JP2008025973A - Heat exchange system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchange system, to which gas brine, high-pressure fluid or supercritical fluid can be applied. <P>SOLUTION: In the heat exchange system, a high temperature-side heat exchanger 4 for absorbing heat and a low temperature-side heat exchanger 3 for releasing heat are mutually connected through a conduit 5 in a closed loop environment, and a medium composed of high-pressure gas brine such as carbon dioxide gas, methane, ethane or air is sealed in the closed loop environment while preventing its phase change. One of both the heat exchangers is disposed as a using-side heat exchanger, and the other as a heating source-side heat exchanger, and at least the heat source-side heat exchanger is formed of a heat exchanger including a number of thin flow passages 22 connected with the conduit. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a heat exchange system that performs heat exchange basically using a gaseous brine without causing a phase change.

Conventionally, a refrigerator or an air conditioner, a refrigerator, or a heat pump uses a refrigerant or a heat medium that generates a large amount of heat of evaporation when a liquid changes phase to a gas. As this refrigerant, for example, ammonia, methyl claloid, Freon F-11, and Freon F-22 are used, and in addition to these gases, carbon dioxide (CO ₂ ) is also used.

  In a high-temperature heat exchanger such as a nuclear power plant, sodium (melting point = 97.8 (° C.), boiling point = 760 (° C.)), sodium-potassium alloy (melting point = 19 (low melting point) and high boiling point. ° C), boiling point = 825 (° C)) and the like are used.

  On the other hand, as a medium for transferring heat, in addition to a refrigerant or a heat medium, brine (a medium in which a phase state is not converted between gas and liquid) is used. The types of brine can be divided into liquid brine and gas brine.

  As the liquid brine, for example, liquids such as water, inorganic brine (calcium chloride solution, magnesium chloride solution), organic brine (ethylene glycol, propylene glycol) and the like are used. The water as the liquid brine is used for cooling an automobile engine, for example, and enables appropriate temperature management of the automobile engine. On the other hand, an engine for a motorcycle is an open heat exchange system by air cooling, but water is also used as a liquid brine.

  The gas brine is excellent in thermal stability (characteristic that does not decompose by heat), safety (no toxicity), and viscosity coefficient (pressure loss during circulation (energy loss)). As this gas brine, there is, for example, water vapor (constant pressure specific heat = 2.05 (J / g / ° C.) at 100 (° C.)). This water vapor is a very stable brine and is an excellent medium that is also utilized as a high temperature brine. The water vapor as the gaseous brine is used for boilers, steam heaters, and the like, for example.

  However, in the above-mentioned gas brine, boilers and steam heaters that use water vapor make good use of the phase change between water vapor and water when considered as a whole system. It is not a system that uses. In addition, as in the case of water vapor, there is no example in which carbon dioxide gas having an effect of absorbing and radiating radiant heat is used as a brine.

Moreover, the technique which comprises a heat exchanger by several lotus root-shaped pore flow paths is proposed (for example, refer patent document 1-patent document 3). In this technique, by providing a plurality of fine pore channels having a diameter of about 20 μm, the total area of the channel cross-sectional area (heat exchange area A) of the pore channels through which the brine is sent can be increased. it can.
Japanese Patent No. 3040371 Japanese Patent Application No. 2000-26223 Japanese Patent Application No. 2001-247144

  As described above, at present, liquid brine is used, but gas brine is not used. Conventionally, for example, for use in automobile engines, nuclear power plants, etc., as a suitable heat transfer medium in the system, the specific heat is large, the thermal conductivity is large, the specific weight is large, the viscosity coefficient is small, A stable and safe medium that becomes liquid at low filling pressures is desired. However, basically, there is no gas as an optimal brine that satisfies these characteristics, and the specific weight and thermal conductivity are significantly inferior to water. It is no exaggeration to say that the viscosity coefficient is only small.

That is, the following two reasons (1) and (2) can be cited as reasons why the gas brine is not used.
(1) “Product of specific weight Cp × specific heat γ” is about 1/200 to 1/300 times smaller than the liquid, that is, “heat capacity” is small.

This is because the “heat exchange amount dQ (kJ / s)” is the specific heat of the medium “Cp (kJ / kg / k)”, the specific weight “γ (kg / m ³ )”, and the volume flow rate “dV ( m ³ / s) ”and the temperature difference is“ ΔT (k) ”, the heat exchange amount is given by the following equation.

dQ = (Cp × γ) × dV × ΔT (A)
As in the above equation, in order to obtain the same “dQ” with the same “ΔT”, the flow rate dV must be increased by the proportion of (Cp × γ), but this flow rate dV is increased by 200 times. It is practically impossible to increase it by ˜300 times or more (in order to obtain the same performance as water when the liquid brine is water, approximately 4000 times the flow rate dV is required).
(2) The “thermal conductivity” of gas is smaller than that of liquid.

  When considering heat exchange dQ, assuming that the heat transfer rate is H, the heat exchange area (area where the brine is in contact with the pipe) is A, and the temperature difference is ΔT, the relationship with the heat transfer rate is given by the following equation.

dQ = H × A × ΔT (B)
(Where H = 1 / (1 / α + L / λ), α = heat transfer coefficient, L = thickness, λ = heat conductivity)
As in the above formula, the actual heat transmission rate is composed of “thermal conductivity, heat transfer rate”, but here, when considered simply as “H∝λ”, ΔT is the same as In order to equalize the heat exchange amount dQ of “carbon dioxide gas” with respect to “water”, “A” water / “A” carbon dioxide gas = 2.2 / 600 = 1/273. As is clear from this, when carbon dioxide is used as it is, a heat exchange area 273 times that of water is required. This value is also difficult from the current heat exchanger structure.

  The present invention has been made in view of the above-described circumstances, and enables the application of a gas brine, a high-pressure fluid, or a supercritical fluid without enlarging the entire system, and for feeding these gas brines and the like. It aims at providing the heat exchange system which can reduce motive power.

  In the present invention, a high-temperature side heat exchanger that absorbs heat and a low-temperature side heat exchanger that releases heat are connected in a closed loop environment via a pipe, and carbon dioxide, methane, ethane, or A medium composed of high-pressure gas brine such as air is circulated in a state that does not cause a phase change, and either one of the two heat exchangers is a heat exchanger on the use side, and the other is a heat exchanger on the heat source side. And at least the heat source side heat exchanger is constituted by a heat exchanger provided with a large number of pore flow channels connected to the pipe line.

  According to this configuration, even if high-pressure gas brine is used, heat exchange can be performed without increasing the size of the entire system.

  Further, in the present invention, a high-temperature side heat exchanger that absorbs heat and a low-temperature side heat exchanger that releases heat are connected in a closed loop environment via a pipeline, and ethane, propane, ethylene is connected in the closed loop environment. A medium consisting of high-pressure liquid such as carbon dioxide is circulated in a state that does not cause a phase change, and either one of the two heat exchangers is used as the heat exchanger on the use side, and the other is used as the heat exchange on the heat source side. And at least the heat source side heat exchanger is constituted by a heat exchanger provided with a large number of pore channels connected to the pipe line.

  According to this configuration, even if a high-pressure fluid is used, heat exchange can be performed without enlarging the entire system.

  Further, in the present invention, a high-temperature side heat exchanger that absorbs heat and a low-temperature side heat exchanger that releases heat are connected in a closed loop environment via a pipeline, and ethane, propane, ethylene is connected in the closed loop environment. A medium composed of a supercritical fluid such as carbon dioxide or water is circulated in a state that does not cause a phase change, and either one of the two heat exchangers is used as a heat exchanger and the other is used as a heat source side. And at least the heat exchanger on the heat source side is configured by a heat exchanger having a large number of pore channels connected to the pipe.

  According to this configuration, even if a supercritical fluid is used, heat exchange can be performed without enlarging the entire system.

  In this case, the pore diameter of the pore channel is formed so that the heat exchange area of the pore channel is larger than the heat exchange area of the channel when the pore channel is not provided.

  According to this configuration, the heat exchange area can be reduced by setting the pore diameter of the pore flow channel to be smaller than, for example, φ2 to 20 μm or less, which is the smallest diameter currently used in automobile radiators. Can be bigger.

  Further, the heat exchanger on the use side and the heat exchanger on the heat source side are arranged vertically, and the pipe connecting the both heat exchangers can be constituted by a central axis tube and a double tube of an outer tube surrounding the periphery. .

  According to this configuration, it is possible to eliminate the need for a device for forcibly sending the gas brine or the like by generating an upward flow and a downward flow.

  Furthermore, a piston or impeller composed of a permanent magnet or the like is included in the pipe line, and an electromagnet that drives the piston or impeller for circulation is arranged outside the pipe line, and the piston or impeller is driven by driving the piston or impeller. The medium can be circulated.

  According to this configuration, it is possible to configure a completely sealed structure heat exchanger using a simple composition of gas brine that does not denature.

  Furthermore, an open valve that is opened when the pressure in the pipe line reaches an abnormally high pressure can be connected to the pipe line, and a box that expands the medium can be connected to the open valve.

  According to this structure, the safety system which prevents the abnormal high voltage | pressure in a pipe line can be provided.

  The low temperature side heat exchanger may be an engine cooling jacket.

  According to this configuration, the present system can be used for engine cooling.

  The low temperature side heat exchanger may be disposed in the computer heat generation unit.

  According to this configuration, the present system can be used for cooling the computer heat generation unit.

  According to the present invention, since the gas brine is used, even if the pore channel is used, the pressure loss due to the viscosity coefficient of the gas brine is small, and there is no risk of deposit formation or clogging due to the modification of the gas brine. . Therefore, a large heat exchange area can be secured by using the pore channel. As a result, it is not necessary to enlarge the entire system in order to increase the heat exchange area. Further, by performing heat exchange using a gas brine having a small viscosity coefficient, power for sending the gas brine can be reduced. Further, carbon dioxide and other gases such as methane and ethane can be used effectively.

  Further, according to the present invention, since a high-pressure liquid or a supercritical fluid is used, even if a pore channel is used, the pressure loss due to the viscosity coefficient of the gas brine is small, the formation of deposits due to the modification of the gas brine, There is no risk of clogging. Therefore, a large heat exchange area can be secured by using the pore channel. As a result, it is not necessary to enlarge the entire system in order to increase the heat exchange area. Further, by performing heat exchange using a gas brine having a small viscosity coefficient, power for sending the gas brine can be reduced. Further, carbon dioxide and other gases such as methane and ethane can be used effectively.

  FIG. 1 is a schematic diagram of a “sealed cycle”, which is a heat exchange system according to an embodiment of the present invention, in which gas brine is sent using a blower. A technique for enabling application of “gas brine” will be described with reference to FIG.

  As shown in FIG. 1, the heat exchange system 1 is connected to a blower 2 for sending a gas brine, a low-temperature side heat exchanger 3 connected to a low temperature region (outside air region) for radiating heat, and a high temperature region. And a high temperature side heat exchanger 4 that absorbs heat. A heat exchange unit 6 is provided in each of the low temperature side heat exchanger 3 and the high temperature side heat exchanger 4. Further, the blower 2, the heat exchange unit 6 of the low temperature side heat exchanger 3, and the heat exchange unit 6 of the high temperature side heat exchanger 4 are respectively connected by a flow path (pipe) 5 to form a circulation path in a closed loop environment. Has been. The flow path 5 is filled with a gas brine, and the gas brine sent by the blower 2 circulates in the circulation path.

  In FIG. 1, the blower 2 is configured to draw heat from the high temperature side 10 and to release heat from the low temperature side 11 by being sent clockwise. Further, by sending it counterclockwise, heat is absorbed from the low temperature side 11 and heat can be released on the high temperature side.

  2A is a side sectional view showing a heat exchange unit 6 used in the low temperature side heat exchanger 3 and the high temperature side heat exchanger 4, and FIG. 2B is a cross section of FIG. 2A. FIG.

  As shown in FIGS. 2A and 2B, the heat exchange unit 6 includes a plurality of stainless steel pipes 21 through which gas brine passes (19 pipes 21 in FIG. 2B). For example, it can be 10,000 or more). The stainless steel (other than metal) pipe 21 is provided with a through hole (pore channel) 22. For example, in the case of the current technology, the pore channel 22 has a diameter of about 0.02 mm (about 20 μm). In the future, if the diameter is about 0.001 mm (about 1 μm) or less, it can be realized, and a pressure resistance performance exceeding about 100 MPa can be secured. These pore channels 22 are connected to the channel 5 respectively. In addition, the shape in the cross section orthogonal to the longitudinal direction of the pore channel 22 may be a shape other than a round shape, for example, a rectangle or other shapes as long as it can be manufactured.

  These stainless steel (including metal) pipes 21 are accommodated in a large stainless steel outer tube 23, and a gap between the outer surface of the plurality of stainless steel pipes 21 inside the outer tube 23. Is filled with a metal gap filling material 24. The metallic gap filling material 24 is a powdery material such as aluminum, tin, lead, brass, silver, gold, copper or the like having a melting point lower than that of the stainless steel outer tube 23. Is melted at a melting temperature and filled in a porous shape.

  In this heat exchange unit 6, when the gas brine is sent to all the through holes 22, the heat of the gas brine is transferred to the porous metal gap filling material 24 with excellent thermal conductivity. Further, since the filling portion of the metallic gap filling material 24 is porous and has a large heat exchange area, the filling portion of the metallic gap filling material 24 includes, for example, air or hydrogen. If a fluid such as air is flowed, fluid such as air or hydrogen can be heated or cooled with extremely high heat exchange efficiency.

  In addition, the structure of the heat exchange unit 6 mentioned above is an example, and the structure of the other heat exchange unit provided with the pore flow path 22 is also included in the technical idea of this Embodiment. For example, as shown in FIG. 3, the heat exchanger unit 25 is configured by disposing a metal rope-shaped heat exchange element 26 inside a tube body 29. The heat exchange element 26 includes a plurality of flow paths, and heat exchange is performed through a medium in the flow paths. As shown in FIG. 4, the rope-shaped heat exchange element 26 is formed by twisting a plurality of (for example, six) thin tubes 27 made of stainless steel (including other metal) having a flow path through which a medium passes. (For example, three) basic materials 28 are formed, and each basic material 28 is further twisted. According to this manufacturing method, the rope-shaped heat exchange element 26 having a large number of pore channels 22 can be easily manufactured. Moreover, even if it is another structure, if it increases a heat exchange area, it is contained in the technical idea of this Embodiment.

  “Stable gas brine that is not heat denatured” is used as the gas brine to be sent. Since this gas brine has the advantage that the viscosity coefficient is lower than that of the liquid brine, the pressure loss due to the viscosity coefficient, which is a problem when using the liquid brine, and the formation and clogging of deposits due to the modification of the heat medium are large. The problem can be solved. In addition, a wide range of heat exchange systems ranging from −200 ° C. to 1500 ° C. is made possible by taking advantage of the stability without heat denaturation.

For example, carbon dioxide (CO ₂ ), methane, ethane, or air is used as the gas brine. For example, the carbon dioxide gas is a supercritical fluid that has been processed at a high temperature (for example, 1500 ° C., which is the melting point of carbon dioxide gas) and at a high pressure (for example, 100 MPa or more). In addition, this carbon dioxide gas can be substituted for methane, ethane, air or the like in a temperature environment that reaches a supercritical fluid.

  In addition to gas brine, a medium composed of a high-pressure liquid such as ethane, propane, ethylene, carbon dioxide, or a medium composed of a supercritical fluid such as ethane, propane, ethylene, carbon dioxide, water can be sent.

According to the heat exchange system 1 based on such a configuration, for example, when N = 10,000 fine pore channels 22 are formed, the heat exchange area A (channel area A) is √ of a single tube. Since N times = 100 times, dQ also becomes 100 times under the same conditions. Therefore, in the high pressure resistance performance up to 100 MPa, the basic formula of heat transfer dQ = C × A × ΔT
(DQ = amount of heat transferred per unit time, C = heat transfer coefficient, A = heat exchange area, ΔT = heat exchange temperature difference)
, Gas brine is filled and circulated in the form of high pressure “gas” / high pressure “liquid” / high pressure “supercritical fluid”, from the “refrigerant” region (−200 ° C. or higher) to the “heat medium” region. It can be applied in a wide range (1500 ° C. or less).

When this flow path cross-sectional area A is estimated, for example, as an example equivalent to the flow path cross-sectional area A0 of “radiation tube of diameter 8 mm × 20 pipes × L300 mm” as a typical example of an automobile radiator, “20 μm pore The ratio α1 of the channel cross-sectional area A1 of the heat exchange element (MT) having a multi-tube structure of “channel × L300 mm” is
α1 = A1 / A0
= Number of MT-type flow paths x MT-type heat exchange area / heat-exchange area of commercial radiator = (8 ² x 20 / 0.02 ² ) x (0.02π x 300) / (8π x 20 x 300)
= 400 times. That is, heat exchange as large as 400 times is possible.

Further, the ratio α2 of the channel cross-sectional area A2 of the heat exchange element (MT) having a multi-tube structure in which the pore channel 22 is configured with a diameter of 1 μm is:
α2 = A2 / A0
= Number of MT-type flow passages x MT-type heat exchange area / heat exchange area of commercially available radiator = (8 ² × 20 / 0.001 ² ) × (0.001π × 300) / (8π × 20 × 300)
= 8000 times, that is, heat exchange as large as 8000 times becomes possible.

  On the other hand, the viscosity coefficient will be described. The viscosity of the supercritical fluid has a characteristic of “proportional to the viscosity coefficient” in the laminar flow state and “proportional to the square of the viscosity coefficient” in the turbulent flow state. However, the viscosity coefficient of gas is extremely smaller than that of liquid such as water, and in particular, in the case of “supercritical fluid”, it has physical properties of gas while having liquid characteristics, and its viscosity coefficient is small. That is, the use of the high-pressure gas brine can reduce the work of the blower 2 (circulation pump).

For example, when compared at 0 ° C,
Viscosity coefficient of “water” = 1.829 × 10 ⁻⁴ (kg · s / m ² )
(Kinematic viscosity coefficient = 64.4 × 10 ⁻⁴ (m ² / hour))
Viscosity coefficient of “carbon dioxide gas” = 1.58 × 10 ⁻⁵ (kg · s / m ² )
(Kinematic viscosity coefficient = 4.83 × 10 ⁻⁴ (m ² / hour))
And
Viscosity coefficient of carbon dioxide gas / Viscosity coefficient of “water” >> ≒ (1 / 11.6)
(Kinematic viscosity coefficient; (1 / 13.3))
Since the viscosity of carbon dioxide gas is significantly small, even if the circulation flow rate is increased about twice to ensure the same heat capacity, the flow path pressure loss is predicted to be about 1/2 to 1/5 smaller. Is done. That is, even if the same heat exchange performance is maintained, the driving energy of the circulation pump (boiler) can be reduced by about 1/2 to 1/5.

  In addition, the value of (Cp × γ) can be increased by using the above-mentioned gas brine and increasing the heat exchanger area A to be equal to or higher than the ratio of the thermal conductivity of water to the thermal conductivity of the gas brine. it can.

As an example, in the case of metallic sodium (200 ° C.) used in nuclear power plants, the product of specific heat and specific weight (Cp × γ) Na is
(Cp × γ) Na = 1.325 (kJ / kg · k) × 903 (kg / m ³ )
≒ 1197 (kJ / kg ・ k) ・ (kg / m ³ )
It is.

Further, in the case of a gas brine having a heat capacity equivalent to this and simply increasing the pressure, and in the case of carbon dioxide (CO ₂ ), the product of specific heat and specific weight (Cp × γ) CO ₂ is
(Cp × γ) CO ₂ = 1.977 (kJ / kg · k) × 0.82 (kg / m ³ )
≒ 1.62 (kJ / kg ・ k) ・ (kg / m ³ )
It is.

These ratios α are
α = (Cp × γ) Na / (Cp × γ) CO ₂
= 1197 / 1.62
≒ 738 times. In other words, if considered on the basis of atmospheric pressure,
It becomes equivalent when α = 738 × 0.1013≈74.8 (MPa abs).
That is, if a heat exchanger having a pressure resistance of 100 MPa or more is prepared, in principle, heat exchange with the same heat capacity as water is possible.

On the other hand, the gas is liquefied by high pressure and becomes a supercritical fluid when the critical point is exceeded. In the case of liquefied carbon dioxide gas, “γ” ≈933 kg / m ³ and specific heat “Cp” ≈1.97 kJ / kg · k,
(Cp × γ) CO ₂ liquid = 1.97 (kJ / kg · k) × 933 (kg / m ³ )
≒ 1838 (kJ / kg ・ k) × (kg / m ³ )
It becomes.

In the case of water,
(Cp × γ) Water = 4.18 (kJ / kg · k) × 998 (kg / m ³ )
= 4172 (kJ / kg · k) x (kg / m ³ )
It is.

From these, in the system using “cooling water”, compared with the system using “liquid carbon dioxide”,
“4172/1838” ≈2.3 times the circulation flow rate is required.

On the other hand, when compared in the 0 (° C) state,
Viscosity coefficient of “water” = 1.829 × 10 ⁻⁴ (kg · s / m ² ) {Kinematic viscosity coefficient = 64.4 × 10 −4 (m ² / hour)}
Against
Viscosity coefficient of “carbon dioxide gas” = 1.58 × 10 ⁻⁵ (kg · s / m ² ) {Kinematic viscosity coefficient = 4.83 × 10 ⁻⁴ (m ² / hour)}}
And
Viscosity coefficient of “carbon dioxide” / viscosity coefficient of “water” >> ≈ (1 / 11.6) {kinematic viscosity coefficient; (1 / 13.3)}
It becomes.
Since the viscosity of “carbon dioxide gas” is significantly small, the flow pressure loss is predicted to be about 1/2 (turbulent flow) to 1/5 (laminar flow) even if the circulation flow rate is increased by about 2 times. Is done.

  Here, the high-pressure gas brine will be described.

When the pressure of the gas is increased,
Specific weight (G / V) = (P / RT)
(However, P = filling pressure, R = gas constant of the gas, T = gas temperature)
And increases in a proportional relationship with the filling pressure P. However, as is clear from the example of the phase change diagram of “water” and “carbon dioxide” shown in FIG. 5, the high pressure of the gas brine is related to the temperature as “high pressure gas → liquefied gas → supercritical fluid”. Cause a phase change. In the present embodiment, a technique applicable to all of these “high-pressure gas → liquefied gas → supercritical fluid” is proposed. In other words, the application of gas brine is obstructed (Cp × γ), and by increasing the pressure of gas brine and improving “γ” and the like, the heat capacity is increased so that efficient heat exchange can be performed. .

  FIG. 6 shows a list of critical pressures and temperatures of various gases, and FIG. 7 shows a relationship between “temperature and saturation pressure” of various gases. As is apparent from FIG. 7, water is maintained as a liquid at a saturation pressure in the region of 0 ° C. or higher, indicating that it is an excellent heat medium. And it turns out that classic ammonia turns into a liquid at the load of about 0.5 Mpa or less, and is a heat medium which cannot be obtained when it uses from the area | region near -78 degreeC or more.

  Thus, in order to improve (Cp × γ), the pressure of the gas brine is increased to cause a phase change of “liquefied gas to supercritical fluid”. As the “heating medium”, (Cp × γ) as a gas, “thermal conductivity” is large, liquefaction pressure (saturation pressure) is low, critical conditions are low, safe and environmentally friendly, and so on. However, it is no exaggeration to say that there is no gas brine that satisfies all of these. Therefore, it is possible to deal with all of these gases and realize “ultra high pressure resistance up to 100 MPa or more” and, as described above, “heat passage rate (heat transfer rate, heat transfer rate) × heat exchange area” performance. By realizing the technical configuration, a heat exchange system using gas brine is constructed.

  For automobile engine cooling systems, hydrocarbons such as “ethane” and “propane” are desirable because (Cp × γ) is relatively large and the liquefaction pressure is low. There is a problem in terms of safety. For this reason, the critical temperature is as low as 31 ° C, and supercritical fluid operation is expected in the vicinity of 80 ° C, which is the optimal temperature for engine management, and reduction and immobilization as a global warming substance is a social problem. If it is charged and fixed as a cooling medium for "automobile engine", it has social significance, so we considered the application of "carbon dioxide" to the automobile engine.

As shown in FIG. 5, the phase state of carbon dioxide changes depending on the filling pressure and temperature. Carbon dioxide gas becomes a supercritical fluid at a critical pressure of 7.38 MPa (73 kg / cm ² gauge) or higher and a critical temperature of 31 ° C. or higher. Supercritical fluids are fluids that cannot be classified into liquids and gases.The fluctuations in molecular density are large and the molecular density is close to that of liquids, but the viscosity coefficient is close to that of gas and the diffusion is fast. There is a feature that is large. This characteristic is because a heat exchanger having a pore flow path, such as a multi-tube heat exchange element having a large number of pore flow paths, can reduce the flow path pressure loss. It is most suitable for the method of greatly improving the heat transfer area.

  This characteristic is applicable not only to carbon dioxide but also to other gases such as ethane. In particular, in the case of ethylene (CH2 = CH2), the molecular weight is large and the critical point is 5.04 MPa, 9.2 ° C., which is close to the engine operating temperature. This is considered to be effective. In the case of application as a high-pressure carbon dioxide brine to an automobile engine, for example, when the filling pressure is about 5 MPa, the liquid state is maintained in a 20 ° C. environment. However, when the engine temperature rises, the density changes from liquid to gas at that portion, and the density decreases. As a result, a strong convection phenomenon occurs. Further, when the temperature of the filling brine rises due to engine heat dissipation, the filling pressure increases due to the temperature, and if it exceeds 7.38 MPa, the supercritical fluid state is entered. In supercritical fluids, density is greatly affected by pressure as well as temperature, so diffusivity and strong convection are also expected. In this way, a cooling system that does not require a circulation pump can be considered. For this reason, in the case of this example, application to a “motorcycle engine” requiring a simple and lightweight system is conceivable. However, if the heat dissipation is insufficient, such as a large “automotive engine”, a circulation pump is used together.

  What makes these systems possible is a high-pressure gas brine system using heat exchanger technology that has ultra-high pressure performance up to 100 MPa and enables an enormous heat exchanger area.

  In such a configuration, for example, when the automobile engine is cooled by the heat exchange system shown in FIG. 1, the high temperature side 10 is arranged at a place corresponding to the engine, receives heat from the engine from the cylinder outer wall, It is connected to the low temperature side 11 (outside air) through the flow path 5. Then, the outside air is cooled by the low temperature side heat exchanger 3 (radiator) disposed on the low temperature side 11 for heat radiation, and the cooled brine is supplied again to the cylinder outer wall of the engine by the blower 2. Yes.

  At present, “antifreeze added—cooling water” is used as the “heat medium”. By changing this to brine of the “high pressure carbon dioxide” component, there is no change over time such as red rust generation or loss due to evaporation, etc. The engine state can be secured.

  Liquid carbon dioxide brine as a refrigerant is a conceivable method of use, and when used as a cooling heat medium, the temperature of the engine is maintained at a temperature maintaining range of 80 ° C. or outside, for example, at a brine pressure of about 5 MPa. It may be gasified and hinder heat exchange. For use in such a cooling system of an “automotive engine”, brine is enclosed at a filling pressure of 7.43 MPa or more which is a critical pressure of carbon dioxide gas. As a result, the “filled carbon dioxide gas” becomes a “supercritical fluid”, and in general, the “supercritical fluid” has improved diffusivity, so the temperature boundary layer that inhibits heat exchange is destroyed, and heat transfer is prevented. In the basic formula “dQ = C × A × ΔT”, the heat transfer rate “C” is expected to be greatly improved with the same temperature difference ΔT and the same heat exchange area A. Is expected to be improved. In addition, “the combustion pressure inside and outside 6 MPa” is repeatedly applied inside the cylinder liner, and there is no concern about leakage, so it can be said that the application is easy.

  The above-mentioned temperature boundary layer is the same as the layer formed around the skin when gently bathed in a hot bath so as not to disturb the surroundings of the body. The reason why the temperature suddenly becomes hot is that this temperature boundary layer is destroyed.

  At present, brine is divided into use areas for refrigerant and heat medium. However, by using a heat exchanger having “high pressure resistance” and “high heat exchange” performance, gas brine containing carbon dioxide, air, etc. containing water vapor can be converted into a refrigerant region (−200 ° C. or higher) to a heat medium region ( It was possible to apply in a wide range of 1500 ° C. or less. In particular, in an automobile engine, by performing a high pressure (for example, 7.5 MPa or more) filling with carbon dioxide gas, it is possible to perform temperature control more than the current water cooling by utilizing diffusion characteristics.

  FIG. 8 is a heat exchange system 100 according to an embodiment of the present invention, and is a schematic diagram of a “convective closed cycle”.

  In this “convection type closed cycle”, as shown in FIG. 8, a heat exchanger on the use side and a heat exchanger on the heat source side are arranged vertically, and a pipe connecting the both heat exchangers is a central axis tube and its It consists of a double tube with an outer tube that surrounds it. For example, when cooling an automobile engine, the high temperature side 110 is disposed at a location corresponding to the engine, the high temperature side heat exchanger 104 receives the heat radiation of the engine from the cylinder outer wall of the engine, and the gas brine filled in the system is changed. When heated, the density decreases and an upward flow is generated in the communication channel 105. On the other hand, the low temperature side heat exchanger 103 for dissipating heat provided on the low temperature side 111 (outside air) cools the gas brine, increases the density, and generates a downward flow. Thus, in the “convection type”, the blower 2 configured in FIG. 1 is not necessary, and the cooling system can be made more compact and energy saving.

  In addition, when supercritical carbon dioxide is used as the “heating medium” of the system shown in FIG. 8, the coastal temperature condition is as low as 31 ° C. or lower with respect to 80 ° C., which is the approximate engine maintenance temperature. A stable cooling state is expected from the diffusion performance (expected improvement in heat transfer coefficient) that can enter the gap, fluidity (because it has gas characteristics and convection is expected), and the like.

  In addition, there exists a heat pipe to perform the same operation | movement as FIG. This is because the heat exchanger is filled with a small amount of water or alcohol, the internal pressure is set to vacuum, and vaporization (evaporation) and condensation (liquefaction) are used, and heat conduction takes place at almost the speed of sound. It exerts great power for cooling the air, storing the cold energy of the outside air, melting snow, etc. However, in order for this heat pipe to function, a condensing (liquefying) portion (low temperature portion) must be formed at one end, which is restricted in this respect. On the other hand, in the method using the heat medium as in the present embodiment, for example, heat can be received from the high temperature side of 1000 ° C., and heat storage of 1000 (° C.) can be performed on the low temperature side.

  FIG. 9 is a schematic diagram showing a heat exchange system 200 using a gas brine and a circulation heat exchanger (so-called heat pump) having a throttle channel.

  As an existing technology, “carbon dioxide” is generally used as a heat medium because of environmental problems. In addition, those having a high boiling point such as “Freon” and “Ammonia” are used. As described above, even a well-known heat pump has a different operation system from the present embodiment. That is, in the heat pump, if the low temperature side 211 is a region where the room temperature is desired to be lowered (for example, an air conditioner), the flow path 205 is filled with carbon dioxide gas, and the compressor 202 compresses the generated heat. The heat medium carbon dioxide gas is liquefied by radiating heat with water for using hot water for daily life through the high-temperature side heat exchanger 204. Next, the liquefied heat medium is expanded through the diaphragm 206, the heat medium temperature is lowered by the heat of evaporation, and the indoor air temperature is lowered by the low temperature side heat exchanger 203. In the case of this example, the lower the temperature of the high temperature side 210, the lower the temperature of the low temperature side heat exchanger 203. On the other hand, when the high temperature side 210 is used for a hot water heater or the like, the temperature of the low temperature side heat exchanger 203 is increased to use, for example, waste heat or solar heat. However, both use heat of evaporation (condensation heat) at the time of phase change from gas to liquid, and are different from the application example of “high-pressure gas brine” that does not change phase as in this embodiment. The fact that the phase does not change does not include, for example, a case where a trace amount of gas becomes liquid unintentionally, and basically means that the phase does not change.

  FIG. 10 is a heat exchange system according to an embodiment of the present invention, and shows a schematic diagram of a “sealed-convection heat exchanger” using a high-pressure gas brine.

  The basic configuration is the same as that of the system shown in FIG. That is, the cooling jacket portion 321 in the engine 320 is configured as one end of the high temperature side heat exchanger. As a heat medium for cooling the engine 320, a high-pressure gas brine (for example, carbon dioxide gas) is filled in the system. The engine 320 and the low temperature side heat exchanger 303 for heat radiation (cooling) are connected by a flow path 305.

The flow path 305 is connected to the upper side of the engine 320 and has a structure in which the heat medium heated by the engine 320 generates upward convection due to a decrease in specific weight. When the temperature of the heat medium exceeds, for example, 60 ° C., a temperature control valve such as the thermostat valve 322 is opened to prompt the heat medium to flow into the low temperature side heat exchanger 303. A pressure gauge 323 for confirming whether or not the filling gas is normal is connected to the flow path 305 or the like (the place may be anywhere because of a sealed structure).
When the heat medium is cooled by the low temperature side heat exchanger 303, the “specific weight” increases and a downward flow is caused. This is connected to the lower side of the engine 320 by a flow path 324 to form a circulation flow of “flow path 324 to flow path 305”. In this way, a cooling system that does not require a “circulation pump” is configured.

The low temperature side heat exchanger 303 has (1) pressure resistance performance and (2) heat exchange efficiency (heat exchange area), for example, “Heat exchange composed of many lotus-like pore channels” A vessel (see FIG. 2) is used.

  Further, in order to reduce the load on the low temperature side heat exchanger 303, heat radiation fins 325 may be provided on the outer periphery of the engine 320. A cooling fan 326 is provided to reduce the temperature in the engine room by the low temperature side heat exchanger 303 and the heat radiating fins 325, and receives a signal of the heat medium temperature or the engine room temperature from the thermometer 327, The electromagnetic clutch 328 (or electric motor) functions to drive the cooling fan 326. In addition, in order to ensure safety in the event of an emergency, an automatic valve 329 (open valve) may be provided in connection with the flow path. That is, when the pressure in the flow path exceeds an arbitrary pressure, the automatic valve 329 is opened over the “spring pressing force and back pressure”, and the heat medium pressure is released. Then, it is released to the atmosphere or released to the reservoir tank (box) 330.

  The excellent point of the system shown in FIG. 10 is that (a) since a stable substance such as “carbon dioxide” is used as a heat medium, semipermanent operation is expected, and (b) “supercritical fluid”. In the region, the diffusivity makes it possible to manage the engine temperature uniformly. (C) In the “supercritical fluid”, the “viscosity coefficient” of the gas is used with the characteristic of “specific weight × specific heat” of the liquid. Therefore, it is possible to use a high-performance heat exchanger composed of many lotus root-like channels, and (d) since natural convection is used, a “circulation pump” is not required. Energy savings, (e) maintenance-free operation at -50 ° C and below, without additives such as antifreeze, and (f) carbon dioxide resource recycling and immobilization technology Can contribute to environmental conservation. This system can also be applied to motorcycle engines.

  FIG. 11 is a heat exchange system according to an embodiment of the present invention, and is a schematic diagram of a “closed-circulation heat exchanger” using a high-pressure gas brine (basic operation diagram, such as a cooling fan). Omit auxiliary equipment). The basic configuration is the same as the system shown in FIG.

  In the case of a large vehicle engine or a high output engine, the natural convection heat exchanger described above may not be able to perform sufficient cooling control. For this purpose, a system for forcibly circulating the heat medium in the engine and managing the temperature of the engine is the embodiment of FIG.

  The engine 420 is filled with “high pressure gas brine (for example, carbon dioxide gas)” as a heat medium. The heat medium that has cooled the engine 420 is guided to a low-temperature side heat exchanger 403 for heat dissipation through a flow path 405 connected to the engine 420. The heat medium cooled by the low temperature side heat exchanger 403 is circulated to the engine 420 via the flow path 424 by the circulation pump 421.

  In the example of FIG. 11, the circulation flow path is from the upper side (high temperature side) to the lower side (low temperature side) of the engine 420, but for the homogenization of the engine 420 temperature, the flow path may be reversed to this description. . A pressure gauge 423 is provided in the flow path 405 for checking and managing whether or not “high-pressure gas brine” is properly filled. In addition, a thermometer 427 and a motor controller 428 having functions such as PID control are provided for proper management of the engine 420 temperature. The motor controller 428 having a function such as PID control performs appropriate circulation flow rate management of the heat medium.

  The advantages of this system are (a) that a stable substance such as carbon dioxide is used as the heat medium, and that semipermanent operation is expected. (B) In the supercritical fluid region, due to its diffusivity. (C) “Supercritical fluid” is a characteristic of “specific weight x specific heat” of liquid, and it uses the viscosity coefficient of gas to create a large number of lotus root flow paths. It is possible to use a high-performance heat exchanger that is configured, (d) it is possible to perform temperature control equivalent to or higher than the current “cooling water system” by performing forced circulation, (e) antifreeze, etc. It is possible to operate maintenance-free at an environmental temperature of “−50 (° C.) −” Without any additive, and (f) to contribute to environmental conservation due to the resource and immobilization technology of “carbon dioxide gas”. And so on.

  Although not shown in the figure, in order to ensure safety in the event of a failure of the circulation pump 421, as in the example of FIG. 10, when the line pressure of the flow path rises abnormally, the pressure is released (not shown) In some cases, a valve and a reservoir tank (not shown) for temporarily storing the heat medium are attached.

  Here, the reduction effect of carbon dioxide when carbon dioxide is used as a cooling heat medium for automobile engines will be described.

  According to the statistics of 2004, the world's automobile production is about 62 million, and Japan's production is about 20 million, which is increasing more and more. It is assumed that the amount of “liquefied carbon dioxide” as a cooling heat medium for an automobile engine is 5 (liters / unit), and 10% of new vehicles produced worldwide use this. As a result, 622,000,000 units / year × 0.1 × 5 liter = 311,000,000 (liter / year) = 31,000 (kiloliter / year) of carbon dioxide gas is fixed. This amount corresponds to 31000000 (liter / year) / 200 = 155000 (can / year) ≈160,000 (can / year) in terms of a 200-liter drum.

Assuming that the specific weight at the critical (liquefaction) is 925 (kg / m ³ ) (0 ° C .; Hideo Uchida-P.379, Heat Transfer Engineering), 31 million (liters / year) × A reduction effect of 925 (kg / m ³ ) / 1000 (m ³ / liter) = 286675 (kg / year) ≈28675 (ton / year) is expected. If 30% of new cars are adopted, a reduction effect of 28675 × 3 = 86025 (ton / year) is expected only in the automobile field.

  FIG. 12 (A) and FIG. 12 (B) are schematic views of a “circulation-heat exchanger” using a “high-pressure gas brine” in the heat exchange system according to the embodiment of the present invention. Is.

It is extremely inefficient to obtain temperature management for maintaining the human living environment from thermal energy such as petroleum or converted electric energy. For example, the thermal energy per kg at 50 ° C is equivalent to about 217 times that of a dam with a drop of 100m (Shinichi Tanuma, Professor Emeritus, The University of Tokyo “Energy Conversion” Co., Ltd. P. 9). That is, assuming that a room of 3.6 m × 2.7 m × H3 m equivalent to 6 tatami mats is warmed to 25 ° C. in an environment where the outside air temperature is 0 ° C. from room temperature = 0 ° C., (25/50) × 3.6 × as saying that ^{2.7 × 3 × 1.29kg / m 3} × 217 ≒ 4081, it takes the energy equivalent of what "4081 times" of the drop 100m dam. In this way, it is extremely difficult to reconvert energy converted from electrical energy, which is "multi-use energy (electricity can be converted into many forms such as light, motor, heat, etc.)" into thermal energy again. It's a waste. For this purpose, it is important to utilize the natural energy of the atmosphere in regions where there is a difference in temperature and warmth blessed with natural energy.

  In the case of the “circulation heat exchanger” in FIG. 12A (in the temperature range where one end is solidified (liquefied), the heat pipe is superior. For example, in the case of cold energy storage) The system configuration in the case of storing warm energy such as solar heat. As the heat medium, high-pressure gas brine is used.

  Heat collection fins 525 are provided on the outer peripheral portion of a high-performance heat exchanger such as a multi-tube heat exchange element, which is composed of a lotus root-shaped pore channel 501. The heat medium heated by the heat collecting fins 525 is reversed in the reversing tank 530 and sent to the heat accumulating tank side through the “heat medium oil feeding pipe” provided on the central shaft 531. By sending a high-temperature heat medium through a “heat medium oil feed pipe” provided on the central shaft 531, improvement in heat loss during transportation is achieved. Then, it is reversed in the reversing tank 530 through the reverse support valve 532, sent to the multi-tube heat exchange element 533, and warm energy is transmitted to the heat medium in the heat accumulating tank by the radiation fins 534.

  The heat medium that has transmitted the warm energy to the heat storage tank is sent to the “heat collecting section” via the heat medium transport pipe 535 disposed on the outer periphery. In the example shown in FIG. 12A, the heat medium is circulated in the heat medium transport pipe 535. In the example shown in FIG. 12A, the piston is composed of a spring 536, a permanent magnet 537, a reed valve (phaser valve) 538, and a labyrinth seal 539. This is performed by a valve 540 and an electromagnetic driving device 541. Specifically, when the electromagnetic driving device 541 is operated, the permanent magnet 537 of the reed valve 538 is attracted toward the electromagnetic driving device 541 against the elasticity of the spring 536, and the piston valve 540 is opened.

  The above-described structure does not cause internal deterioration because of a completely sealed heat exchanger using a simple composition gas brine that does not denature. As a result, permanent operation is possible. Further, instead of the above-described circulation piston valve 540, for example, a heat medium may be circulated using a circulation impeller (not shown).

  FIG. 12B shows a system configuration in the case where “cold energy” such as solar heat is stored in the “cold storage tank”. The operation system is exactly the same as the above-described “cold storage system”, and “high pressure gas brine” is used as the heat medium. The difference is that the circulation direction (fluid flow direction) is reversed, and the cooled heat medium is sent to the “cold storage tank” via the heat medium transport pipe 635 disposed on the outer periphery. In other words, the cooling fins 625 are provided on the outer peripheral portion of a high-performance heat exchanger such as the multi-tube heat exchange element 633 constituted by the lotus root-shaped pore channel 601. In the example of FIG. 12B, the heat medium cooled by the cooling fins 625 is provided inside the heat medium transport pipe 635 disposed on the outer periphery via the heat medium transport pipe 635 disposed on the outer periphery. Circulation is performed by a piston valve 640 including a spring 636, a permanent magnet 637, a reed valve (phaser valve) 638, a labyrinth seal 639, and an electromagnetic drive device 641. Further, instead of the piston valve 640, for example, an impeller may be used to circulate the heat medium.

  The heat medium sent to the multi-tube heat exchange element 633 is transmitted “cold energy” to the “heat medium of the cold storage tank” by the heat radiation fins 634. And it is reversed by the inversion tank 630, and is sent to a cold collection part through the heat-medium oil feed pipe provided in the center axis | shaft 631. The rising heat medium is reversed in the reversing tank 630 through the reverse support valve 632, sent to the multi-tube heat exchange element 633, and receives “cold energy” by the cooling fins 625 (if it is limited to cold energy storage). , Heat pipe is better).

  This operation explanation is a general operation example of the “forced circulation heat exchanger”, and the application of a “natural convection heat exchanger” shown in FIG. Included in systems using “high pressure gas brine”.

  FIG. 13 shows a heat exchange system according to the embodiment of the present invention. FIG. 13A shows a “heat storage system” and FIG. 13B shows a “cold storage system”. 13C is a cross-sectional view taken along the line AA in FIG. 13A, and FIG. 13D is an enlarged view of a portion B in FIG. Since these two have the same basic structure except that the flow direction by convection is different, the “heat storage system” will be described below.

  Prior to the description of FIG. 13, an existing “cold storage system” using a “heat medium” will be briefly described with reference to FIG. 14.

  In the existing system, the same heat medium that transfers heat in the low temperature side heat exchanger 703 has been used as the cold storage agent 702 (heat medium) of the cold storage tank 701. For example, as such a heat medium, a liquid having a large specific weight, specific heat, thermal conductivity, etc., such as a calcium chloride solution or a magnesium chloride solution, can easily construct an efficient system. In the case of this example, a flow path 705 is inserted into the upper end of the regenerator 702 of the regenerator 701, and one end thereof is connected to a low-temperature side heat exchanger 703 for absorbing heat from cold outside air. The other end of the low temperature side heat exchanger 703 is connected to the vicinity of the bottom of the cold storage tank 701 by a flow path 705.

  When the heat medium is cooled by the low temperature side heat exchanger 703, the specific weight of the heat medium becomes large, and thus a downward flow is generated as shown by an arrow 706 in FIG. In parallel with the temperature of the regenerator 702, this convection action is stopped. As described above, a cold storage system without a circulation pump can be conventionally used, but a circulation pump is usually used because it is difficult to configure a closed cycle including the cold storage tank 701. In the case of this conventional specification, it is difficult to use gas brine for the heat medium passing through the low temperature side heat exchanger 703 due to the problem of “specific weight × specific heat”.

  Returning to FIG. 13A, the “heat storage system” of the present invention will be described.

  For the heat storage tank 801, an optimum heat storage agent 802 having a large “specific weight × specific heat” including liquid, powder, and solid is selected. In the heat storage agent 802, a high temperature side heat exchanger 804 for heat dissipation (heat storage) is embedded. A flow path 805 connected to the high temperature side heat exchanger 804 is filled with high-pressure gas brine. Then, heat is absorbed by the high temperature side heat exchanger 804 and the heat medium temperature rises, whereby the specific weight is reduced and a flow in the upward direction is generated. On the other hand, heat is released to the heat storage agent 802 in the heat exchanger 807 connected to the high temperature side heat exchanger 804 and the flow path 805. As a result, a downward flow is generated due to a decrease in the temperature of the heat medium and an increase in the specific weight. In this way, energy is stored in the heat storage tank 801 by natural convection.

  By using high-pressure gas brine for the heat exchanger 807 and the high-temperature side heat exchanger 804 having a pore flow channel structure with a diameter of 1 μm, the operation is semipermanent without any change over time such as clogging or heat medium degeneration. Is possible. In the application at the nuclear power plant, the high temperature side heat exchanger 804 corresponds to heat exchange in the nuclear reactor core, and the turbine is driven by using the heat energy of the heat storage agent 802 isolated from the flow path 805 heat medium. Therefore, the pollutant is not leaked to the outside.

  FIG. 15 is a heat exchange system according to an embodiment of the present invention, and shows a schematic diagram applied to a computer using a “circulation pump”.

  In the channel 901, for example, liquefied carbon dioxide gas is sealed as a high-pressure gas brine. The circulation pump 902 supplies the high-performance heat exchanger like a multi-tube heat exchange element 904 provided in the computer heat generation unit 903. Here, the heat generated by the computer is received and guided to the heat-dissipating heat exchanger 906 via the connection channel 905, and the heat generated by the computer is discharged (a natural convection type that does not use a circulation pump is also possible).

  The merit of using high-pressure gas brine (liquefied carbon dioxide, supercritical fluid) such as carbon dioxide is, for example, (1) Corrosion because there is no reactivity to metal in the case of “carbon dioxide”. The optimum thermal conductivity material can be used without taking into account. (2) Semi-permanent operation is possible because there is no change over time such as heat denaturation. (3) The viscosity coefficient is as small as “about 1/10” of the “water” medium, and even if the flow rate is about twice to achieve the same heat capacity circulation, the circulation pressure loss is “½ (turbulence) in the case of“ water ”. Flow) to 1/5 (laminar flow) ". (4) When the “heat medium” leaks, the “leak heat medium” does not damage the equipment. (5) Since the operating temperature environment is expected to be “−50 (° C.) in the case of carbon dioxide gas” in contrast to “0 ° C. of water”, it is safe even in cold regions of 0 (° C.) or less. It can be used with heart.

The heat exchange system according to the embodiment of the present invention has the following industrial utility value.
(1) By using high-pressure gas brine, heat exchange can be performed in a wide temperature range of approximately -200 ° C to 1500 ° C, including heat exchange from high-temperature energy such as nuclear power plants.
(2) Moreover, since it is not heat-denatured, it does not cause deposit formation or clogging of heat exchangers such as multi-tube heat exchange elements composed of a large number of pore channels, so that it is semi-permanent without change over time. Enables operation.
(3) It is possible to provide a high-performance heat exchanger using a gaseous brine such as carbon dioxide gas that is desired to be fixed or dumped into the deep sea as a greenhouse gas. In particular, in supercritical fluids, the density transformation pressure due to pressure and temperature is large at the critical point, and the realization of an effective natural convection heat exchanger that takes advantage of these features is expected.
(4) By using a gas inferior in thermal conductivity as the brine, it is possible to reduce unnecessary heat loss from outside the heat exchanger. However, in the heat exchange performance part, a multi-tube type heat exchange element that enables a huge heat exchange area, etc. is used, and a system with low heat loss is constructed by enabling heat conductivity equivalent to water. It becomes possible.
(5) By filling the gas with high pressure, it is possible to provide a technique that compensates for the disadvantage of the gas brine having a small “specific heat × specific weight”. Further, since the viscosity coefficient is small, even if the pore flow path is configured as in the multi-tube type heat exchange element structure, the flow pressure loss may be small, so that the required driving work for the circulation pump is small. As a result, when using solar heat, the driving power can be covered by solar power generation.
(6) The heat exchanger according to the present embodiment can provide a heat exchanger tailored to its characteristics in all states of high-pressure gas, liquefied gas, and supercritical fluid according to the degree of pressure of the filling gas. It becomes.

  In the heat exchange system according to the embodiment of the present invention, an environment-safe heat exchange system can be realized by using gas brine such as nitrogen gas, air, and carbon dioxide gas. In addition, a permanent operation heat exchanger can be realized using a gas brine that is a permanent stable material that does not change with time such as evaporation and loss.

  Further, the low-temperature side heat exchanger 3 and the high-temperature side heat exchanger 4 are configured by a heat exchanger having a pressure resistance performance of 100 MPa or more by using a plurality of pore channels 22, and using a supercritical fluid as a gas brine , (Cp × γ) can be increased, and the amount of heat Q can be made close to that of liquid brine.

  Furthermore, with respect to the “thermal conductivity”, a high-performance heat exchanger (multi-tube structure heat exchange element) composed of a large number of pore channels 22 or the like is used. The heat exchange area is increased up to the ratio α of the thermal conductivity of water to α (α = for example, in the case of air, the thermal conductivity of water / the thermal conductivity of air = 600/2 = 300) Exchange performance can be achieved.

  Furthermore, in the past, in the case of heat exchange from a high-temperature heat source, a liquid metal that is highly corrosive or reactive is generally used, but by using a high-pressure carbon dioxide component as a gas brine, corrosion due to the occurrence of red rust, etc. The risk of being lost.

  Furthermore, liquid metals could only be used at temperatures above their melting points. For example, in the case of carbon dioxide, -50 ° C to 1500 ° C, and in the case of nitrogen gas, a wide range such as -140 ° C to 1500 ° C. Heat exchange at is possible.

  On the other hand, as a kind of greenhouse gas emitted from automobiles, etc., the increase of carbon dioxide gas has become a big problem, and its reduction, fixation, and dumping into the ground and deep sea have been screamed. The right to sell is now commercialized, and sales from countries that cannot reduce carbon dioxide gas to countries with low emissions are going to be made. In the heat exchange system according to the present embodiment, the liquefied “carbon dioxide for disposal” can be effectively utilized including its production energy. That is, it is possible to provide a “heat exchanger” that can use “discarding carbon dioxide” as a brine for a heat medium / refrigerant, and can be isolated and effectively used semi-permanently. Thus, the application to the automobile engine contributes to the global environmental conservation together with the effective use of such carbon dioxide gas.

  In addition, when used in an automobile engine, it is possible to provide a new “small and light” cooling system and to secure a stable engine state.

  On the other hand, in order to improve the heat exchange performance under the same temperature condition, the coefficient “C” such as heat transfer coefficient and heat conductivity, heat exchange area, etc. in “Basic Formula of Heat Transfer—dQ = C × A × ΔT” Although it is necessary to improve “A”, in the heat exchanger composed of many lotus root-like pores, the inner diameter of the pore channel 22 can be 1 μm or less. In the “heat exchanger” having the hole flow path 22, “deposit” and “flow path clogging” due to modification of the working fluid have been problems. However, the use of “stable gas brine” eliminates such concerns, and supercritical fluids with gas diffusivity while having liquid properties can reduce flow path pressure loss due to viscosity coefficient. Can be planned.

  In addition, since the heat exchanger on the use side and the heat exchanger on the heat source side are arranged vertically, the pipe connecting the two heat exchangers is composed of a central axis tube and a double tube of an outer tube surrounding the periphery. By generating an upward flow and a downward flow in a gas brine or the like, it is possible to eliminate the need for a device that forcibly sends the flow. As a result, it is possible to save energy and simplify the system configuration.

  Further, a circulation piston 540 or an impeller composed of a permanent magnet or the like is provided in the pipe line 535, and an electromagnetic driving device 541 for driving the piston 540 or the impeller is disposed outside the pipe line 535, so that the piston or the impeller Since the medium is circulated by driving, a heat exchanger having a completely sealed structure using a gas brine having a simple composition that does not denature can be formed.

  Further, the automatic valve 329 that is opened when the pressure in the pipe line reaches an abnormally high pressure is connected to the pipe line, and the reservoir tank 330 that expands the medium is connected to the automatic valve 329. A safety system that prevents abnormally high pressure in the road can be built in the system.

  Further, by using the low temperature side heat exchanger as the engine cooling jacket 321, the present system can be used for engine cooling.

  Further, by disposing the low temperature side heat exchanger in the computer heat generation unit 903, the present system can be used for cooling the computer heat generation unit.

It is a heat exchange system concerning an embodiment of the invention, and is a schematic diagram of a "sealed cycle" in which gaseous brine is sent using a blower. FIG. 2A is a cross-sectional view, and FIG. 2B is a side view of FIG. 2A, which is a heat exchange unit used in the heat exchanger of FIG. It is a schematic diagram which shows the other structure of a heat exchange unit. It is a perspective view which shows a rope-shaped heat exchange element. It is a figure which shows the phase change of gas. It is a table | surface which shows the critical pressure and temperature of various gas. It is a figure which shows the relationship between temperature and saturation pressure. 1 is a schematic diagram of a “convective closed cycle”, which is a heat exchange system according to an embodiment of the present invention. It is a heat exchange system using gas brine, and is a schematic diagram showing a circulation type heat exchanger (heat pump) having a throttle channel. It is a heat exchange system concerning an embodiment of the invention, and is a schematic diagram of a "sealed-convection heat exchanger" using high-pressure gas brine. It is a heat exchange system concerning an embodiment of the invention, and is a schematic diagram of a "sealing-circulation type heat exchanger" using high-pressure gas brine. 1 is a schematic diagram of a “circulation-heat exchanger” using a “high-pressure gas brine”, which is a heat exchange system according to an embodiment of the present invention. FIG. 13 (A) is a schematic diagram of a heat storage system, FIG. 13 (B) is a schematic diagram of a cold storage system, and FIG. 13 (C) is a diagram illustrating a heat exchange system according to an embodiment of the present invention. Sectional drawing cut | disconnected by the AA line of (A), FIG.13 (D) is the B section enlarged view of FIG. 13 (A). It is a schematic diagram which shows the existing system of the "cold storage system" shown in FIG.13 (B). It is the heat exchange system which concerns on embodiment of this invention, Comprising: It is the schematic diagram applied to the computer using the "circulation pump."

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Heat exchange system 2 Blower 3 Low temperature side heat exchanger 4 High temperature side heat exchanger 5 Flow path 6 Heat exchange unit 10 High temperature side 11 Low temperature side 21 Stainless steel pipe 22 Porous flow path (through hole)
23 Stainless steel outer tube 24 Metal gap filling material 103 Low temperature side heat exchanger 105 Communication channel 110 High temperature side 111 Low temperature side 203 Low temperature side heat exchanger 204 High temperature side heat exchanger 205 Channel 206 Throttle 210 High temperature side 211 Low temperature Side 303 low temperature side heat exchanger 304 high temperature side heat exchanger 305 flow path 320 engine 321 cooling jacket portion 322 thermostat valve 323 pressure gauge 324 flow path 325 heat radiation fin 326 cooling fan 327 thermometer 328 electromagnetic clutch (electric motor)
329 Automatic valve 330 Reservoir tank (box)
403 Low temperature side heat exchanger 405 Flow path 420 Engine 421 Circulating pump 423 Pressure gauge 424 Flow path 427 Thermometer 428 Motor controller 501 and 601 Pore flow path 525 Heat collecting fins 530 and 630 Inversion tank 531 and 631 Central shafts 532 and 632 Check valves 533 and 633 Multi-tube heat exchange elements 534 and 634 Radiation fins 535 and 635 Heat transfer pipes 536 and 636 Springs 537 and 637 Permanent magnets 538 and 638 Reed valves (phasor valves)
539, 639 Labyrinth seal 540, 640 Piston valve 541, 641 Electromagnetic drive device 625 Cold collector fin 701 Cold storage tank 702 Cold storage agent 703 Low temperature side heat exchanger 705 Flow path 706 Arrow 801 Heat storage tank 802 Thermal storage agent 804 High temperature side heat exchanger 805 Channel 806 Arrow 807 Heat exchanger 901 Channel 902 Circulation pump 903 Computer heat generation unit 904 Multi-tube heat exchange element 905 Articulated channel 906 Heat exchanger for heat dissipation

Claims (9)

  A high-temperature side heat exchanger that absorbs heat and a low-temperature side heat exchanger that releases heat are connected in a closed loop environment via a pipe line, and high pressure such as carbon dioxide, methane, ethane, or air is connected to the closed loop environment. A medium consisting of gaseous brine is circulated in a state that does not cause a phase change, and either one of the two heat exchangers is arranged as a heat exchanger on the use side and the other as a heat exchanger on the heat source side, A heat exchange system, wherein at least the heat exchanger on the heat source side is constituted by a heat exchanger provided with a large number of pore channels connected to the pipe line.   A high-temperature side heat exchanger that absorbs heat and a low-temperature side heat exchanger that releases heat are connected via a pipeline in a closed loop environment, and high pressures such as ethane, propane, ethylene, and carbon dioxide gas are connected to the closed loop environment. A liquid medium is circulated in a state that does not cause a phase change, and either one of the two heat exchangers is arranged as a heat exchanger on the use side and the other as a heat exchanger on the heat source side, and at least The heat exchange system, wherein the heat exchanger on the heat source side is configured by a heat exchanger having a large number of pore channels connected to the pipe line.   A high-temperature side heat exchanger that absorbs heat and a low-temperature side heat exchanger that releases heat are connected via a pipeline in a closed loop environment, and ethane, propane, ethylene, carbon dioxide, water, etc. are contained in the closed loop environment. A medium consisting of a supercritical fluid is circulated in a state that does not cause a phase change, and either one of the two heat exchangers is arranged as a heat exchanger on the use side and the other as a heat exchanger on the heat source side. A heat exchange system, wherein at least the heat source side heat exchanger is configured with a heat exchanger having a large number of pore channels connected to the pipe line.   The pore diameter of the pore channel is formed so that the heat exchange area of the pore channel is larger than the heat exchange area of the channel when the pore channel is not provided. The heat exchange system according to any one of claims 1 to 3.   The heat exchanger on the use side and the heat exchanger on the heat source side are arranged vertically, and the pipe connecting the two heat exchangers is composed of a central axis tube and a double tube of an outer tube surrounding it. The heat exchange system according to any one of claims 1 to 4.   A circulation piston or impeller composed of a permanent magnet or the like is provided in the pipe, and an electromagnet for driving the piston or impeller is arranged outside the pipe, and the medium is moved by driving the piston or impeller. The heat exchange system according to any one of claims 1 to 5, wherein the heat exchange system is circulated.   7. An opening valve connected to the pipe line when the pressure in the pipe line reaches an abnormally high pressure is connected, and a box for expanding the medium is connected to the opening valve. The heat exchange system as described in any one.   The heat exchange system according to any one of claims 1 to 4, wherein the low temperature side heat exchanger is an engine cooling jacket. The heat exchange system according to any one of claims 1 to 4, wherein the low-temperature side heat exchanger is disposed in a computer heat generation unit.

Images