JP2968230B2 - Air conditioning system - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioning system, and more particularly to an air conditioning system capable of continuously performing a desiccant moisture adsorption process and a heat pump desiccant regeneration process.

[0002]

FIG. 6 shows a prior art disclosed in US Pat. No. 4,430,864, which includes a processing air path A, a regeneration air path B, and two desiccant beds 103A, 1A.
03B and a heat pump 200 for regenerating the desiccant and cooling the processing air. This heat pump 200 has two desiccant beds 103A and 103B.
The heat exchangers 220 and 240 buried in the air are used as high and low heat sources. One desiccant bed performs an adsorption step by passing process air, and the other desiccant performs a regeneration step by passing regeneration air. After the air-conditioning process has been performed for a predetermined time, the four-way switching valves 105 and 106 are switched to flow the regeneration and processing air to the opposite desiccant bed to perform the opposite process.

[0003]

In the prior art as described above, since the high and low heat sources of the heat pump 200 and the respective desiccants are integrated with each other, the amount of heat corresponding to the cooling effect ΔQ is equal to the heat pump (refrigerator). Is loaded as is. That is, the effect beyond the capacity of the heat pump (refrigerator) cannot be obtained. Therefore, it is not possible to obtain the effect of simply increasing the complexity of the device.

In order to solve such a problem, as shown in FIG. 7, a high-temperature heat source 220 of a heat pump is disposed in a regeneration air path B to heat regeneration air, and a heat pump of a heat pump is disposed in a processing air path A. It is conceivable to arrange the low-temperature heat source 240 to cool the processing air, and to provide the heat exchanger 104 for performing sensible heat exchange between the processing air after passing through the desiccant 103 and the regeneration air before passing through the desiccant 103.
Here, the desiccant 103 uses a desiccant rotor that rotates over both the processing air path A and the regeneration air path B.

Thus, as shown in the psychrometric chart of FIG. 8, in addition to the cooling effect by the heat pump, a cooling effect (ΔQ) combining the cooling effect by sensible heat exchange between the processing air and the regeneration air is obtained. Therefore, higher efficiency than the air conditioning system of FIG. 6 can be obtained with a compact configuration.

A heat pump used for such an application has a high heat source temperature of 65 ° C. required for desiccant regeneration.
The above temperature and a low heat source temperature of about 10 ° C. required for cooling the processing air are required. FIG. 9 illustrates a vapor compression refrigeration cycle having such a high heat source temperature and a low heat source temperature on a Mollier diagram of the refrigerant HFC134a. As shown in FIG. 9, the temperature rise width of the heat pump is 55
° C, and the pressure ratio and compression power are close to those of a conventional air conditioner (air conditioner) heat pump using refrigerant HCFC22. Therefore, there is a possibility that a heat pump for desiccant air conditioning can be configured using a compressor for refrigerant HCFC22. If the sensible heat of the superheated steam (80 ° C. in the figure) at the outlet of the machine is used, there is a possibility that the regeneration air can be heated to a temperature higher than the condensation temperature.

However, also in the air conditioning system of this configuration, the relationship between the temperature change of the refrigerant and the regeneration air and the enthalpy change when the entire amount of the regeneration air is passed through the high heat source heat exchanger of the heat pump shown in FIG. Is shown in FIG. As shown in FIG. 10, assuming that the temperature efficiency of the condensing heat transfer portion where the refrigerant of the high heat source heat exchanger 220 condenses is 80%, the regeneration air is heated at 20 ° C. from 40 ° C. to about 60 ° C. As shown in FIG. 9, the amount of heat that can be heated by the superheated steam of the refrigerant in the heating capacity of the refrigerant occupies only 12% of the entire heat generation. 20 ° C./0.88)×0.12=2.7° C. Therefore, the sensible heat of the superheated steam at the outlet of the compressor hardly contributes to the temperature rise of the regeneration air. Regeneration air at a temperature lower than the condensation temperature (62.7 in the figure)
C) to regenerate the desiccant. On the other hand, when a material such as silica gel is used as the desiccant, as the regeneration temperature in a temperature range up to 90 ° C., the desiccant after regeneration tends to have a higher moisture absorbing capacity as the temperature is higher.
The higher the temperature of the regenerating air, the higher the latent heat treatment capacity of the desiccant air conditioner and the better the cooling capacity. Therefore, if the condensing temperature is raised to 75% to increase the regeneration temperature for such a purpose.
Attempting to increase the temperature to about ° C. results in a cycle as shown by the dotted line in FIG. 9, and the condensing pressure of the refrigerant is abnormally high (24.
1 kg / cm ² ), and a heat pump for desiccant air conditioning can no longer be configured using a compressor for the refrigerant HCFC22, and the compression power increases to lower the coefficient of performance.

[0008] The present invention is to increase the desiccant regeneration temperature,
An object of the present invention is to provide an air-conditioning system that is capable of increasing the moisture absorbing capacity of a desiccant, has excellent dehumidifying capacity, and saves energy.

[0009]

Means for Solving the Problems The present invention has been made to achieve the above object, and the invention according to claim 1 has a desiccant that adsorbs moisture in the processing air, a compressor, and the processing air is provided. A low heat source, a heat pump that operates as a high heat source using the regeneration air to supply heat for desiccant regeneration to the regeneration air, wherein the refrigerant flowing into the compressor of the heat pump is compressed with saturated vapor of the refrigerant. An air conditioning system characterized in that the temperature of a compressed refrigerant is increased by heating and then heat exchange is performed with regenerated air.

As described above, the refrigerant flowing into the compressor of the heat pump is heated by the saturated vapor of the compressed refrigerant to increase the temperature, that is, the enthalpy of the superheated refrigerant after compression, and occupies the amount of heat released by the high heat source of the heat pump. By increasing the ratio of the sensible heat and then conducting heat exchange with the regeneration air, the regeneration temperature of the desiccant can be increased, and the desiccant's ability to absorb moisture can be increased.

According to a second aspect of the present invention, at least a first section for performing a process of adsorbing moisture of the processing air and a second section for performing a process of regenerating the regeneration air are provided in a flow path section for the processing air and the regeneration air passing through the desiccant. And the desiccant is configured to return to the first section through the first section and the second section, and the heat source high heat source heat exchanger of the heat pump is provided at least.
A first high heat source heat exchanger and a second high heat source heat exchanger, wherein the refrigerant discharged from the compressor is supplied from the first high heat source heat exchanger to the second high heat source. A heat exchanger, and the regeneration air flows from the second heat source heat exchanger to the first heat source heat exchanger, and then passes through the second section of the desiccant; and A refrigerant heat exchanger is provided in a low pressure path of the refrigerant connecting the low heat source heat exchanger of the heat pump and the compressor, and a first high heat source heat exchanger and a second heat pump of the heat pump are provided in another medium path of the refrigerant heat exchanger. leading the refrigerant of the high pressure path of the refrigerant connecting the high heat source heat exchanger so as to heat exchange
A conditioning system according to claim 1, characterized in that configured.

As described above, the flow of the regeneration air and the flow of the refrigerant are formed in countercurrent, and the regeneration air first exchanges heat with the second high heat source heat exchanger of the heat pump operating at the condensing temperature, and then the temperature is reduced. Increasing the desiccant regeneration temperature and increasing the desiccant moisture absorption capacity by conducting heat exchange with the first high heat source heat exchanger of the heat pump that exchanges sensible heat with the superheated vapor of the high refrigerant and then guiding the heat to the desiccant regeneration section. Can be.

In the above air conditioning system, the desiccant may have a rotor shape, and the desiccant may rotate to return to the first section via the first section and the second section .

As described above, the desiccant is made to have a rotor shape and the desiccant is rotated so that the desiccant can be continuously subjected to moisture adsorption processing and desiccant regeneration processing by heating the superheated steam of the heat pump refrigerant. can do.

[0015] The air conditioning system according to the third aspect of the present invention provides the air conditioning system according to the third aspect.
3. The system according to 2, wherein a gas-liquid separator is provided in a high-pressure path of the refrigerant connecting the first heat source heat exchanger and the second heat source heat exchanger of the heat pump, and the gas-liquid separator The method is characterized in that the refrigerant is separated, and the refrigerant is introduced into the refrigerant heat exchanger and condensed, thereby heating the refrigerant flowing into the compressor.
You.

As described above, only the dry saturated refrigerant vapor used for increasing the degree of superheat of the refrigerant sucked into the compressor of the heat pump is separated and taken out by the gas-liquid separator, whereby the high-pressure refrigerant flowing through the refrigerant heat exchanger is removed. Low flow rate,
The pipe diameter of the refrigerant system and the refrigerant heat exchanger can be made small.

[0017] The air conditioning system according to the fourth aspect is characterized in that:
3. The system according to 3 , wherein a path of the high-pressure refrigerant for extracting the gas phase of the gas-liquid separator is guided to the refrigerant heat exchanger, and a throttle is provided in the middle of the path for extracting the liquid phase of the gas-liquid separator. After they are merged and the route of the high refrigerant which has flowed through via path and said refrigerant heat exchanger, you characterized by being configured to direct the second high heat source heat exchanger of the heat pump.

As described above, by providing the throttle in the middle of the path for extracting the liquid phase of the gas-liquid separator, the differential pressure across the high-pressure refrigerant path of the refrigerant heat exchanger through which the gas-phase refrigerant flows can be secured. Even if the refrigerant heat exchanger is installed in a place away from the first high heat source heat exchanger and the second high heat source heat exchanger,
High-pressure refrigerant vapor in a dry and saturated state can reliably flow to the refrigerant heat exchanger.

[0019]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a desiccant air conditioner according to the present invention will be described below with reference to the drawings. FIG. 1 is a diagram showing a basic configuration of a first embodiment of an air conditioning system according to the present invention,
Of these, the part of the vapor compression heat pump is the compressor 26
0, low heat source heat exchanger (evaporator) 240, first high heat source heat exchanger (sensible heat exchanger) 230, second high heat source heat exchanger (condenser) 220, expansion valve 250 In addition to the above-described vapor compression refrigeration cycle, a refrigerant heat exchanger 270 is provided in a path from the low heat source heat exchanger (evaporator) 240 to the compressor 260 in this cycle. Previous low pressure refrigerant and sensible heat exchanger 230
After the heat exchange with the high-pressure wet steam flowing out of the heat exchanger, the high-pressure wet steam flows to the condenser 220 to form a cycle. Then, in the evaporator 240, the wet steam of the low-pressure refrigerant has a heat exchange relationship with the processing air after passing through the desiccant 103, and in the sensible heat exchanger 230, the reheated air and the superheated vapor of the refrigerant before passing through the desiccant 103 have a heat exchange relationship. And the heat vapor of the high-pressure refrigerant in the condenser 220 forms a heat exchange relationship with the regenerated air before passing through the sensible heat exchanger 230.

The desiccant rotor 103 is configured so that the desiccant rotates in a predetermined cycle across both the processing air path A and the regeneration air path B in the same manner as described with reference to FIG. The processing air path A is connected to the air-conditioned space and the suction port of the blower 102 for introducing the return air through a path 107, and the discharge port of the blower 102 is connected to the first section and the path 108 where the desiccant rotor 103 performs the moisture adsorption process. The outlet of the processing air of the desiccant rotor 103 is connected to the sensible heat exchanger 104, which has a heat exchange relationship with the regeneration air, via the path 109, and the sensible heat exchanger 1
04 is connected to the evaporator (cooler) 240 via the path 110, and the processing air outlet of the evaporator 240 is connected to the humidifier 105 via the path 111.
The processing air outlet 05 is connected to a processing air outlet serving as an air supply port via a path 112 to form a processing air cycle.

On the other hand, the regeneration air path B is connected to a suction port of a blower 140 for introducing outside air, which becomes regeneration air, via a path 124, and a discharge port of the blower 140 has a sensible heat heat exchange relation with the processing air. The outlet of the regeneration air of the sensible heat exchanger 104 is connected to the condenser 220 and the passage 126.
The outlet of the regenerating air of the condenser 220 is connected to the sensible heat exchanger 230 via the path 127, and the outlet of the regenerating air of the sensible heat exchanger 230 is connected to the desiccant rotor 103.
And the outlet of the regenerated air in the second section for performing the regenerating process of the regenerated air of the desiccant rotor 103 is connected to the external space and the path 129. A cycle for connecting and taking in regeneration air from the outside and exhausting to the outside is formed. In the figure,
The circled letters K to U are symbols indicating the state of air corresponding to FIG.

The cycle of the vapor compression refrigeration cycle of the desiccant air conditioner constructed as described above will be described below. The refrigerant is desiccant 10 in the evaporator (cooler) 240.
Evaporating the latent heat of evaporation from the dehumidified processing air in step 3,
After reaching the refrigerant heat exchanger 270 via the path 209, the heat is exchanged with the high-pressure saturated steam that has exited the sensible heat exchanger 230, and then sucked and compressed by the compressor 260. The compressed refrigerant flows into the sensible heat exchanger 230 via the path 201 and releases the sensible heat of the superheated vapor of the refrigerant to the regenerated air before flowing into the desiccant 103, and then passes through the path 202 to the refrigerant heat exchanger 270
Here, heat exchange is performed with the low-pressure refrigerant in a dry and saturated state before suction of the compressor, and a part of the refrigerant is condensed. The high-pressure refrigerant that has exited the refrigerant heat exchanger 270 flows into the condenser 220 and discharges the heat of condensation to the regenerated air before flowing into the sensible heat exchanger 230 to be condensed. The condensed refrigerant reaches the expansion valve 250 via the path 206, is decompressed and expanded there, and then returns to the evaporator (cooler) 240.

Such a refrigerant cycle will be described with reference to FIG. 2 which is a Mollier diagram. The refrigerant evaporates in the evaporator 240 (state g) and passes through the path 209 to the refrigerant heat exchanger 270
Then, after heat exchange with the high-pressure saturated steam exiting the sensible heat exchanger 230 (state a), the refrigerant is sucked and compressed by the compressor 260. The compressed refrigerant (state b) flows into the sensible heat exchanger 230 and converts the sensible heat of the superheated vapor of the refrigerant to the desiccant 10.
After being discharged to the regeneration air before flowing into 3 (state c), the refrigerant reaches the refrigerant heat exchanger 270 where it exchanges heat with the dry saturated low-pressure refrigerant before suctioning the compressor and partially condenses (state f). At this time, since the low-pressure refrigerant (states g to a) is not heated to a temperature higher than the condensing temperature, the amount of heat transfer is limited, and in the refrigerant heat exchanger 270, the high-pressure saturated vapor drops in dryness to state f and the enthalpy increases. On the other hand, the low-pressure refrigerant becomes superheated steam (state a) and the enthalpy increases. The high-pressure refrigerant (state f) that has exited the refrigerant heat exchanger 270 flows into the condenser 220 and discharges the heat of condensation into the regenerated air before flowing into the sensible heat exchanger 230 and condenses (state d). The condensed refrigerant reaches the expansion valve 250 and is decompressed and expanded there (state e), and then returns to the evaporator 240. In this embodiment, the refrigerant enthalpy at the inlet of the condenser 220 (state f) decreases, while the refrigerant enthalpy at the inlet of the sensible heat exchanger 230 increases at the compressor outlet. The ratio of the heat transfer amount of the heat exchanger 230 increases, and the heat transfer amount of the sensible heat exchanger 230 becomes 35% of the total heat amount of the heat pump and the condenser 220 becomes 65% of the heat transfer amount.

Next, the operation of the desiccant air conditioning system using the heat pump configured as described above as a heat source will be described with reference to the psychrometric chart of FIG. The introduced return air (process air: state K) is sucked into the blower 102 via the path 107, pressurized, and passed through the path 108 to the desiccant rotor 10.
The moisture is adsorbed by the desiccant rotor in the first section where the moisture adsorption step 3 is performed, and the moisture in the air is adsorbed. The absolute humidity decreases and the temperature of the air rises due to the heat of adsorption (state L). The air whose humidity has decreased and its temperature has increased is sent to the sensible heat exchanger 104 via the path 109 and exchanges heat with outside air (regenerated air) to be cooled (state M). The cooled air is cooled by passing through the evaporator (cooler) 240 via the path 110 (state N). The cooled processing air is sent to the humidifier 105, and its temperature is reduced in the isenthalpy process by water injection or vaporization humidification (state P), and is returned to the air-conditioned space via the path 112 as air supply.

On the other hand, the regeneration of the desiccant rotor is performed as follows. Outside air used as regeneration air (state Q)
Is suctioned by the blower 140 via the passage 124, is pressurized and sent to the sensible heat exchanger 104, cools the processing air to increase its temperature (state R), and passes through the passage 126 to the condenser 22.
0, and is heated by the wet steam of the refrigerant to increase the temperature (state S). Further, the regenerated air exiting the condenser 220 is sent to the sensible heat exchanger 230, where it is further heated by the superheated vapor of the refrigerant to increase the temperature (state T).
After passing through the section of the desiccant rotor 103 where the regeneration process is performed, the moisture of the desiccant rotor is removed to perform the regeneration operation (state U), and is discarded as exhaust gas through the path 129 to the outside.

As described above, the air conditioning by the desiccant can be performed by repeating the regeneration of the desiccant and the dehumidification and cooling of the processing air. In this embodiment, as described above, the regeneration in the sensible heat exchanger 230 is performed. The heating amount of the regenerated air in the sensible heat exchanger 230 can be increased by setting the ratio of the heating amount of the air to the heating amount of the regeneration air in the condenser 220 to 35%: 65%. It is possible to heat the temperature of the regeneration air to a temperature higher than the condensation temperature. Therefore, the desiccant's dehumidifying ability is improved as compared with the conventional case. This will be described below using examples.

FIG. 4 shows the enthalpy (calorific value) of the high-pressure refrigerant of the heat pump serving as the heating source and the regeneration air of the embodiment of FIG.
It is a figure showing the relation between the amount of change and temperature. When heat exchange between the refrigerant of the heat pump and the regeneration air is performed, the amounts of change in the enthalpy of the refrigerant and the regeneration air are the same from the heat balance. Since the specific heat of the air passes through a sensible heat change that is almost constant, the air becomes a continuous straight line in the figure, and the refrigerant goes through a latent heat change and a sensible heat change, so that the portion of the latent heat change becomes horizontal. Therefore,
When the temperature of the regeneration air at the outlet of the condenser 220 is determined, the temperature of the regeneration air at the exit of the sensible heat exchanger 230 can be calculated from the heat balance irrespective of the temperature of the heated steam of the refrigerant on the other side that exchanges heat.

Therefore, in FIG. 4, when the refrigerant cycle is the cycle of FIG. 2 and the inlet temperature of the condenser 220 of the regeneration air is 40 ° C. and the refrigerant condensing temperature is 65 ° C., according to the present embodiment, The temperature efficiency of the condenser 220 is set to 8
Assuming 0%, the temperature Ts of the state S is as follows: Ts = 40 + (65−40) × 80/100 = 60 ° C. After that, if the regenerated air is to be heated with superheated steam at 35% of the total heating amount, the temperature Tt in the state T is
As described above, from the heat balance, Tt = 60 + 20 × 35/65 = 70.8 ° C. Therefore, regenerated air having a temperature 5.8 ° C. higher than the condensation temperature 65 ° C. is obtained.

As described above, according to the present embodiment, the desiccant of the desiccant rotor 103 can be regenerated at a temperature higher than the condensing temperature, so that the desiccant's dehumidifying ability can be improved as compared with the prior art. Therefore, it is possible to provide an air-conditioning system that is excellent in dehumidifying capacity and energy saving.

Although the method of using the exhaust air accompanying the indoor ventilation as the regeneration air has been widely used in the desiccant air conditioning, the exhaust gas from the room may be used as the regeneration air in the present invention. The same effect as that of the embodiment can be obtained.

FIG. 5 shows a second embodiment of the present invention. In this embodiment, the parts of the vapor compression heat pump include a compressor 260, a low heat source heat exchanger (evaporator) 240, a first high heat source heat exchanger (sensible heat exchanger) 230, and a second high heat source. In addition to the vapor compression refrigeration cycle including the heat exchanger (condenser) 220 and the expansion valve 250 as components, the refrigerant heat exchange in the path from the low heat source heat exchanger (evaporator) 240 to the compressor 260 in this cycle. 270 is provided, and the refrigerant heat exchanger 270 is provided.
Pressure refrigerant and sensible heat exchanger 2 before suction
This is the same as the first embodiment in which the cycle is configured such that the high-pressure wet steam flowing to the condenser 220 flows after heat exchange with the high-pressure wet steam that has exited 30. In the present embodiment, furthermore, The high-pressure refrigerant vapor that has exited the sensible heat exchanger 230 branches off the refrigerant path in the gas-liquid separator 280, and one side from which the gas phase is taken out is connected to the refrigerant heat exchanger 2 via the path 203.
A throttle 285 is provided in the middle of a path for extracting the liquid phase of the gas-liquid separator 280, and a path 205 passing through the throttle 285 and a path 204 of the high-pressure refrigerant passing through the refrigerant heat exchanger 270 are merged. After that, it was configured to guide to the condenser 220. In the evaporator 240, the wet steam of the low-pressure refrigerant has a heat exchange relationship with the processing air after passing through the desiccant 103, and in the sensible heat exchanger 230, the reheated air and the superheated vapor of the refrigerant before passing through the desiccant 103 exchange heat. The cycle in which the wet steam of the high-pressure refrigerant has a heat exchange relationship with the regenerated air before passing through the sensible heat exchanger 230 in the condenser 220 is the same as in the first embodiment.

Since the configuration of the air-side cycle is not different from that of the first embodiment, here, the difference of the cycle of the vapor compression refrigeration cycle from that of the first embodiment will be described. In this embodiment, the high-pressure refrigerant vapor (which is almost dry and saturated) exiting the sensible heat exchanger 230 is branched into a refrigerant path by the gas-liquid separator 280, and one of the gaseous phases is taken out by the refrigerant heat. Exchanger 270
Where it is condensed by exchanging heat with a dry and saturated low-pressure refrigerant before suctioning the compressor. The amount of the refrigerant condensed in the refrigerant heat exchanger 270 is small because the specific heat of the low-pressure refrigerant on the heated side is small and a sensible heat change, so that the temperature cannot rise above the condensing temperature. Is not condensed and is less than 20% of the compressor discharge refrigerant flow rate. Therefore, the amount of the high-pressure refrigerant guided to the refrigerant heat exchanger 270 may be small, and the pipe diameter of this system can be reduced.

On the other hand, about 80% of the flow rate of the refrigerant discharged from the compressor can be introduced directly to the condenser 220 by bypassing the refrigerant heat exchanger 270 in the path for taking out the liquid phase of the gas-liquid separator 280. Since it is desirable that the sensible heat exchanger 230 and the condenser 220 be installed close to each other due to the configuration of the desiccant air conditioner, about 80% of the flow rate of the refrigerant discharged from the compressor is directly bypassed to the refrigerant heat exchanger 270 in this way. The ability to guide the refrigerant to the condenser 220 has the effect of reducing piping costs. If there is no resistance in the bypass path 205, most of the refrigerant bypasses the refrigerant heat exchanger 203. Therefore, it is necessary to provide a throttle 285 to adjust the bypass flow rate ratio. Even if it is not strict and a large amount of refrigerant is set to flow through the refrigerant heat exchanger 270, there is no problem in operation because the amount of heat transferred is limited as described above.

As described above, only the dry saturated refrigerant vapor used for increasing the degree of superheat of the refrigerant sucked into the compressor of the heat pump is separated and taken out by the gas-liquid separator.
The flow rate of the high-pressure refrigerant flowing through the refrigerant heat exchanger can be reduced, and the piping diameter of the refrigerant system and the refrigerant heat exchanger can be reduced. Also, by providing a throttle in the middle of the path for extracting the liquid phase of the gas-liquid separator, a differential pressure across the high-pressure refrigerant path of the refrigerant heat exchanger through which the gas-phase refrigerant flows can be secured. Even if the high-pressure refrigerant vapor is in a dry and saturated state, it can flow to the refrigerant heat exchanger 270 without fail even if it is installed at a location away from the heat exchanger 230 and the condenser 220.

When a commercially available refrigerant compressor is used for the compressor 260 of the present invention, many commercially available refrigerant compressors have a structure in which a drive motor is cooled by the suction refrigerant of the compressor. There is a concern that the motor may overheat, but as a countermeasure, a jacket may be formed around the motor to allow low-pressure saturated steam to flow, or a coolant may be injected to cool the motor. No problem.

[0036]

As described above, according to the present invention, the superheated refrigerant is heated by the superheated refrigerant after compression by the heat pump, the refrigerant vapor is heated by the refrigerant vapor, the superheat of the refrigerant sucked into the compressor is increased, and then the compressor is compressed. By increasing the degree of superheat at the outlet, the ratio of the latent heat (condensed portion) and the sensible heat (superheated portion) in the amount of heat transferred from the high-pressure refrigerant to the regenerating air is changed, and the ratio of the sensible heat that can contribute to the temperature rise of the regenerating air is increased. By increasing the desiccant regeneration temperature, the desiccant regeneration temperature can be increased, so that the desiccant's moisture absorption capacity can be increased, and a compact, energy-saving air-conditioning system with excellent dehumidification capacity can be provided.

[Brief description of the drawings]

FIG. 1 is an explanatory diagram showing a basic configuration of a first embodiment of an air conditioning system according to the present invention.

FIG. 2 is a Mollier diagram showing a refrigerant cycle of the embodiment of FIG.

FIG. 3 is an explanatory diagram showing a desiccant air-conditioning cycle of air of the air conditioner of FIG. 1 in a psychrometric chart.

FIG. 4 is a diagram showing the relationship between the amount of change in enthalpy (calorific value) of the high-pressure refrigerant of the heat pump serving as the heating source and the regeneration air of the embodiment of FIG. 1 and the temperature.

FIG. 5 is an explanatory diagram showing a basic configuration of a second embodiment of the air conditioning system according to the present invention.

FIG. 6 is an explanatory diagram showing a configuration of a conventional air conditioning system.

FIG. 7 is an explanatory diagram showing a basic configuration of another conventional air conditioning system.

FIG. 8 is an explanatory diagram showing a desiccant air-conditioning cycle of air in a conventional desiccant air-conditioning in a psychrometric chart.

FIG. 9 is a Mollier chart showing a refrigerant cycle of the embodiment of FIG. 8;

FIG. 10 is a diagram showing a relationship between a change in temperature and a change in enthalpy of a refrigerant and regeneration air in a conventional desiccant air conditioner.

[Explanation of symbols]

 200 heat pump 102,140 blower 103 desiccant rotor 104 total heat exchanger 220 second high heat source heat exchanger 230 first high heat source heat exchanger 240 low heat source heat exchanger 260 compressor A process air path B regenerative air path

──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int. Cl. ⁶ , DB name) F24F 3/00

Claims (4)

(57) [Claims] 1. A heat pump having a desiccant for adsorbing moisture in processing air and a compressor, operating as a low heat source for the processing air and a high heat source for the regeneration air, and supplying heat for desiccant regeneration to the regeneration air. In an air conditioning system with
An air conditioning system characterized in that a refrigerant flowing into a compressor of the heat pump is heated with saturated vapor of the compressed refrigerant, thereby increasing the temperature of the compressed refrigerant and then performing heat exchange with regenerated air. 2. A flow path section for the processing air and the regeneration air passing through the desiccant is divided into at least a first section for performing a process for adsorbing moisture of the processing air and a second section for performing a regeneration step for the regeneration air. The desiccant is configured to return to the first section via the first section, the second section, and the high heat source heat exchanger of the heat pump includes at least a first high heat source heat exchanger.
And a second high heat source heat exchanger, wherein the refrigerant discharged from the compressor flows from the first high heat source heat exchanger to the second high heat source heat exchanger in order, and the regeneration air Is the second
Flowing from the high heat source heat exchanger to the first high heat source heat exchanger in order, and then passing through the second section of the desiccant.
A refrigerant heat exchanger is provided in a low pressure path of the refrigerant connecting the low heat source heat exchanger of the heat pump and the compressor, and a first high heat source heat exchanger of the heat pump and a second heat source heat exchanger are provided in another medium path of the refrigerant heat exchanger. The air conditioning system according to claim 1, wherein the air conditioning system is configured to guide the refrigerant in a high pressure path of the refrigerant that connects the second heat source heat exchangers to perform heat exchange. 3. A gas-liquid separator is provided in a high-pressure path of a refrigerant connecting the first high heat source heat exchanger and the second high heat source heat exchanger of the heat pump, and the gas-liquid separator is used for the gas-liquid separator. The air conditioning system according to claim 2 , wherein the refrigerant flowing into the compressor is heated by being separated, guided to the refrigerant heat exchanger, and condensed. 4. A path for a high-pressure refrigerant for extracting a gas phase of a gas-liquid separator to a refrigerant heat exchanger, and a throttle provided in a middle of a path for extracting a liquid phase of the gas-liquid separator, and a path passing through the throttle. 4. The air conditioning system according to claim 3 , wherein the air-conditioning system is configured to join the high-pressure refrigerant through the refrigerant heat exchanger and then to a second high heat source heat exchanger of the heat pump.