EP3009779A1 - A tube of the gas cooler for the condenser - Google Patents
A tube of the gas cooler for the condenser Download PDFInfo
- Publication number
- EP3009779A1 EP3009779A1 EP14461576.2A EP14461576A EP3009779A1 EP 3009779 A1 EP3009779 A1 EP 3009779A1 EP 14461576 A EP14461576 A EP 14461576A EP 3009779 A1 EP3009779 A1 EP 3009779A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- tube
- cooling medium
- channels
- flow
- diameter
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000002826 coolant Substances 0.000 claims abstract description 32
- 238000000034 method Methods 0.000 claims description 3
- 238000001125 extrusion Methods 0.000 claims description 2
- 238000004088 simulation Methods 0.000 description 4
- 238000005728 strengthening Methods 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000007797 corrosion Effects 0.000 description 2
- 238000005260 corrosion Methods 0.000 description 2
- 238000005219 brazing Methods 0.000 description 1
- 230000009172 bursting Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 230000006378 damage Effects 0.000 description 1
- 238000010230 functional analysis Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000013517 stratification Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
Definitions
- the present invention relates to a tube of the gas cooler for the condenser, in particular the tube of the gas cooler for the condenser, having a flattened shape, defined by two mutually parallel flat walls and two curved side walls positioned opposite to each other and connecting these flat walls.
- the tube is elongated in the transverse direction X.
- the tube comprises a plurality of identical channels for the flow of cooling medium arranged in parallel and in series next to each other in the transverse direction X of the tube 10, with spacing between them, having a circular cross-section.
- the dimensions of the channel for the cooling medium were selected based on the simulation and the internal lumen was fixed in the range of 0.35 to 0.8 mm, and the ratio of the air flow opening (Pr) was selected in accordance with the following formula: 0.1429 x Td 2 + 0.1343 * Td + 0.139 ⁇ Pr ⁇ 0.1429 x Td 2 + 0.1343 x Td + 0.113 wherein Td is the dimension between the outer side of the tube and the upper side of the passage for the cooling medium in the direction of the stratification of the tubes.
- the ratio of four times the cross-sectional area to the internal perimeter is set between 0.9 mm and 2.0 mm.
- the obtained value of the ratio of the material cross-section i.e. the section of the pipe body to the free flow cross-section, i.e. to the total cross-sectional area of all the flow channels between is between 1.4 and 4.5.
- the wall thickness of the tube was adopted in a range between about 0.2 mm and 0.6 mm, and in the individual cases, slightly more than 1 mm.
- the object of the invention is to provide such a tube construction which would mainly ensure high resistance to high working pressure flowing through it, and would have sufficient resistance to corrosion and impact of stones and other objects.
- bursting tests and corrosion tests during designing the tube performed tests consisting of striking the edge of the tube with grit to simulate the potential impact of stones during the use of the car.
- this test it was confirmed the need to reinforce the wall of the tube in the region between the flow channel of the cooling medium located closest to the outer side wall of the tube and this wall.
- the object of the invention is to provide such a pipe structure that would take into account a restriction which the process of pressing the tube with channels having a diameter less than ⁇ 0.35 mm is subjected to.
- the tube of the cooler which is characterized in that the side walls of the tube, have a thickness which satisfies the following relationships: 1.25 x D ⁇ A ⁇ 1.68 x D 2.12 x B ⁇ A ⁇ 3.05 x B wherein:
- the tube is manufactured in an extrusion process, and is preferably formed by folding.
- a tube of the gas cooler for the condenser has a flattened shape, defined by two mutually parallel flat walls 13, 15 and two curved side walls 12, 14 positioned opposite and connecting these flat wall 13,15.
- the tube 10 is elongated in the transverse direction X.
- the tube 10 includes a plurality of identical channels 11 for the flow of cooling medium arranged in parallel and in series next to each other in the transverse direction X of the tube 10, with spacing between them.
- the channels 11 for the flow of cooling medium have a circular shape of cross-section with a diameter D.
- the channels 11 are spaced from the inner surface of flat walls 13, 15 of the tube by an amount B.
- Transverse direction X is appointed by the straight line parallel to the flat walls 13,15 and crossing central points of the channels 11 circular cross-section.
- the distance B is the distance between the inner surface of the flat walls 13,15, and the channels 11 for the flow of cooling medium, measured in the direction Y perpendicular to the direction X, along the diameter D of the channel 11.
- the radii of curvature of the rounding of the side walls 12,14 are the fixed radii.
- a part C of the tube, indicated in Fig. 1 is a part inserted into the manifold, therefore the pressure acting on the tube in this part as well as inside is compensated, and therefore the tube 10 can be locally thinned.
- a part C of the tube called an "endforming" is provided to introduce the tube into the manifold. Size of the part C results from the construction of the manifold.
- the tube 10 is designed according to the following description of the currently designed gas cooler with the depth of the core of 12 mm.
- the tube 10 of the cooler is designed where the side walls 12, 14 have a thickness A, which satisfies the following relationships: 1.25 x D ⁇ A ⁇ 1.68 x D 2.12 x B ⁇ A ⁇ 3.05 x B wherein:
- the dimensioning of the flat tube 10 taking into account in particular the area of strengthening selected in such a way that the flat tube 10 on one hand meets the requirements for burst pressure made to the coolers of the motor vehicles, on the other hand has a low weight and high efficiency of heat conversion.
- Multi-channel flat tube made this way with a reinforced wall meets the requirements concerning required destruction pressure (so-called burst test).
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
wherein:
A - is the distance measured along the transverse direction (X) between the outer surfaces of the side walls (12,14) and the outermost channels (11) for the flow of cooling medium of the tube (10),
D - is the diameter of the channels (11) for the flow of cooling medium,
B - is the distance between the inner surface of the flat walls (13,15) and channels (11) for the flow of cooling medium, as measured in a direction (Y) perpendicular to the direction (X) along the diameter (D) of the channel (11) for the flow of cooling medium.
Description
- The present invention relates to a tube of the gas cooler for the condenser, in particular the tube of the gas cooler for the condenser, having a flattened shape, defined by two mutually parallel flat walls and two curved side walls positioned opposite to each other and connecting these flat walls. The tube is elongated in the transverse direction X. The tube comprises a plurality of identical channels for the flow of cooling medium arranged in parallel and in series next to each other in the transverse direction X of the
tube 10, with spacing between them, having a circular cross-section. - It is known from the patent specification
US-A-4998580 andDE 10060104 multi-stream condenser of the cooling medium with a plurality of tubes and ribs, which are disposed sandwiched between a pair of manifolds. The tubes comprise a plurality of flow channels. The tubes are arranged in layers and are suitable for passage through the two-phase cooling medium in the case of condensation of the cooling medium flowing through the passage of the cooling medium. Furthermore, the condenser has ribs which are interposed between each of the adjacent tubes and the manifolds, each of which is located on the two longer ends of the tubes. The manifolds are connected to the cooling medium flow channels. As disclosed in patent specificationDE 10060104 the dimensions of the channel for the cooling medium were selected based on the simulation and the internal lumen was fixed in the range of 0.35 to 0.8 mm, and the ratio of the air flow opening (Pr) was selected in accordance with the following formula: 0.1429 x Td2 + 0.1343 * Td + 0.139 ≥ Pr ≥ 0.1429 x Td2 + 0.1343 x Td + 0.113 wherein Td is the dimension between the outer side of the tube and the upper side of the passage for the cooling medium in the direction of the stratification of the tubes. - It is known from the patent specification
EP 090828 - Given the known solutions of the radiator tubes and taking into account six times higher working pressure than in the conventional coolers, the present inventors have come to the conclusion that it should be considered first of all to design strengthening the walls of the condenser tube. As a result of undertaken studies they came to the conclusion that this may be achieved by an increase in the wall thickness of the tube and reduction of the diameter of the cooling medium flow channels. Given the known solutions which combine the diameter of the tube channel with a pitch of the pipe (so called pitch type) the inventors made such a selection that it provides high resistance to high working pressure and good performance.
- The object of the invention is to provide such a tube construction which would mainly ensure high resistance to high working pressure flowing through it, and would have sufficient resistance to corrosion and impact of stones and other objects. For this purpose, in addition to the bursting tests and corrosion tests during designing the tube performed tests were included consisting of striking the edge of the tube with grit to simulate the potential impact of stones during the use of the car. As a result of this test it was confirmed the need to reinforce the wall of the tube in the region between the flow channel of the cooling medium located closest to the outer side wall of the tube and this wall.
- The object of the invention is to provide such a pipe structure that would take into account a restriction which the process of pressing the tube with channels having a diameter less than Φ 0.35 mm is subjected to. By way of simulations and tests the result was obtained based on which it was found out that the number of channels and the width of the tube does not significantly affect the mechanical strength of the tube, and only the wall thickness of the side wall of the tube does.
-
- A
- - is the distance measured along the transverse direction X between the outer surfaces of the side walls and the outermost channels for the flow of cooling medium of the tube,
- D
- - is the diameter of the channels for the flow of cooling medium,
- B
- - is the distance between the inner surface of the flat walls and channels for the flow of cooling medium, as measured in a direction Y perpendicular to the direction X along the diameter D of the
channel 11 for the flow of cooling medium. - According to the invention, the tube is manufactured in an extrusion process, and is preferably formed by folding.
- These and other features of the embodiments of the invention will now be described in detail with reference to the accompanying drawings, in which:
-
Figure 1 shows a tube of the cooler according to the invention in cross-section and partly in perspective view; -
Figure 2 shows a tube of the cooler ofFigure 2 in cross section. - The present invention will be described in more detail hereinafter with reference to the accompanying drawings in which is shown a preferred embodiment of the invention.
- Shown in
Fig. 1 a tube of the gas cooler for the condenser according to the invention has a flattened shape, defined by two mutually parallelflat walls curved side walls flat wall tube 10 is elongated in the transverse direction X. Thetube 10 includes a plurality ofidentical channels 11 for the flow of cooling medium arranged in parallel and in series next to each other in the transverse direction X of thetube 10, with spacing between them. Thechannels 11 for the flow of cooling medium have a circular shape of cross-section with a diameter D. Thechannels 11 are spaced from the inner surface offlat walls flat walls channels 11 circular cross-section. - As illustrated in
Fig. 1 andFig.2 the distance B is the distance between the inner surface of theflat walls channels 11 for the flow of cooling medium, measured in the direction Y perpendicular to the direction X, along the diameter D of thechannel 11. The radii of curvature of the rounding of theside walls Fig. 1 is a part inserted into the manifold, therefore the pressure acting on the tube in this part as well as inside is compensated, and therefore thetube 10 can be locally thinned. In addition, a part C of the tube called an "endforming" is provided to introduce the tube into the manifold. Size of the part C results from the construction of the manifold. - In order to design the most optimal dimensions of the
tube 10 and the area A of the strengthening the following examples were taken into account and a simulation was performed under the following conditions: - Adopted - the depth of the core of
gas cooler 12 mm with 16 holes with a diameter of Φ 0.37 mm. - Adopted - the depth of the core of gas cooler 16 mm with 20 holes with a diameter of Φ 0.37 mm, the distance of 0.38 mm between the channels.
- Adopted - the depth of the core of gas cooler 16 with 14 holes with a diameter of Φ 0.50 mm, the distance of 0.58 mm between the channels.
- Adopted - the depth of the core of
gas cooler 12 mm with 10 holes with a diameter of Φ 0.50 mm, a distance of 0.61 mm between the channels. - Adopted - the depth of the core of
gas cooler 12 mm with 11 holes with a diameter of Φ 0.50 mm Φ, the distance of 0.50 mm between the channels. - Adopted - the depth of the core of
gas cooler 12 mm with 12 holes with a diameter of Φ 0.50 mm, the distance of 0.41 mm between the channels. - Adopted - the depth of the core of gas cooler 12 mm with 13 holes with a diameter of Φ 0.50 mm, the distance of 0.34 mm between the channels.
- The
tube 10 is designed according to the following description of the currently designed gas cooler with the depth of the core of 12 mm. - Two options were proposed:
- 1. A
tube 10 with achannel 11 having a diameter D of Φ 0.37 mm, which gives the best mechanical strength but is disadvantageous in the case of pressure drop of the cooling medium as well as due to the risk of clogging thechannel 11 during brazing. - 2. A
tube 10 with achannel 11 having a diameter D of Φ 0.5 mm, which gives the best compromise for the mechanical strength and the ability to manufacture. - Based on the functional analysis and simulation, the radii of curvature of the
side walls tube 10 are identified as the most critical area. Therefore, thetube 10 of the cooler is designed where theside walls
wherein: - A
- - is the distance measured along the transverse direction X between the outer surfaces of the
side walls outermost channels 11 for the flow of cooling medium of thetube 10, - D
- - is the diameter of the
channels 11 for the flow of cooling medium, - B
- - is the distance between the inner surface of the
flat walls channels 11 for the flow of cooling medium, as measured in a direction Y perpendicular to the direction X along the diameter D of thechannel 11 for the flow of cooling medium. - The dimensioning of the
flat tube 10 taking into account in particular the area of strengthening selected in such a way that theflat tube 10 on one hand meets the requirements for burst pressure made to the coolers of the motor vehicles, on the other hand has a low weight and high efficiency of heat conversion. - Multi-channel flat tube made this way with a reinforced wall meets the requirements concerning required destruction pressure (so-called burst test).
Claims (3)
- A tube (10) of the gas cooler for the condenser, having a flattened shape, defined by two mutually parallel flat walls (13, 15) and two curved side walls (12,14) positioned opposite to each other and connecting these flat walls (13,15), the tube (10) being elongated in the transverse direction (X), said tube (10) comprises a plurality of identical channels (11) for the flow of cooling medium arranged in parallel and in series next to each other in the transverse direction (X) of the tube (10), with spacing between them, having a circular cross-section, characterized in that the side walls (12, 14) of the tube (10) have a thickness (A), which satisfies the following relationships:
wherein:A - is the distance measured along the transverse direction (X) between the outer surfaces of the side walls (12,14) and the outermost channels (11) for the flow of cooling medium of the tube (10),D - is the diameter of the channels (11) for the flow of cooling medium,B - is the distance between the inner surface of the flat walls (13,15) and channels (11) for the flow of cooling medium, as measured in a direction (Y) perpendicular to the direction (X) along the diameter (D) of the channel (11) for the flow of cooling medium. - The tube of the gas cooler according to claim. 1,
characterized in that it is produced in an extrusion process. - The tube of the gas cooler according to claim. 1,
characterized in that it is produced by folding.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP14461576.2A EP3009779B1 (en) | 2014-10-15 | 2014-10-15 | A tube of the gas cooler for the condenser |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP14461576.2A EP3009779B1 (en) | 2014-10-15 | 2014-10-15 | A tube of the gas cooler for the condenser |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3009779A1 true EP3009779A1 (en) | 2016-04-20 |
EP3009779B1 EP3009779B1 (en) | 2019-05-15 |
Family
ID=51690991
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14461576.2A Active EP3009779B1 (en) | 2014-10-15 | 2014-10-15 | A tube of the gas cooler for the condenser |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP3009779B1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10955595B2 (en) * | 2016-03-07 | 2021-03-23 | Asml Netherlands B.V. | Multilayer reflector, method of manufacturing a multilayer reflector and lithographic apparatus |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0090828A1 (en) | 1981-10-01 | 1983-10-12 | Ucerpo S/A. Ideias, Pesquizas E Invencoes | Trough-like collar for the upper external rim of fuel reservoirs for cooling thereof |
US4998580A (en) | 1985-10-02 | 1991-03-12 | Modine Manufacturing Company | Condenser with small hydraulic diameter flow path |
DE10060104A1 (en) | 1999-12-09 | 2001-06-13 | Denso Corp | Coolant liquefier has coolant passage with tube inner passage height selected in range from 0.5 to 0.7 millimeters |
DE102004024825A1 (en) * | 2003-05-23 | 2004-12-09 | Denso Corp., Kariya | Heat exchange tube with several fluid paths |
EP2485006A1 (en) * | 2009-09-30 | 2012-08-08 | Daikin Industries, Ltd. | Heat-exchanging flat tube |
-
2014
- 2014-10-15 EP EP14461576.2A patent/EP3009779B1/en active Active
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0090828A1 (en) | 1981-10-01 | 1983-10-12 | Ucerpo S/A. Ideias, Pesquizas E Invencoes | Trough-like collar for the upper external rim of fuel reservoirs for cooling thereof |
US4998580A (en) | 1985-10-02 | 1991-03-12 | Modine Manufacturing Company | Condenser with small hydraulic diameter flow path |
DE10060104A1 (en) | 1999-12-09 | 2001-06-13 | Denso Corp | Coolant liquefier has coolant passage with tube inner passage height selected in range from 0.5 to 0.7 millimeters |
DE102004024825A1 (en) * | 2003-05-23 | 2004-12-09 | Denso Corp., Kariya | Heat exchange tube with several fluid paths |
EP2485006A1 (en) * | 2009-09-30 | 2012-08-08 | Daikin Industries, Ltd. | Heat-exchanging flat tube |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10955595B2 (en) * | 2016-03-07 | 2021-03-23 | Asml Netherlands B.V. | Multilayer reflector, method of manufacturing a multilayer reflector and lithographic apparatus |
Also Published As
Publication number | Publication date |
---|---|
EP3009779B1 (en) | 2019-05-15 |
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