KR100563899B1 - Waste heat recoverable air conditioner - Google Patents

Abstract

It is an object of the present invention to provide a waste heat recovery type air conditioner that can exhibit high defrost ability and at the same time effectively utilize waste heat from an engine to realize a high coefficient of performance (COP).

A refrigerant circuit (10) including an compressor (11), an indoor side heat exchanger (12), an expansion valve (16), and an outdoor unit side heat exchanger (13) driven by an engine (90) to compress a refrigerant; A cooling means 23 for transferring waste heat from the 90 to the cooling water, a radiator 21 for discharging the waste heat to the outside, a heat exchanger for waste heat recovery 30 connected in parallel to the outdoor unit side heat exchanger 13, And a cooling circuit 20 having a cooling water pump 24 for circulating the cooling water between the cooling means 23, the first cooling water operation chamber 30b, and the radiator 21. Defrosting is performed by installing a refrigerant preheating heat exchanger 31 connected upstream of the outdoor unit side heat exchanger 13 and heating a refrigerant circulating in the outdoor unit side heat exchanger 13 as necessary.

Compressor, expansion valve, radiator, heat exchanger, cooling circuit, coolant working room

Description

Waste heat recovery air conditioner {WASTE HEAT RECOVERABLE AIR CONDITIONER}

1 is a schematic diagram of a waste heat recovery type air conditioner according to a first embodiment.

2 is a schematic view showing a modification of the first embodiment.

3 is a schematic diagram of a waste heat recovery type air conditioner according to a second embodiment.

4 is a schematic view showing a modification of the second embodiment.

5 is a schematic diagram of a waste heat recovery type air conditioner according to a third embodiment.

6 is a schematic view showing a modification of the third embodiment.

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

10: refrigerant circuit

11: compressor

15: accumulator

12: indoor side heat exchanger

13: outdoor unit heat exchanger

16: expansion valve

17: throttle

18: 4-way selector valve

19: refrigerant line

20: cooling circuit

21: radiator

23: exhaust heat exchanger

24: cooling pump

29: cooling water pipe

30: heat exchanger for waste heat recovery

30a: first refrigerant operating chamber

30b: 1st cooling water operation chamber

31: refrigerant preheating heat exchanger

31a: second refrigerant operating chamber

31b: second coolant operating chamber

40: heating unit

50: bypass passage

v1 to v5: electronic control valve

v6: check valve

The present invention relates to a waste heat recovery type air conditioner using a heat pump driven by a gas engine, and more particularly, to a waste heat recovery type air conditioner that can be efficiently defrosted.

In the air conditioner using the heat pump, there is a problem in that frost is formed on the heat exchanger on the outdoor unit side when the outside temperature is low. The conventional air conditioner is provided with a bypass passage for connecting the high pressure refrigerant circuit and the low pressure refrigerant circuit in parallel with the electromagnetic expansion valve, and installs a control valve whose opening can be adjusted as a pressure reducing valve in the middle of the bypass passage. . Further, by providing a heat exchanger for performing heat exchange between the upstream and downstream portions of the control valve, a technique is disclosed in which heat dissipation and condensation of the high pressure refrigerant flowing into the bypass passage is performed and the heat is applied to the low pressure side. (Patent Document 1).

Moreover, the technique which raises the evaporation temperature of a refrigerant | coolant through heat transfer of a plate fin indirectly by the radiator built-in the engine heat of a heat in a gas heat pump (patent document 2 and 3) is disclosed.

[Patent Document 1]

Japanese Patent Laid-Open No. 2001-21229

[Patent Document 2]

Japanese Patent Laid-Open No. 60-116161

[Patent Document 3]

Japanese Patent No. 2815921

However, in the above-described first technique, since the temperature of the refrigerant on the low pressure side is raised, there is a limit to the defrosting ability. In addition, in the second technology, since the temperature of the outdoor unit side heat exchanger is increased by the waste heat of the engine, the refrigerant condensation capacity is lowered, thereby lowering the air conditioning performance coefficient (COP) of the heat pump. In addition, during the heating operation, the temperature of the outdoor unit heat exchanger is increased due to the waste heat of the engine, so that the low pressure of the refrigerant is excessively increased. As a result, the high pressure of the refrigerant is increased more than necessary, so that the system cannot be continuously operated or the engine is cooled. There is a problem that the water temperature is too high. In addition, during the standard heating operation (when the outside air temperature is about 5 to 10 ℃), the temperature of the outdoor heat exchanger rises due to the waste heat of the engine, and the heat exchange capacity with the outside air is lowered. ) Has a problem that can be reduced.

Disclosure of Invention The present invention has been made to solve these problems, and provides a waste heat recovery type air conditioner that can exhibit high defrost ability and can effectively use high efficiency waste heat from the engine to realize a high coefficient of performance (COP). It has a purpose to solve it.

The waste heat recovery type air conditioner to which the present invention is applied has an engine, a refrigerant circuit, a cooling circuit, and a heat exchanger for waste heat recovery.

A refrigerant circuit is driven by the engine to compress the refrigerant, a first heat exchanger connected to the compressor, an expansion valve connected to the first heat exchanger, and a refrigerant valve connected to the expansion valve to reflux the refrigerant to the compressor. A second heat exchanger is provided. The cooling circuit includes cooling means for transferring waste heat from the engine to a cooling fluid, a radiator connected to the cooling means for releasing waste heat delivered to the cooling fluid into an atmosphere, and the cooling fluid between the cooling means and the radiator. It has a cooling fluid pump for circulating. The waste heat recovery heat exchanger includes a first refrigerant operating chamber connected to the refrigerant circuit in parallel with the second heat exchanger, a first cooling fluid operating chamber connected to the cooling circuit in parallel or in series with the radiator, and the first refrigerant. And a heat transfer wall partitioning the operation chamber and the first cooling fluid operation chamber, wherein a part of the waste heat from the engine is transferred to the refrigerant.

The first refrigerant operating chamber of the waste heat recovery heat exchanger of the refrigerant circuit may be connected in series between the second heat exchanger and the compressor instead of a position parallel to the second heat exchanger (claim 2).

Further, a second cooling fluid operating chamber connected to the cooling circuit in series or in parallel with the radiator and / or the heat exchanger for waste heat recovery, and a second connecting between the expansion valve of the refrigerant circuit and the second heat exchanger. And a heat exchanger wall partitioning the second cooling fluid operating chamber and the second cooling fluid operating chamber, and a refrigerant preheating heat exchanger configured to transfer waste heat from the engine to the refrigerant flowing into the second heat exchanger. It is characterized by.

That is, the frost removal effect can be exhibited by heating the refrigerant | coolant which flows into the 2nd heat exchanger corresponded to the outdoor unit side heat exchanger by waste heat from an engine by the refrigerant | coolant preheating heat exchanger. Here, since the waste heat from the engine is not only introduced into the refrigerant preheating heat exchanger but also into the radiator and the waste heat recovery heat exchanger, the high pressure of the refrigerant under the heating overload condition and the engine coolant easily rise excessively, and the heating standard operating conditions Since the temperature of the second heat exchanger in the state does not rise more than necessary, heat exchange with the outside air is possible, and the decrease in the coefficient of performance (COP) can be minimized.

Here, the first cooling fluid working chamber is preferably connected in parallel to the radiator. Further, the second cooling fluid working chamber is preferably connected in parallel to each of the radiator and the waste heat recovery heat exchanger. It is possible to independently control the amount of cooling fluid circulated in the first and second cooling fluid operating chambers to the radiator, and to operate the system (external temperature, difference in heating operation or cooling operation, required heating capability, frost condensation). It is because it can control suitably according to whether or not).

In addition, the waste heat recovery type air conditioner of the present invention which solves the above-mentioned problems is the waste heat recovery type air conditioner according to claim 1 or 2, wherein the waste heat recovery heat exchanger is used instead of the refrigerant preheating heat exchanger. And a bypass passage having a first control valve for controlling the flow rate by connecting between the motor and the compressor to the compressor, and between the expansion valve and the second heat exchanger (claim 3).

The refrigerant heated by the waste heat recovery heat exchanger is partially refluxed and introduced into the second heat exchanger, thereby achieving the defrost effect. Since the amount of reflux to the first control valve can be adjusted, the decrease in the coefficient of performance (COP) can be suppressed to a minimum, and the increase in cost can also be suppressed to a minimum because it is not necessary to install a heat exchanger for preliminary cooling of the refrigerant.

In addition, when the first refrigerant operating chamber of the heat recovery heat exchanger is connected in parallel with the second heat exchanger, the refrigerant circuit is configured to prevent the refrigerant from flowing into the second heat exchanger from the expansion valve to the second heat exchanger. It is preferred to have a second control valve for adjusting the amount (claim 4). When the first refrigerant operating chamber of the heat recovery heat exchanger is connected in parallel with the second heat exchanger, the pressure loss of the refrigerant is smaller than when connected in series. By installing the second control valve, as the external temperature increases, the amount of refrigerant flowing to the waste heat recovery heat exchanger can be relatively reduced, thereby improving the coefficient of performance (COP). In addition, when the external temperature is low, it is possible to prevent the decrease in capacity by stopping the introduction of the refrigerant into the second heat exchanger. By making the second heat exchanger higher in capacity than the heat exchanger for waste heat recovery, it is possible to cope with various operating states with only the second control valve.

If the second control valve is completely closed and the inflow of the refrigerant to the second heat exchanger is completely stopped, the refrigerant may flow back from the outlet side (gas side) of the second heat exchanger and liquefy and stay inside the second heat exchanger. However, retention of the refrigerant can be prevented by flowing a minimum amount of the first control valve or the second control valve to the second heat exchanger. Since the refrigerant circulated to the second heat exchanger is heated in the waste heat recovery heat exchanger (when the first control valve is opened) or the refrigerant preheating heat exchanger (when the second control valve is opened), the surface of the second heat exchanger Prevents frost on the

When the retention of the coolant occurs, not only the amount of coolant in the coolant circuit is reduced, but also the coolant oil for lubrication is also retained together with the coolant, which may damage the system. In addition, even if the second control valve is slightly opened without using the refrigerant preheating heat exchanger, and the refrigerant is introduced into the second heat exchanger, the retention can be prevented, but there is a fear that frost may form in the second heat exchanger.

When the surface temperature of the second heat exchanger is less than or equal to the frost point, or when frost forms on the surface of the second heat exchanger, the second control valve is adjusted in the closing direction. In other cases, it is preferable to have control means for adjusting the second regulating valve to the open position (claim 5).

In addition, when providing an independent refrigerant preheating heat exchanger, it is preferable to have a 3rd control valve which adjusts the quantity of the cooling fluid which flows into the said refrigerant preheating heat exchanger (claim 5). By the 3rd control valve, heating according to external temperature can be implement | achieved. In addition, when the waste heat recovery type air conditioner is also used for the cooling operation, the reduction of the cooling capacity and the efficiency can be prevented by stopping the inflow of the refrigerant into the refrigerant preheating heat exchanger by the third control valve. For example, when the surface temperature of the second heat exchanger is less than or equal to the frost point of the atmosphere of the second heat exchanger or when frost forms on the surface of the second heat exchanger, the first control valve or the third control valve. It may have a control means for adjusting the to the open direction, otherwise the first control valve or the third control valve to the closed position (claim 7).

In addition, a part of the conduit connecting the compressor, the first heat exchanger, and the second heat exchanger, respectively, of the refrigerant circuit has a heating part and a cooling part, and the refrigerant circuit has air conditioning for independently switching the heating part and the cooling part. It is preferable to have a switching valve, and the said refrigerant | coolant preheating heat exchanger is provided in the said heating part (claim 8). Since the refrigerant preheating heat exchanger becomes a resistance in the circulation of the refrigerant, it is possible to exhibit high cooling capability by using a different pipe than during heating in the cooling operation without fear of frost formation.

EMBODIMENT OF THE INVENTION Below, the waste heat recovery type air conditioner of this invention is demonstrated in detail based on drawing. Although a gas engine is illustrated and demonstrated as an engine in this apparatus, it does not specifically limit. In addition, the drawing used for description is schematic, and the member of the detail with few relations with the nature of invention is abbreviate | omitted. In addition, the code | symbol in drawing may attach | subject the same code | symbol to the member which has a substantially common function for convenience of description.

[First Embodiment]

(Configuration)

The outline of the waste heat recovery type air conditioner of this embodiment is shown in FIG. The apparatus recovers waste heat from the gas engine 90 (engine) as a driving source and waste heat from the gas engine 90 as cooling water (cooling fluid), and also cools the gas engine 90 ( 20). The refrigerant circuit 10 includes the compressor 11, the indoor side heat exchanger 12 (the first heat exchanger), the expansion valve 16, the opening degree adjustable electronic control valve v2 (the second control valve), and the outdoor side. A heat exchanger 13 (second heat exchanger) and an accumulator 15 and a refrigerant pipe 19 connecting them are provided. In the indoor heat exchanger 12 and the outdoor heat exchanger 13, fan (not shown) which can adjust a rotation speed, respectively is arrange | positioned closely.

In addition, the refrigerant circuit 10 has a four-way switching valve 18 (cooling and heating switching valve) for switching the heating operation and the cooling operation. The four-way switching valve 18 has a first port 18a connected to one of the second port 18b and the third port 18c, and the fourth port 18d is connected to the second port 18b and the first port 18a. It is connected to the other of the three ports 18c. In FIG. 1, the connection state at the time of heating operation is shown by the solid line, and the connection state at the time of cooling operation is shown by the broken line.

The cooling circuit 20 includes an exhaust heat exchanger 23 (cooling means) and a cooling jacket (not shown: cooling means) formed in the cylinder block of the gas engine 90, the radiator 21, and the coolant pump 24 (cooling fluid). Pump) and are connected in this order by the cooling water pipe (29).

The refrigerant circuit 10 and the cooling circuit 20 are moved by the heat energy by the heat exchanger 30 for waste heat recovery and the heat exchanger 31 for preheating the refrigerant. The heat recovery heat exchanger 30 includes a first refrigerant operating chamber 30a connected to the refrigerant circuit 10 and a first cooling water operating chamber 30b connected to the cooling circuit 20 (first cooling fluid operating chamber). And a heat transfer wall 30c that divides the first refrigerant operation chamber 30a and the first cooling water operation chamber 30b. The refrigerant preheating heat exchanger 31 includes a second refrigerant operating chamber 31a connected to the refrigerant circuit 10 and a second cooling water operating chamber 31b connected to the cooling circuit 20 (second cooling fluid operating chamber). ) And a heat transfer wall 31c that divides the second refrigerant operating chamber 31a and the second cooling water operating chamber 31b.

The refrigerant conduit 19 includes the first port 18a of the four-way switching valve 18 and the discharge port 11a of the compressor 11, the suction port 11b of the compressor 11, and the discharge port 15a of the accumulator 15. ) And the inlet port 15b of the accumulator 15 and the fourth port 18d of the four-way switching valve 18 are respectively connected. In addition, the refrigerant conduit 19 includes the second port 18b of the four-way switching valve 18, the indoor heat exchanger 12, the expansion valve 16, and the second refrigerant of the heat exchanger 31 for preheating the refrigerant. The operating chamber 31a, the outdoor unit side heat exchanger 13, and the third port 18c of the four-way switching valve 18 are connected in series. In addition, the third port 18c of the four-way switching valve 18 passes through the expansion valve 16 and the refrigerant preheating heat exchanger 31 via the first refrigerant operation chamber 30a of the waste heat recovery heat exchanger 30. Is connected between the second refrigerant operating chambers 31a.

In the heating operation, the compressor 11, the indoor side heat exchanger 12, the expansion valve 16, the electromagnetic control valve v2, the outdoor side heat exchanger 13, the accumulator 15, and the compressor 11 are in order. The coolant is connected to circulate, radiated by the indoor heat exchanger 12 and endothermic by the outdoor heat exchanger 13. The refrigerant absorbs the waste heat from the gas engine 90 by the waste heat recovery heat exchanger 30 provided in parallel with the outdoor heat exchanger 13. The check valve v6 is connected in series to the 1st refrigerant | coolant operation chamber 30a of the waste heat recovery heat exchanger 30, and a refrigerant | coolant flows to the waste heat recovery heat exchanger 30 only at the time of the heating operation shown by a solid line. In addition, the refrigerant flowing into the outdoor heat exchanger 13 can be heated by the refrigerant preheating heat exchanger 31 provided in series in the outdoor heat exchanger 13.

During the cooling operation, the compressor 11, the outdoor side heat exchanger 13, the electromagnetic control valve v2, the expansion valve 16, the indoor side heat exchanger 12, and the accumulator 15 are connected in the order of the outdoor side. Heat is dissipated in the heat exchanger 13 and endothermic in the indoor heat exchanger 12.

The cooling water pipe 29 is connected in series so that the cooling water circulates through the cooling water pump 24, the exhaust heat exchanger 23, and the radiator 21 in this order. In the meantime, the 1st cooling water operation chamber 30b of the waste heat recovery heat exchanger 30 and the 2nd cooling water operation chamber 31b of the refrigerant | coolant preheating heat exchanger 31 are connected in parallel to the radiator 21, respectively. The first cooling water operating chamber 30b, the second cooling water operating chamber 31b and the radiator 21 are connected in parallel to each other. The coolant circuit 20 includes an electromagnetic control valve v4 and an electronic control valve that can independently adjust the flow rate of the coolant to the radiator 21, the second coolant operating chamber 31b, and the first coolant operating chamber 30b, respectively. (v3) (third control valve) and electromagnetic control valve v5. As the solenoid valves v4, v3, v5, and v2, solenoid valves capable of adjusting the throttle opening are used, and are controlled by a control device (not shown).

(Action effect)

<Cooling circuit>

The cooling circuit 20 has a function of removing waste heat from the gas engine 90. With the operation of the gas engine 90, the cooling pump 24 is operated to circulate the cooling water in the cooling circuit 20. In the state where the temperature of the gas engine 90 is low, the electromagnetic control valve v4 in the coolant pipe 29 to the radiator 21 is closed to prevent the coolant from being circulated in the radiator 21. When the temperature of the gas engine 90 rises and the cooling water rises above the predetermined temperature, the solenoid regulating valve v4 is opened to circulate the cooling water in the radiator 21. Cooling water circulating in the cooling circuit 20 absorbs waste heat from the gas engine 90 in the cooling jacket and the exhaust heat exchanger 23. The coolant then flows to the radiator 21. Cooling water is radiated from the radiator 21 to the outside atmosphere.

In the heating operation, the cooling water circulated in the waste heat recovery heat exchanger 30 heats a part of the refrigerant. In addition, the coolant is circulated in the refrigerant preheating heat exchanger 31 as necessary to heat the refrigerant circulating in the outdoor unit side heat exchanger 13. The amount of cooling water circulated in the refrigerant preheating heat exchanger 31 is controlled so that the surface temperature of the outdoor unit side heat exchanger 13 does not fall below the frost point of the outside air. Therefore, when the outside temperature is high and the temperature of the coolant is not lower than or equal to the frost point, the coolant is not circulated to the coolant preheating heat exchanger 31 in order to improve heating efficiency.

In addition to controlling the amount of cooling water circulated in the refrigerant preheating heat exchanger (31), frost is detected on the surface of the outdoor unit side heat exchanger (13) until the frost is removed. The cooling water is circulated to the preheating heat exchanger (31). That is, the second refrigerant of the heat exchanger 31 for preheating the refrigerant is operated to a minimum amount capable of suppressing or allowing frost formation on the outdoor unit side heat exchanger 13 by heating the refrigerant circulated to the second heat exchanger. It is preferable to circulate the cooling water in the chamber 31a.

<Refrigerant Circuit: During Heating Operation>

The refrigerant circuit 10 will be described. First, the heating operation in which the four-way switching valve 18 is in a solid line state will be described. The compressor 11 is driven by the gas engine 90 to compress the gas-type refrigerant sucked from the accumulator 15 and feed it to the indoor heat exchanger 12 via the four-way switching valve 18 at high temperature and high pressure. In the indoor side heat exchanger (12), the refrigerant releases heat to the indoor air and exerts a heating effect. Some or all of the refrigerant is condensed and liquefied by heat radiation. The refrigerant is further depressurized by the expansion valve 16, and a part of the refrigerant is introduced into the outdoor unit side heat exchanger 13, and the remaining amount is introduced into the heat exchanger 30 for waste heat recovery to vaporize. The vaporized refrigerant flows into the accumulator 15, and the liquid phase refrigerant is separated and returned to the compressor 11 to perform heating operation.

In the heat exchanger 30 for waste heat recovery, the heating capacity is improved by vaporizing the waste heat of the gas engine 90. When the outside temperature is high, the coefficient of performance (COP) can be improved by opening the electromagnetic control valve v2 to circulate the maximum amount of refrigerant in the outdoor unit side heat exchanger 13. It is also possible to throttle the output of the gas engine 90.

On the contrary, when external temperature is low, the fall of heating capability is suppressed by reducing the quantity of the refrigerant | coolant circulated to the outdoor unit side heat exchanger 13 by throttling the electromagnetic control valve v2. The refrigerant which flows slightly with respect to the outdoor unit side heat exchanger 13 is heated by the refrigerant preheating heat exchanger 31, so that the temperature of the outdoor unit side heat exchanger 13 is not cooled below the frost point so that frost does not form.

In this case, in order to improve the heating capability, when the external temperature is low, a form in which the solenoid regulating valve v2 is completely closed to completely circulate the refrigerant in the outdoor unit side heat exchanger 13 is also considered. However, by circulating the refrigerant slightly to the outdoor unit side heat exchanger 13 without completely stopping the circulation of the refrigerant to the outdoor unit side heat exchanger 13 as in the present embodiment, the refrigerant flows back from the four-way switching valve 18 side to the outdoor unit side heat exchanger 13, By staying liquefied, it is possible to prevent occurrence of insufficient refrigerant amount.

<Refrigerant circuit: during cooling operation>

Next, a description will be given of the cooling operation in which the four-way switching valve 18 is broken. The compressor 11 compresses the gaseous refrigerant sucked from the accumulator 15 and feeds it to the outdoor unit side heat exchanger 13 via a four-way switching valve 18 at high temperature and high pressure. The refrigerant is cooled by the outside air to condense liquefaction of some to all. The refrigerant is further depressurized by the expansion valve 16, and flows into the indoor side heat exchanger 12 to vaporize, thereby taking the latent heat from the indoor air and exerting a cooling effect. The vaporized refrigerant flows into the accumulator 15 and the liquid phase refrigerant is separated and returned to the compressor 11 again.

During the cooling operation, the refrigerant is not circulated to the waste heat recovery heat exchanger 30 by the check valve v6, and the solenoid control valve v3 and the solenoid control valve v5 are closed to thereby cool the refrigerant preheating heat exchanger ( The cooling water is not circulated to the second cooling water operation chamber 31b of 31) and the first cooling water operation chamber 30b of the heat exchanger 30 for recovering waste heat. Therefore, the waste heat of the cooling water is not supplied to the refrigerant, and the cooling ability is improved.

(Control means)

The control method of the electromagnetic control valve v4-v2 and the gas engine 90 which a control means performs is as follows.

The solenoid control valve v4 controls in the closing direction when the temperature of the coolant is low and does not require cooling of the gas engine 90 such as immediately after starting the gas engine 90. In addition, the solenoid control valve v4 controls in the closing direction to circulate the coolant as much as possible in the heat exchanger 30 for recovering waste heat during heating. However, when the outside air temperature is high and the heat exchanger 30 for waste heat recovery cannot sufficiently lower the temperature of the cooling water, control is performed in the opening direction to the limit. In this case, the output of the gas engine 90 can also be reduced. During cooling, the heat is controlled to the open position and the waste heat is mainly released by the radiator 21 to the outside air.

The solenoid regulating valve v3 can normally maximize the efficiency of the outdoor unit side heat exchanger 13 by controlling it to the closed position, and also improves the cooling capability of the gas engine 90. Especially in cooling operation, it is controlled to the closed position. When the outside temperature is low at the time of heating operation and the refrigerant is circulated to the outdoor unit heat exchanger 13 as it is, the surface temperature of the outdoor unit side heat exchanger 13 drops below the frost point of the outside air, and the frost is formed for the first time. The valve v3 is controlled in the open direction. In that case, the opening degree of the solenoid regulating valve v3 is controlled so as to heat above the minimum temperature at which the surface of the outdoor unit side heat exchanger 13 does not form frost. As a preferable control method, the opening degree of the solenoid control valve v3 is controlled so that it may become the minimum temperature which does not produce frost.

Another preferred control method is to open the solenoid regulating valve v3 at predetermined time intervals when the surface temperature of the outdoor unit side heat exchanger 13 is below the frost point of the outside air so that the formed frost can be removed at predetermined time intervals. Thereby, there is a method of heating the outdoor unit side heat exchanger 13 to remove frost.

The electronic control valve v5 is controlled to the open position to recover the waste heat in the refrigerant at the time of heating, and to the closed position to maximize the cooling capability at the time of cooling. By controlling to the closed position when it is not necessary to use the waste heat recovery heat exchanger 30 as in the case of cooling, approximately all the cooling water can be circulated to the radiator 21, so that the heat dissipation in the radiator 21 can be increased.

The electromagnetic regulating valve v2 is normally controlled to the open position. Especially during cooling operation, it is controlled to the open position. Even when the heating operation is high, when the outside temperature is high, it is controlled to the open position. As the outside temperature is lowered and the refrigerant circulating in the outdoor unit side heat exchanger 13 cannot be sufficiently heated, the control is performed in the closing direction. When the external air temperature is equal to or lower than the temperature of the refrigerant circulating in the outdoor unit side heat exchanger 13, the electromagnetic control valve v2 is in the most throttled state. However, in order to prevent retention of refrigerant | coolant etc. in the outdoor unit side heat exchanger 13, it does not set it as a complete closed position. Opening of the solenoid regulating valve v2 slightly to circulate the refrigerant heated by the refrigerant preheating heat exchanger 31 to the outdoor unit side heat exchanger 13 to retain the refrigerant and the like in the outdoor unit side heat exchanger 13 and the outdoor unit. Frost formation on the side heat exchanger 13 can be prevented.

As described above, the refrigerant circuit 10 not only obtains heat from the outside air by the outdoor unit side heat exchanger 13, but also effectively recovers waste heat from the gas engine 90. In addition, by using the waste heat from the gas engine 90, it is possible to prevent or eliminate frost condensation generated in the outdoor unit side heat exchanger 13 when the external temperature is low. The heating of the refrigerant by the refrigerant preheating heat exchanger 31 is direct, and the surface temperature of the outdoor unit side heat exchanger 13 can be adjusted quickly. As a result, removal of frost and prevention of frost formation can be performed quickly. In addition, the defrosting can be realized only by slightly changing the operating state from the normal heating operation, so that the deterioration of the heating quality can be minimized.

[Modified form of the first embodiment]

The schematic diagram of the waste heat recovery type air conditioner of this modification is shown in FIG. That is, the portion where the refrigerant circulates during the heating operation between the expansion valve 16 and the outdoor unit side heat exchanger 13 (the refrigerant preheating heat exchanger 31, the check valve v6, and the electromagnetic control valve v2: Heating section] and a conduit line 40 (cooling section) through which coolant circulates during the cooling operation provided in parallel to the heating section, and has substantially the same configuration as the apparatus of the first embodiment. The pipe line 40 simply connects between the refrigerant preheating heat exchanger 31 and the expansion valve 16, and has a check valve v6 so that the refrigerant does not circulate during the heating operation. The heating part also has a check valve v6 so that the refrigerant does not circulate during the cooling operation.

Therefore, the device of the present embodiment does not circulate the refrigerant to the refrigerant preheating heat exchanger 31 which is basically not necessary for the cooling operation as well as the effect of the device of the first embodiment. Improve your skills.

[2nd Embodiment]

(Configuration)

3 is a schematic view of the waste heat recovery type air conditioner according to the present embodiment. In the apparatus of the present embodiment, the cooling circuit 20 is substantially the same as the apparatus of the first embodiment, and the refrigerant circuit 10 connects the outdoor unit side heat exchanger 13 and the waste heat recovery heat exchanger 30 in series. Other than that, it has the structure substantially the same as the apparatus of 1st Embodiment. In detail, the cooling circuit 20 has the electromagnetic control valve v5 which controls the cooling water circulated to the 1st cooling water operation chamber 30b of the waste heat recovery heat exchanger 30 newly. The refrigerant circuit 10 recovers waste heat between the third port 18c of the four-way switching valve 18 and the outdoor unit heat exchanger 13 without using the solenoid regulating valve v2 and the check valve v6. The heat exchanger 30 is connected in series. In addition, the heat exchanger 30 for waste heat recovery is not limited to the position shown in FIG. The waste heat recovery heat exchanger 30 can be installed between the outdoor unit side heat exchanger 14 and the accumulator 15.

(Action effect)

The operation of each circuit 10 and 20 is basically the same as that of the apparatus of the first embodiment. The opening degree control of the electromagnetic regulating valves v4 v3 and v5 is the same as that of the apparatus of the first embodiment.

In the apparatus of the first embodiment, the outdoor unit side heat exchanger 13 and the waste heat recovery heat exchanger 30 are connected in parallel to appropriately control the opening degree of the solenoid regulating valves v4 to v2 so that the gas engine 90 Although both the recovery of waste heat from the air and the absorption of heat energy from the outside air can be efficiently performed, the device of the present embodiment recovers high heat by recovering waste heat without requiring complicated control and refrigerant circuit 10 by connecting both in series. Can demonstrate ability

[Modified Embodiment of Second Embodiment]

4 is a schematic view of the waste heat recovery type air conditioner of the present modification. That is, the portion where the refrigerant circulates during the heating operation between the expansion valve 16 and the outdoor unit side heat exchanger 13 (the refrigerant preheating heat exchanger 31, the check valve v6, and the electromagnetic control valve v2: Heating section] and a conduit line 40 (cooling section) through which coolant circulates during the cooling operation provided in parallel to the heating section, and has substantially the same configuration as the apparatus of the second embodiment. The pipeline 40 has a check valve v6 so as not to circulate the refrigerant during the heating operation by simply connecting the refrigerant preheating heat exchanger 31 and the expansion valve 16. The heating part also has a check valve v6 so that the refrigerant does not circulate during the cooling operation.

Therefore, the apparatus of the present embodiment does not circulate the refrigerant through the heat exchanger 31 for refrigerant preheating, which is basically not necessary for the cooling operation as well as the effect of the apparatus of the second embodiment, so that the flow path resistance can be reduced, thereby cooling. Improve your skills.

[Third Embodiment]

(Configuration)

5 shows a waste heat recovery type air conditioner according to the present embodiment. The apparatus does not use the refrigerant preheating heat exchanger 31 and the solenoid regulating valve v3, the bypass passage 50 having the solenoid regulating valve v1 (first regulating valve) and two throttles. Except having newly made (17), it has substantially the same structure as the apparatus in 1st Embodiment shown in FIG. One throttler 17 is provided between a portion where the bypass passage 50 branches from the outlet of the first refrigerant operating chamber 30a and a portion that joins the refrigerant circulating from the outdoor unit side heat exchanger 13. . The other throttler 17 is installed between a portion where the refrigerant circulating from the expansion valve 16 branches to the outdoor unit side heat exchanger 13, and a portion that joins the bypass passage 50. The bypass passage 50 is provided between the outlet 301a of the first refrigerant operation chamber 30a of the waste heat recovery heat exchanger 30, the outdoor unit side heat exchanger 13, and the electromagnetic control valve v2. connection via v1). The throttle 17 can employ | adopt normal means, such as a capillary.

(Action effect)

The operation of each circuit 10 and 20 is basically the same as that of the apparatus of the first embodiment. The opening degree control of the solenoid regulating valves v4, v2, v5 and v1 is approximately the same as that of v4, v2, v5 and v3 of the apparatus of the first embodiment. That is, the control of the solenoid regulating valve v1 is controlled to the normally closed position, thereby maximizing the efficiency of the outdoor unit side heat exchanger 13. Especially in the cooling operation, it is controlled to the closed position. When the outside temperature is low during the heating operation and the refrigerant is circulated to the outdoor unit heat exchanger 13 as it is, when the surface temperature of the outdoor unit side heat exchanger 13 falls below the frost point of the outside air and forms frost, the solenoid regulating valve is applied for the first time. (v1) is controlled in the opening direction.

In that case, the surface of the outdoor unit side heat exchanger 13 controls the opening degree of the solenoid regulating valve v1 so as to be heated to the minimum without frost. In addition, in this embodiment, when the external temperature is low and the capacity of the outdoor unit side heat exchanger 13 cannot be sufficiently exhibited, the solenoid regulating valve v2 can be completely closed. Since the refrigerant circulates from the bypass passage 50 to the outdoor unit heat exchanger 13 even when the solenoid regulating valve v2 is completely closed, the storage of the refrigerant such as refrigerant into the outdoor unit side heat exchanger 13 or the outdoor unit side heat exchanger 13 Can effectively prevent frost. In addition, the throttler 17 has an action of adjusting the pressure balance of the refrigerant so that the refrigerant can circulate from the outlet of the first refrigerant operating chamber 30a to the inlet of the outdoor unit side heat exchanger 13.

The present apparatus can have the effect of the apparatus of the first embodiment by using the bypass passage 50, which is a simpler means, instead of the refrigerant preheating heat exchanger 31. That is, lower cost than the apparatus of the first embodiment can be realized. In addition, since only a part of the refrigerant circulating in the outdoor unit side heat exchanger 13 is heated in the waste heat recovery heat exchanger 30, the agent for heating all the incoming refrigerant in the refrigerant preheating heat exchanger 31. The flow path resistance can be made smaller as compared with the device of the first embodiment.

[Modified form of the third embodiment]

6 is a schematic view of the waste heat recovery type air conditioner of the present modification. That is, the refrigerant passage is circulated from the outlet 302a provided in the middle of the first refrigerant operating chamber 30a of the waste heat recovery heat exchanger 30 to the inlet of the outdoor unit side heat exchanger 13. It has a structure substantially the same as that of the apparatus of 3rd embodiment except not using the throttle 17 previously installed from the exit of the 1st refrigerant | coolant operation chamber 30a of the heat exchanger 30 for waste heat recovery. By providing the bypass passage 50 from the outlet 302a, a part of the 1st refrigerant | coolant operation chamber 30a can exhibit the effect as an throttler.

Therefore, the apparatus of this embodiment can reduce the effect of the apparatus of 3rd embodiment, and implement | achieves one throttle.

[Other forms]

In the apparatus of the above-mentioned first to third embodiments, the thermostat valve provided in a portion where the downstream of the radiator 21 and the downstream of the first cooling water operation chamber 30b communicate with each other instead of the electromagnetic control valve v4; The bypass orifice which communicates downstream of the 1st cooling water operation chamber 30b and downstream of a thermostat valve can be employ | adopted.

When the temperature of the coolant is low, the thermostat valve closes the radiator side to open the first coolant operating chamber 30b side, and when the temperature of the coolant reaches a predetermined temperature or more, the thermostat valve opens the first coolant operating chamber 30b. Close the side. Bypass orifice can circulate a certain amount of coolant to the first coolant operation chamber 30b even if the thermostat valve is in the closed position of the first coolant operation chamber 30b. In other words, it is possible to realize the same control without using an expensive solenoid valve.

In addition, a three-way valve or a four-way valve can be used instead of the electromagnetic control valves v3 to v5 provided at the branched portions of the cooling water flow paths.

According to the present invention, there is provided a waste heat recovery type air conditioner capable of exhibiting a high defrost ability and achieving a high coefficient of performance (COP) by effectively utilizing waste heat from the engine.

Claims (8)

Engine, A compressor driven by the engine to compress the refrigerant, a first heat exchanger connected to the compressor, an expansion valve connected to the first heat exchanger, and a second heat exchanger connected to the expansion valve to reflux the refrigerant to the compressor A refrigerant circuit having a group; Cooling means for transferring waste heat from the engine to a cooling fluid, a radiator connected to the cooling means for releasing waste heat delivered to the cooling fluid into an atmosphere, and circulating the cooling fluid between the cooling means and the radiator. A cooling circuit having a cooling fluid pump, A first refrigerant operating chamber connected to the refrigerant circuit in parallel with the second heat exchanger, a first cooling fluid operating chamber connected to the cooling circuit in parallel or in series with the radiator, the first refrigerant operating chamber and the first cooling A waste heat recovery type air conditioner having a heat transfer wall for partitioning a fluid working chamber and having a heat exchanger for waste heat recovery for transferring a part of waste heat from the engine to the refrigerant, A second cooling fluid operation chamber connected in series or in parallel with the radiator and / or the waste heat recovery heat exchanger to the cooling circuit, and a second refrigerant operation connected between the expansion valve and the second heat exchanger of the refrigerant circuit; And a heat transfer wall partitioning the second cooling fluid operation chamber and the second refrigerant operation chamber, and having a refrigerant preheating heat exchanger for transferring waste heat from the engine to the refrigerant flowing into the second heat exchanger. Waste heat recovery type air conditioner. The waste heat recovery air conditioner according to claim 1, wherein the first refrigerant operating chamber is connected in series between the second heat exchanger and the compressor instead of a position parallel to the second heat exchanger. The flow rate control according to claim 1 or 2, wherein the flow rate is controlled by connecting between the waste heat recovery heat exchanger to the compressor and the expansion valve to the second heat exchanger instead of the refrigerant preheating heat exchanger. A waste heat recovery type air conditioner having a bypass passage having a first control valve. The waste heat recovery type according to claim 1 or 2, wherein the refrigerant circuit includes a second control valve for adjusting the amount of the refrigerant flowing into the second heat exchanger between the expansion valve and the second heat exchanger. Air conditioner. The waste heat recovery type air conditioner according to claim 1 or 2, further comprising a third control valve for adjusting an amount of cooling fluid flowing into the refrigerant preheating heat exchanger. The second control valve according to claim 4, wherein when the surface temperature of the second heat exchanger is equal to or lower than the frost point in the atmosphere of the second heat exchanger, or when frost forms on the surface of the second heat exchanger, Adjusted in the closing direction, Otherwise, a waste heat recovery type air conditioner having control means for adjusting the second control valve to the closed position. The method of claim 3, wherein the surface temperature of the second heat exchanger is less than or equal to the frost point in the atmosphere of the second heat exchanger, or the frost is formed on the surface of the second heat exchanger. The third regulating valve is adjusted in the opening direction, Otherwise, the waste heat recovery type air conditioner having control means for adjusting the first control valve or the third control valve to the closed position. The part of the pipe line which connects the said compressor of the said refrigerant circuit, the said 1st heat exchanger, and the said 2nd heat exchanger, respectively, has a heating part and a cooling part, The refrigerant circuit has a cooling and heating switching valve for switching the heating unit and the cooling unit independently, The heat exchanger for preheating the refrigerant is a waste heat recovery type air conditioner in the heating unit.

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