KR20030028959A - Heat pump type air conditioner using a waste heat of compressor - Google Patents

Abstract

PURPOSE: A heat pump type air conditioner for heating and cooling is provided to prevent deterioration of performance. CONSTITUTION: An air conditioner comprises a compressor(32); a first air-conditioning case(20) having a first heat exchanger(22) cooling or heating part of indoor air introduced through a first air supply damper(24) and a second air supply damper(25) and outside air, and an air supply blower fan(26) supplying chilled or heated air into a room; a second air-conditioning case(10) having a second heat exchanger(11) liquefying or expanding refrigerant with heat exchange with part of indoor air introduced through a first exhaust damper(13) and a second exhaust damper(14) and the outside air, and an exhaust blower fan(12) discharging air having exchanged heat into the atmosphere; a compressor case(30) covering the compressor to prevent discharge of waste heat generated in the compressor to the outside; an introduction chamber(15) selectively supplying the second heat exchanger with waste heat introduced from the compressor case through a first introduction damper(15a) introducing the outside air to be supplied to the second heat exchanger, and a compressor waste heat recovery duct(51); and a third double heat exchanger(50) placed near the first exhaust damper.

Description

HEAT PUMP TYPE AIR CONDITIONER USING A WASTE HEAT OF COMPRESSOR}

The present invention relates to a waste heat recovery type air-conditioning combined air conditioner, and more specifically, to the performance of the system by supplying the waste heat generated from the compressor to the evaporator while maximizing the waste heat of the room ventilated indoors in cold winter with low outside temperature The present invention relates to a waste heat recovery type air-conditioning combined air conditioner capable of preventing degradation and improving heating efficiency, and recovering a part of condensate during summer to improve cooling performance according to the heat transfer of the condenser.

In general, indoor spaces require proper cooling and heating in response to external temperature changes, and should be periodically ventilated due to carbon dioxide or food smells emitted during the breathing of inhabitants. To this end, most modern buildings are equipped with air conditioning and heating facilities, and in order to save space and reduce equipment, the supply of air conditioners for both air conditioning and heating, which can perform summer cooling and winter heating in one system, is steadily increasing. have.

As an example of a conventional air-conditioning combined air conditioner, Korean Utility Model Publication No. 197795, registered July 14, 2000, discloses a combined air-conditioning and air-conditioning control rate of ventilation recovery. As shown in Figure 1, this is an integrated heat pump type air conditioner, the overall configuration is a compressor 64 for compressing the refrigerant on a summer basis in one case, and the compressed air to cool the liquid A condenser coil 71 made of a refrigerant, an evaporator coil 70 in which the refrigerant expanded by pressure drop while passing through the expansion valve heat exchanges with the surrounding air, and the air cooled by passing the evaporator coil 70 is pumped into the room. An air supply blower 65 for discharging, an exhaust blower 66 for discharging the heat-exchanged air to the outside while passing through the condenser coil 71, and an exhaust damper 67 for adjusting the amount of air supplied to the condenser coil 71; 62), the air supply dampers (69, 63) for adjusting the air supply amount supplied to the evaporator coil (70).

The operation of the conventional air-conditioning combined air conditioner configured as described above will be described by dividing the cooling mode and the heating mode.

First, in the summer cooling mode, when the opening degrees of the second damper 69 and the third damper 62 are 70%, and the opening degrees of the first damper 67 and the fourth damper 63 are set to 30%, Heat exchange is performed while 70% of cold indoor air and 30% of hot outdoor air for ventilation passes through the evaporator coil 70 and the cooled air is supplied to the room along the arrow direction 72 by the air supply blower 65. do.

Next, in the heating mode in winter, when the opening degrees of the second damper 69 and the third damper 62 are set to 70%, and the opening degrees of the first damper 67 and the fourth damper 63 are set to 30%, , 70% of hot indoor air and 30% of cold outdoor air for ventilation pass through the evaporator coil 70 and heat exchange is performed, and the warmed air is moved into the room along the arrow direction 72 by the air supply blower 65. Supplied.

In the air conditioner according to the prior art configured as described above, the compressor is built in the air conditioner in the cooling mode, so that the air pressure is exhausted toward the condenser coil 71 generated by the outside air temperature and the compressor during the hot summer season, thereby increasing the high pressure and acting the system There is a problem that affects both the cooling capacity and the increase of power consumption.

In addition, in the heating mode, when the outside temperature drops below zero, there is a problem in that the heating heat is insufficient due to the decrease of the heat of evaporation due to the reduction of the evaporation heat due to the cold air of the outside air. In addition, the evaporator coil, the air supply fan, the exhaust fan, etc. are integrated to provide a problem in securing the space size.

In order to solve such limitations on the installation space, Korean Patent Publication No. 2000-12499 published March 6, 2000 discloses a heating and cooling air conditioner of a detachable structure. This air conditioner can solve the above-mentioned space problem by arranging two air-conditioning cases side by side horizontally or vertically. However, when the outside air temperature drops to below zero during heating in cold winter, sufficient endothermic action in the evaporator is achieved. There is a lack of heating capacity is not made, and has the above-mentioned problems, such as the need to additionally provide a plurality of heat exchangers to supplement this.

The present invention to solve this problem is to supply the waste heat generated from the compressor with the waste heat of the room ventilated indoors in cold winter when the outside temperature is low to the evaporator waste heat that can prevent the performance degradation of the system and improve the heating efficiency The purpose is to provide a recovery air conditioning combined air conditioning unit.

Another object of the present invention is to recover a part of the condensate in the hot summer of high outside temperature and supply it to the third double heat exchanger disposed adjacent to the condenser to improve the cooling performance according to the heat transfer of the condenser, The present invention provides a waste heat recovery type air-conditioning combined air conditioner that prevents condensation from accumulating and prevents contamination and propagation of pathogens.

Another object of the present invention is to supply the hot water brine stored in the hot water brine tank in the cold winter season with low outside temperature through the compressor head to the third dual heat exchanger, thereby improving the heat exchange performance in the second heat exchanger to improve the heating efficiency. It is to provide a waste heat recovery type air-conditioning combined air conditioner that can be increased.

1 is a block diagram of a conventional air-conditioning combined air conditioner according to the prior art,

2 is a block diagram of a waste heat recovery type air-conditioning combined air conditioner according to the present invention,

Figure 3 is a flow chart of the waste heat cold and hot recovery in the air conditioner according to the present invention,

4 is a flow chart of the cooling and cooling refrigerant circulation in the air conditioner according to the present invention,

Figures 5a and 5b, respectively, the performance test conditions and Molyel diagram of the air conditioner according to the present invention as an experimental example,

6A and 6B are performance test conditions and a moliel diagram of a conventional air conditioner as Comparative Example 1, respectively.

7A and 7B are performance test conditions and a moliel diagram of another conventional air conditioner as Comparative Example 2, respectively.

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

10 second air conditioning case 11 second heat exchanger

12: second blowing fan 13, 14, 15a, 15b, 24, 25, 31: damper

16 spray tube 17 exhaust heat exchange chamber

18: exhaust mixing chamber 19: waste heat recovery inlet

20: first air conditioning case 21: indoor ventilation inlet

22: first heat exchanger 23: pre-filter

26: first blowing fan 27: air supply heat exchange chamber

28: air supply mixing chamber 29: drain plate

30: compressor case 31: indoor waste heat recovery duct

32: compressor 33: grill

34: oil separator 35: indoor ventilation duct

36: hot water brine tank 37: hot water brine water pipe

38: hot water brine return pipe 39: drain pipe

40: drain pump 41: cold water supply pipe

42: spray water supply pipe 43: three-way valve

44: hot water brine pump 45: rectifier circuit

46: receiver 47: expansion valve

48: back flow valve 49: liquid heater

50: third dual heat exchanger 51: compressor waste heat recovery duct

52: compressor head 53: 4-way valve

Waste heat recovery type air-conditioning combined air conditioner of the present invention for achieving the above object is a compressor for compressing a refrigerant, a part of the indoor ventilation introduced through the first and second air supply damper and the first to cool or warm the outside air Refrigerant is liquefied through heat exchange with a first air-conditioning case equipped with a heat exchanger, an air supply fan for supplying cooling air or warm air to the room, and a part of indoor air introduced through the first and second exhaust dampers and the outside air. Or a second heat exchanger having a second heat exchanger for expanding and a second air conditioning case having an exhaust blower fan for releasing air after heat exchange into the atmosphere, wherein the waste heat generated by the compressor is discharged to the outside. A compressor casing which is prevented from being discharged, a first inflow damper into which the outside air to be supplied to the second heat exchanger is introduced, and the compressor k Claim for selectively supplying the waste heat from the first heat exchange group is characterized in that it comprises an inlet chamber, a second inlet damper.

The waste heat recovery type air-conditioning combined air conditioner of the present invention for achieving the above-mentioned other objects is a waste heat recovery type air-conditioning combined air conditioner that improves cooling and heating efficiency by using waste heat of indoor air. A first heat exchanger having a first heat exchanger for cooling or warming a part of indoor ventilation introduced through the second air supply damper and an outside air, and an air supply fan for supplying cooling air or warm air to the room; A second heat exchange case including a second heat exchanger for liquefying or expanding a refrigerant through heat exchange with a part of the indoor ventilation introduced through the second exhaust damper and the outside air, and an exhaust blower fan for releasing air after heat exchange into the atmosphere And a compressor case surrounding the waste heat generated by the compressor not to be discharged to the outside, and to be supplied to the second heat exchanger. An inlet chamber provided with a second inlet damper for selectively supplying waste heat introduced from the compressor case to the second heat exchanger via a first inlet damper into which the first inlet damper and a compressor waste heat recovery duct are introduced, and adjacent to the first exhaust damper; And a third dual heat exchanger disposed.

Hereinafter, with reference to the accompanying Figures 2 to 4 will be described in detail with the waste heat recovery type air-conditioning combined air conditioner according to a preferred embodiment of the present invention.

2 is a block diagram of a waste heat recovery type air-conditioning combined air conditioner according to the present invention, Figure 3 is a flow chart of the waste heat recovery in the air conditioner according to the present invention, Figure 4 is an air conditioner according to the present invention Is a flow chart of cooling and cooling refrigerant circulation.

In the waste heat recovery type air-conditioning combined air conditioner for improving the heating and cooling efficiency by using the waste heat of indoor air, the first and second air supply dampers 24 and 25 and the first and second exhaust dampers 13 according to cooling and heating. By adjusting the opening degree of the 14 and 14, the heating efficiency of the winter is increased by controlling the ventilation amount of the room discharged through the indoor waste heat recovery duct 31 and the indoor ventilation duct 35.

In the constitution of the waste heat recovery type air-conditioning combined air conditioner, the compressor 32 compresses the refrigerant, and a part of the indoor ventilation introduced through the first and second air supply dampers 24 and 25 and the outside air are cooled. Alternatively, a first air exchange case (20) having a first heat exchanger (22) for heating and an air supply blower fan (26) for supplying cooling air or warm air to the room, and first and second exhaust dampers (13). And a second heat exchanger 11 for liquefying or expanding the refrigerant through heat exchange with part of the indoor ventilation introduced through (14) and the outside air, and an exhaust blower fan 12 for releasing air after the heat exchange into the atmosphere. The second air conditioning case 10 is provided.

Among them, the first air conditioning case 20 is provided with an indoor ventilation inlet 21 through which the indoor air flows through the indoor ventilation duct 35, and an outdoor air inlet 33 with a grill, and thus, the first According to the opening degree of the air supply damper 24 and the 2nd air supply damper 25, the introduction ratio of indoor ventilation and external air changes. At the rear of the first air supply damper 24 and the second air supply damper 25, a prefilter 23 for removing various dusts and foreign matters is disposed. The first air supply damper 24 and the second air supply damper 25 is configured to adjust the opening degree while opening or closing manually or automatically.

On the other hand, the air supply heat exchange chamber 27 provided between the air supply blower 26 and the first heat exchanger 22 is configured to improve the heat transfer effect by ensuring that the air supply is distributed over the entire area. In addition, the air supply mixing chamber 28 provided between the prefilter 23 and the first heat exchanger 22 also provides sufficient room ventilation and outdoor air to enter through the first air supply damper 24 and the second air supply damper 25. It is formed with enough free space to mix.

The second air conditioning case 10 has a waste heat recovery inlet 19 through which indoor waste heat is introduced through an indoor waste heat recovery duct 31, and includes a first exhaust damper 13 and a second exhaust damper 14. The rate of introduction of waste heat and outside air in the room changes with the degree of opening. The first exhaust damper 13 and the second exhaust damper 14 are also configured to adjust the opening degree while opening or closing manually or automatically.

On the other hand, the exhaust heat exchange chamber 17 provided between the exhaust blower 12 and the second heat exchanger 11 is configured to ensure sufficient space so that the exhaust air is distributed over the entire area to improve the heat transfer effect. In addition, the exhaust mixing chamber 18 provided in front of the second heat exchanger 11 is also sufficient to allow sufficient mixing of the indoor and outdoor air coming through the first exhaust damper 13 and the second exhaust damper 14. It is formed with free space.

In the air conditioner for air conditioning and heating in this configuration, the waste heat generated from the compressor is supplied to the evaporator while using the waste heat of the room ventilated indoors in the cold winter when the outside temperature is low to prevent deterioration of the system and improve heating efficiency. In the preferred embodiment of the present invention, a method of supplying waste heat generated from the compressor 32 to the second air conditioning case 10 is illustrated.

To this end, the air conditioner of the present invention includes a compressor case 30 which surrounds the waste heat generated by the compressor 32 so as not to be discharged to the outside and a first air into which the outside air to be supplied to the second heat exchanger 11 is introduced. An inlet provided with a second inlet damper 15b for selectively supplying waste heat introduced from the compressor case 30 to the second heat exchanger 11 via an inlet damper 15a and a compressor waste heat recovery duct 51. A chamber 15 and a third double heat exchanger 50 disposed adjacent to the first exhaust damper 13 are further provided.

Here, the compressor case 30 and the inflow chamber 15 communicate with each other via the compressor waste heat recovery duct 51, so that the waste heat from the compressor 32 collected in the compressor case 30 is transferred to the inflow chamber 15. It can be supplied with. When the second air conditioning case 10 and the compressor case 30 are integrally manufactured, the length of the compressor waste heat recovery duct 51 may be shortened or omitted in some cases.

In addition, the first air conditioning case 20 and the second air conditioning case 10 may be arranged side by side vertically or horizontally, and the compressor case 30 and the second air conditioning case 10 may be manufactured integrally or separately. have.

The width of the inlet chamber 15 is approximately equal to the width of the first exhaust damper 13, and the width of the third dual heat exchanger 50 is approximately equal to the width of the first exhaust damper 13. It is preferable to construct.

In addition, in a preferred embodiment of the present invention to recover a part of the condensate in the summer to improve the cooling performance according to the heat transfer of the condenser, the condensate discharged from the first heat exchanger in accordance with the switching of the drain pump 40 A portion of is selectively supplied to one of the spray pipes 16 of the third double heat exchanger 50 or the second heat exchanger 11.

Therefore, when the drain water generated in the first heat exchanger 22, which is an evaporator, accumulates in the drain plate 29 in the hot summer, the front upper portion of the second heat exchanger 11, which is a condenser, is operated in accordance with the operation of the drain pump 40. The second heat exchanger 11 was configured to function by air cooling and water cooling by being pumped into the spray pipe 16 provided at regular intervals. At this time, when scattering or contamination occurs in the exhaust duct (3-D), the three-way valve 43 is operated so that condensed water is supplied to the coil of the third dual heat exchanger 50 to be drained through the drain pipe 39. Contamination by condensate or pathogens are suppressed.

As shown in FIG. 3, the compressor case 30 includes a hot water brine tank 36 for storing hot water brine, and hot water brine stored in the hot water brine tank 36 via the compressor head 52. A hot water brine pump 44 which is pumped to the third dual heat exchanger 50 is further provided.

Next, the operation of the waste heat recovery type air-conditioning and air conditioner according to the present invention having such a configuration will be described.

First, referring to FIG. 2, the air flow by the duct during cooling is explained. When 100% of the air from the room is circulated through the RA, some (eg, 30%) of the air is evacuated in consideration of the health of indoor rooms. 70% is supplied to the air supply mixing chamber 28 through the second air supply damper 25, and then mixed with 30% of outdoor air introduced through the first air supply damper 24, and then the prefilter 23 and the first heat exchange. It cools while passing through the machine 22, and is supplied to the room.

On the other hand, some (eg, 30%) of air circulated to the RA is mixed with 70% of outside air and then exhausted out through the second heat exchanger (11).

Here, in the conventional air conditioners of the past, since 30% of the air exhausted from the room was exhausted immediately without passing through the second heat exchanger 11, which is a condenser, the indoor cold air was not utilized. Thus, when the outside air temperature rises, estrus occurs frequently in the refrigerator system when the high pressure of the second heat exchanger 11, which is a condenser, rises.

In order to prevent such a phenomenon and to achieve optimal system efficiency, the waste heat of the indoor air is utilized, and the second heat exchanger 11 as the condenser is used to collect condensed water generated in the first heat exchanger 22, which is the evaporator shown in FIG. ) By intermittently automatic supply or by supplying condensed water to the third dual heat exchanger (50) to allow drainage, so that the refrigerator system can be operated at optimum efficiency without estrus.

At this time, the first inlet damper 15a installed in the compressor case 30 shown in FIG. 2 is open and the second inlet damper 15b is operated to open and close according to the situation.

Next, the air flow chart by the duct at the time of heating is demonstrated in detail with reference to FIG.

When 100% air is circulated through the RA in the room, part of the air amount B is exhausted, and the remaining air amount A is mixed with the outdoor air amount C, and then the first air supply damper 24 and the second air supply damper ( After passing through the pre-filter 23 and the first heat exchanger 22 in accordance with the opening of 25), the air is supplied into the room according to the operation of the air supply blower 26.

At this time, a part of the air amount (B) circulated to the RA is introduced into the compressor case 30 and mixed with the air amount (D) warmed to an intermediate temperature by the compressor waste heat, and then the compressor waste heat hot water brine is circulated. Passing through the double heat exchanger 50, it passes through the second heat exchanger 11 which is an evaporator. As a result, the performance of the evaporator is prevented to the maximum when the outside air temperature is lowered, thereby exhibiting optimal performance and increasing system efficiency.

At the same time, the hot water brine coming out of the hot water brine tank 36 and passing through the compressor water cooling head 52 by the operation of the hot water brine pump 44 as shown in FIG. 3 is supplied to the third dual heat exchanger 50. The heating efficiency can be further improved.

At this time, the first inlet damper 15a installed in the inlet chamber 15 maintains the closed state, and the second inlet damper 15b maintains the open state. At this time, the drain pump 40 does not operate.

Here, in the conventional air-conditioning heat exchanger, a part of the air amount B circulated is exhausted to the outside as it is, and the outside air amount does not pass through the compressor 32, but is immediately mixed with the B air amount to be the second heat exchanger 11 which is an evaporator. Was exhausted through).

Next, Figure 4 is a view showing a cooling and heating circulation flow chart.

As shown, in the refrigerant circulation flow diagram, a conventional four-way valve 53, a liquid heater 49, a receiver 46, and an oil separator 34 including a compressor 32 in the compressor case 30. ), Built-in sight glass.

In the figure, the solid line represents the cooling cycle direction, and the dotted line represents the heating cycle direction.

First, during cooling, a gaseous refrigerant of a high temperature and high pressure compressed from the compressor 32 is discharged, and is passed through the second heat exchanger 11 by a four-way valve 53 to be a liquid refrigerant and rectified circuit 45. The refrigerant expands by the pressure drop in the receiver 46 and the expansion valve 47 and heat exchanges in the first heat exchanger 22 which is an evaporator during cooling. Next, it passes through the four-way valve 53 and the liquid heater 49, is again sucked into the compressor 32, compressed and discharged into a gas refrigerant having a high temperature and high pressure. During cooling, the above process is continued to cool the room.

On the other hand, during heating, the cycle proceeds in contrast to the cooling operation, and the refrigerant of the high-temperature, high-pressure gas state compressed from the compressor 32 is discharged, and the first heat exchanger 22 is operated by the four-way valve 53. After passing through the liquid refrigerant, the refrigerant is expanded by the pressure drop in the receiver 46 and the expansion valve 47 through the rectifier circuit 45, and the heat exchange in the second heat exchanger 11 which is an evaporator during heating. . Next, the low temperature low pressure refrigerant passing through the four-way valve 53 and the liquid heater 49 is sucked into the compressor and compressed and discharged again into a high temperature high pressure gas refrigerant. At the time of heating, the above process is continued to heat the room.

On the other hand, in the case of automatic control for carrying out the present invention, at the time of cooling, the drain pump 40 shown in Figs. 2 and 3 is operated, and the first inlet damper 15a is opened and the second inlet damper is opened. 15b remains closed.

And through the four-way valve 53 shown in Figure 4, to control the flow of the four-way valve 41 to flow the discharged high-temperature, high-pressure gas refrigerant to the second heat exchanger (11) which is a condenser when cooling.

During heating, the first inlet damper 15a is closed and the second inlet damper 15b is controlled to open. At this time, the drain pump 40 is not operated. In addition, the four-way valve 53 controls the flow of the four-way valve 53 to flow the discharged high-temperature, high-pressure gas refrigerant to the first heat exchanger 22 which is a condenser when heating.

Next, with reference to Figures 5 to 7 will be described by comparing the heating performance for the waste heat recovery type air-conditioning combined air conditioner according to the present invention and the conventional air conditioner.

First, Figures 5a and 5b, respectively, as a test example shows the performance test conditions and Molieel diagram of the air conditioner according to the present invention. In FIG. 5A, the heating waste heat generator refers to the third dual heat exchanger 50 of the present invention utilizing waste heat from the compressor.

In order to determine the heating performance of the experimental example, the outlet temperature {t} _ {outlet} was obtained in the following order.

2. {Q} _ {Hot Water} = m · C · dt = 1,272 ℓ / h × 5 ℃ × 1 = 6360 Kcal (at 3RT)

3. 2,120 Kcal / h for 1 RT

4. Therefore 2120 = 540 × 1.5 × 0.29 × ({t} _ {exit} + 5.2)

{t} _ {exit} = 3.2 ℃

5. Criterion: Evaporator inlet and outlet temperature difference is set to 8 ℃, evaporation temperature is the outlet temperature difference and 5 ℃ reference, the Molieel diagram can be represented as shown in Figure 5b.

6. The specific volume υ at this time is 0.055 {m} ＾ {3} / Kg, which is obtained from the diagram of FIG. 5B.

7. Thus, refrigerant circulation amount ego,

8. The refrigerating capacity at this time = refrigeration effect × refrigerant circulation = (148-110.5) × 69 = 2587.5 Kcal / h, and the heat of condensation and the heat of compression are as follows.

9. Heat of condensation (heating heat) = condensation effect × refrigerant circulation = (157.5-110.5) × 69 = 3243 Kcal / h.

10. Compression work = Compression effect × Refrigerant circulation = (157.5-148) × 69 = 655.5 Kcal / h

11. Heating performance coefficient at this time = to be.

6A and 6B show the performance test conditions and Molieel diagram of the conventional air conditioner (product A) as Comparative Example 1, respectively.

Here, in order to find out the heating performance of the experimental example, the calorific value (Q _{hot water} ) value and the outlet temperature {{t} _ {outlet}) obtained in Experimental Examples 1 to 5 items are used as they are.

Similarly, in the case of Comparative Example 1, when the evaporator inlet and outlet temperature difference is set to 8 ° C, and the evaporation temperature is based on the outlet temperature difference and 5 ° C, the Molieel diagram as shown in FIG. 6B can be drawn.

6. The specific volume at this time is 0.125 {m} ＾ {3} / Kg.

In addition, the refrigerant circulation amount, the freezing capacity, the heat of condensation, the amount of compression work and the heating performance coefficient can be obtained as follows.

7. Refrigerant circulation

8. Refrigeration capacity = freezing effect × refrigerant circulation = (146-110.5) × 30.4 = 1079.2 Kcal / h

9. Heat of condensation (heating of heat) = Condensation effect × refrigerant circulation = (159-110.5) × 30.4 = 1474.4 Kcal / h

10. Compression work = Compression effect × Refrigerant circulation = (159-146) × 30.4 = 395.2 Kcal / h

11. Heating performance factor =

Next, Fig. 7A and Fig. 7B show the performance test conditions and Molieel diagram of another conventional air conditioner (Product B) as Comparative Example 2, respectively.

Here, in order to find out the heating performance of the experimental example, the calorific value (Q _{hot water} ) value and the outlet temperature {{t} _ {outlet}) obtained in Experimental Examples 1 to 5 items are used as they are.

Similarly, in the case of Comparative Example 2, when the evaporator inlet and outlet temperature difference is set to 8 ° C, and the evaporation temperature is based on the outlet temperature difference and 5 ° C standard, it is possible to draw a Molieel diagram as shown in Figure 7b.

6. The specific volume at this time is 0.092 {m} ＾ {3} / Kg.

In addition, the refrigerant circulation amount, the freezing capacity, the heat of condensation, the amount of compression work and the heating performance coefficient can be obtained as follows.

7. Refrigerant circulation

8. Refrigeration capacity = Refrigeration effect × refrigerant circulation = (146.8-110.5) × 41.3 = 1499.2 Kcal / h

9. Heat of condensation (heating of heat) = Condensation effect × refrigerant circulation = (158.2-110.5) × 41.3 = 1970 Kcal / h

10. Compression work = Compression effect × Refrigerant circulation = (158.2-146.8) × 41.3 = 470.8 Kcal / h

11. Heating performance factor =

Next, the data obtained above is compared with Table 1 and shown.

TABLE 1

(Unit: Kcal / h) (Winter)

As described above, the heat pump of Korea, that is, the air conditioner combined with air conditioning and heating, has a lower performance than the developed product in the summer, but it is excluded from the comparative data because the air conditioner does not perform as bad as it does not function. . However, in winter, when the outside air temperature drops below zero, poor performance occurs, so other companies often use auxiliary electric heating heaters to heat.

The above data is a figure showing the heating performance comparison value of the present invention using the compressor cover when the auxiliary heating heater is not used, and the heat of condensation (heating use) is 120% compared to the conventional A product, and the conventional B 65% heating calorie improvement compared to the product.

According to the present invention described above, by connecting the compressor waste heat recovery duct to the second air conditioning case provided with the second heat exchanger, the waste heat generated from the compressor is supplied to the second heat exchanger, and the exhaust mixture is mixed in the second air conditioning case. By installing the third double heat exchanger opposite the second heat exchanger with the seals interposed therebetween, in the cold winter season when the outdoor temperature is low, the waste heat generated by the compressor is supplied to the second heat exchanger to reduce the performance due to the decrease in the outside air temperature without a separate heat source. It is possible to improve the heating efficiency and energy saving by preventing the condensate water in the hot summer season to the third dual heat exchanger to improve the cooling performance according to the heat transfer of the condenser.

In addition, by supplying the condensed water collected in the drain plate to the third dual heat exchanger by the operation of the 3-way valve, if the contamination occurs in the scattering and exhaust duct due to the on-site conditions, the drain water is sent to the water pipe coil for high ambient temperature It is possible to prevent condenser high pressure and estrus by passing through.

Claims (12)

A compressor for compressing a refrigerant, a first heat exchanger for cooling or warming a part of indoor ventilation introduced through the first and second air supply dampers, and an air supply fan for supplying cooling air or warm air to the room are provided. A second heat exchanger for liquefying or expanding the refrigerant through heat exchange with the first air conditioning case, a part of indoor ventilation introduced through the first and second exhaust dampers, and the outside air, and for releasing air after the heat exchange to the atmosphere In the waste heat recovery type air-conditioning combined air conditioner including a second air conditioning case provided with an exhaust blower fan, A compressor case 30 surrounding the waste heat generated by the compressor 32 so as not to be discharged to the outside; A second inlet damper for selectively supplying waste heat from the first inlet damper 15a and the compressor case 30 to which the outside air to be supplied to the second heat exchanger 11 is introduced to the second heat exchanger 11. A waste heat recovery type air-conditioning combined air conditioner, comprising an inflow chamber 15 provided with a 15b. The method of claim 1, The compressor case 30 and the inlet chamber 15 are in communication with each other via the compressor waste heat recovery duct (51), characterized in that the heat recovery combined air conditioning and air conditioner. The method of claim 1, The width of the inlet chamber 15 is substantially the same as the width of the first exhaust damper 13, the waste heat recovery type air-conditioning combined air conditioner. The method of claim 1, A waste heat recovery type air-conditioning combined air conditioner, characterized in that the third double heat exchanger (50) is further installed adjacent to the first exhaust damper (13). The method of claim 4, wherein The width of the third double heat exchanger (50) is substantially the same as the width of the first exhaust damper (13) waste heat recovery type air-conditioning combined air conditioner. The method of claim 4, wherein According to the switching of the drain pump 40, a part of the condensed water discharged from the first heat exchanger is selectively provided to one of the spray tubes 16 of the third double heat exchanger 50 or the second heat exchanger 11. Waste heat recovery type air-conditioning combined air conditioner, characterized in that the supply. The method according to claim 1 or 4, In the compressor case 30, a hot water brine tank 36 storing hot water brine and a hot water brine stored in the hot water brine tank 36 are pumped to the third dual heat exchanger 50 via the compressor head 52. Waste heat recovery type air-conditioning combined air conditioner, characterized in that the hot water brine pump 44 is further installed. In the waste heat recovery type air-conditioning combined air conditioner that uses the waste heat of indoor air to improve the cooling and heating efficiency, A compressor 32 for compressing the refrigerant, A part of indoor ventilation introduced through the first and second air supply dampers 24 and 25 and a first air exchanger 22 for cooling or warming the outside air and an air supply air supply for supplying cooling air or warm air to the room The first air conditioning case 20 is provided with a fan 26, A part of the indoor ventilation introduced through the first and second exhaust dampers 13 and 14 and a second heat exchanger 11 for liquefying or expanding the refrigerant through heat exchange with outside air and air after heat exchange A second air conditioning case 10 having an exhaust blower fan 12 for discharging to the inside, A compressor case 30 surrounding the waste heat generated by the compressor 32 so as not to be discharged to the outside; Waste heat introduced from the compressor case 30 is interposed between the first inlet damper 15a through which the outside air to be supplied to the second heat exchanger 11 is introduced and the compressor waste heat recovery duct 51. An inlet chamber 15 provided with a second inlet damper 15b to selectively feed to 11), A waste heat recovery type air-conditioning combined air conditioner comprising a third dual heat exchanger (50) disposed adjacent to the first exhaust damper (13). The method of claim 8, The first air conditioning case 20 and the second air conditioning case 10 are waste heat recovery type air-conditioning combined air conditioner, characterized in that arranged in the vertical or horizontal. The method of claim 8, The compressor case 30 is a waste heat recovery type air-conditioning combined air conditioner, characterized in that configured integrally or separated from the second air conditioning case (10). The method of claim 8, According to the switching of the drain pump 40, a part of the condensed water discharged from the first heat exchanger is selectively selected from one of the spray tubes 16 of the third double heat exchanger 50 or the second heat exchanger 11. Waste heat recovery type air-conditioning combined air conditioner, characterized in that the supply. The method of claim 8, In the compressor case 30, a hot water brine tank 36 storing hot water brine and a hot water brine stored in the hot water brine tank 36 are pumped to the third dual heat exchanger 50 via the compressor head 52. Waste heat recovery type air-conditioning combined air conditioner, characterized in that the hot water brine pump 44 is further installed.