JP5402564B2 - Adsorption refrigerator and refrigerator - Google Patents

Description

  The present invention relates to an adsorption refrigerator that exhibits a refrigerating capacity by adsorbing a refrigerant to an adsorbent and desorbs an adsorbed refrigerant by heating the adsorbent, and a refrigeration apparatus using the same.

  Conventionally, it has an adsorber filled with an adsorbent, evaporates the refrigerant by adsorbing the adsorbent in the gas phase state to the adsorbent during the adsorption process, exhibits its refrigeration capacity by its latent heat of evaporation, and desorbs An adsorption refrigerator that desorbs the adsorbing refrigerant by heating the adsorbent during the process is known.

  In this type of adsorption refrigerator, generally, two first and second adsorbers are provided, and a first operation in which the first adsorber is used as an adsorption process and the second adsorber is used as a desorption process. By switching between the mode and the second operation mode in which the first adsorber is in the desorption process and the second adsorber is in the adsorption process, the refrigerating capacity can be continuously exhibited. ing.

  For example, in the engine-driven refrigeration apparatus disclosed in Patent Document 1, a vapor compression refrigeration cycle apparatus having an engine-driven compressor and an evaporator that cools indoor blown air, and two first and second adsorptions When the indoor blast air is cooled by the refrigeration cycle device, the adsorption chiller is operated while switching between the first operation mode and the second operation mode every predetermined time. I am letting.

  Further, in the first operation mode, the refrigerant for the refrigeration cycle discharged from the compressor is cooled by the refrigeration capacity exhibited by the first adsorber, and the adsorbent of the second adsorber is heated using engine cooling water as a heat source. In the second operation mode, the refrigerant for the refrigeration cycle discharged from the compressor is cooled by the refrigerating capacity exhibited by the second adsorber, and the adsorbent of the first adsorber is heated using engine cooling water as a heat source.

  This effectively cools the refrigerant for the refrigeration cycle discharged from the compressor efficiently and continuously using the engine waste heat, and lowers the enthalpy of the refrigerant flowing into the evaporator, so that the entire engine-driven refrigeration system As the cooling capacity is improved.

Japanese Patent Laid-Open No. 11-14215

  Incidentally, some adsorbents used in this type of adsorption refrigerator include those whose adsorption isotherm and desorption isotherm change as shown in FIG.

  More specifically, in FIG. 2, the adsorption isotherm shows a change in the amount of refrigerant adsorbed on the adsorbent per unit mass during the adsorption process with respect to a change in relative humidity at a predetermined temperature, and is shown as a desorption isotherm. The change in the amount of refrigerant adsorbed on the adsorbent per unit mass during the desorption process with respect to the change in the relative humidity at a predetermined temperature is shown.

  The relative humidity is the vapor pressure ratio of the vapor pressure P1 of the actual adsorption refrigerant in the atmosphere in which the adsorbent is present to the saturated vapor pressure P2 of the adsorbent refrigerant in the atmosphere in which the adsorbent is present (atmosphere in the adsorber). (P1 / P2). In FIG. 2, an adsorbent made of aluminum oxide, phosphoric acid, and silica gel is used as the adsorbent.

  As is clear from FIG. 2, the adsorption isotherm and desorption isotherm do not completely match and have hysteresis, so depending on the operating conditions, the same time is taken during the adsorption step and the desorption step. Even if the relative humidity is changed by a predetermined amount, the amount of adsorbed refrigerant adsorbed on the adsorbent does not match the amount of desorbed refrigerant desorbed from the adsorbent.

  In other words, depending on the operating conditions, the amount of adsorbed refrigerant per unit time during the adsorption step (hereinafter referred to as adsorption rate) and the amount of desorbed refrigerant per unit time during the desorption step (hereinafter referred to as desorption rate). ) Will not match.

  For example, in FIG. 2, under the operating conditions in which the relative humidity is changed between the first relation humidity A and the second relation humidity B during the adsorption process and the desorption process, the relation humidity is the first relation humidity A during the desorption process. The amount of the desorbed refrigerant when it decreases from the second related humidity B to the second related humidity B is smaller than the amount of the adsorbed refrigerant when the related humidity increases from the second related humidity B to the first related humidity A during the adsorption step. That is, the desorption rate is slower than the adsorption rate.

  Therefore, even if the relative humidity is changed by a predetermined amount during the desorption process, the refrigerant adsorbed during the adsorption process cannot be sufficiently desorbed. Even if the adsorbent is made to adsorb the refrigerant again, the amount of adsorbed refrigerant decreases with respect to the adsorbent from which all the adsorbed refrigerant has been desorbed, so that sufficient refrigeration capacity cannot be exhibited.

  Further, for example, in FIG. 2, under the operating conditions in which the relative humidity is changed between the second relational humidity B and the third relational humidity C during the adsorption process and the desorption process, the relational humidity is the third relational humidity during the adsorption process. The amount of adsorbed refrigerant when increasing from C to the second related humidity B is less than the amount of desorbed refrigerant when the related humidity decreases from the third related humidity C to the second related humidity B during the desorption process. . That is, the adsorption rate becomes slower than the desorption rate.

  Therefore, even if the relative humidity is changed by a predetermined amount during the adsorption process, the adsorbent is switched to the desorption process before sufficiently adsorbing the refrigerant, so that sufficient refrigeration capacity cannot be exhibited. . Therefore, in the adsorption type refrigerator that employs an adsorbent whose adsorption rate and desorption rate do not coincide with each other, like the adsorption type refrigerator of Patent Document 1, the first operation mode and the second operation mode are simply It is not possible to exhibit a sufficient refrigerating capacity by simply switching at a predetermined time.

  In view of the above points, an object of the present invention is to provide an adsorption refrigerator that can continuously exhibit sufficient refrigeration capacity even when an adsorbent whose adsorption rate and desorption rate do not match is employed. To do.

  In addition, the present invention provides a refrigeration apparatus to which an adsorption refrigerator that can continuously exhibit sufficient refrigeration capacity even when an adsorbent whose adsorption rate and desorption rate do not match is employed. For other purposes.

In order to achieve the above object, according to the first aspect of the present invention, a plurality of adsorbers (21a to 21a) in which an adsorbent (S) that adsorbs a refrigerant and desorbs the adsorbed refrigerant by being heated is enclosed. 21c), among the plurality of adsorbers (21a to 21c), an adsorber serving as an adsorption process for adsorbing the refrigerant on the adsorbent (S) and a desorption process for desorbing the refrigerant adsorbed from the adsorbent (S) Operation mode switching means (32a to 32c, 33a to 33c, 42a to 42c, 43a to 43c) for switching a plurality of operation modes by switching the adsorbers, and the operation mode switching means (32a to 43c), Adsorption refrigeration that continuously exhibits refrigeration capability by switching at least one of the plurality of adsorbers (21a to 21c) to the adsorption step when switching to any of the operation modes. There is,
Three or more adsorbers (21a to 21c) are provided, and the three or more adsorbers (21a to 21c) perform the adsorbent (S) so as to perform the adsorption step and the desorption step independently. ) For cooling the cooling medium (30) and the heating medium (40) for heating the adsorbent (S) . ) Is switched to any operation mode, the number of adsorbers serving as the adsorption process is different from the number of adsorbers serving as the desorption process, and the operation mode switching means (32a... 43c) is operated in the operation mode. When the adsorber is switched, an adsorber that maintains the adsorption process or the desorption process is provided, and any one of the three or more adsorbers (21a to 21c) is an adsorption process. Time and desorption process The remaining time among the three or more adsorbers (21a to 21c) is also the time for the adsorption step and the time for the desorption step. It is the same as one adsorber .

According to this, when the operation mode switching means (32a... 43c) switches the operation mode, an adsorber that maintains the adsorption process or the desorption process is provided, and three or more adsorbers ( In any one of the adsorbers 21a to 21c), the time of the adsorption process is different from the time of the desorption process, and three or more adsorbers (21a to 21c) have different times. Among the remaining adsorbers, the time for the adsorption process and the time for the desorption process are the same as the one adsorber.
For this reason, the time of the adsorption process and the time of the desorption process are different in any of the adsorbers (21a to 21c), and further, the adsorption process in each of the adsorbers (21a to 21c) Since the adsorption time and the desorption rate are equal to each other, even if an adsorbent whose adsorption rate does not match the desorption rate is used, the amount of adsorbed refrigerant and the amount of desorbed refrigerant The amount can be an equivalent amount.

  In addition, the equivalent in this claim does not only mean that the amount of the adsorbed refrigerant and the amount of the desorbed refrigerant are completely the same, but it is possible to cause the adsorption refrigerator to exhibit sufficient refrigeration capacity. This means that the amount of adsorbed refrigerant and the amount of desorbed refrigerant are approximately equal to the extent possible.

  Therefore, the adsorber that has not sufficiently desorbed the refrigerant from the adsorbent (S) during the desorption process is switched to the adsorption process, or the adsorber in the adsorption process is sufficiently charged with the adsorbent (S). By avoiding switching to the desorption step before the adsorption, the adsorption refrigerator can exhibit a sufficient refrigeration capacity.

  Further, since the number of adsorbers used as the adsorption process is different from the number of adsorbers used as the desorption process, the predetermined adsorber is desorbed when the operation mode switching means (32a... 43c) switches the operation mode. Even if it maintains in a process, another adsorption machine can be certainly made into an adsorption process. As a result, it is possible to provide an adsorption refrigerator that can continuously exhibit sufficient refrigeration capacity even when an adsorbent whose adsorption rate and desorption rate do not match is employed.

  Specifically, as in the invention described in claim 2, in the adsorption refrigerator according to claim 1, the plurality of adsorbers (21a to 21c) include the first to third adsorbers (21c). 3 or more are provided, and as a plurality of operation modes, the first adsorber (21a) is set as an adsorption step, the second adsorber (21b) is set as a desorption step, and a third adsorber ( After the first operation mode in which 21c) is one of the adsorption step and the desorption step, and after the first operation mode, the first adsorber (21a) is set as the desorption step and the second adsorber (21b) ) As an adsorption step, and further, a second operation mode in which the third adsorber (21c) is the same one step as the first operation mode is provided.

  Thus, specifically, the third adsorber (21c) is set as the adsorption process in the first operation mode, so that the third adsorber (21c) becomes the adsorption process than the time during which it is in the desorption process. You can lengthen your time. Further, by setting the third adsorber (21c) as the desorption process in the first operation mode, the time during which the third adsorber (21c) is in the desorption process is longer than the time during which the third adsorber (21c) is in the adsorption process. can do.

  Here, as described with reference to FIG. 2 described above, when the adsorption refrigerator is operated under an operating condition in which the pressure of the desorbed refrigerant is high and the relative humidity is high, the desorption rate is slower than the adsorption rate. Conversely, if the adsorption refrigerator is operated under operating conditions where the pressure of the desorbed refrigerant is low and the relative humidity is low, the adsorption rate becomes slower than the desorption rate.

  Therefore, as in the third aspect of the invention, in the adsorption type refrigerator of the second aspect, the operation mode switching means (32a... 43c) is desorbed by the adsorber as a desorption step. When the pressure of the separated refrigerant (Pc) is equal to or higher than a predetermined first reference pressure (XPc), the third adsorber (21c) may be used as the desorption step in the first operation mode.

  As a result, the time during which the third adsorber (21c) is in the desorption process is made longer than the time during which the third adsorber (21c) is in the adsorption process during the operating condition in which the desorption speed is slower than the adsorption speed. The refrigerant can be sufficiently desorbed from the adsorbent of the vessel (21c).

  Further, as in the invention according to claim 4, in the adsorption refrigerator as claimed in claim 2 or 3, the operation mode switching means (32a ... 43c) is desorbed by an adsorber which is a desorption step. When the pressure (Pc) of the desorbed refrigerant is lower than the predetermined first reference pressure (XPc), the third adsorber (21c) may be used as the adsorption step in the first operation mode.

  As a result, the time during which the third adsorber (21c) is in the adsorption step is longer than the time during which the third adsorber (21c) is in the desorption step during the operating condition in which the adsorption rate is slower than the desorption rate. Sufficient refrigerant can be adsorbed to the adsorbent of the vessel (21c).

  In addition, as described with reference to FIG. 2 described above, when the adsorption refrigerator is operated under an operation condition in which the pressure of the adsorbed refrigerant is increased and the relative humidity is high, the desorption rate becomes slower than the adsorption rate. Conversely, if the adsorption refrigerator is operated under operating conditions where the pressure of the adsorbed refrigerant is low and the relative humidity is low, the adsorption rate becomes slower than the desorption rate.

  Therefore, as in the fifth aspect of the invention, in the adsorption type refrigerator of the second aspect, the operation mode switching means (32a... 43c) is an adsorption refrigerant adsorbed by the adsorber that serves as an adsorption step. When the pressure (Pe) is equal to or higher than a predetermined second reference pressure (XPe), the third adsorber (21c) may be used as the desorption step in the first operation mode.

  As a result, the time during which the third adsorber (21c) is in the desorption process is made longer than the time during which the third adsorber (21c) is in the adsorption process during the operating condition in which the desorption speed is slower than the adsorption speed. The refrigerant can be sufficiently desorbed from the adsorbent of the vessel (21c).

  Further, as in the invention described in claim 6, in the adsorption type refrigerator according to claim 2 or 3, the operation mode switching means (32a ... 43c) is adsorbed by an adsorber serving as an adsorption step. When the refrigerant pressure (Pe) is lower than a predetermined second reference pressure (XPe), the third adsorber (21c) may be used as the adsorption step in the first operation mode.

  As a result, the time during which the third adsorber (21c) is in the adsorption step is longer than the time during which the third adsorber (21c) is in the desorption step during the operating condition in which the adsorption rate is slower than the desorption rate. Sufficient refrigerant can be adsorbed to the adsorbent of the vessel (21c).

In the invention according to claim 7, a plurality of adsorbers (21a, 21b) each enclosing an adsorbent (S) that adsorbs the refrigerant and desorbs the refrigerant adsorbed by being heated, Among the adsorbers (21a, 21b), an adsorber that is an adsorption step for adsorbing the refrigerant to the adsorbent (S) and an adsorber that is a desorption step for desorbing the refrigerant adsorbed from the adsorbent (S) are switched. Accordingly, an operation mode switching means (61g, 61h) for switching a plurality of operation modes is provided. When the operation mode switching means (61g, 61h) is switched to any of the operation modes, the plurality of adsorbers (21a , 21b) is an adsorption chiller that continuously exhibits the refrigerating capacity by making at least one of the adsorption steps,
A cooling heat medium supply means (31) for supplying a cooling heat medium for cooling the adsorbent (S) to the adsorber used for the adsorption process, and an adsorbent ( Heating medium supply means (41) for supplying a heating medium for heating S),
Either one of the cooling heat medium supply means (31) and the heating heat medium supply means (41) has an amount of adsorbed refrigerant adsorbed by an adsorber that serves as an adsorption step for a predetermined time and a predetermined time. Further, the operation is performed so that the amount of the desorbed refrigerant desorbed by the adsorber which is the desorption step becomes equal.

  According to this, any one of the cooling heat medium supply means (31) and the heating heat medium supply means (41) has an amount of adsorbed refrigerant adsorbed by the adsorber that is an adsorption step in a predetermined time. Since the operation is performed so that the amount of the desorbed refrigerant desorbed in the adsorber that becomes the desorption process at a predetermined time becomes equal, an adsorbent whose adsorption rate and desorption rate do not match is adopted. In addition, the adsorption refrigeration machine can exhibit sufficient refrigeration capacity.

  In addition, the equivalent in this claim does not only mean that the amount of the adsorbed refrigerant and the amount of the desorbed refrigerant are completely the same, but it is possible to cause the adsorption refrigerator to exhibit sufficient refrigeration capacity. This means that the amount of adsorbed refrigerant and the amount of desorbed refrigerant are approximately equal to the extent possible.

  In the invention according to claim 8, in the adsorption refrigeration machine according to claim 7, when the pressure of the desorbed refrigerant (Pc) is equal to or higher than a predetermined first reference pressure (XPc), desorption is performed. The heating heat medium supply capability of the heating medium supply means (41) is increased so that the relative humidity of the separated refrigerant is lower than that of the adsorption refrigerant.

  According to this, the heating-heat-medium supply capability of the heating-heat-medium supply means (41) can be increased, and the amount of desorbed refrigerant in the adsorber that is in the desorption process can be increased. Therefore, even if the adsorption refrigeration machine is operated under an operating condition in which the pressure of the desorbed refrigerant becomes equal to or higher than the first reference pressure (XPc) and the desorption rate tends to be slower than the adsorption rate, the desorption rate is increased. Thus, the amount of the adsorbed refrigerant and the amount of the desorbed refrigerant can be made equal.

  In the invention according to claim 9, in the adsorption refrigerator according to claim 7, when the pressure (Pe) of the adsorbed refrigerant is equal to or lower than a predetermined second reference pressure (XPe), the adsorbed refrigerant The cooling heat medium supply capability of the cooling heat medium supply means (31) is increased so that the relative humidity of the refrigerant becomes higher than that of the desorbed refrigerant.

  According to this, it is possible to increase the amount of the adsorbed refrigerant of the adsorber that is in the adsorption process by increasing the cooling heat medium supply capability of the cooling heat medium supply means (31). Therefore, even if the adsorption refrigeration machine is operated under an operating condition in which the pressure of the adsorbed refrigerant becomes equal to or lower than the second reference pressure (XPe) and the adsorption speed tends to be slower than the desorption speed, the adsorption speed is increased. The amount of adsorbed refrigerant and the amount of desorbed refrigerant can be made equal.

  Further, in the adsorption refrigerator according to any one of claims 1 to 9, the adsorbent (S) is made of aluminum oxide, phosphoric acid and silica gel as in the invention of claim 10. The adsorbent (S) may be made of aluminum oxide, phosphoric acid and iron oxide, as in the invention described in claim 11.

  These adsorbents (S) have large hysteresis of adsorption isotherm and desorption isotherm as shown in FIG. 2 described above. For this reason, in the adsorption type refrigerator using these adsorbents (S), the amount of the adsorbed refrigerant and the amount of the desorbed refrigerant can be made equal in order to continuously exhibit sufficient refrigeration capacity. Is extremely effective.

  According to a twelfth aspect of the present invention, the adsorption refrigeration machine (20) according to any one of the first to eleventh aspects, a compressor (11) driven by an internal combustion engine (16), and a refrigerant for a refrigeration cycle. And a vapor compression refrigeration cycle device (10) having an evaporator (14) for evaporating the indoor blown air to cool the indoor blown air. In the adsorber that is a desorption step, the cooling water of the internal combustion engine (16) is used as a heat source. The refrigeration apparatus is characterized in that the adsorbent (S) is heated and the refrigerant for the refrigeration cycle discharged from the compressor (11) is cooled by the refrigeration capacity exhibited by the adsorber that serves as an adsorption step.

  According to this, the refrigeration cycle refrigerant discharged from the compressor (11) is efficiently cooled using the waste heat of the internal combustion engine (16), and the enthalpy of the refrigerant flowing into the evaporator (14) is reduced. Can be reduced. Furthermore, since the adsorption refrigerator (20) according to any one of claims 1 to 11 is provided, an adsorption rate and a desorption rate are used as the adsorbent (S) of the adsorption refrigerator (20). Even if the incompatible adsorbent (S) is employed, sufficient refrigeration capacity can be exhibited.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

It is a whole block diagram of the stationary air conditioner of 1st Embodiment. It is a graph which shows the adsorption isotherm and desorption isotherm of the adsorbent of 1st Embodiment. It is a flowchart which shows the principal part of control of the adsorption | suction type refrigerator of 1st Embodiment. (A) is a time chart which shows the change of the operation mode at the time of the desorption priority operation | movement of the adsorption | suction type refrigerator of 1st Embodiment, (b) is a time chart which shows the change of the operation mode at the time of adsorption | suction priority operation. It is. It is a flowchart which shows the principal part of control of the adsorption type refrigerator of 2nd Embodiment. It is a whole block diagram of the stationary air conditioner of 3rd Embodiment. It is a whole block diagram of the stationary air conditioner of 4th Embodiment. It is a flowchart which shows the principal part of control of the adsorption type refrigerator of 4th Embodiment. It is a flowchart which shows the principal part of control of the adsorption type refrigerator of 5th Embodiment.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is an overall configuration diagram of an engine-driven stationary air conditioner 1 that is a refrigeration apparatus of the present embodiment. This stationary air conditioner 1 includes a vapor compression refrigeration cycle apparatus 10 and an adsorption refrigeration machine 20, and performs a cooling operation for cooling indoor blown air blown into the room and a heating operation for heating indoor blown air. It is configured to be switchable.

  In addition to the compressor 11, the outdoor heat exchanger 12, the decompression device 13, and the indoor heat exchanger 14, the refrigeration cycle apparatus 10 uses a refrigerant flow path for the refrigerant for the refrigeration cycle as a refrigerant flow path for the cooling operation and a heating flow operation. An electric four-way valve 15 or the like that switches to the refrigerant flow path is provided. In FIG. 1, the solid line arrows in the vicinity of the refrigerant flow path of the refrigeration cycle apparatus 10 indicate the refrigerant flow during the cooling operation, and the broken line arrows indicate the refrigerant flow during the heating operation.

  The compressor 11 sucks, compresses and discharges the refrigerant for the refrigeration cycle, and is driven by a rotational driving force output from the internal combustion engine (engine) 16 via a pulley and a belt. In the present embodiment, a normal chlorofluorocarbon refrigerant is employed as the refrigerant for the refrigeration cycle, but, of course, a hydrocarbon refrigerant, carbon dioxide, or the like may be employed.

  Further, in the present embodiment, a swash plate type variable displacement compressor capable of continuously variably controlling the discharge capacity by a control signal output from an air conditioning controller 50 described later is employed as the compressor 11. In the compressor 11, the refrigerant discharge capacity can be changed by the discharge capacity control by the air conditioning controller 50. Of course, a fixed capacity compressor may be adopted as the compressor 11 and the refrigerant discharge capacity may be changed by controlling the rotational speed of the engine 16.

  The engine 16 is a diesel engine using kerosene as fuel, and has a starter (not shown), a fuel injection valve, and a fuel injection valve drive device, and the valve opening degree of the fuel injection valve is changed by the fuel injection valve drive device. By controlling the fuel injection amount, the rotational speed is controlled. The operation of the fuel injection valve driving device is controlled by a control signal from the air conditioning control device 50.

  Since the engine 16 generates heat during operation, the engine 16 is connected to an engine coolant circuit 40 that circulates engine coolant for cooling the engine 16. The engine coolant circuit 40 includes an electric engine coolant pump 41 for circulating the engine coolant, a radiator (not shown) that radiates heat by exchanging heat between the engine coolant and the atmosphere.

  The operation of the engine coolant pump 41 is controlled by the control voltage of the air conditioning controller 50. Moreover, as engine cooling water, ethylene glycol aqueous solution is employable, for example.

  Furthermore, the engine cooling water circuit 40 is connected to first to third adsorption cores 24a to 24c of the adsorption refrigeration machine 20 described later connected in parallel to the radiator. Details of the connection relationship between the first to third adsorption cores 24a to 24c and the engine coolant circuit 40 will be described later.

  The refrigerant discharge side of the compressor 11 of the refrigeration cycle apparatus 10 is connected to the refrigerant inlet side of an oil separator 17 that separates compressor lubricating oil mixed in the refrigeration cycle refrigerant. The oil separator 17 separates oil in the refrigerant and returns the oil to the refrigerant inlet side of the compressor 11 through a decompression mechanism (not shown). As this pressure reducing mechanism, a fixed throttle such as a capillary tube or an orifice can be employed.

  An electric four-way valve 15 is connected to the refrigerant outlet side of the oil separator 17 as a flow path switching means for switching between a refrigerant flow path for cooling operation and a refrigerant flow path for heating operation.

  The electric four-way valve 15 is a refrigerant circuit for cooling operation that connects the refrigerant outlet side of the compressor 11 and the outdoor heat exchanger 12 and the indoor heat exchanger 14 and the refrigerant inlet side of the accumulator 19 simultaneously. (The flow path indicated by the solid line arrow in FIG. 1) and the refrigerant discharge port side of the compressor 11 and the indoor heat exchanger 14 and the outdoor heat exchanger 12 and the refrigerant inlet side of the accumulator 19 are connected simultaneously. The refrigerant circuit for heating operation (a flow path indicated by a broken line arrow in FIG. 1) is switched. The operation of the electric four-way valve 15 is controlled by the control voltage of the air conditioning control device 50.

  The outdoor heat exchanger 12 exchanges heat between the refrigerant passing through the inside and the outdoor air blown by the blower 12a. The blower 12a is an electric blower that drives an axial fan by an electric motor. The rotational speed (air flow rate) of the blower 12 a is controlled by the control voltage of the air conditioning control device 50.

  The indoor heat exchanger 14 exchanges heat between the refrigerant passing through the interior and the indoor blast air blown by the blower 14a. The basic configuration of the blower 14a is the same as that of the blower 12a. Accordingly, the rotational speed (air flow rate) of the blower 14 a is also controlled by the control voltage of the air conditioning control device 50.

  The accumulator 19 is a gas-liquid separator that separates the gas-liquid of the refrigerant and stores excess refrigerant. The gas-phase refrigerant outlet of the accumulator 19 is connected to the refrigerant suction side of the compressor 11.

  Further, as indicated by solid line arrows in FIG. 1, an adsorption evaporator 23 of an adsorption refrigeration machine 20 described later is connected to the refrigerant outlet side of the outdoor heat exchanger 12 during the cooling operation. The detailed configuration of the adsorption evaporator 23 will be described later. Further, the refrigerant outlet side of the adsorption evaporator 23 during the cooling operation is provided with a first check valve 18a that only allows the refrigerant for the refrigeration cycle to flow from the adsorption evaporator 23 side to the decompression device 13 side. A decompressor 13 is connected.

  The decompression device 13 decompresses and expands the high-pressure refrigeration cycle refrigerant discharged from the compressor 11 to a predetermined pressure. In the present embodiment, a fixed throttle such as a capillary tube or an orifice is employed. ing. Of course, a variable throttle such as an electric expansion valve or a temperature expansion valve may be employed.

  Furthermore, the adsorption evaporator 23 and the decompression device are not allowed to flow between the refrigerant outlet side of the outdoor heat exchanger 12 and the refrigerant inlet side of the decompression device 13 during the cooling operation without circulating the refrigerant to the outdoor heat exchanger 12. 13 is provided. The bypass circuit 18c is provided with a second check valve 18b that only allows the refrigerant for the refrigeration cycle to flow from the decompression device 13 side to the outdoor heat exchanger 12 side.

  Therefore, due to the action of the first and second check valves 18a and 18b, the refrigerant flowing out of the outdoor heat exchanger 12 is adsorbed during the cooling operation in which the refrigerant for the refrigeration cycle flows as shown by the solid line arrows in FIG. It flows into the decompression device 13 through the evaporator 23 for use. Further, during the heating operation in which the refrigerant for the refrigeration cycle flows as shown by the broken line arrows in FIG. 1, the refrigerant that has flowed out from the decompression device 13 flows into the outdoor heat exchanger 12 through the bypass circuit 18c.

  Next, the adsorption refrigerator 20 will be described. The adsorption refrigerator 20 of the present embodiment includes a plurality of adsorbers (specifically, three adsorbers of first to third adsorbers 21a to 21c), an adsorption condenser 22, an adsorption evaporator 23, and the like. It is configured.

  The first adsorber 21a is configured such that the first adsorbing core 24a is accommodated (enclosed) in a heat insulating container whose inside is substantially vacuum, and the adsorbing refrigerant can be circulated around the first adsorbing core 24a. is there. The first adsorption core 24a exchanges heat between the adsorbent S and the heating heat medium that heats the adsorbent S or the cooling heat medium that cools the adsorbent S, and is a so-called fin-and-tube heat exchanger. The adsorbent S is joined to the surface.

  More specifically, the first adsorbing core 24a is simply referred to as a heating medium from the outside of the above-described heat insulating container. .) Is arranged in parallel between the inflow side tank communicating with the inflow port for inflowing, the outflow side tank communicating with the outflow port for allowing the heat medium to flow out of the heat insulating container, the inflow side tank, and the outflow side tank. A plurality of tubes that circulate the heat medium and heat transfer fins that are arranged between adjacent tubes and promote heat exchange are provided.

  An adsorbent S is filled in a gap formed between the inflow side tank, the outflow side tank, the tube, and the heat transfer fin. The adsorbent S adsorbs the adsorption refrigerant in the gas phase state and desorbs the adsorbed refrigerant adsorbed by being heated. In the present embodiment, as the adsorbent S, aluminum oxide, phosphoric acid and The one made of silica gel is used. Therefore, the adsorption isotherm and desorption isotherm of the adsorbent S change as shown in FIG.

  The basic configuration of the second and third adsorbers 21b and 21c is the same as that of the first adsorber 21a. Accordingly, the second and third adsorption cores 24b and 24c having the same configuration as the first adsorption core 24a are accommodated (enclosed) in the heat insulating containers of the second and third adsorption devices 21b and 21c, respectively. . In the present embodiment, water is used as the adsorption refrigerant.

  Further, the first to third adsorption cores 24a to 24c are provided with the above-described engine cooling water circuit 40 and the adsorbent cooling water circuit 30 for supplying the adsorbent cooling water to the first to third adsorption cores 24a to 24c. It is connected. The adsorbent cooling water circuit 30 includes an electric adsorbent cooling water pump 31 for circulating the adsorbent cooling water, and an adsorbent radiator 34 that radiates heat by exchanging heat with the adsorbent cooling water. Has been.

  Here, the connection relationship between the first to third adsorption cores 24a to 24c and the adsorbent coolant circuit 30 and the connection relationship between the first to third adsorption cores 24a to 24c and the engine coolant circuit 40 will be described. . In FIG. 1, thick solid arrows shown in the vicinity of the refrigerant flow path of the adsorbent cooling water circuit 30 indicate the flow of the adsorbent cooling water, and white arrows indicate the flow of the engine cooling water.

  First, when the first to third adsorbers 21a to 21c are used as the adsorption process for adsorbing the adsorbing refrigerant to the adsorbent S, the desorption process is completed as is apparent from the adsorption isotherm in FIG. It is necessary to increase the relative humidity from the time. Therefore, the heat of condensation when the adsorbent S adsorbs the adsorption refrigerant must be dissipated.

  Therefore, in the present embodiment, the adsorbent cooling water cooled by exchanging heat with the atmosphere in the adsorbent radiator 34 is passed through the adsorbent cooling water circuit 30 to the first to third adsorption cores 24a to 24c. The adsorbent S is supplied and cooled. Therefore, the adsorbent cooling water of the present embodiment is a cooling heat medium, and the adsorbent cooling water pump 31 constitutes a cooling heat medium supply means.

  Further, the first to third adsorption cores 24 a to 24 c are connected in parallel to the adsorbent radiator 34 in the adsorbent cooling water circuit 30. Further, upstream side open / close valves 32a to 32c, which are electromagnetic valves for opening and closing the adsorbent cooling water circuit 30, are arranged on the upstream side of the adsorbent cooling water flow of the first to third adsorbing cores 24a to 24c. Downstream opening / closing valves 33a to 33c, which are electromagnetic valves for opening / closing the adsorbent coolant circuit 30, are arranged on the downstream side of the water flow.

  Therefore, the first to third adsorption cores 24a to 24c to which the adsorbent cooling water is supplied can be switched by changing the open / close states of the upstream side open / close valves 32a to 32c and the downstream side open / close valves 33a to 33c. That is, the adsorber that is the adsorption process can be switched.

  The operation of the adsorbent cooling water pump 31, the upstream opening / closing valves 32a to 32c, and the downstream opening / closing valves 33a to 33c is controlled by the control voltage of the air conditioning control device 50. Further, the same coolant as the engine coolant (in this embodiment, an ethylene glycol aqueous solution) is employed as the adsorbent coolant. Therefore, in the 1st-3rd adsorption | suction core 24a-24c, even if adsorbent cooling water and engine cooling water mix, a malfunction does not arise.

  Next, when the desorption process for desorbing the adsorption refrigerant adsorbed from the first to third adsorbers 21a to 21c is performed, as is apparent from the desorption isotherm of FIG. It is necessary to lower the relative humidity from the end point of. Therefore, the adsorbent S must be heated to increase the saturated vapor pressure of the adsorbing refrigerant at the ambient temperature where the adsorbent S is present.

  Therefore, in the present embodiment, the engine coolant heated by the engine 16 is supplied to the first to third adsorption cores 24a to 24c via the engine coolant circuit 40, and the adsorbent S is heated. Therefore, the engine cooling water of the present embodiment is a heating heat medium, and the engine cooling water pump 41 constitutes a heating heat medium supply means.

  Further, the first to third adsorption cores 24 a to 24 c are connected in parallel to the radiator in the engine coolant circuit 40. Further, upstream side on / off valves 42a to 42c, which are electromagnetic valves for opening and closing the engine cooling water circuit 40, are arranged on the upstream side of the engine cooling water flow of the first to third adsorption cores 24a to 24c, and the engine cooling water flow downstream. On the side, downstream side open / close valves 43a to 43c, which are electromagnetic valves for opening and closing the engine coolant circuit 40, are arranged.

  Therefore, the first to third adsorption cores 24a to 24c to which the engine coolant is supplied can be switched by changing the open / close state of the upstream side open / close valves 42a to 42c and the downstream side open / close valves 43a to 43c. That is, the adsorber that is the desorption step can be switched. The operations of the upstream side opening / closing valves 42 a to 42 c and the downstream side opening / closing valves 43 a to 43 c are controlled by the control voltage of the air conditioning control device 50.

  That is, in this embodiment, the upstream side open / close valves 32a to 32c and the downstream side open / close valves 33a to 33c of the adsorbent coolant circuit 30, and the upstream side open / close valves 42a to 42c and the downstream side open / close valves of the engine coolant circuit 40 are shown. The operation mode switching means is constituted by 43a to 43c, and the operation mode control means is constituted by software and hardware for controlling these on-off valves 32a ... 43c in the air conditioning control device 50.

  The adsorption condenser 22 exchanges heat between the refrigerant for adsorption in the gas phase (hereinafter referred to as desorption refrigerant) desorbed from the adsorbent S of the first to third adsorption cores 24a to 24c and the outdoor air. This is a heat exchanger for condensation that condenses the desorbed refrigerant.

  Further, the first to third adsorption cores 24a to 24c function as check valves that permit only desorption refrigerant to flow from the first to third adsorption cores 24a to 24c side to the adsorption condenser 22, respectively. It is connected to the adsorption condenser 22 via the first to third condensation side water vapor valves 25a to 25c.

  The adsorption evaporator 23 evaporates the adsorption refrigerant by exchanging heat between the liquid phase adsorption refrigerant and the refrigerant for the refrigeration cycle, and adsorbs the adsorption refrigerant S on the first to third adsorption cores 24a to 24c. It is a heat exchanger for evaporation that generates a gas-phase adsorption refrigerant (hereinafter referred to as an adsorption refrigerant).

  Further, the first to third adsorption cores 24a to 24c function as check valves that permit only the desorbed refrigerant to flow from the adsorption evaporator 23 side to the first to third adsorption cores 24a to 24c side, respectively. The first to third evaporation side water vapor valves 26a to 26c are connected to the adsorption evaporator 23.

  The adsorption condenser 22 and the adsorption evaporator 23 are connected by a refrigerant return circuit 44 that returns the adsorption refrigerant condensed in the adsorption condenser 22 to the adsorption evaporator 23. The refrigerant return circuit 44 is provided with a refrigerant return valve 45 that is an electromagnetic valve that opens and closes the refrigerant return circuit 44.

  The operation of the refrigerant return valve 45 is controlled by the control voltage of the air conditioning control device 50, and the air conditioning control device 50 opens and closes the refrigerant return valve 45 at predetermined time intervals, whereby the adsorption condenser 22 is operated. The adsorbing refrigerant condensed in step 1 is returned to the adsorbing evaporator 23.

  Next, the air conditioning control device 50 will be described. The air conditioning control device 50 is composed of a well-known microcomputer including a CPU, ROM, RAM and the like and its peripheral circuits, and performs various calculations and processing based on a control program stored in the ROM. The operation of various components of the apparatus 10 and the adsorption chiller 20 is controlled.

  A sensor group for air conditioning control and a remote controller 51 are connected to the input side of the air conditioning controller 50, and a detection signal of the sensor group and an operation signal of the remote controller 51 are input. The air conditioning control device 50 performs predetermined arithmetic processing based on these input signals and outputs control signals to various components of the refrigeration cycle device 10 and the adsorption chiller 20 connected to the output side.

  As the sensor group, specifically, an outside air temperature sensor 52 that detects an outdoor air temperature, an inside air temperature sensor 53 that detects an indoor air temperature that is an air-conditioning target space, and a condensed refrigerant pressure Pc in the adsorption condenser 22 are detected. A condenser pressure sensor 54, an evaporator pressure sensor 55 for detecting the evaporated refrigerant pressure Pe in the adsorption evaporator 23, and the like are connected.

The remote controller 51 is provided with an operation switch for operating the stationary air conditioner 1, an operation changeover switch for switching between cooling operation and heating operation, a target temperature setting switch for setting a target temperature in the room, and the like. In FIG. 1, for clarity of illustration, omitting the connection wiring between the connection wiring and the air conditioning controller 50 and sensors with various constituent equipment of the air conditioning control device 50 and the refrigeration cycle apparatus 10 and the adsorption refrigerating machine 20 doing.

  Next, the operation of this embodiment in the above configuration will be described. First, when the operation switch of the remote controller 51 is turned on, the air conditioning control device 50 operates the blowers 12a and 14a and the engine cooling water pump 41 at a predetermined number of revolutions, and the discharge capacity of the compressor 11 and The rotational speed of the engine 16 is controlled.

  The discharge capacity of the compressor 11 and the rotational speed of the engine 16 are based on the detected value detected by the sensor group described above and the indoor target temperature set by the target temperature setting switch of the remote controller 51. With reference to a control map stored in advance in the air conditioning control device 50, it is determined so that the refrigeration cycle device 10 can exhibit the required refrigeration capacity.

  Further, when the operation switch is turned on and the cooling operation is selected by the operation changeover switch, the air conditioning control device 50 operates the adsorbent coolant pump 31 at a predetermined number of revolutions, and The cooling operation is executed by switching the refrigerant flow path of the refrigeration cycle apparatus 10 to a cooling medium flow path for cooling operation.

  Specifically, the electric four-way valve 15 simultaneously connects between the refrigerant discharge port side of the compressor 11 and the outdoor heat exchanger 12 and between the indoor heat exchanger 14 and the refrigerant inlet side of the accumulator 19. Switch to.

  As a result, the refrigerant for the refrigeration cycle, as indicated by the solid line arrow in FIG. 2, is the compressor 11 → (oil separator 17 → electric four-way valve 15 →) outdoor heat exchanger 12 → adsorption evaporator 23 → (first A known vapor compression refrigeration cycle that circulates in the order of the check valve 18a →) the pressure reducing device 13 → the indoor heat exchanger 14 → (the electric four-way valve 15 → the accumulator 19 →) the compressor 11 is configured. Therefore, by cooling the refrigerant for the refrigeration cycle and exhibiting an endothermic effect in the indoor heat exchanger 14, it is possible to cool the indoor blown air and realize the cooling operation.

  Further, in the cooling operation, the air conditioning control device 50 controls the operation of the adsorption refrigeration machine 20 as shown in the flowchart of FIG. Note that the flowchart shown in FIG. 3 is executed as a subroutine of a main routine executed by the air conditioning control device 50.

  First, in step S1, it is determined whether or not the condensed refrigerant pressure Pc in the adsorption condenser 22 detected by the condenser pressure sensor 54 is equal to or higher than the first reference pressure XPc. The first reference pressure XPc is a value set to determine whether or not the operating condition of the adsorption refrigeration machine 20 is an operating condition in which the desorption rate is slower than the adsorption rate.

  Here, for example, as shown in FIG. 2, a range in which the relative humidity is high as in the case where the relative humidity is changed between the first relative humidity A and the second relative humidity B during the adsorption process and the desorption process. When the adsorption refrigeration machine 20 is operated under these operating conditions, the desorption rate becomes slower than the adsorption rate. Conversely, when the adsorption refrigeration machine 20 is operated under operating conditions in a range where the relative humidity is low, as in the case where the relative humidity is changed between the second relative humidity B and the third relative humidity C, the adsorption rate is greater than the desorption rate. Will also be late.

  Therefore, when the relative humidity of the desorbed refrigerant at the end of the desorption process is equal to or higher than the first reference pressure XPc, it can be determined that the operating condition is such that the desorption rate is slower than the adsorption rate. . Conversely, if the relative humidity of the desorbed refrigerant at the end of the desorption process is lower than the first reference pressure XPc, it is determined that the operating condition is such that the adsorption rate is slower than the desorption rate. it can.

  Furthermore, in the adsorber that is the desorption step, the pressure of the refrigerant for adsorption in the heat insulating container rises, so that the condensation side water vapor valve is opened. Therefore, the condensed refrigerant pressure Pc is equal to the pressure of the desorbed refrigerant. Therefore, by using the condensed refrigerant pressure Pc, it can be determined whether or not the operating condition of the adsorption refrigeration machine 20 is an operating condition in which the desorption speed is slower than the adsorption speed.

  When it is determined in step S1 that the condensed refrigerant pressure Pc is equal to or higher than the first reference pressure XPc, the process proceeds to step S2 and it is determined that the adsorption refrigeration machine 20 performs the desorption priority operation. To return to the main routine.

  On the other hand, if the condensed refrigerant pressure Pc is lower than the first reference pressure XPc in step S1, the process proceeds to step S3, where it is determined that the adsorption type refrigerator 20 is to perform the adsorption priority operation, and the main routine is executed. Return to. In the main routine, the adsorption refrigerator 20 is operated as determined in steps S2 and S3.

  The desorption priority operation and the adsorption priority operation will be described with reference to the time chart of FIG. 4A is a time showing a change in the first to third adsorbers 21a to 21c that is an adsorption step or a desorption step in the desorption priority operation, that is, a change in the operation mode of the adsorption refrigeration machine 20. FIG. FIG. 4B is a time chart showing the change of the operation mode during the suction priority operation.

  First, in the desorption priority operation, as shown in FIG. 4A, the air conditioning control device 50 changes the operation mode of the adsorption refrigeration machine 20 every predetermined time (in this embodiment, 60 seconds). Then, the first operation mode → the second operation mode → the third operation mode is switched in this order, the process returns to the first operation mode again, and the switching is repeated in this order.

  The predetermined time is the time during which the adsorbent S can adsorb a sufficient amount of the adsorbing refrigerant or the time during which the adsorbent S can sufficiently desorb the adsorbed refrigerant S. It can be appropriately set according to the characteristics of the material S.

  In the first operation mode, the air conditioning control device 50 opens the upstream opening / closing valve 32a and the downstream opening / closing valve 33a of the adsorbent coolant circuit 30, and the upstream opening / closing valves 32b and 32c and the downstream opening / closing valves 33b and 33c. Is closed. Further, the upstream side open / close valve 42a and the downstream side open / close valve 43a of the engine coolant circuit 40 are closed, and the upstream side open / close valves 42b and 42c and the downstream side open / close valves 43b and 43c are opened.

  As a result, the adsorbent cooling water is supplied to the first adsorption core 24a and the engine cooling water is supplied to the second and third adsorption cores 24b and 24c. 2. The 3rd adsorption machines 21b and 21c can be made into a desorption process.

  In the next second operation mode, the air conditioning control device 50 opens the upstream opening / closing valve 32b and the downstream opening / closing valve 33b of the adsorbent coolant circuit 30, and the upstream opening / closing valves 32a, 32c and the downstream opening / closing valve 33a. , 33c are closed. Further, the upstream side open / close valve 42b and the downstream side open / close valve 43b of the engine coolant circuit 40 are closed, and the upstream side open / close valves 42a, 42c and the downstream side open / close valves 43a, 43c are opened.

  As a result, the adsorbent cooling water is supplied to the second adsorption core 24b and the engine cooling water is supplied to the first and third adsorption cores 24a and 24c, so that the first adsorber 21a is switched to the desorption process, The second adsorber 21b can be switched to the adsorption process, and the third adsorber 21c can be maintained in the desorption process.

  In the next third operation mode, the air conditioning control device 50 opens the upstream opening / closing valve 32c and the downstream opening / closing valve 33c of the adsorbent coolant circuit 30, and the upstream opening / closing valves 32a, 32b and the downstream opening / closing valve 33a. , 33b are closed. Further, the upstream side opening / closing valve 42c and the downstream side opening / closing valve 43c of the engine coolant circuit 40 are closed, and the upstream side opening / closing valves 42a, 42b and the downstream side opening / closing valves 43a, 43b are opened.

  Thereby, the adsorbent cooling water is supplied to the third adsorption core 24c, and the engine cooling water is supplied to the first and second adsorption cores 24a and 24b, so that the first adsorber 21a is maintained in the desorption process, The second adsorber 21b can be switched to the desorption process, and the third adsorber 21c can be switched to the adsorption process.

  When switching from the third operation mode to the first operation mode again, the first adsorber 21a is switched to the adsorption process, the second adsorber 21b is maintained in the desorption process, and the third adsorber 21c is desorbed. Can be switched to.

  In other words, in the desorption priority operation, the number of adsorbers that serve as the adsorption process and the number of adsorbers that serve as the desorption process among the first to third adsorbers 21a to 21c when switching to any operation mode. And any one of the adsorbers is used as an adsorption process. Further, an adsorber that maintains the desorption process when the operation mode is switched is provided, and in any of the adsorbers 21a to 21c, the time that is the desorption process is longer than the time that is the adsorption process. It is long.

  Next, in the adsorption priority operation, as shown in FIG. 4B, as in the desorption priority operation, the air conditioning control device 50 sets the operation mode of the adsorption refrigeration machine 20 to the fourth operation mode every predetermined time. → Switch in the order of the fifth operation mode → the sixth operation mode, return to the fourth operation mode again, and repeat switching in this order.

  In the fourth operation mode, the air conditioning control device 50 opens the upstream opening / closing valves 32a, 32c and the downstream opening / closing valves 33a, 33c of the adsorbent coolant circuit 30, and the upstream opening / closing valve 32b and the downstream opening / closing valve 33b. Is closed. Further, the upstream side open / close valves 42a, 42c and the downstream side open / close valves 43a, 43c of the engine coolant circuit 40 are closed, and the upstream side open / close valve 42b and the downstream side open / close valve 43b are opened.

  As a result, the adsorbent cooling water is supplied to the first and third adsorption cores 24a and 24c, and the engine cooling water is supplied to the second adsorption core 24b, so that the first and third adsorbers 21a and 21c are adsorbed. In addition, the second adsorber 21b can be a desorption step.

  In the next fifth operation mode, the air conditioning control device 50 opens the upstream side open / close valves 32b and 32c and the downstream side open / close valves 33b and 33c of the adsorbent coolant circuit 30 and opens the upstream side open / close valve 32a and the downstream side open / close valve. The valve 33a is closed. Further, the upstream side open / close valves 42b, 42c and the downstream side open / close valves 43b, 43c of the engine coolant circuit 40 are closed, and the upstream side open / close valve 42a and the downstream side open / close valve 43a are opened.

  As a result, the adsorbent cooling water is supplied to the second and third adsorbing cores 24b and 24c, and the engine cooling water is supplied to the first adsorbing core 24a, so that the first adsorber 21a is switched to the desorption process, The second adsorber 21b can be switched to the adsorption process, and the third adsorber 21c can be maintained in the adsorption process.

  In the next sixth operation mode, the air conditioning control device 50 opens the upstream opening / closing valves 32a, 32b and the downstream opening / closing valves 33a, 33b of the adsorbent coolant circuit 30, and opens the upstream opening / closing valve 32c and the downstream opening / closing. The valve 33c is closed. Further, the upstream side open / close valves 42a, 42b and the downstream side open / close valves 43a, 43b of the engine coolant circuit 40 are closed, and the upstream side open / close valve 42c and the downstream side open / close valve 43c are opened.

As a result, the adsorbent cooling water is supplied to the first and second adsorption cores 24a and 24b and the engine cooling water is supplied to the third adsorption core 24c, so that the first adsorber 21a is switched to the adsorption process, The adsorber 21b can be maintained in the adsorption process, and the third adsorber 21c can be switched to the desorption process.

  When switching from the sixth operation mode to the fourth operation mode again, the first adsorber 21a is maintained in the adsorption step, the second adsorber 21b is switched to the desorption step, and the third adsorber 21c is changed to the adsorption step. Can be switched.

  That is, in the adsorption priority operation, when switching to any operation mode, among the first to third adsorbers 21a to 21c, the number of adsorbers to be the adsorption process and the number of adsorbers to be the desorption process And any one of the adsorbers is used as a desorption process. Further, an adsorber that maintains the adsorption process when the operation mode is switched is provided, and in any of the adsorbers 21a to 21c, the time that is the adsorption process is longer than the time that is the desorption process. doing.

  Therefore, in the adsorption refrigeration machine 20 of the present embodiment, at least one of the first to third adsorbers 21a to 21c is the adsorption step even if the operation mode is switched to any one of the first to sixth operation modes. It becomes.

  And in the adsorber used as an adsorption process, since the adsorbent S is cooled by the adsorbent cooling water, the pressure of the adsorbing refrigerant in the heat insulating container is lowered. The valve is closed and the evaporation side water vapor valve is opened. Furthermore, since the relative humidity around the adsorbent S decreases due to a decrease in the pressure of the adsorbing refrigerant in the heat insulating container, the adsorbing material S adsorbs the adsorbing refrigerant in the adsorption evaporator 23.

  As a result, the adsorption refrigerant in the adsorption evaporator 23 evaporates. At this time, in the adsorber serving as the desorption process, the adsorbent S is heated by the engine cooling water, whereby the pressure of the adsorbing refrigerant in the heat insulating container increases. The valve opens and the evaporation side water vapor valve closes. Therefore, the desorbed refrigerant does not flow into the adsorption evaporator 23 side, and the adsorbed refrigerant does not flow into the adsorption condenser 22 side.

  Therefore, by sequentially switching the adsorbers serving as the adsorption process, the adsorbent S of the adsorber serving as the adsorption process can continuously evaporate the liquid-phase refrigerant in the adsorption evaporator 23. When the liquid phase refrigerant in the adsorption evaporator 23 evaporates, the refrigerant for the refrigeration cycle is continuously removed by continuously taking away the latent heat of evaporation from the refrigerant for the refrigeration cycle passing through the adsorption evaporator 23. Can be cooled.

  On the other hand, when the operation switch is turned on and the heating operation is selected by the operation switch, the air conditioning control device 50 switches the refrigerant flow path of the refrigeration cycle apparatus 10 to the refrigerant flow path for the heating operation. Thus, the heating operation is executed. Specifically, the electric four-way valve 15 simultaneously connects between the refrigerant discharge port side of the compressor 11 and the indoor heat exchanger 14 and between the outdoor heat exchanger 12 and the refrigerant inlet side of the accumulator 19. Switch to.

  As a result, the refrigerant for the refrigeration cycle is changed from the compressor 11 → (oil separator 17 → electric four-way valve 15 →) indoor heat exchanger 14 → pressure reducing device 13 → (second check valve 18b →) outdoor heat exchanger 12 → A well-known vapor compression refrigeration cycle that circulates in the order of the electric four-way valve 15 → accumulator 19 → compressor 11 is configured. Therefore, the indoor heat exchanger 14 can dissipate the refrigerant for the refrigeration cycle discharged from the compressor 11 and heat the indoor blown air to realize the heating operation.

  During the heating operation, the refrigerant for the refrigeration cycle does not flow into the adsorption evaporator 23 due to the action of the first check valve 18a. Accordingly, it is not necessary for the adsorption refrigerator 20 to exhibit the refrigeration capacity.

  Therefore, in the heating operation of the present embodiment, the air conditioning control device 50 closes the upstream side open / close valves 32a to 32c and the downstream side open / close valves 33a to 33c of the adsorbent coolant circuit 30 and upstream of the engine coolant circuit 40. The side opening / closing valves 42a to 42c and the downstream opening / closing valves 43a to 43c are opened.

  Thereby, at the time of heating operation, an engine cooling water can be supplied to the 1st-3rd adsorption | suction core 24a-24c, and it can be set as a desorption process. Therefore, when switching to the cooling operation next time, the adsorbing refrigerant can be sufficiently adsorbed to the adsorbent S of the adsorber which is the adsorption step.

  Since the stationary air conditioner 1 of the present embodiment operates as described above, during the cooling operation, the indoor air can be cooled by the indoor heat exchanger 14 of the refrigeration cycle apparatus 10 to cool the room. . At this time, the adsorber serving as the adsorption process is sequentially switched to cause the adsorption refrigeration machine 20 to continuously exhibit the refrigerating capacity, and from the adsorbent S of the adsorber serving as the desorption process using the engine cooling water of the engine 16 as a heat source. The adsorption refrigerant is desorbed.

  Therefore, the refrigerant for the refrigeration cycle discharged from the compressor 11 can be cooled by the refrigeration capacity exhibited by the adsorption refrigeration machine 20 while effectively using the engine waste heat. As a result, the enthalpy of the refrigerant flowing into the indoor heat exchanger 14 acting as an evaporator can be reduced, and the cooling capacity of the stationary air conditioner 1 can be improved. Moreover, at the time of heating operation, indoor air can be heated by heating indoor air with the indoor heat exchanger 14.

  Furthermore, in the stationary air conditioner 1 of the present embodiment, by sequentially switching the operation mode of the adsorption refrigeration machine 20, the time during which the first to third adsorbers 21a to 21c are in the adsorption process, the desorption process, You can make the time different. In addition, the time for the adsorption process and the time for the desorption process can be set equal in each of the adsorbers 21a to 21c. Therefore, even if an adsorbent whose adsorption rate and desorption rate do not match is employed, the amount of adsorbed refrigerant and the amount of desorbed refrigerant can be made equal.

  As a result, the adsorber that has not sufficiently desorbed the adsorbing refrigerant from the adsorbent S during the desorption process can be switched to the adsorbing process, or the adsorber in the adsorbing process can be replaced with the adsorbent S sufficiently. Thus, the adsorption refrigeration machine 20 can exhibit sufficient refrigeration capacity by avoiding switching to the desorption process before adsorbing the refrigeration.

  As a result, even if the adsorbing material S whose adsorption speed and desorption speed do not coincide with each other is adopted in the adsorption refrigerator 20, the adsorption refrigerator 20 can continuously exhibit sufficient refrigerating capacity. As a result, the cooling capacity of the stationary air conditioner 1 as a whole can be continuously improved.

  More specifically, in this embodiment, when it is determined in step S1 of FIG. 3 that the operating condition of the adsorption refrigeration machine 20 is an operating condition in which the desorption rate is slower than the adsorption rate. Since the desorption priority operation is performed, in any of the adsorbers 21a to 21c, the time for the desorption step can be made longer than the time for the adsorption step.

  Accordingly, in any of the adsorbers 21a to 21c, the adsorption refrigerant can be sufficiently desorbed from the adsorbent S during the desorption process, and the adsorption refrigerant can be sufficiently desorbed from the adsorbent S during the desorption process. It is possible to reliably avoid switching the adsorber that has not been used to the adsorption process.

  On the other hand, when it is determined in step S1 that the operation condition of the adsorption refrigerator 20 is not the operation condition in which the desorption rate is slower than the adsorption rate, the adsorption priority operation is performed, so any adsorber 21a. Also in -21c, the time during the adsorption step can be made longer than the time during the desorption step.

  Therefore, in any of the adsorbers 21a to 21c, the adsorption refrigerant can be sufficiently adsorbed by the adsorbent S during the adsorption process, and the adsorber in the adsorption process can sufficiently adsorb the adsorption refrigerant to the adsorbent S. It is possible to reliably avoid switching to the desorption process before.

  Further, as in this embodiment, in the adsorption refrigerator 20 in which an adsorbent having a large hysteresis of the adsorption isotherm and desorption isotherm is adopted as the adsorbent S, the time when the adsorber is in the adsorption process and the desorption are reduced. The fact that the amount of adsorbed refrigerant and the amount of desorbed refrigerant can be made equal by changing the time of the separation process is that the adsorption refrigerator 20 continuously exhibits sufficient refrigerating capacity. It is extremely effective.

(Second Embodiment)
In the first embodiment, in step S1 of the subroutine executed by the air conditioning control device 50, the operation condition of the adsorption refrigeration machine 20 using the condensed refrigerant pressure Pc is an operation condition in which the desorption speed is slower than the adsorption speed. In this embodiment, as shown in the flowchart of FIG. 5, the same is applied using the evaporative refrigerant pressure Pe in the adsorption evaporator 23 detected by the evaporator pressure sensor 55. Judgment is made.

  Specifically, in step S1 of the present embodiment, it is determined whether or not the evaporative refrigerant pressure Pe is equal to or higher than the second reference pressure XPe. The second reference pressure XPe is a value set to determine whether or not the operating condition of the adsorption refrigeration machine 20 is an operating condition in which the desorption speed is slower than the adsorption speed.

  As described above, in the adsorption refrigeration machine 20, the relationship between the adsorption rate and the desorption rate varies depending on the operating conditions (range of operating relative humidity). Therefore, when the relative humidity of the adsorbed refrigerant at the start of the adsorption process is equal to or higher than the second reference pressure XPe, it can be determined that the operating condition is such that the desorption rate is slower than the adsorption rate. Conversely, when the relative humidity of the adsorbed refrigerant at the start of the adsorption process is lower than the second reference pressure XPe, it can be determined that the operating condition is that the adsorption rate is slower than the desorption rate.

  Furthermore, in the adsorber that serves as the adsorption step, the pressure of the refrigerant for adsorption in the heat insulating container decreases, so the evaporation side water vapor valve opens. Therefore, the evaporative refrigerant pressure Pe is equal to the pressure of the adsorbed refrigerant. Therefore, by using the evaporative refrigerant pressure Pe, it is possible to determine whether or not the operating condition of the adsorption refrigeration machine 20 is an operating condition in which the desorption speed is slower than the adsorption speed.

  If it is determined in step S1 that the evaporative refrigerant pressure Pe is equal to or higher than the second reference pressure XPe, the process proceeds to step S2 and it is determined that the adsorption-type refrigerator 20 is to perform the desorption priority operation. To return to the main routine.

  On the other hand, if the evaporative refrigerant pressure Pe is lower than the second reference pressure XPe in step S1, the process proceeds to step S3, where it is determined that the adsorption-type refrigerator 20 is to perform the adsorption priority operation, and the main routine is executed. Return to. In the main routine, the adsorption refrigerator 20 is operated as determined in steps S2 and S3.

  Other configurations and operations of the stationary air conditioner 1 are the same as those in the first embodiment. Therefore, when the stationary air conditioner 1 of this embodiment is operated, the same effect as that of the first embodiment can be obtained. That is, even if the adsorbing material S whose adsorption speed and desorption speed do not coincide with each other is adopted in the adsorption refrigeration machine 20, the adsorption refrigeration machine 20 can continuously exhibit sufficient refrigeration capacity, and stationary air conditioning. The cooling capacity of the device 1 can be improved reliably.

(Third embodiment)
In the above-described embodiment, the example in which the operation mode switching means is configured by the opening / closing valves 32a... 43c arranged in the adsorbent coolant circuit 30 and the engine coolant circuit 40 has been described. As shown, these on-off valves 32a... 43c are abolished, and the first to sixth electric four-way valves 61a to 61f are arranged in the adsorbent coolant circuit 30 and the engine coolant circuit 40, and the operation mode switching means is shown. An example in which is configured will be described.

  FIG. 6 is an overall configuration diagram of the stationary air conditioner 1 of the present embodiment, and shows the flow of adsorbent coolant and engine coolant in the first operation mode in the present embodiment. Moreover, in FIG. 6, the same code | symbol is attached | subjected to the same or equivalent part as 1st Embodiment. The same applies to the following drawings.

  The first to sixth electric four-way valves 61a to 61f are configured to simultaneously switch two flow paths of the adsorbent coolant circuit 30 and the engine coolant circuit 40. Specifically, the circuits shown by solid lines in FIG. And a circuit indicated by a broken line. The operations of the first to sixth electric four-way valves 61a to 61f are controlled by the control voltage of the air conditioning control device 50, respectively.

  For example, when the air-conditioning control device 50 switches the first to sixth electric four-way valves 61a to 61f to the state of the solid line in FIG. 6, the adsorbent cooling water flowing out from the adsorbent radiator 34 is the first adsorbing core 24a. The first adsorber 21a is an adsorption process. Further, the engine cooling water flowing out from the engine 16 is supplied to the second and third adsorption cores 24b and 24c, and the second and third adsorbers 21b and 21c are in the desorption process. That is, the first operation mode is realized.

  Next, when the air-conditioning control device 50 switches the first and fifth electric four-way valves 61a and 61e from the state of the first operation mode to the state of the broken line in FIG. The material cooling water is supplied to the second adsorption core 24b, and the engine cooling water flowing out from the engine 16 is supplied to the first and third adsorption cores 24a and 24c to switch the first adsorber 21a to the desorption process. The second adsorber 21b can be switched to the adsorption process, and the third adsorber 21c can be maintained in the desorption process. That is, the second operation mode is realized.

  Next, when the air conditioning control device 50 switches the second and sixth electric four-way valves 61b and 61f to the state of the broken line in FIG. 6 from the state of the second operation mode, the adsorption that has flowed out of the adsorbent radiator 34 The material cooling water is supplied to the third adsorption core 24c, and the engine cooling water flowing out from the engine 16 is supplied to the first and second adsorption cores 24a and 24b to maintain the first adsorber 21a in the desorption process. Then, the second adsorber 21b can be switched to the desorption process, and the third adsorber 21c can be switched to the adsorption process. That is, the third operation mode is realized.

  Further, when the air conditioning control device 50 switches the first, third, fourth, and fifth electric four-way valves 61a, 61c, 61d, and 61e to the state of the broken line in FIG. The adsorbent cooling water flowing out from the material radiator 34 is supplied to the first and third adsorption cores 24a and 24c, and the first and third adsorbers 21a and 21c become the adsorption process. Further, the engine cooling water flowing out from the engine 16 is supplied to the second adsorption core 24b, and the second adsorber 21b becomes the desorption process. That is, the fourth operation mode is realized.

  Next, when the air-conditioning control device 50 switches the first and fifth electric four-way valves 61a and 61e to the solid line state of FIG. 6 from the state of the fourth operation mode, the adsorption that has flowed out of the adsorbent radiator 34 The material cooling water is supplied to the second adsorption cores 24b and 24c, and the engine cooling water flowing out from the engine 16 is supplied to the first adsorption core 24a, so that the first adsorber 21a is switched to the desorption process, and the second The adsorber 21b can be switched to the adsorption process, and the third adsorber 21c can be maintained in the desorption process. That is, the fifth operation mode is realized.

  Next, when the air-conditioning control device 50 switches the second and sixth electric four-way valves 61b and 61f to the state of the broken line in FIG. 6 from the state of the fifth operation mode, the adsorption that has flowed out of the adsorbent radiator 34. The material cooling water is supplied to the first and second adsorption cores 24a and 24b, and the engine cooling water flowing out from the engine 16 is supplied to the third adsorption core 24c, and the first adsorber 21a is switched to the adsorption process. The second adsorber 21b can be maintained in the desorption process, and the third adsorber 21c can be switched to the desorption process. That is, the sixth operation mode is realized.

  Other configurations are the same as those of the first embodiment. Therefore, also in the stationary air conditioner 1 of the present embodiment, during the cooling operation, the adsorption refrigeration machine 20 switches the first to sixth operation modes in the same manner as in the first embodiment, so that the same as in the first embodiment. The effect of can be obtained.

  In the present embodiment, the example in which the operation mode switching unit is configured by only the electric four-way valves 61a to 61f has been described. However, the configuration of the operation mode switching unit is not limited thereto. That is, the operation mode switching means may be configured such that the first to sixth operation modes can be realized by combining flow path switching means such as an on-off valve, an electric three-way valve, and an electric four-way valve.

(Fourth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 7, an adsorption type having two first and second adsorbers 21 a and 21 b in which the third adsorber 21 c is abolished with respect to the first embodiment. An example in which the refrigerator 20 is applied will be described. In this example, as in the first embodiment, the amount of adsorbed refrigerant and the desorption are used as the adsorbent S of the adsorption refrigerator 20 even if an adsorbent whose adsorption rate and desorption rate do not match is employed. An example in which the amount of the refrigerant is set to an equivalent amount will be described.

  In the adsorption refrigerator 20 of the present embodiment, the third adsorber 21c is abolished with respect to the first embodiment, and therefore the third condensing side water vapor valve 25c connected to the third adsorber 21c and the third The evaporation side water vapor valve 26c is also abolished. Furthermore, the connection relationship between the first and second adsorbers 21a and 21b, the adsorbent coolant circuit 30 and the engine coolant circuit 40, and the configuration of the operation mode switching means are different from the first embodiment.

  Specifically, in this embodiment, the seventh and eighth electric four-way valves 61g and 61h are arranged in the adsorbent coolant circuit 30 and the engine coolant circuit 40 to constitute the operation mode switching means. The seventh and eighth electric four-way valves 61g and 61h simultaneously switch the adsorbent coolant circuit 30 and the engine coolant circuit 40. The operations of the seventh and eighth electric four-way valves 61g and 61h are controlled by the control voltage of the air conditioning control device 50, respectively.

  Then, when the air conditioning control device 50 switches the seventh and eighth electric four-way valves 61g and 61h to the state of the solid line in FIG. 7, the adsorbent cooling water flowing out from the adsorbent radiator 34 becomes the first adsorbent core 24a. The first adsorber 21a is an adsorption process. Further, the engine cooling water flowing out from the engine 16 is supplied to the second adsorption core 24b, and the second adsorber 21b becomes the desorption process. In the present embodiment, this operation mode is referred to as a seventh operation mode.

  Further, when the air-conditioning control device 50 switches the seventh and eighth electric four-way valves 61g and 61h to the state of the broken line in FIG. 7, the adsorbent cooling water flowing out from the adsorbent radiator 34 is the second adsorbent core 24b. The second adsorber 21b becomes an adsorption process. Further, the engine cooling water flowing out from the engine 16 is supplied to the first adsorption core 24a, and the first adsorber 21a becomes the desorption process. In the present embodiment, this operation mode is referred to as an eighth operation mode.

  Other configurations are the same as those of the first embodiment. Next, the operation of this embodiment in the above configuration will be described. First, when the operation switch of the remote controller 51 is turned on, the air-conditioning control device 50 operates the blowers 12a and 14a and the engine coolant pump 41 at a predetermined number of revolutions as in the first embodiment. The discharge capacity of the compressor 11 and the rotational speed of the engine 16 are controlled.

  Further, when the operation switch is turned on and the cooling operation is selected by the operation changeover switch, the air conditioning control device 50 operates the adsorbent coolant pump 31 at a predetermined number of revolutions, and The cooling operation is executed by switching the refrigerant flow path of the refrigeration cycle apparatus 10 to the refrigerant flow path for the cooling operation as in the first embodiment.

  Further, in the cooling operation, the air conditioning control device 50 controls the operation of the adsorption refrigeration machine 20 as shown in the flowchart of FIG. The flowchart shown in FIG. 8 is executed as a subroutine of the main routine executed by the air conditioning control device 50.

  First, in step S1, it is determined whether or not the condensed refrigerant pressure Pc in the adsorption condenser 22 is equal to or higher than the first reference pressure XPc. As in the first embodiment, the first reference pressure XPc is set to determine whether or not the operating condition of the adsorption refrigeration machine 20 is an operating condition in which the desorption speed is slower than the adsorption speed. Value.

  If it is determined in step S1 that the condensed refrigerant pressure Pc is equal to or higher than the first reference pressure XPc, the process proceeds to step S2, and the rotational speed of the engine coolant pump 41, which is a heating medium supply means, That is, the heating medium supply capacity for the first and second adsorption cores 24a and 24b is increased, and the process returns to the main routine.

  Here, when it is determined that the condensed refrigerant pressure Pc is equal to or higher than the first reference pressure XPc, the operation condition of the adsorption refrigeration machine 20 is an operation condition in which the desorption speed is slower than the adsorption speed. Yes. Therefore, if the engine cooling water pump 41 is maintained at a predetermined rotation speed, the temperature around the adsorbent S in the adsorber that is in the desorption process cannot be quickly increased, and the adsorbent S is sufficiently removed. The adsorption refrigerant cannot be desorbed.

  Therefore, in step S2 of this embodiment, the amount of adsorbed refrigerant adsorbed by the adsorber that becomes the adsorption process at a predetermined time (60 seconds in the present embodiment) and the desorption process at the predetermined time. The number of rotations of the engine cooling water pump 41 (heating medium supply capability) is increased so that the amount of the desorbed refrigerant desorbed by the adsorber becomes equal.

  More specifically, the amount of adsorbed refrigerant is calculated based on the relative humidity of the adsorbed refrigerant obtained from the evaporated refrigerant pressure Pe detected by the evaporator pressure sensor 55, and the amount of adsorbed refrigerant and the amount of desorbed refrigerant are calculated. Determine the target relative humidity of the desorbed refrigerant to be equivalent. Then, the rotational speed of the engine coolant pump 41 is increased until the relative humidity of the desorbed refrigerant determined by the condensed refrigerant pressure Pc detected by the condenser pressure sensor 54 becomes the target relative humidity.

  Accordingly, the rotational speed of the engine coolant pump 41 is increased so that the relative humidity of the desorbed refrigerant is lower than the relative humidity of the adsorbed refrigerant. On the other hand, if it is determined in step S1 that the condensed refrigerant pressure Pc is not equal to or higher than the first reference pressure XPc, the process returns to the main routine without changing the rotational speed of the engine coolant pump 41.

  In the main routine, the above-described seventh and eighth operation modes are repeatedly switched every predetermined time (in this embodiment, 60 seconds). Thereby, in the adsorption type refrigerator 20, the first adsorber 21 a can be used as the adsorption process in the seventh operation mode, and the second adsorber 21 b can be used as the adsorption process in the eighth operation mode. Therefore, similarly to the first embodiment, the refrigerant for the refrigeration cycle can be continuously cooled.

  On the other hand, when the operation switch is turned on and the heating operation is selected by the operation changeover switch, the air conditioning control device 50 heats the refrigerant flow path of the refrigeration cycle apparatus 10 as in the first embodiment. By switching to the refrigerant flow path for operation, the heating operation is executed.

  During the heating operation, the refrigerant for the refrigeration cycle does not flow into the adsorption evaporator 23 due to the action of the first check valve 18a. Accordingly, it is not necessary for the adsorption refrigerator 20 to exhibit the refrigeration capacity. Therefore, in the heating operation of the present embodiment, the air conditioning control device 50 stops the operation of the adsorbent coolant pump 31.

  Since the stationary air conditioner 1 of the present embodiment operates as described above, during the cooling operation, as in the first embodiment, the refrigerating capacity is continuously applied to the adsorption refrigeration machine 20 while effectively using engine waste heat. And the cooling capacity of the stationary air conditioner 1 can be improved. Moreover, at the time of heating operation, indoor air can be heated by heating indoor air with the indoor heat exchanger 14.

  Further, in the stationary air conditioner 1 of the present embodiment, the engine cooling water pump 41 is operated when the operating condition of the adsorption refrigeration machine 20 is an operating condition in which the desorption speed is slower than the adsorption speed during the cooling operation. The rotation speed is increased. Therefore, even if an adsorbent whose adsorption rate and desorption rate do not match is employed, the amount of adsorbed refrigerant and the amount of desorbed refrigerant can be made equal.

  This avoids switching the adsorber that has not sufficiently desorbed the adsorbing refrigerant from the adsorbent S during the desorption process to the adsorption process, and allows the adsorption refrigerator 20 to exhibit sufficient refrigeration capacity. be able to. As a result, even if an adsorbent S whose adsorption rate and desorption rate do not coincide with each other is adopted in the adsorption refrigerator 20, the adsorption refrigerator 20 is allowed to continuously exhibit a sufficient refrigerating capacity, so that the stationary type The cooling capacity of the air conditioner 1 as a whole can be continuously improved.

(Fifth embodiment)
In the fourth embodiment, in step S1 of the subroutine executed by the air conditioning control device 50, the operation condition of the adsorption refrigeration machine 20 using the condensed refrigerant pressure Pc is an operation condition in which the desorption speed is slower than the adsorption speed. In this embodiment, as shown in the flowchart of FIG. 9, the same determination is made using the evaporative refrigerant pressure Pe. Other configurations are the same as those of the fourth embodiment.

  Specifically, in step S1 of this embodiment, it is determined whether or not the evaporative refrigerant pressure Pe in the adsorption evaporator 23 is equal to or lower than the second reference pressure XPe. Similar to the second embodiment, the second reference pressure XPe is set to determine whether the operation condition of the adsorption refrigeration machine 20 is an operation condition in which the desorption speed is slower than the adsorption speed. Value.

  If it is determined in step S1 that the evaporative refrigerant pressure Pe is equal to or lower than the second reference pressure XPe, the process proceeds to step S2 and the rotation speed of the adsorbent coolant pump 31 serving as the cooling heat medium supply means. That is, the cooling heat medium supply capacity for the first and second adsorption cores 24a and 24b is increased, and the process returns to the main routine.

  Here, when it is determined that the evaporative refrigerant pressure Pe is equal to or lower than the second reference pressure XPe, the operation condition of the adsorption refrigerator 20 is an operation condition in which the adsorption speed is slower than the desorption speed. Yes. Therefore, if the adsorbent cooling water pump 31 is maintained at a predetermined number of rotations, the temperature around the adsorbent S in the adsorber, which is the adsorption process, cannot be quickly reduced, and the adsorbent S is sufficient. The adsorption refrigerant cannot be adsorbed.

  Therefore, in step S2 of the present embodiment, the amount of the adsorbed refrigerant adsorbed by the adsorber that becomes the adsorption process at a predetermined time and the desorbed refrigerant desorbed by the adsorber that becomes the desorption process at the predetermined time. The rotation speed (cooling heat medium supply capability) of the adsorbent coolant pump 31 is increased so that the amounts are equal.

  More specifically, the amount of desorbed refrigerant is calculated based on the relative humidity of the desorbed refrigerant determined by the condensed refrigerant pressure Pc detected by the condenser pressure sensor 54, and the amount of desorbed refrigerant and the amount of adsorbed refrigerant are calculated. Determine the target relative humidity of the adsorbed refrigerant with the same amount. Then, the rotational speed of the adsorbent coolant pump 31 is increased until the relative humidity of the adsorbed refrigerant obtained from the evaporated refrigerant pressure Pe detected by the evaporator pressure sensor 55 becomes the target relative humidity.

  Therefore, the rotational speed of the adsorbent coolant pump 31 is increased so that the relative humidity of the adsorbed refrigerant is higher than that of the desorbed refrigerant. On the other hand, if it is determined in step S1 that the evaporative refrigerant pressure Pe is not less than or equal to the second reference pressure XPe, the process returns to the main routine without changing the rotational speed of the adsorbent coolant pump 31. Other controls are the same as in the fourth embodiment.

  Since the stationary air conditioner 1 of the present embodiment operates as described above, the cooling capacity of the stationary air conditioner 1 can be improved during the cooling operation, just like the fifth embodiment, and during the heating operation, The room can be heated.

  Further, in the stationary air conditioner 1 of the present embodiment, the rotation speed of the adsorbent cooling water pump 31 is the operating condition of the adsorption refrigeration machine 20 when the adsorption speed is slower than the desorption speed during the cooling operation. Is increasing. Therefore, even if an adsorbent whose adsorption rate and desorption rate do not match is employed, the amount of adsorbed refrigerant and the amount of desorbed refrigerant can be made equal.

  Thereby, it is avoided that the adsorber in the adsorption process is switched to the desorption process before sufficiently adsorbing the adsorbing refrigerant on the adsorbent S, and the adsorption refrigeration machine 20 exhibits sufficient refrigerating capacity. be able to. As a result, even if an adsorbent S whose adsorption rate and desorption rate do not coincide with each other is adopted in the adsorption refrigerator 20, the adsorption refrigerator 20 is allowed to continuously exhibit a sufficient refrigerating capacity, so that the stationary type The cooling capacity of the air conditioner 1 as a whole can be continuously improved.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) In the above-described embodiment, an example in which the adsorbent S is made of aluminum oxide, phosphoric acid, and silica gel has been described. However, the adsorbent S is not limited to this, and any adsorbent can be used. Furthermore, an adsorbent having a large hysteresis of the adsorption isotherm and desorption isotherm, such as those made of aluminum oxide, phosphoric acid and iron oxide, or synthetic zeolite, may be employed.

  (2) In the first to third embodiments described above, the adsorption refrigeration machine 20 employing the three adsorbers, the first to third adsorbers 21a to 21c, has been described, but the number of adsorbers is limited to this. Not. When three or more adsorbers are provided and the operation mode is switched, an adsorber for maintaining the adsorption process or desorption process is provided, and by sequentially switching the adsorbers for maintaining the adsorption process or desorption process, The same effect as in the first embodiment can be obtained.

  Further, in the fourth and fifth embodiments described above, the adsorption refrigeration machine 20 employing the first and second adsorbers 21a and 21b has been described, but the number of adsorbers is not limited thereto. . A plurality of adsorbers may be provided, and an adsorber serving as an adsorption process and an adsorber serving as a desorption process may be sequentially switched. In this case, an even number of adsorbers may be provided, and the number of adsorbers serving as the adsorption process may be the same as the number of adsorbers serving as the desorption process.

  (3) In the first and fourth embodiments described above, whether or not the desorption speed is lower than the adsorption speed using the condensed refrigerant pressure Pc detected by the condenser pressure sensor 54 is determined. Although it is determined, the detection value that can be used for this determination is not limited to the condensed refrigerant pressure Pc. For example, not only can the physical quantity having a correlation with the pressure in the closed container of the adsorber being the desorption process, the pressure in the closed container of the adsorber being the desorption process be adopted, You may employ | adopt internal temperature, surface temperature, external temperature, etc.

  In the second and fifth embodiments described above, the evaporative refrigerant pressure Pe detected by the evaporator pressure sensor 55 is used to determine whether or not the operating condition is such that the adsorption rate is slower than the desorption rate. However, the detection value that can be used for this determination is not limited to the evaporative refrigerant pressure Pe. For example, not only can a physical quantity correlated with the pressure in the closed container of the adsorber serving as the adsorption process and the pressure in the closed container of the adsorber used as the adsorption process, Internal temperature or surface temperature may be adopted.

  (4) In the above-described embodiment, the first to third adsorption cores 24 a to 24 c of the first to third adsorbers 21 a to 21 c are connected in parallel to each other in the adsorbent coolant circuit 30 and the engine coolant circuit 40. Although the example which connected is demonstrated, the connection of the 1st-3rd adsorption | suction core 24a-24c of the 1st-3rd adsorption device 21a-21c is not limited to this. For example, for the adsorber that is the same process (adsorption process or desorption process), the adsorption cores of the adsorber that are the same process may be connected in series.

  (5) In the above-described embodiment, an example in which a diesel engine using kerosene as fuel has been described, but the type of the engine 16 is not limited to this. For example, other types of engines using gasoline, natural gas, propane gas, light oil, hydrogen or the like as fuel may be employed. Further, waste heat of the fuel cell system, solar heat, or other natural energy may be used as a heat source for heating the adsorbent S of the adsorber that is in the desorption process.

  (6) In the above-described embodiment, the example in which the adsorption refrigerator 20 of the present invention is applied to the stationary air conditioner 1 has been described. However, the adsorption refrigerator 20 is applied to a system such as a vehicle air conditioner or a hot water supply device. May be.

DESCRIPTION OF SYMBOLS 11 Compressor 14 Indoor heat exchanger 16 Engine 21a-21b 1st-3rd adsorber 31 Adsorbent cooling water pump 32a-32c Upstream side opening / closing valve 33a-33c Downstream side opening / closing valve 41 Engine cooling water pump 42a-42c Upstream side Open / close valve 43a to 43c Downstream open / close valve 61a to 61h First to eighth electric four-way valves

Claims (12)

A plurality of adsorbers (21a to 21c) in which an adsorbent (S) that adsorbs the refrigerant and desorbs the adsorbed refrigerant by being heated is enclosed;
Among the plurality of adsorbers (21a to 21c), an adsorber serving as an adsorption process for adsorbing the refrigerant to the adsorbent (S) and a desorption process for desorbing the adsorbed refrigerant from the adsorbent (S). Operation mode switching means (32a-32c, 33a-33c, 42a-42c, 43a-43c) for switching a plurality of operation modes by switching the adsorber to be
Even when the operation mode switching means (32a... 43c) is switched to any of the operation modes, at least one of the plurality of adsorbers (21a to 21c) is set as the adsorption step, thereby continuously. An adsorption refrigerator that exhibits refrigeration capacity,
Three or more of the plurality of adsorbers (21a to 21c) are provided,
The three or more adsorbers (21a to 21c) include a cooling heat medium circuit (30) for cooling the adsorbent (S) so as to perform the adsorption step and the desorption step independently, and the Are provided in parallel to the heating medium (40) for heating the adsorbent (S),
Even when the operation mode switching means (32a... 43c) is switched to any operation mode, the number of the adsorbers serving as the adsorption process and the number of adsorbers serving as the desorption processes are different.
Furthermore, when the operation mode switching means (32a ... 43c) switches the operation mode, an adsorber is provided that maintains the adsorption step or the desorption step,
In any one of the three or more adsorbers (21a to 21c), the time for the adsorption step is different from the time for the desorption step,
Of the three or more adsorbers (21a to 21c), the remaining adsorbers also have the same time for the adsorption step and the time for the desorption step as the one adsorber. adsorption type refrigerating machine, characterized by being. The plurality of adsorbers (21a to 21c) includes three or more including the first to third adsorbers (21c),
As the plurality of operation modes,
The first adsorber (21a) is the adsorption step, the second adsorber (21b) is the desorption step, and the third adsorber (21c) is the adsorption step and the desorption step. A first operation mode as one of the processes,
After the first operation mode, the first adsorber (21a) is set as the desorption step, the second adsorber (21b) is set as the adsorption step, and the third adsorber (21c) is set. The adsorption refrigeration machine according to claim 1, further comprising a second operation mode that is the same one step as the first operation mode.   In the operation mode switching means (32a ... 43c), the pressure (Pc) of the desorbed refrigerant desorbed by the adsorber that is the desorption step becomes equal to or higher than a predetermined first reference pressure (XPc). The adsorption refrigeration machine according to claim 2, wherein the third adsorber (21c) is used as the desorption step during the first operation mode.   In the operation mode switching means (32a ... 43c), the pressure (Pc) of the desorbed refrigerant desorbed by the adsorber that serves as the desorption step is lower than a predetermined first reference pressure (XPc). The adsorption type refrigerator according to claim 2 or 3, wherein the third adsorber (21c) is set as the adsorption step during the first operation mode.   The operation mode switching means (32a ... 43c) is configured such that when the pressure (Pe) of the adsorbed refrigerant adsorbed by the adsorber serving as the adsorption step is equal to or higher than a predetermined second reference pressure (XPe). The adsorption type refrigerator according to claim 2, wherein the third adsorber (21c) is used as the desorption step in the first operation mode.   The operation mode switching means (32a ... 43c) is configured such that when the pressure (Pe) of the adsorbed refrigerant adsorbed by the adsorber serving as the adsorption step is lower than a predetermined second reference pressure (XPe), The adsorption type refrigerator according to claim 2 or 3, wherein the third adsorber (21c) is used as the adsorption step in the first operation mode. A plurality of adsorbers (21a, 21b) in which an adsorbent (S) that adsorbs the refrigerant and desorbs the adsorbed refrigerant by being heated is enclosed;
Of the plurality of adsorbers (21a, 21b), an adsorber serving as an adsorption process for adsorbing the refrigerant on the adsorbent (S) and a desorption process for desorbing the adsorbed refrigerant from the adsorbent (S). An operation mode switching means (61g, 61h) for switching a plurality of operation modes by switching the adsorber to be
Even when the operation mode switching means (61g, 61h) switches to any of the operation modes, at least one of the plurality of adsorbers (21a, 21b) is set as the adsorption step, thereby continuously. An adsorption refrigerator that exhibits refrigeration capacity,
A cooling heat medium supplying means (31) for supplying a cooling heat medium for cooling the adsorbent (S) to the adsorber serving as the adsorption step;
A heating heat medium supplying means (41) for supplying a heating heat medium for heating the adsorbent (S) to the adsorber to be the desorption step;
One of the cooling heat medium supply means (31) and the heating heat medium supply means (41) is the amount of adsorbed refrigerant adsorbed by the adsorber that is the adsorption step at a predetermined time. And an adsorption refrigerator that operates so that the amount of the desorbed refrigerant desorbed by the adsorber that is the desorption step during the predetermined time is equal.   When the pressure (Pc) of the desorbed refrigerant is equal to or higher than a predetermined first reference pressure (XPc), the relative humidity of the desorbed refrigerant is lower than the relative humidity of the adsorbed refrigerant, The adsorptive refrigerator according to claim 7, wherein the heating medium supply capacity of the heating medium supply means (41) is increased.   When the pressure (Pe) of the adsorbed refrigerant is equal to or lower than a predetermined second reference pressure (XPe), the relative humidity of the adsorbed refrigerant is higher than the relative humidity of the desorbed refrigerant. The adsorption refrigeration machine according to claim 7, wherein the cooling heat medium supply capacity of the cooling heat medium supply means (31) is increased.   The adsorption type refrigerator according to any one of claims 1 to 9, wherein the adsorbent (S) is made of aluminum oxide, phosphoric acid, and silica gel.   The adsorption type refrigerator according to any one of claims 1 to 9, wherein the adsorbent (S) is made of aluminum oxide, phosphoric acid, and iron oxide. An adsorption refrigerator (20) according to any one of claims 1 to 11,
A compressor (11) driven by an internal combustion engine (16) and a vapor compression refrigeration cycle device (10) having an evaporator (14) for evaporating refrigerant for the refrigeration cycle and cooling indoor blown air,
In the adsorber serving as the desorption step, the adsorbent (S) is heated using the cooling water of the internal combustion engine (16) as a heat source,
The refrigeration apparatus, wherein the refrigerant for the refrigeration cycle discharged from the compressor (11) is cooled by the refrigeration capacity exhibited by the adsorber serving as the adsorption step.

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