KR102087678B1 - Device for heat transfer - Google Patents

Abstract

The invention relates in particular to a heat transfer device (1) for transferring heat between a first fluid and a second fluid. The device (1) has a closed housing (3) with a heat exchanger unit (2) disposed inside a volume completely enclosed by a housing (3), and the heat exchanger units (2) are arranged spaced apart from each other It is formed of tubes (10, 11, 15, 16). The heat exchanger unit (3) has at least one cylindrical spiral (9, 14) having a central axis and at least two cylindrical spiral tubes (10, 11, 15, 16). The invention also relates, in particular, to the use of the device 1 according to the invention which is used for the refrigerant circulation system of the air conditioning system of a motor vehicle.

Description

Heat transfer device {DEVICE FOR HEAT TRANSFER}

The present invention particularly relates to a heat transfer device for use in automobiles. At this time, heat is transferred between the first fluid and the second fluid, preferably the fluid in the liquid state and the refrigerant. As a liquid fluid, water or a water-glycol-mixture that absorbs heat from the refrigerant or releases heat to the refrigerant is used. Carbon dioxide, also referred to as R744 or CO2, is preferably used as the refrigerant. The device has a closed housing with a heat exchanger unit disposed inside a volume completely enclosed by the housing. The heat exchanger unit is formed of tubes.

In the prior art, air conditioning systems for automobiles are known which have a refrigerant circulation system and a heat exchanger integrated in the refrigerant circulation system, in which case the heat exchanger is on one side as an evaporator and with it for cooling the fluid and the other. On the one hand, it acts as a condenser for heating the fluid. When flowing through the evaporator, the refrigerant evaporates, while when flowing through the condenser, the refrigerant is liquefied. Heat transfer is always under the phase shift of the refrigerant.

In the refrigerant circulation system, conventional refrigerants having much lower pressure than carbon dioxide, such as R134a and 1234yf, circulate. In addition, the refrigerant circulatory process using R744 is particularly transcritical. The heat at this time is always absorbed at a pressure lower than the critical pressure, ie at a pressure below the critical, when flowing through the evaporator, for example in processes where R134a is used. However, at a pressure above the critical pressure, ie at a pressure above the critical pressure, heat is released to the environment. The heat exchanger is referred to as a condenser when operation is performed below a threshold using R134a, or when the refrigerant is liquefied under certain ambient conditions using R744. Some heat transfer takes place at a constant temperature. When heat is released in a heat exchanger exceeding a threshold, the temperature of the refrigerant decreases constantly. In this case, the heat exchanger is also called a gas cooler.

The gas cooler for heat transfer between ambient air and R744 as a heat absorbing fluid has a structure and size corresponding to conventional condensers for R134a. Also, the installation position in the vehicle, particularly in the front area, is the same. When the refrigerant flows through the gas cooler, sensible heat must be transferred to the air, so uniform flow by ambient air with as low a temperature as possible to reach a sufficiently high exchange degree. ) Must be guaranteed. However, the high level of exchange and, in addition, the efficient operation of the gas cooler, are becoming increasingly difficult as the number of heat exchangers and driver-assisted systems placed in the front area of the vehicle, especially for transferring heat to the surrounding air, increases according to the general trend. You can.

Refrigerant-refrigerant-heat exchangers, known in the prior art, that use liquid refrigerant as a fluid that absorbs or releases heat, ie for refrigerants such as R134a and 1234yf, are formed as plate heat exchangers. At this time, the plates made from thin-walled aluminum or steel plates, respectively, at a predetermined pressure, for example, a working pressure of 4 bar and a bursting pressure of 31 bar in the evaporator and a working pressure of 16 bar and a burst of 60 bar in the condenser. Corresponds to the required level of strength of refrigerant at pressure. In the case of applying R744 as refrigerant, the required burst pressure level is placed at 260 bar for the evaporator and 340 bar, which is about several times higher for the condenser / gas cooler.

Thus, for the refrigerant R744 at the same temperature demand level, both the burst pressure and the working pressure are up to about 10 times higher than for the refrigerant R134a or 1234yf. To correspond to a much higher level of liquid demand, the wall of the plate sheet must be formed with a much thicker thickness and / or from other fabrication materials such as special steel. However, the pressure-resistant parts, which correspond to the above-mentioned requirements, for example heat exchangers made of thicker walls and / or special steels, have a particularly heavy weight and large installation space, and are very difficult to manufacture and maintain. It is cost intensive.

From EP 2 402 694 A1, a heat exchanger, particularly a heat exchanger for an automotive air conditioning plant, which is operated as a condenser, is proposed. The condenser is provided with a tube bundle and a housing for transferring heat between the refrigerant and the coolant, in which case the refrigerant is guided through the tubes of the tube bundle, and the coolant is guided through the housing. Coolant flows around the tube from the outer side. Each of the tubes communicates with the inside of the member formed by the collector at each end. The heat exchanger is operated cross-flow. The material of the housing is plastic.

In the case of the refrigerant-heat exchanger known in the prior art, a lot of installation space has to be used for heat transfer with air, and especially in the front area of a vehicle, this installation space becomes smaller. In addition, in the case of a conventional heat exchanger for R134a or 1234yf compared to R744, the design pressure requirements of the components in the refrigerant circulation system are significantly lower.

An object of the present invention is to provide a heat exchanger for efficiently transferring heat between two fluids, particularly between a liquid fluid and a refrigerant as a coolant. With the heat exchanger, the maximum heat output must be able to be delivered when the size of the structure is minimal or when the installation space demand is minimal. The heat exchanger must be suitable for operation using carbon dioxide. In addition, the heat exchanger must have a minimum weight and must cause minimal manufacturing and material costs.

The above object is solved by objects having the features of independent patent claims. Improvements are described in the dependent patent claims.

The above object is solved by a heat transfer device according to the present invention, in particular a device for transferring heat between a first fluid and a second fluid. The device has a closed housing with a heat exchanger unit disposed inside a volume completely enclosed by the housing. The heat exchanger unit is formed of pipes spaced apart from each other.

According to the concept of the present invention, the heat exchanger unit has at least one cylindrical spiral having a central axis and at least two cylindrical spirally curved tubes. In this case, the term “cylindrical spiral” means a helix or helicoid, and the helix or helix is a curve with a constant slope and is arranged around the side of the circular cylinder. The cylindrical spiral-shaped tube is preferably a tube having a circular flow cross-section, wherein the circular flow cross-section depicts a cylindrical spiral and is formed in a spiral shape. Cylindrical spiral-shaped tubes are generally also referred to as tube-cylindrical spirals.

The at least two cylindrical spirally curved pipes are preferably connected to each other through connecting members and connecting lines, and heat can be transferred between the fluids not only in the areas of the tubes but also in the areas of the connecting members and connecting lines. So that they are spaced apart from each other and placed inside a volume surrounded by the housing.

When one or more cylindrical spirals are arranged, the central axes of these cylindrical spirals are preferably aligned parallel to each other.

According to one improvement of the invention, the cylindrical spiral type has at least one cylindrical spiral-shaped inner tube and a cylindrical spiral-shaped outer tube. At this time, the cylindrical spiral-shaped inner tube is disposed coaxially to the central axis of the cylindrical spiral, and is disposed inside the volume surrounded by the outer tube curved in the cylindrical spiral type. Therefore, the central axis of the tubes corresponds to the central axis of the cylindrical spiral. Tube-cylindrical spirals made of inner and outer tubes with different diameters are coaxially coupled.

According to one preferred embodiment of the present invention, guide devices are arranged inside a volume surrounded by a housing, and the guide devices are used to transfer one of two fluids for heat transfer to the outer surface of the tubes of the heat exchanger unit. Therefore, in order to guide through the flow paths, flow paths for the one fluid are formed upon connection with the housing.

A separating member is preferably arranged as a guide device between the cylindrical spirally curved inner tube and the cylindrical spirally curved outer tube disposed radially adjacent to the central axis, so that the volume completely enclosed by the housing flows Is subdivided into. In this case, the separating member is aligned coaxially with the central axis of the cylindrical spiral. The separating member is preferably formed in a hollow cylindrical shape, in particular in a circular cross-section, with the result that the inner tube is arranged inside a volume enclosed by the separating member and the outer tube is arranged in a cylindrical spiral manner around the separating member. .

In a further preferred embodiment of the present invention, a displacement member is formed as a guide device inside the volume surrounded by the inner tube bent in a cylindrical spiral shape. At this time, the displacement member is disposed coaxially with respect to the central axis of the inner tube bent into a cylindrical spiral or a cylindrical spiral. The displacement member is preferably formed in a cylindrical shape, in particular in a circular cross-section, with the result that the inner tube is arranged in a cylindrical spiral-like manner around the displacement member.

As a result, the flow paths are limited by the housing and the separating member, and by the separating member and the displacement member, respectively by the outer face of the tube. The inlets and outlets of the flow paths are formed spaced apart from each other in the direction of the central axis, so that the fluid is guided through the flow paths substantially parallel to the central axis. The at least two flow paths, preferably coaxially aligned, can be perfused sequentially or simultaneously by a fluid.

According to a further preferred embodiment of the present invention, the tubes are ribbed on the outer surface. Formed from a very good thermally conductive material, especially aluminum, which increases the heat transfer surface on the outer side of the tubes, and the ribs in thermal contact with the tubes for turbulent flow generation and / or for mutual matching of coaxial flow paths, And it is preferably curved to form a radial dimension without gaps. The first fluid, in particular the refrigerant, then flows inside the tubes, while the second fluid, especially the coolant, is guided along the ribbed outer surface of the tubes. The tubes are also preferably formed from metal, especially aluminum.

According to one improvement of the present invention, the housing is formed of two parts, the first housing member and the second housing member. Preferably, the housing members are arranged in a manner to contact the separation surface. The housing hermetically seals the heat exchanger unit to the periphery, in which case additional seals, in particular flat seals, are preferably formed in the area of the separation surface between the housing members. In the assembled state of the device, the housing members are tightly connected to each other, preferably screwed together. According to alternative embodiments, the housing members are clamped or glued to one another or welded or crimped to one another. At this time, the crimping coupling can be understood as a coupling method for bending the edge to make a flange, and in this case, the two component parts are connected to each other by plastic deformation. Inside the crimped area, a seal, for example an O-shaped ring seal, also called a crimping, can be inserted in an integrated manner.

The housing is preferably formed from plastic or metal, especially aluminum and / or cast aluminum. The housing preferably has connectors for guiding the fluid. At this time, the fluid may be guided into the housing through the inlet, and may be guided outward from the housing through the outlet. The connectors are preferably both sides protruding from the wall of the housing.

A preferred embodiment of the present invention as a heat exchange device that can operate in purely countercurrent or in crossflow or in a combination of orthogonal and countercurrent can be used in refrigerant circulation systems, especially in refrigerant circulation systems of air conditioning systems, It is used to cool or heat the fluid in the cooling circulation system or the heating circulation system. At this time, the heat exchanger unit can be used in different applications as a condenser, gas cooler or evaporator, in particular of carbon dioxide, for example as a coolant cooled heat exchanger as well as a supercharged air cooler provided with refrigerant, exhaust gas cooler or oil It can be used as a cooler. At this time, other mediums, such as water or oil or exhaust gas, may also be used as a refrigerant or as a coolant. The heat transfer device can preferably be used as a refrigerant-heat exchanger, in particular a refrigerant-coolant-heat exchanger, especially as a carbon dioxide-water-heat exchanger.

When using the device according to the invention, the conventional air-cooled gas cooler can be replaced by 70% to 90% coolant cooling, in particular water-cooled gas cooler, and to allow the use of a larger space in the front area of the vehicle It can be moved from the front area. Although an attractive installation space of this type is required for recooling of the coolant in the coolant-air-heat exchanger, all heat exchangers to be arranged in the vehicle front area can be more flexibly arranged with each other. All requirements are met for sensible heat transfer inside the R744 gas cooler and for efficient operation of the air conditioning system. Efficient operation of an air conditioning system with a refrigerant circulation system that uses carbon dioxide as a refrigerant in a specific vehicle cannot be guaranteed due to insufficient cooling or heat release, without the possibility of relocating the gas cooler and recirculating the secondary refrigerant circulation system. . For many applications, there is already a second coolant system in the vehicle in addition to the original engine cooling, for example in the case of hybrid vehicles there is a second coolant system for cooling the electric parts or for supercharged air. It is thus possible to integrate the coolant cooling gas cooler into the already existing second coolant system. The additional complexity required for coolant recooling is small. In the case of using the device according to the invention as a coolant cooling gas cooler in an air conditioner system of an electric vehicle which can also be operated in a heating operation mode or a heat pump mode in addition to the operation mode as a cooling device, the device can be used as an evaporator or gas cooler as required It is activated, in which case the refrigerant circulation system can be switched by valves. At this time, if the device is integrated in the coolant circulation system of the electric parts and operated as an evaporator, the waste heat of the electric parts, for example, the battery and / or the electric motor can be evaluated and used for heating purposes.

In summary, the heat transfer device according to the present invention has various advantages as follows:

-Efficient heat transfer between two fluids, especially liquid and refrigerant as coolants,

-When the size of the structure is minimal or when the installation space demand is minimal, that is, the ratio of the heat transferable to the retrofitted volume is optimal, the maximum heat output can be delivered,

High pressure-resistant heat exchangers can be provided due to the combination of multiple tube-cylindrical spiral or spiral tube coils that can be connected in parallel and / or in series,

-A modular structure of multiple tube-cylindrical spirals, in particular ribbed tube-cylindrical spirals, which can be connected in parallel and / or in series can be provided, thereby enabling heat exchangers with minimum weight at high output ranges to be realized and And it can be applied modularly to fluid combinations,

-Suitable for operation using carbon dioxide, especially for automotive applications, and

-Manufacturing cost is minimized and material cost is minimized.

Still other details, features and advantages of the present invention are revealed from the following detailed description of embodiments made with reference to the associated drawings. Description of drawings:
1 is a view showing a heat transfer device having a closed housing formed of a first housing member and a second housing member,
2 to 4 is a heat transfer device, a view showing a housing and a heat exchanger unit disposed in the housing in a cross-sectional view,
5 is a view showing a heat exchanger unit of the heat transfer device,
6A and 6B are views showing a heat exchanger unit of the heat transfer device of FIG. 5 embedded in a second housing member,
Figure 6c is a heat exchanger unit of the heat transfer device of Figures 6a, 6b, embedded in the second housing member, a view showing the heat exchanger unit in a sectional view,
7 is an exploded view showing a heat transfer device and a heat exchanger unit with housing members,
8A is an exploded view showing heat exchanger units made of first and second cylindrical spirals each having an outer tube and an inner tube,
8B is an exploded view of the heat exchanger unit of FIG. 8A with displacement members and separation members,
FIG. 9 is a view showing a cylindrical spiral tube having a portion with a bare tube and ribs and a portion with the ribs shown in cross-section, and
10 is a sectional view showing a tube-cylindrical spiral of the heat exchanger unit.

1 shows a heat transfer device 1 having a housing 3 formed of a first housing member 3a, also referred to as the upper half of the housing, and a second housing member 3b, also referred to as the lower half of the housing. have. The housing members 3a, 3b of the housing 3 made up of two parts abut the separation surface 4 from each other in a closed state.

The first housing member 3a is formed so as to completely surround the volume by engaging with the second housing member 3b. The first housing member 3a and the second housing member 3b correspond to each other in the assembled state of the device 1. The two housing halves 3a, 3b can be assembled by simply combining.

The housing members 3a, 3b are each provided with one connection pipe 5, 6 for the inflow and outflow of coolant. The coolant flows into the device 1 through the inlet 5 and from the device 1 through the outlet 6. The refrigerant flows into the device 1 through the inlet pipe 7 and is discharged from the device 1 through the outlet pipe 8. The inlet pipe 7 and the outlet pipe 8 for the refrigerant penetrate the wall of the first housing member 3a of the housing 3.

2 to 4 are heat transfer devices 1 in cross section, respectively, of a housing 3 and a heat exchanger unit 2 disposed inside the housing 3, i.e. inside a volume enclosed by the housing 3, respectively. As presented. At this time, the heat exchanger unit 2 is formed as an arrangement made of ribbed pipes having connecting members 19 and connecting lines 20. The preferred fabrication material for the heat exchanger unit 2 is aluminum, and for the housing 3 plastic is preferred.

The housing 3 seals the volume surrounding the heat exchanger unit 2 with respect to its surroundings in a sealed manner. In the operating state of the device 1, a refrigerant flows inside the heat exchanger unit 2, while coolants such as liquid fluids, especially water or water-glycol-mixtures, also circulate through the heat exchanger unit 2. The coolant flowing into the device 1 through the inlet 5 in the flow direction 21 is the gaps formed between the walls of the housing members 3a, 3b and the heat exchanger unit 2 and together with the heat exchanger unit On the outer surface of (2) it passes through the device (1) and is discharged from the device (1) through the outlet (6). As a result, the coolant is guided in the flow direction 21 between the components of the heat exchanger unit 2 and the inner surface of the housing 3. The coolant circulates through the connecting members 19 and connecting lines 20 of the heat exchanger unit 2, and consequently the connecting members 19 and connecting lines 20 participate in heat transfer between the coolant and the refrigerant. .

The heat exchanger unit 2 is formed of a first cylindrical spiral 9 and a second cylindrical spiral 14 as two sub-units each having two tube-cylindrical spirals arranged coaxially with each other. The first cylindrical spiral (9) and the second cylindrical spiral (14) are provided with outer tubes (10, 15) and inner tubes (11, 16) curved in a cylindrical spiral type, respectively. Each is arranged coaxially about the common central axis. The central axes of the first cylindrical spiral 9 and the second cylindrical spiral 14 are again aligned parallel to each other. The outer tubes 10 and 15 and the inner tubes 11 and 16 of the cylindrical spirals 9 and 14 are formed as ribbed tubes.

Hollow cylindrical separation members 12 and 17 are disposed between the outer tubes 10 and 15 and the inner tubes 11 and 16 of the cylindrical spirals 9 and 14, respectively. The separating members 12, 17 having a circular cross-section, coaxially aligned again with respect to the common central axis of the cylindrical spiral of the inner tube 11, 16 and the cylindrical spiral of the outer tube 10, 15, are provided with the inner tube 11 , 16) separate the volume enclosed by the cylindrical spiral of the outer tube and the volume enclosed by the cylindrical spiral of the outer tube (10, 15). The volume surrounded by the central axis by the cylindrical spirals 9 and 14 and the inner tube 11 of the first cylindrical spiral 9 and the inner tube 15 of the second cylindrical spiral 14, respectively. Displacement members 13 and 18 are disposed inside. The displacement members 13 and 18 have a fully cylindrical shape or a rod shape with a circular cross section, and are coaxially aligned with respect to the central axis of the cylindrical spirals 9 and 14. Accordingly, both the first cylindrical spiral 9 and the second cylindrical spiral 14 are formed from inside to outside as follows: displacement members 13, 18, cylindrical spirals of the inner tubes 11, 16, and separating members Cylindrical spirals of (12, 17) and outer tubes (10, 15). The inner pipes 11 and 16 are respectively fluidically connected to the outer pipes 10 and 15 through the connecting line 20 and the connecting member 19, and as a result, the pipes 10, 11 and 15, The volumes surrounded by 16) form a volume associated with the refrigerant supply.

The tubes (10, 11) of the first cylindrical spiral (9), the refrigerant is guided to the tubes (15, 16) of the second cylindrical spiral (14) through the connecting member (19) and the connecting line (20) Before, it can be perfused simultaneously or sequentially by the refrigerant as needed. The pipes 15 of the second cylindrical spiral 14 can likewise be perfused simultaneously or sequentially by a refrigerant, if necessary. In particular, the simultaneous perfusion of the tubes 10, 11 of the first cylindrical spiral 9 and / or the tubes 15, 16 of the second cylindrical spiral 14 allows the refrigerant to control the pressure loss of the refrigerant during individual perfusion. Precise control of perfusion is premised. Alternatively, the refrigerant can also be supplied to the outer tubes 10, 15 simultaneously, and the refrigerant can be supplied to the inner tubes 11, 16 simultaneously or sequentially, or all of the tubes 10, 11, 15, 16) the refrigerant may be supplied simultaneously or sequentially. As a result, the heat exchanger unit 2 is formed in one row or multiple rows depending on the output requirements, and the number of cylindrical spirals 9, 14 is variable. In addition to the first cylindrical spiral 9 and the second cylindrical spiral 14 whose path is provided, additional cylindrical spirals not shown in the figure can be provided.

The tubes 10, 11, 15, 16, the separating members 12, 17 disposed between the tubes 10, 11, 15, 16 and the cylindrical spirals 9, 14 Upon formation of the housing 3 in relation to the displacement members 13, 18, the coolant is guided along the outer surface of the heat exchanger unit 2 as intended, with the heat exchanger unit in the flow direction 21 ( 2) In the circumference, perfusion of the device 1 by the coolant is determined. As a result, the flow paths for the coolant in which the diverters are formed are structurally combined of the heat exchanger unit 2 and the recesses, grooves and similar members formed in the housing 3 and the heat exchanger unit 2 integrally disposed in the housing 3. Is given from In this case, in particular, both the separating members 12 and 17 and the displacement members 13 and 18 are formed so that the mass flow of the coolant is divided as intended, especially in terms of its length.

In particular, as shown in FIG. 3, after the coolant flows in, it flows through the inlet 5 in the flow direction 21, around the outer tube 10 and inner tube 11 of the first cylindrical spiral 9 After being divided into two partial mass flows through the formed volume, they flow generally parallel to each other and parallel to the central axis of the cylindrical spiral 9. The first partial mass flow of coolant will pass between the housing 3 and the wall of the separating member 12. The second partial mass flow of coolant is passed between the separation member 12 and the displacement member 13. In the case of an embodiment of tubes as a screw tube, not shown in the figure, also the flow paths are actually wound in a cylindrical spiral type by cylindrical spiral tubes. In the embodiment of the tubes 10, 11 as a ribbed tube, flow paths run through the gaps formed between the ribs. The displacement members 13 abut the housing 3 by their end faces, respectively, to ensure fixed support. The end faces of the separating member 12 protrude more than the end faces of the cylindrical spiral 9, in particular the end faces of the cylindrical spirals of the outer tube 10 and inner tube 11, in this case on one side In order to divide the coolant mass flow, collect the partial mass flows on the other hand again, and guide them to the second cylindrical spiral 14 as a cavity mass flow, the end faces of the separating member 12 and the housing 3 ), The gap is maintained on both sides. After circulating the first cylindrical spiral 9, the coolant mass flow guided to the second cylindrical spiral 14 is actually the center of the second cylindrical spiral 14 between the wall of the housing 3 and the separating member 17. It penetrates parallel to the axis. The end faces of the separating member 17 of the second cylindrical spiral 14 protrude from the ends of the cylindrical spiral 14, in particular the ends of the cylindrical spirals of the outer tube 15 and inner tube 16, in this case the separating member (17) is in the first end face region in contact with the circumferential surface of the housing (3) in a fluid sealing manner, in particular in a coolant sealing manner. The fluid-sealed arrangement is used to guide the coolant around the outer tube 15 formed in a cylindrical spiral shape, without splitting the coolant mass flow. Between the second end face of the separating member 17 and the housing 3 disposed at the end of the first end face, a gap to circulate the mass flow of the coolant after the outer tube 15 is circulated to the inner tube 16 Is formed. After exiting from the flow path by turning the outer tube 15 of the second cylindrical spiral 14, the coolant mass flow is diverted, and the second cylindrical spiral 14 between the separating member 17 and the displacement member 18 The inner tube 16 is turned and guided to the outlet 6 through a flow path. The flow paths of the second cylindrical spiral 14 are sequentially perfused.

5 shows the heat exchanger unit 2 of the heat transfer device 1. Figure 6a, 6b and 6c illustrate a second housing member (3b), i.e. the heat exchanger of the, 5 embedded in the upper half housing unit (2). 6c shows the tubes 10, 11, 15, 16 of cylindrical spirals 9, 14 in cross section as heat exchanger units 2.

During the operation of the device 1, a refrigerant flows inside the heat exchanger unit 2, which flows into the heat exchanger unit 2 through the inlet pipe 7 in the flow direction 22, and the outlet pipe 8 Is discharged through. As shown in FIG. 5, the refrigerant flowing into the heat exchanger through the inlet pipe 7 is partially flowed through the outer tube 10 of the first cylindrical spiral 9 in the connecting member 19, respectively. It is divided into partial mass flows through the inner tube (11). Partial mass flows of the refrigerant are simultaneously supplied to the tubes (10, 11) of the first cylindrical spiral (9). After being discharged from the tubes 10, 11 of the first cylindrical spiral 9, the partial mass flows are collected again in the additional connecting member 19, and through the connecting line 20 the second cylindrical spiral 14 It is led to the tubes 15, 16. After flowing through the tubes (10, 11) of the first cylindrical spiral (9), the refrigerant mass flow guided to the second cylindrical spiral (14) is subsequently guided through the outer tube (15) of the second cylindrical spiral (14) After being discharged from the outer pipe 15, the direction is changed, and then guided to the discharge pipe 8 through the inner pipe 16. The outer tube 15 and the inner tube 16 of the second cylindrical spiral 14 are sequentially flowed through by the refrigerant. Therefore, the refrigerant side of the heat exchanger unit 2 or the heat transfer device 1 is connected in a purely countercurrent manner corresponding to the coolant side (see the embodiment of FIG. 3).

The exemplary connection of the heat transfer device 1 to the refrigerant side is particularly related to the heat exchanger unit 2 operated as a gas cooler, in which case the refrigerant density is significantly increased upon cooling despite a one-step state change, As a result, the tubes 10 and 11 of the first cylindrical spiral 9 are simultaneously perfused, and the tubes 15 and 16 of the second cylindrical spiral 14 are sequentially perfused. Simultaneous perfusion of the first cylindrical spiral 9 of the heat exchanger unit 2 and sequential perfusion of the second cylindrical spiral 14 are special modes of operation for media that do not have latent heat. At this time, the expression latent heat transfer means a heat transfer process in which heat is absorbed or released simultaneously with phase shift. Examples of latent heat transfer may include condensation and evaporation. Heat transfer with no potential ratio is achieved without phase shift of the fluid. Heat transfer processes that do not have a potential ratio take place, for example, in heat exchangers operating above a threshold as a gas cooler, especially in conventional gas coolers for carbon dioxide, cooled with coolant or with water.

7 shows an exploded view of the heat transfer device 1 and the heat exchanger unit 2 with two housing members 3a, 3b. In each of Figures 8a and 8b an exploded view of the outer tube (10, 15) and internal tube (11, 16) a first cylindrical spiral (9) and a second cylindrical heat exchanger unit (2) consisting of a spiral (14) having a Is presented respectively, in which FIG. 8B in particular shows the formation of the separating members 12 and 17 and the displacing members 13 and 18.

The heat exchanger unit 2 is completely enclosed by a housing 3. The housing 3, preferably formed of plastic, metal or other suitable lightweight material, is shown in the open form in FIG. The heat exchanger unit 2 is arranged in the recesses 23 formed inside the housing members 3a, 3b, which are connected to the cylindrical spirals 9, 14, the connecting members 19 It is formed to be suitable for each other in the outer shape of the lines 20 and the arrangement of the component parts. The two housing members 3a, 3b are screwed together with, for example, a flat seal disposed in the separating surface 4. The seal and screw connections are not shown. The coolant connectors 5, 6 are respectively rigidly and fluidly arranged in the housing members 3a, 3b. The inlet pipe 7 and the outlet pipe 8 of the refrigerant are guided through the through opening 24 formed in the upper half 3a of the housing, and are connected to the housing member 3a in a fluid sealing manner.

FIG. 8A shows coaxial inside the arrangement of inner tubes 11, 16 and cylindrical spiral tubes 10, 15 with displacement members 13, 18 arranged coaxially inside the cylindrical spirals 9, 14, respectively. It shows the exploded view of the outer tube (10, 15) with the separating member (12, 17) arranged in. Since both the displacement members 13, 18 and the separation members 12, 17 are used to limit the flow paths formed around the tubes 10, 11, 15, 16, the displacement member 13, 18) and the separating members 12 and 17 are also referred to as guide devices, especially guide devices for coolants. In Figure 8b an exploded view of the displacement members 13, 18 of the inner tubes 11, 16, the separating members 12, 17 and the outer tubes 10, 15 is shown, wherein the parts are of the device 1 In the assembled state, they are arranged in the order mentioned from inside to outside. The connecting members 19 and the connecting lines 20 were mentioned to make up for the heat exchanger unit 2.

9 shows the tubes 10, 11, 15, 16 of a cylindrical spiral 9, 14 having a portion formed of a screw tube and a portion having ribs and a portion having the ribs shown in cross section. The portion of the tube (10, 11, 15, 16) formed of a screw tube has a wall thickness (s) ranging from 0.6 mm to 1.7 mm ± 10%, an outer diameter (d _a ) ranging from 5.5 mm to 8.2 mm ± 0.15 mm and 4.25 It has an inner diameter (d _i ) in the range of mm to 4.8. The outer diameter (d _ar ) of the portion formed by the ribbed tube reaches 9.4 mm, while the minimum inner diameter (d _{i, min} ) of the ribbed tube reaches 4.0 mm. The transition between the screw tube and the ribbed tube has a length 1 of about 15 mm.

The range of the tubes 10, 11, 15, 16 formed of ribbed tubes has a minimum wall thickness s ranging from 0.6 mm to 1.1 mm. The rib height r _n ranges from 0.3 mm to 0.4 mm rib thickness r _s to 1.3 mm ± 10% to 2 mm. 50 / (25.4 mm) is applied as the rib density. Further, it appears that the dimensions of the ribbed tube in the range of -50% to + 200% are suitable for application.

10 shows a cross-sectional view of the tube-cylindrical spiral of the heat exchanger unit 2. The inner diameter (D _i ) of the cylindrical spiral of the outer tubes (10, 15) is 8.8 mm, for example, the outer diameter (d _ar ) of the ribbed tubes (10, 11, 15, 16) in the direction of the central axis of 9.4 mm. When it is ± 0.1 mm to 9.0 mm ± 0.2 mm, it reaches 50.9 mm. Preferably, the preferred outer diameters of the cylindrical spirals 9, 14 are 48 mm, 69 mm, 90 mm and 111 mm with ± 10 mm tolerance, respectively. When the outer diameters of the cylindrical spirals 9 and 14 are 69 mm, the inner diameter of the cylindrical spirals of the outer tubes 10 and 15 is 50 mm, and the outer diameters of the cylindrical spirals of the inner tubes 11 and 16 are 48 mm. , And the inner diameter of the cylindrical spiral of the inner tube (11, 16) is 29㎜. The number of windings of each cylindrical spiral 9, 14 lies between 5 and 50.

1: Heat transfer device
2: Heat exchanger unit
3: housing
3a: first housing member, upper half of housing
3b: second housing member, lower half of housing
4: Separation surface of housing (3)
5: coolant inlet, connector
6: Coolant outlet, connector
7: refrigerant inlet pipe
8: refrigerant discharge pipe
9: First cylindrical spiral
10: outer tube of the first cylindrical spiral (9)
11: Inner tube of the first cylindrical spiral (9)
12: Separation member of the first cylindrical spiral (9)
13; Displacement member of the first cylindrical spiral (9)
14: second cylindrical spiral
15: outer tube of the second cylindrical spiral 14
16: Inner tube of the second cylindrical spiral 14
17: Separation member of the second cylindrical spiral 14
18: displacement member of the second cylindrical spiral (14)
19: Connection member
20: connecting line
21: Coolant flow direction
22: refrigerant flow direction
23: Recess
24: through opening
a: spacing
d _a : External diameter of the screw tube (10, 11, 15, 16)
d _ar : Outer diameter of ribbed tube (10, 11, 15, 16)
d _{i, min} : Minimum inner diameter of ribbed tube (10, 11, 15, 16)
D _i : inner diameter of cylindrical spiral of outer tube (10, 15)
r _h : Rib height
r _s : rib thickness
l: Transition length
s: wall thickness of screw tube (10, 11, 15, 16)

Claims (10)

It has a closed housing (3) with a heat exchanger unit (2) disposed inside a volume completely enclosed by a housing (3), the heat exchanger unit (2) is spaced apart from each other arranged tubes (10, 11, 15, 16) as a heat transfer device (1) for transferring heat between the refrigerant and the coolant,
The heat exchanger unit (2) is provided with at least two cylindrical spiral-shaped curved tubes (10, 11, 15, 16) forming at least one cylindrical spiral (9, 14) having a central axis,
The at least one cylindrical spiral (9, 14) includes a first cylindrical spiral (9) and a second cylindrical spiral (14),
The first cylindrical spiral 9 is a cylindrical spiral-shaped first outer tube 10 and a cylindrical spiral-shaped first inner tube 11 disposed inside a volume surrounded by the first outer tube 10 Equipped with,
The second cylindrical spiral 14 is a cylindrical spiral-shaped second outer tube 15 and a cylindrical spiral-shaped second inner tube 16 disposed inside a volume surrounded by the second outer tube 15 Equipped with,
The refrigerant is divided into a first partial mass flow and a second partial mass flow in the connecting member 19, the first partial mass flow is supplied inside the first outer tube 10, and the second partial mass Flow is supplied to the inside of the first inner tube 11, the refrigerant flows through the inside of the first outer tube 10 and the inside of the first inner tube 11 at the same time,
The refrigerant discharged from the first outer tube (10) and the refrigerant discharged from the first inner tube (11) are gathered again in an additional connecting member (19) and supplied to the inside of the second outer tube (15), The refrigerant discharged from the second outer tube 15 is supplied to the inside of the second inner tube 16, so that the refrigerant is inside the second outer tube 15 and inside the second inner tube 16 Flow through sequentially,
The coolant flows through the outside of the first outer tube 10 and the outside of the first inner tube 11 at the same time, and then the outside of the second outer tube 15 and the outside of the second inner tube 16. It characterized in that it is formed to flow through sequentially, the heat transfer device. delete The method of claim 1,
Guide devices are arranged inside a volume surrounded by the housing 3, and the guide devices are used to transfer one of the fluids for heat transfer to the tubes 10, 11, 15 of the heat exchanger unit 2, A heat transfer device, characterized in that it is arranged in such a way as to form flow paths for the one fluid in combination with the housing (3), for guiding through the flow paths along the outer side of the 16). The method of claim 3,
The cylindrical spiral-shaped inner tube 11 and 16 and the cylindrical spiral-shaped outer tube 10 arranged radially adjacent to the central axis so that the volume completely enclosed by the housing 3 is subdivided into flow paths. , 15) is a separation device (12, 17) is disposed as a guide device, the separation member (12, 17) is characterized in that it is arranged coaxially on the central axis of the cylindrical spiral (9, 14) , Heat transfer device. The method of claim 4, wherein
As the separation members 12 and 17 are formed in a hollow cylindrical shape, the inner tube 11 and 16 are inside a volume surrounded by the separation members 12 and 17 and the outer tube 10 and 15 are A heat transfer device, characterized in that arranged in a cylindrical spiral shape around the separation member (12, 17). The method of claim 3,
Displacement members 13 and 18 are formed as a guide device inside the volume surrounded by the cylindrical spiral-shaped inner tubes 11 and 16, and the displacement members 13 and 18 are the cylindrical spirals 9 and 14 ) Is arranged coaxially with respect to the central axis. The method of claim 6,
Since the displacement members 13 and 18 are formed in a cylindrical shape, the inner tube 11 and 16 are arranged in a cylindrical spiral shape around the displacement members 13 and 18. , Heat transfer device. The method of claim 1,
The tube (10, 11, 15, 16) is characterized in that it is formed in a ribbed (ribbed) on the outer surface, heat transfer device. The method of claim 1,
The housing 3 is characterized in that it is formed of at least two parts of the first housing member (3a) and the second housing member (3b), the heat transfer device. The heat transfer device according to any one of claims 1, 3 to 9, characterized in that it is used for a refrigerant circulation system of an air conditioning system.

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