JPH02306064A - Operation control device for heat reserve type air conditioner - Google Patents

Abstract

PURPOSE:To improve the utilization efficiency of cold accumulation and reduce power consumption by contriving a means to control the taking-out amount of cold accumulation. CONSTITUTION:At the time of cold accumulation recovery operation which carries out space cooling operation by utilizing cold thermal heat produced by the melted ice in a heat accumulator 9 as a result of heat reserve recovery after ice making operation, a primary opening and closing valve 11 is opened and a secondary one 14 is closed and the operation is carried out in the condition that the openings of a secondary electronic valve 12 and a tertiary one 13 are mutually being controlled and a part of refrigerant condensed at an outdoor heat exchanger 3 flows in a branched flow passage 20 and is overcooled by the water W in the accumulator 9 and the remaining refrigerant flows in a liquid line 6a as it is and after they are jointed, the refrigerant is reduced in pressure by a primary electronic expansion valve 4 and is vaporized at an indoor heat exchanger 5 and circulated as it returns back to a compressor 2. At that time, the utilization efficiency of cold accumulation is controlled by a controller 16.

Description

Detailed Description of the Invention (Industrial Field of Application) The present invention relates to a regenerative air conditioner equipped with a heat storage tank having a heat storage medium capable of storing cold heat, and particularly relates to a heat storage air conditioner equipped with a heat storage tank having a heat storage medium capable of storing cold heat. It relates to something that can be adjusted.

(Prior Art) Conventionally, as disclosed in Japanese Utility Model Application Publication No. 55-94661, a heat storage tank having a heat storage medium capable of storing cold heat is arranged in an air conditioner, and heat exchange for storing cold heat is performed in the heat storage tank. By arranging a coil and a supercooling coil for recovering cold storage heat, heat storage operation is performed at night and cold heat is stored in the heat storage tank, while during daytime cooling operation, the cold storage heat is used to operate the supercooling coil. BACKGROUND ART There is a known technique that attempts to improve cooling efficiency and thereby reduce power consumption by cooling liquid refrigerant.

(Problems to be Solved by the Invention) However, in the conventional system described above, the amount of cold storage heat taken out is limited when the cold storage heat is recovered by the supercooling coil, so for example, the air conditioning load is small and the heat source side Even if the capacity of the heat exchanger is sufficient to handle the load, the stored cold heat may be taken out, or conversely, the amount of cold stored heat taken out is small and the stored cold heat in the heat storage tank is not used up in one day and is left over. There was something that made me want to put it away.

Therefore, the above-mentioned conventional device has a problem in that it is not possible to fully utilize the stored cold heat, and the effect of reducing power consumption is small.

The present invention has been made in view of the above points, and its purpose is to improve the utilization efficiency of cold storage heat and significantly reduce power consumption by providing a means for adjusting the amount of cold storage heat taken out. The aim is to achieve this goal.

(Means for Solving the Problems) In order to achieve the above object, the solving means of the present invention is to temporarily divert a part of the refrigerant from the liquid line of the refrigerant circuit to the subcooling coil side during cold storage heat recovery cooling operation to store cold. The purpose is to merge the liquid refrigerant after being supercooled by heat, and to control the division ratio of the refrigerant using the temperature of the liquid refrigerant after the merge as a parameter.

Specifically, the first solution consists of a compressor (2), a heat source side heat exchanger (3), a pressure reducing mechanism (4), as shown in FIG. and user side heat exchanger (5)
a main refrigerant circuit (1) formed by sequentially connecting the following, a heat storage tank (9) having a heat storage medium (W) capable of storing cold heat, and the heat storage tank (9).
) through heat exchange between the heat storage medium (W) and the refrigerant, the heat storage tank (9
) and a cold storage heat storage means (50) for storing cold heat.

As an operation control device for the regenerative air conditioner, it is provided by bypassing the liquid line (6a) between the heat source side heat exchanger (3) of the main refrigerant circuit (1) and the pressure reduction mechanism (4). , after part of the liquid refrigerant is diverted, the liquid line (6a
), and a branch channel (20) that is provided in the branch channel (20) and supercools the branched refrigerant by heat exchange with the heat storage medium (W) in the heat storage tank (9). A subcooling coil (10) and a shunt flow adjustment mechanism (
51) shall be provided.

Furthermore, during the cold storage heat recovery operation, an outlet temperature detection means (T ho ) and the target outlet temperature of the refrigerant (T os
) and a target temperature setting means (52) for setting the outlet temperature (T.sub.ho);
) is set to the target outlet temperature (Tos) set by the target temperature setting means (T ho).
51) is provided.

The second solution, as shown in FIG. 1(a) (including the broken line part), is the cooling load (
A load detecting means (T h1) is provided to detect Qd).

The target temperature setting means (52) sets the target outlet temperature (T os) based on the cooling load (Qd') detected by the load detection means (Th1).

A third solution means, as shown in FIG. 1(b) (excluding the broken line part and dotted line part), in the first solution means, when the cold storage heat recovery cooling operation is performed, the heat source side heat exchanger (3
), an inlet temperature detection means (Th1) for detecting the inlet temperature (T1) of the refrigerant before the branching is provided in the branching path (20).

Then, the target temperature setting means (52) is set to the extraction amount setting means (54) for setting the target value (ΔQs) of the extraction amount of cold storage heat'.
), a circulation amount calculation means (55) for calculating the refrigerant circulation amount (GR), a refrigerant circulation amount (GR) calculated by the circulation amount calculation means (55), and the refrigerant circulation amount setting means (54). target temperature calculation means (56) for calculating a target outlet temperature (Tos) of the liquid refrigerant based on the set target withdrawal amount (ΔQs) and the inlet temperature (T1) detected by the inlet temperature detection means (Th1); It is composed of

A fourth solution, in the third solution, sets the extraction amount setting means (54) to a target extraction amount (ΔQs) of cold storage heat.
is set to a constant value.

As shown in FIG. 1(b) (including the broken line portion), the fifth solution means is a load detection means (T h1 ) will be established.

The extraction amount setting means (54) sets the target extraction amount (ΔQs) according to the cooling load (Qd) detected by the load detection means (T h1).

The sixth solution is as shown in FIG. 1(b) (including a part of the dotted line). In the fourth or fifth solution, the physical state quantity (Te
) is provided.

Then, the circulation amount calculating means (55) is connected to the physical state quantity (
Refrigerant circulation ff is based on the temperature of the liquid refrigerant before division (Ti) detected by the inlet temperature detection means (Th1).
1 (GR) is estimated and calculated.

The seventh solution is as shown in FIG. 1(b) (including the dotted line portion). In the fourth or fifth solution means, capacity detection means (19) detects the operating capacity (F) of the compressor (2) and detects the physical state quantity (Te) of the refrigerant sucked into the compressor (2). Inhalation state detection means (S p1
).

Then, the circulation amount calculating means (55) is connected to the physical state quantity (
Te), the temperature (T1) of the liquid refrigerant before diversion detected by the inlet temperature detection means (Th1), and the capacity detection means (19
) The refrigerant circulation amount (GR) is estimated and calculated based on the operating capacity (F) of the compressor (2) detected by the compressor (2).

An eighth solution is that in the seventh solution, the circulating amount calculation means (55) is replaced by the following formula (A) 0 formula % () (where K, , 2 is a constant, and fl+f2 is a function) ) The refrigerant circulation jl (GR) is calculated based on the following.

A ninth solution is as shown in FIG. 1(b) (including a part of the dotted line). In the fourth or fifth solution, the physical state quantity (T
e)) and a discharge state detection means (S p2) that detects the physical state quantity (Tc) of the refrigerant discharged from the compressor (2).

Then, the circulation amount calculation means (55) is connected to the physical state quantity (T) of the suction refrigerant detected by the suction state detection means (Sp1).
e) and the physical state Jii (Tc) of the discharged refrigerant detected by the discharge state detection means (Sp2), the refrigerant circulation amount (GR) is estimated and calculated.

The tenth solution is as shown in FIG. 1(b) (including a part of the dotted line). In the fourth or fifth solution, the compressor (2) is of a variable capacity type, and the compressor (
2) Capacity detection means (19) for detecting the operating capacity (F)
and the physical state fl(Te) of the refrigerant sucked into the compressor (2)
suction state detection means (S p1) that detects the
2) is provided with a discharge state detection means (S p2) for detecting the physical state quantity (Te ) of the refrigerant discharged from the refrigerant.

Then, the circulation amount calculation means (55) is connected to the operating capacity of the compressor (2) of 1 m (F
), the physical state quantity (Te ) of the suction refrigerant detected by the suction state detection means (S p1), and the physical state quantity (Te ) of the discharge refrigerant detected by the discharge state detection means (S p2).
The amount of refrigerant circulation (GR) is estimated and calculated based on the amount of refrigerant (GR).

An eleventh solution means, as shown in FIG. 1(b) (including a part of the dotted line part), in each of the first to tenth solution means, the branch channel (20) is connected to the supercooling coil ( A first branch pipe (13&>) whose one end is connected to the liquid line 6a) between the heat source side heat exchanger (3) and the pressure reduction mechanism (4) of the main refrigerant circuit (1) so that the refrigerant can flow therethrough. , supercooled coil (10)
The other end is connected to the liquid line (6a) of the first branch pipe (13a).
Liquid line (6a) on the pressure reduction mechanism (4) side of the connection part with
A second branch pipe (13b) is connected to the second branch pipe (13b) so that the refrigerant can flow therethrough, and the branch flow adjustment mechanism (51) is configured to connect the first branch pipe (13b) to the first branch pipe (13b) in the liquid line (6a) of the main refrigerant circuit (1). Second branch pipe (13a) (13b
) and a second flow control valve (15) interposed in the branch flow path (20).
It is composed of the following.

The twelfth solution is as shown in FIG.
In the solution, the second flow control valve (15) has a pressure reducing function and is arranged in the first branch pipe (13a), and the first branch pipe (13a) is connected to the first branch pipe (13a). An on-off valve (11) that opens and closes the first branch pipe (13a).
) and the other end of the supercooling coil (10) and the on-off valve (1
1) is provided with a third branch pipe (13c) connected to the suction line (6b) so that refrigerant can flow therebetween.

Furthermore, during cold storage heat operation, the refrigerant condensed in the heat source side heat exchanger (3) is transferred from the second branch pipe (13b) to the supercooling coil (1).
0) and is evaporated from the third branch pipe (13C) to the suction line (
A circulation path switching means (49) is provided for switching back to the second flow rate control valve (1), and the cold storage heat means (50) is
5) and a supercooling coil (10).

A thirteenth solution is that in the eleventh or twelfth solution, the division control means (53) is connected to the refrigerant division path (2).
When the division rate (F Diversion ratio (F
When RV) is below a second reference value which is smaller than the first reference value, the first flow control valve (12) is fixed to be fully open and the opening degree of the second flow control valve (15) is variably controlled; When the refrigerant division ratio (FRV) is between the first reference value and the second reference value, it is the first. The opening degrees of the second flow control valves (12) and (15) are variably controlled.

A fourteenth solution is that in the eleventh or twelfth solution, the branch control means (53) maintains the sum of the opening degrees of the first and second flow control valves (12) and (15) constant. However, the first. The opening degree of the second flow control valve (12) (15) is controlled.

A fifteenth solution is that in the eleventh or twelfth solution, the flow division control means (53) is a synthetic sum of channel specific resistances of the branched liquid line (6a) side and the branch flow path (20). While keeping constant the 1st and 2nd flow control valves (12) (
15) is designed to control the opening degree.

A sixteenth solution, in the first to tenth solutions described above, is such that the diversion adjustment mechanism (50) is connected to either the diversion channel (20) or the liquid line (6a) between the diversion section and the confluence section. It consists of a single flow control valve provided.

(Function) With the above configuration, in the invention of claim (1), during the cold storage heat recovery operation in which the cold heat stored in the heat storage tank (9) is recovered by the cold storage heat means (50) to perform indoor cooling operation, A part of the refrigerant condensed in the heat source side heat exchanger (3) flows into the liquid line (6a
) to the branch channel (20) side, and supercooling coil (10
) is supercooled by heat exchange with water (W), which is a heat storage medium, while the remaining refrigerant is not supercooled and flows into the liquid line (
6a).

In that case, the target temperature setting means (52) sets the target outlet temperature (Tos) of the liquid refrigerant after merging, and the branching control means (53) sets the outlet temperature detected by the outlet temperature detection means (T ho). (TO) is the target outlet temperature (To
The shunting adjustment mechanism (51) is controlled so that the current flow becomes s). Therefore, the refrigerant flow division ratio (FRV) is adjusted in accordance with the target outlet temperature (Tos), and the stored cold heat is effectively utilized in a manner suitable for the current operating state.

In the invention of claim (2), in the invention of claim (1), the target temperature setting means (52) causes the load detection means (
Since the target outlet temperature (Tos) is set based on the cooling load (Qd) detected by T h1), the capacity is adjusted by the shunting control means (53) according to the required indoor load. This will improve the utilization efficiency of cold storage heat.

In the invention of claim (3), as the function of the target temperature setting means (52) in the invention of claim (1), during the cold storage heat recovery cooling operation, the target temperature calculation means (56) sets the extraction amount setting means ( The target extraction amount of cold storage heat set in 54) (
ΔQS), the target outlet temperature (T
os) is calculated, and the diversion control means (53) controls the diversion adjustment mechanism (51) so that the amount of cold storage heat extracted becomes the target extraction amount (ΔQs).

Therefore, the flow division ratio (FRV) is adjusted while taking into consideration the current amount of cold storage heat taken out, and the cold storage heat is used rationally.

In the invention of claim (4), in the invention of claim (3), the extraction amount setting means (54) sets the extraction amount (ΔQs) of the cold storage heat to a constant value during the cold storage heat recovery operation. According to the above claim (3), based on the total amount of cold storage heat stored during cold storage heat operation at night etc. and the daily operation time, the cold storage heat is utilized in such a way that all the cold storage heat is used up.
The effectiveness of the invention can be obtained.

In the invention of claim (5), in the invention of claim (3), the load detection means (
Since the target extraction of cold storage heat ff1 (ΔQs) is set according to the cooling load (Qd) detected at T h1), when the current cooling load (Qd) is small, the extraction of cold storage heat ff1 (FRY) is reduced. On the other hand, when the cooling load (Qd) is large, such as at the start of cooling operation, a large amount of stored cold heat is taken out, shortening the pull-down time, and the effect of the invention of claim (3) can be obtained.

In the invention of claim (6), the above claims (3) and (4)
Or in the invention of (5), the inhalation state detection means (Sp1
), the physical state quantity (T
e) is detected, and the circulating amount calculating means (55) calculates the circulating amount of the refrigerant ( GR) is calculated.

Therefore, the circulation amount (GR) of the refrigerant can be easily and quickly estimated, and the effects of the invention of claim (3), (4) or (5) can be obtained.

The invention of claim (7') provides the above-mentioned claims (3) and (4).
) or (5), the circulating amount calculation means (55)
Accordingly, the compressor (2) detected by the capacity detection means (19)
), the evaporation temperature (Te) of the suction refrigerant detected by the suction state detection means (S p1), and the inlet temperature of the liquid refrigerant (T h1) detected by the inlet temperature detection means (T h1).
The refrigerant circulation amount (GR) is calculated based on T1). Therefore, a more accurate refrigerant circulation jl (GR) is required compared to the invention of claim (8) above, and
), (4) or (5), more significant effects can be obtained.

In the invention of claim (8), the refrigerant circulation amount is determined by the circulation amount calculation means (55) based on the above formula (A), the constant of which is determined depending on the type, size, etc. of the device. (GR) is estimated, so the evaporation temperature (Te)
, the refrigerant circulation amount (GR) is determined from the operating capacity (F) of the compressor (2) and the refrigerant inlet temperature (Ti), and the effectiveness of the above-mentioned invention can be obtained.

In the invention of claim (9), the above claims (3) and (4)
Or in the invention of (5), the circulation amount calculation means (55) calculates the physical state quantity (Te) of the suction refrigerant detected by the suction state detection means 1 (S p1) and the discharge state detection means (
Physical state quantity (Te) of the discharged refrigerant detected in S92)
The refrigerant circulation amount (, GR) is estimated and calculated simply and quickly based on the above, and the invention of claim (3), [4) or (5) can be achieved.

In the claimed invention, in the invention of claim (3), (4) or (5), the circulation amount calculation means (55) detects the amount of air in the compressor (2) detected by the capacity detection means (19). The operating capacity (F), the physical state quantity (Te) of the suction refrigerant detected by the suction state detection means (S p1), and the physical state quantity (Te) of the wall refrigerant detected by the discharge state detection means (S p2)
Since the refrigerant circulation amount (GR) is calculated according to the refrigerant circulation amount (GR), the refrigerant circulation amount (G
R) is calculated more accurately, and the above claims (3) and (4)
) or (5), more significant effects can be obtained.

In the invention of claim (11), the above claims (1) to (a)
As the function of the flow dividing adjustment mechanism (51) in each of the above inventions, the flow dividing ratio (FRV) is accurately adjusted by adjusting the opening of the first flow control valve (12) and the second flow control valve (15). The effects of each of the inventions of claims (1) to (to) above can be obtained.

In the invention of claim (121), in the invention of claim (11), the circuit connection is switched by the circulation route switching means (49) during the cold storage heat operation, and the liquid refrigerant condensed in the outdoor heat exchanger (3) is flows into the second branch pipe <13b), is depressurized by the second flow control valve (15), and evaporates in the supercooling coil (10) to store cold heat in the heat storage tank (9), and then is inhaled. Return to line (6b).

In this way, since cold storage heat is performed using the supercooling coil (1o) and the second flow control valve (15), the configuration of the device is simplified and costs are reduced.

In the invention of claim (13), the above claim GD or (12)
), the flow control means (53) controls both flow rate control valves (12) in the intermediate region of the flow division ratio (FRV).

Fine adjustment of the flow division ratio (F RV) is performed by adjusting the opening of (15), while in a region where the flow division ratio (F RV) is high or low, the flow rate of one of the control valves (12 or 15) is adjusted. The flow division ratio (F RV) is controlled only by adjusting the opening degree, and the flow division ratio (F RV) can be adjusted with a simple configuration.

In the invention of claim (14), in the invention of claim OD, the first. Since the sum of the opening degrees of the second flow control valves (12) and (15) is controlled to be a constant value, the refrigerant circulation amount (GR) in the circuit is kept almost constant, and the flow division ratio ( When adjusting the F RV), the 1st and 2nd flow control valves (12
) (15) This will prevent the possibility that the operating state of the device will change due to the change in the opening degree and that the control will become unstable.

In the invention of claim (15), the above claim G1) or Oz
In the invention, each flow control valve (1
2) Since the opening degree of (15) is controlled, the flow division ratio (F R
Even if V) changes, the pressure drop in the liquid line (6a) remains constant.

Therefore, the refrigerant state in the circuit is extremely stable, and the opening degree control of the indoor pressure reducing mechanism (4) is stabilized.

In the invention of claim a♂, in the invention of claims (1) to ω, the flow division control means (53) more easily controls the flow division ratio (FRV) by adjusting the opening degree of one flow control valve. That will happen.

(Example) Hereinafter, an example of the present invention will be described based on the drawings from FIG. 2 onwards.

Figure 2 shows the overall configuration of the regenerative air conditioner exclusively for cooling according to the first embodiment, where (2) is a compressor and (3) is an outdoor heat exchanger as a heat source side heat exchanger that functions as a condenser. vessel,
(4) is a first electronic expansion valve as a pressure reduction mechanism that reduces the pressure of the refrigerant condensed in the outdoor heat exchanger (3), and (5) is an indoor heat exchanger as a user-side heat exchanger that functions as an evaporator. The above-mentioned devices (2) to (5) are sequentially connected through refrigerant piping (6) so that refrigerant can flow therethrough, and the outdoor heat exchanger (
A main refrigerant circuit (1) having a heat pump function is configured to provide the cold heat obtained by heat exchange with outdoor air in step 3) to the room using an indoor heat exchanger (5).

Here, (19) is an inverter (19) for variably adjusting the operating capacity of the compressor (1), and the operating capacity of the compressor (1) is determined as the output frequency F by the inverter (19). Therefore, the inverter (19) has a function as a capacitance detection means.

The main refrigerant circuit (1) includes a receiver (7) for temporarily storing refrigerant on the downstream side of the outdoor heat exchanger (3), and a receiver (7) on the upstream side of the compressor (2) as accessory equipment. An accumulator (8) for separating liquid refrigerant in the intake gas to the compressor (2) is interposed in each case.

This air conditioner is provided with a heat storage tank (9) that stores water (W) as a heat storage medium that can store heat, and inside the heat storage tank (9), water (W) is stored through heat exchange with a refrigerant. An ice-making coil (10) is provided that functions as a supercooling coil that makes ice from the water (W) in the heat storage tank (9) and supercools the refrigerant during the cold storage heat recovery operation. The ice making coil (
10) includes first and second branch pipes (13) in order from the upstream side.
a) (13b) is connected to the liquid line (6a) of the main refrigerant circuit (1) so that refrigerant can flow therethrough; The second branch pipe (13a) (13b) and the ice making coil (
10), the heat source side heat exchanger (3) of the main refrigerant circuit (1)
) and the pressure reducing mechanism (4), and is provided to bypass the liquid line (6a), and divides a part of the liquid refrigerant and then divides the liquid refrigerant to join the liquid line (6a) again.
) is configured.

Further, in the liquid line (6a) of the main refrigerant circuit (1), the first. Second branch pipe (13a).

(13b) and two branch points, that is, the above-mentioned branch channel (20)
Dividing point (P) and confluence point (R) between and liquid line (6a)
A second electronic expansion valve (12) as a first flow control valve whose opening degree can be adjusted is provided between the first branch pipe (13a) and the first branch pipe (13a). 13a) is provided, and a third electronic expansion valve (15) as a second flow rate control valve whose opening degree is adjustable is interposed in the second branch pipe (13b). It is set up.

Furthermore, the first on-off valve (11) and the ice-making coil (10)
A third branch pipe (13c) is provided which connects the first branch pipe (13a) between the main refrigerant circuit (1) to the suction line (6b) so that refrigerant can flow, ) is equipped with a second on-off valve (
14) is provided.

That is, the first on-off valve (11) and the second on-off valve (1
4) are closed, the refrigerant flows through the main refrigerant circuit (
1), the bypass becomes impossible, while the first on-off valve (11)
is opened and the second on-off valve (14) is closed, the liquid line (6a) of the main refrigerant circuit (1) passes through the first branch pipe (13a), the ice-making coil (10), and the second branch pipe (13b). )
A part of the refrigerant is branched from the refrigerant and then merges into the liquid line (6a). At that time, the second. By mutually adjusting the opening degrees of the third electronic expansion valves (12) and (15), the flow rate of the refrigerant flowing through the dividing channel (20) side relative to the flow rate of the refrigerant flowing through the liquid line (6a) side, that is, the flow rate is adjusted. The above 2. Third electronic expansion valve (12) (
15) constitutes a flow dividing adjustment mechanism (51).

On the other hand, the first on-off valve (11) and the first electronic expansion valve (4) are closed, and the second electronic expansion valve (12) and the second on-off valve (14) are closed.
When the is opened, the liquid refrigerant flows from the second branch pipe (13b) through the ice making coil (10) and the third branch pipe (13c) to the gas line (
6b), and the refrigerant whose pressure is reduced by the third electronic expansion valve (15) evaporates in the ice-making coil (10), thereby making ice from the water (W) in the heat storage tank (9) and generating cold heat. The third electronic expansion valve (second flow control valve) (15) and the ice making coil (supercooling) are used to store ice.

The coil (10) constitutes a cold storage heat means (50). Also, 1st. Circulation route switching means (49) that switches the refrigerant circulation route using the second on-off valves (11) and (14).
) is configured.

In addition, as described later, the above-mentioned No. 1. second on-off valve (11),
(1'4) will never open at the same time.

Here, the device is equipped with many sensors, (
T h1) is an inlet sensor (T
ho) is an outlet temperature sensor (T h1
) is placed at the air suction port of the indoor heat exchanger (5), and is a room temperature sensor (Th2
) is arranged in the suction pipe (6b) and detects the suction pipe temperature T2, and (Sp1) is arranged in the suction pipe and detects the saturation temperature equivalent to the evaporation pressure of the refrigerant (which is the physical state quantity of the suction refrigerant).
A low pressure sensor detects Te (hereinafter referred to as evaporation temperature), (S
p2) is a high-pressure sensor that is disposed in the discharge pipe and serves as a discharge state detection means for detecting a saturation temperature Te (hereinafter referred to as condensation temperature) corresponding to the condensation pressure of the refrigerant, which is a physical state quantity of the discharged refrigerant.

In addition, the temperature difference (T2 - Tc) between the temperature T2 of the suction superheated refrigerant detected by the suction pipe sensor (T h2) and the evaporation temperature Te detected by the low pressure sensor (S p1) is determined during ice making operation (cold storage). degree of superheating s of the refrigerant during thermal operation)
I am trying to find h.

Each of the above-mentioned sensors is connected to a controller (16) as an operation control means for controlling the operation of the entire device, and the controller (16) controls the operating state of the device and each sensor (Th1), (Tho) (Th1). ,
(Th2), (Sp1), (Sp2), each of the above valves (4) (11) (12) (
14) The opening/closing and opening degree of (15) are controlled.

Next, each operating state of the circuit configured as described above will be explained.

During normal cooling operation without heat storage recovery, the first and second on-off valves (11) and (14) are closed, and the second electronic expansion valve (1) is closed.
2) is open, operation is performed while appropriately adjusting the opening degree of the first electronic expansion valve (4), and the refrigerant compressed by the compressor (2) is condensed in the outdoor heat exchanger (3). After the separation channel (
20) flows only through the liquid line (6a) without being diverted to the side, is depressurized by the first electronic expansion valve (4), evaporated in the indoor heat exchanger (5), and returned to the compressor (2). circulates.

Further, during ice making operation, the first on-off valve (11) is closed, the second electronic expansion valve (12) and the second on-off valve (14) are opened,
In addition, with the first electronic expansion valve (4) closed, operation is performed while appropriately adjusting the opening degree of the third electric expansion valve (15), and the refrigerant condensed in the outdoor heat exchanger (3) is After being depressurized by the third electronic expansion valve (15), evaporated by the ice-making coil (1o), and making ice from the water in the heat storage tank (9) through heat exchange with the water (W) in the heat storage tank (9). It circulates back to the suction side (see solid line arrow in Figure 1). In addition, during the above ice making operation,
The above suction pipe sensor (T h2) and low pressure sensor (S p1
) The opening degree of the third electronic expansion valve (15) is controlled so that the suction superheat degree sh determined by

After this ice-making operation, the heat storage tank (
9) During the cold storage heat recovery operation in which the ice inside is melted and the cold energy is utilized for cooling operation, the first on-off valve (11) opens;
The second on-off valve (14) is closed, and the second electronic expansion valve (12) is closed.
) and the third electronic expansion valve (15), a part of the refrigerant condensed in the outdoor heat exchanger (3) flows into the branch channel (20) and is transferred to the heat storage tank. (9) is subcooled by the water (W) in the tank, while the remaining refrigerant flows through the liquid line (6a) as it is, and after they merge, it is depressurized by the first electronic expansion valve (4), and the indoor heat is reduced. It is evaporated in the exchanger (5) and circulated back to the compressor (2) (see broken line arrow in Figure 1).

At that time, the control of the cold storage heat utilization rate performed by the controller (16) will be described below.

FIG. 3 is a flowchart showing the control contents of the controller (16), in which in step s1 the inlet sensor (
Th1), the inlet temperature T1, outlet temperature To and room temperature Ta of the liquid refrigerant detected by the outlet temperature sensor (T ho) and room temperature sensor (Th1), and the operation of the compressor (2) detected by the inverter (19). Input the values of frequency (operating capacity) and F, and in step S2, use the formula Qd = C+ (
Ta - Tas) (However, Qd is air conditioning load %TJ
IS is the indoor set temperature, C1 is a predetermined constant), and after calculating the air conditioning load Qd, in step S3, the formula ΔQ is calculated.
A target extraction amount ΔQs of cold storage heat is calculated based on s −C2Qd−Cz (where C2 and C3 are predetermined constants).

Next, the refrigerant circulation amount GR is determined based on the following formula (1) (% formula % (1)) (where GR is the refrigerant circulation amount, and 04 to C7 are each a predetermined constant). That is, the above equation (1) expresses the refrigerant circulation amount GR as the evaporation temperature T.
The function fl + f2 in the following formula (A) % formula % () (where Kl r K2 is a constant, f, , f2 represents a function) is expressed using the operating capacity F1 of the e1 compressor (2) and the population temperature T1 as parameters. It is approximated by a linear function.

Next, in step S5, the target outlet temperature Tos is set based on the following ('2J formula % formula % (2) (where Tos is the target outlet temperature and C8 is a predetermined constant).

Then, in step S6, the outlet temperature TO and the target outlet temperature T are
os temperature deviation (To-Tos) is calculated, and step S
7, the above-mentioned 2. Third electronic expansion valve (12).

(15) Driving amount of the opening degree, that is, change amount Δ of the flow division ratio FRV
After calculating FRY, in step S8, FRV-FRV
A new division ratio FRV is determined as +ΔFRV.

Furthermore, in steps 86 to S9, the first
．． By driving the opening degrees of the second flow rate control valves (12) and (15), the branch flow adjustment mechanism (51) is controlled so that the outlet temperature To becomes the target outlet temperature Tos.

In the above flow, step S3 constitutes an extraction amount setting means (54) for setting the target extraction amount ΔQs of cold storage heat, and step S4 constitutes a circulation amount calculation means (55) for calculating the refrigerant circulation amount GR. and step SS
This constitutes a target temperature calculation means (56) that calculates the target outlet temperature Tos of the liquid refrigerant. Further, step S9 configures a diversion control means (53) that controls the diversion adjustment mechanism (51) so that the outlet temperature To becomes the target outlet temperature Tos.

Furthermore, the target temperature setting means (52) sets the value of the target outlet temperature Tos by the above-mentioned withdrawal amount setting means (54), circulation amount calculating means (55) and target temperature calculating means (56).
) is configured.

Here, to explain a specific example of controlling the flow division ratio FRY according to the above control contents, from the state of the device, for example, the above (
1) Find each constant in the equation and determine it as follows.

GR-29Te +4F-5TI +270 (4
) Also, the target outlet temperature Tos is set to the following formula 7% (5). However, if 4℃≦Tos≦16℃%, 3■C8・
ΔQs, for example, as shown in Table 1 below, the target extraction amount of cold storage heat ΔQs is the time (utilization time) to use up the cold storage heat.
(In this example, L, M, and S are set to 12 and 12, respectively, depending on the length of time, M, and S.)
10.8 hours).

From the relationships shown in Table 1, the current evaporation temperature Te, the inverter (1
9) When the output frequency F and inlet temperature TI are detected,
When the refrigerant circulation ff1GR is calculated based on equation (1) and the refrigerant circulation 1tGR is determined, the target outlet temperature Tos is determined in accordance with the preset usage time, M, and S.

Next, the first step in step S9. Second flow control valve (1
2), -(15) To explain a specific example of the control contents for the opening degrees EVI and EV2, steps 86 to S8
Once the diversion ratio FRY is determined, the control mode for that value is set as shown in Table 2 below.

Table 2, FIG. 4(a) shows the second . Opening degree Evl of the third electronic expansion valve (12) (15) (characteristic line a1 in the figure).

(Ev2 (characteristic line b+ in the figure). In other words, as shown in the figure, the diversion ratio FRY is set to the predetermined first reference value FRI (
In the above example, 1800 (expressed as opening pulse ratio)
) or more, the opening degree EV2 of the second flow control valve (15)
is fixed at full open (2000 pulses) and the first flow control valve (
The opening degree EVI of the first flow control valve (12) is variably controlled, and the opening degree E of the first flow control valve (12) is adjusted when the flow division ratio FRY is less than or equal to the second reference value FR2, which is smaller than the first reference value FRI by a predetermined amount.
VI is fixed at full open and the opening degree E of the second flow control valve (15) is
While V2 is variably controlled, the division ratio is set to the above first reference value F.
Between RI and the second reference value FR2, the first. Second flow control valve (12).

(15) The opening degrees EVI and EV2 are continuously changed from the fully closed state.

In addition, FIGS. 4(b) and (C) show the flow from the branch point (P) to the confluence point (R) of the liquid line (6a) corresponding to the above-mentioned opening adjustment.
The composite sum C of the pressure loss Vl between and the flow path specific resistance ゛
It shows the change in v with respect to the change in the division ratio FRY, and in particular, the pressure loss Vl is small in the middle region of the division ratio FRY, and shows a characteristic that it increases as the division ratio FRY becomes smaller or larger from the middle region.

In the flow shown in FIG.
), the following formula (5) GR-CM Te +C
+s F−C+s Tc +CI7 The refrigerant circulation amount GR may be calculated based on (5).

Therefore, in the invention of claim (1), the cold storage heat means (5
During the cold storage heat recovery operation in which the cold heat stored in the heat storage tank (9) is recovered by the outdoor heat exchanger (9) to perform indoor cooling operation, the outdoor heat exchanger (
A part of the refrigerant condensed in step 3) is diverted from the liquid line (6a) to the diversion channel (20) side at the diversion point (P), and is transferred to the ice making coil (
While the refrigerant is supercooled by heat exchange with water (W), which is a heat storage medium, in the subcooling coil (10), the remaining refrigerant flows through the liquid line (6a) without being supercooled, and both reach the confluence point (R
), the pressure is reduced by a first electronic expansion valve (4) serving as a pressure reduction mechanism, and after being evaporated in an indoor heat exchanger (5), it is circulated back to the compressor (2).

In that case, the target temperature setting means (52) sets the target value of the liquid refrigerant temperature TO after merging, that is, the target outlet temperature Tos, and the branching control means (53) sets the outlet temperature sensor (
The diversion adjustment mechanism (51) is controlled so that the outlet temperature To detected at Tho) becomes the target outlet temperature Tos. Therefore, the refrigerant distribution ratio FRY is adjusted in accordance with the target outlet temperature Tos set according to the requirements of the device, and unlike conventional systems that do not have a function to adjust the utilization rate of cold storage heat, Rather than leaving the use of stored cold heat to chance, it is possible to effectively utilize stored cold heat that is appropriate for the current operating conditions.

In the invention of claim (2), in the invention of claim (1), the target temperature setting means (52) sets the room temperature sensor (
Since the target outlet temperature Tos is set based on the cooling load Qd detected by the load detection means) (Th1), it is possible to use the stored cold heat corresponding to the cooling load Qd, and therefore the efficiency of using the stored cold heat is increased. It will improve further.

In the invention of claim (3), as the function of the target temperature setting means (52) in the invention of claim (1), during the cold storage heat recovery cooling operation, the target temperature calculation means (56) sets the extraction amount setting means ( Target extraction amount Δ of cold storage heat set in 54)
The target outlet temperature Tos is calculated based on the current refrigerant circulation amount GR calculated by the Qss circulation amount calculation means (55) and the inlet temperature TI detected by the inlet sensor (Tb1) (
For example, the above ('2J or formula (4)). Then, the diversion control means (53) controls the diversion adjustment mechanism (51) so that the amount of heat exchange between the refrigerant and water (W) in the diversion path (20), that is, the amount of cold storage heat extracted, becomes the target extraction amount ΔQs. controlled.

Therefore, the stored cold heat can be used rationally while taking into account the actual amount of cold stored heat to be taken out, and therefore the effect of reducing power consumption can be significantly achieved.

In the invention of claim (4), in the invention of claim (3), the extraction amount setting means (54) sets the extraction amount ΔQs of cold storage heat to a constant value during the cold storage heat recovery operation.
For example, as shown in Table 1 above, based on the total amount of cold storage heat stored during cold storage heat operation at night, etc., and the daily operating hours, a cold storage heat usage plan can be created to use up the cold storage heat to the fullest. Therefore, the invention of claim (3) above can be carried out effectively.

In the invention of claim (5), in the invention of the above-mentioned claim, the load detection means (T
Since the target extraction amount ΔQs of cold storage heat is set according to the cooling load Qd detected in h1), when the cooling load Qd is small and there is no need to mix the cold storage heat, the extraction amount is made small, while When the cooling load is large, such as at the start of cooling operation, the pull-down time can be shortened by taking out a large amount of stored cold heat, thereby making it possible to achieve the effectiveness of the invention of claim (3). Furthermore, this allows the device to be made smaller.

In the invention of claim (6), the above claims (3) and (4)
Or in the invention of (5), the low pressure sensor (suction state detection means) (S p1) detects the evaporation temperature (physical state quantity) Te of the refrigerant sucked into the compressor (1), and the circulating amount calculation means (55 ), this evaporation temperature Te and the inlet temperature T of the liquid refrigerant detected by the inlet temperature detection means (T h1)
The refrigerant circulation amount GR is calculated based on I. In that case, the operating capacity F of the compressor (1) is normally controlled so that the evaporation temperature Te is constant, so once the value of the evaporation temperature Te is determined, it can be estimated from that value.

Therefore, it is possible to easily and quickly estimate the refrigerant circulation ffi GR, and therefore, the above-mentioned claims (3) and +4
The invention of 1 or (5) can be made effective.

In the invention of claim ('7), the above-mentioned claims (3) and (4)
) or (5), the operating capacity F of the compressor (2) is detected by the inverter (capacity detection means) (19), and the evaporation temperature Te of the suction refrigerant is detected by the low pressure sensor (S p1). Then, the operating capacity F of the compressor (2) is determined by the circulating amount calculation means (55).

The refrigerant circulation amount GR is calculated based on the refrigerant evaporation temperature Te and the liquid refrigerant inlet temperature (Ti) detected by the inlet sensor (Th1). Therefore, the above claim (8)
), the refrigerant circulation amount GR is calculated more accurately than the invention of claim (3), (4) or (5) above.
The effects of the invention can be more clearly exhibited.

In the invention of claim (8), the circulating amount calculating means (55) calculates the above (in the sword invention) using the evaporation temperature Te, the operating capacity F of the compressor (2), and the inlet temperature Tl as parameters. Refrigerant circulation * GR is estimated and calculated based on formula A. Specifically, as shown in formula (3) above, the constants and functions of formula (A) are calculated depending on the size and type of the device, etc. is determined, and the refrigerant circulation amount GR is quickly calculated based on the preset relational expression.Therefore, the invention of claim (7) can be brought into effect.

In the invention of claim (9), in the invention of claim (31, (4) or (S), the circulation amount calculation means (55) calculates the evaporation temperature Te and the refrigerant detected by the low pressure sensor (S p1). High pressure sensor (discharge state detection means) (Sp2
), the refrigerant circulation amount GR can be determined simply and quickly based on the condensation temperature Tc of the refrigerant detected in the above-mentioned claim (3).
, (4) or (5) can be made effective.

In the claimed invention, in the invention of claim (3), (4) or (5), the operating capacity ff1F of the compressor (2) is detected by the inverter (19), and the low pressure sensor (S
p1) and the evaporation temperature Te and condensation temperature Tc detected by the high pressure sensor (S p2), for example, the above (5).
Since the refrigerant circulation mGR is calculated as shown in the equation, the refrigerant circulation amount GR can be calculated more accurately than in the invention of claim (9). Therefore, the above claims), (
The effect of the invention of 4) or (5) can be more significantly exhibited.

In the invention of claim (11), the above claims (1) to (goods)
In each invention of 1. Second branch pipe (13a) (13
b) connects the ice making coil (supercooling coil) (10) and the liquid line (6a) to form a branch channel (20), while the branch channel (20) and the branch point (P) Confluence point (R
) respectively provided in the liquid line (6a) between the
A diversion adjustment mechanism (
51), two electronic expansion valves (12
).

By adjusting the opening degrees EVI and EV2 in (15), the diversion ratio FRV is accurately adjusted, so that the above-mentioned claims (1) to
The effectiveness of the invention of η can be achieved.

In the claimed invention, during the cold storage heat operation, the circuit connection is switched by the circulation route switching means (49), and the liquid refrigerant condensed in the outdoor heat exchanger (3) is transferred from the confluence point (R) to the second The heat storage tank is bypassed to the branch pipe (13b), is depressurized by the third electronic expansion valve (15), evaporated by the ice making coil (10), and then circulated back to the suction line (6b). Cold energy is stored in (9). That is, since the third electronic expansion valve (15) and the ice making coil (subcooling coil) for collecting cold heat storage serve as the cold storage heat means (50), there is no need to provide a separate cold storage heat means, and the configuration is simplified. The structure is simplified, and the cost of the device can therefore be reduced.

In the invention of claim (13), the above claim (11) or (
In the invention of 12), as shown in Table 2 and FIG.
When V is equal to or greater than the first reference value FRVI, the opening EV2 of the third electronic expansion valve (15) is fixed to fully open, and the opening EVI of the second electronic expansion valve (12) is variably adjusted. Second reference value F RV2 smaller than first reference value EVI
In the following cases, the opening degree EVI of the second electronic expansion valve (12)
is fixed at full open, and the opening degree EV of the third electronic expansion valve (15)
2 is variably adjusted. In addition, the diversion rate FRY is the first
In the intermediate region between the reference value FRVI and the second reference value FRV2, both electronic expansion valves (12).

Since the opening degrees E vl and E v2 of (15) are variably adjusted, in the intermediate region both electronic expansion valves (12) and (15)
While finely controlling the division ratio FRY by adjusting the opening of the valve, in the region where the division ratio FRY is higher or lower than the intermediate region, it is easy to adjust the opening of one electronic expansion valve (12 or 1'5). The diversion rate FRY can be controlled as follows.

In the above example, the cold storage heat means (50) is composed of the third electronic expansion valve (15) and the ice making coil (10), but separate heat exchange coils may be provided for supercooling and ice making layers. good. FIG. 5 shows a modification of the first embodiment, in which an ice-making heat exchange coil (10a) and a supercooling heat exchange coil (10b) are arranged in a heat storage tank (9), and the supercooling heat exchange coil (10b) is arranged in a heat storage tank (9). The heat exchange coil (10b) is the same as shown in FIG. 2 above.
, the liquid line (6
a) so that the refrigerant can be divided. On the other hand, the ice-making heat exchange coil (10a) is connected to the liquid line (6a) and the suction line (6b) through two branch pipes (13d) and (13e), respectively, so that refrigerant can flow therethrough.
13d) is provided with an electronic expansion valve (18) that reduces the pressure of the refrigerant during ice-making operation. That is, the heat exchange coil (
10a) produces ice in the heat storage tank (9), while a heat exchange coil (10b) extracts the stored cold heat. The other configurations are the same as those in FIG. 2 above.

In the first embodiment, a so-called bare-type air conditioner in which only one indoor heat exchanger (5) is arranged has been described, but the present invention is not applicable only to bare-type air conditioners. Instead, the present invention can also be applied to so-called multi-type air conditioners in which a plurality of indoor units each having an indoor heat exchanger are connected in parallel. In that case, although the refrigerant circuit is omitted, the calculation is made based on the one with the largest temperature difference (Ta - Ts) among the indoor units operating the cooling load Qd. Other control details are the same as in the first embodiment. However, the operating capacity of the compressor is based on constant low pressure control, and the above temperature difference (Ta
-Ts) is controlled to maximize the refrigerant flow rate of the indoor unit with a large cooling load by increasing the degree of superheating of the refrigerant in the indoor heat exchanger.

Next, a second embodiment according to the invention of claim 04 will be described.

In this embodiment as well, the configuration of the refrigerant circuit is the same as that in the first embodiment, and the control contents are also basically the same as in the flowchart of FIG. 3 above. However, the third
The second step in step S9 of the figure. Third electronic expansion valve (12
) (15) opening degree Evl, Ev2 is EVI-2000-0,5FRV (pulse) (
6) EV2-0.5FRV+500 (P/L, S) In other words, always satisfy the following (8).
It is designed to satisfy the formula (8).

Therefore, in the invention of claim 04), the above claim Gυ
In the invention of 2nd. Third electronic expansion valve (12) (15
) is controlled so that the sum of the opening degrees EVI and EV2 of Therefore, the second and third electronic expansion valves (12) (
15) (7) Opening degree EVI.

By changing EV2, there is an advantage that the flow division ratio FRY can be controlled while effectively preventing the possibility that the operating state of the device changes and the control becomes unstable.

Next, a third embodiment according to the invention of claim a9 will be described. In this embodiment, as the opening degree control of each electronic expansion valve (12) (15) in step S9 in FIG.
The composite sum of vl and Cv2 is set to a constant value.

That is, in general, the flow path specific resistance Cv of a pipe is calculated by the following equation (9), where the flow rate of the refrigerant expressed in mass is W1, the specific gravity of the fluid relative to water is G, and the pressure difference between both ends of the pipe is Δp. 9) From the basic relationship, the following formula Cv-W/27. (15) (ρ−Δp) G
o) (where ρ is the density of the refrigerant). Therefore, the liquid line (6a) side and the branch channel (20)
Specific resistance C excluding side electronic expansion valves (12) and (15)
va1. Cvbl is calculated from the tube diameter, for example, Cval = 4
．． 61, Cva2-0.67, each electronic expansion valve (12
) (15) are Cvl and Cv2, respectively, the specific resistances Cva2. Cvb2 is represented by the following (ID, Q2) formula % formula %).

Here, the composite sum of resistivity is constant, that is, Cva2 +C
vb2-constant, and each of the above specific resistances C
Ite below (1
3), 04) Expression % Formula %) The specific resistance values CVl and Cv2 of each electronic expansion valve (12) (15) can be determined, and further, from the characteristics of the electronic expansion valve (12) (15), Opening degree E vl, E
v2 will be expressed by the diversion rate FRY.

For example, an electronic expansion valve (12) having an opening characteristic expressed as Ev -3800Cv +100 (pulse).

In the case of (15), each opening degree E to satisfy the above relationship
vl, E v2 is Evl=3800/ [1/ (1, OXIO″″’x
FRV+0.5 ) 2-0.047 ] 112+1
00Evl=1/ [1/ (1,OXl0-'xFR
V+0.1 ) 2-2.228 ] It will be expressed as 1/210G.

Figures 6(a) to (c) show the refrigerant circulation amount OR (800K
g/h), the specific gravity of the refrigerant, ρ to 1.15X 1 (11
Each electronic expansion valve (12) when set to 0-3 (/-3)
15) opening degree Evl (characteristic line a2 in Fig. 6(a))
, E, v2 (characteristic line b2 in (a)), total pressure loss VD (Kg/cm 2
) and the change in specific resistance Cv with respect to the current division ratio FRV,
In particular, it is shown as a remarkable feature that the total pressure loss vp and specific resistance Cv are held constant against changes in the flow division ratio FRY.

Therefore, in the invention of claim (15), the above claim O
In the invention of D or claim 02), the dividing control means (5
3), the sum of the channel specific resistances on the liquid line (6a) side and the branch channel (20) side at the time of branching (Cva2+Cvb2)
Since the opening degrees Evl and Ev2 of each electronic expansion valve (12) and (15) are controlled so that is maintained. That is, when comparing FIG. 4 and FIG. 6 above, in FIG.
) and (C)), whereas in Fig. 6, these values are held constant (see (b) and (C) in the same figure).
.

Therefore, the total pressure loss vI in the liquid line (6a)
As a result of keeping I constant, the refrigerant condition is extremely stable,
This provides a significant effect of stabilizing the opening degree control of the first electronic expansion valve (4) on the indoor side.

Next, according to the invention of claim (+6), in particular, the outlet temperature T
A fourth embodiment will be described in which the diversion rate FRY is controlled using only o as an index. In this embodiment, as shown in FIG. 7, the basic configuration is the same as that in FIG. 2 above, but there is a second
Capillary tube (1) instead of electronic expansion valve (12)
2a) is provided, and further bypassed to the bypass path (17) via a third on-off valve (12b). That is, between the branch point (P) and the confluence point (R) of the liquid line (6a), the supercooling coil (10)
A capillary tube (12a) and a third on-off valve (12b)
) are connected in parallel with each other.

Then, the inlet temperature sensor (Th1
) are not placed.

In this embodiment, the refrigerant circulation path in the cold storage heat operation, the normal cooling operation, and the cold storage heat recovery cooling operation is almost the same as that shown in FIG. 2 above. However, during normal cooling operation in which cold storage heat is not recovered, the third on-off valve (12b) opens and most of the refrigerant bypasses the bypass path (17), while during cold storage heat recovery cooling operation, the third on-off valve (12b) ) closes,
By adjusting the opening degree of the third electronic expansion valve (15), the flow division rate FRY is determined based on the difference in pressure reduction with the capillary tube (12a).
control is performed.

Here, the details of the opening degree control of the third electronic expansion valve (15) during the cold storage heat recovery cooling operation will be explained based on the flowchart of FIG. 8. In step S11, the third electronic expansion valve (15) is opened. The opening degree is set to the initial opening value Ev2o, and the magnitude relationship between the outlet temperature To detected by the outlet temperature sensor (Tho) and the target outlet temperature Tos is compared in the step tube SL2. In other words, the predetermined differential is Δ
When TO, if T□>'ros+ΔTO,
It is determined that the opening degree Ev2 is small, that is, the diversion rate FRY is too small, and in step S13, the opening degree drive value ΔEv2 of the third electronic expansion valve (15) is determined by the formula ΔEv2mG (To −T
os) (where G is a positive constant), and further calculate the new opening displacement (
Ev2+ΔEv2) is smaller than the maximum opening value Evsax. If the determination is YES, the opening value Ev2 is increased to the new opening displacement (Ev+ΔE v2) in step SIS, while the determination is NO.
In this case, in step 516, the opening value Ev2 is set to the maximum opening value Evsax.

On the other hand, in the determination in step S12 above, TO80ΔTO≦
If To≦To+ΔTo, it is determined that the current opening degree Ev2 is within an appropriate range, and the opening degree Ev2 is changed in step S+7.
is set to the current opening degree Ev2, and if 70<Tos-ΔTo, it is determined that the current opening degree Ev2 is too large, and in step S18, the opening degree driving value ΔEv2 is set by the formula ΔEv2-G (Tos-To). Further, it is determined whether the new opening degree (Ev2-ΔE v2) after the change is larger than the minimum opening degree value Evsin. And the judgment is YES
If so, the opening value Ev2 is set to the new opening displacement Ev2+ΔEV2 in step 5211, while if the determination is No, the opening value Ev2 is set to the minimum opening value Evsi in step S2+.
Set to n.

In the above flow, step SIS+ SI6+
By S+7132'l and S2+, the shunting control means (
53) is configured.

Therefore, in the invention of claim (16), the above claim (
1) In the inventions of (Foundation), the flow division ratio (F
Since the RV) is controlled, the effects of the inventions of claims (1) and (2) above can be obtained with a simple configuration.

In addition, in the above-mentioned FIG. 7, the third electronic expansion valve (15) is used to adjust the flow division ratio FRY, but the liquid line (6a)
The flow division ratio FR can be adjusted only by the second electronic expansion valve (12) provided in the
Y may also be adjusted.

FIG. 9 shows a modification of the fourth embodiment, in which the third electronic expansion valve (15) is replaced by a branch point (P) and a confluence point (
The second electronic expansion valve (12) provided in the liquid line (6a) between the liquid line (6a) and the liquid line (6a) serves as both a flow control mechanism and a pressure reduction mechanism during cold storage heat operation.

In this case, the second electronic expansion valve (
The opening degree control in step 12) is basically the same as the flowchart shown in FIG. 8 above. However, the magnitude relationship of the opening degree Evl of the second electronic expansion valve (12) with respect to the level of the outlet temperature To is controlled to be opposite to that in the flowchart of FIG. 8 above.

(Effects of the Invention) As explained above, according to the present invention, during the cold storage heat recovery cooling operation of the regenerative air conditioner, the division ratio of the liquid refrigerant to be supercooled is controlled using the liquid refrigerant temperature before depressurization as an index. Unlike the conventional system, which leaves the use of stored cold heat to the end of the day, there are cases where the stored cold heat is wasted, or the stored cold heat is not fully utilized, so the stored cold heat is not used at the end of the day's operation. It is possible to effectively utilize stored cold heat without leaving any surplus.

That is, according to the invention of claim (1), in a regenerative air conditioner in which cold heat is stored in a heat storage medium of a heat storage tank by heat exchange of the refrigerant, a part of the liquid refrigerant is diverted to the liquid line of the refrigerant circuit. In this method, a subcooling coil is installed to recover the stored cold heat through heat exchange with the heat storage medium, and a diversion adjustment mechanism is installed to adjust the diversion rate of the liquid refrigerant. During cold storage heat recovery cooling operation, the outlet temperature after the liquid refrigerant is merged is detected and the diversion rate is adjusted so that the outlet temperature reaches the predetermined target outlet temperature, so it corresponds to the target outlet temperature. Therefore, it is possible to adjust the division ratio of the refrigerant, thereby making it possible to effectively utilize the stored cold heat suitable for the current operating state.

According to the invention of claim (2), in the invention of claim (1), the cooling load is detected and the target outlet temperature is set according to the current cooling load. This makes it possible to adjust the capacity as necessary, thereby improving the efficiency of using stored cold heat.

According to the invention of claim (3), in the invention of claim (1), the inlet temperature of the refrigerant before being diverted is detected, and the target extraction amount of stored cold heat is set, and the current amount of refrigerant circulation is determined. Since the target outlet temperature is calculated and set based on the refrigerant circulation amount, target extraction amount, and refrigerant inlet temperature, it is possible to effectively use the stored cold heat while considering the amount of cold storage heat taken out. Therefore, it is possible to significantly reduce power consumption.

According to the invention of claim (4), in the invention of claim (3), the target extraction amount of the cold storage heat is set to a constant value, so that the cold storage heat stored in the cold storage heat operation at night etc. Based on the total amount and the daily operating hours, it is possible to formulate a usage plan for the stored cold heat so as to use up all the stored cold heat, and therefore the invention of claim (3) above can be made effective.

According to the invention of claim (5), in the invention of claim (3), the target amount of cold storage heat to be taken out is set according to the cooling load, so that when the cooling load is small, wasted cold storage heat is not used. While the extraction can be suppressed, the pull-down time can be shortened by taking out a large amount of stored cold heat when the cooling load is large, such as at the start of cooling operation. can be achieved. Furthermore, this allows the device to be made smaller.

According to the invention of claim (6), the above-mentioned claim (3), (
In the invention of 4) or (5), the amount of physical state of the suction refrigerant is detected, and the amount of refrigerant circulation is calculated based on this amount of physical state and the inlet temperature of the liquid refrigerant. The amount of circulation can be estimated, and therefore, the invention of claim (3), (4), or (5) can be carried out effectively.

According to the invention of claim (7), the above claim (3), +
In the invention of 41 or (5), the refrigerant circulation amount is calculated based on the operating capacity of the compressor, the physical state quantity of the suction refrigerant, and the liquid refrigerant inlet temperature, so that a more accurate refrigerant circulation amount can be determined. Therefore, the above claim (3),
The effect of the invention (4) or (5) can be more significantly exhibited.

According to the invention of claim (8), in the invention of claim (7), the amount of refrigerant circulation is determined based on an arithmetic expression whose parameters are the operating capacity of the compressor, the physical state quantity of the suction refrigerant, and the inlet temperature of the liquid refrigerant. Since the estimation calculation is performed, the amount of refrigerant circulation can be determined quickly and accurately, and therefore, the invention of claim (7) can be made more effective.

According to the invention of claim (9), the above-mentioned claim (3), (
In the invention of 4) or (5), since the amount of refrigerant circulation is estimated and calculated based on the physical state amount of the intake refrigerant and the physical state amount of the discharged refrigerant, it is possible to easily and quickly determine the refrigerant circulation amount. Therefore, the above claim (3).

The invention of (4) or (5) can be made effective.

According to the invention of claim (goods), the above claim (3), (
In the invention of 4) or (5), the operating capacity of the compressor;
Physical state of suction refrigerant! ! Since the refrigerant circulation amount is estimated and calculated based on the three amounts and the physical state quantity of the discharged refrigerant, the refrigerant circulation amount can be calculated more accurately. Alternatively, the effect of the invention (5) can be more significantly exhibited.

According to the invention of claim (11), the above claims (1) to ω
), two branch pipes connect the supercooling coil and the liquid line to form a branch channel (20), while the branch pipe and the liquid line through which the remaining branched refrigerant flows are connected to each other. Since a flow rate control valve is provided for each, and the flow division ratio is adjusted by adjusting the opening degree of these two flow rate control valves, the flow division ratio can be finely adjusted. It is possible to make the invention more effective.

According to the invention of claim 02), in the invention of claim (11), one end side of the supercooling coil is connected to the suction line, and the shunting adjustment mechanism and the supercooling coil are utilized during the cold storage heat operation. Since cold heat is stored in the heat storage medium, the configuration of the device can be simplified, and costs can therefore be reduced.

According to the invention of claim a'3I, the above claim GD or O
In the invention of No. 9, the flow division ratio is divided into three regions according to the size, and in the middle region, the opening degree of two flow rate control valves is adjusted, and outside the middle region, one is fixed at full open and the other is variably adjusted. By controlling the diversion rate,
While finely controlling the flow division ratio in the intermediate region, the flow division ratio can be easily controlled outside the intermediate region by simply adjusting the opening degree of one of the flow rate control valves.

According to the invention of Claim Threshold), the above claim (11) or a
In the '2J invention, since the sum of the opening degrees of the two flow rate control valves is controlled to be a constant value, the overall refrigerant circulation amount can be controlled to be almost constant with simple control contents. Therefore, the flow division ratio can be controlled while effectively avoiding unstable control.

According to the invention of claim (15), the above claim 0D or Q
In the invention of 2J, the opening degrees of the two flow rate control valves are controlled so that the combined sum of the flow path specific resistances on the liquid line side and the diversion path side during diversion becomes constant. Regardless of the situation, the pressure loss in the liquid line can be kept constant, and therefore, the state of the liquid refrigerant is stabilized and the opening degree control of the pressure reducing valve on the indoor side is stabilized.

According to the invention of claim OD, the above claims (1) to (g)
), a flow rate control valve is provided only in either the liquid line or the diversion path between the diversion section and the confluence section, and the diversion rate is controlled by adjusting the opening degree of the valve, resulting in a simpler configuration. This allows the flow rate to be controlled.

[Brief explanation of the drawing]

FIGS. 1(a) and 1(b) are block diagrams showing the configuration of the present invention. 2 to 5 show a first embodiment of the present invention, FIG. 2 is a refrigerant piping system diagram of an air conditioner according to the first embodiment, and FIG. 3 shows details of control of the division ratio by the controller. The flowchart diagrams, FIGS. 4(a) to (C) are
Characteristic diagrams showing changes in the opening degree of the two flow control valves, pressure loss in the liquid line, and composite sum of the specific resistance of the liquid line with respect to changes in the flow division ratio, respectively. Figure 5 shows the refrigerant piping of the air conditioner according to the modified example. The system diagram and FIGS. 6(a) to (c) show the third embodiment, and the characteristic diagrams corresponding to FIGS. 4(a) to (c), respectively, and FIGS. 7 to 9 show the fourth embodiment. For example, the seventh
8 is a flowchart showing the control contents of the controller, and FIG. 9 is a refrigerant piping system diagram of the air conditioner according to a modification thereof. 1 Main refrigerant circuit 2 Compressor 3 Outdoor heat exchanger (heat source side heat exchanger) 4 First electronic expansion valve (pressure reduction mechanism) 5 Indoor heat exchanger (user side heat exchanger) 6a Liquid line 6b Suction line 9 Heat storage tank 10 Ice making coil (supercooling coil) 12 Second electronic expansion valve (first flow control valve) 15 Third electronic expansion valve (second flow control valve) 20 Branch flow path 49 Circulation route switching means 50 Cold storage heat means 51 Branch flow adjustment mechanism 52 Target temperature setting means 53 Diversion control means 54 Output amount setting means 55 Circulation amount calculation means 56 Target temperature calculation means spt Low pressure sensor (suction state detection means) Sp2
High pressure sensor (discharge state detection means) Thl Room temperature sensor (load detection means) 'Thi Population temperature sensor (inlet temperature detection means) Tho Outlet temperature sensor (outlet temperature detection means) W Water (thermal storage medium) Fig. 3 Fig. 1 ( b) Figure 1 (Q)

Claims (1)

[Claims] (1) A main refrigerant circuit (1) in which a compressor (2), a heat source side heat exchanger (3), a pressure reduction mechanism (4), and a user side heat exchanger (5) are connected in sequence. , a heat storage tank (9) having a heat storage medium (W) capable of storing cold heat, and a cold heat storage tank (9) that stores cold heat in the heat storage tank (9) through heat exchange between the heat storage medium (W) of the heat storage tank (9) and a refrigerant. In the regenerative air conditioner comprising means (50), the liquid line (6a) between the heat source side heat exchanger (3) of the main refrigerant circuit (1) and the pressure reduction mechanism (4) is bypassed. After separating a part of the liquid refrigerant, the liquid line (6
a), and a branch channel (20) that is provided in the branch channel (20) to supercool the branched refrigerant by heat exchange with the heat storage medium (W) in the heat storage tank (9). a subcooling coil (10) that controls the flow of the refrigerant, and a flow control mechanism (51) that adjusts the flow rate (FRV) of the refrigerant from the main refrigerant circuit (1) to the branch flow path (20). , from the branch channel (20) to the liquid line (6a
) for detecting the outlet temperature (To) of the refrigerant on the upstream side of the pressure reducing mechanism (4).
o), target temperature setting means (52) for setting the target outlet temperature (Tos) of the refrigerant, and outlet temperature detection means (
The outlet temperature (To) receives the output of the target outlet temperature (To) set by the target temperature setting means (Tho).
s). An operation control device for a regenerative air conditioner, characterized in that it is equipped with a flow division control means (53) for controlling the flow division adjustment mechanism (51) so as to achieve the following. (2) Load detection means (Th
1), the target temperature setting means (52) is equipped with the load detecting means (Th
The operation control device for a regenerative air conditioner according to claim 1, wherein the target outlet temperature (Tos) is set based on the cooling load (Qd) detected in step 1). (3) Cold storage heat recovery During cooling operation, the heat source side heat exchanger (3
), the branching path (20) is provided with inlet temperature detection means (Thi) for detecting the inlet temperature (Ti) of the refrigerant before the branching, and the target temperature setting means (52) is configured to set the target amount of cold storage heat to be taken out. An extraction amount setting means (54) for setting the value (ΔQs) and a circulation amount calculation means (55) for calculating the refrigerant circulation amount (G_R).
, the refrigerant circulation amount (G_R) calculated by the circulation amount calculation means (55), the target extraction amount (ΔQs) set by the extraction amount setting means (54), and the inlet temperature detection means (Th
target temperature calculation means (5) for calculating the target outlet temperature (Tos) of the liquid refrigerant based on the inlet temperature (Ti) detected in i);
6) Claim (1)
An operation control device for the regenerative air conditioner described above. (4) Operation control of the regenerative air conditioner according to claim (3), wherein the extraction amount setting means (54) sets the target extraction amount (ΔQs) of the cold storage heat to a constant value. Device. (5) Load detection means (Th
1), and the extraction amount setting means (54) is connected to the load detection means (Th1).
) according to the cooling load (Qd) detected at
3. The operation control device for a regenerative air conditioner according to claim 3, wherein the operation control device sets ΔQs). (6) Suction state detection means (Sp1) for detecting the physical state quantity (Te) of the suction refrigerant of the compressor (2), and the circulation amount calculation means (55) includes the suction state detection means (S
Estimating the amount of refrigerant circulation (G_R) based on the physical state quantity (Te) of the suction refrigerant detected in p1) and the temperature (Ti) of the liquid refrigerant before diversion detected by the inlet temperature detection means (Thi). Claim (3), characterized in that (
4) or the operation control device for a regenerative air conditioner according to (5). (7) The compressor (2) is of variable capacity type;
), a capacity detection means (19) for detecting the operating capacity (F) of the compressor (2), and a suction state detection means (Sp1) for detecting the physical state quantity (Te) of the refrigerant drawn into the compressor (2), The calculation means (55) is configured to detect the inhalation state detection means (S
the physical state quantity (Te) of the suction refrigerant detected at p1);
The amount of refrigerant circulation is determined based on the temperature of the liquid refrigerant before diversion (Ti) detected by the inlet temperature detection means (Thi) and the operating capacity (F) of the compressor (2) detected by the capacity detection means (19). The operation control device for a regenerative air conditioner according to claim 3, wherein the operation control device estimates and calculates (G_R). (8) The circulation amount calculating means (55) calculates the following formula G_R=K_1・Te+f_1(F)−f_2(Ti)
+K_2 (where K_1 and K_2 are constants and f_1 and f_2 represent functions), the refrigerant circulation amount (G_R) is calculated based on Operation control device. (9) Physical state quantity (Te) of the refrigerant sucked into the compressor (2)
a suction state detection means (Sp1) that detects the
), and the circulation amount calculation means (55) includes a discharge state detection means (Sp2) that detects the physical state quantity (Tc) of the refrigerant discharged from the refrigerant, and the circulation amount calculation means (55)
the physical state quantity (Te) of the suction refrigerant detected at p1);
Refrigerant circulation amount (G_R) based on the physical state quantity (Tc) of the discharged refrigerant detected by the discharge state detection means (Sp2)
Claim (3)
), (4) or (5). (10) The compressor (2) is of variable capacity type, and the compressor (2) is of variable capacity type.
); capacity detection means (19) for detecting the operating capacity (F) of the compressor (2); suction state detection means (Sp1) for detecting the physical state quantity (Te) of the refrigerant drawn into the compressor (2); ) Discharge state detection means (Sp2) for detecting the physical state quantity (Tc) of the refrigerant discharged from the refrigerant, and the circulation amount calculation means (55) includes the capacity detection means (19).
The operating capacity (F) of the compressor (2) detected by the compressor (2), the physical state quantity (Te) of the suction refrigerant detected by the suction state detection means (Sp1), and the discharge state detection means (Sp2) detected by the discharge state detection means (Sp2). The heat storage type air according to claim (3), (4) or (5), wherein the refrigerant circulation amount (G_R) is estimated and calculated based on the physical state quantity (Tc) of the discharged refrigerant. Operation control device for harmonization equipment. (11) The branch passage (20) connects one end of the subcooling coil (10) to the liquid line 6a) between the heat source side heat exchanger (3) of the main refrigerant circuit (1) and the main pressure reducing mechanism (4). A first branch pipe (13a) connected to allow refrigerant flow and a subcooling coil (10
) to the liquid line (6a) of the first branch pipe (13a).
) The liquid line (6a
) in the liquid line (6a) of the main refrigerant circuit (1). 13a), (13
b) A first flow control valve (12) interposed between the connection part with
and a second flow control valve (15) interposed in the branch flow path (20).
) Claim (1)
), (2), 13), (4), (5), (6), (7)
, (8), (9) or (10). (11) The second flow control valve (15) has a pressure reducing function, is arranged in the second branch pipe (13b), and is arranged in the first branch pipe (13b).
a) includes an on-off valve (11) that opens and closes the first branch pipe (13a).
) is interposed and connects the other end of the supercooling coil (10) of the first branch pipe (13a) and the on-off valve (11) to the suction line (6b) so that refrigerant can flow therebetween. Branch pipe (
13c) is provided, and during cold storage heat operation, the refrigerant condensed in the heat source side heat exchanger (3) is evaporated from the second branch pipe (13b) in the subcooling coil (10) and transferred to the third branch pipe (13c). The cold storage heat means (50) includes a circulation path switching means (49) for switching from the second flow control valve (13c) to return to the suction line (6b).
15) and a supercooling coil (10). (13) The branch flow control means (53) includes a refrigerant branch flow path (20
) is equal to or higher than the first reference value, the second flow control valve (15) is fixed at full open, the opening degree of the first flow control valve (12) is variably controlled, and the refrigerant is diverted. Rate (FRV
) is below a second reference value, which is smaller than the first reference value, the first flow control valve (12) is fixed at full open and the opening degree of the second flow control valve (15) is variably controlled. Claim characterized in that the opening degrees of the first and second flow control valves (12) and (15) are variably controlled when the flow division ratio (FRV) is between the first reference value and the second reference value. (11) or (12)
) The operation control device for the regenerative air conditioner described in ). (14) The branch control means (53) maintains the sum of the opening degrees of the first and second flow control valves (12) and (15) constant, while maintaining the sum of the opening degrees of the first and second flow control valves (12) and ( Claim (11) or (15) characterized in that the opening degree of (15) is controlled.
12) The operation control device for an air conditioner as described above. (15) The diversion control means (53) controls the first and second flow control valves ( 12), (
15) The operation control device for a regenerative air conditioner according to claim 11 or 12, characterized in that the device controls the opening degree of the regenerative air conditioner. (16) The diversion adjustment mechanism (50) is a single flow control valve provided in either the diversion channel (20) or the liquid line (6a) between the diversion section and the confluence section. Claims (1), (2), (3), (4), (5), (6)
), (7), (8), (9) or (10).