JP2948776B2 - 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 requires a temperature of about 10 ° C. as a low heat source temperature required for cooling the processing air. 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, even in the air conditioning system having this configuration, if the entire amount of the regeneration air is passed through the high heat source heat exchanger of the heat pump for heat exchange as shown in FIG. Although it is necessary to increase the temperature by 20 ° C. up to about 0 ° C., the amount of heat that can be heated by the superheated steam of the refrigerant among the heating capacity on the heat pump side occupies only 12% of the entire heat generation as shown in FIG. It means that the temperature can be raised only by 20 ° C. × 0.12 = 2.4 ° C., so that the sensible heat of the superheated steam at the compressor outlet hardly contributes to the temperature rise of the regeneration air, and as a result, is lower than the condensation temperature The desiccant must be regenerated with regenerated air at the temperature.

On the other hand, when a material such as silica gel is used for the desiccant, in the temperature range up to 90 ° C., the higher the temperature, the higher the desiccant's ability to absorb moisture after regeneration tends to be. The higher the temperature, 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 about 80 ° C. in order to increase the regeneration temperature for such a purpose, a cycle as shown by a dotted line in FIG. 9 occurs, and the condensing pressure of the refrigerant is abnormally high (26.8 kg / cm ^2). ), 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.

SUMMARY OF THE INVENTION The present invention has been made in view of the above points, and has a high heat source heat exchanger for a heat pump of an air conditioning system capable of continuously performing a desiccant moisture adsorption process and a desiccant regeneration process using a heat pump. Two high heat source heat exchangers, the refrigerant discharged from the compressor is configured to flow from the first high heat source heat exchanger to the second high heat source heat exchanger in order, and the regenerated air is supplied to the second high heat source heat exchanger. After passing through the heat source heat exchanger, it is branched and a part of the first regenerated desiccant is regenerated, and the remaining branched regenerated air passes through the first high heat source heat exchanger of the heat pump. By performing the second regeneration, the last regeneration temperature in the desiccant regeneration step is increased by utilizing the sensible heat of the superheated vapor of the refrigerant after compression of the heat pump, and the moisture absorption capacity of the desiccant is reduced. To allow pressurized, excellent dehumidification capacity,
Another object of the present invention is to provide an energy-saving air conditioning system.

[0010]

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. In an air conditioning system equipped with a low heat source and a heat pump that operates as a high heat source and supplies heat for desiccant regeneration to the regeneration air, a portion of the regeneration air is heated by superheated vapor of a refrigerant compressed by a compressor. This is an air conditioning system characterized by regenerating desiccant.

As described above, by heating a part of the regenerated air with the superheated steam of the refrigerant, the heat capacity of the regenerated air is reduced and a large change in sensible heat can be obtained. Heat can also increase the temperature of the regeneration air and increase the desiccant's ability to absorb moisture.

According to a second aspect of the present invention, a flow path section for the processing air and the regeneration air passing through the desiccant is provided with a first section for performing at least a moisture adsorption step of the processing air and a first regeneration step for the regeneration air. A second compartment to perform and a second
And a third section in which the desiccant is returned to the first section via the first section, the second section, and the third section, and a high heat source heat exchange of the heat pump is performed. At least a first high heat source heat exchanger and a second high heat source
A heat exchanger and at least two heat exchangers, the refrigerant discharged from the compressor is configured to flow from the first high heat source heat exchanger to the second high heat source heat exchanger, and regeneration air branches after passing through the second high heat source heat exchanger, a portion passes through the second compartment, the remaining regeneration air that has branched the first high heat source heat exchanger of the heat pump The air-conditioning system according to claim 1, wherein after passing through the third section, the remaining regenerated air branched is heated with superheated steam of a refrigerant to regenerate the desiccant. It is.

As described above, of the desiccant process in which the moisture absorption process and the regeneration process are repeated, the regeneration process is divided into two, the first regeneration is performed with low-temperature regeneration air, and then the high-temperature regeneration is performed with the superheated steam of the refrigerant. By performing the second regeneration with the regeneration air, the desiccant is regenerated in a stepwise manner, and the desiccant's moisture absorbing ability can be increased.

According to a third aspect of the present invention, the desiccant has a rotor shape, and the desiccant rotates to return to the first section through the first section, the second section, and the third section. The air conditioning system according to claim 2, wherein the air conditioning system is configured.

As described above, the desiccant is formed into 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.

According to a fourth aspect of the present invention, the temperature of the compressed refrigerant is increased by heating the refrigerant flowing into the compressor of the heat pump with the saturated vapor of the compressed refrigerant. An air conditioning system according to any one of 1 to 3.

As described above, the superheat degree of the refrigerant sucked into the compressor of the heat pump is increased and then compressed, so that the superheat degree at the compressor outlet is increased, and a part of the heat of condensation is used to increase the superheat degree of the refrigerant. By changing the ratio of the latent heat (condensed portion) and the sensible heat (superheated portion) to the amount of heat transferred from the high-pressure refrigerant to the regeneration air, the ratio of the sensible heat that can contribute to the temperature rise of the regeneration air is increased. The air temperature can be increased, and the desiccant's ability to absorb moisture can be increased.

According to a fifth aspect of the present invention, the refrigerant in the refrigerant path connecting the first high heat source heat exchanger and the second high heat source heat exchanger of the heat pump exchanges heat with the refrigerant flowing into the compressor. The air conditioning system according to claim 4, wherein the refrigerant flowing into the compressor is heated by the heating.

As described above, in the first heat source heat exchanger of the heat pump, the regenerated air is heated by the superheated refrigerant at the compressor outlet to remove the sensible heat, and then compressed by the latent heat of condensation of saturated steam in the refrigerant heat exchanger. The superheat at the compressor outlet is increased by increasing the superheat of the refrigerant sucked into the compressor before compression, and part of the heat of condensation is used to increase the superheat of the refrigerant, so that the refrigerant is transferred from the high-pressure refrigerant to the regeneration air. By changing the ratio of latent heat (condensed component) and sensible heat (superheated component) to the amount of heat generated and increasing the ratio of sensible heat that can contribute to the temperature rise of the regeneration air, the temperature of the regeneration air can be increased, The desiccant's ability to absorb moisture can be increased.

According to a sixth aspect of the present invention, 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 heat pump is provided in the other medium path of the refrigerant heat exchanger. The refrigerant flowing into the compressor is heated by guiding the refrigerant in the high pressure path of the refrigerant connecting the first high heat source heat exchanger and the second high heat source heat exchanger to perform heat exchange. An air conditioning system according to item 4 or 5.

As described above, after the regeneration air is heated by the superheated refrigerant at the compressor outlet in the first heat source heat exchanger of the heat pump to remove the sensible heat, the heat pump is heated by the latent heat of condensation of the saturated vapor in the refrigerant heat exchanger. The superheat of the dry and saturated compressor suction refrigerant that has exited the low heat source heat exchanger is increased before being compressed, thereby increasing the superheat at the compressor outlet and increasing the superheat of the refrigerant as part of the condensation heat By changing the ratio of latent heat (condensed portion) and sensible heat (overheated portion) to the amount of heat transferred from the high-pressure refrigerant to the regeneration air, the ratio of sensible heat that can contribute to the temperature rise of the regeneration air is increased. As a result, the temperature of the regeneration air can be increased, and the desiccant's ability to absorb moisture can be increased.

According to a seventh aspect of the present invention, 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 the first high heat source heat exchanger of the heat pump is connected to the first heat source heat exchanger. A gas-liquid separator is provided in a high-pressure path of the refrigerant connecting the high heat source heat exchangers of No. 2 and the gas-liquid separator is separated by the gas-liquid separator, and guided to the refrigerant heat exchanger to be condensed. The air conditioning system according to any one of claims 4 to 6, wherein the inflowing refrigerant is heated.

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, so that 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.

According to the present invention, 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 restriction is provided in the middle of the path for extracting the liquid phase of the gas-liquid separator. 8. The method according to claim 7, wherein a path passing through the throttle and a path of the high-pressure refrigerant passing through the refrigerant heat exchanger are merged and then guided to a second high heat source heat exchanger of the heat pump. It is an air conditioning system of description.

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.

[0026]

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,
Among them, the configuration of the part of the vapor compression heat pump includes 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 heat exchanger. A vapor compression refrigeration cycle is formed by using an exchanger (condenser) 220 and an expansion valve 250 as components, and an evaporator 240
And the humid vapor of the low-pressure refrigerant has a heat exchange relationship with the treated air after passing through the desiccant 103, and the sensible heat exchanger 2
At 30, the regenerated air before passing through the desiccant 103 and the superheated vapor of the refrigerant have a heat exchange relationship, and the wet steam of the high-pressure refrigerant has heat exchange with the regenerated air before passing through the sensible heat exchanger 230 and the desiccant 103 at the condenser 220. A cycle that forms a relationship.

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 via a path 124 to a suction port of a blower 140 for introducing outside air which becomes regeneration air, 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 branched into two, one of which is connected to the second section for performing the first regenerating step of the regenerating air of the desiccant rotor 103, the path 128A, the punching metal and the like. Connected via the aperture mechanism 150,
The other branch is the sensible heat exchanger 230 and the path 127B.
And the outlet of the regenerated air of the sensible heat exchanger 230 is connected to the third section of the desiccant rotor 103 through which the second regenerating process of the regenerated air is performed through the path 128B to regenerate the desiccant rotor 103. The outlet of the regenerated air in the second section for performing the first regenerating step of the air and the desiccant rotor 103
The outlet of the regeneration air in the third section for performing the second regeneration process of the regeneration air merges with the external space through the path 129 to take in the regeneration air from the outside and exhaust it to the outside. I do. In the figure, circled letters K to U are symbols indicating the state of air corresponding to FIG.

The desiccant that rotates in a predetermined cycle across both the processing air path A and the regeneration air path B is:
As shown in the detailed desiccant diagram of FIG.
To the first section, which is connected to the first path through the paths 108 and 109 to perform the moisture adsorption step, and to the path 128 to the regeneration air path B.
A, a second section which is connected via A, 129 and performs a first regeneration step of the regeneration air;
8B, 129 and a third section for performing the second regeneration step of the regeneration air, and the desiccant is passed through the first section, the second section, and the third section to the first section. Configure to return to parcel.

Next, the cycle of the vapor compression refrigeration cycle of the desiccant air conditioner constructed as described above will be described. 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 being sucked and compressed by the compressor 260 via the path 209 and flowing into the first high heat source heat exchanger (sensible heat exchanger) 230 via the path 201, the sensible heat of the superheated steam of the refrigerant before flowing into the desiccant 103 After being discharged to the regenerated air, flows into the second high heat source heat exchanger (condenser) 220 via the path 202 and transfers the heat of condensation to the desiccant 103 and the first high heat source heat exchanger (sensible heat exchanger) 230. It is released to the regeneration air before inflow and condensed. The condensed refrigerant passes through the path 206 and enters the expansion valve 25.
0, and after expanding under reduced pressure there, evaporator (cooler) 24
Reflux to 0.

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 branched into two, and one of the regenerated air passes through a second section of the desiccant rotor 103 in which the first regeneration step of the regenerated air is performed to remove water from the desiccant rotor 103 and to perform a regeneration operation. (State UA), and the other branch 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), and then the desiccant rotor 103 is regenerated. After passing through the third section for performing the second regeneration step of the air, the desiccant rotor is removed to perform the regeneration action (state U
-A), the regeneration air that has passed through the third section of the desiccant rotor 103 that performs the second regeneration step of the regeneration air has passed through the second section that performs the first regeneration step of the regeneration air of the desiccant rotor 103. After being mixed with the regeneration air (state U), it is discarded to the outside as exhaust gas via a path 129.

In this manner, the desiccant is air-conditioned by repeating the regeneration of the desiccant and the dehumidification and cooling of the processing air. In this embodiment, however, a part of the regenerated air exits the condenser 220. After branching into two, one of them is heated with the superheated steam of the refrigerant compressed by the compressor after reducing the flow rate and the heat capacity, so even with a small heat amount of about 12% of the total heat amount, It is possible to heat the temperature of the regeneration air to a temperature higher than the condensing temperature by the sensible heat of the desiccant rotor 10 at that temperature.
Since the desiccant in the third section where the second regeneration step of the regeneration air of No. 3 is performed can be regenerated, the desiccant dehumidifying ability immediately before shifting to the adsorption step is improved as compared with the conventional method. This will be described below using examples.

Now, suppose that the refrigerant cycle is the cycle shown in FIG. 9 and the conventional condenser inlet temperature of the regeneration air is 40.degree. C., the temperature rise width is 20.degree. C., and the refrigerant condensation temperature is 65.degree. According to the present embodiment, the condenser 2 of the heat pump
Since the heating amount by 20 becomes 88%, the temperature Ts of the state S
Ts = 40 + 20 × 88/100 = 57.6 ° C. After that, if the regenerated air is branched and the air equivalent to 15% is superheated with superheated steam with 12% heat, the condition is as follows.
The temperature Tt of T is: Tt = 57.6 + 20 × 12/100 / 0.15 = 73.6
° C. When the temperature efficiency of the heat exchanger at this time is obtained, Φ = (73.6-57.6) / (80−57.6) × 10
0% = 71.4%, which is sufficiently achievable if a countercurrent heat exchanger is used as the sensible heat exchanger 230, and regenerated air at a temperature 8.3 ° C. higher than the condensation temperature of 65 ° C. can be obtained. .

As described above, according to this embodiment, the desiccant in the third section where the second regeneration step of the regeneration air of the desiccant rotor 103 is performed at a temperature higher than the condensation temperature can be regenerated. The desiccant dehumidifying capacity immediately before shifting to the adsorption step can be improved as compared with the related art, and therefore, an air-conditioning system having excellent dehumidifying capacity and energy saving can be provided.

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

FIG. 3 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
After the heat exchange with the high-pressure wet steam exiting from 30, the cycle is configured so that the high-pressure wet steam flows 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 In the condenser 220, the wet vapor of the high-pressure refrigerant is passed through the sensible heat exchanger 230 and the desiccant 103
The cycle that forms a heat exchange relationship with the regeneration air before passing 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, the cycle of the vapor compression refrigeration cycle portion of the desiccant air conditioner configured as described above will be described below. The refrigerant evaporates by removing the latent heat of evaporation from the processing air dehumidified by the desiccant 103 in the evaporator (cooler) 240, evaporates, reaches the refrigerant heat exchanger 270 via the path 209, and exits the sensible heat exchanger 230 there. After the heat exchange with the saturated steam, the air is sucked and compressed by the compressor 260. The compressed refrigerant flows into the sensible heat exchanger 230 via the path 201, releases the sensible heat of the superheated vapor of the refrigerant to the regenerated air before flowing into the desiccant 103, and then reaches the refrigerant heat exchanger 270 via the path 202. Then, heat exchange occurs with the low-pressure refrigerant in a dry and saturated state before suction of the compressor, and a portion of the refrigerant condenses. Refrigerant heat exchanger 2
The high-pressure refrigerant that has exited 70 flows into the condenser 220 and discharges the heat of condensation into the regenerated air before flowing into the desiccant 103 and the first high-heat-source heat exchanger (sensible heat exchanger) 230 to condense.
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. 4 which is a Mollier diagram. Refrigerant is evaporator (cooler)
After evaporating at 240 (state g), the refrigerant reaches the refrigerant heat exchanger 270 via the path 209 and exchanges heat with the high-pressure saturated steam exiting the sensible heat exchanger 230 (state a).
Is sucked and compressed. The compressed refrigerant (state b) flows into the sensible heat exchanger 30 and releases the sensible heat of superheated vapor of the refrigerant into the regenerated air before flowing into the desiccant 103 (state c), and then reaches the refrigerant heat exchanger 270. , Heat exchanges with the dry saturated low-pressure refrigerant before the suction of the compressor, and a part of the refrigerant is condensed (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 enthalpy is reduced. 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 to the regenerated air before flowing into the desiccant 103 and the sensible heat exchanger 230 (state d). The condensed refrigerant reaches the expansion valve 250 and is decompressed and expanded there (state e), and then returns to the evaporator (cooler) 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 sensible heat exchanger 230 increases, and the heat transfer amount of the sensible heat exchanger 230 is 35%, and that of the condenser 220 is 65%.

The operation on the air side of the air-conditioning system constructed as in this embodiment can be described with reference to the psychrometric chart of FIG. 2 similarly to the first embodiment. As compared with the example, the flow rate of the air passing through the sensible heat exchanger 230 can be increased. In the refrigerant cycle of FIG. 4, the condensation temperature is set to 60 ° C. in consideration of such an effect. Hereinafter, this effect will be described using an example.

According to the present embodiment, the amount of heating by the condenser 220 of the heat pump is 65%, so the temperature Ts in the state S is Ts = 40 + 20 × 65/100 = 53 ° C. Thereafter, if the regenerated air is branched and the air equivalent to 30% is superheated with superheated steam at a heat amount of 35%, the temperature Tt of the state T is Tt = 53 + 20 × 30/100 / 0.3 = 73 ° C. (Substantially the same temperature as in the first embodiment). When the temperature efficiency of the heat exchanger at this time is obtained, Φ = (73−53) / (105−53) × 100% = 3
8.4%, which is sufficiently achievable as a heat exchanger, and regenerated air at a temperature 13 ° C. higher than the condensation temperature of 60 ° C. is obtained.

After the regeneration air is heated by the superheated refrigerant at the compressor outlet in the sensible heat exchanger 230 to remove the sensible heat, the refrigerant heat exchanger 270 uses the latent heat of condensation of the saturated vapor to evaporate the heat pump. Increasing the superheat at the compressor outlet by increasing the superheat of the dry-saturated compressor suction refrigerant exiting 240 and then increasing the superheat at the compressor outlet, and using a part of the heat of condensation to increase the superheat of the refrigerant The ratio of the latent heat (condensed portion) and the sensible heat (superheated portion) to the amount of heat transferred from the high-pressure refrigerant to the regenerating air without increasing the compression ratio of the compressor (in this embodiment, the compression ratio is rather reduced) To perform the second regeneration step of the regeneration air of the desiccant rotor 103 at a temperature higher than the condensation temperature by increasing the ratio of the sensible heat that can contribute to the temperature rise of the regeneration air. Since the desiccant in the section can be regenerated, the desiccant dehumidifying capacity immediately before shifting to the adsorption step can be improved as compared with the conventional art, and therefore, it is possible to provide an air conditioning system that is excellent in dehumidifying capacity and energy saving. it can.

FIG. 5 shows a third 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 second embodiment in which the cycle is configured such that the high-pressure wet steam flowing to the condenser 220 flows after the heat exchange with the high-pressure wet steam exiting 30. 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. In the condenser 220, the wet vapor of the high-pressure refrigerant is passed through the sensible heat exchanger 230 and the desiccant 103
The cycle that forms a heat exchange relationship with the regeneration air before passing is the same as in the first and second embodiments.

Since the configuration of the air-side cycle is not different from the first and second embodiments, the difference between the cycle of the vapor compression refrigeration cycle and the above-described 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. The refrigerant is led to the exchanger 270, where the refrigerant exchanges heat with the dry saturated low-pressure refrigerant before suctioning the compressor to condense the refrigerant. 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, 20% of the refrigerant flow rate
Is less than. 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 270. Therefore, it is necessary to provide the throttle 285 and 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.

[0047]

As described above, according to the present invention, the last regeneration temperature in the desiccant regeneration step is increased by utilizing the sensible heat of the superheated vapor of the refrigerant after compression of the heat pump, or Latent heat in the amount of heat transferred from the high-pressure refrigerant to the regeneration air by increasing the superheat of the refrigerant drawn into the compressor and increasing the superheat at the compressor outlet by increasing the superheat of the refrigerant drawn into the compressor with the refrigerant vapor after heating the regeneration air with the superheated refrigerant (Condensed matter)
By increasing the ratio of sensible heat that can contribute to a rise in the temperature of the regenerated air by changing the ratio of the sensible heat (superheated component) to the temperature of the regenerated air used in the final step of the desiccant regeneration, Can provide an air-conditioning system that is excellent in dehumidifying capacity, compact, and energy saving.

[Brief description of the drawings]

FIG. 1 shows a first embodiment of an air conditioning system according to the present invention.
(A) is an explanatory view showing a basic configuration, and (b) is a perspective view showing a part of a desiccant rotor.

FIG. 2 is an explanatory diagram showing a desiccant air-conditioning cycle of air of the air conditioner of FIG. 1 in a psychrometric chart.

FIG. 3 shows a second embodiment of the air conditioning system according to the present invention;
(A) is an explanatory view showing a basic configuration, and (b) is a perspective view showing a part of a desiccant rotor.

FIG. 4 is a Mollier diagram showing a refrigerant cycle of the embodiment of FIG. 3;

FIG. 5 shows a third embodiment of the air conditioning system according to the present invention;
(A) is an explanatory view showing a basic configuration, and (b) is a perspective view showing a part of a desiccant rotor.

FIG. 6 is an explanatory diagram showing a basic 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;

[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 the front page (58) Field surveyed (Int. Cl. ⁶ , DB name) F24F 3/00 F25B 29/00 F28D 21/00

Claims (8)

(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 by regenerating a desiccant by heating a part of regenerated air with superheated steam of a refrigerant compressed by a compressor. 2. A flow path section for processing air and regeneration air passing through a desiccant, a first section for performing at least a moisture adsorption step of processing air, a second section for performing a first regeneration step of regeneration air, A third section for performing a second regeneration step of the regeneration air, wherein the desiccant is configured to return to the first section via the first section, the second section, the third section, and the heat pump. At least the first heat source heat exchanger
At least two heat exchangers including the first heat source heat exchanger and the second high heat source heat exchanger, and the refrigerant discharged from the compressor is provided with the first high heat source heat exchanger. configured to flow from vessel in the order of the second high heat source heat exchanger, and regeneration air is branched after passing through the second high heat source heat exchanger, a portion passes through the second compartment, the branch after the remaining regeneration air which has passed through the first high heat source heat exchanger of the heat pump, by configuring so as to pass the third compartment, and the branch remaining
The air conditioning system according to claim 1, wherein the regenerated air is heated by superheated steam of the refrigerant to regenerate the desiccant. 3. The desiccant has a rotor shape, and is configured to return to the first section via the first section, the second section, and the third section by rotating the desiccant. The air conditioning system according to claim 2. 4. The compressor according to claim 1, wherein the refrigerant flowing into the compressor of the heat pump is heated with saturated vapor of the compressed refrigerant to increase the temperature of the compressed refrigerant. The described air conditioning system. 5. A refrigerant in a refrigerant path connecting the first heat source heat exchanger and the second high heat source heat exchanger of the heat pump and the refrigerant flowing into the compressor are heat-exchanged to flow into the compressor. The air conditioning system according to claim 4, wherein the refrigerant is heated. 6. A refrigerant heat exchanger is provided in a low pressure path of a refrigerant connecting the low heat source heat exchanger of the heat pump and the compressor, and a first heat source heat of the heat pump is provided in another medium path of the refrigerant heat exchanger. The refrigerant flowing into the compressor is heated by guiding the refrigerant in a high pressure path of the refrigerant connecting the exchanger and the second high heat source heat exchanger to perform heat exchange.
Or the air conditioning system according to 5. 7. A first heat source heat exchanger and a second high heat source heat exchanger of a heat pump, wherein 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. Providing a gas-liquid separator in a high-pressure path of the refrigerant connecting the refrigerant, separating the gas-phase refrigerant by the gas-liquid separator, guiding the refrigerant to the refrigerant heat exchanger, condensing the refrigerant, and heating the refrigerant flowing into the compressor. The air conditioning system according to any one of claims 4 to 6, wherein: 8. A high-pressure refrigerant path for extracting a gaseous phase of the gas-liquid separator is guided to a refrigerant heat exchanger, and a throttle is provided in the middle of a path for extracting the liquid phase of the gas-liquid separator. The air-conditioning system according to claim 7, wherein the air-conditioning system is configured to join the high-pressure refrigerant through the refrigerant heat exchanger and then to a second heat source heat exchanger of the heat pump.