed in any one of the shape of hemispherical, semi-elliptic, conical, conical The method of claim 5, The capillary tube is provided with a plurality, heat pump characterized in that the inner diameter gradually increases along the direction of the refrigerant. The method of claim 8, The heat pump, characterized in that the inner circumferential surface of the capillary in the cross section including the central axis of the capillary is inclined or curved with respect to the central axis. The method of claim 5, The blocking film is provided with a plurality of heat pump, characterized in that to form a multi-layer. The method of claim 1, And a first heat exchanger configured to perform heat exchange with the refrigerant discharged from the evaporator using the refrigerant discharged from the condenser. The method of claim 11, The refrigerant discharged from the evaporator and the heat exchanged through the first liquid heater is introduced into the liquid separator. The method of claim 11, And a second heat exchanger configured to perform heat exchange with the refrigerant discharged from the evaporator using hot water introduced from the outside. The method of claim 13, The hot water passing through the second liquid heater is introduced into the condenser, heat pump characterized in that the heat exchange with the refrigerant introduced from the compressor. The method of claim 14, A first temperature sensor for sensing the temperature of the hot water flowing into the second liquid heater to control the operation of the compressor, a second temperature sensor for sensing the temperature of the hot water discharged from the condenser, and a hot water outlet side And a fifth solenoid valve opened and closed by the second temperature sensor. The method of claim 14, Some of the refrigerant discharged from the evaporator is introduced into the second liquid heater, and the rest is introduced into the liquid separator. The method of claim 14, Some of the refrigerant discharged from the evaporator is introduced into the first liquid heater, and the rest is introduced into the liquid separator. The method of claim 1, A receiver is provided between the first column and the evaporator, And a second solenoid valve which is opened and closed by the third temperature sensor between the receiver and the liquid separator. The method of claim 18, Further comprising a pressure gauge for measuring the refrigerant pressure of the receiver, And a third solenoid valve which is opened and closed by the pressure gauge between the receiver and the first heater. The method of claim 18, And performing a heat exchange by introducing a refrigerant from the receiver, and further comprising a cold water tank configured to introduce the heat-exchanged refrigerant into the liquid separator, the first liquid heater, and the second liquid heater.

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