JPH11316060A - Refrigerating/air conditioning apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To uniformly store heat in a heat storage tank, and effectively store heat even when a heat transfer medium is altered by preventing deterioration of heat storage efficiency due to a non-azeotropic mixture refrigerant in a heat storage type refrigerating/air conditioning apparatus. SOLUTION: Cold heat or hot heat produced in a heat source apparatus is stored in a heat storage material in a heat storage tank 10 through a heat storage heat exchanger 11, and the stored cold heat or hot heat is supplied to an indoor heat exchanger 5 being a load apparatus. A non-azeotropic mixture refrigerant is used as a heat transfer medium in the heat source apparatus to positively or negatively change over a flow direction of a refrigerant in the heat storage heat exchanger 11. The changeover of the positive or negative flow direction of the refrigerant is performed under temperature of the refrigerant, pressure of the refrigerant, a heat storage state of the heat storage material, and a predetermined time interval all detected by a temperature detector 25. Further, the heat storage heat exchanger 11 is constructed such that it has such pressure loss as a temperature change width of the refrigerant in the heat storage heat exchanger 11 becoming a predetermined value or less.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerating air conditioner having a heat storage tank for storing cold or hot heat, and more particularly to a refrigerating air conditioner provided in a heat storage tank when a non-azeotropic mixed refrigerant is used as a heat transfer medium. And improvement of the heat storage heat exchanger.

[0002]

2. Description of the Related Art Conventionally, as a means for reducing power demand at the time of a cooling load peak and expanding power demand at an off-peak time, cold energy is stored in a heat storage tank at the time of a cooling load off-peak, and the cold heat is used for cooling operation at a peak time. The development of regenerative refrigeration and air-conditioning systems for use in air conditioning is in progress.

FIG. 30 shows, for example, Japanese Patent Publication No. 8-250824.
It is a refrigerant circuit diagram which shows the conventional refrigerating air-conditioner shown in No. 0 publication. In the figure, 1 is a compressor, 2 is a four-way valve for switching the flow of refrigerant during cooling and heating, 3 is an outdoor heat exchanger,
Reference numeral 4 denotes a first expansion valve, and reference numeral 5 denotes an indoor heat exchanger, which are connected by piping to form a refrigeration cycle. Reference numeral 11 denotes a heat storage heat exchanger installed in the heat storage tank 10, and its inlet side pipe is connected to a pipe between the outdoor heat exchanger 3 and the first expansion valve 4 via a second expansion valve 20. I have. The outlet pipe of the heat storage heat exchanger 11 is connected to the pipe between the indoor heat exchanger 5 and the four-way valve 2 by a first solenoid valve 21, and is connected to the first expansion valve 4 by a second solenoid valve 22. It is connected to a pipe between the outdoor heat exchangers 3. The first electromagnetic valve 21 and the second electromagnetic valve 22 are configured so that the refrigerant circuit for the heat storage operation and the cooling operation using the heat storage can be switched. Also, a third pipe is provided between the outdoor heat exchanger 3 and the first expansion valve 4.
An electromagnetic valve 23 is provided. Further, Freon R22, which is a single refrigerant, is sealed in the refrigeration air conditioner.

FIG. 31 is a diagram showing in detail the configuration of the heat storage tank 10 relating to the heat storage type refrigerating and air-conditioning apparatus shown in FIG. 30. FIG. 31 (a) is a top view, and FIG. It is. The heat storage heat exchanger 11 is composed of heat transfer tubes meandering in the vertical direction as shown in FIG. 31, and a plurality of, for example, four heat transfer tubes are connected in parallel in order to reduce pressure loss during the heat storage operation. In addition, a smooth tube is used as a heat transfer tube. The meandering pitches of the heat transfer tubes are substantially equal.
Further, a distributor 12 for distributing the refrigerant to the plurality of heat transfer tubes is provided at an inlet of the heat storage heat exchanger 11, and a header 13 for joining the refrigerant from the plurality of heat transfer tubes is provided at an outlet. . The inside of the heat storage tank 10 is filled with water, and during the heat storage operation, the heat storage heat exchanger 1
In step 1, the water is cooled and iced, and ice is deposited on the surface of the heat transfer tube to store cold heat in the heat storage tank 10.

Next, the operation of the conventional refrigeration and air-conditioning apparatus having the above-described configuration during the heat storage operation and the heat storage cooling operation will be described. During the heat storage operation, the first solenoid valve 21 is opened, the second solenoid valve 22 is closed, and the third solenoid valve 23 is closed.
Further, the second expansion valve 20 is controlled to have an appropriate opening. As shown by solid arrows in FIG. 30, the flow of the refrigerant during the heat storage operation is as follows. 2 The heat storage heat exchanger 1 is decompressed to a low pressure by the expansion valve 20
Flow into 1. The refrigerant flowing into the heat storage heat exchanger 11 evaporates by removing heat from the water in the heat storage tank 10. At this time, since the heat storage heat exchanger 11 is constituted by a heat transfer tube in which a plurality of smooth tubes are connected in parallel, the pressure loss during evaporation is very small, and the evaporation temperature is substantially constant. Therefore, ice adheres to the surface of the heat transfer tube of the heat storage heat exchanger 11 with a uniform thickness.
The refrigerant evaporated in the heat storage heat exchanger 11 returns to the compressor 1 through the first solenoid valve 21 and the four-way valve 2.

[0006] During the cooling operation using heat storage, the first solenoid valve 21 is closed, the second solenoid valve 22 is opened, and the third solenoid valve 23 is closed.
The flow of the refrigerant at this time is as shown by the dashed arrow in FIG. 30, and the high-temperature and high-pressure refrigerant vapor discharged from the compressor 1 is condensed and liquefied in the outdoor heat exchanger 3 through the four-way valve 2 and the second expansion. Valve 20
Through the heat storage heat exchanger 11. During this operation, the opening degree of the second expansion valve 20 is fully opened. The high-pressure liquid refrigerant that has flowed into the heat storage heat exchanger 11 is further cooled by ice in the heat storage tank 10 and flows out with an increased degree of supercooling. The liquid refrigerant having an increased degree of supercooling is reduced to a low pressure by the first expansion valve 4 through the second solenoid valve 22, flows into the indoor heat exchanger 5 and evaporates, passes through the four-way valve 2, and evaporates. Return to

[0007] During the heating operation, the four-way valve 2 is switched, the first solenoid valve 21 and the second solenoid valve 22 are closed, and the third solenoid valve 23 is opened. Then, a refrigeration cycle is configured without using the heat storage tank 10.

[0008]

In the above-mentioned conventional refrigeration and air-conditioning apparatus, since a single refrigerant such as Freon R22, which does not change in temperature during evaporation, is used as the refrigerant, a plurality of heat storage heat exchangers 11 are used. By reducing the pressure loss by configuring the heat transfer tubes connected in parallel with the smoothing tubes, it is possible to obtain a substantially constant evaporation temperature during the heat storage operation. As a result, the surface of the heat transfer tubes of the heat storage heat exchanger 11 Ice adheres and is generated with a uniform thickness, and efficient heat storage operation becomes possible.

However, in recent years, awareness of protecting the global environment has been increasing, and it is desired to use a refrigerant having a high ozone depletion coefficient and a low ozone depletion coefficient for Freon R22. Thus, for example, Freon R407C has an ozone depletion potential of zero, but its properties are slightly different from a single refrigerant such as Freon R22, and Freon R32 / R125 / R13.
4a is a non-azeotropic mixed refrigerant composed of 23/25/52% by weight. If a non-azeotropic mixed refrigerant that changes in temperature during evaporation is used, the evaporation temperature in the heat storage heat exchanger during heat storage operation will not be constant, and the ice will become thicker at the heat storage heat exchanger inlet where the evaporation temperature is low, Ice is not generated at the outlet of the heat storage heat exchanger where the evaporation temperature is high. As a result, the thickness of ice generated on the surface of the heat transfer tube of the heat storage heat exchanger becomes uneven, and the efficiency during the heat storage operation is reduced, and a sufficient amount of ice is not obtained in the entire heat storage tank. there were. In addition, since the ice thickness at the inlet of the heat storage heat exchanger having the lowest evaporation temperature is the thickest, there is also a problem that the ice in this portion is fused to cause deformation or breakage of the heat transfer tube or the heat storage tank.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and uses a non-azeotropic mixed refrigerant whose temperature changes during the evaporation process as a refrigerant, and can efficiently store heat in a heat storage tank. It is intended to obtain a refrigeration and air-conditioning system with high performance. Furthermore, not only one non-azeotropic mixed refrigerant is used as the heat transfer medium, but also other non-azeotropic mixed refrigerants or azeotropic refrigerants or single refrigerants that do not change in temperature during the evaporation process can be used to configure the apparatus. It is an object of the present invention to obtain a refrigeration / air-conditioning apparatus that can efficiently store heat in a heat storage tank without changing the temperature.

[0011]

SUMMARY OF THE INVENTION A refrigerating air conditioner according to the present invention has a heat source device for generating cold or warm heat using a non-azeotropic refrigerant mixture as a heat transfer medium, a heat storage heat exchanger and a heat storage material. A refrigeration / air-conditioning apparatus comprising: a heat storage tank that stores cold or warm heat generated by the heat source device in the heat storage material via the heat storage heat exchanger; and a load device to which the cold or warm heat stored in the heat storage tank is supplied. , The flow direction of the non-azeotropic mixed refrigerant in the heat storage heat exchanger can be switched between forward and reverse.

The refrigeration and air-conditioning apparatus according to the present invention further includes a temperature detector for detecting a temperature of the non-azeotropic mixed refrigerant flowing through the heat storage heat exchanger, and the heat storage heat exchange is performed in accordance with an output value of the temperature detector. The flow direction of the non-azeotropic mixed refrigerant in the vessel is switched.

The refrigeration / air-conditioning apparatus according to the present invention further includes a pressure detector for detecting the pressure of the non-azeotropic mixed refrigerant flowing through the heat storage heat exchanger, and the heat storage heat exchange is performed in accordance with an output value of the pressure detector. The flow direction of the non-azeotropic mixed refrigerant in the vessel is switched.

The refrigeration / air-conditioning apparatus according to the present invention is configured such that the flow direction of the non-azeotropic mixed refrigerant in the heat storage heat exchanger is switched at predetermined time intervals.

Further, the refrigeration / air-conditioning apparatus according to the present invention is provided with a detector for detecting the heat storage state of the heat storage material in the heat storage tank. The flow direction of the boiling mixed refrigerant is switched.

Further, a refrigeration / air-conditioning apparatus according to the present invention has a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, and a heat storage heat exchanger and a heat storage material. The refrigerating air conditioner, comprising: a heat storage tank configured to store the generated cold or hot heat in the heat storage material via the heat storage heat exchanger; and a load device to which the cold or hot heat stored in the heat storage tank is supplied. The heat transfer characteristics at the outlet of the heat exchanger are higher than those at the inlet.

Further, in the refrigeration heat storage device according to the present invention, the heat transfer characteristic at the outlet of the heat storage heat exchanger is reduced by making the pipe diameter at the outlet of the heat storage heat exchanger smaller than the pipe diameter at the inlet. It is higher than the heat transfer characteristics of the part.

Further, in the refrigeration heat storage device according to the present invention, the non-azeotropic mixed refrigerant is branched into a plurality of flow paths at the inlet of the heat storage heat exchanger, and the number of flow paths at the outlet of the heat storage heat exchanger is reduced. By reducing the number of flow paths at the inlet, and making the total cross-sectional area of the flow path at the outlet smaller than the total cross-sectional area of the flow path at the inlet, the power transfer at the outlet of the heat storage heat exchanger is achieved. The heat characteristics are higher than the heat transfer characteristics at the inlet.

A refrigeration / air-conditioning apparatus according to the present invention includes a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, a heat storage heat exchanger and a heat storage material. The refrigerating air conditioner, comprising: a heat storage tank configured to store the generated cold or hot heat in the heat storage material via the heat storage heat exchanger; and a load device to which the cold or hot heat stored in the heat storage tank is supplied. The heat transfer tube at the inlet and the heat transfer tube at the outlet of the heat exchanger are brought into thermal contact.

A refrigeration / air-conditioning apparatus according to the present invention has a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, and a heat storage heat exchanger and a heat storage material. In a refrigeration air-conditioning apparatus comprising: a heat storage tank for storing the generated cold heat or hot heat in the heat storage material via the heat storage heat exchanger; and a load device to which the cold or hot heat stored in the heat storage tank is supplied. In the heat exchanger, a plurality of non-azeotropic mixed refrigerant flow paths are provided, and the flow paths are arranged so that the flow direction of the non-azeotropic mixed refrigerant is opposite in the adjacent flow paths.

A refrigeration / air-conditioning apparatus according to the present invention comprises a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, and a heat storage heat exchanger and a heat storage material. The refrigerating air conditioner, comprising: a heat storage tank configured to store the generated cold or hot heat in the heat storage material via the heat storage heat exchanger; and a load device to which the cold or hot heat stored in the heat storage tank is supplied. A heat exchanger is constituted by arranging a plurality of heat transfer tubes in parallel, and the heat transfer tubes are arranged so that the flow direction of the non-azeotropic mixed refrigerant is reversed in the adjacent heat transfer tubes, and At least two heat tubes are in thermal contact with each other.

A refrigeration / air-conditioning apparatus according to the present invention comprises a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, a heat storage heat exchanger and a heat storage material. The refrigerating air conditioner, comprising: a heat storage tank configured to store the generated cold or hot heat in the heat storage material via the heat storage heat exchanger; and a load device to which the cold or hot heat stored in the heat storage tank is supplied. In the heat exchanger, the heat transfer tubes are arranged in a meandering manner in the vertical or horizontal direction, and the meandering pitch at the inlet of the heat storage heat exchanger is larger than that at the outlet.

The refrigeration / air-conditioning apparatus according to the present invention includes a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, a heat storage heat exchanger and a heat storage material. The refrigerating air conditioner, comprising: a heat storage tank configured to store the generated cold or hot heat in the heat storage material via the heat storage heat exchanger; and a load device to which the cold or hot heat stored in the heat storage tank is supplied. The heat exchanger has a refrigerant pressure loss that cancels a rise in temperature of the non-azeotropic mixed refrigerant in the heat storage heat exchanger,
The temperature of the non-azeotropic mixed refrigerant in the heat storage heat exchanger is substantially constant.

A refrigeration / air-conditioning apparatus according to the present invention comprises a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, and a heat storage heat exchanger and a heat storage material. In a refrigeration air-conditioning apparatus comprising: a heat storage tank that stores the generated cold or hot heat in the heat storage material via the heat storage heat exchanger; and a load device to which the cold or hot heat stored in the heat storage tank is supplied. The heat storage heat exchanger is configured to have a refrigerant pressure loss such that a temperature change width of the azeotropic mixed refrigerant in the heat storage heat exchanger is equal to or less than a predetermined value.

A refrigeration / air-conditioning apparatus according to the present invention has a heat source device for generating cold or hot heat using a heat transfer medium, and has a heat storage heat exchanger and a heat storage material, and cools or heats generated by the heat source device. In a refrigeration / air-conditioning apparatus including a heat storage tank that stores heat in the heat storage material via the heat storage heat exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank, a non-azeotropic heat transfer medium is used as the heat transfer medium. When the mixed refrigerant is used, and when the single refrigerant or the azeotropic refrigerant or the non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant is used, the heat transfer in the heat storage heat exchanger is performed. The heat storage heat exchanger is configured to have a refrigerant pressure loss such that a temperature change width of the medium is equal to or less than a predetermined value.

Further, in the refrigeration / air-conditioning apparatus according to the present invention, the predetermined value when the temperature change width of the heat transfer medium in the heat heat exchanger is set to a predetermined value or less is set to 3.5 ° C. It is characterized by the following.

A refrigeration / air-conditioning apparatus according to the present invention comprises a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, and a heat storage heat exchanger and a heat storage material. In a refrigeration air-conditioning apparatus comprising: a heat storage tank for storing the generated cold heat or hot heat in the heat storage material via the heat storage heat exchanger; and a load device to which the cold or hot heat stored in the heat storage tank is supplied. The temperature difference between the temperature of the non-azeotropic mixed refrigerant at the inlet of the heat exchanger and the temperature of the heat storage material is regarded as the temperature difference at the inlet, and the temperature of the non-azeotropic mixed refrigerant at the outlet of the heat storage heat exchanger. The heat storage heat exchanger is configured to have a refrigerant pressure loss such that a temperature difference between the temperature of the heat storage material and an outlet temperature difference is a ratio of the inlet temperature difference and the outlet temperature difference within a predetermined range. It was done.

The refrigeration / air-conditioning apparatus according to the present invention further comprises a heat source device for generating cold or warm heat using a heat transfer medium;
A heat storage tank that has a heat storage heat exchanger and a heat storage material and stores the cold or hot heat generated by the heat source device in the heat storage material via the heat storage heat exchanger; and the cold or hot heat stored in the heat storage tank is supplied. And a non-azeotropic mixed refrigerant different from a single refrigerant or an azeotropic refrigerant or the non-azeotropic mixed refrigerant when a non-azeotropic mixed refrigerant is used as the heat transfer medium. In any case, the temperature difference between the temperature of the heat transfer medium at the inlet of the heat storage heat exchanger and the temperature of the heat storage material is defined as the temperature difference at the inlet, and at the outlet of the heat storage heat exchanger. Outlet temperature difference between the temperature of the heat transfer medium and the temperature of the heat storage material,
The heat storage heat exchanger is configured to have a refrigerant pressure loss such that a ratio between the inlet temperature difference and the outlet temperature difference is within a predetermined range.

The refrigeration / air-conditioning apparatus according to the present invention further comprises an inlet temperature difference which is a temperature difference between the temperature of the heat transfer medium and the temperature of the heat storage material at the inlet of the heat storage heat exchanger, and the outlet of the heat storage heat exchanger. Outlet temperature difference, which is the difference between the temperature of the heat transfer medium and the temperature of the heat storage material at
x, when the smaller value is ΔTmin, the heat storage heat exchanger is configured so that the temperature difference ratio ΔTmin / ΔTmax has a refrigerant pressure loss satisfying ΔTmin / ΔTmax> 0.5. is there.

In the refrigeration / air-conditioning apparatus according to the present invention, cold heat is stored by utilizing the latent heat of fusion of the heat storage material. The solidification temperature of the heat storage material is used as the temperature of the heat storage material.

Further, the refrigeration / air-conditioning apparatus according to the present invention has a refrigerant pressure loss such that a decrease in operating efficiency from an operating efficiency of the heat source device when the refrigerant pressure loss of the heat storage heat exchanger is zero is equal to or less than a predetermined value. The heat storage heat exchanger is configured as follows.

[0032]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1 FIG. 1 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 1 of the present invention. This refrigerating air conditioner has a configuration having, for example, a cooling function, a heating function, and a heat storage function. In the figure, 1 is a compressor, 2 is a first four-way valve for switching the flow of refrigerant during cooling and heating, 3 is an outdoor heat exchanger, 4 is a first expansion valve, and 5 is an indoor heat exchanger. Are connected by piping to form a refrigeration cycle. Reference numeral 11 denotes a heat storage heat exchanger installed in the heat storage tank 10, and a second four-way valve 24 is connected to the pipes at both ends of the heat storage heat exchanger 11.
By switching 4, the flow direction of the refrigerant in the heat storage heat exchanger 11 can be switched between forward and reverse. The inlet pipe of the heat storage heat exchanger 11 is connected to a pipe between the outdoor heat exchanger 3 and the first expansion valve 4 via the second expansion valve 20. The outlet pipe of the heat storage heat exchanger 11 is provided with the first solenoid valve 2.
1 connects the pipe between the indoor heat exchanger 5 and the first four-way valve 2, and connects the second solenoid valve 22 to the pipe between the first expansion valve 4 and the outdoor heat exchanger 3. By switching between the first solenoid valve 21 and the second solenoid valve 22,
The outlet-side piping of the heat storage heat exchanger 11 can be switched between the flow to the first expansion valve 4 and the flow to the first four-way valve 2 between the heat storage cooling operation and the heat storage operation. In addition, the outdoor heat exchanger 3
A third solenoid valve 23 is provided in a pipe between the first expansion valve 4 and the first expansion valve 4. In this refrigeration / air-conditioning apparatus, a non-azeotropic mixed refrigerant Freon R407 is used as a heat transfer medium (hereinafter, referred to as a refrigerant).
C is enclosed. Reference numeral 25 denotes a temperature detector provided in a pipe between the second expansion valve 20 and the second four-way valve 24, which can detect a refrigerant temperature at an inlet of the heat storage heat exchanger 11.

FIG. 2 is a diagram showing in detail the configuration of the heat storage tank 10 relating to the regenerative refrigerating air conditioner shown in FIG. 1, wherein FIG. 2 (a) is a top view and FIG. 2 (b) is a longitudinal sectional view. It is. The heat storage heat exchanger 11 is composed of heat transfer tubes meandering in the vertical direction as shown in FIG. 2, and a plurality of, for example, four heat transfer tubes are connected in parallel in order to reduce pressure loss during the heat storage operation. In addition, a smooth tube is used for the heat transfer tube. Further, the meandering pitch of the heat transfer tubes is configured to be equal. Further, a distributor 12 for distributing the refrigerant to a plurality of heat transfer tubes is provided at an inlet and an outlet of the heat storage heat exchanger 11, respectively. The heat storage tank 10 is filled with, for example, water as a heat storage material. During the heat storage operation, the water is cooled and iced by the heat storage heat exchanger 11, and ice is attached to the surface of the heat transfer tube to generate cold heat so that the heat is stored in the heat storage tank 10. It is configured to store.

Next, the operation of the refrigeration / air-conditioning apparatus configured as described above during the heat storage operation and during the heat storage cooling operation will be described. Here, the heat storage operation refers to a heat storage heat exchanger that operates as an evaporator by using the cold generated by the heat source device including the compressor 1, the outdoor heat exchanger 3 that operates as a condenser, and the second expansion valve 20. This is an operation in which heat is stored in the heat storage tank 10 via the heat storage 11. In addition, the heat storage cooling operation is an operation in which the heat storage heat exchanger 11 is operated as a condenser and the cold stored in the heat storage tank 10 is supplied to the indoor heat exchanger 5 as a load device. The flow of the refrigerant in the heat storage heat exchanger 11 during the heat storage operation is changed from 11a to 11b in FIG.
Is the heat storage operation A, and vice versa.
The case of a is defined as the heat storage operation B. During the heat storage operation and the heat storage cooling operation, the first four-way valve 2 is connected as shown by a solid line.

During the heat storage operation, the first solenoid valve 21 is opened, the second solenoid valve 22 is closed, and the third solenoid valve 23 is closed.
First, at the start of the heat storage operation, the second four-way valve 24 is connected as indicated by a solid line so that, for example, the heat storage operation A in which the flow of the refrigerant in the heat storage heat exchanger 11 changes from 11a to 11b. As shown by the solid arrows in FIG. 1, the flow of the refrigerant during the heat storage operation A is such that the high-temperature and high-pressure refrigerant vapor discharged from the compressor 1 passes through the first four-way valve 2 and condenses and liquefies in the outdoor heat exchanger 3. . And
The pressure is reduced to a low pressure by the second expansion valve 20 and flows through the second four-way valve 24 into the heat storage heat exchanger 11 from 11a. The refrigerant that has flowed into the heat storage heat exchanger 11 evaporates by removing heat from the water in the heat storage tank 10, flows out of the heat storage heat exchanger 11 b, and flows out of the second four-way valve 24, the first solenoid valve 21, 1 Return to the compressor 1 through the four-way valve 2. At this time, the water in the heat storage heat exchanger 11 is cooled, and ice is deposited on the surface of the heat transfer tube to store cold heat in the heat storage tank 10.

FIG. 3 shows the operation during the heat storage operation A on a pressure-enthalpy diagram. In the figure, the horizontal axis is enthalpy and the vertical axis is pressure. In the figure, point a indicates the compressor 1 outlet, point b indicates the outdoor heat exchanger 3 outlet, point c indicates the inlet of the heat storage heat exchanger 11, and d indicates the outlet of the heat storage heat exchanger 11. As shown in FIG. 2, since the heat storage heat exchanger 11 is constituted by a heat transfer tube in which a plurality of smooth tubes are connected in parallel, the pressure loss during evaporation is very small. The pressure also becomes almost constant. However, in the refrigeration / air-conditioning apparatus of the present embodiment, since the non-azeotropic mixed refrigerant is used as the refrigerant, the evaporation temperature is lowest at the inlet of the heat storage heat exchanger 11 and lowest at the outlet of the heat storage heat exchanger 11. Get higher. For example, when Freon R407C is used as the refrigerant, FIG.
As shown in the figure, the inlet of the heat storage heat exchanger 11 at the point c is -6.
° C, and the outlet of the heat storage heat exchanger 11 at point d becomes -1 ° C.

As a result, in the heat storage operation A, ice does not adhere to the surface of the heat transfer tube of the heat storage heat exchanger 11 with a uniform thickness, and the ice thickness at the inlet of the heat storage heat exchanger 11 having a low evaporation temperature is reduced. On the contrary, the ice thickness at the outlet of the heat storage heat exchanger 11 having a high evaporation temperature becomes thin. When the heat storage operation A proceeds in this state, excessive ice is generated at the inlet of the heat storage heat exchanger 11,
The efficiency of the heat storage heat exchanger 11 as a whole decreases, and the evaporation temperature or the evaporation pressure decreases.

Therefore, in the present embodiment, the direction of the flow of the refrigerant in the heat storage heat exchanger 11 is reversed during the heat storage operation so as to make the ice thickness uniform. That is, the heat storage heat exchanger 11 is provided by the temperature detector 25 provided at the inlet of the heat storage heat exchanger 11.
Then, a decrease in efficiency due to uneven icing is detected, and the operation proceeds to the heat storage operation B. When the refrigerant temperature detected by the temperature detector 25 becomes equal to or lower than a predetermined value, for example, equal to or lower than -7 ° C., it is determined that the ice has been sufficiently made on the inlet side of the heat storage heat exchanger 11. Can be. For this reason, the second four-way valve 24
And heat storage operation B is executed. This heat storage operation B
The opening and closing states of the first solenoid valve 21, the second solenoid valve 22, and the third solenoid valve 23 are the same as those in the heat storage operation A, and are performed by switching the second four-way valve 24 as shown by the dotted line in FIG.

The flow of the refrigerant during the heat storage operation B is such that the high-temperature and high-pressure refrigerant vapor discharged from the compressor 1 passes through the first four-way valve 2 and passes through the outdoor heat exchanger 3 The condensed liquid is reduced to a low pressure by the second expansion valve 20 and flows into the heat storage heat exchanger 11b through the second four-way valve 24. Refrigerant flowing through the heat storage heat exchanger 11 from 11b to 11a takes heat from water in the heat storage tank 10 and evaporates. Machine 1
Return to

The flow direction of the refrigerant in the heat storage heat exchanger 11 during the heat storage operation B is as shown by the dashed line arrow in FIG.
The flow is opposite to the flow during the heat storage operation A indicated by the solid arrow. FIG. 4 is a graph showing the temperature distribution in the heat storage heat exchanger 11 in the heat storage operation A and the heat storage operation B. The horizontal axis indicates the position of the heat storage heat exchanger, and the vertical axis indicates the temperature (° C.). As shown by the dashed line in FIG.
The temperature change in the heat storage heat exchanger 11 during the heat storage operation B is opposite to that during the heat storage operation A. In the heat storage operation B, the evaporating temperature of the portion where the amount of ice making was small during the heat storage operation A becomes low and the ice making amount increases. Therefore, the amount of ice making of the entire heat storage heat exchanger 11 becomes uniform.

During the cooling operation using heat storage, the first solenoid valve 21 is closed, the second solenoid valve 22 is opened, and the third solenoid valve 23 is closed.
At this time, the second four-way valve 24 is set so that the flow of the refrigerant in the heat storage heat exchanger 11 changes from 11a to 11b. As shown by the dashed arrow in FIG. 1, the flow of the refrigerant during the heat storage operation is as follows.
It flows into the heat storage heat exchanger 11 through the second expansion valve 20.
During this operation, the degree of opening of the second expansion valve 20 is fully open. The high-pressure liquid refrigerant flowing through the heat storage heat exchanger 11 from 11 a to 11 b
It is cooled from about 0 ° C. to about 0 ° C. and flows out with an increased degree of supercooling. The liquid refrigerant having an increased degree of supercooling passes through the second solenoid valve 22 and is reduced in pressure to a low pressure by the first expansion valve 4, so that the indoor heat exchanger 5
And evaporates, and returns to the compressor 1 through the first four-way valve 2.

As described above, in this embodiment, by switching the second four-way valve 24 and reversing the flow direction of the refrigerant in the heat storage heat exchanger 11, a non-azeotropic mixed refrigerant can be used as the refrigerant. By reversing the high temperature part and the low temperature part of the evaporation temperature of the non-azeotropic refrigerant mixture in the heat storage heat exchanger 11, ice of a uniform thickness can be generated in the heat storage heat exchanger 11, and the heat storage operation can be performed efficiently. Becomes possible. In addition, excessive ice is generated in a part of the heat storage heat exchanger 11, and the ice in this part fuses to form a heat transfer tube or the heat storage tank 1.
0 can be prevented from being deformed or damaged, and a highly reliable refrigeration / air-conditioning apparatus can be obtained.

In the present embodiment, the temperature of the refrigerant flowing into the heat storage heat exchanger 11 is detected by the inexpensive temperature detector 25, and when the temperature of the refrigerant falls below a predetermined temperature, the second four-way valve is used. Since the switching of the heat exchanger 24 is performed, the flow direction of the refrigerant in the heat storage heat exchanger 11 can be reliably switched in the reverse direction. The location for detecting the refrigerant temperature is not limited to the inlet portion of the heat storage heat exchanger 11, but may be provided in a pipe from the second four-way valve 24 to a branch portion between the first solenoid valve 21 and the second solenoid valve 22. Alternatively, the temperature of the outlet of the heat storage heat exchanger 11 may be detected and switched. Furthermore, a temperature detector is provided in the heat storage heat exchanger 11 in the heat storage tank 10 to detect the heat storage state from the refrigerant temperature in the heat storage tank 10, and to switch the flow of the refrigerant according to the result. Is also good.

Instead of detecting the temperature of the refrigerant flowing into the heat storage heat exchanger 11, a pressure detector is provided at the inlet of the heat storage heat exchanger 11, and the pressure detector is used to detect the pressure.
Even if the pressure of the refrigerant flowing through the heat storage heat exchanger 11 is detected and the refrigerant temperature at the inlet of the heat storage heat exchanger is estimated to switch the flow of the refrigerant, the flow direction of the refrigerant in the heat storage heat exchanger 11 is surely reversed. Can be switched to The installation location of the pressure detector is not limited to the inlet of the heat storage heat exchanger 11, and may be provided at the outlet of the heat storage heat exchanger 11 or at the heat storage heat exchanger 11 in the heat storage tank 10.
The same effect as described above is achieved.

In place of the temperature detector and the pressure detector,
An ice thickness detector for detecting, for example, the thickness of ice as the state of ice in the heat storage tank 10 is provided in the heat storage tank 10, and when it is detected that the ice thickness has reached a predetermined thickness, the second four-way valve 24 May be controlled to be switched. By detecting the state of the ice in the heat storage tank 10, the flow direction of the refrigerant in the heat storage heat exchanger 11 can be reliably switched in the opposite direction. A highly reliable refrigeration / air-conditioning device can be obtained without causing breakage. That is, as long as the state of heat storage in the heat storage tank 10 can be grasped from the detection result of the detector, the detector may be installed anywhere and the state quantity to be detected may be any. Further, in this embodiment, water is used as the heat storage material, and the cold water is stored by using the water filled in the heat storage tank 10 as ice to store the cold heat. May be used to store cold or warm heat.

However, as described in the above embodiment,
It is desirable to use water as the heat storage material in terms of cost and ease of handling, and the temperature detector 25 is used as the heat storage state detecting means.
When the temperature detector 25 is provided at the inlet of the heat storage heat exchanger 11, the temperature of the refrigerant flowing into the heat storage heat exchanger 11 can be detected in both the heat storage operation A and the heat storage operation B, and can be attached to the pipe. , It can be easily implemented.

In the above description, the flow direction of the refrigerant in the heat storage heat exchanger 11 is switched only during the heat storage operation. However, the flow direction of the refrigerant in the heat storage heat exchanger 11 may be switched also during the heat storage cooling operation. When the flow direction of the refrigerant is switched during the cooling operation using the heat storage, the ice is uniformly melted in the heat storage tank 10 and the cold heat can be supplied stably.

In the above description, the configuration in which cold heat is stored in the heat storage tank 10 has been described. However, in the air conditioner in which the heat generated by the heat source device is stored in the heat storage tank 10, the heat storage heat exchanger 11
Even if the flow direction of the refrigerant is switched, the heat can be uniformly stored in the heat storage tank 10 in the same manner as described above.

In this embodiment, an example in which one indoor heat exchanger is connected to one outdoor heat exchanger is described. However, the present invention is not limited to this. A refrigeration and air-conditioning system to which two indoor heat exchangers are connected exhibits the same effect.

Further, in this embodiment, the case where Freon R407C having a zero ozone layer destruction coefficient is used as the refrigerant of the refrigeration and air-conditioning apparatus has been described. However, the present invention is not limited to this. A refrigerant may be used.
Further, from the viewpoint of preventing global warming, a non-azeotropic mixed refrigerant using a natural refrigerant such as propane, butane, or ammonia exhibits the same effect.

Embodiment 2 FIG. 5 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 2 of the present invention. In the figure, 34 is a fourth solenoid valve, 35 is a fifth solenoid valve, 36 is a sixth solenoid valve, and 37 is a seventh solenoid valve. Heat storage heat exchanger 11
A fourth solenoid valve 34 and a fifth solenoid valve 35 are provided on the inlet side pipe, and a sixth solenoid valve 36 is provided on the outlet side pipe of the heat storage heat exchanger 11.
And the seventh electromagnetic valve 37, and the flow direction of the refrigerant during the heat storage operation can be switched between forward and reverse by a combination of opening and closing of the electromagnetic valve. Note that the same components as those shown in FIG. 1 are denoted by the same reference numerals, and redundant description will be omitted.

In the present embodiment, the fourth solenoid valve 34 is opened, the fifth solenoid valve 35 is closed, the sixth solenoid valve 36 is opened, and the seventh solenoid valve 37 is closed during the heat storage operation A at the beginning of the heat storage operation. The flow direction of the refrigerant in the heat storage heat exchanger 11 is defined as a direction from 11a to 11b. Thereafter, after a lapse of a predetermined time, the fourth solenoid valve 34
, The fifth solenoid valve 35 is opened, the sixth solenoid valve 36 is closed, the seventh
The electromagnetic valve 37 is opened to shift to the heat storage operation B, and the flow direction of the refrigerant in the heat storage heat exchanger 11 is set to the direction from 11b to 11a. As described above, since the flow direction of the non-azeotropic mixed refrigerant in the heat storage heat exchanger 11 can be switched between forward and reverse, a high temperature portion of the evaporation temperature of the non-azeotropic mixed refrigerant in the heat storage heat exchanger 11 can be obtained. And the low temperature part can be reversed, and ice can be uniformly generated in the heat storage heat exchanger 11.

In this embodiment, the switching of the flow direction of the refrigerant in the heat storage heat exchanger 11 is controlled by an inexpensive timer. That is, for example, when the heat storage operation time is 8 hours, by setting the heat storage operation A to 4 hours and the heat storage operation B to 4 hours, the uniform ice making can be performed inexpensively and surely without using a temperature detector or a pressure detector. Can be realized.

The operation times of the heat storage operation A and the heat storage operation B do not need to be the same. For example, when the heat storage operation time is 8 hours, the heat storage operation A is set to 5 hours and the heat storage operation B is set to 3 hours. The heat storage operation A may be 3 hours, and the heat storage operation B may be 5 hours.

Switching between the heat storage operation A and the heat storage operation B is as follows.
The operation is not limited to one time, and when the heat storage operation time is 8 hours, if the heat storage operation A and the heat storage operation B are controlled to be switched every two hours, uniform ice making can be realized more reliably.

Embodiment 3 FIG. 6 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 3 of the present invention. In the figure, 1 is a compressor, 2 is a four-way valve for switching the flow of refrigerant during cooling and heating, 3 is an outdoor heat exchanger, 4 is a first expansion valve,
Reference numeral 5 denotes an indoor heat exchanger, which is connected by piping to form a refrigeration cycle. Reference numeral 11 denotes a heat storage heat exchanger installed in the heat storage tank 10, and its inlet side pipe is connected to a pipe between the outdoor heat exchanger 3 and the first expansion valve 4 via a second expansion valve 20. I have. The outlet pipe of the heat storage heat exchanger 11 is connected to a pipe between the indoor heat exchanger 5 and the four-way valve 2 via a first solenoid valve 21 and a first expansion valve via a second solenoid valve 22. 4 and a pipe between the outdoor heat exchanger 3. By opening and closing the first solenoid valve 21 and the second solenoid valve 22, the refrigerant circuit can be switched between the cooling operation using heat storage and the heat storage operation. A third solenoid valve 23 is provided in a pipe between the outdoor heat exchanger 3 and the first expansion valve 4. Further, Freon R407C, which is a non-azeotropic mixed refrigerant, is sealed in the refrigerating air conditioner.

The heat storage heat exchanger 11 is composed of heat transfer tubes meandering in the vertical direction as in FIG. 31, and a plurality of, for example, four heat transfer tubes are connected in parallel in order to reduce the pressure loss during the heat storage operation. And a smooth tube is used for the heat transfer tube. Further, the outside diameter is 6.35 m from the center of the heat storage heat exchanger 11 to the upstream side.
m heat transfer tube 11c, and the outer diameter is 4m from the center to the downstream side.
m heat transfer tubes 11d are used. The heat storage tank 10 is filled with, for example, water as a heat storage material. During the heat storage operation, the water is cooled and iced by the heat storage heat exchanger 11, and ice is attached to the surface of the heat transfer tube to generate cold heat. Is configured to be stored.

Next, the operation of the refrigeration / air-conditioning apparatus configured as described above during the heat storage operation and during the heat storage cooling operation will be described. During the heat storage operation, the first solenoid valve 21 is opened, the second solenoid valve 22 is closed, and the third solenoid valve 23 is closed. The flow of the refrigerant during the heat storage operation is as shown by the solid line arrow in FIG. The pressure is reduced to a low pressure by the expansion valve 20 and flows into the heat storage heat exchanger 11. The refrigerant that has flowed into the heat storage heat exchanger 11 removes heat from the water in the heat storage tank 10 and evaporates, and ice adheres to the surface of the heat transfer tube to generate. The refrigerant evaporated in the heat storage heat exchanger 11 returns to the compressor 1 through the first solenoid valve 21 and the four-way valve 2.

In the heat storage heat exchanger 11, the Freon R407C, whose temperature changes during evaporation, evaporates. Therefore, the temperature of the heat transfer tube of the heat storage heat exchanger 11 becomes lowest at the inlet and gradually rises in the flow direction of the refrigerant. The outlet of the heat storage heat exchanger 11 is highest. However, in the present embodiment, the diameter of the heat transfer tube 11d on the outlet side of the heat storage heat exchanger 11 having a high evaporation temperature is smaller than the diameter of the heat transfer tube 11c on the inlet side having a low evaporation temperature. The flow rate of the refrigerant in the heat transfer tube of the section is higher than that of the inlet, and the heat transfer coefficient of the refrigerant is higher at the outlet than at the inlet. Therefore, at the outlet of the heat storage heat exchanger 11, the temperature of the heat transfer tube rises due to the change in the evaporation temperature of the Freon R407C, and the temperature difference from the water temperature in the heat storage tank 10 becomes smaller, but the heat transfer characteristics are higher than the inlet. Therefore, ice is generated even with a small temperature difference, and as a result, the ice thickness of the entire heat storage heat exchanger 11 becomes uniform.

During the cooling operation using heat storage, the first solenoid valve 21 is closed, the second solenoid valve 22 is opened, and the third solenoid valve 23 is closed. As shown by the dashed arrow in FIG. 6, the flow of the refrigerant during the heat storage operation is such that the high-temperature and high-pressure refrigerant vapor discharged from the compressor 1 is condensed and liquefied in the outdoor heat exchanger 3 through the four-way valve 2, It flows into the heat storage heat exchanger 11 through the expansion valve 20. In addition,
During this operation, the second expansion valve 20 is fully opened. The high-pressure liquid refrigerant that has flowed into the heat storage heat exchanger 11 is cooled from, for example, about 40 ° C. to about 0 ° C. by ice in the heat storage tank 10 and flows out with an increased degree of supercooling. The liquid refrigerant having an increased degree of supercooling is reduced to a low pressure by the first expansion valve 4 through the second solenoid valve 22, flows into the indoor heat exchanger 5 and evaporates, passes through the four-way valve 2, and evaporates. Return to In this cooling operation using heat storage, the heat storage tank 10
When supplying the cold heat obtained by melting the ice generated in the outdoor heat exchanger 5 as a load device, the heat storage heat exchanger 11
Because the heat transfer characteristics of the outlet side of the is higher than that of the inlet side,
Ice can be uniformly thawed and cold heat can be supplied stably.

As described above, in the present embodiment, the diameter of the heat transfer tubes downstream from the center of the heat storage heat exchanger 11 is smaller than the diameter of the heat transfer tubes 11c upstream from the center. Since the heat transfer characteristics of the heat transfer tube 11d on the downstream side from the central portion where the evaporation temperature is high are improved, the amount of ice making at the outlet portion where the evaporation temperature is high is increased even when a non-azeotropic mixed refrigerant that changes the evaporation temperature is used. As a result, the ice making amount can be made substantially equal to the ice making amount at the inlet portion having a low evaporation temperature, and ice can be generated almost uniformly in the heat storage heat exchanger 11. Also, when using cold heat, it is possible to stably supply cold heat.

In the above embodiment, the heat storage heat exchanger 1
The diameter of the heat transfer tube from the center to the downstream side is smaller than the diameter of the heat transfer tube from the center to the upstream side. Although an example of improving the heat transfer is described, the present invention is not limited to this, and a heat transfer tube having a higher heat transfer characteristic than the heat transfer tube from the center to the upstream is used for the heat transfer tube from the center to the downstream of the heat storage heat exchanger 11. Is also good. For example, if all the heat transfer tubes of the heat storage heat exchanger 11 have the same diameter, the upstream heat transfer tubes from the center are smooth tubes, and the downstream heat transfer tubes from the center are inner grooved tubes. The amount of ice can be made uniform with a simple configuration.
Further, by changing the material of the heat storage heat exchanger, the heat transfer tube may be formed by using a material having a low heat transfer characteristic such as stainless steel on the inlet side and using a material having a high heat transfer characteristic such as copper on the outlet side. .
In addition, it is not necessary to change the heat transfer characteristics of the heat transfer tubes on the upstream side and the downstream side separately at the center, and three or more types of heat transfer tubes having different heat transfer characteristics are used. It may be configured so as to be higher than the heat transfer characteristics.

Embodiment 4 FIG. 7 is a configuration diagram showing a heat storage tank according to Embodiment 4 of the present invention. Heat storage heat exchanger 1
The non-azeotropic refrigerant mixture is branched into a plurality of, for example, two flow paths at one inlet. The heat transfer tube 11c on the upstream side from the center of the heat storage heat exchanger 11 is configured by connecting two flow paths in parallel. The heat transfer tube 11d is composed of one flow path. Here, only the heat storage tank 10 is shown, and other parts constituting the refrigeration / air-conditioning apparatus are the same as those shown in FIG. 6, and the overlapping description will be omitted.

The refrigerant flowing into the heat storage heat exchanger 11 during the heat storage operation first branches into two, flows through the heat transfer tube 11c having two flow paths connected in parallel, and evaporates. The refrigerant merges at the approximate center of the heat storage heat exchanger 11, flows into the heat transfer tube 11d, and evaporates. Therefore, the flow rate of the refrigerant in the heat transfer tube 11d on the outlet side of the heat storage heat exchanger 11 having a high evaporation temperature is larger than that of the heat transfer tube 11c on the inlet side having a low evaporation temperature, and the heat transfer coefficient of the refrigerant at the outlet portion is lower than that of the inlet portion. More than parts. Therefore, at the outlet of the heat storage heat exchanger 11, the temperature of the heat transfer tube rises due to the change in the evaporation temperature of the Freon R407C, and the temperature difference from the water temperature in the heat storage tank 10 becomes smaller, but the heat transfer characteristics are higher than the inlet. Therefore, ice is generated even with a small temperature difference, and as a result, the ice thickness of the entire heat storage heat exchanger 11 becomes uniform.

As described above, in the present embodiment, the number of flow paths on the outlet side of the heat storage heat exchanger 11 is made smaller than the number of flow paths on the inlet side, and the cross-sectional area of the flow path at the outlet of the heat storage heat exchanger 11 Is smaller than the sum of the cross-sectional areas of the inlet passages, so that the heat transfer characteristics of the outlet side having a higher evaporation temperature can be improved as compared with the inlet side having a lower evaporation temperature. The amount of ice making at the outlet where the evaporation temperature of the non-azeotropic mixed refrigerant is high is increased to about the same as the amount of ice making at the inlet where the evaporation temperature is low,
It is possible to realize uniform ice making in the heat storage tank 10.

In this embodiment, the heat transfer tubes 1 on the upstream side
Although the number of 1c is two and the number of the heat transfer tubes 11d on the downstream side is one, it is not limited to this. To make the heat transfer characteristic of the outlet of the heat storage heat exchanger 11 higher than that of the inlet,
What is necessary is just to comprise so that the total cross-sectional area of the flow path of an outlet part may become smaller than the total of cross-sectional area of the flow path of an inlet part. For example, the number of heat transfer tubes 11c on the upstream side may be three or more, and the number of heat transfer tubes 11d on the downstream side may be smaller than that on the upstream side. Also, without changing the number of flow passages formed by the heat transfer tubes in the central part of the heat storage heat exchanger 11 in two parts, for example, the number of heat transfer tubes is gradually reduced from the upstream side to the downstream side. May be.
At this time, the diameter of the heat transfer tube may be changed between the upstream side and the downstream side, but the total cross-sectional area of the flow path at the outlet of the heat storage heat exchanger 11 is larger than the total cross-sectional area of the flow path at the inlet. It is configured to be small.

Embodiment 5 FIG. 8 is a perspective view showing a heat storage heat exchanger 11 according to Embodiment 5 of the present invention. The heat storage heat exchanger 11 is configured by connecting two flow paths in parallel,
The two flow paths are turned back at the approximate center portion 11e, and the heat transfer tube 11c on the upstream side from the center portion and the heat transfer tube 11d on the downstream side from the center portion are soldered, for example, so as to be in thermal contact with each other. I have. In the figure, the soldered portions are indicated by oblique lines. Here, only the heat storage heat exchanger 11 is shown, and the other parts constituting the refrigeration / air-conditioning apparatus are the same as those shown in FIG. Here, the two heat transfer tubes being in thermal contact with each other means that at least a part of the two heat transfer tubes is directly
Alternatively, it refers to a configuration in which heat transfer tubes can conduct heat by contacting each other with a material having a high thermal conductivity.

The refrigerant flowing into the heat storage heat exchanger 11 during the heat storage operation first flows through the upstream heat transfer tube 11c and evaporates. This refrigerant is stored in a substantially central portion 11e of the heat storage heat exchanger 11.
And flows into the downstream heat transfer tube 11d to evaporate. In this configuration, since the upstream heat transfer tube 11c having a low evaporation temperature and the downstream heat transfer tube 11d having a high evaporation temperature are soldered and in thermal contact, the wall surface temperature of the heat transfer tube of the heat storage heat exchanger 11 is Make uniform. As a result, even if a non-azeotropic mixed refrigerant that changes in temperature during evaporation is used, the thickness of ice adhered to the entire heat storage heat exchanger 11 and generated is uniform.

In this embodiment, the upstream heat transfer tube 11c having a low evaporation temperature and the downstream heat transfer tube 11d having a high evaporation temperature are provided.
Although the method of soldering the heat transfer tubes as the thermal contact means has been described, the present invention is not limited to this. It is effective. In addition, it is not always necessary to turn the heat transfer tube at the center so that the upstream side and the downstream side of the heat transfer tube are in thermal contact with each other. You may comprise so that the upstream and downstream of different heat transfer tubes may be in thermal contact. At this time, the flow directions of the refrigerant flowing through the heat transfer tubes on the upstream side and the downstream side which are brought into thermal contact may be the same direction or the opposite directions. . Further, as shown in FIG. 9, the upstream heat transfer tube 11c and the downstream heat transfer tube 11d may be partially brought into thermal contact with a thin plate 40 made of aluminum or copper. Further, as shown in FIG. 10, two sets of aluminum or copper plates 41a and 41b are joined,
To form two refrigerant passages, each of which is connected to the upstream heat transfer tube 11.
c and the downstream heat transfer tube 11d.

As described above, in the present embodiment, since the heat transfer tube at the inlet and the heat transfer tube at the outlet of the heat storage heat exchanger are in thermal contact with each other, non-azeotropic mixing in which a temperature change occurs during evaporation. Even if a refrigerant is used, the low-temperature portion and the high-temperature portion of the non-azeotropic refrigerant mixture are thermally conducted to make the heat transfer tube surface temperature uniform, so that uniform ice making in the heat storage heat exchanger can be realized.

Embodiment 6 FIG. FIG. 11 is a refrigerant circuit diagram illustrating a refrigeration / air-conditioning apparatus according to Embodiment 6 of the present invention. The heat storage heat exchanger 11 is configured by connecting a plurality of, for example, four heat transfer tubes in parallel, and further includes a heat transfer tube 11f (a refrigerant flows rightward in the drawing) and a heat transfer tube 11g in which the flow direction of the refrigerant is opposite. (The refrigerant flows in the left direction as viewed in the figure) are alternately arranged in the heat storage tank 10. The heat transfer tubes are arranged with a certain distance between adjacent heat transfer tubes, for example, at least twice the diameter of the heat transfer tubes. The same components as those shown in FIG. 6 are denoted by the same reference numerals, and the description thereof will not be repeated.

In the heat storage heat exchanger 11, Freon R407C, whose temperature changes during evaporation, evaporates, so that the temperature of the heat transfer tube of the heat storage heat exchanger 11 gradually rises from the inlet to the outlet, and the heat storage heat exchange is performed. The ice thickness at the inlet portion of the vessel 11 is large, and the ice thickness at the outlet portion is small. However, in the present embodiment, heat transfer tubes 11f and heat transfer tubes 11g having different flow directions of the refrigerant are alternately arranged in the heat storage tank 10, and the heat transfer tubes 11f
The outlet of the heat transfer tube 11g with a low evaporation temperature is arranged next to the inlet with a high evaporation temperature of f. Therefore, as shown in FIG. 12, a portion where the thickness of ice adhered to the heat transfer tube 11f is thick and a portion where the thickness of ice adhered to the heat transfer tube 11g is thin are adjacent to each other. The thin part and the thick ice attached to the heat transfer tube 11g are adjacent to each other. That is, the heat transfer tube 11f and the heat transfer tube 1
Ice is generated almost uniformly in the space between 1 g. For this reason, excessive ice is generated at the inlet portion of the heat transfer tube as in the conventional apparatus, and it is possible to prevent the ice in this portion from fusing and causing deformation or breakage of the heat transfer tube or the heat storage tank.

As described above, in this embodiment, a plurality of heat transfer tubes are arranged so that the flow directions of the refrigerants are different from each other. Therefore, when a non-azeotropic mixed refrigerant such as Freon R407C is used as the refrigerant, one transfer tube is used. The inlet portion of the heat pipe having a low evaporation temperature is adjacent to the outlet portion of another heat transfer tube having a high evaporation temperature provided in parallel with the inlet portion. For this reason, the heat transfer tubes having a small ice thickness are arranged next to the heat transfer tubes having a large ice thickness, and even if the ice generated on the surface of each heat transfer tube is not uniform, the heat transfer tubes 11f
Ice is uniformly attached to and generated in the space between the heat transfer tube 11g. Therefore, it is possible to prevent the ice generated by adhering to the adjacent heat transfer tubes from fusing together to cause deformation or breakage of the heat transfer tubes or the heat storage tank, and a highly reliable refrigeration / air-conditioning apparatus can be obtained.

Embodiment 7 FIG. 13 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 7 of the present invention. The heat storage heat exchanger 11 has a plurality of, for example, two heat transfer tubes 11f, 11
g are connected in parallel, and the heat transfer tubes 11f and 11g
Are arranged so that the flow directions of the refrigerant are reversed, and the two heat transfer tubes 11f and 11g are soldered so as to be in thermal contact with each other. In the figure, the soldered portions are indicated by oblique lines. Here, the two heat transfer tubes being in thermal contact means that at least a part of the two heat transfer tubes come into contact with each other directly or through a material having high thermal conductivity such as copper or aluminum. Means that the heat transfer tubes can conduct heat with each other. The same components as those shown in FIG. 6 are denoted by the same reference numerals, and the description thereof will not be repeated.

The non-azeotropic mixed refrigerant such as Freon R407C that has flowed into the heat storage heat exchanger 11 during the heat storage operation
f, 11g, and evaporates while evaporating temperature rises. In the present embodiment, two heat transfer tubes whose flow directions are opposite to each other are soldered, and in particular, soldered so that the inlet and outlet of the flow are in thermal contact. That is,
The portion of the heat transfer tube 11f where the evaporation temperature is low is in thermal contact with the portion of the heat transfer tube 11g where the evaporation temperature is high, and the heat transfer tube 11f
The portion having a high evaporation temperature is in thermal contact with the portion having a low evaporation temperature of the heat transfer tube 11g. For this reason, even if a non-azeotropic mixed refrigerant having a temperature change at the inlet and outlet at the time of evaporation is used, the wall surface temperature of the heat transfer tubes of the heat storage heat exchanger 11 becomes uniform,
The thickness of the ice formed on the surface becomes uniform.

In the above-described embodiment, the method of soldering the heat transfer tubes 11f and 11g, which is opposite to the flow direction of the refrigerant, as the thermal contact means, is not limited thereto. The same effect can be achieved by simply contacting the heat tubes. The configuration is the same as that of FIG.
The heat transfer tube 11f and the heat transfer tube 11g may be brought into thermal contact by partially connecting them with a thin plate made of aluminum or copper. Further, the structure is the same as that of FIG. 10, two sets of aluminum or copper plate members are joined, two refrigerant flow paths are formed therebetween, and one of the heat transfer tubes 11 f is used, and the other is in the opposite direction to the heat transfer tubes 11 f. The flowing heat transfer tube 11g may be used.

In the above-described embodiment, the heat storage heat exchanger 11 is described by connecting the two heat transfer tubes 11f and 11g in parallel. However, the present invention is not limited to this. For example, a pair of heat transfer tubes 11f, 1
A plurality of 1 g may be arranged in parallel at intervals to form a heat storage heat exchanger. Further, three or more heat transfer tubes may be thermally contacted by soldering or the like. Since the wall surfaces of the heat transfer tubes are made uniform by thermally contacting the heat transfer tubes, the number of heat transfer tubes flowing in one direction and the number of heat transfer tubes flowing in the opposite direction are preferably the same.

As described above, in the present embodiment, the heat storage heat exchanger 11 is composed of a plurality of heat transfer tubes, and the heat transfer tubes in which the refrigerant flows in opposite directions are alternately arranged. Since at least two heat transfer tubes are in thermal contact with each other, even if a non-azeotropic mixed refrigerant that changes in temperature during evaporation is used, a low-temperature portion and a high-temperature portion of the evaporation temperature of the non-azeotropic mixed refrigerant are used. The heat transfer between the heat transfer tube and the heat transfer tube surface is made uniform, and uniform ice making in the heat storage heat exchanger can be realized.

Embodiment 8 FIG. FIG. 14 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 8 of the present invention. The heat storage heat exchanger 11 is configured by disposing heat transfer tubes in a meandering manner, for example, in a vertical direction. The meandering pitch of the heat transfer tubes is increased at the entrance where the evaporation temperature is low and is decreased at the exit where the evaporation temperature is high. The same components as those shown in FIG. 6 are denoted by the same reference numerals, and the description thereof will not be repeated.

In the heat storage operation, since the CFC R407C, whose temperature changes during evaporation, evaporates in the heat storage heat exchanger 11, the heat transfer tube temperature of the heat storage heat exchanger 11 gradually increases from the inlet to the outlet. . For this reason,
The ice thickness generated at the inlet of the heat storage heat exchanger 11 is large, and the ice thickness at the outlet is small. However, in the present embodiment, the meandering pitch of the heat transfer tubes at the inlet portion having a low evaporation temperature is increased, and the meandering pitch of the heat transfer tubes at the outlet portion having a high evaporation temperature is reduced. In other words, even if ice is excessively generated at the inlet of the heat transfer tube, the ice-making space in this portion is large, so that the ice generated in the adjacent heat transfer tubes due to meandering fuses to deform the heat transfer tubes and the heat storage tank. Or damage can be prevented, and the reliability of the device is improved. The heat storage heat exchanger 11
The same applies to the case where the heat transfer tube is not limited to the vertical direction but is configured to meander in the horizontal direction.The space where the ice generated at the inlet with a low evaporation temperature is larger than the space at the outlet. I just need.

FIG. 15 is a top view showing a heat storage tank according to another example of the present embodiment. The heat storage tank 10 has a cylindrical shape and includes eight heat transfer tubes meandering in the vertical direction to constitute a heat storage heat exchanger 11. The inlet of each of the heat transfer tubes is located on the outer peripheral side of the cylindrical shape, and the outlet of each of the heat transfer tubes is configured to join at the center of the cylindrical shape. As shown in the drawing, the meandering pitch of the heat transfer tubes is configured to be large at the inlet portion on the outer peripheral side, and is gradually reduced toward the outlet portion at the center. For this reason, in the heat transfer tube at the inlet portion where the evaporation temperature is low, the adjacent heat transfer tube 1 is meandered.
The interval between 1h and 11i is widened, and narrowed in the heat transfer tube at the outlet part where the evaporation temperature is high. In particular, in this configuration, the heat storage tank 10 has a cylindrical shape, and the heat storage
In each of the heat transfer tubes, the interval between the meandering adjacent heat transfer tubes is narrowed from the inlet to the outlet, and the interval between the adjacent heat transfer tubes such as the heat transfer tubes 11h and 11j is also smaller than the inlet. From the exit to the exit. That is, since the space around the heat transfer tube at the inlet is made larger than the space around the heat transfer tube at the outlet, even if the ice thickness generated at the inlet with a low evaporation temperature becomes thicker, Can be prevented from causing deformation and breakage of the heat transfer tube and the heat storage tank, and a highly reliable refrigeration and air-conditioning apparatus with a simple configuration can be obtained. Also,
In the present embodiment, the meandering pitch is gradually reduced from the inlet to the outlet of the heat storage heat exchanger 11, but the pitch is not limited to this, and the pitch may be changed stepwise. . For example, the pitch may be changed at one location in the center of one heat transfer tube, or the pitch may be changed at several locations.

As described above, in the present embodiment, the heat storage heat exchanger 11 is formed so that the heat transfer tubes meander vertically or horizontally at intervals and meander the heat transfer tubes at the inlet portion during heat storage. Pitch is larger than the pitch of the outlet, so the ice making space is widened at the low evaporating temperature of the non-azeotropic refrigerant, and the ice making space is narrowed at the high evaporating temperature. Even if the generated ice thickness is increased, it is possible to prevent the ice in this portion from fusing and causing deformation or breakage of the heat transfer tube or the heat storage tank, and a highly reliable refrigeration / air-conditioning apparatus with a simple configuration can be obtained.

Embodiment 9 FIG. FIG. 16 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 9 of the present invention. In the present embodiment, the refrigerant pressure loss of the heat storage heat exchanger 11 is made large enough to cancel the temperature rise of the non-azeotropic mixed refrigerant in the heat storage heat exchanger 11. Specifically, for example, the diameter of the heat transfer tubes constituting the heat storage heat exchanger 11 is reduced, the number of heat transfer tubes connected in parallel is reduced, the length of the heat transfer tubes is increased, and the heat transfer tubes are smoothed. Refrigerant pressure loss can be increased by using an inner grooved tube instead of a tube, or by using a throttle in the middle of the heat transfer tube. The same components as those shown in FIG. 6 are denoted by the same reference numerals, and the description thereof will not be repeated.

FIG. 17 shows the operation during the heat storage operation on a pressure-enthalpy diagram. The point a in the figure is the compressor 1
, The point b indicates the outlet of the outdoor heat exchanger 3, the point c indicates the inlet of the heat storage heat exchanger 11, and the point d indicates the outlet of the heat storage heat exchanger 11.
The heat storage heat exchanger 11 is a Freon R40 indicated by a chain line in the figure.
The refrigerant pressure loss is increased to match the 7C isotherm. For this reason, Freon R40 in the heat storage heat exchanger 11
The evaporation temperature of 7C is substantially constant, and the thickness of the ice adhered to the surface is also uniformed. The change in the evaporating temperature of Freon R407C under a constant pressure is about 5 ° C., and by setting the refrigerant pressure loss of the heat storage heat exchanger 11 to about 0.8 kg / cm ² , the evaporating temperature becomes substantially constant. . However, the numerical value of the refrigerant pressure loss is a numerical value set according to the type of the non-azeotropic mixed refrigerant.

To set the refrigerant pressure loss to about 0.8 kg / cm ² , for example, a refrigeration capacity of 6400
In a refrigeration air conditioner of kcal / h, a heat transfer tube constituting a conventional heat storage heat exchanger has an outer diameter of 6.35 mm, a wall thickness of 0.47 mm, and a total extension of 216 m.
The refrigerant pressure loss was set to about 0.1 kg / cm ² by arranging about 48 smooth pipes having a pipe length of 5 m in parallel, but the outer diameter was 6.35 mm, the wall thickness was 0.47 mm, and the total length was 216m and 6 smooth pipes with a length of 36m per pipe
0.8kg / cm of refrigerant pressure loss
Can be set to about ² .

As described above, in the present embodiment, the heat storage heat exchanger 11 is constructed so as to have a refrigerant pressure loss that cancels the rise in temperature of the non-azeotropic mixed refrigerant in the heat storage heat exchanger 11, and Since the temperature of the refrigerant in the heat exchanger 11 is substantially constant, even if a non-azeotropic mixed refrigerant that changes in temperature during evaporation is used, the wall surface temperature of the heat transfer tube is made uniform by the configuration of the heat storage heat exchanger 11. Thus, uniform ice making in the heat storage tank 10 can be realized.

Embodiment 10 In the ninth embodiment, uniform ice making is realized by making the temperature of the non-azeotropic mixed refrigerant in the heat storage heat exchanger 11 approximately constant, and an efficient ice making operation is realized. The refrigerant pressure loss of the exchanger 11 is set so that the change width of the temperature of the non-azeotropic mixed refrigerant in the heat storage heat exchanger 11 is equal to or less than a predetermined temperature. Particularly, in the ninth embodiment, the refrigerant pressure loss is set such that the change in the temperature of the refrigerant in the heat storage heat exchanger becomes zero by focusing on the heat storage efficiency. However, this setting may reduce the operating efficiency of the refrigeration cycle. There is. Therefore, in the present embodiment, attention is paid not only to the heat storage efficiency but also to the operation efficiency of the refrigeration cycle, so that a change in the temperature of the refrigerant in the heat storage heat exchanger is equal to zero, and the heat storage efficiency is obtained. The refrigerant pressure loss was set so as to be in a range where the reduction could be prevented. here,
Water is used as the heat storage material, and cold heat is stored in the form of ice, and the non-azeotropic refrigerant is operated so as to have a temperature of about -5 ° C. for forming ice. The refrigerant pressure loss of the heat storage heat exchanger 11 is set so that the temperature change width of the non-azeotropic mixed refrigerant is, for example, 3.5 ° C. or less as a predetermined temperature.

FIG. 18 shows a case where water is used as a heat storage material and cold heat is stored in the form of ice, and the temperature of the non-azeotropic refrigerant mixture is set to a temperature for making ice, for example, around -5 ° C. Of the temperature change [° C.] in the heat storage heat exchanger 11 and the average heat transmission rate [kcal] during the ice making operation in the heat storage heat exchanger 11
/ M ² h ° C.] is a graph showing the result obtained by analyzing the relationship. The average heat transfer rate is a value obtained by the following equation, and the fact that the average heat transfer rate is large means that a large amount of heat transfer can be obtained with the same temperature difference and the same heat transfer area, and that the heat transfer efficiency is good. Is shown.

[0089]

(Equation 1)

The temperature change width of the heat storage heat exchanger 11 can be determined by providing a temperature detector at the pipe between the inlet and the outlet of the heat storage heat exchanger 11, and using the temperature detector to detect the temperature of the inlet and the heat storage heat exchanger 11. The temperature of the non-azeotropic mixed refrigerant at the outlet is detected, and the temperature difference is calculated. Instead of measuring the temperature with a temperature detector, a pressure detector may be provided to detect the pressure, and the saturation temperature calculated from the pressure may be used. As shown in FIG. 18, the average heat transmission rate is
When the temperature change width at 1 is larger than 3.5 ° C., the temperature rapidly decreases. However, when the temperature change width in the heat storage heat exchanger 11 is 3.5 ° C. or less, the average heat transfer rate hardly changes, and the temperature change width is 0 ° C., that is, the temperature change of the refrigerant in the heat storage heat exchanger 11. It is almost the same as the average heat transmission rate when uniform ice making can be realized without any problem.

When the temperature of the non-azeotropic mixed refrigerant changes at the inlet and outlet of the heat storage heat exchanger 11, the temperature difference between the solidification temperature of the heat storage material water and the temperature of the refrigerant is large. While the ice grows faster, the ice grows at a point where the temperature difference between the freezing temperature of the water and the temperature of the refrigerant is small. When the temperature change width in the heat storage heat exchanger 11 is larger than 3.5 ° C.,
For example, the refrigerant temperature at the inlet of the heat storage heat exchanger 11 is set to -10.
℃, the refrigerant temperature at the outlet is -5 ℃, the temperature change width is 5
In the case of ° C., the temperature difference between the solidification temperature of water at the inlet and the temperature of the refrigerant is 10 ° C., and 5 ° C. at the outlet. Assuming that the temperature of the refrigerant changes linearly, the temperature change at the inlet with respect to the temperature difference of 10 ° C. and the temperature change at the outlet with respect to the temperature difference of 5 ° C. show that the water at the outlet is more solidified than at the inlet. The rate of change of the temperature difference between the temperature and the temperature of the refrigerant increases. For this reason, the difference in ice thickness between the portion where the ice growth is fast and the portion where the ice growth is slow increases, and an ice-making state having a large degree of unevenness is obtained. Accordingly, bridging occurs where ice generated between the heat transfer tubes fuses early in a portion where ice growth is fast and the ice thickness is large. The effect of the decrease in the heat transfer efficiency due to the bridging increases, the heat transfer efficiency in the heat storage heat exchanger 11 decreases, and the heat storage efficiency in the ice making operation decreases.

On the other hand, when the temperature change width in the heat storage heat exchanger 11 is 3.5 ° C. or less, the degree of variation in the ice thickness generated on the heat transfer tube surface of the heat storage heat exchanger 11 is small and substantially uniform. Therefore, bridging of ice around each heat transfer tube occurs almost simultaneously around each heat transfer tube, and the bridging of the ice in the ice making operation is compared with the case where there is a temperature change width larger than 3.5 ° C. The time to occur is delayed. Therefore, the influence of the decrease in the heat transfer efficiency due to bridging is reduced, the heat transfer efficiency in the heat storage heat exchanger 11 is improved, and an ice making operation with a high heat storage efficiency can be realized.

The temperature of the refrigerant is low at the inlet 11a of the heat storage heat exchanger 11 and at the outlet 11b of the heat storage heat exchanger 11.
In both cases where the temperature change width is the same, the same characteristics are obtained when the temperature change width is the same. The same can be said. That is, when the temperature change width of the refrigerant in the heat storage heat exchanger 11 is 3.5 ° C. or less, an ice making operation with good heat storage efficiency can be realized. FIG.
Uses water as a heat storage material, and the temperature of the non-azeotropic refrigerant mixture is -5.
It is a characteristic in the vicinity of ° C., and it is desirable that the temperature change width of the non-azeotropic refrigerant in the heat storage heat exchanger 11 be 3.5 ° C. or less from the viewpoint of heat storage efficiency. However, when another heat storage material such as ethylene glycol is used, it is necessary to set the temperature of the refrigerant to a temperature suitable for heat storage. Figure 1 shows the relationship between the average heat transmission rates.
8 may be slightly different. However, in that case,
If the temperature exceeds the predetermined temperature, the average heat transmittance tends to decrease significantly.Therefore, the minimum temperature change width at which the average heat transmittance greatly decreases is defined as the predetermined temperature. What is necessary is just to set the refrigerant pressure loss of the vessel 11.

In FIG. 19, when the refrigerant pressure loss [kg / cm ² ] in the heat storage heat exchanger 11 is plotted on the horizontal axis and the refrigerant pressure loss is plotted on the vertical axis, Freon R22 and Freon R407 are used as refrigerants.
6 is a graph showing a temperature change (outlet temperature−inlet temperature) [° C.] in the heat storage heat exchanger 11 when C is used. here,
This characteristic is such that the temperature of the refrigerant is around −5 ° C., which is the temperature of the refrigerant when heat is stored in the form of ice using the heat storage material as water. From FIG. 19, when Freon R407C is used as the refrigerant, the refrigerant pressure loss in the heat storage heat exchanger 11 is 0.25 k
When it is set to g / cm ² or more, the temperature change width in the heat storage heat exchanger 11 can be set to 3.5 ° C. or less. Also, even if the refrigerant pressure loss in the heat storage heat exchanger 11 is larger than 0.6 kg / cm ² , the temperature change width of the refrigerant in the heat storage heat exchanger 11 becomes 3.5 ° C. or less, and ice making with good heat storage efficiency The operation can be realized, but if the refrigerant pressure loss is too large, the efficiency of the refrigeration cycle during the ice making operation decreases, which is not preferable.

Here, a refrigeration / air-conditioning apparatus that can improve the efficiency of heat storage in the heat storage tank 10 and the operating efficiency of the refrigeration cycle will be described. At this time, as the refrigerant, for example, R407C which is a non-azeotropic mixed refrigerant is used. FIG. 20 shows the refrigerant pressure loss [k in the heat storage heat exchanger 11 on the horizontal axis.
g / cm ² ], and the vertical axis shows the operating efficiency of the refrigeration cycle when the pressure loss is present. In FIG. 20, the average heat transmittance in the heat storage heat exchanger 11 is a constant value, and the change in the average heat transmittance due to the above-described pressure loss is not taken into account. In general, the operating efficiency of the refrigeration / air-conditioning apparatus is improved as the operating efficiency of the compressor, which is a heat source device, is improved. The compression ratio in the compressor increases.
When the compression ratio increases, the operating efficiency of the compressor decreases, and the operating efficiency of the refrigeration cycle constituting the refrigeration air conditioner also decreases. Therefore, when operating the refrigeration cycle, it is desirable that the refrigerant pressure loss in the heat storage heat exchanger 11 be as small as possible in consideration of the operating efficiency of the compressor. As shown in FIG. 20, as compared with the operation efficiency of the refrigeration cycle when the refrigerant pressure loss in the heat storage heat exchanger 11 is 0, the operation efficiency is approximately 5% when the refrigerant pressure loss is approximately 0.6 kg / cm ^2. Is declining. That is, in order to suppress the decrease in the operating efficiency of the refrigeration cycle to a predetermined value, for example, 5%, 0.6 kg / cm
^The heat storage heat exchanger 11 has a refrigerant pressure loss of ² or less.
It is desirable to configure However, the predetermined value indicating the allowable degree of the decrease in the operating efficiency may be set according to the usage status of the refrigeration and air conditioning system. In order to further improve the operation efficiency of the refrigeration cycle, the decrease in the operation efficiency is set to about 3%, and the refrigerant pressure loss of the heat storage heat exchanger 11 is set to 0.6 kg.
It may be less 0.4 kg / cm ² than / cm ^2. Further, when the operation efficiency of the refrigeration cycle is not given much importance, the decrease in the operation efficiency is set to about 8%, and the refrigerant pressure loss of the heat storage heat exchanger 11 is set to 0.1% which is larger than 0.6 kg / cm ² . It may be 7 kg / cm ² .

In FIG. 21, the horizontal axis indicates the refrigerant pressure loss [kg / cm ² ] in the heat storage heat exchanger 11, and the vertical axis indicates the heat passage rate of the heat storage heat exchanger 11 when the refrigerant pressure loss is present. It is a characteristic diagram. As described above, when the temperature change width in the heat storage heat exchanger 11 is equal to or less than 3.5 ° C., the operation with high heat transfer efficiency in the heat storage heat exchanger 11 can be realized. Therefore, considering heat transfer efficiency in the heat storage heat exchanger 11, it is preferable that the refrigerant pressure loss in the heat storage heat exchanger 11 be 0.25 kg / cm ² or more.

FIG. 22 is a characteristic diagram showing the refrigerant pressure loss [kg / cm ² ] in the heat storage heat exchanger 11 on the horizontal axis and the operating efficiency of the refrigeration cycle on the vertical axis. The operation efficiency of the refrigeration cycle at this time is based on FIG. 20 and FIG.
1 in consideration of the change in the average heat transmittance.
Assuming that the decrease in the operating efficiency of the refrigeration cycle is 5%, from the characteristic curve shown in FIG. 22, the refrigerant pressure loss of the heat storage heat exchanger 11 is 0.25 kg / cm ² or more and 0.6 kg / cm 2.
It is preferably set to ² or less.

Hereinafter, the refrigerant pressure loss is set to 0.25 kg / cm
A configuration in which the value is set to ² or more and 0.6 kg / cm ² or less will be specifically described. To increase the refrigerant pressure loss, for example, reducing the diameter of the heat transfer tubes constituting the heat storage heat exchanger 11, reducing the number of heat transfer tubes connected in parallel, increasing the length of the heat transfer tubes, The heat transfer tube may be an inner grooved tube instead of a smooth tube, or a throttle may be provided in the middle of the heat transfer tube. For example, the refrigeration capacity during the ice making operation is 6400 kcal.
/ H, when the heat transfer tubes of the heat storage heat exchanger 11 are constituted by smooth tubes having an outer diameter of 6.35 mm, a wall thickness of 0.47 mm, and a total length of 216 m, each tube has 11.4 m.
The refrigerant pressure loss can be set to about 0.25 kg / cm ² by arranging about 19 smooth pipes of the same length in parallel, and the refrigerant can be set by arranging about 6 smooth pipes of 36 m per pipe in parallel. Pressure loss can be set to about 0.6 kg / cm ² . In order to reduce the refrigerant pressure loss during this period, use a smooth tube with a length between 11.4 m and 36 m per tube, and arrange the number of tubes so that the total length is 216 m. May be configured.

[0099] Further, by using an internally grooved tube rather than a smooth tube as a heat transfer tube, specifically showing the configuration set to about 0.6 kg / cm ² refrigerant pressure loss from 0.25 kg / cm ^2. For example, the refrigeration capacity during the ice making operation is 6400 kcal.
/ H, when the heat transfer tubes of the heat storage heat exchanger 11 are constituted by grooved tubes having an outer diameter of 6.35 mm, a wall thickness of 0.47 mm, and a total length of 172 m, each tube length is 9.1 m. The refrigerant pressure loss can be set to about 0.25 kg / cm ² by arranging about 19 grooved pipes in parallel, and about 7 grooved pipes with a pipe length of 24.6 m per pipe can be set. Thus, the refrigerant pressure loss can be set to about 0.6 kg / cm ² .
In addition, in order to reduce the refrigerant pressure loss during this period, use a tube with an inner surface groove having a length between 9.1 m and 24.6 m per tube, and set the number of tubes such that the total extension becomes 172 m. What is necessary is just to arrange in parallel.

Further, the number of heat transfer tubes connected in parallel to the heat transfer tubes constituting the heat storage heat exchanger 11 can be reduced, the length of the heat transfer tubes can be increased, or the heat transfer tubes can be formed into inner grooved tubes instead of smooth tubes. However, the present invention is not limited to setting the refrigerant pressure loss, and the refrigerant pressure loss may be set by another configuration.
For example, the refrigerant pressure loss can be set to be large by reducing the diameter of the heat transfer tube or reducing the diameter in the middle of the heat transfer tube.

As described above, in the present embodiment, the heat storage heat exchanger 11 is controlled so that the non-azeotropic mixed refrigerant has a refrigerant pressure loss such that the temperature change width in the heat storage heat exchanger 11 becomes equal to or less than the predetermined temperature. With this configuration, even if a non-azeotropic refrigerant mixture that changes in temperature during evaporation is used, the heat storage heat exchanger 11 realizes substantially uniform ice making with a small degree of variation in ice thickness generated on the heat transfer tube surface. It is possible to realize an ice making operation with good heat storage efficiency.

Embodiment 11 FIG. In the tenth embodiment, one non-azeotropic mixed refrigerant is used as the heat transfer medium, and the temperature change width of the non-azeotropic mixed refrigerant in the heat storage heat exchanger 11 is set to a predetermined temperature or less, so that the heat storage efficiency is improved. Realizing ice making operation,
Further, the refrigerant pressure loss of the heat storage heat exchanger 11 is reduced to 0.6 k.
By controlling the refrigeration cycle to not more than g / cm ² , a decrease in the operation efficiency of the refrigeration cycle was prevented. In the present embodiment, at least one
Heat in the heat storage heat exchanger 11 with respect to one non-azeotropic mixed refrigerant and one or more of the single refrigerant, the azeotropic refrigerant, and the non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant. The heat storage heat exchanger 11 is configured such that the change width of the temperature of the transmission medium is equal to or less than a predetermined temperature.

At present, Freon R22, which is a single refrigerant, is used in many refrigeration and air conditioning systems having a heat storage function.
However, Freon R22 has a high ozone depletion potential, and the Montreal Protocol concluded in 1992 stipulates that Freon R22 be completely abolished in 2020 to protect the ozone layer. Therefore, a refrigeration / air-conditioning apparatus having a heat storage function that currently uses Freon R22 is required to change the heat transfer medium used by 2020 at the latest.
At that time, it is considered that the heat transfer medium is frequently changed to Freon R407C, which is a non-azeotropic refrigerant having similar thermodynamic properties and does not destroy the ozone layer. At the time of this change, a retrofit in which only the change of the heat transfer medium is performed while the refrigeration air conditioner is kept as it is is more preferable in terms of cost than a new refrigeration air conditioner corresponding to the change of the heat transfer medium. . When retrofitting is performed, the operation using both of the two heat transfer media, for example, Freon R22 and Freon R407C, is performed without changing the configuration of the refrigeration / air-conditioning apparatus. Is required to be able to operate efficiently with either heat transfer medium. Furthermore, it is very effective to configure a refrigeration / air-conditioning apparatus that can efficiently operate all the heat transfer media that can be used in advance.

Today, as shown in FIG. 23, a refrigeration and air-conditioning system that uses a single refrigerant, Freon R22, as a refrigerant and does not have a heat storage function composed of an outdoor unit 30 and an indoor unit 31 is newly provided. A refrigeration and air-conditioning system having a heat storage function by adding a unit 32 is often used. In such a case, the operation of the refrigerating air conditioner is currently performed using, for example, Freon R22, and the heat storage operation such as the ice making operation is also performed using Freon R22. However, by 2020, the refrigerant was changed to Freon R407C, which is a non-azeotropic mixed refrigerant, and after retrofitting, the operation of the refrigeration and air-conditioning system including the heat storage operation such as ice making operation was performed using Freon R407C. Will be done. Therefore, in the heat storage heat exchanger 11 in the newly added heat storage unit 32, it is possible to efficiently perform the heat storage operation using either the single refrigerant Freon R22 or the non-azeotropic refrigerant mixture Freon R407C as the refrigerant. Desired.

In the present embodiment, in both Freon R22, which is a single refrigerant, and Freon R407C, which is a non-azeotropic refrigerant mixture, the temperature change width of the heat storage heat exchanger 11 is a predetermined temperature, for example, 3.5 ° C. or less. Heat storage heat exchanger 11
Set the refrigerant pressure loss at. The graph showing the relationship between the refrigerant pressure loss [kg / cm ² ] in the heat storage heat exchanger 11 and the temperature change [° C.] (outlet temperature−inlet temperature) in the heat storage heat exchanger 11 shown in FIG. The relationship between Freon R22, which is one refrigerant, and Freon R407C, which is a non-azeotropic mixed refrigerant, is shown. As described in the tenth embodiment, Freon R
The refrigerant pressure loss in the heat storage heat exchanger 11 when using 407C is 0.25 kg / cm ² or more and 0.6 kg / cm ²
If you set so that the cm ² or less, freon R407C
The temperature change width in the heat storage heat exchanger 11 when using
° C or less, and an ice making operation with good heat storage efficiency can be performed. On the other hand, when the refrigerant pressure loss in the heat storage heat exchanger 11 when using Freon R22 is set to be 0.5 kg / cm ² or less, the temperature in the heat storage heat exchanger 11 when using Freon R22 is used. The change width becomes 3.5 ° C or less,
It becomes possible to perform an ice making operation with good heat storage efficiency. That is, in order to make the temperature change width in the heat storage heat exchanger 11 3.5 ° C. or less in both Freon R22 and Freon R407C, the refrigerant pressure loss in the heat storage heat exchanger 11 is 0.25
It is preferable to set the pressure to not less than kg / cm ^{2 and not} more than 0.5 kg / cm ² . When the refrigerant pressure loss of the heat storage heat exchanger 11 is set as described above, the temperature change width of the heat storage heat exchanger 11 is 3.times. For both Freon R22 and Freon R407C.
The temperature is 5 ° C. or less, and the ice making operation can be performed with high heat storage efficiency using either Freon R22 or Freon R407C. When the refrigerant pressure loss of the heat storage heat exchanger 11 is set within this range, the operation efficiency of the refrigeration cycle can be maintained in a good state as shown in FIG.

The refrigerant pressure loss of the heat storage heat exchanger 11 is 0.2
A configuration in which the pressure is set to 5 kg / cm ² or more and 0.5 kg / cm ² or less will be specifically described. For example, in a refrigerating air conditioner having a refrigerating capacity of 6400 kcal / h during an ice making operation, an outer diameter is 6.35 mm, a wall thickness is 0.47 mm, and a total extension is 21 mm.
When a smooth pipe of 6 m is used, the refrigerant pressure loss can be set to about 0.25 kg / cm ² by arranging about 19 smooth pipes each having a pipe length of 11.4 m, so that 21 pipes per pipe can be used. By arranging about 10 smooth pipes having a pipe length of 0.6 m in parallel, the refrigerant pressure loss can be set to about 0.5 kg / cm ² . Also, if the refrigerant pressure loss during that period is attempted,
What is necessary is just to use a smooth tube with a length between 11.4 m and 21.6 m, and to arrange the number of tubes so that the total length is 216 m. Further, the refrigerant pressure loss may be set to be large by using an inner grooved tube, reducing the diameter of the heat transfer tube, or providing a restriction in the middle of the heat transfer tube.

In the above description, the case where Freon R407C is used as the non-azeotropic mixed refrigerant and Freon R22 is used as the single refrigerant and the refrigerant is changed from Freon R22 to Freon R407C, but the present invention is not limited to this.
At least two refrigerants, at least one of the refrigerants is a non-azeotropic mixed refrigerant, and the other refrigerant is a single refrigerant or an azeotropic refrigerant or a non-azeotropic mixed refrigerant different from one refrigerant,
With respect to those refrigerants, if the configuration has a refrigerant pressure loss of the heat storage heat exchanger 11 so that the temperature change width of the refrigerant at the inlet part and the outlet part in the heat storage heat exchanger 11 becomes a predetermined value or less. Good. For example, Freon R404A or another non-azeotropic mixed refrigerant may be used as one non-azeotropic mixed refrigerant of the two refrigerants. Further, from the viewpoint of preventing global warming, a non-azeotropic mixed refrigerant using a natural refrigerant such as propane, butane, ammonia, or carbon dioxide may be used as the non-azeotropic mixed refrigerant.
Further, as the other refrigerant of the two refrigerants, that is, a single refrigerant or an azeotropic refrigerant or a non-azeotropic mixed refrigerant different from the one non-azeotropic mixed refrigerant, for example, Freon R123, propane or butane, ammonia, carbon dioxide gas, or the like Natural refrigerant (single refrigerant), non-azeotropic mixed refrigerant using natural refrigerant, Freon R4
10A (azeotropic refrigerant), Freon R404A (non-azeotropic refrigerant mixture) and the like may be used. In the above description, a single refrigerant, Freon R22, is replaced by a non-azeotropic refrigerant, Freon R40.
Although the case where the refrigerant is changed to 7C has been described, the refrigerant is changed from a non-azeotropic mixed refrigerant to a single refrigerant or an azeotropic refrigerant or a non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant, or vice versa. Is changed, the temperature change width of the refrigerant at the inlet and the outlet at the heat storage heat exchanger 11 becomes smaller than or equal to a predetermined value for both the refrigerant before the change and the refrigerant after the change. The heat storage heat exchanger 11 may be configured to have a refrigerant pressure loss. In particular, from the viewpoint of preventing global warming, CFC R407C (non-azeotropic mixed refrigerant), which has a strong global warming effect, is a single refrigerant, and has a low global warming effect, such as propane, butane, ammonia, and carbon dioxide. This embodiment is effective when changing to a refrigerant.

Also, not only for the two refrigerants,
With respect to a plurality of refrigerants that will be used in the future, the heat storage heat so as to have a refrigerant pressure loss such that the temperature change width of the refrigerant at the inlet and the outlet in the heat storage heat exchanger 11 becomes a predetermined value or less. If the exchanger 11 is configured, it is possible to quickly respond to the change of the refrigerant, always provide good heat storage efficiency, select the refrigerant, and obtain a versatile refrigeration / air-conditioning apparatus.

Next, for example, a heat storage heat exchanger for implementing a retrofit in which the refrigerant is changed between two refrigerants, a single refrigerant, or an azeotropic refrigerant and a non-azeotropic mixed refrigerant on the way. The method for setting the optimum refrigerant pressure loss within the setting range of the refrigerant pressure loss will be described. For example, Freon R407C as a non-azeotropic mixed refrigerant and R as a single refrigerant
Assuming that the cooling medium 22 is used, the refrigerant pressure loss in the heat storage heat exchanger 11 during the heat storage operation must be 0.4 kg / cm ² in order to realize an ice making operation with good heat storage efficiency when both refrigerants are used.
What is necessary is just to set so that it is about. Hereinafter, the operation when the refrigerant pressure loss in the heat storage heat exchanger 11 is set to 0.4 kg / cm ² will be described. 24, 25 and 26 show that the refrigerant pressure loss in the heat storage heat exchanger 11 is 0 kg / cm ² ,
0.8 kg / cm ^2, when set to be 0.4 kg / cm ^2, Freon R2 as a refrigerant for the refrigeration air conditioning system
2. Heat storage heat exchanger 11 using Freon R407C
In each graph, the horizontal axis indicates the position in the heat storage heat exchanger, 11a indicates the inlet, and 11b indicates the outlet. The vertical axis indicates the temperature.

The refrigerant pressure loss in the heat storage heat exchanger 11 is 0 k
When g / cm ² , as shown in FIG. 24, when Freon R22 is used as the refrigerant, there is no temperature change in the heat storage heat exchanger 11, and the ice thickness generated on the heat transfer tube surface becomes uniform, so that efficient ice making is achieved. You can drive. Conversely, the refrigerant is Freon R4
When 07C is used, the temperature change width in the heat storage heat exchanger 11 is as large as 5 ° C., and ice is thicker in a low temperature portion and thin in a high temperature portion. Become uneven and bridging occurs early.
Therefore, the effect of the decrease in the heat transfer efficiency due to bridging increases, the heat transfer efficiency in the heat storage heat exchanger 11 decreases, and the efficiency of the ice making operation decreases.

The refrigerant pressure loss in the heat storage heat exchanger 11 is 0.
When the pressure is 8 kg / cm ² , as shown in FIG. 25, when Freon R407C is used as the refrigerant, the heat storage heat exchanger 1
1, there is almost no temperature change, the ice thickness generated on the heat transfer tube surface becomes uniform, and an efficient ice making operation can be performed. Conversely, when Freon R22 is used as the refrigerant, the heat storage heat exchanger 11
The temperature change width becomes large at about 5.5 ° C, the ice becomes thicker in the low temperature part, and the ice becomes thinner in the high temperature part. Causes bridging. Therefore, the effect of the decrease in the heat transfer efficiency due to bridging increases, the heat transfer efficiency in the heat storage heat exchanger 11 decreases, and the efficiency of the ice making operation decreases.

The refrigerant pressure loss in the heat storage heat exchanger 11 is 0.
When the pressure is 4 kg / cm ² , the temperature change width is about 2.5 ° C. regardless of whether Freon R22 or Freon R407C is used as the refrigerant as shown in FIG. In this case, Freon R
The temperature change width in the heat storage heat exchanger 11 is smaller than 3.5 ° C. in any of 407C and Freon R22, and both Freon R22 and Freon R407C are used as refrigerants.
The ice thickness generated on the surface of the heat transfer tube becomes substantially uniform, and an efficient ice making operation can be performed. As described above, when two refrigerants are used, the inlet 11a and the outlet 1 of the heat storage heat exchanger 11 are used.
If the refrigerant has a refrigerant pressure loss such that the temperature difference from the refrigerant 1b is substantially the same between the two refrigerants, the heat storage efficiencies when both refrigerants are used can be made substantially the same, and an optimal refrigeration / air-conditioning apparatus can be configured. be able to.

As described above, in the present embodiment, the variation range of the temperature of the non-azeotropic mixed refrigerant in the heat storage heat exchanger 11 becomes equal to or less than the predetermined temperature, and the single refrigerant, the azeotropic refrigerant, or the non-azeotropic refrigerant. When any one of the non-azeotropic mixed refrigerants different from the azeotropic mixed refrigerant is used, a change in the temperature of the refrigerant in the heat storage heat exchanger 11 has a refrigerant pressure loss such that the change width is equal to or less than a predetermined temperature. The heat storage heat exchanger 11 was configured. With this configuration, as a retrofit of the refrigerant, when the refrigerant is switched from a single refrigerant or an azeotropic refrigerant or a non-azeotropic mixed refrigerant to a non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant, or When the refrigerant is switched from an azeotropic mixed refrigerant to one of a single refrigerant or an azeotropic refrigerant or a non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant, a non-azeotropic mixed refrigerant is used in both cases. In the operation and the operation using either a single refrigerant or an azeotropic refrigerant or a non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant, the ice thickness generated on the heat transfer tube surface in each operation. An almost uniform ice making with a small degree of variation can be realized, and an ice making operation with good heat storage efficiency can be realized.

Embodiment 12 FIG. In the tenth embodiment, the refrigerant pressure loss of the heat storage heat exchanger 11 is set such that the variation width of the temperature of the non-azeotropic mixed refrigerant in the heat storage heat exchanger 11 is equal to or less than a predetermined temperature, thereby improving heat storage efficiency. Ice making operation was realized. In the present embodiment, at the inlet and outlet of the heat storage heat exchanger, the temperature difference between the temperature of the heat storage material and the temperature of the non-azeotropic mixed refrigerant is calculated, and the ratio of the inlet temperature difference and the outlet temperature difference is calculated. Is set to a predetermined range. Here, it is assumed that water is used as the heat storage material, and cold heat is stored in an ice state using the latent heat of melting of water. The temperature of the heat storage material at the inlet and outlet of the heat storage heat exchanger is calculated based on the solidification temperature (0 ° C.). In addition, Freon R407C is used as the non-azeotropic mixed refrigerant.

FIG. 27 is a graph for explaining the temperature change with respect to the position in the heat storage heat exchanger 11 when a non-azeotropic mixed refrigerant is used as the heat transfer medium. The horizontal axis indicates the position in the heat storage heat exchanger 11, The vertical axis shows the temperature, and also shows the solidification temperature of water (0 ° C.). As shown in this graph, the heat storage heat exchanger 1
1 changes in the temperature of the non-azeotropic mixed refrigerant in the heat storage heat exchanger 11.
Due to the refrigerant pressure loss occurring in the above, the pressure increases monotonically when the pressure loss is small, or monotonically decreases when the pressure loss is large. Therefore, when the temperature difference between the solidification temperature of water (0 ° C.) and the temperature of the non-azeotropic mixed refrigerant at the inlet 11 a and the outlet 11 b of the heat storage heat exchanger 11 is obtained, the difference between the inlet temperature and the outlet temperature is obtained. One of them is the maximum value of the difference between the freezing temperature of water (0 ° C) and the non-azeotropic mixed refrigerant, and the other is the minimum value of the difference between the freezing temperature of water (0 ° C) and the non-azeotropic mixed refrigerant. Becomes Assuming that the maximum value of the difference between the freezing temperature of water (0 ° C.) and the non-azeotropic mixed refrigerant is ΔTmax, and the minimum value of the difference between the freezing temperature of water (0 ° C.) and the non-azeotropic mixed refrigerant is ΔTmin, this embodiment In the embodiment, the refrigerant pressure loss of the heat storage heat exchanger 11 is set so that ΔTmin / ΔTmax> 0.5.

FIG. 28 shows a case in which water is used as a heat storage material and cold heat is stored in the form of ice, and the temperature of the non-azeotropic mixed refrigerant is set to a temperature for forming ice, for example, around -7 ° C. 6 is a graph showing the results obtained by analyzing the relationship between ΔTmin / ΔTmax and the average heat transmission rate [kcal / m ² h ° C.] during the ice making operation in the heat storage heat exchanger 11 at the time of the above. This property is
Even if the type of refrigerant and the temperature of the refrigerant when storing heat change,
It shows almost the same relationship. As shown in FIG. 28, the average heat transmittance rapidly decreases when ΔTmin / ΔTmax ≦ 0.5, while the average heat transmittance when ΔTmin / ΔTmax> 0.5 is ΔTmin = ΔTmax, that is, The average heat transmission rate when the temperature of the refrigerant in the heat storage heat exchanger 11 is the same and uniform ice making can be realized. ΔT
When min / ΔTmax ≦ 0.5, ice growth at a point where the temperature difference between the water coagulation temperature and the refrigerant becomes maximum (a point where the temperature difference becomes ΔTmax) is accelerated, while water coagulation is accelerated. The point where the temperature difference between the temperature and the refrigerant becomes minimum (the temperature difference is ΔTmin
Ice growth slows down. In addition, since the rate of change in the temperature difference between the solidification temperature of water (0 ° C.) and the refrigerant near the point where the temperature difference becomes ΔTmin increases, the difference between the portion where the ice growth is fast and the portion where the ice growth is slow is large. And an ice-making state with a high degree of non-uniformity. Therefore, in a portion where the ice growth is fast and the ice thickness is large, the ice generated between the heat transfer tubes causes bridging at an early stage, and the influence of the decrease in the heat transfer efficiency due to the bridging becomes large, and the heat storage heat exchanger 11 The heat transfer efficiency decreases, and the heat storage efficiency of the ice making operation decreases.

On the other hand, when ΔTmin / ΔTmax> 0.5, the rate of change of the temperature difference between the solidification temperature of water (0 ° C.) and the refrigerant becomes smaller, and therefore the surface of the heat transfer tube of the heat storage heat exchanger 11 is changed. The degree of variation in the ice thickness generated is small and ice is made almost uniformly, so the bridging of ice around each heat transfer tube occurs almost simultaneously around each heat transfer tube, and the time when bridging occurs in the ice making operation Slows down. Therefore, the influence of the decrease in heat transfer efficiency due to bridging is reduced, the heat transfer efficiency in the heat storage heat exchanger 11 is improved, and an ice making operation with high heat storage efficiency can be realized.

As a heat transfer medium, for example, Freon R407
C, when water is used as the heat storage material, the inlet temperature of Freon R407C in the heat storage operation is, for example, about −7 ° C. When the refrigerant inlet temperature in the heat storage heat exchanger 11 is −7 ° C., the maximum value of the temperature difference between the freezing temperature of water (0 ° C.) and the non-azeotropic mixed refrigerant is ΔTmax, and the freezing temperature of water (0 ° C.) The minimum value of the temperature difference of the non-azeotropic mixed refrigerant is ΔTmin, and ΔTmin / Δ
In order to make Tmax> 0.5, the refrigerant outlet temperature in the heat storage heat exchanger 11 only needs to be −14 ° C. <refrigerant outlet temperature <−3.5 ° C. In order to set the refrigerant outlet temperature in this manner, the refrigerant temperature change in the heat storage heat exchanger 11 (the outlet temperature-
−7 ° C. <change in refrigerant temperature in the heat storage heat exchanger 11 <+3.5
The temperature may be set so as to be ℃. According to FIG. 19, in order to cause such a change in the refrigerant temperature in the heat storage heat exchanger 11, the refrigerant pressure loss in the heat storage heat exchanger 11 must be 0.25 kg.
It can be seen that the setting should be larger than / cm ² . The refrigerant pressure loss in the heat storage heat exchanger 11 is 0.6 kg / cm.
Even if it is larger than ^two , if the change in the refrigerant temperature in the heat storage heat exchanger 11 is within a range higher than −7 ° C.,
However, if the refrigerant pressure loss is too large, the operation efficiency of the refrigeration cycle during the ice making operation decreases, which is not preferable. Therefore, when Freon R407C is used, the refrigerant pressure loss in the heat storage heat exchanger 11 is reduced by a temperature change of 3.5 ° C. in the heat storage heat exchanger 11.
By setting the temperature to be greater than 0.25 kg / cm ² and 0.6 kg / cm ² or less, the temperature change in the heat storage heat exchanger 11 becomes substantially equal to 0 ° C., and the operating efficiency of the refrigeration cycle Can also be maintained well. Refrigerant pressure loss greater than 0.25 kg / cm ² and 0.6 kg
The specific configuration of the heat storage and heat exchange 11 for setting the temperature to / cm ² or less is the same as that of the tenth embodiment.

As described above, in the present embodiment, the maximum value of the difference between the freezing temperature of water (0 ° C.) and the temperature of the non-azeotropic mixed refrigerant is ΔT
max, and ΔTmin is the minimum value of the temperature difference between the freezing temperature of water (0 ° C.) and the non-azeotropic refrigerant mixture, ΔTmin / ΔTmax>
Since the heat storage heat exchanger 11 is configured to have the refrigerant pressure loss of the heat storage heat exchanger 11 so as to be 0.5, the heat storage heat exchanger can be used even if a non-azeotropic mixed refrigerant that changes in temperature during evaporation is used. According to the configuration of No. 11, it is possible to realize substantially uniform ice making with a small degree of variation in ice thickness generated on the heat transfer tube surface, and to realize an efficient ice making operation.

In the above description, the heat storage heat exchanger 11
The temperature of the heat storage material at the inlet and outlet of the
° C), but the temperature of water in the heat storage tank 10 near the inlet and the outlet of the heat storage heat exchanger 10 may be measured and used. In particular, when a mixed solution of water and ethylene glycol is used as the heat storage material, the coagulation temperature changes depending on the concentration of the mixed solution. It is more preferable to measure and use the temperature difference between the measured temperature of the heat storage material and the temperature of the heat transfer medium. Also in this case, the refrigerant pressure loss of the heat storage heat exchanger 11 may be set using the calculated temperature difference so that the ratio between the inlet temperature difference and the outlet temperature difference is within a predetermined range.

Further, in the above description, the case where cold heat is stored in the heat storage tank, and when hot heat is stored, numerical values such as temperature are different. However, the temperature difference between the solidification temperature of the heat storage material at the inlet of the heat storage heat exchanger and the refrigerant temperature is defined as the inlet temperature difference, and the temperature between the solidification temperature of the heat storage material at the outlet of the heat storage heat exchanger and the refrigerant temperature. If the difference is the outlet temperature difference, if the ratio of the inlet temperature difference and the outlet temperature difference is set to have a refrigerant pressure loss of the heat storage heat exchanger so as to be within a predetermined range, even when storing cold heat Even when storing heat, a heat storage heat exchanger having good heat storage efficiency can be obtained. In addition, depending on the arrangement of the heat transfer tubes of the heat storage heat exchanger 11, the relationship between the ratio of the temperature difference between the inlet portion and the outlet portion of the heat storage heat exchanger 11 to the average heat transmittance of the heat storage heat exchanger 11 is shown in FIG. May be slightly different. For example, when the interval between the heat transfer tubes at the inlet portion is sparse and the interval between the heat transfer tubes at the outlet portion is dense, the ratio of the temperature difference between the inlet portion and the outlet portion is less than 0.5. Bridging at the entrance does not occur even if it is small. However, even in such a case, the average heat transmission rate becomes substantially constant in a predetermined range of the ratio, and tends to decrease greatly outside the predetermined range. Therefore, the refrigerant pressure loss of the heat storage heat exchanger 11 must be set so as to be in the predetermined range. I just need.

Embodiment 13 FIG. In the twelfth embodiment, the efficiency of the heat storage operation can be improved by setting the ratio of the inlet temperature difference and the outlet temperature difference to a predetermined range for one non-azeotropic mixed refrigerant as the heat transfer medium. In the present embodiment, at least one non-azeotropic mixed refrigerant is targeted, and one or more of a single refrigerant, an azeotropic refrigerant, and a non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant described above. The heat storage heat exchanger 11 was also configured such that the ratio of the inlet temperature difference and the outlet temperature difference of the heat storage heat exchanger 11 was within a predetermined range for the heat transfer medium described above. Thus, it is possible to obtain a refrigeration / air-conditioning apparatus capable of improving the efficiency of the heat storage operation for a plurality of heat transfer media and responding to the change of the heat transfer media. Here, as in Embodiment 12, water is used as the heat storage material, and the solidification temperature of water (0 ° C.) is used as the inlet temperature and the outlet temperature of the heat storage material. Solidification temperature of water (0
° C) and the used refrigerant, ΔTmax, and the minimum value of the temperature difference between the freezing temperature of water (0 ° C) and the used refrigerant is ΔTmin, ΔTmin / ΔTmax> 0.5. The refrigerant pressure loss of the heat storage heat exchanger 11 is set as described above. The used refrigerant is at least two refrigerants,
One is a non-azeotropic refrigerant mixture, the other is a single refrigerant,
Either an azeotropic refrigerant or a non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant. The refrigerant pressure loss of the heat storage heat exchanger 11 is set so that the above relationship is established for the at least two refrigerants.

For example, as a non-azeotropic refrigerant, Freon R4
07C, a single refrigerant, an azeotropic refrigerant, when using a non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant, Freon R22 which is a single refrigerant, the ice making operation using Freon R407C. The refrigerant temperature at the inlet of the heat storage heat exchanger 11 is, for example, −7 ° C., and the refrigerant temperature at the inlet of the heat storage heat exchanger 11 is, for example, −3.5 ° C. when the ice making operation is performed using Freon R22. In some cases CFC R407
C, the temperature change (outlet temperature−inlet temperature) in the heat storage heat exchanger 11 is smaller than 3.5 ° C., and CFC R22
The refrigerant pressure loss in the heat storage heat exchanger 11 is set so that the change in temperature (outlet temperature-inlet temperature) in the heat storage heat exchanger 11 when using is larger than -3.5 ° C. By setting the refrigerant pressure loss in this way, the solidification temperature of water (0 ° C.)
When the maximum value of the temperature difference between the refrigerant and the refrigerant used is ΔTmax, and the minimum value of the temperature difference between the solidification temperature of water (0 ° C.) and the refrigerant used is ΔTmin, in both Freon R22 and Freon R407C, 0.5 <ΔTmin / ΔTmax. The relationship is satisfied. When this relationship is satisfied as described in the twelfth embodiment, the heat storage operation can be efficiently performed using either Freon R22 or Freon R407C. Therefore, even if the retrofit is performed to switch from Freon R22 to Freon R407C, efficient heat storage operation can be performed in operation using either Freon R22 or Freon R407C.

The temperature change (outlet temperature−inlet temperature) in the heat storage heat exchanger 11 when using Freon R22 and Freon R407C is larger than the predetermined temperature (above −3.5 ° C. for Freon R22). 3.5 for Freon R407C
In this case, the refrigerant pressure loss in the heat storage heat exchanger 11 may be set based on FIG. The refrigerant pressure loss in the heat storage heat exchanger 11 shown in FIG.
From the relationship of the temperature change in the heat storage heat exchanger 11 when using 07C, the refrigerant pressure loss in the heat storage
If it is set to be larger than 5 kg / cm ² and smaller than 0.5 kg / cm ² , the temperature change (outlet temperature−inlet temperature) in the heat storage heat exchanger 11 when Freon R407C is used is reduced from 3.5 ° C. The temperature change (outlet temperature−inlet temperature) in the heat storage heat exchanger 11 when using Freon R22 can be made larger than −3.5 ° C., and the heat storage operation can be efficiently performed using either Freon R22 or Freon R407C. Can be performed. When the refrigerant pressure loss of the heat storage heat exchanger 11 is set within this range, the operation efficiency of the refrigeration cycle can be maintained in a good state as shown in FIG.

The pressure loss of the refrigerant in the heat storage heat exchanger 11 is set to 0.2
A configuration that is set to be larger than 5 kg / cm ² and smaller than 0.5 kg / cm ² will be specifically described. For example, in a refrigeration / air-conditioning apparatus having a refrigeration capacity of 6400 kcal / h during the ice making operation, when each of the refrigeration and air-conditioning units is constituted by a smooth tube having an outer diameter of 6.35 mm, a wall thickness of 0.47 mm, and a total length of 216 m, each tube has 11.1 mm.
By arranging about 19 smooth pipes each having a pipe length of 4 m, the refrigerant pressure loss can be set to about 0.25 kg / cm ^2.
By arranging about 10 smooth pipes having a pipe length of 21.6 m per pipe, the refrigerant pressure loss can be set to about 0.5 kg / cm ² . In order to reduce the refrigerant pressure loss during that time, use a smooth pipe with a length between 11.4m and 21.6m per pipe, and arrange a number of pipes so that the total length is 216m. What is necessary is just to comprise. Further, the refrigerant pressure loss may be set to be large by using an inner grooved tube, reducing the diameter of the heat transfer tube, or providing a restriction in the middle of the heat transfer tube.

In the above description, the case where Freon R407C is used as the non-azeotropic mixed refrigerant, Freon R22 is used as the single refrigerant, and the refrigerant is changed from Freon R22 to Freon R407C, but the present invention is not limited to this.
At least two refrigerants, at least one of the refrigerants is a non-azeotropic mixed refrigerant, and the other refrigerant is a single refrigerant or an azeotropic refrigerant or a non-azeotropic mixed refrigerant different from one refrigerant,
The heat storage heat exchanger 11 may be configured to have a refrigerant pressure loss such that the ratio between the inlet temperature difference and the outlet temperature difference in the heat storage heat exchanger 11 falls within a predetermined range. For example, Freon R404A or another non-azeotropic mixed refrigerant may be used as one non-azeotropic mixed refrigerant of the two refrigerants. Further, from the viewpoint of preventing global warming, a non-azeotropic mixed refrigerant using a natural refrigerant such as propane, butane, ammonia, or carbon dioxide may be used as the non-azeotropic mixed refrigerant. Further, as the other refrigerant of the two refrigerants, that is, a single refrigerant or an azeotropic refrigerant or a non-azeotropic mixed refrigerant different from the one non-azeotropic mixed refrigerant, for example, Freon R123, propane or butane, ammonia, carbon dioxide gas, or the like Natural refrigerant (single refrigerant), non-azeotropic mixed refrigerant using natural refrigerant, Freon R41
0A (azeotropic refrigerant), Freon R404A (non-azeotropic mixed refrigerant) and the like may be used. In the above description, a single refrigerant, Freon R22, is replaced by a non-azeotropic refrigerant, Freon R40.
Although the case where the refrigerant is changed to 7C has been described, the refrigerant is changed from a non-azeotropic mixed refrigerant to a single refrigerant or an azeotropic refrigerant or a non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant, or vice versa. Is changed so that the ratio between the inlet temperature difference and the outlet temperature difference in the heat storage heat exchanger 11 is within a predetermined range for both the refrigerant before the change and the refrigerant after the change. The heat storage heat exchanger 11 may be configured to have a pressure loss. In particular, from the viewpoint of preventing global warming, CFC R407C (non-azeotropic mixed refrigerant), which has a strong global warming effect, is a single refrigerant, and has a low global warming effect, such as propane, butane, ammonia, and carbon dioxide. This embodiment is effective when changing to a refrigerant.

Also, not only for the two refrigerants,
For a plurality of refrigerants that will be used in the future, the heat storage heat exchanger has a refrigerant pressure loss such that the ratio of the inlet temperature difference and the outlet temperature difference in the heat storage heat exchanger 11 falls within a predetermined range. With the configuration of 11, the refrigeration and air-conditioning apparatus which can quickly respond to the change of the refrigerant, always has good heat storage efficiency, can select the refrigerant, and has high versatility can be obtained.

As described above, in this embodiment, the heat storage heat exchanger 11 sets the maximum value of the difference between the freezing temperature of water (0 ° C.) and the non-azeotropic mixed refrigerant to ΔTmax, the freezing temperature of water (0 ° C.). ) And the minimum value of the temperature difference between the non-azeotropic mixed refrigerant is ΔTmin, ΔTmin / ΔTmax> 0.5, and a single refrigerant, an azeotropic refrigerant, and a non-azeotropic refrigerant different from the non-azeotropic mixed refrigerant. When any of the mixed refrigerants is used, the maximum value of the difference between the solidification temperature of water (0 ° C.) and the used refrigerant is ΔTmax, and the minimum value of the solidification temperature of water (0 ° C.) and the temperature difference between the used refrigerants. Is defined as ΔTmin, ΔTmin / ΔTmax> 0.5. Therefore, as a refrigerant retrofit, any one of a single refrigerant, an azeotropic refrigerant, and a non-azeotropic mixed refrigerant is used as the non-azeotropic mixed refrigerant. If the refrigerant is changed to a non-azeotropic mixed refrigerant different from the One refrigerant,
Azeotropic refrigerant, when the refrigerant is changed to any one of the non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant, the operation using the non-azeotropic mixed refrigerant in either case, or a single refrigerant,
Azeotropic refrigerant, the operation using any of the non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant, the degree of variation in the ice thickness generated on the heat transfer tube surface in each operation is small,
Almost uniform ice making can be realized, and efficient heat storage operation can be realized.

Embodiment 14 FIG. In the first to thirteenth embodiments, the heat storage material such as water stored in the heat storage tank 10 is supplied via the non-azeotropic mixed refrigerant to the heat storage material such as water stored in the heat storage tank 10 both when storing heat and when using heat storage. In the description, the heat transfer is performed. This is what is called an internal melting type heat storage tank. In this embodiment, a case in which the present invention is applied to an external fusion type heat storage tank will be described. The refrigeration / air-conditioning apparatus according to the present embodiment has, for example, only a cooling function without a heating function.

FIG. 29 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 14 of the present invention. In the figure, 1 is a compressor, 3 is an outdoor heat exchanger, 4 is an expansion valve, 10 is a heat storage tank, 11 is a heat storage heat exchanger installed in the heat storage tank 10, and these are connected by piping and are frozen. Make up the cycle. Reference numeral 5 denotes an indoor heat exchanger which circulates, for example, water in the heat storage tank 10 by a pump (P), thereby
This is a configuration that uses cold heat stored in zero. in this way,
An external melting type heat storage tank which is configured such that water or the like is circulated directly around the heat storage heat exchanger 11 of the heat storage tank 10 at the time of using heat storage to melt ice formed around the heat transfer tube to obtain cold heat. It is called.

Also in the externally-fused heat storage tank, the heat storage operation performs the same operation as that of the internally-fused heat storage tank. Therefore, if the flow direction of the refrigerant flowing through the heat storage heat exchanger 11 during the heat storage operation is switched between forward and reverse, the uniformity can be obtained. Ice can be generated in the heat storage tank 10.
Hereinafter, the operation will be described in detail. Heat storage heat exchanger 11
A four-way valve 24 is connected to the pipes at both ends of the heat storage heat exchanger 11. By switching the four-way valve 24, the flow direction of the refrigerant in the heat storage heat exchanger 11 can be switched between forward and reverse. The inlet pipe of the heat storage heat exchanger 11 is connected to the expansion valve 4, and the outlet pipe is connected to the compressor 1. 25 is a temperature detector provided in a pipe between the expansion valve 4 and the four-way valve 24;
The refrigerant temperature at the inlet of the heat storage heat exchanger 11 can be detected. Further, Freon R407C, which is a non-azeotropic mixed refrigerant, is sealed in the refrigeration air conditioner as a refrigerant.

The heat storage tank 10 is filled with, for example, water as a heat storage material. During the heat storage operation, the water is cooled and iced by the heat storage heat exchanger 11, and ice is adhered to the surface of the heat transfer tube to generate and heat the heat storage tank 10. It is configured to store cold heat. The case where the flow of the refrigerant in the heat storage heat exchanger 11 during the heat storage operation changes from 11a to 11b in FIG. 29 is defined as the heat storage operation A, and the case where the flow changes from 11b to 11a in FIG. 29 is defined as the heat storage operation B.

At the time of the heat storage operation, for example, the four-way valve 24 is connected as shown by a solid line so as to perform the heat storage operation A in which the flow of the refrigerant in the heat storage heat exchanger 11 changes from 11a to 11b. As shown by solid arrows in FIG. 29, the refrigerant flow during the heat storage operation A is such that the high-temperature and high-pressure refrigerant vapor discharged from the compressor 1 is condensed and liquefied in the outdoor heat exchanger 3 and is reduced to a low pressure by the expansion valve 4. The pressure is reduced and flows into the heat storage heat exchanger 11 through the four-way valve 24.
The refrigerant flowing into the heat storage heat exchanger 11 evaporates by removing heat from the water in the heat storage tank 10, flows out of the heat storage heat exchanger 11, and returns to the compressor 1 through the four-way valve 24.

When the non-azeotropic mixed refrigerant evaporates in the heat storage heat exchanger 11, a temperature change occurs, and the heat transfer tube temperature of the heat storage heat exchanger 11 gradually increases in the refrigerant flow direction. As a result,
At the time of the heat storage operation A, ice does not adhere to the surface of the heat transfer tube of the heat storage heat exchanger 11 with a uniform thickness, and the ice thickness at the inlet portion of the heat storage heat exchanger 11 having a low evaporation temperature increases, and conversely, the evaporation occurs. The ice thickness at the outlet of the heat storage heat exchanger 11 having a high temperature is reduced. When the heat storage operation A proceeds in this state, excessive ice is generated at the inlet of the heat storage heat exchanger 11, the efficiency of the heat storage heat exchanger 11 as a whole decreases, and the evaporation temperature or the evaporation pressure decreases.

Therefore, in the present embodiment, the direction of the flow of the refrigerant in the heat storage heat exchanger 11 is reversed during the heat storage operation, so that the ice thickness is made uniform. That is, the heat storage heat exchanger 11 is provided by the temperature detector 25 provided at the inlet of the heat storage heat exchanger 11.
Then, a decrease in efficiency due to uneven icing is detected, and the operation proceeds to the heat storage operation B. When the refrigerant temperature detected by the temperature detector 25 becomes equal to or lower than a predetermined value, for example, equal to or lower than -7 ° C., it is determined that the ice has been sufficiently made on the inlet side of the heat storage heat exchanger 11. Can be. Therefore, the heat storage operation B is performed by switching the four-way valve 24. This heat storage operation B is performed by switching the four-way valve 24 as shown by the dotted line in FIG.

The flow of the refrigerant during the heat storage operation B is such that the high-temperature and high-pressure refrigerant vapor discharged from the compressor 1 is condensed and liquefied in the outdoor heat exchanger 3 as indicated by the one-dot chain line arrow in FIG.
The pressure is reduced to a low pressure through the four-way valve 24 and the heat storage heat exchanger 1
1b. The heat storage heat exchanger 11 is changed from 11b to 11a.
Refrigerant evaporates by removing heat from the water in the heat storage tank 10 and returns to the compressor 1 through the four-way valve 24.

The flow direction of the refrigerant in the heat storage heat exchanger 11 during the heat storage operation B is opposite to the flow during the heat storage operation A indicated by the solid line arrow. Accordingly, the temperature change in the heat storage heat exchanger 11 during the heat storage operation B is opposite to the temperature change during the heat storage operation A. Therefore, during the heat storage operation B, the evaporation temperature of the portion where the amount of ice is small during the heat storage operation A is low. And the amount of ice making increased,
Conversely, during the heat storage operation A, the evaporating temperature of the portion where the amount of ice making is large becomes high and the amount of ice making decreases, so that the amount of ice making of the entire heat storage heat exchanger 11 becomes uniform. As described above, in the heat storage operation, ice having a uniform thickness can be generated in the heat storage heat exchanger by reversing the high temperature part and the low temperature part of the evaporation temperature of the non-azeotropic mixed refrigerant in the heat storage heat exchanger. In addition, highly efficient heat storage operation can be performed. In addition, excessive ice is generated in a part of the heat storage heat exchanger, and the ice in this part can be prevented from fusing and causing deformation or breakage of the heat transfer tube or the heat storage tank, and a highly reliable refrigeration and air-conditioning device can be obtained. .

During the cooling operation utilizing heat storage, for example, water is circulated between the heat storage tank 10 and the indoor heat exchanger 5 by the pump (P). That is, in the heat storage tank 10, water of about 5 ° C. is caused to flow around the heat storage heat exchanger 11, and the ice in the heat storage tank 10 is thawed to obtain water of about 0 ° C. The cold heat carried by the low-temperature water is used in the indoor heat exchanger 5. After utilizing the cold energy, the water whose temperature has increased by about 5 ° C. is returned to the heat storage tank 10 again.

Thus, in the present embodiment, the four-way valve 2
By switching 4 and reversing the flow direction of the refrigerant in the heat storage heat exchanger 11, even if a non-azeotropic mixed refrigerant is used as the refrigerant, ice of a uniform thickness can be generated in the heat storage heat exchanger 11, Efficient heat storage operation becomes possible. The heat storage heat exchanger 11
Excessive ice is generated in a part of the heat transfer pipe, and the fusion of the ice in this part can be prevented from causing deformation and breakage of the heat transfer tube and the heat storage tank 10, so that a highly reliable refrigeration and air-conditioning apparatus can be obtained.

Further, in the present embodiment, the temperature of the refrigerant flowing into the heat storage heat exchanger 11 is detected by the inexpensive temperature detector 25, and when the temperature of the refrigerant falls below the predetermined temperature, the four-way valve 24 is opened. Switching to ensure that the heat storage heat exchanger 1
The flow direction of the refrigerant in 1 can be reversed. Further, the detection location of the refrigerant temperature is not limited to the inlet of the heat storage heat exchanger 11, but is provided in a pipe from the four-way valve 24 to the compressor 1 to detect the temperature of the outlet of the heat storage heat exchanger 11. The switching may be performed. Furthermore, a temperature detector is provided in the heat storage heat exchanger 11 in the heat storage tank 10 to detect the heat storage state from the refrigerant temperature in the heat storage tank 10, and to switch the flow of the refrigerant according to the result. Is also good.

Instead of detecting the temperature of the refrigerant flowing into the heat storage heat exchanger 11, a pressure detector is provided at the inlet of the heat storage heat exchanger 11, and the pressure detector uses the pressure detector.
Even if the pressure of the refrigerant flowing through the heat storage heat exchanger 11 is detected and the refrigerant temperature at the inlet of the heat storage heat exchanger is estimated to switch the flow of the refrigerant, the flow direction of the refrigerant in the heat storage heat exchanger 11 is surely reversed. Can be switched to The installation location of the pressure detector is not limited to the inlet of the heat storage heat exchanger 11, and may be provided at the outlet of the heat storage heat exchanger 11 or at the heat storage heat exchanger 11 in the heat storage tank 10.
The same effect as described above is achieved.

Further, instead of the temperature detector and the pressure detector,
An ice thickness detector that detects, for example, the thickness of ice as the state of ice in the heat storage tank 10 is provided in the heat storage tank 10, and when it is detected that the ice thickness has reached a predetermined thickness, the four-way valve 24 is switched. May be controlled as follows. By detecting the state of the ice in the heat storage tank 10, the flow direction of the refrigerant in the heat storage heat exchanger 11 can be reliably switched in the opposite direction. A highly reliable refrigeration / air-conditioning device can be obtained without causing breakage. That is, as long as the state of heat storage in the heat storage tank 10 can be grasped from the detection result of the detector, the detector may be installed anywhere and the state quantity to be detected may be any. In the present embodiment, water is used as the heat storage material, and the cold water is stored by using the water filled in the heat storage tank 10 as ice to store the cold heat. For example, a latent heat storage material such as ethylene glycol or hexadecane is stored in the heat storage tank 10. May be used to store cold heat.

However, as described in the above embodiment,
It is desirable to use water as the heat storage material in terms of cost and ease of handling, and the temperature detector 25 is used as the heat storage state detecting means.
When the temperature detector 25 is provided at the inlet of the heat storage heat exchanger 11, the temperature of the refrigerant flowing into the heat storage heat exchanger 11 can be detected in both the heat storage operation A and the heat storage operation B, and can be attached to the pipe. , It can be easily implemented.

In the above description, the configuration in which cold heat is stored in the heat storage tank 10 has been described. However, in an air conditioner in which the heat generated by the heat source device is stored in the heat storage tank 10, the heat storage heat exchanger 11 is used.
Even if the flow direction of the refrigerant is switched, the heat can be uniformly stored in the heat storage tank 10 in the same manner as described above.

In the present embodiment, the simplest refrigerator having one outdoor heat exchanger and one indoor heat exchanger has been described as a refrigerating and air-conditioning apparatus having a heat storage tank. However, the same effect can be obtained in a refrigeration / air-conditioning system in which a plurality of indoor heat exchangers are connected to one outdoor heat exchanger.

Further, in the present embodiment, the case where Freon R407C having an ozone layer depletion coefficient of zero is used as the refrigerant of the refrigeration and air-conditioning apparatus has been described. However, the present invention is not limited to this. Freon R404A and other non-azeotropic mixtures A refrigerant may be used.
In addition, from the viewpoint of preventing global warming, non-azeotropic mixed refrigerants using natural refrigerants such as propane, butane, ammonia, and carbon dioxide exert the same effect.

In such an external fusion type heat storage tank,
Even when the configuration as shown in any of Embodiments 2 to 13 is applied, the same effect as that of the internal melting type heat storage tank can be obtained.

[0148]

As described above, according to the present invention, a heat source device for generating cold or warm heat by using a non-azeotropic mixed refrigerant as a heat transfer medium, a heat storage heat exchanger and a heat storage material, In a refrigerating air-conditioning apparatus comprising: a heat storage tank that stores the cold or warm heat generated in the heat storage material via the heat storage heat exchanger; and a load device to which the cold or warm heat stored in the heat storage tank is supplied. By making it possible to switch the flow direction of the non-azeotropic mixed refrigerant in the heat storage heat exchanger forward and reverse, the high temperature part and the low temperature part of the evaporation temperature of the non-azeotropic mixed refrigerant in the heat storage heat exchanger Invert, ice of uniform thickness can be generated in the heat storage heat exchanger, and efficient heat storage operation becomes possible. In addition, excessive ice is generated in a part of the heat storage heat exchanger, and the ice in this part can be prevented from fusing and causing deformation or breakage of the heat transfer tube or the heat storage tank, and a highly reliable refrigeration and air-conditioning device can be obtained. .

Further, according to the present invention, a temperature detector for detecting the temperature of the non-azeotropic mixed refrigerant flowing through the heat storage heat exchanger is provided, and the temperature in the heat storage heat exchanger is changed according to the output value of the temperature detector. By switching the flow direction of the non-azeotropic refrigerant mixture, a refrigeration / air-conditioning apparatus that can reliably and inexpensively switch the flow direction of the refrigerant can be obtained.

Further, according to the present invention, a pressure detector for detecting the pressure of the non-azeotropic mixed refrigerant flowing through the heat storage heat exchanger is provided, and the pressure in the heat storage heat exchanger is changed according to the output value of the pressure detector. By switching the flow direction of the non-azeotropic mixed refrigerant described above, a refrigeration air conditioner capable of reliably switching the flow direction of the refrigerant can be obtained.

Further, according to the present invention, the flow direction of the non-azeotropic mixed refrigerant in the heat storage heat exchanger is switched at predetermined time intervals, so that the flow direction of the refrigerant can be switched at low cost. A refrigeration and air-conditioning system that can be obtained.

Further, according to the present invention, a detector for detecting the heat storage state of the heat storage material in the heat storage tank is provided, and the non-azeotropic mixed refrigerant in the heat storage heat exchanger is provided according to the detection result of the detector. The flow direction of the refrigerant can be switched at low cost by changing the flow direction of the refrigerant, and furthermore, it is possible to prevent the fusion of the ice and to cause the heat transfer tube or the heat storage tank to be deformed or damaged, thereby improving the reliability. A high refrigeration air conditioner is obtained.

Further, according to the present invention, a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, a heat storage device having a heat storage heat exchanger and a heat storage material, Alternatively, in the refrigeration air conditioner including a heat storage tank that stores heat in the heat storage material via the heat storage heat exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank, the heat storage heat exchanger By making the heat transfer characteristics of the outlet part higher than that of the inlet part, the amount of ice making at the outlet part where the evaporation temperature of the non-azeotropic mixed refrigerant is high is increased, and the amount of ice making at the inlet part where the evaporation temperature is low is increased. A refrigeration / air-conditioning apparatus capable of making the ice making amount uniform can be obtained.

According to the present invention, the pipe diameter at the outlet of the heat storage heat exchanger is made smaller than the pipe diameter at the inlet, and the heat transfer characteristic at the outlet of the heat storage heat exchanger is changed at the heat transfer at the inlet. By making the characteristics higher than the characteristics, it is possible to obtain a refrigeration / air-conditioning apparatus that can increase the amount of ice at the outlet having a high evaporation temperature with a simple configuration and can equalize the amount of ice.

According to the present invention, the non-azeotropic mixed refrigerant is branched into a plurality of flow paths at the inlet of the heat storage heat exchanger, and the number of flow paths at the outlet of the heat storage heat exchanger is reduced. Less than the number of channels, the sum of the cross-sectional areas of the outlet channels is smaller than the sum of the cross-sectional areas of the inlet channels, and the heat transfer characteristics of the outlet of the heat storage heat exchanger By making the heat transfer characteristics higher than the heat transfer characteristics of the section, it is possible to obtain a refrigeration / air-conditioning apparatus capable of increasing the amount of ice making at the outlet section having a high evaporation temperature with a simple configuration and making the amount of ice making uniform.

Further, according to the present invention, a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, a cold storage device having a heat storage heat exchanger and a heat storage material, and Alternatively, in the refrigeration air conditioner including a heat storage tank that stores heat in the heat storage material via the heat storage heat exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank, the heat storage heat exchanger By bringing the heat transfer tube at the inlet and the heat transfer tube at the outlet into thermal contact, heat conduction between the low temperature part and the high temperature part of the evaporation temperature of the non-azeotropic mixed refrigerant makes the heat transfer tube surface temperature uniform, A refrigeration / air-conditioning apparatus capable of equalizing ice formed on the surface can be obtained.

Further, according to the present invention, a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, a cold storage device having a heat storage heat exchanger and a heat storage material, and Alternatively, in the refrigeration air conditioner including a heat storage tank that stores heat in the heat storage material via the heat storage heat exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank, the heat storage heat exchanger By providing a plurality of non-azeotropic mixed refrigerant flow paths in the inside, and by arranging the flow path so that the flow direction of the non-azeotropic mixed refrigerant in the adjacent flow path is reversed, the non-azeotropic mixed refrigerant The low-temperature part and high-temperature part of the evaporation temperature are placed next to each other, and the thin-walled heat transfer tube is placed next to the thick-walled heat transfer tube. Coalescence causes deformation and breakage of heat transfer tubes and heat storage tanks It prevents the highly reliable refrigerating and air-conditioning apparatus can be obtained.

Further, according to the present invention, a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, a cold storage device having a heat storage heat exchanger and a heat storage material and generated by the heat source device Alternatively, in the refrigeration air conditioner including a heat storage tank that stores heat in the heat storage material via the heat storage heat exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank, the heat storage heat exchanger A plurality of heat transfer tubes are arranged side by side, and the heat transfer tubes are arranged so that the flow direction of the non-azeotropic mixed refrigerant is opposite in the adjacent heat transfer tubes, and at least the adjacent heat transfer tubes are arranged. The two pieces are brought into thermal contact with each other to conduct heat between the low-temperature part and the high-temperature part of the non-azeotropic refrigerant mixture to make the surface temperature of the heat transfer tube uniform and to make the ice generated on the surface uniform. Refrigeration and air conditioning system It is.

Further, according to the present invention, there is provided a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, and a heat storage device having a heat storage heat exchanger and a heat storage material. Alternatively, in the refrigeration air conditioner including a heat storage tank that stores heat in the heat storage material via the heat storage heat exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank, the heat storage heat exchanger The heat transfer tubes are arranged in a meandering manner in the vertical or horizontal direction, and the meandering pitch of the inlet portion of the heat storage heat exchanger is made larger than that of the outlet portion, so that the evaporation temperature of the non-azeotropic mixed refrigerant is reduced. The ice making space is widened in the low temperature area and the ice making space is narrow in the high temperature area, so that even if the ice generated on the heat transfer tube surface is uneven with a simple configuration, the ice fuses and the heat transfer tube and heat storage Causes deformation and breakage of the tank To the can be prevented, high reliability refrigeration air conditioning system is obtained.

Further, according to the present invention, a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, a cold storage device having a heat storage heat exchanger and a heat storage material, and Alternatively, in the refrigeration air conditioner including a heat storage tank that stores heat in the heat storage material via the heat storage heat exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank, the heat storage heat exchanger It is assumed that the non-azeotropic mixed refrigerant has a refrigerant pressure loss that cancels the temperature rise in the heat storage heat exchanger, and the temperature of the non-azeotropic mixed refrigerant in the heat storage heat exchanger is substantially constant. By doing so, it is possible to obtain a refrigeration / air-conditioning apparatus which can make the non-uniform evaporation temperature of the non-azeotropic mixed refrigerant uniform by the configuration of the heat storage heat exchanger, and can make the ice generated on the heat transfer tube surface uniform.

Further, according to the present invention, a heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, a cold storage device having a heat storage heat exchanger and a heat storage material, and Alternatively, in the refrigeration air-conditioning apparatus including a heat storage tank that stores heat in the heat storage material via the heat storage heat exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank, the non-azeotropic mixing is performed. Refrigeration and air conditioning with good heat storage efficiency that can store heat almost uniformly by configuring the heat storage heat exchanger so as to have a refrigerant pressure loss such that the temperature change width of the refrigerant in the heat storage heat exchanger is equal to or less than a predetermined value. A device is obtained.

Further, according to the present invention, a heat source device for generating cold or hot heat using a heat transfer medium, and a heat storage heat exchanger and a heat storage material, wherein the cold or hot heat generated by the heat source device is stored in the heat storage device. In a refrigeration air conditioner including a heat storage tank that stores heat in the heat storage material via an exchanger, and a load device to which cold or warm heat stored in the heat storage tank is supplied, a non-azeotropic mixed refrigerant is used as the heat transfer medium. When used, both when using a single refrigerant or azeotropic refrigerant or non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant,
By configuring the heat storage heat exchanger so as to have a refrigerant pressure loss such that the temperature change width of the heat transfer medium in the heat storage heat exchanger is equal to or less than a predetermined value, a single retrofit of the refrigerant Refrigerant, azeotropic refrigerant, when the refrigerant is changed from any of the non-azeotropic mixed refrigerant to a non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant, or from a non-azeotropic mixed refrigerant to a single refrigerant, an azeotropic refrigerant When the refrigerant is changed to any one of the non-azeotropic mixed refrigerants different from the non-azeotropic mixed refrigerant, the operation using the non-azeotropic mixed refrigerant in either case, or a single refrigerant, an azeotropic refrigerant, In the operation using any one of the non-azeotropic mixed refrigerants different from the non-azeotropic mixed refrigerant, heat can be stored almost uniformly in each operation, and a refrigeration / air-conditioning apparatus with good heat storage efficiency can be obtained.

Further, according to the present invention, the predetermined value when the temperature change width of the heat transfer medium in the heat storage heat exchanger is set to a predetermined value or less is set to 3.5 ° C. A refrigeration / air-conditioning apparatus that can uniformly store heat and has high heat storage efficiency can be obtained.

Further, according to the present invention, a heat source device for generating cold or warm heat by using a non-azeotropic mixed refrigerant as a heat transfer medium, a cold heat generated by the heat source device having a heat storage heat exchanger and a heat storage material. Alternatively, in the refrigeration air conditioner including a heat storage tank that stores heat in the heat storage material via the heat storage heat exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank, the heat storage heat exchanger The temperature difference between the temperature of the non-azeotropic mixed refrigerant at the inlet and the temperature of the heat storage material is defined as the temperature difference at the inlet, and the temperature of the non-azeotropic mixed refrigerant at the outlet of the heat storage heat exchanger and the heat storage material By setting the temperature difference between the temperature and the outlet temperature difference, by configuring the heat storage heat exchanger so as to have a refrigerant pressure loss such that the ratio of the inlet temperature difference and the outlet temperature difference is within a predetermined range. , Heat can be stored almost uniformly Good refrigeration and air conditioning equipment of is obtained.

Further, according to the present invention, a heat source device for generating cold or warm heat using a heat transfer medium, and a heat storage heat exchanger and a heat storage material, wherein the cold or warm heat generated by the heat source device is stored in the heat storage device. In a refrigeration air conditioner including a heat storage tank that stores heat in the heat storage material via an exchanger, and a load device to which cold or warm heat stored in the heat storage tank is supplied, a non-azeotropic mixed refrigerant is used as the heat transfer medium. When used, both when using a single refrigerant or azeotropic refrigerant or non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant,
The temperature difference between the temperature of the heat transfer medium at the inlet of the heat storage heat exchanger and the temperature of the heat storage material is defined as an inlet temperature difference, and the temperature of the heat transfer medium at the outlet of the heat storage heat exchanger and the heat storage The temperature difference between the temperature of the material and the outlet temperature difference, the heat storage heat exchanger is configured to have a refrigerant pressure loss such that the ratio of the inlet temperature difference and the outlet temperature difference is within a predetermined range. As a refrigerant retrofit, when the refrigerant is changed from a single refrigerant, an azeotropic refrigerant, a non-azeotropic mixed refrigerant to a non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant, or non-azeotropic Single refrigerant, azeotropic refrigerant, mixed refrigerant,
When the refrigerant is changed to any one of the non-azeotropic mixed refrigerants different from the non-azeotropic mixed refrigerant, in either case, the operation using the non-azeotropic mixed refrigerant, or a single refrigerant, an azeotropic refrigerant, In the operation using any one of the non-azeotropic mixed refrigerants different from the azeotropic mixed refrigerant, in each operation, heat can be stored almost uniformly, and a refrigeration / air-conditioning apparatus with good heat storage efficiency can be obtained.

According to the present invention, the temperature difference between the inlet of the heat storage heat exchanger and the temperature difference between the temperature of the heat storage medium and the temperature at the outlet of the heat storage heat exchanger. Assuming that a larger value is ΔTmax and a smaller value is ΔTmin, a temperature difference ratio ΔTmin / Δ, of the outlet temperature difference which is the temperature difference between the temperature of the heat transfer medium and the temperature of the heat storage material.
By configuring the heat storage heat exchanger so that Tmax has a refrigerant pressure loss satisfying ΔTmin / ΔTmax> 0.5, heat can be stored almost uniformly,
A refrigeration / air-conditioning device with good heat storage efficiency can be obtained.

Further, according to the present invention, cold heat is stored using the latent heat of fusion of the heat storage material, and the temperature of the heat storage material at the inlet of the heat storage heat exchanger and the temperature of the heat at the outlet of the heat storage heat exchanger. By using the solidification temperature of the heat storage material as the temperature of the heat storage material, it is possible to accurately grasp the temperature difference between the heat storage material and the heat transfer medium, and obtain a refrigeration / air-conditioning apparatus that can store heat almost uniformly and has high heat storage efficiency. Can be

Further, according to the present invention, the refrigerant pressure loss is set such that the decrease in operating efficiency from the operating efficiency of the heat source device when the refrigerant pressure loss of the heat storage heat exchanger is 0 is equal to or less than a predetermined value. With the configuration of the heat storage heat exchanger, it is possible to prevent a decrease in the operation efficiency of the refrigeration cycle, and to obtain a refrigeration / air-conditioning apparatus with high heat storage efficiency that can store heat almost uniformly.

[Brief description of the drawings]

FIG. 1 is a refrigerant circuit diagram illustrating a refrigeration / air-conditioning apparatus according to Embodiment 1 of the present invention.

FIG. 2 is a diagram showing a heat storage tank according to Embodiment 1, wherein FIG. 2 (a) is a top view of the heat storage tank and FIG. 2 (b) is a longitudinal sectional view of the heat storage tank.

FIG. 3 is a characteristic diagram illustrating an operation state of the refrigerating air-conditioning apparatus according to Embodiment 1 during a heat storage operation.

FIG. 4 is a graph showing a temperature distribution of the heat storage heat exchanger according to the first embodiment.

FIG. 5 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 2 of the present invention.

FIG. 6 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 3 of the present invention.

FIG. 7 is a configuration diagram showing a heat storage tank according to Embodiment 4 of the present invention.

FIG. 8 is a perspective view showing a heat storage heat exchanger according to Embodiment 5 of the present invention.

FIG. 9 is a perspective view showing another configuration of the heat storage heat exchanger according to the fifth embodiment.

FIG. 10 is a perspective view showing still another configuration of the heat storage heat exchanger according to the fifth embodiment.

FIG. 11 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 6 of the present invention.

FIG. 12 is an explanatory diagram showing ice adhering around a heat transfer tube according to the sixth embodiment.

FIG. 13 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 7 of the present invention.

FIG. 14 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 8 of the present invention.

FIG. 15 is a top view showing another configuration of the heat storage tank according to the eighth embodiment.

FIG. 16 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 9 of the present invention.

FIG. 17 is a characteristic diagram illustrating an operation state of the refrigeration and air-conditioning apparatus according to Embodiment 9 during a heat storage operation.

FIG. 18 is a graph showing a relationship between a temperature change width in the heat storage heat exchanger according to Embodiment 10 of the present invention and an average heat transmittance of the heat storage heat exchanger.

FIG. 19 is a graph showing a relationship between a refrigerant pressure loss in the heat storage heat exchanger according to the tenth embodiment and a temperature change in the heat storage heat exchanger.

FIG. 20 is a characteristic diagram showing a relationship between a refrigerant pressure loss [kg / cm ² ] in a heat storage heat exchanger and an operation efficiency of a refrigeration cycle according to the tenth embodiment.

FIG. 21 is a characteristic diagram showing a relationship between a refrigerant pressure loss [kg / cm ² ] in the heat storage heat exchanger and an average heat transmittance of the heat storage heat exchanger according to the tenth embodiment.

FIG. 22 is a characteristic diagram showing a relationship between the refrigerant pressure loss [kg / cm ² ] in the heat storage heat exchanger and the operating efficiency of the refrigeration cycle in consideration of the average heat transmittance of the heat storage heat exchanger according to the tenth embodiment. It is.

FIG. 23 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 11 of the present invention.

FIG. 24 is a graph showing a refrigerant temperature distribution of the heat storage heat exchanger when the refrigerant pressure loss is 0 kg / cm ^{2 according to} the eleventh embodiment.

FIG. 25 is a graph showing a refrigerant temperature distribution of the heat storage heat exchanger when the refrigerant pressure loss is 0.8 kg / cm ^{2 according to} the eleventh embodiment.

FIG. 26 is a graph showing a refrigerant temperature distribution of the heat storage heat exchanger when the refrigerant pressure loss is 0.4 kg / cm ^{2 according to} the eleventh embodiment.

FIG. 27 is a graph showing a refrigerant temperature distribution of the heat storage heat exchanger according to Embodiment 12 of the present invention.

FIG. 28 is a graph showing the relationship between the rate of change of the temperature difference between the solidification temperature and the refrigerant temperature in the heat storage heat exchanger according to Embodiment 12 and the average heat transfer rate of the heat storage heat exchanger.

FIG. 29 is a refrigerant circuit diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 14 of the present invention.

FIG. 30 is a refrigerant circuit diagram showing a conventional refrigeration / air-conditioning apparatus.

FIG. 31 is a view showing a configuration of a heat storage tank relating to a conventional refrigeration / air-conditioning apparatus, where FIG. 31 (a) is a top view and FIG. 31 (b)
Is a longitudinal sectional view.

[Explanation of symbols]

1 compressor, 2 first four-way valve, 3 outdoor heat exchanger, 4
1st expansion valve, 5 indoor heat exchanger, 10 heat storage tank, 11
Heat storage heat exchanger, 20 second expansion valve, 21 first solenoid valve,
22 second solenoid valve, 23 third solenoid valve, 24 second four-way valve, 25 temperature detector.

Claims (21)

[Claims] 1. A heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, a heat storage device including a heat storage heat exchanger and a heat storage material, wherein the cold or warm heat generated by the heat source device is stored in the heat storage device. In a refrigeration / air-conditioning apparatus including a heat storage tank that stores heat in the heat storage material via an exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank, the non-shared heat exchanger in the heat storage heat exchanger A refrigeration / air-conditioning apparatus characterized in that the flow direction of a boiling mixed refrigerant can be switched between forward and reverse. 2. A temperature detector for detecting a temperature of a non-azeotropic mixed refrigerant flowing through a heat storage heat exchanger, wherein the non-azeotropic mixing in the heat storage heat exchanger is performed according to an output value of the temperature detector. 2. The refrigeration / air-conditioning apparatus according to claim 1, wherein a flow direction of the refrigerant is switched. 3. A pressure detector for detecting a pressure of the non-azeotropic mixed refrigerant flowing through the heat storage heat exchanger, wherein the non-azeotropic mixing in the heat storage heat exchanger is performed according to an output value of the pressure detector. 2. The refrigeration / air-conditioning apparatus according to claim 1, wherein a flow direction of the refrigerant is switched. 4. The refrigeration / air-conditioning apparatus according to claim 1, wherein the flow direction of the non-azeotropic mixed refrigerant in the heat storage heat exchanger is switched at predetermined time intervals. 5. A detector for detecting a heat storage state of a heat storage material in a heat storage tank, wherein a flow direction of a non-azeotropic mixed refrigerant in the heat storage heat exchanger is switched according to a detection result of the detector. The refrigeration / air-conditioning apparatus according to claim 1, wherein 6. A heat source device that generates cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, and includes a heat storage heat exchanger and a heat storage material, wherein the cold or warm heat generated by the heat source device is stored in the heat storage device. In a refrigeration / air-conditioning apparatus including a heat storage tank that stores heat in the heat storage material via an exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank, heat transfer at an outlet of the heat storage heat exchanger A refrigeration / air-conditioning system characterized in that the characteristics are higher than the heat transfer characteristics at the inlet. 7. The heat transfer characteristic at the outlet of the heat storage heat exchanger is made higher than the heat transfer characteristic at the inlet by making the pipe diameter at the outlet of the heat storage heat exchanger smaller than the pipe diameter at the inlet. The refrigeration / air-conditioning apparatus according to claim 6, wherein: 8. The non-azeotropic mixed refrigerant is branched into a plurality of flow paths at an inlet of the heat storage heat exchanger, and the number of flow paths at the outlet of the heat storage heat exchanger is made smaller than the number of flow paths at the inlet. By making the sum of the cross-sectional areas of the flow passages of the outlet portion smaller than the sum of the cross-sectional areas of the flow passages of the inlet portion, the heat transfer characteristics of the outlet portion of the heat storage heat exchanger are changed to the heat transfer characteristics of the inlet portion. 7. The refrigeration and air-conditioning apparatus according to claim 6, wherein the refrigeration and air-conditioning apparatus is set higher. 9. A heat source device that generates cold or hot heat using a non-azeotropic mixed refrigerant as a heat transfer medium, and has a heat storage heat exchanger and a heat storage material and uses the cold or hot heat generated by the heat source device as the heat storage heat. In a refrigeration / air-conditioning apparatus including a heat storage tank that stores heat in the heat storage material via an exchanger, and a load device that is supplied with cold or hot heat stored in the heat storage tank, a heat transfer tube at an inlet of the heat storage heat exchanger And a heat transfer tube at an outlet portion in thermal contact. 10. A heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, and comprising a heat storage heat exchanger and a heat storage material, wherein the cold or hot heat generated by the heat source device is stored in the heat storage device. In a refrigeration air-conditioning apparatus including a heat storage tank that stores heat in the heat storage material via an exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank,
A plurality of non-azeotropic mixed refrigerant flow paths in the heat storage heat exchanger are provided, and the flow paths are arranged such that the flow direction of the non-azeotropic mixed refrigerant is opposite in the adjacent flow paths. Refrigeration and air conditioning equipment. 11. A heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, and comprising a heat storage heat exchanger and a heat storage material, wherein the cold or warm heat generated by the heat source device is stored in the heat storage device. In a refrigeration air-conditioning apparatus including a heat storage tank that stores heat in the heat storage material via an exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank,
The heat storage heat exchanger is configured by arranging a plurality of heat transfer tubes in parallel,
The heat transfer tubes are arranged so that the flow direction of the non-azeotropic refrigerant mixture is opposite in the adjacent heat transfer tubes, and at least two of the adjacent heat transfer tubes are thermally contacted. Refrigeration air conditioner. 12. A heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, a heat storage device including a heat storage heat exchanger and a heat storage material, wherein the cold or warm heat generated by the heat source device is stored in the heat storage device. In a refrigeration air-conditioning apparatus including a heat storage tank that stores heat in the heat storage material via an exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank,
The refrigeration and air conditioning system is characterized in that the heat storage heat exchanger is provided with heat transfer tubes meandering in a vertical or horizontal direction, and the meandering pitch at the inlet of the heat storage heat exchanger is larger than that at the outlet. apparatus. 13. A heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, a heat storage device including a heat storage heat exchanger and a heat storage material, wherein the cold or warm heat generated by the heat source device is stored in the heat storage device. In a refrigeration air-conditioning apparatus including a heat storage tank that stores heat in the heat storage material via an exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank,
The heat storage heat exchanger has a refrigerant pressure loss that cancels the temperature rise of the non-azeotropic mixed refrigerant in the heat storage heat exchanger, and the non-azeotropic mixed refrigerant in the heat storage heat exchanger A refrigeration / air-conditioning apparatus characterized in that the temperature is substantially constant. 14. A heat source device for generating cold or hot heat using a non-azeotropic mixed refrigerant as a heat transfer medium, and a heat storage device including a heat storage heat exchanger and a heat storage material, wherein the cold or hot heat generated by the heat source device is stored in the heat storage device. In a refrigeration air-conditioning apparatus including a heat storage tank that stores heat in the heat storage material via an exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank,
A refrigeration air conditioner wherein the heat storage heat exchanger is configured to have a refrigerant pressure loss such that a temperature change width of the non-azeotropic mixed refrigerant in the heat storage heat exchanger is equal to or less than a predetermined value. 15. A heat source device for generating cold or warm heat using a heat transfer medium, a heat storage heat exchanger and a heat storage material, wherein the cold or warm heat generated by the heat source device is passed through the heat storage heat exchanger. In a refrigeration / air-conditioning apparatus including a heat storage tank that stores heat in a heat storage material and a load device to which cold or warm heat stored in the heat storage tank is supplied, when a non-azeotropic mixed refrigerant is used as the heat transfer medium, In any case where one refrigerant or an azeotropic refrigerant or a non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant is used, the temperature change width of the heat transfer medium in the heat storage heat exchanger is equal to or less than a predetermined value. A refrigerating and air-conditioning apparatus, wherein the heat storage heat exchanger is configured to have a refrigerant pressure loss as follows. 16. The predetermined value when the temperature change width of the heat transfer medium in the heat storage heat exchanger is set to a predetermined value or less,
The refrigeration / air-conditioning apparatus according to claim 14 or 15, wherein the temperature is 3.5 ° C. 17. A heat source device for generating cold or warm heat using a non-azeotropic mixed refrigerant as a heat transfer medium, a heat storage heat exchanger and a heat storage material, wherein the cold or warm heat generated by the heat source device is stored in the heat storage device. In a refrigeration air-conditioning apparatus including a heat storage tank that stores heat in the heat storage material via an exchanger, and a load device that is supplied with cold or warm heat stored in the heat storage tank,
The temperature difference between the temperature of the non-azeotropic mixed refrigerant at the inlet of the heat storage heat exchanger and the temperature of the heat storage material is defined as an inlet temperature difference, and the temperature of the non-azeotropic mixed refrigerant at the outlet of the heat storage heat exchanger. The heat storage heat exchanger such that the temperature difference between the temperature and the temperature of the heat storage material is defined as the outlet temperature difference, and the refrigerant pressure loss is such that the ratio of the inlet temperature difference and the outlet temperature difference is within a predetermined range. A refrigeration and air-conditioning system characterized by comprising: 18. A heat source device for generating cold or warm heat using a heat transfer medium, a heat storage heat exchanger and a heat storage material, wherein the cold or warm heat generated by the heat source device is supplied to the heat storage device via the heat storage heat exchanger. In a refrigerating and air-conditioning apparatus including a heat storage tank that stores heat in a heat storage material and a load device to which cold or warm heat stored in the heat storage tank is supplied, when a non-azeotropic mixed refrigerant is used as the heat transfer medium, The temperature of the heat transfer medium at the inlet of the heat storage heat exchanger and the temperature of the heat storage material, regardless of whether one refrigerant or an azeotropic refrigerant or a non-azeotropic mixed refrigerant different from the non-azeotropic mixed refrigerant is used. The temperature difference between the temperature and the inlet portion temperature difference, the temperature difference between the temperature of the heat transfer medium and the temperature of the heat storage material at the heat storage heat exchanger outlet portion as the outlet portion temperature difference, the inlet portion temperature difference and The ratio of the outlet temperature difference is within a predetermined range. A refrigeration / air-conditioning apparatus characterized in that the heat storage heat exchanger is configured to have a refrigerant pressure loss as described below. 19. An inlet temperature difference, which is a temperature difference between the temperature of the heat transfer medium and the temperature of the heat storage material at the inlet of the heat storage heat exchanger;
Outlet temperature difference between the temperature of the heat transfer medium and the temperature of the heat storage material at the outlet of the heat storage heat exchanger,
Assuming that the larger value is ΔTmax and the smaller value is ΔTmin, the heat storage heat exchanger is such that the temperature difference ratio ΔTmin / ΔTmax has a refrigerant pressure loss satisfying ΔTmin / ΔTmax> 0.5. 19. The refrigeration / air-conditioning apparatus according to claim 17, wherein: 20. The heat storage tank stores cold heat by utilizing latent heat of fusion of the heat storage material, wherein the temperature of the heat storage material at an inlet of the heat storage heat exchanger and the heat storage material at an outlet of the heat storage heat exchanger. 20. The refrigeration / air-conditioning apparatus according to claim 17, wherein a solidification temperature of the heat storage material is used as the temperature. 21. The heat storage heat exchanger is configured to have a refrigerant pressure loss such that a decrease in operating efficiency from an operating efficiency of the heat source device when the refrigerant pressure loss of the heat storage heat exchanger is 0 is equal to or less than a predetermined value. The refrigeration / air-conditioning apparatus according to any one of claims 13 to 20, wherein: