JP2001235189A - Regenerative refrigerating system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a regenerative refrigerating system which can be operated in a mode where it could not be performed hitherto, by simple constitution. SOLUTION: A compressor 10, an outdoor heat exchanger 14, an indoor decompressor 31, and an indoor heat exchanger 32 are connected in order by pipes, and the connection port on liquid side of the outdoor heat exchanger 14 and the connection port on liquid side of the indoor heat exchanger 32 are connected with each other through an opening and closing valve 23 and a liquid refrigerant pump 22 in order. Moreover, one end of the heat exchanger 20a for heat storage and a pert between the vapor side of the indoor heat exchanger 32 and the suction side of the compressor 10 are connected with each other through an opening and closing valve 26, and the other end of the heat exchanger 20a for heat storage and the middle between the connection port on liquid side of the outdoor heat exchanger 12 and the opening and closing valve 23 are connected with each other through a decompressor 21 for heat storage. According to this system, a regenerative refrigerating system can be constructed in simpler constitution than that of a conventional one.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a regenerative refrigeration system for storing heat by using surplus electric power generated at night or the like and performing operation using the heat storage when necessary at daytime or the like.

[0002]

2. Description of the Related Art Such a regenerative refrigeration system has advantages such as effective use of surplus electric power, and is therefore used as a cooling and heating facility for buildings. Such a regenerative refrigeration system is disclosed in, for example,
No. 157297. FIG. 12 shows a configuration diagram of this conventional heat storage refrigeration system. This figure 1
2, a compressor 100, a condenser 101, a first decompression mechanism 102, an evaporator 103, and an accumulator 104 are sequentially connected by piping, and these are used for performing a cooling operation using the compressor 100. A cooling path is formed.

[0005] A heat storage tank 105, a liquid refrigerant pump 106, and a second pressure reducing mechanism 107 are sequentially connected via pipes before and after the evaporator 103. A heat storage heat exchanger 108 is housed inside the heat storage tank 105, and around the heat storage heat exchanger 108, water or the like that exchanges heat with the heat storage heat exchanger 108 is provided. The heat storage medium 109 is accommodated. The heat storage tank 105, the liquid refrigerant pump 106, and the like form a cooling path by the liquid refrigerant pump 106.

Further, an outlet side of the first pressure reducing mechanism 102 and a heat storage heat exchanger 108 and a liquid refrigerant pump 106 are connected by a heat storage bypass circuit 110.
Compressor 100, condenser 101, first pressure reducing mechanism 102,
A heat storage path is sequentially formed through the heat storage bypass circuit 110, the heat storage heat exchanger 108, and the accumulator 104.

In the conventional regenerative refrigeration system configured as described above, a normal cooling operation using the compressor 100, a cold heat storage operation using the compressor 100, and a cooling operation using the heat storage using the liquid refrigerant pump 106 are performed. Alternatively, the combined cooling operation in which the cooling operation and the heat storage utilizing cooling operation are simultaneously performed can be switched and performed.

[0006] The normal cooling operation using the compressor 100 is performed when sufficient heat is not stored in the heat storage tank 105 during the daytime in summer, and the open / close devices 111 to 113 are closed. This is performed by setting the devices 116 to 118 to the open state. Under this setting, when the compressor 100 is operated with the liquid refrigerant pump 106 stopped, the refrigerant is compressed by the compressor 100 to become a high-temperature and high-pressure vapor refrigerant, and is radiated and condensed by the condenser 101 to become a liquid refrigerant. Then, it is slightly adiabatically expanded by the first pressure reducing mechanism 102, flows into the evaporator 103, evaporates in the evaporator 103, absorbs heat from room air, cools, and vaporizes itself. Then, the refrigerant returns to the compressor 100 via the accumulator 104.

[0007] The cold heat storage operation using the compressor 100 is performed, for example, at night in the summer, and the switching devices 111, 115, 113, and 118 are opened and the switching device 1 is opened.
14, 116 and 117 are set to the closed state.
Under this setting, when the compressor 100 is operated with the liquid refrigerant pump 106 stopped, the refrigerant
The heat flows into the heat storage heat exchanger 108 via the condenser 101, the first pressure reducing mechanism 102, and the heat storage bypass circuit 110 in this order. Then, the refrigerant absorbs heat from the heat storage medium in the heat storage heat exchanger 108 to store cold heat, and vaporizes itself, and passes through the accumulator 104 to the compressor 1.
Return to 00. By this refrigerant circulation, the heat storage medium 109 is frozen or the like, and cold heat can be stored.

The cooling operation utilizing heat storage using the liquid refrigerant pump 106 is performed, for example, when the cooling load during the daytime in summer is less than a predetermined value.
7, 113 and 114 are set to the open state,
5, 116 and 118 are set to the closed state. Under this setting, when the compressor 100 is stopped and the liquid refrigerant pump 106 is operated, the refrigerant
The pressure is raised at 6 to become a low-temperature, low-pressure supercooled refrigerant, slightly adiabatically expanded by the second decompression mechanism 107, flows into the evaporator 103, absorbs heat from room air, cools, and evaporates itself. . The refrigerant is stored in the heat storage heat exchanger 10.
At 8, the heat is released to condense and liquefy, and the process returns to the liquid refrigerant pump 106.
By this refrigerant circulation, cooling can be performed using cold heat stored in the heat storage medium 109.

In this cooling operation utilizing heat storage, the power consumption of the liquid refrigerant pump 106 is very small as compared with that of the compressor 100, so that the cooling is performed with less power than in the case of performing the normal cooling operation by the compressor 100. Can be performed.

The combined cooling operation is performed, for example, when cold heat is stored in the heat storage tank 105 and the cooling load in summer daytime is equal to or higher than a predetermined value. This is performed by setting the closed state and other open / close devices to the open state. In this setting, when both the compressor 100 and the liquid refrigerant pump 106 are operated, the cooling in the cooling operation by the compressor 100 and the cooling in the heat storage utilizing cooling operation using the liquid refrigerant pump 106 described above are performed. Simultaneously, the total refrigerant flow during both operations flows through the evaporator 103.

In this combined cooling operation, the ratio between the amount of refrigerant circulated by the compressor 100 and the amount of refrigerant circulated by the liquid refrigerant pump 106 can be arbitrarily set. Can be set to

[0012]

In such a conventional heat storage refrigeration system, the heat storage bypass circuit 110 and the heat storage bypass circuit 110 are used to switch between the heat storage operation by the compressor 100 and the heat storage cooling operation by the liquid refrigerant pump 106. It is necessary to provide a large number of opening / closing devices 111 to 118, and there is a problem that the system configuration is complicated and the system cost is increased.

Further, in the conventional regenerative refrigeration system, various operations can be performed as described above, while a path from the compressor 100 to the evaporator 103 and a path from the compressor 100 to the heat storage tank 105 are provided. Are arranged separately, so that there is a problem that the heat storage operation using the compressor 100 cannot be performed.

Further, in the conventional regenerative refrigeration system, since the circulation direction of the refrigerant is fixed in one direction, a heating operation using the compressor 100, a heat storage operation for storing heat, or a heat storage operation for storing heat. There is a problem that the heat storage utilizing heating operation using the heat storage cannot be performed.

When various operations are performed using the liquid refrigerant pump 106, if steam is generated at the suction port of the liquid refrigerant pump 106, cavitation occurs and its performance and reliability are reduced. Was not done at all.

When the required cooling load or heating load is large, the heat storage tank 1 is generally provided together with the compressor 100 and the like.
The driving ability is enhanced by installing a plurality of 05s. However, in the conventional refrigeration system, heat is simply stored individually in the plurality of heat storage tanks 105, and heat is simply radiated from the heat storage tank 105 individually. Therefore, for example, even when the heat storage in one heat storage tank 105 is completely consumed and the heat storage in another heat storage tank 105 is still left, the remaining heat storage is stored in another heat storage tank 105. It could not be used effectively and the efficiency of the whole system was sometimes reduced.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-described problems in a conventional regenerative refrigeration system, and has a simple configuration that allows operation in a mode that could not be conventionally performed. The purpose is to obtain a refrigeration system.

[0018]

In order to achieve the above object, a regenerative refrigeration system according to the present invention comprises at least a compressor, an outdoor heat exchanger, a use side pressure reducing device, and a use side heat exchanger. A regenerative refrigeration system connected by piping and having a heat storage heat exchanger, wherein a first opening and closing is performed between a liquid-side connection port of an outdoor heat exchanger and a liquid-side connection port of a use-side heat exchanger. One end of the heat storage heat exchanger and one end of the heat storage heat exchanger and the steam side of the use side heat exchanger and the suction side of the compressor are connected via a second on-off valve via a valve and a liquid refrigerant conveying means. The other end of the heat storage heat exchanger is connected to the liquid side connection port of the outdoor heat exchanger and the first on-off valve via a heat storage pressure reducing device.

The regenerative refrigeration system according to the next invention has
One end of the heat storage heat exchanger and the second opening / closing valve are connected to each other between the liquid refrigerant conveying means and the liquid side connection port of the use side heat exchanger via a third opening / closing valve. .

[0020] The regenerative refrigeration system according to the next invention comprises:
A cooling vapor refrigerant flow path for communicating the discharge side of the compressor with the steam side of the outdoor heat exchanger, and the vapor side of the use side heat exchanger with the suction side of the compressor, respectively, and the discharge side of the compressor. A steam refrigerant passage switching means for switching between a steam side of the side heat exchanger, and a heating steam refrigerant passage for communicating the steam side of the outdoor heat exchanger with the suction side of the compressor, respectively. It is a thing.

The regenerative refrigeration system according to the next invention has the following features.
The liquid-side connection port of the outdoor heat exchanger and the suction port of the liquid refrigerant conveying means,
And, a cooling liquid refrigerant flow path for communicating the discharge port of the liquid refrigerant transport means and the liquid side connection port of the use side heat exchanger, respectively,
A heating liquid refrigerant flow path for communicating the liquid side connection port of the use side heat exchanger and the suction port of the liquid refrigerant transporting means, and the discharge port of the liquid refrigerant transporting means and the liquid side connection port of the outdoor heat exchanger, respectively; Are provided with liquid refrigerant flow path switching means for switching between the two.

The regenerative refrigeration system according to the next invention has
At least a compressor, an outdoor heat exchanger, a heat storage decompression device, and a primary cycle configured by sequentially connecting heat storage heat exchangers with piping, and at least a liquid refrigerant conveying means, a use side decompression device, and utilization. A secondary cycle configured by sequentially connecting the side heat exchangers with pipes, and between the primary cycle and the secondary cycle, a heat storage material of the heat exchanger for heat storage of the primary cycle is provided. And an intermediate heat exchanger for exchanging heat with the refrigerant in the secondary cycle.

The regenerative refrigeration system according to the next invention has
In the primary cycle, a cooling steam refrigerant flow path that communicates the discharge side of the compressor and the steam side of the outdoor heat exchanger, and one end of the heat storage heat exchanger and the suction side of the compressor, respectively, A vapor refrigerant flow path for switching between a discharge side of the heat exchanger and one end of the heat storage heat exchanger, and a heating vapor refrigerant flow path for communicating the vapor side of the outdoor heat exchanger and the suction side of the compressor, respectively. It is provided with switching means.

The regenerative refrigeration system according to the next invention has
In the secondary-side cycle, the cooling liquid refrigerant flow for communicating the intermediate heat exchanger with the suction port of the liquid refrigerant conveying means, and the discharge port of the liquid refrigerant conveying means and the liquid side connection port of the use side heat exchanger, respectively. Path, a liquid-side connection port of the use-side heat exchanger and a suction port of the liquid-refrigerant transporting means, and a heating-use liquid-refrigerant flow path that respectively connects the discharge port of the liquid-refrigerant transporting means and the intermediate heat exchanger, It is provided with a liquid refrigerant flow switching means for switching between them.

[0025] The regenerative refrigeration system according to the next invention comprises:
The liquid refrigerant flow path switching means is a bridge path that switches between the cooling liquid refrigerant flow path and the heating liquid refrigerant flow path by opening and closing the four on-off valves.

The regenerative refrigeration system according to the next invention has the following features.
The liquid refrigerant flow switching means is a four-way valve.

[0027] The regenerative refrigeration system according to the next invention comprises:
At least a compressor and an outdoor heat exchanger as an outdoor unit,
At least a heat storage decompression device, a heat storage heat exchanger, and
The liquid refrigerant transport means is configured as a heat storage unit, at least a use side pressure reducing device and a use side heat exchanger as a use side unit, and at least one of the outdoor unit, the heat storage unit, or the use side unit is provided in plurality. It is provided.

[0028] The regenerative refrigeration system according to the next invention comprises:
At least a compressor and an outdoor heat exchanger as an outdoor unit,
At least a heat storage decompression device, a heat storage heat exchanger, and
The liquid refrigerant transport means is configured as a heat storage unit, at least a use side decompression device and a use side heat exchanger as a use side unit, and a plurality of heat storage refrigeration cycle systems including these outdoor units, heat storage units, and use side units are provided. Provided, via the intermediate heat exchanger, at least one of the heat storage material of the heat storage heat exchanger of the regenerative refrigeration cycle system, and the refrigerant of the utilization side unit of at least one of the other regenerative refrigeration cycle systems This allows heat exchange between them.

The regenerative refrigeration system according to the next invention has
An accumulator is provided in front of the suction port of the compressor, and when switching from a predetermined operation using the compressor to a predetermined operation using the liquid refrigerant conveying means, a heat storage decompression device or a utilization device is provided to collect excess refrigerant in the accumulator. The opening of the side pressure reducing device can be adjusted.

The regenerative refrigeration system according to the next invention has
A liquid reservoir is provided on the refrigerant inflow side of the liquid refrigerant conveying means.

The regenerative refrigeration system according to the next invention has the following features:
The flow rate of the liquid refrigerant by the liquid refrigerant conveying means is controlled based on the degree of supercooling of the liquid refrigerant in the vicinity of the refrigerant inflow side of the liquid refrigerant conveying means.

The regenerative refrigeration system according to the next invention has
Temperature detection means for detecting the temperature of the liquid refrigerant in the vicinity of the refrigerant inflow side of the liquid refrigerant conveyance means, pressure detection means for detecting the pressure of the liquid refrigerant in the vicinity of the refrigerant inflow side, and these temperature detection means Calculating means for calculating the degree of supercooling of the liquid refrigerant based on the detected temperature and the pressure detected by the pressure detecting means.

The regenerative refrigeration system according to the next invention has
In order to perform natural circulation of the refrigerant, a bypass pipe that bypasses the liquid refrigerant pump is provided.

The regenerative refrigeration system according to the next invention has
The heat storage material of the heat storage heat exchanger is water or an aqueous solution in which an antifreeze is mixed with water.

[0035]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments 1 to 8 of an animal thermal refrigeration system according to the present invention will be described below in detail with reference to the drawings. However, the present invention is not limited by the embodiment.

Embodiment 1 FIG. 1 is a configuration diagram showing a regenerative refrigeration system according to Embodiment 1 of the present invention. In FIG. 1, the system includes an outdoor unit 1, a heat storage unit 2, and an indoor unit (use side unit) 3.

Of these, the outdoor unit 1 is a means for performing heat exchange outdoors, and includes a compressor 10, a four-way valve (vapor refrigerant flow path switching means) 11, an outdoor heat exchanger 1
2, built-in accumulator 13 and outdoor blower 14. These parts are connected as shown in the figure. In particular, the four-way valve 11 has a first port 11a on the discharge side of the compressor 10 and a second port 11b on the outdoor heat exchanger 12.
, The third port 11c is connected to the suction side of the compressor 10 via the accumulator 13, and the fourth port 11d is connected to the steam side of an indoor heat exchanger 32 to be described later via a steam pipe. The outdoor unit 1 thus configured is connected to the heat storage unit 2 at the vapor-side connection port 4 and the liquid-side connection port 5.

The heat storage unit 2 includes a heat storage tank 20, a heat storage pressure reducing device 21, a liquid refrigerant pump (liquid refrigerant conveying means) 22, an on-off valve (first on-off valve) 23, first and second valves. The heat storage side temperature detectors 24 and 25 are built in. A heat storage heat exchanger 20a is disposed in the heat storage tank 20, and an arbitrary heat storage material 20b such as water is provided around the heat storage exchanger 20a. The liquid side connection port 5 and the liquid side connection port 6 are connected by a liquid pipe 40 via an on-off valve 23 and a liquid refrigerant pump 22. In addition, the space between the steam side connection port 4 and the steam side connection port 7 is
They are connected by a steam pipe 41. Further, the first and second heat storage side temperature detectors 24 and 25 are arranged on the vapor side and the liquid side of the heat storage heat exchanger 20a, respectively, and detect the refrigerant temperature.

Further, one end on the liquid side of the heat storage heat exchanger 20a extends outside the heat storage tank 20, and is connected to the heat storage pressure reducing device 21.
Is connected to the liquid pipe 40 via the. On the other hand, the other end of the heat storage heat exchanger 20a on the steam side extends to the outside of the heat storage tank 20 and is connected to the steam pipe 4 via an on-off valve (second on-off valve) 26.
1 and connected to a liquid pipe 40 via an on-off valve (third on-off valve) 27 and a liquid pipe 42.

The indoor unit 3 has a built-in indoor decompression device (use-side decompression device) 31, an indoor heat exchanger (use-side heat exchanger) 32, and an indoor blower 33. One end of the indoor heat exchanger 32 is
The liquid pipe 43 is connected via the indoor pressure reducing device 31, and the other end is connected to a steam pipe 44. Furthermore, the liquid pipe 4
3 is connected to the liquid-side connection port 6 of the heat storage unit 2, and the steam pipe 44 is connected to the steam-side connection port 7 of the heat storage unit 2.

Each component of each of these units can be configured in the same manner as in the prior art, unless otherwise specified. For example, as the liquid refrigerant pump 22 of the heat storage unit 2,
Any pump such as a rotary pump, a centrifugal pump, an axial flow pump, a friction pump and the like can be used. However, the liquid refrigerant pump 22 has a structure that allows the liquid refrigerant to pass therethrough even when its operation is stopped.

FIG. 2 is a schematic diagram showing the configuration of a gear pump belonging to a rotary pump as an example of the liquid refrigerant pump 22. In FIG. 2, the liquid refrigerant pump 22 as a gear pump includes a pair of gears 22b and 22c, which are rotors, housed in a casing 22a in a state where they are meshed with each other. During operation of the liquid refrigerant pump 22, the drive-side gear 22b is driven to rotate,
The driven gear 22c rotates. And the gear 22b,
When each tooth of 22c is located near the inlet, liquid refrigerant flows into the tooth groove, and this liquid refrigerant is sent to the outlet side while being surrounded between the inner surface of the casing 22a and the tooth grooves of the gears 22b and 22c, The liquid refrigerant is pushed to the outlet side by meshing the teeth at the outlet side. In such a gear pump, even if the operation is stopped, the gear 22 between the casing 22a and the gears 22b and 22c, or the gear 22
The liquid refrigerant can pass between b and 22c.

(Driving Operation) A description will be given of a driving operation in the present system configured as described above. FIG. 3 shows the relationship between each operation mode of the present system and the open / close state of the on-off valve and the like. As shown in FIG. 3, in the present system, a cold heat storage operation using the compressor 10, a cooling operation using heat storage using the liquid refrigerant pump 22, a cooling operation using heat storage using the compressor 10, There are five modes of a normal cooling operation using the compressor and a normal heating operation using the compressor 10, and the operation can be performed by arbitrarily switching these modes. In particular, the cooling operation using heat storage using the compressor 10 and the heating operation using the compressor 10 are operation modes that could not be performed conventionally.

(Cold heat storage operation (compressor 10))
A cold heat storage operation using the compressor 10 will be described. This operation is mainly performed when it is desired to use surplus power in a certain time zone as power in another time zone, and is performed, for example, at night during a summer cooling period. In this operation mode, the four-way valve 11 of the outdoor unit 1 is set so that the first port 11a and the second port 11b communicate with each other and the third port 11c and the fourth port 11d communicate with each other ( Vapor refrigerant flow path for cooling). As shown in FIG. 3, the on-off valve 26 of the heat storage unit 2 is set to an open state, and the on-off valves 23 and 27 are set to a closed state. The indoor pressure reducing device 31 of the indoor unit 3 is set to a fully closed state. The opening degree of the heat storage pressure reducing device 21 will be described later.

Under such a setting, the liquid refrigerant pump 2
When the compressor 10 is operated with the compressor 2 stopped, the refrigerant is
The refrigerant is compressed by the compressor 10 to become a high-temperature and high-pressure vapor refrigerant, flows into the outdoor heat exchanger 12 through the first port 11a and the second port 11b of the four-way valve 11, and radiates heat to outdoor air sent by the outdoor blower 14. Condensed and liquefied to become a medium-temperature, high-pressure liquid refrigerant. This liquid refrigerant flows into the heat-storage decompression device 21 through the liquid-side connection port 5 and is decompressed by the heat-storage decompression device 21 to become a low-temperature, low-pressure gas-liquid two-phase refrigerant, and becomes a heat storage heat exchanger 20a. And becomes a low-temperature and low-pressure vapor refrigerant by absorbing heat from the heat storage material 20b.

At this time, the heat storage material 20b is cooled on the surface of the heat storage heat exchanger 20a, so that cold heat is stored. For example, when the heat storage material 20b is water, it is cooled and becomes ice, and adheres and grows on the surface of the heat storage heat exchanger 20a to store cold heat. On the other hand, the refrigerant vaporized in the heat exchanger for heat storage 20 a is supplied to the on-off valve 26, the steam pipe 41, the steam-side connection port 4, the fourth port 11 d and the third port 11 of the four-way valve 11.
c, and sequentially returns to the suction side of the compressor 10 via the accumulator 13.

The adjustment of the operation capacity in the cold heat storage operation is performed by adjusting the opening of the heat storage pressure reducing device 21. Specifically, the opening degree of the heat storage decompression device 21 is
Temperature T1 detected by first heat storage side temperature detector 24
And the temperature T detected by the second heat storage side temperature detector 25.
2 is automatically or manually controlled so that the difference (T1−T2) approaches the predetermined target value SH1. This target value SH
Basically, 1 is a temperature drop caused by a pressure loss of the refrigerant inside the heat storage heat exchanger 20a and a heat storage heat exchanger 2a.
0a is determined based on the state of the target refrigerant at the vapor side outlet.

For example, the refrigerant may be a single fluorocarbon refrigerant such as R22 or R134a, a hydrocarbon refrigerant such as R290 or R600a, carbon dioxide, or ammonia. In the case where the refrigerant is a refrigerant whose temperature is uniquely determined regardless of the flow rate ratio (dryness) between liquid and vapor, the target value SH1 is determined as follows. That is, assuming that the temperature drop due to the pressure loss from the inlet to the outlet of the heat storage heat exchanger 20a is 2 [deg] and the degree of superheat of the refrigerant at the steam side outlet of the heat storage heat exchanger 20 a is 3 [deg], The target value SH1 = 3-2 = 1 [deg] is determined.
According to this determination method, as in the case of a chlorofluorocarbon-based azeotropic refrigerant such as R410A, in a gas-liquid two-phase state under a certain pressure, the temperature slightly increases as the degree of dryness increases, but the saturated liquid and the saturated vapor The same applies to the case where the temperature difference is about 0.1 ° C. and the refrigerant can be regarded as substantially the same.

On the other hand, in a gas-liquid two-phase state under a certain pressure, such as a CFC-based non-azeotropic refrigerant such as R407C and R407E, the temperature increases as the dryness increases, and the saturated liquid and the saturated vapor In the case of a refrigerant having a temperature difference of several degrees Celsius, the temperature rise Tg from the saturated liquid to the saturated vapor Tg
It is preferable to determine the target value SH1 in consideration of r [deg]. For example, the temperature drop due to the pressure loss from the inlet to the outlet of the heat storage heat exchanger 20a is 2 [deg], and the superheat degree of the refrigerant at the vapor side outlet of the heat storage heat exchanger 20a is 3 [d].
eg], temperature rise from saturated liquid to saturated vapor Tgr = 5
[deg], the target value SH1 = 3-2 + 5 = 6 [deg].

(Cooling operation using heat storage (liquid refrigerant pump 2
2)) Next, a cooling operation using heat storage using the liquid refrigerant pump 22 will be described. This operation is mainly performed when the amount of heat stored in the heat storage tank 20 is sufficient and the peak time of the power consumption needs to be cut, for example, 13:00 to 15:00 in the daytime in summer. is there. In this operation mode, as shown in FIG.
26 is open, on-off valve 27 is closed, and heat storage pressure reducing device 2
1 is set to a fully open state. Also, the four-way valve 11
Is the same as in the cold heat storage operation by the compressor 10. In addition, the opening degree of the indoor side decompression device 31 will be described later.

When the compressor 10 is stopped and the liquid refrigerant pump 22 is operated under such a setting, the liquid refrigerant discharged from the liquid refrigerant pump 22 receives the liquid pipe 40, the liquid side connection port 6, the liquid pipe 43, The refrigerant flows into the indoor heat exchanger 32 through the indoor decompression device 31 in order, absorbs heat from the indoor air sent by the indoor blower 33, cools, and vaporizes itself. The steam refrigerant flows into the heat storage heat exchanger 20a through the steam pipe 44, the steam-side connection port 7, the steam pipe 41, and the on-off valve 26 in order, and is condensed and liquefied by releasing heat to the heat storage material 20b. The liquid refrigerant returns to the liquid refrigerant pump 22 via the heat storage pressure reducing device 21 and the on-off valve 23 in that order. By such an operation, cooling using heat storage is performed.

Naturally, the operation capacity in the cooling operation using heat storage greatly depends on the heat exchange capacity of the heat storage heat exchanger 20a. It is necessary to improve the heat transfer coefficient outside the tube of the exchanger 20a. That is, heat exchange in the heat storage heat exchanger 20a is performed by heating the heat storage material 20b with the steam refrigerant via the heat storage heat exchanger 20a. It is necessary to increase the heat transfer coefficient outside the tube of the exchanger 20a. Various structures are conceivable for this purpose. For example, fins may be provided on the outer periphery of the heat storage heat exchanger 20a to increase the extra-tube heat transfer area.

In the initial stage of melting of the heat storage material 20b, the heat conductivity of water generated by the melting substantially determines the heat transfer coefficient outside the tube of the heat storage heat exchanger 20a. Heat storage heat exchanger 2
The external heat transfer coefficient of Oa may be improved. For example, a material having high thermal conductivity such as metal scrap is mixed in water as the heat storage material 20b, or a stirring means is provided inside the heat storage tank 20,
Forced convection may be applied to the water formed by the melting of the ice.

Alternatively, as shown in FIG.
Is provided with a pipe 20c, and gas such as air is sent into the pipe 20c using an air pump (not shown), and the heat storage tank 20 is passed through a bubble blowing hole 20d provided in the pipe 20c.
May be blown from below.
In this case, the blown bubbles 20e enter the molten water formed between the ice 20f formed around the heat storage heat exchanger 20a and the heat storage heat exchanger 20a, and the molten water By promoting the degree of turbulence, the heat transfer coefficient outside the tube can be greatly improved.

The adjustment of the operation capacity in the cooling operation utilizing heat storage using the liquid refrigerant pump 22 is performed by the indoor side decompression device 31.
The adjustment is performed by adjusting the opening degree. The degree of opening of the indoor side decompression device 31 is determined by the difference between the vapor side outlet temperature TG1 of the indoor side heat exchanger 32 measured by a temperature detector (not shown) and the liquid side outlet temperature TL1 (TG1-TL1 = superheat degree). )
Is controlled so as to approach the preset degree of superheat SHin1 of the indoor-side heat exchanger 32 set in advance. In addition,
When a plurality of indoor units 3 are installed with a height difference,
The inlet pressure of the indoor decompression device 31 installed at the lower part rises by the liquid head corresponding to the height difference between the indoor decompression device 31 installed at the upper part and the indoor decompression device 31 installed at the lower part. Accordingly, in this case, the indoor decompression device 3
The opening degree of 1 may be controlled so that the opening degree of the upper indoor side decompression device 31 becomes larger by this pressure rise. The method for determining the outlet superheat degree SHin1 is the same as the method for determining the target value SH1 described above.

(Heat Storage Utilization Cooling Operation (Compressor 10)) Next, a heat storage utilization cooling operation using the compressor 10 will be described. This operation is mainly performed when the amount of heat stored in the heat storage tank 20 is sufficient and a peak of power consumption does not need to be cut, for example, in the morning or evening in summer. In this operation, as shown in FIG. 3, the on-off valves 23 and 26 are closed, the on-off valve 27 is open,
The heat storage pressure reducing device 21 is set to a fully open state. The setting of the four-way valve 11 is the same as that of the cold heat storage operation by the compressor 10, and the opening degree of the indoor decompression device 31 is
It is adjusted in the same manner as in the cooling operation using heat storage using.

When only the compressor 10 is operated under such a setting, the high-temperature and high-pressure vapor refrigerant discharged from the compressor 10 is condensed and liquefied in the outdoor heat exchanger 12, and is connected to the liquid-side connection port 5 and the decompression for heat storage. It flows into the heat exchanger for heat storage 20a via the device 21 sequentially. Here, the liquid refrigerant is the heat storage material 2
The refrigerant is cooled by the ice of 0b and becomes a low-temperature and high-pressure supercooled liquid refrigerant, flows into the indoor-side decompression device 31 via the on-off valve 27, is decompressed, and becomes a low-pressure and low-temperature two-phase refrigerant. This two-phase refrigerant absorbs heat from the indoor air in the indoor heat exchanger 32 to perform cooling, and also evaporates itself to become a vapor refrigerant,
The steam returns from the accumulator 13 to the suction side of the compressor 10 through the steam pipes 44 and 41 and the fourth port 11d and the third port 11c of the four-way valve 11 in order.

As described above, in the present system, it is possible to perform the cooling operation utilizing the heat storage using the compressor 10, which could not be performed conventionally. In this cooling operation using heat storage, as in the cooling operation using heat using the liquid refrigerant pump 22, the operation capacity can be improved by improving the heat transfer coefficient outside the tube of the heat storage heat exchanger 20a.

(Cooling Operation (Compressor 10)) Next, a normal cooling operation using the compressor 10 will be described. This operation is performed when the ice in the heat storage tank 20 is used up,
This is performed when it is desired to suppress the power consumption due to the heat storage operation. During this operation, the on-off valve 23 is set to the open state, the on-off valves 26 and 27 are set to the closed state, and the heat storage pressure reducing device 21 is set to the fully closed state. The setting of the four-way valve 11 is the same as during the heat storage operation by the compressor 10 and the like, and the opening of the indoor pressure reducing device 31 is adjusted in the same manner as the heat storage cooling operation using the liquid refrigerant pump 22.

When only the compressor 10 is operated under such a setting, the high-temperature and high-pressure vapor refrigerant discharged from the compressor 10 is condensed and liquefied in the outdoor heat exchanger 12 and is opened and closed.
The pressure is reduced by the indoor pressure reducing device 31 via the liquid refrigerant pump 3 and the liquid refrigerant pump 22 in order to become a low-pressure low-temperature two-phase refrigerant. The two-phase refrigerant absorbs heat from the indoor air in the indoor heat exchanger 32 to perform cooling, and itself becomes a low-temperature and low-pressure vapor refrigerant. The steam refrigerant is supplied to the steam pipes 44 and 41, the four-way valve 1
The air returns from the accumulator 13 to the suction side of the compressor 10 through the first fourth port 11d and the third port 11c.

Although an example in which only the cooling operation is performed is described here, the cooling operation and the heat storage operation by the compressor 10 can be performed simultaneously. To this end, the on-off valve 26 is opened, and the heat storage pressure reducing device 21 may be controlled to an appropriate opening degree. In this case, the degree of opening of the indoor decompression device 31 and the heat storage decompression device 21 may be controlled so that the cooling capacity according to the indoor heat load is obtained, and the remaining cooling capacity may be allocated to heat storage. .

(Heating Operation (Compressor 10)) Next, a normal heating operation will be described. During this operation,
As shown in FIG. 3, the on-off valves 23, 26, and 27 are set in the same manner as in the normal cooling operation. Also, the outdoor unit 1
The four-way valve 11 is set so that the first port 11a and the fourth port 11d communicate with each other, and the second port 11b and the third port 11c communicate with each other (heating steam refrigerant flow path). As described above, the heating operation that could not be performed conventionally can be performed because the four-way valve 11 can switch the cooling vapor refrigerant flow path to the heating vapor refrigerant flow path. Here, the heat storage pressure reducing device is set to a fully closed state. The opening degree of the indoor decompression device 31 will be described later.

When only the compressor 10 is operated under such a setting, the vapor refrigerant which has been compressed by the compressor 10 and has become high temperature and high pressure is supplied from the first port 11 a to the fourth port 11 a of the four-way valve 11.
d, the indoor heat exchanger 3 via the steam pipes 41 and 44 sequentially.
Flow into 2. Here, the high-temperature and high-pressure refrigerant radiates heat to room air to condense and liquefy, so that the room air is heated and heated, and the refrigerant becomes a medium-temperature and high-pressure liquid refrigerant. The liquid refrigerant is decompressed by the indoor decompression device 31 to become a low-temperature, low-pressure gas-liquid two-phase refrigerant, and flows into the outdoor heat exchanger 12 through the liquid pipe 43, the liquid refrigerant pump 22, and the on-off valve 23 in order. Here, the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat from the outdoor air and evaporates.
It returns to the suction side of the compressor 10 via the port 11c and the accumulator 13 in order.

The adjustment of the operation capacity in such a heating operation is performed by adjusting the opening of the indoor side pressure reducing device 31. The degree of opening of the indoor side decompression device 31 is determined by a saturation temperature TC1 with respect to a detection pressure of a pressure detector (not shown) provided on the discharge side of the compressor 10 and a liquid supply outlet of the indoor side heat exchanger 32 shown in FIG. The difference (TC1−TL1 = degree of supercooling) from the temperature detection value TL1 of the second pipe temperature detector which is not used is determined by the indoor heat exchanger 32 which is set in advance.
Is controlled so as to approach the outlet subcooling degree SCin1.
Further, the degree of supercooling SCin1 at the outlet of the indoor heat exchanger 32 is also described.
Is preferably set to about 10 to 15 ° C. so that the indoor heat exchanger 32 can obtain a sufficient heating capacity.

As described above, in the present system, the compressor 1 which could not be used conventionally
A cooling operation using heating and a heating operation using 0 can be performed. In addition, when it is not necessary to perform the heating operation, the four-way valve 11 is omitted, the discharge port of the compressor 10 is simply connected to the steam side of the outdoor heat exchanger 12, and the compressor 10
May be connected to the steam side of the indoor heat exchanger 32 via the accumulator 13. Also in this case, the cooling operation using heat storage using the compressor 10 can be performed.

Alternatively, when it is not necessary to perform the cooling operation utilizing heat storage using the compressor 10, the pipe 42 and the on-off valve 27 may be omitted. Also in this case, similarly to the above, the cold heat storage operation using the compressor 10, the heat storage utilizing cooling operation using the liquid refrigerant pump 22, the normal cooling operation using the compressor 10, and the use of the compressor 10 The usual heating operation can be performed. In particular, in this configuration,
The cooling operation using heat storage using the liquid refrigerant pump 22 can be performed with a simple configuration in which the liquid refrigerant pump 22 and the opening / closing valve are simply added to a normal ice storage air conditioner, so that the system configuration is simplified. And system cost can be reduced.

When a refrigerant pump is provided as in the present system, various problems may occur. Hereinafter, such a problem and a configuration for solving the problem will be described. Generally, lubrication of each sliding portion of the liquid refrigerant pump 22 is performed not by lubricating oil but by the liquid refrigerant (for example, water) transported by the liquid refrigerant pump 22 itself. Since the lubricating effect of the liquid refrigerant increases in proportion to the viscosity thereof, the lubricating effect is reduced when a CFC-based or hydrocarbon-based liquid refrigerant having a viscosity about one order smaller than that of water is conveyed. Therefore, in the case of transporting such a CFC-based liquid refrigerant, poor lubrication may occur in each sliding portion of the liquid refrigerant pump 22 and the wear thereof may be accelerated. In such a case, the abrasion powder mixes in the refrigerant flow passage, and the expansion valve is clogged.
May be damaged.

In order to avoid such a problem, for example, a removing device such as a filter for removing abrasion powder in the liquid refrigerant may be provided at the outlet of the liquid refrigerant pump 22.
In this case, since the abrasion powder can be removed, an adverse effect on the liquid refrigerant pump 22 due to the abrasion powder can be prevented, and the reliability of the entire system can be improved.

When a gear pump as shown in FIG. 2 is used as the liquid refrigerant pump 22, as described above, the liquid refrigerant can pass even when the operation is stopped. Therefore, flow resistance may be caused by the passage of the liquid refrigerant. The effect of the flow resistance can be eliminated by increasing the opening of the indoor pressure reducing device 31 as compared with the case where the liquid refrigerant pump 22 is not provided. In addition, the flow resistance can be adjusted by appropriately setting the gap between the casing 22a and the gears 22b and 22c.

Although the cooling operation using only the compressor 10 has been described above, the liquid refrigerant pump 22 may be operated together with the compressor 10. In this case, since the flow resistance when the liquid refrigerant passes through the liquid refrigerant pump 22 can be reduced, the opening degree of the indoor decompression device 31 can be performed in the same manner as in the ordinary cooling operation by the compressor 10. it can.

Next, a description will be given of structural features relating to prevention of cavitation and the like. Generally, the amount of refrigerant circulating during operation of the liquid refrigerant pump 22 depends on the compressor 10
Compared to the amount during operation. In order to absorb such a difference in the amount, the accumulator 13 is provided in the present system.
Is provided. That is, when the compressor 10 is operating, excess refrigerant is stored in the accumulator 13, and when the liquid refrigerant pump 22 is operating, the refrigerant is replenished from the accumulator 13. According to such a configuration, an optimal amount of the refrigerant can be circulated both during the operation of the liquid refrigerant pump 22 and during the operation of the compressor 10, and the system efficiency can be improved.

However, when the accumulator 13 is simply provided, the amount of the refrigerant may not be optimized. That is, when the operation of the compressor 10 is switched to the operation of the liquid refrigerant pump 22 simply by opening and closing the valve, the excess refrigerant stored in the accumulator 13 is not supplied smoothly, so that the operation of the liquid refrigerant pump 22 is not performed. Sometimes, the amount of the refrigerant may be insufficient. In this case, the refrigerant flowing into the liquid refrigerant pump 22 becomes a two-phase refrigerant so that a predetermined cooling capacity cannot be obtained, or cavitation occurs inside the liquid refrigerant pump 22 and the liquid refrigerant pump 22 is damaged. May be equal. As is well known, the cavitation is a phenomenon in which a gas appears in a flowing liquid to form a cavity, which is generally not accompanied by sound or vibration and is undesirable because it lowers the pump efficiency.

Therefore, in the present embodiment, in order to prevent the occurrence of such cavitation and the like, when the operation of the compressor 10 is switched to the operation of the liquid refrigerant pump 22, for example, the cold heat storage by the compressor 10 is performed. When switching from the operation to the cooling operation using heat storage by the liquid refrigerant pump 22, the pressure reducing device 21 for heat storage or the indoor pressure reducing device 3 is used.
1 is controlled to be small, and a refrigerant recovery operation for recovering excess refrigerant stored in the accumulator 13 is performed. By performing such a refrigerant recovery operation, a liquid refrigerant is reliably supplied to the liquid refrigerant pump 22 during operation using the liquid refrigerant pump 22,
Stable liquid refrigerant pump 2 without causing shortage of refrigerant amount
2 operation can be performed.

Embodiment 2 FIG. 6 is a configuration diagram showing a regenerative refrigeration system according to Embodiment 2 of the present invention. In the present embodiment, as compared with the configuration of the first embodiment, two heat storage units are dispersed and arranged.
The configuration is such that the piping 42 and the on-off valve 27 in FIG. 1 are omitted. The configuration that is not particularly described is the same as that of the first embodiment, and the same configuration is denoted by the same reference numeral.

In this system, the two heat storage units 2A and 2B are connected to the outdoor unit 1 and the indoor unit 3 at branch points 8a to 8d as shown in the drawing. In this system, basically, the first embodiment
In the same manner as in the case where the pipe 42 and the opening / closing valve 27 are omitted, a cold heat storage operation using the compressor 10, a heat storage utilizing cooling operation using the liquid refrigerant pump 22, a normal cooling operation using the compressor 10, and A normal heating operation using the compressor 10 can be performed.

In particular, in the present system, the heat storage units 2A and 2B are arranged in a distributed manner, and therefore have an advantage different from that of the first embodiment. Hereinafter, this advantage will be described. First, when the indoor unit 3 is increased in size or the like, the total heat load of the indoor unit 3 increases, so it is naturally necessary to increase the heat treatment capacity of the heat storage unit 2. Specifically, it is necessary to increase the size of the liquid refrigerant pump 22 and the heat storage tank 20 constituting the heat storage unit 2. However, in this case, the heat storage unit 2 is undesirably increased in overall size and weight.

When the heat storage unit 2 becomes large in size, it becomes difficult to secure the installation space, which hinders the spread of the system. In particular, when this system is introduced to renew existing air conditioning equipment, the installation space is already fixed, making installation more difficult and limiting the weight strength of the installation surface. In some cases, it is difficult to introduce them. Even if the heat storage unit 2 can be installed, if any failure occurs inside the heat storage unit 2, the heat storage unit 2
When the operation of the system is disabled, the air-conditioning operation of the entire system is stopped.

Therefore, in the present embodiment, the heat storage units 2A and 2B are configured in a distributed manner as described above, so that each of the heat storage units 2A and 2B can be downsized. In this case, the heat storage units 2A, 2B
Since the space required for installation is reduced, for example, each heat storage unit 2A, 2B can be installed on a separate floor in a building, and the weight load on the installation surface can be reduced. In addition, even when any part of each of the heat storage units 2A and 2B has a problem, the heat storage units 2A and 2B can be stopped and the operation of the entire system can be continued. Can be configured. In the present embodiment,
An example is shown in which one outdoor unit 1 and one indoor unit 3 are connected to two heat storage units 2, respectively.
A configuration in which a plurality of outdoor units 1 and indoor units 3 are installed may be adopted.

Embodiment 3 FIG. 6 is a configuration diagram illustrating a regenerative refrigeration system according to Embodiment 3 of the present invention. This embodiment is different from the first embodiment in that the pipe 42 and the on-off valves 23 and 27 shown in FIG. 1 are omitted, and a bridge path for switching the discharge direction of the liquid refrigerant pump is provided. The present invention relates to a regenerative refrigeration system. The configuration that is not particularly described is the same as that of the first embodiment, and the same configuration is denoted by the same reference numeral.

In FIG. 6, the heat storage unit 2 is provided with a bridge path (liquid refrigerant flow switching means) 28 as shown in the drawing, which includes opening / closing valves 28a to 28d, in which the liquid refrigerant pump 22 is disposed. Have been. In this system, basically, similarly to the case where the pipe 42 and the opening / closing valve 27 are omitted in the first embodiment, a cold heat storage operation using the compressor 10, a heat storage utilizing cooling operation using the liquid refrigerant pump 22, A normal cooling operation using the compressor 10 and a normal heating operation using the compressor 10 can be performed.

That is, in the present system, the open / close valve 23 in FIG. 1 is also omitted, but the open state of the open / close valve 23 is such that the open / close valves 28c and 28a are open and the open / close valves 28b and 28b
This can be achieved by setting 28d to a closed state (cooling liquid refrigerant flow path). The closed state of the on-off valve 23 can be achieved by setting the on-off valves 28b and 28c to the closed state. Therefore, a cold heat storage operation using these compressors 10, a heat storage utilization cooling operation using the liquid refrigerant pump 22,
Normal cooling operation using the compressor 10 and the compressor 1
The normal heating operation using 0 can be performed by performing the same valve setting and the opening adjustment of the pressure reducing device as in the first embodiment, and thus the description thereof is omitted.
It should be noted that an on-off valve is connected between the steam-side end of the heat storage heat exchanger 20a and the on-off valve 26, and between the liquid-side connection port 6 in the liquid pipe 40 and the bridge path 28. If the connection is made via a pipe, the cooling operation utilizing heat storage by the compressor 10 can be performed as in the first embodiment.

Further, in the present system, the compressor 1
0 can be used for thermal storage operation.
By switching the discharge direction of the liquid refrigerant pump 22 to the opposite direction using the bridge path 28, a heating operation using heat storage using the liquid refrigerant pump 22 can be performed. That is, the discharge direction can be reversed by setting the on-off valves 28d and 28b to the open state and the on-off valves 28a and 28c to the closed state (heating liquid refrigerant flow path).

To be precise, in the first embodiment, the thermal storage operation was also possible, but the heating operation using the thermal storage could not be performed, so that the thermal storage operation could not be used substantially. It was what was. Hereinafter, the thermal storage operation and the storage-using heating operation will be described.

(Heat Heat Storage Operation (Compressor 10)) The heat heat storage operation using the compressor 10 is performed in order to store heat mainly by using nighttime power during the winter heating period. In this operation mode, the four-way valve 11 of the outdoor unit 1 is set to a vapor refrigerant flow path for heating, the open / close valve 26 of the heat storage unit 2 is opened, the open / close valves 28b and 28c are closed, and the indoor unit 3 The pressure reducing device 31 is set to a fully closed state. The opening adjustment of the heat storage decompression device 21 is the same as the opening adjustment of the indoor decompression device 31 during the heating operation described in the first embodiment.

When only the compressor 10 is operated under such a setting, the refrigerant compressed by the compressor 10
The heat storage heat exchanger 20a passes from the first port 11a to the fourth port 11d of the four-way valve 11 through the steam pipe 41 and the on-off valve 26.
Into the heat storage material 20b to be condensed and liquefied. At this time, the heat storage material 20b is heated and becomes, for example, hot water, and stores heat. The condensed and liquefied medium-temperature and high-pressure liquid refrigerant is decompressed by the heat storage decompression device 21 to become a low-temperature and low-pressure two-phase refrigerant, flows into the outdoor heat exchanger 12, absorbs heat from the outdoor air, and is vaporized. The low-temperature and low-pressure vapor refrigerant returns to the compressor 10 through the second port 11b of the four-way valve 11, the third port 11c, and the accumulator 13. According to such an operation, heat can be stored in the heat storage material 20b.

(Heating operation using heat storage (liquid refrigerant pump 2
2)) Next, a heating operation using heat storage using the liquid refrigerant pump 22 will be described. In this operation mode, the on-off valve 2
6 is set to an open state, the bridge path 28 is set to a heating liquid refrigerant flow path, and the heat storage decompression device 21 is set to a fully open state. The degree of opening of the indoor pressure reducing device 31 can be adjusted in the same manner as in the heating operation of the first embodiment.

Under such a setting, the liquid refrigerant pump 2
2 is operated, the liquid refrigerant discharged from the liquid refrigerant pump 22 flows into the heat storage heat exchanger 20a via the on-off valve 28b and the heat storage pressure reducing device 21 in order, and
Endothermic from b. This vapor refrigerant is supplied to the on-off valve 2
6, the steam pipe 41, the steam-side connection port 7, and the steam pipe 44 sequentially flow into the indoor heat exchanger 32, radiate heat to indoor air to perform heating, and condense and liquefy to become a liquid refrigerant. . The liquid refrigerant is slightly depressurized by the indoor decompression device 31, and then returns to the liquid refrigerant pump 22 through the liquid pipes 43 and 40 and the on-off valve 28d in order. According to such an operation, heating can be performed using the heat stored in the heat storage material 20b.

As described above, according to the present embodiment, a simple configuration in which the bridge path 28 including the liquid refrigerant pump 22 is added to a normal ice storage air conditioner,
Not only cold heat storage and heat storage cooling, but also heat heat storage and heat storage heating can be performed, and there is an effect that power peaks can be cut during the daytime in summer or winter during the day when power demand peaks. Further, the peak cut of the cooling and the heating can be performed by one liquid refrigerant pump 22, and an inexpensive and simple refrigerant path can be configured.

Embodiment 4 FIG. 7 is a configuration diagram illustrating a regenerative refrigeration system according to Embodiment 4 of the present invention. The present embodiment relates generally to a regenerative refrigeration system in which a four-way valve is provided in place of the bridge path in the basic configuration of the third embodiment, and the rotation control of the liquid refrigerant pump is automatically performed. Things. The configuration that is not particularly described is the same as in the first and third embodiments described above.
The same components are denoted by the same reference numerals.

In FIG. 7, the heat storage unit 2 is provided with a four-way valve (liquid refrigerant flow path switching means) 29 as shown. Further, the heat storage pressure reducing device 21 in the liquid pipe 40
An opening / closing valve 50 is provided between the connection portion and the four-way valve 29, and an opening / closing valve 51 is provided between the connection portion and the liquid-side connection port 5. Further, a liquid storage container 52, a pressure detecting section (pressure detecting means) 53, and a third heat storage side temperature detector (temperature detecting means) 54 are sequentially connected to the inflow side of the liquid refrigerant pump 22 as shown in the figure. Calculation unit (calculation means) 5
5 are provided as shown. The calculation unit 55 calculates the target rotation speed of the liquid refrigerant pump 22 based on the pressure detected by the pressure detection unit 53 and the temperature detected by the third heat storage temperature detector 54.

In the system configured as described above,
Basically, the same operation as in the third embodiment can be performed. That is, by setting the second port 29b and the third port 29c of the four-way valve 29 to be in communication with the first port 29a and the fourth port 29d, respectively, a cooling liquid refrigerant flow path can be configured. . Also, the first port 29 of the four-way valve 29
By setting a and the second port 29b to communicate with the third port 29c and the fourth port 29d, a liquid refrigerant flow path for heating can be configured. Further, by closing the on-off valve 50, the same state as when the on-off valves 28b and 28c are closed can be achieved (the on-off setting of the on-off valve 51 will be described later).

Therefore, a cold heat storage operation using the compressor 10, a heat storage utilizing cooling operation using the liquid refrigerant pump 22, a normal cooling operation using the compressor 10,
In addition to the normal heating operation using the compressor, a heat storage operation using the compressor 10 and a heating operation using heat storage using the liquid refrigerant pump 22 can be performed.

As described above, when the four-way valve 29 is used instead of the bridge path, the number of on-off valves can be reduced as compared with the case where the bridge path is used. can do. The four-way valve 29
For example, a pilot-type four-way valve that uses a pressure difference between the discharge pressure and the suction pressure of the liquid refrigerant pump 22 to switch the flow path may be used, or a pressure difference required for switching the flow path may be used. When is small, a rotary four-way valve can be used.

In addition to the points described above, the present system
It has various structural features different from those of the other embodiments. Hereinafter, this point will be described. First, in Embodiments 1 to 3 described above, the heat storage heat exchanger 20a and the liquid refrigerant pump 22 are connected to the liquid-side connection port 5 so as to simply communicate with each other. Therefore, during the cooling operation using heat storage using the liquid refrigerant pump 22, there is a possibility that the liquid refrigerant condensed and liquefied in the heat storage heat exchanger 20a flows into the outdoor unit 1 through the liquid side connection port 5. During the heating operation using the refrigerant pump 22, there is a possibility that the liquid refrigerant discharged from the liquid refrigerant pump 22 flows into the outdoor unit 1 via the liquid side connection port 5. Therefore, in order to compensate for this inflow, it was necessary to fill the system with an extra refrigerant.

On the other hand, in this embodiment, the on-off valve 51 is provided as described above, and by opening and closing this on-off valve 51, it is possible to prevent the liquid refrigerant from flowing into the outdoor unit 1. it can. In other words, the liquid refrigerant flows into the outdoor unit 1 by setting the on-off valve 51 to the closed state during the cooling operation using the heat storage using the liquid refrigerant pump 22 and the heating operation, and setting the open / close valve 51 to the open state only during other operations. This eliminates the need to charge the refrigerant. Therefore, the present system can be operated more stably. It should be noted that such a structure for preventing the inflow of the liquid refrigerant can be similarly applied to other embodiments.

Next, a description will be given of structural features relating to prevention of cavitation and the like. As described in the description of the first embodiment, in the present system, the accumulator 13 is provided so that excess refrigerant can be stored, and when switching from the operation of the compressor 10 to the operation of the liquid refrigerant pump 22 is performed, The opening degree of the heat storage decompression device 21 or the indoor decompression device 31 is controlled to be small, and a refrigerant recovery operation for recovering the excess refrigerant stored in the accumulator 13 is performed to prevent the shortage of the refrigerant amount. .

In addition, in the present system, a liquid reservoir 52 is provided at the inflow portion of the liquid refrigerant pump 22.
Since the excess refrigerant is always stored in the liquid storage container 52, when the refrigerant recovery operation is insufficient or when the amount of the refrigerant is transiently insufficient, the liquid stored in the liquid storage container 52 is The refrigerant is supplied to the liquid refrigerant pump 22. Therefore, the liquid refrigerant can be reliably supplied to the liquid refrigerant pump 22, and the stable operation of the liquid refrigerant pump 22 can be performed.

As described above, in the present system, the occurrence of cavitation is prevented by preventing the shortage of the refrigerant amount. However, even if such various measures are taken, there is a possibility that cavitation may occur due to overlapping bad conditions. For this reason, in the present system, even when cavitation occurs, the system is devised to minimize the effect.

More specifically, two different measures are taken depending on whether or not the liquid refrigerant pump 22 has reduced reliability due to cavitation. That is, the effect of cavitation on the liquid refrigerant pump 22 differs depending on the type of the liquid refrigerant pump 22, and a pump that causes problems such as noise / vibration and corrosion promotion when cavitation occurs. Although pumps do not occur, pumps are roughly classified into pumps whose discharge flow rate is reduced because the refrigerant is in a two-phase state. Therefore, in this system, different countermeasures are taken according to the characteristics of such a pump.

Specifically, on the suction side of the liquid refrigerant pump 22, based on the temperature detected by the third heat storage side temperature detector 54 and the pressure detected by the pressure detection section 53,
The degree of supercooling SCpin of the suction port of the liquid refrigerant pump 22 is calculated by the calculation unit 55. This supercooling degree SCpin is the third
The temperature detected by the heat storage side temperature detector 54 is Tpin, and the saturated liquid temperature corresponding to the pressure detected by the pressure detector 53 is Tspin.
Then, SCpin = Tspin−Tpin. When the degree of supercooling SCpin is calculated in this manner, the target rotation speed is calculated by the calculation unit 55 based on the degree of supercooling SCpin, and the rotation speed of the liquid refrigerant pump 22 is controlled to be the rotation speed. You.

For example, when the degree of supercooling SCpin becomes 5 ° C. or less, and in the case of the liquid refrigerant pump 22 that is less affected by cavitation, the cooling capacity is increased by increasing the target flow rate to increase the refrigerant flow rate. Let it recover. In addition, in the case of the liquid refrigerant pump 22 in which the above-described problem occurs with respect to cavitation, the target rotation speed is reduced and the
Suppress cavitation by restoring the pin.

As described above, in the present system, the influence of cavitation can be reduced by adjusting the number of revolutions according to the state of the liquid refrigerant pump 22 and its characteristics. It should be noted that such a system for adjusting the number of revolutions can be similarly applied to other embodiments.

Embodiment 5 FIG. FIG. 8 is a configuration diagram showing a regenerative refrigeration system according to Embodiment 5 of the present invention. This embodiment is different from the basic configuration of the third embodiment in that a refrigerant path (primary cycle) for air-conditioning operation by the compressor 10 and a refrigerant path (secondary side) for air-conditioning operation by the liquid refrigerant pump 22 are provided. Cycle) from each other,
The present invention relates to a regenerative refrigeration system in which heat exchange between these two cycles is performed via an intermediate heat exchanger. The configuration that is not particularly described is the same as that of the third embodiment described above, and the same configuration is denoted by the same reference numeral.

As shown in FIG. 8, in the present system, one end of the heat storage tank 20 is directly connected to the steam-side connection port 4, and the heat storage material 20 b is supplied from the heat storage tank 20 to the heat storage material transfer pump 6.
0 circulates outside. A part of the circulation path is drawn into the intermediate heat exchanger 61. Further, the steam-side connection port 7 and the bridge path 28 are directly connected, and a part of this connection path is drawn into the intermediate heat exchanger 61. The heat storage material 20b in the primary cycle and the refrigerant in the secondary cycle can exchange heat with each other via the intermediate heat exchanger 61.

In the first to third embodiments described above, the primary cycle and the secondary cycle are communicated with each other, and the air conditioning capacity necessary for the cooling operation or the heating operation by the liquid refrigerant pump 22 is obtained. If not, a backup operation using the compressor 10 in addition to the liquid refrigerant pump 22 can be performed. On the other hand, in the present embodiment, the primary cycle and the secondary cycle are separated, and the backup operation as described above cannot be performed, but cooling and heating are performed only in the secondary cycle. It has become possible. Such a separated refrigerant path configuration is
For example, it is suitable when the heat transfer area of the heat storage tank 20 or the heat storage heat exchanger 20a is sufficiently large and the air conditioning operation by the liquid refrigerant pump 22 alone can sufficiently cover the necessary air conditioning load.

The operation of the present system configured as described above will be described. The operation modes of the present system include at least four modes of a cold heat storage operation by a compressor, a heat storage cooling operation by a liquid refrigerant pump, a heat storage operation by a compressor, and a heat storage heating operation by a liquid refrigerant pump. The operation can be performed by switching to each other. In each operation, the four-way valve 11
The setting of opening and closing of the bridge path 28 and the adjustment of the opening degree of the heat storage decompression device 21 and the indoor decompression device 31 are the same as the corresponding operation operations of the third embodiment, unless otherwise specified.

(Cold Heat Storage Operation (Compressor 10)) First, the cold heat storage operation using the compressor 10 will be described. First, when only the compressor 10 is operated, the vapor refrigerant compressed by the compressor 10 flows from the first port 11a of the four-way valve to the second port 11a.
It flows into the outdoor heat exchanger 12 through the port 11b, and radiates heat to outdoor air to become a liquid refrigerant. This liquid refrigerant is decompressed by the heat storage decompression device 21 via the liquid side connection port 5 to become a two-phase refrigerant,
The heat flows into the heat storage heat exchanger 20a to store cold heat in the heat storage tank 20 and vaporizes itself. The evaporated refrigerant is supplied from the vapor side connection port 4, the fourth port 11d to the third port 11c of the four-way valve,
It returns to the suction side of the compressor 10 via the accumulator 13 in order.

(Cooling operation using heat storage (liquid refrigerant pump 2
2)) Next, a cooling operation using heat storage using the liquid refrigerant pump 22 will be described. First, when only the liquid refrigerant pump 22 is operated, the liquid refrigerant discharged from the liquid refrigerant pump 22 is supplied to the chamber via the on-off valve 28a, the liquid-side connection port 6, the liquid pipe 43, and the indoor-side pressure reducing device 31 in this order. It flows into the inner heat exchanger 32 and absorbs heat from the room air to perform cooling and evaporates itself. The vapor refrigerant flows into the intermediate heat exchanger 61 through the vapor pipe 44 and the vapor-side connection port 7, and radiates heat to the heat storage material 20b sent from the heat storage tank 20 by the heat storage material transport pump 60 to condense and liquefy. The operation returns to the liquid refrigerant pump 22 via the valve 28c.

(Heat Heat Storage Operation (Compressor 10))
The thermal storage operation using the compressor 10 will be described. First, when only the compressor 10 is operated, the vapor refrigerant compressed by the compressor 10 flows from the first port 11a of the four-way valve to the heat storage heat exchanger 20a via the fourth port 11d, Heat is dissipated to the heat storage material 20b to store warm heat, and the liquid itself condenses and liquefies. This liquid refrigerant is decompressed by the heat storage decompression device 21 to become a gas-liquid two-phase refrigerant, and further flows into the outdoor heat exchanger 12 to absorb heat from outdoor air and evaporate. The low-temperature and low-pressure vapor refrigerant returns to the compressor 10 via the third port 11c of the four-way valve, the second port 11b, and the accumulator 13 sequentially.

(Heating operation using heat storage (liquid refrigerant pump 2
2)) Next, a heating operation using heat storage using the liquid refrigerant pump 22 will be described. First, when only the liquid refrigerant pump 22 is operated, the liquid refrigerant discharged from the liquid refrigerant pump 22 flows into the intermediate heat exchanger 61 via the on-off valve 28b, absorbs heat from the heat storage material 20b, and evaporates. I do. The vapor refrigerant flows into the indoor heat exchanger 32 through the vapor-side connection port 7 and the vapor pipe 44 in order, radiates heat to indoor air to heat, and liquefies itself. This liquid refrigerant is slightly decompressed by the indoor side decompression device 31, and the liquid pipe 43, the liquid side connection port 6,
The operation returns to the liquid refrigerant pump 22 via the on-off valve 28d.

As described above, in the system according to the present embodiment, the refrigerant path is separated into a primary cycle using the compressor 10 and a secondary cycle using the liquid refrigerant pump 22, and the secondary cycle is used. Since the configuration is such that the room can be cooled or heated only by the cycle, there is an effect that the peak of the power can be cut during the daytime in summer or winter when power demand peaks.

Further, such a separated type system has an advantage that is not provided by the integrated type system as in the first to fourth embodiments. For example, in Embodiment 1,
When a natural refrigerant such as a chlorofluorocarbon-based refrigerant or a hydrocarbon-based refrigerant is used, the liquid refrigerant pump 22 wears due to a small lubricating effect, and the worn powder flows into the compressor 10 to damage the compressor 10. Phenomenon occurs.

On the other hand, in the present embodiment, since the primary refrigerant path and the secondary refrigerant path are separated, even if abrasion powder is generated in the liquid refrigerant pump 22, this is generated on the primary side. Since there is no mixing, the compressor 10 can be prevented from being damaged. Therefore, it is not necessary to provide a filter for capturing abrasion powder at the outlet of the liquid refrigerant pump 22, and a more reliable heat storage refrigeration system can be constructed.

In the case of replacing the refrigerant with an alternative refrigerant such as R22 to R407C or an HC-based natural refrigerant, in an integrated system, the lubricating oil inside the compressor 10 flows toward the indoor unit 3. Therefore, it is necessary to clean the indoor unit 3 with piping. On the other hand, in the present embodiment, since the secondary cycle does not have the compressor 10 and does not require lubricating oil, it is only necessary to replace the refrigerant, and it is possible to omit operations such as pipe cleaning accompanying the refrigerant exchange. Therefore, when replacing the refrigerant or renewing the air conditioner,
Only the outdoor unit 1 needs to be replaced with hardware, and it is possible to obtain an air conditioner having a high renewal property that does not require cleaning of the piping of the indoor unit 3.

Embodiment 6 FIG. FIG. 9 is a configuration diagram illustrating a regenerative refrigeration system according to Embodiment 6 of the present invention. In this embodiment, the bridge route is replaced with a four-way valve in the system of the fifth embodiment.
Further, a liquid reservoir is provided on the refrigerant inflow side of the liquid refrigerant pump. Configurations not particularly described are the same as those of the above-described fourth and fifth embodiments, and the same configurations are denoted by the same reference numerals.

In this system, the bridge path is replaced by a four-way valve 29. Therefore, Embodiment 3
Of the four-way valve 29 in the fourth embodiment.
As in the case of substituting the above, there is an effect that an inexpensive and simple refrigerant path configuration can be configured. Further, since the liquid storage container 52 is provided on the refrigerant inflow side of the liquid refrigerant pump 22, the liquid refrigerant can be reliably supplied to the liquid refrigerant pump 22 as in the fourth embodiment, and the cavitation in the liquid refrigerant pump 22 is reduced. It is possible to prevent the generation of the air conditioner, and it is possible to construct a more reliable thermal storage type air conditioner. In addition, the types of the operation modes, the operation conditions under each operation mode, and the like are the same as those in the fourth and fifth embodiments, and thus the description thereof is omitted.

Embodiment 7 FIG. FIG. 10 is a configuration diagram showing a regenerative refrigeration system according to Embodiment 7 of the present invention. The present system is different from the system of the sixth embodiment in that heat storage units 2A and 2B and indoor units 3A and 3B are arranged in a distributed manner, and a liquid storage container provided on the refrigerant inflow side of the liquid refrigerant pump 22 is provided. It depends on the omitted system. The configuration that is not particularly described is the same as that of the above-described sixth embodiment, and the same configuration is denoted by the same reference numeral, and the description of the configuration and operation is omitted.

The advantages of disposing the heat storage units 2A and 2B in a distributed manner will be described. This advantage is basically the same as the advantage described in the second embodiment.
That is, as in the present system, a plurality of indoor units 3
In the case where A and 3B are provided, the total heat load is larger than in the case of a single unit, so that it is necessary to increase the size of the heat storage unit 2. In particular, in this system, the primary cycle and the secondary cycle are separated from each other, and the liquid refrigerant pump 2
Since it is necessary to cover the full load of cooling and heating only by the heat storage utilization operation of No. 2, the heat storage tank 20 needs to be increased in size, and the heat storage unit 2 further increases in size.

As described above, it is not preferable to increase the size of the heat storage unit 2. Therefore, in the present system, the heat storage units 2 A,
By providing 2B, the weight load on the installation surface can be reduced, and the reliability of the entire system can be improved. In the present embodiment, two heat storage units 2
Although an example in which one indoor unit 3 and one outdoor unit 1 are connected to each of the above is shown, a plurality of indoor units 3 and a plurality of outdoor units 1 may be installed in each heat storage unit 2.

Embodiment 8 FIG. FIG. 11 is a configuration diagram of a regenerative refrigeration system according to Embodiment 8 of the present invention. This system roughly relates to a regenerative refrigeration cycle in which a plurality of units are provided to constitute a plurality of regenerative refrigeration cycle systems. The configuration that is not particularly described is the same as that of the above-described fifth embodiment, and the same configuration is denoted by the same reference numeral, and description of the configuration and operation is omitted.

As shown in FIG. 11, the system according to the present embodiment includes a plurality of outdoor units 1A,
1B, heat storage units 2A and 2B, and indoor unit groups 3A and 3B. Each of the indoor unit groups 3A and 3B includes a plurality of indoor units 3 respectively.
Is provided. An inter-system heat exchange unit 9 is arranged between the heat storage units 2A and 2B and the indoor unit groups 3A and 3B, and can exchange heat via the inter-system heat exchange unit 9. .

In such a configuration, the outdoor unit 1
A, the heat storage unit 2A, and the indoor unit group 3A constitute a first heat storage refrigeration cycle system, and the outdoor unit 1B, the heat storage unit 2B, and the indoor unit group 3B form a second heat storage refrigeration cycle system. Is configured. In the present system, since the first heat storage refrigeration cycle system and the second heat storage refrigeration cycle system are provided as described above, the outdoor unit 1A or the heat storage unit 2A is located at a position away from the outdoor unit 1B or the heat storage unit 2B. Can be installed in For example, the outdoor unit 1A and the first heat storage unit 2A can be installed on the upper floor of the building, and the outdoor unit 1B and the second heat storage unit 2B can be installed on the lower floor of the building.

Next, the configuration of the inter-system heat exchange unit 9 will be described. The inter-system heat exchange unit 9 is provided with two intermediate heat exchangers 61. That is, in the systems shown in FIGS. 8 to 10 in the fifth to seventh embodiments, the intermediate heat exchanger 61 is disposed in the heat storage unit 2, but in the present system, the intermediate heat exchanger An exchange 61 is arranged. The heat storage material inlet 62 of the intermediate heat exchanger 61 is connected to both the heat storage units 2A and 2B via the heat storage material transport pump 60 and the on-off valves 63A and 63B. The heat storage material outlet 64 of the intermediate heat exchanger 61 is connected to the on-off valves 65A, 65A.
5B, it is connected to both heat storage units 2A, 2B.

FIG. 11 shows an example in which one heat storage material transport pump 60 is installed between the heat storage material merging portion 66 and the heat storage material branching portion 67 sent from the heat storage units 2A and 2B. However, as for the position, the heat storage material merging portion 66 and the on-off valves 63A and 63B and the heat storage material branching portion 6
7 may be arranged between the heat storage material inlets 62 of the two intermediate heat exchangers 61, and not limited to one, and a plurality of heat storage materials may be arranged in parallel or in series.

[0125] The driving operation of the present system configured as described above will be described. However, the setting of the basic operation mode and the operation conditions, and the operation of the heat storage utilizing cooling operation and the heating operation using the liquid refrigerant pump 22 are the same as those of the fifth to seventh embodiments, and therefore the description thereof is omitted. In the following, a description will be given of an operation operation when the cooling load on the upper floor of the building is larger than the cooling load on the lower floor at the peak of the cooling load in the daytime in summer. It is assumed that the outdoor unit 1A and the first heat storage unit 2A are installed on the upper floor of the building, and the outdoor unit 1B and the second heat storage unit 2B are installed on the lower floor of the building.

Generally, a first heat storage refrigeration cycle system,
When the second heat storage refrigeration cycle systems are provided completely independently of each other (in the present embodiment, the on-off valve 63B,
65B is closed), since the cooling load is higher on the upper floor, the heat storage material 20b of the heat storage unit 2A
Is completely melted, the temperature becomes relatively high, and the amount of heat exchange in the intermediate heat exchanger 61 is reduced, so that a required cooling capacity cannot be obtained. However, since the cooling load is smaller on the lower floor than on the upper floor, the heat storage unit 2
The operation of the day ends with sufficient ice remaining in the heat storage tank 20 of B. That is, since the heat storage amounts of the heat storage tanks 20 of the two heat storage refrigeration cycle systems are mutually unequal, the operation efficiency of the entire system decreases, energy loss occurs, and the running cost increases. Results.

For this reason, in this system, the on-off valve 6
By using 3A, 63B, 65A, and 65B, the heat storage amount can be uniformly and efficiently operated between the two cycle systems. For example, under the situation where the cooling load is higher on the upper floor as described above, the on-off valves 63A, 65
By setting A to the closed state and the on-off valves 63B and 65B to the open state, the insufficient heat of the first heat storage unit 2 can be obtained from the heat storage tank 20 of the second heat storage unit 2. That is, in such a valve state, the heat storage material 20b of the heat storage unit 2B sucked by the heat storage material transport pump 60 flows into the intermediate heat exchanger 61 via the on-off valve 63B, and the indoor heat exchanger 61 It exchanges heat with the refrigerant circulating in the unit group 3A, and is returned to the heat storage tank 20 of the heat storage unit 2B again via the on-off valve 65B.

On the contrary, if the cooling load is higher on the lower floor, the on-off valves 63B and 65B are set to the closed state and the on-off valves 63A and 65A are set to the open state, contrary to the above assumption. Insufficient cold heat in the heat storage unit 2B can be obtained from the heat storage tank 20 of the heat storage unit 2A. Naturally, the relationship between the arrangement position of the indoor unit 3 and the like of the first heat storage refrigeration cycle system and the arrangement position of the indoor unit 3 and the like of the second heat storage refrigeration cycle system depends on the upper floor and the lower floor. It is not limited, and can be arranged at any two positions where the cooling loads may be different from each other.

As described above, in the present embodiment, at least one of the heat storage materials 2 of the heat storage units 2A and 2B is used.
0b is supplied to the intermediate heat exchanger 61, and the intermediate heat exchanger 61 has a structure capable of exchanging heat with the indoor unit groups 3A and 3B, so that the operation efficiency of the entire system can be improved and the The heat storage material 20b of the heat storage tank 20 can be operated effectively.

The present invention has been described so far, but the present invention may be embodied in other different forms within the scope of the technical idea described in the claims. Hereinafter, such other forms will be further described.

First, the heat storage material 20b is not limited to water (ice), and any other fluid medium can be used. For example, the heat storage material 20b may be an aqueous solution in which a solute such as ethylene glycol, propylene glycol, sorbitol, or calcium chloride is dissolved in water. In this case, since the freezing temperature is lower than that in the case of fresh water in accordance with the concentration of the solute, the evaporation temperature during the heat storage operation is further lower than that in the case of fresh water. Therefore, when the evaporation temperature of the refrigerant in the indoor heat exchanger 32 is required to be lower than that for air conditioning, for example, when the indoor unit 3 is a showcase or a freezer, more cooling heat is required. Can be stored, and a regenerative refrigeration system having a wide application range can be constructed.

In the above embodiment, one or two indoor heat exchangers 32 are provided in one refrigerant passage. However, three or more indoor heat exchangers may be provided. In addition, the outdoor unit 1, the heat storage unit 2, and the indoor unit 3
Can be provided in an arbitrary number and connected at an arbitrary ratio. Further, in the eighth embodiment, the case where two heat storage refrigeration cycle systems are provided is shown. However, three or more heat storage refrigeration cycle systems may be provided. In this case, the heat storage material 20b in each refrigerant path is also provided. By performing heat exchange by one or more intermediate heat exchangers 61, heat storage in each cycle system can be effectively operated.

Furthermore, in the first to eighth embodiments, the example in which the outdoor heat exchanger 12 radiates heat to the outdoor air has been described. However, the present invention is not limited to this, and cooling water, river water, seawater,
It may be configured to radiate heat to any environment other than outdoor air, such as sewage, soil, or unused indoor air. Similarly, the example in which the indoor heat exchanger 32 dissipates heat to the indoor air has been described. However, the present invention is not limited to this example. May be configured to radiate heat.

In the first to eighth embodiments,
Although the liquid refrigerant pump 22 is provided as a refrigerant circulation drive source, the liquid refrigerant pump 22 may be omitted in an installation environment where the refrigerant can be naturally circulated. For example, when there is a height difference required for the refrigerant to circulate naturally between the heat storage unit 2 and the indoor unit 3, the liquid refrigerant pump 22 can be omitted assuming that the refrigerant circulates naturally.

Alternatively, either the circulation by the liquid refrigerant pump 22 or the natural circulation may be selectable. For example, a bypass pipe that connects the vicinity of the liquid refrigerant pump 22, for example, a position near the inlet side and a position near the outlet side of the liquid refrigerant pump 22 is provided, and according to the installation conditions of the heat storage unit 2 and the indoor unit 3, The operation of the liquid refrigerant pump 22 and the natural circulation operation may be selectable. When the natural circulation is used, the power consumption of the regenerative refrigeration system can be further reduced.

[0136]

As described above in detail, the regenerative refrigeration system according to the present invention connects at least a compressor, an outdoor heat exchanger, a use side decompression device, and a use side heat exchanger sequentially with piping. A regenerative refrigeration system including a heat exchanger for heat storage, comprising a first on-off valve and a liquid refrigerant transfer between a liquid-side connection port of an outdoor heat exchanger and a liquid-side connection port of a use-side heat exchanger. Means, and one end of the heat storage heat exchanger is connected via a second on-off valve between the steam side of the use side heat exchanger and the suction side of the compressor. The other end of the heat exchanger, the liquid-side connection port of the outdoor heat exchanger, and the first on-off valve are connected via a heat storage decompression device. It is possible to perform cold heat storage operation, etc., simply by providing liquid refrigerant transport means and a small number of on-off valves for air conditioners. Possible to the traditional can build regenerative refrigeration system with a simple structure in comparison with, it is the power of the peak cut the time zone of the summer daytime will peak power demand.

A regenerative refrigeration system according to the next invention is characterized in that the heat storage refrigeration system is provided between one end of the heat storage heat exchanger and a second on-off valve.
By connecting the liquid refrigerant transfer means and the liquid side connection port of the use side heat exchanger via a third on-off valve, the cooling operation and the cold heat storage operation by the compressor, and the heat storage utilization by the liquid refrigerant transfer means In addition to the cooling operation, it is possible to perform a cooling operation utilizing heat storage by the compressor.

[0138] The regenerative refrigeration system according to the next invention comprises a discharge side of the compressor, a steam side of the outdoor heat exchanger, and
A cooling steam refrigerant flow path for communicating the steam side of the use side heat exchanger with the suction side of the compressor, the steam side of the compressor and the steam side of the use side heat exchanger, and the steam of the outdoor heat exchanger. The steam refrigerant flow path for heating and the steam refrigerant flow path for communicating the suction side of the compressor and the suction side of the compressor are each provided with a vapor refrigerant flow path switching means for switching between them, whereby the circulation direction of the vapor refrigerant can be switched, Further, a heating operation by the compressor can be performed, and a system for both cooling and heating can be constructed with a simple configuration.

The regenerative refrigeration system according to the next invention comprises a liquid-side connection port of the outdoor heat exchanger, a suction port of the liquid refrigerant transfer means, a discharge port of the liquid refrigerant transfer means, and a liquid side of the use-side heat exchanger. A cooling liquid refrigerant flow path communicating the connection ports with each other, a liquid side connection port of the use side heat exchanger and a suction port of the liquid refrigerant transfer means, and a discharge port of the liquid refrigerant transfer means and the liquid of the outdoor heat exchanger. The liquid refrigerant flow path for heating, which communicates with the side connection ports, and the liquid refrigerant flow switching means for switching between the liquid refrigerant flow paths can be switched, so that the circulation direction of the liquid refrigerant can be switched. Heating using heat storage by the liquid refrigerant conveying means becomes possible. For this reason, the peak cut of cooling and heating can be performed by one liquid refrigerant conveying means, and an inexpensive and simple refrigerant path can be configured.

A regenerative refrigeration system according to the next invention comprises a primary cycle comprising at least a compressor, an outdoor heat exchanger, a decompression device for heat storage, and a heat exchanger for heat storage sequentially connected by piping. At least liquid refrigerant conveying means,
A use side decompression device, and a use side heat exchanger are sequentially connected by piping, and a secondary side cycle is provided. Between these primary side cycles and the secondary side cycle, heat storage of the primary side cycle is provided. By providing an intermediate heat exchanger for performing heat exchange between the heat storage material of the heat exchanger for use and the refrigerant of the secondary cycle, the heat storage utilizing cooling operation by the liquid refrigerant conveying means can be performed with a simple configuration. Since it becomes possible, the peak of power can be cut in the daytime in summer or winter when power demand peaks. In particular, since the primary side cycle and the secondary side cycle are separated, cooling and heating can be performed only by the secondary side cycle, and cooling and heating under a small load can be performed efficiently.

In the regenerative refrigeration system according to the next invention, in the primary cycle, the discharge side of the compressor and the steam side of the outdoor heat exchanger, and one end of the heat storage heat exchanger and the suction side of the compressor are provided. A cooling vapor refrigerant flow path for communicating the
A vapor refrigerant for mutually switching a discharge side of the compressor and one end of the heat storage heat exchanger, and a heating vapor refrigerant flow path for communicating the vapor side of the outdoor heat exchanger and the suction side of the compressor, respectively. With the provision of the flow path switching means, the circulation direction of the vapor refrigerant can be switched, and the heating operation by the compressor can be further performed, so that a system for both cooling and heating can be constructed with a simple configuration. it can.

In the regenerative refrigeration system according to the next invention, in the secondary cycle, the intermediate heat exchanger and the suction port of the liquid refrigerant transfer means, and the discharge port of the liquid refrigerant transfer means and the use side heat exchanger are connected. A cooling liquid refrigerant flow path that communicates with the liquid side connection port, a liquid side connection port of the use side heat exchanger and a suction port of the liquid refrigerant conveyance means, and a discharge port of the liquid refrigerant conveyance means and the intermediate heat exchanger. And a liquid refrigerant flow path switching means for mutually switching the liquid refrigerant flow path for heating, which allows the liquid refrigerant to communicate with the liquid refrigerant flow path, so that the circulation direction of the liquid refrigerant can be switched. Heat storage utilizing heating by means can be achieved. For this reason, the peak cut of cooling and heating can be performed by one liquid refrigerant conveying means, and an inexpensive and simple refrigerant path can be configured.

In the regenerative refrigeration system according to the next invention, the liquid refrigerant flow switching means includes a bridge for switching between the cooling liquid refrigerant flow path and the heating liquid refrigerant flow path by opening and closing four on-off valves. 4
The circulation direction of the liquid refrigerant can be switched by a simple configuration in which only two on-off valves are provided.

In the regenerative refrigeration system according to the next invention, since the liquid refrigerant flow switching means is a four-way valve, the circulation direction of the liquid refrigerant can be switched without using an on-off valve, and a bridge path is used. The system configuration can be performed with a simpler configuration than in the case.

A regenerative refrigeration system according to the next invention uses at least a compressor and an outdoor heat exchanger as an outdoor unit, at least a heat storage pressure reducing device, a heat storage heat exchanger, and a liquid storage medium as a heat storage unit. The side pressure reducing device and the use side heat exchanger are configured as use side units, respectively, and these outdoor units, heat storage units,
Alternatively, by providing at least one of the plurality of use-side units, each unit can be downsized, the installation space for each floor in the building is reduced, and the weight for the building floor surface is reduced. The load can be reduced. Further, the influence range at the time of failure or the like can be narrowed, and a highly reliable regenerative refrigeration system can be constructed.

A regenerative refrigeration system according to the next invention uses at least a compressor and an outdoor heat exchanger as an outdoor unit, at least a heat storage decompression device, a heat storage heat exchanger, and a heat storage unit as a liquid refrigerant transport means. The side pressure reducing device and the use side heat exchanger are configured as use side units, respectively, and these outdoor units, heat storage units,
And, provided with a plurality of regenerative refrigeration cycle systems having a use-side unit, via the intermediate heat exchanger, at least one of the heat storage material of the heat storage heat exchanger of the regenerative refrigeration cycle system, By enabling heat exchange with the refrigerant of the utilization side unit of one other regenerative refrigeration cycle system, it is possible to effectively use heat storage between a plurality of regenerative refrigeration cycle systems, Operation efficiency can be improved as a whole.

In the regenerative refrigeration system according to the next invention, an accumulator is provided in front of the suction port of the compressor.
When switching from the predetermined operation using the compressor to the predetermined operation using the liquid refrigerant conveying means, the opening degree of the heat storage decompression device or the use side decompression device can be adjusted so as to recover the excess refrigerant in the accumulator. Thereby, the liquid refrigerant is reliably supplied to the liquid refrigerant transport unit during the operation using the liquid refrigerant transport unit, and a stable operation without causing the shortage of the refrigerant amount can be performed.

In the regenerative refrigeration system according to the next invention, the provision of the liquid storage container on the refrigerant inflow side of the liquid refrigerant transfer means allows the liquid refrigerant transfer to be performed even when the amount of refrigerant is insufficient shortly. The liquid refrigerant can be reliably supplied to the means, and a more stable operation can be performed.

The regenerative refrigeration system according to the next invention is characterized in that the flow rate of the liquid refrigerant by the liquid refrigerant transport means is controlled based on the degree of supercooling of the liquid refrigerant near the refrigerant inflow side of the liquid refrigerant transport means. In the case where cavitation occurs, the refrigerant conveying means can be controlled to avoid the cavitation, and a more stable operation can be performed.

The regenerative refrigeration system according to the next invention comprises a temperature detecting means for detecting the temperature of the liquid refrigerant near the refrigerant inflow side of the liquid refrigerant conveying means, and a pressure of the liquid refrigerant near the refrigerant inflow side. Pressure detecting means, and a temperature detected by these temperature detecting means, based on the pressure detected by the pressure detecting means, by comprising a calculating means for calculating the degree of supercooling of the liquid refrigerant, The degree of supercooling of the liquid refrigerant can be easily calculated, and cavitation in the refrigerant conveying means can be quickly and easily avoided.

The regenerative refrigeration system according to the next invention is provided with a bypass pipe for bypassing the liquid refrigerant pump for natural circulation of the refrigerant, so that it can be adapted to the installation conditions of the heat storage tank and the use side heat exchanger. Therefore, it is possible to switch between the operation by the liquid refrigerant transfer means and the natural refrigerant circulation operation, and the power consumption of the regenerative refrigeration system can be further reduced.

In the regenerative refrigeration system according to the next invention, the heat storage material of the heat storage heat exchanger is water or an aqueous solution in which an antifreeze solution is mixed with water, so that heat is stored at a temperature corresponding to the use temperature. Therefore, a regenerative refrigeration system having a wide range of application can be constructed.

[Brief description of the drawings]

FIG. 1 is a diagram showing a configuration of a regenerative refrigeration system according to Embodiment 1 of the present invention.

FIG. 2 is a schematic diagram showing a configuration of a gear pump used in the system shown in FIG.

3 is a diagram showing a relationship between each operation mode of the system shown in FIG. 1 and an open / close state of an on-off valve and the like.

FIG. 4 is a diagram showing a configuration of a heat storage tank used in the system shown in FIG.

FIG. 5 is a diagram illustrating a configuration of a regenerative refrigeration system according to Embodiment 2 of the present invention.

FIG. 6 is a diagram illustrating a configuration of a regenerative refrigeration system according to Embodiment 3 of the present invention.

FIG. 7 is a diagram showing a configuration of a regenerative refrigeration system according to Embodiment 4 of the present invention.

FIG. 8 is a diagram showing a configuration of a regenerative refrigeration system according to Embodiment 5 of the present invention.

FIG. 9 is a diagram showing a configuration of a regenerative refrigeration system according to Embodiment 6 of the present invention.

FIG. 10 is a diagram showing a configuration of a regenerative refrigeration system according to Embodiment 7 of the present invention.

FIG. 11 is a diagram showing a configuration of a regenerative refrigeration system according to Embodiment 8 of the present invention.

FIG. 12 is a diagram showing a configuration of a conventional heat storage refrigeration system.

[Explanation of symbols]

1 outdoor unit, 2 heat storage unit, 3 indoor unit, 4, 7 vapor side connection port, 5, 6 liquid side connection port, 8a
８8d junction, 9 heat exchange units between systems, 10 compressor, 11, 29 four-way valve, 12 outdoor heat exchanger, 13
Accumulator, 14 outdoor blower, 20 heat storage tank, 20a heat exchanger for heat storage, 20b heat storage material, 20c
Piping, 20d bubble outlet, 20e bubble, 20f
Ice, 21 heat storage decompression device, 22 liquid refrigerant pump, 22
a casing, 22b, 22c gears, 23, 26, 2
7, 28a to 28d, 50, 51, 63A, 63B, 6
5A, 65B opening / closing valve, 24 1st heat storage side temperature detector, 25 2nd heat storage side temperature detector, 28 bridge path, 31 indoor pressure reducing device, 32 indoor heat exchanger, 3
3 indoor blower, 40, 43 liquid piping, 41, 44 steam piping, 52 liquid storage container, 53 pressure detector, 54
Third heat storage side temperature detector, 55 arithmetic unit, 60 heat storage material transport pump, 61 intermediate heat exchanger, 62 heat storage material inlet, 64 heat storage material outlet, 66 heat storage material merging unit, 67
Thermal storage material branch.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Hiroyu Shiba 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Inside Mitsubishi Electric Co., Ltd. (72) Moriya Miyamoto 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsubishi Electric Corporation

Claims (17)

[Claims] 1. A regenerative refrigeration system comprising at least a compressor, an outdoor heat exchanger, a use-side decompression device, and a use-side heat exchanger sequentially connected by piping, and comprising a heat storage heat exchanger. The liquid-side connection port of the heat exchanger and the liquid-side connection port of the use-side heat exchanger are sequentially connected via the first on-off valve and the liquid refrigerant conveying means, and one end of the heat storage heat exchanger, The steam side of the use side heat exchanger and the suction side of the compressor are connected via a second on-off valve, and the other end of the heat storage heat exchanger and the liquid side connection port of the outdoor heat exchanger are connected to each other. A regenerative refrigeration system, wherein the refrigerating system is connected to a first on-off valve via a depressurizing device for heat storage. 2. A third on-off valve connects between one end of the heat storage heat exchanger and the second on-off valve and between the liquid refrigerant conveying means and the liquid-side connection port of the use-side heat exchanger. The regenerative refrigeration system according to claim 1, wherein the refrigeration system is connected. 3. A cooling vapor refrigerant flow path for communicating the discharge side of the compressor with the vapor side of the outdoor heat exchanger, and the vapor side of the use side heat exchanger and the suction side of the compressor, respectively. A steam refrigerant flow for switching between a discharge side of the heat exchanger and a steam side of the use side heat exchanger, and a heating steam refrigerant flow path for communicating the steam side of the outdoor heat exchanger with the suction side of the compressor, respectively. The regenerative refrigeration system according to claim 1 or 2, further comprising a road switching unit. 4. A cooling device for connecting the liquid-side connection port of the outdoor heat exchanger with the suction port of the liquid refrigerant transfer means, and the discharge port of the liquid refrigerant transfer means with the liquid-side connection port of the use-side heat exchanger. Heating for communicating the liquid refrigerant flow path, the liquid side connection port of the use side heat exchanger and the suction port of the liquid refrigerant transfer means, and the discharge port of the liquid refrigerant transfer means and the liquid side connection port of the outdoor heat exchanger, respectively. The regenerative refrigeration system according to any one of claims 1 to 3, further comprising a liquid refrigerant flow path switching means for switching between the liquid refrigerant flow path for use and the liquid refrigerant flow path. 5. A primary cycle comprising at least a compressor, an outdoor heat exchanger, a heat storage decompression device, and a heat storage heat exchanger sequentially connected by piping, at least a liquid refrigerant conveying means, and a use side decompression. Apparatus, and a secondary cycle configured by sequentially connecting the use-side heat exchangers with piping,
Between these primary cycle and secondary cycle, an intermediate heat exchanger for performing heat exchange between the heat storage material of the heat storage heat exchanger of the primary cycle and the refrigerant of the secondary cycle. A regenerative refrigeration system comprising: 6. A cooling-vapor refrigerant flow that communicates a discharge side of the compressor and a vapor side of the outdoor heat exchanger, and one end of the heat storage heat exchanger and a suction side of the compressor, respectively, in the primary cycle. Path, the discharge side of the compressor and one end of the heat storage heat exchanger, and the heating steam refrigerant flow path that communicates the steam side of the outdoor heat exchanger and the suction side of the compressor, respectively, for switching between them. The regenerative refrigeration system according to claim 5, further comprising a steam refrigerant flow switching means. 7. In the secondary side cycle, the intermediate heat exchanger and the suction port of the liquid refrigerant transfer means, and the discharge port of the liquid refrigerant transfer means and the liquid side connection port of the use side heat exchanger are communicated with each other. A liquid refrigerant channel for cooling, a liquid refrigerant connection port of the use side heat exchanger, a suction port of the liquid refrigerant transporting means, and a heating liquid refrigerant for communicating the discharge port of the liquid refrigerant transporting means with the intermediate heat exchanger, respectively. The regenerative refrigeration system according to claim 5 or 6, further comprising a liquid refrigerant flow path switching means for switching between the flow path and the liquid refrigerant. 8. The liquid refrigerant flow path switching means is a bridge path that switches between a cooling liquid refrigerant flow path and a heating liquid refrigerant flow path by opening and closing four on-off valves. Item 8. A regenerative refrigeration system according to item 4 or 7. 9. The regenerative refrigeration system according to claim 4, wherein the liquid refrigerant flow switching means is a four-way valve. 10. At least a compressor and an outdoor heat exchanger as an outdoor unit, at least a heat storage decompression device, a heat storage heat exchanger, and a liquid refrigerant transport means as a heat storage unit, at least a utilization side decompression device and a utilization side heat exchanger. Are respectively configured as use-side units, and a plurality of at least one of the outdoor unit, the heat storage unit, and the use-side unit are provided.
10. A regenerative refrigeration system according to any one of claims 9 to 9. 11. At least a compressor and an outdoor heat exchanger are an outdoor unit, at least a heat storage decompression device, a heat storage heat exchanger, and a liquid refrigerant transport means are a heat storage unit, at least a use side decompression device and a use side heat exchanger. Each of these is configured as a use side unit, and these outdoor units, heat storage units, and a plurality of heat storage refrigeration cycle systems including the use side units are provided, and at least one of the heat storage refrigeration systems is provided via the intermediate heat exchanger. The heat exchange material between the heat storage material of the heat exchanger for heat storage of the cycle system and the refrigerant of the utilization side unit of at least one of the other heat storage refrigeration cycle systems has been enabled. 10. The regenerative refrigeration system according to any one of 9 above. 12. An accumulator is provided at a stage preceding the suction port of the compressor, and when the operation is switched from the predetermined operation using the compressor to the predetermined operation using the liquid refrigerant conveying means, the heat storage is performed so as to collect the excess refrigerant in the accumulator. The regenerative refrigeration system according to any one of claims 1 to 11, wherein an opening degree of the pressure reducing device for use or the use-side pressure reducing device is adjustable. 13. The regenerative refrigeration system according to claim 1, wherein a liquid reservoir is provided on the refrigerant inflow side of the liquid refrigerant conveying means. 14. The method according to claim 1, wherein the flow rate of the liquid refrigerant by the liquid refrigerant conveying means is controlled based on the degree of supercooling of the liquid refrigerant in the vicinity of the refrigerant inflow side of the liquid refrigerant conveying means. A regenerative refrigeration system according to any one of the preceding claims. 15. A temperature detecting means for detecting the temperature of the liquid refrigerant near the refrigerant inflow side of the liquid refrigerant conveying means, a pressure detecting means for detecting the pressure of the liquid refrigerant near the refrigerant inflow side, and these temperature detecting means. The temperature detected by the means;
The regenerative refrigeration system according to claim 14, further comprising: a calculating unit that calculates a degree of supercooling of the liquid refrigerant based on the pressure detected by the pressure detecting unit. 16. The regenerative refrigeration system according to claim 1, further comprising a bypass pipe for bypassing the liquid refrigerant pump for performing natural circulation of the refrigerant. 17. The regenerative refrigeration according to claim 1, wherein the heat storage material of the heat storage heat exchanger is water or an aqueous solution obtained by mixing an antifreeze with water. system.