Shell-and-tube heat exchanger and cooling or heating system comprising a shell-and-tube heat exchanger

Abstract

The present invention relates to a shell-and-tube heat exchanger (2), comprising a housing (10) which extends along a longitudinal axis (X) and comprising a housing wall (16) enclosing an interior space (15), a tube bundle (20) with a plurality of tubes (25) which are guided through the interior space (15) along the longitudinal axis (X), and at least one deflector plate (30), wherein at least one sealing element (40) is arranged which seals a gap (19) between the at least one deflector plate (30) and the housing wall (16), wherein the at least one sealing element (40) comprises a first portion (41) and a second portion (42) angled towards the first portion (41), and wherein the second portion (42) comprises at least two tabs (45) which project from the first portion (41). In addition, the present invention relates to a cooling or heating system (1).

Description

The present invention relates to a shell-and-tube heat exchanger with the features of claim 1 and a cooling or heating system with the features of claim 16.

Shell-and-tube heat exchangers in various designs are known from the prior art and are used to transfer heat between a first medium and a second medium, or vice versa. Shell-and-tube heat exchangers typically comprise a housing that extends along a longitudinal axis and having a housing wall enclosing an interior space. In addition, the shell-and-tube heat exchanger comprises a tube bundle with a plurality of tubes that run along the longitudinal axis through the interior space. The interior space of the housing is flowed through by the first medium and the tubes of the tube bundle by the second medium, wherein heat can be transported from the first medium to the second medium, or vice versa. Deflector plates are typically arranged in the interior space of the housing, through which the first medium in the interior space is deflected along a flow path, thereby improving the flow in the interior space and the heat transfer. In addition, the tubes of the tube bundle can be held in position in the interior space by the at least one deflector plate.

Shell-and-tube heat exchangers are used in cooling or heating systems, for example, such as condensers, evaporators, oil coolers, or desuperheaters. The first medium can be a coolant that is cooled or liquefied by means of compression in a shell-and-tube heat exchanger that emits heat, or that is vaporized again after the expansion process by absorbing heat through heating. In many applications, it is desirable for a phase transition from vapor to liquid or from liquid to vapor to take place in the shell-and-tube heat exchanger, as the phase transition allows additional thermal energy in the form of latent heat to be transported from the coolant.

Shell-and-tube heat exchangers have proven effective in the past. There is a gap between the deflector plates and the inner wall of the housing due to production-related out-of-roundness and/or tolerances. On the one hand, this gap enables the shell-and-tube heat exchanger to be assembled. However, this gap has a negative effect on the flow deflection, as bypass flows occur through the gap. These bypass flows reduce the flow velocity, and the bypass flow only comes into reduced contact with the tubes of the tube bundle, which is why the transfer performance is significantly reduced.

To address this known problem, conventional sealing materials such as EPDM or silicone have been used in the past. However, shell-and-tube heat exchangers with these sealing materials can only be used to a limited extent, as these sealing materials are not compatible with a wide range of possible media and cannot be used in all desired temperature and/or pressure ranges.

This is where the present invention comes in.

The present invention is dedicated to the object of proposing an improved shell-and-tube heat exchanger which expediently eliminates the disadvantages known from the prior art. The shell-and-tube heat exchanger to be proposed should be cost-effective to manufacture and highly efficient.

These objects are achieved by a shell-and-tube heat exchanger having the features of claim 1, and by a cooling or heating system having the features of claim 16.

Further advantageous embodiments of the present invention are given in the dependent claims.

The shell-and-tube heat exchanger according to the invention with the features of claim 1 comprises a housing which extends along a longitudinal axis and having a housing wall enclosing an interior space. The housing preferably has a circular cross-section. The housing can also have a polygonal or oval cross-section, or a mixture of both. Furthermore, the shell-and-tube heat exchanger according to the invention comprises a tube bundle with a plurality of tubes and at least one deflector plate arranged in the interior space. The tubes are arranged along the longitudinal axis in the interior space.

A first medium can be passed through the interior space of the housing, wherein preferably the first medium can flow into the interior space through a first inlet opening in the housing and can leave the interior space through a first outlet opening. A second medium can be passed through the tube bundle or through each respective tube of the tube bundle, wherein heat can be transferred in the interior space between the two media.

The first medium can be deflected by the at least one deflector plate in the interior space in such a manner that the first medium flows around the tubes of the tube bundle in the best possible manner, thereby improving heat transfer.

In addition, at least one sealing element is arranged to seal a gap between the at least one deflector plate and the housing wall. The at least one sealing element further comprises a first portion and a second portion angled away from the first portion, wherein the second portion comprises at least two tabs extending from the first portion.

The present invention is based on the idea of sealing the gap between the at least one deflector plate and the housing wall by means of a preferably elastic sealing element. The at least one sealing element is preferably in contact with both the housing wall and the at least one deflector plate, wherein the freely protruding tabs prevent the second portion from swelling, in particular at the curved housing wall. Furthermore, the angled tabs can compensate for production-related tolerances and/or interact in a sealing manner with the at least one deflector plate. It is particularly advantageous if the first portion or the second portion rests at least in portions on or preferably directly on the housing wall of the housing, and the respective other portion is arranged on or preferably directly on the at least one deflector plate. It is particularly advantageous if the at least two tabs of the second portion rest on the housing wall of the outer housing, at least in some areas, and the first portion rests against the deflector plate in a sealing manner.

In a further embodiment, the second portion can lie prestressed against the housing wall or against the at least one deflector plate. In particular, it is advantageous if the second portion rests prestressed against the housing wall, whereby, on the one hand, the at least two tabs position the at least one deflector plate centered in the interior space during assembly of the shell-and-tube heat exchanger according to the invention and, on the other hand, the at least two tabs enable compensation for manufacturing tolerances, in particular out-of-roundness.

The at least two tabs can be angled by bending, wherein the bending angle is preferably less than 90°, whereby the aforementioned prestressing is achieved. The preferred bending angle is 60° to 85°. Accordingly, the opening angle is preferably 95°-120°.

A further embodiment of the present invention provides that the at least one sealing element is made from a sheet metal, in particular from a thin sheet metal. The thin sheet metal preferably has a thickness of less than 1 mm. Thin sheet metal is typically a rolled metal product, which is why sheet metal, particularly stainless steel sheet, is highly compatible with the media and can be used over a wide pressure and temperature range. In particular, it is preferable if the sheet metal is made of a precious metal.

According to a preferred further embodiment of the present invention, a slot is arranged between the at least two tabs, wherein the slot is preferably V-shaped. The slot therefore tapers from the free ends of the tabs. Preferably, the slot is designed in such a manner that the angled at least two tabs do not rest on top of one another, but—preferably directly—next to one another and even further preferably butt to butt. This can reduce any potential gap flows through the slot or between the housing and the tab.

A further development of the present invention provides that the at least two tabs are each bent along a bending edge. Preferably, the respective bending edge is arranged along a straight line or a curve. Further preferably, neighboring bending edges meet at a point of intersection. Preferably, two adjacent bending edges formed as straight lines intersect at an intersection angle, wherein the intersection angle corresponds to a pitch angle of one of the at least two tabs.

In a folded state of the at least one sealing element, the bending edges of the at least two tabs rest on a first radius R1, and the free ends of the at least two tabs rest on a second radius R2. A width b of the respective slot at the free ends of the at least two tabs can be determined via a relationship b=2*π*(R2−R1)/N, wherein N describes the number of tabs over a complete circumference of the housing. Preferably, an arc length of the at least one tab is less than 50 mm, whereby corrugations are avoided in the angled state of the at least two tabs.

Preferably, the slots end on or immediately adjacent to the bending edge, in particular at the point of intersection of the bending edges of the at least two tabs. It should be noted at this point that, by definition, immediately adjacent to the bending edge also describes a distance from the bending edge, wherein the distance is preferably smaller than the bending radius at which the at least two tabs are bent.

Furthermore, a further embodiment of the invention may comprise at least one passage on the at least one sealing element. The outlet opens the gap between the at least one deflector plate and the housing wall, and a leakage flow can occur through the at least one outlet. Preferably, the at least one passage is arranged between two tabs, wherein the at least one outlet extends radially inwards from the free end of the tabs beyond the first radius—i.e. preferably further than the bending radius. On the one hand, the passage can serve as an assembly aid in order to predetermine the circumferential position of the at least one sealing element relative to the at least one deflector plate and/or the housing. On the other hand, the at least one passage can serve as a flow path for gaseous or liquid media in specific applications, e.g. oil coolers.

It can be advantageous if two outlets are provided on diametrically opposite sides, which allows, for example, an alternating arrangement of a plurality of deflector plates along the longitudinal axis with identical deflector plates.

In addition, the at least one passage is preferably arranged in a bottom-side area of the housing. It may always be necessary to drain the first medium from the interior space for maintenance purposes. The at least one passage makes it possible for the first medium to be drained almost completely from the interior space, as the first medium can flow through the at least one outlet in the bottom-side area of the housing.

A further embodiment of the present invention provides that the housing and/or the at least one deflector plate are circular or oval, at least in portions. In particular, it is preferred if the housing is circular and has an inner radius, wherein the inner radius is larger than an outer radius of the deflector plate. This creates the aforementioned gap, which allows for easy assembly, among other things.

Furthermore, it is preferred if the outer radius of the deflector plate or the inner radius of the housing corresponds to the first radius of the sealing element. In particular, it is preferred if the inner radius of the housing corresponds approximately to the outer radius of the deflector plate or to the first radius of the sealing element plus a gap dimension of the gap. Accordingly, it is preferable if the inner radius is smaller than the inner radius of the housing by the gap dimension. It is also preferred if the second radius is larger than the inner radius of the housing, wherein the difference between the second radius and the first radius of the housing indicates the length of the tabs.

A further development of the present invention provides that the housing comprises a first inlet opening and a first outlet opening along the longitudinal axis. Furthermore, it is preferred if the at least one deflector plate is arranged along the longitudinal axis between the first inlet opening and the first outlet opening. The at least one deflector plate can either be oriented transversely to the longitudinal axis or inclined at an angle, for example to generate a flow along a helical flow path in the interior space.

The at least one deflector plate can be formed in one piece or from a plurality of deflector plate segments. For example, the at least one deflector plate can be in one or more pieces, and be spiral-, rotor- or propeller-shaped.

In addition, it has proven to be advantageous if the at least one sealing element is arranged along the longitudinal axis, on the side of the at least one deflector plate facing the first inlet opening. This arrangement means that the at least one sealing element is pressed against the housing wall of the housing by the flow, which improves the sealing effect of the tabs.

Furthermore, it is advantageous if the second portion with the at least one sealing element protrudes from the first portion on the side facing the first inlet opening. Due to this arrangement, the at least two tabs of the at least one sealing element are pressed against the housing wall of the housing by the flow, which improves the sealing effect of the tabs.

According to a further embodiment of the present invention, at least one fastening means is provided by which the at least one sealing element is fastened to the at least one deflector plate. The at least one fastening means can comprise a screw or a rivet, for example, and enables the sealing element to be attached to the deflector plate easily and cost-effectively.

Furthermore, it is advantageous if the at least one fastening means comprises a counter-holder, wherein the at least one sealing element is held clamped between the counter-holder and the at least one deflector plate, for example by means of the fastening means, in particular by means of screws or rivets.

In addition, a further embodiment of the present invention provides that the at least one deflector plate comprises at least one recess and at least one perforation for at least one tube of the tube bundle. Preferably, the at least one tube of the tube bundle is held supported in the perforation, while the first medium can flow through the recess in the deflector plate. The at least one recess can, for example, form a secondary outlet through which the first medium can flow in the longitudinal axis through the at least one deflector plate. The at least one recess can also be annular or circular, whereby the axial passage is formed either radially around the at least one deflector plate or within the at least one deflector plate.

It has also proven to be advantageous if a plurality of deflector plates are arranged at a distance from one another between the inlet opening and the outlet opening. In particular, it is preferred if the plurality of deflector plates is arranged in a row along the longitudinal axis, wherein even further preferably the plurality of deflector plates is arranged equidistantly from one another. It can also be advantageous if the distance between the plurality of deflector plates increases or decreases along the longitudinal axis in order to take into account any changes in density of the medium in the interior space between the first inlet opening and the second inlet opening.

In addition, it has proven to be advantageous if the plurality of deflector plates with the at least one recess is arranged alternately along the longitudinal axis in order to provide a wavy or meandering flow path from the first inlet opening to the first outlet opening. For example, the deflector plates, which have a secondary recess, can be arranged in such a manner that the secondary recesses are arranged alternately on opposite sides in the interior space, thereby defining the undulating or meandering flow path. It is advantageous if the alternately arranged recesses do not overlap when viewed along the longitudinal axis.

A further aspect of the present invention relates to a cooling or heating system with at least one shell-and-tube heat exchanger according to the invention.

In the following, with reference to the attached drawings, a cooling system and two embodiment examples of a shell-and-tube heat exchanger and their further embodiments are described in detail. In the figures:

FIG. 1 is a schematic and highly simplified cooling system with three shell-and-tube heat exchangers, a compressor, and an expansion element,

FIG. 2 is a schematic, highly simplified and partially sectioned view of a first embodiment example of the shell-and-tube heat exchanger according to FIG. 1, wherein the shell-and-tube heat exchanger has a plurality of deflector plates in an interior space formed in a housing, wherein sealing elements with angled tabs are provided which seal a gap between the deflector plate and the housing,

FIG. 3 is a partially sectioned detailed view of the sealing element and the housing as shown in FIG. 2,

FIG. 4 is a sectional view of the sealing element and the housing as shown in FIG. 3,

FIG. 5 is a partially sectioned and perspective detailed view of the sealing element and the housing as shown in FIGS. 2-4,

FIG. 6a is a top view of the sealing element as shown in FIGS. 2-5, wherein the tabs have not yet been bent,

FIG. 6b is a detailed view of the sealing element shown in FIG. 6a,

FIG. 7 is a further embodiment of the sealing element shown in FIG. 6a,

FIG. 8 is a schematic, highly simplified, partially sectioned and perspective view of a second embodiment example of the shell-and-tube heat exchanger according to FIG. 1, and

FIG. 9 is a partially sectioned view and a side view of the shell-and-tube heat exchanger shown in FIG. 8.

Identical or functionally identical components are designated by the same reference symbols. In addition, not all identical or functionally identical components are given a reference number in the figures.

FIG. 1 shows a cooling system 1, comprising a compressor 3, three shell-and-tube heat exchangers 2, and an expansion element 4, wherein the three shell-and-tube heat exchangers 2 are identified by the reference symbols 2a, 2b and 2c for better understanding.

A first medium A coming from the compressor 3 is directed to a first shell-and-tube heat exchanger 2a and liquefied by transferring heat to a second medium B. Subsequently, the first medium A is then passed via an expansion element 4 to the second shell-and-tube heat exchanger 2b, wherein the heat from a third medium C to be cooled can be absorbed by the first medium A in the second shell-and-tube heat exchanger 2b, whereby the first medium A of the cooling circuit evaporates again and is sucked in by the compressor 3 for recompression.

The first medium A coming from the compressor 3 can be passed through an oil separator 5 upstream of the first shell-and-tube heat exchanger 2a, through which oil entrained in the first medium A can be separated. The separated oil can be cooled by means of a third shell-and-tube heat exchanger 2c before it is fed back to compressor 3.

The shell-and-tube heat exchanger 2 can be used both in the cooling system shown in FIG. 1 and in a heating system—also known as a heat pump. The shell-and-tube heat exchanger 2 can also be used to desuperheat oil or other liquid or gaseous media, wherein the respective first medium A can also undergo a phase change from liquid to vapor and vice versa in the shell-and-tube heat exchanger 2.

FIG. 2 shows a schematic, highly simplified, and partially sectioned view of a first exemplary embodiment of the shell-and-tube heat exchanger 2.

The shell-and-tube heat exchanger 2 comprises a housing 10, referred to as a whole, which extends along a longitudinal axis X and comprises a housing wall 16 enclosing an interior space 15. The housing 10 can preferably be cylindrical in shape, wherein the longitudinal axis X can be an axis of symmetry of the housing 10. The housing 10 extends along the longitudinal axis X between a first end area 13 and a second end area 14.

The housing 10 comprises a first inlet opening 11 and a first outlet opening 12. The first inlet opening 11 is arranged in the first end area 13, and the first outlet opening 12 is arranged along the longitudinal axis X on the opposite side in the second end area 14.

A first medium A can be fed into the interior space 15 through the first inlet opening 11, and the first medium A can be discharged from the interior space 15 through the first outlet opening 12.

Furthermore, the shell-and-tube heat exchanger 2 comprises a tube bundle 20 with a plurality of tubes 25, which are guided along the longitudinal axis X and parallel thereto through the interior space 15.

For reasons of simplification, only two tubes 25 are shown in FIG. 2. The tubes 25 of the tube bundle 20 are guided parallel to the longitudinal axis X through the interior space 15 and extend between the first end area 13 and the second end area 14.

The respective tube 25 or the tube bundle 20 is connected to a second inlet opening 21, and a second outlet opening 22 and can be flowed through by a second medium B.

The respective tube 25 can have a smooth surface or be ribbed in order to increase the heat transfer surface.

The respective tube 25 is configured to separate the first medium A in the interior space 15 from the second medium B in the respective tube 25 and to transfer a heat flow through the wall of the tube 25 between the two media A, B.

The respective tube 25 opens in the first end area 13 and in the second end area 14 in a distribution or collection cover 18, which, depending on the flow direction of the second medium B, distributes the second medium B from the second inlet opening 21 to the tubes 25 of the tube bundle 20 or collects the second medium B from the tube bundle 20 and directs it to the second outlet opening 22.

The housing 10 or the interior space 15 is each closed in the first end area 13 and in the second end area 14 by a tube base 17, whereby the second medium B in the distribution or collection cover 18 is separated from the first medium A in the interior space 15. The tubes 25 can penetrate the tube bases 17 and are connected to them by welding, brazing, flanging, or gluing, for example.

A plurality of deflector plates 30 is arranged in a row along the longitudinal axis X in the interior space 15. The deflector plates 30 can be connected to one another by one or more rods, e.g., threaded rods.

The deflector plates 30 are arranged along the longitudinal axis X between the first inlet opening 11 and the first outlet opening 12, wherein the deflector plates 30 are preferably arranged equidistant from one another. In the exemplary embodiment shown, the deflector plates 30 are arranged transversely to the longitudinal axis X.

The deflector plates 30 can be connected by means of rods 36, with which the deflector plates 30 can be held in position in the interior space 15. The respective rod 36 can be a threaded rod, for example.

The respective deflector plate 30 may be made of a sheet metal and comprises a plurality of perforations 32, wherein a tube 25 is inserted through the respective perforation 32, as indicated in FIG. 2. The respective perforation 32 is adapted to the shape and size of the respective tube 25.

It is already noted at this point that all deflector plates 30 are generally designated by the reference symbol 30. FIG. 2 shows that two different deflector plates 30 are arranged alternately along the longitudinal axis X, wherein these are referred to below as first deflector plates 30a and the others as second deflector plates 30b. The differences between the first deflector plates 30a and the second deflector plates 30b will be discussed in detail below.

The first deflector plate 30a should rest as tightly as possible against the housing wall 16 in order to avoid bypass flows, but due to the manufacturing process, a gap 19 is formed between the housing wall 16 and the first deflector plate 30, through which a bypass flow can form. The gap 19, see FIG. 4, preferably has an average gap dimension S in the range of 1 mm≤S≤10 mm, preferably S≤5 mm.

As will be explained below—in particular with reference to FIGS. 3-5-a sealing element 40 is arranged on the first deflector plates, which seals the gap 19 between the respective first deflector plate 30a and the housing wall 16. The respective sealing element 40 can be ring-shaped or arc-shaped and can be made from a sheet metal or stainless steel sheet. In particular, it is preferred if the sealing element 40 is made from a thin sheet metal, wherein the sheet thickness is 1 mm or less.

The respective sealing element 40 can preferably be arranged along the longitudinal axis X on the side of the first deflector plate 30a facing the first inlet opening 11.

The sealing element 40 can be arranged on the deflector plate 30 by fastening means 50. As indicated in FIG. 5, the at least one fastening means 50 can comprise a screw or a rivet 52 and/or a counter-holder 54—see FIG. 4. The counter-holder 54 clamps the sealing element 40 between the deflector plates 30, pressing it flat against the deflector plate 30. The counter-holder 54 can, for example, be connected to the deflector plate 30 by means of screws or rivets.

The respective sealing element 40 comprises a first portion 41 and a second portion 42, wherein the second portion 42 has a plurality of tabs 45 projecting from the first portion 41, in particular at an angle when installed.

The first portion 41 interacts in a sealing way with the first deflector plate 30a, and the second portion formed by the angled tabs 45 interacts in a sealing way with the wall 16 of the housing 10.

As can be seen in particular from FIGS. 3 and 4, the tabs 45, in particular the free ends of the tabs 45, rest against the wall 16, wherein preferably the tabs 45 press pre-tensioned against the wall 16.

The pre-tension can be used in particular to compensate for production-related tolerances, such as out-of-roundness. As a further advantage of pre-tension, it can be mentioned that the first deflector plate 30a is positioned centrally in the interior space 15, in particular during assembly. This facilitates the assembly of the shell-and-tube heat exchanger 2.

A slot 46 is arranged between each of the tabs 45, wherein the slot 46 is preferably V-shaped, see FIG. 6. The slot 46 tapers starting from the free ends of the tabs 45.

The respective slot 46 can be designed in such a manner that the tabs 45, in particular the free ends of the tabs 45, do not rest on top of one another, but ideally rest side by side in the angled or installed state of the sealing element in the housing 10.

The sealing element 40 can either be produced by bending and/or the sealing element is bent with the sealing element 40 arranged on the deflector plate when the deflector plate is inserted. Before bending, the sealing element 40 according to the exemplary embodiment shown in FIG. 6a is flat and in particular ring-shaped.

A further embodiment of the sealing element 40 in FIG. 7 shows that the sealing element 40 can also be arc-shaped. The use of arc-shaped sealing elements 40 can be expedient if, for example, only an area around the circumference of a deflector plate 30 is to be sealed. Several sealing elements 40 can also be arranged around the circumference. This can, for example, lead to cost advantages and/or enable simpler production and/or easier handling during assembly.

To bend the tabs 45 in the second portion 42, the exemplary strips shown in FIG. 6a, 6b or 7 are bent, wherein the bending of the respective tab 45 can take place along a bending edge 43 with a bending radius R.

With reference to FIG. 6 or 7, it can be seen that the sealing element 40 has a first radius R1 and a second radius R2.

In a folded state of the sealing element 40 according to FIG. 6 or 7, the bending edges 43 of the at least tabs 45 intersect at the first radius R1, and the free ends of the tabs lie at a second radius R2.

FIGS. 6 and 7 show that the respective bending edge 43 is ideally arranged along a straight line or a curve. Preferably, neighboring bending edges intersect at a point of intersection. Preferably, two adjacent bending edges 43 formed as straight lines intersect at an angle, wherein the angle corresponds to a pitch angle of one of the at least two tabs 45.

As already mentioned, the respective slot 46 may be V-shaped and, as shown in FIGS. 6 and 7, taper towards the first radius R1 starting from the free ends of the tabs 45.

A width b of the respective slot 46—see FIG. 6b—at the free ends of the at least two tabs 45 can be determined via a relationship

$b=\frac{2\pi \left(R2-R1\right)}{N},$

wherein N describes the number of tabs 45 over a complete circumference of the housing 10. Preferably, an arc length of the at least one tab 45 is less than 50 mm, whereby corrugations are avoided in the angled state of the tab 45.

Furthermore, it can be seen in particular from FIG. 6a that the sealing element 40 can have two outlets 49 through which the first medium A can flow.

The respective passage 49 opens the gap 19 between the at least one deflector plate 30 and the housing wall 16 and a leakage flow can occur through the at least one passage 49.

The respective passage 49 is arranged between two tabs 45, wherein the passage 49 extends radially inwards from the free end of the tabs 45 beyond the first radius R1—i.e. preferably beyond the bending radius. On the one hand, the passage 49 can serve as an assembly aid in order to predetermine the circumferential position of the sealing element relative to the at least one deflector plate 30 and/or the housing 10. On the other hand, the at least one passage 49 can serve as a flow path for gaseous or liquid media in special applications, e.g. oil coolers.

The passage 49 is preferably arranged in a bottom-side area of the housing 10, wherein a maintenance outlet can more preferably be arranged in the bottom-side area of the housing 10.

For example, it may be necessary to drain the first medium A from the interior space 15 for maintenance purposes. The passage 49 prevents the deflector plates 30 from causing the first medium in the interior space 15 to back up. Through the passage, the first medium A can preferably be completely drained from the interior space 15 through the maintenance outlet.

The sealing element 40 can have a passage opening 48 on an inner side, wherein the passage opening 48 can be shaped such that the tube bundle 20 or parts thereof can be passed through.

Furthermore, the sealing element 40 may have openings 56 for the fastening means 50.

Referring again to the first exemplary embodiment of the shell-and-tube heat exchanger 2—shown in FIG. 2—it can be seen that the deflector plates 30 each have a recess 34 in addition to the perforations for the tubes 25 of the tube bundle 20.

The first deflector plates 30a in FIG. 2a have a concentric recess 34a and the second deflector plates 30b have a ring-shaped recess 34a for forming an annular channel between the second deflector plate 30b and the housing wall 16.

The first deflector plates 30a and the second deflector plates 30b are arranged alternately in a row along the longitudinal axis. As a result, the first medium A is guided from the first inlet opening 11 to the first outlet opening 12 along an undulating or meandering flow path, as indicated by the arrow lines in FIG. 2.

In the exemplary embodiment shown in FIG. 2, the gap 19 between the housing wall 16 and the first deflector plate 30a is sealed around the circumference by at least one sealing element 40. The first medium flows through the center of the first recess 34a in the first deflector plate 30a.

The second deflector plates 30b do not have a sealing element, and the first medium A can flow through the annular channel between the housing wall and the second deflector plate 30b. The undulating flow path improves the flow in the interior space 15 and the heat transfer.

FIGS. 8 and 9 show a second exemplary embodiment of the shell-and-tube heat exchanger 2, wherein only the differences to the previously described exemplary embodiment are discussed. It should be noted that, for reasons of simplification, some features, such as the perforations 32 for the tubes 25 or the tube bundle 20, are not shown in FIGS. 8 and 9.

As can be seen from FIGS. 8 and 9, a plurality of deflector plates 30 is arranged along the longitudinal axis X, which are designated with the reference symbol 30c for better understanding. The respective deflector plate 30c has a secant-type recess 34c, through which the first medium A can flow along the longitudinal axis X. The deflector plates 30c can be arranged alternately along the longitudinal axis, as shown in FIGS. 8 and 9. In other words, the deflector plates 30c are each arranged alternately, rotated by 180° about the longitudinal axis X. As a result, the first medium A is guided from the first inlet opening 11 to the first outlet opening 12 along an undulating or meandering flow path, as indicated by the arrow lines in FIG. 9.

A sealing element 40 is arranged on the respective deflector plate 30c, wherein the sealing element 40 is arc-shaped and seals the gap 19 between the housing wall 16 and the deflector plate 30c. No sealing element 40 is required in the area where the recess 34 c is formed.

LIST OF REFERENCE SYMBOLS

• • 1 cooling system
  • 2 shell-and-tube heat exchanger
  • 3 compressor
  • 4 expansion element
  • 5 oil separator
  • 10 housing
  • 11 first inlet opening
  • 12 first outlet opening
  • 13 first end area
  • 14 second end area
  • 15 interior space
  • 16 housing wall
  • 17 tube base
  • 18 collection cover
  • 19 gap
  • 20 tube bundle
  • 21 second inlet opening
  • 22 second outlet opening
  • 25 tube
  • 30 deflector plate
  • 32 perforation
  • 34 recess
  • 36 rod
  • 40 sealing element
  • 41 first portion
  • 42 second portion
  • 43 bending edge
  • 45 tab
  • 46 slot
  • 48 passage opening
  • 49 passage
  • 50 fastening means
  • 52 rivet
  • 54 counter-holder
  • 56 opening
  • A first medium
  • B second medium
  • R bending radius
  • R1 first radius
  • R2 second radius
  • RA outer radius of 30
  • RI inner radius of 10
  • X longitudinal axis

Claims

1. A shell-and-tube heat exchanger (2), comprising

a housing (10) extending along a longitudinal axis (X) and comprising a housing wall (16) enclosing an interior space (15),

a tube bundle (20) with a plurality of tubes (25), which are guided along the longitudinal axis (X) through the interior space (15), and

at least one deflector plate (30),

characterized in that

at least one sealing element (40) is arranged, which seals a gap (19) between the at least one deflector plate (30) and the housing wall (16),

wherein the at least one sealing element (40) comprises a first portion (41) and a second portion (42) angled towards the first portion (41), and

wherein the second portion (42) comprises at least two tabs (45) projecting from the first portion (41).

2. The shell-and-tube heat exchanger (1) according to claim 1,

characterized in that

the first portion (41) is arranged on the at least one deflector plate (30) and the second portion (42) bears against the housing wall (16), or the first portion (41) rests against the housing wall (16) and the second portion (42) is arranged on the at least one deflector plate (30).

3. Shell-and-tube heat exchanger (2) according to claim 1,

characterized in that

the second portion (42) rests pre-tension against the housing wall (16) or against the at least one deflector plate (30).

4. The shell-and-tube heat exchanger (2) according to claim 1,

characterized in that

the at least one sealing element (40) is made from a thin sheet metal, preferably with a sheet thickness of less than 1 mm.

5. The shell-and-tube heat exchanger (2) according to claim 1,

characterized in that

a slot (46) is arranged between the at least two tabs (45), which slot is preferably V-shaped.

6. The shell-and-tube heat exchanger (2) according to claim 1,

characterized in that

the at least two tabs (45) are each angled along a bending edge (43) by bending.

7. The shell-and-tube heat exchanger (2) according to claim 1,

characterized in that

the at least one sealing element (40) has a passage (49) which opens the gap (19).

8. The shell-and-tube heat exchanger (2) according to claim 1,

characterized in that

the at least one sealing element (40) is fastened to the at least one deflector plate (30) by at least one fastening means (50).

9. The shell-and-tube heat exchanger (2) according to claim 1,

characterized in that

the at least one fastening means (50) comprises a counter-holder (54), wherein the at least one sealing element (40) is held clamped between the counter-holder (54) and the at least one deflector plate (30).

10. The shell-and-tube heat exchanger (2) according to claim 1,

characterized in that

the at least one deflector plate (30) has at least one recess (34) and at least one perforation (32) for at least one tube (25) of the tube bundle (20).

11. The shell-and-tube heat exchanger (2) according to claim 1,

characterized in that

the interior space (15) of the housing (10) has a first inlet opening (11) and a first outlet opening (12) along the longitudinal axis (X), and in that the at least one deflector plate (30) is arranged along the longitudinal axis (X) between the first inlet opening (11) and the first outlet opening (12).

12. The shell-and-tube heat exchanger (2) according to claim 1,

characterized in that

the at least one sealing element (40) is arranged on the side of the at least one deflector plate (30) facing the first inlet opening (11).

13. The shell-and-tube heat exchanger (2) according to claim 1,

characterized in that

the second portion (42) of the at least one sealing element (40) protrudes from the first portion (41) on the side facing the first inlet opening (11).

14. The shell-and-tube heat exchanger (2) according to claim 1,

characterized in that

a plurality of deflector plates (30) are arranged between the first inlet opening (11) and the first outlet opening (12).

15. The shell-and-tube heat exchanger (2) according to claim 1,

characterized in that

the plurality of deflector plates (30) with the at least one recess (34) are arranged alternately along the longitudinal axis (X) in order to provide an undulating or meandering flow path from the first inlet opening (11) to the first outlet opening (12).

16. A cooling or heating system (1) comprising a shell-and-tube heat exchanger (2) according to claim 1.