JPH03241251A - Ice reservoir for air condition - Google Patents

Abstract

PURPOSE:To improve a heat transfer coefficient and uniform heat transfer by filling liquid refrigerant in the shell of an evaporator in a sufficient amount of covering a tube in the shell while a refrigerant circulating cycle is formed in a heat pump and operating. CONSTITUTION:A shell side cooling vessel 18 is operated as a function of an evaporator of a heat pump apparatus, and formed as a full-liquid type evaporator. That is, liquid refrigerant 21 is filled in the vessel 18 in a sufficient amount of immersing a heat transfer tube 17, i.e., its liquid level 22 is disposed above the tube 17 in the vessel during the operation of the apparatus, the upper space of the level 22 is maintained under negative pressure, and the tube 17 is heated by the refrigerant 21 to boil the liquid. Thus, when overcooled water is produced to manufacture sherbetlike ice to reserve ice cold for air conditioning, an overcooler 2 of its central device is formed in a boiling heat transfer type full-liquid evaporator, thereby improving a heat transfer coefficient and performing uniform heat transfer in the entire heat transfer tube.

Description

[Detailed description of the invention] [Industrial application field] The present invention relates to an ice heat storage device for air conditioning.

[Prior technology] When performing air conditioning by circulating cold and hot water through the water side heat exchange tube of a fan coil Unisotoya water source heat pump unit installed in a building, the cold heat during cooling is stored in the form of ice in a heat storage tank. The so-called ice heat storage method, which stores heat in ice, is attracting attention and is now being used in some cases. 9. For example, ice is made by driving a refrigerator with electricity at night, storing a large amount of cold heat in the form of water in a heat storage tank, and then extracting the cold heat of that water as cold water during cooling operation and sending it to the secondary heat exchanger. It is cyclical,
Since it uses the latent heat of water, it can store a large amount of cold energy even in a small-scale device.

Depending on the ice making method, the ice stored in this ice storage method can be stored in the form of ice blocks (solid or dome) and jar-head (shaped).
mixture of fine ice and water (kid-like or slurry-like)
It can be divided into Both methods have their advantages and disadvantages, but in the ice block method, when ice blocks are generated in a heat storage water tank (generated on the surface of a heat exchanger), as the water layer thickens, heat conduction decreases, so a large thickness is used. Therefore, there is a limit to the ice filling rate (1, P, F,
) is only around 10%, and it is inevitable that the heat storage efficiency will deteriorate. 1. There have also been reports of using a special solution with additives to make P and F oriented in the same direction, or of configuring the body of two heat storage water tanks as pressure vessels. There are many problems in directly applying air conditioning equipment to the water M-heat system. On the other hand, in the case of manufacturing ice cubes, 1. Although I' and F can be made very large, converting a large volume of water into a tube generally requires very large-scale equipment. Regarding this heat storage method in the form of a heat exchanger, 1, for example, JP-A No. 63-123
Those described in 968-9 and JP-A-63-129274-5 are known. Also, JP-A No. 63217171 and JP-A No. 63-1989 filed by the same applicant.
Publication No. 231157.

We proposed a method and device for making fine ice from supercooled water, and discussed their improvements with the requirement that this supercooled water be continuously produced using heat transfer tubes.

JP-A-63-271074, JP-A-64-758
Publication No. 69.

JP-A-64-90973, JP-A-1-11468
Publication No. 2.

Utility Model Application No. 63-139459, Utility Model Application No. 1-8823
No. 5 Publication No. 1-88236, Utility Model Application No. 1-88
237 Publication, Utility Model Application Publication No. 1-97135, Utility Model Application Publication No. 1999
-112345, Japanese Utility Model Application No. 1-120022, Japanese Utility Model Application No. 1-125940, Japanese Utility Model Application No. 1-1368
Publication No. 32, Publication of Utility Model Application No. 1148538, Publication of Utility Model Application No. 1999-
Various proposals were made in Publication No. 178528, Publication No. 2-527 of Utility Model Application, etc. In any case, the supercooler of the ice-making system that was proposed for producing globular ice from over-extracted water into a jar has a heat transfer tube placed inside the cooling container through which water passes. Brine from a refrigerator is passed through the cooling container as a cooling medium, or the cooling container is configured to function as an evaporator of a heat pump device. As a result, if the inner wall temperature of the heat transfer tube is maintained at -5.8℃ or lower, although it is below zero degrees Celsius, supercooled water will continue to flow without freezing inside the tubes, regardless of fluctuations in the water's population temperature or flow rate. can be manufactured.

[Problem that the invention seeks to solve]

In the above supercooler, the inner wall temperature of the heat transfer tube was set to 5.8°C.
It is important to control the temperature to ~0°C, but in the method of passing the brine of the refrigerator through a cooling container with heat transfer tubes, the heat transfer between the heat transfer tubes and the brine is due to convection heat transfer (liquid convection). Become. In addition, even when the cooling container is used as the evaporator of a heat pump device, convective heat transfer (
gas convection). Such convection heat transfer methods have limits to improvement in terms of heat transfer coefficient and uniform heat transfer.

The present invention aims to overcome this limitation.

[Means to solve problems]

In the present invention, heat transfer in the supercooler is not performed by convective heat transfer as described above, but by 7!1! This process is carried out by heat transfer by heating, and is characterized by a liquid-filled evaporator with a transfer vessel in which a heat transfer tube is placed. That is, according to the present invention, the heat source water for air conditioning stored in the heat storage tank is continuously supplied to the evaporator of the heat pump device to reduce the temperature to subcooled water below zero degrees Celsius, and this supercooled water is transferred to the evaporator. In an ice heat storage device for air conditioning, the water-water slurry is stored in the heat storage tank by discharging it as a continuous flow from the ice storage tank and supplying the discharged flow to the heat storage tank while releasing the supercooled state,
The evaporator of the heat pump device described in J is composed of a shell-and-dupe heat exchanger, in which the heat source water is continuously passed through the tube side, and the refrigerant of the heat pump is supplied to the soil side. While the human pump device is operating forming a cycle of refrigerant returning from the evaporator to the evaporator via the compressor, condenser and expansion valve, liquid refrigerant is shelled in the well of the evaporator. To provide an air conditioning ice heat storage device characterized in that it is configured to be filled with enough ice to cover an inner tube.

According to the present invention, in addition to the characteristic configuration of using the supercooler using the flooded florescent device, the refrigerant circulation cycle of the heat pump device is further changed from the evaporator to
The cycle consists of a compressor → condenser → liquid receiver → liquid/M heat exchanger → expansion valve → the smoke generator.

In this liquid-liquid heat exchanger, the liquid refrigerant is continuously supplied to the evaporator. The heat source water in the point heat storage tank is circulated independently between the heat source side circulation waterway that returns to the tank and the load side circulation waterway that passes through the nine load side heat exchangers for air conditioning and returns to the heat storage tank. The heat source water in the point M heat tank, which is continuously supplied to the evaporator after passing through the load side heat exchanger for air conditioning, is transferred to the load side heat exchanger for air conditioning and the cough fluid/liquid heat exchanger. The invention was devised by continuously supplying the water to the evaporator after passing through the process.

[Effect]

Generally, the evaporator of a heat pump device performs expansion evaporation by injecting refrigerant liquid into a low-pressure device, and in the supercooler proposed earlier, the evaporator of a heat pump device also performs expansion evaporation by injecting refrigerant liquid into a low-pressure device. In the present invention, the evaporator is filled with a liquid refrigerant and the liquid refrigerant is brought to a boil. Stirring improves heat transfer and allows heat to be uniformly transferred throughout the heat transfer tubes in the vessel.

In addition, a liquid-liquid heat exchanger is placed in the refrigerant circulation cycle of the heat pump, and by exchanging heat between the refrigerant and the heat source water in this liquid-liquid heat exchanger, the refrigerant before entering the evaporator exceeds the capacity of the heat pump device. Since the water is excessively cooled, the cooling capacity of the evaporator increases, and the heat source water before entering the evaporator 5 is heated, thereby preventing freezing in the evaporator.

Furthermore, by continuously supplying the heat source water in the heat storage tank to the load-side heat exchanger for air conditioning and then to the evaporator, the equipment can be simplified, and the Ice-making operation can be performed at the same time as air-conditioning operation) with a high coefficient of performance.

In addition, the device of the present invention provides various functions as explained in the following examples, and as a whole, an energy-saving and efficient ice heat storage device for air conditioning is provided.

Embodiment C] FIG. 1 shows an embodiment of the apparatus of the present invention. 1
2 is a heat storage tank, 2 is a supercooler, and 3 is a circulation pump. Water in the heat storage tank 1 is continuously supplied to the supercooler 2 through a heat source side circulation waterway 4 by the drive of the pump 3. As a result, the supercooled water 5 becomes subcooled water 5 below zero degrees Celsius and is discharged into the atmosphere. Depending on the case, the discharge flow of the supercooled water 5 collides with the supercooled state release device 6 and is returned to the heat storage tank 1. When the supercooled state is released, it becomes fine ice, and Scherchent-shaped ice 8 accumulates in the heat storage tank l. In the illustrated example, a filter 9 for collecting fine ice is interposed on the suction side of the pump 3 in the circulation waterway 4 on the heat source side, and a liquid/forming heat exchange is performed in the path from the pump 3 to the supercooler 2. A buffer tank 11 is interposed between the container IO and its lower side. On the other hand, there is an independent load-side i-ring water channel 13 through which the cold water in the 1M heat tank l passes through the load-side heat exchanger 12 for air conditioning and then returns to the heat storage tank. That is, the cold water in the heat storage IWl is filtered through the filter 14.
Load side pump 15. Load side heat exchanger 12. water sprinkler j6
After that, it returns to the tank. A liquid/TL heat exchanger is normally used as the load side heat exchanger I2, and the water (F,'I P
#! 23 to exchange heat with the secondary insolvent hot water that circulates. In some cases, the load-side heat exchanger 12 itself can be used as a heat exchanger for an air conditioner.

The supercooling 2W 2 of the heat source side circulation waterway 4 consists of an L&tube type heat exchanger 2 in which a large number of heat transfer tubes 17 are arranged inside a nonyl 18. Each duplex 17 (hereinafter referred to as a heat exchanger tube 17) is disposed through a shell 18 (hereinafter referred to as a cooling vessel 18), and one end thereof is open to the recruitment rohenoda part 20, and the other end is open to the atmosphere. Therefore, the water introduced into the header portion 20 flows through each heat transfer tube 17 and is discharged into the atmosphere from the other open end. The cooling container 18 on the nonyl side functions as an evaporator of the heat pump device, and a major feature of the present invention is that this is configured as a 7-night type evaporator. That is,
When the heat pump device is in operation, liquid refrigerant 2 is in the cooling container IB.
1 is sufficient to submerge the heat transfer tube 17, that is, the liquid level 2
The space above the i-plane 22 is maintained at a negative pressure, and the liquid refrigerant 21 is heated by the heat exchanger tubes 17, so that the liquid refrigerant 21 is heated by the heat exchanger tubes 17. placed in a boiling state.

In addition, in Fig. 1, 24 is a compressor, 25 is O'*2
S, 26 ha? f! A heat pump device is constructed by connecting refrigerant piping between these parts. In addition, the liquid receiver 2
6 and the expansion valve 27 is interposed with the liquid-liquid heat exchanger lO mentioned above. The condenser 25 is composed of an air-cooled fin-tube heat exchange coil, and radiates heat of condensation of the high-pressure refrigerant discharged from the compressor 24 by passing air through it by driving a fan 28. Once this liquid refrigerant receives liquid 2S2
6, and is cooled by exchanging heat with the heat source water before entering the supercooler 2 in the liquid-i heat exchanger 10, and then introduced into the cooling container 18, which is an evaporator, through the expansion valve 27. At that time,
By providing a liquid refrigerant inlet 29 at the lower part of the cooling container 18, the refrigerant is introduced from below through the expansion valve 27 into the layer of liquid refrigerant 21 inside the container. Gaseous refrigerant is sucked into the compressor 24 from the gaseous refrigerant outlet 30 provided at the upper part of the cooling container 18, thereby maintaining the inside of the cooling container 18 at a low pressure. Since heat is imparted by f! i. Refrigerant 21 causes boiling. At that time, a controlled operation is performed so that the liquid level 22 of the I&R medium 2I is maintained at a steady position, and the temperature of the liquid refrigerant 21 is controlled by this boiling HB to a temperature of 158° C. The temperature is controlled so that it is cooled to a temperature below zero degrees Celsius.

As a result, a continuous flow 5 of supercooled water supercooled to below zero degree Celsius is discharged from the discharge port of the heat exchanger tube 17 of the supercooler 2, and this is a discharge flow composed of an inclined collision plate, a distribution plate, a rotating plate, etc. By touching the supercooling state release device 6 that applies an impact to the supercooled state, fine water is precipitated and accumulated in the heat storage tank l.

FIG. 2 shows a device according to the invention that is similar to FIG. 1 except that a load-side heat exchanger 12 for air conditioning is interposed in the heat source-side circulation channel 4. FIG. That is, in Fig. 1, the load side heat exchange 2
S]2 was provided independently of the heat source side circulation waterway 4,
In the case of FIG. 2, the load side circulation waterway is omitted by inserting the load side heat exchanger 12 into the heat source side circulation waterway 4,
Therefore, filter 14 of FIG. Pump 15. Watering device 1
6th grade is also omitted. The appropriate insertion position of the load-side heat exchanger 12 into the heat source-side circulation waterway 4 is between the pump 3 and the liquid-liquid heat exchanger 10. In this way, the load side heat exchanger tf
By inserting the A vessel 12 into the heat source side circulation waterway 4.

The equipment is simpler than the case shown in FIG. 1, and it is also more advantageous in terms of performance. In other words, thermal storage systems generally use a combination of nighttime thermal storage operation and daytime chasing operation from an economic standpoint including equipment costs, but those that apply power-saving capacity control with a constant cooling capacity. As such, the higher the temperature of the heat source water inlet to the heat transfer tubes 17 of the supercooler 2, the better the coefficient of performance of the heat pump device. In the example of Fig. 2, when driving during the day, the load side heat exchanger I2
The water, which has become hotter than that shown in Figure 1 due to the insertion of the heat exchanger tube 1,
7, so he will be able to drive with a high coefficient of performance.

(Effects of the Invention) As described above, according to the present invention, when producing supercooled water and producing ice in the form of 7-year logs to store water for air conditioning, the supercooler which is the center of the Since this is configured as an /A liquid type stem generator using a boiling heat transfer method, the heat transfer coefficient is improved compared to the conventional convection heat transfer method, and uniform heat transfer is achieved throughout the heat transfer tube. Therefore, highly efficient and accurate operation is possible for the production of supercooled water, which requires accurate control of the inner surface temperature of the heat exchanger tubes. In addition, by installing a liquid-liquid heat exchanger that exchanges heat between the refrigerant and the heat source water in the refrigerant circulation cycle of the heat pump, it is possible to reduce the amount of water in the heat transfer tubes without affecting the overall cooling capacity of the heat pump. Freezing can be prevented. Furthermore, by inserting the load-side heat exchanger into the heat source-side circulation waterway, the heat pump has a higher coefficient of performance during operation, achieving energy savings, and many other effects not found in conventional methods. , it can make a great contribution as an air conditioning system using the ice heat storage method.

[Brief explanation of drawings]

FIG. 1 is a schematic sectional system diagram not showing one embodiment of the air conditioning ice heat storage device according to the present invention, and FIG. 2 is a schematic sectional system diagram not showing another embodiment of the air conditioning water M heat storage device according to the present invention. . ■... Heat storage tank, 2... Supercooler 3... Pump,
4. Heat source side circulation waterway 5. Supercooled water,
6.Supercooling state release device 9..Filter, 10..Liquid-liquid heat exchanger 11.Buffer tank, 12..Load side heat exchanger 13..Load side circulation waterway, 18..Heat transfer tube 1
9. Cooling container (Ner), 21.. Liquid refrigerant 22.. Fractured surface of liquid refrigerant, 24.. Compressor 25 ・ Condenser 6 Fi receiver 27 ・ Expansion valve 29.. Liquid refrigerant inlet 30 ・ Gas refrigerant outlet.

Claims (7)

[Claims] (1) Heat source water for air conditioning stored in a heat storage tank is continuously supplied to the evaporator of the heat pump device, cooled to subcooled water below zero degrees Celsius, and this supercooled water is discharged as a continuous flow from the evaporator. In the ice heat storage device for air conditioning, the discharge flow is released from its supercooled state and is supplied to the heat storage tank to store ice-water slurry in the heat storage tank. It consists of a shell and tube type heat exchanger in which the heat source water is continuously passed through the tube side and the refrigerant of the heat pump is supplied to the shell side,
While the heat pump device is operating by forming a circulation cycle of refrigerant from the evaporator through the compressor, condenser and expansion valve and back to the evaporator, liquid refrigerant is in the shell of the evaporator. An air conditioning ice storage device configured to be filled in sufficient quantity to cover the tubes. (2) The refrigerant circulation cycle of the heat pump device forms a cycle consisting of the evaporator → compressor → condenser → liquid receiver → liquid-liquid heat exchanger → expansion valve → the evaporator. The ice heat storage device for air conditioning according to claim 1, wherein the liquid refrigerant is heat exchanged with heat source water before being continuously supplied to the evaporator in the heat exchanger. (3) The heat source water in the heat storage tank is divided into a heat source-side circulation waterway that passes through the evaporator and then returns to the heat storage tank, and a load-side circulation waterway that passes through the load-side heat exchanger for air conditioning and then returns to the heat storage tank. The ice heat storage device for air conditioning according to claim 1 or 2, wherein the ice heat storage device is circulated independently. (4) The ice heat storage device for air conditioning according to claim 1 or 2, wherein the heat source water in the heat storage tank is continuously supplied to the evaporator after passing through a load-side heat exchanger for air conditioning. (5) The ice heat storage device for air conditioning according to claim 2, wherein the heat source water in the heat storage tank is continuously supplied to the evaporator after passing through a load-side heat exchanger for air conditioning and the liquid-liquid heat exchanger. . (6) Claims 1, 2, and 3, wherein the heat source water in the heat storage tank is once passed through a buffer tank before being supplied to the evaporator.
The ice heat storage device for air conditioning according to , 4 or 5. (7) The ice heat storage device for air conditioning according to claim 1, 2, 3, 4, 5, or 6, wherein the inner surface temperature of the tube of the evaporator is maintained at -5.8 degrees Celsius or higher and zero degrees Celsius or lower.