JP2005291484A - Heating piping - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide heating piping having high layout performance, and reducing a heat loss of a forward pipe and a return pipe, by constituting an outer peripheral surface of the forward pipe so as to be adjacent to the return pipe. <P>SOLUTION: This heating piping has the forward pipe 10 connected between a water-cooled engine 90 and a front heater 91 for heating air and making hot water flow in the front heater 91, and the return pipe 11 making the hot water flowed out of the front heater 91 flow in the water-cooled engine 90. The forward pipe 10 and the return pipe 11 are formed in a substantially circular shape in a passage cross section, and are composed of a double tube structure for arranging the forward pipe 10 on the inner peripheral side of the return pipe 11. Thus, the layout performance is enhanced, and the heat loss of the forward pipe and the return pipe can be reduced. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a heating pipe connected between, for example, a water-cooled engine and a heating unit that heats air, and circulates the heating medium to the heating unit. The present invention relates to a pipe structure in which a pipe and a return pipe for returning a heat medium flowing out from a heating means to a water-cooled engine are integrally formed.

  Conventionally, as this type of heating pipe, for example, one having a configuration as shown in FIG. 9 is known. As shown in FIG. 9, the heating pipes 100 a and 100 b are connected among the water-cooled engine 101, the front heater 102, and the rear heater 103. The heating pipes 100a and 100b flow out of the forward pipe 100a through which engine cooling water (hereinafter referred to as hot water) from the water-cooled engine 101 flows into the front heater 102 and the rear heater 103, and out of the front heater 102 and the rear heater 103. And a return pipe 100b for returning the warm water to the water-cooled engine 101. Further, the forward pipes 100 a and the return pipes 100 b are connected by a heater hose 104.

  The forward pipe 100 a and the return pipe 100 b circulate hot water heated by the cooling of the water-cooled engine 101 to the front heater 102 and the rear heater 103. That is, the hot water flowing into the front heater 102 and the rear heater 103 from the water-cooled engine 101 via the forward pipe 100a heats the air for air conditioning. The hot water deprived of air by the air-conditioning air flows out of the front heater 102 and the rear heater 103 via the return pipe 100b and returns to the water-cooled engine 101 again.

  However, the forward pipe 100a on the heater inflow side and the return pipe 100b on the heater outflow side are separately arranged separately. For this reason, the degree of freedom of the piping route was low. Moreover, the installation space of these piping 100a, 100b for heating was large, and the installation space of the other member was tightened. That is, there is a problem that the layout property is low.

  Further, the forward pipe 100a on the heater inflow side is barely arranged. For this reason, the heat loss from the forward pipe 100a was large. In other words, the temperature of the hot water has dropped significantly before the front heater 102 and the rear heater 103 flow in. This tendency was particularly remarkable in the forward pipe 100a on the side of the rear heater 103 having a long pipe length. Similarly, the return pipe 100b has a problem of large heat loss.

  Further, depending on the vehicle model, the forward pipe 100a and the return pipe 100b may be arranged at the bottom of the vehicle. That is, these pipes 100a and 100b are exposed to the outside of the vehicle, and in this case, the hot water temperature in the forward pipe 100a and the return pipe 100b is greatly increased in combination with the cooling effect by the airflow during vehicle travel. It will drop to.

  Here, in order to suppress the temperature drop of the hot water, it is conceivable to cover the forward pipe 100a and the return pipe 100b with a heat retaining member. However, even in the present situation, the number of parts increases further and the assembly work becomes more complicated. There is a problem.

  Accordingly, an object of the present invention is to take the above-mentioned points into consideration, and by configuring the outer peripheral surface of the forward pipe so as to be adjacent to the return pipe, the layout property is high and the heat loss of the forward pipe and the return pipe is reduced. It is in providing the piping for heating which can aim at reduction.

  In order to achieve the above object, the technical means according to claims 1 to 11 are employed. That is, in the first aspect of the invention, the forward pipe is connected between the heat source device (90) and the heating means (91, 92) for heating the air and allows the heat medium to flow into the heating means (91, 92). (10) and a heating pipe comprising a return pipe (11) for allowing the heat medium flowing out from the heating means (91, 92) to flow into the heat source device (90), wherein the forward pipe (10) and the return pipe ( And 11) are integrally configured so as to be adjacent to each other.

  According to the first aspect of the present invention, the heat medium flowing through the forward pipe (10) is higher than the outside air temperature. For this reason, the temperature difference between the heat medium flowing through the forward pipe (10) and the heat medium flowing through the return pipe (11) is smaller than the temperature difference between the outside air temperature and the heat medium flowing through the return pipe (11). Therefore, in the present invention, the forward pipe (10) and the return pipe (11) are integrated so as to be adjacent to each other, so that the forward pipe (10 ) And the return heat from the return pipe (11). Thereby, it becomes possible to make small the temperature fall width by the side of an outgoing pipe (10).

  Further, since the forward pipe (10) and the return pipe (11) are integrally formed, the forward pipe (10) and the return pipe (11) are installed as compared with the case where they are separately arranged separately. Less space is required. For this reason, the installation space of other members is not tightened. Moreover, since the degree of freedom of the piping route is high, the layout is high.

  The invention according to claim 2 is characterized in that the forward pipe (10) is arranged on the inner peripheral side of the return pipe (11). According to the second aspect of the present invention, the forward pipe (10) is arranged on the inner peripheral side of the return pipe (11), and specifically, a double pipe structure is formed. Since the forward pipe (10) on the higher temperature side is blocked by the outside air and covered with the return pipe (11), particularly, heat loss from the forward pipe (10) to the return pipe (11) can be reduced.

  The invention according to claim 3 is characterized in that the forward pipe (10) is arranged on the inner peripheral side of the return pipe (11) via a heat insulating layer (15). According to the invention described in claim 3, since the heat exchange inside the forward pipe (10) and the return pipe (11) is suppressed, the forward pipe ( The heat loss from 10) to the return pipe (11) can be reduced.

  In the invention according to claim 4, the forward pipe (10) and the return pipe (11) are formed so that the cross section of the passage is substantially circular, and the forward pipe (10) and the return pipe (11) are substantially coaxial. It is characterized by comprising the above double pipe structure. According to the fourth aspect of the invention, the heat retaining effect of the return pipe (10) by the return pipe (11) can be made substantially uniform over the outer periphery of the forward pipe (10).

  Further, since the forward pipe (10) and the return pipe (11) are constituted by a coaxial double pipe structure, the forward pipe (10) and the return pipe (10) are compared with the case where they are individually arranged separately. The installation space with the pipe (11) may be smaller. For this reason, the installation space of other members is not tightened. Moreover, since the degree of freedom of the piping route is high, the layout is higher.

  The invention according to claim 5 is characterized in that the forward pipe (10) is formed of a material having a lower thermal conductivity than the return pipe (11). According to the invention described in claim 5, if the return pipe (11) disposed on the outer peripheral side of the forward pipe (10) is, for example, an aluminum material, the forward pipe (10) is more thermally conductive. By reducing the rate, the heat loss from the forward pipe (10) to the return pipe (11) can be reduced.

  In the invention according to claim 6, the return pipe (11) is provided with a rib portion (12) extending radially outward at one or a plurality of positions in the circumferential direction of the forward pipe (10). It is characterized by. According to the sixth aspect of the present invention, the forward pipe (10) that is the inner pipe can be held by the rib portion (12) by the return pipe (11) that is the outer pipe. In addition, the arrangement | positioning of the going pipe (10) with respect to a return pipe (11) is stabilized by increasing the number of rib parts (12).

  In the invention according to claim 7, the forward pipe (10) and the return pipe (11) are formed so that the cross section of the passage is formed in a substantially circular shape, and the partition wall (13) that divides the passage into two or four. ) Is formed, and the forward pipe (10) is arranged in one of the two or four divided passages, and the return pipe (11) is arranged in the other.

  According to the invention described in claim 7, in the above-described claims 1 to 6, the forward pipe (10) and the return pipe (11) are configured in a double pipe structure, but not limited thereto, The forward pipe (10) and the return pipe (11) may be partitioned by a partition wall (13) and may be adjacent to each other by the partition wall (13). According to this, compared with the case where it arrange | positions separately by the conventional each separately, the thermal radiation surface radiated | emitted by the external air of an outgoing pipe (10) and a return pipe (11) can be decreased.

  In addition, since the heat exchange area of a partition wall (13) is smaller than the said double pipe structure, an internal heat exchange amount can be suppressed. That is, the heater performance can be expected to be improved by reducing the temperature drop width on the forward pipe (10) side.

  In addition, according to the configuration of the present invention, the wet diameter is smaller than that of the double tube structure, so that the pressure loss is small and the tube diameter can be reduced. Thereby, installation space may be less than a double tube structure. For this reason, the installation space of other members is not tightened. In addition, since the degree of freedom of the piping route is high, layout is high. Furthermore, since the partition wall (13) is larger in the four sections than in the two sections, heat loss can be reduced. Further, the pressure loss can be reduced in the two compartments compared to the four compartments.

  The invention according to claim 8 is characterized in that the partition wall (13) has a heat insulating layer (15) formed therein. The internal heat exchange between the forward pipe (10) and the return pipe (11) is suppressed, so that the forward pipe (10) to the return pipe (11) is the same as in the third aspect. Reduction of heat loss can be achieved.

  The invention according to claim 9 is characterized in that the forward pipe (10) and the return pipe (11) have a passage area configured so that the pressure loss ratio is about 1: 1. According to the ninth aspect of the invention, when the pressure loss ratio is about 1: 1, the water supply performance is improved as compared with the heating pipe having an equivalent area ratio of about 1: 1. It becomes.

  In the invention according to claim 10, when the forward pipe (10) and the return pipe (11) are configured with a double pipe structure, the return pipe (11) is smaller than the passage area of the forward pipe (10). The passage area is about 1.8 to about 2.05 times. More specifically, according to the invention described in claim 10, if the return pipe (11) has a passage area of about 1.8 to about 2.05 times that of the forward pipe (10), power saving can be obtained. be able to.

  The invention according to claim 11 is characterized in that the heat source device (90) is a water-cooled engine (90) for a vehicle, and the heat medium is engine cooling water. According to the eleventh aspect of the present invention, according to the vehicle heating apparatus in which the heating means (91, 92) is installed in the vehicle interior, the forward pipe (10) and the return pipe (11) are located outside the vehicle compartment. Since the outgoing pipe (10) is placed in contact with the return pipe (11) without being brought into contact with outside air, heat loss on the outgoing pipe (10) side can be reduced. This is suitable for use in a vehicle heating device.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of embodiment mentioned later.

(First embodiment)
Hereinafter, the heating pipe in the first embodiment of the present invention will be described with reference to FIGS. 1 to 4. FIG. 1 is an example in which the heating pipe of the present invention is applied to a vehicle heating apparatus, and is a schematic view showing the overall configuration of the vehicle heating apparatus, and FIG. 2 is a heating pipe 1 in the first embodiment of the present invention. It is a longitudinal cross-sectional view which shows the structure. FIG. 3 is a longitudinal sectional view showing the configuration of the heating pipe 1 in a modification of the first embodiment.

  First, as shown in FIG. 1, the vehicle heating device includes a water-cooled engine 90 that is a heat source means, a front heater 91 that is a heating means disposed in the passenger compartment, and a heating pipe 1 that connects them. Has been. As is well known, the water-cooled engine 90 is a liquid-cooled internal combustion engine for vehicle travel, and engine cooling water (hereinafter referred to as hot water) that is a heat medium flows out. The front heater 91 is a heating unit that heats the vehicle interior by heating conditioned air that is blown into the vehicle interior using hot water from the water-cooled engine 90 as a heat source.

  The heating pipe 1 of this embodiment is connected between the water-cooled engine 90 and the front heater 91 via heater hoses 3a to 3d and a joint 2a. The heating pipe 1 includes an outward pipe 10 that allows warm water to flow into the front heater 91 and a return pipe 11 that returns the warm water flowing out from the front heater 91 to the water-cooled engine 90.

  Specifically, as shown in FIG. 2, the cross section of the passage through which the hot water flows is formed in a substantially circular shape, and the forward pipe 10 and the return pipe 11 are arranged on the inner peripheral side and are substantially coaxial. It is configured as a single unit so as to have a double tube structure. That is, the forward pipe 10 and the return pipe 11 are configured to be adjacent to each other. Reference numeral 12 shown in the drawing is a rib portion for holding the inner periphery side forward pipe 10 with the return pipe 11. In this embodiment, the forward pipe 10 is provided at two locations in the circumferential direction of the forward pipe 10. 10 are formed integrally so as to extend outward in the radial direction. Therefore, the passage of the return pipe 11 is divided into two by the rib portion 12.

  In the present embodiment, the rib portions 12 provided on the return pipe 11 are provided at two locations with respect to the circumferential direction of the forward pipe 10, but the present invention is not limited to this, and FIG. 3 (a) and FIG. 3 (b). And as shown in FIG.3 (c), you may provide the rib part 12 in one place or multiple places (3 pieces, 4 pieces). Thereby, the holding | maintenance of the going-out pipe | tube 10 is stabilized, so that the number of the rib parts 12 increases.

  Here, in the heating pipe 1 of the present embodiment, the passage area ratio between the forward pipe 10 and the return pipe 11 is determined and formed such that the pressure loss ratio is 1: 1. That is, in the double pipe structure, when the passage area ratio between the forward pipe 10 and the return pipe 11 is formed at 1: 1, the return length of the return pipe 11 contacts the pipe wall more than the forward pipe 10. As the wetting tab length increases, the pressure loss in the return pipe 11 becomes larger in the return pipe 11 than in the forward pipe 10, so that the pressure loss ratio of the return pipe 11 and the forward pipe 10 is 1: 1. The ratio is formed.

  Therefore, the area ratio is obtained from the characteristic diagram shown in FIG. FIG. 4 is a characteristic diagram showing the relationship between the pressure loss ratio between the forward pipe 10 and the return pipe 11 and the area ratio between the forward pipe 10 and the return pipe 11 in the double pipe structure. Incidentally, the parameters indicating the types of pipes shown in the figure are obtained by changing the pipe length and pipe diameter. For example, in the case of 10 mmφ28, the pipe length is 10 mm, the pipe diameter is 28 mm, and 10 mmD1 In this case, the pipe length is 10 mm and the pipe diameter is 1 inch (25.4 mm). Therefore, the relationship between the pressure loss ratio and the area ratio of each type is obtained using six types as parameters.

  Therefore, more preferably, the area ratio is about 1.95 when the pressure loss ratio is about 1: 1. That is, if the heating pipe 1 is formed so that the return pipe 11 side has a passage area that is about 1.95 times the passage area of the forward pipe 10, a pressure loss ratio of 1: 1 can be obtained. Preferably, considering the variation range of the pressure loss ratio, for example, if the pressure loss ratio is in the range of about 0.7 to 1.3, the area ratio is about 1.8 to 2.05 times. desirable.

  Further, the heating pipe 1 having the above shape is formed into a long cylindrical shape by, for example, extrusion processing made of an aluminum material, and a separate joint 2 a is connected to the end of the heating pipe 1. ing. Here, the joint 2a is a molded product made of a resin material (for example, made of PA66), and a connecting portion is linearly formed so that the forward pipe 10 is connected to the heater hoses 3a and 3b, and a return pipe is formed. A connecting member is formed by crossing about 90 degrees with respect to the axis of the heating pipe 1 so that 11 is connected to the heater hoses 3c and 3d.

  The joint 2a and the heater hoses 3a to 3d are fixed by a hose clamp (not shown). Each of the heater hoses 3a, 3b, 3c, and 3d is formed of a rubber material reinforced with PA (polyamide) fibers, and each end is press-fitted with the joint 2a, the water-cooled engine 90, and the front heater 91. It is connected.

  Next, the flow of hot water in this embodiment will be described. The warm water flowing out from the water-cooled engine 90 is heated to the front heater via the heater hose 3a → the inner peripheral chamber (not shown) of the joint 2a → the forward pipe 10 → the inner peripheral chamber (not shown) of the joint 2a → the heater hose 3b. 91. The hot water flowing into the front heater 91 heats the air for air conditioning. The hot water deprived of the air for air conditioning passes through the heater hose 3d → the outer peripheral chamber of the joint 2a (not shown) → the return pipe 11 → the outer peripheral chamber of the joint 2a (not shown) → the heater hose 3c. It is returned to the water-cooled engine 90 again. In this way, the hot water circulates between the water-cooled engine 90 and the front heater 91.

  Therefore, in the heating pipe 1 having the double pipe structure according to the present embodiment, since the forward pipe 10 having a high hot water temperature is covered with the return pipe 11, the heat loss of the forward pipe 10 can be reduced. Therefore, the temperature drop width on the forward pipe 10 side can be reduced. Further, since the passage area between the forward pipe 10 and the return pipe 11 is formed at an area ratio with a pressure loss ratio of 1: 1, water supply performance is improved as compared with a heating pipe having the same area ratio. Power saving.

  According to the heating pipe 1 according to the first embodiment described above, the hot water flowing through the forward pipe 10 is higher than the outside air temperature. For this reason, the temperature difference between the warm water flowing through the forward pipe 10 and the warm water flowing through the return pipe 11 is smaller than the temperature difference between the outside air temperature and the warm water flowing through the return pipe 11. Therefore, in the present invention, the forward pipe 10 is disposed on the inner peripheral side of the return pipe 11, so that the heat loss on the forward pipe 10 side is particularly greater than in the case where each of the conventional pipes is separately disposed separately. Becomes smaller. That is, it is possible to reduce the temperature drop width on the forward tube 10 side.

  In addition, since the forward pipe 10 and the return pipe 11 are integrated so as to be adjacent to each other, the installation space for the forward pipe 10 and the return pipe 11 is small as compared with the case where they are individually arranged separately. Good. For this reason, the installation space of other members is not tightened. Moreover, since the degree of freedom of the piping route is high, the layout is high.

  In addition, since the forward pipe 10 and the return pipe 11 are configured in a substantially coaxial double pipe structure, the heat retaining effect of the forward pipe 10 by the return pipe 11 is substantially uniform over the outer periphery of the forward pipe 10. Can do. Further, the return pipe 11 is provided with a rib portion 12 extending radially outward at one or a plurality of locations in the circumferential direction of the forward pipe 10, so that the forward pipe 10 that is an inner pipe is an outer pipe. A certain return pipe 11 can be held by the rib portion 12. In addition, the arrangement | positioning of the going pipe 10 with respect to the return pipe 11 is stabilized by increasing the number of the rib parts 12. FIG.

  Further, if the forward pipe 10 and the return pipe 11 have a passage area such that the pressure loss ratio is about 1: 1, for example, the return pipe 11 is 1.95 relative to the forward pipe 10 passage area. Since it is about double, the water supply performance is improved as compared with the double pipe structure in which the area ratio is set to be equal to 1: 1. Considering the variation range of the pressure loss ratio, for example, if the pressure loss ratio is in the range of about 0.7 to 1.3, the area ratio is preferably about 1.8 to 2.05 times.

  In addition, since the forward pipe 10 and the return pipe 11 are provided between the water-cooled engine 90 and the front heater 91, the forward pipe 10 is routed to the return pipe 11 without being in contact with the outside air. By making it adjoin, the heat loss by the forward tube 10 side can be made small. Thereby, the piping 1 for heating is suitable for using for a vehicle heating device.

(Second Embodiment)
In the first embodiment described above, the double pipe structure in which the forward pipe 10 is arranged on the inner peripheral side of the return pipe 11 is used. However, the present invention is not limited to this, and is shown in FIGS. 5 (a) and 5 (b). As shown in the figure, the cross section of the passage is formed in a substantially circular shape, and a partition wall 13 that partitions the passage into two or four is formed, and the forward pipe 10 is formed in one of the two or four sections. The return pipe 11 may be arranged on the other side.

  Specifically, FIG. 5 (a) shows a case in which the area ratio is obtained so that the pressure loss between the forward pipe 10 and the return pipe 11 is 1: 1 and is divided into two chambers by the partition wall 13. In FIG. 5B, similarly, the chamber is partitioned into four chambers by the partition wall 13, and the forward tube 10 is disposed in one of the four chambers, and the return tube 11 is disposed in the other.

  Here, when hot water and cold water are compared, the viscosity of hot water is smaller than that of cold water. Therefore, in order to reduce the pressure loss to 1: 1, it is better to slightly increase the area of the hot water. That is, in FIG. 5A, it is preferable to flow hot water through the forward pipe 10 and cold water through the return pipe 11. Further, since heat performance is reduced by exchanging heat between warm water and cold water, it is preferable to flow warm water through the forward pipe 10 and cold water through the return pipe 11 in FIG. That is, the side-by-side arrangement is preferable to the opposed arrangement.

  According to this, compared with the case where it arrange | positions separately by the conventional each separately, the thermal radiation surface thermally radiated by the outside air of the going pipe 10 and the return pipe 11 can be decreased. Therefore, heat loss from the forward pipe 10 and the return pipe 11 can be reduced. 2 and 3, the heating pipe 1 having a double-pipe structure has a large amount of internal heat exchange between hot water and cold water, but is divided by the partition wall 13 as shown in FIGS. 5 (a) and 5 (b). In the present embodiment having the shape shown in FIG. 2, the amount of internal heat exchange can be suppressed because the heat exchange area is small. That is, it is possible to improve the heater performance by reducing the temperature drop width on the forward pipe 10 side.

  In addition, according to the configuration of the present embodiment, the wet diameter is smaller than that of the double pipe structure, so that the pipe diameter can be reduced because the pressure loss is small. Thereby, installation space may be less than a double tube structure. For this reason, the installation space of other members is not tightened. In addition, since the degree of freedom of the piping route is high, layout is high. Furthermore, since the heat radiation surface of the partition wall 13 is larger in the four sections than in the two sections, the heat loss can be reduced. Further, the pressure loss can be reduced in the two compartments compared to the four compartments.

(Third embodiment)
In this embodiment, the forward pipe 10 is arranged on the inner peripheral side of the return pipe 11 via a heat insulating layer. Specifically, as shown in FIG. A heat insulating layer 15 is formed at a portion where the inner periphery of the return pipe 11 is adjacent to each other, and is configured integrally. For example, the heat insulating layer 15 is provided with any one of an air layer, a vacuum layer, and a heat insulating material. According to this, the heat loss from the forward pipe 10 to the return pipe 11 is less than in the first embodiment by suppressing the heat exchange inside the forward pipe 10 and the return pipe 11 having a high hot water temperature. Can be reduced.

  Further, in the heating pipe 1 according to the second embodiment in which the forward pipe 10 and the return pipe 11 are partitioned by the partition wall 13, as shown in FIG. 6B, a heat insulating layer 15 is formed inside the partition wall 13. In addition, for example, any one of an air layer, a vacuum layer, a heat insulating material, and the like may be disposed on the heat insulating layer 15. According to this, the heat loss from the forward pipe 10 to the return pipe 11 can be reduced as compared with the first embodiment, as in FIG.

(Fourth embodiment)
In the above embodiment, the heating pipe 1 is integrally formed by, for example, an extrusion process made of an aluminum material. However, the present invention is not limited to this, and the return pipe 11 and the forward pipe 10 are formed from separate materials. May be. Specifically, as shown in FIG. 7, if the return pipe 11 arranged on the outside is made of, for example, an aluminum material, the forward pipe 10 arranged on the inner peripheral side of the return pipe 11 has a higher thermal conductivity than the aluminum material. You may form with a small material.

  However, the forward pipe 10 disposed on the inner peripheral side of the return pipe 11 is preferably made of a material having a low thermal conductivity. However, the outer pipe 10 arranged on the outer peripheral side of the forward pipe 10 may have an outer diameter or a plate thickness. The amount of heat dissipated in is not constant. Furthermore, the amount of heat exchange from the forward pipe 10 to the return pipe 11 is not constant due to the outer diameter and thickness of the forward pipe 10.

  Incidentally, if the return pipe 11 is formed of an aluminum material, examples of the material having a lower thermal conductivity include ceramics, ceramics such as magnetism, glasses such as quartz glass and glass ceramics, natural rubber, and silicon rubber. Rubbers, plastics resins such as polyethylene, silicon, and polypropylene, rocks, soil, limes, bricks, concretes, woods, and various heat insulating materials such as rigid urethane foam and glass wool are suitable. .

  According to the heating pipe 1 of the fourth embodiment described above, the forward pipe 10 disposed on the inner peripheral side of the return pipe 11 is formed of a material having a lower thermal conductivity than the return pipe 11, thereby By suppressing the internal heat exchange between the high forward pipe 10 and the return pipe 11, heat loss from the forward pipe 10 to the return pipe 11 can be reduced as compared with the first embodiment. Further, by manufacturing the forward pipe 10 and the return pipe 11 separately, terminal processing or spinning (squeezing) processing of the respective pipes 10 and 11 can be performed in the same manner as the conventional product.

(Other embodiments)
In the above embodiment, the present invention is applied to the piping for heating connected between the water-cooled engine 90 that is the heat source means and the front heater 91 that is the heating means disposed in the vehicle interior. Instead, as shown in FIG. 8, the present invention may be applied to a heating pipe connected between a rear heater 92 that is a heating means installed at the rear of the vehicle interior.

  In the figure, reference numerals 4 and 5 denote branch pipes, and a front heater 91 and a rear heater 92 are connected in parallel to the forward pipe 10 and the return pipe 11. 3e-3g is a heater hose, and each end part is connected by press-fitting like the heater hoses 3a-3d. Of the reference numerals shown in the figure, the same components as those in the first embodiment are indicated by the same reference numerals and the description thereof is omitted. According to the above configuration, since the heating pipe 1 becomes longer and is arranged at the bottom of the vehicle, the effect of the present invention for reducing heat loss is great.

  In the above embodiment, the present invention is applied to a vehicle heating apparatus using the water-cooled engine 90 as a heat source means as a heat source. However, the present invention is not limited to this, and a fuel cell is mounted as the heat source means. You may use for the heating apparatus which heats a vehicle using the cooling water for cooling a fuel cell.

It is a schematic diagram which shows the whole structure of the heating apparatus for vehicles to which this invention is applied. It is a longitudinal cross-sectional view which shows the structure of the piping 1 for heating in 1st Embodiment of this invention. (A), (b), and (c) are longitudinal cross-sectional views which show the structure of the piping 1 for heating in the modification of 1st Embodiment. It is a characteristic view which shows the relationship between the pressure loss ratio and area ratio for calculating | requiring the area ratio of the forward pipe 10 and the return pipe 11 in 1st Embodiment of this invention. (A) And (b) is a longitudinal cross-sectional view which shows the structure of the piping 1 for heating in 2nd Embodiment of this invention. (A) And (b) is a longitudinal cross-sectional view which shows the structure of the piping 1 for heating in 3rd Embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the piping 1 for heating in 4th Embodiment of this invention. It is a schematic diagram which shows the whole structure of the heating apparatus for vehicles to which this invention in other embodiment is applied. It is a schematic diagram which shows the whole structure of the heating apparatus for vehicles in a prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Outward pipe 11 ... Return pipe 12 ... Rib part 13 ... Partition wall 15 ... Heat insulation layer 90 ... Water-cooled engine (heat source apparatus)
91 ... Front heater (heating means)
92 ... Rear heater (heating means)

Claims (11)

Connected between the heat source device (90) and the heating means (91, 92) for heating the air, the forward pipe (10) for flowing a heat medium into the heating means (91, 92) and the heating means (91, 92) 92) a heating pipe comprising a return pipe (11) for allowing the heat medium flowing out from the heat source apparatus (90) to flow into the heat source apparatus,
A heating pipe characterized in that the forward pipe (10) and the return pipe (11) are integrally formed so as to be adjacent to each other.   The heating pipe according to claim 1, wherein the forward pipe (10) is arranged on an inner peripheral side of the return pipe (11).   The heating pipe according to claim 2, wherein the forward pipe (10) is disposed on an inner peripheral side of the return pipe (11) via a heat insulating layer (15).   The forward pipe (10) and the return pipe (11) have a substantially circular passage cross section, and the forward pipe (10) and the return pipe (11) are substantially coaxial. The heating pipe according to any one of claims 1 to 3, wherein the heating pipe has a structure.   The heating pipe according to claim 4, wherein the forward pipe (10) is made of a material having a lower thermal conductivity than the return pipe (11).   The return pipe (11) is provided with a rib portion (12) extending radially outward at one or a plurality of locations in the circumferential direction of the forward pipe (10). The piping for heating as described in any one of thru | or 4.   The forward pipe (10) and the return pipe (11) are formed so that a cross section of the passage is formed in a substantially circular shape, and a partition wall (13) that divides the passage into two or four is formed. The heating pipe according to claim 1, wherein the forward pipe (10) is disposed in one of the four passages, and the return pipe (11) is disposed in the other passage.   The piping for heating according to claim 7, wherein the partition wall (13) has a heat insulating layer (15) formed therein.   9. The passage area according to claim 1, wherein the forward pipe (10) and the return pipe (11) form a passage area so that a pressure loss ratio is about 1: 1. The piping for heating according to one item.   When the forward pipe (10) and the return pipe (11) have a double-pipe structure, the return pipe (11) is approximately 1. with respect to the passage area of the forward pipe (10). The heating pipe according to claim 9, wherein the passage area is 8 to about 2.05 times.   The said heat-source apparatus (90) is a water-cooled engine (90) for vehicles, Comprising: The said heat medium is engine cooling water, The cooling water according to any one of Claim 1 thru | or 10 characterized by the above-mentioned. Piping for heating.

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