JPH08233397A - Air-conditioning device - Google Patents

Abstract

PURPOSE: To perform effective utilization of energy of the drive source of a compressor even when a radiation amount of a condenser is increased to an excessive value compared with a heat absorbing amount of a vaporizer by a method wherein a heat feed part on the indoor machine side and a heat feed part on the outdoor machine side are provided and heat is fed to a refrigerant from the heat feed part on the outdoor machine side. CONSTITUTION: Since, during heating operation, three-way valve A allows the flow of cooling water to a direction 2, a flow rate q1 of cooling water is fed through a cooling water line 4e to a double pipe heat-exchanger 11 and a quantity ΔQ is exerted on a refrigerant flowing therethrough. In which case, the refrigerant is heated by a quantity of ΔQ and all is vaporized for gasification and further, overheating thereof is effected. In this case, the refrigerant flows through a double pipe heat-exchanger 11 to a four-way valve 5. The refrigerant flows through a four-way valve 5 to a suction line 3b side and guided to an accumulator 6. Gas and liquid of the refrigerant are separated by the accumulator 6 and a gas phase refrigerant is sucked to a compressor 2. This constitution with a compressor left driven, cooling or heating operation is practicable and energy of the drive source of the compressor is effectively utilized.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner provided with a heat supply section capable of supplying heat to a refrigerant from the outside.

[0002]

2. Description of the Related Art An air conditioner has at least a switching unit such as a compressor, a four-way valve, an indoor heat exchanger (hereinafter referred to as an indoor unit), an expansion valve and an outdoor heat exchanger in a refrigerant circuit for circulating a refrigerant. , The outdoor unit) is provided, but during heating operation, the refrigerant circulates through the refrigerant circuit in the order of the compressor, the switching unit, the indoor unit that functions as a condenser, the expansion valve, and the outdoor unit that functions as an evaporator. To do. Also, during cooling operation,
The refrigerant circulates through the refrigerant circuit in the order of the compressor, the switching unit, the outdoor unit functioning as a condenser, the expansion valve and the indoor unit functioning as an evaporator.

By the way, when the heating capacity is insufficient due to insufficient heat radiation in the indoor unit during the heating operation, and when the outdoor unit can hardly absorb heat due to the low outside air temperature, the refrigerant remains in the compressor without being vaporized. It will be sucked in and cause a malfunction of the compressor. Therefore, when the driving of the compressor is stopped, heating by circulating the refrigerant becomes impossible. In such a case, there has been proposed a method of compensating for the shortage with the heat value of the auxiliary heater (that is, a method of directly warming the room with the auxiliary heater without passing through a refrigerant) (Japanese Patent Laid-Open No. 5-25).
6496 publication).

[0004]

However, according to the above method, even if the auxiliary heater enables heating, the power source for driving the compressor cannot be used, and from the viewpoint of effective use of energy. Is not an advantage.

Even during the cooling operation, if the amount of heat dissipated in the outdoor unit is too large and therefore the amount of heat absorbed in the indoor unit is not sufficient, the drive source of the compressor cannot be effectively utilized as well. Becomes

The present invention has been made in view of the above problems, and an object of the present invention is that the heat radiation amount of the condenser is excessively large in comparison with the heat absorption amount of the evaporator in the cooling operation or the heating operation. However, it is still another object of the present invention to provide an air conditioner that can drive a compressor as it is and effectively utilize the energy of the drive source.

[0007]

In order to achieve the above object, the invention according to claim 1 is directed to a compressor-side refrigerant circuit from a suction line to a compressor to a discharge line, a suction line end and a discharge line end. A switching unit connected to the unit, an indoor unit side refrigerant circuit from the switching unit to the expansion valve via the indoor unit, and an outdoor unit side refrigerant circuit from the switching unit to the expansion valve via the outdoor unit, The switching unit connects the discharge line and the indoor unit side refrigerant circuit in the heating state and the suction line and the outdoor unit side refrigerant circuit in the heating state, and connects the discharge line and the outdoor unit side refrigerant circuit in the cooling state. In the air conditioner that connects the suction line and the indoor unit side refrigerant circuit, the indoor unit side heat supply unit capable of supplying heat to the refrigerant from the outside, the outdoor unit side heat supply unit the indoor unit side refrigerant circuit,
Each of them is provided in the outdoor unit side refrigerant circuit, and heat can be supplied to the refrigerant from the outdoor unit side heat supply unit in the heating state, and / or heat can be supplied to the refrigerant from the indoor unit side heat supply unit in the cooling state. And

According to a second aspect of the present invention, in the first aspect of the invention, heat can be supplied to the refrigerant from the indoor unit side heat supply section and the outdoor unit side heat supply section, and at the same time, in the heating state, the outdoor unit side. The heat supply amount from the heat supply unit to the refrigerant is set to be larger than the heat supply amount from the indoor unit side heat supply unit to the refrigerant.

According to a third aspect of the present invention, in the invention according to the first or second aspect, heat can be supplied to the refrigerant from the indoor unit side heat supply section and the outdoor unit side heat supply section, and in the cooling state, the indoor The heat supply amount from the machine-side heat supply unit to the refrigerant is set to be larger than the heat supply amount from the outdoor unit-side heat supply unit to the refrigerant.

The invention according to a fourth aspect is characterized in that, in the invention according to the first, second or third aspect, the indoor unit side heat supply section is arranged inside the indoor unit or between the indoor unit and the switching section. .

A fifth aspect of the present invention is characterized in that, in the first to third or fourth aspects of the invention, the outdoor unit side heat supply unit is arranged in the outdoor unit or between the outdoor unit and the switching unit. .

[0012]

According to the invention as set forth in claim 1, in both the cooling operation and the heating operation, the shortage of the heat absorption amount in the indoor unit or the outdoor unit functioning as the evaporator is given from the outside in the heat supply unit. Because it is supplemented by, the refrigerant is completely evaporated and vaporized before it is sucked into the compressor,
Therefore, the liquid-phase refrigerant is not sucked into the compressor, the cooling or heating operation can be performed while the compressor is driven, and the energy of the drive source of the compressor can be effectively used.

According to the second aspect of the invention, the amount of heat supplied from the outdoor unit side heat supply unit to the refrigerant in the heating state is made larger than the amount of heat supply from the indoor unit side heat supply unit to the refrigerant. Is low, therefore even if the heat absorption amount of the refrigerant in the outdoor unit is not sufficient, all of the refrigerant is completely evaporated and vaporized before being sucked by the compressor, and the liquid phase refrigerant to the compressor Suction is reliably prevented.

According to the third aspect of the present invention, the amount of heat supplied from the indoor unit side heat supply unit to the refrigerant in the cooling state is made larger than the amount of heat supply from the outdoor unit side heat supply unit to the refrigerant. Even if the amount of heat dissipation in the indoor unit is excessive and the amount of heat absorbed in the indoor unit is not sufficient, the insufficient amount of heat is given to the refrigerant in the indoor unit side heat supply unit, so the refrigerant is compressed. All of them are completely evaporated and vaporized before being sucked into, and the suction of the liquid phase refrigerant to the compressor is surely prevented.

According to the fourth aspect of the invention, since the indoor unit side heat supply section is provided on the downstream side of the expansion valve, the indoor unit side heat supply section supplies the low temperature and low pressure refrigerant passing through the expansion valve. Since heat is given, the efficiency of supplying heat to the refrigerant is increased.

According to the fifth aspect of the invention, since the outdoor unit side heat supply section is provided on the downstream side of the expansion valve, the outdoor unit side heat supply section supplies the low temperature and low pressure refrigerant passing through the expansion valve. Since heat is given, the efficiency of supplying heat to the refrigerant is increased.

[0017]

Embodiments of the present invention will be described below with reference to the accompanying drawings.

<First Embodiment> FIG. 1 is a circuit diagram showing the basic construction of an engine-driven air conditioner according to a first embodiment of the present invention, and FIG. 2 is a characteristic diagram of a linear three-way valve provided in a cooling water circuit. FIG. 3 is a Mollier diagram showing changes in the state of the refrigerant.

In FIG. 1, 1 is a water-cooled engine, 2 is a compressor driven by the engine 1, and this air conditioner cools the engine 1 and the refrigerant circuit 3 that includes the compressor 2 and forms a closed loop. A coolant water circuit 4 for circulating cooling water is included.

The refrigerant circuit 3 is a circuit for circulating a refrigerant such as CFC by the compressor 2, which is the compressor 2
Discharge line 3a from the discharge side to the four-way valve 5 and the four-way valve 5
To the compressor 2 via the accumulator 6 to the compressor 2, a compressor side refrigerant circuit 3A, an indoor unit side refrigerant circuit 3B from the four-way valve 5 to the indoor unit 7 to the expansion valve 8, and a four-way valve The outdoor unit side refrigerant circuit 3C from 5 to the expansion valve 8 via the outdoor unit 9 is included.

Thus, in this embodiment, a double-tube heat exchanger 10 constituting an indoor unit side heat supply section is provided between the four-way valve 5 of the indoor unit side refrigerant circuit 3B and the indoor unit 7. The
Further, a double-tube heat exchanger 1 constituting an outdoor unit side heat supply section is provided between the outdoor unit 9 and the four-way valve 5 of the outdoor unit side refrigerant circuit 3C.
1 is provided. As shown in FIG. 1, a room temperature sensor 12 and two refrigerant temperature sensors 13 and 14 are provided indoors, and an outside air temperature sensor 15 is provided outdoors.

On the other hand, the cooling water circuit 4 is a circuit in which the cooling water for cooling the engine 1 is circulated by a cooling water pump 16, which passes from the discharge side of the cooling water pump 16 through the exhaust gas heat exchanger 17. The cooling water line 4a reaching the cooling water inlet of the engine 1, the cooling water line 4b reaching the double pipe heat exchanger 10 through the cooling water jacket 1a of the engine 1 and the cooling from the double pipe heat exchanger 10. The cooling water line 4c reaching the water pump 16 is included.
A linear three-way valve 18 having the characteristics shown in FIG. 2 is provided in the middle of the cooling water line 4b, and a cooling water line 4d branched from the linear three-way valve 18 and connected to the cooling water line 4c is provided. A radiator 19 is provided on the way. A three-way valve A is provided downstream of the linear three-way valve 18 in the cooling water line 4b, and the cooling water line 4e connected to the three-way valve A is connected to the double pipe heat exchanger 11. The cooling water line 4f led out from the double pipe heat exchanger 11 is connected to the cooling water line 4c.

The engine 1 has a thermostat 100.
When the engine 1 is in the cold state immediately after starting, the thermostat 100 detects that the temperature of the cooling water is low, and the cooling water jacket 1a and the cooling water line 4b are connected to each other. To the communication state with the cooling water line 4g. As a result, the cooling water is circulated only between the cooling water jacket 1a and the exhaust gas heat exchanger 17, and the engine 1 can be warmed up. At this time, the cooling water pump 16 is stopped.
Further, the discharge directions of the cooling water pumps 16 and 101 may be reversed. In this case, the thermostat 100 senses the cylinder wall temperature and switches between the communication state between the cooling water lines 4b and 4a and the communication state between the cooling water lines 4b and 4g.

Next, the operation of the air conditioner according to this embodiment during the heating operation will be described with reference to the Mollier diagram shown in FIG.

When the compressor 2 is driven by the engine 1, the state shown by a in FIG. 3 (pressure P ₁ , enthalpy i
The gas-phase refrigerant of ₁ ) is sucked into the compressor 2 through the suction line 3b and compressed, and becomes a high-temperature high-pressure refrigerant in a state (pressure P ₂ , enthalpy i ₂ ) shown in b of FIG. The required power of the compressor 2 (output of the engine 1) AL at this time is (i ₂
-I ₁ ).

Thus, the high-temperature and high-pressure gas-phase refrigerant reaches the four-way valve 5 through the discharge line 3a, but during heating operation, as shown by the broken line in FIG. b and ports c and d are in communication with each other, therefore
The high temperature and high pressure vapor phase refrigerant flows to the indoor unit side refrigerant circuit 3B,
It is guided to the indoor unit 7 that functions as a condenser.

As described above, the high-temperature and high-pressure gas-phase refrigerant introduced into the indoor unit 7 releases the condensation heat Q ₂ to the indoor air to be liquefied and supercooled (subcooled) to be in the state c shown in FIG. It becomes a liquid-phase refrigerant of (pressure P ₂ , enthalpy i ₃ ), and the amount of heat radiation Q ₂ (= i ₂ −i ₃ ) at this time heats the room.

Thus, the high-pressure liquid-phase refrigerant liquefied in the indoor unit 7 is decompressed by the expansion valve 8 and becomes a state (pressure P ₁ , enthalpy i ₃ ) shown in FIG. Is vaporized and guided to the outdoor unit 9 that functions as an evaporator.

Here, in this embodiment, since the outside air temperature is low, the refrigerant in the outdoor unit 9 takes away the heat of vaporization of Q ₁ from the outside air and only a part thereof is vaporized. The state indicated by e (pressure P ₁ , enthalpy i ₄ ) is introduced to the double-tube heat exchanger 11. The amount of heat of evaporation Q _{1 at} this time is represented by (i ₄ −i ₃ ).

On the other hand, the cooling water circulating in the cooling water circuit 4 by the driving of the cooling water pump 16 is discharged from the cooling water pump 16 and flows through the cooling water line 4a, and in the middle of the process, in the exhaust gas heat exchanger 17, the engine After collecting and heating the heat of the exhaust gas discharged from the engine 1, the engine 1 is cooled through the cooling water jacket 1a of the engine 1. Then, the cooling water used for cooling the engine 1 flows through the cooling water line 4b and reaches the three-way valve 18. The three-way valve 18 corresponds to the heat load of the double pipe heat exchanger 10 or 11 described later. 2 shows the characteristics shown in FIG. 2, and the cooling water amount q upstream of the three-way valve 18
Is q ₁ depending on the heat load of the double-tube heat exchanger 10 or 11.
(Amount of cooling water flowing to the double-tube heat exchanger 10 or 11) and q
₂ (the amount of cooling water flowing through the radiator 19), the cooling water having a flow rate q ₁ flowing through the double-tube heat exchanger 10 or 11 heats the refrigerant flowing therethrough while being cooled by the refrigerant,
The cooling water having a flow rate q ₂ flowing through the radiator 19 radiates heat to the atmosphere, returns to the cooling water pump 16, and thereafter circulates in the cooling water circuit 4 similarly.

The three-way valve A switches the flow direction of the cooling water to the direction shown in FIG.
Flow direction of cooling water during cooling operation and heating operation,
Are switched as shown in Table 1.

[0032]

[Table 1] Thus, as shown in Table 1, the three-way valve A allows the flow of cooling water in the direction of the heating operation, so that the cooling water having the flow rate q ₁ passes through the cooling water line 4e and the double pipe heat exchanger. 11
To the refrigerant flowing therethrough and giving a heat quantity ΔQ ₁ . Then, the refrigerant is heated by the heat quantity ΔQ ₁ , all of it is evaporated and vaporized, and further superheated (superheat) to return to the state (pressure P ₁ , enthalpy i ₁ ) shown in a of FIG. At this time, the heat quantity ΔQ ₁ given to the refrigerant from the cooling water in the double-tube heat exchanger 10 is (i ₁ −i ₄ ).
(See FIG. 3).

After that, the refrigerant reaches the four-way valve 5 from the double-pipe heat exchanger 11, but as described above, the four-way valve 5 is operated during the heating operation.
Because the ports c and d of the
Flow toward the suction line 3b through the accumulator 6
Be led to. And in the accumulator 6,
The gas-liquid of the refrigerant is separated, the gas-phase refrigerant is sucked into the compressor 2, and thereafter, the same operation as described above is repeated to be used for heating the room.

In the above heating operation, since the heat absorption amount Q ₁ of the refrigerant in the outdoor unit 9 from the outside air is small due to the low outside air temperature, when only the heat absorption amount Q ₁ does not vaporize all the refrigerant in the outdoor unit 9. However, since the refrigerant is given a heat quantity ΔQ ₁ in the double-tube heat exchanger 11, all of the refrigerant evaporates and vaporizes. At this time, in the double-pipe heat exchanger 11, since the heat quantity ΔQ ₁ is applied from the cooling water to the refrigerant that has passed through the expansion valve 8 and has become the low temperature and low pressure, the efficiency of supply of the heat quantity ΔQ _{1 to} the refrigerant is improved. To be enhanced.

Therefore, in this embodiment, even if the outside air temperature is low and therefore the heat absorption amount Q ₁ of the refrigerant in the outdoor unit 9 is not sufficient, the suction of the liquid phase refrigerant to the compressor 2 is prevented. Therefore, the compressor 2 can be driven as it is to perform the heating operation, the energy of the engine 1 can be effectively used, and an auxiliary heater or the like for directly heating the room is not required.

Next, the operation of the present air conditioner during the cooling operation will be described with reference to the Mollier diagram shown in FIG.

When the compressor 2 is driven by the engine 1, the state indicated by a in FIG. 3 (pressure P ₁ , enthalpy i
The gas-phase refrigerant of ₁ ) is compressed by the compressor 2 to be b in FIG.
The high-temperature high-pressure refrigerant in the state (pressure P ₂ , enthalpy i ₂ ) indicated by ( ₃ ) reaches the four-way valve 5 through the discharge line 3 a.
In the cooling operation, the ports a and c of the four-way valve 5 and the ports b and d of the four-way valve 5 are in communication with each other, as shown by the solid line in FIG.
It flows to C. Here, in the cooling operation, as shown in Table 1, since the three-way valve A allows only the flow in the direction of the cooling water, the cooling water is not supplied to the double pipe heat exchanger 11,
Therefore, the refrigerant that has passed through the four-way valve 5 is guided as it is to the outdoor unit 9 that functions as a condenser.

The high-temperature and high-pressure gas-phase refrigerant introduced to the outdoor unit 9 releases the condensation heat Q ₂ to the outside air, is liquefied, and is supercooled.
It becomes a liquid-phase refrigerant in the state of c (pressure P ₂ , enthalpy i ₃ ) shown in FIG. The condensation heat Q _{2 at} this time is (i ₂ −i ₃ ).
It is represented by.

The high-pressure liquid-phase refrigerant liquefied in the outdoor unit 9 is depressurized by passing through the expansion valve 8,
After becoming a state (pressure P ₁ and enthalpy i ₃ ) shown in FIG. 3 by a part of which vaporizes, the indoor unit 7 functioning as an evaporator is reached, where the heat of evaporation Q ₁ is removed from the indoor air. Part of that is taken and vaporized, and the state shown by e in FIG. 3 (pressure P
₁ and enthalpy i ₄ ).

By the way, during the cooling operation, as shown in Table 1, the three-way valve A allows the flow of the cooling water in the direction of the cooling water. Therefore, the refrigerant passing through the indoor unit 7 reaches the double pipe heat exchanger 10, The amount of heat from the cooling water flowing there ΔQ ₁ (= i ₁ −i
₄ ) is applied, all of it evaporates and vaporizes, and is further heated to the state of a shown in FIG. 3 (pressure P ₁ , enthalpy i).
Return to ₁ ). At this time, in the double-pipe heat exchanger 10, the heat quantity ΔQ ₁ is applied from the cooling water to the refrigerant that has passed through the expansion valve 8 and has become low temperature and low pressure, so that the supply efficiency of the heat quantity ΔQ _{1 to} the refrigerant is improved. To be enhanced.

The refrigerant passing through the double-tube heat exchanger 10 reaches the four-way valve 5, but since the ports b and d of the four-way valve 5 communicate with each other during the cooling operation as described above, the refrigerant is four-way. It flows through the valve 5 to the suction line 3b side and is guided to the accumulator 6. Then, in the accumulator 6, the gas-liquid of the refrigerant is separated, the gas-phase refrigerant is sucked into the compressor 2, and thereafter, the same operation as described above is repeated to be used for indoor cooling.

When the heat radiation amount Q ₂ in the outdoor unit 9 is excessive during the cooling operation and the heat absorption amount Q ₁ in the indoor unit 7 is not sufficient for that reason, the heat amount ΔQ _{1 for the} shortage is two. Since the refrigerant is completely vaporized by being given by the cooling water in the heavy-tube heat exchanger 10, suction of the liquid-phase refrigerant to the compressor 2 is prevented. Therefore, even in the cooling operation, the compressor 2 can be driven as it is, and the energy of the engine 1 can be effectively used.

In this embodiment, the cooling water supply amount to the double-tube heat exchanger 10 is set to 0 during the heating operation, and the cooling water supply amount to the double-tube heat exchanger 11 is set to 0 during the cooling operation. However, a linear three-way valve is installed in place of the three-way valve A, and the supply amount of cooling water to the double-tube heat exchanger 10 is limited during the heating operation to restrict the refrigerant in the other double-tube heat exchanger 11. The heat supply amount to the double-tube heat exchanger 10 is made larger than that in the double-tube heat exchanger 10, and the supply amount of cooling water to the double-tube heat exchanger 11 is limited during the cooling operation to limit the other double-tube heat exchange. The heat supply amount to the refrigerant in the vessel 10 may be made larger than that in the double-tube heat exchanger 11.

Further, in this embodiment, the double tube heat exchangers 10 and 1 are
1 is provided between the four-way valve 5 of the indoor unit side refrigerant circuit 3B and the indoor unit 7 and between the four-way valve 5 of the outdoor unit side refrigerant circuit 3C and the outdoor unit 9, respectively. You may provide in each inside the machine 9.

In the above cooling operation, when the amount of heat radiated in the outdoor unit 9 is excessive and therefore the amount of heat absorbed in the indoor unit 7 is sufficient, the insufficient amount of heat (the refrigerant passing through the expansion valve 8 is Since the heat quantity necessary for complete vaporization ΔQ ₁ is given by the cooling water in the double-tube heat exchanger 10, the suction of the liquid-phase refrigerant to the compressor 2 is prevented. Therefore, even in the cooling operation, the compressor 2 can be driven as it is,
The energy of the engine 1 can be effectively used.

Further, in this case, the pressure on the high pressure side, which is the upstream side of the expansion valve 8, excessively decreases, so that the amount of the refrigerant passing through the expansion valve 8 excessively decreases, and the heat absorption by the indoor unit 7 on the low pressure side occurs. However, since the double-tube heat exchanger 10 can apply heat to the refrigerant, the enthalpy at the suction port of the compressor 2 increases, and as a result, the high pressure side It is possible to prevent a decrease in pressure at the temperature, and to prevent a decrease in the circulation amount of the refrigerant.

The condensation heat Q ₂ in FIG. 3 is not only released from the refrigerant only in the indoor unit 7 in the heating state or the outdoor unit 9 in the cooling state, but also from the discharge port of the compressor 2 to the expansion valve 8. It includes all the amount of heat released in the high pressure side refrigerant pipe. Similarly, the heat of vaporization Q ₁
Is not only absorbed by the refrigerant only in the outdoor unit 9 in the heating state or the indoor unit 7 in the cooling state, but is also absorbed by the refrigerant in the low pressure side refrigerant circuit from the expansion valve 8 to the suction port of the compressor 2. It includes the amount of heat. However, the engine cooling water is piped in the liquid-phase refrigerant stored in the accumulator instead of the positions where the double-tube heat exchangers 10 and 11 and the two devices are arranged. It is not included in the amount of heat absorbed by the refrigerant by the heater for heating the refrigerant using water or the auxiliary refrigerant heater such as an electric heater. The heat load is ΔQ ₁
And ΔQ ₁ = Q ₂ −Q ₁ −AL.

[0048] That is, whether the condensation heat Q ₂ becomes excessive relative to the heat of evaporation Q _1, if the heat of evaporation Q ₁ is made too small relative to the condensing heat Q _2, the thermal load is increased, the auxiliary coolant heater It is necessary to heat the refrigerant by.

For example, in the case of, there may be a case where the number of indoor units 7 to be operated is reduced in the cooling state when the number of indoor units 7 is greater than the number of outdoor units 9. In this case, the heat dissipation capacity of the outdoor unit 9 becomes considerably larger than the heat absorption capacity of the indoor unit 7. Therefore, as shown in FIG. 9, based on the cooling information from the cooling / heating changeover switch 102, the three-way valve A drive actuator 109 is caused to output a drive command based on Table 1 from the control device 200, and the indoor unit operation switch 103 is operated from the indoor unit operation switch 103. 7, the linear three-way valve 18 drive actuator 1 assumes that the thermal load is larger as the number of operating vehicles is less than a predetermined value and the number of operating vehicles is smaller.
08 is driven to increase the circulating amount of hot water to the double tube heat exchanger 10.

Further, in the case of, based on the outside air temperature information from the outside air temperature sensor 15 during cooling, when the outside air temperature is lower than the predetermined temperature, the lower the temperature is, the higher the condensation heat Q ₂ is, so that the heat load is large. However, similarly, the circulation amount of hot water to the double-tube heat exchanger 10 may be increased.

In the above case, the larger the difference between the set temperature of the indoor temperature setting switch 104 during heating and the indoor temperature detected by the indoor temperature sensor 12, the larger the fan 1 of the indoor unit 7.
It is also possible to increase the number of revolutions of 12 and increase the amount of hot water circulating to the double-tube heat exchanger 11 on the assumption that the heat load is large.

Further, in the case of, based on the outside air temperature information from the cooling outside air temperature sensor 15, when the outside air temperature is below a predetermined temperature, the condensation heat Q ₂ becomes smaller as the temperature is lower than the predetermined temperature, and in some cases Q _{Since 2} becomes negative, the fan 113 of the outdoor unit 9 may be stopped and the hot water circulation amount to the double-tube heat exchanger 11 may be similarly increased.

When the high-pressure side pipe is longer than the low-pressure side pipe, Q ₂ becomes excessive during cooling. In this case, the installer of the air conditioner operates the pipe layout correction switch 105. The control device 200 may correct the increase in heat load due to the information of the switch 105 and the cooling operation information by increasing the circulating amount of hot water to the double-tube heat exchanger 10.

Further, only the high pressure side pressure value of the high pressure side pressure sensor 106 on the upstream side of the expansion valve 8 or the low pressure side pressure sensor 1 on the low pressure side of the expansion valve 8 as a boundary.
Based on the pressure difference from the low pressure side pressure value of 07, the opening degree of the expansion valve 8 is increased as the high pressure side pressure value becomes lower or the differential pressure becomes smaller, or the double pipe heat exchanger 10 is cooled during cooling. It is also possible to increase the circulating amount of hot water to the double pipe heat exchanger 11 during heating or to increase both the opening degree of the expansion valve 8 and the circulating amount.

Both pressure sensors 106 are arranged on the compressor 2 side with the four-way valve 5 as a boundary (see FIG. 1). However, both pressure sensors 106, 1 are arranged on the side of the expansion valve 8 with the four-way valve 5 as a boundary.
When the pressure sensors 106 and 107 are arranged in both the refrigerant circuit on the indoor unit 7 side and the refrigerant circuit on the outdoor unit 9 with the expansion valve 8 as the boundary, the information of the cooling / heating changeover switch 102 is set to the information. Based on the above, the control device is configured such that the pressure sensor arranged in the refrigerant circuit of the indoor unit 7 is on the high pressure side during heating and the pressure sensor arranged on the refrigerant circuit on the outdoor unit 9 side is on the low pressure side, and is reversed during cooling. Determined by 200.

<Second Embodiment> Next, a second embodiment of the present invention will be described with reference to FIGS. 4 is a circuit diagram showing the basic configuration of the engine-driven air conditioner according to the second embodiment, and FIG. 5 is a Mollier diagram showing changes in the state of the refrigerant. In FIG. 4, the same as shown in FIG. The same reference numerals are given to the elements, and description thereof will be omitted below.

In this embodiment, as shown in FIG.
The double-tube heat exchanger 10 which is the indoor unit side heat supply unit is provided between the indoor unit 7 and the expansion valve 8 of the indoor unit side refrigerant circuit 3B, and the double-tube heat exchanger 11 which is the outdoor unit side heat supply unit. Is provided between the outdoor unit 9 of the outdoor unit side refrigerant circuit 3B and the expansion valve 8.

Thus, according to the present embodiment, the refrigerant that has passed through the expansion valve 8 during the heating operation and the cooling operation is as shown in FIG.
First, as shown in FIG.
1. During the cooling operation, the heat quantity ΔQ ₁ (= i ₄ −i ₃ ) is given from the cooling water in the double-tube heat exchanger 10 to be in the state indicated by e (pressure P ₁ , enthalpy i ₄ ), and then evaporation In the outdoor unit 9 (during heating operation) or the indoor unit 7 (during cooling operation) that functions as a heater, the heat quantity Q from the outside air or indoor air
₁ (= i ₁ −i ₄ ) is taken away, all of it evaporates and vaporizes, and is further heated to the state shown by a in FIG. 5 (pressure P ₁ ,
Return to enthalpy i ₁ ).

<Third Embodiment> Next, a third embodiment of the present invention will be described with reference to FIG. FIG. 6 is a circuit diagram showing the basic configuration of the engine-driven air conditioner according to the third embodiment. In this figure, the same elements as those shown in FIG. A description thereof will be omitted.

In this embodiment, as shown in FIG.
The double-tube heat exchanger 10, which is an indoor unit side heat supply unit, is provided between the four-way valve 5 of the indoor unit-side refrigerant circuit 3B and the indoor unit 7, and the double-tube heat exchanger is an outdoor unit side heat supply unit. 11 is provided between the outdoor unit 9 of the outdoor unit side refrigerant circuit 3B and the expansion valve 8.

Thus, according to the present embodiment, the refrigerant passing through the expansion valve 8 is first heated in the double pipe heat exchanger 11 from the cooling water in the heating operation ΔQ ₁ (= i) as shown in FIG.
₄₋ i ₃ ) is applied and the state indicated by e (pressure P ₁ , enthalpy i ₄ ) is reached, and thereafter, in the outdoor unit 9 functioning as an evaporator, the heat quantity Q ₁ (= i ₁ −i ₄ ) from the outside air or the like.
, And all of them are vaporized and vaporized, and further heated to return to the state (pressure P ₁ , enthalpy i ₁ ) shown by a in FIG.

On the other hand, during the cooling operation, the refrigerant having passed through the expansion valve 8 first robs the heat quantity Q ₁ (= i ₄ −i ₃ ) in the indoor unit 7 and a part thereof is vaporized. The state indicated by e (pressure P ₁ , enthalpy i ₄ ) is reached, and thereafter, the amount of heat ΔQ ₁ from the cooling water in the double-tube heat exchanger 10 is increased.
(= I ₁ −i ₄ ), all of them are vaporized and vaporized, and further heated to a state (pressure P ₁ ,
Return to enthalpy i ₁ ).

That is, according to this embodiment, the cycle shown in FIG. 5 is executed during the heating operation, and the cycle shown in FIG. 2 is executed during the cooling operation.

<Fourth Embodiment> Next, a fourth embodiment of the present invention will be described with reference to FIG. FIG. 7 is a circuit diagram showing the basic structure of the engine-driven air conditioner according to the fourth embodiment. In this figure, the same elements as those shown in FIG. 1 are designated by the same reference numerals. A description thereof will be omitted.

In this embodiment, as shown in FIG.
The double-tube heat exchanger 10 which is the indoor unit side heat supply unit is provided between the indoor unit 7 and the expansion valve 8 of the indoor unit side refrigerant circuit 3B, and the double unit heat exchanger which is the outdoor unit side heat supply unit. 11 is provided between the four-way valve 5 of the outdoor unit side refrigerant circuit 3B and the outdoor unit 9.

Thus, according to this embodiment, the refrigerant having passed through the expansion valve 8 first robs the heat quantity Q ₁ (= i ₄ −i ₃ ) in the outdoor unit 9 as shown in FIG. 2 during the heating operation. Then, a part of it is vaporized to a state indicated by e (pressure P ₁ , enthalpy i ₄ ), and thereafter, the heat quantity ΔQ ₁ (= i ₁ −i ₄ ) is given from the cooling water in the double tube heat exchanger 11. All of them are evaporated and vaporized, and further heated to return to the state (pressure P ₁ , enthalpy i ₁ ) shown by a in FIG.

On the other hand, during the cooling operation, the refrigerant passing through the expansion valve 8 is first given a heat quantity ΔQ ₁ (= i ₄ −i ₃ ) from the cooling water in the double tube heat exchanger 10 as shown in FIG. Then, a part of it is vaporized to a state indicated by e (pressure P ₁ , enthalpy i ₄ ), and thereafter, the heat quantity Q ₁ (= i ₁ −i ₄ ) is taken in the indoor unit 7 and all of it is evaporated. The state shown by a in FIG. 5 after vaporization and further heating (pressure P ₁ ,
Return to enthalpy i ₁ ).

That is, according to this embodiment, contrary to the third embodiment, the cycle shown in FIG. 2 is executed during the heating operation,
During the cooling operation, the cycle shown in FIG. 5 is executed.

<Fifth Embodiment> Next, a fifth embodiment of the present invention will be described with reference to FIG. FIG. 8 is a circuit diagram showing the basic structure of the engine-driven air conditioner according to the fifth embodiment. In this figure, the same elements as those shown in FIG. A description thereof will be omitted.

In this embodiment, as shown in FIG.
The tank 20 that constitutes the indoor unit side heat supply unit is provided between the four-way valve 5 of the indoor unit side refrigerant circuit 3B and the indoor unit 7, and the tank 21 that constitutes the outdoor unit side heat supply unit is the outdoor unit side refrigerant circuit 3C.
It is provided between the four-way valve 5 and the outdoor unit 9.

Thus, in this embodiment, during the heating operation, the three-way valve A permits the flow of the cooling water in the direction shown in Table 1, so that the cooling water is supplied to the tank 21. 21 functions as an accumulator, and imparts a heat quantity ΔQ ₁ to the liquid-phase refrigerant stored therein.

Further, during the cooling operation, the three-way valve A permits the flow of the cooling water in the direction shown in Table 1, so that the cooling water is supplied to the tank 20. Therefore, the tank 20 functions as an accumulator. A heat quantity ΔQ ₁ is applied to the liquid-phase refrigerant stored therein.

Therefore, in this embodiment, the cycle shown in FIG. 2 is executed during the heating and cooling operations, and the first
The same operation and effect as the embodiment can be obtained.

Also in each of the embodiments shown in FIGS. 4, 6, 7 and 8, the controller 200 determines the magnitude of the heat load based on the information of the sensor group or the switch group as described above, and each actuator Is driven to switch the three-way valve A depending on whether it is cold or warm, and the circulating amount of hot water to the double-tube heat exchanger 10 or 11 or the tank 20 or 21 is increased or decreased according to the magnitude of the heat load, or electricity is supplied. The amount of electric power supplied to the heater 115 (see FIG. 9) is increased or decreased.

Note that, instead of the four-way valve 5, two three-way valves E and F are arranged as shown in FIG. 10. During heating, the three-way valve E side opens the communication and the communication closes the side, and the three-way valve F side. The communication may be closed, the communication may be opened, and the control may be reversed when cooling.

[0076]

As is apparent from the above description, claim 1
According to the described invention, in both the cooling operation and the heating operation, the shortage of the heat absorption amount in the indoor unit or the outdoor unit functioning as an evaporator is compensated for by the heat given from the outside in the heat supply unit, so that the refrigerant Is completely evaporated and vaporized before being sucked into the compressor, so that the liquid-phase refrigerant is not sucked into the compressor, and cooling or heating operation can be performed with the compressor being driven, The effect that the energy of the drive source of the compressor can be effectively used is obtained.

According to the second aspect of the invention, since the heat supply amount from the outdoor unit side heat supply unit to the refrigerant is made larger than the heat supply amount from the indoor unit side heat supply unit in the heating state, the outside air temperature Is low, therefore even if the heat absorption amount of the refrigerant in the outdoor unit is not sufficient, all of the refrigerant is completely evaporated and vaporized before being sucked by the compressor, and the liquid phase refrigerant to the compressor The effect that suction can be reliably prevented is obtained.

According to the third aspect of the present invention, the amount of heat supplied from the indoor unit side heat supply unit to the refrigerant in the cooling state is made larger than the amount of heat supply from the outdoor unit side heat supply unit to the refrigerant. Even if the amount of heat dissipation in the indoor unit is excessive and the amount of heat absorbed in the indoor unit is not sufficient, the insufficient amount of heat is given to the refrigerant in the indoor unit side heat supply unit, so the refrigerant is compressed. All of them are completely vaporized and vaporized before being sucked into the compressor, so that suction of the liquid-phase refrigerant to the compressor can be reliably prevented.

According to the fourth aspect of the invention, since the indoor unit side heat supply section is provided on the downstream side of the expansion valve, the indoor unit side heat supply section supplies the low temperature low pressure refrigerant passing through the expansion valve. Since heat is applied, the effect of increasing the efficiency of heat supply to the refrigerant can be obtained.

According to the fifth aspect of the invention, since the outdoor unit side heat supply section is provided on the downstream side of the expansion valve, the outdoor unit side heat supply section supplies the low temperature and low pressure refrigerant passing through the expansion valve. Since heat is applied, the effect of increasing the efficiency of heat supply to the refrigerant can be obtained.

[Brief description of drawings]

FIG. 1 is a circuit diagram showing a basic configuration of an engine-driven air conditioner according to a first embodiment of the present invention.

FIG. 2 is a characteristic diagram of a linear three-way valve provided in the cooling water circuit of the engine-driven air conditioner according to the first embodiment of the present invention.

FIG. 3 is a Mollier diagram showing changes in the state of the refrigerant in the engine-driven air conditioner according to the first example of the present invention.

FIG. 4 is a circuit diagram showing a basic configuration of an engine-driven air conditioner according to a second embodiment of the present invention.

FIG. 5 is a Mollier diagram showing changes in the state of the refrigerant in the engine-driven air conditioner according to the second embodiment of the present invention.

FIG. 6 is a circuit diagram showing a basic configuration of an engine-driven air conditioner according to a third embodiment of the present invention.

FIG. 7 is a circuit diagram showing a basic configuration of an engine-driven air conditioner according to a fourth embodiment of the present invention.

FIG. 8 is a circuit diagram showing a basic configuration of an engine-driven air conditioner according to a fifth embodiment of the present invention.

FIG. 9 is a block diagram showing a configuration of a control system of the air conditioning apparatus according to the present invention.

FIG. 10 is a partial circuit diagram showing a configuration example that replaces a four-way valve.

[Explanation of symbols]

 1 Engine (driving source) 2 Compressor 3 Refrigerant circuit 3A Compressor side refrigerant circuit 3B Indoor unit side refrigerant circuit 3C Outdoor unit side refrigerant circuit 3a Discharge line 3b Suction line 5 Four-way valve (switching part) 7 Indoor unit 8 Expansion valve 9 Outdoor unit 10 Double tube heat exchanger (indoor unit side heat supply section) 11 Double tube heat exchanger (outdoor unit side heat supply section) 20 Tank (indoor unit side heat supply section) 21 Tank (outdoor unit side heat supply) Part)

Claims (5)

[Claims] 1. A compressor-side refrigerant circuit from a suction line to a discharge line via a compressor, a switching unit connected to the suction line end and the discharge line end, and an expansion valve from the switching unit to an indoor unit. The indoor unit side refrigerant circuit to reach, and the outdoor unit side refrigerant circuit from the switching unit to the expansion valve via the outdoor unit
In the heating state, the switching line connects the discharge line to the indoor unit side refrigerant circuit, and also connects the suction line to the outdoor unit side refrigerant circuit, and connects the discharge line and the outdoor unit side refrigerant circuit in the cooling state. With the air conditioner connecting the suction line and the indoor unit side refrigerant circuit, an indoor unit side heat supply unit capable of supplying heat to the refrigerant from the outside,
The outdoor unit side heat supply unit is provided in each of the indoor unit side refrigerant circuit and the outdoor unit side refrigerant circuit, and heat can be supplied to the refrigerant from the outdoor unit side heat supply unit in the heating state and / or the indoor unit side heat in the cooling state. An air conditioner characterized in that heat can be supplied to a refrigerant from a supply unit. 2. Heat can be supplied to the refrigerant from the indoor unit side heat supply section and the outdoor unit side heat supply section, and the heat supply amount from the outdoor unit side heat supply section to the refrigerant in the heating state is set to the indoor unit side. The air conditioner according to claim 1, wherein the amount of heat supplied from the heat supply unit to the refrigerant is made larger. 3. Heat can be supplied to the refrigerant from the indoor unit side heat supply section and the outdoor unit side heat supply section, and the amount of heat supplied from the indoor unit side heat supply section to the refrigerant in the cooling state is set to the outdoor unit side. The air conditioner according to claim 1 or 2, wherein the amount of heat supplied from the heat supply unit to the refrigerant is larger than that of the refrigerant. 4. The air conditioner according to claim 1, wherein the indoor unit side heat supply unit is arranged inside the indoor unit or between the indoor unit and the switching unit. 5. The air conditioner according to claim 1, wherein the outdoor unit side heat supply unit is arranged in the outdoor unit or between the outdoor unit and the switching unit.