KR20070059405A - Heat pump type heating apparatus raising the heating capacity - Google Patents

Abstract

A heat pump type heating apparatus increasing a heating capacity is provided to realize a high level of the heating capacity with reducing power consumption by use enough performance of a compressor. A heat pump type heating apparatus increasing a heating capacity includes a casing(101), a compressor(102), a condenser(103), an expansion valve(105), a heating unit(106), and a main heater(107). The heating unit makes coolant having a low temperature and pressure by heating as a high temperature and a low pressure condition of the coolant by using some of coolant having a high temperature from the compressor. The compressor is stably installed on a bottom of the casing, compresses the coolant as a high temperature and pressure condition, and circulates the coolant. The condenser is connected to the compressor, condenses the coolant in an evaporation state, and generates heat. The expansion valve is connected between the condenser and the compressor. The main heater is installed on a second branch pipe and heats coolant flowing through the second branch pipe for making the coolant have high temperature.

Description

Heat pump type heating device with improved heating performance {HEAT PUMP TYPE HEATING APPARATUS RAISING THE HEATING CAPACITY}

1 is a block diagram of a heating and cooling device according to the prior art.

2 is a configuration diagram for explaining the configuration according to the first embodiment of the present invention.

Figure 3 is a perspective view for explaining a plate heat exchanger as a heating means according to the first embodiment of the present invention.

Figure 4 is a perspective view for explaining the configuration of the main heater according to the first embodiment of the present invention.

5 is a partial cross-sectional view of the main heater according to the first embodiment of the present invention.

6 is a perspective view for explaining a modified configuration of the main heater according to the first embodiment of the present invention.

7 is a partial cross-sectional view for explaining a modified configuration of the main heater according to the first embodiment of the present invention.

8 is an operation diagram for explaining a state change of the heating cycle according to the first embodiment of the present invention.

9 is a configuration diagram for explaining the configuration according to the second embodiment of the present invention;

10 is an operation diagram for explaining a state change of the heating cycle according to the second embodiment of the present invention.

11 is a configuration diagram for explaining the configuration of the modified second embodiment according to the present invention.

12 is a configuration diagram for explaining the configuration according to the third embodiment of the present invention.

13 is an operation diagram for explaining a state change of the heating cycle according to the third embodiment of the present invention.

14 is a configuration diagram for explaining a third modified embodiment of the present invention.

15 is a configuration diagram for explaining the configuration according to the fourth embodiment of the present invention.

16 is an operation diagram for explaining a state change of the refrigerant by the heating cycle of the present invention.

17 is a configuration diagram for explaining a fourth modified embodiment of the present invention.

18 is a configuration diagram for explaining a fourth embodiment modified to another embodiment of the present invention.

19 is a configuration diagram for explaining the configuration of the present invention.

20 is a reference diagram for explaining an operation during heating of the present invention.

21 is a reference diagram for explaining an operation during cooling of the present invention.

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

101,201,301,401,501 Casing 102,202,302,402,502 Compressor

103,203,303: Response device 105,205,305,404,504: Expansion valve

106: heating means 107,207,307A, 307B, 508: heater

171: heater body 175: heating bar

108A, 108B, 208A, 208B, 308A, 308B: Temperature Sensor

109,209,209,408 Controller 403,503 First heat exchanger

405, 505: second heat exchanger 406: third heat exchanger

403,503: first heat exchanger

405, 505: second heat exchanger 406: third heat exchanger

The present invention relates to a heat pump type heating apparatus, and in particular, in order to maintain the state of the refrigerant flowing into the compressor in an optimal state so that the compressor can exhibit the best performance during heating, the heating is realized only by the heating cycle by the refrigerant circulation. Of course, the present invention relates to a heat pump type heating device having a heating performance that can dramatically improve heating performance.

In general, air conditioners are devices that selectively realize cooling and heating by means of two heat exchangers alternately performing the roles of a compressor and a condenser.

Here, the cooling and heating device is the first heat exchanger and the second heat exchanger provided alternately performs the role of the condenser and the evaporator, respectively, the refrigerant is circulated according to the cooling and heating cycle having a continuous process of compression-condensation-expansion-evaporation In reverse circulation, cooling and heating are realized.

The cooling performance depends on how effectively the first heat exchanger cools down during cooling, and the heating performance depends on how effectively the first heat exchanger heats up during heating.

Basically, the heating and cooling performance varies greatly depending on how well the heating and cooling cycle with a continuous process of compression-condensation-expansion-evaporation is performed.

Thus, Figure 1 is a block diagram of a conventional heating and cooling device.

As shown, the conventional air conditioner is a compressor (12), the first heat exchanger (13), the expansion valve (14), the evaporator for cooling and the condenser for heating that serves as a condenser for cooling and the evaporator for heating. A continuous process of compression-condensation-expansion-evaporation, comprising a second heat exchanger (15) serving and an auxiliary heater (19) installed between the compressor (12) and the second heat exchanger (15). As we progressed, we could selectively implement cooling and heating.

Here, the auxiliary heater 19 is provided to further enhance the performance of the second heat exchanger 15 that acts as a condenser during heating and generates latent heat according to the phase change of the refrigerant. Described in 2005-0093645.

However, in the conventional air conditioner, although the performance of the second heat exchanger 15 serving as a condenser is increased, the refrigerant rapidly expands in the expansion valve 14 so that the temperature drops considerably and the surrounding air is removed. There was a problem that the cooling performance is reduced because of this. In addition, the circulation of the refrigerant is not smooth as the erosion around the expansion valve 14, the compressor 12 does not exhibit sufficient performance, the performance of the entire heating cycle is reduced, and as a result adversely affect the overall heating performance Caused.

For reference, in order to compress the refrigerant to a high temperature and a high pressure while the compressor 12 is fully functioning, the temperature of the refrigerant flowing into the compressor 12 should be about 15 [° C.] or more. However, in the winter season when the heating is actually required, the temperature of the ambient air is considerably low, and the expansion process of the expansion valve 14 and the evaporation process of the first heat exchanger 13 are installed whether the compressor 12 is installed outdoors or indoors. The refrigerant flowing into the compressor 12 immediately after passing through is overcooled to a temperature below zero, such that the compressor 12 does not normally satisfy the temperature condition for proper function.

In addition, the conventional air conditioner causes a problem of lowering heating performance while cooling the surrounding air together with the expansion valve 14 because the first heat exchanger 13 still evaporates during heating. In addition, there is a problem in that the device is complicated by installing unnecessary first heat exchanger 13 and an accompanying discharge fan (not shown).

Accordingly, the present invention has been proposed to solve the above conventional problems, the object of the present invention is to realize the heating only by the heating cycle by the refrigerant circulation, the state of the refrigerant flowing into the compressor to improve the heating performance It is to provide a heat pump type heating device with improved heating performance to control the.

In order to achieve the above object, a heat pump type heating apparatus having a high heating performance according to the technical idea of the present invention includes a compressor for compressing a refrigerant to be discharged in a high temperature, high pressure steam state, and connected to the compressor. A condenser for generating heat by converting the refrigerant in a vapor state into a liquid state at room temperature and high pressure, an expansion valve connected to the condenser and a compressor, and expanding the refrigerant sent from the condenser to the compressor; And a heating means installed between the compressor and the low temperature refrigerant flowing into the compressor from the expansion valve.

Here, the heating means may be characterized in that the heat exchange with the low-temperature refrigerant from the expansion valve by branching some of the high-temperature refrigerant from the compressor.

In addition, the heating means, a plurality of thin metal plate formed with a plurality of flow paths through which the high-temperature refrigerant from the compressor and the low-temperature refrigerant flowing from the expansion valve is stacked, the high-temperature refrigerant and low-temperature refrigerant flows along the flow paths It may be characterized in that the plate heat exchanger.

And a first branch pipe for branching some of the refrigerant from the compressor to the condenser to the heating means, and a second branch pipe for discharging the refrigerant heat-exchanged with the low temperature refrigerant from the heating means to the condenser. The two branch pipes may be further provided with a main heater for heating the refrigerant sent to the condenser.

On the other hand, the present invention, a compressor for compressing the refrigerant to be discharged to a high temperature and high pressure steam state, and a condenser connected to the compressor, and converts the refrigerant in the vapor state sent from the compressor to a liquid state of the normal temperature and high pressure to generate heat And an expansion valve connected to the condenser and the compressor and expanding the refrigerant sent from the condenser to the compressor, installed between the expansion valve and the compressor, and heating the refrigerant entering the compressor to pass through the expansion valve. It may be characterized by the technical configuration that the main heater is configured to have a state of the coolant at room temperature.

Here, a temperature sensor for measuring the temperature of the refrigerant is installed between the main heater and the compressor, the controller for controlling the main heater in accordance with the value measured by the temperature sensor to optimally maintain the temperature of the refrigerant entering the compressor It may be characterized in that it further comprises.

In addition, it may be characterized in that it further comprises a bypass pipe for branching some of the refrigerant from the compressor sent to the condenser to the main heater.

On the other hand, the present invention is a compressor for compressing the refrigerant to take out the high-temperature high-pressure steam state, a condenser connected to the compressor, and converts the refrigerant in the vapor state sent from the compressor to a liquid state of the normal temperature and high pressure to generate heat; An expansion valve connected to the condenser and the compressor and expanding the refrigerant sent from the condenser to the compressor, and installed between the condenser and the expansion valve, and heating the refrigerant entering the expansion valve to pass through the expansion valve. It may be configured to include a main heater to bring the state of the refrigerant to room temperature.

Here, a temperature sensor for measuring the temperature of the refrigerant is installed between the expansion valve and the compressor, the controller to control the main heater according to the value measured by the temperature sensor to maintain the room temperature of the refrigerant passing through the expansion valve It may be characterized in that it further comprises.

The apparatus may further include a first auxiliary heater installed between the expansion valve and the compressor to selectively heat the refrigerant by the controller, and a temperature sensor installed between the first auxiliary heater and the compressor. have.

In addition, after the branch between the compressor and the condenser is connected between the expansion valve and the compressor may be characterized in that the bypass pipe is further installed to send a portion of the high-temperature, high-pressure refrigerant from the compressor to the compressor.

In addition, the bypass pipe may be further provided with a second auxiliary heater for selectively heating the refrigerant of the high temperature and high pressure branched out.

In addition, the heating apparatus of the present invention includes a compressor for compressing a refrigerant to be discharged in a high temperature, high pressure steam state, an expansion valve for pressure dropping the high pressure liquid refrigerant to a low pressure liquid refrigerant, and a high pressure receiving the steam refrigerant compressed by the compressor. A first heat exchanger acting as a condenser to generate heat while condensing with the liquid refrigerant, a second heat exchanger which is operated only during heating to vaporize a portion of the low pressure liquid refrigerant from the expansion valve, and the second heat exchanger; It may be characterized by the technical configuration that is configured to include a third heat exchanger that serves as an evaporator to accept and vaporize the refrigerant in a part of the vaporized state.

In addition, the heating apparatus of the present invention is a compressor for compressing a refrigerant to be discharged to a high-temperature, high-pressure steam state, a first heat exchanger that receives the vapor refrigerant compressed by the compressor and generates heat while condensing into a high-pressure liquid refrigerant, And a second heat exchanger for heating and vaporizing the low pressure liquid refrigerant from the expansion valve by receiving a low pressure liquid refrigerant and reducing the pressure of the high pressure liquid refrigerant condensed in the first heat exchanger. It may be characterized by technical configuration.

Here, a temperature sensor for measuring the temperature of the refrigerant entering the compressor is installed on the refrigerant inlet side of the compressor, and the temperature of the refrigerant entering the compressor is controlled by controlling the second heat exchanger according to a value measured by the temperature sensor. It can be characterized in that the controller is further installed.

In addition, the second heat exchanger has an insertion hole, a heater body provided with a chamber through which refrigerant flows in and stays inside the wall, and an electric coil therein to generate heat of resistance, and in the insertion hole. It may be characterized in that it comprises a pair of heating bars that are inserted to indirectly heat the refrigerant introduced into the chamber.

In addition, it may be characterized in that it further comprises a bypass pipe for sending the refrigerant from the second heat exchanger and sent to the third heat exchanger to the compressor.

On the other hand, the heating device of the present invention, the expansion valve for cooling for reducing the high-pressure liquid refrigerant to low-pressure liquid refrigerant, the compressor for compressing the refrigerant, and the low-pressure liquid refrigerant pressure-reduced in the cooling expansion expansion valve for vaporizing A first heat exchanger serving as an evaporator, a second heat exchanger serving as a condenser that generates heat by converting a vapor refrigerant into a liquid refrigerant, and a refrigerant which is installed between the compressor and the second heat exchanger and is discharged from the compressor during heating. Although it penetrates, it may be characterized by the technical configuration that comprises a heating expansion valve for reducing the pressure to a high temperature and high pressure of the refrigerant before the penetration and the pressure drop in the state of high temperature and low pressure after the penetration.

Here, the heating expansion valve is formed longer than the length of the expansion valve for cooling, it may be characterized in that the refrigerant before penetration through the high temperature and high pressure than the expansion valve for cooling.

The apparatus may further include a main heater installed between the second heat exchanger and a heating expansion valve to further heat a high temperature refrigerant from the heating expansion valve.

The heater may further include a heater body having an insertion hole, a heater body having a chamber in which refrigerant flows into and stays in the wall, and an electric coil therein to generate heat of resistance, and may be inserted into the insertion hole. It may be characterized in that it comprises a heating bar for indirectly heating the refrigerant introduced into the chamber.

In addition, the bimetal to block the abnormal high temperature of the main heater may be characterized in that it is further installed.

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

[First Embodiment]

The heat pump type heating apparatus of the present invention is configured to allow the compressor to fully exhibit its original performance, and to more actively utilize a heating cycle that starts with the compression process by the compressor. This makes it possible to realize a high level of heating performance with a small amount of electricity.

The heat pump type heating apparatus of the present invention drastically omits various components such as an evaporator and an accompanying discharge fan, thereby drastically reducing the production cost of the product, and is a product for heating exclusively in which a cooling cycle is impossible due to the reverse circulation of the refrigerant. to be.

In addition, the present invention can be usefully used as a portable type indoors since no outdoor unit is required at all.

Hereinafter, the configuration of the heat pump type heating apparatus with improved heating performance according to the present invention will be described in detail.

2 is a configuration diagram for explaining the configuration according to the first embodiment of the present invention, Figure 3 is a perspective view for explaining a plate heat exchanger which is a heating means according to the first embodiment of the present invention, Figure 4 is a present invention 5 is a perspective view for explaining the configuration of the main heater according to the first embodiment of the present invention, Figure 5 is a partial cross-sectional view of the main heater according to the first embodiment of the present invention.

As shown, the present invention includes a casing 101, a compressor 102, a condenser 103, an expansion valve 105, a heating means 106, and a main heater 107 as main components.

 According to the present invention, the heating means 106 is used to heat the low-temperature low-pressure refrigerant from the expansion valve 105 by using some of the high-temperature refrigerant from the compressor 102 to bring it to a low-temperature state of normal temperature. As a result, a refrigerant having an appropriate temperature of about 15 [° C.] can be introduced into the compressor 102, so that the compressor 102 can exhibit sufficient performance, and the heating cycle is smoothly performed. Hereinafter, the configuration of the present invention will be described in more detail based on the technical gist of the present invention.

First, the casing 101 can be made small and simple in a portable internal space. This is because parts, such as the evaporator, which has been cooled unlike the conventional art, and the discharge fan accompanying the evaporator, have been completely removed. A blower 111 is installed in the casing 101, and the blower 111 sucks indoor air to exchange heat with the condenser 103, and then blows it back into the room to provide warmth for indoor heating. Done.

The compressor 102 is normally installed stably at the bottom of the casing 101 in relation to a significant load, and plays an important role of compressing and circulating the refrigerant in a high temperature, high pressure steam state. The compressor 102 according to the present invention can fully exhibit the original function because the refrigerant maintains the proper temperature by the main heat 107 to increase the temperature of the refrigerant. As a result, the heating cycle is smoothly performed, and the room can be sufficiently heated without having a separate electric heater.

The condenser 103 is installed in connection with the compressor 102 and serves to generate heat while condensing the refrigerant in the vapor state sent from the compressor 102 into a liquid state at room temperature and high pressure.

The expansion valve 105 is connected between the condenser 103 and the compressor 102, and serves to expand the refrigerant sent from the condenser 103 to the compressor (102). At this time, the refrigerant is expanded by the expansion valve 105 and experiences a temperature decrease to some extent. However, since the refrigerant enters the compressor 102 through the main heater 107, the refrigerant 102 maintains an appropriate room temperature at which the compressor 102 can operate smoothly.

The heating means 106 is installed between the expansion valve 105 and the compressor 102 to heat the refrigerant entering the compressor (102). The purpose of installing the heating means 107 is to allow the refrigerant to enter the compressor 102 while maintaining a normal temperature of about 15 [° C.]. As a result, the compressor 102 can fully ensure its performance while ensuring smooth operation of the entire heating cycle.

As shown in FIG. 3, the heating means 106 includes a plurality of thin metal plates each having flow paths through which high-temperature refrigerant from the compressor 102 and low-temperature refrigerant from the expansion valve 105 flow. It is provided with a plate heat exchanger. The flow paths of the plate heat exchanger are the inlet side 106A and the outlet side 106B of the high temperature refrigerant into which the high temperature refrigerant from the compressor 102 flows in and out, and the low temperature refrigerant from the expansion valve 105. Has an inflow side 106C and an outflow side 106D of the refrigerant flowing in and out. Here, the inlet side 106A of the high temperature refrigerant is connected to the first branch pipe 110 for branching some of the high temperature refrigerant flowing out of the compressor into the condenser 103. The outlet side 106B of the high temperature refrigerant discharges the refrigerant heat-exchanged with the low temperature refrigerant in the plate heat exchanger, which is the heating means 106, to the condenser 103 (exactly, the compressor 102 and the condenser 103). It is connected to the second branch pipe (111) to be discharged to the pipe connecting. The inlet side 160C of the low temperature refrigerant is connected to the expansion valve 105. The outlet side 106D of the low temperature refrigerant is connected to the inlet side of the compressor 102.

The plate heat exchanger, which is the heating means 106, is for heat-exchanging two or more kinds of fluids, and corresponds to a known technology in which various excellent products such as a brazing type have already been developed in other fields. Therefore, detailed description of the configuration will be omitted.

On the other hand, temperature sensors 108A, 108B and controller 109 are further installed to maximize the action of the heating means 106. The temperature sensors 108A and 108B are installed between the expansion valve 105 and the heating means 106, and between the heating means 106 and the compressor 102, respectively, immediately after passing through the expansion valve 105. The refrigerant temperature and the refrigerant temperature immediately after being heated by the heating means 106 are measured. The controller 109 adjusts the amount of the high temperature refrigerant flowing branched to the heating means 106 according to the values measured by the temperature sensors 108A and 108B. Of course, for this purpose, it is preferable that a flow control valve (not shown) is installed on the first branch pipe (110). The controller controls the degree of heating the low-temperature refrigerant passing through the heating means 106 by adjusting the amount of the high-temperature refrigerant passing through the heating means 106 using the flow control valve. For example, when the temperature of the refrigerant immediately after passing through the expansion valve 105 is higher than an appropriate value, the controller 109 reduces the amount of high temperature refrigerant passing through the heating means 106 to lower the heating degree. On the other hand, when the temperature of the refrigerant immediately after passing through the expansion valve 105 is lower than an appropriate value, the amount of high temperature refrigerant passing through the heating means 106 is increased to increase the degree of heating. In addition, the temperature sensor 108B installed after the imparting means 106 measures the temperature of the refrigerant entering the compressor 102 and informs the controller 109. This allows the controller 109 to adjust the amount of refrigerant via the heating means 106 to an appropriate level.

The main heater 107 is installed in the second branch pipe 111 to exchange heat with the low temperature refrigerant flowing from the expansion valve 105 to the compressor 102, and then re-cools the refrigerant flowing through the second branch pipe 111. It plays a role of making high temperature refrigerant by heating. To this end, the main heater 107 includes a heater body 171 and a heating bar 175. The heater body 171 has an insertion hole 173 at the center, and a chamber 172 is provided inside the wall surface where the refrigerant flows in and stays out as shown by the arrow. The heating bar 175 is provided with an electric coil 176 therein and is connected to a power source to generate resistance heat, and has a shape that can be inserted into the insertion hole 173. The heating bar 175 indirectly heats the refrigerant flowing into the chamber 173 while being inserted into the insertion hole 173.

In addition, the main heater 107 is further provided with a bimetal (not shown) serves to block the abnormal high temperature of the main heater 107.

On the other hand, the main heater 107 according to the present invention can be a modified configuration in which a plurality of heating bar is installed in one heater body.

Thus, Figure 6 is a perspective view for explaining a modified configuration of the main heater according to the first embodiment of the present invention, Figure 7 is a view for explaining a modified configuration of the main heater according to the first embodiment of the present invention Partial section view.

As shown, the deformed main heater 107 is provided with a plurality of heating bars 175A, 175B in one heater body 171, for this purpose the insertion hole 173 in the heater body 171 ) Is provided to match the number of the heating bar (175A, 175B). As such, when a plurality of heating bars 175A and 175B are provided, a larger amount of the refrigerant may be quickly heated.

Hereinafter, the operation of the present invention will be described in detail with reference to FIG. 8 and other accompanying drawings. 8 is an operation diagram for explaining a state change of the heating cycle according to the first embodiment of the present invention.

As shown, the refrigerant compressed in the compressor 102 in the operation of the present invention is a high temperature and high pressure steam state, most of the flow into the condenser 103, some of the heating means (1) through the first branch pipe (110) 106 is passed through the heating means 106 and then flows into the condenser 103 through the second branch pipe 111.

After the refrigerant is condensed into a liquid in the condenser 103 is a liquid at room temperature and high pressure. In this process, heat generated by the phase change is generated to heat the room.

Thereafter, the refrigerant is expanded while passing through the expansion valve 105 to be in a state of low temperature and low pressure. At this time, as the phase change occurs, the refrigerant becomes a mixture of steam and liquid or a vapor state, and the temperature drops rapidly.

Thereafter, the refrigerant exiting the expansion valve 105 is heated while passing through the heating means 106 to be at a low temperature at room temperature, and enters the compressor 102 in a state where liquid and vapor are mixed. Here, the heating of the refrigerant exiting the expansion valve 105 is performed while exchanging heat in the heating means 106 with the high temperature refrigerant branched from the compressor 102 through the first branch pipe 110. As a result, the refrigerant, which has been low temperature immediately after exiting the expansion valve 105, is heated to a temperature of room temperature.

The compressor 102 receives the refrigerant that has become the optimum temperature by the main heater 107 and compresses it back into steam of high temperature and high pressure while smoothly compressing the refrigerant.

On the other hand, the refrigerant is branched from the compressor 102 and the heat exchanger with the low temperature refrigerant while passing through the heating means 106, the refrigerant temperature is lowered to room temperature while passing through the second branch pipe 111 to the main heater 107 Is heated and flows back into the condenser 103 at a high temperature.

As described above, the heat pump type heating apparatus of the present invention may allow the compressor 102 to smoothly operate the refrigerant introduced into the compressor 102 by the heating means 106 installed between the expansion valve 105 and the compressor 102. Heating to the optimal temperature. This allows the compressor 102 to operate smoothly while heating the room with only a heating cycle.

Subsequently, a second embodiment of the present invention will be described.

Second Embodiment

9 is a configuration diagram for explaining the configuration according to the second embodiment of the present invention.

As shown, the second embodiment of the present invention includes a casing 201, a compressor 202, a condenser 203, an expansion valve 205, and a main heater 207 as main components.

In the second embodiment of the present invention, the main heater 207 is provided to heat the low-temperature low-pressure refrigerant from the expansion valve 205 and to bring it to normal-temperature low-pressure. As a result, a refrigerant having an appropriate temperature of about 15 [° C.] can be introduced into the compressor 202, so that the compressor 202 can exhibit sufficient performance and the heating cycle is smoothly performed. Hereinafter, the configuration of the present invention will be described in more detail based on the technical gist of the present invention.

First, the casing 201 can be made to be a small and simple portable interior space. This is because parts, such as the evaporator, which has been cooled unlike the conventional art, and the discharge fan accompanying the evaporator, have been completely removed. A blower 211 is installed in the casing 201, and the blower 211 sucks indoor air to exchange heat with the condenser 203, and then blows it back into the room to provide warmth for indoor heating. Done.

The compressor 202 is generally installed stably in the bottom of the casing 201 in relation to a considerable load, and plays an important role of compressing and circulating the refrigerant in a high temperature and high pressure vapor state. Since the compressor 202 according to the present invention maintains the proper temperature by the main heat 207 to increase the temperature of the refrigerant, the original function can be sufficiently exhibited. As a result, the heating cycle is smoothly performed, and the room can be sufficiently heated without having a separate electric heater.

The condenser 203 is installed in connection with the compressor 202, and serves to generate heat while condensing the refrigerant in the vapor state sent from the compressor 202 into a liquid state at room temperature and high pressure.

The expansion valve 205 is connected between the condenser 203 and the compressor 202 and serves to expand and send the refrigerant sent from the condenser 203 to the compressor 202. In this case, the refrigerant is expanded by the expansion valve 205 and experiences a temperature decrease to some extent. However, since the refrigerant enters the compressor 202 through the main heater 207, the refrigerant 202 maintains an appropriate temperature at which the compressor 202 can operate smoothly.

The main heater 207 is installed between the expansion valve 205 and the compressor 202 to heat the refrigerant entering the compressor 202. The purpose of installing the main heater 207 is to allow the refrigerant to enter the compressor 202 while maintaining a normal temperature of approximately 15 [° C.]. As a result, the compressor 202 can fully ensure performance while ensuring smooth operation of the entire heating cycle.

Since the main heater 207 is substantially the same as the configuration of the main heater 107 according to the first embodiment, detailed description of the configuration is omitted.

Meanwhile, temperature sensors 208A and 208B and a controller 209 are further installed to maximize the action of the main heater 207. The temperature sensors 208A and 208B are installed between the expansion valve 205 and the main heater 207, and between the main heater 207 and the compressor 202, respectively, immediately after passing through the expansion valve 205. The refrigerant temperature and the refrigerant temperature immediately after being heated by the main heater 207 are measured. The controller 209 controls the main heater 207 in accordance with the value measured by the temperature sensors 208A, 208B to adjust the degree of heating the refrigerant. For example, the controller 209 adjusts the main heater 207 to lower the degree of heating when the refrigerant temperature immediately after passing through the expansion valve 205 is higher than an appropriate value, and the main heater 207 operates. Don't let that happen. On the other hand, when the refrigerant temperature immediately after passing through the expansion valve 205 is lower than the appropriate value, the heating degree is increased by adjusting the main heater 207. In addition, the temperature sensor 208B installed after the main heater 207 measures the temperature of the refrigerant entering the compressor and informs the controller 209. As a result, the controller 209 may determine how much the main heater 207 heats the refrigerant to adjust the heating degree of the main heater 207.

In addition, the main heater 207 is further provided with a bimetal (not shown) to block the abnormal high temperature of the main heater 207.

Hereinafter, the operation of the second embodiment of the present invention will be described in detail with reference to FIG. 10 and other accompanying drawings. 10 is an operation diagram for explaining a state change of the heating cycle according to the second embodiment of the present invention.

As shown, the refrigerant compressed in the compressor during operation of the present invention is a high temperature, high pressure steam between the compressor 202 and the condenser 203.

After the refrigerant is condensed into a liquid in the condenser 203 is a liquid at room temperature and high pressure. In this process, heat generated by the phase change is generated to heat the room.

Thereafter, the refrigerant is expanded while passing through the expansion valve 205 to be in a state of low temperature and low pressure. At this time, as the phase change occurs, the refrigerant becomes a mixture of steam and liquid or a vapor state, and the temperature drops rapidly.

Thereafter, the refrigerant exiting the expansion valve 205 is heated by the main heater 207 to a low temperature at room temperature, and enters the compressor 202 in a state where liquid and vapor are mixed.

The compressor 202 receives the refrigerant at the optimum temperature by the main heater 207 and compresses it into steam of high temperature and high pressure while smoothly compressing the refrigerant.

As described above, the heat pump type heating apparatus of the present invention may allow the compressor 202 to smoothly operate the refrigerant flowing into the compressor 202 by the main heater 207 installed between the expansion valve 205 and the compressor 202. Heating to the optimum temperature. This allows the compressor 202 to operate smoothly while heating the room using only a heating cycle.

11 is a configuration diagram for explaining the configuration of the modified second embodiment according to the present invention.

As shown, the second modified embodiment of the present invention further comprises a bypass pipe 210 for branching some refrigerant from the compressor 202 and sent to the condenser 203 to the main heater 205. do.

When the bypass pipe 210 is further installed, some of the refrigerant having a high temperature immediately after exiting the compressor 202 is sent to the condenser 203 to directly enter the compressor 202 instead of contributing to indoor heating. Is sent. As a result, the temperature of the entire refrigerant entering the compressor 202 can be adjusted to room temperature more easily.

Subsequently, a third embodiment according to the present invention will be described.

Third Embodiment

The third embodiment of the present invention achieves a high level of heating by improving the performance of the compressor and has a simple configuration in which unnecessary evaporators are removed. In addition, the refrigerant passing through the expansion valve is maintained at a room temperature to expand the expansion valve. It is characterized by preventing the cooling of the surrounding air due to the action of.

Hereinafter, the configuration according to the third embodiment of the present invention will be described in detail.

12 is a configuration diagram for explaining the configuration according to the third embodiment of the present invention.

As shown, the third embodiment of the present invention includes a casing 301, a compressor 302, a condenser 303, an expansion valve 305, and a main heater 307A as main components.

 In the third embodiment of the present invention, the main heater 307A is provided to heat the refrigerant having a normal temperature and high pressure from the condenser 303 so as to be in a state of high temperature and high pressure. As a result of this, it is important to suppress the excessive temperature drop due to the expansion of the refrigerant in the expansion valve 305 so that the refrigerant passing through the expansion valve 305 maintains the normal temperature and low pressure.

As a result, the air around the expansion valve is prevented from being excessively cooled to increase the heating performance, and the circulation of the refrigerant is prevented from being disturbed while the frost is caught. In addition, the refrigerant having an appropriate temperature of about 15 [° C.] can be introduced into the compressor 302, so that the compressor 302 can exhibit sufficient performance, and the heating cycle is smoothly performed. Hereinafter, the configuration according to the third embodiment of the present invention will be described in detail with reference to the technical main points.

First, the casing 301 is a portable type having a single inner space and can be made small and simple. This is because, unlike the related art, an evaporator which has been cooled, and ancillary devices such as a discharge fan accompanying the evaporator, have been removed. In addition, since the expansion valve 305 does not excessively cool the surrounding air, it is not necessary to provide an isolated zone for effective heating. A blower 311 is installed in the casing 301, and the blower 311 sucks indoor air to exchange heat with the evaporator 303, and then blows it back into the room to provide warmth for indoor heating. Done.

The compressor 302 is usually installed stably on the bottom surface of the casing 301 in relation to a significant load, and plays an important role of compressing and circulating the refrigerant in a high temperature and high pressure vapor state. Since the compressor 302 according to the present invention maintains the room temperature of the refrigerant after passing through the expansion valve 307B by the main heater 307A, which increases the temperature of the refrigerant, the original function can be sufficiently exhibited.

The condenser 303 is connected to the compressor 302 as in the second embodiment, and serves to generate heat by condensing the refrigerant in the vapor state sent from the compressor 302 into the liquid state at room temperature and high pressure. do.

The expansion valve 305 is connected to the condenser 303 and the compressor 302, and serves to expand and send the refrigerant sent from the condenser 303 to the compressor 302. At this time, the refrigerant is expanded by the expansion valve 305 to experience a temperature decrease to some extent. However, since the refrigerant has already been changed from the state of high temperature and high pressure to the state of high temperature and high pressure through the main heater 307A, the refrigerant 302 maintains at least a proper temperature at which the compressor 302 operates even though it passes through the expansion valve 305. Done.

The main heater 307A is installed between the condenser 303 and the expansion valve 305 to heat the refrigerant entering the expansion valve 305. The purpose of installing the main heater 307A is to maintain a normal temperature of about 15 [° C.] of the refrigerant passing through the expansion valve 305. Then, due to the expansion and phase change of the refrigerant by the expansion valve 305 it is inevitable to lower the ambient temperature to some extent, but it is possible to prevent excessive temperature decrease. Therefore, while maintaining the temperature of the refrigerant itself at room temperature, it is possible to prevent the phenomenon that the ambient temperature drops below zero, such as frost around the expansion valve. As a result, while the compressor 302 is fully performing, the smooth operation of the entire heating cycle is ensured and the deterioration of the heating performance due to the cooling of the ambient air can be prevented. Since the shape of the main heater 307A is substantially the same as that of the first embodiment, detailed description thereof will be omitted.

Meanwhile, the first auxiliary heater 307B, the temperature sensors 308A and 308B, and the controller 309 are further installed to maximize the action of the main heater 307A. The first auxiliary heater 307B is installed between the expansion valve 305 and the compressor 302 to selectively further heat the refrigerant passing through the expansion valve 305 as necessary. The temperature sensors 308A and 308B are installed between the expansion valve 305 and the first auxiliary heater 307B, and between the first auxiliary heater 307B and the compressor 302, respectively. The refrigerant temperature immediately after passing and the refrigerant temperature immediately after heating by the first auxiliary heater 307B are measured. The controller 309 controls the degree of heating the refrigerant by controlling the main heater 307A and the first auxiliary heater 307B according to the values measured by the temperature sensors 308A and 308B. For example, when the refrigerant temperature immediately after passing through the expansion valve 305 is higher than an appropriate value, the controller 309 adjusts the main heater 307A to lower the heating degree and the first auxiliary heater 307B. Does not work. On the other hand, if the refrigerant temperature immediately after passing through the expansion valve 305 is lower than the appropriate value, the heating degree is increased by adjusting the main heater 307A. In addition, in the case of the first auxiliary heater 307B and the temperature sensor 308B installed thereafter, the temperature control function of the main heater 307A is complemented to more precisely control the temperature of the refrigerant. This is because, in the case of the refrigerant heated in the main heater 307A, it is difficult to predict and adjust the final temperature because the expansion valve 305 undergoes a phase change.

In addition, a bimetal (not shown) is further installed on the main heater 307A to block abnormal high temperatures of the main heater 307A.

Hereinafter, the operation of the present invention will be described in detail with reference to FIG. 13 and other accompanying drawings. 13 is an operation diagram for explaining a state change of the heating cycle according to the third embodiment of the present invention.

As shown, the refrigerant compressed in the compressor 302 in the operation of the present invention is a high temperature, high pressure steam between the compressor 302 and the condenser 303.

After that, the refrigerant is condensed into liquid in the condenser 303 and becomes a liquid at room temperature and high pressure. In this process, heat generated by the phase change is generated to heat the room.

Thereafter, the refrigerant is heated to a liquid state of high temperature and high pressure while being heated by the main heater 307A in a liquid state of room temperature and high pressure.

Thereafter, the refrigerant is expanded while passing through the expansion valve 305 to a low pressure state. At this point, the phase change occurs to some extent, and the refrigerant becomes a mixture of vapor and liquid, and the temperature decreases somewhat, but does not drop to below zero. This is because the refrigerant is previously heated by the main heater 307A and passed through the expansion valve 305 in a state of high temperature and high pressure. As a result, the action of the expansion valve 305 is suppressed so that the surrounding temperature does not drop rapidly. In addition, the refrigerant passing through the expansion valve 305 can be maintained at room temperature without being overcooled, thereby creating a condition for the compressor 302 to operate smoothly.

Thereafter, the refrigerant exiting the expansion valve 305 is introduced into the compressor 302 in a state where the room temperature low pressure, steam and liquid are mixed as described above, and is compressed into high temperature and high pressure steam.

14 is a configuration diagram for explaining a third modified embodiment of the present invention.

As shown, in the modified third embodiment of the present invention, the bypass pipe 313 connected between the expansion valve 305 and the compressor 302 after branching between the compressor 302 and the condenser 303. This is installed more. The bypass pipe 313 serves to send a part of the high temperature and high pressure refrigerant from the compressor 302 to the compressor 302. In addition, the bypass pipe 3013 is further provided with a second auxiliary heater (307C) for selectively heating the branched high-temperature, high-pressure refrigerant. However, the first auxiliary heater 307B used in the third embodiment before deformation is removed.

In addition, on the bypass pipe 313, a flow control valve 315 is installed at a position immediately after branching, so that the amount of refrigerant branched can be adjusted and shut off.

In this modified third embodiment, a portion of the high temperature and high pressure refrigerant from the compressor 302 is used to raise the temperature of the refrigerant passing through the expansion valve 305 instead of entering the condenser 303 for heating. By doing so, it contributes to the smooth operation of the entire heating cycle and ultimately to the heating performance.

Fourth Embodiment

The fourth embodiment of the present invention is characterized in that it is configured to facilitate the implementation of the heating apparatus of the present invention by utilizing a conventional air conditioner that combines conventional cooling and heating operation.

Hereinafter, the configuration according to the fourth embodiment of the present invention will be described in detail.

15 is a configuration diagram for explaining the configuration according to the fourth embodiment of the present invention.

As shown, the fourth embodiment of the present invention is the casing 401, the compressor 402, the first heat exchanger 403, the second heat exchanger 405, the expansion valve 404, which operates only when heating, The third heat exchanger 406, the temperature sensor 407, and the controller 408 are included as main components.

Referring to FIG. 15, in the fourth embodiment of the present invention, the second heat exchanger 405 that operates only when heating is a technical part, and the compressor 402, the third heat exchanger 406, The refrigerant is circulated in the order of the second heat exchanger 405, the expansion valve 404, and the first heat exchanger 403, and when the heating is performed, the flow direction of the refrigerant is changed by the four-way valve 417. The refrigerant is circulated in the compressor 402, the first heat exchanger 403, the expansion valve 404, the second heat exchanger 405, and the third heat exchanger 406. In the present invention, most of the components except for the second heat exchanger 405, the temperature sensor 407, and the controller 408 may be used as they are used in known air conditioners. Therefore, when cooling the second heat exchanger 405 is not used, it can be said that the action and effect are much the same as compared with the conventional air conditioner.

However, the present invention is a low-temperature low-pressure liquid from the expansion valve 404 by heating and vaporizing the refrigerant sequentially through the secondary by the second heat exchanger 405 and the third heat exchanger 406 during heating. The refrigerant is brought into an optimal temperature (temperature of about 15 [deg.] C.) state (steam state) required by the compressor 402, thereby improving the heating effect. As a result, the performance of the compressor 402 can be sufficiently increased, thereby improving the performance of the entire heating cycle and ultimately improving the heating performance. Hereinafter, a fourth embodiment of the present invention will be described in more detail with reference to the technical main points.

First, the casing 401 has a machine chamber 411 having an inlet and an exhaust port at a lower portion thereof, and a blower chamber 413 isolated from the machine chamber 411 at an upper portion thereof.

Here, the compressor 402, the second heat exchanger 405 and the third heat exchanger 406 are installed in the machine room 411, and the first heat exchanger 403 and the expansion are provided in the blower chamber 413. The valve 404 and the four-way valve 417 which switch the direction of the refrigerant are provided. In addition, a blower 415 is installed in the blower chamber 413, and the blower 415 provides cold or warm air for indoor cooling or heating.

The compressor 402 is usually installed stably in the bottom of the machine room 411 in relation to a significant load, and plays an important role in circulating the refrigerant while compressing the refrigerant at a high temperature and a high pressure.

The role of the compressor 402 should be performed at the same time during the cooling operation or the heating operation, but during the heating operation performed in the winter, the temperature of the refrigerant flowing into the compressor 402 becomes much lower than the proper temperature. You will not be able to function fully. Even when the temperature of the coolant drops to below zero, the compressor 402 is often overcooled, and thus, almost no function is achieved.

However, the compressor 402 according to the fourth embodiment of the present invention can fully perform its original function with the help of the second heat exchanger 405. As a result, the heating cycle is smoothly performed, and the room can be sufficiently heated without having a large electric heater on its own.

The expansion valve 404 serves to pressure drop the high pressure liquid refrigerant to a low pressure liquid refrigerant.

The first heat exchanger 403 serves as an evaporator that receives and vaporizes a low-pressure liquid refrigerant that is dropped in the expansion valve 404 during cooling. In addition, during heating, the steam refrigerant compressed by the compressor 402 is received and serves as a condenser that generates heat while condensing it into a high-pressure liquid refrigerant.

The second heat exchanger 405 operates only during heating to heat the low pressure liquid refrigerant from the expansion valve 404 to vaporize a portion thereof. The purpose of the installation of the second heat exchanger is to maintain a normal temperature of about 15 [° C.] around the state of the refrigerant entering the compressor 402. This can prevent excessive temperature drop due to the third heat exchanger 406. Therefore, while maintaining the temperature of the refrigerant itself at room temperature, it is possible to prevent the phenomenon that the ambient temperature drops rapidly below zero, such as frost around the third heat exchanger (406). As a result, while the compressor 402 fully exhibits its performance, smooth operation of the entire heating cycle is ensured and the deterioration of the heating performance due to the cooling of the ambient air can be prevented.

The second heat exchanger 405 has a configuration substantially similar to that of the main heater 107 (see FIGS. 4 to 7) of the first embodiment, and detailed description thereof will be omitted.

Meanwhile, the temperature sensor 407 and the controller 408 are further installed to maximize the action of the second heat exchanger 405. The temperature sensor 407 is installed on the refrigerant inlet side of the compressor 402 to measure the temperature of the refrigerant entering the compressor 402 and notify the controller 408. The controller 408 controls the second heat exchanger 405 according to the value measured by the temperature sensor 407 to adjust the intensity of heating the refrigerant. For example, the controller 409 lowers the degree of heating by adjusting the second heat exchanger 405 when the refrigerant temperature flowing into the compressor 402 is higher than an appropriate value. On the other hand, when the temperature of the refrigerant flowing into the compressor 402 is lower than an appropriate value, the degree of heating is increased by adjusting the second heat exchanger 405.

In addition, the second heat exchanger 405 is further provided with a bimetal (not shown) to block the abnormal high temperature of the second heat exchanger 405. In the case of the bimetal, a known technique may be applied as it is.

In addition, the third heat exchanger 406 serves as a condenser that receives the vapor refrigerant compressed by the compressor 402 and converts the liquid refrigerant into a high-pressure liquid refrigerant during cooling, and partially in the second heat exchanger 405 when heating. It serves as an evaporator to accept and vaporize the refrigerant in the vaporized state. The third heat exchanger 406 further heats the refrigerant, which has been heated in the second heat exchanger 405 and is partially steamed, to make almost all of the refrigerant into a vapor state. However, in this case, since the phase change of the refrigerant has already occurred to some extent in the second heat exchanger 405, a sudden temperature change can be avoided, so that the frost is thickened on the surface of the third heat exchanger 406 or the ambient temperature is rapidly lowered. The phenomenon can be prevented.

16 is an operation diagram for explaining a state change of the refrigerant by the heating cycle of the present invention.

As shown, the refrigerant compressed in the compressor 402 in the operation of the present invention is a high temperature and high pressure steam between the compressor 402 and the first heat exchanger 403.

Since the refrigerant is condensed into liquid in the first heat exchanger 403, the refrigerant is in a liquid state at room temperature and high pressure. In this process, heat generated by the phase change is generated to heat the room.

Thereafter, the refrigerant is expanded while passing through the expansion valve 404 in a liquid state at room temperature and high pressure to become a liquid state at low temperature and low pressure.

Thereafter, the refrigerant is heated while passing through the second heat exchanger 405 to a state of low temperature at room temperature, and part of the refrigerant is vaporized into a vapor state.

Thereafter, the refrigerant is further heated while passing through the third heat exchanger 406 to a state of low temperature at room temperature, and almost entirely vaporized.

Thereafter, the refrigerant exiting the third heat exchanger 406 enters the compressor 402 at a temperature of room temperature.

17 is a configuration diagram illustrating a modified fourth embodiment of the present invention.

As shown in the fourth modified embodiment of the present invention, the bypass pipe 409 and the three-way passing the refrigerant from the second heat exchanger 405 to the third heat exchanger 406 to the compressor 402. The valve 410 may be further installed. According to this modified configuration, the direction of the refrigerant passing through the second heat exchanger 405 during heating can be directly sent to the compressor 402 without passing through the third heat exchanger 406.

Therefore, the effect of completely removing the third heat exchanger 406 which can be said to be almost unnecessary at the time of heating can be expected only by simply installing the bypass pipe 409.

18 is a configuration diagram for explaining a fourth embodiment modified to another embodiment of the present invention.

As shown, another embodiment of the fourth embodiment may simply be configured for heating purposes only, including the compressor 402, the first heat exchanger 403, the expansion valve 404, and the second heat exchanger 405. have.

The compressor 402 compresses the refrigerant and sends it out in a high temperature, high pressure steam state.

The first heat exchanger 403 receives the vapor refrigerant compressed by the compressor 402 and generates heat while condensing it into a high pressure liquid refrigerant.

The expansion valve 404 receives the high pressure liquid refrigerant condensed in the first heat exchanger 403 and receives the low pressure liquid refrigerant to reduce the pressure.

The second heat exchanger 405 heats and vaporizes the low pressure liquid refrigerant from the expansion valve 404.

This modified fourth embodiment has a configuration in which the third heat exchanger 406, which serves as a condenser for cooling and an evaporator for heating, is completely removed as compared to before the modification. As a result, the third heat exchanger 406 as well as peripheral devices (not shown), such as the blower accompanying it, are removed to allow a simpler configuration. In addition, the outdoor unit is not required at all, and only a simple casing 401 having only one internal space is required.

[Example 5]

The fifth embodiment of the present invention is characterized in that it is configured to facilitate the implementation of the heating apparatus of the present invention by utilizing the air-conditioner which combines the conventional cooling and heating operation like the foregoing fourth embodiment.

Furthermore, it is configured to further improve the performance of the second heat exchanger, which serves as a condenser during heating, to realize a high level of heating.

Hereinafter, the configuration according to the fourth embodiment of the present invention will be described in detail.

19 is a configuration diagram for explaining the configuration of the present invention, Figure 20 is a reference diagram for explaining the operation during heating of the present invention, Figure 21 is a reference diagram for explaining the operation during cooling of the present invention.

As shown, the present invention includes a casing 501, a compressor 502, a first heat exchanger 503, a cooling expansion valve 504, a second heat exchanger 505, including a heating expansion valve 506. And a heater 508 for heating only.

 The present invention comprises a technical main part to increase the temperature and the pressure drop of the refrigerant flowing into the second heat exchanger 505 by heating the expansion valve 506 for heating only. The present invention can thereby improve the performance of the second heat exchanger 505 acting as a condenser during heating, the performance of the first heat exchanger 503 serving as a compressor, and smooth operation of the entire heating cycle. Hereinafter, the configuration of the present invention will be described based on the technical main points.

First, the casing 501 has a mechanical chamber 511 having an inlet and an exhaust port at a lower portion thereof, and a blower chamber 513 isolated from the mechanical chamber 511 is formed at an upper portion thereof.

Here, the compressor 502 and the first heat exchanger 503 are installed in the machine room 511, and the second heat exchanger 505, the expansion valve 504 for cooling, and heating are installed in the blower chamber 513. A dedicated expansion valve 506 and a heating dedicated heater 508 are installed. Here, the cooling expansion valve 504 may be installed in the machine room 511. In addition, a blower 515 is installed in the blower chamber 513, and the blower 515 sucks indoor air into the blower chamber 513 to exchange heat with the second heat exchanger 505, and then, Blowing back to the room provides cold or warm air for cooling or heating the room.

The compressor 502 is usually installed stably on the bottom surface of the machine room 511 because of its considerable load, and plays an important role in circulating the refrigerant while compressing it at a high temperature and a high pressure.

The role of the compressor 502 should be the same in the cooling operation or the heating operation, but in the heating operation performed in the winter, the temperature of the refrigerant flowing into the compressor 502 becomes much lower than an appropriate temperature. You will not be able to function fully. In many cases, even when the temperature of the refrigerant dropped to below zero, the compressor 502 was overcooled, thereby hardly exhibiting its proper function.

However, the compressor 502 according to the present invention can fully perform its original function with the help of the expansion-only expansion valve 506 and the heater-only heater 508 for raising the temperature of the refrigerant from an early point in time. As a result, the heating cycle is smoothly achieved, and the room can be sufficiently heated without a separate large electric heater.

The first heat exchanger 503 is installed in the machine room 511 and serves as a condenser to convert the vapor refrigerant compressed by the compressor 502 into a high pressure liquid refrigerant during cooling.

In addition, the first heat exchanger 503 is converted to act as an evaporator during heating to vaporize the liquid refrigerant flowing from the expansion expansion valve 504 for cooling. At this time, the performance of the first heat exchanger 503 is considerably lowered, which is because the refrigerant already sufficiently depressurized by the expansion-only expansion valve 506 flows into the expansion-only valve 504 for cooling. This is because the pressure drop does not occur at 504.

Here, the role of the condenser refers to the role of a conventional condenser that converts the vapor refrigerant compressed in the compressor 502 into a high-pressure liquid refrigerant, and the role of the evaporator refers to the liquid refrigerant flowing from the expansion valve 504 for cooling only. It refers to the role of a conventional evaporator to vaporize. Of course, these components include, without limitation, a range of functions and roles which have been changed to some extent with respect to functions and roles generally known in their functions and roles.

The expansion expansion valve 504 for cooling is located in the middle connecting the first heat exchanger 503 and the second heat exchanger 505, and is usually installed at an appropriate place in the blower chamber 5013. Thus, the cooling expansion valve 504 receives a high pressure liquid refrigerant from the first heat exchanger 503 or the second heat exchanger 505 serving as a condenser and performs a pressure drop to a low pressure liquid refrigerant. Done. However, the expansion expansion valve 504 for cooling according to the present invention can not perform any further pressure drop action due to the introduction of the refrigerant having already sufficiently reduced pressure during heating due to the installation of the expansion expansion valve 506 for heating.

The second heat exchanger 505 is installed in the blower chamber 5013, and serves as an evaporator to vaporize the low pressure liquid refrigerant pressure-reduced by the expansion expansion valve 504 for cooling. In addition, the second heat exchanger 505 is switched to act as a condenser when heating. It should be noted that the second heat exchanger 505 does not directly receive the high temperature and high pressure refrigerant compressed by the compressor 502, but the heating expansion valve 506 and the heating exclusive heater 508 disposed between the compressor 502. It is inverted to low pressure by) and receives a refrigerant heated to a higher temperature.

The heating expansion valve 506 is installed between the compressor 502 and the second heat exchanger 505 to increase the temperature and decrease the pressure of the refrigerant flowing into the second heat exchanger 505 during heating. In this process, the high-temperature and high-pressure refrigerant flowing out of the compressor 502 further increases in temperature and pressure until passing through the capillary tube inside the expansion valve 506 for heating, and then expands in an instant while exiting the capillary tube. Becomes As a result, the high temperature and high pressure refrigerant from the compressor 502 passes through the expansion valve 506 for heating purposes, and the temperature increases and the pressure decreases. On the other hand, the length of the heating expansion valve 506 is formed longer than the length of the cooling expansion valve 504. This is to prevent the pressure drop of the refrigerant from the expansion expansion valve 504 for cooling only by sufficiently lowering the pressure of the refrigerant flowing into the cooling expansion expansion valve 504 in advance.

Considering the effect of the heating expansion valve 506 having such a configuration as follows. That is, the second heat exchanger 505 may generate more heat because the second heat exchanger 505 receives a refrigerant of a higher temperature. Since the instantaneous pressure drop of the refrigerant does not occur in the expansion expansion valve 504 for cooling, the compressor 502 is deteriorated due to deterioration in the performance of the first heat exchanger 503 and a decrease in the temperature drop width, and a phenomenon in which the pipe is defrosted. The inability to function properly disappears. The compressor 502 is already heated to a high temperature by the expansion-only expansion valve 506 and the heating-only heater 508 before passing through the second heat exchanger 505 and has a higher temperature due to the aftermath. Since the medium is introduced, the compression performance is further improved. Therefore, the present invention generates more heat during heating and smoothly operates the entire heating cycle.

In the present invention, the bypass pipe 507 is installed to bypass the heating expansion valve 506 when cooling, and an electromagnetic valve 571 is provided to selectively open and close the bypass pipe 507.

The heating-only heater 508 is installed between the second heat exchanger 505 and the expansion-only expansion valve 506 for heating. As a result, the high temperature refrigerant passing through the heating expansion valve 506 may be further heated to flow into the second heat exchanger 505. When the heating-only heater 508 is provided, more heat is generated in the second heat exchanger 505 as the above-mentioned heating-only expansion valve 506 works, and the compression performance of the compressor 502 is improved. Overall higher levels of heating performance can be achieved. Here, the heating-only heater 508 adopts an indirect heating method of heating a pipe through which the refrigerant flows, rather than directly heating the refrigerant (usually freon).

Comparing FIG. 20 with FIG. 21, the difference between the heating operation and the cooling operation of the present invention can be clearly seen. That is, during heating, a pressure drop and heating of the refrigerant are performed between the compressor 502 and the second heat exchanger 505, and an expansion valve for cooling is used between the second heat exchanger 505 and the first heat exchanger 503. The pressure drop by 504 is not made. On the other hand, during cooling, the pressure drop and the heating of the refrigerant are not made at all between the compressor 502 and the second heat exchanger 505, and only for cooling between the second heat exchanger 505 and the first heat exchanger 503. Only the pressure drop by the expansion valve 504 is made.

The operation according to the fourth embodiment of the present invention will be described below.

First, during cooling, the first heat exchanger 503 and the second heat exchanger 505 serve as condensers and evaporators, respectively, and the refrigerant is a compressor 502, a first heat exchanger 503, and an expansion valve for cooling. 504, the second heat exchanger 505, the heating-only heater 508, the bypass pipe 507, and the compressor 502 are sequentially cycled to undergo a continuous cooling cycle of compression, condensation, expansion, and evaporation. . At this time, the heating expansion valve 506 or the heating dedicated heater 508 does not operate.

On the other hand, during heating, the first heat exchanger 503 and the second heat exchanger 505 serve as an evaporator and a condenser, respectively, and the heating exclusive expansion valve 506 and the heating exclusive heater 508 operate or It will work. At this time, the refrigerant in which the flow direction is switched by the four-way valve 517 is a compressor 502, an expansion valve for heating 507, a heater for heating 508, a second heat exchanger 505, expansion valve 504 for cooling Compression (compressor) -expansion (heating expansion valve) -heating (heater for heating) -condensation (second heat exchanger) -expansion (cold-heating) in reverse order of first heat exchanger 503 and compressor 502 Anti-expansion valve) -evaporation (first heat exchanger) undergoes a continuous heating cycle.

The operation of the expansion-only expansion valve 506 and the heater-only heater 508 centering on the change of the state of the refrigerant in the heating cycle process is as follows.

That is, the high temperature and high pressure refrigerant flowing out of the compressor 502 is stagnant until it exits the capillary of the heating expansion valve 506, and the pressure and temperature gradually increase.

Subsequently, as the refrigerant, which has risen to a considerable level in pressure and temperature, exits the capillary of the heating-only expansion valve 506, the pressure drops rapidly and becomes a low pressure state. At this time, the temperature still remains high.

Thereafter, the refrigerant in the high temperature low pressure state is heated while passing through the heating exclusive heater 508 to have a higher temperature.

As such, the refrigerant having a significantly increased temperature and pressure through the expansion-only expansion valve 506 and the heater-only heater 508 is condensed in the second heat exchanger 505 serving as a condenser to form a low temperature low pressure refrigerant in a liquid state. At this time, the refrigerant emits a greater amount of heat as it is heated while passing through the heating expansion valve 506 and the heating exclusive heater 508.

Thereafter, the refrigerant changed into a liquid low temperature and low pressure passes through the expansion expansion valve 504 for cooling, but the pressure drop does not occur because the pressure of the cooling medium is already considerably lowered by the expansion expansion valve 506 for heating. Therefore, the pressure drops sharply and the frost on the pipe no longer occurs.

Thereafter, the refrigerant flowing into the first heat exchanger 503 serving as the evaporator is reduced in evaporation performance due to the aftermath of the performance reduction of the air-conditioning expansion valve 504, so that heat is absorbed only to the surroundings.

Thereafter, the refrigerant flowing into the compressor 502 ensures a higher ambient temperature due to the deterioration of the performance of the first heat tester 503, including the influence of the heating expansion valve 506 and the heating exclusive heater 508. And a refrigerant having a higher temperature and pressure can be received. Therefore, the compressor 502 can perform the compression process of the refrigerant while exhibiting the best performance, thereby smoothing the heating cycle.

As described above, the air-conditioning apparatus of the present invention lowers the pressure of the refrigerant in advance and heats it to a high temperature before the refrigerant is introduced into the second heat exchanger 505 serving as a condenser during heating. 505) and the compressor 502 can be improved and the heating performance can be dramatically improved by enabling smooth operation of the entire heating cycle.

The preferred embodiment of the present invention has been described above. The present invention may use various changes, modifications, and equivalents. It is clear that the present invention can be applied in the same manner by appropriately modifying the above embodiments. Accordingly, the above description does not limit the scope of the invention as defined by the limitations of the following claims.

As described above, the bottom-pump heating device with improved heating performance according to the present invention, the compressor is able to fully exhibit the performance, while achieving a high level of heating performance while achieving a smooth heating cycle can reduce the electricity consumption. have.

In addition, the present invention can maintain the room temperature of the refrigerant passing through the expansion valve to prevent the cooling of the ambient air due to the action of the expansion valve can improve the heating performance.

In addition, the present invention has a simple configuration in that the devices such as the evaporator and the discharge fan accompanying the evaporator is removed, thereby reducing the cost.

In addition, the present invention is very useful for utilizing as a portable type only indoors without an outdoor unit.

In addition, the present invention can avoid the phenomenon that some of the components thicken the frost or sharply lower the ambient temperature.

Claims (22)

A compressor for compressing the refrigerant and discharging the refrigerant into a high temperature and high pressure vapor state; A condenser connected to the compressor and configured to generate heat by converting a refrigerant in a vapor state sent from the compressor into a liquid state at room temperature and high pressure; An expansion valve connected to the condenser and the compressor and expanding the refrigerant sent from the condenser to the compressor; And a heating means installed between the expansion valve and the compressor to heat the low temperature refrigerant flowing into the compressor from the expansion valve. The method of claim 1, The heating means is a heat pump type heating device having a heating performance, characterized in that the heat exchange with the low-temperature refrigerant from the expansion valve by branching some of the high-temperature refrigerant from the compressor. The method of claim 2, The heating means is a plate-type heat exchanger in which a plurality of thin metal plates formed with a plurality of thin metal plates formed with flow paths through which a high temperature coolant from the compressor and a low temperature coolant from the expansion valve flow, are heated along the flow paths. Heat pump type heating device with improved heating performance, characterized in that. The method of claim 3, wherein A first branch pipe for branching some of the refrigerant from the compressor and sent to the condenser to the heating means, and a second branch pipe for discharging the refrigerant heat-exchanged with the low-temperature refrigerant from the heating means to the condenser, Heat pump type heating device to increase the heating performance, characterized in that the second branch pipe is further provided with a main heater for heating the refrigerant sent to the condenser. A compressor for compressing the refrigerant and discharging the refrigerant into a high temperature and high pressure vapor state; A condenser connected to the compressor and configured to generate heat by converting a refrigerant in a vapor state sent from the compressor into a liquid state at room temperature and high pressure; An expansion valve connected to the condenser and the compressor and expanding the refrigerant sent from the condenser to the compressor; The heat pump type is provided between the expansion valve and the compressor, comprising a main heater for heating the refrigerant entering the compressor to the state of the refrigerant passing through the expansion valve to room temperature Heating. The method of claim 5, A temperature sensor for measuring the temperature of the refrigerant is installed between the main heater and the compressor, and further comprising a controller for optimally maintaining the temperature of the refrigerant entering the compressor by controlling the main heater according to the value measured by the temperature sensor. Heat pump type heating device characterized in that the heating performance is improved. The method of claim 5, And a bypass pipe for branching a part of the refrigerant from the compressor to the main heater. A compressor for compressing the refrigerant and discharging the refrigerant into a high temperature and high pressure vapor state; A condenser connected to the compressor and configured to generate heat by converting a refrigerant in a vapor state sent from the compressor into a liquid state at room temperature and high pressure; An expansion valve connected to the condenser and the compressor and expanding the refrigerant sent from the condenser to the compressor; A heat pump provided between the condenser and the expansion valve and including a main heater for heating the refrigerant entering the expansion valve to allow the state of the refrigerant passing through the expansion valve to be at room temperature. Type heating system. The method of claim 8, A temperature sensor for measuring the temperature of the refrigerant is installed between the expansion valve and the compressor, the controller for controlling the main heater in accordance with the value measured by the temperature sensor to maintain the room temperature of the refrigerant passing through the expansion valve further Heat pump type heating device with a heating performance comprising a. The method of claim 9, And a first auxiliary heater installed between the expansion valve and the compressor to selectively heat the refrigerant by the controller, and a temperature sensor installed between the first auxiliary heater and the compressor. Increased heat pump type heating system. The method of claim 8, Branched between the compressor and the condenser and connected between the expansion valve and the compressor is a heat pump type heating device, characterized in that the bypass pipe is further installed to send a portion of the high-temperature high-pressure refrigerant from the compressor to the compressor . The method of claim 11, And a second auxiliary heater for selectively heating the branched high-temperature and high-pressure refrigerant in the bypass pipe. A compressor for compressing the refrigerant and discharging the refrigerant into a high temperature and high pressure vapor state; An expansion valve for dropping the high pressure liquid refrigerant into the low pressure liquid refrigerant; A first heat exchanger serving as a condenser that receives the vapor refrigerant compressed by the compressor and condenses it into a high pressure liquid refrigerant and generates heat; A second heat exchanger which is operated only during heating to vaporize a portion of the low pressure liquid refrigerant from the expansion valve; A heat pump type heating device having a heating performance including a third heat exchanger which serves as an evaporator for receiving and evaporating a refrigerant in a partially evaporated state in the second heat exchanger. A compressor for compressing the refrigerant and discharging the refrigerant into a high temperature and high pressure vapor state; A first heat exchanger which receives the vapor refrigerant compressed by the compressor and generates heat while condensing it into a high pressure liquid refrigerant; An expansion valve configured to receive a high pressure liquid refrigerant condensed in the first heat exchanger and receive a low pressure liquid refrigerant; And a second heat exchanger configured to heat and vaporize the low-pressure liquid refrigerant from the expansion valve. The method according to claim 13 or 14, On the refrigerant inlet side of the compressor is installed a temperature sensor for measuring the temperature of the refrigerant entering the compressor, and according to the value measured by the temperature sensor to control the second heat exchanger to maintain the temperature of the refrigerant entering the compressor at a set temperature Heat pump type heating device to increase the heating performance, characterized in that the controller is further installed. The method of claim 15, wherein the second heat exchanger, A heater body having an insertion hole and having a chamber in which refrigerant flows in and stays inside the wall; Heat pump type heating with improved heating performance, characterized in that it comprises a pair of heating bars having an electric coil therein to generate heat of resistance and is inserted into the insertion hole to indirectly heat the refrigerant introduced into the chamber. Device. The method of claim 13, And a bypass pipe which sends the refrigerant from the second heat exchanger to the compressor, the refrigerant being sent to the third heat exchanger. An expansion valve for cooling the pressure lowering the high pressure liquid refrigerant to the low pressure liquid refrigerant; A compressor for compressing the refrigerant; A first heat exchanger serving as an evaporator for vaporizing the low pressure liquid refrigerant depressurized in the cooling expansion expansion valve; A second heat exchanger serving as a condenser that generates heat by converting a vapor refrigerant into a liquid refrigerant; It is installed between the compressor and the second heat exchanger to penetrate the refrigerant flowed out of the compressor during heating, but before passing through the refrigerant to the high temperature and high pressure, and after passing through the pressure-only expansion valve for heating the pressure drop to a state of low temperature Heat pump type heating device with improved heating performance. The method of claim 18, The heating expansion valve is formed longer than the length of the expansion valve for cooling, heat pump type heating device to increase the heating performance, characterized in that to make the refrigerant before passing through the high temperature and high pressure than the expansion valve for cooling. The method of claim 19, And a main heater installed between the second heat exchanger and an expansion valve for heating and further heating a high temperature refrigerant from the heating expansion valve. The method according to any one of claims 4 to 12, 20, wherein the heater, A heater body having an insertion hole and having a chamber in which refrigerant flows in and stays inside the wall; Heat resistance heating device having a heating performance, characterized in that it comprises a heating bar having an electric coil therein to generate resistance heat, is inserted into the insertion hole for indirectly heating the refrigerant introduced into the chamber. The method of claim 21, Heat pump type heating device to increase the heating performance, characterized in that the bimetal is further installed to block the abnormal high temperature of the main heater.

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