JP2013130389A - Air source heat pump device - Google Patents

Abstract

An air heat source heat pump device including a dry desiccant device that can be operated without frost formation even at low outside air temperatures.
[Solution]
The air heat source heat pump device 100 of the present invention is alternately adsorbed to a working medium circulation circuit 10 in which a compressor, a condenser, an expansion valve, and an evaporator are connected via a pipe, and a dehumidifying region 36 and a regeneration region 37. And a dry desiccant device 30 having a dehumidifying rotor for moving the agent, and the adsorbent of the dry desiccant device 30 is mesoporous silica having a pore size that does not freeze.
[Selection] Figure 3

Description

  The present invention relates to an air heat source heat pump device.

  The conventional air heat source compression heat pump device has a problem that the evaporator forms frost during heating operation or hot water supply operation at a low outside air temperature (for example, at an outside air temperature of 0 ° C.). However, there is a problem that defrost operation is required. Therefore, for example, in the air conditioner described in Patent Document 1, frost formation is prevented by providing means for preheating the air to be blown to the evaporator.

  On the other hand, as a device for removing moisture in the air, for example, a dry desiccant device described in Patent Document 2 is known. In such a dry desiccant apparatus, a rotor in which an adsorbent such as silica gel, zeolite, or mesoporous silica is supported on ceramic paper using a binder is used.

JP 2008-39374 A JP 2003-200016 A

In the conventional air conditioner, it was possible to prevent frosting of the evaporator by blowing preheated air. However, since it is necessary to prepare a heater or the like in addition to the air heat source heat pump device, there is a problem that energy consumption increases.
Therefore, it is conceivable to prevent the evaporator from frosting by combining a dry desiccant device with the air heat source heat pump device. However, when the conventional dry desiccant device is operated under a low outside air temperature condition of 0 ° C. or lower, The dehumidifying ability is lower than that at a temperature of about 20 ° C., and in some cases, ice is adsorbed on the rotor and the use as an adsorbent may not be achieved.

The present invention has been made in view of the above-described problems of the prior art, and an object thereof is to provide a dry desiccant device that can perform dehumidification with high efficiency even at a low outside air temperature.
Another object of the present invention is to provide an air heat source heat pump device including a dry desiccant device, which is excellent in energy saving.

In order to solve the above problems, the dry desiccant device of the present invention is a dry desiccant device provided with a dehumidification rotor that moves the adsorbent alternately between the dehumidification region and the regeneration region, wherein the adsorbent moves the dehumidification region. The ratio of the dehumidification region passage time t _ad passing through and the regeneration region passage time t _de passing through the regeneration region is determined by the adsorption time constant T _ad of the adsorbent at the temperature of the processing air supplied to the dehumidification region and the regeneration. It is a value roughly proportional to the ratio of the adsorbent desorption time constant T _de at the temperature of the regeneration air supplied to the region.

In the conventional dry desiccant device, the dehumidification area and the regeneration area of the dehumidification rotor are fixed, and about half of the dehumidification rotor on the rotating disk is the dehumidification area and the other half is the regeneration area. In adsorption dehumidification at a normal air conditioning temperature (about 20 ° C.) and operation at a relatively low desorption regeneration temperature (about 80 ° C.), the adsorption time constant T _ad and the desorption time constant T _de are almost equal. There was no problem with the configuration.

However, in winter operation in a negative temperature environment, moisture adsorption in the air at 0 ° C. or lower is performed, so the mass transfer coefficient is small, and the adsorption time constant T _ad is about one order longer than the desorption time constant T _de . Therefore, when the dehumidification area and the regeneration area are fixed, the dehumidification amount in the adsorption zone is reduced, but the regeneration capacity becomes excessive.
On the other hand, in the present invention, the ratio of the adsorbent dehumidification region passage time and the regeneration region passage time is set corresponding to the ratio of the adsorption time constant T _ad and the desorption time constant T _de at the use temperature. The maximum dehumidification amount can be obtained even in a temperature environment where the adsorption time constant _Tad of 0 ° C. or less is extremely long.

_{t ad: t de = T ad} : T de, _{or, t ad: t de = T} ad / 2: It is preferred that _{T de.}
That is, it is preferable that the ratio between the dehumidification region passage time t _ad and the regeneration region passage time t _de is equal to the ratio between the adsorption time constant T _ad and the desorption time constant T _de . By adopting such a configuration, the balance between the adsorption capacity and the regeneration capacity is optimized, and the dehumidification amount can be maximized.
Alternatively, it may be ½ of the ratio between the adsorption time constant T _ad and the desorption time constant T _de . As described above, since the adsorption time constant T _ad is about one order longer than the desorption time constant T _de , the ratio between the dehumidification region passage time and the regeneration region passage time is determined depending on the equipment configuration. _In some cases, the ratio between _ad and the desorption time constant T _de cannot be made equal. In this case, the adsorbing capacity is lowered, but the above passing time may be set so that t _ad : t _de = T _ad / 2: T _de .

The dehumidification rotor has a substantially disk shape that is rotatable about an axis, and an air path separation member that divides the dehumidification rotor into the dehumidification area and the regeneration area around the rotation axis is provided, The ratio of the partition angle θ _ad of the air path separation member on the region side and the partition angle θ _de on the regeneration region side is a value approximately proportional to the ratio of the dehumidification region passage time t _ad and the regeneration region passage time t _de. Preferably there is.
With such a configuration, a dry desiccant device that can obtain the maximum dehumidifying amount can be easily obtained. In the dry desiccant device of the present invention, the ratio between the dehumidification region passage time t _ad and the regeneration region passage time t _de can be easily adjusted by adjusting the angular position of the air passage separation member.

The dehumidification rotor has a substantially disk shape that is rotatable about an axis, and an air path separation member that divides the dehumidification rotor into the dehumidification area and the regeneration area around the rotation axis is provided. It is preferable that the road separation member is configured so that a partition angle between the dehumidifying region and the regeneration region is variable.
According to this configuration, the ratio between the dehumidification zone passage time and the regeneration zone passage time can be changed according to the environmental temperature change, and the dry desiccant device can be obtained easily with the maximum dehumidification amount.

A temperature measuring device for measuring the temperatures of the processing air and the regeneration air at the inlet side of the processing air in the dehumidification region and the inlet side of the regeneration air in the regeneration region, and a temperature input from the temperature measurement device It is preferable to include an air path control device that moves the air path separation member based on the information and controls a partition angle between the dehumidification area and the regeneration area.
According to this configuration, the current adsorption time constant T _ad and the desorption time constant T _de can be acquired based on the temperature information, and the partition angle of the air path separation member can be adjusted based on these time constants. Can do. As a result, a dry desiccant device that automatically sets the ratio between the dehumidifying area and the regeneration area in accordance with the change in the environmental temperature and obtains the maximum dehumidifying amount can be obtained.

The dehumidification rotor has a substantially disc-shaped adsorbent container having a space inside, and a granular adsorbent accommodated in the adsorbent container, and the adsorbent container is disposed on the surface of the adsorbent container. It is preferable that a plurality of through holes through which air is circulated are formed. Furthermore, the board surface of the adsorbent container is preferably mesh-shaped.
With such a configuration, the particulate adsorbent can be fixed to the dehumidifying rotor without using a binder, and therefore, it is avoided that the binder freezes and the adsorption capacity is reduced during moisture adsorption in a minus temperature range. be able to.

An air heat source heat pump device according to the present invention includes the dry desiccant device described above.
According to this configuration, the dry desiccant device that can set the dehumidifying region passage time and the regeneration region passage time of the adsorbent in consideration of the change of the adsorption time constant accompanying the change of the environmental temperature and can obtain the maximum dehumidifying amount. It is possible to provide an air heat source heat pump device including

The air heat source heat pump device of the present invention moves the adsorbent alternately between a working medium circulation circuit formed by connecting a compressor, a condenser, an expansion valve, and an evaporator via a pipe, and a dehumidification region and a regeneration region. An air heat source heat pump device comprising a dry desiccant device provided with a dehumidifying rotor, wherein the adsorbent of the dry desiccant device is mesoporous silica having a pore size that does not freeze.
Also, a dew point temperature measuring device that measures the dew point temperature of the processing air that has passed through the dehumidifying region of the dehumidifying rotor, and an evaporation temperature of the evaporator is _{equal to} or higher than a dew point temperature T _dp measured by the dew point temperature measuring device. And a control device for controlling the operating state of the compressor.

The air heat source heat pump device of the present invention moves the adsorbent alternately between a working medium circulation circuit formed by connecting a compressor, a condenser, an expansion valve, and an evaporator via a pipe, and a dehumidification region and a regeneration region. A dry desiccant device having a dehumidification rotor, an air heat source heat pump device comprising a dew point temperature measurement device for measuring a dew point temperature of the processing air that has passed through the dehumidification region of the dehumidification rotor, and evaporation of the evaporator And a control device that controls the operating state of the compressor so that the temperature is _{equal to} or higher than the dew point temperature T _dp measured by the dew point temperature measuring device.
According to this configuration, the dew point temperature T _dp is measured, and the operation state of the compressor is controlled so that the evaporation temperature of the evaporator becomes higher than the dew point temperature T _dp . As a result, in addition to the effect of preventing frost formation by blowing dry air from the dry desiccant device to the evaporator, the evaporator can be reliably used even under conditions where the dehumidifying capacity of the dry desiccant device is insufficient due to changes in environmental temperature and humidity. The effect which can prevent frost formation of is obtained.

  The air heat source heat pump device of the present invention moves the adsorbent alternately between a working medium circulation circuit formed by connecting a compressor, a condenser, an expansion valve, and an evaporator via a pipe, and a dehumidification region and a regeneration region. A dry desiccant device provided with a dehumidification rotor, and an air heat source heat pump device comprising a secondary medium heated by the condenser, with respect to the regeneration region of the dry desiccant device, The regeneration air heated by the secondary medium is blown.

  According to this configuration, the regeneration air supplied to the regeneration region of the dry desiccant device is heated by the secondary medium heated by the condenser, so there is no need to provide a separate heater or the like for heating the regeneration air. An energy-saving air heat source heat pump device can be provided.

A water storage tank, a heating pipe connected to the condenser and connected to the low temperature water area and the high temperature water area of the water storage tank, and a hot water pipe connected to a medium temperature water area of the water storage tank, The regeneration air is preferably heated by heat exchange with the hot water pipe.
In a hot water supply device that returns cold water from a water storage tank to a water storage tank using a heat exchanger, medium temperature water in the water storage tank is not used for hot water supply. Therefore, in the present invention, the regeneration air of the dry desiccant apparatus is heated with medium-temperature water that is not used for the original hot water supply. Thereby, it is possible to realize an energy-saving air heat source heat pump device capable of heating the regenerated air without causing a problem in a hot water supply application and without providing a heater for heating the regenerated air.

The working medium circulation circuit is provided with first and second condensers, and the secondary medium is heated by the first condenser, while the regeneration air is heated by the second condenser. It can also be set as the structure made.
According to this configuration, since the regeneration air is heated using the second condenser which is a part of the working medium circulation circuit, there is no need to separately provide a heater for heating the regeneration air, and the energy-saving air heat source heat pump device. Can be realized.
By the way, in winter operation where the outside air temperature is low, the dryness of the working medium in the evaporator increases, so that the refrigerant distribution amount in the evaporator decreases compared to the summer operation. However, since the amount of the working medium enclosed is an amount that corresponds to the summer operation that requires more refrigerant, the refrigerant becomes excessive in winter. Therefore, as in the present invention, by using the second condenser for heating the regeneration air of the dry desiccant device, the refrigerant dryness in the evaporator can be reduced by reducing the refrigerant dryness at the inlet of the evaporator. While increasing, it becomes possible to store an excessive refrigerant | coolant in a 2nd condenser, and COP can be improved.

It is preferable that the regeneration air after passing through the regeneration region of the dehumidifying rotor is supplied into a room in which the condenser or the first condenser is disposed.
With such a configuration, it is possible to realize an air heat source heat pump device that can prevent frosting of the evaporator and can also humidify the room.

ADVANTAGE OF THE INVENTION According to this invention, the dry desiccant apparatus which can obtain the maximum dehumidification amount according to environmental temperature can be provided.
According to the present invention, an air heat source capable of preventing frosting of the evaporator by blowing dry air dehumidified by a dry desiccant device to the evaporator, and enabling energy saving operation by preventing performance degradation due to frosting. A heat pump device can be provided.
Also, by controlling the operating state of the compressor based on the dew point temperature of the dehumidified air blown from the dry desiccant device to the evaporator, the evaporation temperature of the working medium in the evaporator is controlled to be higher than the dew point temperature. Thus, it is possible to provide an air heat source heat pump device that can more reliably prevent frost formation.
In addition, as a heat source for heating the regenerative air of the dry desiccant device, the use of a secondary medium heat-exchanged with the condenser of the heat pump eliminates the need to separately provide the above heat source and enables energy-saving operation. An air heat source heat pump device can be provided.

The schematic block diagram of a dry-type desiccant apparatus. The graph explaining an adsorption temperature curve and inlet relative humidity. 1 is a schematic configuration diagram of an air conditioner according to a first embodiment of the present invention. The schematic block diagram of the air conditioning apparatus which concerns on the modification of 1st Embodiment. The schematic block diagram of the hot water supply apparatus which concerns on 2nd Embodiment of this invention. The schematic block diagram of the hot water supply apparatus which concerns on the modification of 2nd Embodiment. The ph diagram of the hot-water supply apparatus which concerns on the modification of 2nd Embodiment.

  Embodiments of the present invention will be described below with reference to the drawings.

(Dry desiccant equipment)
Fig.1 (a) is a figure which shows one Embodiment of the dry desiccant apparatus based on this invention, FIG.1 (b) is an A direction arrow directional view of Fig.1 (a).

  As shown in FIG. 1A, the dry desiccant device 30 includes a disc-shaped dehumidifying rotor 34, a cylindrical casing 31 having a diameter corresponding to the outer diameter of the dehumidifying rotor 34, and a casing 31. The installed air passage separation plate 38, the first motor 40 that drives the air passage separation plate 38, the second motor 43 that rotates the dehumidification rotor 34, and the desiccant control device 44 that controls the dry desiccant device 30 (air passage) Control device).

The dehumidifying rotor 34 is accommodated in the central portion of the casing 31 in the axial direction (the left-right direction in the drawing). The dehumidifying rotor 34 includes a disc-shaped adsorbent container 32 having a space inside, and a granular adsorbent 33 accommodated in the adsorbent container 32.
The adsorbent container 32 includes a cylindrical side wall member 32a and two mesh-like lid bodies 32b that are respectively attached to openings on both sides of the side wall member 32a. A shaft 35 disposed along the axial direction of the casing 31 is inserted through the center of the adsorbent container 32, and the dehumidifying rotor 34 is rotatable around the axis of the shaft 35.

  A drive belt 43b is stretched between the outer peripheral surface of the side wall member 32a of the adsorbent container 32 and the drive shaft 43a of the second motor 43, and the dehumidifying rotor 34 is transmitted via the drive belt 43b. The second motor 43 is rotationally driven around the shaft 35 by the driving force of the second motor 43. The second motor 43 is connected to the desiccant control device 44, and the rotational speed of the dehumidifying rotor 34 is controlled by controlling the rotational speed of the second motor 43 by the desiccant control device 44.

  It is preferable to use an adsorbent 33 that is granular and does not freeze even when moisture is adsorbed. As such an adsorbent, for example, mesoporous silica can be used. The mesoporous silica here refers to a porous silica material having an average pore diameter of 1.5 nm to 100 nm, and aluminum, titanium, vanadium, boron, manganese or the like may be introduced into the porous silica material.

  The mesoporous silica used for the adsorbent 33 according to the present embodiment is composed of a pure silica porous body in which pores having a pore diameter of about 1.5 nm to 3 nm occupy 70% or more of the whole and do not introduce a binder. It is preferable. By using such mesoporous silica, an adsorbent capable of maintaining adsorption performance without being frozen even when moisture is adsorbed in a low temperature range up to about −40 ° C. can be configured.

  The adsorbent 33 is accommodated in the adsorbent container 32 without using a binder. As a result, the dehumidification rotor 34 introduces the processing air (or regenerated air) into the inside from the opening (gap) of the mesh-like lid body 32 b, and the air flowing through the gaps in the granular adsorbent 33 is supplied to the adsorbent 33. By contacting, dehumidification of the processing air or regeneration of the adsorbent 33 is performed.

  In addition, the particle size of the adsorbent 33 can be appropriately selected according to a request for moisture adsorbability and air flow rate. The lid 32b of the adsorbent container 32 is set to a mesh opening width in a range where the adsorbent 33 can be prevented from falling off and a mesh opening ratio that does not hinder the air flow in the dehumidifying rotor 34. Further, the lid body 32b may be a punching metal provided with a through hole in a plate material.

The air path separation plate 38 includes four plate-like members 38 a to 38 d that reach the inner peripheral wall from the central axis (shaft 35) of the housing 31.
The plate-like members 38a and 38b are disposed on the processing air outlet side (right side in the drawing) of the dehumidifying rotor 34, and the space on the processing air outlet side of the dehumidifying rotor 34 is separated into an adsorption zone 36 (dehumidifying region) and a desorption zone 37 ( Playback area). On the other hand, the plate-like members 38c and 38d are disposed on the processing air inlet side (the left side in the figure) of the dehumidifying rotor 34, and the space on the processing air inlet side of the dehumidifying rotor 34 is separated from the adsorption zone 36 (dehumidifying region) and the desorption zone. 37 (reproduction area). As shown in FIG. 2B, the adsorption zone 36 and the desorption zone 37 partitioned by the air path separation plate 38 are respectively a sector area having an angle θ _ad and an angle θde in a side view (in the direction of arrow A). This is a fan-shaped area.

  The plate-like member 38 a and the plate-like member 38 c are provided at the same angular position around the shaft 35 and are fixed so as not to move with respect to the housing 31. On the other hand, the plate-like members 38b and 38d are connected to the shaft 35 at their long side ends and swing around the axis of the shaft 35 in a variable manner in conjunction with the rotation of the shaft 35. The shaft 35 is coupled to the drive shaft of the first motor 40, and the first motor 40 is connected to the desiccant control device 44. And the position control of the plate-shaped members 38b and 38d is made by controlling the moving angle of the 1st motor 40 by the desiccant control apparatus 44. FIG.

Temperature sensors (temperature measuring devices) are provided at the inlet and outlet of the adsorption zone 36 and the desorption zone 37, respectively. The temperature sensor 41 is provided at the inlet of the adsorption zone 36 and measures the temperature of the inlet side processing air A <b> 11 before being dehumidified by the dehumidifying rotor 34. The temperature sensor 45 is provided at the outlet of the adsorption zone 36 and measures the temperature of the outlet side processing air A12 after being dehumidified by the dehumidifying rotor 34.
The temperature sensor 42 is provided at the inlet of the desorption zone 37 and measures the temperature of the inlet side regeneration air A21 that is used for regeneration of the dehumidifying rotor 34. The temperature sensor 46 is provided at the outlet of the desorption zone 37 and measures the temperature of the outlet side regeneration air A22 after being used for regeneration of the dehumidifying rotor 34.

The desiccant control device 44 includes a temperature measurement unit 44a, a time constant calculation unit 44b, and a motor control unit 44c.
The temperature measurement unit 44 a is connected to four temperature sensors 41, 42, 45, 46 provided on the housing 31. The temperature measurement unit 44 a measures the temperature of the air flowing through the dry desiccant device 30 using the temperature sensors 41, 42, 45, 46.
The time constant calculation unit 44b is connected to the temperature measurement unit 44a and the motor control unit 44c. The time constant calculation unit 44b calculates the adsorption time constant T _ad and the desorption time constant T _de in the dehumidifying rotor 34 based on the temperature information input from the temperature measurement unit 44a. Then, the calculated adsorption time constant T _ad and desorption time constant T _de are output to the motor control unit 44c.
The motor control unit 44c, based on the adsorption time constant T _ad and the desorption time constant T _de input from the time constant calculation unit 44b, the rotation angle of the first motor 40 (that is, the partition angles θ _ad and θ _de ), The rotation speed of the second motor 43 is calculated, and the first motor 40 and the second motor 43 are driven based on the calculated rotation angle and rotation speed.

  The dry desiccant apparatus 30 having the above configuration dehumidifies the inlet side processing air A11 supplied from the outside by the adsorbent 33 of the dehumidifying rotor 34 in the adsorption zone 36 and discharges it as the dried outlet side processing air A12. Further, in the desorption zone 37, the adsorbent 33 that has absorbed moisture is regenerated by the inlet-side regeneration air A21 supplied from the outside, and the air that has absorbed moisture from the adsorbent 33 is discharged as the outlet-side regeneration air A22.

  In the dry desiccant device 30 of the present embodiment, the air path separation plate 38 is configured to have a variable angle, so that the partition angle (the size of the air path) between the adsorption zone 36 and the desorption zone 37 can be freely changed. it can. The maximum dehumidifying amount can be obtained by controlling the partition angle and the rotational speed of the dehumidifying rotor 34.

Here, FIG. 2 is a diagram showing the moisture adsorption rate of the adsorbent. FIG. 2A shows a state in which the moisture adsorption amount q [kg _{H 2 O} ] per 1 kg of the adsorbent increases with the elapse of time t [min]. In the figure, the curve G1 is a curve of the moisture adsorption amount q when the temperature of the inlet side processing air A11 is relatively high (for example, about 20 ° C.), and the curve G2 is a low temperature of the inlet side processing air A11 ( It is a curve of the amount of moisture adsorption q in the case of a minus temperature range).

As shown in FIG. 2A, the adsorption time constant T _ad2 in the curve G2 is longer than the adsorption time constant T _ad1 in the curve G1, and there is a difference of one order level between the two. Of course, as shown in adsorption isotherm diagram in FIG. 2 (b), equal inlet relative humidity [Phi ₁ in the curve G1, G2, equilibrium adsorption amount q ^* _.phi.1 is in equal conditions.
On the other hand, even in a minus temperature environment, the supplied inlet side regeneration air A21 is a relatively high temperature air, so the desorption time constant T _de2 is at the same level as the adsorption time constant T _ad1 shown in FIG. .

Therefore, when the dry desiccant device is operated in a minus temperature environment, the desiccant cycle repeats adsorption at a low temperature of 0 ° C. or less and desorption at a relatively high temperature (50 ° C.), and the adsorption operation has a very long adsorption time constant T _ad2. The desorption operation with a short desorption time constant T _de2 ( _{≈T ad1} ) is repeated. Then, when the air passages of the adsorption zone and the desorption zone have the same cross-sectional area as in the conventional dry desiccant device, the dehumidification amount is greatly reduced as compared with the case where it is used in an ambient temperature environment of about 20 ° C. End up.

On the other hand, in the dry desiccant device 30 according to the present embodiment, since the air path separation plate 38 is variable in angle, by adjusting the partition angle between the adsorption zone 36 and the desorption zone 37, the adsorption time constant T _ad prevent deterioration of the dehumidifying amount due to the difference between the desorption time constant T _de, you are possible to obtain the maximum dehumidification amount.

More specifically, in the dry desiccant device 30 of the present embodiment, the ratio between the adsorption zone passage time t _ad (dehumidification region passage time) and the desorption zone passage time t _de (regeneration region passage time) in the dehumidification rotor 34 is determined at the time of adsorption. The partition angles θ _ad and θ _de of the air path separation plate 38 of the dehumidifying rotor 34 are set by the desiccant control device 44 so as to be a value approximately proportional to the ratio between the constant T _ad and the desorption time constant T _de .

In the desiccant control device 44, temperature information at the position of each temperature sensor is collected by the temperature measurement unit 44a and output to the time constant calculation unit 44b. In the time constant calculation unit 44b, the adsorption time constant _Tad is calculated based on the temperature of the inlet side processing air A11 of the adsorption zone 36 measured by the temperature sensor 41. Further, the desorption time constant T _de is calculated based on the temperature of the inlet side regeneration air A21 in the desorption zone 37. The calculated adsorption time constant T _ad and desorption time constant T _de are output to the motor control unit 44c.

The motor control unit 44c calculates the adsorption zone passage time t _ad [min] and the desorption zone based on the input adsorption time constant T _ad and desorption time constant T _de and the following (Equation 1) or (Equation 2). The ratio of the passage time t _de [min] is set.
(Equation 1) t _ad : t _de = T _ad : T _de
(Expression 2) t _ad : t _de = T _ad / 2: T _de

In the motor control unit 44c, (Expression 1) and (Expression 2) are selected according to the ratio of the adsorption time constant T _ad and the desorption time constant T _de . In general, the ratio of the adsorption zone passage time t _ad and the desorption zone passage time t _de is equal to the ratio of the adsorption time constant T _ad and the desorption time constant T _de (Formula 1). It is preferable to set. This is because the balance between dehumidification and regeneration of the dehumidification rotor 34 can be optimized.

However, as described above, since the adsorption time constant T _ad2 in the minus temperature range is one order level longer than the adsorption time constant T _ad1 at about 20 ° C., the transit time t _ad is based on (Equation 1). and setting t _de, or beyond the movable range of the air passage separating plate 38, when the desorption operation becomes substantially impossible partitioning angles are contemplated. In this case, the amount of dehumidification is somewhat reduced, but in order to set partition angles θ _ad and θ _de that can be set, (Equation 2) is selected and partition angle calculation is executed.

The formulas that can be set in the motor control unit 44c are not limited to (Formula 1) and (Formula 2). For example, instead of (Expression 2), (Expression 3) t _ad : t _de = 2T _ad / 3: T _de or (Expression 4) t _ad : t _de = T _ad / 3: T _de is adopted. Also good.

If the adsorption zone passage time t _ad and the desorption zone passage time t _de are determined by the above calculation, the rotor rotational speed N of the dehumidification rotor 34 and the partition angle θ _ad of the air path separation plate 38 are determined based on these values. , Θ _de are determined. The rotor rotational speed N can be calculated by the following equation (Equation 5) N [rph] = 60 / (t _ad + t _de ), t _ad = T _ad (or double speed t _ad = T _ad / 2). . On the other hand, the partition angle θ _ad of the air path separation plate 38 can be calculated by the following equation (Equation 6) θ _ad [°] = t _ad / (t _ad + t _de ) × 360.

The desiccant control device 44 determines the rotation angle of the first motor 40 based on the set partition angle θ _ad and outputs a control signal to the first motor 40. The first motor 40 rotates the shaft 35 based on the control signal, and moves the plate-like members 38b and 38d to a position corresponding to the set partition angle _θad .
Further, the desiccant control device 44 outputs a control signal based on the set rotor rotational speed N to the second motor 43. The second motor 43 rotates the drive shaft 43a based on the input control signal, and rotates the dehumidification rotor 34 at the set rotor rotational speed N.

As described above in detail, the dry desiccant device 30 according to the present embodiment includes the air path separation plate 38 having a variable angle, the temperature of the inlet side processing air A11 measured by the temperature sensors 41 and 42, and the inlet side. The partition angle between the adsorption zone 36 and the desorption zone 37 is adjusted based on the temperature of the regeneration air A21. Thereby, the maximum dehumidification capability can be obtained even in an environment where the adsorption time constant _Tad of the adsorbent 33 changes greatly due to a change in the outside air temperature.

Further, the dehumidification rotor 34 includes a granular adsorbent 33 accommodated in the adsorbent container 32 without using a binder. As a result, in the temperature environment from about 0 ° C. to about −40 ° C., the dehumidification rotor 34 does not freeze even when moisture is adsorbed, and the dehumidification capacity does not decrease due to freezing.
In particular, it is important that no binder is used. Even if a hard-to-freeze adsorbent such as mesoporous silica is used for the adsorbent 33, if the adsorbent 33 is fixed to the dehumidifying rotor 34 via a binder such as silica gel, the binder may freeze and reduce the dehumidifying ability. is there.

In the above embodiment, the configuration in which the partition angles θ _ad and θ _de of the air path separation plate 38 are automatically controlled by the desiccant control device 44 has been described. However, the partition angles θ _ad and θ of the air path separation plate 38 are described. _{The de} may be manually adjusted.
In this case, for example, a table in which setting values of the partition angle θ _ad (or θ _de ) corresponding to the temperature of the inlet processing air A11 and the temperature of the inlet regeneration air A21 are prepared, and the operator Is easily set to the optimum partition angle θ _ad . The setting table of the partition angle θ _ad is calculated based on the same arithmetic expression as that of the motor control unit 44c.

In addition, when the dry desiccant device 30 is used in an environment where the temperatures of the inlet side processing air A11 and the inlet side regeneration air A21 hardly change, the partition angles θ _ad and θ _de of the air path separation plate 38 are fixed. It may be.
In this case, the partition angles θ _ad and θ _de calculated by the same arithmetic expression as the motor control unit 44c are set based on the temperature of the inlet side processing air A11 and the temperature of the inlet side regeneration air A21 during operation. Is done.

(Air heat source heat pump device)
Next, a plurality of embodiments of an air heat source heat pump device according to the present invention will be described with reference to the drawings.

[First Embodiment]
FIG. 3 is a schematic configuration diagram of an air conditioner which is the first embodiment of the air heat source heat pump device according to the present invention. In addition, the numerical value shown in the chain line frame in the figure shows the air temperature and absolute humidity in each part when the air conditioner 100 is operated at a typical environmental temperature, and the temperature of the working medium.

An air conditioner (air heat source heat pump device) 100 shown in FIG. 3 includes a heat pump 10 (working medium circulation circuit) and a dry desiccant device 30 according to the present invention.
The heat pump 10 connects an inverter-controlled compressor 11, a first condenser 12, a second condenser 13, an electronic expansion valve 14, and an evaporator 15 in order via a pipe 16, and internally. In this configuration, a working medium such as CO ₂ is enclosed. A dry desiccant device 30 is disposed between the exhaust side of the second condenser 13 and the supply side of the evaporator 15.
FIG. 3 shows the operating state of the heat pump 10 during heating operation. During the cooling operation, the first condenser 12 that is an indoor heat exchanger is an evaporator, and the evaporator 15 that is an outdoor heat exchanger is Operates as a condenser.

  The first condenser 12 is disposed in a room to be air-conditioned. The indoor return air RA exchanges heat with the first condenser 12 and becomes the indoor air supply SA. A simultaneous air supply / exhaust fan 22 is provided in the vicinity of the first condenser 12. The simultaneous air supply / exhaust fan 22 includes an air supply unit 22a and an exhaust unit 22b. The air supply unit 22 a is connected to the outlet of the desorption zone 37 of the dry desiccant device 30 via the atmosphere open end 23 and the fan 26. The exhaust part 22 b communicates with the outside air via the atmosphere open end 24. Further, the exhaust part 22 b is also connected to the inlet of the adsorption zone 36 of the dry desiccant device 30 via an exhaust damper 27.

The second condenser 13, the evaporator 15, and the dry desiccant device 30 are arranged outdoors.
The supply side of the second condenser 13 communicates with the outside air OA, and the exhaust side is connected to the inlet of the desorption zone 37 of the dry desiccant device 30. A fan 26 is provided at the outlet of the desorption zone 37 of the dry desiccant device 30. By the operation of the fan 26, the outside air OA is blown to the second condenser 13, and the outside air OA heated by exchanging heat with the second condenser 13 is supplied to the desorption zone 37 as the inlet side regeneration air A 21. The outlet side regeneration air A22 discharged from the desorption zone 37 is blown by the fan 26 to the air supply section 22a of the simultaneous supply / exhaust fan 22.

  The supply side of the evaporator 15 is connected to the outlet of the adsorption zone 36 of the dry desiccant device 30, and a fan 28 is provided on the exhaust side. Further, the inlet of the adsorption zone 36 of the dry desiccant device 30 communicates with the outside air OA. Therefore, by the operation of the fan 28 provided on the exhaust side of the evaporator 15, the outside air OA is supplied to the dry desiccant device 30 as the inlet side processing air A 11, passes through the dehumidification rotor 34, and is discharged from the outlet of the adsorption zone 36. The outlet side processing air A <b> 12 is sent to the evaporator 15. The air that has passed through the evaporator 15 is released to the atmosphere via the fan 28.

  Further, a dew point temperature sensor 20 (dew point temperature measuring device) is provided on the supply side of the evaporator 15 (exit of the adsorption zone 36), and the dew point temperature of the outlet side processing air A12 can be measured. Further, the evaporator 15 is provided with an evaporation temperature sensor 25 for measuring the temperature of the working medium conveyed from the electronic expansion valve 14.

Operation in the air conditioner 100 of the present embodiment having the above configuration will be described.
In the heat pump 10, the working medium compressed to high temperature and high pressure by the compressor 11 heats the room by the first condenser 12 disposed in the room, the working medium itself condenses and liquefies, and the second condenser 13. To be transported. In the second condenser 13, the working medium exchanges heat with the outside air OA to become a supercooled liquid, and is transferred to the evaporator 15 as a low-temperature and low-pressure (−15 ° C.) two-phase refrigerant by the electronic expansion valve 14. Then, the evaporator 15 which is an outdoor heat exchanger exchanges heat with the outlet side processing air A <b> 12 blown from the dry desiccant device 30 and returns to the compressor 11.

In the air conditioner 100 of the present embodiment, in the heat pump cycle described above, the air blown to the evaporator 15 is the outlet side processing air A12 that is discharged from the adsorption zone 36 of the dry desiccant device 30. That is, the dry air dehumidified by the dehumidifying rotor 34 of the dry desiccant device 30 is blown to the evaporator 15. For example, in the example shown in FIG. 3, the inlet side processing air A11 (humidity 1.7 g / kgDA) of the adsorption zone 36 passes through the dehumidifying rotor 34 and the outlet side processing air A12 (humidity 1.2 g / kgDA, air dew point temperature). −15 ° C.) and then blown to the evaporator 15.
Thereby, even in a temperature environment of 0 ° C. or lower, the evaporator 15 is not frosted, and an air conditioner that does not cause a decrease in capacity due to frosting can be realized.

Further, in the present embodiment, the dew point temperature T _dp of the outlet side processing air A12 is observed by the dew point temperature sensor 20 provided on the supply side of the evaporator 15, and the evaporation temperature ET in the evaporator 15 is determined by the evaporation temperature sensor 25. Observe and control the operating state of the compressor 11 based on the dew point temperature _Tdp and the evaporation temperature ET. That is, the compressor 11 is operated by lowering the inverter frequency of the compressor 11 so that the evaporation temperature ET is always higher than the dew point temperature _Tdp .
Thereby, even under the situation where the dehumidifying capacity of the dry desiccant device 30 is insufficient, frosting of the evaporator 15 can be reliably prevented.

Further, in this embodiment, the outside air OA heated by the second condenser 13 and having a reduced relative humidity is supplied as the inlet side regeneration air A21 to the desorption zone 37 of the dry desiccant device 30, so that the dehumidification rotor 34 is regenerated. There is no need to provide a separate high-temperature heat source, and energy-saving operation is possible.
Further, the high-temperature and high-humidity outlet-side regeneration air A22 used for the desorption regeneration of the dehumidifying rotor 34 is sent to the air supply section 22a of the indoor simultaneous air supply / exhaust fan 22 by the fan 26 and used for indoor humidification. . Thereby, the air conditioning quality can be improved particularly in the winter season when the room is easily dried.
An air release end 23 is provided between the air supply unit 22a of the simultaneous supply / exhaust fan 22 and the fan 26, and the difference between the air flow rate by the fan 26 and the air flow rate of the air supply unit 22a is automatically adjusted. Is done.

  The exhaust section 22 b of the simultaneous supply / exhaust fan 22 communicates with the outside air at the atmosphere open end 24 and is connected to the inlet of the adsorption zone 36 of the dry desiccant device 30 via the exhaust damper 27. The exhaust damper 27 opens to return the indoor air exhausted from the exhaust part 22b to the dry desiccant device 30 when humidity recovery from the room is necessary. On the other hand, when the humidity recovery from the room is not required, the exhaust damper 27 is closed and the exhaust of the exhaust part 22b is released from the atmosphere open end 24 to the atmosphere.

  Moreover, COP in the air conditioner 100 of 1st Embodiment was computed based on the parameter shown below. As shown below, a high COP can be obtained in both the heating operation and the cooling operation.

(Heating operation)
Outside temperature: -7 ° C to 16 ° C
Heat pump evaporation temperature: -15 ° C to 6 ° C
Heat pump condensation temperature: 50 ° C
COP: 2.4-4.3

(Cooling operation)
Outside temperature: 24 ° C to 35 ° C
Heat pump evaporation temperature: 14-25 ° C
Heat pump condensation temperature: 39 ° C-50 ° C
COP: 5.9 to 7.3

Moreover, the air conditioner 100 of 1st Embodiment and the conventional air conditioner were also compared. The conventional air conditioner used as a comparison object is obtained by omitting the dry desiccant device from the air conditioner 100. Therefore, in the conventional air conditioner, in the operation in the minus temperature range, the capacity is reduced due to the frost formation of the evaporator.
Table 1 compares the COPs of the conventional air conditioner and the air conditioner 100 according to the present invention. As shown in Table 1, in the air conditioner 100 of this embodiment that includes the dry desiccant device 30 and enables non-frost operation, the COP can be greatly improved as compared with the conventional air conditioner.

[Modification]
Next, a modification of the first embodiment will be described with reference to FIG.
FIG. 4 is a diagram illustrating a schematic configuration of an air conditioner 100A according to a modification.

  The air conditioner 100A includes a heat pump 10A in which a connection path of devices is changed instead of the heat pump 10 in the air conditioner 100 shown in FIG. 4, the same reference numerals are given to the same components as those in FIG. 3, and detailed description thereof will be omitted.

The heat pump 10A has a structure in which a compressor 11, a first condenser 12, a second condenser 13, an electronic expansion valve 14, and an evaporator 15 are connected via a pipe 16 enclosing a working medium. It is. The equipment configuration of the heat pump 10A is the same as that of the heat pump 10 in FIG. 3, but the connection order of the equipment is different.
Specifically, after the working medium sent out from the compressor 11 is transported in the order of the second condenser 13 and the first condenser 12 and used for indoor heating in the first condenser 13. The electronic expansion valve 14 and the evaporator 15 are sequentially conveyed.

  With such a configuration, the second condenser 13 is supplied with a working medium having a higher temperature than in the case of the first embodiment, so that the inlet side regeneration air A21 of the dry desiccant device 30 is heated to a higher temperature. can do. Therefore, the regeneration capability of the dehumidifying rotor 34 in the dry desiccant device 30 is improved, and a wider adsorption zone 36 can be secured. Therefore, the amount of dehumidification by the dry desiccant device 30 is increased, and frost formation in the evaporator 15 can be more reliably prevented.

[Second Embodiment]
FIG. 5 is a schematic configuration diagram of a hot water supply apparatus which is the second embodiment of the air heat source heat pump apparatus of the present invention. In addition, the numerical value shown in the chain line frame in the figure indicates the air temperature and absolute humidity, the temperature of the working medium, and the temperature of hot water when the hot water supply device 200 is operated at a typical environmental temperature. It is a thing.

A hot water supply apparatus 200 shown in FIG. 5 includes a heat pump 50 (working medium circulation circuit), a water storage tank 62, and a dry desiccant apparatus 30 according to the present invention.
The heat pump 50 includes an inverter-controlled compressor 51, a gas cooler 52 (condenser), an electronic expansion valve 53, and an evaporator 54. A dew point temperature sensor 64 is provided on the supply side of the evaporator 54. Further, an evaporation temperature sensor 65 that measures the temperature of the working medium flowing into the evaporator 54 is provided.

  A heating pipe 67 that circulates water from the low temperature water region 62c to the high temperature water region 62a is connected to the water storage tank 62. The pump 64 and the gas cooler 52 are connected to the heating pipe 67 in order from the low temperature water region 62c side. The cold water conveyed by the pump 64 exchanges heat with the working medium of the heat pump 50 in the gas cooler 52, becomes hot water, and is returned to the high-temperature water region 62 a of the water storage tank 62.

  Further, a hot water pipe 68 for circulating the water in the intermediate hot water region 62b to the outside is connected to the intermediate hot water region 62b of the water storage tank 62. A pump 65 and a heat exchanger 63 are provided in the path of the hot water pipe 68, and medium hot water is pumped into the hot water pipe 68 by the pump 65.

  The inlet of the adsorption zone 36 of the dry desiccant device 30 communicates with the outside air OA, and the outlet of the adsorption zone 36 is connected to the supply side of the evaporator 54. The fan 55 provided on the exhaust side of the evaporator 54 introduces the outside air OA into the adsorption zone 36 as the inlet side processing air A11, and the outlet side processing air dehumidified by the dehumidifying rotor 34 is blown to the evaporator 54. .

  A heat exchanger 63 through which medium-temperature water is circulated is provided at the inlet of the desorption zone 37 of the dry desiccant device 30, and a fan 66 is provided at the outlet of the desorption zone 37. The outside air OA is blown to the heat exchanger 63 by the fan 66, and the air warmed by heat exchange with the heat exchanger 63 is introduced into the desorption zone 37 as the inlet side regeneration air A21. The outlet side regeneration air A22 after being used for regeneration of the dehumidifying rotor 34 is released to the atmosphere by the fan 66.

  In the hot water supply apparatus 200 of the present embodiment having the above configuration, the air blown to the evaporator 54 is dry air discharged from the dry desiccant apparatus 30. That is, the outlet side processing air A12 that is the outside air OA that has been dried by adsorbing moisture in the adsorption zone 36 of the dry desiccant device 30 is blown to the evaporator 54. Thereby, the frost formation of the evaporator 54 at the time of winter use can be prevented, and the capability fall of the heat pump 50 by frost formation can be prevented.

Further, in the present embodiment, the dew point temperature T _dp of the outlet side processing air A12 blown to the evaporator 54 by the dew point temperature sensor 64 is measured, and the evaporation temperature ET in the evaporator 54 is measured by the evaporation temperature sensor 65. ing. The operating state of the compressor 51 is controlled based on the dew point temperature _Tdp and the evaporation temperature ET. That is, the compressor 51 is operated by lowering the inverter frequency of the compressor 51 so that the evaporation temperature ET is always higher than the dew point temperature _Tdp .
Thereby, even under a situation where the dehumidifying capacity of the dry desiccant device 30 is insufficient, frosting of the evaporator 54 can be reliably prevented.

  Further, in the present embodiment, the inlet side regeneration air A21 of the dry desiccant device 30 uses the intermediate temperature water supplied from the intermediate temperature water region of the water storage tank 62 to raise the temperature of the outside air OA by the heat exchanger 63, and to increase the relative humidity. In the lowered state, it is supplied to the desorption zone 37 of the dry desiccant device 30. Thereby, the relative humidity of the inlet side regeneration air A21 of the dry desiccant device 30 can be reduced without providing a separate heater or the like, and the dehumidification rotor can be efficiently regenerated. Further, the medium temperature water of the water storage tank 62 is not used for hot water supply, and since it is used, the operation of the hot water supply apparatus 200 is not adversely affected.

  Moreover, when COP in the hot water supply apparatus 200 of 2nd Embodiment was calculated based on the parameter shown below, it was confirmed that high COP is obtained as shown below.

Outside temperature: -7 ° C to 35 ° C
Heat pump evaporation temperature: -15 ° C to 15 ° C
Gas cooler inlet temperature: 90 ° C
COP: 4.3 to 6.0

Moreover, the hot water supply apparatus 200 of 2nd Embodiment and the conventional hot water supply apparatus were also compared. The conventional hot water supply apparatus as a comparison object is obtained by omitting the dry desiccant apparatus from the hot water supply apparatus 200. Therefore, in the conventional hot water supply apparatus, in the operation in the minus temperature range, the capacity is reduced due to frosting of the evaporator.
Table 2 compares the COPs of the conventional hot water supply apparatus and the hot water supply apparatus 200 according to the present invention. As shown in Table 2, the hot water supply apparatus 200 of the present embodiment provided with the dry desiccant apparatus 30 and capable of non-frost operation can obtain a higher COP than the conventional hot water supply apparatus.

[Modification]
FIG. 6 is a diagram illustrating a modification of the hot water supply device according to the second embodiment. A hot water heater 200 </ b> A shown in FIG. 6 includes a heat exchanger as a regeneration desorption heat source of the dry desiccant device 30.

As shown in FIG. 6, the hot water supply device 200 </ b> A includes a heat pump 50 </ b> A (working medium circulation circuit), a water storage tank 62, and a dry desiccant device 30.
The heat pump 50 </ b> A includes a compressor 51, a gas cooler 521 (first condenser), a heat exchanger 522 (second condenser), an electronic expansion valve 53, and an evaporator 54. In the vicinity of the evaporator 54, a dew point temperature sensor 64 and an evaporation temperature sensor 65 are provided.

  The water storage tank 62 is connected to the gas cooler 521 through a heating pipe 67. Cold water is supplied from the low temperature water region 62c to the gas cooler 521 by the pump 64, and the hot water produced by heat exchange with the gas cooler 521 is returned to the high temperature water region 62a.

The outside air OA is supplied to the adsorption zone 36 of the dry desiccant device 30 as the inlet side processing air A11 by the operation of the fan 55, and the outlet side processing air A12 that has become the dry air by the dehumidifying rotor 34 is blown to the evaporator 54. Is done.
On the other hand, a heat exchanger 522 is disposed at the inlet of the desorption zone 37 of the dry desiccant device 30. By the operation of the fan 66, the outside air OA is blown to the heat exchanger 522, and the air warmed by the heat exchange with the heat exchanger 522 is supplied to the desorption zone 37 as the inlet side regeneration air A21. The outlet side regeneration air A22 after being used for regeneration of the dehumidifying rotor 34 is released to the atmosphere by the fan 66.

Thus, in the hot water supply apparatus 200 </ b> A according to the modification, the heat exchanger 522 is disposed at the subsequent stage of the gas cooler 521. By heating the outside air OA by the heat exchanger 522 that is a part of the heat pump 50A and supplying it to the dry desiccant device 30, there is no need to provide a heater or the like for heating the regeneration air A21 on the inlet side, and energy saving operation is possible. become.
Note that the position of the heat exchanger 522 is not limited to the subsequent stage of the gas cooler 521, and it depends on the characteristics of the adsorbent 33 and the like between the compressor 51 and the expansion valve 53 in which the gas cooler 521 is disposed. Any position between can be selected. For example, the heat exchanger 522 may be disposed in front of the gas cooler 521. Alternatively, the gas cooler 521 may be divided into a plurality of parts and disposed between the divided gas coolers 521.

Furthermore, the heat exchanger 522 also functions as a refrigerant storage unit in winter. This is because the heat exchanger 522 exchanges heat with the outside air OA in winter, which is cooler than the water temperature in the low temperature water region 62c in the water storage tank 62, so that the high-pressure CO ₂ reaches the temperature of the outside air OA (5 ° C. or less). This is because the refrigerant can be cooled. This refrigerant storage function will be described in more detail with reference to FIG.

FIG. 7 is a ph diagram of the CO ₂ refrigerant (working medium), showing the refrigerant operating points during (a) summer operation and (b) winter operation.
In the supercritical refrigerant circuit on the gas cooler 521 side, the refrigerant temperature changes from 20 ° C. to 90 ° C. with a constant pressure. Therefore, the operating pressure and temperature state of the first gas cooler 521 hardly change between summer and winter, as can be seen from the cold water boiling temperature (15 ° C. to 90 ° C.).

On the other hand, the pressure and temperature on the evaporator 54 side are completely different in summer and winter. In summer, the outside air temperature at the entrance of the evaporator 54 is about 30 ° C., and the refrigerant evaporation temperature is about 15 ° C. On the other hand, in winter, since the outside air temperature is about 5 ° C., the refrigerant evaporation temperature is about −10 ° C. Accordingly, the operating pressure P _e2 in the winter evaporator 54 shown in FIG. 7B is lower than the summer operating pressure P _e1 shown in FIG. Therefore, the dryness of the refrigerant in the evaporator 54 inlet is greater than the dryness fraction x _e1 it is summer winter dryness fraction x _e2, the refrigerant distribution amount in the evaporator 54 towards the winter is less than in summer.

And since the amount of initial stage refrigerant | coolants enclosed in a refrigerant circuit is made into the quantity match | combined at the time of the summer driving | operation which requires more refrigerant | coolants amount, a refrigerant | coolant will be in an excessive state in winter. In this regard, the hot water supply apparatus 200A according to the modification includes the heat exchanger 522, and the inlet side regenerative air A21 supplied to the desorption zone of the dry desiccant apparatus 30 during the winter operation in which the evaporator 54 is prone to frost. A heat exchanger 522 is used for heating. Thus, as indicated by the broken line in FIG. 6 (b), the dryness of the inlet of the evaporator 54 during winter operation, can be a dryness fraction x _e3 lower than in summer dryness fraction x _e1. Thereby, much refrigerant | coolant can be stored in the evaporator 54 also in winter.
Therefore, according to the hot water supply apparatus 200A according to the modified example, surplus refrigerant generated in winter can be accumulated in the heat exchanger 522 and the evaporator 54, and high COP operation is possible.

  30 dry desiccant device, 100, 100A air conditioner (air heat source heat pump device), 200, 200A hot water supply device (air heat source heat pump device), 10, 10A, 50, 50A heat pump (working medium circulation circuit), 11, 51 compressor, 12 First condenser, 13 Second condenser, 14, 53 Electronic expansion valve, 15, 54 Evaporator, 20, 64 Dew point temperature sensor (dew point temperature measuring device), 22 Simultaneous supply / exhaust fan, 25, 65 Evaporation Temperature sensor, 31 housing, 32 adsorbent container, 32b lid (panel surface), 33 adsorbent, 34 dehumidification rotor, 36 adsorption zone (dehumidification area), 37 desorption zone (regeneration area), 38 air path separation plate (wind) (Path separation member), 41, 42, 45, 46 temperature sensor (temperature measurement device), 44 desiccant control device (airway control device), 52 gas Cooler (condenser), 62 water storage tank, 62a high temperature water region, 62b medium temperature water region, 62c low temperature water region, 67 heating piping, 68 hot water piping, 521 gas cooler (first condenser), 522 heat exchanger (first 2 condenser), A11 inlet side processing air, A12 outlet side processing air, A21 inlet side regeneration air, A22 outlet side regeneration air

Claims (7)

A dry-type desiccant device having a working medium circulation circuit in which a compressor, a condenser, an expansion valve, and an evaporator are connected via a pipe; and a dehumidifying rotor that moves an adsorbent alternately between a dehumidifying region and a regeneration region; An air heat source heat pump device comprising:
The air heat source heat pump device, wherein the adsorbent of the dry desiccant device is mesoporous silica having a pore size that does not freeze. A dry-type desiccant device having a working medium circulation circuit in which a compressor, a condenser, an expansion valve, and an evaporator are connected via a pipe; and a dehumidifying rotor that moves an adsorbent alternately between a dehumidifying region and a regeneration region; An air heat source heat pump device comprising:
A dew point temperature measuring device that measures the dew point temperature of the processing air that has passed through the dehumidifying region of the dehumidifying rotor;
A control device for controlling an operating state of the compressor so that an evaporation temperature of the evaporator is _{equal to} or higher than a dew point temperature T _dp measured by the dew point temperature measuring device;
An air heat source heat pump device comprising: A dry-type desiccant device having a working medium circulation circuit in which a compressor, a condenser, an expansion valve, and an evaporator are connected via a pipe; and a dehumidifying rotor that moves an adsorbent alternately between a dehumidifying region and a regeneration region; An air heat source heat pump device comprising:
Having a secondary medium heated by the condenser;
An air heat source heat pump device, wherein the regeneration air heated by the secondary medium is blown to the regeneration region of the dry desiccant device. A dew point temperature measuring device that measures the dew point temperature of the processing air that has passed through the dehumidifying region of the dehumidifying rotor;
A control device for controlling an operating state of the compressor so that an evaporation temperature of the evaporator is _{equal to} or higher than a dew point temperature T _dp measured by the dew point temperature measuring device;
The air heat source heat pump device according to claim 1, comprising: A water storage tank, a heating pipe connected to the condenser and connected to the low temperature water area and the high temperature water area of the water storage tank, and a hot water pipe connected to a medium temperature water area of the water storage tank,
The air heat source heat pump device according to claim 3, wherein the regeneration air is heated by heat exchange with the hot water pipe. The working medium circulation circuit is provided with the first and second condensers;
The air heat source heat pump device according to claim 3, wherein the secondary medium is heated by the first condenser, and the regeneration air is heated by the second condenser.   The regeneration air after passing through the regeneration region of the dehumidifying rotor is supplied to a room in which the condenser or the first condenser is disposed. The air heat source heat pump device according to Item 1.

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