JPH0784964B2 - Operation control device for heat storage type air conditioner - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an operation control device for a heat storage type air conditioner, and more particularly to a measure for ensuring a cold storage heat capacity and improving operating efficiency during simultaneous cooling and cold storage heat operation. .

(Prior Art) Conventionally, as disclosed in, for example, Japanese Patent Application Laid-Open No. 59-208364, a refrigerant circuit formed by connecting a compressor, a heat source side heat exchanger, a pressure reducing valve and a use side heat exchanger, and a cold storage In a heat storage type air conditioner equipped with a heat storage tank having a heat storage medium capable of heating and a heat storage heat exchanger for applying cold heat to the heat storage tank by heat exchange with the refrigerant of the refrigerant circuit, an evaporating action in the use side heat exchanger By enabling simultaneous cooling and cold storage heat operation that simultaneously performs the cold storage heat operation in the heat storage heat exchanger, while performing the indoor cooling operation, the heat storage heat exchanger side stores the cold heat when the cooling load is small. It is a well-known technique to improve the operation efficiency as a whole.

(Problems to be solved by the invention) By the way, normally, the cold storage heat operation of storing cold heat in the heat storage tank is performed at night when the electricity rate is low, but even at night, there is a case where there is a demand for cooling indoors due to continuation of work. is there. In such a case, by using the above-mentioned conventional one, it is possible to meet the present cooling demand while storing the cold heat for tomorrow.

However, the above-mentioned conventional device does not take any means for adjusting the ratio of the capacity of the heat exchanger on the utilization side to the capacity of the heat storage heat exchanger. Therefore, the capacity tends to be biased toward one of the heat exchangers, and in particular, it often meets the demand of the normal use side heat exchanger, so that there is a possibility that the planned amount of cold storage heat cannot be secured at night.

On the contrary, when high-performance driving is performed even though there is a surplus of capacity, the so-called coefficient of performance may be deteriorated.

The present invention has been made in view of such a point, and an object thereof is to provide a means for distributing the capacity to the use side exchanger side and the heat storage heat exchanger side with reference to the necessary capacity of the heat storage heat exchanger. By doing so, it is intended to secure the amount of cold storage heat and improve the operation efficiency.

(Means for Solving the Problem) In order to achieve the above-mentioned object, the solution means of the present invention is required from the current amount of cold storage heat of the heat storage tank while controlling the capacity of the compressor so that the suction saturation temperature converges to a target value. And calculate the target value of the saturation temperature equivalent to the suction pressure necessary to secure the required cold storage heat capacity,
The opening degree of the pressure reducing valve of the heat exchanger on the utilization side is limited so as to satisfy the saturation temperature equivalent to the suction pressure.

Specifically, the first solving means is, as shown in FIG. 1 (not including the broken line portion), the variable capacity compressor (1), the heat source side heat exchanger (3), the use side electric expansion valve. A refrigerant circuit (10) in which (6) and a heat exchanger (7) on the use side are sequentially connected,
Heat storage tank (11) having heat storage medium (W) capable of storing cold heat
And a heat storage heat exchanger (12) for applying cold heat to the heat storage tank (11) by heat exchange with the refrigerant in the refrigerant circuit (10).

Then, as an operation control device of the heat storage type air conditioner, a saturation temperature detecting means (SP) for detecting a saturation temperature equivalent to the suction pressure of the refrigerant, and an intake air detected by the saturation temperature detecting means (SP) at predetermined intervals. A capacity control means (51) for setting and controlling the operating capacity of the compressor (1) is provided so that the saturation temperature equivalent to the pressure converges to its target value.

Furthermore, at the time of simultaneous cooling and cold storage heat operation in which the evaporation action by the use side heat exchanger (7) side and the cold storage heat action by the heat storage heat exchanger (12) are performed simultaneously, the heat storage medium (W in the heat storage tank (11) ) Cold storage amount detection means (Cl) for detecting the current cold storage amount
And a heat storage heat exchanger (12) based on the operating capacity of the compressor (1) controlled by the capacity control means (51) at the time of the previous sampling, which receives the output of the cold storage amount detection means (Cl).
And a target value calculation means (52) for calculating a target value of the saturation temperature equivalent to the suction pressure so that the cold storage heat capacity at the required cold storage heat capacity obtained from the difference between the target cold storage heat quantity of the heat storage tank (11) and the current cold storage heat capacity. And an opening degree limiting means (53) for limiting the opening degree of the use side electric expansion valve (6) so that the suction pressure equivalent saturation temperature converges to the target value calculated by the target value calculating means (52). It is configured to be provided.

A second solving means is the opening limiting means (53) in the first solving means, in which the present operating capacity of the compressor (1) is the maximum and the present value and the target value of the intake pressure equivalent saturation temperature are set. When the difference is greater than or equal to a predetermined value, the maximum opening value of the use side electric expansion valve (6) is reduced.

As shown in FIG. 1 (including the broken line portion), the third solving means is, in addition to the above first or second solving means, when the operating capacity of the compressor (1) is below a certain value, A maximum opening increasing means (54) for changing the maximum opening value of the use side electric expansion valve (6) is provided.

(Operation) With the above configuration, in the invention of claim (1), the suction pressure equivalent saturation temperature detected by the saturation temperature detecting means (SP) by the capacity control means (51) is set at predetermined time intervals. The operating capacity of the compressor (1) is adjusted so that it converges to the target value, and the target value calculation means (52) causes the heat storage heat exchanger (12).
The target value of the saturation temperature equivalent to the suction pressure is calculated so that the cold storage heat capacity at becomes the required cold storage heat capacity. Then, the opening degree control means (53) limits the maximum opening degree of the use side electric expansion valve (6) so that the suction pressure equivalent saturation temperature converges to the target value.

That is, since the value of the saturation temperature equivalent to the suction pressure is controlled so as not to deviate from the value capable of maintaining the required cold storage heat capacity,
Even if a cooling request is made during the cold storage operation at night or the like, the cooling operation is performed in accordance with the cooling request while surely ensuring the scheduled cool storage heat. In addition, during that time, the operating capacity of the compressor (1) is adjusted so that the saturation temperature equivalent to the suction pressure converges to the target value, so that operation exceeding the required capacity is avoided. Therefore, the planned amount of cold storage heat is secured and the operation efficiency as a whole is improved.

According to claim (2), in the invention according to claim (1), the operating capacity of the compressor (1) is maximized and the suction pressure equivalent saturation temperature and its target value are set by the opening degree restricting means (53). When the difference between and exceeds a predetermined value, the user-side electric expansion valve (6)
Is limited so that the intake pressure equivalent saturation temperature is about to deviate from the target value because there is not enough capacity, the capacity distribution to the use side heat exchanger (6) As a result, the reduction of the cold storage heat capacity on the heat storage heat exchanger (12) side is suppressed. Therefore, claim (1)
The invention of can be effectively implemented.

In the invention of claim (3), the above claim (1) or (2)
In addition to the invention described above, the maximum opening degree increasing means (54) changes the maximum opening degree of the use-side electric expansion valve (6) to increase when the operating capacity of the compressor (1) is below a certain value. Therefore, when the capacity is sufficient, the restriction on the distribution of the capacity to the indoor side is relaxed, and a predetermined cooling request can be met. Therefore, in addition to the invention of claim (1) or (2), the cooling capacity is secured.

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

FIG. 2 shows an overall configuration of an air conditioner according to an embodiment of the present invention, in which a plurality of indoor units (A), (B), ... Are connected to an outdoor unit (X), a so-called multi-type air. It is a harmony device.

In the outdoor unit (X), (1) is a variable capacity compressor in which the operating frequency is variably adjusted by the inverter (41), and (2) is switched as shown by the solid line in the figure during the cooling operation, and during the heating operation. A four-way switching valve that switches as shown by the broken line in the figure, (3) is an outdoor heat exchanger that is a heat source side heat exchanger that functions as a condenser during cooling operation, and as an evaporator during heating operation, and (4) is cooling during cooling operation. Adjust the flow rate,
An outdoor electric expansion valve that functions as a refrigerant pressure reducing valve during heating operation, (5) a receiver for adjusting the amount of refrigerant,
(8) is an accumulator for removing the liquid component in the suction refrigerant.

On the other hand, each of the indoor units (A), (B), ... Has the same configuration, and (6) functions as a pressure reducing valve during the cooling operation and is an indoor electric motor that is a use-side electric expansion valve that adjusts the refrigerant flow rate during the heating operation. The expansion valve (7) is an indoor heat exchanger that is a utilization side heat exchanger that functions as an evaporator during cooling operation and as a condenser during heating operation.

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

Further, in the device, a heat storage unit (Y) for storing cold heat or warm heat by exchanging heat with the refrigerant flowing through the main refrigerant circuit (10) or for utilizing the cold heat or heat storage is arranged. Has been done. 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),
A heat storage heat exchanger for exchanging heat between water (W) and a refrigerant, the heat storage heat exchanger (12) and the outdoor electric expansion valve (4) of the main refrigerant circuit (10) -indoor electric expansion The first bypass passage (13a) and the second bypass passage (13b) are connected to the liquid line (9a) between the valves (6) so that the refrigerant can flow therethrough. Then, the first bypass path (13
A heat storage electric expansion valve (14) for decompressing the refrigerant when cold heat is stored in water (W) is provided in a), and the second bypass path (13b) is provided with a second bypass path (13b). A first on-off valve (15) for opening and closing is installed.

Further, the first on-off valve (15) of the second bypass passage (13a)
− 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.

That is, during the cold heat storage operation, the liquid refrigerant is bypassed from the main refrigerant circuit (10) to the first bypass passage (13a), decompressed by the heat storage electric expansion valve (14), and evaporated by the heat storage heat exchanger (12). As a result, cold heat is applied to the water (W) to make ice.

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, and the above valves (2), (4),
(6) By switching the opening / closing of (14), (15), (16), (17) or adjusting the opening, the circulation path of the refrigerant is switched according to each operation mode.

Further, sensors are arranged in the device, (Thw) is arranged in the water of the heat storage tank (11), a water temperature sensor for detecting the water temperature Tw, and (Tha) is air of the outdoor heat exchanger (3). An outside air temperature sensor, which is arranged at the suction port and detects the outside air temperature Ta,
(Thi) is a cooling inlet sensor arranged on the upstream side of the junction of the liquid line (9a) with the second bypass passage (13b) during cooling operation, and (Tho) is the first bypass passage of the liquid line (9a). A cooling outlet sensor arranged on the downstream side of the joint portion with (13a) during cooling operation, (Ths) is a suction pipe sensor for detecting a suction pipe temperature, and (SP) is arranged in a gas line (9b). , A pressure sensor as a saturation temperature detecting means for detecting a high pressure side pressure during a heating cycle and a suction temperature equivalent saturation temperature Te during a cooling cycle, (Cl) is arranged near the water surface of the heat storage tank (11) to detect the water level Is a water level sensor as a cool storage amount detecting means for detecting the current cool storage heat amount Qn.

Further, as shown in FIG. 3, the heat storage tank (11) has a water supply device for controlling water supply in the heat storage tank (11) when the water (W) in the heat storage tank (11) is replaced. Is provided, and (3
1) has a water supply port (31a) opened above the heat storage tank (11), and a water supply pipe (32) for supplying water (W) from the water supply port (31a) to the heat storage tank (11), A manual opening / closing valve of the water supply pipe (31) which is normally opened, (33) a drain pipe for discharging water (W) from the heat storage tank (11), and (34) normally closed and the heat storage tank (11). Drainage valve that is opened only when the water (W) in
(35) is an overflow pipe of the heat storage tank (11), (36) is its drain pit, (37) is a water supply valve for controlling the supply of water (W) from the water supply pipe (31), When supplying water (W) from the water supply pipe (31) to the heat storage tank (11), the water supply valve (37) is opened until the water level in the heat storage tank (11) reaches a predetermined reference water level, It is closed when the standard water level is reached. Further, when the water level rises excessively during the water supply, excess water (W) is discharged from the overflow pipe (35).

The drain valve (34) and the water supply valve (37) are connected by a signal line of a controller (40) that controls the operation of the device, and the number of times the cold storage heat of the heat storage tank (11) is used is a constant value. When it reaches, the drain valve (34) is automatically opened and the heat storage tank (1
While discharging the water (W) in 1), it is judged that the drainage is completed after a certain time has passed from the start of drainage, and the open / close control of the water supply valve (37) controls the heat storage tank (11). By supplying water and replacing the water (W) in the heat storage tank (11), deterioration of the cold heat storage function due to contamination of the water (W) or the like is prevented. In other words, by automatically performing maintenance, it is possible to prevent forgetting to replace the water (W) during use and to save labor for water replacement.

Here, the circulation path of the refrigerant in each operation mode will be described. In the above air conditioner, during the cooling operation using ice heat, the four-way switching valve (2) is switched as shown by the solid line in the figure, as shown by the solid line arrow in FIG. 2, the outdoor electric expansion valve (4), the flow rate. Control valve (17), indoor electric expansion valve (6),
..., the first on-off valve (15) and the heat storage electric expansion valve (14) are opened, the second on-off valve (16) is closed, the operation is performed, and the refrigerant condensed in the outdoor heat exchanger (3) is discharged. After flowing through the first and second bypass passages (13a) and (13b) and being cooled by the heat storage heat exchanger (12) 4, the indoor electric expansion valve (6) returns to the main refrigerant circuit (10). It is decompressed by and is circulated so as to be evaporated in each indoor heat exchanger (7), ... And returned to the compressor (1).

On the other hand, during the ice making operation in which water (W) in the heat storage tank (11) is ice-stored to store cold heat, as shown by the broken line arrow in the figure, the outdoor electric expansion valve (4), the flow control valve (17), the heat storage electric The outdoor heat exchanger (3) is operated with the expansion valve (14) and the second opening / closing valve (16) opened, and the indoor electric expansion valves (6), ... And the first opening / closing valve (15) closed. The liquid refrigerant condensed in 1. flows by bypassing the first bypass passage (13a), is decompressed by the heat storage electric expansion valve (14), evaporates in the heat storage heat exchanger (12) and returns to the compressor (1). To circulate. At that time, the heat storage heat exchanger (12) exchanges heat with the refrigerant to make water (W), which is a heat storage medium, into ice to store cold heat.

Then, during the simultaneous cooling and cold storage heat operation in which the evaporation action by the indoor heat exchanger (7) and the cold storage heat action by the heat storage heat exchanger (12) are simultaneously performed, the operation is performed with only the first opening / closing valve (15) closed. The liquid refrigerant condensed in the outdoor heat exchanger (3) passes through the receiver (5) and then branches into the main refrigerant circuit (10) side and the first bypass path (13a) side, and each heat exchanger After being evaporated at (7), ... And (12) respectively, they are merged and circulated so as to return to the compressor (1).

Here, as a feature of the present invention, the control of the controller (40) during the cooling and cold storage heat simultaneous operation, will be described with reference to the flow chart of FIG. 4, the predetermined first set time in step S ₁ TM ₁ There waiting for the elapse, in step S _2, the target value of the intake pressure corresponding saturation temperature Te of obtaining the suction pressure equivalent saturation temperature Te at the previous sampling (hereinafter, the target evaporation temperature) in order to converge to Tes,
The control amount ΔFk of the operating capacity of the compressor (1) is calculated as follows.

That is, e (t) = Te−Tes, Δtc is a sampling time, Kc is a gain, and Ti is an integration time, and the following equation ΔFk = Kc [{e (t) −e (t−Δtc} + (Δtc / 2Ti) {E (t) + e (t-Δtc)}], where the integration time Ti is set as follows.

(I) | e (t) | <e ₁ Ti = ∞ However, when e ₁ = −0.005Ft + 1.65 (ii) | e (t) |> 10deg Ti = 5sec (iii) e ₁ ≤ | When e (t) | ≦ 10deg Ti = 60− (22/3) (| e (t) | −2.5) However, the lower limit value of Fk Fkmin = 50Hz Next, in step S ₃ , , The new capacity Fk of the compressor (1), the compressor (1) at the time of the previous sampling
The setting control is performed as the sum of the operating capacity Fk (t-Δtc) of the above and the capacity change amount ΔFk of the compressor (1).

Fk (t) = Fk (t−Δtc) + ΔFk Next, after performing the above control, in step S ₄ , a predetermined second set time TM ₂ longer than the first set time TM ₁ is passed. After waiting, in step S ₅ , the target value Tes of the saturation pressure equivalent saturation temperature Te is calculated by the following procedure.

That is, Qn is the amount of cold storage heat detected by the water level sensor (Cl), Qs is the target amount of cold storage heat, and TM is the remaining cold storage heat operation time.
If it is c, the required cold storage heat capacity Qr per unit time is expressed by the following equation Qr = (Qs-Qn) / TMc (1).

On the other hand, when the water temperature is Tw and the saturation temperature equivalent to the evaporation pressure in the heat storage heat exchanger (12) is Tew, the cold storage heat capacity Q of the heat storage heat exchanger (12) is expressed by the following formula Q = C ₁ · (Tw−Tew) It is represented by (2) (however, the temperature is converted into the dimension of capacity with a constant of C ₁ ).

When the suction pressure equivalent saturation temperature Te is controlled to the target evaporation temperature value Tes, Tes and the heat storage heat exchanger (12)
In consideration of the pressure loss of the pipe in the middle, the following equation Tes = Tew−C ₂ · Ft (3) is established between the vaporization pressure equivalent saturation temperature Tew in Eq.

Therefore, from the above equations (1) to (3), Tes = {Tw− (Qs−Qn) / TMc} / C ₁ −C ₂ · Ft (4), and the water temperature Tw, the current cold storage heat quantity Q, the compressor (1 ), The target evaporation temperature value Tes is calculated from the operating capacity Ft.

Then, the target evaporation temperature value Te under the control of the step S ₅
When calculating the s, in step S _6, waits for the second set third set time TM ₃ longer predetermined than the time TM ₂ has elapsed, the process proceeds to stiff S _7, at step S _7, the suction pressure equivalent The opening degree of the indoor electric expansion valve (6) is controlled so that the saturation temperature Te converges on the target evaporation temperature Tes.

That is, when Te−Tes ≧ C ₃ (C ₃ is a constant), the maximum opening value Amax of the indoor electric expansion valve (6) is lowered by one step (for example, a value of about 50 pulses) to increase the indoor electric expansion valve (6). Limit the opening. On the other hand, when the operating capacity Fk of the compressor (1) is Ft ≤ C ₄ (C ₄ is a constant of, for example, about 110 Hz), the maximum opening value Amax of the indoor electric expansion valve (6) is set to be increased by one step. Then, the restriction on the opening is relaxed. In addition,
The above control is performed at every predetermined sampling time (for example, about 2 minutes).

In the above flow, the capacity control means (51) for setting and controlling the operating capacity of the compressor (1) by steps S ₂ and S _{3 so} that the suction pressure equivalent saturation temperature Te converges to the target value Tes.
From step S ₅ , based on the operating capacity of the compressor (1) at the time of the previous sampling, the cold storage heat capacity of the heat storage heat exchanger (12) is the target cold storage heat quantity Qs of the heat storage tank (11) and the current cold storage capacity. Target value Tes of saturation temperature Te equivalent to suction pressure Te so that the required cold heat storage capacity Qr can be obtained from the difference with the heat quantity Qn
Target value calculation means (52) for calculating
An opening degree limiting means for limiting the opening degree of the use side electric expansion valve (6) so that the suction pressure equivalent saturation temperature Te converges to the target value Tes calculated by the target value calculating means (52) by S _7. (53) is configured.

Further, in the invention of claim (2), under the control of the step S _7, the current operating capacity of the compressor (1) is increased,
Further, when the difference between the current value of the saturation temperature Te corresponding to the suction pressure Te and the target value Tes is equal to or more than a predetermined value, the opening degree limiting means (5 that reduces the maximum opening value Amax of the use side electric expansion valve (6) by one step.
The function of 3) is configured.

Further, in the invention of claim (3), the control of step S _7, 1 step a maximum opening value Amax of the usage-side motor-operated expansion valve (6) when the operating capacity Fk is equal to or less than a predetermined value of the compressor (1) The maximum opening increasing means (54) for increasing the opening degree is configured.

Therefore, in the invention of claim (1), the suction pressure equivalent saturation temperature detected by the pressure sensor (saturation temperature detection means) (SP) by the capacity control means (51) at every predetermined set time (sampling time). The operating capacity of the compressor (1) is adjusted so that Te converges to the target evaporation temperature value Tes, and the target value calculation means (52) requires the cold storage heat capacity Q in the heat storage heat exchanger (12). Target evaporation temperature Te
s is calculated. Then, by the opening degree limiting means (53),
The opening degree of the indoor electric expansion valve (6) is limited so that the suction pressure equivalent saturation temperature Te converges to the target evaporation temperature Tes.

That is, since the value of the saturation pressure Te equivalent saturation temperature Te is controlled so as not to deviate from the value capable of maintaining the required cold storage heat capacity Qr, even if a cooling request is made during cold storage operation at night or the like. It is also possible to perform the cooling operation in accordance with the cooling request while surely ensuring the scheduled cold storage heat. Moreover, during that time, since the operating capacity of the compressor (1) is controlled so that the suction pressure-equivalent saturation temperature Te converges to the target value Tes, it is possible to avoid an operation exceeding the required capacity.
(Coefficient of performance) can be improved. Therefore, it is possible to secure the amount of cold storage heat and improve the operation efficiency as a whole.

According to the invention of claim (2), in the invention of claim (1), the operating capacity of the compressor (1) is maximized by the opening degree restricting means (53), and the suction pressure equivalent saturation temperature Te and the target evaporation are increased. When the difference (Te-Tes) between the temperatures Tes exceeds a predetermined value, the opening degree of the indoor electric expansion valve (6) is controlled to be reduced by one step. If the temperature is to deviate from the target evaporating temperature Tes, the distribution of the capacity to the indoor heat exchanger (6) decreases, and as a result, the cool storage heat capacity of the heat storage heat exchanger (12) falls below the required capacity. The decline will be suppressed. Therefore, the invention of claim (1) can be realized.

In the invention of claim (3), the above claim (1) or (2)
In addition to the invention described above, the maximum opening degree increasing means (54) changes the maximum opening degree value Amax of the indoor electric expansion valve (6) to increase when the operating capacity of the compressor (1) is below a certain value. Therefore, when the capacity is sufficient, the restriction on the distribution of the capacity to the indoor side is relaxed, and a predetermined cooling request can be met. Therefore, in addition to the invention of claim (1) or (2), there is an effect that the cooling capacity can be secured.

In the above embodiment, a so-called multi-type air conditioner in which a plurality of indoor heat exchangers (7), ... Are arranged has been described, but the present invention is of a pair type having only one indoor heat exchanger. Can also be applied. However, particularly in a multi-type air conditioner, a remarkable effect can be obtained when there is a demand for cooling in a small number of indoor units (A), ...

(Effect of the invention) As described above, according to the invention of claim (1), as the operation control device of the heat storage type air conditioner in which the heat storage tank is arranged, the suction pressure equivalent saturation is achieved during the simultaneous operation of cooling and cold storage heat. While controlling the operating capacity of the compressor so that the temperature converges to its target value, the required amount of cold storage heat is calculated from the current amount of cold storage heat, and the capacity of the heat storage heat exchanger necessary to secure that amount of cold storage heat is used. Since the target value of the saturation pressure equivalent saturation temperature is calculated, the opening of the use-side electric expansion valve is limited so that the intake pressure equivalent saturation temperature converges to the target value.
It is possible to meet the cooling demand while securing the required cold storage heat, and thus it is possible to secure the amount of cold storage heat and improve the operation efficiency as a whole.

According to the invention of claim (2), in the invention of claim (1), when the operating capacity of the compressor is maximum and the difference between the suction pressure equivalent saturation temperature and its target value is equal to or more than a predetermined value, it is used. Since the maximum opening value of the side electric expansion valve has been reduced, if the overall capacity is insufficient, the capacity of the heat storage heat exchanger should be secured by limiting the capacity of the heat exchanger on the use side. Therefore, the invention of claim (1) can be achieved.

According to the invention of claim (3), in addition to the invention of claim (1) or (2), the maximum opening value of the use side electric expansion valve is increased when the operating capacity of the compressor is equal to or less than a certain value. Therefore, when there is a margin in the capacity, the capacity limitation of the heat exchanger on the utilization side can be relaxed. Therefore, in addition to the effect of the invention of claim (1) or (2), the cooling capacity can be increased. There is an advantage that can be effectively secured.

[Brief description of drawings]

FIG. 1 is a block diagram showing the configuration of the invention. 2 and the following show an embodiment of the present invention, FIG. 2 is a refrigerant piping system diagram showing a configuration of a heat storage type air conditioner, FIG. 3 is a longitudinal sectional view showing a structure of a heat storage tank and a water supply / drainage pipe configuration, FIG. 4 is a flow chart showing the control contents of the controller. 1 …… Compressor 3 …… Outdoor heat exchanger (heat source side heat exchanger) 6 …… Indoor electric expansion valve (use side electric expansion valve) 7 …… Indoor heat exchanger (use side heat exchanger) 10 …… Main refrigerant circuit 11 …… Heat storage tank 12 …… Heat storage heat exchanger 51 …… Capacity control means 52 …… Target value calculation means 53 …… Opening restriction means 54 …… Maximum opening increase means Cl …… Water level sensor (cold storage Quantity detection means) SP ... Pressure sensor (saturation temperature detection means)

Claims (3)

[Claims] 1. A refrigerant circuit (10) comprising a variable capacity compressor (1), a heat source side heat exchanger (3), a use side electric expansion valve (6) and a use side heat exchanger (7), which are sequentially connected. ), A heat storage tank (11) having a heat storage medium (W) capable of storing cold heat, and heat exchange between the refrigerant in the refrigerant circuit (10) and the heat storage tank (1).
In a heat storage type air conditioner equipped with a heat storage heat exchanger (12) for applying cold heat to 1), a saturation temperature detecting means (SP) for detecting a saturation temperature equivalent to a suction pressure of a refrigerant, and a predetermined temperature Saturation temperature detection means (SP)
The intake pressure-equivalent saturation temperature detected by the above is provided with a capacity control means (51) for setting and controlling the operating capacity of the compressor (1) so as to converge to its target value, and by the use side heat exchanger (7) side. A cool storage amount detecting means for detecting the current cool storage heat amount of the heat storage medium (W) in the heat storage tank (11) during the simultaneous cooling and heat storage operation for simultaneously performing the evaporation operation and the cold storage heat operation by the heat storage heat exchanger (12). (Cl) and the output of the cold storage amount detecting means (Cl), the capacity control means (5
Based on the operating capacity of the compressor (1) controlled in 1) at the previous sampling, the cold storage heat capacity of the heat storage heat exchanger (12) is the difference between the target cold storage heat amount of the heat storage tank (11) and the current cold storage heat amount. Target value calculating means (52) for calculating a target value of the saturation pressure equivalent saturation temperature so as to obtain the required cold storage heat capacity obtained from the above, and a target value for calculating the suction pressure equivalent saturation temperature by the target value calculating means (52). Opening limit means (53) for limiting the opening of the use-side electric expansion valve (6) so as to converge to
An operation control device for a heat storage type air conditioner, comprising: 2. The opening degree limiting means (53), when the current operating capacity of the compressor (1) is maximum and the difference between the current value of the saturation temperature equivalent to the suction pressure and the target value is a predetermined value or more, The operation control device for a heat storage type air conditioner according to claim 1, wherein the maximum opening value of the use side electric expansion valve (6) is reduced. 3. A maximum opening increasing means (54) for changing the maximum opening value of the use side electric expansion valve (6) when the operating capacity of the compressor (1) is below a certain value. The operation control device for the heat storage type air conditioner according to claim 1 or 2.