AU746338B2 - Heat transfer tube with internal grooves and method and device for manufacturing the tube - Google Patents
Heat transfer tube with internal grooves and method and device for manufacturing the tube Download PDFInfo
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- AU746338B2 AU746338B2 AU36748/00A AU3674800A AU746338B2 AU 746338 B2 AU746338 B2 AU 746338B2 AU 36748/00 A AU36748/00 A AU 36748/00A AU 3674800 A AU3674800 A AU 3674800A AU 746338 B2 AU746338 B2 AU 746338B2
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- grooves
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- transfer pipe
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES, PROFILES OR LIKE SEMI-MANUFACTURED PRODUCTS OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
- B21C37/00—Manufacture of metal sheets, rods, wire, tubes, profiles or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape
- B21C37/06—Manufacture of metal sheets, rods, wire, tubes, profiles or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape of tubes or metal hoses; Combined procedures for making tubes, e.g. for making multi-wall tubes
- B21C37/15—Making tubes of special shape; Making tube fittings
- B21C37/20—Making helical or similar guides in or on tubes without removing material, e.g. by drawing same over mandrels, by pushing same through dies ; Making tubes with angled walls, ribbed tubes or tubes with decorated walls
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES, PROFILES OR LIKE SEMI-MANUFACTURED PRODUCTS OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
- B21C37/00—Manufacture of metal sheets, rods, wire, tubes, profiles or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape
- B21C37/06—Manufacture of metal sheets, rods, wire, tubes, profiles or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape of tubes or metal hoses; Combined procedures for making tubes, e.g. for making multi-wall tubes
- B21C37/08—Making tubes with welded or soldered seams
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- 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
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
-1- Specification HEAT-TRANSFER PIPE WITH INTERNAL GROOVES AND MANUFACTURING METHOD AND MANUFACTURING DEVICE
THEREFOR
TECHNICAL FIELD The present invention relates to a structure of a heat-transfer pipe with internal grooves having grooves in an inner surface of a pipe body.
BACKGROUND ART A heat-transfer pipe in a heat exchanger such as an evaporator, a condenser or the like for an air conditioner is conventionally provided with spiral grooves in an inner surface of the pipe from a viewpoint of improvement in its heat transfer efficiency as shown in Japanese Patent Laid-Open Publication No. Hei 9-42881 so that a heat-transfer area is enlarged and an agitation effect is improved by allowing a refrigerant flowing in the pipe to annularly flow.
In the case of a heat-transfer pipe in this constitution, however, liquid film portions are uniformly distributed generally in the pipe when a condensation action proceeds to some extent and the thickness gradually ,.Th V-Z4TtVS V -2increases. Consequently, heat resistance and diffusion resistance increase and thereby a heat-transfer performance is deteriorated.
In order to address this problem, there is a proposal that the inner surface of the pipe is divided into a plurality of areas in the circumferential direction, each having a plurality of rows of grooves arranged in V-shaped patterns, for example, which are symmetric with respect to the direction of a pipe axis and have equal widths in the circumferential direction, for example, as shown in Japanese Patent Laid-Open Publication No. Hei 9-42880.
In the case of this constitution,. the distribution of the refrigerant flowing in the pipe in the pipe circumferential direction can be made ununiform because of flow merging and dividing actions by the plurality of the grooves arranged in V-shaped patterns provided in the inner surface of the pipe which are symmetric with respect to the pipe axis direction and have equal widths in the circumferential direction as compared with the aforementioned heat-transfer pipe having the spiral grooves.
Since high heat transfer efficiency is achieved in areas where the liquid refrigerant becomes a thin film as a result, the heat transfer efficiency at the time of condensation is improved.
However, in the case of the above-described heat-transfer pipe having grooves arranged in V-shaped patterns in the inner surface of the pipe which are symmetric with respect to the pipe axis direction and have equal widths in the circumferential direction, 1. Since refrigerant flows are collided and merged due to the grooves arranged in Vshaped patterns, flow resistance is high. For example, in the case where this heat-transfer pipe is used as an evaporator or the like, sufficient improvement of the heat transfer performance, which is affected by a great pressure loss, can not necessarily be obtained.
2. In areas where a refrigerant flow rate is low (areas having little refrigerant circulation), there is little effect even though the refrigerant distribution is made ununiform by the grooves arranged in V-shaped patterns. In the case where the heat-transfer pipe is used as an evaporator, in particular, a heat transfer performance enhancing effect cannot be obtained since a sufficient liquid refrigerant cannot be supplied in the pipe circumferential direction due to the groove structure. That is, improvement of the performance cannot be expected in some use areas.
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ftoffo°f ft ft f ft t [R:\LlBLL I 2493.doc:FDP:VJP I I It is thus desirable to provide a heat-transfer pipe with internal grooves having a heat transfer performance improved as much as possible by reducing a pressure loss and appropriately controlling refrigerant flows in the pipe to be even when a refrigerant flow rate is low, and a manufacturing method thereof as well as a manufacturing device, by which the s above-described problems can be solved.
It is the object of the present invention to substantially overcome or at least ameliorate one or more of the prior art disadvantages or to achieve at least one of the above desires.
Summary of the Invention The present invention provides a heat-transfer pipe with internal grooves, wherein a plurality of rows of grooves arranged in V-shaped patterns symmetric with respect to a pipe axis direction are provided on an inner surface of a pipe body; and widths of the plurality of rows of the grooves arranged in the V-shaped patterns are made unequal in a circumferential direction.
Thus, when the plurality of rows of the grooves arranged in V-shaped patterns are provided side by side with unequal widths in the circumferential direction, a component of force in the swirling direction are generated in a refrigerant liquid so that the refrigerant liquid flows in an ununiform manner in the pipe axis direction while repeatedly merging and [R:\LIBLL] 12493.doc:FDP:VP dividing at edges of respective grooves arranged in the V-shaped patterns. Consequently, an annular flow close to the one obtained by combination of spiral grooves can be obtained.
Further, an agitation effect is achieved and thereby a heat transfer performance is improved.
Preferably, secondary grooves having a prescribed depth are formed from a top side towards a base side at least in part of projected portions formed between respective grooves of the plurality of rows of the grooves arranged in the V-shaped patterns.
With the secondary grooves, the flow resistance of the refrigerant flowing in the pipe is further reduced by the secondary grooves and thereby a heat transfer performance is effectively improved even when a refrigerant flow rate is low.
Preferably, the secondary grooves are notched grooves arranged in a spiral direction relative to the pipe axis.
In this case, the flow resistance of the refrigerant flowing in the pipe is effectively reduced by the secondary grooves composed of the notched grooves in the spiral direction.
Further, a swirling force is increased in the spiral direction and thereby the heat transfer performance is improved.
•o o *o *oo 12493.doc:FDP:VJP Alternatively, secondary grooves having a prescribed depth are formed in an outer surface of at least part of projected portions formed between respective grooves of the rows of grooves arranged in the V-shaped patterns.
Thus, a pressure loss is reduced since the flow resistance of the refrigerant flowing in the pipe is reduced by the secondary grooves and thereby a heat transfer performance is effectively improved even when a refrigerant flow rate is low.
Preferably, the secondary grooves are fine grooves extending from one side surface of the projected portions to the other side surface thereof.
The flow resistance of the refrigerant flowing in the pipe is effectively reduced by the secondary grooves composed of fine grooves extending from one side surface to the other side surface of the projected portions in this case, and therefore the heat transfer performance is improved. Also, even when the pipe is expanded, both sides of the fine grooves are not crushed and thereby the heat-transfer performance is not deteriorated.
The present invention also provides a method for manufacturing a heat-transfer pipe with internal grooves, comprising the steps of: oo* o oo o ooo e e e [R:\LIBLL 112493.doc:FDP:VJP marking a plurality of rows of primary grooves arranged in V-shaped patterns symmetrical with respect to an axial direction of the pipe and unequal in width in a circumferential direction of the pipe on a flat plate-like heat-transfer pipe material by using a first marking roll; marking secondary grooves at least in part of projected portions formed between the rows of the primary grooves by using a second marking roll; and forming the flat plate-like heat-transfer pipe material into a cylindrical pipe by using a roll forming device, wherein marking of the primary grooves, marking of the secondary grooves and forming of the flat plate-like heat-transfer pipe material into the cylindrical pipe are continuously conducted.
In this method of manufacturing a heat-transfer pipe with internal grooves, the heattransfer pipe with internal grooves having the features of the above preferred embodiments can be easily manufactured only by combining the above-described first and second marking is rolls in the direction of the movement of the flat plate-like heat-transfer pipe material to perform continuous markings successively in two stages.
9* *g ooo 8 The present invention also provides a device for manufacturing a heat-transfer pipe with internal grooves, the device comprising: a first marking roll for marking a plurality of rows of grooves arranged in V-shaped patterns symmetrical with respect to an axial direction of the pipe and unequal in width in a circumferential direction of the pipe on a flat plate-like heat-transfer pipe material; a second marking roll for marking secondary grooves at least in part of projected portions formed between the rows of the primary grooves; and a roll forming device for forming the flat plate-like heat-transfer pipe material into a cylindrical pipe; wherein the first marking roll, the second marking roll and the roll forming device are provided successively side by side in a direction of movement of the flat plate-like heattransfer pipe material such that marking of the primary grooves, marking of the secondary grooves and forming of the flat plate-like heat-transfer pipe material into the cylindrical pipe are continuously conducted.
*o° eoooe **o *go By this device for manufacturing the heat-transfer pipe with internal grooves, the heat-transfer pipe with internal grooves having the features of the above preferred embodiments can be easily manufactured only by combining the above-described first and second marking rolls in the direction of the movement of the flat plate-like heat-transfer pipe material to perform markings successively in two stages.
As a result of the above preferred embodiments of the heat-transfer pipe with internal grooves and the manufacturing method thereof and the manufacturing device, a pressure loss, heat resistance in the heat-transfer pipe and diffusion resistance are reduced even in the case of being constituted as a condenser or an evaporator or even in the case where a refrigerant flow rate is low when the pipe is constituted as
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an evaporator. Consequently, a heat exchanger with sufficiently high heat transfer performance can be provided.
BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is an enlarged view showing part of a structure in an opened state of a pipe body of a heattransfer pipe with internal grooves according to a first embodiment of the present invention; Fig. 2 is an enlarged view of an essential part of the inner surface of the pipe body; Fig. 3 is a perspective view of a cut-off section of the essential' part of the inner surface of the pipe body; Fig. 4 is an enlarged view showing a structure of an essential part of the inner surface of a pipe body of a heat-transfer pipe with internal grooves according to a second embodiment of the present invention; Fig. 5 is an enlarged perspective view of the essential part; Fig. 6 is a perspective view of a cut-off section of the essential part of the inner surface of the pipe body; Fig. 7 is an enlarged view showing a structure of an essential part of the inner surface of a pipe body of 2, a heat-transfer pipe with internal grooves according to a h t -11third embodiment of the present invention; Fig. 8 is an enlarged perspective view of a cutoff section of the essential part; and Fig. 9 is a perspective view showing manufacture of a heat-transfer pipe with internal grooves according to the third embodiment of the present invention and a constitution of a manufacturing device.
BEST MODE FOR CARRYING OUT THE INVENTION First Embodiment Figs. 1 to 3 show a structure of a heat-transfer pipewith internal grooves according to a first embodiment of the present invention.
First, as shown in Figs. 1 to 3 for example, in the heat-transfer pipe 1 with internal grooves according to this embodiment, first to fifth groups A E of a plurality of rows of grooves is provided on an inner surface 2 of a pipe body la having an electric welded pipe structure.
Those groups of grooves are comprised of grooves 3 which are arranged to be symmetric, with respect to a pipe axis direction and to form relatively sharp V-shape patterns, and which are arranged with width of the grooves unequal to each other in the circumferential direction and with a lead angle 8 of the grooves different from each other, so as to promote a turbulent flow of a refrigerant liquid flowing in the pipe RA4, Sp R
V
-12body la and to promote the refrigerant liquid to become a thin film because coarse and minute refrigerant liquid portions are formed by dividing and merging the refrigerant liquid flow.
In Fig. 3, reference numeral 5 denotes a projected portion formed between the respective grooves 3 arranged in V-shaped patterns. Reference numerals 5a and denote a top and a base of the projected portion, respectively.
Thus, since the first to fifth groups A E composed of rows of grooves, which are arranged in V-shaped patterns and have a lead angle e different in next groups, are provided side by side with unequal widths in the circumferential direction, the refrigerant liquid flows ununiformly in the circumferential direction to swirl while repeatedly dividing and merging at edge portions of V-shape patterns of the respective grooves 3. Consequently, the grooves of the present invention can obtain an annular flow close to the one conventionally obtained by combination of spiral grooves even though the grooves arranged in V-shaped patterns are used. Thus, an effective agitation effect is achieved and thereby a heat transfer performance is improved.
Respective grooves 3 in the first to fifth groups A E are formed with a prescribed lead angle 0, a prescribed depth H and a prescribed number of grooves N so -13that the flow resistance of each groove portion is made as small as possible to reduce the pressure loss. Therefore, even when the heat-transfer pipe of the present invention is used for an evaporator at a low refrigerant flow rate, the pressure loss is reduced and thereby the heat transfer performance is improved.
According to the results of experiments conducted by the present inventors, the flow resistance was the smallest and the pressure loss was effectively reduced when the aforementioned lead angle 8, groove depth H, and number of grooves N are in the range of 5 15°, 0.2 0.3 mm and 45 55, respectively, in the case of a heat-transfer pipe having an outer dimension of 4 7 mm.
As described above, according to the constitution of the heat-transfer pipe with internal grooves of this embodiment, widths of groups A E composed of rows of grooves 3, which are arranged in V-shaped patterns and have a lead angle 8 different from each other, are set unequal in the circumferential direction rather than equal.
Therefore, the refrigerant in the pipe has swirling flow as in the case of the conventional pipe with spiral grooves.
Consequently, the heat transfer promotion effect is not deteriorated even when a refrigerant flow rate is low because the refrigerant is effectively supplied in the direction of the pipe.
-14- The lead angle 8, the groove depth H and the groove number N of the grooves 3 formed in the V-shaped patterns, the first to fifth groups A E of which are arranged in the inner surface of the pile, are set to the values by which the smallest flow resistance is obtained corresponding to the aforementioned experiment results.
Therefore, since the flow resistance can be made as small as possible to reduce the pressure loss as a result, a heattransfer pipe for a heat exchanger having a sufficiently high performance can be obtained.
Second Embodiment Figs. 4 to 6 show a structure of a heat-transfer pipe with internal grooves according to a second embodiment of the present invention.
First, in the heat-transfer pipe 1 with internal grooves according to this embodiment, first to fifth groups A E of a plurality of rows of grooves is provided on an inner surface 2 of a pipe body la having the same electric welded pipe structure as described above. Those groups of grooves are comprised of grooves 3 which are arranged to be symmetric with respect to a pipe axis direction and to form relatively sharp V-shape patterns, and which are arranged with width of the grooves unequal to each other in the circumferential direction and with a lead angle 8 of the grooves different from each other, so as to promote a turbulent flow of a refrigerant liquid flowing in the pipe body la and to promote the refrigerant liquid to become a thin film because coarse and minute refrigerant liquid portions are formed by dividing and merging the refrigerant liquid flow.
In Figs. 5 and 6, reference numeral 5 denotes a projected portion formed between the respective grooves 3 arranged in V-shaped patterns. Reference numerals 5a and denote a top and a base of the projected portion respectively. In this embodiment, secondary grooves 6 are provided and the secondary grooves 6 are composed of notched grooves (chipped grooves) in the spiral direction with a prescribed depth d from the top 5a towards the base Consequently, the flow resistance of the refrigerant is reduced and the refrigerant is further urged in the swirling direction.
Thus, since .the first to fifth groups A E composed of rows of grooves, which are arranged in V-shaped patterns and have a lead angle 8 different in next groups, are provided side by side with unequal widths in the circumferential direction, the refrigerant liquid flows ununiformly in the circumferential direction to swirl while repeatedly dividing and merging at edge portions of V-shape patterns of the respective grooves 3. Consequently, the ggrooves of the present invention can obtain an annular flow -1 -16close to the one conventionally obtained by combination of spiral grooves even though the grooves arranged in V-shaped patterns are used. Thus, an effective agitation effect is achieved and thereby a heat transfer performance is improved.
Respective grooves 3 in the first to fifth groups A E are formed with the secondary grooves 6 composed of notched grooves (chipped grooves) in the spiral direction as described above as well as a prescribed lead angle E, a prescribed depth H and a prescribed number of grooves as in the first embodiment, so that the flow resistance of each groove portion is made as small as possible to reduce the pressure loss. Therefore, even when the heat-transfer pipe of the present invention is used for an evaporator at a low refrigerant flow rate, the pressure loss is reduced and thereby the heat transfer performance is improved.
According to the results of experiments conducted by the present inventors as described above, the flow resistance was the smallest and the pressure loss was effectively reduced when the aforementioned lead angle 8, groove depth H, and number of grooves N are in the range of 150, 0.2 0.3 mm and 45 55, respectively, in the case of a heat-transfer pipe having an outer dimension of 4 7 mm.
As described above, according to the -17constitution of the heat-transfer pipe with internal grooves of this embodiment, widths of groups A E composed of rows of grooves 3, which are arranged in V-shaped patterns and have a lead angle 8 different from each other, are set unequal in the circumferential direction. Therefore, the refrigerant in the pipe has swirling flow as in the case of the conventional pipe with spiral grooves. Consequently, the heat transfer promotion effect is not deteriorated even when a refrigerant flow rate is low because the refrigerant is effectively supplied in the circumferential direction of the pipe.
The lead angle 08, the groove depth H and the groove number N of the grooves 3 formed in the V-shaped patterns, the first to fifth groups A E of which are arranged in the inner surface of the pile, are set to the values by which the smallest flow resistance is obtained.
In addition, the secondary grooves 6 are formed in the projected portions 5 provided between the respective grooves 3 as main grooves in V-shaped patterns and the secondary grooves 6 are notched grooves from the top 5a towards the base 5b of the projected portions 5 and are directed in the spiral direction. Therefore, since the flow resistance can be made as small as possible to reduce the pressure loss and swirling force in the spiral direction can be further increased, a heat-transfer pipe for a heat exchanger having A A -18a still higher performance can be obtained.
Third Embodiment Figs. 7 to 9 show a structure of a heat-transfer pipe with internal grooves according to a third embodiment of the present invention and a constitution of a manufacturing device employing a method for manufacturing the heat-transfer pipe, respectively.
First, in the heat-transfer pipe 1 with internal grooves according to this embodiment, first to fifth groups A E of a plurality of rows of grooves is provided on an inner surface 2 of a pipe body la having the same electric welded pipe structure as described above. Those groups of grooves are comprised of grooves 3 which are arranged to be symmetric with respect to a pipe axis direction and to form relatively sharp V-shape patterns, and which are arranged with width of the grooves unequal to each other in the circumferential direction and with a lead angle 8 of the grooves different from each other, so as to promote a turbulent flow of a refrigerant liquid flowing in the pipe body la and to promote the refrigerant liquid to become a thin film because coarse and minute refrigerant liquid portions are formed by dividing and merging the refrigerant liquid flow.
In Figs. 7 and 8, reference numeral 5 denotes a projected portion formed between the respective grooves 3 -19arranged in V-shaped patterns. Reference numerals 5a and denote a top and a base of the projected portion respectively. In this embodiment, secondary grooves 7 composed of fine grooves having a prescribed depth are formed from one side of an outer surface of the projected portion 5 to the other side thereof to direct toward, for example, the spiral direction. Consequently, the flow resistance of the refrigerant is reduced and the refrigerant is further urged in the swirling direction.
Thus, since the first to fifth groups A E composed of rows of grooves, which are arranged in V-shaped patterns and have a lead angle 8 different in next groups, are provided side by side with unequal widths in the circumferential direction, the refrigerant liquid flows ununiformly in the circumferential direction to swirl while repeatedly dividing and merging at edge portions of V-shape patterns of the respective grooves 3. Consequently, the grooves of the present invention can obtain an annular flow close to the one conventionally obtained by combination of spiral grooves even though the grooves arranged in V-shaped patterns are used. Thus, an effective agitation effect is achieved and thereby a heat transfer performance is improved.
Respective grooves 3 in the first to fifth groups A E are formed with the secondary fine grooves 7 formed from one side of an outer surface of the projected -0 1 ~~nTr oj portion 5 to the other side thereof in a prescribed depth to direct toward the spiral direction as well as with a prescribed lead angle 0, a prescribed- depth H and a prescribed number of grooves as in the first embodiment.
Consequently, the flow resistance of each groove portion is made as small as possible to reduce the pressure loss.
Therefore, even when the heat-transfer pipe of the present invention is used for an evaporator at a low refrigerant flow rate, the pressure loss is reduced and thereby the heat transfer performance is improved. Also, even when the pipe is expanded, the fine grooves on the side portions are not crushe d and thereby- the heat transfer' performance is not deteriorated.
According to the results of experiments conducted by the present inventors as described above, the flow resistance was the smallest and the pressure los s was effectively reduced when the aforementioned lead angle 0, groove depth H, and number of grooves N are in the range of 150, 0.2 0.3 mm and 45 55, respectively, in the case of a heat-transfer pipe having an outer dimension of 4 7
MM.
As described above, a ccording to the constitution of the heat-transfer pipe with internal grooves of this embodiment, widths of groups A E composed of rows of grooves 3, which are arranged in V-shaped patterns and >2 :7 -21have a lead angle e different from each other, are set unequal. Therefore, the refrigerant in the pipe has swirling flow as in the case of the conventional pipe with spiral grooves. Consequently, the heat transfer promotion effect is not deteriorated even when a refrigerant flow rate is low because the refrigerant is effectively supplied in the circumferential direction of the pipe.
The lead angle 0, the groove depth H and the groove number N of the grooves 3 formed in the V-shaped patterns, the first to fifth groups A E of which are arranged in the inner surface of the pile, are set to the values by which the smallest flow resistance is obtained.
In addition, the secondary grooves 7 composed of fine grooves are formed from one side of an outer surface of the projected portion 5 to the other side thereof to direct toward, for example, the spiral direction. Therefore, since the flow resistance can be made as small as possible to reduce the pressure loss and swirling force in the spiral direction can be further increased, a heat-transfer pipe for a heat exchanger having a still higher performance can be obtained. Also, even when the pipe is expanded, the fine grooves on the side portions are not crushed and thereby the heat transfer performance is not deteriorated.
The heat-transfer pipe with internal grooves -22having the groups A E of rows of the grooves arranged in V-shaped patterns and secondary grooves 7 described above are easily manufactured by the following method by using, for example, a manufacturing device shown in Fig. 9.
In Fig. 9, reference numeral 11 denotes a first marking roll which has a marking processing surface lla corresponding to the first to fifth groups A E of rows of grooves arranged as main' grooves in V-shaped patterns.
Reference numeral 12 denotes a second marking roll which has a marking processing surface 12a for marking the fine grooves 7 provided to extend, for example, in the spiral direction from one side to. the other side -of an outer surface of the projected portion 5 formed between the grooves 3 arranged in V-shaped patterns in the first to fifth groups A E. Reference numeral 13 denotes a flat plate-like heat-transfer pipe material. Reference numeral 16 denotes a heating device for heating and softening the heat-transfer pipe material at the time of roll forming.
Reference numeral 14 denotes a first pressure roller for sandwiching and pressing the flat plate-like heat-transfer pipe material 13 with the aforementioned first marking roll 11. Reference numeral 15 denotes a second pressure roller for sandwiching and pressing the flat plate-like heattransfer pipe material 13 with the aforementioned second marking roll 12. Reference numeral 17 denotes a roll -23forming device having a roll forming hole 17a for rollforming into a cylindrical shape the heat-transfer pipe material 13 which has the first to fifth groups A E of rows of grooves arranged in V-shaped patterns and the secondary grooves 7 formed thereon via the first and second marking rollers 11, 12 and is heated and softened by the heating device 16. The first marking roll 11 and the first pressure roller 14, the second marking roll 12 and the second pressure roller 15, the heating device 16 and the roll forming device 17 are successively provided side by side at predetermined intervals in the movement direction (see the arrow) of the heat-transfer pipe material 13.
Therefore, in the device for manufacturing the heat-transfer pipe with internal grooves, the first marking roll 11 and the first pressure roller 14 are used for marking the first to fifth groups A E of rows of grooves arranged in V-shaped patterns, the second marking roll 12 and the second pressure roller 15 are used for marking the secondary grooves 7 in part of the projected portions formed between the respective grooves 3 of the first to fifth groups A E of rows of grooves arranged in V-shaped patterns, and the heating device 16 and the roll forming device 17 are used for forming the flat plate-like heattransfer pipe material 13 into a cylindrical pipe. The first and second marking rolls 11, 12 are rotatably operated h -24so that the respective grooves 3 of the first to fifth groups A E and the secondary grooves 7 are successively marked -in two stages on the flat plate-like heat-transfer pipe material 13, and then the heat-transfer pipe material 13 can be heated and softened by the heating device 16 and then roll-formed by the roll forming device 17 to form a cylindrical pipe.
That is, in the method and device for manufacturing the heat-transfer pipe with internal grooves, the heat-transfer pipe with internal grooves having a constitution shown in Figs. 7 and 8 can be easily manufactured only by two 'stage successive marking of the grooves with the above-described first and second marking rolls 11, 12 combined. in the direction of the movement of the flat plate-like heat-transfer pipe material 13.
Other Embodiments Although a heat-transfer pipe of a electric welded pipe type is described as an example in the above embodiments, it is needless to say that the internal groove structures of the above embodiments can be also applied to a seam welded type of heat-transfer pipe.
INDUSTRIAL APPLICABILITY As described above, the heat-transfer pipe with internal grooves and the manufacturing method thereof and the manufacturing device according to the present invention are useful for a heat-transfer pipe of a heat exchanger and particularly suitable for a heat-transfer pipe used for an evaporator or a condenser in an air-conditioner.
Claims (9)
1. A heat-transfer pipe with internal grooves, wherein a plurality of rows of grooves arranged in V-shaped patterns symmetric with respect to a pipe axis direction are provided on an inner surface of a pipe body; and widths of the plurality of rows of the grooves arranged in the V-shaped patterns are made unequal in a circumferential direction.
2. The heat-transfer pipe with internal grooves according to claim 1, wherein secondary grooves having a prescribed depth are formed from a top side towards a base side at least in part of projected portions formed between respective grooves of the plurality of rows of the grooves arranged in the V-shaped patterns.
3. The heat-transfer pipe with internal grooves according to claim 2, wherein the secondary grooves are notched grooves arranged in a spiral direction relative to the pipe axis.
4. The heat-transfer pipe with internal grooves according to claim 1, wherein secondary grooves having a prescribed depth are formed in an outer surface of at least part of projected portions formed between respective grooves of the rows of grooves arranged in the V-shaped patterns. The heat-transfer pipe with internal grooves according to claim 4, wherein the secondary grooves are fine grooves extending from one side surface of the projected portions to the other side surface thereof.
V
6. A method for manufacturing a heat-transfer pipe with internal grooves, comprising the steps of: marking a plurality of rows of primary grooves arranged in V-shaped patterns symmetrical with respect to an axial direction of the pipe and unequal in width in a 25 circumferential direction of the pipe on a flat plate-like heat-transfer pipe material by using a first marking roll; o marking secondary grooves at least in part of projected portions formed between *the rows of the primary grooves by using a second marking roll; and forming the flat plate-like heat-transfer pipe material into a cylindrical pipe by using a roll forming device, wherein marking of the primary grooves, marking of the secondary grooves and forming of the flat plate-like heat-transfer pipe material into the cylindrical pipe are O ontinuously conducted. [R:\LIBLL 12493.doc:FDP:VJP
7. A device for manufacturing a heat-transfer pipe with internal grooves, the device comprising: a first marking roll for marking a plurality of rows of grooves arranged in V-shaped patterns symmetrical with respect to an axial direction of the pipe and unequal in width in a circumferential direction of the pipe on a flat plate-like heat-transfer pipe material; a second marking roll for marking secondary grooves at least in part of projected portions formed between the rows of the primary grooves; and a roll forming device for forming the flat plate-like heat-transfer pipe material into a cylindrical pipe; wherein the first marking roll, the second marking roll and the roll forming device are provided successively side by side in a direction of movement of the flat plate-like heat- transfer pipe material such that marking of the primary grooves, marking of the secondary grooves and forming of the flat plate-like heat-transfer pipe material into the cylindrical pipe are continuously conducted.
8. A heat-transfer pipe with internal grooves substantially as hereinbefore described with reference to Figs. 1 to 3; Figs. 4 to 6; or Figs. 7 to 9 of the accompanying drawings.
9. A method for manufacturing a heat-transfer pipe with internal grooves, the method substantially as hereinbefore described with reference to Figs. 1 to 3; Figs. 4 to 6; or Figs. 7 to 9 of the accompanying drawings. A device for manufacturing a heat-transfer pipe with internal grooves, the device substantially as hereinbefore described with reference to Figs. 1 to 3; Figs. 4 to 6; or Figs. 7 to 9 of the accompanying drawings. Dated 20 February, 2002 .25 Daikin Industries, Ltd *o Patent Attorneys for the Applicant/Nominated Person ••o::SPRUSON FERGUSON o .a
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10076799A JP3296325B2 (en) | 1999-04-08 | 1999-04-08 | Heat transfer tube with internal groove |
| JP11-100767 | 1999-04-08 | ||
| PCT/JP2000/002300 WO2000062001A1 (en) | 1999-04-08 | 2000-04-10 | Heat transfer tube with internal grooves and method and device for manufacturing the tube |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| AU3674800A AU3674800A (en) | 2000-11-14 |
| AU746338B2 true AU746338B2 (en) | 2002-04-18 |
Family
ID=14282656
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| AU36748/00A Ceased AU746338B2 (en) | 1999-04-08 | 2000-04-10 | Heat transfer tube with internal grooves and method and device for manufacturing the tube |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP1087198A4 (en) |
| JP (1) | JP3296325B2 (en) |
| CN (1) | CN1313947A (en) |
| AU (1) | AU746338B2 (en) |
| WO (1) | WO2000062001A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10210016B9 (en) * | 2002-03-07 | 2004-09-09 | Wieland-Werke Ag | Heat exchange tube with a ribbed inner surface |
| KR100752636B1 (en) * | 2006-05-02 | 2007-08-29 | 삼성광주전자 주식회사 | Refrigerator heat exchanger and its manufacturing method |
| EP2645040B1 (en) * | 2012-03-28 | 2017-06-21 | ABB Research Ltd. | Heat exchanger for traction converters |
| CN104708292A (en) * | 2015-03-02 | 2015-06-17 | 金龙精密铜管集团股份有限公司 | Machining method for heat conducting pipe |
| CN104949564A (en) * | 2015-07-08 | 2015-09-30 | 赤峰宝山能源（集团）贺麒铜业有限责任公司 | Straight tooth and high-low tooth internal thread heat transfer pipe |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6447880A (en) * | 1987-08-18 | 1989-02-22 | Nippon Steel Corp | Stainless steel having ceramics layer on surface |
| JPH10206060A (en) * | 1997-01-17 | 1998-08-07 | Kobe Steel Ltd | Heating tube having grooved inner surface |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5560089U (en) * | 1978-10-12 | 1980-04-23 | ||
| JPH02165875A (en) * | 1988-12-16 | 1990-06-26 | Furukawa Electric Co Ltd:The | Heat exchanger tube and its manufacture |
| JPH04288197A (en) | 1991-03-18 | 1992-10-13 | Hitachi Ltd | Washing control for washing machine |
| JP2721755B2 (en) * | 1991-05-16 | 1998-03-04 | 株式会社神戸製鋼所 | Heat transfer tube and method of manufacturing the same |
| JP3292043B2 (en) * | 1995-06-19 | 2002-06-17 | 株式会社日立製作所 | Heat exchanger |
| US5791405A (en) * | 1995-07-14 | 1998-08-11 | Mitsubishi Shindoh Co., Ltd. | Heat transfer tube having grooved inner surface |
| JP3199636B2 (en) * | 1996-05-30 | 2001-08-20 | 住友軽金属工業株式会社 | Heat transfer tube with internal groove |
| JP3286171B2 (en) * | 1996-08-06 | 2002-05-27 | 株式会社神戸製鋼所 | Heat transfer tube with internal groove |
| JPH1183368A (en) * | 1997-09-17 | 1999-03-26 | Hitachi Cable Ltd | Heat transfer tube with internal groove |
| JPH1190530A (en) * | 1997-09-25 | 1999-04-06 | Sumitomo Light Metal Ind Ltd | Heat transfer tube manufacturing method and manufacturing apparatus |
-
1999
- 1999-04-08 JP JP10076799A patent/JP3296325B2/en not_active Expired - Fee Related
-
2000
- 2000-04-10 EP EP00915441A patent/EP1087198A4/en not_active Withdrawn
- 2000-04-10 AU AU36748/00A patent/AU746338B2/en not_active Ceased
- 2000-04-10 CN CN 00801029 patent/CN1313947A/en active Pending
- 2000-04-10 WO PCT/JP2000/002300 patent/WO2000062001A1/en not_active Ceased
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6447880A (en) * | 1987-08-18 | 1989-02-22 | Nippon Steel Corp | Stainless steel having ceramics layer on surface |
| JPH10206060A (en) * | 1997-01-17 | 1998-08-07 | Kobe Steel Ltd | Heating tube having grooved inner surface |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1087198A1 (en) | 2001-03-28 |
| JP2000292088A (en) | 2000-10-20 |
| AU3674800A (en) | 2000-11-14 |
| CN1313947A (en) | 2001-09-19 |
| JP3296325B2 (en) | 2002-06-24 |
| EP1087198A4 (en) | 2005-04-27 |
| WO2000062001A1 (en) | 2000-10-19 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FGA | Letters patent sealed or granted (standard patent) |