JPH10185349A - Air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To permit low-capacity heating operation with a small electric power by a method wherein fluorocarbon based refrigerant, which recovered waste heat, is circulated employing a refrigerant transfer means to heat indoor without employing any compressor. SOLUTION: When heating operation is effected upon normal time or under a low load, a compressor 101 is stopped and a first flow passage switching means 1 is switched so that refrigerant flows through a refrigerant transfer means 6 and an outdoor heat exchanger 10 while a second flow passage switching means 2 is switched so that the refrigerant flows through a four-way valve 3 and the refrigerant transfer means 6. Further, the four-way valve 3 is switched into the direction of a dotted line in a diagram and the refrigerant is discharged through the refrigerant transfer means 6 at first, then, heat exchange is effected in an outdoor hot-water heat exchanger 10 between cooling water, whose temperature is increased to a high value by waste heat from the cooling unit of a thermal engine 113 such as a diesel engine or the like, whereby high-temperature refrigerant is obtained. The high-temperature refrigerant is introduced into an indoor heat exchanger 8 to effect the heating of a room. In this case, the refrigerant transfer means 6 is stopped in a cold district or the like and the compressor 101 is driven to effect the heating operation.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner, and more particularly to a heat pump driven by a heat engine and a generator, and by exchanging heat exhausted from the heat engine with a refrigerant, thereby making the heat exhausted from the heat engine air-conditioned. The present invention relates to an air conditioner that is used effectively.

[0002]

2. Description of the Related Art Conventionally, an air conditioner of this type is known from Japanese Patent Application Laid-Open No. 1-318829. Hereinafter, the air conditioner will be described with reference to FIG. As shown in FIG. 36, a compressor 101 is driven by a motor 102, and heat exchangers 103, 104
Are refrigerant tubes 105 and 106 through which the refrigerant flows.
Are arranged respectively. Heat exchanger 103
Is for causing heat to be exchanged between the outside air and the refrigerant flowing through the refrigerant pipe 105, and the other heat exchanger 104
Is for causing heat exchange between the circulating water introduced by the circulation pump 107 and the refrigerant flowing through the refrigerant pipe 106. The compressor 101 and the heat exchanger 10
3 and 104 are connected by switching valves 110 and 111 together with a pressure reducing valve 108 and a heat storage unit 109 connected in series with the pressure reducing valve 108. The generator 112 is driven by a heat engine 113 and connected in series with a power switch 114,
It is connected to the motor 102 for driving the compressor 101 via 115. The heat engine 113 is provided with a hot water generating unit 116 that generates hot water using the exhaust heat. The hot water generator 116 is configured to supply the introduced water and heat engine 1
A cooling water heat exchanger 117 for exchanging heat with the cooling water 13 and an exhaust heat arranged in the exhaust pipe 118 of the heat engine 113 for exchanging heat between the introduced water and the exhaust water. It comprises an exchanger 119 and a switching valve 120 for switching the flow direction of the introduced water. The delivery pipe 121 from the hot water generation unit 116 is branched in two directions in the middle thereof, and one of the delivery pipes 121 is connected to a hot water pipe 123 disposed in a hot water storage tank 122 via a flow control valve 124. I have. The other is further branched in two directions in the middle thereof, and one of the two branches is provided in the heat exchanger 103 with a hot water pipe 125 disposed in front of the refrigerant pipe 105 in the flowing direction of the outside air. The other is connected to a hot water pipe 128 disposed in another heat exchanger 127 for adjusting a heat load, which is arranged in parallel with the heat exchanger 103. The downstream ends of the hot water pipes 123, 125, and 128 are joined to an introduction pipe 129 to the hot water generation unit 116. When the air-conditioning apparatus configured as described above performs the heating operation, the outside air introduced into the heat exchanger 103 is heated by the hot water pipe 1.
After the temperature is raised by heat exchange with the warm water flowing through the inside of the coolant tube 25, the coolant comes into contact with the coolant tube 105 and exchanges heat with the coolant flowing through the coolant tube 105. Therefore, even in the severe cold season when the temperature of the outside air is low, a sufficient temperature difference can be generated between the refrigerant and the outside air that comes into contact with the refrigerant via the refrigerant pipe 105, and a high heating capacity can be maintained. Also, the refrigerant pipe 105
When frost occurs on the air, the air introduced into the heat exchanger 103 comes into contact with the refrigerant pipe 105 in a sufficiently warmed state by fully opening the flow control valve 126, and the frost is removed. You.

[0003]

In such a conventional air conditioner, since the compressor is driven even when a low heating capacity is required, there is a problem that the power consumption corresponding to the required capacity becomes large, and the power consumption is reduced. Is required. When a plurality of indoor units are connected,
There is a problem that the cooling operation and the heating operation cannot be performed at the same time among a plurality of indoor units, and it is required to enable the simultaneous cooling and heating operation between the plurality of indoor units. In addition, during the dehumidifying operation, there is a problem that the room temperature decreases because the weak cooling operation is performed, and it is required to dehumidify without lowering the room temperature.

[0004] The present invention is to solve such a conventional problem, it is possible to perform a low-capacity heating operation with power saving, and to efficiently transport the liquid refrigerant by the refrigerant transport means, In addition, it improves the efficiency of the turbo engine as a heat engine, enables simultaneous operation of air conditioning and heating, and can perform heating operation properly according to the load based on the set temperature in the room. It is an object of the present invention to provide an air conditioner that can obtain an auxiliary power of a refrigerant transport unit, can perform a dehumidifying operation without lowering a room temperature, and can perform a dehumidifying operation in which a temperature can be changed according to a setting of an indoor temperature. I have.

[0005]

In order to achieve the above object, an air conditioner according to the present invention has an outdoor unit for exchanging heat between refrigerant conveying means, and refrigerant on the discharge side of the refrigerant conveying means and cooling water of a heat engine. It has a configuration provided with a hot water heat exchanger.

According to the present invention, an air conditioner capable of performing a low-capacity heating operation with small electric power is obtained.

Further, as another means, first flow path switching means is provided between the four-way valve and the indoor heat exchanger, and second flow path switching means is provided between the four-way valve and the outdoor heat exchanger. In this configuration, both ends of a circuit in which the outdoor hot water heat exchanger is connected to the discharge side of the refrigerant transfer means are connected to the first and second flow path switching means so as to be in parallel with the four-way valve.

According to the present invention, an air conditioner capable of performing a low-capacity heating operation with small electric power is obtained.

Another means is a first flow path switching means between the four-way valve and the indoor heat exchanger, and an outdoor heat exchanger and the first heat exchanger.
A second flow path switching means is provided between the first and second flow path switching means, and both ends of a circuit in which the outdoor hot water heat exchanger is connected to the discharge side of the refrigerant conveying means are connected to the first and second flow path switching means. It is configured.

According to the present invention, an air conditioner capable of performing a low-capacity heating operation with small electric power is obtained.

Another means is a third flow switching means between the outdoor heat exchanger and the second flow switching means, and a third flow switching means between the four-way valve and the first flow switching means. And a refrigerant flowing between the second flow path switching means and the refrigerant conveying means, and a refrigerant flowing between the third flow path switching means and the fourth flow path switching means. An inter-refrigerant heat exchanger for exchanging heat with the refrigerant is provided, and a second throttle means is provided between the inter-refrigerant heat exchanger and the third flow path switching means.

According to the present invention, an air conditioner capable of performing a low-capacity heating operation with small electric power is obtained.

Another means is provided with a turbo engine as a heat engine.
And an intake cooling heat exchanger for exchanging heat with the refrigerant flowing between the flow path switching means and the fourth flow path switching means.

According to the present invention, there is provided an air conditioner capable of performing a low-capacity heating operation with low power.

Further, another means includes a plurality of first throttling means and a plurality of indoor heat exchangers, and a plurality of fifth throttling means between the plurality of first throttling means and the second flow path switching means. Channel switching means,
A sixth path between the plurality of indoor heat exchangers and the first flow path switching means.
And a pipe between the outdoor heat exchanger and the second flow path switching means is branched and connected to a plurality of fifth flow path switching means. In this configuration, a pipe between the valve and the valve is branched and connected to a plurality of sixth flow path switching means.

According to the present invention, there is provided an air conditioner capable of performing simultaneous cooling and heating operations between a plurality of indoor units.

Further, the other means includes a first storage means for storing and outputting the indoor set temperature, a first temperature detection means provided in the indoor unit for detecting the indoor temperature, and a detection by the first storage means. First calculating means for calculating the difference between the value and the value detected by the first temperature detecting means, first determining means for determining the result of calculation by the first calculating means, and Second determining means for determining the degree of opening of the first restricting means from the result of the determination, and second calculating means for calculating the degree of opening of the first restricting means from the result of the determination by the second determining means; A first control means for controlling the throttle opening of the first throttle means on the basis of the result of calculation by the second calculation means, and a third control means for calculating the rotation speed of the refrigerant conveying means on the basis of the result of determination by the second determination means. Calculation means and the calculation result by the third calculation means Ri and a second control means for controlling the rotational speed of the refrigerant carrying means, opening of the first throttle means, and is obtained by the configuration for controlling the rotational speed of the refrigerant carrying means.

According to the present invention, an air conditioner capable of performing a low-capacity heating operation with low power and an air conditioner capable of performing a simultaneous cooling and heating operation among a plurality of indoor units are obtained.

Still another means is that a cooling water circuit of the heat engine has a hot water flow rate adjusting means, a hot water conveying means device, a hot water heat exchanger, a cooling heat exchanger, and a blower for the cooling heat exchanger. A third determining means for determining the number of revolutions of the refrigerant conveying means based on the determination result by the second determining means,
A fourth calculating means for calculating the opening of the hot water flow rate adjusting means from the result of the determination by the third determining means, and a third means for controlling the opening degree of the hot water flow rate adjusting means from the result of the calculation by the fourth calculating means. Control means, the opening degree of the first throttle means,
The number of revolutions of the refrigerant transporting means and the opening of the hot water flow rate adjusting means are controlled.

According to the present invention, an air conditioner capable of performing low-capacity heating operation with low power and an air conditioner capable of performing simultaneous cooling and heating operation among a plurality of indoor units are obtained.

The other means includes a fourth judging means for judging the degree of opening of the hot water flow rate adjusting means based on the judgment result by the third judging means, and a rotation of the hot water conveying means based on the judgment result by the fourth judging means. A fifth calculating means for calculating the number of rotations, and a fourth control means for controlling the number of revolutions of the hot water conveying means based on the result of the calculation by the fifth calculating means. The rotation number of the means, the opening degree of the hot water flow rate adjusting means, and the rotation number of the hot water conveying means are controlled.

According to the present invention, an air conditioner capable of performing low-capacity heating operation with low power and an air conditioner capable of performing simultaneous cooling and heating operation among a plurality of indoor units are obtained.

Another means is a fifth determining means for determining the rotational speed of the hot water conveying means from the result of the determination by the fourth determining means, and the rotational speed of the heat engine is determined by the result of the determination by the fifth determining means. A sixth calculating means for calculating, and a fifth calculating means for controlling the number of revolutions of the heat engine based on the calculation result by the sixth calculating means.
Control means for controlling the opening degree of the first throttle means, the rotation speed of the refrigerant conveyance means, the opening degree of the hot water flow rate adjustment means, the rotation speed of the hot water conveyance means, and the rotation speed of the heat engine. It was done. According to the present invention, an air conditioner capable of performing low-capacity heating operation with low power and an air conditioner capable of performing simultaneous cooling and heating operation between a plurality of indoor units are obtained.

Another means is a sixth determining means for determining the rotational speed of the heat engine from the result of the determination by the fifth determining means, and calculates the rotational speed of the compressor from the result of the determination by the sixth determining means. And a sixth control means for controlling the number of rotations of the compressor based on the result of the calculation by the seventh calculation means, the opening degree of the first throttle means, the number of rotations of the refrigerant conveying means. , The opening degree of the hot water flow control means, the rotation speed of the hot water transport means, the rotation speed of the heat engine, and the rotation speed of the compressor.

According to the present invention, an air conditioner capable of performing low-capacity heating operation with low power and an air conditioner capable of performing simultaneous cooling and heating operation among a plurality of indoor units are obtained.

Further, another means includes a second temperature detecting means for detecting the refrigerant temperature and a first pressure detecting means for detecting the refrigerant pressure between the second flow path switching means and the inter-refrigerant heat exchanger. A third temperature detecting means for detecting a refrigerant temperature between the second throttle means and the inter-refrigerant heat exchanger, and calculating a saturation temperature of the refrigerant from a detection result by the first pressure detecting means. Calculating means for calculating a difference between a calculation result obtained by the eighth calculating means and a detection result obtained by the second temperature detecting means.
Calculating means, a seventh judging means for judging the state of the refrigerant from the calculation result by the ninth calculating means, a detection result by the third temperature detecting means from a judgment result by the seventh judging means, A tenth calculating means for calculating a difference from a detection result by the second temperature detecting means, and an eighth calculating means for determining a temperature difference between the refrigerants based on a calculation result by the tenth calculating means.
Determination means, a ninth determination means for determining the rotational speed of the compressor based on the determination result by the eighth determination means, and a ninth determination means.
A tenth determining means for determining the opening degree of the second throttle means from the determination result by the determining means; and an eleventh calculating means for calculating the opening degree of the second throttle means from the determination result by the tenth determining means. Computing means, and seventh control means for controlling the degree of opening of the second restricting means based on the result of computation by the eleventh computing means, the degree of opening of the first restricting means, the number of revolutions of the refrigerant conveying means. , The opening degree of the hot water flow adjusting means, the rotation speed of the hot water transport means, the rotation speed of the heat engine, the rotation speed of the compressor, and the second throttle means.

According to the present invention, an air conditioner capable of performing a low-capacity heating operation with small electric power is obtained.

Another means is that the refrigerant conveying means is provided with an auxiliary power means for obtaining power by using exhaust gas discharged from the heat engine.

According to the present invention, an air conditioner capable of performing low-capacity heating operation with low power and an air conditioner capable of performing simultaneous cooling and heating operation among a plurality of indoor units are obtained.

The other means includes an indoor heat exchanger having one end connected to a four-way valve and the other end connected to a first throttle means, and an indoor hot water heat exchanger through which cooling water conveyed from the hot water conveying means flows. It is an indoor unit provided with a vessel.

According to the present invention, an air conditioner capable of performing a dehumidifying operation without lowering the room temperature is obtained.

Another means is provided in a first storage means for storing and outputting the set temperature in the room, and in the indoor unit,
First temperature detecting means for detecting a room temperature, first calculating means for calculating a difference between a value detected by the first storage means and a value detected by the first temperature detecting means, and the first calculating means And fourth control means for controlling the degree of opening of the hot water flow rate adjusting means based on the result of calculation by the fourth calculating means. The configuration is such that the opening degree of the hot water flow rate adjusting means is controlled.

According to the present invention, an air conditioner capable of performing a dehumidifying operation without lowering the room temperature is obtained.

Another means is a fourth determining means for determining the degree of opening of the hot water flow rate adjusting means, and a fifth calculating means for calculating the number of revolutions of the hot water conveying means from the result of the determination by the fourth determining means. And a fourth control means for controlling the number of rotations of the hot water conveying means based on the result of the calculation by the fifth calculating means, wherein the opening degree of the hot water flow rate adjusting means and the number of rotations of the hot water conveying means are controlled. It is what it was. According to the present invention, an air conditioner capable of performing a dehumidifying operation without lowering the room temperature is obtained.

Another means is a plurality of indoor heat exchangers,
A plurality of indoor hot water heat exchangers, a plurality of first throttle means,
It is configured to include a plurality of hot water flow control valves.

According to the present invention, there is provided an air conditioner capable of performing simultaneous cooling and heating operations between a plurality of indoor units.

[0037]

BEST MODE FOR CARRYING OUT THE INVENTION The present invention has a structure in which the interior of a room can be heated by circulating a CFC-based refrigerant from which exhaust heat has been recovered using a refrigerant transfer means without using a compressor. When a normal heating operation or a low-load heating operation is performed in the air-conditioning apparatus configured as described above, the refrigerant discharged from the refrigerant conveying means recovers exhaust heat to make a high-temperature refrigerant. The high-temperature refrigerant having the exhaust heat is transported as it is by the refrigerant transport means, exchanges heat with the indoor air, and radiates the exhaust heat to heat the room. Thereafter, the refrigerant whose temperature has been lowered by the heat radiation returns to the refrigerant conveying means again and repeats the above operation. In this way, since heating is performed using exhaust heat of the heat engine without driving the compressor, a low-capacity heating operation can be performed while suppressing power consumption.

Further, a heat engine having a cooling water circuit cooled by the cooling water, a generator driven by the heat engine, a compressor for compressing the refrigerant, and piping connected to a discharge side of the compressor. A first flow path switching means, a second flow path switching means connected to the suction side of the compressor by piping, and a four-way pipe connected to one end of the first flow path switching means and one end of the second flow path switching means. A valve, an outdoor heat exchanger connected to one end of the four-way valve, a first throttle unit connected to the other end of the outdoor heat exchanger, and another end of the first flow path switching unit. An outdoor unit comprising a refrigerant conveying means connected to the other end of the second flow path switching means by piping; one end connected to a four-way valve by piping and the other end connected to the first throttle means by piping; An indoor unit including an indoor heat exchanger, wherein the refrigerant on the discharge side of the refrigerant conveying means and a heat machine And the cooling water is obtained by a configuration in which the outdoor hot water heat exchanger for heat exchange. In the air-conditioning apparatus configured as described above, when performing the normal heating operation or the heating operation at a low load, first, the first flow path switching unit is switched from the discharge side of the refrigerant conveying unit as switching of the direction of circulation of the refrigerant. The refrigerant is switched so that the refrigerant flows to the outdoor hot water heat exchanger, and the second flow path switching means is switched so that the refrigerant flows from the four-way valve to the suction side of the refrigerant conveying means,
The four-way valve switches so that the refrigerant flows from the outdoor hot water heat exchanger to the indoor heat exchanger, and the refrigerant flows from the outdoor heat exchanger to the second switching means. In this state, the refrigerant discharged from the refrigerant conveying means first exchanges heat with the hot water flowing out of the heat engine in the outdoor hot water heat exchanger, thereby recovering the exhaust heat of the heat engine to become a high-temperature refrigerant. The high-temperature refrigerant then flows into the indoor heat exchanger, where it exchanges heat with the indoor air, and radiates heat to the indoor air to heat the room. The refrigerant that has thus undergone heat exchange in the indoor heat exchanger then passes sequentially from the indoor heat exchanger to the first throttling means, the outdoor heat exchanger, the four-way valve, and the second flow path switching means, and It flows back into the means and repeats the above operation. In this manner, during the heating operation, the heating is performed by using the exhaust heat of the heat engine without driving the compressor, so that the low-capacity heating operation can be performed while suppressing the power consumption.

Further, an outdoor hot water heat exchanger is disposed on the discharge side of the refrigerant conveying means, a first flow path switching means is disposed between the four-way valve and the indoor heat exchanger, and a second flow path switching means is provided. Is disposed between the four-way valve and the outdoor heat exchanger, and the outdoor hot water heat exchanger and the refrigerant transfer means are provided between the other end of the first flow path switching means and the other end of the second flow path switching means. This is a configuration provided. In the air-conditioning apparatus configured as described above, when performing a normal heating operation or a heating operation at a low load, the first flow path switching unit first switches the direction of flow of the refrigerant from the outdoor hot water heat exchanger to the indoor. The refrigerant is switched so as to flow to the heat exchanger, and the second flow path switching means is switched so that the refrigerant flows from the outdoor heat exchanger to the suction side of the refrigerant conveying means.
In this state, the refrigerant discharged from the refrigerant conveying means first recovers exhaust heat of the heat engine by performing heat exchange with hot water flowing out of the heat engine in the outdoor hot water heat exchanger in the outdoor hot water heat exchanger. And becomes a high-temperature refrigerant. The high-temperature refrigerant then flows into the indoor heat exchanger, where it exchanges heat with the indoor air, and radiates heat to the indoor air to heat the room. The refrigerant that has exchanged heat in the indoor heat exchanger in this manner subsequently passes from the indoor heat exchanger to the first throttle unit, the outdoor heat exchanger, and the second flow path switching unit, and then returns to the refrigerant transfer unit. And the above operation is repeated.
In this way, during the heating operation, the interior of the room can be heated using the exhaust heat of the heat engine without driving the compressor, and the refrigerant circulates without passing through the four-way valve. Thus, low-capacity heating operation can be performed while suppressing power consumption.

Further, an outdoor hot water heat exchanger is disposed on the discharge side of the refrigerant conveying means, a first flow path switching means is disposed between the four-way valve and the indoor heat exchanger, and a second flow path switching means is provided. Is disposed between the outdoor heat exchanger and the first throttle means, and the outdoor hot water heat exchanger and the refrigerant transfer means are connected to the other end of the first flow path switching means and the other end of the second flow path switching means. This is a configuration provided between them. In the air conditioner configured as described above, when performing the normal heating operation or the heating operation at a low load, the first flow path switching unit causes the refrigerant to flow from the outdoor hot water heat exchanger to the indoor heat exchanger. And the second flow path switching means switches so that the refrigerant flows from the first throttle means to the refrigerant conveying means. In the refrigerant circuit in such a state, the refrigerant discharged from the refrigerant conveying means in the outdoor hot water heat exchanger,
It exchanges heat with the warm water flowing out of the heat engine and absorbs heat to become a high-temperature refrigerant. The high-temperature refrigerant flows into the indoor heat exchanger, exchanges heat with the indoor air in the indoor heat exchanger, and radiates heat to heat the room. After performing the heat exchange in the indoor heat exchanger as described above, the refrigerant sequentially passes from the indoor heat exchanger through the first throttle means and the second flow path switching means, flows into the refrigerant conveying means again, and performs the above operation. repeat. In this manner, when performing the normal heating operation or the heating operation at a low load, the heating operation is performed using the exhaust heat of the heat engine without driving the compressor, and the refrigerant is heated by the four-way valve and the outdoor heat. Since it does not pass through the exchanger, low-capacity heating operation can be performed while suppressing power consumption without being affected by the pressure loss of the four-way valve and the outdoor heat exchanger.

A third flow path switching means is provided between the outdoor heat exchanger and the second flow path switching means, and a fourth flow path is provided between the four-way valve and the first flow path switching means. A switching unit for exchanging heat between the refrigerant flowing between the second channel switching unit and the refrigerant conveying unit and the refrigerant flowing between the third channel switching unit and the fourth channel switching unit; A heat exchanger for refrigerant is provided, and a second throttle means is provided between the heat exchanger for refrigerant and the third flow path switching means. In the air conditioner configured as described above, when performing the normal heating operation or the heating operation at a low load, the first flow path switching unit causes the refrigerant to flow from the outdoor hot water heat exchanger to the indoor heat exchanger. The second flow path switching means is switched so that the refrigerant flows from the first throttle means to the inter-refrigerant heat exchanger, and the third flow path switching means is switched from the outdoor heat exchanger to the second throttle means. The fourth flow path switching means switches so that the refrigerant flows from the inter-refrigerant heat exchanger to the four-way valve, and the four-way valve switches the refrigerant from the discharge side of the compressor to the outdoor heat exchanger. The flow is switched so that the refrigerant flows from the fourth flow path switching means to the suction side of the compressor. The refrigerant discharged from the refrigerant conveying means in the refrigerant circuit in such a state exchanges heat with the hot water flowing out of the heat engine in the outdoor hot water heat exchanger and absorbs heat to become a high-temperature refrigerant. This high-temperature refrigerant passes through the first refrigerant switching means, flows into the indoor heat exchanger,
The indoor heat exchanger heats the room by exchanging heat with the indoor air to radiate heat. After performing the heat exchange in the indoor heat exchanger in this manner, the refrigerant flows from the indoor heat exchanger to the first heat exchanger.
And then flows into the inter-refrigerant heat exchanger. On the other hand, the high-temperature and high-pressure refrigerant discharged from the compressor passes through the four-way valve, flows into the outdoor heat exchanger, exchanges heat with the outside air in the outdoor heat exchanger, releases heat, and condenses. The condensed refrigerant passes from the outdoor heat exchanger through the third flow path switching means, passes through the second throttle means, and
When passing through the throttle means, the refrigerant becomes low-temperature and low-pressure refrigerant and flows into the inter-refrigerant heat exchanger. The refrigerant that has flowed into the inter-refrigerant heat exchanger from the second flow path switching means and the refrigerant that has flowed into the inter-refrigerant heat exchanger from the second throttle means perform heat exchange in the inter-refrigerant heat exchanger. The refrigerant that has flowed into the inter-refrigerant heat exchanger from the path switching means is cooled by the heat absorbing action of the refrigerant that has flowed into the refrigerant pipe heat exchanger from the second throttle means, and flows again into the refrigerant conveying means. The refrigerant flowing from the means into the inter-refrigerant heat exchanger sequentially passes through the fourth flow path switching means and the four-way valve, flows into the compressor again, and repeats the above operation. In this manner, when performing the normal heating operation or the heating operation at the time of a low load, the suction side refrigerant of the refrigerant conveyance unit is cooled so as to be always a liquid refrigerant, so that the efficiency of the refrigerant conveyance unit can be prevented from decreasing. it can.

Further, a turbo engine is provided as a heat engine, and intake air cooling for exchanging heat between the intake side air of the turbo engine and the refrigerant flowing between the third flow path switching means and the fourth flow path switching means. This is a configuration provided with a heat exchanger. In the air conditioner configured as described above,
When performing the normal heating operation or the heating operation at the time of low load, the first flow path switching means switches so that the refrigerant flows from the outdoor hot water heat exchanger to the indoor heat exchanger, and the second flow path switching means The third flow path switching means is switched so that the refrigerant flows from the first throttle means to the intake cooling heat exchanger, and the third flow path switching means is switched such that the refrigerant flows from the outdoor heat exchanger to the second throttle means. The flow path switching means switches so that the refrigerant flows from the intake cooling heat exchanger to the four-way valve, the four-way valve allows the refrigerant to flow through the outdoor heat exchanger from the discharge side of the compressor, and The switching is performed so that the refrigerant flows to the suction side of the compressor. In the refrigerant circuit in such a state, the refrigerant discharged from the refrigerant conveying means exchanges heat with the hot water flowing out of the heat engine in the outdoor hot water heat exchanger and absorbs heat to become a high-temperature refrigerant. The high-temperature refrigerant passes through the first flow path switching means, flows into the indoor heat exchanger, exchanges heat with indoor air in the indoor heat exchanger, and radiates heat to heat the room. After performing the heat exchange in the indoor heat exchanger as described above, the refrigerant sequentially passes from the indoor heat exchanger through the first throttle unit and the second flow path switching unit, and flows into the intake cooling heat exchanger. On the other hand, the high-temperature and high-pressure refrigerant discharged from the compressor passes through the four-way valve, flows into the outdoor heat exchanger, exchanges heat with the outside air in the outdoor heat exchanger, releases heat, and condenses. After performing the heat exchange in the outdoor heat exchanger in this manner, the refrigerant passes from the outdoor heat exchanger, passes through the third flow path switching unit, passes through the second throttle unit, and passes through the second throttle unit. At this time, the refrigerant becomes a low-temperature low-pressure refrigerant and flows into the intake cooling heat exchanger. The air on the intake side of the turbo engine passes through the intake cooling heat exchanger and flows into the turbo engine. Then, in the intake cooling heat exchanger, the refrigerant flowing into the intake cooling heat exchanger from the second flow path switching means exchanges heat with the refrigerant flowing into the intake cooling heat exchanger from the second throttle means, and The refrigerant flowing from the throttle means into the intake cooling heat exchanger is cooled by the endothermic action of the refrigerant and flows into the refrigerant conveying means, and the air on the intake side of the turbo engine flows from the second flow path switching means into the intake cooling heat exchanger. After the heat exchange with the refrigerant, the second throttle means exchanges heat with the refrigerant flowing into the intake cooling heat exchanger, and the refrigerant flows from the second throttle means into the intake cooling heat exchanger to be cooled by heat absorption. As a result, the specific weight of the air becomes larger than that before the air flows into the intake cooling heat exchanger, and is sucked into the turbo engine. The refrigerant flowing from the second throttle means into the intake air cooling heat exchanger sequentially passes through the fourth flow path switching means and the four-way valve, flows into the compressor, and repeats the above operation. In this way, the air on the intake side of the turbo engine is heat-exchanged with the refrigerant and cooled by utilizing the heat of evaporation of the refrigerant, thereby increasing the specific weight of the air on the intake side of the turbo engine, thereby increasing the efficiency of the turbo engine. Can be improved.

Also, a plurality of first throttling means and a plurality of indoor heat exchangers are provided, and a plurality of fifth flow path switching means are provided between the plurality of first throttling means and the second flow path switching means. And a sixth flow path switching means between the plurality of indoor heat exchangers and the first flow path switching means, and a plurality of pipes between the outdoor heat exchanger and the second flow path switching means. And the piping between the first flow path switching means and the four-way valve is branched and connected to a plurality of sixth flow path switching means. In the air conditioner configured as described above, when cooling and heating are simultaneously performed among a plurality of indoor units, the first flow path switching means transmits the refrigerant from the outdoor hot water heat exchanger to the sixth flow path switching means. Is switched to flow, and the second flow path switching means is switched to flow the refrigerant from the fifth flow path switching means to the refrigerant conveying means, and is connected to the indoor unit performing the cooling operation and the first throttle means. The connected fifth flow path switching unit is configured to connect the first heat exchanger to the first heat exchanger.
The refrigerant is switched so as to flow to the first throttle means, and the fifth flow path switching means connected to the indoor unit performing the heating operation via the first throttle means is connected to the second flow from the first throttle means. It is switched so that the refrigerant flows to the path switching means,
The sixth flow path switching means connected to the indoor unit performing the cooling operation switches so that the refrigerant flows from the indoor unit to the four-way valve, and the sixth flow path switching connected to the indoor unit performing the heating operation The means is switched so that the refrigerant flows from the first flow path switching means to the indoor unit. The four-way valve flows the refrigerant from the discharge side of the compressor to the outdoor heat exchanger. The switching is performed so that the refrigerant flows to the suction side of the compressor. In the refrigerant circuit in such a state, the refrigerant discharged from the refrigerant conveying means exchanges heat with the hot water flowing out of the heat engine in the outdoor hot water heat exchanger and absorbs heat to become a high-temperature refrigerant. The high-temperature refrigerant passes through the first flow path switching unit, passes through the sixth flow path switching unit whose flow path is switched to the indoor unit that performs the heating operation, and is mounted on the indoor unit that performs the heating operation. The air flows into the indoor heat exchanger and exchanges heat with indoor air in the indoor heat exchanger to radiate heat, thereby heating the room. After performing heat exchange in the indoor heat exchanger, the refrigerant sequentially passes from the indoor heat exchanger through the first throttle means, the fifth flow path switching means, and the second flow path switching means, and flows into the refrigerant conveying means. I do. On the other hand, the high-temperature and high-pressure refrigerant discharged from the compressor passes through the four-way valve, flows into the outdoor heat exchanger, exchanges heat with the outside air in the outdoor heat exchanger, releases heat, and condenses. After performing the heat exchange in the outdoor heat exchanger as described above, the refrigerant passes through the fifth flow path switching unit that is switched from the outdoor heat exchanger to the indoor unit that performs the cooling operation, and passes through the second throttle unit. When passing through the second throttle means, it becomes a low-temperature low-pressure refrigerant and flows into an indoor heat exchanger mounted on an indoor unit performing a cooling operation,
The indoor heat exchanger exchanges heat with indoor air and absorbs heat to cool the room. The refrigerant that has exchanged heat in the indoor heat exchanger sequentially passes through the sixth flow path switching means and the four-way valve, and flows into the compressor. In this manner, the heating circuit using the exhaust heat of the heat engine and the cooling circuit as a normal heat pump are switched between the first flow path and the second flow path switching means.
Since the fifth flow path switching means and the sixth flow path switching means are made independent by switching, cooling and heating can be simultaneously operated between a plurality of indoor units.

Further, the apparatus is provided with a control means for performing a heating operation appropriately in accordance with the indoor load so that the heating capacity can be increased or decreased in accordance with the temperature difference between the set temperature and the indoor temperature. In the above configuration, the set temperature and the room temperature are taken in. If the room temperature is lower than the set temperature, the heating capacity is insufficient, so the heating capacity is controlled to be further increased. Conversely, if the room temperature is higher than the set temperature, the heating capacity is excessive, so that the heating capacity is controlled to decrease. In this manner, the temperature difference between the set temperature and the room temperature is calculated, and the heating capacity can be increased or decreased in accordance with the temperature difference, so that the heating operation can be performed appropriately according to the load based on the room set temperature. .

Further, first storage means for storing and outputting the indoor set temperature, first temperature detection means provided in the indoor unit for detecting the indoor temperature, and a value detected by the first storage means and the first storage means. A first calculating means for calculating a difference between the detected value by the temperature detecting means, a first determining means for determining a result of the calculation by the first calculating means, and a first determining means for determining a calculation result by the first determining means. A second judging means for judging the degree of opening of the first throttling means, a second calculating means for calculating the degree of opening of the first throttling means from the judgment result by the second judging means; First control means for controlling the throttle opening of the first throttle means based on the calculation result of the calculation means, and third calculation means for calculating the rotation speed of the refrigerant transport means based on the determination result by the second determination means. From the calculation result by the third calculation means. Is obtained by a structure in which a second control means for controlling the rotational speed of the unit. In the above configuration, the first calculating means calculates the temperature difference between the set temperature stored by the first storing means and the room temperature detected by the first temperature detecting means, and determines whether the calculated result is positive or negative. The calculation result is determined by the first determination means. If the result of the calculation by the first calculating means is positive, it is determined by the second determining means whether or not the aperture of the first throttle means is maximum;
As a result, when the throttle opening of the first throttle means is the maximum, the rotation speed of the refrigerant conveyance means is calculated by the third calculation means, and the rotation speed of the refrigerant conveyance means is calculated from the calculation result by the second control means. To increase. If the first throttle opening is not the maximum, the throttle opening of the first throttle means is calculated by the second calculating means, and the throttle opening of the first throttle means is calculated based on the calculation result. Increased by control means. On the other hand, if the result of the calculation by the first calculating means is negative, it is determined by the second determining means whether or not the first throttle means has the smallest opening degree. Is the minimum, the rotation speed of the refrigerant transfer means is calculated by the third calculation means, and the rotation number of the refrigerant transfer means is reduced by the second control means from the calculation result. If the aperture of the first aperture is not the minimum, the aperture of the first aperture is calculated by the second calculating means, and from this calculation result, the aperture of the first aperture is calculated. Is reduced by the first control means. In this way, the temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated, and the heating capacity can be increased or decreased in accordance with this temperature difference. Since the opening degree of the throttle means, the number of revolutions of the refrigerant conveying means, and the opening degree of the hot water flow rate adjusting means can be increased or decreased, the heating operation can be accurately performed according to the load based on the set temperature in the room. .

The cooling water circuit of the heat engine includes a hot water flow rate adjusting means, a hot water conveying means, a hot water heat exchanger, a cooling heat exchanger, and a blowing means for blowing air to the cooling heat exchanger. A third judging means for judging the rotation speed of the refrigerant conveying means from the judgment result by the second judging means, and a fourth judging means for calculating the opening of the hot water flow rate adjusting means from the judgment result by the third judging means. The configuration is provided with a calculating means and a third control means for controlling the opening of the hot water flow rate adjusting means based on the calculation result by the fourth calculating means. In the above configuration, the first calculating means calculates a temperature difference between the set temperature stored by the first storing means and the room temperature detected by the first temperature detecting means. The positive / negative of the operation result is determined by the first determining means.
If the result of the calculation by the first calculating means is positive, then the second determining means determines whether or not the first throttle means has the maximum aperture opening. When the opening degree is the maximum, it is further determined whether or not the rotation speed of the refrigerant conveying means is the maximum by the third determining means. As a result, when the rotation speed of the refrigerant conveying means is the maximum, The opening degree is calculated by the fourth calculating means, and the opening degree of the hot water flow rate adjusting means is increased by the third control means based on the calculation result. If the rotational speed of the refrigerant transporting means is not the maximum, the rotational speed of the refrigerant transporting means is calculated by the third calculating means, and the rotational speed of the refrigerant transporting means is increased by the second control means based on the calculation result. If the aperture of the first aperture is not the maximum, the aperture of the first aperture is calculated by the second calculator, and the aperture of the first aperture is calculated from the calculation result. Increased by the first control means. On the other hand, when the determination of the first calculation result is negative, first, the second determination unit determines whether the aperture of the first aperture unit is minimum, and as a result, the aperture of the first aperture unit is determined. If the opening degree is the minimum, it is further determined by the third determination means whether the rotation speed of the refrigerant transport means is the minimum, and as a result, if the rotation speed of the refrigerant transport means is the minimum, The opening degree is calculated by the fourth calculating means, and the opening degree of the hot water flow rate adjusting means is reduced by the third control means based on the calculation result. If the number of revolutions of the refrigerant conveying means is not the minimum, the number of revolutions of the refrigerant conveying means is calculated by the third calculating means, and the number of revolutions of the refrigerant conveying means is reduced by the second control means based on the calculation result. If the opening degree of the first throttle means is not the minimum, the opening degree of the first throttle means is calculated by the second calculating means.
The throttle opening of the throttle means is reduced by the first control means. In this manner, the temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated, and the first heating means can increase or decrease the heating capacity in accordance with this temperature difference. The opening degree of the throttle means, the number of revolutions of the refrigerant conveying means, and the opening degree of the hot water flow rate adjusting means can be increased or decreased, so that the heating operation can be accurately performed according to the load based on the set temperature in the room.

Further, fourth determining means for determining the opening of the hot water flow rate adjusting means based on the determination result by the third determining means,
Fifth calculating means for calculating the number of rotations of the hot water conveying means from the result of the determination by the fourth determining means, and fourth control means for controlling the number of rotations of the hot water conveying means from the result of the calculation by the fifth calculating means. And a configuration provided with: In the above configuration, the first calculating means calculates the temperature difference between the set temperature stored by the first storing means and the room temperature detected by the first temperature detecting means, and determines whether the calculated result is positive or negative. The determination is made by the first determination means. If the first
If the result of the calculation by the calculation means is positive, then the second determination means determines whether or not the first throttle means has the maximum aperture. As a result, the first throttle means has a maximum aperture. When the rotation speed of the refrigerant transporting means is maximum, the third determining means determines whether the rotation speed of the refrigerant transporting means is maximum. As a result, when the rotation speed of the refrigerant transporting means is maximum, the opening degree of the hot water flow rate adjusting means is determined. The fourth determining means determines whether or not it is the maximum. As a result, when the opening of the hot water flow rate adjusting means is the maximum, the rotation speed of the hot water conveying means is calculated by the fifth calculating means, and from the calculation result, The number of revolutions of the hot water conveying means is increased by the fourth control means. If the opening degree of the hot water flow rate adjusting means is not the maximum, the opening degree of the hot water flow rate adjusting means is calculated by the fourth calculating means, and the opening degree of the hot water flow rate adjusting means is increased by the third control means from the calculation result. Let it. If the rotation speed of the refrigerant transfer means is not the maximum, the rotation speed of the refrigerant transfer means is calculated by the third calculation means, and the calculation result is increased by the second control means. When the aperture of the first aperture is not the maximum, the aperture of the first aperture is calculated by the second calculator, and the aperture of the first aperture is calculated from the calculation result. First
Control means. On the other hand, when the determination of the first calculation result is negative, the second determination unit determines whether the aperture of the first aperture unit is minimum, and as a result,
If the throttle opening of the throttle means is the minimum, the third determination means determines whether the rotation speed of the refrigerant transport means is the minimum. As a result, if the rotation speed of the refrigerant transport means is the minimum, the flow rate of the hot water is determined. The fourth determining means determines whether the opening degree of the adjusting means is the minimum. If the opening degree of the hot water flow rate adjusting means is the minimum as a result, the rotation number of the hot water conveying means is calculated by the fifth calculating means. Then, the rotation speed of the hot water conveying means is reduced by the fourth control means from the calculation result. If the opening degree of the hot water flow rate adjusting means is not the minimum, the opening degree of the hot water flow rate adjusting means is calculated by the fourth calculating means, and from the calculation result, the opening degree of the hot water flow rate adjusting means is calculated by the third control means. Decrease. If the number of revolutions of the refrigerant conveying means is not the minimum, the number of revolutions of the refrigerant conveying means is calculated by the third calculating means.
Control means. If the throttle opening is not the minimum, the throttle opening of the first throttle means is calculated by the second calculating means, and the throttle opening of the first throttle means is calculated from the calculation result by the first control means. To reduce. The set temperature stored by the first storage means and the first
The temperature difference from the room temperature detected by the temperature detecting means is calculated, and the opening degree of the first restricting means, the rotation speed of the refrigerant conveying means, the flow rate of hot water are adjusted so that the heating capacity can be increased or decreased in accordance with the temperature difference. Since the degree of opening of the adjusting means and the number of revolutions of the hot water conveying means can be increased or decreased, the heating operation can be accurately performed according to the load based on the set temperature in the room.

A fifth judging means for judging the rotation speed of the hot water conveying means from the judgment result by the fourth judging means and a sixth judging means for calculating the rotation speed of the heat engine from the judgment result by the fifth judging means. And a fifth control means for controlling the number of revolutions of the heat engine based on the calculation result of the sixth calculation means. In the above configuration, the first calculating means calculates the temperature difference between the set temperature stored by the first storing means and the room temperature detected by the first temperature detecting means, and determines whether the calculated result is positive or negative. 1
Is determined by the determining means. If the result of the calculation by the first calculating means is positive, then the second determining means determines whether or not the first throttle means has the maximum aperture opening. When the opening degree is the maximum, it is further determined whether or not the rotation speed of the refrigerant conveying means is the maximum by the third determining means. As a result, when the rotation speed of the refrigerant conveying means is the maximum, The fourth determining means determines whether the opening degree is the maximum. As a result, when the opening degree of the hot water flow rate adjusting means is the maximum, the fifth determining means determines whether the rotation speed of the hot water conveying means is the maximum. If the result is that the rotation speed of the hot water conveying means is the maximum, the rotation speed of the heat engine is calculated by the sixth calculation means, and the rotation speed of the heat engine is increased by the fifth control means from the calculation result. Let it. If the rotation speed of the hot water transfer means is not the maximum, the rotation speed of the hot water transfer means is calculated by the fifth calculation means, and the rotation speed of the hot water transfer means is increased by the fourth control means based on the calculation result. If the opening degree of the hot water flow rate adjusting means is not the maximum, the opening degree of the hot water flow rate adjusting means is calculated by the fourth calculating means, and the opening degree of the hot water flow rate adjusting means is calculated by the third control means from the calculation result. Increase. If the number of revolutions of the refrigerant transporting means is not the maximum, the number of revolutions of the refrigerant transporting means is calculated by the third calculating means, and from the calculation result, the number of revolutions of the refrigerant transporting means is increased by the second control means. If the opening degree of the first throttle means is not the maximum, the opening degree of the first throttle means is calculated by the second calculating means, and from the calculation result, the opening degree of the first throttle means is calculated. Is increased by the first control means. On the other hand, if the determination of the first calculation result is negative, the second determination means determines whether or not the aperture of the first aperture means is minimum. As a result, the aperture of the first aperture means is determined. If the degree is the minimum, it is determined by the third determining means whether the rotation speed of the refrigerant conveying means is the minimum, and as a result, if the rotation number of the refrigerant conveying means is the minimum, the opening degree of the hot water flow rate adjusting means is 4th is the least
When the opening degree of the hot water flow rate adjusting means is the minimum, the fifth determining means determines whether the rotation speed of the hot water conveying means is the minimum, and as a result, When the rotation speed is the minimum, the rotation speed of the heat engine is calculated by the sixth calculation means, and the rotation speed of the heat engine is reduced by the fifth control means from the calculation result. If the number of revolutions of the hot water conveying means is not the minimum, the number of revolutions of the hot water conveying means is calculated by the fifth calculating means, and the number of revolutions of the hot water conveying means is reduced by the fourth control means based on the calculation result. If the opening degree of the hot water flow rate adjusting means is not the minimum, the opening degree of the hot water flow rate adjusting means is calculated by the fourth calculating means, and from the calculation result, the opening degree of the hot water flow rate adjusting means is calculated by the third control means. Decrease. If the number of revolutions of the refrigerant transporting means is not the minimum, the number of revolutions of the refrigerant transporting means is calculated by the third calculating means, and the number of revolutions of the refrigerant transporting means is reduced by the second control means from the calculation result. If the aperture of the first aperture is not the minimum, the aperture of the first aperture is calculated by the second calculator, and the aperture of the first aperture is calculated from the calculation result. It is reduced by one control means. In this way, the temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated, and the heating capacity can be increased or decreased in accordance with this temperature difference. (1) Since the throttle opening degree of the throttle means, the rotation speed of the refrigerant transport means, the opening degree of the hot water flow rate adjusting means, the rotation speed of the hot water transport means and the rotation speed of the heat engine can be increased or decreased, the indoor setting can be accurately performed. The heating operation according to the load depending on the temperature can be performed.

Further, sixth determining means for determining the number of revolutions of the heat engine based on the determination result by the fifth determining means,
And a sixth control means for controlling the number of rotations of the compressor based on the result of calculation by the seventh calculation means. It is what it was. In the above configuration, the first calculating means calculates the temperature difference between the set temperature stored by the first storing means and the room temperature detected by the first temperature detecting means, and determines whether the calculated result is positive or negative. The determination is made by the first determination means. If the result of the calculation by the first calculating means is positive, then the second determining means determines whether or not the first throttle means has the maximum aperture opening. When the opening degree is the maximum, it is further determined whether or not the rotation speed of the refrigerant conveying means is the maximum by the third determining means. As a result, when the rotation speed of the refrigerant conveying means is the maximum, Determine if the opening is the maximum
If the opening degree of the hot water flow rate adjusting means is the maximum, the fifth determining means determines whether the rotation speed of the hot water conveying means is the maximum, and as a result, When the rotation speed is the maximum, the sixth determination unit determines whether the rotation speed of the heat engine is the maximum,
As a result, when the rotation speed of the heat engine is the maximum, the compressor is driven, and the rotation speed of the compressor is calculated by the seventh calculation means.
From the calculation result, the rotation speed of the compressor is increased by the sixth control means. If the number of revolutions of the heat engine is not the maximum, the number of revolutions of the heat engine is calculated by the sixth calculating means, and the number of revolutions of the heat engine is increased by the fifth control means from the calculation result. If the rotation speed of the hot water transfer means is not the maximum, the rotation speed of the hot water transfer means is calculated by the fifth calculation means, and the rotation speed of the hot water transfer means is increased by the fourth control means from the calculation result. . If the opening degree of the hot water flow rate adjusting means is not the maximum, the opening degree of the hot water flow rate adjusting means is calculated by the fourth calculating means, and the opening degree of the hot water flow rate adjusting means is calculated by the third control means from the calculation result. Increase. If the number of revolutions of the refrigerant transporting means is not the maximum, the number of revolutions of the refrigerant transporting means is calculated by the third calculating means, and from the calculation result, the number of revolutions of the refrigerant transporting means is increased by the second control means. If the opening degree of the first throttle means is not the maximum, the opening degree of the first throttle means is calculated by the second calculating means, and from the calculation result, the opening degree of the first throttle means is calculated. Is increased by the first control means. On the other hand, if the determination of the first calculation result is negative, the first
The second determination means determines whether the throttle opening of the first throttle means is the minimum. As a result, when the throttle opening of the first throttle means is the minimum, the rotation speed of the refrigerant conveying means is the minimum. Is determined by the third determining means. If the rotation speed of the refrigerant conveying means is the minimum, the fourth determining means determines whether the opening of the hot water flow rate adjusting means is the minimum. When the opening degree of the flow rate adjusting means is the minimum, the fifth judging means judges whether the rotation speed of the hot water conveying means is the minimum. As a result, when the rotation speed of the hot water conveying means is the minimum, the compressor The rotation speed of the compressor is calculated by the seventh calculation means, and the rotation speed of the compressor is reduced by the sixth control means from the calculation result. If the number of revolutions of the heat engine is not the minimum, the number of revolutions of the heat engine is calculated by the sixth calculating means, and the number of revolutions of the heat engine is reduced by the fifth control means from the calculation result. If the number of revolutions of the hot water conveying means is not the minimum, the number of revolutions of the hot water conveying means is calculated by the fifth calculating means, and the number of revolutions of the hot water conveying means is reduced by the fourth control means from the calculation result. . If the opening degree of the hot water flow rate adjusting means is not the minimum, the opening degree of the hot water flow rate adjusting means is calculated by the fourth calculating means, and from the calculation result, the opening degree of the hot water flow rate adjusting means is calculated by the third control means. Decrease.
If the number of revolutions of the refrigerant transporting means is not the minimum, the number of revolutions of the refrigerant transporting means is calculated by the third calculating means, and the number of revolutions of the refrigerant transporting means is reduced by the second control means from the calculation result. If the aperture of the first aperture is not the minimum, the aperture of the first aperture is calculated by the second calculator, and the aperture of the first aperture is calculated from the calculation result. It is reduced by one control means. In this way, the temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated, and the heating capacity can be increased or decreased in accordance with this temperature difference. 1, the opening degree of the throttle means, the rotation speed of the refrigerant conveyance means, the opening degree of the hot water flow rate adjustment means, the rotation speed of the hot water conveyance means,
Since the number of revolutions of the heat engine and the number of revolutions of the compressor can be increased or decreased, the heating operation can be accurately performed according to the load based on the set temperature in the room.

Further, a second temperature detecting means for detecting a refrigerant temperature and a first pressure detecting means for detecting a refrigerant pressure are provided between the second flow path switching means and the inter-refrigerant heat exchanger. Eighth temperature calculating means for calculating the saturation temperature of the refrigerant from the result of detection by the first pressure detecting means, comprising third temperature detecting means for detecting the temperature of the refrigerant between the throttle means and the heat exchanger between refrigerants. A ninth calculating means for calculating a difference between a calculation result by the eighth calculating means and a detection result by the second temperature detecting means; and a ninth calculating means for determining a state of the refrigerant from the calculation result by the ninth calculating means. And a first calculating means for calculating a difference between a detection result obtained by the third temperature detecting means and a detection result obtained by the second temperature detecting means based on the judgment result obtained by the seventh judging means.
0, an eighth judging means for judging the temperature difference between the refrigerants based on the calculation result by the tenth calculating means, and a eighth judging means for judging the rotational speed of the compressor from the judgment result by the eighth judging means. Nineth determination means, tenth determination means for determining the opening degree of the second throttle means based on the determination result by the ninth determination means, and second determination means based on the determination result by the tenth determination means. An eleventh calculating means for calculating the opening degree and a seventh control means for controlling the opening degree of the second throttle means based on the calculation result by the eleventh calculating means are provided. In the above configuration, first, the saturation temperature of the refrigerant flowing through the inter-refrigerant heat exchanger and flowing into the refrigerant conveying means is calculated by the eighth calculating means from the pressure detected by the first pressure detecting means. The temperature difference between the saturation temperature obtained as a result and the refrigerant temperature detected by the second temperature detecting means is calculated by the ninth calculating means, and the sign of the calculation result is determined by the seventh determining means. If the calculation result by the ninth calculation means is negative, the temperature of the refrigerant in the portion flowing through the inter-refrigerant heat exchanger and flowing into the refrigerant conveyance means, detected by the second temperature detection means, The difference in the temperature of the refrigerant in the portion passing through the second restrictor and flowing into the inter-refrigerant heat exchanger, detected by the temperature detector of
Is calculated by the calculating means. Then, the positive / negative of the refrigerant temperature difference is determined by the fifth determining means from the result of the calculation by the tenth calculating means. If the result of the determination by the fifth determining means is negative, it is determined by the ninth determining means whether the rotational speed of the compressor is the maximum. If the result is that the rotational speed of the compressor is not the maximum, the second determination is made. The tenth determination means determines whether or not the opening degree of the throttle means is maximum. If the opening degree of the second throttle means is not maximum, the opening degree of the second throttle means is determined by the eleventh calculation means. And calculate the seventh from the calculation result.
Control means increases the opening of the second throttle means.
If the opening degree of the second throttle means is maximum, the rotation speed of the compressor is calculated by the seventh calculation means, and from the calculation result, the rotation speed of the compressor is increased by the sixth control means. If the rotational speed of the compressor is the maximum, the rotational speed of the refrigerant transporting means is calculated by the third arithmetic means, and the rotational speed of the refrigerant transporting means is reduced by the second control means from the calculation result. On the other hand, when the determination result of the fifth determination means is positive,
Alternatively, if the result of the determination by the seventh determining means is positive, the calculation returns to the detection by the first pressure detecting means, and the calculation of the saturation temperature of the refrigerant is started again by the eighth calculating means. The degree of supercooling of the refrigerant obtained by calculating the difference between the saturation temperature of the refrigerant flowing into the refrigerant conveying means calculated by the eighth calculating means and the temperature detected by the second temperature detecting means, The temperature difference between the temperature of the cooling refrigerant detected by the temperature detecting means and the temperature of the refrigerant to be cooled is determined, and the degree of supercooling of the refrigerant, but the degree of opening of the second restricting means to be positive, Since the number of revolutions of the compressor and the number of revolutions of the refrigerant conveying means can be increased or decreased, it is possible to prevent a decrease in the efficiency of the refrigerant conveying means. Further, the refrigerant transfer means is provided with an auxiliary power means for obtaining power using exhaust gas discharged from the heat engine. In the air-conditioning apparatus configured as described above, when performing the normal heating operation or the heating operation at a low load, the exhaust gas discharged from the heat engine drives the auxiliary power means connected to the refrigerant conveyance means to perform the refrigerant conveyance. The device discharges refrigerant by the power obtained by this auxiliary power means,
Circulate refrigerant. In this manner, when performing the normal heating operation or the heating operation at the time of a low load, the heating operation is performed by using the exhaust heat of the heat engine without driving the compressor, and the driving power of the refrigerant transfer unit is assisted. Since the driving load is reduced by using the exhaust of the heat engine by the power means to assist, the power consumption of the refrigerant conveying means can be suppressed.

Also, a hot water flow rate adjusting means is provided in the cooling water circuit,
A heat engine having a hot water conveying device, a heat exchanger for hot water, a heat exchanger for cooling, and blowing means for blowing air to the heat exchanger for cooling, a generator driven by the heat engine, and a refrigerant A four-way valve connected to the discharge and suction sides of the compressor, an outdoor heat exchanger connected to one end of the four-way valve, and a pipe connected to the other end of the outdoor heat exchanger. An outdoor unit having a first throttle unit connected thereto, an indoor heat exchanger having one end connected to the four-way valve by piping and the other end connected to the first throttle unit, and transported from the hot water transport unit. And an indoor unit including an indoor hot water heat exchanger through which the cooling water flows. In the air conditioner configured as described above, when performing the dehumidifying operation, the four-way valve allows the refrigerant to flow from the discharge side of the compressor to the outdoor heat exchanger, and from the indoor heat exchanger to the suction side of the compressor. It is switched so that the refrigerant flows. In the refrigerant circuit in such a state, the high-temperature and high-pressure refrigerant discharged from the compressor passes through the four-way valve, flows into the outdoor heat exchanger, exchanges heat with the outside air in the outdoor heat exchanger, releases heat, and condenses. After performing the heat exchange in the outdoor heat exchanger in this way, the refrigerant passes through the first throttle means,
When passing through the throttle means, the refrigerant becomes low-temperature and low-pressure refrigerant, flows into the indoor heat exchanger, exchanges heat with indoor air in the indoor heat exchanger, and absorbs heat to cool the indoor air. During this cooling process, the air is dehumidified. After performing heat exchange in the indoor heat exchanger, the refrigerant passes through the four-way valve and flows into the compressor. On the other hand, the high-temperature cooling water that has absorbed the heat of the heat engine discharged by the hot water conveying means and passed through the hot water flow rate adjusting means, flows into the indoor hot water heat exchanger, and is cooled by passing through the indoor heat exchanger. By exchanging heat with the heated air and radiating heat, the air cooled in the dehumidification process is warmed. After performing heat exchange in the indoor hot water heat exchanger, the cooling water flows into the heat engine. In this way, the indoor air that has absorbed and dehumidified by the indoor heat exchanger as the evaporator of the heat pump can be heated by radiating hot water in the outdoor hot water heat exchanger as a cooling circuit of the heat engine. The dehumidifying operation can be performed without lowering the room temperature.

Further, a first storage means for storing and outputting the indoor set temperature, a first temperature detection means provided in the indoor unit for detecting the indoor temperature, a value detected by the first storage means and A first calculating means for calculating a difference from a value detected by the first temperature detecting means, a fourth calculating means for calculating an opening degree of the hot water flow rate adjusting means based on a calculation result by the first calculating means, Third control means for controlling the degree of opening of the hot water flow rate adjusting means based on the calculation result of the calculating means of No. 4. The temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated by the first calculation means, and the degree of opening of the hot water flow rate adjustment means is calculated based on the calculation result. The opening degree of the hot water flow rate adjusting means is increased by the third control means if the first arithmetic result is positive, and the opening degree of the hot water flow rate adjusting means is increased if the first arithmetic result is negative by the third controlling means. Control is performed to decrease the opening of the flow rate adjusting means. Thus the first
Calculates the temperature difference between the set temperature stored by the storage means and the room temperature detected by the first temperature detection means, and increases or decreases the opening degree of the hot water flow rate adjustment means so that the heating capacity can be increased or decreased in accordance with this temperature difference. Therefore, it is possible to perform the dehumidifying operation while suppressing the change in the room temperature.

Further, fourth determining means for determining the degree of opening of the hot water flow rate adjusting means, fifth calculating means for calculating the number of revolutions of the hot water conveying means based on the result of determination by the fourth determining means, And a fourth control means for controlling the number of revolutions of the hot water conveying means based on the calculation result of the calculation means of No. 5. The temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated by the first calculation means, and the opening degree of the hot water flow rate adjustment means is calculated by the fourth determination means. Judge whether it is the maximum,
When the opening degree of the hot water flow adjusting means is the maximum, the rotation speed of the hot water transport means is calculated by the fifth arithmetic means, and the rotation speed of the hot water transport means is calculated by the fourth control means from the calculation result. Is positive, the rotation speed of the hot water transport means is increased, and if negative, the rotation speed of the hot water transport means is controlled to decrease.If the opening degree of the refrigerant flow rate adjustment means is not the maximum, the hot water flow rate adjustment means The opening is calculated by a fourth calculating means,
The opening degree of the hot water flow rate adjusting means is increased by the third control means when the first arithmetic result is positive, and the opening degree of the hot water flow rate adjusting means is increased by the third control means when the first arithmetic result is negative. Control to decrease. The temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated, and the hot water flow rate is adjusted so that the heating capacity can be increased or decreased in accordance with the temperature difference. Since the opening degree of the means and the number of revolutions of the hot water conveying means can be increased or decreased, the change in the room temperature can be suppressed with high accuracy and the dehumidifying operation can be performed.

Further, the apparatus comprises a plurality of indoor heat exchangers, a plurality of indoor hot water heat exchangers, a plurality of first throttling means, and a plurality of hot water flow control valves. In the air conditioner configured as described above, when cooling and heating are simultaneously performed between a plurality of indoor units, the hot water flow rate adjustment connected to the indoor hot water heat exchanger provided in the indoor unit performing the cooling operation The means is fully closed, the first throttle means connected to the indoor heat exchanger provided in the indoor unit performing the heating operation is fully closed, and the four-way valve is connected to the outdoor heat exchanger from the discharge side of the compressor to the outdoor heat exchanger. And the refrigerant flows from the indoor heat exchanger to the suction side of the compressor. In the refrigerant circuit in such a state, the high-temperature and high-pressure refrigerant discharged from the compressor passes through the four-way valve, flows into the outdoor heat exchanger, exchanges heat with the outside air in the outdoor heat exchanger, releases heat, and condenses. After performing the heat exchange in the outdoor heat exchanger as described above, the refrigerant passes through the first throttle unit connected to the indoor heat exchanger that performs the cooling operation, and when passing through the first throttle unit, the refrigerant has a low temperature. The refrigerant becomes low-pressure refrigerant, flows into the indoor heat exchanger, exchanges heat with indoor air in the indoor heat exchanger, and absorbs heat, thereby cooling the room. Thus, the refrigerant after performing heat exchange in the indoor heat exchanger,
It passes through a four-way valve and flows into the compressor. On the other hand, the high-temperature cooling water that absorbs the heat discharged by the hot water conveying means passes through the hot water flow rate adjusting means connected to the indoor hot water heat exchanger performing the heating operation, and flows into the indoor hot water heat exchanger. In the indoor hot water heat exchanger, heat is exchanged with room air to radiate heat, thereby heating the room. After performing heat exchange in the indoor hot water heat exchanger, the cooling water flows into the heat engine. In this way, since the heat pump circuit using the compressor and the heating circuit using the heat radiation of the cooling water of the heat engine are made independent, cooling and heating can be simultaneously operated between the two indoor units.

[0055]

【Example】

(Embodiment 1) Hereinafter, a first embodiment of the present invention will be described with reference to FIG. The same parts as those in the conventional example are denoted by the same reference numerals, and detailed description is omitted.

As shown in FIG. 1, a heat engine 113 cooled by cooling water, a generator 112 driven by the heat engine, a compressor 101 for compressing refrigerant, and a pipe connection to the discharge side of the compressor First switching means 1 to be connected, second flow switching means 2 connected to the suction side of the compressor by piping, and piping connected to one end of the first flow switching means and the second flow switching means. A four-way valve 3, an outdoor heat exchanger 4 connected to one end of the four-way valve 3, a first throttle means 5 connected to the other end of the outdoor heat exchanger 4, and a first flow path Switching means 1
Outdoor unit 7 comprising a refrigerant transfer means 6 connected by piping between the other end of the second flow path switching means 2 and the other end of the second flow path switching means 2
And an indoor unit 9 having an indoor heat exchanger 8 having one end connected to the four-way valve 3 and the other end connected to the first throttle means 1. An outdoor hot water heat exchanger 10 for exchanging heat with the cooling water of the heat engine 113 is provided. The refrigerant is R22, the heat engine 113 is a diesel engine, and the first switching means 1 or the second switching means. Represents a three-way valve, a trochoid pump as a liquid pump as the refrigerant transfer means 6, a first
The expansion means 5 has an electric expansion valve, the outdoor heat exchanger 4 or the indoor heat exchanger 8 has a fin-tube type heat exchanger, and the outdoor hot water heat exchanger 10 has a double pipe structure.

When the air-conditioning apparatus having the above-described configuration performs the normal heating operation or the heating operation at a low load, the compressor 101 is stopped, and then the first flow path switching is performed as the refrigerant flow direction. The means 1 is switched so that the refrigerant flows through the refrigerant conveying means 6 and the outdoor hot water heat exchanger 10, and the second flow path switching means 2 includes the four-way valve 3 and the refrigerant conveying means 6.
Is switched so that the refrigerant flows. The four-way valve 3 is switched in the direction of the dotted line in FIG.
The refrigerant flows through the indoor heat exchanger 8 and the outdoor heat exchanger 3.
And the second switching means 2 is switched so that the refrigerant flows. In this state, the refrigerant is first discharged from the refrigerant conveying means 6, and then in the outdoor hot water heat exchanger 10, heat exchange is performed with the cooling water, which has been heated by the exhaust heat received from the cooling portion of the heat engine 113, and It becomes a refrigerant. The high-temperature refrigerant then flows into the indoor heat exchanger 8, exchanges heat with the indoor air in the indoor heat exchanger, radiates heat, and heats the room. After performing the heat exchange in the indoor heat exchanger 8 in this manner, the refrigerant flows from the indoor heat exchanger 8 to the first throttle means 5, the outdoor heat exchanger 4, the four-way valve 3, the second flow path switching means 2
, Sequentially flow into the refrigerant conveying means 6, and the above operation is repeated. When the heating operation is performed at a low temperature or a high load, such as in a cold region, the refrigerant transporting unit 6 is in a stopped state, and then the first flow switching unit 1 Outdoor hot water heat exchanger 10 from discharge side
The second flow path switching means 2 switches so that the refrigerant flows from the four-way valve 3 to the suction side of the compressor 101. In this state, the refrigerant stored in the outdoor hot water heat exchanger 10 is first discharged at a high temperature and a high pressure from the electric power stored by the generator or the compressor 101 driven by the commercial power supply.
Heat exchange with the cooling water, which has become hot due to the exhaust heat received from the cooling part, recovers the exhaust heat. The high-temperature refrigerant then flows into the indoor heat exchanger 8, exchanges heat with the indoor air in the indoor heat exchanger, radiates heat, and heats the room. After performing the heat exchange in the indoor heat exchanger 8 in this manner, the refrigerant flows from the indoor heat exchanger 8 to the first throttle means 5, the outdoor heat exchanger 4, the four-way valve 3, the second flow path switching means 2 , Sequentially flow into the compressor 101 again, and the above operation is repeated.

On the other hand, when performing the cooling operation, the first flow path switching means 1 switches so that the refrigerant flows from the discharge side of the compressor 101 to the outdoor hot water heat exchanger 10, and the second flow path switching means 2 Is switched so that the refrigerant flows from the four-way valve 3 to the suction side of the compressor 101. Further, the four-way valve 3 is switched in the direction of the solid line in FIG. 1 so that the refrigerant flows through the outdoor hot water heat exchanger 10 and the outdoor heat exchanger 4, and the refrigerant flows through the indoor heat exchanger 8 and the second switching means 2. Switch to The electric power stored by the generator 112 or the high-temperature and high-pressure refrigerant discharged from the compressor 101 driven by the commercial power supply passes through the outdoor hot water heat exchanger 10 and then flows into the outdoor heat exchanger 4 via the four-way valve 3. I do. Here, the refrigerant is condensed and liquefied by exchanging heat with outdoor air, and then the first throttling means 5
After that, it flows into the indoor heat exchanger 8, exchanges heat with the indoor air, and absorbs and evaporates to cool the room. Thereafter, the vaporized refrigerant returns to the compressor 101 through the four-way valve 3 again.

As described above, according to the present invention, during the heating operation,
Since heating is performed using the exhaust heat of the heat engine 113 without driving the compressor 101, a low-capacity heating operation can be performed while suppressing power consumption.

In the present embodiment, R22 was used as the refrigerant.
07c, etc., and R410A, R4
Similar effects can be obtained by using 10B or the like, or HC-based propane (R290).

Although a diesel engine is used as the heat engine 113, a similar effect can be obtained by using a gas engine, a gasoline engine or the like instead.

Although a trochoid pump is used as the refrigerant transport means, a similar effect can be obtained by using a liquid pump or the like instead.

Although a three-way valve is used as the first switching means 1 and the second switching means 2, the same operation and effect can be obtained by using an electromagnetic valve instead.

Although a double tube is used as the outdoor hot water heat exchanger 10, a similar effect can be obtained by using a shell and tube heat exchanger instead.

The power stored in the generator 112 or the commercial power is used as the power supplied to the compressor 101 by driving the generator 113. The same effect can be obtained by using the generated power.

(Embodiment 2) Next, a second embodiment of the present invention will be described with reference to FIG. The same parts as those in the first embodiment are denoted by the same reference numerals, and detailed description is omitted.

As shown in FIG. 2, the outdoor hot water heat exchanger 10
Is disposed on the discharge side of the refrigerant conveying means 6, the first flow path switching means 1 is disposed between the four-way valve 3 and the indoor heat exchanger 4, and the second flow path switching means 2 is disposed with the four-way valve 3. It is arranged between the outdoor heat exchanger 4 and the outdoor hot water heat exchanger 10 and the refrigerant conveying means 6 between the other end of the first flow path switching means 1 and the other end of the second flow path switching means 2. Is provided.

When the air-conditioning apparatus configured as described above performs the normal heating operation or the heating operation at a low load, the compressor 101 is stopped and then the first flow switching is performed as the refrigerant flow direction. Means 1 is an outdoor hot water heat exchanger 1
From 0, the refrigerant is switched to flow to the indoor heat exchanger 8, and the second flow path switching means 2 is switched to flow the refrigerant from the outdoor heat exchanger 4 to the four-way valve 3. As a result, the refrigerant does not pass through the four-way valve 3 formed by using many bent pipes that cause a pressure loss. In this state, the refrigerant is first discharged from the refrigerant conveying means 6, and then in the outdoor hot water heat exchanger 10, heat exchange is performed with the cooling water, which has been heated by the exhaust heat received from the cooling portion of the heat engine 113, and It becomes a refrigerant. The high-temperature refrigerant then flows into the indoor heat exchanger 8, where it exchanges heat with indoor air to release heat and heat the room. After performing the heat exchange in the indoor heat exchanger 8 in this manner, the refrigerant sequentially passes from the indoor heat exchanger 8 through the first throttle means 5, the outdoor heat exchanger 4, and the second flow path switching means 2. Then, the refrigerant flows into the refrigerant conveying means 6 again, and the above operation is repeated. When the heating operation is performed at a low temperature or a high load, such as in a cold region, the refrigerant transporting means 6 is stopped, and then the first flow path switching means 1 moves from the four-way valve 3 as the refrigerant flowing direction. The refrigerant is switched to the indoor hot water heat exchanger 8 so that the refrigerant flows therethrough.
Is switched so that the refrigerant flows from the outdoor heat exchanger 4 to the four-way valve 3. Further, the four-way valve 3 switches in the direction of the dotted line in FIG. In this state, the electric power stored by the generator or the refrigerant from the compressor 101 driven by the commercial power supply is first discharged in a high-temperature and high-pressure state, and then flows into the indoor heat exchanger 8 through the four-way valve 3, The indoor heat exchanger 8 exchanges heat with room air to radiate heat and heat the room. After performing the heat exchange in the indoor heat exchanger 8 in this manner, the refrigerant flows into the indoor heat exchanger 8.
Then, the pressure is reduced in the first throttle means 5, and then the heat is exchanged with the outdoor air in the outdoor heat exchanger 4, where it is evaporated and vaporized. Then, the evaporated and vaporized refrigerant sequentially passes through the four-way valve 3 and the second flow path switching means 2, flows into the compressor 101 again, and repeats the above operation.

On the other hand, when performing the cooling operation, the first flow path switching means 1 switches the flow direction of the refrigerant so that the refrigerant flows from the four-way valve 3 to the outdoor heat exchanger 4, and the second flow path is switched. The means 2 is switched so that the refrigerant flows from the indoor heat exchanger 8 to the four-way valve 3. Further, the four-way valve 3 is switched in the direction of the solid line in FIG. 2, and the refrigerant flows from the discharge side of the compressor 101 to the outdoor heat exchanger 4 and the refrigerant flows from the indoor heat exchanger 8 to the suction side of the compressor 101. Switch to
In this state, the electric power stored by the generator or the high-temperature and high-pressure refrigerant discharged from the compressor 101 driven by the commercial power supply flows into the outdoor heat exchanger 4 through the four-way valve 3. Here, the refrigerant is condensed and liquefied by exchanging heat with outdoor air, and then decompressed by the first throttle means 5,
After that, it flows into the indoor heat exchanger 8, exchanges heat with the indoor air, and absorbs and evaporates to cool the room. Thereafter, the vaporized refrigerant returns to the compressor 101 again through the four-way valve 3 and repeats the above operation.

As described above, according to the present invention, during the heating operation,
The interior of the room can be heated using the exhaust heat of the heat engine 113 without driving the compressor 101, and the refrigerant circulates without passing through the four-way valve 3, so that the pressure loss and power consumption of the cycle are suppressed to a small value. While performing the low-capacity heating operation.

(Embodiment 3) Next, a third embodiment of the present invention will be described with reference to FIG. The same parts as those in the first and second embodiments are denoted by the same reference numerals, and detailed description is omitted.

FIG. 3 shows that the outdoor hot water heat exchanger 10 is arranged on the discharge side of the refrigerant conveying means 6, the first flow path switching means 1 is arranged between the four-way valve 3 and the indoor heat exchanger 8, The second flow path switching means 2 is disposed between the outdoor heat exchanger 4 and the first throttle means 5,
This is an air conditioner in which the outdoor hot water heat exchanger 10 and the refrigerant conveying means 6 are provided between the other end of the first flow path switching means 1 and the other end of the second flow path switching means 2.

In the air conditioner configured as described above, when performing the normal heating operation or the heating operation at a low load, the compressor 101 is stopped, and the first flow path switching means 1 The refrigerant is switched so that the refrigerant flows from the hot water heat exchanger 10 to the indoor heat exchanger 8, and the second flow path switching unit 2 switches so that the refrigerant flows from the first throttle unit 5 to the refrigerant transport unit 6. As a result, the refrigerant does not pass through the four-way valve 3 and the outdoor exchanger 4 that are formed by using many bent pipes that cause pressure loss. In such a state, the refrigerant is first discharged from the refrigerant conveying means 6, and then exchanges heat with the hot water flowing out of the heat engine 113 in the outdoor hot water heat exchanger 10 to absorb the heat of the hot water to become a high-temperature refrigerant. The high-temperature refrigerant flows into the indoor heat exchanger 8 and exchanges heat with indoor air in the indoor heat exchanger 8 to radiate heat, thereby heating the room. After performing the heat exchange in the indoor heat exchanger 8 in this manner, the refrigerant sequentially passes from the indoor heat exchanger 8 through the first throttle means 5 and the second flow path switching means 2,
The refrigerant flows into the refrigerant conveying means 6 again, and the above operation is repeated.

When the heating operation is performed at a low temperature or a high load in a cold region or the like, the refrigerant transporting means 6 is in a stopped state. The second flow switching means 2 is switched so that the refrigerant flows from the first throttle means 5 to the outdoor heat exchanger 4, and the four-way valve 3 is switched to a circuit indicated by a broken line. Next, the compressor 101 is started, and the refrigerant is first discharged from the compressor 101, then passes through the first flow path switching means 1, flows into the indoor heat exchanger 8, and in the indoor heat exchanger 8, The room is heated by heat exchange and heat dissipation. After performing the heat exchange in the indoor heat exchanger 8 in this manner, the refrigerant sequentially passes from the indoor heat exchanger 8 through the first throttle means 5 and the second flow path switching means 2, and passes through the outdoor heat exchanger 4. And heat exchanges with the outside air in the outdoor heat exchanger 4 to absorb heat and evaporate. After performing the heat exchange in the outdoor heat exchanger 4 in this manner, the refrigerant passes through the four-way valve 3 and flows into the compressor 101 again to repeat the above operation.

On the other hand, when performing the cooling operation, first, the first
Is switched so that the refrigerant flows from the indoor heat exchanger 8 to the four-way valve 3, and the second flow path switching means 2 flows the refrigerant from the outdoor heat exchanger 4 to the first throttle means 5. And the four-way valve 3 switches to the circuit shown by the solid line. Next, the compressor 101 is driven by electric power or commercial electric power supplied from a generator 112 driven by a heat engine 113, and the high-temperature and high-pressure refrigerant discharged from the compressor 101 passes through the four-way valve 3 to perform outdoor heat exchange. It flows into the vessel 4, exchanges heat with the outside air, and condenses by releasing heat. After performing the heat exchange in the outdoor heat exchanger 4 in this manner, the refrigerant
, And then passes through the first throttle means 5, changes into a low-temperature low-pressure refrigerant when passing through the first throttle means, and then passes through the indoor heat exchanger 8. Inflow. The refrigerant flowing into the indoor heat exchanger 8 is
The room is cooled by exchanging heat with indoor air and absorbing heat. After the heat exchange in the indoor heat exchanger 8 as described above, the refrigerant sequentially passes through the first flow path switching means 1 and the four-way valve 3, is sucked into the compressor 101 again, and repeats the above operation.

As described above, according to the present invention, when performing the normal heating operation or the heating operation at a low load, the compressor 10
1 is driven without using the exhaust heat of the heat engine 113, and the refrigerant does not pass through the four-way valve 3 and the outdoor heat exchanger 4, so that the four-way valve 3 and the outdoor heat exchanger 4 The low-capacity heating operation can be performed while suppressing power consumption without being affected by the pressure loss.

(Embodiment 4) Next, a fourth embodiment of the present invention will be described with reference to FIG. Note that the first and second
The same parts as those of the third embodiment are denoted by the same reference numerals, and detailed description is omitted.

FIG. 4 shows that a third flow path switching means 11 is provided between the outdoor heat exchanger 4 and the second flow path switching means 2 so that the four-way valve 3 and the first flow path switching means 1 can be connected to each other. A fourth flow path switching means 12 is provided therebetween, and a refrigerant flowing between the second flow path switching means 2 and the refrigerant conveying means 6; a third flow path switching means 11 and a fourth flow path switching means. A heat exchanger 13 for exchanging heat with the refrigerant flowing between the heat exchanger 12 and the second flow restrictor 14 between the heat exchanger 13 for refrigerant and the third flow path switching means 11. The air conditioner has a configuration using a double pipe as the heat exchanger between refrigerants 13.

In the air conditioner configured as described above, when performing the normal heating operation or the heating operation at a low load, the compressor 101 is stopped, and first, the first flow path switching means 1 is set to the outdoor state. The refrigerant is switched so that the refrigerant flows from the hot water heat exchanger 10 to the indoor heat exchanger 8, and the second flow path switching unit 2 is switched so that the refrigerant flows from the first throttle unit 5 to the inter-refrigerant heat exchanger 13. The third flow path switching means 11 switches so that the refrigerant flows from the outdoor heat exchanger 4 to the second throttle means 14, and the fourth flow path switching means 12 switches from the inter-refrigerant heat exchanger 13 to the four-way valve 3. , And the four-way valve 3 switches to the circuit indicated by the solid line. In such a state, the refrigerant is discharged from the refrigerant conveying means 6, and then exchanges heat with the hot water flowing out of the heat engine in the outdoor hot water heat exchanger 10 to absorb the heat of the hot water to become a high-temperature refrigerant. The high-temperature refrigerant passes through the first flow path switching means 1, flows into the indoor heat exchanger 8, and exchanges heat with indoor air in the indoor heat exchanger 8 to radiate heat, thereby heating the room. After performing the heat exchange in the indoor heat exchanger 8 in this manner, the refrigerant flows from the indoor heat exchanger 8 to the first throttling unit 5 and the second
, And flows into the inter-refrigerant heat exchanger 13.

The compressor 101 is driven by electric power or commercial electric power supplied from a generator 112 driven by a heat engine 113. The high-temperature and high-pressure refrigerant discharged from the compressor 101 passes through the four-way valve 3, Next, the outdoor heat exchanger 4
And exchanges heat with the outside air in the outdoor heat exchanger 4 to dissipate heat and condense. Next, the refrigerant passes from the outdoor heat exchanger 4 through the third flow path switching unit 11 and then passes through the second throttle unit 4. When passing through the second throttle means 14, it becomes a low-temperature low-pressure refrigerant and flows into the inter-refrigerant heat exchanger 13. The refrigerant flowing from the second flow path switching means 2 into the inter-refrigerant heat exchanger 13 and the refrigerant flowing from the second throttle means into the inter-refrigerant heat exchanger 13 exchange heat in the inter-refrigerant heat exchanger 13. The refrigerant flowing from the second flow path switching means 2 into the inter-refrigerant heat exchanger 13 is cooled by radiating heat to the refrigerant flowing into the inter-refrigerant heat exchanger 13 from the second throttle means, and the refrigerant is conveyed again. It flows into the means 6. Further, the refrigerant that has flowed into the inter-refrigerant heat exchanger 13 from the second throttle means 14 performs heat exchange in the inter-refrigerant heat exchanger 13 and then sequentially passes through the fourth flow path switching means 12 and the four-way valve 3. Then, it flows into the compressor 101 again. The refrigerant flowing into the refrigerant conveying means 6 and the compressor 101 again repeats the above operation.

When the heating operation is performed at a low temperature or a high load, such as in a cold region, the refrigerant transporting means 6 is in a stopped state, and the first flow switching means 1 is first switched to the fourth flow switching means 12. Is switched so that the refrigerant flows from the first heat exchanger to the indoor heat exchanger 8.
The third flow path switching means 11 is switched from the second flow path switching means 2 to the outdoor heat exchanger 4 so that the refrigerant flows through the third flow path switching means 11,
The fourth flow path switching means 12 switches from the four-way valve 3 to the first flow path switching means 1 so that the refrigerant flows, and the four-way valve 3 switches to a circuit indicated by a broken line. Next, the compressor 101 is started, the refrigerant is first discharged from the compressor 101, and then the four-way valve 3, the fourth flow path switching means 12, the first flow path switching means 1
, And flows into the indoor heat exchanger 8, where the indoor heat exchanger 8 exchanges heat with indoor air to radiate heat and heat the room. After performing the heat exchange in the indoor heat exchanger 8 in this manner, the refrigerant passes from the indoor heat exchanger 8 to the first throttle unit 5, the second channel switching unit 2, and the third channel switching unit 11. After passing through sequentially, it flows into the outdoor heat exchanger 4 and exchanges heat with the outside air in the outdoor heat exchanger 4 to absorb heat and evaporate. After performing the heat exchange in the outdoor heat exchanger 4 in this manner, the refrigerant passes through the four-way valve 3 and flows into the compressor 101 again to repeat the above operation.

On the other hand, when performing the cooling operation, the first flow path switching means 1 is connected to the fourth flow path switching means 1 by the indoor heat exchanger 8.
The second flow path switching means 2 is switched from the third flow path switching means 11 to the first throttle means 5.
The third flow path switching means 11 is switched so that the refrigerant flows from the outdoor heat exchanger 4 to the second flow path switching means 2, and the fourth flow path switching means 1
2 switches so that the refrigerant flows from the first flow path switching means 1 to the four-way valve 3, and the four-way valve 3 switches to a circuit indicated by a solid line. Next, the compressor 101 is driven by electric power supplied from a generator 112 driven by a heat engine 113, and the high-temperature and high-pressure refrigerant discharged from the compressor 101 passes through the four-way valve 3 and flows into the outdoor heat exchanger 4. Then, it condenses by exchanging heat with the outside air and releasing heat. After performing the heat exchange in the outdoor heat exchanger 4 in this manner, the refrigerant flows into the third flow path switching unit 1.
First, the refrigerant passes through the second flow path switching means 2 sequentially, passes through the first throttle means 5, changes into a low-temperature and low-pressure refrigerant when passing through the first throttle means 5, and changes into the indoor heat exchanger 8. Flows into. The refrigerant flowing into the indoor heat exchanger 8 is
The room is cooled by exchanging heat with indoor air and absorbing heat. After performing the heat exchange in the indoor heat exchanger 8, the refrigerant sequentially passes through the first flow path switching means 1, the fourth flow path switching means 12, and the four-way valve 3, and is sucked into the compressor 101 again, and Repeat the operation.

As described above, according to the present invention, when performing the normal heating operation or the heating operation at a low load, the refrigerant on the suction side of the refrigerant conveying means 6 is cooled so as to always become the liquid refrigerant. 6 can be reduced.

Although a double tube is used as the heat exchanger 13 between refrigerants in the present embodiment, a similar effect can be obtained by using a shell-and-tube heat exchanger.

(Embodiment 5) Next, a fifth embodiment of the present invention will be described with reference to FIG. The same parts as those in the first, second, third and fourth embodiments are designated by the same reference numerals,
Detailed description is omitted.

FIG. 5 shows a turbo engine 15 as a heat engine.
And a configuration in which an intake cooling heat exchanger 16 for exchanging heat between the intake side air of the turbo engine and the refrigerant flowing between the third flow path switching means 11 and the fourth flow path switching means 12 is provided. The air-conditioning apparatus has an intake cooling heat exchanger 16
From the second flow path switching means 2 to the intake cooling heat exchanger 1
6, a double pipe for performing heat exchange between the refrigerant flowing into the intake cooling heat exchanger 16 from the second throttle means 14 and the intake air of the turbo engine 15, and the second flow path switching means 2. From the second throttle means 14 which has exchanged heat with the refrigerant flowing into the intake cooling heat exchanger 16 from the intake cooling heat exchanger 16
A heat exchanger having a structure in which double tubes that exchange heat with the refrigerant flowing into the heat exchanger is connected in series.

In the air conditioner configured as described above, when performing the normal heating operation or the heating operation at a low load, the compressor 101 is stopped, and the first flow path switching means 1 first sets the outdoor hot water heat Heat exchanger 8 to indoor heat exchanger 8
The second flow path switching means 2 switches so that the refrigerant flows from the first throttle means 5 to the intake cooling heat exchanger 16, and the third flow path switching means 1
1 is switched so that the refrigerant flows from the outdoor heat exchanger 4 to the second throttle means 14, and the fourth flow path switching means 12 is switched so that the refrigerant flows from the inter-refrigerant heat exchanger 13 to the four-way valve 3. , The four-way valve switches to the circuit shown by the solid line. In such a state, the refrigerant is discharged from the refrigerant conveying means 6 and then exchanges heat with the hot water flowing out of the turbo engine 15 in the outdoor hot water heat exchanger 10 to absorb the heat of the hot water to become a high-temperature refrigerant. This high-temperature refrigerant passes through the first flow path switching means, flows into the indoor heat exchanger 8, exchanges heat with the indoor air in the indoor heat exchanger 8, and releases heat to heat the room. The refrigerant after performing the heat exchange in the indoor heat exchanger 8 sequentially passes from the indoor heat exchanger 8 through the first throttle means 5 and the second flow path switching means 2 to the intake cooling heat exchanger 16. Inflow. The compressor 101 is driven by electric power supplied from a generator 112 driven by the turbo engine 15 or commercial electric power, and the high-temperature and high-pressure refrigerant discharged from the compressor 101 passes through the four-way valve 3 and then exchanges outdoor heat. It flows into the vessel 4 and exchanges heat with the outside air in the outdoor heat exchanger 4 to be condensed. After performing the heat exchange in the outdoor heat exchanger 4 in this manner, the refrigerant passes from the outdoor heat exchanger 4 through the third flow path switching unit 11, passes through the second throttle unit 14, and passes through the second throttle unit 14.
When passing through the throttle means 14, the refrigerant becomes a low-temperature and low-pressure refrigerant and flows into the intake cooling heat exchanger 16. In addition, the intake side air of the turbo engine 15 passes through the intake cooling heat exchanger 16 and flows into the turbo engine 15. Then, in the intake cooling heat exchanger 16, the refrigerant flowing from the second flow path switching means 2 into the intake cooling heat exchanger 16 exchanges heat with the refrigerant flowing from the second throttle means 14 into the intake cooling heat exchanger 16. After the heat is released and cooled, the refrigerant flows into the refrigerant conveying means 6, and the air on the intake side of the turbo engine 15 exchanges heat with the refrigerant flowing from the second flow path switching means 2 into the intake cooling heat exchanger 16. The refrigerant exchanges heat with the refrigerant flowing into the intake cooling heat exchanger 16 from the second throttle means 14, radiates heat and is cooled, and becomes air having a larger specific weight and is sucked into the turbo engine 15. Further, the second cooling means 14 supplies the heat to the intake cooling heat exchanger 1.
The refrigerant that has flowed into 6 passes through the fourth flow path switching means 12 and the four-way valve 3 sequentially and flows into the compressor 101.

When the heating operation is performed at a low temperature or a high load, such as in a cold region, the refrigerant transporting means 6 is in a stopped state, and the first flow switching means 1 is first switched to the fourth flow switching means 12. Is switched so that the refrigerant flows from the first heat exchanger to the indoor heat exchanger 8.
The third flow path switching means 11 is switched from the second flow path switching means 2 to the outdoor heat exchanger 4 so that the refrigerant flows through the third flow path switching means 11,
The fourth flow path switching means 12 switches from the four-way valve 3 to the first flow path switching means 1 so that the refrigerant flows, and the four-way valve 3 switches to a circuit indicated by a broken line. Next, the compressor 101 is started, the refrigerant is first discharged from the compressor 101, and then the four-way valve 3, the fourth flow path switching means 12, the first flow path switching means 1
, And flows into the indoor heat exchanger 8, where the indoor heat exchanger 8 exchanges heat with indoor air to radiate heat and heat the room. After performing the heat exchange in the indoor heat exchanger 8 in this manner, the refrigerant passes from the indoor heat exchanger 8 to the first throttle unit 5, the second channel switching unit 2, and the third channel switching unit 11. After passing through sequentially, it flows into the outdoor heat exchanger 4 and exchanges heat with the outside air in the outdoor heat exchanger 4 to absorb heat and evaporate. After performing the heat exchange in the outdoor heat exchanger 4 in this manner, the refrigerant passes through the four-way valve 3 and flows into the compressor 101 again to repeat the above operation.

When the cooling operation is performed, the first flow switching means 1 is connected to the fourth flow switching means 12 from the indoor heat exchanger 8.
The second flow path switching means 2 is switched so that the refrigerant flows from the third flow path switching means 11 to the first throttle means 5, and the third flow path switching means 11 Is switched so that the refrigerant flows from the outdoor heat exchanger 4 to the second flow path switching means, and the fourth flow path switching means 12 causes the refrigerant to flow from the first flow path switching means 1 to the four-way valve 3. , And the four-way valve 3 switches to the circuit indicated by the solid line. Next, the compressor 101 is driven by electric power supplied by a generator 112 driven by the turbo engine 15,
The high-temperature and high-pressure refrigerant discharged from the compressor 101 is supplied to the four-way valve 3
, Flows into the outdoor heat exchanger 4, exchanges heat with the outside air, and condenses by radiating heat. After performing the heat exchange in the outdoor heat exchanger 4 in this manner, the refrigerant sequentially passes through the third flow path switching means 11 and the second flow path switching means 2 and then passes through the first throttle means 5. When passing through the first throttle means 5, the refrigerant changes into a low-temperature low-pressure refrigerant and flows into the indoor heat exchanger 8. The refrigerant flowing into the indoor heat exchanger 8 is
In, heat exchange is performed with room air to absorb heat and cool the room. After the heat exchange in the indoor heat exchanger 8 as described above, the refrigerant sequentially passes through the first flow path switching means 1, the fourth flow path switching means 12, and the four-way valve 3, and is sucked into the compressor 101 again. The above operation is repeated.

As described above, according to the present invention, the specific weight of the air on the intake side of the turbo engine 15 is increased by exchanging heat with the refrigerant on the air on the intake side of the turbo engine 15 and utilizing the heat of evaporation of the refrigerant. By doing so, the efficiency of the turbo engine 15 can be improved.

In this embodiment, the intake cooling heat exchanger 16
From the second flow path switching means 2 to the intake cooling heat exchanger 1
6, a double pipe for performing heat exchange between the refrigerant flowing into the intake cooling heat exchanger 16 from the second throttle means 14 and the intake air of the turbo engine 15, and the second flow path switching means 2. From the second throttle means 14 which has exchanged heat with the refrigerant flowing into the intake cooling heat exchanger 16 from the intake cooling heat exchanger 16
Although the heat exchanger having a configuration in which the double tubes that perform heat exchange with the refrigerant flowing into the heat exchanger were used in series was used, a configuration in which the arrangement of the double tubes was replaced, a configuration in which the double tubes were connected in parallel, or The same operation and effect can be obtained even when the double tube is configured as a shell-and-tube heat exchanger.

Embodiment 6 Next, a sixth embodiment of the present invention will be described with reference to FIG. The same parts as those of the first, second, third, fourth and fifth embodiments are designated by the same reference numerals, and the detailed description is omitted.

FIG. 6 includes first throttling means 5a, 5b and indoor heat exchangers 8a, 8b.
Fifth flow path switching means 1 between the first flow path switching means 2 and the second flow path switching means 2
7a, 17b, and between the indoor heat exchangers 8a, 8b and the first flow path switching means 1, sixth flow path switching means 18a, 1b.
8b, the pipe between the outdoor heat exchanger 4 and the second flow path switching means 2 is branched and connected to the fifth flow path switching means 17a and 17b, and the first flow path switching means 1 and the four-way This is an air conditioner configured to branch and connect a pipe between the valve 3 and the sixth flow path switching means 18a and 18b.
7a, 17b and a configuration using a three-way valve as the sixth flow path switching means.

In the air conditioner configured as described above, when the indoor unit 9a performs the cooling operation and the indoor unit 9b performs the heating operation, first, the first flow path switching means 1
Is the outdoor hot water heat exchanger 10 to the sixth flow path switching means 18
a, 18b, so that the refrigerant flows to the refrigerant flow means 6 from the fifth flow path switching means 17a, 17b.
Indoor unit 9a for performing cooling operation and first throttle means 5a
The fifth flow path switching means 17a connected via
The outdoor heat exchanger 4 and the first throttle unit 5a are switched so that the refrigerant flows therethrough, and the indoor unit 9b for performing the heating operation is connected to the fifth channel switching unit 17b via the first throttle unit 5b. Is switched so that the refrigerant flows through the first throttle means 5b and the second flow path switching means 2, and the sixth flow path switching means 18a connected to the indoor unit 9a performing the cooling operation is the indoor unit 9a. And the four-way valve 3 is switched so that the refrigerant flows, and the sixth flow path switching unit 18b connected to the indoor unit 9b that performs the heating operation is the first
Is switched so that the refrigerant flows through the flow path switching means 1 and the indoor unit 9b, and the four-way valve 3 switches to the circuit indicated by the solid line. In such a state, the refrigerant discharged from the refrigerant conveying means 6 exchanges heat with the hot water flowing out of the heat engine 113 in the outdoor hot water heat exchanger 10 to absorb the heat of the hot water to become a high-temperature refrigerant. The high-temperature refrigerant passes through the first flow path switching means 1, passes through the sixth flow path switching means 18b whose flow path is switched to the indoor unit 8b that performs the heating operation, and flows into the indoor heat exchanger 8b. In the indoor heat exchanger 8b, heat is exchanged with indoor air to radiate heat to heat the room. After performing heat exchange in the indoor heat exchanger 8b, the refrigerant sequentially passes from the indoor heat exchanger 8b through the first throttle means 5, the fifth flow path switching means 17b, and the second flow path switching means 2, The refrigerant flows into the refrigerant conveying means 6 again, and the above operation is repeated. The compressor 101 is driven by electric power or commercial electric power supplied from a generator 112 driven by a heat engine 113. The high-temperature and high-pressure refrigerant discharged from the compressor 101 passes through the four-way valve 3 and passes through the outdoor heat exchanger 4 And exchanges heat with the outside air in the outdoor heat exchanger 4 to dissipate heat and condense. After performing the heat exchange in the outdoor heat exchanger 4 as described above, the refrigerant flows from the outdoor heat exchanger 4 to the fifth flow path switching unit 17 switched to the indoor unit 8a that performs the cooling operation.
a, passes through the first throttle means 5a, becomes a low-temperature and low-pressure refrigerant when passing through the first throttle means 5a, and then flows into the indoor heat exchanger 8a. The room is cooled by exchanging heat with indoor air and absorbing heat. After performing heat exchange in the indoor heat exchanger 8a, the refrigerant sequentially passes through the sixth flow path switching means 18a and the four-way valve 3, flows into the compressor 101 again, and repeats the above operation.

When the indoor unit 9a performs the heating operation and the indoor unit 9b performs the cooling operation, the fifth flow unit connected to the indoor unit 9b performing the cooling operation via the first throttle unit 5b is used. The path switching unit 17b switches between the outdoor heat exchanger 4 and the first throttle unit 5b so that the refrigerant flows, and the indoor unit 9a that performs the heating operation and the first unit
The fifth flow path switching means 17a connected via the first expansion means 5a switches the first expansion means 5a and the second flow path switching means 2 so that the refrigerant flows, and performs the cooling operation. The sixth channel switching means 18b connected to the unit 9b switches between the indoor unit 9b and the four-way valve 3 so that the refrigerant flows, and performs the heating operation on the indoor unit 9a.
The sixth flow path switching means 18a connected to the first flow path switching means 1 and the indoor unit 9a are switched so that the refrigerant flows through the first flow path switching means 1 and the indoor unit 9a. The refrigerant is circulated and the indoor unit 9a performs a heating operation, and the indoor unit 9b performs a cooling operation.

When both the indoor units 9a and 9b perform the cooling operation, the refrigerant conveying means 6 is in a stopped state, and the first flow path switching means 1 is switched to the sixth flow path switching means 18
a, 18b, so that the refrigerant flows from the outdoor heat exchanger to the four-way valve, the second flow path switching means 2 switches so that the refrigerant flows from the outdoor heat exchanger to the fifth flow path switching means 17a, 17b. The flow switching means 17a, 17b are switched so that the refrigerant flows from the second flow switching means 2 to the first throttle means 5a, 5b.
a and 18b are switched so that the refrigerant flows from the indoor heat exchangers 8a and 8b to the first flow path switching means.
The refrigerant is circulated by the driving of 01 to perform the cooling operation.

When both the indoor units 9a and 9b perform the normal heating operation and the heating operation at a low load, the compressor 101 is in the stopped state, and the first flow path switching means 1
Is the outdoor hot water heat exchanger 10 to the sixth flow path switching means 18
a, 18b, so that the refrigerant flows to the refrigerant flow means 6 from the fifth flow path switching means 17a, 17b.
The fifth flow path switching means 17a, 17b are switched so that the refrigerant flows from the first throttle means 5a, 5 to the second flow path switching means 2, and the sixth flow path switching means 18a, 18b.
Is switched so that the refrigerant flows from the first flow path switching means 1 to the indoor heat exchangers 8a and 8b, the refrigerant is circulated by the refrigerant transport means 6, heat absorption in the outdoor hot water heat exchanger 10, and the indoor heat exchanger 8a , 8b to perform the heating operation.

When both the indoor units 9a and 9b perform the heating operation at the time of low temperature or high load in a cold district or the like, the refrigerant conveying means 6 is in a stopped state, and first the first flow path switching means is a four-way valve. Third to sixth channel switching means 18a, 1
8b, the second flow path switching means 2 switches so that the refrigerant flows from the fifth flow path switching means 17a, 17b to the outdoor heat exchanger 4, and the fifth flow path switching is performed. The means 17a, 17b are provided with the first throttle means 5a,
5 so that the refrigerant flows to the second flow path switching means 2 and the sixth flow path switching means 18a and 18b
The flow is switched from the flow path switching means 1 to the indoor heat exchangers 8a and 8b so that the refrigerant is circulated by driving the compressor 101, and the heating operation is performed by the heat radiation in the indoor heat exchangers 8a and 8b.

As described above, according to the present invention, the heat engine 113
The first flow path switching 1, the second flow path switching means 2, the fifth flow path switching means 17a, 17b, the sixth flow path Since the switching units 18a and 18b are switched independently, cooling and heating can be simultaneously operated between the two indoor units.

In this embodiment, the fifth switching means 17
Although a three-way valve is used as a and 17b and the sixth flow path switching means 18a and 18b, the same operation and effect can be obtained by using an electromagnetic valve. The switching of the fifth flow path switching means 7a, 17b and the sixth flow path switching means 18a, 18b may be either manual or automatic.

The indoor units 8a and 8b, the fifth flow path switching means 17a and 17b, and the sixth flow path switching means 1
8a18b are provided two each.
The same operation and effect can be obtained with more than one configuration.

(Embodiment 7) Next, a seventh embodiment of the present invention will be described with reference to FIGS. The same parts as those in the first, second, third, fourth, fifth and sixth embodiments are designated by the same reference numerals, and detailed description is omitted.

FIG. 7 is a control block diagram of the air conditioner of the present embodiment.
Storage means 19, a first temperature detection means 20 provided in the indoor unit 9 for detecting the indoor temperature, and a difference between a detection value by the first storage means 19 and a detection value by the first temperature detection means 20. First calculating means 21 for calculating, first determining means 22 for determining the result of calculation by the first calculating means 21, and the aperture of the first aperture means 5 based on the determination result by the first determining means 22. Second determination means 2 for determining the opening degree
3 and the first determination result obtained by the second determination means 23
Calculating means 24 for calculating the aperture of the throttle means 5
And first control means 25 for controlling the degree of opening of the first throttle means 5 based on the result of calculation by the second calculation means 24.
A third calculating means 26 for calculating the number of revolutions of the refrigerant conveying means 6 based on the result of the determination by the second determining means 23; The first storage means 19 is built in the indoor unit 9 as a memory circuit made of a semiconductor, and a temperature sensor is used as the first temperature detecting means in the indoor unit 9. 9, a first calculating means 21, a first determining means 22, and a second determining means 2.
3, the second arithmetic means 24, the first control means 25, the third arithmetic means 26, and the second control means 27 use a microcomputer.

The operation of the above configuration will be described with reference to FIG. FIG. 8 is a control flowchart of the air conditioner of the seventh embodiment of the present invention, and details will be described along the flow.

The temperature difference ΔT = Tm−Ts between the set temperature Tm stored by the first storage means 19 and the room temperature Ts detected by the first temperature detection means 20 is calculated by the first calculation means 2.
1 and the first determination means 22 calculates the calculation result Δ
It is determined whether T is positive or negative. If ΔT is positive, it means that the heating capacity is insufficient. Therefore, it is determined by the second determination unit 23 whether the throttle opening Re1 of the first throttle unit 5 is the maximum. In the case where the throttle opening Re1 of the first throttle means 5 is the maximum, the rotational speed increase / decrease amount ΔNr of the refrigerant transport means 6 is increased by the third arithmetic means 26 as shown in FIG.
The second control means 27 increases the rotational speed Nr of the refrigerant transport means 6 from the result of the calculation. When the throttle opening Re1 of the first throttle unit 5 is not the maximum, the throttle opening change ΔRe1 of the first throttle unit 5 is increased by the second calculating unit 24 as shown in FIG. The first control means 25 increases the throttle opening Re1 of the first throttle means 5 from the calculation result.
On the other hand, if the determination of ΔT, which is the calculation result by the first calculation means 21, is negative, it means that the heating capacity is excessive, and it is determined whether the throttle opening Re1 of the first throttle means 5 is the minimum. When the throttle opening Re1 of the first throttle unit 5 is the minimum, the rotation speed increase / decrease amount ΔNr of the refrigerant transport unit 6 is further reduced so as to further reduce the refrigerant flow rate.
Is calculated by the third calculating means 26 as shown in FIG. 10, and the rotational speed Nr of the refrigerant conveying means 6 is reduced by the second control means 27 from the result of the calculation. Also, the first aperture means 5
When the throttle opening Re1 of the first throttle means 5 is not the minimum, the throttle opening increase / decrease amount ΔR
e1 is calculated by the second calculating means 24 as shown in FIG.
From this calculation result, the first control means 25 reduces the throttle opening Re1 of the first throttle means 5.

As described above, according to the present invention, the temperature difference ΔT between the set temperature Tm stored by the first storage means 19 and the room temperature Ts detected by the first temperature detection means 20 is calculated, and this temperature is calculated. Since the throttle opening Re1 of the first throttle unit 5 and the rotation speed Nr of the refrigerant conveying unit 6 can be increased or decreased so that the heating capacity can be increased or decreased in accordance with the difference ΔT,
The heating operation according to the load based on the set temperature in the room can be appropriately performed.

Embodiment 8 Next, an eighth embodiment of the present invention will be described with reference to FIGS. In addition,
The same parts as those in the first, second, third, fourth, fifth, sixth, and seventh embodiments are designated by the same reference numerals, and detailed description is omitted.

FIG. 11 is a cycle diagram of the air conditioner of this embodiment. In the cooling water circuit of the heat engine 113, the hot water conveying means 28, the hot water flow adjusting means 29, and the hot water heat exchanger 1 are shown.
0, the cooling heat exchanger 30 and the cooling heat exchanger 30
And a blowing means 31 for blowing air to the
A liquid pump as the hot water conveying means 28, and a hot water flow rate adjusting means 2
9 is an electric valve, a cooling heat exchanger 30 is a fin-tube heat exchanger, and a blower means 31 is a motor-driven propeller fan.

FIG. 12 is a control flow chart of the air conditioner of this embodiment, in which the third judgment means 32 for judging the rotation speed of the refrigerant conveying means 6 based on the judgment result by the second judgment means 23, and the third judgment means. A fourth calculating means 33 for calculating the opening degree of the hot water flow rate adjusting means 29 from the determination result by the determining means 32, and a fourth calculating means for controlling the opening degree of the hot water flow rate adjusting means 29 based on the calculation result by the fourth calculating means 33. 3 control means 3
4 and the third determination means 32,
The fourth arithmetic unit 33 and the third control unit 34 are configured using a microcomputer.

The operation of the above configuration will be described with reference to FIG. FIG. 13 is a control flowchart of the air conditioner according to the eighth embodiment of the present invention, and details will be described along the flow. The first calculating means 21 calculates a temperature difference ΔT = Tm−Ts between the set temperature Tm stored by the first storing means 19 and the room temperature Ts detected by the first temperature detecting means 20, and makes a first determination. ΔT by means 22
If ΔT is positive, the heating capacity is insufficient, so the second determination means 23 determines whether the throttle opening Re1 of the first throttle means 5 is the maximum, and the first throttle means 5 when the throttle opening Re1 is the maximum.
The third determining means 32 determines whether the rotational speed Nr of the refrigerant is the maximum, and furthermore, if the rotational speed Nr of the refrigerant conveying means 6 is the maximum, the opening degree increase / decrease ΔRh of the hot water flow rate adjusting means 29 is determined by the fourth determining means 32. As shown in FIG. 14 by the calculating means 33, the opening degree Rh of the hot water flow rate adjusting means 29 is increased by the third control means 34 from the calculation result, and the amount of heat exchange with the refrigerant is increased by increasing the hot water flow rate. Increase the heating capacity. If the rotation speed Nr of the refrigerant transfer means 6 is not the maximum, the rotation speed increase / decrease amount ΔNr of the refrigerant transfer means 6 is calculated by the third calculation means 2.
As shown in FIG. 10, the second control means 27 increases the rotation speed Nr of the refrigerant conveying means 6 from this calculation result, and increases the flow rate of the refrigerant to increase the heating capacity. If the throttle opening Re1 of the first throttle unit 5 is not the maximum, the throttle opening increase / decrease ΔR of the first throttle unit 5
e1 is calculated by the second calculating means 24 as shown in FIG.
From this calculation result, the throttle opening Re1 of the first throttle unit 5 is increased by the first control unit 25, and the heating capacity is increased by increasing the refrigerant flow rate. On the other hand, when the determination of ΔT, which is the calculation result by the first calculation unit 21, is negative, the heating capacity is excessive, and it is determined whether the throttle opening Re1 of the first throttle unit 5 is the minimum. When the throttle opening Re1 of the first throttle unit 5 is the minimum, the third determination unit 32 determines whether the rotation speed Nr of the refrigerant conveying unit 6 is the minimum. When the rotation speed Nr of the conveying means 6 is the minimum, the opening / closing amount ΔRh of the hot water flow rate adjusting means 29 is calculated by the fourth calculating means 33 as shown in FIG.
Is decreased by the third control means 34 and the flow rate of hot water flowing into the outdoor hot water heat exchanger 10 is reduced, thereby reducing the amount of heat exchange with the refrigerant and lowering the heating capacity. If the rotation speed Nr of the refrigerant transfer means 6 is not the minimum, the rotation speed increase / decrease ΔNr of the refrigerant transfer means 6 is calculated by the third calculation means 26 as shown in FIG. Nr is reduced by the second control means 27, and the heating capacity is reduced by reducing the flow rate of the refrigerant. If the throttle opening Re1 of the first throttle means 5 is not the minimum, the throttle opening increase / decrease ΔRe1 of the first throttle means 5 is calculated by the second calculating means 24 as shown in FIG. The throttle opening Re1 of the first throttle unit 5 is reduced by the first control unit 25.

As described above, according to the present invention, the temperature difference ΔT between the set temperature Tm stored by the first storage means 19 and the room temperature Ts detected by the first temperature detection means 20 is calculated, and this temperature is calculated. In order to increase or decrease the heating capacity in accordance with the difference ΔT, the throttle opening Re1 of the first throttle means 5, the rotation speed Nr of the refrigerant conveying means 6, and the opening R of the hot water flow rate adjusting means 29 are set.
Since h can be increased or decreased, it is possible to appropriately perform the heating operation according to the load based on the indoor set temperature.

(Embodiment 9) Next, a ninth embodiment of the present invention will be described with reference to FIGS. In addition,
First, second, third, fourth, fifth, sixth, seventh and eighth
The same parts as those of the embodiment are denoted by the same reference numerals, and detailed description is omitted.

FIG. 15 is a control block diagram of the air conditioner of the present embodiment, in which a fourth judging means 35 for judging the opening of the hot water flow rate adjusting means 29 based on the judgment result by the third judging means 32, Fifth calculating means 36 for calculating the number of rotations of the hot water transport means 28 based on the determination result by the fourth determining means 35, and controlling the number of rotations of the hot water transport means 28 based on the calculation result of the fifth calculating means 36. Fourth control means 37
The fourth determination means 35, the fifth calculation means 36, and the fourth control means 37 use a microcomputer.

The operation of the above configuration will be described with reference to FIG. FIG. 16 is a control flowchart of the air conditioner of the ninth embodiment of the present invention, and details will be described along the flow.

The temperature difference ΔT = Tm−Ts between the set temperature Tm stored by the first storage means 19 and the room temperature Ts detected by the first temperature detection means 20 is calculated by the first calculation means 2.
1 and the first determining means 22 determines whether ΔT, which is the result of the calculation by the first calculating means 21, is positive or negative.
If ΔT is positive, the heating capacity is insufficient, and the second determination unit 23 determines whether the throttle opening Re1 of the first throttle unit 5 is the maximum, and the throttle opening of the first throttle unit 5 is determined. Degree Re
If 1 is the maximum, the third determination means 34 determines whether the rotation speed Nr of the refrigerant transporting means 6 is the maximum. If the rotation speed Nr of the refrigerant transporting means 6 is the maximum, the hot water flow rate adjusting means is determined. The fourth determination means 35 determines whether or not the opening Rh of the hot water 29 is the maximum, and when the opening Rh of the hot water flow rate adjusting means 29 is the maximum, the rotation speed change Δ
17 is calculated by the fifth calculating means 36 as shown in FIG. 17, and from this calculation result, the rotation speed Nh of the hot water conveying means 28 is increased by the fourth control means 37, and the heat exchanger 1 for hot water is
By increasing the flow rate of the hot water flowing to zero, the amount of heat exchange with the refrigerant is increased, and the heating capacity is increased. When the opening Rh of the hot water flow rate adjusting means 29 is not the maximum, the opening degree increase / decrease ΔRh of the hot water flow rate adjusting means 29 is calculated by the fourth calculating means 33 as shown in FIG. Is increased by the third control means 34 and the flow rate of hot water flowing through the hot water heat exchanger 10 is increased to increase the amount of heat exchange with the refrigerant and increase the heating capacity. If the rotational speed Nr of the refrigerant transporting means 6 is not the maximum, the rotation speed increase / decrease amount ΔNr of the refrigerant transporting means 6 is calculated by the third calculating means 26 as shown in FIG. The heating capacity is increased by increasing the number Nr by the second control means 27 and increasing the flow rate of the refrigerant. If the throttle opening Re1 of the first throttle unit 5 is not the maximum, the throttle opening change ΔR of the first throttle unit 5
e1 is calculated by the second calculating means 24 as shown in FIG.
From this calculation result, the throttle opening Re1 of the first throttle unit 5 is increased by the first control unit 25, and the heating capacity is increased by increasing the refrigerant flow rate. On the other hand, when ΔT, which is the result of the calculation by the first calculating means 21, is negative, the capability is excessive, and it is determined whether the aperture opening Re1 of the first throttle means 5 is the minimum. And the first
When the throttle opening Re1 of the throttle means 5 is the minimum, the third determination means 32 determines whether the rotation speed Nr of the refrigerant conveyance means 6 is the minimum, and determines whether the rotation speed Nr of the refrigerant conveyance means 6 is the minimum. In some cases, the fourth determining means 35 determines whether or not the opening Rh of the hot water flow rate adjusting means 29 is the minimum. If the opening degree Rh of the hot water flow rate adjusting means 29 is the minimum, the rotation of the hot water conveying means 28 The number increase / decrease amount ΔNh is calculated by the fifth calculating means 36 as shown in FIG. 17, and the rotation speed Nh of the hot water conveying means 28 is reduced by the fourth control means 37 from the calculation result. By reducing the flow rate of the flowing hot water, the amount of heat exchange with the refrigerant is reduced, and the heating capacity is reduced. If the opening degree of the hot water flow rate adjusting means 29 is not the minimum, the opening degree increase / decrease ΔRh of the hot water flow rate adjusting means 29 is calculated by the fourth calculating means 33 as shown in FIG. The opening degree Rh is reduced by the third control means 34, and the amount of heat exchange with the refrigerant is reduced by decreasing the flow rate of the hot water flowing through the hot water heat exchanger 10, thereby lowering the heating capacity. Number of rotations N of refrigerant conveying means 6
If r is not the minimum, the rotation speed increase / decrease amount Δ of the refrigerant conveying means 6
Nr is calculated by the third calculating means 26 as shown in FIG. 10, and from this calculation result, the rotation speed Nr of the refrigerant conveying means 6 is reduced by the second control means 27, and the heating capacity is reduced by reducing the refrigerant flow rate. Lower. If the throttle opening Re1 of the first throttle means 5 is not the minimum, the throttle opening increase / decrease ΔRe1 of the first throttle means 5 is calculated by the second calculating means 24 as shown in FIG. First throttle means 5
Is reduced by the first control means 25.

As described above, according to the present invention, the temperature difference ΔT between the set temperature Tm stored by the first storage means 19 and the room temperature Ts detected by the first temperature detection means 20 is calculated. In order to increase or decrease the heating capacity in accordance with the difference ΔT, the throttle opening Re1 of the first throttle 5, the rotation speed Nr of the refrigerant conveying means 6, the opening Rh of the hot water flow rate adjusting means 29, and the opening degree Rh of the hot water conveying means 28. Since the number of revolutions Nh can be increased or decreased, the heating operation can be accurately performed according to the load based on the indoor set temperature.

Embodiment 10 Next, a tenth embodiment of the present invention will be described with reference to FIGS. The first, second, third, fourth, fifth, sixth, seventh, eighth
The same parts as those of the ninth embodiment are denoted by the same reference numerals, and detailed description is omitted.

FIG. 18 is a control block diagram of the air-conditioning apparatus of the present embodiment. Sixth calculating means 39 for calculating the number of revolutions of heat engine 113 from the result of determination by fifth determining means 38
And a fifth control means 40 for controlling the number of revolutions of the heat engine 113 based on the calculation result by the sixth calculation means 39. The fifth determination means 38, the sixth calculation means 39, the fifth control means 40 is configured using a microcomputer.

The driving operation in the above configuration will be described with reference to FIG. FIG. 19 is a control flowchart of the air conditioner of the tenth embodiment of the present invention, and details will be described along the flow.

The temperature difference ΔT = Tm−Ts between the set temperature Tm stored by the first storage means 19 and the room temperature Ts detected by the first temperature detection means 20 is calculated by the first calculation means 2.
1 and the first determining means 22 determines whether ΔT, which is the result of the calculation by the first calculating means 21, is positive or negative.
When ΔT is positive, the heating capacity is insufficient, and the second determination unit 23 determines whether the throttle opening Re1 of the first throttle unit 5 is the maximum. Opening R
If e1 is the maximum, the third determining means 32 determines whether the rotational speed Nr of the refrigerant transporting means 6 is the maximum. If the rotational speed Nr of the refrigerant transporting means 6 is the maximum, the hot water flow rate adjusting means 29 is determined. Is determined by the fourth determination means 35. If the opening Rh of the hot water flow rate adjusting means 29 is maximum, it is determined whether the rotation speed Nh of the hot water transport means 28 is maximum. When the rotation speed Nh of the hot water conveying means 28 is the maximum, the heat engine 11
The rotation speed increase / decrease ΔNe of the third engine 3 is calculated by the sixth calculation means 39 as shown in FIG. 20, and the rotation speed of the heat engine 113 is increased by the fifth control means 40 based on the calculation result.
By increasing the amount of exhaust heat discharged from the heat exchanger 13, the amount of heat of the hot water flowing through the hot water heat exchanger 10 is increased, and further, the amount of heat exchange with the refrigerant is increased, thereby increasing the heating capacity. If the rotation speed Nh of the hot water transport means 28 is not the maximum, the fifth arithmetic means 36 calculates the rotation speed increase / decrease Δ
Nh is calculated as shown in FIG. 17, and from this calculation result, the rotation speed Nh of the hot water conveying means 28 is increased by the fourth control means 37, and the flow rate of the hot water flowing through the hot water heat exchanger 10 is increased. To increase the amount of heat exchanged with the heater, thereby increasing the heating capacity. When the opening Rh of the hot water flow rate adjusting means 29 is not the maximum, the opening degree increase / decrease ΔRh of the hot water flow rate adjusting means 29 is calculated by the fourth calculating means 33 as shown in FIG. Is increased by the third control means 34 and the flow rate of hot water flowing through the hot water heat exchanger 10 is increased to increase the amount of heat exchange with the refrigerant and increase the heating capacity. If the rotational speed Nr of the refrigerant transporting means 6 is not the maximum, the rotation speed increase / decrease amount ΔNr of the refrigerant transporting means 6 is calculated by the third calculating means 26 as shown in FIG. Number N
r is increased by the second control means 27, and the heating capacity is increased by increasing the refrigerant flow rate. When the throttle opening Re1 of the first throttle means 5 is not the maximum, the throttle opening increase / decrease ΔRe1 of the first throttle means 5 is calculated by the second calculating means 24 as shown in FIG. The heating capacity is increased by increasing the throttle opening Re1 of the first throttle unit 5 by the first control unit 25 and increasing the refrigerant flow rate. On the other hand, ΔT which is the calculation result of the first calculation means 21
Is negative, the throttle opening Re of the first throttle means 5 is determined.
It is determined by the second determination means 23 whether 1 is the minimum,
When the throttle opening Re1 of the first throttle unit 5 is the minimum, the third determination unit 32 determines whether the rotation speed Nr of the refrigerant conveyance unit 6 is the minimum, and the rotation speed Nr of the refrigerant conveyance unit 6 is determined.
When the opening degree Rh of the hot water flow rate adjusting means 29 is the minimum, the fourth determining means 35 determines whether the opening degree Rh of the hot water flow rate adjusting means 29 is the minimum. The rotation speed Nh of the hot water conveying unit 28 is determined by the fifth determination unit 38 whether the rotation speed Nh of the
Is minimum, the rotational speed increase / decrease ΔNe of the heat engine 113
Is calculated by the sixth calculating means 39 as shown in FIG. 20, and the rotational speed Ne of the heat engine 113 is reduced by the fifth control means 40 from the result of this calculation, so that the exhaust heat discharged from the heat engine 113 is reduced. This reduces the amount of heat of the hot water flowing through the hot water heat exchanger 10, further reduces the amount of heat exchange with the refrigerant, and lowers the heating capacity. If the rotation speed Nh of the hot water transfer means 28 is not the minimum, the rotation speed increase / decrease ΔNh of the hot water transfer means 28 is calculated by the fifth calculation means 36 as shown in FIG. The number Nh is reduced by the fourth control means 37, and the amount of heat exchange with the refrigerant is reduced by reducing the flow rate of the hot water flowing through the hot water heat exchanger 10, thereby lowering the heating capacity. If the opening degree of the hot water flow rate adjusting means 29 is not the minimum, the opening degree increase / decrease ΔRh of the hot water flow rate adjusting means 29 is calculated by the fourth calculating means 33 as shown in FIG. The opening degree Rh is reduced by the third control means 34, and the amount of heat exchange with the refrigerant is reduced by decreasing the flow rate of the hot water flowing through the hot water heat exchanger 10, thereby lowering the heating capacity. If the rotation speed Nr of the refrigerant transfer means 6 is not the minimum, the rotation speed increase / decrease ΔNr of the refrigerant transfer means 6 is calculated by the third calculation means 26 as shown in FIG. Nr is reduced by the second control means 27, and the heating capacity is reduced by reducing the flow rate of the refrigerant. If the throttle opening Re1 of the first throttle means 5 is not the minimum, the change ΔR in the throttle opening of the first throttle means 5
e1 is calculated by the second calculating means 24 as shown in FIG.
From this calculation result, the first control means 25 reduces the throttle opening Re1 of the first throttle means 5.

As described above, according to the present invention, the temperature difference ΔT between the set temperature Tm stored by the first storage means 19 and the room temperature Ts detected by the first temperature detection means 20 is calculated, and this temperature is calculated. In order to increase or decrease the heating capacity according to the difference ΔT, the throttle opening Re1 of the first throttle means 5, the rotation speed Nr of the refrigerant conveying means 6, the opening Rh of the hot water flow rate adjusting means 29,
Since the number of revolutions Nh of the hot water conveying means 28 and the number of revolutions Ne of the heat engine 113 can be increased or decreased, the heating operation can be accurately performed according to the load based on the set temperature in the room.

Embodiment 11 Next, an eleventh embodiment of the present invention will be described with reference to FIGS. Note that the same parts as those in the first, second, third, fourth, fifth, sixth, seventh, eighth, ninth, and tenth embodiments have the same reference numerals, and a detailed description thereof will be omitted.

FIG. 21 is a control block diagram of the air conditioner of the present embodiment. The sixth judgment means 4 for judging the rotation speed of the heat engine 113 based on the judgment result by the fifth judgment means 38.
7 and a seventh calculating means 42 for calculating the rotational speed Nc of the compressor 101 from the result of the determination by the sixth determining means 41.
And a sixth control means 43 for controlling the rotation speed Nc of the compressor 101 based on the calculation result by the seventh calculation means 42. The sixth determination means 41 and the seventh calculation The means 42 and the sixth control means 43 use a microcomputer.

The operation of the above configuration will be described with reference to FIG. FIG. 22 is a control flowchart of the air conditioner according to the eleventh embodiment of the present invention, and details will be described along the flow.

The temperature difference ΔT = Tm−Ts between the set temperature Tm stored by the first storage means 19 and the room temperature Ts detected by the first temperature detection means 20 is calculated by the first calculation means 2.
1 and the first determining means 22 determines whether ΔT, which is the result of the calculation by the first calculating means 21, is positive or negative.
When ΔT is positive, the heating capacity is insufficient, and the second determination unit 23 determines whether the throttle opening Re1 of the first throttle unit 5 is the maximum. Opening R
If e1 is the maximum, the third determining means 32 determines whether the rotational speed Nr of the refrigerant transporting means 6 is the maximum. If the rotational speed Nr of the refrigerant transporting means 6 is the maximum, the hot water flow rate adjusting means 29 is determined. Is determined by the fourth determination means 35. If the opening Rh of the hot water flow rate adjusting means 29 is maximum, it is determined whether the rotation speed Nh of the hot water transport means 28 is maximum. If the rotation speed Nh of the hot water conveying means 28 is the maximum, as determined by the fifth determining means 38, the heat engine 1
The rotation speed Ne of the heat engine 113 is determined by the sixth determination unit 42 to determine whether or not the rotation speed Ne of the heat engine 113 is the maximum.
, And the rotation speed increase / decrease ΔNc of the compressor 101 is calculated by the seventh calculation means 42 as shown in FIG. 23, and from this calculation result, the rotation speed Nc of the compressor 101 is calculated by the sixth control means 43.
By performing the heat pump operation using the compressor 101 as well as utilizing the exhaust heat of the heat engine 113, the flow rate of the refrigerant is increased, and the heating capacity is increased. If the rotation speed Ne of the heat engine 113 is not the maximum,
The rotation speed increase / decrease ΔNe of No. 3 is calculated by the sixth calculation means 39 as shown in FIG. 20, and from this calculation result, the rotation speed Ne of the heat engine 113 is increased by the fifth control means 40 and discharged from the heat engine 113. The amount of heat discharged from the hot water heat exchanger 10 is increased by increasing the amount of exhaust heat to be discharged, and the amount of heat exchange with the refrigerant is increased, thereby increasing the heating capacity.
If the rotation speed Nh of the hot water transfer means 28 is not the maximum, the rotation speed increase / decrease ΔNh of the hot water transfer means 28 is calculated by the fifth calculation means 36 as shown in FIG. The number Nh is increased by the fourth control means 37, and the amount of heat exchange with the refrigerant is increased by increasing the flow rate of the hot water flowing through the hot water heat exchanger 10, thereby increasing the heating capacity. If the opening degree Rh of the hot water flow rate adjusting means 29 is not the maximum, the opening degree increase / decrease ΔR of the hot water flow rate adjusting means 29
h is calculated by the fourth calculating means 33 as shown in FIG.
From this calculation result, the opening degree Rh of the hot water flow rate adjusting means 29 is increased by the third control means 34, and the hot water heat exchanger 10
The amount of heat exchange with the refrigerant is increased by increasing the flow rate of the warm water flowing through the heater, thereby increasing the heating capacity. Refrigerant conveying means 6
If the rotation speed Nr of the refrigerant conveyance device 6 is not the maximum, the rotation speed change amount ΔNr of the refrigerant conveyance device 6 is calculated by the third calculation device 26 as shown in FIG. The heating capacity is increased by increasing the refrigerant flow rate by the second control means 27 and increasing the refrigerant flow rate. If the throttle opening Re1 of the first throttle means 5 is not the maximum, the increase / decrease amount ΔRe1 of the throttle opening of the first throttle means 5 is calculated by the second calculating means 2.
4 as shown in FIG. 9, and from this calculation result, the throttle opening Re1 of the first throttle means 5 is increased by the first control means 25, and the refrigerant flow rate is increased to increase the heating capacity. On the other hand, when the determination of ΔT, which is the calculation result of the first calculation means 21, is negative, the heating capacity is excessive,
The second determining means 23 determines whether or not the throttle opening Re1 of the throttle means 5 is the minimum. If the throttle opening Re1 of the first throttle means 5 is the minimum, the rotation speed N of the refrigerant conveying means 6 is determined.
The third determining means 32 determines whether or not r is the minimum.
When the rotation speed Nr of the refrigerant conveying means 6 is the minimum, the fourth determining means 35 determines whether or not the opening Rh of the hot water flow adjusting means 29 is the minimum, and the opening R of the hot water flow adjusting means 29 is determined.
When h is the minimum, the rotation speed Nh of the hot water conveying means 28
Is determined by the fifth determination means 38, and when the rotation speed Nh of the hot water transport means 28 is the minimum, the rotation speed increase / decrease ΔNc of the compressor 101 is determined by the seventh calculation means 42 in FIG. From the result of this operation.
The rotation speed Nc of 1 is reduced by the sixth control means 43, and when the rotation speed Nc becomes 0, the compressor 101 is stopped, the refrigerant flow rate by the heat pump operation using the compressor 101 is reduced, and the heating is performed. Increase ability. If the rotation speed Ne of the heat engine 113 is not the minimum,
The rotation speed Ne of the heat engine 113 is calculated by the sixth calculation means 39 as shown in FIG.
e is reduced by the fifth control means 40, and if the rotation speed Nh of the hot water transport means 28 is not the minimum, the hot water transport means 2
8 is calculated by the fifth calculating means 36 as shown in FIG.
8 is decreased by the fourth control means 37,
By reducing the flow rate of the hot water flowing through the hot water heat exchanger 10, the amount of heat exchange with the refrigerant is reduced, and the heating capacity is reduced. If the opening degree of the hot water flow rate adjusting means 29 is not the minimum, the opening degree increase / decrease ΔRh of the hot water flow rate adjusting means 29 is calculated by the fourth calculating means 33 as shown in FIG. The opening degree Rh is controlled by the third control
By reducing the flow rate of hot water flowing through the hot water heat exchanger 10, the amount of heat exchange with the refrigerant is reduced, and the heating capacity is reduced. If the rotation speed Nr of the refrigerant transfer means 6 is not the minimum, the rotation speed increase / decrease ΔNr of the refrigerant transfer means 6 is calculated by the third calculation means 26 as shown in FIG. Nr is reduced by the second control means 27, and the heating capacity is reduced by reducing the flow rate of the refrigerant. The throttle opening R of the first throttle means 5
If e1 is not the minimum, the amount of increase or decrease ΔRe1 in the aperture of the first aperture means 5 is calculated by the second calculating means 24 as shown in FIG. Re1 is reduced by the first control means 25.

As described above, according to the present invention, the temperature difference ΔT between the set temperature Tm stored by the first storage means 19 and the room temperature Ts detected by the first temperature detection means 20 is calculated. In order to increase or decrease the heating capacity in accordance with the difference ΔT, the throttle opening Re1 of the first throttle unit 5, the rotation speed Nr of the refrigerant conveying unit 6, the opening Rh of the hot water flow rate adjusting unit 29,
Since the number of revolutions Nh of the hot water conveying means 28, the number of revolutions Ne of the heat engine 113, and the number of revolutions Nc of the compressor 101 can be increased or decreased, it is possible to appropriately perform the heating operation according to the load based on the set temperature in the room. it can.

(Embodiment 12) Next, a twelfth embodiment of the present invention will be described with reference to FIGS. The same parts as those in the first, second, third, fourth, fifth, sixth, seventh, eighth, ninth, tenth, and eleventh embodiments are denoted by the same reference numerals, and detailed description is omitted. .

FIG. 24 is a control block diagram of the air conditioner of the present embodiment, in which a second temperature detection for detecting the refrigerant temperature between the second flow path switching means 2 and the refrigerant heat exchanger 13 is performed. Means 44 means 43 and first pressure detecting means 45 for detecting the refrigerant pressure, the second throttling means 14 and the refrigerant heat exchanger 1
Temperature detecting means 46 for detecting the refrigerant temperature between the third temperature detecting means 46 and the third temperature detecting means 46.
Means 45 for calculating the saturation temperature of the refrigerant from the result of detection by the first pressure detecting means 45.
A ninth calculating means 48 for calculating a difference between a calculation result obtained by the eighth calculating means 47 and a detection result obtained by the second temperature detecting means 44; A seventh determining means 54 for determining the state, and a determination result of the third temperature detecting means 46 means 45 and a detection result of the second temperature detecting means 44 means 43 based on the determination result by the seventh determining means 54. The tenth to calculate the difference
Calculation means 50 and an eighth determination means 5 for determining a temperature difference between refrigerants based on a calculation result by the tenth calculation means 50.
1, a ninth determining means 47 for determining the rotational speed of the compressor 101 based on the determination result by the eighth determining means 51, and an opening of the second throttle means 14 based on the determination result by the ninth determining means 47. A tenth determining means 53 for determining the degree, an eleventh calculating means 54 for calculating the degree of opening of the second throttle means 14 based on the determination result by the tenth determining means 53, and an eleventh calculating means 54 And a seventh control means 55 for controlling the degree of opening of the second throttle means 14 based on the result of the calculation by the second temperature detecting means 44 and the third temperature detecting means 46. Sensor, pressure sensor as first pressure detecting means 45, second temperature detecting means 44, first pressure detecting means 45, third temperature detecting means 46, eighth calculating means 47, ninth calculating means 48 , Seventh
Determination means 49, tenth calculation means 50, eighth determination means 51, ninth determination means 52, tenth determination means 53,
The eleventh arithmetic means 54 and the seventh control means 55 are configured using a microcomputer.

The operation of the above configuration will be described with reference to FIG. FIG. 25 is a control flowchart of the air conditioner of the twelfth embodiment of the present invention, and details will be described along the flow.

The saturation temperature Tsat of the refrigerant flowing into the refrigerant conveying means 6 after passing through the inter-refrigerant heat exchanger 13 is calculated from the pressure detected by the first pressure detecting means 45 to the eighth calculating means 4.
7 is calculated. The calculation of Tsat is derived from an approximate expression built in the microcomputer or a numerical value of a stored saturation temperature table. Tsat, which is the saturation temperature of the refrigerant flowing into the inter-refrigerant heat exchanger 13, and the second temperature detecting means 44
ΔTref = Tsat, which is the temperature difference from the refrigerant temperature Tr1 also flowing into the inter-refrigerant heat exchanger 13 detected by
-Tr1 is calculated by the ninth calculating means 48, and the positive or negative of the calculation result is determined by the seventh determining means 49. ΔT
When ref is negative, the refrigerant is in a two-phase state of gas-liquid mixing in which the degree of supercooling of the refrigerant is not sufficient, and the efficiency of the refrigerant conveying means 6 is reduced. It is determined that there is. Therefore, the temperature Tr1 of the refrigerant flowing into the refrigerant conveying means 6 through the inter-refrigerant heat exchanger 13 detected by the second temperature detecting means 44 and the second throttle detected by the third temperature detecting means 46 ΔTr12 = Tr1-Tr2, which is the temperature difference between the temperatures Tr2 of the refrigerant flowing through the means 14 and flowing into the inter-refrigerant heat exchanger 13, is calculated by the tenth calculating means 5.
The positive and negative of the temperature difference ΔTr12 of the refrigerant are determined by an eighth determining means 51. If ΔTr12 is negative, it means that the temperature of the cooling refrigerant Tr2 is higher than the temperature of the cooling target Tr1, and it is determined that the temperature of the cooling refrigerant Tr2 needs to be lowered. Next, the ninth determination unit 52 determines whether the rotation speed Nc of the compressor 101 is the maximum. If the rotation speed Nc of the compressor 101 is not the maximum, the opening Re2 of the second expansion unit 14 is the maximum. Is there a tenth
If the opening degree Re2 of the second throttle means 14 is not the maximum, the opening increase / decrease ΔRe2 of the second throttle means 14 is calculated by the eleventh calculation means 54 as shown in FIG. From the calculation result, the opening degree Re2 of the second throttle means 14 is increased by the seventh control means 55,
When the opening degree of the throttle means 14 is the maximum, the rotation speed Nc of the compressor 101 is calculated by the seventh calculation means 42 as shown in FIG. The control unit 54 increases the rotation speed Nc of the compressor 101 and increases the flow rate of the refrigerant, thereby lowering the temperature of the cooling refrigerant Tr2. On the other hand, the degree of opening Re2 of the second expansion means 14 is returned to the seventh control means 55 as a value of ΔRe2 if the degree of superheating is obtained, due to the degree of superheating of the refrigerant on the suction side of the compressor 101. If the degree of superheat is not obtained, Δ
A negative value is returned to the seventh control means 55 as Re2. As a result of appropriate superheat control of the compressor 101, the compressor 101
Is improved, and the temperature of Tr2 decreases. When the rotation speed Nc of the compressor 101 is the maximum, the cooling of the refrigerant to be heated by the cooling refrigerant is at a limit, and the degree of supercooling of the refrigerant to be cooled can be obtained by reducing the flow rate of the refrigerant on the refrigerant to be cooled. Therefore, the rotation speed increase / decrease amount ΔNr of the refrigerant conveying means 6 is calculated by the third calculating means 26 as shown in FIG.
decrease r. When ΔTref, which is the determination content of the seventh determination means 49, is positive, and when ΔTr12, which is the determination content of the eighth determination means 51, is positive, the routine proceeds to the eighth routine.
Return to the calculation means.

As described above, according to the present invention, the difference between the saturation temperature Tsat of the refrigerant flowing into the refrigerant conveying means 6 calculated by the eighth calculating means 47 and Tr1 detected by the second temperature detecting means 44 is calculated. And the temperature difference ΔTr12 between the temperature Tr2 of the cooling refrigerant and the temperature Tr1 of the refrigerant to be cooled detected by the third temperature detecting means 46, and determine the degree of supercooling of the refrigerant. Δ
Since the throttle opening Re2 of the second throttle means 14, the rotation speed Nc of the compressor 101, and the rotation speed Nr of the refrigerant conveying means 6 can be increased or decreased so that Tref becomes positive, the efficiency of the refrigerant conveying means 6 decreases. Can be prevented.

(Thirteenth Embodiment) Next, a thirteenth embodiment of the present invention will be described with reference to FIG. The same parts as those of the first, second, third, fourth, fifth, sixth, seventh, eighth, ninth, tenth, eleventh, and twelfth embodiments are designated by the same reference numerals, and detailed description will be given. Is omitted.

FIG. 29 shows that the cooling medium transport means 6 includes the heat engine 11.
The air conditioner has an auxiliary power unit 56 that obtains power using exhaust gas discharged from the air conditioner 3, and uses a turbine as the auxiliary power unit 56.

In the air-conditioning apparatus configured as described above, when performing the normal heating operation or the heating operation at a low load, the compressor 101 is in the stopped state, and the first flow path switching means 1 first operates the refrigerant transfer device. Means 6 to outdoor hot water heat exchanger 1
The refrigerant is switched to zero so that the refrigerant flows, the second flow path switching means 2 switches so that the refrigerant flows from the four-way valve 3 to the refrigerant conveying means 6, and the four-way valve 3 switches to the circuit indicated by the broken line. The exhaust gas discharged from the heat engine 113 collides with a turbine provided on the side opposite to the turbine on the refrigerant transport side of the auxiliary power means 56 connected to the refrigerant transport means 6 and transports the refrigerant via a shaft connecting the two turbines. The refrigerant transporting device 6 that drives the turbine on the side and is driven by electric power supplied from the generator 112 by driving of the heat engine 113 or driven by commercial electric power receives the refrigerant while assisting the power obtained by the auxiliary power means 56 as auxiliary. Discharge. In such a state, the refrigerant is discharged from the refrigerant conveying means 6 and then exchanges heat with the hot water flowing out of the heat engine 113 in the outdoor hot water heat exchanger 10 to absorb the heat of the hot water to become a high-temperature refrigerant. This high-temperature refrigerant passes through the four-way valve 3 and flows into the indoor heat exchanger 8,
The indoor heat exchanger 8 exchanges heat with room air to radiate heat, thereby heating the room. After performing the heat exchange in the indoor heat exchanger 8, the refrigerant sequentially passes from the indoor heat exchanger 8 through the first throttle means 5, the outdoor heat exchanger 4, the four-way valve 3, and the second flow path switching means 2. Flows into the refrigerant conveying means 6 again, and repeats the above operation.

When the heating operation is performed at a low temperature or a high load in a cold region or the like, the refrigerant transfer means 6 is in a stopped state, and the first flow path switching means 1 first sends the compressor 101 a signal from the outdoor hot water heat exchanger 10. The refrigerant is switched to flow to
The second flow path switching means 2 switches so that the refrigerant flows from the four-way valve 3 to the compressor 101, and the four-way valve 3 switches to a circuit indicated by a broken line. Next, the compressor 101 is started, and the refrigerant is first discharged from the compressor 101 to have a high temperature and a high pressure, and then passes through the first flow path switching means 1 and flows into the outdoor hot water heat exchanger 10, where the outdoor hot water heat exchanger At 10, the heat engine 113
It exchanges heat with the warm water flowing out of the furnace, absorbs the heat of the warm water, and becomes a high-temperature refrigerant. After performing heat exchange in the outdoor hot water heat exchanger 10, the refrigerant passes through the four-way valve 3, flows into the indoor heat exchanger 8, and exchanges heat with indoor air in the indoor heat exchanger 8 to radiate heat. To heat. After performing the heat exchange in the indoor heat exchanger 8 in this manner, the refrigerant passes from the indoor heat exchanger 8 through the first throttle means 5 and is passed through the outdoor heat exchanger 4.
And heat exchanges with the outside air in the outdoor heat exchanger 4 to absorb heat and evaporate. After performing the heat exchange in the outdoor heat exchanger 4 in this manner, the refrigerant sequentially passes through the four-way valve 3 and the second flow path switching means 2, flows into the compressor 101 again, and repeats the above operation.

On the other hand, when performing the cooling operation, the refrigerant conveying means 6 is in a stopped state, and the first flow path switching means 1 is switched so that the refrigerant flows from the compressor 101 to the four-way valve 3, and The flow switching means 2 is connected to the compressor 10 from the four-way valve 3.
1 so that the refrigerant circulates, and the four-way valve 3 switches to the circuit indicated by the solid line. In such a state, the compressor 101 is driven by the generator 112 driven by the heat engine 113.
Driven by electric power or commercial power supplied by
The high-temperature and high-pressure refrigerant discharged from the compressor 101 passes through the outdoor hot-water heat exchanger 10 and the four-way valve 3 sequentially, and
And condenses by exchanging heat with the outside air and releasing heat. The condensed refrigerant changes to low-temperature and low-pressure refrigerant when passing through the first throttle means 5 and flows into the indoor heat exchanger 8. The refrigerant that has flowed into the indoor heat exchanger 8 exchanges heat with indoor air in the indoor heat exchanger 8 to absorb heat, thereby cooling the room. After performing heat exchange in the indoor heat exchanger 8, the refrigerant sequentially passes through the four-way valve 3 and the second flow path switching means 2, is sucked into the compressor 101 again, and repeats the above operation.

As described above, according to the present invention, when performing the normal heating operation or the heating operation at a low load, the compressor 10
1 is driven by utilizing the exhaust heat of the heat engine 113 without driving the heating engine 1, and the driving power of the refrigerant conveying means 6 is assisted by the auxiliary power means 56 using the exhaust of the heat engine 113. Since the load is reduced, the power consumption of the refrigerant conveying means 6 can be suppressed.

(Embodiment 14) Next, a fourteenth embodiment of the present invention will be described with reference to FIG. The same parts as those in the first, second, third, fourth, fifth, sixth, seventh, eighth, ninth, tenth, eleventh, twelfth, and thirteenth embodiments have the same numbers, Detailed description is omitted.

FIG. 30 shows that the hot water flow rate adjusting means 29, the hot water conveying means 28, and the indoor hot water heat exchanger 57 are provided in the cooling water circuit.
, A heat engine 113 including a cooling heat exchanger 30, and a blower 31 for blowing air to the cooling heat exchanger 30, a generator 112 driven by the heat engine 113, and a compressor for compressing the refrigerant 101, a four-way valve 3 connected to the discharge side and the suction side of the compressor 101, an outdoor heat exchanger 4 connected to one end of the four-way valve 3 and a second end of the outdoor heat exchanger 4. An outdoor unit 7 including a first throttle means 5 connected by piping, an indoor heat exchanger 8 having one end connected to the four-way valve 3 and the other end connected to the first throttle means, and a hot water transporter And an indoor unit 8 including an indoor hot water heat exchanger 57 through which cooling water conveyed from the means 28 flows. The indoor heat exchanger 8 It is arranged ahead of the hot water heat exchanger 57.

In the air conditioner configured as described above, when performing the dehumidifying operation, first, the four-way valve 3 switches to the circuit shown by the solid line. Next, the compressor 101 is connected to the heat engine 113.
The high-temperature and high-pressure refrigerant discharged from the compressor 101 is driven by the electric power supplied by the generator 112 driven by the compressor, flows into the outdoor heat exchanger 4 through the four-way valve 3, And heat exchange to condense. The condensed refrigerant passes through the first throttle means 5, changes into a low-temperature and low-pressure refrigerant when passing through the first throttle means 5, subsequently flows into the indoor heat exchanger 8, and exchanges indoor heat. The unit 8 exchanges heat with the room air to dehumidify the room air. During this dehumidification process, the air is cooled below the dew point. After performing heat exchange in the indoor heat exchanger 8, the refrigerant passes through the four-way valve 3, flows into the compressor 101 again, and repeats the above operation.

On the other hand, the cooling water which has absorbed the heat of the heat engine 113 discharged by the hot water conveying means 28 and has become high temperature passes through the hot water flow rate adjusting means 29, flows into the indoor hot water heat exchanger 57, and Heat exchange is performed with the cooled air after passing through the exchanger 8 to warm the cooled air in the dehumidification process.
After performing heat exchange in the indoor hot water heat exchanger 57, the hot water flows into the heat engine 113 again, and the above operation is repeated.

When the cooling operation is performed, the hot water flow rate adjusting means 29 is fully closed, and the high-temperature cooling water that has absorbed the heat of the heat engine 113 does not flow into the indoor hot-water heat exchanger 57. It flows into the cooling heat exchanger 30 and is cooled by radiating heat in the cooling heat exchanger 30, flows into the heat engine 113 again, and repeats the above operation. Then, the four-way valve 3 is switched to a circuit shown by a solid line, and the compressor 101 is driven by electric power or commercial electric power supplied from a generator 112 driven by a heat engine 113, and is a high-temperature and high-pressure refrigerant discharged from the compressor 101. Passes through the four-way valve 3, flows into the outdoor heat exchanger 4, exchanges heat with the outside air, and condenses by radiating heat. After performing the heat exchange in the outdoor heat exchanger 4 in this manner, the refrigerant passes through the first throttle unit 5, and when passing through the first throttle unit 5, changes into a low-temperature low-pressure refrigerant. It flows into the heat exchanger 8. The refrigerant that has flowed into the indoor heat exchanger 8 exchanges heat with indoor air in the indoor heat exchanger 8 and absorbs heat to cool the room. After performing heat exchange in the indoor heat exchanger 8, the refrigerant passes through the four-way valve 3, is sucked into the compressor 101 again, and repeats the above operation.

When performing the normal heating operation or the heating operation at a low load, the compressor 101 is in a stopped state,
The high-temperature cooling water that has absorbed the heat of the heat engine 113 discharged by the hot water conveying means 28 and passed through the hot water flow rate adjusting means 29, flows into the indoor hot water heat exchanger 57, and Heats the room by exchanging heat with room air and releasing heat. After performing heat exchange in the indoor hot water heat exchanger 57, the hot water flows into the heat engine 113 again, and the above operation is repeated.

When the heating operation is performed at a low temperature or a high load in a cold region or the like, first, the four-way valve 3 is switched to a circuit indicated by a broken line. Next, the compressor 101 is connected to the heat engine 11.
The high-temperature and high-pressure refrigerant discharged from the compressor 101 is driven by the electric power supplied by the generator 112 driven by the compressor 3, passes through the four-way valve 3, flows into the indoor heat exchanger 8, and exchanges heat with indoor air. The room is heated by radiating heat. The refrigerant after performing the heat exchange in the indoor heat exchanger 8 as described above passes through the first throttle unit 5, and changes into a low-temperature and low-pressure refrigerant when passing through the first throttle unit 5, It flows into the outdoor heat exchanger 4. The refrigerant flowing into the outdoor heat exchanger 4 exchanges heat with the outside air in the outdoor heat exchanger 4 to absorb heat and evaporate. The refrigerant having undergone heat exchange in the outdoor heat exchanger 4 passes through the four-way valve 3 and is sucked into the compressor 101 again, and the above operation is repeated.

If the heating capacity is still insufficient even in the above-mentioned heating operation, the hot water discharged from the hot water conveying means 28 and absorbing the exhaust heat of the heat engine 113 and heated to a high temperature is appropriately cooled by the hot water flow rate adjusting means 29. After the flow rate is adjusted to a suitable value, the air flows into the indoor hot water heat exchanger 57, where the exhaust heat of the cooling water is radiated to the air passing through the indoor heat exchanger 8 to further warm the air and secure the heating capacity. I do. The cooling water that has exchanged heat in the indoor hot water heat exchanger 57 in this way flows into the heat engine 113 again, and repeats the above operation.

As described above, according to the present invention, the indoor air absorbed and dehumidified by the indoor heat exchanger 8 as the evaporator of the heat pump is converted into the hot water in the outdoor hot water heat exchanger as the cooling circuit of the heat engine 113. Since heating can be performed by heat radiation, the dehumidifying operation can be performed without lowering the room temperature.

(Embodiment 15) Next, a fifteenth embodiment of the present invention will be described with reference to FIGS. 14, 31 and 32. FIG. The same parts as those in the first, second, third, fourth, fifth, sixth, seventh, eighth, ninth, tenth, eleventh, twelfth, and thirteenth embodiments have the same numbers, Detailed description is omitted.

FIG. 31 is a control block diagram of the air conditioner of the present embodiment.
Storage means 19, a first temperature detection means 20 provided in the indoor unit 9 for detecting an indoor temperature, and a difference between a value detected by the first storage means 19 and a value detected by the first temperature detection means 20. A first calculating means 21 for calculating, and a hot water flow rate adjusting means 29 based on a calculation result by the first calculating means 21.
And a third control means 34 for controlling the degree of opening of the hot water flow rate adjusting means 29 based on the result of calculation by the fourth calculating means 33. I have.

The operation of the above configuration will be described with reference to FIG. FIG. 32 is a control flowchart of the air conditioner of the fifteenth embodiment of the present invention, and details will be described along the flow.

The temperature difference ΔT = Tm−Ts between the set temperature Tm stored by the first storage means 19 and the room temperature Ts detected by the first temperature detection means 20 is calculated by the first calculation means 2.
When the calculation result ΔT is positive, it means that the heating capacity is insufficient. Therefore, the opening / closing amount ΔRh of the hot water flow rate adjusting means 29 is calculated by the fourth calculating means 33 as shown in FIG. Then, the opening degree of the hot water flow rate adjusting means 29 is increased by the third control means 34 based on the calculation result.
On the other hand, if ΔT, which is the result of the calculation by the first calculating means 21, is negative, it means that the heating capacity is excessive, and the fourth calculating means 33 determines the amount of increase / decrease ΔRh of the hot water flow rate adjusting means 29 as shown in FIG. The opening degree of the hot water flow rate adjusting means 29 is reduced by the third control means 34 based on the calculation result.

As described above, according to the present invention, the temperature difference ΔT between the set temperature Tm stored by the first storage means 19 and the room temperature Ts detected by the first temperature detection means 20 is calculated, and this temperature difference is calculated. Since the opening Rh of the hot water flow rate adjusting means 29 can be increased or decreased so that the heating capacity can be increased or decreased in accordance with ΔT, a change in the room temperature can be suppressed and the dehumidifying operation can be performed.

(Embodiment 16) Next, a sixteenth embodiment of the present invention will be described with reference to FIG. 14, FIG. 17, FIG. 33 and FIG. The first, second, third, fourth, fifth, sixth, seventh, eighth, ninth, tenth, eleventh, and first
The same parts as those in the second, thirteenth, fourteenth, and fifteenth embodiments have the same reference numerals, and a detailed description thereof will be omitted.

FIG. 33 is a control block diagram of the air conditioner of this embodiment. The fourth judgment means 35 for judging the degree of opening of the hot water flow rate adjusting means 29 and the judgment result by the fourth judgment means 35 are shown. A configuration including fifth calculating means 36 for calculating the number of rotations of the hot water conveying means 28, and fourth control means 37 for controlling the number of rotations of the hot water conveying means 28 based on the calculation result by the fifth calculating means 36. It has become.

The operation of the above configuration will be described with reference to FIG. FIG. 34 is a control flowchart of the air conditioner of the sixteenth embodiment of the present invention, and details will be described along the flow.

The temperature difference ΔT = Tm−Ts between the set temperature Tm stored by the first storage means 19 and the room temperature Ts detected by the first temperature detection means 20 is calculated by the first calculation means 2
1, if the calculation result ΔT is positive, it means that the heating capacity is insufficient.
5 is used to determine whether the opening Rh of the hot water flow rate adjusting means 29 is the maximum. If the opening degree Rh of the hot water flow rate adjusting means 29 is the maximum, the rotation speed of the hot water conveying means 28 is increased so as to further increase the hot water circulation amount. The increase / decrease amount ΔNh is calculated by the fifth calculating means 36 as shown in FIG. 17, and from this calculation result, the rotation speed Nh of the hot water transport means 28 is increased by the fourth control means 37 and the opening degree of the refrigerant flow rate adjusting means 29 is increased. If Rh is not the maximum, the opening / closing amount ΔRh of the hot water flow rate adjusting means 29 is calculated by the fourth calculating means 33 as shown in FIG. It is increased by the control means 34. On the other hand, if ΔT, which is the result of calculation by the first calculating means 21, is negative, it means that the heating capacity is excessive, and the fourth calculating means 33 determines the amount of increase / decrease ΔRh of the water flow rate adjusting means 29. The calculation is performed as shown in FIG. 14, and the opening degree Rh of the hot water flow rate adjusting means 29 is reduced by the third control means 34 based on the calculation result.

As described above, according to the present invention, the temperature difference ΔT between the set temperature Tm stored by the first storage means 19 and the room temperature Ts detected by the first temperature detection means 20 is calculated, and this temperature difference is calculated. Since the opening Rh of the hot water flow rate adjusting means 29 and the rotation speed Nh of the hot water conveying means 28 can be increased or decreased so that the heating capacity can be increased or decreased in accordance with ΔT, the change in the room temperature can be suppressed with high accuracy and the dehumidification can be performed. Driving can be performed.

(Embodiment 17) Next, a seventeenth embodiment of the present invention will be described with reference to FIG. The first, second, third, fourth, fifth, sixth, seventh, eighth, ninth, tenth, eleventh, twelfth, thirteenth, fourteenth, and fifteenth
The same parts as those of the sixteenth embodiment are denoted by the same reference numerals, and detailed description is omitted.

FIG. 35 shows two indoor heat exchangers 8a and 8b.
, Two indoor hot water heat exchangers 57a, 57b, two first throttle means 5a, 5b, and two hot water flow control valves 2.
9a, 29b.

In the air conditioner configured as described above, when the indoor unit 9a performs a cooling operation and the indoor unit 9b performs a heating operation, first, the indoor hot water heat exchange provided in the indoor unit 9a that performs the cooling operation is performed. The hot water flow rate adjusting means 29a connected to the heater 57a is fully closed, and the first throttle means 5b connected to the indoor heat exchanger 8b provided in the indoor unit 9b performing the heating operation is fully closed,
The four-way valve 3 switches to the circuit shown by the solid line. In such a state, the high-temperature and high-pressure refrigerant discharged from the compressor 101 passes through the four-way valve 3 and flows into the outdoor heat exchanger 4, where the outdoor heat exchanger 4 exchanges heat with the outside air and condenses. After performing the heat exchange in the outdoor heat exchanger 4 in this manner, the refrigerant is
After passing through the first throttle means 5a connected to the indoor heat exchanger 8a performing the cooling operation, when passing through the first throttle means 5a, it becomes a low-temperature and low-pressure refrigerant and flows into the indoor heat exchanger 8a. The room is cooled by absorbing the heat of the room air in the heat exchanger 8a. After performing the heat exchange in the indoor heat exchanger 8a in this manner, the refrigerant passes through the four-way valve 3,
It flows into the compressor 101 again, and the above operation is repeated.

On the other hand, the heat of the heat engine 113 discharged by the hot water conveying means 28 is absorbed, and the high-temperature cooling water passes through the hot water flow rate adjusting means 29b connected to the indoor hot water heat exchanger 57b for performing the heating operation. And the indoor hot water heat exchanger 57b
To heat the room by exchanging heat with room air in the room hot water heat exchanger 57b to radiate heat. The hot water that has exchanged heat in the indoor hot water heat exchanger 57b flows into the heat engine 113 again and repeats the above operation.

When the indoor unit 9a performs the heating operation and the indoor unit 9b performs the cooling operation, the hot water flow rate adjusting means 29b is fully closed and the first throttle means 5a is fully closed, and the operation is performed in the same manner as described above. You.

When both the indoor units 9a and 9b perform the cooling operation, the hot water flow rate adjusting means 29a and 29b are fully closed, the heat of the heat engine 113 is absorbed, and the high-temperature cooling water is supplied to the indoor hot water heat exchangers 57a and 57b. Does not flow into the heat exchanger 30, but flows into the cooling heat exchanger 30, radiates heat in the cooling heat exchanger 30, is cooled, flows again into the heat engine 113, and repeats the above operation. Then, the four-way valve 3 switches to the circuit shown by the solid line, and then the compressor 101 is driven by the electric power or the commercial power supplied by the generator 112 driven by the heat engine 113, and the high-temperature and high-pressure discharged from the compressor 101 Passes through the four-way valve 3, flows into the outdoor heat exchanger 4, exchanges heat with the outside air in the outdoor heat exchanger 4, and condenses by radiating heat. After performing the heat exchange in the outdoor heat exchanger 4 in this manner, the refrigerant passes through the first throttle means 5a and 5b, and when passing through the first throttle means 5a and 5b, turns into a low-temperature low-pressure refrigerant. And then flows into the indoor heat exchangers 8a and 8b. The refrigerant that has flowed into the indoor heat exchangers 8a and 8b exchanges heat with indoor air in the indoor heat exchangers 8a and 8b to absorb heat, thereby cooling the room. Indoor heat exchanger 8
a, after the heat exchange in 8b, the refrigerant
And is sucked into the compressor 101 again to repeat the above operation.

In the case where the indoor units 9a and 9b perform the heating operation, and when the heating operation is performed in the normal heating operation or when the load is low, the compressor 101 is in the stopped state and the heat discharged by the hot water conveying means 28 is stopped. The cooling water that has become high temperature by absorbing the heat of the engine 113 is supplied to the hot water flow rate adjusting means 29.
a, 29b, and passes through the indoor hot water heat exchangers 57a, 57b.
To heat the room by exchanging heat with room air in the room hot water heat exchangers 57a and 57b to radiate heat. After performing the heat exchange in the indoor hot water heat exchangers 57a and 57b, the hot water flows into the heat engine 113 again, and the above operation is repeated.

Next, when the heating operation is performed at a low temperature or a high load in a cold district or the like, first, the four-way valve 3 is switched to a circuit indicated by a broken line. Next, the compressor 101 is connected to the heat engine 11.
The high-temperature and high-pressure refrigerant discharged from the compressor 101 is driven by the electric power supplied by the generator 112 driven by the compressor 3, and flows through the four-way valve 3, flows into the indoor heat exchangers 8a and 8b, and is cooled by the indoor air and heat. The room is heated by exchanging and radiating heat. After performing the heat exchange in the indoor heat exchangers 8a and 8b in this manner, the refrigerant flows into the first throttle means 5a and 5b.
When passing through the first throttle means 5a, 5b, the refrigerant changes into a low-temperature, low-pressure refrigerant and flows into the outdoor heat exchanger 4. The refrigerant flowing into the outdoor heat exchanger 4 exchanges heat with the outside air in the outdoor heat exchanger 4 to absorb heat and evaporate. After performing heat exchange in the outdoor heat exchanger 4, the refrigerant is supplied to the four-way valve 3.
, And is sucked into the compressor 101 again, and the above operation is repeated.

If the heating capacity is insufficient even in the above-described heating operation, the cooling water discharged by the hot water conveying means 28 and having a high temperature by absorbing the exhaust heat of the heat engine 113 is supplied to the hot water flow adjusting means 29a, 29b. After adjusting to an appropriate flow rate by
The air flows into the indoor hot water heat exchangers 57a and 57b, and the exhaust heat of the cooling water is radiated to the air passing through the indoor heat exchangers 8a and 8b to further warm the air and secure the heating capacity. Thus, the indoor hot water heat exchangers 57a,
The cooling water that has exchanged heat in 7b flows into the heat engine 113 again, and repeats the above operation.

As described above, according to the present invention, the compressor 101
Is independent of the heating circuit using the heat radiation of the cooling water of the heat engine 113, so that cooling and heating can be simultaneously operated between the two indoor units.

The first throttle means 5a and 5b, the indoor heat exchangers 8a and 8b, the indoor units 9a and 9b, the hot water flow rate adjusting means 29a and 29b, and the indoor hot water heat exchanger 57
a and 57b are provided two each.
The same operation and effect can be obtained with more than one configuration.

[0168]

As is clear from the above embodiments, according to the present invention, during heating operation, heating is performed by using the exhaust heat of the heat engine without driving the compressor, so that power consumption can be reduced. It is possible to provide an air conditioner having an effect that a low-capacity heating operation can be performed.

In the heating operation, the interior of the room can be heated by using the exhaust heat of the heat engine without driving the compressor, and the refrigerant circulates without passing through the four-way valve. Thus, it is possible to provide an air conditioner having an effect of performing a low-capacity heating operation while suppressing power consumption to be small.

When the heating operation is performed in a normal heating operation or at a low load, the heating operation is performed using the exhaust heat of the heat engine without driving the compressor. Since the air conditioner does not pass through the exchanger, it is possible to provide an air conditioner having an effect of performing low-capacity heating operation while suppressing power consumption without being affected by the pressure loss of the four-way valve and the outdoor heat exchanger.

Further, when the heating operation is performed in a normal heating operation or at a low load, the refrigerant on the suction side of the refrigerant conveying means is cooled so as to be always a liquid refrigerant. An air conditioner having an effect of being able to be provided can be provided.

Further, the efficiency of the turbo engine is increased by increasing the specific weight of the air on the intake side of the turbo engine by exchanging heat with the refrigerant on the air on the intake side of the turbo engine and cooling by utilizing the evaporation heat of the refrigerant. An air conditioner having an effect of being able to be improved can be provided.

Further, the heating circuit using the exhaust heat of the heat engine and the cooling circuit as the ordinary heat pump are switched between the first flow path switching means, the second flow path switching means, the fifth flow path switching means, and the sixth flow path switching means. Since the air conditioner is made independent by switching the flow path switching means, it is possible to provide an air conditioner having an effect that cooling and heating can be simultaneously operated between two indoor units.

Also, the temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated, and the heating capacity can be increased or decreased in accordance with this temperature difference. Since the opening degree of the throttle means and the number of revolutions of the refrigerant conveying means can be increased or decreased, an air conditioner having the effect of being able to perform a heating operation properly according to the load based on the set temperature in the room. Can be provided.

Further, a temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated, and the heating capacity can be increased or decreased in accordance with the temperature difference. Since the opening degree of the throttle means, the rotation speed of the refrigerant conveying means, and the opening degree of the hot water flow rate adjusting means can be increased or decreased, the heating operation can be accurately performed according to the load based on the set temperature in the room. An air conditioner having such an effect can be provided.

Further, a temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated, and the heating capacity can be increased or decreased in accordance with the temperature difference. 1, the opening degree of the throttle means, the rotation speed of the refrigerant conveying means, the opening degree of the hot water flow rate adjusting means, and the rotation speed of the hot water conveying means can be increased or decreased. An air conditioner having an effect of performing a heating operation can be provided.

Further, a temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated, and the heating capacity can be increased or decreased in accordance with the temperature difference. (1) Since it is possible to increase or decrease the throttle opening degree of the throttle means, the rotation speed of the refrigerant transfer means, the opening degree of the hot water flow rate adjustment means, the rotation speed of the hot water transfer means, and the rotation speed of the heat engine, the indoor setting can be accurately performed. An air conditioner having an effect of performing a heating operation according to a load depending on temperature can be provided.

Further, a temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated, and the heating capacity can be increased or decreased in accordance with the temperature difference. 1, the opening degree of the throttle means, the rotation speed of the refrigerant transfer means, the opening degree of the hot water flow rate adjustment means, the rotation speed of the hot water transfer means, the rotation speed of the heat engine, and the rotation speed of the compressor can be increased or decreased. It is possible to provide an air conditioner having an effect that a heating operation can be appropriately performed according to a load based on a set temperature in a room.

The supercooling degree of the refrigerant obtained by calculating the difference between the saturation temperature of the refrigerant flowing into the refrigerant conveying means calculated by the eighth calculating means and the temperature detected by the second temperature detecting means, The temperature difference between the temperature of the cooling refrigerant detected by the temperature detecting means and the temperature of the refrigerant to be cooled is determined, and the degree of supercooling of the refrigerant is determined to be positive, but the degree of opening of the second restricting means is positive. Since the number of revolutions of the compressor and the number of revolutions of the refrigerant conveying means can be increased or decreased, it is possible to provide an air conditioner having an effect of preventing a decrease in the efficiency of the refrigerant conveying means.

When the heating operation is performed in a normal heating operation or at a low load, the heating operation is performed by using the exhaust heat of the heat engine without driving the compressor, and the driving power of the refrigerant conveying means is assisted. Since the driving load is reduced by using the exhaust of the heat engine by the power means to assist, it is possible to provide an air conditioner having an effect that the power consumption of the refrigerant conveying means can be suppressed.

Further, the indoor air absorbed and dehumidified by the indoor heat exchanger as the evaporator of the heat pump can be heated by the heat radiation of the hot water in the outdoor hot water heat exchanger as the cooling circuit of the heat engine. An air conditioner having an effect that a dehumidifying operation can be performed without lowering the room temperature can be provided.

The temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated, and the flow rate of the hot water is increased or decreased so that the heating capacity can be increased or decreased in accordance with the temperature difference. Since the opening degree of the adjusting means can be increased or decreased, it is possible to provide an air conditioner having an effect of suppressing a change in room temperature and performing a dehumidifying operation.

Further, a temperature difference between the set temperature stored by the first storage means and the room temperature detected by the first temperature detection means is calculated, and the flow rate of the hot water is increased or decreased so as to increase or decrease the heating capacity in accordance with the temperature difference. Since the degree of opening of the adjusting means and the number of rotations of the hot water conveying means can be increased or decreased, it is possible to provide an air conditioner having an effect of suppressing a change in room temperature with high accuracy and performing a dehumidifying operation.

Further, since the heat pump circuit using the compressor and the heating circuit using the heat radiation of the cooling water of the heat engine are made independent, cooling and heating can be simultaneously operated between the two indoor units. An air conditioner can be provided.

[Brief description of the drawings]

FIG. 1 is a refrigeration cycle diagram of an air conditioner according to Embodiment 1 of the present invention.

FIG. 2 is a refrigeration cycle diagram of the air-conditioning apparatus according to Embodiment 2 of the present invention.

FIG. 3 is a refrigeration cycle diagram of the air-conditioning apparatus according to Embodiment 3 of the present invention.

FIG. 4 is a refrigeration cycle diagram of the air-conditioning apparatus according to Embodiment 4 of the present invention.

FIG. 5 is a refrigeration cycle diagram of the air-conditioning apparatus according to Embodiment 5 of the present invention.

FIG. 6 is a refrigeration cycle diagram of the air-conditioning apparatus according to Embodiment 6 of the present invention.

FIG. 7 is a control block diagram of an air conditioner according to a seventh embodiment of the present invention.

FIG. 8 is a control flowchart of the air conditioner.

FIG. 9 is a graph showing the amount of increase / decrease of the opening degree of the first throttle means with respect to the difference between the set temperature and the room temperature.

FIG. 10 is a graph showing the amount of increase / decrease in the number of revolutions of the refrigerant conveying means with respect to the difference between the set temperature and the room temperature.

FIG. 11 is a refrigeration cycle diagram of the air-conditioning apparatus according to Embodiment 8 of the present invention.

FIG. 12 is a control block diagram of the air conditioner.

FIG. 13 is a control flowchart of the air conditioner.

FIG. 14 is a graph showing the amount of increase or decrease in the opening degree of the hot water flow rate adjusting means with respect to the difference between the set temperature and the room temperature.

FIG. 15 is a control block diagram of an air conditioner according to a ninth embodiment of the present invention.

FIG. 16 is a control flowchart of the air conditioner.

FIG. 17 is a graph showing an increase / decrease in the number of revolutions of the hot water conveying means with respect to a difference between a set temperature and a room temperature.

FIG. 18 is a control block diagram of an air conditioner according to Embodiment 10 of the present invention.

FIG. 19 is a control flowchart of the air conditioner.

FIG. 20 is a graph showing an increase / decrease in the number of revolutions of a heat engine with respect to a difference between a set temperature and a room temperature.

FIG. 21 is a control block diagram of an air conditioner according to Embodiment 11 of the present invention.

FIG. 22 is a control flowchart of the air conditioner.

FIG. 23 is a graph showing an increase / decrease in the number of revolutions of a compressor with respect to a difference between a set temperature and a room temperature.

FIG. 24 is a control block diagram of an air conditioner according to Embodiment 12 of the present invention.

FIG. 25 is a control flowchart of the air conditioner.

FIG. 26 is a graph showing a second relationship between the temperature difference between the cooling refrigerant and the refrigerant to be cooled;
Graph showing the amount of increase / decrease in the opening degree of the throttle means

FIG. 27 is a graph showing an increase / decrease in the number of revolutions of the compressor with respect to a temperature difference between the cooling refrigerant and the refrigerant to be cooled;

FIG. 28 is a graph showing the amount of increase or decrease in the number of revolutions of the refrigerant conveying means with respect to the temperature difference between the cooling refrigerant and the refrigerant to be cooled.

FIG. 29 is a refrigeration cycle diagram of the air-conditioning apparatus according to Embodiment 13 of the present invention.

FIG. 30 is a refrigeration cycle diagram of the air-conditioning apparatus according to Embodiment 14 of the present invention.

FIG. 31 is a control block diagram of an air conditioner according to Embodiment 15 of the present invention.

FIG. 32 is a control flowchart of the air conditioner.

FIG. 33 is a control block diagram of an air conditioner according to Embodiment 16 of the present invention.

FIG. 34 is a control flowchart of the air conditioner.

FIG. 35 is a refrigeration cycle diagram of the air-conditioning apparatus according to Embodiment 17 of the present invention.

FIG. 36 is a refrigeration cycle diagram of a conventional air conditioner.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 1st flow-path switching means 2 2nd flow-path switching means 3 Four-way valve 4 Outdoor heat exchanger 5 1st throttling means 5a 1st throttling means 5b 1st throttling means 6 Refrigerant conveyance means 7 Outdoor unit 8 Indoor heat exchanger 8a Indoor heat exchanger 8b Indoor heat exchanger 9 Indoor unit 10 Outdoor hot water heat exchanger 11 Third flow switching means 12 Fourth flow switching means 13 Inter-refrigerant heat exchanger 14 Second throttle Means 15 Turbo engine 16 Intake cooling heat exchanger 17 Fifth flow switching means 17a Fifth flow switching means 17b Fifth flow switching means 18 Sixth flow switching means 18a Sixth flow switching means 18b Sixth flow switching means 19 First storage means 20 First temperature detecting means 21 First calculating means 22 First determining means 23 Second determining means 24 Second calculating means 25 First control Means 26 Third Performance Calculation means 27 Second control means 28 Hot water transport means 29 Hot water flow rate adjustment means 29a Hot water flow rate adjustment means 29b Hot water flow rate adjustment means 30 Cooling heat exchanger 31 Blowing means 32 Third determination means 33 Fourth calculation means 34 Third control means 35 Fourth determination means 36 Fifth calculation means 37 Fourth control means 38 Fifth determination means 39 Sixth calculation means 40 Fifth control means 41 Sixth determination means 42 Seventh Calculation means 43 Sixth control means 44 Second temperature detection means 45 First pressure detection means 46 Third temperature detection means 47 Eighth calculation means 48 Ninth calculation means 49 Seventh determination means 50 Tenth Calculation means 51 Eighth determination means 52 Ninth determination means 53 Tenth determination means 54 Eleventh determination means 55 Seventh control means 56 Auxiliary power means 57 Indoor hot water heat exchanger 5 7a Indoor hot water heat exchanger 57b Indoor hot water heat exchanger 101 Compressor 112 Generator 113 Heat engine

Claims (19)

[Claims] 1. An air conditioner capable of heating a room by circulating a CFC-based refrigerant having recovered exhaust heat using a refrigerant conveying means without using a compressor. 2. A heat engine having a cooling water circuit cooled by cooling water, a generator driven by the heat engine, a compressor for compressing a refrigerant, and piping connected to a discharge side of the compressor. A first flow switching means, a second flow switching means connected to the suction side of the compressor by piping, and a pipe connected to one end of the first flow switching means and one end of the second flow switching means. A four-way valve, an outdoor heat exchanger connected to one end of the four-way valve by piping, a first throttle unit connected to the other end of the outdoor heat exchanger by piping, and a first flow switching unit. The other end and the second
An outdoor unit comprising a refrigerant conveying means connected to the other end of the flow path switching means by piping, one end connected to the four-way valve by piping, and the other end connected to the first throttle means by piping. An indoor unit including an indoor heat exchanger, and an outdoor hot water heat exchanger for exchanging heat between the refrigerant on the discharge side of the refrigerant conveying means and the cooling water of the heat engine, 2. A room can be heated by utilizing exhaust heat of the heat engine without driving the compressor.
The air conditioner according to any one of the preceding claims. 3. An outdoor hot water heat exchanger is disposed on the discharge side of the refrigerant conveying means, a first flow path switching means is disposed between the four-way valve and the indoor heat exchanger, and a second flow path switching means is provided. Is disposed between the four-way valve and the outdoor heat exchanger, and the outdoor hot water heat exchanger and the refrigerant conveying means are connected to the other end of the first flow path switching means and the second
The configuration provided between the other end of the flow path switching means and the refrigerant can heat the room using the exhaust heat of the heat engine without passing the refrigerant through the four-way valve during heating. 3. The air conditioner according to 1 or 2. 4. An outdoor hot water heat exchanger is disposed on the discharge side of the refrigerant conveying means, a first flow path switching means is disposed between the four-way valve and the indoor heat exchanger, and a second flow path switching means is provided. Is disposed between the outdoor heat exchanger and the first throttle means, and the outdoor hot water heat exchanger and the refrigerant transfer means are connected to the other end of the first flow path switching means and the second flow path switching means. By using a configuration provided between the heat exchanger and the other end of the heat engine, it is possible to heat the room using the exhaust heat of the heat engine without passing the refrigerant through the four-way valve and the outdoor heat exchanger during heating. Item 3. The air conditioner according to item 1 or 2. 5. A method according to claim 5, further comprising a third flow path switching means between the outdoor heat exchanger and the second flow path switching means, and a fourth flow path between the four-way valve and the first flow path switching means. A refrigerant flowing between the second flow path switching means and the refrigerant conveying means, and a refrigerant flowing between the third flow path switching means and the fourth flow path switching means. Equipped with an inter-refrigerant heat exchanger for heat exchange,
By providing the second throttle means between the inter-refrigerant heat exchanger and the third flow path switching means, the refrigerant on the suction side of the refrigerant transfer means is cooled during heating to transfer the refrigerant. 5. The air conditioner according to claim 1, wherein the efficiency of the means is prevented from being reduced. 6. A turbo engine as a heat engine, and intake air cooling for exchanging heat between air on the intake side of the turbo engine and refrigerant flowing between the third flow path switching means and the fourth flow path switching means. By adopting a configuration with a heat exchanger,
The air conditioner according to claim 1, wherein the air on the intake side of the turbo engine is cooled to improve the efficiency of the turbo engine. 7. A plurality of fifth flow path switching means comprising a plurality of first throttle means and a plurality of indoor heat exchangers, wherein a plurality of fifth flow path switching means are provided between said plurality of first throttling means and second flow path switching means. Means between the plurality of indoor heat exchangers and the first flow path switching means.
And a pipe between the outdoor heat exchanger and the second flow path switching means is branched and connected to a plurality of the fifth flow path switching means, and the first flow path switching means is provided. The cooling and heating can be simultaneously operated between a plurality of indoor units by making a configuration in which a pipe between the means and the four-way valve is branched and connected to the plurality of sixth flow path switching means. 5. The air conditioner according to 2 or 4. 8. A control means for performing a heating operation appropriately in accordance with a load in a room so that a heating capacity can be increased or decreased in accordance with a temperature difference between a set temperature and a room temperature.
The air conditioner according to 5, 6, or 7. 9. A first storage means for storing and outputting an indoor set temperature, a first temperature detection means provided in an indoor unit for detecting an indoor temperature, a value detected by the first storage means, and First calculating means for calculating a difference from a value detected by the first temperature detecting means, first determining means for determining a result of the calculation by the first calculating means, and a determination result by the first determining means A second judging means for judging the degree of opening of the first restricting means, a second calculating means for calculating the degree of opening of the first restricting means from the result of the judgment by the second judging means, First control means for controlling the degree of throttle opening of the first throttle means on the basis of the result of calculation by the second calculation means; and third control means for calculating the rotational speed of the refrigerant transport means from the result of determination by the second determination means. Calculation means and the calculation result by the third calculation means A second control unit for controlling the number of revolutions of the refrigerant conveying unit.
The air conditioner according to 3, 4, 5, 6, 7, or 8. 10. A cooling water circuit of a heat engine, comprising: a hot water flow rate adjusting means, a hot water conveying means, a hot water heat exchanger, a cooling heat exchanger, and a blowing means for blowing air to the cooling heat exchanger. A third judging means for judging the rotation speed of the refrigerant conveying means from the judgment result by the second judging means, and a fourth judging means for calculating an opening of the hot water flow rate adjusting means from the judgment result by the third judging means. And a third control means for controlling an opening degree of the hot water flow rate adjusting means based on a calculation result by the fourth calculation means.
10. The air conditioner according to 7, 8, or 9. 11. A fourth judging means for judging the degree of opening of the hot water flow rate adjusting means based on the judgment result by the third judging means, and calculating the rotation speed of the hot water conveying means from the judgment result by the fourth judging means. 5. A device according to claim 1, further comprising: fifth calculating means, and fourth control means for controlling the number of revolutions of said hot water conveying means based on a result of calculation by said fifth calculating means.
The air conditioner according to 5, 6, 7, 8, 9 or 10. 12. A fifth judging means for judging the rotation speed of the hot water conveying means from the judgment result by the fourth judging means, and a sixth judging means for calculating the rotation speed of the heat engine from the judgment result by the fifth judging means. And a fifth control means for controlling the number of revolutions of the heat engine based on a result of the calculation by the sixth calculation means.
The air conditioner according to 8, 9, 10 or 11. 13. A sixth determining means for determining the rotational speed of the heat engine from the determination result by the fifth determining means, and a seventh calculating means for calculating the rotational speed of the compressor from the determination result by the sixth determining means. 9. The computer according to claim 1, further comprising: a calculating means, and sixth control means for controlling a rotation speed of said compressor based on a result of calculation by said seventh calculating means. , 9,
13. The air conditioner according to 10, 11, or 12. 14. A second temperature detecting means for detecting a refrigerant temperature and a first pressure detecting means for detecting a refrigerant pressure are provided between the second flow path switching means and the inter-refrigerant heat exchanger. A third temperature detecting means for detecting a refrigerant temperature between the throttle means and the inter-refrigerant heat exchanger, and an eighth calculating means for calculating a saturation temperature of the refrigerant from a detection result by the first pressure detecting means. Calculating means, a ninth calculating means for calculating a difference between a calculation result by the eighth calculating means and a detection result by the second temperature detecting means, and a state of the refrigerant based on a calculation result by the ninth calculating means. A seventh judging means for judging, and a tenth calculation for calculating a difference between the detection result by the third temperature detecting means and the detection result by the second temperature detecting means based on the judgment result by the seventh judging means. Means and the calculation result by the tenth calculation means. Determining means for determining the temperature difference between the refrigerants, ninth determining means for determining the rotational speed of the compressor based on the determination result by the eighth determining means, and determination results by the ninth determining means. A tenth determining means for determining the opening degree of the second throttle means, an eleventh calculating means for calculating the opening degree of the second throttle means from the determination result by the tenth determining means, 9. The air conditioner according to claim 1, further comprising: seventh control means for controlling an opening degree of said second throttle means based on a calculation result by an eleventh calculation means. 15. The refrigerant conveying means is provided with an auxiliary power means for obtaining power using exhaust gas discharged from the heat engine, whereby power consumption of the refrigerant conveying means can be suppressed.
2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12,
15. The air conditioner according to 13 or 14. 16. The cooling water circuit includes a hot water flow rate adjusting means, a hot water conveying means device, a hot water heat exchanger, a cooling heat exchanger, and a blowing means for blowing air to the cooling heat exchanger. A heat engine, a generator driven by the heat engine, a compressor for compressing a refrigerant, a four-way valve connected to a discharge side and a suction side of the compressor, and a pipe connected to one end of the four-way valve. An outdoor unit comprising: an outdoor heat exchanger; and first throttle means connected to the other end of the outdoor heat exchanger by piping.
An indoor heat exchanger having one end connected to the four-way valve and the other end connected to the first throttle means, and an indoor hot water heat exchanger through which cooling water conveyed from the hot water conveyance means flows. An indoor unit is configured to heat the air dehumidified and cooled by the indoor heat exchanger with the indoor hot water heat exchanger using exhaust heat of the heat engine during the dehumidifying operation, thereby reducing the room temperature without lowering the room temperature. Air conditioner that can dehumidify air. 17. A first system for storing and outputting a set temperature in a room.
A first temperature detecting means provided in the indoor unit for detecting an indoor temperature, and calculating a difference between a value detected by the first storing means and a value detected by the first temperature detecting means. A first calculating means for calculating an opening degree of the hot water flow rate adjusting means from a result of the calculation by the first calculating means;
17. The air conditioner according to claim 8, further comprising: a calculating unit configured to calculate an opening degree of the hot water flow rate adjusting unit based on a calculation result obtained by the fourth calculating unit. 18. A fourth determining means for determining an opening of the hot water flow rate adjusting means, a fifth calculating means for calculating a rotation speed of the hot water conveying means from a result of the determination by the fourth determining means,
18. The air conditioner according to claim 8, further comprising: fourth control means for controlling the number of revolutions of the hot water transport means based on a calculation result by the fifth calculation means. 19. A configuration comprising a plurality of indoor heat exchangers, a plurality of indoor hot water heat exchangers, a plurality of first throttling means, and a plurality of hot water flow control valves, thereby providing a plurality of indoor heat exchangers. 19. The air conditioner according to claim 16, 17 or 18, wherein cooling and heating can be simultaneously operated between units.