JP2710552B2 - Thermal storage type air conditioner - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention cools or heats a heat storage agent in a heat storage using a time period of low power consumption, and uses the heat stored in the heat storage agent as a cooling heat source or a heating heat source. The present invention relates to a heat storage type air conditioner.

[0002]

2. Description of the Related Art Conventionally, a regenerative air conditioner of this type is shown in FIG.

[0003] This regenerative air conditioner includes a compressor 50,
It has a cooling circuit sequentially connected to the condenser 51, the expansion valve 52, and the brine heat exchanger 53, and the refrigerant flows from the compressor 50 to the condenser 5.
1 → expansion valve 52 → brine heat exchanger 53 → compressor 50 in order (solid arrows). In addition, it has a brine circuit in which the brine heat exchanger 53, the regenerator 54, the air-conditioning heat exchanger 55, and the pump 56 are sequentially connected, and the brine is supplied from the pump 56 → the brine heat exchanger 53 → the regenerator 54 → heat for air conditioning. It circulates sequentially from the exchanger 55 to the pump 56 (dotted line arrow).

In this heat storage type air conditioner, when performing the heat storage operation, both the cooling circuit and the brine circuit are operated. Thereby, heat is exchanged between the refrigerant of the cooling circuit and the brine of the brine circuit in the brine heat exchanger 53,
The heat storage agent 54a having a low heat storage temperature in the heat storage 54 is cooled and heat is stored (in this operation, the air-conditioning heat exchanger 55
Of the blower 55a is stopped. ). On the other hand, when performing the cooling operation, only the brine circuit is operated and the blower 55a is driven. As a result, the brine is cooled by the heat storage agent 54a in the heat storage unit 54, the cooled brine is heat-exchanged by the air-conditioning heat exchanger 55, and low-temperature air is blown into the room.

On the other hand, when performing a heating operation, the brine heat exchanger 53 is made to function as a condenser, and the condenser 51 is replaced with an evaporator, while the heat storage agent 5 in the regenerator 54 is used.
As 4a, one having a high heat storage temperature is used. In this configuration, when the refrigerant in the cooling circuit is caused to flow backward, the heat storage agent 5
4a is heated and can be used as a heating heat source. Even when the cooling circuit constitutes a cooling circuit (a circuit in which the brine heat exchanger 53 functions as an evaporator), a heating operation can be performed by adding a heating device to the brine circuit. .

[0006]

As described above, in the conventional thermal storage type air conditioner, when performing the thermal storage operation for cooling, the brine is once cooled and the thermal storage agent 54a is cooled by the cooled brine. When performing indoor cooling, the brine is cooled by the heat storage agent 54a.

[0007] However, this regenerative air conditioner has a problem that the cooling loss increases because all operations are indirectly cooled through brine. In addition, this brine circuit increases the number of devices such as pumps and the size of the entire device, and is disadvantageous in terms of weight and installation space.

As described above, there are various problems during the heat storage operation, but there are also various problems during the cooling operation. That is, since the heat storage amount of the heat storage agent 54a gradually decreases as the cooling operation time elapses, the blowout temperature is very low at the beginning of the operation, and the air conditioner is too cold. There is a problem that the state becomes insufficient.

The cooling load varies with the outside air temperature. Generally, the load is small around 8:00 to 9:00 during working hours, reaches its peak at around 14:00, and reaches 17 hours after the end of working. At times, the load is reduced again. Therefore, it is necessary to change the cooling operation so as to correspond to the change in the cooling load, but there is a problem that the conventional regenerative air conditioner cannot sufficiently cope with the change.

As described above, various problems of the conventional regenerative air-conditioning apparatus for cooling have been described. However, the regenerative air-conditioning apparatus for heating also has the same problem.

That is, in the heating operation, there is a possibility that heating will be excessive at the beginning of working hours, insufficient heating will occur at the end of working hours, and the heating load will change following the outside air temperature. However, there is a problem that it cannot cope sufficiently.

SUMMARY OF THE INVENTION In view of the above-mentioned conventional problems, an object of the present invention is to efficiently store heat in a heat storage agent during a heat storage operation, to prevent excessive cooling / heating and insufficient cooling / heating during a cooling / heating operation,
An object of the present invention is to provide a lightweight and compact regenerative air conditioner that can cope with indoor cooling and heating loads.

[0013]

According to the present invention, in order to achieve the above object, a first aspect of the present invention is to store a heat storage agent having a low heat storage temperature in a heat storage chamber. While the air outlet is closed to cool the heat storage agent by the cooling device, during cooling, the air inlet and the air outlet are opened, the room air is sucked into the refrigerator by a blower, heat exchange with the heat storage agent is performed, and the air is blown into the room. In the heat storage type air conditioner, a plurality of heat exchange plates provided with refrigerant pipes of the cooling device are arranged facing each other at a predetermined interval, and a plurality of the heat storage agents are interposed between the heat exchange plates. Features.

According to a second aspect of the present invention, in the regenerative air conditioner according to the first aspect, the refrigerant tube of the cooling device is provided in a meandering manner on a heat exchange plate, and the heat storage agent is provided between adjacent refrigerant tubes. Are formed at predetermined intervals.

[0015] The invention of claim 3 is claim 1 or claim 2.
In the regenerative air conditioner according to the, the cooling device,
A refrigerant refrigerator configured to circulate the refrigerant sequentially through a compressor, a condenser, an expansion means, and a heat exchange plate, and a drain tank for storing drain water from the heat storage, and supplying the drain water to the condenser side. It is characterized by having a pump for feeding and a sprinkler for sprinkling drain water pumped by the pump to the condenser.

According to a fourth aspect of the present invention, a heat storage agent having a high heat storage temperature is stored in a heat storage chamber, and at the time of heat storage, the lower suction port and the upper outlet port are closed to heat the heat storage agent by a heating device. In a regenerative air conditioner that opens the air inlet and the air outlet during heating, blows room air into a refrigerator with a blower, exchanges heat with the heat storage agent, and blows the indoor air, the heat exchange provided with the heating device is provided. A plurality of plates are arranged facing each other at a predetermined interval, and a plurality of the heat storage agents are interposed between the heat exchange plates.

The invention according to claim 5 is the invention according to claims 1 to 4.
In the heat storage type air conditioner according to the present invention, a heat storage chamber in which a heat exchange plate in which the heat storage agent is interposed is arranged in the heat storage chamber, and one end faces the suction port from a lower part of the heat storage chamber,
A bypass passage having the other end facing the outlet and an upper opening of the heat storage chamber, an air hole communicating the heat storage chamber and the bypass passage closer to an upper part in the heat storage, a flow area of the bypass passage, An air mix damper that controls opening and closing of the air holes so as to contradict each other, wherein the blower is installed in the bypass passage between a portion of the air hole and a portion of an upper opening of the heat storage chamber. It is characterized by having done.

The invention according to claim 6 is the invention according to claims 1 to 5
In the regenerative air conditioner according to the above, an intake temperature sensor for detecting the temperature of the intake air, an outlet temperature sensor for detecting the temperature of the outlet air, and an arithmetic operation for calculating a temperature difference between the detected temperatures detected by the temperature sensors. Means, and an opening control means for controlling the opening of the air mix damper based on the temperature difference.

The invention according to claim 7 is the invention according to claims 1 to 6.
In the regenerative air conditioner according to the above, an opening control means for controlling an opening of the air mix damper in accordance with a cooling / heating operation time is provided.

[0020]

According to the first aspect of the present invention, a plurality of heat exchange plates provided with refrigerant pipes of the cooling device are arranged facing each other at a predetermined interval, and a plurality of heat storage agents are interposed between the heat exchange plates. Therefore, the heat storage agent is directly cooled through the heat exchange plate, so that the cooling efficiency of the heat storage agent is improved, and the time lag of the heat storage expiration time of each heat storage agent can be prevented.

According to the second aspect of the present invention, the entire heat exchange plate is uniformly cooled, and the contact area between the heat storage agent and the heat exchange plate is increased by the recess for accommodating the heat storage agent, so that the heat storage agent is efficiently used. Cools well.

According to the third aspect of the present invention, since the drain water in the heat storage is pumped up by the pump and sprayed to the condenser through the water spray device, the heat exchange efficiency of the condenser is improved as compared with the case of simply exchanging heat with room air. In addition, drain water drainage becomes unnecessary.

According to the fourth aspect of the present invention, a plurality of heat exchange plates provided with a heating device are arranged facing each other at a predetermined interval, and a plurality of heat storage agents are interposed between the heat exchange plates. In addition, the heat storage agent is directly heated through the heat exchange plate, so that the heating efficiency of the heat storage agent is improved, and the time lag of the heat storage expiration time of each heat storage agent can be prevented.

According to the fifth aspect of the present invention, during cooling and heating, of the room air flowing into the heat storage chamber from the suction port, the amount of air flowing through the heat storage chamber to the bypass passage through the upper air hole, The flow rate of the air flowing from the lower end to the bypass passage can be controlled by the air mix damper.

Here, the air flowing from one end of the bypass passage to the bypass passage has a small amount of heat exchange with the heat storage agent, while the air flowing through the heat storage chamber to the air hole has a large heat exchange amount with the heat storage agent. ing.

Therefore, the temperature of the blown air in which the two airs are mixed can be arbitrarily set by controlling the opening and closing of the air mix damper.

According to the sixth aspect of the present invention, since the air mix damper can be controlled based on the temperature difference between the temperature of the intake air and the temperature of the blown air, the temperature of the blown air can be controlled so as to have a predetermined temperature difference. Large fluctuations in room temperature can be prevented.

According to the seventh aspect of the present invention, the blown air temperature can be controlled so as to correspond to the cooling / heating load during working hours.

[0029]

1 to 17 show a first embodiment of a regenerative air conditioner according to the present invention. In this embodiment, this regenerative air conditioner for cooling is shown. here,
FIG. 1 is a front view of a heat storage type air conditioner, and FIG. 2 is a side sectional view of the heat storage type air conditioner.

The regenerative air conditioner 1 has a vertically long box-shaped regenerator 2 formed of heat insulating walls. The lower portion of a front wall 2a of the regenerator 2 has an inlet 3 and an upper portion has an outlet. 4 are provided, and the room air is taken into the heat storage chamber 2 from the suction port 3, and the taken air is blown into the room again through the outlet 4.

The heat storage chamber 2 has a heat storage chamber 5 containing a spherical heat storage agent A, and a suction door 7 housed in a door box 6 is installed behind the suction port 3. The inlet 3 is opened and closed by the door 7. In the heat storage chamber 5, a plurality of heat exchange plates 8 constituting a plate type evaporator of a refrigerant refrigerator are installed over almost the entirety. The heat exchange plates 8 cool the heat storage agent A. Then, heat is stored in the heat storage agent A. In addition to the heat exchange plate 8, the refrigerator includes a compressor 9, a condenser 10, which is installed on an upper wall 2 b of the heat storage 2.
An expansion valve 11 and a blower 12 for a condenser are provided, and the refrigerant is compressed by a compressor 9 → a condenser 10 → an expansion valve 11 → a heat exchange plate 8.
→ The refrigerant is circulated sequentially with the compressor 9, and is cooled by the heat of vaporization of the refrigerant passing through the heat exchange plate 8.

The heat storage chamber 5 and the upper wall 2 of the heat storage 2
A bypass passage 14 is formed between b and the rear wall 2c via a partition wall 13. The bypass passage 14 has a lower end opening 14 a through the lower part of the heat storage chamber 5 and the suction port 3.
The upper end opening 14b communicates with the outlet 4. Here, the upper portion of the partition 13 has a mountain shape, and the upper opening 5a of the heat storage chamber 5 that connects the bypass passage 14 and the heat storage chamber 5 is provided on the outlet 4 side of the mountain-shaped partition 13,
An air hole 15 is also provided on the side of the back wall 2c of the chevron-shaped partition wall 13 to allow the bypass passage 14 and the heat storage chamber 5 to communicate with each other. In addition, at the upper end side of the bypass passage 14, the outlet door 1 for selectively opening and closing the outlet 4 and the upper opening 5a is provided.
6 and an air mix damper 17 that opens and closes the air hole 15. A blower 18 is installed in the bypass passage 14 between the air hole 15 and the upper opening 5a, and circulates indoor air as shown by a two-dot chain line arrow in FIG. When cooling the heat storage chamber 5, drain water is generated in the heat storage chamber 5,
This drain water is stored in a drain tank 19 installed below the lower surface wall 2d.

The schematic configuration of the regenerative air conditioner 1 according to the present embodiment is as described above, and the configuration of each part thereof will be described in further detail below. First, the structure of the heat exchange plate 8 and the arrangement structure of the heat storage agent A will be described with reference to FIGS. 2, 3, and 4A and 4B. Here, FIG. 3 is an assembled perspective view of the heat exchange plate 8 and the heat storage agent A, FIG. 4A is a side sectional view of the heat exchange plate 8 and the heat storage agent A, and FIG. 2 is a cross-sectional plan view of a heat storage agent A. FIG.

As shown in FIG. 4, the heat exchange plate 8 is obtained by rolling and bonding two plates having good heat exchange.
A refrigerant pipe 81 as shown in FIG. 4B is formed between the plates. Further, as shown in FIG. 2, the refrigerant pipe 81 is formed to meander up and down.
Between them, a storage recess 82 for the heat storage agent A shown in FIGS. 3 and 4 is formed. The storage recess 82 is formed in a spherical shape so that the inner surface thereof corresponds to the outer surface of the heat storage agent A, and increases the contact area between the heat storage agent A and the heat exchange plate 8.
A rolling absorbing hole 82a is formed in the hole 82, and the rolling absorbing hole 82a absorbs the distortion at the time of press-molding the housing recess 82.
In addition, since the dimensional error becomes large on both the upper and lower sides of the heat exchange plate 8 due to the rolling of the heat exchange plate 8 and the press molding of the housing recess 82, the refrigerant pipes located on both sides of the heat exchange plate 8 are formed. The accommodation recess 82 is not formed outside the hairpin 81 a of the refrigerant pipe 81.
1 is prevented beforehand.

When the heat storage agent A is interposed between the two heat exchange plates 8 configured as described above, the heat exchange plates 8 are opposed to each other as shown in FIG. The heat storage agent A is interposed in the accommodating concave portion 82 of the plate 8, and thereafter, the heat exchange plates 8 are fastened with the screws 83. A large number of the heat exchange plates 8 configured as described above are arranged in the heat storage chamber 5 as shown in FIG. Here, the heat storage agent A is obtained by injecting water (main component) A2 containing a supercooling inhibitor into a hollow spherical resin body A1,
The one with low heat storage temperature is used.

Next, the opening / closing structure of the suction door 7 and the outlet door 16 will be described with reference to FIGS. Here, FIG.
Is a perspective view of the suction door 7 and the outlet door 16, FIG. 6 is a front view of the suction door 7 and the outlet door 16, and FIG. 7 is a side view of the inlet door 7 and the outlet door 16.

The suction door 7 has a horizontally long door body 70 that covers the suction port 3, and the door body 70 is supported by a bracket 72 having a rotating shaft 71 and a rotating arm 73. The rotating arm 73 includes the door body 70 and the rotating shaft 7.
1 and rotates the door body 70 in the vertical direction with the rotation of the rotating shaft 71.

On the other hand, the outlet door 16 has a horizontally long door body 160 that covers the outlet 4, and is supported by a bracket 162 and a rotary arm 163 on which a rotary shaft 161 is mounted, similarly to the suction door 7. The bracket 162 is provided with a reversible first motor 164. An output shaft 164 a of the first motor 164 has a cam 1 for switching.
65 and the rotating arm 166 are connected. A rotating roller 167 is rotatably fixed to the tip of the rotating arm 166, while an operating rod 168 having a substantially U-shaped cross section is
1, the lower end of which is fixed to the operating roller 1
68 is slidably fitted inside. As a result, the rotational force of the first motor 164 is transmitted to the rotating shaft 161 through the rotating arm 166, the rotating roller 167, and the operating rod 168, and the door body 160 fixed to the rotating shaft 161 rotates. When the first motor 164 is driven, the cam 165 rotates accordingly, and the first micro switch 169 provided below the cam 165 is turned on / off. The first micro switch 169 is connected to the door body 160
Is turned on when it enters a closed state and a maximum open state.

The suction door 7 and the outlet door 16 thus configured are connected to each other by the connecting member 20. The connecting member 20 is provided with a rotating arm 200 fixed to the rotating shaft 71 of the suction door 7, a fixed roller 201 fixed to the rotating shaft 161 of the blowout door 16, and installed between the rotating arm 200 and the fixed roller 201. And a connecting wire 203. In addition, while the upper end of the connecting wire 203 is connected to the fixed roller 201 and the lower end thereof is connected to the tip of the rotating arm 200, the middle thereof is guided by the guide roller 202, and the rotating shaft 161 moves in the opening direction of the blowing door 16. When rotating, this connecting wire 203
To rotate the rotating shaft 71 in the opening direction of the suction door 7 through
Conversely, when the blowout door 16 rotates in the closing direction,
The suction door 7 rotates in the closing direction.

Next, the structure of the air mix damper 17 will be described with reference to FIGS. Here, FIG. 8 is a front view of the air mix damper 17, FIG. 9 is a side sectional view of the air mix damper 17, and FIG. 10 is a plan view of the position detection plate.

The air mix damper 17 has a damper body 170 having a substantially U-shaped cross section, and the lower end thereof is fixed to a rotating shaft 171 as shown in FIG.
It is pivotally supported by the partition wall 13 through the two. This rotating shaft 17
A worm wheel 173a is fixed to 1 while a worm 173b meshes with the worm wheel 173a. The worm 173b is connected to the output shaft 174a of the reversible second motor 174, and the rotational force of the second motor 174 in the horizontal direction is converted into vertical rotation by the worm 173b and the worm wheel 173a. The main body 170 is rotated up and down.

The output shaft 1 is located near the second motor 174.
A position detection plate 175 fixed to 74a and an air mix damper control sensor, for example, a photo sensor 176, are installed. As shown in FIG. (Point, point C, point D) and the rotation angle of the second motor 174 (the open / closed state of the damper body 170) is detected. Here, when the second motor 174 performs one forward rotation, that is, when the photo sensor 176 sequentially detects points A → B → C → D → A, the air mix damper 17 is fully opened, while When the photo sensor 176 reverses one direction, that is, when the photo sensor 176 moves from point A to point D to point C to point B to A
The points are set so that the air mix damper 17 is fully closed when sequentially detected.

The air mix damper 17 has a structure for detecting a closed state indicated by a solid line in FIG. 9 and a maximum open state indicated by a two-dot chain line in FIG. This structure includes a plate-like cam 177 extending from the damper body 170 and a cam 1.
A second microswitch 178 installed below 77;
The actuator 179 includes an actuator 179 that cooperates with the cam 177 and the second microswitch 178, and a spring 179a that urges the actuator 179 in a direction in which the second microswitch 178 is turned on. Here, the damper body 170 is in a closed state (the air hole 15 is fully closed and the bypass passage 14 is fully opened) and a maximum open state (the air hole 15 is fully opened and the bypass passage 14 is fully closed). At this time, the actuator 17 is driven by the urging force of the spring 179a.
9 is set to turn on the second microswitch 178. A cushion 179b is provided on the periphery of the air hole 15 and on the inner surface of the bypass passage 14 to maintain airtightness when the air mix damper 17 is opened and closed.

Next, the evaporation structure of the drain water will be described with reference to FIGS. Here, FIG. 11 is a side sectional view of the heat storage type air conditioner 1 partially omitted, and FIG. 12 is a schematic configuration diagram showing a water sprinkler.

In this drain water evaporation structure, a water sprinkling device 21 is installed above the condenser 10 while a drain tank 19
Is drained by a pump 22 and supplied to a sprinkler 21 through a water supply pipe 23. The drain water supplied to the water sprinkling device 21 is sprinkled on the condenser 10 and evaporates in the condenser 10, while the non-evaporated water accumulates in a tray 24 installed on the lower surface of the condenser 10, and is further drained. It is structured to be drained to the drain tank 19 through 25.

The watering device 21 has a watering holder 211 connected to the upper end of the water supply pipe 23, and the watering pipe 2 having a watering hole 212a in the watering holder 211.
12 are slidably housed, and the watering pipe 212
Is reciprocated above the condenser 10 to spray water throughout the condenser 10.

Various known structures have been proposed as means for reciprocating the water sprinkling pipe 212. For example, the structure shown in FIG. 12 is employed. That is, while the movable rack 213 is fixed to the side surface of the water sprinkling pipe 212, a fixed rack 214 is disposed at a portion facing the movable rack 213, and a gear 215 meshes between the racks 213 and 214.
The gear 215 is connected to the crank 2 of the third motor 216.
17 and the connecting rod 218 to rotate the movable rack 213.
Is reciprocated.

The regenerative air conditioner 1 thus configured performs a heat storage operation to store heat in the heat storage agent A, and then performs a cooling operation. FIG. 13 is a block diagram showing a control circuit for each operation. is there.

That is, each operation is controlled by a CPU 26 having a microcomputer configuration.
Is a heat storage switch 27, a cooling switch 28, a drain water evaporation switch 29, micro switches 169 and 178, an internal temperature sensor 30 for detecting the temperature of the heat storage chamber 5, and a suction temperature for detecting the temperature of the air flowing in from the suction port 3. Each of the motors 164, 174, 216, the blower 18, the compressor 9, and the pump 22 is driven based on signals from a sensor 31, an air temperature sensor 32 for detecting a temperature of air blown from the air outlet 4, and a photosensor 176. Drive control is performed via the circuits 33 to 38 as shown in the flowcharts of FIGS.

First, the heat storage operation will be described with reference to FIG. That is, after the end of working hours, the heat storage switch 27 is turned on (S1). At this time, without immediately starting the heat storage operation, the operation is started after the time from 23:00 to 7:00, that is, a time zone in which the electricity rate is discounted at midnight or a time zone with low power consumption (S2). Here, when the operation is started, first, the first motor 164 is driven to rotate in the reverse direction (the suction door 7).
And the closing operation of the blowing door 16), and the second motor 174.
Is driven in reverse (the air mix damper 17 is
Is closed) (S5, S6). Here, when the first and second micro switches 169 and 178 are turned on, that is, when the doors 7 and 16 and the air mix damper 17 are completely closed as shown by the solid line in FIG. The first and second motors 164 and 174 are stopped (S5 to S8).

In the closing operation of the suction door 7 and the outlet door 16, the first motor 164 rotates the outlet door 16 upward to close the outlet 4, as shown in FIG.
On the contrary, the suction door 7 rotates downward through the connecting member 20 to close the suction port 3. Therefore, the downward rotating force of the own weight of the suction door 7 is added to the upward rotating force of the blowing door 16 via the connecting member 20, and the first motor 1
64 requires a small driving force.

When the doors 7, 16 and the air mix damper 17 are closed, the compressor 9 is driven to perform a cooling operation (S9). By this cooling operation, the refrigerant flows into the refrigerant pipe 81 of the heat exchange plate 8 to cool the heat exchange plate 8 and also cool the heat storage agent A interposed in the heat exchange plate 8.

In this cold storage operation, when the inside temperature TN becomes lower than the lower limit temperature TL of the inside set temperature, the compressor 9 is stopped to stop the operation, and on the other hand, the inside temperature TN becomes the inside set temperature. When the temperature becomes higher than the upper limit temperature TH, the compressor 9 is driven to restart the operation, and the heat storage agent A is cooled and stored by repeating this operation (S10 to S12). This operation is repeated in the time period from 23:00 to 7:00, and at the end of this time period, the heat storage switch 27 is turned off (S13, 1).
4). In this way, the heat storage operation is performed in a time zone of a cheap midnight charge or a time zone of low power consumption.

In this heat storage operation, all the heat storage agents A are directly cooled by the heat exchange plate 8 provided with the refrigerant pipes 81, so that all the heat storage agents A are stored in a short time without any time lag, and The coefficient of performance of the machine improves.

When such a heat storage operation is completed and the cooling operation shown in FIG. 15 is performed during working hours, the cooling switch 28
Is turned on (S1). As a result, the first motor 164 rotates forward to rotate the suction door 7 and the outlet door 16, and open the inlet 3 and the outlet 4. Here, when the first micro switch 169 is turned off, that is, in FIGS.
When the doors 7 and 16 are fully opened as shown by the two-dot chain line, the first motor 164 is stopped (S3, S4). The upper opening 5a of the heat storage chamber 5 is closed by the blowing door 16 with the fully opening operation of the blowing door 16. Then
By rotating the second motor 174 forward, the second micro switch 17
8 is turned on, that is, when the air hole 15 is fully opened and the bypass passage 14 is fully closed as shown by the two-dot chain line in FIGS. 2 and 7, the second motor 174 is stopped (S5 to S).
7).

In this state, the blower 18 is driven at a low speed and continues for a predetermined time t (minute) (S8, S8).
9). At this time, as indicated by a two-dot chain line arrow in FIG. 2, the room air flows into the heat storage chamber 5 through the suction port 3 and exchanges heat with the heat exchange plate 8 in which the heat storage agent A is interposed to be cooled. The cooled air flows into the bypass passage 14 through the air hole 15 and is blown into the room from the outlet 4.

The suction temperature T1 stabilized by the driving for t minutes is detected by the suction temperature sensor 31, and the blowout temperature T2 is detected by the blowout temperature sensor 30, and the temperature difference ΔT between the temperatures 30 and 31 is calculated ( S10). Here, ΔT> 8 deg, 6 deg <ΔT ≦ 8 deg, 4
deg <ΔT ≦ 6 deg, 2 deg <ΔT ≦ 4 deg,
While it is determined which of the temperature difference zones of 2deg ≧ ΔT, the photo sensor 176 detects which of the points (A, B, C, D) of the position detection plate 175 is present, The rotation angle is determined (S11 to S21).

Based on these determinations, the driving of the second motor 174 is controlled in accordance with the settings in the table of FIG. For example, at the start of the cooling operation, when the air mix damper 17 is fully opened and the photo sensor 176 detects the point A as shown in FIG. 8 and the temperature difference ΔT is ΔT> 8 deg, that is, when the indoor temperature is very low. When it is high, the damper body 170 is fully opened without driving the second motor 174, and the suction port 3
The air that has flowed into the heat storage chamber 5 is sufficiently cooled and blown into the room from the outlet 4.

The continuation of the cooling operation lowers the indoor temperature. For example, when the temperature difference ΔT becomes 6 deg <ΔT ≦ 8 deg, the second motor 174 is rotated reversely (counterclockwise in FIG. 10) and the photo sensor is turned on. 176 light once (point D)
Upon detection, the second motor 174 is stopped. As a result, the damper body 170 slightly opens the bypass passage 14, and a part of the room air flowing into the heat storage chamber 5 from the suction port 3 exchanges heat with the heat storage agent A, as indicated by a two-dot chain line arrow in FIG. While being cooled and flowing into the bypass passage 14 through the air hole 15, other air flows into the bypass passage 14 from the lower end opening 14 a of the bypass passage 14, and the two airs are mixed and blown into the room from the outlet 4. You.

Here, the air blown out from the blow-out port 4 is mixed with air flowing into the lower end opening 14a of the bypass passage 14 (air not sufficiently exchanged with the heat storage agent A). The temperature is slightly higher.

As described above, when the suction temperature is sufficiently higher than the blow-out temperature, air having a low blow-out temperature is supplied to the room. On the contrary, when there is not much difference from the blow-out temperature, the blow-out temperature is set slightly lower. Therefore, from the start of the cooling operation to the end of the cooling operation, as shown in FIG.
The value of T can be made constant, and thereby stable indoor cooling can be performed.

In this cooling operation, the blower 18
Is driven at a low speed, so that the noise of the blower 18 is small,
Does not impair the indoor environment.

Further, during the cooling operation, the drain water from the heat storage chamber 5 accumulates in the drain tank 19. During the heat storage operation, the drain water is uniformly supplied to the condenser 10 by driving the pump 22 and the third motor 216. Can be sprinkled. Here, the moving speed of the water sprinkling pipe 212 of the water sprinkling device 21 may be 5 to 50 mm / sec, and 20 mm / sec is optimal for its evaporation efficiency. As a result, a large evaporation amount can be obtained with a small flow rate, and the pump 22 can be downsized.
Further, drain water is not required, and the condenser 1
0 improves the heat radiation effect.

FIGS. 18 to 20 show a second embodiment of the regenerative air conditioner according to the present invention. This second embodiment shows another control example of the cooling operation. Here, FIG.
8 is a control flowchart according to the second embodiment, FIG. 19 is a table showing the drive control of the second motor, and FIG. 20 is a graph showing an example of a temperature change in the second embodiment.

That is, when the cooling switch 28 is turned on, the doors 7 and 16 are opened and the inlet 3 and the outlet 4 are fully opened as in steps 1 to 4 of the first embodiment. The air hole 15 is fully closed without driving the second motor. In this state, the blower 18 is driven at a low speed (S5), and the indoor air is guided from the suction port 3 to the lower opening 14a of the bypass passage 14, further circulated into the bypass passage 14, and is blown out from the outlet 4.

When this operation is started, the timer of the CPU 26 sets the operation start time to 8:00 before as shown in FIG.
8:00 to 10:00, 10:00 to 11:00, 11:00 to 12:00, 12:00 to 15:00, 15:00 to 16:00
It is determined whether it is before the hour, or even before 16:00 to 17:00, and this cooling operation is continued for t minutes. Here, it is determined whether the operation continuation time is before 8:00 or from 16:00 to 17:00, and the second motor 174 is drive-controlled as shown in FIG. 19 (S6 to S6).
S9).

For example, when the operation start time is before 8:00, that is, when the working hours have not been reached, all the air flowing from the suction port 3 flows into the lower end opening 14a of the bypass passage 14 to minimize indoor cooling. Hold down. Then, as the outside air temperature increases and the indoor temperature rises from 8:00 to 10:00, from 10:00 to 11:00, and from 12:00 to 15:00, the second motor 174 rotates forward one step at a time and the damper body 170 Are gradually opened, while the flow area of the bypass passage 14 is reduced. On the other hand, as the outside air temperature decreases from 15:00 to 16:00 and from 16:00 to 17:00, the second motor 1
74 is reversed one step at a time to increase the flow area of the bypass passage 14. As a result, the temperature becomes as shown in FIG. 20, and the cooling operation corresponding to the change of the outside air temperature, that is, the fluctuation of the indoor cooling load can be performed. In addition, when the operation start time is from 8:00 to 10:00 before, the operation start time is one step forward, and when the operation start time is from 10:00 to 11:00, the operation start time is two steps normal rotation. The cooling operation corresponding to the cooling load can be performed at any time.

FIG. 21 shows a third embodiment of the regenerative air conditioner according to the present invention. FIG. 21 is a side sectional view of the regenerative air conditioner. In each of the above embodiments, as the heat storage agent A, a material mainly containing water having a low heat storage temperature is used. In the third embodiment, on the contrary, the heat storage agent B having a high heat storage temperature is also used as a heat exchange plate. 8 intervenes. The heat storage agent B has a caustic soda aqueous solution as a main component. In the third embodiment, the refrigerant pipe 81 of the heat exchange plate 8
An electric heater 39, which is a heating device, is installed in parallel with the heater. The heating of the electric heater 39 heats the heat storage agent B to store the heat.

According to this embodiment, when heat is stored for performing indoor cooling, the heat storage agent A may be cooled and stored by the refrigerant passing through the refrigerant pipe 81 in the same manner as in each of the above embodiments. Is performed, the heat storage agent B may be heated and stored by using the electric heater 39, whereby both cooling and heating can be performed in this embodiment.

It should be noted that the regenerative air conditioner for cooling and heating can of course perform the air conditioning control according to the first and second embodiments.

FIG. 22 shows a fourth embodiment of the regenerative air conditioner according to the present invention, and FIG. 22 is a side sectional view of the regenerative air conditioner. In this embodiment, only a heat storage agent B having a high heat storage temperature is interposed in the heat exchange plate 8 as a heat storage agent, and only an electric heater 39 as a heating device is attached to the heat exchange plate 8. Thereby, a regenerative air conditioner dedicated to heating is configured. Needless to say, the regenerative air conditioner dedicated to heating does not require a compressor of a refrigerator or the like.

[0072]

As described above, according to the first aspect of the present invention, a plurality of heat exchange plates provided with the refrigerant pipes of the cooling device are arranged to face each other at a predetermined interval, and the heat exchange plates are disposed between the heat exchange plates. The heat storage agent is cooled directly through the heat exchange plate, improving the cooling efficiency of the heat storage agent and preventing the time lag of the heat storage expiration time of each heat storage agent. The coefficient is improved. Further, since a conventional brine circuit is not required, the size and weight of the apparatus can be reduced.

According to the second aspect of the present invention, the entire heat exchange plate is uniformly cooled, and the contact area between the heat storage agent and the heat exchange plate is increased by the recess for accommodating the heat storage agent, so that the heat storage agent is efficiently used. Cools well.

According to the third aspect of the invention, since the drain water in the heat storage is pumped up by the pump and sprayed to the condenser through the water spray device, the heat exchange efficiency of the condenser is improved as compared with the case of simply exchanging heat with room air. In addition, drain water drainage becomes unnecessary.

According to the fourth aspect of the present invention, a plurality of heat exchange plates provided with a heating device are arranged facing each other at a predetermined interval, and a plurality of heat storage agents are interposed between each heat exchange plate. In addition, the heat storage agent is directly heated through the heat exchange plate, so that the heating efficiency of the heat storage agent is improved, and the time lag of the heat storage expiration time of each heat storage agent can be prevented.

According to the fifth aspect of the present invention, the amount of air flowing into the bypass passage through the upper air hole through the heat storage chamber among the room air flowing into the heat storage chamber from the suction port during cooling and heating, and Since the flow rate of the air flowing from the lower end to the bypass passage can be controlled by the air mix damper, the blowout temperature can be arbitrarily set by controlling the opening and closing of the air mix damper.

According to the sixth aspect of the present invention, since the air mix damper can be controlled based on the temperature difference between the temperature of the intake air and the temperature of the blown air, the temperature of the blown air can be controlled so as to have a predetermined temperature difference. Large fluctuations in room temperature can be prevented.

According to the seventh aspect of the present invention, the temperature of the blown air can be controlled so as to correspond to the cooling / heating load during working hours.

[Brief description of the drawings]

FIG. 1 is a front view of a regenerative air conditioner according to a first embodiment.

FIG. 2 is a side sectional view of the regenerative air conditioner according to the first embodiment.

FIG. 3 shows a heat exchange plate and a heat storage agent A according to the first embodiment.
Perspective view of assembly

FIG. 4 is a sectional view of the heat exchange plate and the heat storage agent according to the first embodiment.

FIG. 5 is a perspective view of a suction door and a discharge door according to the first embodiment.

FIG. 6 is a front view of a suction door and a discharge door according to the first embodiment.

FIG. 7 is a side view of the suction door and the outlet door according to the first embodiment.

FIG. 8 is a front view of the air mix damper according to the first embodiment.

FIG. 9 is a side sectional view of the air mix damper according to the first embodiment.

FIG. 10 is a plan view of the position detection plate according to the first embodiment.

FIG. 11 is a side sectional view of the heat storage type air conditioner according to the first embodiment, which is partially omitted.

FIG. 12 is a schematic configuration diagram showing a partially omitted watering device according to the first embodiment.

FIG. 13 is a block diagram showing a control circuit of each operation according to the first embodiment.

FIG. 14 is a control flowchart of a heat storage operation according to the first embodiment.

FIG. 15 is a control flowchart of a cooling operation according to the first embodiment.

FIG. 16 is a table showing drive control of a second motor according to the first embodiment.

FIG. 17 is a graph showing an example of a temperature change according to the first embodiment.

FIG. 18 is a control flowchart of a cooling operation according to the second embodiment.

FIG. 19 is a table showing drive control of a second motor according to the second embodiment.

FIG. 20 is a graph showing an example of a temperature change according to the second embodiment.

FIG. 21 is a side sectional view of a regenerative air conditioner according to a third embodiment.

FIG. 22 is a side sectional view of a regenerative air conditioner according to a fourth embodiment.

FIG. 23 is a schematic circuit diagram of a conventional regenerative air conditioner.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Heat storage type air conditioner, 2 ... Heat storage, 3 ... Suction port,
4 ... Blow-out port, 5 ... Heat storage chamber, 5a ... Top opening, 7 ... Suction door, 8 ... Heat exchange plate, 9 ... Compressor, 10 ... Condenser, 11 ... Expansion valve, 13 ... Partition wall, 14 ... Bypass passage,
14a: bottom opening, 14b: top opening, 15: air hole,
Reference Signs List 16 blow-out door, 17 air mix damper, 18 blower, 19 drain tank, 20 connecting member, 21 sprinkler, 22 pump, 26 CPU, 30 temperature sensor inside chamber, 31 temperature sensor for suction , 32: blow-out temperature sensor, 39: electric heater, A, B: heat storage agent.

 ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-52-142852 (JP, A) JP-A-62-210334 (JP, A) JP-A-55-28425 (JP, A) 99326 (JP, U) Japanese Utility Model Showa 50-56332 (JP, U) Japanese Utility Model Showa 58-83014 (JP, U)

Claims (7)

(57) [Claims] A heat storage agent having a low heat storage temperature is stored in a heat storage chamber, and when storing heat, the lower inlet and the upper outlet are closed to cool the heat storage agent by a cooling device, while during cooling, the heat storage agent is cooled. In a heat storage type air conditioner in which a suction port and a discharge port are opened, air is sucked into a refrigerator by a blower, heat exchange with the heat storage agent is performed, and the air is blown into the room, a heat exchange plate provided with a refrigerant pipe of the cooling device is provided. A heat storage type air conditioner, wherein a plurality of heat storage agents are disposed facing each other at a predetermined interval, and a plurality of the heat storage agents are interposed between the heat exchange plates. 2. The cooling device according to claim 1, wherein a refrigerant pipe of the cooling device is provided in a meandering manner on a heat exchange plate, and a concave portion for accommodating the heat storage agent is formed at a predetermined interval between adjacent refrigerant pipes. Item 3. A regenerative air conditioner according to Item 1. 3. The cooling device includes a refrigerant refrigerator that sequentially circulates refrigerant through a compressor, a condenser, an expansion unit, and a heat exchange plate, and a drain tank that stores drain water from the heat storage. 3. The heat storage device according to claim 1, further comprising: a pump for feeding the drain water to the condenser side; and a water sprinkler for sprinkling the drain water pumped by the pump to the condenser. Type air conditioner. 4. A heat storage agent having a high heat storage temperature is stored in a heat storage chamber, and when storing heat, the lower inlet and the upper outlet are closed and the heat storage agent is heated by a heating device, while during heating, the heat storage agent is heated. In a regenerative air conditioner, in which a suction port and an air outlet are opened, room air is sucked into a refrigerator by a blower, heat exchange with the heat storage agent is performed, and the air is blown into a room, a heat exchange plate provided with the heating device is disposed at a predetermined interval. Wherein a plurality of the heat storage agents are interposed between the heat exchange plates. 5. A heat storage chamber in which a heat exchange plate having the heat storage agent interposed therein is disposed in the heat storage chamber, one end of which faces the suction port from a lower part of the heat storage chamber, and the other end has the outlet port and the heat storage. A bypass passage facing an upper opening of the chamber; an air hole communicating the heat storage chamber and the bypass passage closer to an upper portion in the heat storage; and a flow area of the bypass passage and a flow area of the air hole being contradictory to each other. An air mix damper that controls opening and closing of the heat storage chamber so that the air blower is installed in the bypass passage between the air hole and an upper opening of the heat storage chamber. The regenerative air conditioner according to any one of claims 4 to 4. 6. An intake temperature sensor for detecting the temperature of the intake air, an outlet temperature sensor for detecting the temperature of the outlet air, and arithmetic means for calculating a temperature difference between the detected temperatures detected by each of the temperature sensors. The regenerative air conditioner according to any one of claims 1 to 5, further comprising an opening control unit that controls an opening of the air mix damper based on a temperature difference. 7. A regenerative storage system according to claim 1, further comprising an opening control means for controlling an opening of said air mix damper in accordance with a cooling / heating operation time. Air conditioner.