JP2000046485A - Heat transporting system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a heat exchange efficiency in a heat exchanger without impairing a transporting power reducing effect at the time of transporting in a heat transporting system in which a surfactant for forming a micell is added in a heating medium. SOLUTION: In the heat transporting system for transporting a heat from a heat exchanger 9b of a heat reception side to a heat exchanger 9a of a heat radiating side by connecting the exchanger 9b to the exchanger 9a through a transporting tube 2 via a transporting pump 1 and feeding a heating medium added with a pressure loss reducing agent into the tube; a branch tube 5 for branching a part of the medium from the tube 2 is provided before the media of the exchangers 9a, 9b are introduced, and a nozzle 7 for converting a flow of the medium in a heat transfer tube into a flow having a momentum component in a vertical direction to a heat transfer surface 31 via a jet pump 6 is provided at the tube 5.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat transport system used in a district cooling / heating system, a building air conditioning system, a snow melting system, and the like.

[0002]

2. Description of the Related Art In a district heating / cooling system or a building air conditioning system, about 25% of air conditioning power is consumed for transporting heat medium by a pump, and reducing the transport power is a major issue. As one of the countermeasures, a surfactant which forms micelles as a power loss reducing agent is added to water which is a heat transport medium, thereby converting the Newtonian fluid into a non-Newtonian fluid, thereby reducing pressure loss in the pipe. (E.g., Document 1: Transactions of the Japan Society of Mechanical Engineers, Volume B, Vol. 61, No. 589 (1995-9), pp. 206-212, Paper No. 95-027
3 Reference 2: JOURNAL OF CHEMICAL ENGINEERING OF JAPAN,
VOL.26, NO.1, 1993, pp103-106].

In a heat transport system in which an aqueous solution to which a surfactant is added is used as a heat medium and circulates between a heat exchanger on a heat receiving side and a heat exchanger on a heat radiating side, the heat medium is disposed in front of these heat exchangers. There is a technique for recovering the heat transfer coefficient by putting particles or bubbles in the heat exchanger and disturbing the aggregate of micelles in the heat exchanger.

Further, in Japanese Utility Model Laid-Open No. 1-11989, a part of the heat medium flowing through the heat exchanger is taken out from the rear inside the heat exchanger, and the taken out heat medium is ejected again from the front inside the heat exchanger. A heat exchanger for promoting heat transfer is described.

[0005]

However, when a surfactant which forms micelles such as polyethylene glycol or fine fibers is added, the flow becomes laminar. It has been clarified that the pressure loss decreases and the heat transfer coefficient also decreases.
Therefore, there is a problem that the efficiency of heating and radiating the heat transport medium is reduced.

Further, in a method in which particles or bubbles are put in a heat medium to disturb the aggregate of micelles in the heat exchanger to recover the heat transfer coefficient, the heat transfer after passing through the heat exchange unit is repeated. In order to make the flow laminar, particles and air bubbles must be removed and a new recovery device must be added. Therefore, there is a problem that the system becomes complicated and the initial cost becomes too high.

Further, in the heat exchanger described in Japanese Utility Model Laid-Open No. 1-11989, a part of the heat medium flowing through the heat exchanger is taken out from the rear inside the heat exchanger, and the taken-out heat medium is again used as the heat exchanger. It blows out from the front inside, and there is a loss in heat exchange efficiency.

An object of the present invention is to provide a heat transport system in which the heat transfer efficiency during heat exchange is not reduced even when a pipe pressure loss reducing agent is added to a heat medium.

[0009]

The object of the present invention is to connect a heat exchanger on the heat receiving side and a heat exchanger on the heat radiating side by a transport pipe via a transport pump, and to add a pressure loss reducing agent into the transport pipe. A heat transport system that transports heat from the heat exchanger on the heat receiving side to the heat exchanger on the heat radiating side by flowing the heat medium.
In the transport pipe before the heat medium to which the pressure loss reducing agent of the heat exchanger has been added flows, a branch pipe that branches a part of the heat medium from the transport pipe is provided.In this branch pipe, via a jet pump,
This is achieved by connecting a nozzle for creating a flow of the momentum component in a direction perpendicular to the heat transfer surface with respect to the flow of the heat medium in the heat transfer tube.

Another object of the present invention is to transport a heat exchanger constituted by inserting and fixing an end of a heat transfer tube into a tube sheet, and transporting the heat exchanger on the heat receiving side and the heat exchanger on the heat radiating side configured as described above. In a heat transport system connected by a pipe via a transport pump, a heat medium to which a pressure loss reducing agent is added flows in the transport pipe to transport heat from the heat exchanger on the heat receiving side to the heat exchanger on the heat radiating side. A heat transfer tube, which is provided with a branch pipe for branching a part of the heat medium from the transport pipe in the transport pipe before the heat medium to which the pressure loss reducing agent of the heat exchanger is added flows, and which is inserted into the pipe sheet and fixed. An injection chamber having a diameter larger than the diameter of the pipe at the center is formed at the inlet end of the heat transfer pipe, and an injection hole for creating a flow of a momentum component in a direction perpendicular to the heat transfer pipe is provided in the heat transfer pipe forming the injection chamber. This is achieved by connecting to a branch pipe.

A further object of the present invention is to provide a double-pipe heat exchanger composed of an inner pipe and an outer pipe, and a heat-receiving-side heat exchanger and a heat-radiating-side heat exchanger configured as described above by a transport pipe. Connected via a transport pump, in a heat transport system that transports heat from the heat exchanger on the heat receiving side to the heat exchanger on the heat radiating side by flowing a heat medium added with a pressure loss reducing agent into the transport pipe, A branch pipe that branches a part of the heat medium from the transport pipe is provided in the transport pipe before the heat medium to which the pressure loss reducing agent of the heat exchanger is added flows, and a fin is attached to the outer surface of the inner pipe. Achieved by

Further, the above object is to provide a heat exchanger having a tank type heat transfer tube, a coil type heat transfer tube wound around the outer surface of the tank type heat transfer tube, and a heat exchanger on the heat receiving side having such a structure. And a heat-exchanger-side heat exchanger are connected by a transfer pipe via a transfer pump, and a heat medium to which a pressure loss reducing agent is added flows through the transfer pipe, and the heat-exchanger-side heat exchanger In a heat transport system that transports heat to vessels,
In the transport pipe before the heat medium to which the pressure loss reducing agent of the heat exchanger is added flows, a branch pipe that branches a part of the heat medium from the transport pipe is provided, and the branch pipe is connected to the tank-type heat transfer pipe. This is achieved by connecting and forming an injection hole in the heat transfer tube.

A further object of the present invention is to provide a plate-type heat exchanger in which plates are stacked and a flow path between the plates in which a first heat medium and a second heat medium flow alternately. The heat exchanger on the heat receiving side and the heat exchanger on the heat radiating side configured as described above are connected by a transport pipe via a transport pump, and a heat medium to which a pressure loss reducing agent is added flows in the transport pipe, and the heat receiving side is connected. In the heat transfer system for transferring heat from the heat exchanger to the heat exchanger on the heat radiation side, a part of the heat medium is transferred to a transfer pipe of the heat exchanger before the heat medium to which the pressure loss reducing agent is added flows. Providing a branch pipe branching from a transport pipe, inserting a nozzle into the laminated plate, and forming an injection hole in a portion of the nozzle in a flow path of a heat medium to which the pressure loss reducing agent is added. Achieved by

Further, the object of the present invention is to connect the heat exchanger on the heat receiving side and the heat exchanger on the heat radiating side by a transport pipe via a transport pump, and to flow a heat medium containing a pressure loss reducing agent into the transport pipe. In the heat transport system for transporting heat from the heat exchanger on the heat receiving side to the heat exchanger on the heat radiating side, the transport pump is installed on an outlet side of a heat medium of the heat exchanger, and near an outlet of the transport pump. A branch pipe for branching a part of the heat medium from the transport pipe is provided in the pipe, and the flow of the heat medium in the heat transfer pipe is supplied to the branch pipe via a flow rate control valve in a direction perpendicular to the heat transfer surface. This is achieved by connecting a flow nozzle with

[0015]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a system diagram of a first embodiment of a transportation system according to the present invention. For example, a description will be given of a thermal transport system for utilizing exhaust heat from a suburban factory for air conditioning of a building in an urban area.

The heat exchanger 9a is installed on the factory side which is a heat source, the heat exchanger 9b is installed on a building which is a heat utilization side, and further, the secondary medium 2 which has exchanged heat with the heat medium in the heat exchanger 9b.
9 is a system configuration for transporting the 9 to a fan coil (not shown) in each room.

In this embodiment, these heat exchangers 9a, 9b
(That is, in front of the heat medium flowing into the heat exchangers 9a and 9b when viewed from the inflow side), a part of the heat medium 3 is branched from the transport pipe 2 by the transport pipe 2 by the branch pipe 5 and passed through the jet pump 6 After pressurization, heat exchangers 9a, 9b
Immediately before the heat transfer surface 31, the branched heat medium 4 is returned to the mainstream again as a jet from the nozzle 7 so as to have a momentum component in a direction perpendicular to the heat transfer surface 31. Since this jet disturbs the main flow of the heat medium 4 flowing in the heat transfer tubes 30 of the heat exchangers 9a and 9b, the heat transfer coefficient of the heat medium 4 in the heat transfer tubes 30 is improved.

FIG. 2 shows a second embodiment of the transportation system according to the present invention.
It is a system diagram of an Example. In this embodiment, the heat exchangers 9a, 9
In the heat transport between b and b, a branch pipe 5 is provided near the outlet of the transport pump 1 for transporting the heat medium 4 via a flow control valve 11, and this branch pipe 5 is connected to the nozzle 7, as shown in FIG. The jet pump 6 shown in FIG. That is, in the present embodiment, a jet is created by utilizing the outlet pressure of the transport pump 1. Reference numeral 10 denotes a buffer tank, which acts as a buffer so that the heat medium 4 does not flow rapidly in the transport pipe 2.

This embodiment is particularly effective when the heat exchangers 9a and 9b and the transport pump 1 can be installed relatively close to each other, and the jet pressure can be sufficiently generated by the outlet pressure of the transport pump 1. It is.

According to this embodiment, the heat transfer rate can be improved without adding a pump to the heat transport system.

FIG. 3 is a longitudinal sectional view of a first embodiment of the heat exchanger in the embodiment of FIG. FIG. 4 is an enlarged view of the vicinity of the heat transfer tube of the embodiment of FIG. In this embodiment, an aqueous solution to which a surfactant for forming micelles is added is flowed as a heat medium 3 inside the tubes of the shell-and-tube type heat exchangers 9a and 9b. The heat medium 4 partially branched from the transport pipe 2 before entering the heat exchangers 9a and 9b is returned to the main flow of the heat medium 3 again immediately before the heat transfer surface 31 through the nozzle 7. The injection hole 8 at the tip of the nozzle 7 is oriented in a direction perpendicular to the heat transfer surface 31, and the branched heat medium 4 ejected from the nozzle hole 8 has a momentum in the direction perpendicular to the heat transfer surface 31. It is gushing. Since the jetted heat medium 4 disturbs the mainstream heat medium 3 in a direction perpendicular to the heat transfer surface 31, the heat transfer coefficient inside the tube is improved (recovered to the value of water).

It is desirable that a plurality of injection holes 8 provided in the nozzle 7 be provided in the circumferential direction of the nozzle 7 as necessary so that the turbulence can continue to the end of the heat transfer tube 12.

In this embodiment, a rectifier 26 is provided near the outlets of the heat exchangers 9a and 9b. This is for removing the turbulence from the heat medium 3 after the heat exchange forcibly and rectifying the heat. If the rectification can be performed efficiently, the space between the outlet of the heat transfer pipe 12 and the inlet of the heat transport pipe is provided. If the turbulence at the outlets of the heat exchangers 9a and 9b is small and does not affect the heat transport, there is no need to provide them.

On the contrary, if the turbulence can be maintained up to the end of the heat transfer tube 12, even a U-tube (or more connected type) shell and tube type heat exchanger can be used. No problem.

FIG. 5 is a longitudinal sectional view of a second embodiment of the heat exchanger in the embodiment of FIG. In this embodiment, the heat transfer tubes 12
On the downstream side of the nozzle 7 provided therein, there is provided a shield 13 that changes the cross section of the pipe. With such a configuration, it is possible to cause the jets emitted from the plurality of injection holes 8 of the nozzle 7 to interfere with each other due to a change in the cross section by the shield 13 so that the turbulence reaches every corner of the mainstream. It is possible to further improve the heat transfer coefficient.

In the present embodiment, a vortex enhancer 28 is provided on the downstream side of the injection hole 8 of the nozzle 7. By providing the vortex enhancer 28, the flow of the main heat medium 3 can be guided to the pipe wall side without difficulty on the downstream side of the injection hole 8, so that the turbulence due to the jet flow can be sufficiently transmitted to the pipe wall. Can be carried. Needless to say, the height of the vortex accelerating member 28 with respect to the inner diameter of the heat transfer tube 12 is set so that the flow velocity of the annular portion formed by the vortex accelerating member 28 and the tube wall does not become excessive.

FIG. 6 is a longitudinal sectional view of a third embodiment of the heat exchanger in the embodiment of FIG. In this embodiment, the heat transfer tubes 12
The nozzle 7 provided inside reaches the end of the heat transfer tube 12, and has a configuration in which injection holes 8 are provided at a plurality of positions in the longitudinal direction of the nozzle 7 (longitudinal direction of the heat transfer tube).

First, the jet from the injection hole 8 near the start end of the heat transfer tube 12 disturbs the heat medium 4, but as it goes to the downstream side,
The disturbance is alleviated. In the vicinity where the turbulence is reduced, the next injection hole 8 is provided, and the new jet strongly disturbs the main flow of the heat medium 4 again. By repeating this in the longitudinal direction, apparently large turbulence can be maintained over the entire length of the heat transfer tube 12 in the longitudinal direction.

That is, this embodiment is particularly suitable for a shell-and-tube type heat exchanger in which the length of the heat transfer tube 12 is long and a U-shaped tube is not used. In the present embodiment, the heat transfer tube 1
In the case where a partially branched heat medium 4 for jet flow is introduced into the nozzle 7 from the start end side and the end side of the nozzle 2, the outlet pressure of the jet pump 6 is sufficient for the total pressure loss of the nozzle 7. May be introduced only from one end of the heat transfer tube 12.

FIG. 7 is a longitudinal sectional view of a fourth embodiment of the heat exchanger in the embodiment of FIG. This embodiment has a configuration in which the nozzle 7 is provided inside a support 14 that supports the heat transfer tube 12. With such a configuration, first, since the starting end of the heat transfer tube 12 is completely opened as compared with that shown in FIG. 3, the pressure loss of the main flow flowing in the heat transfer tube 12 of the heat exchanger 9 can be reduced. In addition, the number of parts constituting the nozzle 7 can be reduced.

Further, by using the inside of the support member 14 as the nozzle 7, a jet can be jetted from the tube wall side, so that large turbulence having an initial amplitude of the tube diameter can be easily produced.

FIG. 8 is a longitudinal sectional view of a fifth embodiment of the heat exchanger in the embodiment of FIG. In this embodiment, an injection chamber 23 having a larger diameter than the central part is provided in the tube plate 23A at the inlet end of the heat transfer tube 12 which is a heat transfer tube, and the injection holes 8 are provided in the upper and lower parts of the injection chamber 23. It has a configuration. Furthermore, the positions of the upper and lower injection holes 8 with respect to the flow direction are provided to be shifted in the longitudinal direction of the heat transfer tube 12. Since the jet flow from the upper part to the lower part and the jet flow from the lower part to the upper part of the injection chamber 23 are jetted from the injection holes 8 having such an arrangement, it is possible to form a vertical vortex in the main flow in the flow direction. For this reason, compared with what is shown in FIG. 3, even with the same jet flow rate, large turbulence can be maintained efficiently.

It is preferable that the diameter of the injection chamber 23 is larger than the diameter of the central portion of the heat transfer tube 12 so that the vortex is easily formed, and the flow velocity of the mainstream heat medium 4 is reduced. In addition, it is preferable that the injection hole 8 located on the upstream side is provided with a large inclination on the downstream side so as to easily form a vortex even in the flow of the main stream, and is injected toward the upstream side.

FIG. 9 is a longitudinal sectional view of a sixth embodiment of the heat exchanger in the embodiment of FIG. FIG. 10 is an enlarged view of the vicinity of the nozzle in the embodiment of FIG. In the present embodiment, an aqueous solution containing a surfactant forming micelles was added to the inside of the pipe of a bayonet type shell-and-tube heat exchanger.
It is configured to flow as the heat medium 3. In this embodiment, as shown in FIG. 8A, the outlet of the inner pipe 15 is a nozzle 7 that creates a jet, and the total heat medium 3 flowing between the inner pipe 15 and the outer pipe 16 is in a state of being greatly disturbed. Has become
Heat transfer efficiency is greatly improved (recovers to water value).

In particular, in this embodiment, the guide member 27 is provided near the outlet of the nozzle 7, so that the jet flowing out of the nozzle hole 8 of the nozzle 7 can reduce the loss of momentum, Direction. In this embodiment, since all the heat medium 3 is pressurized before the heat exchanger, it is effective for a system with a relatively small flow rate.

FIG. 11 is a longitudinal sectional view of a seventh embodiment of the heat exchanger in the embodiment of FIG. In this embodiment, the inner pipe 15
In addition to the injection holes 8a provided at the outlets, the injection holes 8 are provided at a plurality of locations in the longitudinal direction. With such a configuration, the main flow of the heat medium 3 can be largely disturbed in the entire area of the heat transfer tube, and the flow of the injection hole 8 By adding a jet from the turbulence, more complicated turbulence can be formed and the heat transfer efficiency can be improved.

Further, as compared with the embodiment shown in FIG. 8, the flow rate of the heat medium 3 is larger and the heat transfer tube 30 has a longer length and is suitable for a large-capacity heat exchanger 9.

FIG. 12 is a longitudinal sectional view of an eighth embodiment of the heat exchanger. In this embodiment, a double-pipe heat exchanger including an inner pipe 15 and an outer pipe 16 is formed, and micelles are formed between the outer surface of the inner pipe 15 and the inner surface of the outer pipe 16. It is configured to flow an aqueous solution to which a surfactant is added. By forming the nozzle 7 for ejecting the partially branched heat medium 4 into a shape protruding into the annular portion, the main flow heat medium 3 is squeezed at this portion to form a jet, and then a jet from the injection hole 8 is further added. it can.

Further, in this embodiment, fins 17 for increasing the heat transfer area are provided on the outer surface of the inner tube 15, and the fins 17 also serve to further disturb the jet. With such a configuration, the turbulence of the main flow of the heat medium 3 due to the jet from the nozzle 7 and the restriction of the main flow, and the expansion and turbulence of the heat transfer area due to the fins 17 provided on the outer surface of the inner tube 15 The heat transfer efficiency is greatly improved by promoting the heat transfer.

FIG. 13 is a longitudinal sectional view of a ninth embodiment of the heat exchanger. Although the basic configuration is the same as that of the eighth embodiment, the difference is that a constricted portion 32 is formed in a part of the outer tube 16 and the injection hole 8 is formed in the constricted portion 32. The heat medium 4 which is partially branched is jetted.

According to the present embodiment, the pressure is reduced at the constricted portion 32, and a so-called ejector pump is formed. Therefore, it is not necessary to provide a separate pump for ejecting the heat medium 4, so that the cost of the heat transport system is reduced. Reduction can be achieved.

FIG. 14 is a longitudinal sectional view of a tenth embodiment of the heat exchanger. In this embodiment, an aqueous solution obtained by adding a surfactant is used as the heat medium 3 in the fluid in the tank of the coil tank type heat exchanger. The main flow of the fluid in the tank flows into the tank from the inlet pipe 19 and flows out from the outlet pipe 20. In addition to this flow, the heat medium 4 partially branched before the heat exchanger 9 is blown out from the injection hole 8 of the nozzle 7 provided at the center of the coiled heat transfer tube 18 and is added again to the main flow. This jet disturbs the heat medium 3 around the coiled heat transfer tube 18 to improve the heat transfer coefficient.

In particular, in the present embodiment, the distribution density of the injection holes 8 can be changed according to the temperature distribution of the heat medium flowing in the coiled heat transfer tube 18 and the like, so that heat can be exchanged more efficiently. Further, by changing the number of turns of the coil heat transfer tube 18 and the distribution density of the injection holes 8, design changes such as scale-up can be performed relatively easily.

FIG. 15 is a longitudinal sectional view of an eleventh embodiment of the heat exchanger. FIG. 16 is a sectional view taken along the line aa ′ in FIG. The present embodiment has a configuration in which an aqueous solution to which a surfactant is added is used as the A heat medium 3a, which is one heat medium of the plate type heat exchanger. A heat medium 3a before the heat exchanger
The nozzle 7 for returning the heat medium 4a, which has been partially branched from the main flow, to the main flow again as a jet,
Along the flow path of the heat medium 3a, the heat medium reaches the inlet of the heat medium flow path 22 between the plates. Further, the nozzle 7 is provided with one or a plurality of injection holes 8 at a portion corresponding to an inlet of the heat medium flow path 22 between the plates.

That is, in this embodiment, as shown in FIG. 16, a plurality of injection holes 8 are provided in the heating medium flow path 22 between one plate, or injection holes having various shapes and hole diameters are provided. It is easy to provide the holes 8 in combination. For this reason, the heat transfer coefficient can be further improved by combining these to cause the jets to interfere with each other so that the turbulence extends to every corner.

The nozzle 7 is also constructed and arranged on the B heat medium side in the same manner as the A heat medium 3a, so that the B heat medium 3b
Since an aqueous solution to which a surfactant is added can be used, the present embodiment can be widely applied to heat exchange between aqueous solutions to which a surfactant is added.

FIG. 17 quantitatively explains the effect of improving the heat transfer coefficient according to the present invention.

An aqueous solution to which a surfactant was added was passed through a rectangular tube, and the heat transfer coefficient was measured when one wall surface (upper surface) of the rectangular tube was used as a heat transfer surface for heat exchange. The Reynolds number Re (dimensionless) is plotted on the horizontal axis, and the heat transfer reduction rate ε (dimensionless) is plotted on the vertical axis.

In the figure, the circles indicate the results of an aqueous solution (surfactant: cetyltrimethylammonium chloride, counter ion agent: sodium salicylate) to which 500 ppm of a surfactant was added. 5 shows an example of a result when% is used as a jet. Note that the jet flows from the wall (lower surface) facing the heat transfer surface just before the heat transfer surface.
The jet was ejected perpendicular to the main stream flowing through the rectangular tube. For the representative diameter in calculating the Reynolds number on the horizontal axis, the diameter equivalent to hydraulic power obtained by dividing the cross-sectional area in the flow direction by 4 times the length of the immersion side is used, and the heat transfer reduction rate ε on the vertical axis is The one defined by the following equation (1) was used.

Ε = h (S) / h (W) (1) where h (W) is the heat transfer coefficient when only water is used, and h (S) is the heat transfer coefficient when the surfactant-added aqueous solution is used. Or the heat transfer coefficient when 12% of this aqueous solution is used as a jet. As is clear from this figure, in the case of the aqueous solution to which the surfactant was added at 500 ppm, the heat transfer reduction rate ε was reduced to about 0.2, while when 12% of the aqueous solution was jetted, It can be seen that the heat transfer reduction rate ε has increased (recovered) to about 0.9.

Since the effect varies depending on the pipe diameter, the circulation velocity, the diameter of the injection hole, and the ratio of the jet, it goes without saying that the optimum combination is selected.

[0052]

According to the present invention, in a heat transport system in which a surfactant that forms micelles is added to the heat medium, a part of the heat is transferred from the transport pipe before the heat medium enters the heat exchanger. After the medium is branched and pressurized, it is mixed again into the main flow of the heat medium immediately before the heat exchanger as a jet having a component perpendicular to the heat transfer surface of the heat exchanger.

Alternatively, before the heat exchanger, all the heat medium is pressurized and then introduced into the heat exchanger as a jet. By doing so, the mixed jet creates turbulence in the heat medium, so that the heat transfer coefficient can be improved.

Accordingly, since the flow is disturbed only in the heat exchanger, the effect of reducing the pressure loss in the pipe due to the addition of the surfactant is not impaired during the heat transport.

[Brief description of the drawings]

FIG. 1 is a system diagram of a first embodiment of a transportation system according to the present invention.

FIG. 2 is a system diagram of a second embodiment of the transportation system according to the present invention.

FIG. 3 is a longitudinal sectional view of a first embodiment of the heat exchanger in the transportation system of FIG. 1;

FIG. 4 is an enlarged view of the vicinity of the heat transfer tube of the first embodiment of FIG.

FIG. 5 is a longitudinal sectional view of a second embodiment of the heat exchanger.

FIG. 6 is a longitudinal sectional view of a third embodiment of the heat exchanger.

FIG. 7 is a longitudinal sectional view of a fourth embodiment of the heat exchanger.

FIG. 8 is a longitudinal sectional view of a fifth embodiment of the heat exchanger.

FIG. 9 is a longitudinal sectional view of a sixth embodiment of the heat exchanger.

FIG. 10 is an enlarged view of the vicinity of the heat transfer tube of the embodiment of FIG.

FIG. 11 is a longitudinal sectional view of a seventh embodiment of the heat exchanger.

FIG. 12 is a longitudinal sectional view of an eighth embodiment of the heat exchanger.

FIG. 13 is a longitudinal sectional view of a ninth embodiment of the heat exchanger.

FIG. 14 is a longitudinal sectional view of a tenth embodiment of the heat exchanger.

FIG. 15 is a longitudinal sectional view of an eleventh embodiment of the heat exchanger.

FIG. 16 is a sectional view taken along the line aa ′ in the embodiment of FIG. 11;

FIG. 17 is a diagram quantitatively explaining an improvement in the efficiency of heat transfer in the transportation system according to the present invention.

[Description of Signs] 1 ... Transport pump, 2 ... Transport pipe, 3 ... Heat medium, 3a ... A
Heating medium, 3b ... B heating medium, 4 ... partially branched heating medium,
4a: A heat medium partially branched, 5: branch pipe, 6: jet pump, 7: nozzle, 8: injection hole, 9, 9a, 9b: heat exchanger, 10: buffer tank, 11: flow rate adjustment Valve, 12: heat transfer tube, 13: shield, 14: support, 15
... inner tube, 16 ... outer tube, 17 ... fin, 18 ... coiled heat transfer tube, 19 ... inlet tube, 20 ... outlet tube, 21 ... plate,
22: A heat medium flow path between plates, 23: injection chamber, 24a
... A heat medium inlet, 24b ... B heat medium inlet, 25a ... A heat medium outlet, 25b ... B heat medium outlet, 26 ... Rectifier, 27
... Guide, 28 ... Swirl accelerator, 29 ... Secondary medium, 30 ... Heat transfer tube, 31 ... Heat transfer surface.

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Toshihiko Fukushima 502 Kandate-cho, Tsuchiura-shi, Ibaraki F-term in Machinery Research Laboratory, Hitachi, Ltd. (Reference) 3L103 AA16 AA37 AA39 BB42 DD05 DD08 DD15 DD19 DD38 DD42 DD43 DD55 DD58 DD62

Claims (6)

[Claims] 1. A heat exchanger on a heat receiving side and a heat exchanger on a heat radiating side are connected by a transport pipe via a transport pump, and a heat medium to which a pressure loss reducing agent is added flows through the transport pipe to receive the heat. In the heat transport system for transporting heat from the heat exchanger on the side to the heat exchanger on the heat radiating side, a part of the heat medium is inserted into a transport pipe of the heat exchanger before the heat medium to which the pressure loss reducing agent is added flows. A branch pipe is provided for branching from the transport pipe, and a nozzle for creating a flow of a momentum component in a direction perpendicular to the heat transfer surface through the flow of the heat medium in the heat transfer pipe is connected to the branch pipe via a jet pump. A heat transport system, characterized in that: 2. A heat exchanger configured by inserting and fixing an end of a heat transfer tube into a tube sheet, and transporting the heat exchanger on the heat receiving side and the heat exchanger on the heat radiation side configured as described above by a transport tube. A heat medium to which a heat medium to which a pressure loss reducing agent has been added flows through the heat transfer pipe to transfer heat from the heat exchanger on the heat receiving side to the heat exchanger on the heat radiating side. A branch pipe that branches a part of the heat medium from the transport pipe is provided in the transport pipe before the heat medium to which the pressure loss reducing agent of the exchanger is added flows, and the inlet side of the heat transfer pipe that is inserted into and fixed to the tube sheet. An injection chamber having a diameter larger than the diameter of the pipe at the center is formed at the end, and an injection hole for creating a flow of a momentum component in a direction perpendicular to the heat transfer pipe is provided in the heat transfer pipe forming the injection chamber. A heat transport system characterized by connecting. 3. A pump for transporting a double-pipe heat exchanger composed of an inner pipe and an outer pipe, and a heat-receiving-side heat exchanger and a heat-radiating-side heat exchanger configured as described above by a transport pipe. And a heat transfer system in which a heat medium to which a pressure loss reducing agent is added flows in the transfer pipe to transfer heat from the heat exchanger on the heat receiving side to the heat exchanger on the heat radiating side. In the transport pipe before the heat medium to which the pressure loss reducing agent is added flows, a branch pipe that branches a part of the heat medium from the transport pipe is provided, and a fin is attached to an outer surface of the inner pipe. Heat transport system. 4. A heat exchanger comprising a tank-type heat transfer tube, a coil-type heat transfer tube wound around the outer surface of the tank-type heat transfer tube, a heat exchanger on the heat receiving side and a heat radiating side having such a structure. Is connected to the heat exchanger through a transport pump by a transport pipe, and a heat medium to which a pressure loss reducing agent is added flows through the transport pipe to transfer heat from the heat exchanger on the heat receiving side to the heat exchanger on the radiating side. In the heat transport system for transporting, the transport pipe before the heat medium to which the pressure loss reducing agent of the heat exchanger is added flows, a branch pipe that branches a part of the heat medium from the transport pipe is provided, and the tank type is provided. A heat transfer system, wherein the branch pipe is connected to the heat transfer pipe and an injection hole is formed in the heat transfer pipe. 5. A plate type heat exchanger in which plates are stacked and a flow path between the plates in which a first heat medium and a second heat medium flow alternately is provided. The heat exchanger on the heat receiving side and the heat exchanger on the heat radiating side are connected by a transport pipe via a transport pump, and a heat medium to which a pressure loss reducing agent is added flows in the transport pipe to cause heat exchange on the heat receiving side. In the heat transfer system for transferring heat from the heat exchanger to the heat exchanger on the heat radiation side, a part of the heat medium is transferred from the transfer pipe to a transfer pipe before the heat medium to which the pressure loss reducing agent of the heat exchanger is added flows. A branch pipe for branching is provided, a nozzle is inserted into the laminated plate, and an injection hole is formed in a portion of the nozzle in a flow path of a heat medium to which the pressure loss reducing agent is added. Heat transport system. 6. A heat exchanger on a heat receiving side and a heat exchanger on a heat radiating side are connected by a transport pipe via a transport pump, and a heat medium to which a pressure loss reducing agent is added flows through the transport pipe to receive the heat. In the heat transfer system for transferring heat from the heat exchanger on the heat transfer side to the heat exchanger on the heat radiation side, the transfer pump is installed on the heat medium outlet side of the heat exchanger. A branch pipe that branches a part of the medium from the transport pipe is provided. In this branch pipe, a flow having a momentum component in a direction perpendicular to the heat transfer surface through the flow of the heat medium in the heat transfer pipe through a flow control valve. A heat transport system characterized by connecting a nozzle.