JPH0573996B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a laminate-type heat exchanger.

BACKGROUND TECHNOLOGY A conventional laminated plate heat exchanger, as shown in FIGS. 13 to 15, has a heat transfer plate 42 formed by drilling groove-shaped fluid passages 41A and 41B in a thick flat plate. laminate a plurality of sheets, or as shown in FIG.
The template plates 52 with the fluid passages 41A, 41B or 51A, 51A, 52A and 52 having
Fluid supply nozzles 44 each communicating with 51B
A, 45A and fluid discharge nozzles 44B, 45B
The end plates 46 and 47 were provided.

Furthermore, a structure in which thin plates are laminated at regular intervals has also been proposed.

Problems to be Solved by the Invention According to the above configuration, the fluid passages 41A, 4 are provided in the flat plate.
To form 1B, etching, coining, or cutting is performed, but with the etching method, it is difficult to control the depth of the groove, and the material removed by etching is wasted. In addition, with the coining method, it is difficult to process deep grooves and it is difficult to create complex groove shapes. Furthermore, the method of cutting the groove portion takes too much time. Further, in order to provide the fluid passages 51A and 51B through the template 52, there is a limit to the manufacturing accuracy of the template 52, and there are disadvantages such as a large number of joints. Furthermore, in each of the above methods, the thickness of the heat exchanger plate is large, so the weight of the heat exchanger tends to be large. In addition, the type with laminated thin plates cannot be used when there is a pressure difference in the fluid because if there is a pressure difference in the fluid that exchanges heat, the thin plates may deform and block the passage. .

The present invention solves the above-mentioned problems, and the processing of the heat exchanger plates is easy, the number of joints between the heat exchanger plates is small, the weight of the heat exchanger can be reduced, and the pressure difference between the fluids can be reduced. The purpose of the present invention is to provide a laminated plate heat exchanger that can be used even if it is large.

Means for Solving the Problems In order to solve the above problems, the present invention provides spiral grooves formed by the uneven shape of the heat exchanger plate itself on the upper and lower surfaces of the left and right portions of the first heat exchanger plate. A through hole is formed at the center of each of the spiral grooves on the left and right portions, and the respective ends of the spiral grooves on the left and right portions on the upper and lower surfaces are communicated with each other, so that a second heat exchanger plate that is plane symmetrical to the first heat exchanger plate is formed. the first and second heat exchanger plates are stacked alternately, and the bottom outer surfaces of the opposite spiral grooves are joined to form a cross-sectional honeycomb structure; 1 fluid passage is formed, and a second fluid passage is formed by opposing spiral grooves of the first heat exchanger plate and another second electric heating plate, and the left and right spiral centers of each first fluid passage are formed by the through holes. A configuration in which the left and right spiral groove centers of each second fluid passage are communicated with each other to form an inflow passage and an outflow passage for the first fluid, and the left and right spiral groove centers of each second fluid passage are communicated through the through hole to form an inflow passage and an outflow passage for the second fluid. That is.

Effect With the above configuration, each fluid is sent from the inflow passage to each fluid passage, exchanges heat with each adjacent fluid passage around the fluid passage through each heat transfer plate, and then is discharged from each outflow passage. . At this time, even if there is a pressure difference between each fluid, the fluid is flowed throughout the entire compartment space through the fluid passage formed by the honeycomb-shaped cross section, so there is no formation of a heat transfer plate. Heat exchange can be performed.

Embodiment An embodiment of the present invention will be described below with reference to FIGS. 1 to 7.

1 to 5, reference numeral 1 denotes a first heat exchanger plate in which a thin plate is formed in an uneven shape, and a first spiral groove 2A having an inverted trapezoidal cross section is formed on the upper surface of the left and right portions, and the lower surface thereof. It has a second spiral groove 2B having an inverted trapezoidal cross section formed by the unevenness of the first spiral groove 2A. Then, on the upper surface of this first heat exchanger plate 1, a first
A first recess 3A is formed in the center of the spiral groove 2A, and the ends of the first spiral groove 2A on the left and right portions are connected to form each first recess 3.
A are in communication with each other, and the first recess 3A has a first
A through hole 4A is formed. Further, on the lower surface of the first heat exchanger plate 1, a second recess 3B is formed in the center of the second spiral groove 2B, and the second spiral groove 2B communicates with the second spiral groove 2B. The ends are connected and the second recesses 3B communicate with each other, forming a second through hole 4B at the center of the second recess 3B. The depths of the spiral grooves 2A, 2B and the recesses 3A, 3B are set to be the same, and an outer peripheral edge 5 is formed around the first heat exchanger plate 1 flush with the bottom outer surface of the second spiral groove 2B. be done.

Reference numeral 6 denotes a second heat exchanger plate that is plane symmetrical to the first heat exchanger plate 1, and includes the first and second spiral grooves 2A, 2B of the first heat exchanger plate 1, the first and second recesses 3A, 3B, and the first and second heat exchanger plates. Second
Through holes 4A, 4B, third and fourth spiral grooves 7A, 7B facing outer peripheral edge 5, third and fourth recesses 8A, 8B, third and fourth through holes 9A,
9B and an outer peripheral edge 10 are formed.

Reference numeral 11 denotes a heat exchanger body in which a plurality of first heat exchanger plates 1 and second heat exchanger plates 6 (six sheets each in the drawing) are laminated alternately, and the joints 20a to 20c, that is, FIGS. 2 and 3 As shown in FIG.
The bottom outer surfaces 20a of A and 7A, 2B and 7B, the bottom outer surfaces 20b of recesses 3A and 8A, 3B and 8B, and the inner surfaces 20c of outer peripheral edges 5 and 10 are joined to form a honeycomb-shaped cross section. 12A, 12B
is an end plate disposed at the end of the heat exchanger 11 in parallel with the heat transfer plates 1 and 6, and one end plate 12A has first and third through holes 4A and 9A and a first fluid at an opposing position. A inflow nozzle 13A and outflow nozzle 13B
are provided through the second and fourth through holes 4.
An inflow nozzle 1 for the second fluid B is located at a position opposite to B, 9B.
4A and an outflow nozzle 14B are installed through it. In this end plate 12A, the bottom outer surface 20a of the four spiral grooves 7B of the second end heat transfer plate 6 and the bottom outer surface 20b of the fourth recess 8B are joined to the other end plate 12B. The bottom outer surface 20a of the first spiral groove 1A of the heat exchanger plate 1 and the bottom outer surface 20b of the first recess 3A are joined.

15 are first and third spiral grooves 2 facing each other;
A, 7A, or a first fluid passage formed by the end plates 12A, 12B and the first or third spiral grooves 2A, 7A of the end heat exchanger plates 1, 6, and the first and third recesses facing each other. 3A, 8A, or end plate 17
A, 17B and the first or third recesses 3A, 8A of the end heat exchanger plates 1, 6, and communicate with each other through the first and third through holes 4A, 9A.
The inflow passage 16A and the outflow passage 16B are communicated with each other.

17 are second and fourth spiral grooves 2 facing each other;
B, 7B, or a second fluid passage formed by the end plates 12A, 12B and the second or fourth spiral grooves 2B, 7B of the end heat exchanger plates 1, 6, and second and fourth recesses facing each other. 3B, 8B, or end plate 17
A, 17B and the second or fourth recesses 3B, 8B of the end heat exchanger plates 1, 6, and communicated with each other by the second and fourth through holes 4B, 9B.
The inflow passage 18A and the outflow passage 18B are communicated with each other. In these fluid passages 15, 17,
Each of the fluids A, B is directed in opposite directions to each other, e.g.
When the fluid A is flown from the left part to the spiral first fluid passage 15 in the right part, the second fluid B is flowed from the right part to the spiral second fluid passage 17 in the left part, and A second fluid outflow passage 18B is located near the first fluid inflow passage 16A on the right side, and a first fluid outflow passage 16B is located near the second fluid inflow passage 18A on the right side.
is formed.

Next, the manufacturing method of the above embodiment is shown in FIGS. 6 and 7.
This will be explained using figures.

As shown in FIG. 6, each through hole 4A, 4B, 9
A and 9B are respectively formed, and the planar first and second heat exchanger plates 1' and 6' whose joint parts 20a to 20c are coated or plated with brazing material are stacked alternately, and their ends are At the end, there is an end heat exchanger plate 1',
End plates 12A, 12 with brazing material coated or plated on the surfaces facing the joints 20a to 20c of 6'.
B is arranged as shown in FIG. 7, and each heat exchanger plate 1',
6' and the end plates 12A and 12B are brazed and joined. Each nozzle 13A, 13B of the end plate 12A,
14A and 14B are attached by welding to the end plate 12A in advance or by welding after the above brazing.
Next, fluid is pressurized from each nozzle 13A, 13B, 14A, and 14B, and the inflow passage 16A, fluid passage 15, and outflow passage 16B of the first fluid A are
, the inflow and passage 18A of the second fluid B, and the fluid passage 17
and the outflow passage 18B are inflated and formed into a predetermined shape.

Next, the effect will be explained.

The first fluid A supplied from the first fluid inflow nozzle 13A to the first fluid inflow passage 16A is sent to the spiral first fluid passage 15 on the left and right sides, as shown in FIG. From the second fluid inflow nozzle 14A to the second
The second fluid B supplied to the fluid inflow passage 18A is
As shown in FIG. 3, the fluid is sent to the spiral second fluid passages 17 on the left and right sides. At this time, in FIG. 1, the first fluid A shown in dots and the second fluid B shown in plain color
are alternately flown through the honeycomb-shaped cross section, and each fluid A, B is almost surrounded by the other fluid, and heat is exchanged with high efficiency via each heat exchanger plate 1, 6. Each of the fluids A and B after heat exchange flows through the outflow passage 16B,
It is discharged from outflow nozzles 13B and 14B via 18B.

8 to 12 show other embodiments. In the above embodiment, this corresponds to the first and second fluid passages 1
In order to adjust the amount of fluid flowing into the fluid passages 15 and 17, throttle portions 33 and 34 are provided at the inlets 31 and 32 of the fluid passages 15 and 17 from the inlet passages 16A and 18A, respectively.
was formed. These aperture parts 33, 34
As shown in FIGS. 10 to 12, respectively,
The width e of the joining part 35 on the side of the entrances 31, 32 is wider than the width E of the conventional joining part 10e, and the narrowed parts 33a, 34a in the width direction are extended toward the entrances 31, 32, and the height h of the entrances 31, 32. Groove portions 2A and 7A facing each other,
A constricted part 33 in the height direction that eliminates the joint between the bottom outer surfaces of 2B and 7B and makes the height smaller than the conventional height H.
b, 34b are configured to reduce the inlet area, and by adjusting the amount of restriction of the restricting portions 34, 35, the fluid A,
Distribute the flow rate of B evenly.

The narrowed portions 34 and 35 are formed in the spiral groove 2 during manufacturing.
It is formed by adjusting the joints on the bottom outer surfaces of A, 2B, 7A, and 7B. That is, when joining each heat exchanger plate 1, 6 and end plate 12A, 12B, spiral grooves 2A facing each other on the sides of inlets 33, 34
and 7A, 2B, and 7B, and the width e of the brazing material applied or plated to these bottom outer surfaces and the opposing end plates 12A, 12B, respectively, to the inlet 33, 34 side, and ，
By removing the brazing material applied or plated on the bottom outer surfaces of the spiral grooves 2A and 7A, 2B and 7B forming the spiral grooves 34, the inlets 33,
34 is narrowed and the bulge in the height h direction is reduced.

According to each of the above embodiments, the cross section has a honeycomb structure and the fluid is sent through alternate passages, so even if there is a pressure difference between the fluids, heat exchange is possible without causing deformation of the heat exchanger plate. be. In addition, flat first and second heat exchanger plates 1 and 6 with brazing material applied or plated at their joints are alternately stacked, and end plates 12A and 12B and each heat exchanger plate 1 and 6 are joined together. Then, the fluid is sent to each nozzle 13A, 13B, 14A,
By press fitting from 14B, each fluid passage 1
5, 17 can be formed easily and in a short time, and the manufacturing cost can be reduced. Furthermore, as shown in other embodiments, the constricted parts 33 and 34 that adjust the flow rate of fluid can be formed very easily by simply increasing or decreasing the joint parts, and the fluid can be evenly distributed to each fluid passage. structure becomes possible.

In each of the above embodiments, the flat heat exchanger plates 1',
Although the fluid passages 15 and 17 were formed by press-fitting fluid after joining 6', each heat exchanger plate may be formed by press working and then joined.

Effects of the Invention As described above, according to the present invention, spiral grooves are formed on the upper and lower surfaces of the first heat exchanger plate, and the spiral grooves are stacked alternately with the plane-symmetrical second heat exchanger plate to form a cross-sectional honeycomb structure. Since the first fluid and the second fluid are configured to flow through the respective fluid passages, even if there is a pressure difference between the fluids, heat exchange can be performed with high efficiency without deforming the heat transfer plate. It also solves the conventional problems of wasted material and large weight.

[Brief explanation of the drawing]

1 to 7 show one embodiment of the present invention, in which FIG. 1 is a front sectional view, FIGS. 2 and 3 are views shown in FIG. Figures a and b are perspective views of the first heat exchanger plate, Figures a and b are perspective views of the second heat exchanger plate, Figures a and b are views showing the joints of the first heat exchanger plate, Fig. 7 is an exploded perspective view showing the manufacturing method, Figs. 8 to 12 show other embodiments, Fig. 8 is a plan sectional view, and Fig. 9 is shown in Fig. 8.
The arrow view, Fig. 10 and Fig. 11 are respectively
A perspective view of a heat exchanger plate, a perspective view of a second heat exchanger plate, a first
2 is a view shown in FIG. 8 - FIG. 16 shows a conventional example, FIG. 13 is an overall perspective view,
FIG. 14 is a cross-sectional view, FIG. 15 is a view taken along the arrow shown in FIG. 14, and FIG. 16 is a plan sectional view showing another conventional example. 1...First heat exchanger plate, 2A...First spiral groove, 2B
...Second spiral groove, 3A...First recess, 3B...Second recess, 4A...First through hole, 4B...Second through hole, 5...Outer periphery, 6...Second heat transfer Board, 7A...
3rd spiral groove, 7B... 4th spiral groove, 8A... 3rd
recess, 8B... fourth recess, 9A... third through hole,
9B... Fourth through hole, 10... Outer periphery, 11...
Heat exchanger, 12A, 12B... end plate, 15... first fluid passage, 16A... first fluid inflow passage, 16
B...First fluid outflow passage, 17...Second fluid passage, 18A...Second fluid inflow passage, 18B...Second fluid outflow passage, 31, 32...Inlet, 33,3
4... Aperture section.

Claims (1)

[Claims] 1. A spiral groove formed by the uneven shape of the heat exchanger plate itself is provided on the upper and lower surfaces of the left and right portions of the first heat exchanger plate, and a through hole is provided at the center of each of the spiral grooves on the left and right portions. At the same time, the respective ends of the spiral grooves on the left and right portions of the upper and lower surfaces are communicated with each other, and a second heat exchanger plate is provided which is plane symmetrical to the first heat exchanger plate, and these first and second heat exchanger plates are alternately arranged. are stacked on top of each other, and the bottom outer surfaces of the spiral grooves facing each other are joined to form a cross-sectional honeycomb structure, and the opposed spiral grooves of the first and second heat exchanger plates form a first fluid passage.
A second fluid passage is formed by the opposed spiral grooves of the heat exchanger plate and another second heat exchanger plate, and the centers of the left and right spiral grooves of each first fluid passage are communicated with each other through the through hole to allow the inflow of the first fluid. A laminated plate type heat exchanger characterized in that a passage and an outflow passage are formed, and the left and right spiral groove centers of each second fluid passage are penetrated by the through hole to form an inflow passage and an outflow passage for the second fluid. exchanger. 2. The laminated plate heat exchanger according to claim 1, further comprising a constriction portion for adjusting the inflow amount of each fluid near the inlet of each fluid passage.