JPH041276B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a high-performance, robust, and compact annular heat exchanger in which Z-flow type plate-fin heat exchangers are arranged in an annular manner.

For example, in a conventional annular heat exchanger used in a recuperator heat exchanger of a gas turbine system, as shown in FIG.
A large number of secondary fluid outlet channels c are alternately provided, and a partition wall e is provided with a circumferential secondary fluid channel d between the channels b and c, and a radial direction is provided between the channels b and c. A large number of partition walls g provided with primary fluid flow paths f are stacked alternately.

The primary fluid enters the heat exchanger through the central flow path h formed by the partition walls e and g, and as it passes through the primary fluid flow path f of the partition walls g stacked every other layer, it is heat exchanged and flows outside. leak. In addition, the secondary fluid enters the heat exchanger through the secondary fluid inlet flow path b, and when passing through the secondary fluid flow path d of the partition wall e stacked every other layer, heat is exchanged and the secondary fluid flows into the secondary fluid outlet flow. It enters the passage c and further exits the heat exchanger through the passage c.

Therefore, such conventional annular heat exchangers have the following problems.

(i) The secondary fluid flow path d of the partition e is in the circumferential direction, and the partition wall g
Since the primary fluid flow path f is in the radial direction, the primary fluid and the secondary fluid intersect at right angles in the heat exchange section, resulting in poor heat exchange performance.

(ii) Since the partition walls e and g are provided with a large number of secondary fluid inlet and outlet flow passages b and c, the flow passage area becomes large and the volume of the heat exchanger becomes large.

(iii) It is impossible to investigate problems such as leaks because the surface that seals the fluid is inside the heat exchanger.

(iv) There are many surfaces that seal the fluid, making it difficult to manufacture.

(v) Since the fins use the partition wall as a base material, it is not possible to have a large expansion area ratio, and there is no suitable method for promoting heat transfer.

The present invention was made in order to eliminate the problems of the conventional annular heat exchanger described above, and consists of plate-shaped or plate-fin-shaped heat transfer elements having counterflow sections and diagonal flow sections arranged concentrically. The primary fluid is introduced from the center, exchanged heat with the heat transfer element, and then released radially to the outside, while the secondary fluid is introduced into the secondary fluid inflow duct from one longitudinal side and The annular heat exchanger achieves high performance, robustness, compactness, and easy manufacturing by distributing heat to the heating elements and exchanging heat, then collecting it in a secondary fluid discharge duct and discharging it in one or both longitudinal directions. It depends on the container.

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 2 shows an embodiment of the present invention, in which the counterflow section 1
A large number of Z-flow type plate-fin heat exchangers 3 having a hexagonal cross section and having diagonal flow sections 2 and 2' are laminated to form a hexagonal columnar heat transfer element 4. The sides of the counterflow section 1 are fixed to each other to form a set, and the set is arranged in six concentric circles,
A total of 12 heat transfer elements 4 are arranged in a ring shape, and ducts 5 are fixed at six locations in total between the two vertices of the oblique flow section of each set of heat transfer elements 4 on the outer circumferential side over the entire length of the heat transfer elements 4. At the same time, a duct 7 is provided along the entire length of the heat transfer element 4 between the vertices of the diagonal flow portions 2' of adjacent pairs of heat transfer elements on the inner circumferential side. It is fixed at a total of 6 locations to form a secondary fluid outlet flow path 8.
The annular heat exchanger 9 is formed by forming an annular heat exchanger 9.

As shown in FIGS. 3 to 5, the hexagonal Z-flow type plate fin heat exchanger 3 has six
A Z-flow type corrugated plate 11 is arranged between the rectangular plate-shaped partition walls 10, 10, and the opposing flow paths 16,
The torsion plates 12 are respectively housed in the corrugated plates 16', and seal plates 13 are attached to both side surfaces of the corrugated plates 11. Outlet channel 15', 15
A plurality of hexagonal columnar heat transfer elements 4 are formed by laminating a plurality of heat transfer elements 4 in such a manner that they intersect obliquely with each other.

FIG. 6 shows the parts of each component, and the front side of the partition wall 10 is a flow path for the primary fluid, and a corrugated plate 11 that functions as a fin is arranged to seal the primary fluid and flow the secondary fluid. Seal plates 17, 18 are provided for the passage configuration. Partition wall 10 and partition wall 1
0' is a flow path for the secondary fluid, and a corrugated plate 11 that functions as a fin is arranged similarly to the secondary fluid side, and seal plates 19 and 20 are further provided for sealing the secondary fluid. ing. In the above, corrugated plates 11, 11, seal plates 17, 18, 19
Six pieces are arranged for each flow path.

With the above configuration, the primary fluid flows into the center of the annular heat exchanger 9 and enters the heat transfer element 4 from the primary fluid inlet flow path 14 through the opening facing inside of each heat transfer element 4. The fluid enters the flow path, passes through the opposing flow path 16, and is discharged to the outside from the outlet flow path 15 of the oblique flow section 2.
Further, the secondary fluid flows into each inlet flow path 6 formed by each duct 5, and the secondary fluid inlet flow path flows from the opening facing into each of the inlet flow paths 6 of each heat transfer element 4. 1
4' into the heat transfer element 4 and flows out through the counterflow channel 16' from the outlet channel 15' of the diagonal flow channel 2' into the secondary fluid outlet channel 8 formed by each duct 7. .

In the above, the primary fluid and the secondary fluid can be introduced from either or both of the center of the annular heat exchanger 9 and the openings at both ends of the inlet channel 6, and the secondary fluid can be introduced into the outlet channel 8. The water can flow out from either or both of the openings at both ends.

In this way, the primary fluid and the secondary fluid flow oppositely through the jet-shaped flow path partitioned by the partition wall, and heat is exchanged with each other.

FIG. 7 shows another embodiment of the present invention, in which, in a configuration roughly similar to that of the previous embodiment, six heat transfer elements 4 are arranged on a concentric circle instead of a set of two heat transfer elements 4 as in the previous embodiment. The heat transfer elements 4 are arranged in an annular manner, and between the two vertices of the oblique current portions of two adjacent heat transfer elements 4 on the outer circumferential side.
The duct 5' is fixed at a total of three locations over the entire length of the duct 5' to form an inlet flow path 6' for the secondary fluid, and an adjacent heat transfer element different from the heat transfer element to which the duct 5' is fixed is formed on the inner peripheral side. This is an example in which ducts 7' are fixed at three locations in total between the vertices of the oblique flow section 2' of the heat transfer element 4 over the entire length of the heat transfer element 4 to form an outlet flow path 8' for the secondary fluid. . In FIG. 7, the same reference numerals as in FIGS. 2 to 6 indicate the same parts.

In this example, the same heat exchange effect as in the previous example can be obtained. In particular, in this example, the number of heat transfer elements is 6, which is half of that in the previous example, so that the outer diameter of the annular portion is The inner diameter becomes smaller and the heat transfer area can be increased for the same volume.

Note that the annular heat exchanger of the present invention is not limited to the above-mentioned embodiments, and any plate-fin heat exchanger can be used as long as it is a Z-flow type, and corrugated plates that act as fins can be used. It does not depart from the gist of the present invention, such as not using a torsion plate inside, and providing fluid flow path ducts on the inlet and outlet sides of the primary fluid so as to be able to cope with the inflow and outflow of the primary fluid. Of course, various changes can be made within the scope.

As described above, the annular heat exchanger of the present invention exhibits various excellent effects as described below.

() The primary fluid is introduced from the center and discharged to the outer circumference, and the secondary fluid is introduced from the outer circumferential duct and discharged from the inner circumferential duct, and heat exchange is performed mainly by counterflow, thereby improving heat exchange performance. Can be used as a high heat exchanger.

() Since the secondary fluid flow path can be installed in a location other than the area occupied by the heat transfer element surrounded by the annular inner and outer peripheries, the heat exchange area can be used effectively.
The heat transfer area per unit volume can be increased.

() The sealing surface joins the seal plate and the partition wall with good flatness, resulting in good sealing performance and robustness.

() Since the bulkhead and corrugated plate are separate, it is possible to select a fin structure that suits the fluid conditions.

() If a heat transfer promoter such as a torsion plate is provided between the fins, heat transfer performance can be improved and the heat exchanger can be further downsized.

[Brief explanation of drawings]

FIG. 1 is an explanatory diagram of a conventional annular heat exchanger, FIG. 2 is an explanatory diagram of an embodiment of the annular heat exchanger of the present invention, FIG. 3 is a detailed explanatory diagram of the part shown in FIG. 2, and FIG. FIG. 5 is an assembled view of the heat transfer element shown in FIG. 3, FIG. 5 is a view taken in the - direction of FIG. 3, FIG. 6 is an explanatory diagram of the constituent parts of the annular heat exchanger in FIG. shows an explanatory view of another embodiment of the annular heat exchanger of the present invention. 1 is an opposing flow section, 2 and 2' are oblique flow sections, 4 is a heat transfer element, 5, 5', 7, and 7' are ducts, 6 and 6' are inlet channels, and 8 and 8' are outlet sides. Channel 9 indicates an annular heat exchanger.

Claims (1)

[Claims] 1. A heat transfer element formed by stacking Z-flow type plate-fin heat exchangers is arranged in an annular shape so that the primary fluid introduced from the center of the annular body is discharged to the outer periphery of the annular body. A duct for introducing the secondary fluid is provided on the outer peripheral portion, and a duct for taking out the secondary fluid is provided in the center of the annular body, so that heat is exchanged between the primary fluid and the secondary fluid in counterflow. An annular heat exchanger characterized by: