JPH03241271A - Cool heat generating equipment and operation of the same - Google Patents

Abstract

PURPOSE:To improve cooling capacity and save energy by providing a compressive freezing system in which an overcooler is arranged on the rear stage of a condenser in a refrigerant circulation passage. CONSTITUTION:A compressive freezing system 10 has a refrigerant circulation passage 20 in which a compressor 12 driven by an electric motor 11, a condenser 14 which exchanges heat between cooling water cooled by atmosphere in a cooling tower 25 arranged on a roof of a building and supplied through a pump 26 and pipe passage 21 and refrigerant, a liquid receiving tank 16, an expansion valve 17, a vaporizer 18 which exchanges heat between cool water to be supplied to the place to be cooled and refrigerant, and an accumulator 19 are arranged in this order in the refrigerant flowing direction. Further, an overcooler 15 which cools or overcools the refrigerant having been cooled by the condenser 14 is arranged on the rear stage of the condenser 14 in the refrigerant circulation passage 20. By this, the cooling capacity can be improved and energy can be saved.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a cold heat generating facility in which a compression type refrigeration system is used as the main part, and in particular, to cool a relatively large building or area, and a method of operating the same. .

[Conventional technology]

BACKGROUND ART Cold heat generating equipment, particularly cold heat generating equipment designed to cool relatively large buildings or areas such as hotels, office buildings, hospitals, factories, and housing complexes, often uses a compression refrigeration system as the main part thereof. As is well known, compression refrigeration equipment used in such cold heat generation equipment compresses refrigerant.

The basic configuration is to cool the cold water to be supplied to the cooling destination by using the latent heat of evaporation of the refrigerant in the evaporation step of the refrigeration cycle consisting of the steps of condensation, expansion, and evaporation.

Further, as a compression type refrigeration apparatus having such a basic configuration with a hot water extraction function added, for example, the one shown in FIG. 5 is known. The compression type refrigeration system shown in FIG. 5 has a compressor 102. A condenser 1 performs heat exchange between cooling water cooled by the atmosphere in a cooling tower 125 disposed on the roof of a building, and supplied through a pump 126 and a pipe 121, and a refrigerant flowing in a refrigerant circulation passage.
04. Liquid receiving tank 106, expansion valve 107. An evaporator 108 that performs heat exchange between the chilled water to be supplied to the cooling destination and the circulating refrigerant.
An accumulator 109 is provided, and a hot water extraction heat exchanger 103 (sometimes referred to as a double bundle condenser together with the condenser 104) is provided upstream of the condenser 104 in the refrigerant circulation passage 110. In this hot water extraction heat exchanger 103, the pipe line 12 is connected from the outside.
3, and the high temperature and high pressure refrigerant compressed and discharged by the compressor 102, thereby making the water 50 suitable for use in hot water supply equipment etc. from the pipe 124. It is possible to obtain hot water around ~60°C.

[Problems to be Solved by the Invention] In general, cold heat generating equipment needs to be designed so that its cooling capacity does not run out even when the cooling load is at its maximum in the building etc. in which it is used. The increase in demand for air conditioners in recent years has forced them to become larger, resulting in a rise in equipment costs.

Incorporating a heat storage device into cold heat generation equipment is being considered as one measure to counter the soaring equipment costs associated with such enlargement. In other words, since the cooling load is typically only particularly large during the 4-5 daytime hours in the summer, compression refrigeration equipment, etc., should not be used outside of these hours, especially late at night when electricity is available cheaply. By storing cold or hot heat in the refrigerator and extracting it for use when necessary, it is possible to cope with increased cooling loads without increasing the size (larger capacity) of the compression refrigeration equipment. It can be done.

However, in conventional cold heat generation equipment that incorporates heat storage devices, the compression refrigeration system itself, which is the main part, is basically the same as before, so improvements in cooling capacity and energy savings are expected. It's hard to say.

On the other hand, the applicant of the present application has previously developed a compression type refrigeration system and a concentration differential heat storage system, as shown in Japanese Patent Application Laid-Open No. 62-218773, with the main purpose of downsizing and energy saving of cold heat generating equipment. We are proposing cooling and heat generating equipment that is cleverly combined with other equipment. Broadly speaking, such cold heat generation equipment uses a condenser required in a compression type refrigeration system as a heat storage material heating means in a concentration difference heat storage system, and
The evaporator is used as a heat medium condensing means in a concentration difference heat storage system.

In a concentration difference heat storage system, a heat storage operation is performed in which the absorbed heat medium is evaporated and separated from the heat storage material, and a heat radiation operation is performed in which the heat medium is evaporated and absorbed into the heat storage material. The basic idea is to supply cold water whose temperature has been lowered by the latent heat of vaporization of the medium to the cooling destination. Further, when the cooling capacity is insufficient due to an increase in the cooling load, the cold water obtained by the heat dissipation operation is combined with the cold water obtained by the compression type refrigeration system, and the mixture is supplied to the cooling destination.

In cold heat generation equipment configured in this way, although the compression type refrigeration system can be downsized and the equipment can save energy to some extent, the combination of the compression type refrigeration system and the concentration difference heat storage system is ingenious. Therefore, it is inevitable that the configuration of the equipment becomes complicated, and there is a risk that the equipment will become expensive.

An object of the present invention is to provide cold heat generation equipment that can improve cooling capacity and save energy without increasing the size of a compression refrigeration system.

Another object of the present invention is to effectively combine a compression type refrigeration system and a concentration differential heat storage system to reduce equipment costs and operating costs and improve overall equipment efficiency without increasing the size and complexity of the equipment. It is an object of the present invention to provide cold/heat generating equipment that can save energy, and to provide a method for efficiently operating the equipment.

[Means to solve the problem]

In order to achieve the above object, the inventors of the present application conducted extensive research and obtained the following findings.

That is, in the compression type refrigeration system, as described above, the latent heat of vaporization of the refrigerant in the weeding process is used to cool the cold water to be supplied to the cooling destination. Therefore, if the latent heat of vaporization of the refrigerant can be increased by some means, the cooling capacity can be increased. One possible way to increase the latent heat of vaporization is to increase the amount of refrigerant circulation. However, the conventional measure to increase the amount of refrigerant circulation is to increase the amount of refrigerant discharged from the compressor, which inevitably leads to an increase in the size of the compressor and equipment costs. This results in an increase in operating costs.

Therefore, we changed our perspective and focused on the relationship between the change in the state of the refrigerant flowing through the refrigerant circulation passage in a compression refrigeration system and the temperature, and found that in the current compression refrigeration system, strictly speaking, the refrigerant can produce saturated liquid - saturated vapor. It was discovered that the latent heat between steam and saturated steam is not fully utilized, but rather the change in latent heat between relatively dry wet steam and saturated steam is utilized. In other words, in conventional compression refrigeration systems, the refrigerant that is compressed to high temperature and pressure by a compressor is cooled by a condenser, but the cooling water used in the condenser is usually cooled by the atmosphere in a cooling tower. The temperature of the refrigerant is said to be around 30°C in summer, so the temperature of the refrigerant in the condenser is around 40°C (
The temperature is lowered only to saturated liquid (at high pressure).

When this saturated liquid of refrigerant is subjected to adiabatic expansion (isenthalpic change) and the pressure is lowered, it becomes wet steam at that pressure, but under such pressure, it becomes wet steam with a relatively high degree of dryness (about 25%). The amount of latent heat of vaporization of a refrigerant, which corresponds to its cooling capacity, is the amount of change in enthalpy from wet vapor to saturated vapor. There will be no.

The cold heat generation equipment according to the present invention was developed based on the above-mentioned research results and considerations based thereon, and specifically, a compressor, a condenser, an expansion valve, and an evaporator are sequentially arranged. The refrigerant circulation passage is configured to cool the refrigerant in the refrigerant circulation passage using cooling water obtained when the condenser is cooled by the atmosphere, and the refrigerant in the refrigerant circulation passage is disposed downstream of the condenser in the refrigerant circulation passage. The refrigerating system is equipped with a compression type refrigeration system in which a supercooler is provided to further cool the refrigerant.

In addition to the compression type refrigeration system according to claim 1, another cold heat generation equipment according to the present invention includes a heat storage operation in which the absorbed heat medium is evaporated and separated from the heat storage material, and a heat storage operation in which the absorbed heat medium is evaporated to be separated from the heat storage material. A concentration difference heat storage system is provided which performs a heat dissipation operation by absorbing heat into the material, and uses the latent heat of evaporation of the heating medium during the heat dissipation operation of the concentration difference heat storage system to cool the refrigerant in the supercooler installed in the compression type refrigeration system. Cooling water whose temperature has been lowered is used.

Furthermore, an important feature of the cold heat generating equipment according to the present invention is that the heat radiation operation section and the heat storage operation section are separately provided in the concentration difference heat storage system, so that the heat radiation operation and the heat storage operation can be executed in parallel. and configured.

On the other hand, the method of operating a cold heat generation facility according to the present invention is for a cold heat generation facility equipped with the above-mentioned compression type refrigeration system and a concentration difference heat storage system, and specifically, the method is based on data regarding cooling load fluctuation factors. , predict the cooling load on the target day,
If the refrigerant is not subcooled by the subcooler on the target day based on the difference between the predicted cooling load and the cooling capacity that would be obtained assuming that the subcooler does not subcool the refrigerant. Calculate the amount of heat that is required in the concentration difference heat storage system in order to compensate for the calculated amount of insufficient heat by supercooling the refrigerant using the supercooler. The heat storage operation period in the concentration difference heat storage system is set based on the difference between the required heat storage amount and the actual heat storage amount in the concentration difference heat storage system, and the concentration difference heat storage system is caused to perform heat storage operation during the set heat storage operation period. be done.

[Effect]

In the cold heat generation equipment according to the present invention having the above-described configuration, the refrigerant cooled by the condenser in the compression refrigeration system is further cooled by the subcooler, so that the refrigerant is evaporated by the evaporator. The amount of latent heat of vaporization increases, the amount of enthalpy change in the evaporation process increases, and as a result, the cooling capacity increases.

Furthermore, by using the cooling water whose temperature has been lowered by the latent heat of evaporation of the heating medium during the heat dissipation operation of the concentration difference heat storage system to cool the refrigerant in the supercooler installed in the compression type refrigeration system, It becomes possible to lower the temperature of the refrigerant to the required temperature using the supercooler only when necessary.

Furthermore, in the concentration difference heat storage system, when the heat radiation operation section and the heat storage operation section are provided separately, the heat radiation operation and the heat storage operation can be performed simultaneously and continuously.

On the other hand, by predicting the cooling load and setting the heat storage operation period, the operation period (1) of the concentration difference heat storage system is made the minimum necessary period, and energy saving is achieved.

(Example〕 Embodiments of the present invention will be briefly described below with reference to the drawings.

FIG. 1 shows an embodiment of cold generation equipment according to the present invention,
The cold heat generation equipment of this example includes a compression type refrigeration system 10, a concentration difference heat storage system 30, and a cold water tower 25 which is a common part thereof.

The compression type refrigeration system 10 includes a compressor 12 driven by an electric motor 11, and cooling water and refrigerant that are cooled by the atmosphere in a cooling tower 25 placed on the roof of a building and supplied through a pump 26 and a pipe 2I. a condenser 14 for exchanging heat with the liquid receiving tank 16, an expansion valve 17, an evaporator 18 for exchanging heat between the cold water to be supplied to the cooling light and the refrigerant, and an accumulator 1.
9 has refrigerant circulation passages 20 arranged sequentially along the flow direction of the refrigerant, and the condenser 1 in this refrigerant circulation passage 20
A supercooler 15 for further cooling (supercooling) the refrigerant cooled by the condenser is disposed downstream of the refrigerant 4 . In addition,
In such a compression type refrigeration system 10, a refrigerant circulation passage 20
R-22, which is generally used as a refrigerant sealed in
(Freon 22) is used.

On the other hand, the concentration difference heat storage system 30 includes a heat storage and radiation container 40, a heat storage material storage tank 41, a heat medium storage tank 42, pumps 45, 46, 55,
It has an auxiliary heat exchanger 39 and the like. Heat storage and radiation container 40
, the first heat exchange chamber 31 and the second heat exchange chamber 32 are connected to the partition wall 3.
The first heat exchange chamber 31 is provided with a heat exchanger 35 for heat storage material and a heat storage material dispersion device 43, and the second heat exchange chamber 32 is provided with a heat exchanger 36 for heat medium and a heat exchanger 36 for heat storage material. A heat medium diffuser 44 is arranged.

One end of the heat exchanger 35 for heat storage material is connected to a supply boat of the cooling tower 25 via a pipe 53 and a pump 26 in which a three-way valve 56 is arranged, and a hot water supply pipe via the three-way valve 56. 58, and the other end is connected to the inlet boat of the cooling tower 25 via the downstream portion of the pipe 54 and the pipe 48, in which the three-way valve 57 is disposed, and the three-way valve 57
The heat exchanger 36 for heat medium can be connected to the hot water discharge pipe 59 via the three-way valve 51.
The cooling tower 25 is
can be connected to the supply boat of the supercooler 15 through the three-way valve 51 and the pipe 61, and to the introduction boat of the supercooler 15,
The other end is connected to the introduction boat of the cooling tower 25 via a pipe 48 in which a three-way valve 52 is disposed, and the three-way valve 52.
Pump 55. It can be connected to the outlet boat of the subcooler 15 via a conduit 62.

In addition, in the concentration difference heat storage system 30, a lithium bromide aqueous solution is used as a heat storage material (absorbing material), and water is used as a heat medium.

In the concentration difference heat storage system 30 having such a configuration,
A heat storage operation for concentrating the heat storage material and a heat dissipation operation for diluting the heat storage material are selectively performed. The heat storage operation and the heat radiation operation will be explained below.

Heat storage operation: When this is done, the three-way valve 56, 57° 51.52
is connected as shown by the solid line in FIG. 1, and the pump 45 is driven, but the pump 46 is stopped. As a result, hot water etc. heated by an external heating source are supplied to the heat exchanger 35 for heat storage material via the pipe line 58, and the heat storage material in the heat storage material storage tank 41 is transferred to the auxiliary heat exchanger 39. After being heated through heat exchange with the heat storage material from the heat exchange chamber 31 and raised in temperature, the first
It is dispersed into the heat exchange chamber 31. As a result, the heat storage material is heated and the moisture (heat medium) contained therein evaporates. In this case, since the cooling water from the cold water tower 25 is supplied to the heat exchanger 36 for heat medium, the moisture evaporated from the heat storage material is condensed and stored in the heat medium storage tank 42.

Therefore, the heat storage material that has been concentrated by evaporation of water is
This means that the ability to absorb moisture (water vapor) as a heat medium has been increased, or in other words, heat has been stored.

Note that the external heating source for heat storage operation is exhaust heat.

Any one of solar heat, heated waste water, waste combustion heat, and fossil fuel combustion heat is used.

Further, during such heat storage operation, the compression type refrigeration system 10 and the concentration difference heat storage system 30 are in a state of being separated, and the supercooler 15 is not substantially present in the compression type refrigeration system 10.

Heat dissipation operation: When this is turned on, the three-way valve 56,5751.52
are connected as shown by broken lines in FIG. 1, and in addition to pump 45, pump 46 is also driven. As a result, the cooling water from the cold water tower 25 is supplied to the heat exchanger 35 for heat storage material via the pipe 53, and the heat storage material in the heat storage material storage tank 41 is first heat exchanged in the auxiliary heat exchanger 39. After exchanging heat with the heat storage material from the chamber 31 and lowering the temperature, it is guided to the heat storage material dispersion device 43 and transferred to the first heat exchange chamber 31.
be dispersed.

On the other hand, in such a case, the heat exchanger 36 for heat medium and the subcooler 1
5 are connected to each other, cooling water is circulated between them, and the water in the heat medium storage tank 42 is guided by the pump 46 to the heat medium distribution device 44 via the pipe line 38, and the second heat exchange chamber 32 distributed within.

Under such conditions, the pressure inside the heat storage and heat dissipation container 4° is reduced, so that a situation is created in which the water sprayed from the heat medium sprayer 44 is likely to evaporate. As a result, the water evaporates violently, and the latent heat of evaporation causes the heat exchanger 36 for the heat medium to
The cooling water flowing therein is deprived of heat and lowered in temperature, and the cooled water is supplied to the supercooler 15, and in the supercooler 15, the coolant circulation passage 20 cooled by the condenser 14 is cooled. of refrigerant will be further cooled. Then, the refrigerant supercooled by the supercooler I5 is transferred to the expansion valve 1
7, the temperature and pressure are lowered and the cooled water is led to the evaporator 18. In the evaporator 18, heat is taken from the cold water that has returned from the cooling end through the pipe 23, and the water is evaporated. be guided. Furthermore, the cooled water that has been deprived of heat is sent to the cooling destination again through the pipe line 24.

Next, the effects of supercooling the refrigerant circulating in the refrigerant circulation passage 20 by the supercooler 15 as described above will be explained with reference to the Mollier diagram for R-22 in FIG. 3.

The refrigerant compressed by the compressor 12 is at a high temperature (approximately 90"C) and a high pressure (approximately 26 kg/cii) as shown at point A in FIG.
) is introduced into the condenser 14, and the condenser 1
The temperature is about 60°C, the pressure is about 26kg/cd, as shown by point Ba, and the temperature is about 60°C, and the pressure is about 26kg/cd. It becomes a saturated liquid. On the other hand, the cooling water is returned to the cooling tower 25 through the pipe 22, where it is cooled by the atmosphere and supplied to the condenser 14 again.

The refrigerant that has become a saturated liquid is introduced into the supercooler 15. As mentioned above, the supercooler 15 is supplied with cooling water whose temperature is lowered to about 10"C by the latent heat of vaporization of the heating medium (water) during the heat dissipation operation of the concentration difference heat storage system 30. Therefore, the refrigerant is further cooled to a temperature of about 20"C as shown by point Be, and is introduced into the evaporator 18 via the liquid receiving tank 16 and the expansion valve 17 as described above.
There, as shown at point Cc, the pressure is about 5 kg/
crMl becomes a saturated gas with a temperature of about O'C.

On the other hand, in the basic system (Comparative Example 1) in which the supercooler 15 is removed from the compression refrigeration system 10 shown in FIG.
The temperature of the refrigerant at the outlet of the condenser is approximately 60°C,
The state change of the refrigerant connects A-Ba-Ca-D in Fig. 3, and as shown in Fig. 5 described above, a heat exchanger for hot water extraction is arranged in the front stage of the condenser. In (Comparative Example 2), the cooling water used in the condenser is cooled by the atmosphere, so the temperature of the refrigerant at the outlet of the condenser is limited to approximately 40°C, and the change in the state of the refrigerant occurs only after a short period of time. In Figure 3, it connects A-Bb-Cb-D.

Here, the amount of heat contributing to cooling is Ca, C
This is the difference between the enthalpy at each point b and Cc and the enthalpy at point D, that is, the difference in the amount of latent heat of vaporization of the refrigerant. In this case, ■Comparative example 1 -------・-149-119=30■Comparative example 2-・-141-112=37■This example ---
--149-105=44 (all units are kcal/
kg), and the input to the compressor 12 is 158 14
Since 9=9 (kcal/kg) is common, the respective coefficients of performance are 3.3 for ■, 4.1 for ■, and 4.9 for ■, and even under the same specifications and conditions, the present invention It is understood that such a system can provide over 30% more cooling output than the basic system.

The cold water production capacity of the compression type refrigeration system 10 in this example is the difference in the amount of heat shown between Ba and Ba in FIG. 3, which is about 1/3 of the amount of cooling heat in the condenser 14.

Next, a method of operating the cold heat generating equipment shown in FIG. 1 mentioned above will be explained.

First, when the cooling load is not very large (that is, when the cooling capacity obtained assuming that the refrigerant is not supercooled by the supercooler 15 is sufficient to satisfy the cooling load, It is not necessary to perform a heat dissipation operation only by performing a heat storage operation as appropriate in the concentration difference heat storage system 30.

On the other hand, when the cooling load increases significantly in the middle of summer, etc., the cooling load on the target day is determined based on data on cooling load fluctuation factors on the target day (e.g., the next day), such as the situation of gathering of one person due to the weather, etc. Based on the difference between the predicted cooling load and the cooling capacity obtained assuming that the refrigerant is not subcooled by the subcooler 15, the amount of refrigerant used by the subcooler 15 on the target day Calculate the amount of heat that would be insufficient if supercooling is not performed. In other words, it is predicted that the cooling load on the target day will change over time as shown in Figure 4, and the cooling capacity obtained under the assumption that the refrigerant will not be supercooled by supercooler 5 will be S
In this case, the amount of heat is insufficient in the area indicated by hatching in the figure.

In this way, after the insufficient amount of heat is calculated, the amount of heat storage required in the depth difference heat storage system 30 is calculated in order to compensate for the insufficient amount of heat by supercooling the refrigerant by the supercooler 15. calculate. Then, a heat storage operation period in the concentration difference heat storage system is set based on the difference between the calculated required heat storage amount and the actual heat storage amount in the concentration difference heat storage system.

In that case, the actual amount of heat storage in the concentration difference heat storage system 30 is
For example, the concentration and amount of the heat storage material in the heat storage material storage tank 41 can be measured and calculated based on the measurement results. During the heat storage operation period set in this way, the concentration difference heat storage system 30 performs heat storage operation, and the cooling load is obtained assuming that the refrigerant is not supercooled by the supercooler 15. When it is predicted that the temperature will exceed the capacity, the concentration difference heat storage system 30 is caused to perform a heat dissipation operation. In that case, switching between the heat storage operation and the heat dissipation operation can be achieved by switching the connection state or operating state of the three-way valves 56, 57, 57, 52, the pumps 45, 46, 55, etc. as described above.

Note that switching between heat storage operation and heat dissipation operation in the concentration difference heat storage system 30 as described above can be achieved by, for example, installing a control unit using a microcomputer or the like, and inputting data regarding cooling load fluctuation factors into this control unit. This allows the control unit to predict the cooling load on the target day, based on the difference between the predicted cooling load and the cooling capacity obtained assuming that the refrigerant is not supercooled by the supercooler 15. Calculate the amount of heat that would be insufficient if the refrigerant is not supercooled by the supercooler 15 on the target day, and transfer the calculated amount of insufficient heat to the supercooler 15.
Calculation of the amount of heat storage required in the concentration difference heat storage system 30 to compensate by supercooling the refrigerant, and the difference between the calculated required heat storage amount and the actual heat storage amount in the concentration difference heat storage system 30. The setting of the heat storage operation period in the concentration difference heat storage system 30 based on When it is predicted that the cooling capacity will be greater than that obtained under the assumption that there is no cooling capacity, it is also possible to automate the piping system control that causes the concentration difference heat storage system 30 to perform heat dissipation operation.

Further, in the above example, by changing the subcooling temperature of the refrigerant by the subcooler 15, the cooling capacity can be made variable without changing the discharge capacity of the compressor 12, etc.

Specifically, for example, adjusting the amount of heat storage material and/or heat medium sprayed from the heat storage material spreader 43 and/or heat medium spreader 44 to adjust the amount of evaporation of the heat medium; The refrigerant cooling capacity of the supercooler 15 is adjusted by changing the flow rate of the cooling water flowing through the heat exchanger 35 and/or the heat exchanger 36 for heat medium, thereby changing the cooling capacity of the compression refrigeration system 10. becomes possible.

In addition, if there is a surplus in the amount of heat stored in the concentration difference heat storage system 30, as shown by the dashed line in FIG. , a cold water return pipe 65 may be connected to supply the cooling water obtained by the heat medium heat exchanger 36 to the cooling light.

Next, another embodiment of the present invention will be described with reference to FIG.

In this example, parts corresponding to those shown in FIG. 1 are given the same reference numerals, and detailed explanation thereof will be omitted.

This example differs greatly from the one shown in FIG. 1 because, in the concentration difference heat storage system 30, a heat storage operation container 80 and a heat radiation operation container 70 are provided separately, and heat storage operation and heat radiation operation are performed in parallel. The main point is that it can be executed by

In addition, in the compression type refrigeration system 10, the refrigerant is circulated through a salt water extraction heat exchanger 13 similar to the hot water extraction heat exchanger 113 shown in FIG. The pipes 23.2 and 23.2 are arranged upstream of the condenser 14 in the pipes 23.2 and 23.2, respectively, to supply cold water and take out hot water.
4, and the other parts are constructed in the same way as shown in FIG.

The heat radiation operation container 70 in the concentration difference heat storage system 30 includes a partition wall 73. First heat exchange chamber 71. Second heat exchange chamber 72. Heat exchanger for heat storage material 75. Heat medium heat exchanger 76, heat storage material spreader 7
7, a heat medium diffuser 78 is provided, and the heat storage operation container 8o is provided with a partition wall 83. First heat exchange chamber 81. Second heat exchange chamber 82° heat exchanger for heat storage material 85. A heat exchanger 86° for heat medium and a heat storage material spreader 84 are provided.

The cold water from the cold water tower 25 is supplied to the heat exchanger 75 for heat storage material in the container 7o for heat dissipation operation, and the cold water is passed through the pipe 91 to the heat exchanger 86 for heat medium in the container 80 for heat storage operation. The inlet boat and the outlet boat of the heat medium heat exchanger 76 are connected to the outlet boat and the inlet boat of the supercooler 15 via the conduits 62 and 61, respectively. , cooling water is circulated by a pump 55 within the circulation path formed by them. Further, hot water or the like heated by the above-mentioned external heating source is supplied to and discharged from the heat exchanger 85 for heat storage material in the container 80 for heat storage operation through the pipes 58 and 59.

In the cold heat generating equipment configured in this way, the heat storage operation and the heat dissipation operation can be performed simultaneously and continuously. Therefore, when the amount of heat generated by the heat source for heating the heat storage material is insufficient, the heat storage operation is continuously executed to store the concentrated heat storage material in the heat storage material storage tank 41, and the heat dissipation operation is performed as necessary. can be executed to supply cooling water to the supercooler 15, thereby making it possible to increase the cooling capacity of the compression refrigeration system 10 whenever necessary.

〔Effect of the invention〕

As is clear from the above explanation, in the cold heat generating equipment according to the present invention, the refrigerant cooled by the condenser in the compression type refrigeration system is further cooled by the supercooler, so that the refrigerant when evaporated by the evaporator is The amount of latent heat of evaporation of the refrigerant increases, and the amount of enthalpy change in the evaporation process increases, resulting in improved cooling capacity.

In addition, cooling water whose temperature has been lowered by the latent heat of evaporation of the heating medium during the heat dissipation operation of the concentration difference heat storage system is used to cool the refrigerant in the supercooler installed in the compression refrigeration system. This makes it possible to lower the temperature of the refrigerant to the required temperature using the supercooler only when the cooling load is at its maximum, eliminating the need to set the compressor capacity etc. according to when the cooling load is at its maximum. Energy saving can be achieved without increasing complexity.

Furthermore, in the concentration difference heat storage system, when the heat radiation operation section and the heat storage operation section are provided separately, the heat radiation operation and the heat storage operation can be performed simultaneously and continuously.

On the other hand, by predicting the cooling load and setting the heat storage operation period, the operation (II!tJI) of the concentration difference heat storage system is minimized, reducing operating costs and saving energy.

[Brief explanation of drawings]

FIG. 1 is an overall configuration diagram showing an example of the cold heat generating equipment according to the present invention, FIG. 2 is an overall configuration diagram showing another example of the cold heat generating equipment according to the present invention, and FIG. 3 is an operation/operation of the present invention. FIG. 4 is a diagram used to explain the operation of the example shown in FIG. 1, and FIG. 5 is a diagram used to explain the conventional cooling and heat generating equipment. The symbols and names of parts in the figure correspond as follows. 10-compression refrigeration system, 12-compressor 14-condenser, 15--supercooler, 18-evaporator, 20-refrigerant circulation passage 25-chilling water tower, 3o-concentration difference heat storage system 40-thermal storage Container for heat radiation 70 - Container for heat radiation action 80 - Container for heat storage action

Claims (1)

[Claims] 1. In a cold heat generation facility having a refrigerant circulation passage in which a compressor, a condenser, an expansion valve, and an evaporator are sequentially arranged, the condenser cools the cooling water obtained by being cooled by the atmosphere. the refrigerant in the refrigerant circulation passage, and a compression type refrigeration system in which a supercooler is disposed downstream of the condenser in the refrigerant circulation passage to further cool the refrigerant. Cold heat generating equipment characterized by: 2. In addition to the compression type refrigeration system according to claim 1, a concentration difference that performs a heat storage operation in which the absorbed heat medium is evaporated and separated from the heat storage material, and a heat radiation operation in which the heat medium is evaporated and absorbed into the heat storage material. A heat storage system is provided, and the cooling water whose temperature is lowered by the latent heat of evaporation of the heating medium during the heat dissipation operation of the concentration difference heat storage system is used to cool the refrigerant in the supercooler disposed in the compression refrigeration system. Cold and heat generating equipment characterized by: 3. The cold heat generation equipment according to claim 2, wherein the supply of cooling water to the condenser in the compression type refrigeration system and the supply of cooling water to the concentration difference heat storage system are performed from a common cooling water tower. 4. The cold heat generating equipment according to claim 2, wherein in the concentration difference heat storage system, a heat radiation operation section and a heat storage operation section are provided separately, so that the heat radiation operation and the heat storage operation can be executed in parallel. 5. The heat source for heat storage operation in the concentration difference heat storage system is exhaust heat,
3. The cold heat generating equipment according to claim 2, wherein the cold heat generation equipment is any one of solar heat, waste hot water, waste combustion heat, and fossil fuel combustion heat. 6. Cooling load prediction means for predicting the cooling load on the target day based on input data regarding cooling load fluctuation factors, and cooling load predicted by the cooling load prediction means and supercooling of refrigerant by a supercooler. a heat deficit calculating means for calculating a heat deficit when the refrigerant is not supercooled by a supercooler on a target day based on the difference between the cooling capacity obtained under the assumption that the cooling capacity is not supercooled; a necessary heat storage amount calculation means for calculating the amount of heat storage required in the concentration difference heat storage system in order to compensate for the insufficient heat amount calculated by the calculation means by supercooling the refrigerant by a supercooler; a heat storage operation period setting means for setting a heat storage operation period in the concentration difference heat storage system based on the difference between the required heat storage amount calculated by the heat storage amount calculation means and the actual heat storage amount in the concentration difference heat storage system; 3. The cold heat generation equipment according to claim 2, further comprising piping system control means for causing the concentration difference heat storage system to perform heat storage operation during the heat storage operation period set by the means. 7. Based on the data on cooling load fluctuation factors, predict the cooling load on the target day, and compare the predicted cooling load with the cooling capacity that would be obtained assuming that the refrigerant is not overcooled by the supercooler. Based on the difference, calculate the amount of heat that would be insufficient if the refrigerant was not supercooled by the supercooler on the target day, and compensate for the calculated lack of heat by supercooling the refrigerant using the supercooler. The heat storage amount required in the concentration difference heat storage system is calculated, and the heat storage operation period in the concentration difference heat storage system is set based on the difference between the calculated required heat storage amount and the actual heat storage amount in the concentration difference heat storage system. 3. The method of operating a cold heat generation facility according to claim 2, wherein the set heat storage operation period causes the concentration difference heat storage system to perform a heat storage operation.