DE102014216216A1 - Circular heat exchanger with molded dryer and refrigeration circuit with this heat exchanger - Google Patents

Abstract

The present invention comprises a circular heat exchanger having the following features: first and second piping having vanes extending radially from the first and second piping while a refrigerant is passable through the first and second piping and the first piping is first and second piping the second pipe forming a second planar spiral, wherein the first and the second pipe of the first and the second planar spiral in a radial inner region or a radially outer region of the spirals in fluid communication with each other and are flowed through by a common refrigerant.

Description

1. Field of the invention

The present invention relates to a circular heat exchanger and a refrigeration cycle in combination with this circular heat exchanger.

2. Background of the invention

In the prior art, refrigeration circuits are well known, which are used in air conditioning, refrigerators and freezers. Such a refrigeration cycle usually consists of an evaporator in which a refrigerant is evaporated. The required energy is withdrawn from the medium, which is to be washed around the evaporator and cooled. Thereafter, the vaporized refrigerant is supplied to a compressor, where during the compression of the refrigerant, the pressure and the temperature of the refrigerant are increased. In a subsequently installed condenser, the refrigerant is condensed, whereby condensation heat is dissipated to the environment of the condenser. The liquid refrigerant is then supplied to an expansion device, such as an expansion valve, to reduce the pressure in the refrigerant. Within this known refrigeration cycle, heat exchangers are used as evaporator and condenser, respectively, in order to realize an efficient energy exchange between the refrigerant within the heat exchanger and the environment.

Such a refrigeration cycle is in DE 199 05 354 C2 described. The two heat exchangers, which are used as condenser and evaporator, consist of a meander-shaped curved round tube. Such a planar structure is suitable, for example, as a back wall condenser, which is installed at the rear of a freezer.

Out US 1,709,176 is a funnel-shaped arrangement of several circularly curved pipes known to form a heat exchanger. These annular pipes have different diameters and are arranged one behind the other to form a funnel. The individual annular pipes are fastened in two opposite holders, which simultaneously realize the inlet and outlet of the refrigerant.

The complex structure thus requires that each individual annular pipe is individually supplied with refrigerant. In addition, the annular pipes are arranged in the radial edge region of the flow of the medium to be cooled, so that the surface of the heat exchanger is not optimally in contact with the flowing medium.

US 1,635,869 describes a cooling or heating device, which will be described below using the example of the cooling device. This cooling device comprises a centrally arranged fan. Before and behind the fan in the flow direction, a spiral and funnel-shaped coiled coolant line is arranged in each case. Due to the funnel-shaped spirals initially the cooling unit takes up a lot of space. The funnel-shaped spirals create strong turbulence in the cooling air flow, resulting in performance losses.

Another construction of a heat exchanger is in US 7,367,380 B2 disclosed. Here, a fan is positioned within a sleeve-shaped assembly consisting of a wound wing tube. The air flow to be cooled is guided by the fan through the sleeve-like arrangement, wherein the existing of wing tubes radial inside of the sleeve-like arrangement realizes the heat exchange between the refrigerant and the environment. Another heat exchange between the refrigerant and the flowing environment is ensured by a flat spiral of a pipe, this planar spiral closes the sleeve-like arrangement on one side as far as possible. In order to improve the heat exchange between the refrigerant and the flowing environment, a plurality of sleeve-like arrangements of different diameter are arranged nested. The disadvantage of this design is that different pipes are used for the heat exchange between the refrigerant and the environment. This increases the design and manufacturing costs. In addition, the lines of the refrigerant are in the radial edge region of the medium flow to be cooled. This does not allow the full surface area of the refrigerant line to be used for the required heat exchange.

Out US 2,974,500 Air conditioning is known. A fan of this air conditioner sucks air through two pipe spirals arranged transversely to the flow direction of the air. These pipe coils are arranged side by side, centrally connected to each other and serve to direct a coolant. A disadvantage has been found that the coolant lines of the two spirals provide only a limited surface for the heat exchange available. Furthermore, there is one spiral in the lee of the other spiral during the Ansorgvorgangs the air through the fan. In this way, the effectiveness of the heat exchange between the environment and the heat exchanger is reduced.

It is therefore the object of the present invention to provide an alternative to the prior art heat exchanger, which is characterized by an improved heat exchange between the Characterizes refrigerant and the flowing environment to be cooled.

3. Summary of the invention

The above object is achieved by a circular heat exchanger according to the independent protection claim 1, by an air conditioning, refrigeration or freezer with a refrigeration cycle according to the independent claim 15 and by a manufacturing method according to the independent claim 16 or 17.

The circular heat exchanger according to the invention has the following features: first and second piping with vanes extending radially from the first and second pipelines, while a refrigerant is passable through the first and second pipelines and the first piping is first and the second piping form a second planar spiral, wherein the first and the second pipe of the first and the second planar spiral in a radial inner region or a radially outer region of the spirals in fluid communication with each other and are flowed through by a common refrigerant.

The heat exchanger according to the invention preferably consists of at least two flat spirals, which are wound from respective pipes. Therefore, this heat exchanger is particularly suitable for installation in pipelines or for placement adjacent to a fan. In this case, the existing of the pipes flat spirals have the advantage that they provide a large area in a space-saving arrangement available, which can be used for heat exchange between the flowing medium and the refrigerant. Depending on the heat exchange performance of the heat exchanger two or more flat spirals can be arranged side by side, in order to optimally adapt the surface of the pipeline of the refrigerant required for cooling purposes. To increase the available heat exchange surface area of the first and second pipe, these have radially extending from the first and second pipe wings. These wings increase the surface area of the pipeline through which additional heat exchange of the environment with the refrigerant in the pipeline can take place. The first and the second pipeline preferably have two vanes arranged radially opposite one another or a plurality of vanes extending radially from the pipeline. Further, the first and second pipelines of the first and second planar scrolls are fluidly connected to each other in a radially inner portion or a radially outer portion of the scrolls. Due to the merger of the two adjacently arranged spirals, the liquid circulation of the refrigerant is simplified. Because in this way flows through the same refrigerant both spirals, so not two different cooling circuits must be provided.

According to a further preferred embodiment of the heat exchanger according to the invention, a fan is arranged between the first and the second planar spiral and the first and the second planar spiral are arranged adjacent to the fan.

This design allows the rotating fan to draw airflow on one side through the adjacent planar spiral while blowing air flow through the adjacent spiral on its opposite side. Due to the combination of the spaced apart planar spirals and the arrangement of the fan between these spirals is avoided that is a flat spiral in the lee of the other flat spiral. Furthermore, the operation of the fan is optimally utilized, which generates a sucking air flow and a blown air stream at its two opposite sides in the flow direction.

According to a further preferred embodiment of the present invention, the first and second pipes of the first and second spiral are connected to each other via a U-shaped pipe section in the radially outer region of the first and second spiral. By means of this radially outer coolant connection between the first and the second spiral to achieve a space-saving arrangement of the first and second spiral adjacent to the fan. Furthermore, the preferably U-shaped connection between the two coolant lines of the first and second spiral makes it possible for the first and second spiral to be produced simultaneously in a common winding process. In this way, complex connection methods are avoided in the radial outer region of the two planar spirals.

According to the present invention, it is further preferred that the fan and the first and second planar spirals are held in a housing in concentric arrangement with each other. The concentric arrangement of the scrolls and the fan with respect to each other to ensure that, if possible, all sections of the first and second pipes of the first and second spiral are optimally flowed through the air flow of the fan.

According to a first preferred embodiment of the present invention are the first and the second plane spiral arranged parallel to each other. Further preferably, the first and / or the second pipe radially extending therefrom and oppositely arranged wings on. These wing tubes increase the surface area of the pipeline that is available for heat exchange. According to a further preferred embodiment, the wings of the first and / or the second pipeline extend perpendicularly or at an angle γ of 0 ° ≦ γ <90 ° to the radial plane of the first and / or second spiral in which the wings are arranged. By means of a different arrangement of the wings to the radial plane of the respective spiral, it is also possible to adapt to the flow around the surface of the medium to be cooled of the respective spiral. A compromise is to be found between a large area of the wing tube available for the heat exchange and a minimum flow resistance of the planar spiral for the flowing medium to be cooled.

According to a further preferred embodiment of the present invention, the wings within the first and / or second spiral are aligned parallel to one another or not aligned parallel to one another relative to at least two radial regions of the spiral. It is also preferred that the vanes of the first and second spirals are not arranged parallel to one another or parallel to one another or relative to at least two radial regions of the spiral.

Since at least two planar spirals are arranged parallel to one another, in a further preferred embodiment of the present invention the first and second pipelines of the first and second volutes run parallel to one another or radially offset from one another. In this way, the first and second piping of the first and second scrolls according to the first alternative are arranged exactly one behind the other in the flow direction. According to the second alternative, the second pipe of the second spiral is arranged at least partially or completely in the region of the gap between adjacent turns of the first pipe in the first spiral. These designs also allow for heat transfer customization.

According to an alternative of the invention, the first and second pipes are formed by a continuous pipe from which the first and second spirals are wound.

Preferably, the first and / or the second pipe made of steel, copper or aluminum. According to a further preferred embodiment, the heat exchanger at a downstream and radially inner end of the first or second pipe to a drying section, which is an integral part of the pipeline or which is integrally formed on the end of the pipe. According to a first alternative, the integral drying section is a cylindrical tube section of the original tube, from which the wing tube of the heat exchanger is formed. Preferably, this cylindrical pipe section was not formed into a wing tube, in particular rolled, but left in its original form. Therefore, the integral drying section consists of a round tube section which integrally merges into the wing tube without being deformed for receiving a dryer element. According to a second alternative, the drying section consists of a widened longitudinal section of the first or second pipeline. This construction is suitable when the circular heat exchanger is wound from a source tube with a round cross-section. Since no wings are formed from this cylindrical portion of the original tube, its cross section is larger than in the tubular section for wing tubes (see above). In the drying section, a dryer element and a sieve are preferably arranged. This dryer element removes disturbing moisture from the passing refrigerant, whereby the screen prevents the dryer element from entering the pipeline. At the downstream end of the drying section, an expansion device for the pressurized refrigerant in the form of a capillary is provided. The capillary has been directly or integrally formed from the tube of the drying section or connected to it by suitable methods, for example. By soldering.

The present invention also includes an air conditioning, refrigeration or freezing appliance with a refrigeration cycle, comprising a compressor, an expansion device and at least one heat exchanger according to one of the embodiments described above, which are preferably used as evaporator and / or condenser.

Further, the present invention discloses a manufacturing method for a circular heat exchanger, comprising the steps of providing first and second ducts with vanes extending radially from the duct as two connected and opposite legs of a U-shaped duct, simultaneously winding a first duct a planar spiral from the first conduit and a second planar spiral from the second conduit, wherein each one adjacent to a connection between the first and the second conduit end of the first and the second conduit forms a radially inner beginning of the first and the second spiral.

Two adjacent planar spirals of a first and a second On the one hand, coolant line increase the area available for heat exchange and moreover are easy to produce in a combined production process. During the winding of the first spiral, it is readily possible to simultaneously wind the second plane spiral out of the preferably endless pipeline. For this purpose, it is only necessary that from the endless pipe by means of a U-shaped bend two parallel legs are formed, which are subsequently wound with the same or different diameter to two adjacent planar spirals.

An alternative method of manufacturing a circular heat exchanger according to the invention comprises the steps of providing first and second ducts having vanes extending radially from the duct as two interconnected and opposite legs of a U-shaped duct, simultaneously winding a first planar spiral the first conduit and a second planar scroll from the second conduit, each having a free end of the first and second conduits forming a radial inner beginning of the first and second scrolls, securing the first and second scrolls in a housing and disposing a fan between the first and the second spiral.

According to the further manufacturing method according to the invention, the two adjacent planar spirals are also each wound from a wing tube. These two flat spirals are connected together in their radial outer area via a pipe. Thus, the first and the second planar spiral can be flowed through by a common coolant, wherein the coolant flows into the one spiral in a radial inner region and flows out of the spiral in a radial inner region of the other spiral. Since the first and the second spiral are wound simultaneously from a U-shaped bent pipe, here also results in a time-saving winding process for the heat exchanger forming planar spirals. In order to ensure the air flow through the two flat spirals, a fan is placed between the two flat spirals. The flat spirals and the fan are held in a fixed arrangement of a housing.

In this connection, it is preferable to wind the first and the second pipeline of the first and the second spiral parallel to one another or radially offset relative to one another. According to another embodiment of the present invention already mentioned above, the first and second pipelines form a continuous tube. It is further preferred in the manufacture of the circular heat exchanger, the first and second spiral to be arranged parallel to each other.

According to a further preferred embodiment of the manufacturing method according to the invention, the wing tube is wound into a first and a second plane spiral in such a way that the wings, preferably two wings extending radially from a central pipeline and arranged opposite one another, are at least partially parallel within a plane spiral and / or or are aligned at an angle to each other and / or that the wings of adjacent planar spirals are at least partially aligned parallel and / or angled to each other.

According to a further preferred embodiment, the wings of the first and / or the second pipeline are aligned perpendicular or at an angle γ of 0 ° ≤ γ ≤ 90 ° to the radial plane of the first and / or second spiral. The preferred orientation of the wings with respect to the radial plane of the first and / or second spiral allows optimal adaptation of the sash position to the flow conditions generated by the fan.

Further preferably, the manufacturing method comprises the following further steps: providing a cylindrical pipe section, preferably a source pipe, in a cylindrical shape as a drying section at one end of the pipe section from which at least the first spiral is formed, and introducing a drying material into the cylindrical pipe section, so that the drying material is held there, preferably by means of a sieve. It is also preferred to form the wing tube in the adjoining the cylindrical pipe section second pipe section of the original pipeline, preferably to rollers. Subsequently, the spirals are wound out of the wing tube. According to a further embodiment of the production method, an integral capillary is formed at the downstream end of the drying section, or a capillary is connected to the end of the cylindrical tube section facing away from the wing tube.

4. Brief description of the accompanying drawings

The preferred embodiments of the present invention will be explained in detail with reference to the accompanying drawings. Show it:

1 a schematic representation of a refrigeration cycle of the prior art,

2 A first preferred embodiment of a circular heat exchanger according to the invention in a perspective view,

3 a side view of the circular heat exchanger 2 .

4 a side view of the circular heat exchanger according to 2 with a preferred drying section,

5 a sectional view taken along the line BB 4 .

6 a further side view of the circular heat exchanger according to 2 .

7 a sectional view taken along the line AA 6 .

8th an enlarged view of the circled area 7 .

9 a sectional view of a preferred embodiment of the drying section,

10 an enlarged detail and sectional view of a portion of the drying section 9 .

11 - 15 various perspective views of a preferred embodiment of another circular heat exchanger and

16 a flow chart of a preferred manufacturing method for the circular heat exchanger according to 2 ,

5. Detailed Description of the Preferred Embodiments

1 describes a known refrigeration cycle consisting of a first heat exchanger WT1 as an evaporator, a compressor V, a second heat exchanger WT2 as a condenser and an expansion device E. The evaporator WT1 is arranged upstream of the compressor V in the flow direction. A refrigerant evaporates in the evaporator WT1 with the heat of vaporization, which is extracted from the environment. In the compressor V, the gaseous refrigerant is compressed. In the second heat exchanger WT2, the refrigerant condenses and thereby releases heat to the environment or to another medium. The high pressure liquid refrigerant is then expanded in the expansion device so that liquid refrigerant is again present under normal pressure conditions.

According to the invention, the first and / or second heat exchanger WT1, WT2 is preferably a circular heat exchanger 1 ; 1' used, as in the 2 to 8th according to a first preferred embodiment and in the 11 - 15 is shown in different views according to a second preferred embodiment. The circular heat exchanger 1 ; 1' has a plurality of planar spirals 10 . 20 , preferably two or an integer multiple of two (not shown). These flat spirals 10 . 20 are each from a pipeline 30 wound (step SIII). Similar structural features of the two embodiments of the heat exchanger 1 ; 1' are denoted by the same reference numerals. In addition, the technical descriptions of the heat exchanger apply 1 in the same way for the heat exchanger 1' because both heat exchangers 1 ; 1' are constructed essentially with the same constructive elements.

Preferably, the pipeline exists 30 of a thermally conductive material, such as metal, in particular of steel, copper, aluminum, alloys thereof or other metal alloys.

For the preparation of the two in the heat exchanger 1 ; 1' adjacent planar spirals 10 . 20 it is initially preferred to use two pipelines 30a . 30b to provide the same or different length (step SI). The two pipes 30a . 30b serve at the same time in a manufacturing step, the two flat spirals 10 . 20 to wind (step SIII). For this it is preferable to use the two pipes 30a . 30b as a one-piece pipe 30a . 30b with a connecting U-shaped bend 32 provide (SIIa), so that the two pipes 30a . 30b form the opposite legs of the U-shaped bent pipes. The U-shaped bend 32 the pipeline 30a . 30b One-piece has the advantage of providing a fluid connection between the two pipelines 30a . 30b without providing a liquid-tight connection and a corresponding construction between the pipes 30a . 30b required are.

It is also preferable to use the two pipes 30a . 30b provided separately from each other and each liquid-tight at one end to each other, preferably via a U-shaped bent connecting piece to connect with each other (SIIb).

The pipelines 30a . 30b consist according to one embodiment of a source tube of circular cross-section, from which then, preferably by rolling, wings have been formed. According to another embodiment, the pipeline is based 30 on a source tube also circular in cross-section (here referred to as round tube) but smaller diameter than the original tube for the wing tube. From the wing tube or the circular tube is then preferably the circular heat exchanger wound.

Below are the interconnected piping 30a . 30b simultaneously to two flat spirals 10 . 20 wound (SIII), which in its middle area over the connection 32 connected to each other. It is further preferred that the flat spirals 10 . 20 individually to wrap and then liquid-tight in their middle area to connect together.

For the embodiment of the heat exchanger 1' according to the 11 - 15 be the two interconnected piping 30a . 30b also simultaneously two flat spirals 10 ' . 20 ' wound. At the end of the winding process are the spirals 10 ' . 20 ' connected together in a radial Außenbereicht. The liquid inlet E and the liquid outlet A of the two interconnected pipes 30a . 30b are in a central area of the flat spirals 10 ' . 20 ' arranged. Thus, the flat spirals 10 ' . 20 ' of the heat exchanger 1' of 11 - 15 wrapped in the opposite direction compared to the plane spirals 10 . 20 of the heat exchanger 1 out 2 , Preferably, the flat spirals 10 . 20 and 10 ' . 20 ' wrapped so that the piping 30 in the adjacent flat spirals 10 . 20 and 10 ' . 20 ' parallel to each other. In this case, adjacent pipes point in the same spiral 10 ; 20 (please refer 8th ) and 10 '; 20 ' (please refer 14 ) the same distance x to each other. It is also preferred to have the distance x within a planar spiral 10 ; 20 ; 10 ' . 20 ' to change. According to an alternative (not shown), the distance x ₁ , x _{2 increases} radially outward within the same spiral 10 ; 20 ; 10 ' . 20 ' to, in the middle region of the plane spiral 10 ; 20 ; 10 ' . 20 ' to provide a larger surface area for heat exchange (see 5 as schematic representation). Similarly, it is preferable that the distance between adjacent pipelines 30a . 30b within the same spiral 10 ; 20 ; 10 ' . 20 ' decreases radially outward. According to another preferred embodiment of the present invention, the distance between adjacent pipelines 30 in adjacent flat spirals 10 . 20 ; 10 ' . 20 ' designed differently. According to one embodiment, the distance between adjacent pipelines 30a . 30b in the plane spiral 10 ; 10 ' smaller compared to the distance x ₃ in the plane spiral 20 ; 20 ' , As a result, it is preferably achieved that the plane spiral first flown in the flow direction S 10 ; 10 ' provides a larger surface area for heat exchange than the flat spiral impinged thereafter 20 ; 20 ' , In the same way, it is of course preferred that the first impinged flat spiral 10 with a larger distance x between adjacent pipelines 30 to equip as the then flowed flat spiral 20 , In this way, among other things, the flow resistance of the flat spirals 10 . 20 adaptable to the conditions in the refrigeration cycle.

It is additionally or alternatively preferred further, a different flow of the flat spirals 10 ' . 20 ' to achieve that by having a fan 70 between the flat spirals 10 ' . 20 ' is arranged. This is according to a preferred embodiment in the 11 - 15 shown. Related to the heat exchanger 1 of the 2 For example, a fan, fan, or blower (not shown) is preferably first on only one side of the composite 10 and second spiral 20 positioned.

Preferably, the fan 70 and the flat spirals 10 ' . 20 ' arranged concentrically and parallel to each other. This is one of the spirals 10 ' . 20 ' on a suction side or vacuum side of the fan 70 , from which air through the fan 70 is sucked. The other of the two spirals 10 ' . 20 ' is located on the pressure side or overpressure side of the fan 70 to the air through the fan 70 is blown. Because the two spirals 10 ' . 20 ' can not form a slipstream for each other, the surface of the respective pipeline 30a . 30b be better used for heat exchange with the environment.

It is further preferred that the flat spirals 10 ' . 20 ' adjacent to the fan 70 to arrange. An adjacent arrangement denotes a compact and as gap-free arrangement with the planar spiral 10 ' , the fan 70 and the plane spiral 20 ' , The distance between the fan 70 and the spiral 10 ' . 20 ' should just be sufficient to a rotation of the fan 70 as well as a practicable installation of the fan 70 and the spirals 10 ' . 20 ' in a housing or in a frame structure 80 to ensure.

How to use the 11 - 15 can recognize, is the frame structure 80 preferably from an outer main frame 82 , which has a central opening 84 having. The opening 84 allows an air flow in the flow direction S, through which the pipes 30a . 30b the plane spirals 10 ' . 20 ' to be flowed around. For this purpose are over a holding structure 86 the flat spirals 10 ' . 20 ' and the fan 70 inside or adjacent to the opening 84 on the frame structure 80 attached.

The holding structure 86 is at least one point with the main frame 82 connected. In addition, there is the holding structure 86 preferably from a central ring 87 , from which in the radial direction at least one holding arm 88 , preferably two or four retaining arms 88 , extends. The at least one holding arm 88 is preferably comb-like built up. For this purpose, a plurality of webs extends 90 parallel to the flow direction S or perpendicular to the radial plane of the spirals 10 ' . 20 ' , These bridges 90 are at a distance of the windings of the spiral 10 ' . 20 ' arranged and preferably engage in the spaces between adjacent windings of the spirals 10 ' . 20 ' one. After fixing the spirals 10 ' . 20 ' at the support structure 86 The windings are preferably based on the webs 90 off so the jetties 90 a regular arrangement of the windings of the spirals 10 ' . 20 ' guarantee. Preferably, the support structure 86 attached via a snap connection, locking connection, bayonet connection or the like.

The ventilator 70 will be inside the opening 84 of the main frame 82 at the support structure 86 or attached to a fan attachment (not shown). Preferably, first, the fan 70 in the frame structure 80 arranged and fastened. Below are the flat spirals 10 ' . 20 ' adjacent to the fan 70 positioned and with the support structure 86 attached.

To a compact arrangement consisting of frame structure 80 , Fan 70 and spirals 10 ' . 20 ' to achieve a small thickness in the flow direction S and an effective width in the radial direction of the flat spirals 10 ' . 20 ' have, is the main frame 82 circumferentially broken at one point. In the free space created by the breakthrough, according to one embodiment of the present invention, the radially outer U-shaped connection 32 arranged. It is also preferable to the main frame 32 form closed circumferentially. In this case, preferably the U-shaped connection 32 radially from the flat spirals 10 ' . 20 ' spaced such that the U-shaped connection 32 outside the holding frame 32 and the spirals 10 ' . 20 ' inside the opening 84 are arranged (not shown). It is also preferable that the flat spirals 10 ' . 20 ' with U-shaped connection 32 inside the opening 84 to arrange (not shown).

Preferably, the frame structure exists 80 made of plastic, metal or other suitable material, which has sufficient stability for holding the flat spirals 10 ' . 20 ' and the fan 70 provides.

According to another preferred embodiment of the present invention, adjacent planar spirals become 10 . 20 or with an intermediate fan 70 mutually adjacent planar spirals 10 ' . 20 ' wound so that they have different sized outer diameter. This can be due to different lengths of piping 30a . 30b the plane spirals 10 . 20 ; 10 ' . 20 ' or by a variation of the distances x of the adjacent pipelines 30 in the adjacent flat spirals 10 . 20 ; 10 ' . 20 ' be achieved. According to a further preferred embodiment of the present invention, the pipelines 30a . 30b adjacent planar spirals 10 . 20 ; 10 ' . 20 ' so wrapped that the pipeline 30 the second spiral disposed in the flow direction S flat spiral 20 ; 20 ' opposite a pipe space of the planar spiral 10 ; 10 ' runs. In this way, the surface of the circular heat exchanger according to the invention which flows through a medium becomes 1 ; 1' approximately doubled and is adaptable to existing flow conditions.

Because the flat spirals 10 . 20 are connected to each other centrally, is radially on the outside of each flat spiral 10 . 20 an open pipe end 34 intended. Therefore, through the respective pipeline 30a . 30b the first level spiral 10 and the second plane spiral 20 a refrigerant can be conducted. Once the first level spiral 10 and the second level spiral 20 are in fluid communication with each other, are the piping 30a . 30b the two flat spirals 10 . 20 flowed through by a common refrigerant.

According to the preferred embodiment of 11 - 15 are the flat spirals 10 ' . 20 ' connected on a radial outside (see above). Because of this fluid connection using the U-shaped connection 32 between the flat spirals 10 ' and 20 ' is through the pipes 30a . 30b the two flat spirals 10 ' . 20 ' a common refrigerant conductive.

According to the invention, the first plane spiral is preferred 10 ; 10 ' and the second level spiral 20 ; 20 ' arranged parallel to each other. To heat exchange between in the pipeline 30a . 30b flowing refrigerant and the pipeline 30a . 30b To support flowing medium is preferably as a pipeline 30a . 30b a wing tube 36 provided (see 8th ). The wing tube 36 includes at least two wings 38 extending radially from the pipeline. Preferably, only two oppositely arranged wings 38 intended. The wings 38 preferably run straight or curved in the radial direction. It is also preferable to have a plurality of radially extending vanes on the pipeline 30a . 30b to arrange.

According to a preferred embodiment of the present invention, the wing tubes 36 wrapped so that the wings 38 perpendicular to the plane of the plane spiral 10 ; 20 ; 10 ' . 20 ' are aligned (S IV). In the same way it is preferred the wings 38 the pipeline 30 the first plane spiral 10 ; 10 ' and / or the pipeline 30b the second plane spiral 20 ; 20 ' vertically or in one Angle γ of 0 ° ≤ γ <90 ° to the radial plane of the first 10 ; 10 ' and / or second plane spiral 20 ; 20 ' align (SV). In this context, it is also preferred that the wings 38 within the plane spiral 10 ; 10 ' and / or the plane spiral 20 ; 20 ' are aligned parallel to each other. According to another preferred alternative of the present invention, the wings are 38 based on at least two radial areas within only one spiral 10 ; 20 ; 10 ' . 20 ' not aligned parallel to each other. As a result, within a circular heat exchanger 1 the flow conditions can be influenced by a different angular wing position of the wing 38 in the radial direction of the plane spiral 10 ; 20 ; 10 ' . 20 ' different flow conditions on the circular heat exchanger 1 ; 1' can be achieved. According to another preferred embodiment of the present invention, the wings 38 the plane spiral 10 ; 10 ' and the plane spiral 20 ; 20 ' aligned parallel to each other. It is also preferable that the wings 38 based on at least two radial regions of the flat spirals 10 . 20 ; 10 ' . 20 ' are not aligned parallel to each other in comparison. To these different orientations of the wings 38 with respect to the radial plane RE of the plane spirals 10 . 20 ; 10 ' . 20 ' to achieve the wings 38 according to the winding of the flat spirals 10 . 20 ; 10 ' . 20 ' oriented.

Preferably, the circular heat exchanger 1 ; 1' from the two flat spirals 10 . 20 , which in their middle area over the U-shaped bent connector 32 connected together and therefore a continuous pipe 30 for the refrigerant form. The continuous pipeline 30 has an input E and output A for the refrigerant. According to an embodiment already mentioned above, the heat exchanger 1 ; 1' an integer multiple of the two plane spirals 10 . 20 ; 10 ' . 20 ' on. These are connected to each other via the input E and the output A, that is, connected in series, and the refrigerant flows in series through all interconnected spirals or two planar spirals 10 . 20 are each connected in pairs to the refrigeration circuit and are therefore not connected in series.

The heat exchanger according to the invention preferably comprises 1 ; 1' at the exit A a drying section 40 , which is liquid-tightly connected to the pipeline or out of the pipeline 30c is formed (S VI).

The drying section 40 has an elongated expanded area 42 on, in which the pipeline 30c to a larger outer diameter compared to the rest of the pipeline 30 has been widened. According to another embodiment of the present invention, the drying section is an undeformed cylindrical pipe section 42 the source tube from which the wing tube is formed, for example, rolled, has been. Therefore, the drying section is 40 also integral part of the pipeline, but was not compared to the rest of the pipeline 30a . 30b widened.

In the area 42 becomes a drying material 44 brought in. The drying material 44 The refrigerant flows around and extracts moisture from the refrigerant. Preferably, the drying material is 44 as a bulk material, preferably in spherical form, for example in a small bag, as a cylindrical rod, as a plurality of rods or as one or more hollow cylindrical elements. The bulk material 44 has the advantage that it can be filled with inexpensive production in any size tube cross sections, without being impaired in its function. The drying material 44 will be in the area 42 through a sieve 46 held at the downstream end of the area 42 is arranged (see 9 and 10 ).

A drying section connected by soldering to a heat exchanger is in DE 199 05 354 C2 described in this context by reference in the description.

The drying section 40 goes into a capillary at its downstream end 50 above. The capillary 50 serves as an expansion device within the refrigeration cycle according to 1 , This capillary 50 is an integral part of the drying section or connected to it by a separate operation, preferably by soldering.

In the in 1 shown refrigerant circuit, the circular heat exchanger described above is preferably used as a heat exchanger WT1 and / or WT2. For improved operation of the circular heat exchanger 1 is he using a blower or fan L1; L2 combinable. Due to its round shape is the inventively preferred circular heat exchanger 1 by means of a corresponding holder made of plastic or metal within a pipeline, free in space or adjacent to the fan R1; R2 installable.

LIST OF REFERENCE NUMBERS

WT1, WT2

heat exchangers

V

compressor

e

expansion device

L1, L2

Blower / fan

1, 1 '

circular heat exchanger

10, 20

flat spiral

30, 30a, 30b

pipeline

e

entrance

A

output

32

connection

34

Pipeline end

36

wing tube

38

wing

40

drying section

42

expanded area

44

drying material

46

scree

50

capillary

x

Distance between adjacent pipelines

RE

radial plane

S

flow direction

70

fan

80

frame structure

82

main frame

84

opening

86

holding structure

87

ring

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 19905354 C2 [0003, 0069]
• US 1709176 [0004]
• US 1635869 [0006]
• US 7367380 B2 [0007]
• US 2974500 [0008]

Claims (25)

Circular heat exchanger ( 1 ; 1' ) having the following features: a first ( 30a ) and a second pipeline ( 30b ) with radially from the first ( 30a ) and the second pipeline ( 30b ) extending wings ( 38 ) while through the first ( 30a ) and second pipeline ( 30b ) a refrigerant is conductive and the first pipeline ( 30a ) a first ( 10 ; 10 ' ) and the second pipeline ( 30b ) a second plane spiral ( 20 ; 20 ' ), the first ( 30a ) and the second pipeline ( 30b ) the first ( 10 ; 10 ' ) and the second plane spiral ( 20 ; 20 ' ) in a radially inner region or a radially outer region of the spirals (FIG. 10 . 20 ) in liquid communication ( 32 ) are interconnected and can be traversed by a common refrigerant. Heat exchanger ( 1 ; 1' ) according to claim 1, in which between the first ( 10 ' ) and the second plane spiral ( 20 ' ) a fan ( 70 ) and the first ( 10 ' ) and the second plane spiral ( 20 ' ) adjacent to the fan ( 70 ) are arranged. Heat exchanger ( 1' ) according to claim 2, in which the first ( 30a ) and second pipeline ( 30b ) the first ( 10 ' ) and second spiral ( 20 ' ) via a U-shaped pipe section in the radially outer region of the first and second spiral ( 10 ' . 20 ' ) are interconnected. Heat exchanger ( 1' ) according to claim 2 or 3, in which the fan ( 70 ) and the first ( 10 ' ) and second plane spiral ( 20 ' ) in a housing ( 80 ) are held in concentric arrangement with each other. Heat exchanger ( 1 ; 1' ) according to one of the preceding claims, in which the first ( 10 ; 10 ' ) and the second plane spiral ( 20 ; 20 ' ) are arranged parallel to each other. Heat exchanger ( 1 ; 1' ) according to one of the preceding claims, in which the first ( 30a ) and / or the second pipeline ( 30b ) two radially extending therefrom and oppositely arranged wings ( 38 ) having. Heat exchanger ( 1 ; 1' ) according to claim 6, in which the wings ( 38 ) the first ( 30a ) and / or the second pipeline ( 30b ) perpendicular or at an angle γ of 0 ° ≤ γ <90 ° to the radial plane (RE) of the first ( 10 ; 10 ' ) and / or second spiral ( 20 ; 20 ' ). Heat exchanger ( 1 ; 1' ) according to claim 7, in which the wings ( 38 ) within the first ( 10 ; 10 ' ) and / or second spiral ( 20 ; 20 ' ) parallel to one another or relative to at least two radial regions of the spiral ( 10 . 20 ; 10 ' . 20 ' ) are not aligned parallel to each other. Heat exchanger ( 1 ; 1' ) according to claim 7, in which the wings ( 38 ) of the first spiral ( 10 ; 10 ' ) and the wings ( 38 ) of the second spiral ( 20 ; 20 ' ) parallel to one another or relative to at least two radial regions of the spirals ( 10 . 20 . 10 '; 20 ' ) are not aligned parallel to each other. Heat exchanger ( 1 ; 1' ) according to claim 5, in which the first ( 30a ) and second pipeline ( 30b ) the first ( 10 ; 10 ' ) and second spiral ( 20 ; 20 ' ) parallel to each other or radially offset from each other. Heat exchanger ( 1 ; 1' ) according to one of the preceding claims, in which the first ( 30a ) and the second pipeline ( 30b ) a continuous pipeline ( 30 ), from which the first ( 10 ; 10 ' ) and second spiral ( 20 ; 20 ' ) are wound. Heat exchanger ( 1 ; 1' ) according to one of the preceding claims, comprising more than two each from a pipeline ( 30 ) existing planar spirals ( 10 . 20 ; 10 ' . 20 ' ), which are in fluid communication with each other. Heat exchanger ( 1 ; 1' ) according to one of the preceding claims, in which the first ( 30a ) and / or second pipeline ( 30b ) consists of steel, copper or aluminum. Heat exchanger ( 1 ; 1' ) according to one of the preceding claims, located at a downstream end (A) of the first (A) 30a ) or second pipeline ( 30b ) a drying section ( 40 ), which is an integral part of the pipeline ( 30 ) or at the end (A) of the pipeline ( 30 ) is formed. Air conditioning, refrigerating or freezing appliance with a refrigeration cycle, comprising a compressor (V), an expansion device (E) and at least one heat exchanger ( 1 ; 1' ) according to one of the preceding claims, preferably as an evaporator and / or condenser. Manufacturing method for a circular heat exchanger ( 1 ), which comprises the following steps: providing a first ( 30a ) and a second pipeline ( 30b ) with radially extending from the pipeline wings ( 38 ) as two interconnected and opposite legs of a U-shaped pipeline, simultaneously winding a first planar spiral ( 10 ) from the first pipeline ( 30a ) and a second plane spiral ( 20 ) from the second pipeline ( 30b ), one each at a junction between the first ( 30a ) and the second pipeline ( 30b ) adjacent end of the first ( 30a ) and the second pipeline ( 30b ) has a radial inner beginning of the first ( 10 ) and the second spiral ( 20 ). Manufacturing method for a circular heat exchanger ( 1' ), which comprises the following steps: providing a first ( 30a ) and a second pipeline ( 30b ) with radially extending from the pipeline wings ( 38 ) as two interconnected and opposite legs of a U-shaped pipeline, simultaneously winding a first planar spiral ( 10 ' ) from the first pipeline ( 30a ) and a second plane spiral ( 20 ' ) from the second pipeline ( 30b ), each one free end of the first ( 30a ) and the second pipeline ( 30b ) has a radial inner beginning of the first ( 10 ' ) and the second spiral ( 20 ' ), and fixing the first ( 10 ) and the second spiral ( 20 ) in a housing and arranging a fan ( 70 ) between the first ( 10 ' ) and the second spiral ( 20 ' ). Manufacturing method according to claim 16 or 17, wherein the first ( 30a ) and the second pipeline ( 30b ) the first ( 10 ; 10 ' ) and the second spiral ( 20 ; 20 ' ) are wound parallel to each other or radially staggered to each other. Manufacturing method according to one of the preceding claims 16 to 18, wherein the first ( 30a ) and the second pipeline ( 30b ) form a continuous tube. Manufacturing method according to one of the preceding claims 16-19, wherein the first ( 10 ; 10 ' ) and second spiral ( 20 ; 20 ' ) are arranged parallel to each other. Manufacturing method according to one of the preceding claims 16 to 20, wherein the wing tube ( 36 ) so to a first ( 10 ; 10 ' ) and a second plane spiral ( 20 . 20 ' ) that the wings ( 38 ) within a plane spiral ( 10 ; 20 ; 10 ' . 20 ' ) are at least partially aligned parallel and / or angled to each other and / or that the wings ( 38 ) the first ( 30a ) and / or the second pipeline ( 30b ) perpendicular or at an angle γ of 0 ° ≤ γ <90 ° to the radial plane (RE) of the first ( 10 ; 10 ' ) and / or second spiral ( 20 ; 20 ' ) are aligned. Manufacturing method according to one of the preceding claims 16 to 21, with the further step: expansion of the pipeline ( 30 ) a radially outer end portion (A) of a planar spiral ( 20 ; 20 ' ) over a longitudinal section ( 42 ) and forming a capillary tube ( 50 ) at the longitudinal section ( 42 ). Manufacturing method according to one of the preceding claims 16 to 21, with the further step of providing a cylindrical tube section ( 30c ), preferably an original pipeline, in cylindrical form and introducing a drying material in the cylindrical pipe section ( 30c ), so that the drying material is held there, preferably by means of a sieve. A manufacturing method according to claim 23, further comprising the step of: forming a wing tube in which the cylindrical tube section is formed ( 30c ) subsequent second pipe section of an original pipeline, from which at least the first spiral ( 10 ; 10 ' ) is wound. A manufacturing method according to claim 24, further comprising the step of forming an integral capillary on or connecting a capillary to a wing tube distal end of the cylindrical tube section ( 30c ).

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