JP2011174679A - Air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air conditioner advantageous in improving APF (Annual Performance Factor) during cooling operation. <P>SOLUTION: An outdoor heat exchanger 7 is divided into a first heat exchanger 71 and a second heat exchanger 72. Heat exchangers 50, 52 for an adsorption heat pump are provided in an air blowing passage portion passing cooling air cooling the second heat exchanger 72. When a cooling load during the cooling operation is a middle load or less, the adsorption heat pump 2 is operated, and a refrigerant delivered from an indoor unit 8 is supplied to the first heat exchanger 71 to promote condensation of the refrigerant and to suppress supply of the refrigerant to the second heat exchanger 72. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to an air conditioner that adjusts the temperature of indoor air.

  In the air conditioner, it is required to increase COP (Coefficient Of Performance) indicating the cooling / heating efficiency per 1 kW of power consumption. Therefore, an air conditioner equipped with an adsorption heat pump having an adsorbent such as silica gel capable of adsorbing a working fluid such as water is known (Patent Documents 1 and 2). According to this, the cooling action obtained by the adsorption heat pump preliminarily cools the refrigerant discharged from the indoor unit and compressed by the compressor during the cooling operation of the indoor unit, thereby reducing the COP during the cooling operation. Intended to improve.

  An air conditioner equipped with such an adsorption heat pump condenses the gaseous working fluid desorbed from the adsorbent in addition to the adsorbing part having an adsorbent such as silica gel that can adsorb the working fluid such as water. The condenser for adsorption, the cooling part that vaporizes the working fluid condensed by the condenser for adsorption and generates a cooling action by latent heat of vaporization, and the temperature of the adsorption part that is heated by executing the adsorption mode is increased. And an intermediate cooling heat exchanger that cools the cooling fluid for the adsorption heat pump that has been cooled by heat exchange with the outside air.

JP 2005-195184 A Japanese Patent Laid-Open No. 11-23093

  The above-mentioned COP is easily influenced by the rated load operation state of the air conditioner. The rated load operation is often executed when starting the air conditioner. As an actual operation state of the air conditioner, it is often operated at an intermediate load or lower, not at a rated load operation. In particular, when the indoor heat insulating structure is high, it is often operated at an intermediate load or less. Therefore, the fact is that it cannot be said that the efficiency of the air conditioner is high just because the COP of the air conditioner is high. Therefore, in recent years, an APF (Annual Performance Factor), which is easy to represent the actual use efficiency of the air conditioner, is provided as an index, and it is required to increase the APF of the air conditioner.

  However, it has been found that an air conditioner equipped with an adsorption heat pump does not improve APF as expected. In other words, compared with air conditioners that do not have adsorption heat pumps, air conditioners with adsorption heat pumps have increased heat exchangers such as adsorption condensers and intercooling heat exchangers used in adsorption heat pumps. To do. For this reason, you have to increase the ventilation area and ventilation volume which cool these heat exchangers. In this case, the size of the blower fan, which is an auxiliary device, is increased, and the power cost of the auxiliary device is increased. For this reason, even if the refrigerant is preliminarily cooled by the cooling action of the adsorption heat pump, the APF of the air conditioner does not improve as expected. This invention is made | formed in view of the above-mentioned situation, and makes it a subject to provide the air conditioning apparatus advantageous to improving APF (year-round energy consumption efficiency) at the time of air_conditionaing | cooling operation.

  An air conditioner according to the present invention is an air conditioner that cools at least a room, and (a) an adsorption mode in which the working fluid is adsorbed by the adsorbent, and the working fluid adsorbed by the adsorbent is desorbed from the adsorbent. An adsorption heat pump having an adsorbing section that can alternately execute the desorption mode to be performed, and a cooling section that generates a cooling action by the latent heat of vaporization of the working fluid in accordance with the execution of the adsorption mode and the desorption mode; Heat exchanger for adsorption heat pump used during operation of adsorption heat pump, (c) compressor for compressing refrigerant discharged from indoor unit during cooling operation of indoor unit, and (d) refrigerant compressed by compressor An outdoor heat exchanger that causes heat to be exchanged and condensed, and (e) a ventilation passage that supplies cooling air to the outdoor heat exchanger and the heat exchanger for adsorption heat pump is formed. And (e) the outdoor heat exchanger is provided so as to come into contact with the cooling air in the air passage and can be supplied with the refrigerant compressed by the compressor. The controller is divided into a first heat exchanger and a second heat exchanger, and (f) when the intermediate value between the no-load and rated load of the cooling load during the cooling operation is an intermediate load, i) When the cooling load during the cooling operation exceeds the intermediate load to the rated load side, the operation of the adsorption heat pump is stopped, and the refrigerant compressed by the compressor is supplied to the first heat exchanger and the second heat exchanger. (Ii) when the cooling load during cooling operation is equal to or less than the intermediate load, the adsorption heat pump heat exchanger is cooled with cooling air while the adsorption heat pump is operated, and , Cold compressed with a compressor Of the first heat exchanger and the second heat exchanger to the heat exchanger on the side where the cooling air passing through the adsorption heat pump heat exchanger does not flow relatively, and the first heat exchanger and the second heat exchanger Among the two heat exchangers, the cooling air passing through the heat exchanger for adsorption heat pump is prevented from being supplied to the heat exchanger on the relatively flowing side.

  According to the present invention, during the cooling operation of the indoor unit, the compressor compresses the refrigerant discharged from the indoor unit. The refrigerant compressed by the compressor is heat-exchanged and condensed in an outdoor heat exchanger that can function as a condenser. The outdoor heat exchanger releases the heat of condensation. Here, the outdoor heat exchanger is divided into a first heat exchanger and a second heat exchanger provided in the air passage. An intermediate value between an unloaded cooling load and a rated load during cooling operation is defined as an intermediate load. The intermediate load can be an arbitrary value of 45 to 55 when the cooling load during the cooling operation is 0 for no load and 100 for the rated load. For example, it can be 50. The rated load means the maximum load at which continuous operation is possible, and is generally specified in the nameplate, catalog, manual, etc.

  When the above-described (i) cooling load during cooling operation exceeds the intermediate load to the rated load side (for example, during rated load operation), the control unit needs to sufficiently condense the refrigerant compressed by the compressor. . Therefore, the control unit supplies the refrigerant compressed by the compressor to both the first heat exchanger and the second heat exchanger, thereby condensing the refrigerant in both the first heat exchanger and the second heat exchanger. Therefore, the amount of refrigerant condensed is ensured. In this case, since the air blowing element operates, the cooling air by the air passes through the air passage, cools the first heat exchanger and the second heat exchanger, exerts the condensing action, and advances the condensation of the refrigerant. Thereby, the first heat exchanger and the second heat exchanger condensing heat dissipate the condensing heat. Due to this heat radiation, the heat exchange action (cooling action) of the heat exchanger for adsorption heat pump is extremely reduced, and the function of preliminarily cooling the refrigerant by the adsorption heat pump may not be sufficiently exhibited. In this case, it becomes a factor which reduces COP. Therefore, according to the present invention, when the cooling load during the cooling operation exceeds the intermediate load to the rated load side, the control unit stops the operation of the adsorption heat pump and performs the heat exchange action in the heat exchanger for the adsorption heat pump. Stop. In this case, since the operation of the adsorption heat pump is stopped, the power consumption is saved, the COP during the rated load operation of the air conditioner is improved, and the APF is improved. Even if the operation of the adsorption heat pump is stopped, the refrigerant is condensed in both the first heat exchanger and the second heat exchanger, so that the indoor cooling capacity is sufficiently obtained.

  On the other hand, when the cooling load during the cooling operation is equal to or less than the intermediate load, the amount of refrigerant to be condensed in the outdoor heat exchanger is not required as in the case of (i), so the first heat exchanger and the second heat exchanger It is sufficient to use one of these as a condenser. Further, when the cooling load during the cooling operation is equal to or less than the intermediate load, the control unit operates the adsorption heat pump. For this reason, the cooling effect | action of a cooling part is favorably obtained by the adsorption type heat pump. Therefore, the refrigerant compressed by the compressor can be preliminarily cooled by the cooling action of the cooling unit, the cooling efficiency can be increased, the COP at the intermediate load is improved, and the APF is improved.

  Here, when the cooling load during the cooling operation is equal to or less than the intermediate load, heat is radiated from the heat exchanger for the adsorption heat pump in order to operate the adsorption heat pump. If, of the first heat exchanger and the second heat exchanger, the heat exchanger on the side where the cooling air passes through the adsorption heat pump heat exchanger is dissipated, the temperature of the adsorption heat pump heat exchanger increases. In addition, there is a possibility that the heat exchange action of the adsorption heat pump may be lowered, and consequently, the capacity of the adsorption heat pump may be lowered. Therefore, according to the present invention, (ii) when the cooling load during the cooling operation is equal to or lower than the intermediate load, the control unit adsorbs the refrigerant compressed by the compressor among the first heat exchanger and the second heat exchanger. The cooling air passing through the heat exchanger for the heat pump is supplied to the heat exchanger on the side where the cooling air does not flow relatively. Further, the control unit converts the refrigerant compressed by the compressor from the first heat exchanger and the second heat exchanger to a heat exchanger on the side where the cooling air passing through the adsorption heat pump heat exchanger flows relatively. Deter supply to For this reason, the heat exchanger for adsorption type heat pump can exhibit the heat exchange effect satisfactorily while avoiding the influence of heat radiation of the first heat exchanger and the second heat exchanger, and the capability of the adsorption type heat pump is ensured well. .

  According to the present invention, when the cooling load during the cooling operation of the air conditioner exceeds the intermediate load toward the rated load side (for example, during the rated load operation), the control unit supplies the refrigerant compressed by the compressor to the first The refrigerant is supplied to both the heat exchanger and the second heat exchanger, thereby condensing the refrigerant in both the first heat exchanger and the second heat exchanger, and ensuring the amount of refrigerant condensed. In this case, when the second heat exchanger dissipates the heat of condensation, the heat exchanger for the adsorption heat pump is heated and the heat exchange function of the heat exchanger for the adsorption heat pump may be deteriorated. In this case, the COP of the air conditioner may be reduced. However, according to the present invention, since the operation of the adsorption heat pump is stopped in this case, the adsorption heat pump heat exchanger is in an inoperative state. For this reason, even if the adsorption heat pump heat exchanger is affected by the heat radiation from the second heat exchanger, there is no problem. For this reason, COP of an air conditioning apparatus improves and by extension, APF improves.

  On the other hand, when the cooling load during the cooling operation of the air conditioner is equal to or lower than the intermediate load, the adsorption heat pump is operated, so that a preliminary cooling function by the adsorption heat pump is obtained. As a result, the refrigerant discharged from the indoor unit and compressed by the compressor can be efficiently cooled by the pre-cooling function of the adsorption heat pump, so that the COP of the air conditioner is improved and thus the APF is improved. In this case, the control unit converts the refrigerant compressed by the compressor into heat on the side where the cooling air passing through the heat exchanger for adsorption heat pump does not flow relatively among the first heat exchanger and the second heat exchanger. Supply to the exchanger. Furthermore, the refrigerant compressed by the compressor is supplied to the heat exchanger on the side where the cooling air passing through the heat exchanger for adsorption heat pump flows relatively among the first heat exchanger and the second heat exchanger. Deter. For this reason, the heat exchanger for adsorption type heat pump can exhibit a heat exchange effect satisfactorily, and the operation of the adsorption type heat pump is performed well.

1 is a conceptual diagram illustrating an outdoor unit according to Embodiment 1. FIG. It is a conceptual diagram which concerns on Embodiment 2 and shows an outdoor unit. It is a conceptual diagram which concerns on Embodiment 3 and shows an outdoor unit. FIG. 10 is a conceptual diagram illustrating the vicinity of an adsorption condenser and an intermediate cooling heat exchanger of an outdoor unit according to a fourth embodiment. FIG. 16 is a conceptual diagram illustrating an outdoor unit according to the fifth embodiment.

  Preferably, the heat exchanger for the adsorption heat pump increases the temperature by cooling the adsorption condenser that condenses the gaseous working fluid desorbed from the adsorbent and the adsorption portion that has been heated by executing the adsorption mode. And an intermediate cooling heat exchanger that cools the cooling fluid for the adsorption heat pump, which is cooled by heat exchange with the cooling air. Thereby, the adsorption heat pump is operated well. Preferably, the heat exchanger for adsorption heat pump is provided downstream or upstream of the second heat exchanger while facing the second heat exchanger in the air passage. In this case, it can contribute to size reduction. Preferably, an engine, a water channel through which engine cooling water for cooling the engine flows, and a radiator that can communicate with the water channel and cool the engine cooling water when the engine cooling water is overheated are provided. In this case, preferably, the radiator is provided independently of the adsorption heat pump heat exchanger. Preferably, the radiator is provided so as to be positioned downstream of the first heat exchanger in a ventilation portion through which cooling air flows in the first heat exchanger in the air passage. In this case, the heat dissipation of the first heat exchanger and the radiator is maintained well. Preferably, the heat exchanger for adsorption heat pump also serves as a radiator. In this case, parts are shared, which is advantageous for downsizing. Preferably, the radiator also serves as an intercooling heat exchanger constituting the adsorption heat pump heat exchanger. In this case, the first heat exchanger is preferably divided into a heat exchanger that faces the radiator and a heat exchanger that does not face the radiator.

(Embodiment 1)
FIG. 1 shows the concept of the outdoor unit 1 of the first embodiment. The air conditioner adjusts the temperature of indoor air. The air conditioner has an outdoor unit 1 having an adsorption heat pump 2. The adsorption heat pump 2 includes a case 20, a first adsorption unit 21 and a second adsorption unit 22 provided in the case 20, a cooling unit 23 that generates latent heat of vaporization, a first four-way valve 24, and a second four-way. The valve 25 and the first port 31 to the eighth port 38 provided in the case 20 are provided. The 1st adsorption | suction part 21 and the 2nd adsorption | suction part 22 have porous adsorbents, such as silica gel, activated carbon, activated alumina which can adsorb | suck working fluids, such as water. The first four-way valve 24 switches between the first passage 26 on the first adsorption portion 21 side and the second passage 27 on the second adsorption portion 22 side. The second four-way valve 25 switches between the first passage 26 on the first adsorption part 21 side and the second passage 27 on the second adsorption part 22 side.

  Further, as shown in FIG. 1, an adsorption condenser 50 capable of ventilating the gaseous working fluid desorbed from the adsorbent is provided outside the case 20 as a heat exchanger for the adsorption heat pump. Yes. The cooling unit 23 receives the liquid-phase working fluid condensed by the adsorption condenser 50 through the communication path 45 and vaporizes the liquid-phase working fluid to generate a cooling action by latent heat of vaporization. The adsorption heat pump 2 is provided with a working fluid passage 40 for circulating the working fluid. As shown in FIG. 1, the working fluid passage 40 in the adsorption heat pump 2 includes a cooling unit 23, a first valve 41, a first adsorption unit 21, a second valve 42, an eighth port 38, an adsorption condenser 50, The seventh port 37, the third valve 43, the second adsorption unit 22, the fourth valve 44, and the cooling unit 23 are communicated in this order, and a communication passage 45 that communicates the adsorption condenser 50 and the cooling unit 23 is provided.

  The cooling water passage 6 (adsorption heat pump cooling fluid passage) alternately cools the first adsorption portion 21 and the second adsorption portion 22 of the adsorption heat pump 2 with cooling water (adsorption heat pump cooling fluid). In the adsorption heat pump 2, the first port 31 of the adsorption heat pump 2, the intermediate cooling heat exchanger 52 capable of ventilating, the cooling water pump 60 (cooling fluid conveyance source for adsorption heat pump), and the second port 32 are used. It is connected to the first passage 26 or the second passage 27. As shown in FIG. 1, the outdoor heat exchanger 7 of the air conditioner is divided into a first heat exchanger 71 and a second heat exchanger 72 that can be ventilated and separated so as to be independent from each other. The division form is not particularly limited, and both may be separated, or may be formed integrally, but may have different refrigerant flow paths. The capacity and shape of the outdoor heat exchanger 7 are set based on rated load operation. The capacity and shape of the first heat exchanger 71 and the second heat exchanger 72 may be the same or different. The refrigerant passage 74 connected to the indoor unit 8 has a return path 74y for returning the refrigerant from the indoor unit 8 to the outdoor heat exchanger 7 and an outward path 74x for moving the refrigerant from the outdoor heat exchanger 7 toward the indoor unit 8. In the refrigerant passage 74, a compressor 83 is provided upstream of the first heat exchanger 71 and the second heat exchanger 72. The compressor 83 compresses the refrigerant discharged from the indoor unit 8 to increase the temperature and pressure.

  When the blower fan 10 as the blower element is driven, the blower passage 11 through which the cooling air passes is formed. The cooling air that passes through the first heat exchanger 71 and cools it is referred to as the first cooling air 17. The cooling air that passes through the second heat exchanger 72 and cools it is referred to as second cooling air 19. In addition, in order to obtain the heat exchange function of the adsorption condenser 50 and the intermediate cooling heat exchanger 52 used for the operation of the adsorption heat pump 2 well, the second cooling air 19 supplied to them should be 35 ° C. or lower. Preferably, 25 degrees C or less is still more preferable. During indoor cooling, the refrigerant discharged from the indoor unit 8 to the return path 74 y of the refrigerant passage 74 is compressed by the compressor 83 to become high temperature and high pressure, and is supplied to the outdoor heat exchanger 7. The outdoor heat exchanger 7 is provided in the blower passage 11 and cools and condenses the refrigerant compressed by the compressor 83 to advance the liquid phase of the refrigerant. When the refrigerant is thus condensed, the outdoor heat exchanger 7 releases the heat of condensation.

  The forward path 74 x from the outdoor heat exchanger 7 to the indoor unit 8 in the refrigerant path 74 has a bypass 76 that communicates with the cooling unit 23 of the adsorption heat pump 2. The detour circuit 76 includes an outbound path 76 x from the outbound path 74 x to the cooling unit 23, a return path 76 y that returns from the cooling unit 23, and a detour valve (three-way valve) 75 that bypasses the refrigerant to the detour circuit 76. The bypass valve 75 is switched to communicate with the bypass circuit 76 side. A refrigerant valve 73 is provided between the second heat exchanger 72 and the compressor 83 to control the amount of refrigerant supplied to the second heat exchanger 72. Outward passage 74 x of refrigerant passage 74 is led out from outlet 71 p of first heat exchanger 71 and outlet 72 p of second heat exchanger 72, and bypass valve 75, forward path 76 x of bypass circuit 76, and fifth port 35. Then, it passes through the cooling part 23 of the adsorption heat pump 2 and is connected to the indoor unit 8 via the return path 76y, the sixth port 36, and the forward path 74x. The indoor unit 8 includes an indoor expansion valve 80 that can expand the refrigerant condensed in the outdoor heat exchanger 7 during cooling, and an indoor heat exchanger 82 that can function as an evaporator during cooling. That is, when the adsorption heat pump 2 is operated during indoor cooling, the refrigerant condensed in the outdoor heat exchanger 7 flows in the forward path 74x of the refrigerant passage 74, and passes through the bypass valve 75, the bypass circuit 76, and the fifth port 35. Is supplied to the cooling unit 23 of the adsorption heat pump 2 and is preliminarily cooled by the cooling unit 23, then discharged from the sixth port 36 and supplied to the indoor unit 8, expanded by the indoor expansion valve 80, The temperature is reduced and reduced by the indoor heat exchanger 82 to evaporate, thereby generating an indoor cooling action. Thus, the vapor-phase refrigerant evaporated in the indoor heat exchanger 82 flows in the return path 74y of the refrigerant passage 74, is compressed again by the compressor 83 to be high temperature and high pressure, and is condensed again in the outdoor heat exchanger 7. And is made into a liquid phase. When the adsorption heat pump 2 is operated, the indoor cooling operation is executed in this way. When the refrigerant condensed in the outdoor heat exchanger 7 is not supplied to the cooling unit 23 of the adsorption heat pump 2, the refrigerant that has passed through the bypass valve 75 travels straight on the forward path 74x without bypassing the bypass circuit 76. The refrigerant is switched so that the refrigerant is supplied to the indoor unit 8, and as a result, the communication between the outdoor heat exchanger 7 (outward path 74x) and the cooling unit 23 is blocked by the bypass valve 75, and the refrigerant of the outdoor heat exchanger 7 is cooled. The air is supplied directly to the indoor unit 8 through the bypass valve 75 without flowing into the section 23, that is, without precooling.

  The control unit 100 includes valve elements such as a first valve 41, a second valve 42, a third valve 43, a fourth valve 44, a first four-way valve 24, a second four-way valve 25, a refrigerant valve 73, and a bypass valve 75, and engine cooling. Drive elements such as the water pump 90, the cooling water pump 60, and the compressor 83 are controlled. The compressor 83 is preferably driven by the engine 14, but may be driven by a motor in some cases. As shown in FIG. 1, a water channel 9 through which engine cooling water for cooling the engine 14 flows is provided. The water channel 9 alternately heats the first adsorption unit 21 and the second adsorption unit 22 of the adsorption heat pump 2 with engine cooling water. The water channel 9 discharges engine cooling water heated by the engine 14 from an outlet 14p of the engine 14 by driving an engine cooling water pump 90 (engine cooling water conveyance source), and the inside of the adsorption heat pump 2 from the third port 33. The gas is supplied to the first passage 26 or the second passage 27, further discharged from the fourth port 34 of the adsorption heat pump 2, and returned to the inlet 14 i of the engine 14 through the engine three-way valve 92 and the engine coolant pump 90. The radiator 91 has an inlet port A and an outlet port B.

  When the engine coolant temperature is excessively high, the engine three-way valve 92 is controlled so that the engine coolant discharged from the fourth port 34 is supplied to the radiator passage 93 and the radiator 91. As a result, the engine coolant discharged from the fourth port 34 is supplied to the inlet port A of the radiator 91 through the radiator passage 93, cooled by heat dissipation of the radiator 91, and then discharged from the outlet port B of the radiator 91. And returned to the engine 14 via the engine three-way valve 92, the engine coolant pump 90, and the inlet 14i. When the engine coolant temperature is in the appropriate temperature range, the control unit 100 operates the engine three-way valve 92 so that the engine coolant is not supplied to the radiator 91 in order to prevent overcooling of the engine coolant.

(First mode)
Next, the operation of the adsorption heat pump 2 will be described. First, the first mode in which the first adsorption unit 21 executes the desorption mode and the second adsorption unit 22 executes the adsorption mode will be described. In the first mode, the first valve 41 and the third valve 43 are closed, and the second valve 42 and the fourth valve 44 are opened. In this state, the control unit 100 controls the first four-way valve 24 and the second four-way valve 25. When the engine coolant pump 90 is operated in this state, the high-temperature engine coolant heated by the engine 14 is discharged from the outlet 14p, the water passage 9x, the third port 33, the first four-way valve 24, and the first passage 26. Is supplied to the first adsorbing part 21 to heat the first adsorbing part 21, and further, the second four-way valve 25, the fourth port 34, the return path 9y of the water channel 9, the passage 9u, the engine three-way valve 92, the engine cooling water It returns to the engine 14 via the pump 90. Thus, the 1st adsorption | suction part 21 is heated with high temperature engine cooling water, and desorption mode is performed. Further, since the cooling water pump 60 operates, the low-temperature cooling water in the cooling water passage 6 cooled by the intermediate cooling heat exchanger 52 is discharged from the outlet 52p of the intermediate cooling heat exchanger 52, and the cooling water passage 6 The second adsorbing unit 22 is cooled by being supplied to the second adsorbing unit 22 through the forward path 6x, the cooling water pump 60, the second port 32, the first four-way valve 24, and the second passage 27. At this time, the cooling water is heated by the heat of the second adsorbing portion 22, and further, the intermediate cooling heat from the inlet 52 i via the second passage 27, the second four-way valve 25, the first port 31, and the return path 6 y of the cooling water passage 6 It returns to the exchanger 52 and is cooled by the second cooling air 19 in the intermediate cooling heat exchanger 52. Since the second adsorption unit 22 is cooled with cooling water and performs the adsorption mode in this manner, overheating of the second adsorption unit 22 is suppressed, and adsorption of the gas-phase working fluid in the second adsorption unit 22 continues. proceed.

  In the first mode, as described above, since the first adsorption unit 21 is heated, the working fluid (generally water) adsorbed by the adsorbent of the first adsorption unit 21 is removed from the first adsorption unit 21. It is separated into a gas phase, moves from the port 50f to the adsorption condenser 50 via the second valve 42 and the first passage 28f, and is cooled by the second cooling air 19 in the adsorption condenser 50 to condense. . As a result, a liquid working fluid is generated in the adsorption condenser 50. The heat of condensation is released from the condenser 50 for adsorption. In this case, since the first valve 41 and the third valve 43 are closed, the gas-phase working fluid (generally water vapor) desorbed from the first adsorption unit 21 is cooled by the cooling unit 23 and the second valve. It does not move to the suction unit 22. The liquid-phase working fluid (generally water) condensed in the adsorption condenser 50 is moved to the cooling unit 23 via the communication path 45 by gravity.

  In the first mode, since the second adsorbing portion 22 is cooled by the cooling water flowing from the cooling water passage 6 through the second passage 27, the pressure of the second adsorbing portion 22 decreases. Here, since the first valve 41 and the third valve 43 are closed and the fourth valve 44 is opened, the pressure of the cooling unit 23 decreases as the pressure of the second adsorption unit 22 decreases, and thus the cooling unit The vaporization of the liquid-phase working fluid accommodated in 23 proceeds. The gas-phase working fluid (generally water) in the cooling unit 23 moves to the second adsorption unit 22 through the open fourth valve 44 and is adsorbed by the second adsorption unit 22. At this time, since the first valve 41 and the third valve 43 are closed, the gas-phase working fluid in the cooling unit 23 does not move to the first adsorption unit 21 and the adsorption condenser 50. Adsorption induces an exotherm. As a result, the second adsorption unit 22 that adsorbs the gas-phase working fluid is heated. In this case, the second adsorbing unit 22 is cooled by the cooling water flowing through the second passage 27, the excessive temperature rise of the second adsorbing unit 22 is prevented, and the adsorption performance of the second adsorbing unit 22 is maintained.

(Second mode)
Next, the second mode in which the second adsorption unit 22 executes the desorption mode and the first adsorption unit 21 executes the adsorption mode will be described. In the second mode, contrary to the first mode, the second valve 42 and the fourth valve 44 are closed, and the first valve 41 and the third valve 43 are opened. In this state, the control unit 100 controls the first four-way valve 24 and the second four-way valve 25 so that the water passage 9 communicates with the second passage 27 and the cooling water passage 6 communicates with the first passage 26. As a result, the high-temperature engine cooling water heated by the engine 14 is operated by the operation of the engine cooling water pump 90, so that the outlet 14p of the engine 14, the forward path 9x of the water channel 9, the third port 33, the first four-way valve 24, and the second It is supplied to the second adsorption unit 22 through the passage 27 and heats the second adsorption unit 22, and then returns to the return path 9 y of the water channel 9 through the second passage 27, the second four-way valve 25, and the fourth port 34. Returned, it flows through the passage 9u, the engine three-way valve 92, and the engine coolant pump 90, and returns to the inside of the engine 14. Furthermore, since the cooling water pump 60 operates, the low-temperature cooling water cooled by the intermediate cooling heat exchanger 52 is discharged from the outlet 52p of the intermediate cooling heat exchanger 52, and the forward path 6x of the cooling water path 6 and the second The first adsorbing unit 21 is supplied via the port 32, the first four-way valve 24, and the first passage 26 to cool the first adsorbing unit 21, and the second four-way valve 25, the first port 31, and the cooling water passage 6 It flows through the return path 6y, is returned to the intermediate cooling heat exchanger 52 from the inlet 52i, and is cooled by the intermediate cooling heat exchanger 52. At this time, the gaseous working fluid is cooled and condensed by the intermediate cooling heat exchanger 52, and the intermediate cooling heat exchanger 52 releases the heat of condensation. Thus, in the second mode, the second adsorbing unit 22 is heated by the high-temperature engine cooling water, so that the working fluid adsorbed by the second adsorbing unit 22 is desorbed from the second adsorbing unit 22 and becomes a gas phase. It moves to the adsorption condenser 50 through the opened third valve 43, the second passage 28s, and the port 50s, and is cooled and condensed by the adsorption condenser 50 to form a liquid phase. As a result, a liquid working fluid is generated in the adsorption condenser 50. At this time, the adsorption condenser 50 releases the heat of condensation. In this case, since the fourth valve 44 and the second valve 42 are closed, the gas-phase working fluid generated in the second adsorption unit 22 does not move to the cooling unit 23.

  In the second mode, the cooling water pump 60 operates and the first adsorption unit 21 is cooled by the cooling water (adsorption heat pump cooling fluid), so the pressure of the first adsorption unit 21 decreases. In this case, since the 2nd valve 42 is closed and the 1st valve 41 opens, the pressure of the cooling unit 23 falls and vaporization of the working fluid of the cooling unit 23 advances. Thereby, the cooling unit 23 is cooled by the latent heat of vaporization. The gas-phase working fluid in the cooling unit 23 moves to the first adsorption unit 21 via the first valve 41 and is adsorbed by the first adsorption unit 21. At this time, the first adsorption portion 21 generates heat due to adsorption heat. In this case, since the cooling water flows through the first passage 26, the first adsorption unit 21 is cooled, and the excessive temperature rise of the first adsorption unit 21 is suppressed. As described above, according to the adsorption heat pump 2, the first adsorption unit 21 and the second adsorption unit 22 adsorb the working fluid adsorbed by the adsorbent in the adsorption mode in which the working fluid is adsorbed by the adsorbent and generates heat. The desorption mode for desorbing from is alternately executed every predetermined time. The predetermined time is set according to the adsorbent, the working fluid, and the like. As described above, when the adsorption heat pump 2 is operated, the cooling unit 23 is cooled in the first mode and the second mode.

(Main part configuration)
Now, according to this embodiment, as shown in FIG. 1, the outdoor heat exchanger 7 for condensing the refrigerant | coolant compressed with the compressor 83 at the time of air_conditionaing | cooling operation is the 1st heat exchanger 71 from which a flow path became independent mutually. And a second heat exchanger 72. The return path 74 y of the refrigerant passage 74 connected to the indoor unit 8 includes a first branch path 741 that goes to the first heat exchanger 71 and a second branch path 742 that goes to the second heat exchanger 72 via the refrigerant valve 73. . When the blower fan 10 is operated, cooling air is generated by the air that exchanges heat with the outdoor heat exchanger 7, and the blower passage 11 that is supplied to the outdoor heat exchanger 7 is formed. As can be understood from the above description, the air passage 11 includes a first air passage 16 through which the first cooling air 17 that cools the first heat exchanger 71 and a second cooling air 19 that cools the second heat exchanger 72. Is divided into a second air passage 18 through which the air flows.

  FIG. 1 is a conceptual diagram only. An intermediate cooling heat exchanger 52 and an adsorption condenser 50 are provided as adsorption heat pump heat exchangers used in the adsorption heat pump 2. As can be understood from FIG. 1, the intermediate cooling heat exchanger 52 and the adsorption condenser 50 are adjacent to the second heat exchanger 72 while facing the second heat exchanger 72. 72 is provided in the second air passage 18 through which the second cooling air 19 for cooling the air 72 passes. Here, since the intermediate cooling heat exchanger 52 and the adsorption condenser 50 are located downstream of the second heat exchanger 72 in the second air passage 18, they are affected by the heat radiation of the second heat exchanger 72. Although it is easy, it is not limited to this, and may be located upstream of the second heat exchanger 72 in some cases. As shown in FIG. 1, the intermediate cooling heat exchanger 52 and the adsorption condenser 50 do not face the first heat exchanger 71, and the first cooling air 17 that cools the first heat exchanger 71. Is not provided in the first air passage 16 through which the air passes.

  An intermediate value between the no load and the rated load is set as the intermediate load during the cooling operation. The intermediate load can be an arbitrary value of 45 to 55 when the cooling load during the cooling operation is 0 for no load and 100 for the rated load. For example, it can be 50. According to the present embodiment, the control unit 100 performs the following controls (i) and (ii) according to the cooling load of the air conditioner, so that the first four-way valve 24, the second four-way valve 25, A valve element such as the bypass valve 75 is controlled.

(I) When the cooling load during cooling operation exceeds the intermediate load to the rated load side (for example, during rated load operation)
In this case, the control unit 100 stops the operation of the adsorption heat pump 2. Thereby, the control unit 100 does not execute both the adsorption mode and the desorption mode of the first adsorption unit 21 and the second adsorption unit 22, and the operation of the adsorption heat pump 2 is stopped. At this time, the cooling water pump 60 is stopped. Further, the control unit 100 controls the three-way valves 92h and 92f so that the engine cooling water is not supplied to the third port 33 of the adsorption heat pump 2 while the engine cooling water pump 90 is operated, and from the outlet 14p of the engine 14 The discharged engine cooling water passes through the forward path 9x of the water 9, the three-way valve 92h, the bypass passage 33p, and the three-way valve 92f and returns to the engine inlet 14i.

  As described above, when the cooling load during the cooling operation exceeds the intermediate load toward the rated load side (for example, during the rated load operation), the control unit 100 needs to sufficiently condense the refrigerant discharged from the indoor unit 8. There is. Therefore, the control unit 100 supplies the refrigerant compressed by the compressor 83 from the first branch path 741 to the first heat exchanger 71 and opens the refrigerant valve 73 to exchange the second heat from the second branch path 742. Also supplied to the container 72. Thereby, condensation of a refrigerant is advanced in both the first heat exchanger 71 and the second heat exchanger 72. In this case, since the blower fan 10 operates, the first cooling air 17 passes through the first air passage 16 to cool the first heat exchanger 71, and the second cooling air 19 passes through the second air passage 18. Then, the second heat exchanger 72 is cooled. For this reason, the 1st heat exchanger 71 and the 2nd heat exchanger 72 are cooled, a condensing effect is exhibited, and condensation of a refrigerant is advanced. In this case, the second cooling air 19 heated by the condensed heat discharged from the second heat exchanger 72 through the second air passage 18 (second heat exchanger 72) is supplied to the intermediate cooling heat exchanger 52 and It passes through the condenser 50 for adsorption.

  In this case, the heat exchange action (cooling action) of the intermediate cooling heat exchanger 52 and the adsorption condenser 50 due to heat radiation from the second heat exchanger 72 may be extremely reduced. In this case, the cooling action by the cooling unit 23 of the adsorption heat pump 2 cannot be obtained, and the preliminary cooling function by the adsorption heat pump 2 may not be sufficiently exhibited. In this case, even if the adsorption heat pump 2 is operated, it becomes a factor of lowering the COP at the intermediate load. Therefore, according to the present embodiment, in the case of (i) described above, the control unit 100 stops the operation of the adsorption heat pump 2 as described above, and the influence of the heat radiation from the second heat exchanger 72. The heat exchange action in the intermediate cooling heat exchanger 52 and the adsorption condenser 50 that receives the heat is stopped. In this case, power consumption for executing the operation of the adsorption heat pump 2 is saved, COP at the rated load operation of the air conditioner is improved, and APF is improved.

  Further, since the operation of the adsorption heat pump 2 is stopped, heat radiation from the intermediate cooling heat exchanger 52 and the adsorption condenser 50 is suppressed. For this reason, even when the air volume of the cooling air is suppressed, it is possible to suppress the heat radiation from the intermediate cooling heat exchanger 52 and the adsorption condenser 50 from affecting the second heat exchanger 72. Heat exchange by the heat exchanger 72 is favorably performed. In this case, both the first heat exchanger 71 and the second heat exchanger 72 condense the refrigerant compressed by the compressor 83, although the cooling load of the air conditioner is larger than that in the case (ii). Can be made. In this case, since the operation of the adsorption heat pump 2 is stopped, preliminary cooling by the cooling unit 23 cannot be obtained. Therefore, the communication between the outdoor heat exchanger 7 and the cooling unit 23 is interrupted, and the bypass valve 75 is connected. Thus, the control unit 100 controls the bypass valve 75 so that the refrigerant is directly supplied to the indoor unit 8.

(Ii) When the cooling load during the cooling operation is equal to or less than the intermediate load In this case, the control unit 100 compresses the refrigerant discharged from the indoor unit 8 to the return path 74y of the refrigerant passage 74 by the compressor 83, and then the refrigerant is The refrigerant is supplied to the first heat exchanger 71 to condense the refrigerant. However, the control unit 100 closes the refrigerant valve 73 and moves the refrigerant compressed by the compressor 83 to the second heat exchanger 72 (the side on which the relatively large amount of cooling air passing through the heat exchanger for adsorption heat pump flows). Do not supply. This is because when the cooling load during the cooling operation is equal to or lower than the intermediate load as described above, the cooling load is small and the amount of refrigerant condensed in the outdoor heat exchanger 7 can be small. Therefore, although the 1st heat exchanger 71 is used as a condenser, the 2nd heat exchanger 72 is not used as a condenser.

  Further, in (ii), the control unit 100 operates the adsorption heat pump 2. For this reason, vaporization of the working fluid of the cooling unit 23 in the adsorption heat pump 2 proceeds, and thus the cooling unit 23 generates a preliminary cooling action by latent heat of vaporization. In this case, the control unit 100 opens the bypass valve 75 and allows the refrigerant discharged from the first heat exchanger 71 to pass through the forward path 74x of the refrigerant passage 74, the bypass valve 75, the fifth port 35, and the forward path 76x of the bypass circuit 76. Then, the refrigerant is caused to flow through the cooling unit 23, is preliminarily cooled by the cooling action of the cooling unit 23, and is supplied to the indoor unit 8 through the return path 76 y and the sixth port 36. Thereby, the cooling efficiency in the indoor unit 8 can be increased, COP at the time of intermediate load is improved, and as a result, APF is improved.

  Here, in addition to the second heat exchanger 72 provided in the second air passage 18, an intermediate cooling heat exchanger 52 and an adsorption condenser 50 used in the adsorption heat pump 2 are provided. Therefore, if the condensation heat is released from the second heat exchanger 72, the intermediate cooling heat exchanger 52 and the adsorption condenser 50 are excessively heated, and the intermediate cooling heat exchanger 52 and the adsorption condenser 50 are heated. The heat exchange function may be excessively reduced. Therefore, according to the present embodiment, in the case of (ii), the control unit 100 converts the refrigerant discharged from the indoor unit 8 and compressed by the compressor 83 into the first heat exchanger 71 (adsorption heat pump) as described above. To the second heat exchanger 72 (the side where the relatively large amount of cooling air that passes through the heat exchanger for adsorption heat pump flows). Will not be supplied. That is, the refrigerant discharged from the indoor unit 8 is not supplied to the second heat exchanger 72. For this reason, it is suppressed that the heat of condensation of the refrigerant is released from the second heat exchanger 72. For this reason, even when the outside air temperature is high, such as in summer, the temperature increase of the second cooling air 19 passing through the second heat exchanger 72 is suppressed, and the intermediate cooling heat exchange used in the adsorption heat pump 2 is suppressed. The excessive temperature rise of the condenser 52 and the adsorption condenser 50 is prevented, and the heat exchange functions of the intermediate cooling heat exchanger 52 and the adsorption condenser 50 are maintained normally. As a result, the pre-cooling function by the adsorption heat pump 2 works normally, COP at the rated load operation of the air conditioner is improved, and APF is improved.

  Thus, according to the present embodiment, the first cooling air 17 passes through the first heat exchanger 71 (first air passage 16) even when the cooling load during the cooling operation is equal to or less than the intermediate load. Therefore, the first heat exchanger 71 is cooled to exhibit a condensing action, and the condensation of the refrigerant proceeds in the first heat exchanger 71. In this case, the condensation heat is released from the first heat exchanger 71, but is cooled by the first cooling air 17 in the first air passage 16. Furthermore, in the case of (ii), since the adsorption heat pump 2 is operated, heat is radiated from the intermediate cooling heat exchanger 52 and the adsorption condenser 50, but the second cooling air passing through the second air passage 18. 19, the intermediate cooling heat exchanger 52 and the adsorption condenser 50 can be effectively cooled. In this case, the adsorption heat pump 2 can be operated satisfactorily. According to the present embodiment, as described above, the intercooling heat exchanger 52 and the adsorption condenser 50 that function as the heat exchanger for the adsorption heat pump have the cooling load at the rated load during the cooling operation of the air conditioner. The heat exchange capacity and size of the intermediate cooling heat exchanger 52 and the adsorption condenser 50 can be reduced, and the fan air volume of the blower fan 10 that is an auxiliary device is increased. Can be suppressed, increase in auxiliary power can be suppressed, and decrease in COP and APF can be suppressed.

(Embodiment 2)
FIG. 2 shows the concept of the second embodiment. The present embodiment basically has the same configuration and operational effects as the first embodiment. Parts common to the first embodiment are denoted by common reference numerals. FIG. 2 mainly shows the outdoor unit 1 of the air conditioner. The outdoor unit 1 includes a base body 15 on which the adsorption heat pump 2 is mounted. The adsorption heat pump 2 includes a case 20 having a first adsorption part and a second adsorption part, and a first port 31 to an eighth port 38 provided in the case 20. As shown in FIG. 2, an adsorption condenser 50 and an intermediate cooling heat exchanger 52 are provided outside the case 20 as an adsorption heat pump heat exchanger. As shown in FIG. 2, the outdoor heat exchanger 7 is divided into first heat exchangers 71f and 71s and second heat exchangers 72f and 72s. A total of two first heat exchangers 71 f and 71 s are provided on the base 15 so as to face each other via the adsorption heat pump 2. A total of two second heat exchangers 72f and 72s are provided on the base 15 so as to face each other via the adsorption heat pump 2 while being positioned above the first heat exchangers 71f and 71s. Therefore, on the outer surface of the base body 15, two first heat exchangers 71f and 71s having the same size (same heat exchange amount) and two second heat exchangers having the same size (same heat exchange amount). Since 72f and 72s are exposed, the appearance design of the outdoor unit 1 is ensured.

  The sizes (heat exchange amounts) of the first heat exchangers 71f and 71s may be substantially the same as or different from the sizes of the second heat exchangers 72f and 72s. The sizes (heat exchange amounts) of the first heat exchangers 71f and 71s may be substantially the same or different from each other. The sizes (heat exchange amounts) of the second heat exchangers 72f and 72s may be substantially the same or different from each other. Here, the contour projection shapes of the first heat exchanger 71f and the radiator 91 may be substantially the same or different. The contour projection shapes of the second heat exchanger 72f and the intermediate cooling heat exchanger 52 may be substantially the same or different. The contour projection shapes of the second heat exchanger 72s and the adsorption condenser 50 may be substantially the same or different.

  As shown in FIG. 2, the blower fan 10 is provided as a blower element on the upper surface of the base body 15. When the blower fan 10 is activated, the blower passage 11 through which the first cooling air 17f and 17s and the second cooling air 19f and 19s flow is formed. As shown in FIG. 2, the air passage 11 includes a first air passage 16f through which the first cooling air 17f flows through the lower first heat exchanger 71f, and a first heat exchanger through which the first cooling air 17s is provided. The first air passage 16s flowing through 71s, the second air passage 18f through which the second cooling air 19f flows through the upper second heat exchanger 72f, and the second air through which the second cooling air 19s flows through the upper second heat exchanger 72s. And two air passages 18s. In addition, since engine cooling water may be high temperature (for example, 70-90 degreeC), even if the 1st cooling air 17f supplied to the radiator 91 becomes high temperature (for example, 70-90 degreeC), the cooling function by the radiator 91 is maintained. Is done.

  As shown in FIG. 2, although the radiator 91 does not face the first heat exchanger 71s, it faces the first heat exchanger 71f while facing the first heat exchanger 71f, and the first heat exchanger 71f is connected to the first heat exchanger 71f. Located inside or downstream. Although the intermediate cooling heat exchanger 52 does not face the lower first heat exchangers 71f and 71s, the intermediate cooling heat exchanger 52 faces the upper second heat exchanger 72f and approaches the second heat exchanger 72f. It is located inside or downstream of the exchanger 72f. The adsorption condenser 50 does not face the lower first heat exchangers 71f and 71s, but faces the second heat exchanger 72s and approaches the second heat exchange in the second ventilation passage 18s. Located inside or downstream of the vessel 72s. In order to obtain the heat exchange function of the adsorption condenser 50 and the intermediate cooling heat exchanger 52 satisfactorily, the second cooling air 19f and 19s supplied to them is 45 ° C. or lower and 40 ° C. or lower. preferable.

  According to the present embodiment, as in the first embodiment, the control unit 100 performs the following controls (i) to (iii) according to the cooling load of the air conditioner.

(I) When the cooling load during indoor cooling operation exceeds the intermediate load toward the rated load side (for example, during rated load operation)
In this case, although the control unit 100 stops the operation of the adsorption heat pump 2, since the cooling load is large, the control unit 100 increases the cooling capacity in the room, so that the gaseous state discharged from the indoor unit 8 to the return path 74y of the refrigerant path 74 is increased. The refrigerant is compressed by the compressor 83, and the refrigerant is supplied to both the first heat exchangers 71f and 71s and the second heat exchangers 72f and 72s. In this case, the control unit 100 stops the cooling water pump 60 so that the cooling water in the cooling water passage 6 does not flow to the second port 32 of the adsorption heat pump 23. Further, although the engine cooling water in the water passage 9 heated by the engine 14 is caused to flow to the radiator 91 through the radiator passage 93 by the operation of the engine cooling water pump 90, the third port 33 and the fourth port 34 of the adsorption heat pump 2. The control unit 100 controls the engine three-way valves 92f, 92s, and 92h. Thereby, since the adsorption heat pump 2 does not execute both the adsorption mode and the desorption mode, the operation of the adsorption heat pump 2 is stopped. Reference numeral 210 denotes an auxiliary heat exchanger that exchanges heat between the engine cooling water and the refrigerant, and 220 denotes an exhaust heat exchanger that exchanges heat between the engine cooling water and the engine exhaust gas.

  Further explanation will be added. The refrigerant (gas phase) discharged from the indoor unit 8 to the return path 74y of the refrigerant passage 74 is compressed by the compressor 83 to become a high-temperature and high-pressure refrigerant (gas phase). In this way, the refrigerant compressed by the compressor 83 is supplied from the branch part 77a and the first branch path 741f to the first heat exchanger 71f, and the first heat exchanger 71s via the branch part 77a and the first branch path 741s. To supply.

  Further, the control unit 100 opens the refrigerant valve 73f, supplies the refrigerant compressed by the compressor 83 to the second heat exchanger 72f via the second branch 742f, and opens the refrigerant valve 73s. It is made to supply to the 2nd heat exchanger 72s via the 2nd branch way 742s. As a result, the condensation of the refrigerant proceeds in all of the first heat exchangers 71f and 71s and the second heat exchangers 72f and 72s. This ensures the necessary amount of refrigerant condensation even during rated load operation. The first heat exchangers 71f and 71s and the second heat exchangers 72f and 72s release the heat of condensation.

  In this case, since the blower fan 10 operates, as can be understood from FIG. 2, the first cooling air 17f passes through the first air passage 16f (first heat exchanger 71f), and the first cooling air 17s is the first. It passes through the air passage 16s (first heat exchanger 71s). Further, the second cooling air 19f passes through the second air passage 18f (the second heat exchanger 72f and the intermediate cooling heat exchanger 52), and the second cooling air 19s passes through the second air passage 18s (the second heat exchanger 72s). And the adsorption condenser 50). For this reason, the 1st heat exchangers 71f and 71s and the 2nd heat exchangers 72f and 72s which are releasing condensation heat are cooled, a condensation action is exhibited, and condensation of a refrigerant is advanced.

  In this case, the intermediate cooling heat exchanger 52 and the adsorption condenser 50 are excessively heated by the heat radiation from the second heat exchangers 72f and 72s for releasing the condensation heat, and the heat exchange action (cooling action) is extremely high. May be reduced. In this case, the precooling function by the adsorption heat pump 2 may not be sufficiently exhibited. In this case, it becomes a factor which reduces COP. Therefore, according to the present embodiment, in the case of (i), the control unit 100 stops the operation of the adsorption heat pump 2 as described above, and is subjected to intermediate cooling that is affected by heat radiation from the second heat exchanger 72f. The heat exchange action in the exchanger 52 is stopped, and the heat exchange action in the adsorption condenser 50 that is affected by the heat radiation from the second heat exchanger 72s is stopped. As a result, the power consumption for performing the operation of the adsorption heat pump 2 is saved, the COP during the rated load operation of the air conditioner is improved, and consequently the APF is improved. Even if the operation of the adsorption heat pump 2 is stopped in this way, the amount of refrigerant condensed by all the first heat exchangers 71f and 71s and the second heat exchangers 72f and 72s is ensured, so the indoor cooling capacity is Maintained.

  Furthermore, in (i), since the operation of the adsorption heat pump 2 is stopped, the release of condensation heat from the intermediate cooling exchanger 52 and the adsorption condenser 50 is suppressed. For this reason, the heat radiation from the intermediate cooling exchanger 52 and the adsorption condenser 50 is the heat exchange action of the second heat exchangers 72f and 72s (the side on which the relatively large amount of cooling air passing through the adsorption heat pump heat exchanger flows). It is prevented from adversely affecting Therefore, the heat exchange amount by the second heat exchangers 72f and 72s is ensured satisfactorily. Therefore, as shown in FIG. 2, the intermediate cooling heat exchanger 52 and the second heat exchanger 72 f can be approached while facing each other, and the adsorption condenser 50 can be approached while facing the second heat exchanger 72 s, thereby reducing the size. Can be further improved.

  In the case of (i), since the operation of the adsorption heat pump 2 is stopped as described above, preliminary cooling by the adsorption heat pump 2 cannot be obtained. For this reason, the control part 100 closes the bypass valve 75f and the on-off valve 75t, and opens the bypass valve 75s so that the communication between the outdoor heat exchanger 7 and the adsorption heat pump 2 is interrupted. Since the bypass valve 75f and the on-off valve 75t are thus closed, the refrigerant in the forward path 74x of the refrigerant path 74 is prevented from flowing into the fifth port 35 and the sixth port 36 of the adsorption heat pump 2.

  As described above, in (i), the refrigerant discharged from the first heat exchangers 71f and 71s and the second heat exchangers 72f and 72s is the forward path 74x of the refrigerant passage 74, the bypass valve 75s, and the branch portions 77h, 77i, and 77c. Then, the air is expanded by the indoor expansion valve 80 of the indoor unit 8 to be reduced in temperature and pressure, and then evaporated in the indoor heat exchanger 82. As described above, the indoor heat exchanger 82 absorbs heat from the latent heat of vaporization and performs a cooling operation in the room. In such a case (i), as can be understood from the above, the refrigerant valves 73f and 73s and the bypass valve 75s are opened, and the bypass valve 75f, the on-off valve 75t and the refrigerant valve 93w are closed. The on-off valve 75t is always closed during the refrigerant operation.

(Ii) When the cooling load during the cooling operation is equal to or less than the intermediate load In this case, the refrigerant (gas phase) used for the cooling operation in the indoor unit 8 is discharged to the return path 74y of the refrigerant passage 74 and compressed by the compressor 83 It becomes high temperature and high pressure. The gas-phase refrigerant compressed in this manner is supplied to the first heat exchangers 71f and 71s (the cooling air passing through the heat exchanger for adsorption heat pump) via the branch part 77a and the first branch paths 741f and 741s. The first heat exchangers 71f and 71s cause the refrigerant to condense. However, since the refrigerant valve 73f is closed and the second branch path 742f is blocked, the refrigerant is cooled by the second heat exchanger 72f facing the intermediate cooling heat exchanger 52 (cooling that passes through the heat exchanger for adsorption heat pump). It is not supplied to the side where a relatively large amount of wind flows. Similarly, since the refrigerant valve 73s is closed and the second branch path 742s is shut off, the refrigerant is cooled by the second heat exchanger 72s facing the adsorption condenser 50 (the cooling that passes through the adsorption heat pump heat exchanger). It is not supplied to the side where a relatively large amount of wind flows. As described above, when the cooling load during the cooling operation is equal to or lower than the intermediate load, the cooling load is small and the amount of refrigerant to be condensed in the outdoor heat exchanger 7 is small. Therefore, only the first heat exchangers 71f and 71s are condensed. Use as a container.

  Further, in (ii), the control unit 100 operates the adsorption heat pump 2 as in the first embodiment. For this reason, the cooling part of the adsorption heat pump 2 generates a preliminary cooling action by latent heat of vaporization. Therefore, the bypass valve 75f is opened while the bypass valve 75s and the open valve 75t are closed. As a result, the refrigerant discharged from the first heat exchangers 71f and 71s is supplied to the cooling portion of the adsorption heat pump 2 from the fifth port 35 via the bypass valve 75f, and is preliminarily cooled. It can be returned to the indoor unit 8 through the 6 port 36 and the branching portions 77i and 77c. Thus, the cooling efficiency in the indoor unit 8 can be increased. Therefore, COP at the time of intermediate load is improved, and as a result, APF is improved. Here, as shown in FIG. 2, in addition to the second heat exchanger 72f being provided in the second air passage 18f, the intermediate cooling heat exchanger 52 used in the adsorption heat pump 2 is provided with the second heat exchange. Adjacent to the container 72f and facing each other. Similarly, in addition to the second heat exchanger 72s provided in the second air passage 18s, the adsorption condenser 50 used in the adsorption heat pump 2 approaches the second heat exchanger 72s and faces the second heat exchanger 72s. While next to it. For this reason, if the heat of condensation is released from the second heat exchangers 72f and 72s, the intermediate cooling heat exchanger 52 and the adsorbing condenser 50 that are adjacent to each other while approaching the second heat exchangers 72f and 72s are excessive. There is a risk that the temperature will rise. In this case, the heat exchange functions of the intermediate cooling heat exchanger 52 and the adsorption condenser 50 may be excessively reduced, and the capability of the adsorption heat pump 2 may be reduced. Therefore, according to the present embodiment, in the case of (ii), as in the first embodiment, the control unit 100 uses the refrigerant discharged from the indoor unit 8 to the return path 74y of the refrigerant path 74 and compressed by the compressor 83. The second heat exchangers 72f and 72s (adsorption heat pump heat exchangers) are supplied to the first heat exchangers 71f and 71s (the side where the cooling air passing through the adsorption heat pump heat exchanger does not flow relatively). To the side where a relatively large amount of cooling air passing through the air flows).

  For this reason, it is suppressed that the heat of condensation of the refrigerant is released from the second heat exchangers 72f and 72s. As a result, even when the outside air temperature is high, such as in summer, the temperature rise of the second cooling winds 19f, 19s passing through the second heat exchangers 72f, 72s is suppressed, so that the intermediate cooling heat exchange is performed. The excessive temperature rise of the condenser 52 and the adsorption condenser 50 is prevented, and the heat exchange functions of the intermediate cooling heat exchanger 52 and the adsorption condenser 50 are maintained normally. As a result, the pre-cooling function by the adsorption heat pump 2 works normally, COP when the air conditioner is below the intermediate load is improved, and APF is improved. In such a case (ii), the bypass valve 75f is opened, and the refrigerant valves 73s, 73f, 93w, the bypass valve 75s, and the open valve 75t are closed.

(Iii) During heating operation In this case, as in the first embodiment, the refrigerant used for the heating operation in the indoor unit 8 is changed from the indoor unit 8 to the return path of the refrigerant passage 74 as a liquid phase or a gas-liquid two phase. It is discharged to the forward path 74x instead of 74y, further expanded by the outdoor expansion valve 99a, and then supplied to the first heat exchangers 71f and 71s via the branch part 77e and second heat via the branch parts 77k and 77u. It is supplied to the exchangers 72f and 72s. Therefore, during heating, the first heat exchangers 71f and 71s and the second heat exchangers 72f and 72s function as an evaporator that vaporizes the refrigerant. The gas-phase refrigerant discharged from the first heat exchangers 71f and 71s and the second heat exchangers 72f and 72s flows to the compressor 83 via the branch part 77a, and is compressed by the compressor 83 to become high temperature and high pressure. It flows from the return path 74y of the passage 74 to the indoor unit 8 and is condensed in the indoor heat exchanger 82 to generate heat of condensation. As a result, the room is heated. Even during such heating operation, since the blower fan 10 operates, the cooling air 17f, 17s, 19f, 19s cools the first heat exchangers 71f, 71s, the second heat exchangers 72f, 72s, and the radiator 91. .

  During such heating operation, as can be understood from the above, the control unit 100 does not operate the adsorption heat pump 2 and returns the refrigerant returning from the indoor unit 8 to all the first heat exchangers 71f and 71s and the first heat exchangers 71f and 71s. 2 Evaporate by supplying to both heat exchangers 72f and 72s. For this reason, heating capacity is ensured. In such a heating operation, the refrigerant valves 73f and 73s, the on-off valve 75t, and the refrigerant valve 93w are opened, and the bypass valves 75f and 75s are closed.

(Embodiment 3)
FIG. 3 shows a third embodiment. The present embodiment has basically the same configuration and operational effects as the first and second embodiments. A common code | symbol is attached | subjected to a common site | part. Hereinafter, the description will focus on the different parts. According to the present embodiment, the radiator 91 that cools the engine cooling water also serves as the intermediate cooling heat exchanger 52 and faces the first heat exchanger 71f. The radiator 91 and the intermediate cooling heat exchanger 52 are both cooled by flowing water, and can be used together. In other words, the radiator 91 that cools the engine coolant can also serve as the intermediate cooling heat exchanger 52 for the adsorption heat pump. Similarly, the intermediate cooling heat exchanger 52 can also serve as the radiator 91.

  Also in this embodiment, control is performed as follows.

(I) When the cooling load during cooling operation exceeds the intermediate load to the rated load side (for example, during rated load operation)
In this case, like the first and second embodiments, the operation of the adsorption heat pump 2 is stopped, but the refrigerant is supplied to all of the first heat exchangers 71f and 71s and the second heat exchangers 72f and 72s. Accordingly, the first heat exchangers 71f and 71s and the second heat exchangers 72f and 72s function as condensers and release condensation heat.

(Ii) When the cooling load during the cooling operation is equal to or less than the intermediate load (at the time of intermediate load) In this case, as in the first and second embodiments, the control unit 100 operates the adsorption heat pump 2 and the adsorption condenser 50 and Both of the intermediate cooling heat exchangers 52 are used as heat exchangers. Accordingly, the adsorption heat pump 2 generates a preliminary cooling action by latent heat of vaporization. That is, as in Embodiments 1 and 2, in the case of (ii), the refrigerant discharged from the indoor unit 8 to the return passage 74y of the refrigerant passage 74 and compressed by the compressor 83 is passed through the branch portion 77a. The heat exchanger 71 s (not facing the radiator 91 that dissipates heat) is used as a condenser, but the refrigerant valve 73 s is closed to supply the refrigerant to the second heat exchanger 72 s (to the adsorption condenser 50 that dissipates heat). It is not allowed to supply to (facing). For this reason, the second heat exchanger 72s does not function as a condenser, and it is possible to suppress the release of condensation heat from the second heat exchanger 72s. Therefore, excessive temperature rise of the adsorbing condenser 50 that is adjacent to the second heat exchanger 72s is prevented, and the heat exchanging function of the adsorbing condenser 50 is maintained normally. As a result, the pre-cooling function by the adsorption heat pump 2 works normally, COP when the air conditioner is below the intermediate load is improved, and APF is improved.

  In (ii), since the adsorption heat pump 2 is operated as described above, it is necessary to supply cooling water to the second port 32 of the adsorption heat pump 2. Therefore, when the cooling water pump 60 of the cooling water passage 6 is activated, the water of the radiator 91 flows to the forward path 6x and the branching portion 6r of the cooling water passage 6 and is absorbed from the second port 32 via the cooling water pump 60. Is further discharged from the first port 31, flows into the return path 6 y of the cooling water passage 6, is returned to the radiator 91 again through the ports 92 m 1 and 92 m 2 of the three-way valve 92 m, and is cooled by the radiator 91. In this case, since the radiator 91 dissipates heat, the radiator 91 can also serve as an intermediate cooling heat exchanger. Thus, when the radiator 91 dissipates heat, the first heat exchanger 71f that is adjacent to the radiator 91 while facing the radiator 91 is affected by heat dissipation. For this reason, in (ii), the use of the first heat exchanger 71f as a condenser is abolished. Therefore, the control unit 100 closes the stop valve 98a communicating with the first heat exchanger 71, and does not supply the refrigerant compressed by the compressor 83 to the first heat exchanger 71f (facing the radiator 91).

  In other words, when the cooling load during the cooling operation is equal to or lower than the intermediate load, the control unit 100 causes the radiator 91 to radiate the cooling water and the refrigerant compressed by the compressor 83 to the lower first heat exchanger 71f, The heat exchanger 71s that does not face the radiator 91 in 71s and the heat exchanger 72f that does not face the adsorption condenser 50 (the other) among the upper second heat exchangers 72f and 72s are supplied. In this case, the control unit 100 adsorbs the refrigerant compressed by the compressor 83 for the heat exchanger 71f facing the radiator 91 in the first heat exchangers 71f and 71s and the heat exchanger 71f and 72s for the second heat exchangers 72f and 72s. The heat is not supplied to the heat exchanger 72s facing the condenser 50. In this case, the heat exchange action of the radiator 91 also serving as the intermediate cooling heat exchanger and the adsorption condenser 50 is ensured satisfactorily.

  In (ii), since the adsorption heat pump 2 is operated, it is necessary to supply the high-temperature engine cooling water in the forward path 9x of the water channel 9 to the third port 33 of the adsorption heat pump 2 and to discharge it from the fourth port 34. is there. Therefore, the forward path 9 x of the water channel 9 communicates with the third port 33 of the adsorption heat pump 2, and the return path 9 y of the water channel 9 communicates with the fourth port 34. In this state, when the engine cooling water pump 90 of the water passage 9 is operated, the high-temperature engine cooling water heated by the engine 14 flows from the outlet 14p to the forward passage 9x of the water passage 9, and the third port via the engine three-way valve 92h. 33 flows into the adsorption heat pump 2 and flows from the fourth port 34 to the return path 9y. The engine cooling water pump passes through the ports 92f1 and 92f2 of the engine three-way valve 92f and the ports 92s1 and 92s2 of the engine three-way valve 92s. 90, and then returned to the engine 14 through the exhaust heat exchanger 220 from the inlet 14i. In this case, since the first adsorption unit or the second adsorption unit is heated by the high-temperature engine cooling water supplied into the adsorption heat pump 2 and the water vapor is desorbed, the adsorption heat pump 2 is operated well. In this case, the water passage 9 through which the engine cooling water flows is not communicated with the radiator 91 by the blocking action of the engine three-way valves 92f and 92s, and is not supplied to the radiator 91.

  Moreover, according to this embodiment, in (ii), using the 1st heat exchanger 71f adjacently provided facing the radiator 91 as a condenser is abolished. The reason is that, as the adsorption heat pump 2 is operated, the radiator 91 that also serves as the intermediate cooling heat exchanger 52 dissipates heat, so that the first heat exchanger 71f (facing the radiator 91) is heated by the heat radiation. This is because the heat exchange function is lowered. Therefore, the control unit 100 closes the stop valve 98a located upstream of the first heat exchanger 71f. Therefore, the refrigerant compressed by the compressor 83 is not supplied to the first heat exchanger 71f. As an alternative, the refrigerant compressed by the compressor 83 is used as the condensers such that the second heat exchanger 72f disposed above the first heat exchanger 71f is used as a condenser, and the branch parts 77a and 77m and the branch path 742f are used. To the second heat exchanger 72f (not facing the radiator 91 and the adsorption condenser 50).

(Embodiment 4)
FIG. 4 shows a main part of the fourth embodiment. The present embodiment has basically the same configuration and operational effects as the first and second embodiments. In the second embodiment described above, as shown in FIG. 2, the intermediate cooling heat exchanger 52 is disposed inside (downstream side) of the second heat exchanger 72f, and inside (downstream side) of the second heat exchanger 72s. An adsorption condenser 50 is arranged. As can be understood from the above description, when the second heat exchangers 72f and 72s function as condensers to dissipate heat, the operation of the adsorption heat pump 2 is stopped, so that the intermediate cooling heat exchanger 52 and the adsorption condenser are used. Since 50 does not work as a heat exchanger, it does not dissipate heat. In the second embodiment, when the intermediate cooling heat exchanger 52 and the adsorption condenser 50 function as heat exchangers to dissipate heat, the second heat exchangers 72f and 72s do not function as condensers and therefore do not dissipate heat. As described above, in both cases (i) and (ii), the set of the intermediate cooling heat exchanger 52 and the adsorption condenser 50 and the set of the second heat exchangers 72f and 72s have a mutual heat exchange function. Does not affect. Therefore, according to the present embodiment, as shown in FIG. 4, the intermediate cooling heat exchanger 52 is disposed so as to face the outside (upstream) of the second heat exchanger 72f, and the outside of the second heat exchanger 72s ( The adsorption condenser 50 is arranged so as to face upstream.

  In general, the air conditioner operates for a longer time than the intermediate load than the time required for the rated load. As described above, when operating at an intermediate load or lower, the second heat exchangers 72f and 72s are not used as heat exchangers, and may act as wind resistors for the second cooling air 19f and 19s. Therefore, according to the present embodiment, as shown in FIG. 4, the intermediate cooling heat exchanger 52 is disposed upstream of the second heat exchanger 72f, and the adsorption condenser 50 is disposed upstream of the second heat exchanger 72s. Has been. In this case, when the adsorption heat pump 2 is operated and the intermediate cooling heat exchanger 52 and the adsorption condenser 50 perform heat exchange, the second heat exchangers 72f and 72s are connected to the intermediate cooling heat exchanger 52 and the adsorption heat pump 52f. The second heat exchangers 72f and 72s are not wind resistors because they are arranged downstream of the condenser 50 for use. Therefore, there is an advantage that the amount of the second cooling air 19f, 19s supplied to the intermediate cooling heat exchanger 52 and the adsorption condenser 50 can be easily secured, and the intermediate cooling heat exchanger 52 and the adsorption condenser 50 are excellent. To be cooled.

(Embodiment 5)
FIG. 5 shows a fifth embodiment. The present embodiment has basically the same configuration and operational effects as the third embodiment. As shown in FIG. 5, the 1st heat exchanger 71 and the 2nd heat exchanger 72 are arrange | positioned at the base | substrate 15 so that it may mutually oppose so that the heat pump 2 may be pinched | interposed. The radiator 91 that cools the engine cooling water also serves as the intermediate cooling heat exchanger 52 as in the third embodiment, and faces the first heat exchanger 71 so as to be positioned downstream thereof. Thus, the radiator 91 and the intermediate cooling heat exchanger 52 are both cooled by flowing water, and can be used together. Further, the adsorption condenser 50 faces the first heat exchanger 71 so as to be positioned downstream thereof.

  Also in the present embodiment, (i) when the cooling load during the cooling operation exceeds the intermediate load toward the rated load side (for example, during the rated load operation), the control unit 100 stops the operation of the adsorption heat pump 2. Meanwhile, the refrigerant compressed by the compressor 83 is supplied to both the first heat exchanger 71 and the second heat exchanger 72 to ensure the refrigerant condensation amount.

  (Ii) When the cooling load during the cooling operation is equal to or lower than the intermediate load (during the intermediate load), the control unit 100 operates the adsorption heat pump 2 to perform the intermediate cooling heat exchanger 52 (also used as the radiator 91) and the adsorption condenser. Heat is released from 50. For this reason, the refrigerant compressed by the compressor 83 is not supplied to the first heat exchanger 71 (the heat exchanger facing the radiator 91 and the adsorption condenser 50 that also serves as the intermediate cooling heat exchanger 52). Two heat exchangers 72 (the heat exchanger not facing the radiator 91 and the adsorption condenser 50 that also serve as the intermediate cooling heat exchanger 52) are supplied.

  (Others) As described above, in the cases (i) and (ii), the group of the intermediate cooling heat exchanger 52 and the adsorption condenser 50 and the group of the second heat exchangers 72f and 72s exchange heat with each other. Does not affect functionality. For this reason, the intermediate cooling heat exchanger 52 and the second heat exchanger 72f facing each other may be either upstream or downstream in the second ventilation passage 18f. Further, the adsorption condenser 50 and the second heat exchanger 72s facing each other may be either upstream or downstream in the second ventilation passage 18s. The first valve 41, the second valve 42, the third valve 43, and the fourth valve 44 may be check valves that allow flow in only one direction but block flow in the other direction. The present invention is not limited to the embodiments described above and shown in the drawings, and can be implemented with appropriate modifications within the scope not departing from the gist.

  1 is an outdoor unit, 10 is a blower fan (blower element), 11 is a blower passage, 11f is a first blower passage, 11s is a second blower passage, 2 is an adsorption heat pump, 21 is a first adsorption unit, and 22 is a second Adsorption part, 23 is a cooling part, 14 is an engine, 15 is a base, 50 is an adsorption condenser (adsorption heat pump heat exchanger), 52 is an intermediate cooling heat exchanger (adsorption heat pump heat exchanger), 40 Is a working fluid passage, 6 is a cooling water passage, 60 is a cooling water pump, 7 is an outdoor heat exchanger, 71 is a first heat exchanger, 72 is a second heat exchanger, 73 is a refrigerant valve, 74 is a refrigerant passage, 76 is a bypass, 8 is an indoor unit, 80 is an indoor expansion valve, 82 is an indoor heat exchanger, 83 is a compressor, 9 is a water passage, 90 is an engine cooling water pump, 91 is a radiator, 92 is an engine three-way valve, 100 is A control part is shown.

Claims (5)

An air conditioner that at least cools the room,
An adsorption unit capable of alternately performing an adsorption mode for adsorbing the working fluid to the adsorbent and a desorption mode for desorbing the working fluid adsorbed on the adsorbent from the adsorbent; An adsorption heat pump having a cooling unit that generates a cooling action by latent heat of vaporization of the working fluid in accordance with execution of the desorption mode;
An adsorption heat pump heat exchanger used during operation of the adsorption heat pump;
A compressor that compresses the refrigerant discharged from the indoor unit during cooling operation of the indoor unit;
An outdoor heat exchanger for exchanging heat and condensing the refrigerant compressed by the compressor;
A blowing element that forms a blowing passage for supplying cooling air to the outdoor heat exchanger and the adsorption heat pump heat exchanger;
And a control unit,
The outdoor heat exchanger is provided so as to be in contact with the cooling air in the air passage, and the first heat exchanger and the second heat that can be supplied with refrigerant discharged from the indoor unit and compressed by the compressor. Divided into exchangers,
When the intermediate value between the no-load and rated load of the cooling load during cooling operation is the intermediate load,
The controller is
(I) When the cooling load during the cooling operation exceeds the rated load side with respect to the intermediate load, the operation of the adsorption heat pump is stopped, and the refrigerant compressed by the compressor is supplied to the first heat exchanger and Allowing both of the second heat exchangers to supply and proceed with condensation of the refrigerant,
(Ii) When the cooling load during the cooling operation is equal to or less than the intermediate load, the adsorption heat pump heat exchanger is cooled with the cooling air while the adsorption heat pump is operated, and the compressor is compressed by the compressor The refrigerant is supplied to a heat exchanger on the side of the first heat exchanger and the second heat exchanger, on which the cooling air passing through the adsorption heat pump heat exchanger does not flow, The air conditioning apparatus which suppresses supplying the cooling air which passes the said heat exchanger for adsorption type heat pumps among the 1 heat exchanger and the said 2nd heat exchanger to the heat exchanger of the side which flows relatively.   The adsorption heat pump heat exchanger according to claim 1, wherein the adsorption heat pump heat exchanger includes an adsorption condenser that condenses the gaseous working fluid desorbed from the adsorbent, and the adsorption unit that is heated by executing the adsorption mode. An air conditioning apparatus comprising: an intermediate cooling heat exchanger that cools an adsorption heat pump cooling fluid that has been heated by cooling by heat exchange with the cooling air.   3. The air conditioner according to claim 1, wherein the heat exchanger for adsorption heat pump is provided downstream or upstream of the second heat exchanger while facing the second heat exchanger in the air passage. . The engine cooling water according to claim 1, wherein the engine, the water channel through which engine cooling water for cooling the engine flows, and the water channel that can communicate with the water channel and the engine cooling water is overheated are cooled. With a radiator,
The said radiator is an air conditioning apparatus provided so that it may be located in the downstream of the said 1st heat exchanger in the ventilation part into which the cooling air flows through the said 1st heat exchanger among the said ventilation paths.   5. The air conditioner according to claim 4, wherein the radiator also serves as the intermediate cooling heat exchanger that constitutes the adsorption heat pump heat exchanger.

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