JP2012159235A - Heat pump system and desiccant air conditioning system using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To stably operate a main heat pump even if a refrigerant load, a hot load or the like is in an imbalanced state, and to sufficiently exhibit performance.SOLUTION: This heat pump system s1 comprises: a heat source system 20 which has heat sources 21, 22 for collecting heat from the surroundings, and in which a first heat medium m2 which receives the heat collected by the heat sources 21, 22 circulates; a heat supply system 30 which has a heat supply body 31 being an object to be supplied with the heat collected by the heat sources 21, 22, and in which a second heat medium m3 which supplies heat to the heat supply body 31 circulates; and a main heat pump 40 into which the first heat medium m2 and the second heat medium m3 are introduced, and which transfers the heat collected by the heat sources 21, 22 to the second heat medium m3 from the first heat medium m2. The heat source system 20 comprises a heater 23 for heating the first heat medium m2 which is introduced into the main heat pump 40.

Description

  The present invention relates to a heat pump system and a desiccant air conditioning system using the same.

In recent years, there is a heat pump system using a hot water heat pump that recovers heat from outside air used for air conditioning and uses the recovered heat for hot water supply equipment. Specifically, heat source water is circulated between a cold water coil installed in the air conditioning equipment and a hot water heat pump, and hot water is circulated between the hot water coil installed in the hot water tank and the hot water heat pump. Then, the heat of the outside air is recovered to the heat source water via the cold water coil, the heat recovered from the outside air is transferred from the heat source water to the hot water via the hot water heat pump, and the heat of the hot water is transferred to the hot water tank via the hot water coil. Hot water is obtained by supplying to the water.
The following techniques are similar to the above heat pump.

JP 2010-276325 A JP 2010-276317 A

  However, in the conventional technology, when the cooling load and the heating load are unbalanced (when the amount of heat received from the cooling water coil by the heat source water is too small compared to the amount of heat supplied to the heating water coil), the performance of the heat pump is reduced. There is a problem that the heat cannot be sufficiently exhibited and heat cannot be stably supplied to the hot water coil or the like.

  The present invention has been made in consideration of such circumstances, and even when the cooling load and the heating load are unbalanced, it is an object to stably operate the heat pump and to sufficiently exhibit the performance. And

In order to achieve the above object, the present invention employs the following means.
That is, the heat pump system according to the present invention has a heat source body that recovers heat from the surroundings, a heat source system in which a first heat medium that receives the heat recovered by the heat source body circulates, and the heat recovered by the heat source body A heat supply system having a heat supply body to be supplied, in which a second heat medium for supplying heat to the heat supply body circulates, the first heat medium and the second heat medium are introduced, and the heat source A main heat pump that moves the heat recovered by the body from the first heat medium to the second heat medium, wherein the heat source system is introduced into the main heat pump. It has the heating apparatus which heats.
In this way, even if the cooling load and the heating load are unbalanced, and the amount of heat received by the first heat medium from the heat source body is too small relative to the amount of heat supplied to the heat supply body, heating is performed. The heat of the first heat medium can be increased in the apparatus. Thereby, the temperature difference between the first heat medium and the second heat medium can be made a temperature difference suitable for the operation of the main heat pump, so that the main heat pump can be operated stably and the performance is sufficiently It can be demonstrated.

Further, the heating device is a refrigerator that circulates the third heat medium between the heat source body and the first heat medium between the main heat pump and the refrigerator. The heat recovered by the heat source body is transferred to the first heat medium via the three heat mediums, and exhaust heat is added to the first heat medium for heating.
In this way, since the heating device is a refrigerator, the cooling medium of the refrigerator can be used as the first heat medium of the main heat pump.

The heat source system may include a cooling device that cools the first heat medium that flows from the main heat pump toward the refrigerator.
In this way, since the cooling device is provided, when the amount of heat of the exhaust heat of the refrigerator exceeds the amount of heat that can cool the first heat medium, it is possible to remove excess exhaust heat.

The heat source system circulates the first heat medium between the heat source body and the main heat pump, and the heating device heats the first heat medium introduced into the heat source body. It is a heat pump.
In this case, since the sub heat pump is provided, the temperature difference between the first heat medium and the second heat medium can be adjusted relatively finely.

In addition, the heat source system includes a high-temperature channel through which the first heat medium flows from the heat source body toward the main heat pump, and a low-temperature channel through which the first heat medium flows from the main heat pump toward the heat source body. Connected to the low-temperature flow path, branched from the low-temperature flow path to branch the first heat medium and introduced into the sub-heat pump, and connected to the high-temperature flow path and heated by the sub-heat pump. And a branched high-temperature channel that joins the first heat medium to the first heat medium flowing through the upstream channel.
In this way, since the first heat medium heated by the sub heat pump can be directly joined to the first heat medium flowing into the main heat pump, the temperature control of the first heat medium is relatively easy. Become. In addition, the present invention can be easily applied to existing facilities.

In addition, an air supply passage for supplying outside air flowing from the outside to the air conditioning target, an exhaust passage for exhausting the return air flowing from the air conditioning target to the outside, and moisture adsorbed from the outside air passing through the air supply passage And a desiccant part for desorbing the adsorbed moisture to the return air passing through the exhaust flow path, and a desiccant part provided between the desiccant part and the outside of the supply air flow path for cooling the outside air. A first heating unit that is provided between the cooling unit and the desiccant unit of the exhaust flow path and the air-conditioning target, and that heats the return air to a regeneration temperature at which the desiccant unit desorbs the moisture; A desiccant air conditioning system comprising the heat pump system according to any one of the above, wherein the heat source body includes the first cooling unit, and the heat supply unit includes the first heating unit. And features.
In this way, since the heat pump system is provided, the main heat pump operates stably even when the temperature difference between the first heat medium and the second heat medium is relatively large. Thereby, air can be stably supplied to the air-conditioning target. Moreover, since heat can be sufficiently supplied to the first heating coil, the adsorbed moisture in the desiccant portion can be reliably desorbed. Therefore, the desiccant air conditioning system can be operated stably.

In addition, an air supply passage for supplying outside air flowing from the outside to the air conditioning target, an exhaust passage for exhausting the return air flowing from the air conditioning target to the outside, and moisture adsorbed from the outside air passing through the air supply passage And a desiccant part for desorbing the adsorbed moisture to the return air passing through the exhaust flow path, and a desiccant part provided between the desiccant part and the outside of the supply air flow path for cooling the outside air. A first heating unit that is provided between the cooling unit and the desiccant unit of the exhaust flow path and the air-conditioning target, and that heats the return air to a regeneration temperature at which the desiccant unit desorbs the moisture; A desiccant air-conditioning system provided between the desiccant part and the air-conditioning target in the air supply channel, and comprising a second heating part for heating the outside air, and the heat pump system, The source body includes the first cooling unit, the heat supply unit includes the first heating unit, and the sub heat pump can be connected to the first cooling unit, independently of the main heat pump. The first heat medium is circulated, and the outside air is cooled together with the main heat pump through the first cooling unit.
If it does in this way, air-conditioning can be performed corresponding to the environment where a cooling load exceeds a heating load for reproducing a desiccant part.

In addition, an air supply passage for supplying outside air flowing from the outside to the air conditioning target, an exhaust passage for exhausting the return air flowing from the air conditioning target to the outside, and moisture adsorbed from the outside air passing through the air supply passage And a desiccant part for desorbing the adsorbed moisture to the return air passing through the exhaust flow path, and a desiccant part provided between the desiccant part and the outside of the supply air flow path for cooling the outside air. A first heating unit that is provided between the cooling unit and the desiccant unit of the exhaust flow path and the air-conditioning target, and that heats the return air to a regeneration temperature at which the desiccant unit desorbs the moisture; A desiccant air-conditioning system provided between the desiccant part and the air-conditioning target in the air supply channel, and comprising a second heating part for heating the outside air, and the heat pump system, The source body includes the first cooling unit, the heat supply unit includes the first heating unit, and the sub heat pump circulates the first heat medium with the second heating unit. The heated first heat medium is supplied to the second heating unit on the condition that the second heating unit can be switched and connected, and the main heat pump is stopped.
If it does in this way, while the thermal load for reproducing | regenerating a cold load and a desiccant part will be 0, air conditioning can be performed corresponding to the environment where the thermal load for heating arises.

  According to the heat pump system of the present invention, the main heat pump can be stably operated and the performance can be sufficiently exhibited.

  In addition, according to the desiccant air conditioning system according to the present invention, stable operation is possible.

It is a schematic structure figure of desiccant air-conditioning system S1 concerning a first embodiment of the present invention. It is operation | movement explanatory drawing of the desiccant air conditioning system S1 which concerns on 1st embodiment of this invention. It is a schematic block diagram of desiccant air-conditioning system S2 which concerns on 2nd embodiment of this invention. It is operation | movement explanatory drawing of desiccant air-conditioning system S2 which concerns on 2nd embodiment of this invention, Comprising: The connection structure of the intermediate period between the summer and winter is shown. It is operation | movement explanatory drawing of desiccant air conditioning system S2 which concerns on 2nd embodiment of this invention, Comprising: The connection structure of the summer is shown. It is operation | movement explanatory drawing of desiccant air conditioning system S2 which concerns on 2nd embodiment of this invention, Comprising: The connection structure of the winter season is shown. It is an annual transition graph of the thermal load amount of the desiccant air conditioning system S2 which concerns on 2nd embodiment of this invention. It is a schematic block diagram of modification S2A of desiccant air-conditioning system S2 which concerns on 2nd embodiment of this invention. It is a schematic block diagram of waste heat utilization system S3 which concerns on 3rd embodiment of this invention.

Embodiments of the present invention will be described below with reference to the drawings.
[First embodiment]
FIG. 1 is a schematic configuration diagram of a desiccant air conditioning system S1 according to the first embodiment of the present invention. The desiccant air-conditioning system S1 supplies ultra-dry air (for example, a dew point temperature of about −45 ° C.) to a production line (air-conditioning target) such as a semiconductor or food, and as shown in FIG. The exhaust flow path 2, the desiccant (desiccant part) 3, and the heat pump system H1 are provided.

  The air supply channel 1 supplies outside air A1 flowing from the outside to the air conditioning target, and the first blower fan 4 takes in the outside air A1 from the external side opening 1a and supplies the air supply A3 from the air conditioning target side opening 1b. To supply.

  The exhaust passage 2 exhausts the return air A4 flowing from the air conditioning target to the outside, and the second blower fan 5 takes in the return air A4 from the air conditioning target side opening 2b and opens the return air A4 to the outside opening. The air is exhausted from 2a. The exhaust passage 2 is arranged in parallel with the air supply passage 1.

The desiccant 3 is a rotary type, and is a disk-shaped rotor member (not shown) made of a bundle of honeycomb-shaped passages, and a silica gel-based adsorbent or polymer sorbed on the surface of the honeycomb-shaped passages of the rotor member. It is composed of materials. The desiccant 3 is disposed across the air supply passage 1 and the exhaust passage 2 so that the return air A4 or the outside air A1 passes through the honeycomb passage, and by rotating the rotor member, The honeycomb passage is exchanged between the air supply passage 1 and the exhaust passage 2.
The desiccant 3 adsorbs moisture contained in the outside air A1 that passes through the honeycomb-shaped passage in the air supply passage 1 to the surface of the passage to obtain dehumidified air A2 of ultra-dry air (for example, a dew point temperature of about −45 ° C.). Then, when the rotor member rotates, the honeycomb-shaped passage that has adsorbed moisture is positioned in the exhaust flow path 2, and the moisture adsorbed by the return air A4 that passes through the honeycomb-shaped passage is desorbed.

  The heat pump system H1 includes a heat source system 20, a heat supply system 30, and a hot water heat pump (main heat pump) 40.

  The heat source system 20 includes a first cold water coil (heat source body, first cooling unit) 21, a second cold water coil (heat source body) 22, a turbo refrigerator (refrigerator) 23, and a hermetic cooling tower (cooling device). 24, chilled water circuits 26 and 27, and a heat source water circuit 28.

  The first cold water coil 21 recovers heat from the periphery of the first cold water coil 21. The first cold water coil 21 is disposed between the desiccant 3 and the external opening 1a in the air supply passage 1, and precools the outside air A1 flowing into the desiccant 3 from the outside.

  The chilled water circuit 26 connects the first chilled water coil 21 and the turbo chiller 23, and circulates chilled water (third heat medium) m <b> 1 between the first chilled water coil 21 and the turbo chiller 23. The cold water m1 of the cold water circuit 26 receives the heat collected by the first cold water coil 21 from the ambient air A1.

  The second cold water coil 22 recovers heat from the periphery of the second cold water coil 22. The second cold water coil 22 is disposed between the desiccant 3 and the air-conditioning target side opening 1b in the air supply channel 1, and cools the dehumidified air A2 that has passed through the desiccant 3.

The chilled water circuit 27 connects the second chilled water coil 22 and the turbo chiller 23, and circulates the chilled water m <b> 1 between the second chilled water coil 22 and the turbo chiller 23. The chilled water circuit 27 branches the chilled water m1 of the chilled water circuit 26 heading from the turbo chiller 23 toward the first chilled water coil 21 and introduces it into the second chilled water coil 22, and the chilled water m1 discharged from the second chilled water coil 22 Then, the chilled water m1 of the chilled water circuit 26 heading from the first chilled water coil 21 to the turbo refrigerator 23 is merged. That is, the cold water circuit 27 and the cold water circuit 26 partially overlap each other.
The cold water m1 of the cold water circuit 27 receives heat recovered by the second cold water coil 22 from the surrounding dehumidified air A2.
In the overlapping range of the chilled water circuit 27 and the chilled water circuit 26, a pump 26 a that pumps the chilled water m <b> 1 is disposed in a pipe where the chilled water m <b> 1 is directed to the turbo refrigerator 23.

  The turbo refrigerator 23 is connected to the first cold water coil 21 and the second cold water coil 22, and is connected to the hot water heat pump 40 via a heat source water circuit 28. The turbo chiller 23 uses the heat consumed by the compressor of the turbo chiller 23 (exhaust heat) to the heat collected by the first cold water coil 21 from the outside air A1 and the heat collected by the second cold water coil 22 from the dehumidified air A2. And is transferred to the heat source water (first heat medium, cooling water as viewed from the turbo refrigerator 23) m2 of the heat source water circuit 28.

The heat source water circuit 28 connects the turbo chiller 23 and the hot water heat pump 40, and circulates the heat source water m2 between the turbo chiller 23 and the hot water heat pump 40. The heat source water m2 of the heat source water circuit 28 is converted into the cold water m1 through the turbo chiller 23 by the heat collected by the first cold water coil 21 from the outside air A1 and the heat collected by the second cold water coil 22 from the outside air A1. Receive from. In addition, the heat source water m <b> 2 receives the power consumption of the compressor of the turbo refrigerator 23 from the turbo refrigerator 23.
The heat source water circuit 28 is provided with a pump 28c that pumps the heat source water m2.

  The hermetic cooling tower 24 releases heat of the heat source water m2 to the outside air by exchanging heat between the heat source water m2 and the outside air in a non-contact state. The hermetic cooling tower 24 is connected via a bypass channel 29 to a low-temperature pipe 28 b where the heat source water m 2 is directed to the turbo refrigerator 23 in the heat source water circuit 28. That is, the heat source water m2 can be selectively circulated to the hermetic cooling tower 24 by opening and closing the flow rate valve 28d disposed between the inlet and the outlet of the bypass channel 29 in the low temperature pipe 28b. is there.

The heat supply system 30 includes a regeneration hot water coil (heat supply body) 31 and a hot water circuit 32.
The regenerating hot water coil 31 is a supply target of heat collected by the first cold water coil 21 and the second cold water coil 22, and is connected to the hot water heat pump 40 via the hot water circuit 32. The regenerating hot water coil 31 heats the return air A <b> 4 flowing into the desiccant 3 from the air-conditioning target by the heat supplied from the hot water heat pump 40 via the hot water circuit 32.
In the present embodiment, the supply air A3 is ultra-dry air, and it is necessary to increase the difference in relative humidity between the outside air A1 and the return air A4 flowing into the desiccant 3, so that the regeneration in which the desiccant 3 is adsorbed is performed. The temperature is set to a relatively high temperature (for example, 80 ° C.).

The hot water circuit 32 connects the hot water heat pump 40 and the regenerating hot water coil 31, and circulates hot water (second heat medium) m3 between the hot water heat pump 40 and the regenerating hot water coil 31. The hot water m3 of the hot water circuit 32 transfers the heat received from the refrigerant c of the hot water heat pump 40 to the regenerating hot water coil 31.
The hot water circuit 32 is provided with a pump 32a that pumps the hot water m3.

The hot water heat pump 40 includes a compressor 40a that compresses the refrigerant c, a condenser 40b that cools and condenses the compressed refrigerant c, an expansion valve 40c that expands the condensed refrigerant c, and an expanded refrigerant c. And an evaporator 40d for evaporating.
In addition, the condenser 40b and the evaporator 40d are refrigerant-water heat exchangers, and a general plate type heat exchanger, a double tube heat exchanger, or the like can be used.

  In the heat pump system H1 having such a configuration, the heat recovered from the outside air A1 and the outside air A1 is applied to the return air A4 as follows. That is, the heat recovered from the outside air A1 by each of the first cold water coil 21 and the second cold water coil 22 is transferred to the cold water m1, and the heat transferred to the cold water m1 via the turbo refrigerator 23 is transferred to the turbo refrigerator. 23 is transferred to the heat source water m2 together with the power consumption of the compressor 23, and the heat transferred to the heat source water m2 is transferred to the hot water m3 together with the power consumption of the compressor 40a of the hot water heat pump 40 through the hot water heat pump 40. Then, the heat supplied to the regenerating hot water coil 31 by the hot water m3 is given to the return air A4.

Next, the operation of the desiccant air conditioning system S1 and the heat pump system H1 configured as described above will be described with reference to FIG.
In the following explanation, after explaining the operation of desiccant air-conditioning system S1 first, the operation of heat pump system H1 is explained.

First, as shown in FIG. 2, the outside air A <b> 1 that has flowed into the air supply passage 1 from the external opening 1 a is recovered by the first cold water coil 21 to be cooled, and the relative humidity is increased.
Next, when the outside air A1 passes through the desiccant 3, the moisture of the outside air A1 is adsorbed on the surface of the honeycomb-shaped passage, and the absolute humidity is lowered.

Next, when the outside air A1 passes through the second cold water coil 22, the outside air A1 is recovered by the second cold water coil 22 and cooled. At this time, since the latent heat load of the cooling load is removed by the desiccant 3, the dehumidified air A2 can be set to the target temperature only by removing the sensible heat load of the cooling load.
Then, the air supply A3 is supplied to the air conditioning target.

Next, when the return air A4 flowing into the exhaust passage 2 from the air conditioning target through the air conditioning target side opening 2b passes through the regeneration hot water coil 31, the return air A4 is returned to the regeneration warm water coil 31 as shown in FIG. Is heated to the regeneration temperature.
Next, when the return air A4 passes through the desiccant 3, the moisture of the desiccant 3 is desorbed, and the absolute humidity of the return air A4 increases.
And this return air A4 is exhausted outside.

Next, the operation of the heat pump system H1 will be described.
First, when the first cold water coil 21 and the second cold water coil 22 recover heat from the outside air A1, the recovered heat is transferred to the cold water m1 circulating in the cold water circuits 26 and 27.
The cold water m <b> 1 receives heat from the first cold water coil 21 and the second cold water coil 22 and passes the received heat to the turbo refrigerator 23. The cold water m1 has a temperature t ₁₁ (for example, 12 ° C.) at the inlet of the turbo refrigerator 23 and a temperature t ₁₂ (for example, 7 ° C.) at the outlet of the turbo refrigerator 23.

  The turbo chiller 23 receives heat from the cold water m1, and uses the received heat (heat collected by the first cold water coil 21 and the second cold water coil 22 from the outside air A1) to consume power of the compressor of the turbo chiller 23. In addition, it passes to the heat source water m2.

The heat source water m <b> 2 circulating through the heat source water circuit 28 delivers the heat received from the turbo refrigerator 23 to the hot water heat pump 40. The heat source water m2 has a temperature t ₂₁ (for example, 35 ° C.) at the inlet of the turbo refrigerator 23 and a temperature t ₂₂ (for example, 40 ° C.) at the outlet of the turbo refrigerator 23.

The hot water heat pump 40 adds the power consumed by the compressor 40a of the hot water heat pump 40 to the heat received from the heat source water m2, and transfers it to the hot water m3. The hot water m3 has a temperature t ₃₁ (for example, 75 ° C.) at the inlet of the hot water heat pump 40 and a temperature t ₃₂ (for example, 85 ° C.) at the outlet of the hot water heat pump 40.

  The heat source water m <b> 2 circulating through the hot water circuit 32 supplies the heat received from the hot water heat pump 40 to the hot water coil 31 for regeneration. The regeneration hot water coil 31 heats the supplied heat to the return air A4 to raise the temperature of the return air A4 to the regeneration temperature (for example, 80 ° C.).

Here, while omitting the turbo refrigerator 23 and considering a virtual example in which the first cold water coil 21 and the second cold water coil 22 and the hot water heat pump 40 are directly connected to circulate the heat source water m2, heat source water is considered. The temperature of m2 is a temperature t ₁₁ (for example, 12 ° C.) at the inlet of the hot water heat pump 40 and a temperature t ₁₂ (for example, 7 ° C.) at the outlet of the hot water heat pump 40 corresponding to the cooling load of the outside air A1 and the dehumidified air A2. There is a need.
On the other hand, the temperature of the hot water m3 corresponds to the temperature load of the return air A4 at the regeneration temperature (for example, 80 ° C.), the temperature t ₃₁ (for example, 75 ° C.) at the inlet of the hot water heat pump 40, and the temperature t at the outlet of the hot water heat pump 40. ₃₂ (for example, 85 ° C.).

  Thus, when the cold load and the thermal load are unbalanced, the first cold water coil 21 and the second cold water coil 22 and the hot water heat pump 40 are directly connected to each other. The temperature difference from the hot water m3 becomes excessive and the heat balance becomes unbalanced. In other words, the amount of heat pumped up from the heat source water m2 by the hot water heat pump 40 is insufficient with respect to the amount of heat that the hot water heat pump 40 supplies to the hot water m3, and the two cannot be balanced. For this reason, the cycle in the hot water heat pump 40 collapses and the hot water heat pump 40 cannot be operated, or even if it can be operated, the return air A4 cannot be brought to the regeneration temperature, and the performance of the desiccant air conditioning system S1 is improved. It will be seriously damaged.

On the other hand, desiccant air-conditioning system S1 connects the 1st cold water coil 21 and the 2nd cold water coil 22, and the hot water heat pump 40 via the turbo refrigerator 23, and heats the heat source water m2 with the turbo refrigerator 23. .
That is, cold water m1 is circulated in the first cold water coil 21 and the second cold water coil 22 instead of the heat source water m2 (temperature t ₁₁ (for example, 12 ° C.) at the inlet of the turbo refrigerator 23), and the outlet of the turbo refrigerator 23 At temperature t ₁₂ (for example, 7 ° C.)). Then, the turbo chiller 23 converts the heat received from the cold water m1 (the heat collected by the first cold water coil 21 from the outside air A1 and the heat collected by the second cold water coil 22 from the dehumidified air A2) into the compressor of the hot water heat pump 40. The consumption power of 40a is added and supplied to the heat source water m2. Therefore, the temperature of the heat source water m2 becomes a temperature t ₂₂ (t ₂₂ > t ₁₁ , for example, 40 ° C.) at the inlet of the hot water heat pump 40.

Thus, even when the cold load and the thermal load are unbalanced, the temperature difference between the heat source water m2 and the hot water m3 flowing into the hot water heat pump 40 becomes appropriate, and the hot water heat pump 40 is stabilized. Operate.
And while satisfy | filling the cooling load (cooling load of the external air A1 and dehumidified air A2) with the cold water m1, it becomes possible to satisfy the heating load (heating load of the regeneration temperature of the return air A4) with the heat source water m2. Accordingly, the desiccant 3 is regenerated with the return air A4 reliably set to the regeneration temperature, and the supply air A3 is stably supplied to the air-conditioning target.

  On the other hand, when the amount of heat of exhaust heat (compressor power consumption) of the turbo chiller 23 exceeds the amount of heat that can be cooled by the heat source water m2, surplus is obtained by circulating the heat source water m2 through the sealed cooling tower 24. Exhaust heat of the minute to the outside air.

  As described above, according to the heat pump system H1, the cooling load and the heating load are unbalanced, and the amount of heat received by the heat source water m2 from the first cooling water coil 21 and the second cooling water coil 22 is the regenerating warm water coil 31. Even when the amount of heat supplied to the heat source is too small, the heat of the heat source water m2 can be increased by the turbo refrigerator 23. Thereby, since the temperature difference between the heat source water m2 and the hot water m3 can be a temperature difference suitable for the operation of the hot water heat pump 40, the hot water heat pump 40 can be operated stably.

  Further, according to the desiccant air conditioning system S1, since the heat pump system H1 is provided, when the supply air A3 is ultra-dry air and the regeneration temperature is set relatively high, in other words, the first cold water coil 21 and the first Even when the temperature difference between the two cold water coils 22 and the regenerating hot water coil 31 is relatively large, the hot water heat pump 40 operates stably. Thereby, the external air A1 and the dehumidified air A2 can be sufficiently cooled, and the supply air A3 of the ultra-dry air can be stably supplied to the air-conditioning target. Moreover, since sufficient heat can be supplied to the regenerating hot water coil 31, the adsorbed moisture of the desiccant 3 can be reliably desorbed. Therefore, the desiccant air conditioning system S1 can be operated stably.

Moreover, since it heats using the turbo refrigerator 23, the cooling water of the turbo refrigerator 23 can be utilized as the heat source water m2 of the hot water heat pump 40.
Further, since the sealed cooling tower 24 is provided, when the amount of heat of the exhaust heat of the turbo chiller 23 exceeds the amount of heat that can cool the heat source water m2, it is possible to remove excess exhaust heat.

  In this embodiment, the dehumidified air A2 having a dew point temperature of about −45 ° C. is exemplified as the ultra-dry air. However, the present invention is not limited to this, and the present invention is used when supplying dry air having other dew point temperatures. May be applied. In particular, the present invention can be favorably applied to a desiccant air conditioning system that supplies dry air having a dew point temperature in the range of −45 ° C. to 5 ° C.

[Second Embodiment]
Next, a second embodiment of the present invention will be described.
FIG. 3 is a schematic configuration diagram of a desiccant air conditioning system S2 according to the second embodiment of the present invention. In the following description and the drawings used in the following description, the same components as those in the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  As shown in FIG. 3, the desiccant air conditioning system S2 includes an air supply passage 1, an exhaust passage 2, and a desiccant 3 as in the first embodiment, but instead of the heat pump system H1, a heat pump system H2 is provided. It differs from the first embodiment in that it is provided.

  The heat pump system H2 includes a heat source system 60, a heat supply system 70, and a hot water heat pump 40.

The heat source system 60 includes a first cold water coil 21, a heat source water circuit 28, and an air-cooled heat pump (sub heat pump) 61.
The heat source water circuit 28 connects the first cold water coil 21 and the hot water heat pump 40, and specifically, a high temperature pipe 28 a and a low temperature pipe 28 b that connect the first cold water coil 21 and the hot water heat pump 40, respectively. have. The heat source water circuit 28 connects the first cold water coil 21 and the hot water heat pump 40, and circulates the heat source water m2 between the first cold water coil 21 and the hot water heat pump 40.

The air-cooled heat pump 61 can exchange heat with the outside air to heat and cool the heat source water m2, and can be switched and connected to the first cold water coil 21, the hot water heat pump 40, and the heat supply system 70. (Described later).
The air-cooling heat pump 61 is connected to the first cold water coil 21 via an introduction pipe 63a and a lead-out pipe 63b. The air cooling heat pump 61 cools the heat source water m <b> 2 that circulates with the first cold water coil 21.

  The heat supply system 70 includes a warm water coil 31 for regeneration, a warm water coil (second heating unit) 71 for heating, a warm water header 72, and a warm water return header 73.

  As shown in FIG. 3, the regenerating hot water coil 31 receives heat from the hot water m3 flowing in from the regenerating high temperature pipe 31a and sends the hot water m3 to the regenerating low temperature pipe 31b.

  The heating hot water coil 71 is disposed between the desiccant 3 and the air-conditioning target in the air supply channel 1, receives heat from the hot water m3 flowing in from the heating high-temperature pipe 71a, and uses the hot water m3 for heating. It sends out to the low temperature pipe 71b.

One of the plurality of inlets of the hot water forward header 72 is provided with a regenerated hot water forward path 74 a that connects the hot water outlet of the hot water heat pump 40.
The other of the plurality of inlets of the hot water header 72 is connected to a heating / hot water path 75a connected to the outlet pipe 63b via a three-way valve s1.
A pipe 76 a is connected to the outlet of the warm water header 72.
The pipe 76a is connected to a regeneration high-temperature pipe 31a and a heating high-temperature pipe 71a via a three-way valve s3.

A pipe 76 b is connected to the inlet of the warm water return header 73.
The pipe 76b is connected to a regeneration cryogenic pipe 31b and a heating cryogenic pipe 71b.
One of the plurality of outlets of the hot water return header 73 is provided with a regenerated hot water return path 74 b that connects the hot water inlet of the hot water heat pump 40.
The other of the plurality of outlets of the hot water return header 73 is connected to a heating hot water return path 75b connected to the introduction pipe 63a.

A branch pipe 62b is disposed between the heating / warm water path 75a and the high-temperature pipe 28a. The branch pipe 62b is connected to the heating / warming water outward path 75a via a three-way valve s6.
A branch pipe 62a is disposed between the heating hot water return path 75b and the low temperature pipe 28b. The branch pipe 62a is connected to the low temperature pipe 28b via a three-way valve s2.

That is, the heat pump system H2 controls the three-way valve s2 to connect the low temperature pipe 28b, the introduction pipe 63a, and the branch pipe 62a through the heating / warm water return path 75b, thereby forming the branch low temperature flow path 67a. Is possible. The branch low-temperature channel 67a diverts the heat source water m2 from the low-temperature pipe 28b and introduces it into the air-cooled heat pump 61.
Similarly, by controlling the three-way valves s1 and s6, the high-temperature pipe 28a, the outlet pipe 63b, and the branch pipe 62b can be communicated with each other via the heating / warm water forward path 75a to configure the branch high-temperature path 67b. . The branch high-temperature channel 67b joins the heat source water m2 heated by the air-cooling heat pump 61 to the heat source water m2 flowing through the high-temperature pipe 28a.

Next, the operation of the desiccant air conditioning system S2 and the heat pump system H2 configured as described above will be described with reference to FIGS.
FIG. 7 is an annual transition graph of the heat load of the desiccant air conditioning system S2.
As shown in FIG. 7, in the intermediate period between summer and winter, the cooling load for cooling the outside air A1 and the dehumidified air A2 is lower than the heating load for setting the return air A4 to the regeneration temperature (however, The thermal load for reheating / heating the dehumidified air A2 is 0). That is, the cold load and the warm load are unbalanced.
Therefore, in order to supply heat to the heat source water m2 flowing into the hot water heat pump 40, the following configuration is adopted.

That is, in the intermediate period between summer and winter, as shown in FIG. 4, by controlling the three-way valve s2 and the three-way valves s1 and s6 in the heat source system 60, the branch low-temperature channel 67a and the branch high-temperature channel 67b Respectively. That is, the heat source water m2 is circulated between the first cold water coil 21 and the hot water heat pump 40, and the heat source water m2 is circulated between the hot water heat pump 40 and the air cooling heat pump 61.
On the other hand, as shown in FIG. 4, in the heat supply system 70, the regenerated hot water return path 74b, the hot water return header 73, the pipe 76b, and the regenerating low temperature pipe 31b are communicated, and the regenerated hot water forward path 74a and the hot water forward header 72 The conduit 76a, the three-way valve s3, and the regeneration high-temperature conduit 31a are connected. That is, the hot water m3 is circulated between the hot water heat pump 40 and the regenerating hot water coil 31.

In the heat source system 60, a part of the heat source water m2 is branched from the low temperature line 28b and heated by the air cooling heat pump 61, and the heated heat source water m2 merges with the heat source water m2 of the high temperature line 28a.
More specifically, heat source water m2 having a temperature t ₁₁ (eg, 10 ° C.) at the inlet of the first cold water coil 21 and a temperature t ₁₂ (eg, 12 ° C.) at the outlet is heated by the air-cooled heat pump 61. , The temperature t ₂₁ (> t ₁₂ , for example, 15 ° C.) at the inlet of the hot water heat pump 40 and the temperature t ₂₂ (> t ₁₁ , for example, 10 ° C.) at the outlet of the hot water heat pump 40.

And the warm water heat pump 40 adds the power consumed by the compressor 40a of the warm water heat pump 40 to the heat received from the heat source water m2, and delivers it to the warm water m3. The hot water m3 has a temperature t ₃₁ (eg, 55 ° C.) at the inlet of the hot water heat pump 40 and a temperature t ₃₂ (eg, 65 ° C.) at the outlet of the hot water heat pump 40.

  The hot water m3 circulating through the hot water circuit 32 supplies the heat received from the hot water heat pump 40 to the hot water coil 31 for regeneration. The regenerating hot water coil 31 heats the supplied heat to the return air A4 to raise the temperature of the return air A4 to the regeneration temperature (for example, 60 ° C.).

  Thus, even when the cold load and the thermal load are unbalanced, the temperature difference between the heat source water m2 and the hot water m3 flowing into the hot water heat pump 40 becomes appropriate, and the hot water heat pump 40 is stabilized. Operate.

On the other hand, in the summer, as shown in FIG. 7, the cooling load for cooling the outside air A1 and the dehumidified air A2 exceeds the heating load for setting the return air A4 to the regeneration temperature (however, the recirculation of the dehumidified air A2). The thermal load for heat and heating is 0).
In this case, as shown in FIG. 5, in the heat source system 60, in addition to circulating the heat source water m <b> 2 between the first cold water coil 21 and the hot water heat pump 40, the first cold water coil 21 and the air cooling heat pump 61. The heat source water m2 is also circulated between the two and the air source heat m61 is cooled by the air cooling heat pump 61.
Specifically, by controlling the three-way valve s1, the communication between the outlet pipe 63b and the heating / warming water forward path 75a is blocked, and by controlling the three-way valve s2, the communication between the low-temperature pipe 28b and the branch pipe 62a. And the air cooling heat pump 61 is connected to the first cold water coil 21.
In this way, the heat source water m2 cooled by the air cooling heat pump 61 is supplied to the first cold water coil 21 (cold water temperature t _{41 at} the outlet of the air cooling heat pump 61 (for example, 7 ° C.)). That is, the heat source water m2 cooled by the air-cooling heat pump 61 removes the portion of the cooling load exceeding the heating load.

On the other hand, in the winter season, as shown in FIG. 7, the heating load for heating the cooling load and the return air A4 to the regeneration temperature becomes zero, while the heating load for heating is generated.
In this case, as shown in FIG. 6, the operation of the hot water heat pump 40 is stopped, and the hot water m3 is circulated between the air cooling heat pump 61 and the heating hot water coil 71.
Specifically, by controlling the three-way valves s1 and s6, the outlet pipe 63b and the heating / warming water forward path 75a are communicated to connect the warm / water feeding header 72 and the air cooling heat pump 61. Further, by controlling the three-way valve s2, the communication between the low temperature pipe 28b and the branch pipe 62a is blocked.
On the other hand, the pipe 76a, the three-way valve s3, and the heating high-temperature pipe 71a are connected to connect the warm water header 72 and the heating hot water coil 71.
By doing in this way, the hot water m3 heated by the air cooling heat pump 61 is supplied to the heating hot water coil 71 (the hot water temperature t ₄₂ (for example, 40 ° C.) at the outlet of the air cooling heat pump 61). The temperature is increased by applying heat to the temperature t ₅₁ (for example, 40 ° C.), the outlet temperature t ₅₂ (for example, 30 ° C.), and the supply air A3.
In this way, in the winter season, warm air for heating is supplied using the air-cooled heat pump 61 without using the hot water heat pump 40.

As described above, according to the heat pump system H2, the temperature difference between the heat source water m2 and the hot water m3 is suitable for the operation of the hot water heat pump 40 in the intermediate period between summer and winter, as in the first embodiment. Therefore, the hot water heat pump 40 can be operated stably.
If the temperature of the heat source water m2 corresponding to the heat load must be 10 ° C. at the inlet of the first cold water coil 21 (the outlet of the hot water heat pump 40) and 15 ° C. at the outlet (the inlet of the hot water heat pump 40), When the temperature reaches 12 ° C. at the outlet of the first cold water coil 21, the temperature of the heat source water m2 gradually decreases, and the hot water heat pump 40 cannot be operated.
However, according to the heat pump system H2, even when the temperature of the heat source water m2 reaches 12 ° C. at the outlet of the first cold water coil 21, the heated heat source water m2 is joined to Since it can be raised to 15 ° C., the hot water heat pump 40 can be operated stably.

In addition, since the air-cooled heat pump 61 is provided, the temperature difference between the heat source water m2 and the hot water m3 can be adjusted relatively finely.
Further, according to the desiccant air conditioning system S2, it is possible to switch between the system configuration for summer and the system configuration for winter, so that the cooling load that varies throughout the year and the thermal load for desiccant regeneration and heating are changed. Correspondingly, it becomes possible to perform optimum air conditioning.
Further, since the heat source water m2 heated by the air-cooled heat pump 61 can be directly joined to the heat source water m2 flowing into the hot water heat pump 40, the temperature control of the heat source water m2 becomes relatively easy. In addition, the present invention can be easily applied to existing facilities.

FIG. 8 is a schematic configuration diagram of a modified example S2A of the desiccant air conditioning system S2.
In the desiccant air conditioning system S2A, the introduction pipe 63a and the lead-out pipe 63b connect the air-cooling heat pump 61 and the heating / cooling combined coil (heat source body) 79, respectively. That is, in the intermediate period, the desiccant air conditioning system S2A supplies warm water to the heating / cooling combined coil 79 to raise the temperature of the outside air A1 in the air supply passage 1, and the first cold water coil 21 and the heat source via the raised outside air A1. Water m2 is heated. On the other hand, in the summer, cold water is supplied to the heating / cooling combined coil 79 to cool the outside air A1, and the cooling load exceeding the heating load is removed.
Even in this configuration, the same effect as that of the desiccant air conditioning system S2 can be obtained.

[Third embodiment]
Subsequently, a third embodiment of the present invention will be described.
FIG. 9 is a schematic configuration diagram of the exhaust heat utilization system S3 according to the third embodiment of the present invention. In the following description and the drawings used in the following description, the same components as those in the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  As shown in FIG. 9, the exhaust heat utilization system S3 includes a heat pump system H3. The heat pump system H3 includes a heat source system 80, a heat supply system 90, and a hot water heat pump 40.

In the heat source system 80, the first cold water coil 21 is disposed in the air conditioner 81, and supplies the heat recovered from the outside air A1 to the turbo refrigerator 23.
In the heat supply system 90, the hot water coil 31 is disposed in the hot water storage tank 91, and supplies the heat supplied from the turbo refrigerator 23 to the hot water stored in the hot water storage tank 91.

  Also in the heat pump system H3 according to the present embodiment, the heat load and the heat load are unbalanced, and the amount of heat received by the heat source water m2 from the first cold water coil 21 and the second cold water coil 22 is the amount of heat supplied to the hot water coil 31. However, the heat of the heat source water m2 can be increased by the turbo chiller 23 even if it is too small. Thereby, since the temperature difference between the heat source water m2 and the hot water m3 can be a temperature difference suitable for the operation of the hot water heat pump 40, the hot water heat pump 40 can be operated stably.

Note that the operation procedure shown in the above-described embodiment, various shapes and combinations of the constituent members, and the like are examples, and various modifications can be made based on design requirements and the like without departing from the gist of the present invention.
For example, the piping configuration in each embodiment described above may be replaced with another piping configuration.

3 ... Desiccant (desiccant part)
20 ... Heat source system 21 ... First cold water coil (heat source body, first cooling section)
22 ... Second cold water coil (heat source)
23 ... Turbo refrigerator (refrigerator)
24 ... Sealed cooling tower (cooling device)
28a ... High-temperature pipe 28b ... Low-temperature pipe 30 ... Heat supply system 31 ... Regeneration hot water coil, hot water coil (heat supply body)
40 ... Hot water heat pump (main heat pump)
60 ... Heat source system 61 ... Air-cooled heat pump (sub heat pump)
67a ... Branching low temperature channel 67b ... Branching high temperature channel 70 ... Heat supply system 71 ... Heating hot water coil (second heating part)
79. Heating / cooling coil (heat source)
A1 ... Outside air A4 ... Return air H1, H2, H3 ... Heat pump system S1, S2, S2A, S3 ... Desicant air conditioning system m1 ... Cold water (third heat medium)
m2 ... Heat source water (first heat medium)
m3 ... Warm water (second heat medium)

Claims (8)

A heat source system that has a heat source body that recovers heat from the surroundings and in which a first heat medium that receives the heat recovered by the heat source body circulates;
A heat supply system that has a heat supply body to be supplied with heat recovered by the heat source body, and a second heat medium that supplies heat to the heat supply body circulates;
A heat pump system comprising: a main heat pump in which the first heat medium and the second heat medium are introduced and heat recovered by the heat source body is moved from the first heat medium to the second heat medium. ,
The heat source system includes a heating device that heats the first heat medium introduced into the main heat pump. The heating device is a refrigerator that circulates the first heat medium with the main heat pump while circulating the third heat medium with the heat source body,
The refrigerator passes the heat recovered by the heat source through the third heat medium to the first heat medium, and heats exhaust heat by adding to the first heat medium. The heat pump system according to claim 1.   The heat pump system according to claim 2, wherein the heat source system includes a cooling device that cools the first heat medium that flows from the main heat pump toward the refrigerator. The heat source system circulates the first heat medium between the heat source body and the main heat pump,
The heat pump system according to claim 1, wherein the heating device is a sub heat pump that heats the first heat medium introduced into the heat source body. The heat source system includes a high-temperature channel through which the first heat medium flows from the heat source body toward the main heat pump,
A low-temperature flow path through which the first heat medium flows from the main heat pump toward the heat source body;
A branched low-temperature channel connected to the low-temperature channel and branching the first heat medium from the low-temperature channel and introducing it into the sub heat pump;
A branched high-temperature flow path connected to the high-temperature flow path and joining the first heat medium heated by the sub-heat pump to the first heat medium flowing through the upstream flow path;
The heat pump system according to claim 4, comprising: An air supply passage for supplying outside air flowing in from the outside to the air-conditioning target;
An exhaust passage for exhausting the return air flowing in from the air conditioning target to the outside;
A desiccant part that adsorbs moisture from the outside air passing through the air supply channel and desorbs the adsorbed moisture to the return air passing through the exhaust channel;
A first cooling part that is provided between the desiccant part and the outside of the air supply channel, and cools the outside air;
A first heating unit that is provided between the desiccant unit and the air-conditioning target in the exhaust channel, and that heats the return air to a regeneration temperature at which the desiccant unit desorbs the moisture;
A desiccant air conditioning system comprising the heat pump system according to any one of claims 1 to 5,
The heat source body includes the first cooling unit,
The desiccant air conditioning system, wherein the heat supply body includes the first heating unit. An air supply passage for supplying outside air flowing in from the outside to the air-conditioning target;
An exhaust passage for exhausting the return air flowing in from the air conditioning target to the outside;
A desiccant part that adsorbs moisture from the outside air passing through the air supply channel and desorbs the adsorbed moisture to the return air passing through the exhaust channel;
A first cooling part that is provided between the desiccant part and the outside of the air supply channel, and cools the outside air;
A first heating unit that is provided between the desiccant unit and the air-conditioning target in the exhaust channel, and that heats the return air to a regeneration temperature at which the desiccant unit desorbs the moisture;
A second heating unit that is provided between the desiccant unit and the air-conditioning target in the air supply channel, and heats the outside air;
A desiccant air conditioning system comprising the heat pump system according to claim 6,
The heat source body includes the first cooling unit,
The heat supply body includes the first heating unit,
The sub heat pump can be switched and connected to the first cooling unit, circulates the first heat medium independently of the main heat pump, and cools the outside air through the first cooling unit together with the main heat pump. Desiccant air conditioning system characterized by that. An air supply passage for supplying outside air flowing in from the outside to the air-conditioning target;
An exhaust passage for exhausting the return air flowing in from the air conditioning target to the outside;
A desiccant part that adsorbs moisture from the outside air passing through the air supply channel and desorbs the adsorbed moisture to the return air passing through the exhaust channel;
A first cooling part that is provided between the desiccant part and the outside of the air supply channel, and cools the outside air;
A first heating unit that is provided between the desiccant unit and the air-conditioning target in the exhaust channel, and that heats the return air to a regeneration temperature at which the desiccant unit desorbs the moisture;
A second heating unit that is provided between the desiccant unit and the air-conditioning target in the air supply channel, and heats the outside air;
A desiccant air conditioning system comprising the heat pump system according to claim 6 or 7,
The heat source body includes the first cooling unit,
The heat supply body includes the first heating unit,
The sub heat pump can be switched to the second heating unit so as to circulate the first heat medium with the second heating unit, and is heated on the condition that the main heat pump is stopped. The desiccant air conditioning system, wherein the first heat medium is supplied to the second heating unit.

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