JPH0792289B2 - Operation control device and operation control method for heat storage type air conditioner - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to an operation control device and an operation control method for a heat storage type air conditioner provided with a heat storage tank that stores a heat storage medium, and more particularly to a cold storage heat storage device. The present invention relates to operation control measures during operation, during normal cooling and simultaneous cold storage heat operation.

(Prior Art) As a general configuration of a heat storage type air conditioner which has been developed in recent years, a compressor, a heat source side heat exchanger, a main pressure reducing valve and a use side heat exchanger are sequentially connected by a refrigerant pipe. A heat storage tank that is configured to form a main cooling circuit and that includes a heat storage tank that stores ice for heat storage, is arranged in the heat storage tank, and is connected to the main refrigerant circuit to perform heat exchange between the refrigerant and the heat storage medium. It comprises a heat exchanger and a cold storage heat decompression mechanism arranged on the refrigerant upstream side of the heat storage heat exchanger.

In addition, various means have been developed so far as means for generating ice as a heat storage medium generated by this heat storage type air conditioner. As an example thereof, there is a heat storage operation control method as disclosed in JP-A-61-289253. The method disclosed in this publication corrects the start time of the heat storage operation by adding / subtracting to / from a preset correction coefficient depending on the difference between the heat storage amount and the target heat storage amount at a predetermined time, and finally The ice making start time is controlled so that the target heat storage amount can be obtained at a predetermined time.

On the other hand, in this main heat storage type air conditioner, there is a problem that operating efficiency is poor due to excess operation performance caused only by performing the normal cooling operation and the cold storage operation alone, and in parallel with the normal cooling operation at night. It is desired to perform the cold storage heat operation, that is, to enable the normal cooling and the cold storage heat simultaneous operation.

(Problems to be Solved by the Invention) However, the heat storage type air conditioner has the following problems during each operation.

That is, when the normal cooling and the cold storage heat simultaneous operation are performed, (I) When the cooling load increases and the evaporation pressure-equivalent saturation temperature rises (for example, −5 ° C. or higher), the temperature of the refrigerant and the water as the heat storage medium are increased. Since the temperature difference from the freezing temperature cannot be sufficiently obtained, the amount of ice making is small and the cold storage heat is not sufficiently performed.

(II) On the other hand, conversely, when the cooling load becomes small and the saturation pressure equivalent to the evaporation pressure becomes low (for example, -10 ° C or lower), the temperature difference between the refrigerant and water can be sufficiently obtained, and the amount of cold storage heat can be sufficiently obtained. However, there is a risk that the air temperature in the room will drop too much, causing drafts, or the user-side (indoor) heat exchanger will freeze, making continuous operation impossible.

Further, during the cold heat storage operation, there is a control for changing the heat storage operation start time in order to achieve the target heat storage amount as shown in the above publications, and in this case, the continuous operation time is constant. In many cases, the compressor is used in a region where the operating frequency is high, and the compressor is not controlled in the best frequency region of the coefficient of performance, leading to an increase in power consumption.

Therefore, the present invention is an operation control of a heat storage type air conditioner capable of performing a cool storage heat operation with good operation efficiency and a highly practical normal cooling and cool storage heat simultaneous operation without causing the various problems described above. An object is to obtain an apparatus and an operation control method.

(Means for Solving the Problem) The solving means of the present invention for achieving the above object will be described below.

First, according to the invention described in claim (1), as shown in FIG. 1, a compressor (1) with variable capacity, a heat source side heat exchanger (3), and a main pressure reducing valve (6) with variable opening degree are provided. ) And the heat exchanger (7) on the use side are sequentially connected by a refrigerant pipe (9), and a heat storage tank (11) for storing ice for cold storage heat.
And a heat storage heat exchanger (12) for performing heat exchange between the refrigerant and the heat storage medium, the heat storage tank being provided in the heat storage tank (11) and connected to the main refrigerant circuit (10). The cold storage heat reducing mechanism (14) is provided. Then, at least during normal cooling operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) flows only through the main refrigerant circuit (10) and is decompressed by the main pressure reducing valve (6), and the use side heat exchanger (7). ) And circulates to return to the compressor (1), and during the cold heat storage operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is decompressed by the cold heat decompression mechanism (14), After being evaporated in the heat exchanger (12), it circulates back to the compressor (1), and during the cold heat recovery operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is discharged from the main refrigerant circuit (10). After being supercooled in the heat storage heat exchanger (12), it is circulated so as to evaporate in the utilization side heat exchanger (7) of the main refrigerant circuit (10) and return to the compressor (1) for normal cooling and cold storage heat. During the simultaneous operation, a part of the liquid refrigerant condensed in the heat source side heat exchanger (3) is vaporized in the use side heat exchanger (7) of the main refrigerant circuit (10). On the other hand, for the heat storage type air conditioner provided with the switching means (51) for switching the circuit connection so as to return to the compressor (1) after the rest of the liquid refrigerant is evaporated in the heat storage heat exchanger (12). There is. Then, during the simultaneous normal cooling and cold storage heat operation, the maximum opening setting for setting the maximum opening of the main pressure reducing valve (6) to a predetermined second maximum opening smaller than the first maximum opening set in the normal cooling operation. Means (52) and evaporation temperature detection means (53) for detecting a saturation temperature equivalent to the evaporation pressure
A capacity detecting means (54) for detecting the maximum capacity operation of the compressor (1), the capacity detecting means (54) detecting the maximum capacity operation of the compressor (1), and the evaporation temperature detecting means. (Five
When the vapor pressure equivalent saturation temperature detected by 3) becomes equal to or higher than the preset set temperature, the maximum opening of the main pressure reducing valve (6) is set to a predetermined third maximum opening smaller than the second maximum opening. The opening regulation means (55) is provided.

On the other hand, the invention according to claim (2), as shown in FIG. 2, has a variable capacity compressor (1), a heat source side heat exchanger (3), a main pressure reducing valve (6), and a use side heat exchange. A main refrigerant circuit (10) formed by sequentially connecting a container (7) with a refrigerant pipe (9),
While having a heat storage tank (11) for storing ice for cold storage heat,
A heat storage heat exchanger (12) arranged in the heat storage tank (11) and connected to the main refrigerant circuit (10) for exchanging heat between the refrigerant and the heat storage medium, and a decompression mechanism for cold storage heat. (14)
It has and. Then, at least during normal cooling operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) flows only through the main refrigerant circuit (10) and is decompressed by the main pressure reducing valve (6), and the use side heat exchanger (7). ) And circulates to return to the compressor (1), and during the cold heat storage operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is decompressed by the cold heat decompression mechanism (14), After being evaporated in the heat exchanger (12), it circulates back to the compressor (1), and during the cold heat recovery operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is discharged from the main refrigerant circuit (10). After being supercooled by the heat storage heat exchanger (12), the main refrigerant circuit (1
Liquid refrigerant that is circulated to return to the compressor (1) after being evaporated in the use side heat exchanger (7) of (0) and condensed in the heat source side heat exchanger (3) during normal cooling and cold storage simultaneous operation Part of the liquid refrigerant evaporates in the use side heat exchanger (7) of the main refrigerant circuit (10), while the rest of the liquid refrigerant evaporates in the heat storage heat exchanger (12),
The heat storage type air conditioner is provided with a switching means (51) for switching the circuit connection so as to return to the compressor (1). Then, the evaporation temperature detecting means (53) for detecting the saturation temperature corresponding to the evaporation pressure during the normal cooling and the cold storage heat simultaneous operation.
And a capacity control means (56) for receiving the output signal of the evaporation temperature detection means (53) and controlling the capacity of the compressor (1) so that the saturation temperature equivalent to the evaporation pressure becomes a preset target value. It has a configuration provided.

The invention according to claim (3) is the operation control device for a heat storage type air conditioner according to claim (1), wherein the capacity control means (56) according to claim (2) is provided. It has been configured.

The invention according to claim (4) is, as shown in FIG. 3, a compressor (1) having a variable capacity, a heat source side heat exchanger (3), a main pressure reducing valve (6) and a use side heat exchange. A main refrigerant circuit (10) formed by sequentially connecting a container (7) with a refrigerant pipe (9),
While having a heat storage tank (11) for storing ice for cold storage heat,
A heat storage heat exchanger (12) arranged in the heat storage tank (11) and connected to the main refrigerant circuit (10) for exchanging heat between the refrigerant and the heat storage medium, and a decompression mechanism for cold storage heat. (14)
It has and. Then, at least during normal cooling operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) flows only through the main refrigerant circuit (10) and is decompressed by the main pressure reducing valve (6), and the use side heat exchanger (7). ) And circulates to return to the compressor (1), and during the cold heat storage operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is decompressed by the cold heat decompression mechanism (14), After being evaporated in the heat exchanger (12), it circulates back to the compressor (1), and during the cold heat recovery operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is discharged from the main refrigerant circuit (10). After being supercooled by the heat storage heat exchanger (12), the main refrigerant circuit (1
Liquid refrigerant that is circulated to return to the compressor (1) after being evaporated in the use side heat exchanger (7) of (0) and condensed in the heat source side heat exchanger (3) during normal cooling and cold storage simultaneous operation Part of the liquid refrigerant evaporates in the use side heat exchanger (7) of the main refrigerant circuit (10), while the rest of the liquid refrigerant evaporates in the heat storage heat exchanger (12),
The heat storage type air conditioner is provided with a switching means (51) for switching the circuit connection so as to return to the compressor (1). Then, during the cold storage heat operation, the cold storage heat time setting means (61) for setting the cold storage heat operation time, the ice making amount detection means (62) for detecting the required ice making amount in the heat storage tank (11), and the cold storage heat time. An arithmetic means (63) for receiving output signals from the setting means (61) and the ice making quantity detecting means (62) and calculating a minimum operating frequency of the compressor (1) required to make the required ice making quantity in a set time. ) And an operation control means (64) for controlling the operation of the compressor (1) on the basis of the compressor operating frequency calculated by the operation means (63) by receiving the output signal from the operation means (63). It is configured.

Further, the invention according to claim (5) is based on the above-mentioned claim (1),
In the operation control device of the heat storage type air conditioner according to (2) or (3), the cold storage heat time setting means (61), the ice making amount detection means (62), and the calculation means (6) according to claim (4).
3) and operation control means (64) are provided.

Finally, the invention according to claim (6) is such that the compressor (1) with a variable capacity, the heat source side heat exchanger (3), the main pressure reducing valve (6) with a variable opening degree, and the use side heat exchanger. A main refrigerant circuit (10) in which (7) is sequentially connected by a refrigerant pipe (9), and a heat storage tank (11) for storing ice for cold storage heat are provided while being arranged in the heat storage tank (11). The main refrigerant circuit (1
A heat storage heat exchanger (12) connected to the heat storage medium (0) for exchanging heat between the refrigerant and the heat storage medium, and a cold storage heat decompression mechanism (14). And at least during normal cooling operation,
The liquid refrigerant condensed in the heat source side heat exchanger (3) flows only in the main refrigerant circuit (10), is decompressed by the main pressure reducing valve (6), and is evaporated in the use side heat exchanger (7) to generate a compressor ( During the cold storage heat operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is depressurized by the cold storage heat decompression mechanism (14) and evaporated in the heat storage heat exchanger (12). Then, it circulates back to the compressor (1), and during the cold storage heat recovery operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is transferred from the main refrigerant circuit (10) to the heat storage heat exchanger (12). After being supercooled, it circulates so as to evaporate in the use side heat exchanger (7) of the main refrigerant circuit (10) and return to the compressor (1), and heat exchange on the heat source side during normal cooling and cold storage heat simultaneous operation. A part of the liquid refrigerant condensed in the device (3) is evaporated in the utilization side heat exchanger (7) of the main refrigerant circuit (10), while the rest of the liquid refrigerant is the heat storage heat exchanger. After evaporation at 12), a operation control method of a thermal storage type air conditioner targeted with a switching means (51) for switching the circuit connection back to each compressor (1). During the cold storage heat operation, the cold storage heat operation time is set by the cold storage heat time setting means (61), and at the same time, the required ice making amount in the heat storage tank (11) is detected by the ice making amount detecting means (6).
After the detection by 2), the calculating means (63) calculates the minimum operating frequency of the compressor (1) required to make the required ice making amount in the above cold storage heat operation time, and the calculated operating frequency of the compressor is calculated. While the operation control means (64) controls the operation of the compressor (1) based on this,
The maximum opening setting means (52) sets the maximum opening of the main pressure reducing valve (6) to a predetermined second maximum opening smaller than the first maximum opening set during normal cooling operation, and the main pressure reducing valve is set. The degree of opening of (6) is controlled by the degree of superheat, the evaporation temperature detecting means (53) detects the saturation temperature equivalent to the evaporation pressure, and the capacity control means (56) changes the capacity of the compressor (1) to the saturation temperature equivalent to the evaporation pressure. Is controlled to reach a predetermined target value, and thereafter, when the capacity detection means (54) detects the maximum capacity operation of the compressor (1) and the saturation temperature corresponding to the evaporation pressure becomes equal to or higher than a predetermined temperature, the maximum opening is reached. The degree regulating means (55) sets the maximum opening degree of the main pressure reducing valve (6) to a third maximum opening degree that is smaller than the second maximum opening degree. In the inventions of (), (5) and (6), the circuit connection is switched by the switching means (51), and the Tufts operation, cold storage heat operation, cold storage heat recovery operation, normal cooling and cold storage heat simultaneous operation is performed.

Then, during the normal cooling and cold storage heat simultaneous operation, the maximum opening degree setting means (52) operates to make the maximum opening degree of the main pressure reducing valve (6) smaller than the first maximum opening degree set during the normal cooling operation. 2 The maximum opening is set to suppress the increase in the saturation temperature equivalent to the evaporation pressure, so that the difference between the temperature of the refrigerant and the freezing temperature of water in the cold storage heat decompression mechanism (14) can be sufficiently taken.
Prevent a decrease in the amount of ice making. When the capacity detecting means (54) detects the maximum capacity operation of the compressor (1) and the evaporation pressure equivalent saturation temperature detected by the evaporation temperature detecting means (53) becomes equal to or higher than a preset temperature. The maximum opening degree of the main pressure reducing valve (6) is set to the second value by the operation of the maximum opening degree regulating means (55).
By setting a predetermined third maximum opening smaller than the maximum opening, an increase in the evaporation pressure equivalent saturation temperature due to an increase in cooling load is suppressed, and control is performed so that a sufficient amount of ice making is obtained. In this way, the cooling load is made variable by adjusting the opening degree of the main pressure reducing valve (6), the evaporative pressure equivalent saturation temperature is always controlled to the optimum state, and the problems caused by the magnitude of the cooling load are eliminated.

Further, in the inventions of claims (2), (3), (5) and (6), the evaporation temperature detecting means (53) detects the saturation temperature equivalent to the evaporation pressure during the normal cooling and cold storage heat simultaneous operation, Upon receiving the output signal of the evaporation temperature detecting means (53), the capacity control means (56) controls the capacity of the compressor (1) so that the saturation temperature equivalent to the evaporation pressure becomes a preset target value. As a result, the vertical movement of the saturation temperature equivalent to the evaporation pressure is suppressed, and the problem caused by the elevation of the saturation temperature equivalent to the evaporation pressure is eliminated.

Further, in the inventions of claims (4), (5) and (6), during the cold storage heat operation, the cold storage heat time setting means (61) sets the cold storage heat operation time, and the ice making amount detection means (62) stores the heat storage. The required amount of ice making in the tank (11) is detected, and the cool storage heat time setting means (6
1) and the output signals from the ice making amount detecting means (62) are sent to the calculating means (63), and the calculating means (63) causes the compressor (1) required to make the required ice making amount in a set time. After calculating the minimum operating frequency, the output signal from the calculating means (63) is sent to the operation controlling means (64), and the compressor operating frequency calculated by the calculating means (63) by the operating controlling means (64). The operation of the compressor (1) is controlled based on the above. This makes it possible to drive the compressor in a region where the operating frequency is low, that is, where the coefficient of performance is high, by maximizing the use of the cool storage heat operation time, which improves energy efficiency with a reduction in power consumption. To do.

(Embodiment) An embodiment of the present invention will be described below with reference to the drawings starting from FIG.

FIG. 4 shows the overall configuration of the air conditioner according to the present embodiment, a so-called multi-type air conditioner in which a plurality of indoor units (A), (B), ... Are connected to the outdoor unit (X). Is.

In the outdoor unit (X), (1) is a compressor,
(2) is a four-way switching valve that switches during cooling operation as shown by the solid line in the figure, and during heating operation as shown by the broken line in the figure,
(3) is an outdoor heat exchanger as a heat source side heat exchanger that functions as a condenser during cooling operation and as an evaporator during heating operation, and (4) adjusts the refrigerant flow rate during cooling operation and reduces the refrigerant during heating operation. An outdoor electric expansion valve functioning as a pressure reducing mechanism, (5) is a receiver for storing the condensed liquid refrigerant, and (8) is an accumulator for removing the liquid component in the suction refrigerant.

On the other hand, the indoor units (A), (B), ... Have the same configuration, and (6) functions as a pressure reducing mechanism during the cooling operation,
An indoor electric expansion valve as a main pressure reducing valve for adjusting the refrigerant flow rate during heating operation, and (7) as an evaporator during cooling operation,
It is an indoor heat exchanger as a utilization side heat exchanger that functions as a condenser during heating operation.

The above-mentioned devices (1) to (8) are sequentially connected to each other through a refrigerant pipe (9) so that the refrigerant can flow therethrough, and have a heat pump action of releasing the heat obtained by heat exchange with the outdoor air to the indoor air. A main refrigerant circuit (10) is configured.

Further, in the device, a heat storage unit (Y) for arranging cold heat storage, heat storage heat, or use of the cold heat storage, heat storage heat by heat exchange with the refrigerant flowing in the main refrigerant circuit (10) is arranged. ing. In the heat storage unit (Y), (11) is a heat storage tank that stores water (W), which is a heat storage medium capable of storing cold heat and warm heat, and (12) is arranged in the heat storage tank (11). W) is a heat storage heat exchanger for exchanging heat with the refrigerant, wherein the heat storage heat exchanger (12) and the outdoor electric expansion valve (4) of the main refrigerant circuit (10) -indoor electric expansion valve ( Between the liquid line (9a) between 6), the first bypass passage (13a) and the second bypass passage (13a)
The bypass passage (13b) is connected to the indoor electric expansion valve (6) so that the refrigerant can flow sequentially from the side. The first bypass path (13a) is provided with a heat storage electric expansion valve (14) as a cold storage heat reducing mechanism that reduces the pressure of the refrigerant when cold water is stored in the water (W). Road (13
In b), a first opening / closing valve (15) for opening / closing the second bypass passage (13b) is provided.

Further, the first on-off valve (15) of the second bypass passage (13b)
− Intermediate piping between the heat storage heat exchanger (12) and the main refrigerant circuit (10)
Is connected to the gas line (9b) by a third bypass passage (13c) so that the refrigerant can flow therethrough, and the third bypass passage (13c) is provided with a second opening / closing valve for opening and closing the bypass passage (13c). (16) is installed.

On the other hand, between the two joints between the liquid line (9a) of the main refrigerant circuit (10) and the first and second bypass passages (13a) and (13b), the flow rate of the refrigerant is variably adjusted. Flow control valve (1
7) is installed. That is, the switching means (51) for switching the circuit connection according to each operating state is the first opening / closing valve (1).
5), the second on-off valve (16), and the flow control valve (17).

Further, sensors are arranged in this heat storage type air conditioner, (Thw) is arranged in the water of the heat storage tank (11), and residual ice in the heat storage tank (11) is detected by detecting the water temperature Tw. A water temperature sensor that detects the presence or absence of air, (Tha) is arranged at the air inlet of the outdoor heat exchanger (3), and an outside air temperature sensor that detects the outside air temperature Ta, and (Thi) is the second bypass of the liquid line (9a). The cooling inlet sensor (Tho) arranged on the upstream side during the cooling operation of the joint portion with the passage (13b) is the liquid line (9a).
The cooling outlet sensor (Ths) is arranged in the suction line (9d) on the downstream side during the cooling operation of the joint with the first bypass passage (13a) of the suction pipe for detecting the temperature of the suction pipe. A sensor, (Sp) is arranged in the gas line (9b), a pressure sensor that detects high pressure Tc during a heating cycle and a low pressure (suction pressure) during a cooling cycle, and (Cl) detects the water level in the heat storage tank (11). This is a water level sensor that detects the amount of residual ice in the heat storage tank (11). Then, the signals detected by these sensors are sent to the first and second controllers (C ₁ ) and (C ₂ ).

Next, these two controllers (C ₁ ) and (C ₂ ) will be described.

The first controller (C ₁ ) has a maximum opening setting means (52) for setting the maximum opening of the indoor electric expansion valve (6) to a small value, and a pressure sensor (SP) when the operating states are normal cooling and cold storage simultaneous operation. ), The evaporation temperature detecting means (53) for detecting the saturation temperature Te corresponding to the evaporation pressure, the capacity detecting means (54) for detecting the maximum capacity operation of the compressor (1), and the evaporation temperature detecting means (53). Upon receiving the signal from the capacitance detecting means (54),
Capacity control means (56) for controlling the capacity of the compressor (1) in response to signals from the maximum opening regulating means (55) for setting the maximum opening of the indoor electric expansion valve (6) and the evaporation temperature detecting means (53). ) And.

On the other hand, the second controller (C ₂ ) has a cold storage heat time setting means (61) for setting a cold storage heat operation time, and a water level sensor (Cl).
Output from the ice storage amount detection means (62) for detecting the required ice production amount in the heat storage tank (11), the cold storage heat time setting means (61) and the ice production amount detection means (62). Receiving a signal and receiving an output signal from a calculating means (63) for calculating a minimum operating frequency of the compressor (1) required to make the required ice making amount in a set time, and an output signal from the calculating means (63), The operation control means (64) controls the operation of the compressor (1) based on the compressor operation frequency calculated by the calculation means (63).

Next, the opening / closing (or opening adjustment) of each valve and the circulation path of the refrigerant in each operation mode of this heat storage type air conditioner will be described based on FIGS. 5 to 12.

During normal cooling operation, as shown by the arrow in FIG. 5, the four-way switching valve (2) is switched as shown by the solid line in the figure, and the outdoor electric expansion valve (4), flow control valve (17), indoor electric expansion valve (6),
... is opened and all the other valves are operated in a closed state, the refrigerant condensed in the outdoor heat exchanger (3) circulates only in the main refrigerant circuit (10), and each indoor electric expansion valve (6 ), ... Decompresses, and each indoor heat exchanger (7) evaporates and returns to the compressor (1).

In the cold storage operation, as shown by the arrow in FIG. 6, the outdoor electric expansion valve (4), the flow control valve (17), the heat storage electric expansion valve (14).
And the second on-off valve (16) opens, and the indoor electric expansion valve (6),
... and operation is performed with the first on-off valve (15) closed,
The liquid refrigerant condensed in the outdoor heat exchanger (3) flows by bypassing the first bypass passage (13a), and the heat storage electric expansion valve (1
It is decompressed in 4), evaporated in the heat storage heat exchanger (12) and circulated back to the compressor (1). At that time, water (W) as a heat storage medium is generated by heat exchange with the refrigerant in the heat storage heat exchanger (12).
Make ice and store cold heat.

During the normal cooling and cold storage heat simultaneous operation, as shown by the arrow in FIG. 7, the outdoor electric expansion valve (4), the flow control valve (17), the indoor electric expansion valve (6), ..., The heat storage electric expansion valve (14) And the second opening / closing valve (16) is opened, the first opening / closing valve (15) is closed, and a part of the liquid refrigerant condensed in the outdoor heat exchanger (3) flows through the main refrigerant circuit (10), While being decompressed by the electric expansion valves (6), ..., Evaporated by the indoor heat exchangers (7), ..., the remaining part of the liquid refrigerant flows to the first bypass passage (13a) side, and the heat storage electric expansion valve (14) It is decompressed and evaporated in the heat storage heat exchanger (12).
Then, these refrigerants in the gas state are circulated so as to return to the compressor (1) which merges in the gas line (9b).

During the cold storage heat recovery operation using the cold heat stored in the cold storage heat operation, as shown by the arrow at the 8th hour, the outdoor electric expansion valve (4), the flow control valve (17), the indoor electric expansion valve (6),
The liquid refrigerant condensed in the outdoor heat exchanger (3) is operated with the heat storage electric expansion valve (14) and the first opening / closing valve (15) open and the second opening / closing valve (16) closed. Part of the refrigerant flows from the main refrigerant circuit (10) to the second bypass passage (13b) side, and is supercooled by heat exchange with water (W) (or ice) in the heat storage heat exchanger (12). While returning from the first bypass path (13a) to the main refrigerant circuit (10), the rest of the liquid refrigerant passes through the flow rate control valve (17) and remains in the liquid line (9) of the main refrigerant circuit (10).
flow through a). Then, after merging, the pressure is reduced by the indoor electric expansion valves (6), ..., Evaporated by the indoor heat exchangers (7), and then circulated so as to return to the compressor (1). At that time, the partial flow rate of the refrigerant is adjusted by adjusting the relative opening of the flow control valve (17) and the heat storage electric expansion valve (14), and is detected by the cooling inlet sensor (Thi) and the cooling outlet sensor (Tho). The subcooling degree of the refrigerant as the temperature difference ΔTl between the liquid refrigerant temperatures Tl1 and Tl2 is appropriately adjusted.

Next, in the normal heating operation, as shown by the arrow in FIG. 9, the four-way switching valve (2) is switched to the broken line side in the figure, and each indoor electric expansion valve (6), ..., Flow control valve (17). ), The outdoor electric expansion valve (4) is opened, and the operation is performed with all the other valves closed, and the discharge gas is condensed in the indoor heat exchangers (7), ... ), Is decompressed, evaporated in the outdoor heat exchanger (3), and then circulated so as to return to the compressor (1).

During the warm storage operation, as shown by the arrow in FIG. 10, the second opening / closing valve (16), the heat storage electric expansion valve (14), the flow control valve (17),
The outdoor electric expansion valve (4) is opened, the indoor electric expansion valves (6), ..., And the first opening / closing valve (15) are closed, and the operation is performed with the discharge gas from the main refrigerant circuit (10) to the third. After bypassing to the bypass passage (13c) and being condensed in the heat storage heat exchanger (12), it flows from the first bypass passage (13a) to the main refrigerant circuit (10) and then at the outdoor electric expansion valve (4). After being decompressed and evaporated in the outdoor heat exchanger (3), it is circulated so as to return to the compressor (1). At that time, the water (W) in the heat storage tank (11) is warmed by heat exchange with the refrigerant in the heat storage heat exchanger (12),
Warm heat is stored.

At the time of simultaneous normal heating and storage heat simultaneous operation, as shown by the arrow in FIG. 11, each indoor electric expansion valve (6), ..., The second opening / closing valve (1
6), the heat storage electric expansion valve (14), the flow control valve (17), the outdoor electric expansion valve (4) are opened and the first opening / closing valve (15) is closed, and the operation is performed, and a part of the discharged gas is discharged. Is the main refrigerant circuit (10)
To the third bypass passage (13c) side, and is condensed in the heat storage heat exchanger (12), while the rest of the discharge gas flows to the main refrigerant circuit (10) side to reach each indoor heat exchanger (7). ), ...
Is condensed in. Then, after both merge, they are decompressed by the outdoor electric expansion valve (4), evaporated in the outdoor heat exchanger (3), and then circulated so as to return to the compressor (1).

Further, during the storage heat recovery defrost operation, as shown by the arrow in FIG. 12, the four-way switching valve (2) is switched to the solid line side in the figure, and the outdoor electric expansion valve (4), the flow control valve (17), The indoor electric expansion valves (6), ..., The heat storage electric expansion valve (14), the second opening / closing valve (16) are opened, the operation is performed with the first opening / closing valve (15) closed, and the discharge gas is discharged outdoors. Part of the liquid refrigerant condensed in the heat exchanger (3) bypasses from the main refrigerant circuit (10) to the first bypass passage (13a) side, and is decompressed by the heat storage electric expansion valve (14). While being evaporated in the heat storage heat exchanger (12), the remaining portion of the liquid refrigerant is decompressed by the indoor electric expansion valves (6), ... Of the main refrigerant circuit (10), and the indoor heat exchangers (7) ,. Evaporates at. Then, they are circulated so as to join each other in the gas line (9b) and return to the compressor (1).
At that time, the discharge gas (hot gas) defrosts the outdoor heat exchanger (3) and increases the condensation capacity of the outdoor heat exchanger (3) by utilizing the stored heat of the heat storage tank (11). It is designed to shorten the defrost operation time.

The feature of the present invention relates to the operation control during the cold storage heat operation described above and the normal cooling and cold storage heat simultaneous operation. The operation control will be described below with reference to each flowchart. Incidentally, FIG. 13 is a flowchart showing the control contents during the cold storage heat operation of this device (including simultaneous operation with normal cooling), and FIG. 14 is the details of the control contents when the cold storage heat operation is performed independently. It is a flowchart showing.

First, as shown in the flow chart of FIG. 13, when the operation mode of the device is switched to the cold storage operation, after starting and initializing, it is determined in step S ₁ whether or not the indoor unit is thermo-on. . That is, if the indoor unit is thermo-off, the cold heat storage operation is performed independently, and if the indoor unit is thermo-on, normal cooling and cold heat storage simultaneous operation are performed. And
If the indoor unit is thermo-ON in this step S ₁ , the normal cooling and cold storage heat simultaneous operation state is started, and the control proceeds to step S ₂ and subsequent steps, while if the indoor unit is thermo-OFF, the cold storage heat is independently operation state is started, the process proceeds to the control of step S ₁₀ follows.

Therefore, first described during cold storage heat operation step S ₁₀ follows. After the indoor unit in Step S ₁ is that is not thermo sensed, in step S _10, the first timer is set, then the routine goes to Step S _11, the operating frequency Fk of the compressor during cold storage heat operation ' after There is calculated, the flow proceeds to step S _6, whether or not changes the thermo-off state of the indoor unit is determined. Then, the flow proceeds to step S ₇ in the case where the indoor unit is thermo-off continues, the indoor unit is determined whether or not thermo-on, if you are thermo-off proceeds to step S _9, in step S ₁₀ set the first timer is determined whether the time is up, the process returns to the step S ₆ until the time is up, the above-described operation is repeated. After that, when the first timer times out, the process moves from step S ₉ to step S ₁₀ , and the above-described operation is repeated. That is, when the indoor unit is in the thermo-off state, the cold heat storage operation is performed, and at the same time, the operating frequency of the compressor (1) is calculated every time the first timer times up. Accordingly, it will be described with reference to the flowchart shown in FIG. 14 for processing (step S ₁₁₎ of the operating frequency of the compressor (1) during the cold storage heat operation.

As shown in this flowchart, first, cold quantity to be obtained during cold storage heat operation ends in step S _21, that is, sets the target cold quantity (IPFS). The target amount of cold heat storage (IPFs) set here is set according to the outside air temperature during the day, and also includes the amount of remaining ice when ice remains in the heat storage tank (11). Therefore, the ice making amount actually generated during the cold storage heat operation is a value obtained by subtracting the remaining ice amount. That is, the water level sensor (Cl) arranged in the heat storage tank (11) detects the amount of remaining ice, and the detection signal is transmitted to the ice making amount detecting means (62), whereby the target amount of stored cold heat (IPFs) ) Is subtracted from the remaining ice amount to obtain the actual ice-making amount. The target amount of stored cold heat (IPFs) is represented by the volume percentage of the amount of ice in the heat storage tank (11).

Next, the target cold quantity obtained in step S ₂₁ (IPFs)
Determining the operation frequency Fk 'of the compressor (1) in step S ₂₂ based on. Here, the cool storage heat time setting means (61) has previously set the cool storage heat operation time to 8 hours or the like, or has set the cool storage heat operation end time, and the number of hours until that time, that is, the cool storage heat Calculate it by calculating the remaining time of thermal operation. Then, the detection signals from the cold storage heat time setting means (61) and the ice making amount detection means (62) are transmitted to the calculation means (63), and the calculation means (63) causes the cold storage heat time setting means (61) to set set time above the target cold quantity obtained in step S ₂₁ (I
Minimum operating frequency F of compressor (1) required to obtain PFs)
k'is calculated. The operating frequency Fk 'is calculated by the calculating means (63) by the following equation.

Fk ′ = (c ₂ / A) (IPFs−IPF) −c ₁ … c ₁ : Constant (= 67) c ₂ : Constant (= 18) IPFs: Cold storage heat quantity at the end of cold storage heat operation A = CTDF−C ₃ (CTDF: cold storage heat operating time remaining (Hr), C _3: constant (= 0.5)) as a limit where, a = 0.2 also when a ≦ 0.2, where calculated the operating frequency Fk ',
When Fk '≤ 50 (Hz), set Fk' = 50 (Hz) so that the natural frequency of the compressor (1) is avoided and other problems are not caused in the low frequency range. FK ′ ≧ 117.
At 5 (Hz), FK 'is set to 135 (Hz), and it is set to perform the acceleration charge operation that accelerates the ice making speed. Based on the operating frequency Fk 'calculated by the calculating means (63) as described above, the signal from the calculating means (63) is changed to the operation control means (6).
4), the operation of the compressor (1) is controlled by the operation of the operation control means (64), and the cold storage operation is started.

Next, a step as a means for correcting this operating frequency Fk '
S ₂₃ for the following control will be described.

Step S ₂₃ the predetermined time interval is cold storage heat operating time remaining by timer, i.e. are counted in 12-minute intervals of the first timer is set in step S _10, after a lapse of the predetermined time, in step S _24, the The amount of cold storage heat stored in the heat storage tank (11) is sampled during the counting time. Then, using the above equation again, step S ₂₅
In the compression required to ice and the remaining required ice quantity to obtain the first in cold storage heat operating time remaining to be determined by the detected time with the timer of step S ₂₁ in the determined target cold quantity (IPFS) Minimum operating frequency of machine (1)
Fk 'is calculated. After that, the process proceeds to step S _26, 'for, set operation frequency Fk at step S _22' The step S ₂₅ the operating frequency calculated in Fk whether requiring a change in comparison with is determined, the changes compressor proceeds to step S ₂₇ a (1) operating frequency Fk 'of change control if necessary, then performs the same control as described above is returned to step S ₂₃ again. On the other hand, 'if it does not require changes, as the operation frequency Fk' operating frequency Fk previously calculated in the step S ₂₆ returns to step S ₂₃ at. That is, the first timer operation in step S ₂₃ to S ₂₇ are performed for each time is up set at the step S ₁₀ as described above, in the above as the correction of the operating frequency is made every 12 minutes Then, the compressor (1) first set in steps S ₂₁ and S ₂₂
The initial operating frequency and the previous operating frequency set in the step S ₂₅ of appropriate, be corrected, or the cooling operation is performed during the thermal storage operation, the compressor following the change of situation, such as when the outside air temperature changes Change the operating frequency (load) in (1). Therefore, the target ice amount set in the step S ₂₁ (IPFs) can be surely obtained at the time of cold storage heat operation end.

Fig. 15 shows the relationship between the required time for cold storage heat and the required ice-making amount at each operating frequency Fk '. If the cold storage heat time (vertical axis) and the ice making amount obtained from the remaining ice amount (horizontal axis) are determined based on this figure, the lowest operating frequency of the compressor (1) is determined, so the cold storage operation is performed. The operating frequency is calculated from the remaining time, etc.

In this way, for the control of the cold storage heat in the independent operation, the operation is performed in the region where the operating frequency of the compressor (1) is as low as possible by using the maximum time during which the cold storage heat can be operated.
The ice-making operation is performed while operating with a high coefficient of performance and reducing the power consumption. Further, since the operating frequency of the compressor (1) is appropriately corrected according to the change in the situation during the cold storage heat operation, it is possible to obtain an accurate amount of cold storage heat.

Next, when it is determined in step S ₁ in FIG. 13 that the indoor unit is thermo-ON, that is, control of simultaneous normal cooling and cold storage heat operation will be described.

First, although a control flow is not shown, when the normal cooling and cold storage heat simultaneous operation is started, the start signal is transmitted to the maximum opening setting means (52), and the maximum opening setting means (52) is operated. The maximum opening (second maximum opening) of the indoor electric expansion valve (6), which has been set to the maximum opening (first maximum opening) of 2000 pls during the normal cooling operation until then, is set to 1250 pls. That is, when all of the following conditions are satisfied, the maximum opening degree of the indoor electric expansion valve (6) is set to the second maximum opening degree that is approximately half the first maximum opening degree.

・ Normal cooling and cold storage heat simultaneous operation mode ・ Cooling heat storage operation ・ Indoor unit is in thermo-ON state The maximum opening of the indoor electric expansion valve (6) is set small with these upper limits as IN conditions, and the flow rate of the refrigerant is suppressed. In this way, the saturation temperature Te equivalent to the evaporation pressure is prevented from rising significantly, and the temperature difference between the freezing temperature of the water in the heat storage tank (11) and the freezing temperature can be sufficiently secured to obtain a sufficient heat storage amount during this heat storage operation. To be able to

When any of the following conditions is satisfied, the maximum opening degree of the indoor electric expansion valve (6) is returned to the first maximum opening degree (2000 pls opening degree).

・ Cold heat storage operation is released ・ Indoor unit is in thermo-off state Also, in this normal cooling and cold heat storage simultaneous operation, the capacity control of the compressor (1), that is, the operating frequency control, is performed and the evaporating pressure equivalent saturation temperature Te Constant control is performed. Hereinafter, this control will be described.

First, in step S ₁ in FIG. 13, the indoor heat exchanger (7)
If the thermostat is turned on, the second timer is set in step S ₂ (for example, 20 seconds), and then the normal cooling and cold storage heat are performed simultaneously during the predetermined time until the set second timer expires. proceeds to step S ₃ to S ₅ as compressor operation control. In step S ₃ with the detection signal of the pressure sensor (SP) is sent to the evaporation temperature detection means (53), by the evaporation temperature detection means (53), the optimum evaporation pressure corresponding saturation temperature Tes (hereinafter the target saturation temperature ) Is calculated based on the following equation.

Tes = -6− (FT−50) × 0.025 ... Next, in order to obtain this target saturation temperature Tes, the increase / decrease amount ΔFk of the operating frequency of the compressor is calculated in step S ₄ .
Increase / decrease in the operating frequency of the compressor in step S ₄ Δ
Fk is calculated by the following equation.

ΔFk = Kc [{e (t) -e (t-Δtc)} + Δtc / 2Ti {e (t) + e (t-tc)}] ... e (t): Te (t) -Tes (t) Δtc: Sampling time Kc: Gain Ti: Integration time Then, in step S ₅ , the increase / decrease amount of the operating frequency of the compressor is added / subtracted to determine the operating frequency Fk of the compressor.

Fk = Fk (t−ΔTc) + ΔFk ... The operating frequency of the compressor (1) thus determined
The operating capacity of the compressor (1) is controlled based on Fk, and the vapor pressure equivalent saturation temperature is maintained at an optimum constant value.

Then, from step S ₅ to step S ₆ , it is determined whether the thermo-on state of the indoor unit has been changed.If the thermo-on state remains, the process proceeds to step S ₇ and it is determined again whether or not the indoor unit is thermo-on. is, in the case of thermo proceeds to step S _8, the second timer is determined whether or not the time is up, step S ₆ until the time is up
On the other hand, when the time is up, the process returns to step S ₂ and the above-described operation is repeated. That is, every 20 seconds of the second timer, the operating frequency of the compressor (1) is calculated so that Te reaches the target value, and the capacity of the compressor (1) is controlled to the frequency.

Further, although not shown, after the evaporation pressure equivalent saturation temperature Te is optimized by controlling the maximum opening of the indoor electric expansion valve (6) and the operating frequency of the compressor (11) as described above,
When the cooling load becomes large, that is, when the evaporation pressure equivalent saturation temperature Te rises, the temperature detected by the evaporation temperature detecting means (53) becomes equal to or higher than a predetermined temperature, and the capacity detecting means (5
When it is detected by 4) that the capacity of the compressor has become maximum, the detection signals from the evaporation temperature detecting means (53) and the capacity detecting means (54) are the maximum opening regulating means (5
5), and as described above, the opening degree of the indoor electric expansion valve (6) whose maximum opening degree (1250 pls) (second maximum opening degree) is changed.
The opening of 500 pls is set to the maximum (3rd maximum opening). That is, by satisfying the following two conditions, the maximum opening degree of the indoor electric expansion valve (6) is set to the third maximum opening degree which is smaller than the second maximum opening degree, and the evaporation pressure equivalent saturation temperature Te is lowered. Try to get a sufficient amount of cold storage heat.

-The maximum opening of the indoor electric expansion valve is set to the second maximum opening.

・ Te> -5 ° C and Fk ≥ 130Hz, or Fk> 107.5Hz and accelerated cold storage operation.

(The IN condition for accelerated cold storage operation is Fk '> 117.5Hz, and OUT
On the other hand, the condition is Fk '<95Hz).
As the T condition, the third maximum opening degree control of the indoor electric expansion valve (6) is released.

-Release of control conditions for the second maximum opening-Fk <85Hz and acceleration cold storage operation release-Fk <65Hz and acceleration cold storage operation start Then, the above-mentioned control is repeated.

As described above, in the operation control device and the operation control method of the heat storage type air conditioner in the present example, the cold storage heat operation remaining time and the cold storage heat amount are detected, and the remaining time is used to the maximum, the compressor By making the operation of (1) as low as possible, the compressor (1) can obtain an operating state in a region where the coefficient of performance is high, and energy saving is improved. In addition, by setting the maximum operating frequency of the indoor electric expansion valve (6) and the compressor (1) in order to keep the saturation temperature Te equivalent to the evaporation pressure constant, the shortage of cold storage heat and the generation of drafts as in the conventional case, Of the indoor heat exchanger (7) is prevented from freezing.

The value of the pulse signal for each maximum opening of the indoor electric expansion valve (6) can be set as appropriate.

Also, the main refrigerant circuit is not limited to that of this embodiment.

(Effect of the Invention) As described above, in the invention of claim (1), the maximum opening degree of the main pressure reducing valve is set during the normal cooling operation by the operation of the maximum opening setting means during the normal cooling and cold heat simultaneous operation. Is set to a predetermined second maximum opening smaller than the first maximum opening to suppress the increase in the evaporation pressure-equivalent saturation temperature, and to prevent the temperature of the refrigerant and the freezing temperature of water in the heat exchanger for heat storage from increasing. Make sure that the difference is sufficient and prevent the amount of ice making from decreasing. Further, when the capacity detection means detects the maximum capacity operation of the compressor and the evaporation pressure equivalent saturation temperature detected by the evaporation temperature detection means becomes equal to or higher than a preset set temperature, the operation of the maximum opening control means causes The maximum opening of the pressure reducing valve is set to a predetermined third maximum opening, which is smaller than the second maximum opening, to suppress the rise of the evaporation temperature equivalent saturation temperature due to the increase of the cooling load, and obtain a sufficient amount of ice making. To be controlled. In this way, by adjusting the opening of the main pressure reducing valve, the saturation temperature equivalent to the evaporating pressure is always controlled to be constant, and the problems caused by the size of the cooling load are eliminated, and a sufficient amount of cold storage heat can be obtained, and at the same time, the heat on the use side Draft and freezing of the exchanger are avoided, and continuous operation is possible, improving the reliability of the device.

Further, in the invention of claim (2), during the normal cooling and the cold storage heat simultaneous operation, the capacity control means receives the output signal of the evaporation temperature detection means so that the evaporation pressure equivalent saturation temperature becomes a preset target value. Controls compressor capacity. As a result, vertical movement of the saturation temperature equivalent to the evaporation pressure can be suppressed, accurate cold storage heat operation can be performed, and freezing of the use-side heat exchanger can be prevented.

Further, according to the invention of claim (3), both normal cooling and cold storage heat can be reliably performed by controlling the opening degree of the main pressure reducing valve and the capacity of the compressor by both actions described in claims (1) and (2). Can drive.

Further, in the invention of claim (4), during the cold storage heat operation, the cold storage heat time setting means sets the cold storage heat operation time, and the ice making amount detection means detects the necessary ice making amount in the heat storage tank, and Output signals from the time setting means and the ice making amount detecting means are sent to the calculating means, and the calculating means calculates the minimum operating frequency of the compressor required to make the required ice making amount in the set time, and then from the calculating means. Is sent to the operation control means, and the operation control means controls the operation of the compressor based on the compressor operation frequency calculated by the operation means.
As a result, the compressor can be operated at the lowest frequency by making the maximum use of the cold storage heat operation time, so it is possible to drive the compressor in a region with a high coefficient of performance, which results in a reduction in power consumption. Energy efficiency is improved.

Finally, in the inventions described in claims (5) and (6), the above claims (1) to (1) to
By the action described in (3) and by the action described in claim (4) during the cold heat storage operation, the degree of closure of the main pressure reducing valve and the operating frequency of the compressor are controlled, and an optimum operating state is obtained.

[Brief description of drawings]

FIG. 1 is a block diagram showing the configuration of the invention described in claim (1). FIG. 2 is a block diagram showing the configuration of the invention described in claim (2). FIG. 3 is a block diagram showing the configuration of the invention described in claim (4). 4 to 15 show an embodiment of the present invention, FIG. 4 is a refrigerant piping system diagram showing the overall configuration of the apparatus, and FIGS. 5 to 8 show respective operation modes in the cooling operation, 5 is a normal cooling operation, FIG. 6 is a cold storage heat operation, FIG. 7 is an explanatory view showing refrigerant circulation in a normal cooling and cold storage heat simultaneous operation, and FIG. 8 is a cold storage heat recovery operation. 9 to 12 show each operation mode in the heating operation, FIG. 9 is a normal heating operation, FIG. 10 is a heat storage / heat storage operation, and FIG. 11 is a normal heating and heat storage / heat storage simultaneous operation, FIG. The figure is an explanatory view showing a circulation path of a refrigerant in the warm storage heat recovery defrost operation. FIG. 13 is a flow chart showing the control content of this device, FIG. 14 is a flow chart showing the control content of the controller during cold storage heat operation, and FIG. 15 is a diagram showing the relationship between the heat storage required time and the amount of residual ice. Is. (1) ...... Compressor (3) …… Outdoor heat exchanger (heat source side heat exchanger) (6) …… Indoor electric expansion valve (main pressure reducing valve) (7) …… Indoor heat exchanger (use side heat Exchanger) (9) …… Refrigerant piping (10) …… Main refrigerant circuit (11) …… Heat storage tank (12) …… Heat storage heat exchanger (14) …… Heat storage electric expansion valve (decompression mechanism for cold storage heat) (51) …… Switching means (52) …… Maximum opening setting means (53) …… Evaporation temperature detecting means (54) …… Capacity detecting means (55) …… Maximum opening regulating means (56) …… Capacity Control means (61) …… Cold storage heat time setting means (62) …… Ice making amount detection means (63) …… Calculation means (64) …… Operation control means

 ─────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-59-208366 (JP, A) JP-A-64-10067 (JP, A) JP-A-64-10068 (JP, A)

Claims (6)

[Claims] 1. A compressor (1) having a variable capacity, a heat source side heat exchanger (3), a main pressure reducing valve (6) having a variable opening degree, and a use side heat exchanger (7) are connected to a refrigerant pipe (9). ), A main refrigerant circuit (10) connected in sequence, and a heat storage tank (1) for storing ice for cold heat storage.
1) and a heat storage heat exchanger (12) arranged in the heat storage tank (11) and connected to the main refrigerant circuit (10) for exchanging heat between the refrigerant and the heat storage medium. And a decompression mechanism (14) for storing cold heat, and at least during normal cooling operation, the heat source side heat exchanger (3)
The liquid refrigerant condensed in circulates only in the main refrigerant circuit (10), is decompressed by the main pressure reducing valve (6), evaporates in the utilization side heat exchanger (7) and returns to the compressor (1). During the cold storage heat operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is decompressed by the cold storage heat decompression mechanism (14), evaporated in the heat storage heat exchanger (12), and then stored in the compressor (1). During the cold heat recovery operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is supercooled in the heat storage heat exchanger (12) from the main refrigerant circuit, and then circulates so as to return to the main refrigerant. It circulates so as to evaporate in the utilization side heat exchanger (7) of the circuit (10) and return to the compressor (1), and is condensed in the heat source side heat exchanger (3) during normal cooling and cold storage simultaneous operation. Part of the liquid refrigerant evaporates in the use side heat exchanger (7) of the main refrigerant circuit (10), while the rest of the liquid refrigerant evaporates in the heat storage heat exchanger (12). A heat storage type air conditioner equipped with a switching means (51) for switching the circuit connection so as to return to the compressor (1) respectively, which is the maximum of the main pressure reducing valve (6) during normal cooling and cold storage simultaneous operation. A maximum opening setting means (52) for setting the opening to a predetermined second maximum opening smaller than the first maximum opening set during normal cooling operation, and an evaporation temperature detecting means (52) for detecting the saturation temperature equivalent to the evaporation pressure ( 53), a capacity detecting means (54) for detecting the maximum capacity operation of the compressor (1), the capacity detecting means (54) detecting the maximum capacity operation of the compressor (1), and the evaporation temperature. When the vapor pressure equivalent saturation temperature detected by the detection means (53) becomes equal to or higher than a preset set temperature, the maximum opening of the main pressure reducing valve (6) is set to a predetermined third maximum opening smaller than the second maximum opening. A heat storage type air conditioner characterized by being provided with a maximum opening control means (55) to be set. The operation control device. 2. A compressor (1) having a variable capacity, a heat source side heat exchanger (3), a main pressure reducing valve (6) and a use side heat exchanger (7) are sequentially connected by a refrigerant pipe (9). Become a main refrigerant circuit (10)
And a heat storage tank (11) for storing ice for cold storage, while being arranged in the heat storage tank (11) and connected to the main refrigerant circuit (10), the refrigerant and the heat storage medium are connected. A heat storage heat exchanger (12) for performing heat exchange and a cold storage heat decompression mechanism (14) are provided, and at least during normal cooling operation, the heat source side heat exchanger (3).
The liquid refrigerant condensed in circulates only in the main refrigerant circuit (10), is decompressed by the main pressure reducing valve (6), evaporates in the utilization side heat exchanger (7) and returns to the compressor (1). During the cold storage heat operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is decompressed by the cold storage heat decompression mechanism (14), evaporated in the heat storage heat exchanger (12), and then stored in the compressor (1). During the cold heat recovery operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is supercooled in the heat storage heat exchanger (12) from the main refrigerant circuit, and then circulates so as to return to the main refrigerant. It circulates so as to evaporate in the utilization side heat exchanger (7) of the circuit (10) and return to the compressor (1), and is condensed in the heat source side heat exchanger (3) during normal cooling and cold storage simultaneous operation. Part of the liquid refrigerant evaporates in the use side heat exchanger (7) of the main refrigerant circuit (10), while the rest of the liquid refrigerant evaporates in the heat storage heat exchanger (12). A heat storage type air conditioner equipped with a switching means (51) for switching the circuit connection so as to return to the compressor (1) respectively, and detects a saturation temperature equivalent to an evaporation pressure during normal cooling and cold storage simultaneous operation. Evaporation temperature detection means (53) and a capacity for receiving the output signal of the evaporation temperature detection means (53) and controlling the capacity of the compressor (1) so that the saturation temperature equivalent to the evaporation pressure becomes a preset target value. An operation control device for a heat storage type air conditioner, comprising: a control means (56). 3. An operation control device for a heat storage type air conditioner according to claim 1, wherein an evaporation pressure equivalent saturation temperature is set to a preset target value in response to an output signal of an evaporation temperature detecting means (53). An operation control device for a heat storage type air conditioner comprising a capacity control means (56) for controlling the capacity of the compressor (1). 4. A compressor (1) having a variable capacity, a heat source side heat exchanger (3), a main pressure reducing valve (6) and a use side heat exchanger (7) are sequentially connected by a refrigerant pipe (9). Become a main refrigerant circuit (10)
And a heat storage tank (11) for storing ice for cold storage, while being arranged in the heat storage tank (11) and connected to the main refrigerant circuit (10), the refrigerant and the heat storage medium are connected. A heat storage heat exchanger (12) for performing heat exchange and a cold storage heat decompression mechanism (14) are provided, and at least during normal cooling operation, the heat source side heat exchanger (3).
The liquid refrigerant condensed in circulates only in the main refrigerant circuit (10), is decompressed by the main pressure reducing valve (6), evaporates in the utilization side heat exchanger (7) and returns to the compressor (1). During the cold storage heat operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is decompressed by the cold storage heat decompression mechanism (14), evaporated in the heat storage heat exchanger (12), and then stored in the compressor (1). During the cold heat recovery operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is supercooled in the heat storage heat exchanger (12) from the main refrigerant circuit, and then circulates so as to return to the main refrigerant. It circulates so as to evaporate in the utilization side heat exchanger (7) of the circuit (10) and return to the compressor (1), and is condensed in the heat source side heat exchanger (3) during normal cooling and cold storage simultaneous operation. Part of the liquid refrigerant evaporates in the use side heat exchanger (7) of the main refrigerant circuit (10), while the rest of the liquid refrigerant evaporates in the heat storage heat exchanger (12). A heat storage type air conditioner equipped with a switching means (51) for switching the circuit connection so as to return to the compressor (1), respectively, wherein a cold storage heat time setting means for setting a cold storage heat operation time during cold storage heat operation. (61), an ice making amount detecting means (62) for detecting a necessary ice making amount in the heat storage tank (11), and output signals from the cold heat storage time setting means (61) and the ice making amount detecting means (62). Calculating means (63) for calculating the minimum operating frequency of the compressor (1) required to make the required ice making amount in a set time.
And an operation control means (64) for receiving the output signal from the arithmetic means (63) and controlling the operation of the compressor (1) based on the compressor operating frequency calculated by the arithmetic means (63). An operation control device of a heat storage type air conditioner characterized by the above. 5. An operation control device for a heat storage type air conditioner according to any one of claims (1), (2) and (3), wherein a cold storage heat time setting means for setting a cold storage heat operation time during cold storage heat operation ( 61), an ice making amount detecting means (62) for detecting a necessary ice making amount in the heat storage tank (11), and the cold storage heat time setting means (6).
1) and an arithmetic means (63) for receiving the output signals from the ice making amount detecting means (62) and calculating the minimum operating frequency of the compressor (1) required to make the required ice making amount in a set time.
And an operation control means (64) for receiving the output signal from the arithmetic means (63) and controlling the operation of the compressor (1) based on the compressor operating frequency calculated by the arithmetic means (63). An operation control device for a heat storage type air conditioner characterized by being provided. 6. A compressor (1) having a variable capacity, a heat source side heat exchanger (3), a main pressure reducing valve (6) having a variable opening degree, and a use side heat exchanger (7) are connected to a refrigerant pipe (9). ), A main refrigerant circuit (10) connected in sequence, and a heat storage tank (1) for storing ice for cold heat storage.
1) and a heat storage heat exchanger (12) arranged in the heat storage tank (11) and connected to the main refrigerant circuit (10) for exchanging heat between the refrigerant and the heat storage medium. And a decompression mechanism (14) for storing cold heat, and at least during normal cooling operation, the heat source side heat exchanger (3)
The liquid refrigerant condensed in circulates only in the main refrigerant circuit (10), is decompressed by the main pressure reducing valve (6), evaporates in the utilization side heat exchanger (7) and returns to the compressor (1). During the cold storage heat operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is decompressed by the cold storage heat decompression mechanism (14), evaporated in the heat storage heat exchanger (12), and then stored in the compressor (1). During the cold heat recovery operation, the liquid refrigerant condensed in the heat source side heat exchanger (3) is supercooled in the heat storage heat exchanger (12) from the main refrigerant circuit, and then circulates so as to return to the main refrigerant. It circulates so as to evaporate in the utilization side heat exchanger (7) of the circuit (10) and return to the compressor (1), and is condensed in the heat source side heat exchanger (3) during normal cooling and cold storage simultaneous operation. Part of the liquid refrigerant evaporates in the use side heat exchanger (7) of the main refrigerant circuit (10), while the rest of the liquid refrigerant evaporates in the heat storage heat exchanger (12). A method for controlling the operation of a heat storage type air conditioner comprising switching means (51) for switching the circuit connection so as to return to the compressor (1), respectively. After setting by the setting means (61), the ice making quantity detecting means (62) detects the necessary ice making quantity in the heat storage tank (11), and then the calculating means (63) makes the necessary ice making quantity in the cold storage heat operation time. The minimum operating frequency of the compressor (1) required for the operation is calculated, and the operation control means (64) controls the operation of the compressor (1) based on the calculated operating frequency of the compressor, while normal cooling and cold storage During the simultaneous heat operation, the maximum opening setting means (52) sets the maximum opening of the main pressure reducing valve (6) to a predetermined second maximum opening smaller than the first maximum opening set during the normal cooling operation. , The degree of superheat control of the opening of the main pressure reducing valve (6), and the evaporation temperature The detection means (53) detects the saturation temperature corresponding to the evaporation pressure, and the capacity control means (56) controls the capacity of the compressor (1) so that the saturation temperature corresponding to the evaporation pressure reaches a predetermined target value. When the detecting means (54) detects the maximum capacity operation of the compressor (1) and the saturation temperature equivalent to the evaporation pressure becomes equal to or higher than a predetermined temperature, the maximum opening regulating means (55) causes the maximum pressure reducing valve (6) to reach the maximum. An operation control method for a heat storage type air conditioner, characterized in that the opening is set to a third maximum opening smaller than the second maximum opening.