JPS61500626A - Plate of plate type heat exchanger - Google Patents

Abstract

A heat exchanger plate has a primary heat exchange part (1b), two secondary heat exchange parts (2b, 3b) placed on each side of this one and four holes or ports (4b, 5b, 6b, 7b). Two of the ports are located at one of the secondary heat exchange parts in the same distance from but on each side of a centre line (M) of the plate. The two other ports are in a corresponding way located at the other secondary heat exchange part. The plate has in all heat exchange parts (1b, 2b, 3b) ridges and valleys embossed into it, which are so placed that when two plates are put against each other - one of them turned 180<o> relative to the other one - ridges in one plate intersectingly rest against ridges in the other plate. At least the ridges and the valleys in the secondary heat exchange parts (2b, 3b) are so embossed that they have a volume of essentially the same size on respective sides of the plate. In a plate of this kind each of the two secondary heat exchange parts is provided with ridges and valleys forming an angle with the centre line (M) of the plate. This angle (or these angles) differs from the angle (the angles) which the ridges and the valleys in the primary heat exchange part (1b) of the plate form with the centre line (M). Furthermore, the ridges and valleys of the plate form such angles with the centre line (M) that in a plate interspace they bring about less flow resistance in the areas of the secondary heat exchange parts (2b, 3b) of the plates - on both sides of the centre line (M) - than in the area of the primary heat exchange part (M) of the plates.

Description

[Detailed description of the invention] Plate of plate heat exchanger 〔Technical field〕 The present invention includes a first heat exchange section located in the center, two second heat exchange sections located on each side of this. 4 holes, two in each second heat exchange section, and two in each second heat exchange section. two of these dates in the second heat exchange section ( Heat exchanger plates equidistant from the centerline of the nibrate and in opposite directions. Regarding rates.

[Background technology]

This type of heat exchanger plate is made of relatively thin plates and is housed in one frame. Large pressures between two relatively thick end plates that are housed together A system consisting essentially of a large number of such heat exchanger plates placed underneath It is a part of a rate heat exchanger. The two heat exchange media are structurally Flowing through the interspace of rates, to and there The heat exchange medium is placed between the bowls located on the heat exchanger plate in line with each other. is guided through a channel formed by the

In the interspace, a flow path isolated from the outside is formed for the heat exchange medium. Gaskets or gaskets to seal between the heat exchangers There are other means in place.

Within each of the interspaces, the heat exchange medium flowing through it is connected to the heat exchanger plate. flow diagonally or essentially parallel to both sides of the plate. Ru. The present invention is concerned with the former case and therefore a heat exchanger according to the invention The boat surrounds all three heat exchange sections and two boats located diagonally. A gasket or the like is provided by known methods.

[Disclosure of the invention]

In the heat exchanger plate according to the invention, the first heat exchange section also has a second heat exchange section. Also in the heat exchange part, the peaks and valleys created by uneven molding of the plate are alternately formed using a well-known method. The backs and valleys of these mountains are formed by two plates (one of which is connected to the other). When they are butted against each other (at a position rotated 180° relative to ) so that the back of the mountain on the other plate crosses over the back of the mountain on the other plate. It is location. The spines and valleys in at least the second heat exchange section are formed on each side of the plate. The concave and convex portions are shaped to have substantially equal volumes.

A heat exchanger plate of the above type is already known from Swedish Patent No. 34λ691. be. In this case, the backs of the ridges and valleys in the second heat exchange section on one side are The back and valley of the peak in the first heat exchange section are the same as <(60° and 120°), and the backs and valleys of the peaks and valleys in the other second heat exchange section are as shown above. It extends parallel to the center line.

The purpose of the special design of the peaks and valleys in the other second heat exchange section is as explained in this patent. According to Akira, this shape allows a ball to be placed in the interspace formed by two plates of the same shape. of these two plates, the heat exchange medium entering through the In other words, the flow path cross-sectional area of the heat exchange medium is better in the region of the first heat exchange part. It essentially consists in reducing the flow resistance in a small area.

In the discussion of this patent, a commonly designed heat exchanger plate The flow resistance in the nearest above region is unreasonably large, and it has no effect on the heat exchange itself. The statement that it cannot be used effectively is correct. that of the first heat exchange section The same should be true on the opposite side, in the area closest to the exit boat.

The aim of the invention is to improve the efficiency of heat exchanger plates in the areas mentioned above by way of introduction. In other words, two plates of the same shape (one of which is at an angle of 180° to the other) flow of the heat exchange medium in the interspace formed (in a rotated position) dynamic resistance in the interspace formed by the already known heat exchanger plates. However, heat exchange itself can be used effectively. The objective is to provide a design for the container plate.

This purpose, according to the invention, is achieved by providing at least a On one side of the center line of the road, there is a mountain back and a valley that form an angle with the center line. The backs and valleys of the above-mentioned peaks and valleys in each of the second heat exchange sections are relative to the center line of the plate. The angle (singular or plural) is different from that of the peak and valley in the first heat exchange section. ), and the angle that the spine and valley of the plate make with the center line of the plate is , two plates (one of which is rotated 1800 times relative to the other) are rotated relative to each other. When butted, the plates intersect and touch each other in the interspace. The flow resistance of unit length in the desired flow direction caused by the back of the mountain is Now, the width in the first heat exchange section (including both sides of the center line) should also be made smaller. being admired. This can be achieved by

The design of the two second heat exchange parts of the plate according to the invention is disclosed in Swedish Patent No. 342 , 691, due to the difference in design of the corresponding part of the plate. Therefore, in the interspace of the plates, the heat exchange medium flowing therein is so that the flow on the plate is particularly favorable, i.e. the second heat exchanger of the plate The exchange section is connected to the port through which the heat exchange medium enters the plate interspace. Heat exchange not only in the vicinity but also on the opposite side of the plate centerline It has been found that it can be used effectively for Second heat exchange section Such a favorable flow would not be obtained if the rather, it is located in the area of the plate interspace closest to the actual inlet port. The reduction in flow resistance achieved is counterbalanced in the region opposite that of the plate centerline. It has been found that this is because it cannot produce the corresponding effect.

Hereinafter, the present invention will be explained in more detail with reference to the drawings.

[Brief explanation of the drawing]

Figure 1 shows the so-called diagonal flow of two heat exchange media on each side of the heat exchanger plate. FIG. 2 is a diagram illustrating the heat exchanger plate in the first embodiment of the present invention. Figure 3 is a cross-sectional view taken along arrow mm in Figure 2, Figures 4 and 5 are butted against each other. The difference in the design of the mountain spines in the two plates that were Figure 6 is a diagram showing how the interspaces of the FIG. 3 shows two heat exchanger plates in a second embodiment of the invention.

[Best mode for carrying out the invention]

In FIG. 1, a first heat exchange section l, two second heat exchange sections 2 and 3, and four Heat exchanger plates with plate through holes (i.e. so-called bows) 4, 5, 6.7 The route is shown schematically. The two solid lines 8 and 9 indicate that the first heat exchange medium is at port 4. Entering from and located diagonally? − How to flow one side of the plate until it reaches the bottom. The two dashed lines 10 and 11 indicate whether the second heat exchange medium is It shows how the other side of the plate can be made to flow from 1 to port 5.

The flow of two heat exchange media as shown in FIG. 1 is commonly referred to as diagonal flow.

In Fig. 2, two heat exchanger plates 12 and 13 are formed with concave and convex shapes in the same shape. It is shown. One plate is 18 in its own plane relative to the other plate. It is in a position rotated by 0°. Each play) 12 and 13 are respectively the first heat exchange section 1 a, two second heat exchange parts 2a and 38. and 4 ports 4a, 5a+6a+ It has 73. On the side of the plate 12 that is visible in Figure 2, there are three heat exchange parts. 1a, 2a, and 3a are all 4-) 4; surrounded by one gasket 14 in a groove. A separate screenshot 5a and 7a, respectively. plate In 13, all of the heat exchange parts 1a, 2a, and 3a are connected together with 5a and 7a. is surrounded in a similar manner by a gasket 15.

In the first heat exchange section 1a, the plates 12 and 13 are both formed by uneven molding. It has a waveform of the back and valley, ξ turn. This nozo turn is the center of the plate Between adjacent plates that are symmetrical about the line λ■ and arranged as shown in Figure 2. In interspace, the back of the mountain on one plate is the back of the mountain on the other plate. It forms an angle with respect to the center line M so that it crosses over the top.

Also in the second heat exchange parts 2a and 3a, the plates 12 and 13 have mountain backs and valleys. However, these are one plate in the interspace of the plates in Figure 2. The back of the mountain in part 2a of the plate crosses over the back of the mountain in part 3a of the other plate. It forms an angle with respect to the center line M, as shown in FIG.

The backs and valleys of the first heat exchange section 1aK of plates 12 and 13 are on one side of the center line M. makes an angle of 60' with it and on the other side of the center line N1 an angle of 120° with it. There is.

In the second heat exchange section 2a, the backs and valleys of the ridges form an angle of 45° with the center line M, and the other In the second heat exchange section 3a, the corresponding angle is 135°. .

As can be seen in Figure 1, on each side of the second heat exchange section of the plate there is a first heat exchange medium. The body flows substantially crosswise to the direction of flow of the second heat exchange medium. both heat exchange To obtain similar flow conditions for the media, use plates for diagonal flow. The above shows that the peak backs and valleys in the second heat exchange section have substantially the same volume on both sides of the plate. It is necessary that the device be designed to have a product.

This is shown in Figure 3, which is a cross-sectional view taken along the line mm in Figure 2. There is. In Figure 3, the 2 Two faces 16 and 17 are shown. Surface 16 on one side of the plate and 2 tangent to it The volume enclosed between the spines of two mountains is The volume enclosed between the plane 17 on the side and the spine of the two mountains adjacent to it and substantially etc. 1. ＜Must.

In Figure 4, plates 12 and 13 are arranged as in Figure 2 to create an interspace. When this is possible, the back of the mountain formed in the second heat exchange section 2a of plate) 12 becomes gray. It shows how it intersects with the back of the mountain formed in the 20th heat exchange section 3a of the seat 13. has been done.

In FIG. 5, the back of the mountain formed in the first heat exchange section 1a of plates 12 and 13 is A similar thing has been shown.

In FIG. 4, the various flow directions of the heat exchange medium are indicated by arrows 18, 19, 20. In addition, FIG. 5 shows arrows 21, 22, and 23 corresponding to these.

The flow resistance of the heat exchange medium in the interspace of the plates Depending on how the heat exchange medium on the back of the formed mountain stretches (direction) with respect to the flow direction, It is generally known that it changes as follows.

The spines of two adjacent plates are substantially perpendicular (90') as shown in Figure 4. ) and cross each other, the flow resistance in the flow direction 18 naturally increases. The drag will be the same as in the flow direction 20. By the way, in this case, in the flow direction 19 The flow resistance is substantially equal to that in the flow direction 18.20.

A case where the mountain spines of two adjacent plates intersect each other at an angle as seen in Figure 5. In this case, the flow resistance varies greatly depending on the flow direction. Flow direction The flow resistance at 21 is several times that in the flow direction 23. Flow in flow direction 22 The resistance will be of a certain magnitude between them. Interspersing plates as shown in Figure 5 The flow resistance in the flow direction 21 in the pace is therefore The flow resistance in any direction in the interspace of the It becomes.

As described above, the direction of the back of the ridges formed on the plate is set to the desired flow direction of the heat exchange medium. The interspacing of the plates can be The flow of those media in different parts of the pace.

The dynamic resistance can be made as desired.

For heat exchange plates 12 and 13 in Figure 2, the above results in the following results: It is occurring. Namely.

Through port 7a of plate 13 (or through port 5a of plate 12) Some heat exchange media flowing into the interspace between the plates can formed by the play) 120 portion 2a of the center space and the portion 3a of the plate 13. The whole area experiences relatively small flow resistance.

As a result of this, the heat exchange medium reaching the first heat exchange part 13 of the plate The various branched flows are such that this portion 1a is substantially different from that in the second heat exchange sections 2a, 3a. are substantially the same size by creating a large flow resistance. child As a result of this, the second heat exchange section as well as the tenth heat exchange section of the plate The heat exchange medium can be used effectively as a plate interspace. The entire pressure drop experienced while passing through the To be used.

In FIG. 6, two heat exchanger plates 24 and 25 are shown which are contoured in the same shape. has been done. These plates are the plates 12 and 13 in FIG. The difference lies in the second heat exchange section of the plate. ! rate 24 The heat exchanger parts of this different design of 25 and 25 are shown in Fig. It is represented. The ports on the plate are jb and 5b.

Each is shown.

As is clear from the figure, the backs and valleys of the peaks and valleys in the heat exchange parts 2b and 3b of each picture 2 are It is formed symmetrically with respect to the center line M of the sheet. On one side of the center line M, there is a mountain The back of both part 2b and part 3b forms an angle of about 45° with the center line M, On the other hand, on the opposite side of the center line λ, the back of the mountain in both parts 2b and 3b is medium. It forms an angle of 135° with the core wire.

Although the design of the second heat exchange section in plates 24 and 25 is different, Therefore, the flow resistance in the interspace formed by these plates is shown in Figure 2. compared to the flow resistance in the interspace formed by plates 12 and 13 of There is no substantial difference. Players may play on either side of center line M or on the opposite side. The backs of the mountains in the second heat exchange section of On the other side, the back of the mountain on one plate is 45 with respect to the center line M of the plate. °, the back of the mountain on the other plate forms an angle of 1356°.

The advantages of the design of the second heat exchange section as shown in FIG. The flow condition is such that the plate 25 is rotated 1806 times around its center line AI. , i.e. rotated so that its back side faces the back side of the plate 24. Even in this case, it is possible to obtain between plates 24 and 25.

This means that the clamping between plates 24 and 25 can be used instead of a rubber gas foot. This is subject to planning if it must be done by brazing or welding. .

The divisions of the concavo-convex molding of the second heat exchange section are shown in Figures 2 and 6. In both embodiments, it is substantially equal to that of the concavo-convex molding of the first heat exchange section.

The two different embodiments of the second heat exchange section seen in FIGS. 2 and 6 are disclosed in the patent claims. This is not to say that we have only listed what is possible within the scope of the present invention.

For example, in each of the second heat exchange parts, the back of the mountain on one side of the center line λf is The back of the mountain on the other side of the center line M makes a 90° angle with it. It is fine if it extends parallel to the eggplant.

Fig, 2 Fig, 4 international search report 1111m7M-m-k PCT/SE85100413

Claims (6)

[Claims] (1) A first heat exchange section (1) located in the center, two heat exchange sections located on each side of this. 2 heat exchange sections (2, 3), and 2 heat exchange sections (2, 3) in each second heat exchange section. A total of four holes or ports located equidistant from the center line (M) of the seat and in opposite directions. (4 to 7), and both the first heat exchange section (1) and the second heat exchange section (2, 3) , two plates are rotated by 180°, one of them relative to the other. When the plates are butted against each other in the The backs and troughs of the ridges are formed on the plate so that they cross over the backs of the ridges of the plate. At least the backs and valleys in the second heat exchange section (2, 3) are are contoured so that they have substantially equal volume on each side of the plate; In the heat exchanger plate, all of the heat exchange parts (1 to 3) were located diagonally Two plays butted against each other with two ports (4,6 or 5,7) surrounded by a gasket or similar placed to provide a seal between the the flow path for the heat exchange medium between the plates is isolated from the outside world. The two second heat exchange parts (2a, 3a or 2b, 13b) each, at least on one side of said centerline (M) of the plate, with said centerline (M); The back of the mountain and the valley which form the angle of the size are provided, and the second heat exchange part (2a, 3a Alternatively, the spines and valleys of the above-mentioned mountains in each of 2b and 3b) are located at the center line of the plate ( M) is different from the case of the back of the mountain and the valley in the first heat exchange section (1a, 1b). The plate's peaks and valleys form two plates. in a position where one of the parts is rotated 180° relative to the other. When butted against each other, they cross and touch each other in the interspace of the plates. The back of the mountain where the flow resistance per unit length in the desired flow direction is the second heat exchange section (2a, 3a or 2b, 3b) in the regions on both sides of the center line (M). of the plate so that it is smaller than in the area of the replacement part (1a or 1b). A heat exchanger plate characterized in that it forms an angle with the center line (M). (2) The backs of mountains and valleys in two plates are When abutted against each other in a position rotated 180° with respect to the The back sides of the mountains that are in contact with each other in the two heat exchange parts (2a, 3a or 2b, 3b) What is the case where the mutual intersection angle is the back of the mountain in the first heat exchange section (1a or 1b)? Heat exchanger plates according to claim 1, which are differentially elongated. (3) The backs and valleys of the ridges over the first heat exchange section (1a or 1b) are inside the plate. While forming an angle of 60° (120°) with the core wire (M), the second heat exchange section (2a, 3 The spines and valleys in a or 2b, 3b) are relative to the center line of the plate (M). A heat exchanger plate according to claim 2 forming an angle of 45° (135°). rate. (4) The backs and valleys of the ridges are aligned with the center line (M) of the plate of the second heat exchange section (2b, 3b). It extends in one direction in the two halves on one side and has a second heat exchange section (2b , 3b) extends in a different direction from the previous one, A heat exchanger plate according to any one of claims 1 to 3. (5) The backs and valleys of each of the second heat exchange parts (2b, 3b) are inside the plate. According to claim 4, the concave and convex molding is formed symmetrically with respect to the core wire (M). heat exchanger plate. (6) The indentation of the concavo-convex molding pattern in the second heat exchange section is similar to that in the first heat exchange section. Claims 1 to 3 are substantially the same as the indentations of the uneven molding pattern. Heat exchanger plate according to any one of clauses 5 to 6.