JP2007186035A - Air conditioning device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To miniaturize a piping connecting structure for heat source fluid input and output and to improve installing work efficiency and an arranging property of outside fluid piping while preventing a rise in cold air temperature caused by the heat radiation of a rotary heating heat exchanger at maximum cooling. <P>SOLUTION: This air conditioning device to adjust a blow-out air temperature by changing a rotating position of the heat exchanger for heating is constituted by constituting piping forming inlet channels 26a, 33a to make a heat source fluid flow into the heat exchanger 15 for heating 15 and piping forming output channels 25a, 32a to make the heat source fluid flow out of the heat exchanger 15 for heating of a coaxial double piping structure 16, constituting the heat exchanger 15 for heating free to rotate around a central axis ○ of the coaxial double piping structure 16 and constituting an inlet channel opening and closing mechanism 39 to close the inlet channels 26a, 33a when the heat exchanger 15 for heating is operated to rotate to a maximum cooling position on the coaxial double piping structure 16. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an air conditioner that has a rotary heating heat exchanger as an air heating means and adjusts the blown air temperature by adjusting the rotational position of the rotary heating heat exchanger. Is suitable.

  Conventionally, as a temperature adjustment method for a vehicle air conditioner, an air mix type in which the air volume ratio between cold air and hot air is adjusted by an air mix door to adjust the temperature of air blown into the vehicle interior is typical.

  In this air mix type vehicle air conditioner, the hot water heating heat exchanger itself is configured to be rotatable so that the hot water heating heat exchanger also serves as an air mix door. The door can be abolished, and at the time of maximum cooling, the hot water heating heat exchanger can be rotated to a position that does not provide resistance to the flow of cold air, that is, to the side of the cold air flow passage so that the amount of cold air can be increased. Has been proposed (see, for example, Patent Document 1 and Patent Document 2).

  By the way, even if the hot water heating heat exchanger is rotated to the side position of the cold air flow passage during maximum cooling, if the hot water still flows through the hot water heating heat exchanger, the hot water heating heat exchanger Since the cold air temperature rises due to heat dissipation from the air, the maximum cooling performance is reduced.

  Therefore, in Patent Document 1 and Patent Document 2, a rotating-side hot water flow path unit integrated with a hot water heating heat exchanger and a fixed-side hot water flow path in which the rotating-side hot water flow path unit is rotatably fitted. A hot water flow blocking mechanism configured to block the hot water flow channel when the hot water heating heat exchanger is rotated to the maximum cooling position is provided in the hot water flow channel mechanism including the unit.

  In addition, the applicant of the present application previously described in Japanese Patent Application No. 2004-201770 (hereinafter referred to as the prior application example), a rotating-side hot water flow path unit integrated with a hot water heating heat exchanger, and this rotation When the hot water heating heat exchanger is rotated to the maximum cooling position, the hot water inlet / outlet portion is moved to the hot water flow passage mechanism that is composed of the fixed hot water flow passage portion in which the side hot water flow passage portion is rotatably fitted. It has been proposed to provide a bypass passage mechanism that communicates directly with each other.

  In this prior application example, the hot water flowing into the hot water inlet at the time of maximum cooling flows through the bypass passage mechanism and is directly guided to the hot water outlet, so that it is possible to suppress the hot water from flowing into the hot water heating heat exchanger.

In the prior application example, the hot water inlet pipe is configured as an outer pipe having a coaxial double pipe structure, and the hot water outlet pipe is configured as an inner pipe having a coaxial double pipe structure. The inner pipe is composed of an inner rotary pipe and an inner fixed pipe, and the inner rotary pipe is rotatably fitted on the outer peripheral side of the inner fixed pipe.
JP 2001-47845 A Japanese Patent Laid-Open No. 2001-246922

  In the former Patent Document 1, the hot water inlet pipe and the hot water outlet pipe are arranged at a predetermined distance in the radial direction of the fixed side disk-shaped member and the rotary side disk-shaped member. There is a problem that the diameter is inevitably increased.

  In the latter Patent Document 2, since the hot water inlet pipe and the hot water outlet pipe protrude in opposite directions from the hot water inlet tank and the hot water outlet tank of the heating heat exchanger, respectively, a fixed side is provided on each side of the heating heat exchanger. It is necessary to perform connection work between the piping and the rotation side piping, which deteriorates the assembly workability. Moreover, since the hot water inlet pipe and the hot water outlet pipe are protruded in opposite directions, the manageability of the hot water pipe is also deteriorated.

  On the other hand, in the prior application example, the hot water inlet pipe and the hot water outlet pipe are constituted by a coaxial double pipe structure. For this reason, the outer diameter of the coaxial double pipe structure can be reduced, and the connection work between the fixed side pipe and the rotary side pipe can be performed in one place, so that the assembly workability is good. The hot water piping is also easy to handle.

  However, the bypass passage mechanism in the prior application example does not actively block the hot water flow to the heating heat exchanger during maximum cooling. For this reason, in a prior application example, since a part of warm water flows into the heat exchanger for heating at the time of maximum cooling, there exists a problem that cold air temperature will rise to some extent at the time of maximum cooling.

  In the prior application example, since the inner rotary pipe is rotatably fitted to the outer peripheral side of the inner fixed pipe, the inlet-side hot water flow (hot water flow in the outer pipe) directly hits the tip of the inner rotary pipe. End up. For this reason, since the front-end | tip part of inner side rotation piping receives the dynamic pressure of warm water directly, there exists a possibility that a warm water leak may generate | occur | produce between the front-end | tip part of inner side rotation piping, and the outer peripheral surface of inner side fixed piping.

  Therefore, it is conceivable to use an elastic sealing material such as an O-ring as a sealing mechanism for the fitting portion between the inner rotating pipe and the inner fixed pipe. However, if an elastic sealing material is used for the fitting portion, sliding frictional force may be used. Therefore, there is a problem that the rotational operation force of the hot water heating heat exchanger increases.

  In view of the above points, the present invention prevents downsizing of the cold air temperature due to heat radiation of the rotary heating heat exchanger during maximum cooling, while reducing the size of the heat source fluid input / output pipe connection structure such as hot water, and the external fluid piping. The purpose is to improve assembly workability and handling.

  In addition, in view of the above points, the present invention provides a heat source fluid in a fitting portion between an inner rotary pipe and an inner fixed pipe of a coaxial double pipe structure while suppressing an increase in rotational operation force of the rotary heating heat exchanger. Another purpose is to suppress leakage.

In order to achieve the above object, the present invention provides an air conditioning case (11) through which air flows,
A heating heat exchanger (15) that is rotatably arranged in the air conditioning case (11) and heats the air in the air conditioning case (11);
By changing the rotational position of the heating heat exchanger (15), the air volume ratio between the hot air passing through the heating heat exchanger (15) and the cold air bypassing the heating heat exchanger (15) is adjusted. In the air conditioner that adjusts the blown air temperature,
A pipe forming an inlet channel (26a, 33a) for allowing the heat source fluid to flow into the heating heat exchanger (15) and an outlet channel (25a, 32a) for allowing the heat source fluid to flow out from the heating heat exchanger (15). The eggplant pipe is constructed with a coaxial double pipe structure (16),
The heating heat exchanger (15) is configured to be rotatable around the central axis (O) of the coaxial double pipe structure (16), and
When the heating heat exchanger (15) is rotated to the maximum cooling position, the inlet channel opening / closing mechanism (39) that closes the inlet channel (26a, 33a) is configured in the coaxial double pipe structure (16),
When the heating heat exchanger (15) is rotated from the maximum cooling position to the maximum heating position, the inlet channel opening / closing mechanism (39) changes in the direction to open the inlet channels (26a, 33a). One feature.

  According to this, since the pipe connection structure for heat source fluid input / output of the rotary heating heat exchanger is constituted by the coaxial double pipe structure (16), the pipe connection structure can be formed into a compact body with a small outer diameter. In addition, the workability of pipe connection and the handling of external fluid pipes can be improved.

  Further, when the heating heat exchanger (15) is rotated to the maximum cooling position, the inlet channel opening / closing mechanism (39) for closing the inlet channel (26a, 33a) is configured in the coaxial double pipe structure (16). Therefore, during the maximum cooling, the flow of hot water to the heating heat exchanger (15) is blocked, and the inflow of hot water to the heating heat exchanger (15) is blocked.

  For this reason, since the heat of the hot water is not released into the air flow from the heating heat exchanger (15) during the maximum cooling, it is possible to prevent an increase in the cold air temperature due to the heat radiation of the heating heat exchanger (15) during the maximum cooling. .

  On the other hand, when the heating heat exchanger (15) is rotated from the maximum cooling position to the maximum heating position, the inlet channel opening / closing mechanism (39) changes in a direction to open the inlet channels (26a, 33a). Therefore, during maximum heating and temperature control (when rotating to the intermediate rotation position between the maximum cooling position and the maximum heating position), the flow of hot water to the heating heat exchanger (15) is generated, and the heating heat Hot water flows into the exchanger (15).

  For this reason, the air heating effect | action by the heat exchanger (15) for a heating can be exhibited at the time of maximum heating and temperature control.

  Combined with these effects, the heat source fluid input / output piping connection structure can be downsized and the assembly work of the external fluid piping can be performed while preventing the rise of the cold air temperature due to the heat radiation of the rotary heating heat exchanger during maximum cooling. In addition, the handling property can be improved.

Specifically, in the present invention, the inlet channel (26a, 33a) includes a rotation side pipe (33) that rotates integrally with the heating heat exchanger (15), and a fixed connection that communicates with the rotation side pipe (33). Side piping (26),
A wall portion (41) with a rotation side opening having a rotation side opening (41b) closes a part of the inlet channel (26a, 33a) at a portion upstream of the heat source fluid flow in the rotation side pipe (33). Are located in
In the fixed side pipe (26), the fixed side opening wall portion (40) having the fixed side opening portion (40b) is disposed so as to face and closely contact the rotation side opening wall portion (41).
When the heating heat exchanger (15) is at the maximum cooling position, the rotation side opening (41b) is located away from the fixed side opening (40b), and the heating heat exchanger (15) is at the maximum cooling position. The rotation side opening (41b) and the fixed side opening (40b) are formed so that the rotation side opening (41b) overlaps with the fixed side opening (40b) when being rotated from the maximum heating position to the maximum heating position. Has been
The inlet channel opening / closing mechanism (39) includes a rotation-side opening-attached wall portion (41) and a fixed-side opening-attached wall portion (40).

  According to this, when the heat exchanger for heating (15) is at the maximum cooling position, the rotation side opening (41b) is located away from the fixed side opening (40b), so at the time of maximum cooling, the rotation side opening is attached. The inlet channel (26a, 33a) is closed by the wall portion (41) and the fixed-side opening-equipped wall portion (40).

  On the other hand, when the heating heat exchanger (15) is rotated from the maximum cooling position to the maximum heating position side, the rotation side opening (41b) is superposed on the fixed side opening (40b). At the time of temperature control, the inlet channels (26a, 33a) are opened through the rotation side opening (41b) and the fixed side opening (40b).

  Therefore, by the inlet channel opening / closing mechanism (39) composed of the rotation-side opening-equipped wall portion (41) and the fixed-side opening-equipped wall portion (40), the heat from the heating heat exchanger (15) is radiated during maximum cooling. An increase in cold air temperature can be prevented.

  In the present invention, more specifically, the rotation-side opening-attached wall portion (41) and the fixed-side opening-attached wall portion (40) are in close contact via an elastic seal member (42).

  Thereby, since the leakage of the heat source fluid between the wall portion with rotation side opening (41) and the wall portion with opening on the fixed side (40) can be prevented, the wall portion with rotation side opening (41) at the time of maximum cooling. And the fixed opening side wall portion (40) can satisfactorily close the inlet channel (26a, 33a).

  More specifically, if the elastic seal member (42) in the present invention is formed integrally with the rotation-side opening-attached wall (41), the number of parts of the inlet channel opening / closing mechanism (39) can be reduced. As a result, product costs can be reduced.

In the present invention, more specifically, a plurality of the rotation side openings (41b) are provided in the rotation direction of the wall portion with the rotation side opening (41).
A large number of fixed side openings (40b) are provided in correspondence with the rotation side openings (41b).

  According to this, compared with the case where only one rotation side opening (41b) and one fixed side opening (40b) are provided, the rotation side opening when the rotation angle of the heating heat exchanger (15) is small. The overlapping area of the portion (41b) and the fixed side opening (40b) can be increased.

  For this reason, when the rotation angle of the heat exchanger for heating (15) is small, the opening area of the inlet channel opening / closing mechanism (39) can be increased, so the flow rate of the hot water passing through the heater core 15 side hot water passage is reduced. Can be increased.

  In the present invention, more specifically, when the heating heat exchanger (15) is rotated to the maximum heating position, the overlapping area of the rotation side opening (41b) and the fixed side opening (40b) is increased. The rotation side opening (41b) and the fixed side opening (40b) are formed so as to be larger than the area of the outlet channel (25a, 32a).

  Thereby, since it is possible to suppress an increase in fluid resistance by the inlet channel opening / closing mechanism (39) at the maximum heating position, the heat exchanger (15) for heating at the time of maximum heating is provided by providing the inlet channel opening / closing mechanism (39). Generation | occurrence | production of the malfunction that the inside heat source fluid flow volume reduces can be suppressed. For this reason, the air heating effect | action by the heat exchanger (15) for a heating at the time of maximum heating can be exhibited without any trouble.

In the present invention, more specifically, the outer pipe of the coaxial double pipe structure (16) includes an outer rotary pipe (33) that rotates integrally with the heat exchanger for heating (15), and an outer rotary pipe ( 33) and an outer fixed pipe (26) communicating with
The inner pipe of the coaxial double pipe structure (16) includes an inner rotary pipe (32) that rotates integrally with the heating heat exchanger (15), and an inner fixed pipe (25) that communicates with the inner rotary pipe (32). Consists of
The outer rotary pipe (33) constitutes the rotary side pipe,
The outer fixed pipe (26) can constitute a fixed pipe.

  In the present invention, more specifically, the inner rotary pipe (32) is fitted to the inner peripheral side of the inner fixed pipe (25).

  According to this, since the fitting tip (32b) of the inner rotary pipe (32) is located on the outlet flow path (25a, 32a) side, the fitting tip (32b) of the inner rotary pipe (32) is Positioning in the inlet channel (26a, 33a) can be avoided. For this reason, since it can avoid that the fitting front-end | tip part (32b) of inner side rotation piping (32) receives the dynamic pressure of the heat source fluid which flows into an inlet flow path (26a, 33a), fitting of inner side rotation piping (32) is possible. It can suppress that a heat source fluid flows in into the said fitting part from a joint tip part (32b).

  On the other hand, since the fitting tip (25b) of the inner fixed pipe (25) is located on the inlet flow path (26a, 33a) side, the fitting tip (25b) of the inner fixed pipe (25) is connected to the inlet flow. It is located in the road (26a, 33a).

  However, since the fitting tip (25b) of the inner fixed pipe (25) faces the downstream side of the heat source fluid flow in the inlet channel (26a, 33a), the fitting tip (25) of the inner fixed pipe (25) ( It can be avoided that 25b) directly receives the dynamic pressure of the heat source fluid flowing through the inlet channels (26a, 33a). For this reason, it can suppress that a heat source fluid flows in into the said fitting part from the fitting front-end | tip part (25b) of an inner side fixed piping (25).

  As a result, it is possible to prevent the heat source fluid from leaking at the fitting portion between the inner rotating pipe (32) and the inner fixed pipe (25). That is, since the heat source fluid leakage can be suppressed without using an elastic sealing material, the heat source fluid leakage at the fitting portion between the inner rotary pipe and the inner fixed pipe is suppressed while suppressing an increase in rotational operation force. be able to.

  In the present invention, more specifically, the minute gap (35) existing between the outer peripheral surface of the inner rotary pipe (32) and the inner peripheral surface of the inner fixed pipe (25) is 0.3 mm or less. As described above, the outer diameter of the inner rotary pipe (32) and the inner diameter of the inner fixed pipe (25) are set.

  Thereby, it turned out that the heat source fluid leakage can be effectively suppressed in the fitting portion between the inner rotating pipe (32) and the inner fixed pipe (25).

In the present invention, more specifically, the outer fixed pipe (26) is formed with an inlet portion (28) of the coaxial double pipe structure (16).
The inner fixed pipe (25) is formed with an outlet part (30) of the coaxial double pipe structure (16).
The inner fixed pipe (25) is formed with a bypass hole (45) that directly communicates the inlet portion (28) and the outlet portion (30),
The inner rotary pipe (32) has a bypass hole opening / closing part (46) that opens and closes the bypass hole (45) as the heating heat exchanger (15) rotates.
When the heating heat exchanger (15) is rotated to the maximum cooling position, the bypass hole opening / closing part (46) opens the bypass hole (45),
When the heating heat exchanger (15) is rotated from the maximum cooling position to the maximum heating position, the bypass hole opening / closing part (46) changes in a direction to close the bypass hole (45).

  According to this, when the heating heat exchanger (15) is rotated to the maximum cooling position, the bypass hole opening / closing part (46) opens the bypass hole (45), so that the coaxial double pipe is formed by the bypass hole (45). The inlet (28) and outlet (30) of the structure (16) are in direct communication.

  For this reason, when the inlet channel opening / closing mechanism (39) is closed, the heat source fluid flowing into the inlet part (28) does not flow to the inlet channel opening / closing mechanism (39) side but passes through the bypass hole (45) and exits. Since it flows in a short circuit to the section (30) side, it is possible to prevent the heat source fluid from staying in the upstream portion of the coaxial double pipe structure (16) upstream of the inlet channel opening / closing mechanism (39).

  As a result, foreign matter (such as cast sand adhering to the production of the vehicle engine) mixed in the heat source fluid is more upstream of the heat source fluid flow than the inlet channel opening / closing mechanism (39) in the coaxial double pipe structure (16) during maximum cooling. It is possible to avoid the problem of collecting in the side portion and biting into the inlet channel opening / closing mechanism (39).

  In addition, since the heat source fluid is blocked and the pressure of the heat source fluid is prevented from rising when the inlet channel opening / closing mechanism (39) is closed, the coaxial double pipe including the inlet channel opening / closing mechanism (39) The pressure strength of the structure (16) can be reduced, and an increase in product cost can be suppressed.

  On the other hand, when the heating heat exchanger (15) is rotated from the maximum cooling position to the maximum heating position, the bypass hole opening / closing portion (46) changes in a direction to close the bypass hole (45). And the heat source fluid that has flowed into the inlet section (28) during temperature control flows through the heating heat exchanger (15). For this reason, the air heating effect | action by the heat exchanger (15) for a heating can be exhibited at the time of maximum heating and temperature control.

In the present invention, more specifically, the inlet portion (28) is formed on the outer radial direction side of the outer fixed pipe (26),
The bypass hole (45) is formed in a part of the inner fixed pipe (25) opposite to the inlet part (28) with respect to the central axis (O).

  Here, the “site opposite to the inlet portion (28) with respect to the central axis (O)” in the present invention refers to the direction in which the inlet portion (28) is disposed with respect to the central axis (O). When it is taken as a degree, it means a part located in the direction of 90 to 270 degrees.

  According to this, since the bypass hole (45) is formed at a portion of the inner fixed pipe (25) opposite to the inlet portion (28) with respect to the central axis (O), the inlet portion (28). It is possible to avoid the bypass hole (45) from directly receiving the dynamic pressure of the heat source fluid flowing into the outer fixed pipe (26).

  For this reason, when the heat exchanger for heating (15) is rotated to the maximum heating position and the bypass hole (45) is closed, the heat source fluid flows between the bypass hole (45) and the bypass hole opening / closing part (46). Can be prevented from leaking.

  In addition, if the bypass hole (45) in the present invention has a size of an equivalent circular diameter of 3 mm or more, it is possible to prevent fluid noise from being generated in the inlet channel opening / closing mechanism (39) and the bypass hole (45) itself. I understood.

  That is, when the rotation angle of the heat exchanger for heating (15) is a minute angle, in other words, when the opening degree of the inlet channel opening / closing mechanism (39) is a minute opening degree, it passes through the bypass hole (45). The flow of hot water can be increased. For this reason, since the flow rate of the heat source fluid flowing through the inlet channel opening / closing mechanism (39) can be suppressed, it can be seen that fluid noise can be prevented from being generated at the minute opening of the inlet channel opening / closing mechanism (39). It was.

  Further, if the bypass hole (45) is made to have an equivalent circular diameter of 3 mm or more, it is possible to suppress an increase in the flow velocity of the heat source fluid passing through the bypass hole (45). It was found that sound can be prevented from being generated.

More specifically, the present invention includes an inlet throttle mechanism (37) that minimizes the opening of the inlet portion (28) when the heating heat exchanger (15) is rotated to the maximum cooling position. Formed on the outer rotating pipe (33),
The inlet throttle mechanism (37) is configured such that the opening degree increases when the heating heat exchanger (15) is rotated from the maximum cooling position to the maximum heating position.

  According to this, when the heating heat exchanger (15) is rotated to the maximum cooling position, the opening of the inlet portion (28) is minimized by the inlet throttle mechanism (37). 28), the flow rate of the heat source fluid flowing into the coaxial double pipe structure (16) can be suppressed.

  For this reason, when the inlet channel opening / closing mechanism (39) is closed, the heat source fluid is blocked and the pressure of the heat source fluid is prevented from increasing, so that the coaxial double pipe including the inlet channel opening / closing mechanism (39) The pressure strength of the structure (16) can be further reduced, and an increase in product cost can be further suppressed.

  On the other hand, when the heating heat exchanger (15) is rotated from the maximum cooling position to the maximum heating position, the opening degree of the inlet section (28) increases, and therefore the inlet section (28 during the maximum heating and temperature control). ) To increase the flow rate of the heat source fluid flowing into the coaxial double pipe structure (16) as compared with the maximum cooling.

  For this reason, the air heating effect | action by the heat exchanger (15) for a heating can be exhibited without any trouble at the time of maximum heating and temperature control.

  More specifically, according to the present invention, the inlet throttle mechanism (37) is configured such that the opening of the inlet (28) has a size of an equivalent circular diameter of 3 mm or more when the opening degree is minimum. Yes.

  Thereby, since it was possible to suppress an increase in the flow rate of the heat source fluid by the inlet throttle mechanism (37), it was found that fluid noise could be prevented from being generated by the inlet throttle mechanism (37).

The present invention also provides an air conditioning case (11) through which air flows,
A heating heat exchanger (15) that is rotatably arranged in the air conditioning case (11) and heats the air in the air conditioning case (11);
By changing the rotational position of the heating heat exchanger (15), the air volume ratio between the hot air passing through the heating heat exchanger (15) and the cold air bypassing the heating heat exchanger (15) is adjusted. In the air conditioner that adjusts the blown air temperature,
A pipe forming an inlet channel (26a, 33a) for allowing the heat source fluid to flow into the heating heat exchanger (15) and an outlet channel (25a, 32a) for allowing the heat source fluid to flow out from the heating heat exchanger (15). The eggplant pipe is constructed with a coaxial double pipe structure (16),
The heating heat exchanger (15) is configured to be rotatable about the central axis (O) of the coaxial double pipe structure (16),
The inner pipe of the coaxial double pipe structure (16) includes an inner rotary pipe (32) that rotates integrally with the heating heat exchanger (15), and an inner fixed pipe in which the inner rotary pipe (32) is rotatably fitted. (25) and
In the fitting portion between the inner rotary pipe (32) and the inner fixed pipe (25), the inner rotary pipe (32) is positioned on the outlet flow path (25a, 32a) side, and the inner fixed pipe (25) is the inlet flow path. The second feature is that it is located on the (26a, 33a) side.

  According to this, since the inner rotary pipe (32) is located on the outlet channel (25a, 32a) side in the fitting portion between the inner rotary pipe (32) and the inner fixed pipe (25), the inner rotary pipe (32) The fitting tip (32b) can be prevented from being located in the inlet channel (26a, 33a).

  For this reason, since it can avoid that the fitting front-end | tip part (32b) of inner side rotation piping (32) receives the dynamic pressure of the heat source fluid which flows into an inlet flow path (26a, 33a), fitting of inner side rotation piping (32) is possible. It can suppress that a heat source fluid flows in into the said fitting part from a joint tip part (32b).

  On the other hand, since the inner fixed pipe (25) is located on the inlet channel (26a, 33a) side in the fitting portion between the inner rotary pipe (32) and the inner fixed pipe (25), the inner fixed pipe (25) The fitting tip (25b) is located in the inlet channel (26a, 33a).

  However, since the fitting front end (25b) of the inner fixed pipe (25) faces the downstream side of the heat source fluid flow in the inlet channel (26a, 33a), the fitting front end ( It can be avoided that 25b) directly receives the dynamic pressure of the heat source fluid flowing through the inlet channels (26a, 33a). For this reason, it can suppress that a heat source fluid flows in into the said fitting part from the fitting front-end | tip part (25b) of an inner side fixed piping (25).

  As a result, it is possible to prevent the heat source fluid from leaking at the fitting portion between the inner rotating pipe (32) and the inner fixed pipe (25). That is, since the heat source fluid leakage can be suppressed without using an elastic sealing material, an increase in the rotational operation force of the heat exchanger for heating (15) is suppressed, and the inner rotary pipe (32) and the inner fixed pipe ( 25) and the heat source fluid leakage at the fitting portion can be suppressed.

  Specifically, the present invention includes an outer peripheral surface and an outer peripheral side of an inner peripheral side pipe (32) arranged on the inner peripheral side in the fitting portion of the inner rotary pipe (32) and the inner fixed pipe (25). The outer diameter of the inner pipe (32) and the outer pipe (32) so that the minute gap (35) existing between the inner pipe of the outer pipe (25) and the inner pipe is 25 mm or less. 25) is set.

  Thereby, it turned out that it can suppress effectively that a heat source fluid leaks in the fitting part of an inner side rotation piping (32) and an inner side fixed piping (25).

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 shows a schematic cross-sectional view of an indoor air conditioning unit of a vehicle air conditioner equipped with a rotary heating heat exchanger according to the present invention, and FIG. 2 shows a rotary heating heat exchanger and a hot water inlet / outlet coaxial double pipe section. FIG. 3 is a cross-sectional view of the main part showing the maximum heating state of the rotary heating heat exchanger and the coaxial double pipe part for hot water in / out.

  First, the outline of the indoor air conditioning unit 10 of the vehicle air conditioner will be described with reference to FIG. 1. Located in the center. In addition, each arrow before and behind in FIG. 1 shows the direction in a vehicle mounting state. The vertical direction in FIG. 1 is the vehicle left-right (width) direction.

  The indoor air-conditioning unit 10 includes a resin air-conditioning case 11 that forms a passage for air flowing toward the passenger compartment. The air-conditioning case 11 is actually formed as a plurality of divided case bodies for convenience in resin molding, assembly of built-in parts, and the like, and the plurality of divided case bodies are integrated by fastening means such as screws and clips. The air-conditioning case 11 is configured by fastening to.

  And in this embodiment, it is the structure which has arrange | positioned the air blower part 12 integrally in the upper part of the vehicle front side among the air-conditioning cases 11. FIG. The blower unit 12 is configured to rotationally drive a centrifugal blower fan 12a by a motor (not shown). An inside / outside air switching box (not shown) is connected to the suction port of the blower fan 12a, and the introduced air (inside air or outside air) from the inside / outside air switching box is sent from the top to the bottom as indicated by the arrow a by the blower fan 12a. It is designed to blow air toward you.

  An evaporator 13 serving as a heat exchanger for cooling is disposed in a lower portion of the air conditioning case 11 on the front side of the vehicle. Here, the outer shape of the evaporator 13 is a rectangular thin shape, and the entire amount of blown air from the blower unit 12 passes as shown by an arrow b. As is well known, the evaporator 13 is a low pressure side heat exchanger of the vapor compression refrigeration cycle, and cools the passing air by absorbing heat from the passing air indicated by the arrow b and evaporating the low pressure refrigerant.

  A drain port 14 is provided at the lowest part of the bottom surface of the air conditioning case 11, and condensed water generated in the evaporator 13 is drained from the drain port 14 to the outside of the passenger compartment.

  In the air conditioning case 11, a heater core 15 is disposed on the leeward side of the evaporator 13. More specifically, the heater core 15 is disposed on the vehicle rear side of the evaporator 13 and in an upper portion. Here, the heater core 15 is a heat exchanger for heating that heats air using hot water (engine cooling water) from a vehicle engine (not shown) as a heat source fluid.

  The outer shape of the heater core 15 is also a rectangular thin shape, and a coaxial double pipe portion 16 for hot water in / out described later is disposed at one end portion 15a of the rectangular outer shape.

  More specifically, in the present embodiment, the coaxial double pipe portion 16 is coupled to the upper end portion 15a of the heater core 15, and the coaxial double pipe portion 16 extends in the left-right direction of the vehicle (perpendicular to the plane of FIG. 1). The coaxial double pipe portion 16 is disposed in close contact with the upper side wall surface of the air conditioning case 11 on the vehicle front side. Thereby, the heater core 15 is rotatable in the vehicle front-rear direction around the coaxial double pipe portion 16.

  In the example of FIG. 1, the coaxial double pipe portion 16 is disposed adjacent to the rear side of the upper end portion of the evaporator 13. A windshield wall 17 for maximum cooling is integrally formed in the air conditioning case 11 between the evaporator 13 and the heater core 15. The wind shielding wall 17 is formed in a plate shape that hangs vertically from a portion between the upper end portion of the evaporator 13 and the upper end portion of the heater core 15 (end portion on the coaxial double pipe portion 16 side) 15a.

  The plate-shaped wind shielding wall 17 is formed in the entire area inside the air conditioning case 11 with respect to the vehicle left-right direction (the direction perpendicular to the plane of FIG. 1). Coupled to the side wall.

  The plate-shaped wind shielding wall 17 is formed in substantially the same area as the heater core 15 so as to cover the entire windward surface (left side surface in FIG. 1) of the heater core 15. A predetermined gap is set between the lower end portion of the wind shielding wall 17 and the lower end portion 15b of the heater core 15 and the bottom surface portion of the air conditioning case 11, and the air passage 18 on the upper side of the heater core is formed by the predetermined gap. . That is, the air passage 18 is formed in a region on the windward side with respect to the rotation operation region of the heater core 15.

  The heater core 15 is rotated to a broken line position MC along the leeward side surface (the right side surface in FIG. 1) of the wind shielding wall 17 during maximum cooling. In the maximum cooling position MC, the wind shielding wall 17 fully closes the windward surface of the heater core 15 and prevents the air on the leeward side of the evaporator 13 from passing through the core portion of the heater core 15.

  Therefore, the entire amount of the air passing through the evaporator (cold air) flows by bypassing the heater core 15 as shown by the arrow c, so that the maximum cooling performance can be exhibited. For this reason, the air passage 18 on the upper side of the heater core acts as a heater core bypass passage during maximum cooling.

  By the way, in this embodiment, the lower end part (end part on the opposite side to the coaxial double pipe part 16) 15b of the heater core 15 approaches the windward air passage 18 formed on the lower end side of the wind shielding wall 17. The heater core 15 is disposed so that the upper end portion 15a of the heater core 15 (the end portion on the coaxial double pipe portion 16 side) is away from the windward air passage 18, so that the lower end portion 15b of the heater core 15 becomes the windward end portion, The upper end 15a of the heater core 15 is the leeward side end.

  Seal ribs 20 are formed on the leeward side of the heater core 15 on the inner wall surface of the air conditioning case 11. The seal rib 20 is integrally formed on the inner wall surface of the air conditioning case 11 and constitutes a case-side seal surface during maximum heating.

  Specifically, the seal rib 20 projects in a frame shape from the inner wall surface of the air conditioning case 11 toward the inside of the air conditioning case 11. A central opening 20 a is opened at the center of the frame-like protruding shape of the seal rib 20.

  During maximum heating, the heater core 15 is rotated to the one-dot chain line position MH in FIG. 1, and the rectangular peripheral edge of the heater core 15 is pressed against the frame-like protruding shape of the seal rib 20. Thereby, at the time of maximum heating, the heater core bypass passage in which the air passage 18 and the central opening 20a directly communicate with each other is blocked, and the space between the lower end portion 15b of the heater core 15 and the inner wall surface of the bottom surface of the air conditioning case 11 directly enters the central opening 20a. The bypass bypass air flow (cold air flow) c is blocked.

  For this reason, since the whole quantity of blowing air in the air conditioning case 11 passes through the core part of the heater core 15 and is heated, the maximum heating performance can be exhibited. The warm air d that has passed through the core portion of the heater core 15 flows through the central opening 20a of the seal rib 20 to the leeward side.

  Moreover, the solid line position in FIG. 1 of the heater core 15 is an example of an intermediate opening (intermediate rotation position) at the time of temperature control. Since the flow on the side bypasses the heater core 15 as indicated by the arrow c, and the upper flow of the evaporator passing air (cold air) passes through the heater core 15 and is heated as indicated by the arrow d ′, It becomes hot air d.

  Therefore, by adjusting the rotational position of the heater core 15, the air volume ratio between the cold air that bypasses the heater core 15 and the hot air that passes through the heater core 15 can be adjusted to continuously adjust the temperature of the air blown into the vehicle interior.

  The cold air that bypasses the heater core 15 and the warm air that passes through the heater core 15 both pass through the central opening 20a of the seal rib 20 and are mixed in the upper region 21 of the seal rib 20, resulting in conditioned air at a desired temperature. Later, it flows into each of the outlet openings 22, 23, 24. The blowout openings 22, 23, and 24 are arranged in the vehicle rear side portion of the blower unit 12 in the air conditioning case 11.

  Of the outlet openings 22, 23, 24, the defroster opening 22 is disposed on the upper surface of the air conditioning case 11, and is connected to a defroster outlet on the upper surface of the vehicle instrument panel (instrument panel) via a defroster duct (not shown). Air is blown out from the exit toward the inner surface of the front window glass of the vehicle.

  Of the blowout openings 22, 23, 24, the face opening 23 is arranged at the rear side of the vehicle with respect to the defroster opening 22, and is arranged at the upper part of the vehicle instrument panel via a face duct (not shown). The air is blown out from the face outlet to the face of the occupant.

  Of the blowing openings 22, 23, 24, the foot opening 24 is disposed on the left and right side walls of the air conditioning case 11, and blows air toward the feet of the occupant through a foot duct (not shown). The defroster opening 22, the face opening 23, and the foot opening 24 are opened and closed by a blowing mode door (not shown).

  Next, a specific configuration of the heater core 15 will be described with reference to FIGS. 2 and 3. A hot water outlet tank 15 a is disposed on one end side of the heater core 15, and a hot water inlet tank 15 b is disposed on the other end side of the heater core 15. 1 to 3, the hot water outlet tank 15 is located at the upper end portion of the heater core 15, and the hot water inlet tank 15 b is located at the lower end portion of the heater core 15. Therefore, the coaxial double pipe portion 16 is disposed on the hot water outlet tank 15a side.

  And between these both tanks 15a and 15b, the heat exchange core part 15e of the all-path type (one-way flow type) is comprised by the laminated structure of the some flat tube 15c and the corrugated heat transfer fin 15d.

  Here, the plurality of flat tubes 15c are arranged in parallel in a line in the left-right direction of the vehicle, and one end portion (upper end portion) of all the flat tubes 15c communicates with the hot water outlet tank 15a and the other end portion (lower end portion). Communicates with the hot water inlet tank 15b. For this reason, the warm water flows in one direction from the warm water inlet tank 15b through all the flat tubes 15c in parallel to the warm water outlet tank 15a.

  Both tanks 15a and 15b are elongated in the direction in which the flat tubes 15c are arranged (the vehicle left-right direction). The blown air in the air conditioning case 10 is heated by passing through the gaps between the flat tubes 15c and the corrugated heat transfer fins 15d.

  Here, hot water flows into the hot water inlet tank 15b from the communication pipe 15f. 2 and 3, the heater core 15 portion constituted by the hot water inlet tank 15 b, the hot water outlet tank 15 a, the flat tube 15 c, the corrugated heat transfer fin 15 d and the connecting pipe 15 f is illustrated by a two-dot chain line.

  In the present embodiment, the coaxial double pipe portion 16 for entering and exiting hot water is disposed on the side of the hot water outlet tank 15a located on the upper end side of the heater core 15 (extending direction in the tank longitudinal direction). The coaxial double pipe portion 16 is roughly divided into a fixed portion 16a and a rotating portion 16b.

  Here, the fixing | fixed part 16a is a fixing member fixed to the air-conditioning case 11 side by attachment means, such as screwing which is not shown in figure. On the other hand, the rotating portion 16 b is a rotating member that is joined to the heater core 15 and rotates together with the heater core 15.

  The fixed portion 16a includes an inner fixed pipe 25 having a minimum diameter portion, an outer fixed pipe 26 having a larger diameter than the inner fixed pipe 25, and an outer fixed pipe disposed on the outer peripheral side of the outer fixed pipe 26. 26 and an annular portion 27 having a maximum diameter portion having a diameter larger than that of the annular portion 26.

  The inner fixed pipe 25, the outer fixed pipe 26, and the annular part 27 of the fixed portion 16a are formed concentrically around the rotation center axis O of the heater core 15, and the inner fixed pipe 25 → the outer fixed pipe 26 → The diameter dimension increases in the order of the annular portion 27.

  An inlet pipe 28 for allowing warm water to flow inside the outer fixed pipe 26 is coupled in a direction perpendicular to the outer fixed pipe 26 (the outer diameter direction of the outer fixed pipe 26). The inlet pipe 28 corresponds to an inlet portion in the present invention, and hot water flows into the inlet pipe 28 from the discharge side of the hot water circuit of the vehicle engine through a hose 29.

  An outlet pipe 30 through which hot water flows out from the inside of the inner fixed pipe 25 is coupled in a direction perpendicular to the inner fixed pipe 25 (a direction perpendicular to the plane of FIG. 2 and FIG. 3). The outlet pipe 30 corresponds to an outlet portion in the present invention, and is coupled to the inner fixed pipe 25 through the outer fixed pipe 26 as shown in FIGS. The warm water in the inner fixed pipe 25 passes through the return hose 31 (FIGS. 4 to 6) and returns to the warm water circuit of the vehicle engine.

  The fixed portion 16a of the present embodiment is integrally formed of a resin material with the entire shape including the inlet pipe 28 and the outlet pipe 30.

  On the other hand, the rotating portion 16b is coupled to the inner rotating pipe 32, the outer rotating pipe 33 positioned at a predetermined interval on the outer peripheral side of the inner rotating pipe 32, and the direction orthogonal to the outer rotating pipe 33. And a communication pipe 34.

  The inner rotary pipe 32 is rotatably fitted to the inner peripheral side of the inner fixed pipe 25 and communicates with the inner fixed pipe 25 in a straight line. A minute gap 35 exists between the outer peripheral surface of the inner rotary pipe 32 and the inner peripheral surface of the inner fixed pipe 25. In this example, the outer diameter of the inner rotary pipe 32 and the inner diameter of the inner fixed pipe 25 are set so that the minute gap 35 is 0.3 mm or less.

  Of the inner rotating pipe 32, the end opposite to the inner fixed pipe 25 (the left end in FIGS. 2 and 3) communicates with one end in the longitudinal direction of the hot water outlet tank 15a.

  An arrow W in FIG. 3 indicates a hot water flow channel, and the inlet pipe 28 of the fixed portion 16a passes through a space 26a between the outer peripheral side of the outer fixed pipe 26 and the inner peripheral side of the inner fixed pipe 25, and then the rotating part. It communicates with a space 33 a between the outer peripheral side of the inner rotary pipe 32 of 16 b and the inner peripheral side of the outer rotary pipe 33. Further, the space 33a communicates with the inlet portion of the connecting pipe 15f on the heater core 15 side through the connecting pipe 34, and the outlet portion of the connecting pipe 15f communicates with one end in the longitudinal direction of the hot water inlet tank 15b.

  As a result, the hot water flowing into the inlet pipe 28 of the fixed portion 16a flows into the hot water inlet tank 15b via the space 26a → the space 33a → the communication pipe 34 → the communication pipe 15f. This hot water is distributed to the plurality of flat tubes 15c in the hot water inlet tank 15b, and flows through the plurality of flat tubes 15c from below to above.

  Hot water from the plurality of flat tubes 15c flows into the hot water outlet tank 15a and gathers, passes through the space 32a in the inner rotating pipe 32 of the rotating part 16b, and enters the space 25a in the inner fixed pipe 25 of the fixing part 16a. leak. The warm water in the space 25a in the inner fixed pipe 25 passes through the return hose 31 and returns to the warm water circuit of the vehicle engine.

  The spaces 26a and 33a correspond to the inlet channel in the present invention, and the spaces 25a and 32a correspond to the outlet channel in the present invention.

  Next, a specific configuration of the coaxial double pipe portion 16 will be described. 4A is an AA enlarged sectional view in FIG. 2, and FIG. 4B is a BB enlarged sectional view in FIG. 5A is an enlarged sectional view taken along the line CC in FIG. 3, and FIG. 5B is an enlarged sectional view taken along the line DD in FIG.

  FIGS. 6A and 6B are cross-sectional views showing the temperature control state (intermediate rotation position) of the coaxial double pipe section 16, and FIG. 6A is shown in FIGS. 4A and 5A. Correspondingly, FIG. 6 (b) corresponds to FIG. 4 (b) and FIG. 5 (b).

  An inlet throttling mechanism 37 that adjusts the flow rate of the hot water flowing into the outer fixed pipe 26 is provided at the downstream side of the hot water flow of the inlet pipe 28 that is the inlet of the coaxial double pipe structure 16. The inlet throttle mechanism 37 includes an inlet opening / closing part 38 formed integrally with the outer rotary pipe 33 and a hot water circulation part 38 a formed at the inlet opening / closing part 38.

  Specifically, the inlet opening / closing portion 38 is a plate having an arcuate cross section that protrudes from a part of the end surface on the upstream side of the hot water flow of the outer rotary pipe 33 toward the fixed portion 16a (the paper surface side in FIGS. 4 to 6). It is formed by.

  The inlet opening / closing part 38 overlaps with the inlet pipe 28 in the axial direction of the coaxial double pipe part 16. A hot water circulation portion 38 a through which hot water flows is formed in a portion of the inlet opening / closing portion 38 that overlaps with the inlet pipe 28. Specifically, the hot water circulation portion 38a is a circular hole having a diameter of 3 mm or more.

  Furthermore, the circumferential position of the inlet opening / closing part 38 is set as follows. That is, when the heater core 15 is rotated to the maximum cooling position, as shown in FIG. 4B, the inlet opening / closing portion 38 is superposed on the inlet pipe 28, and the inlet throttle mechanism 37 is formed only by the hot water circulation portion 38a. It becomes a communication state.

  On the other hand, when the heater core 15 is rotated to the maximum heating position, as shown in FIG. 5B, the inlet opening / closing part 38 moves to a position away from the inlet pipe 28 and the inlet throttle mechanism 37 is fully opened. It becomes a communication state.

  When the heater core 15 is rotated to a temperature control state (intermediate rotation position) of a predetermined rotation angle or more, as shown in FIG. 6 (b), the inlet opening / closing portion 38 is set to a position where the inlet pipe 28 is opened about half. The circumferential position of the inlet opening / closing part 38 is set so that the inlet throttle mechanism 37 moves and enters a communication state with an intermediate opening degree.

  In the vicinity of the fitting portion between the outer fixed pipe 26 and the outer rotary pipe 33, an inlet channel opening / closing mechanism 39 that blocks hot water flowing into the outer rotary pipe 33 is provided.

  This inlet channel opening / closing mechanism 39 includes a fixed-side opening-equipped wall portion 40 disposed at the downstream end portion of the outer fixed pipe 26 and the rotating side disposed at the upstream end portion of the outer rotating pipe 33. It is comprised by the wall part 41 with an opening, and the elastic seal member (packing) 42 laminated | stacked on the wall part 41 with a rotation side opening.

  The fixed opening side wall portion 40 and the rotation side opening wall portion 41 can be formed of a metal such as aluminum or a resin material. The elastic seal member 42 can be formed of an elastic material such as rubber.

  FIG. 7 is a perspective view of the fixed-side opening-equipped wall portion 40 and the outer fixed pipe 27. On the outer peripheral surface of the annular fixed-side opening-equipped wall portion 40, four projecting portions 40a projecting in the outer diameter direction are provided at equal intervals in the circumferential direction. The protrusions 40a are inserted into four recesses 26b formed on the downstream end surface of the outer fixed pipe 26 on the hot water flow side. As a result, the fixed-side opening-equipped wall portion 40 is fixed to the end portion on the downstream side of the warm water flow of the outer fixed pipe 26.

  In this example, four fixed-side openings 40b through which hot water flows are formed in an arc shape in the fixed-side opening-equipped wall 40. The fixed side openings 40b are spaced at equal intervals in the circumferential direction of the fixed side opening-equipped wall 40.

  The wall portion 41 with the rotation side opening and the elastic seal member 42 have the same configuration as the wall portion 40 with the opening on the fixed side. For this reason, the code | symbol corresponding to the wall part 41 with a rotation side opening, the elastic seal member 42, and the outer side rotation piping 33 is attached | subjected in the parenthesis in FIG. 7, and illustration is abbreviate | omitted.

  Specifically, four protrusions 41a protruding in the outer diameter direction are also provided at equal intervals in the circumferential direction on the outer peripheral surface of the annular rotation-side opening-equipped wall portion 41. It is inserted into four recesses 33b formed on the upstream end surface of the outer rotary pipe 33 in the warm water flow.

  In addition, on the outer peripheral surface of the annular elastic seal member 42, four projecting portions 42 a projecting in the outer diameter direction are provided at equal intervals in the circumferential direction, and these projecting portions 42 a are arranged on the outer rotating pipe 33. Inserted into the individual recesses 33b. Therefore, the elastic seal member 42 is laminated on the wall portion 41 with the rotation side opening.

  Thereby, the wall part 41 with a rotation side opening and the elastic seal member 42 are fixed to the warm water flow upstream side edge part of the outer side rotation piping 33, and rotate with rotation of the rotation part 16b.

  Furthermore, the rotation-side opening-equipped wall portion 41 and the elastic seal member 42 have four rotation-side opening portions 41b, 42b through which hot water flows, in the same shape as the fixed-side opening portion 40b of the fixed-side opening-side wall portion 40. Each is formed.

  The circumferential positions of the fixed side opening 40b and the rotation side openings 41b and 42b are set as follows. That is, when the heater core 15 is rotated to the maximum heating position, as shown in FIG. 5A, the rotation side openings 41b and 42b are superimposed on the fixed side opening 40b, and the inlet channel opening / closing mechanism 39 is Fully open communication.

  On the other hand, when the heater core 15 is rotated to the maximum cooling position, as shown in FIG. 4A, the rotation side openings 41b and 42b move to a position away from the fixed side opening 40b, and the inlet flow. The road opening / closing mechanism 39 is in a fully closed blocking state.

  When the heater core 15 is rotated to a temperature control state (intermediate rotation position) of a predetermined rotation angle or more, as shown in FIG. 6A, the rotation side openings 41b and 42b halve the fixed side opening 40b. The circumferential position of the fixed-side opening 40b and the rotation-side openings 41b and 42b is set so that the inlet channel opening / closing mechanism 39 moves to a position that opens to a certain extent and is in a communication state with an intermediate opening.

  FIG. 8 is an enlarged cross-sectional view of the inlet channel opening / closing mechanism 39, showing the maximum heating state. As shown in FIG. 8, the fixed-side opening-equipped wall portion 40 and the rotation-side opening-equipped wall portion 41 are arranged so as to be in close contact via an elastic seal member 42. That is, the elastic sealing member 42 forms a sealing mechanism in the inlet channel opening / closing mechanism 39.

  On the entire periphery of the opening 42 b of the elastic seal member 42, there are a first lip 42 c that protrudes toward the fixed-side opening-attached wall 40, and a second lip 42 d that protrudes toward the rotation-side opening-attached wall 41. Is formed. Accordingly, the first lip portion 42c of the elastic seal member 42 slides with the flat plate surface of the fixed-side opening-equipped wall portion 40 as the rotating portion 16b rotates.

  In this example, by attaching a film 43 (for example, a sheet made of Teflon (registered trademark)) having a small friction coefficient to the first lip portion 42c of the elastic seal member 42, the first lip portion 42c of the elastic seal member 42 and The flat plate surface of the fixed-side opening-equipped wall portion 40 slides smoothly.

  Further, the outer peripheral surface 42 e of the annular elastic seal member 42 is in close contact with the inner peripheral surface of the outer rotary pipe 33, and the inner peripheral surface 42 f of the annular elastic seal member 42 is in close contact with the outer peripheral surface of the inner rotary pipe 32. It has become.

  Although not shown in FIG. 7, a notch 40 c (see FIGS. 3 to 5) through which the inlet opening / closing portion 38 of the fixing portion 16 a penetrates a part of the outer peripheral edge portion of the fixed-side opening-attached wall portion 40. Is formed. The notch 40c is formed in an arc shape in a range in which the inlet opening / closing portion 38 rotates.

  Note that the fixed-side opening-equipped wall portion 40 may be integrally formed with the fixed portion 16a using a resin material. Alternatively, the rotation-side opening-attached wall portion 41 may be formed of a metal such as aluminum and integrally joined to the rotation portion 16b by means such as brazing.

  By the way, in the vicinity of the fitting portion between the inner rotating pipe 32 and the inner fixed pipe 25, a bypass passage that directly connects the inlet pipe 28 that is the inlet portion of the coaxial double pipe structure 16 and the outlet pipe 30 that is the outlet portion. A mechanism 44 is provided.

  The bypass passage mechanism 44 includes a bypass hole 45 that opens to the inner fixed pipe 25 and a bypass hole opening / closing portion 46 that is formed integrally with the inner rotary pipe 32.

  The bypass hole 45 is disposed in a portion of the inner fixed pipe 25 opposite to the inlet pipe 28 (upper side in FIGS. 2 and 3) with respect to the central axis O of the coaxial double pipe portion 16 and has a diameter of 3 mm or more. It is formed in a circular shape. Specifically, the bypass hole opening / closing part 46 is formed in a plate shape having an arcuate cross section protruding from a part of the end surface on the downstream side of the hot water flow of the inner rotary pipe 32 toward the inner fixed pipe 25.

  The bypass hole 45 and the bypass hole opening / closing part 46 are arranged so as to overlap in the axial direction of the coaxial double pipe part 16, and the circumferential position of the bypass hole opening / closing part 46 is set as follows. That is, when the heater core 15 is rotated to the maximum heating position, as shown in FIG. 5B, the bypass hole opening / closing portion 46 is superposed on the bypass hole 45 in a closed state, and the bypass passage mechanism 44 is fully closed. It becomes a cut-off state.

  In contrast, when the heater core 15 is rotated to the maximum cooling position, the bypass hole opening / closing portion 46 moves to a position away from the bypass hole 45 as shown in FIG. It becomes the communication state of.

  When the heater core 15 is rotated to a temperature control state (intermediate rotation position) of a predetermined rotation angle or more, as shown in FIG. 6B, the bypass hole opening / closing part 46 opens the bypass hole 45 by about half. The position of the bypass hole opening / closing portion 46 in the circumferential direction is set so that the bypass passage mechanism 44 is in a communicating state with an intermediate opening degree.

  On the other hand, an annular flange portion 47 is formed on the outer peripheral surface of the outer rotating pipe 33 of the rotating portion 16b. And the outer peripheral surface of the outer side rotation piping 33 fits rotatably to the inner peripheral surface of the outer side fixed piping 26 of the fixing | fixed part 16a.

  And the flange part 47 is clamped by the annular part 27 and the annular member 48 integrally fastened to the annular part 27 by fastening means such as a screw, so that the flat plate surface of the flange part 47 is fixed. It comes in close contact with the flat plate surface of the annular portion 27 of 16a.

  An external leakage seal mechanism 49 using an O-ring is provided in a close contact portion between the flat plate surface of the flange portion 47 and the flat plate surface of the annular portion 27.

  In the external leak seal mechanism 49, the hot water flowing into the outer fixed pipe 26 passes through the fitting gap between the inner peripheral surface of the outer fixed pipe 26 and the outer peripheral surface of the outer rotary pipe 33, and the coaxial double pipe portion 16. To prevent leakage directly to the outside.

  In this embodiment, each member 15a, 15b, 15c, 15d, 15f of the heater core 15 is formed of a metal such as aluminum and assembled by integral brazing. Therefore, the rotating portion 16b is also formed of a metal such as aluminum, and the rotating portion 16b is integrally brazed to the heater core 15 when the heater core 15 is brazed. Thereby, the rotation part 16b can be integrated with the heater core 15 efficiently.

  In addition, since the rotation part 16b is shape | molded with the metal as mentioned above, it is preferable to actually divide | segment and shape the rotation part 16b into a some member, and join the some member integrally by brazing. .

  Next, the assembly structure of the heater core 15 to the air conditioning case 11 and the rotation drive mechanism of the heater core 15 will be described. The wall surface of the air conditioning case 11 shown in FIGS. 2 and 3 is a wall surface on one side in the vehicle left-right direction, and the wall surface of the air conditioning case 11 has a circular shape having an inner diameter that is a predetermined amount larger than the outer diameter of the annular portion 27 of the fixed portion 16a. The through hole 50 is opened.

  Since the rotary part 16b of the coaxial double pipe part 16 is integrated with the heater core 15 in advance, the heater core 15 is assembled into the air conditioning case 11 together with the rotary part 16b. Specifically, a shaft portion is provided at the other end portion in the longitudinal direction of the hot water outlet tank 15a of the heater core 15 (the left end portion in FIGS. 2 and 3, not shown), and a bearing in which the shaft portion is rotatably fitted. Fitting holes (not shown) are provided on the wall surface (not shown) of the air conditioning case 11, so that the shaft portion at the other end in the longitudinal direction of the hot water outlet tank 15 a of the heater core 15 is fitted to the bearing for the air conditioning case 11. Insert it into the hole in a rotatable manner.

  In addition, a double pipe portion composed of the inner rotary pipe 32 and the outer rotary pipe 33 of the rotary part 16 b located on one end side in the longitudinal direction of the hot water outlet tank 15 a of the heater core 15 is inserted into the through hole 50 of the air conditioning case 11.

  Thereafter, the annular portion 27 portion of the fixing portion 16a of the coaxial double pipe portion 16 is inserted into the through hole 50 from the outside of the air conditioning case 11 (right side in FIGS. 2 and 3), and the inner fixing pipe 25 of the fixing portion 16a is inserted. The outer peripheral surface is fitted to the inner peripheral surface of the inner rotary pipe 32 of the rotating portion 16b, and the inner peripheral surface of the outer fixed pipe 26 of the fixed portion 16a is fitted to the outer peripheral surface of the outer rotary pipe 33 of the rotating portion 16b.

  Then, the annular member 48 is integrally fastened from the inside of the air conditioning case 11 (left side in FIGS. 2 and 3) to the annular portion 27 of the fixing portion 16a by fastening means such as screws. As a result, the entire circumference of the annular flange portion 47 of the outer rotary pipe 33 is sandwiched between the annular portion 27 and the annular member 48 of the fixed portion 16a.

  The annular member 48 is actually formed by being divided into two semicircular rings. The two divided annular members 48 are separately fastened to the annular portion 27 of the fixed portion 16a.

  As described above, both ends in the longitudinal direction of the hot water outlet tank 15 a of the heater core 15 can be rotatably supported by the air conditioning case 11.

  In this example, the rotation drive mechanism of the heater core 15 is provided on the opposite side of the coaxial double pipe portion 16 in the direction of the rotation center axis O of the heater core 15. That is, the tip of a shaft portion (not shown) provided at the other end in the longitudinal direction of the hot water outlet tank 15a of the heater core 15 is connected to the outside of the air conditioning case 11 from a fitting hole (not shown) for bearing of the air conditioning case 11. Protruding.

  And the motor 51 (FIG. 1) which makes a drive actuator is arrange | positioned outside the air-conditioning case 11, and the rotation output of this motor 51 protrudes from the fitting hole of the air-conditioning case 11 via the link mechanism 52 (FIG. 1). By transmitting to the shaft portion of the hot water outlet tank 15a, a force in the rotation direction is applied to the shaft portion of the hot water outlet tank 15a.

  The motor 51 is electrically connected to the output side of an air conditioning control device (not shown), and the rotation direction and the rotation amount (operating angle) of the motor 51 are controlled by the output of the air conditioning control device.

  Next, the operation of this embodiment will be described. When the motor 51 is operated, a rotational force is applied to the shaft portion of the hot water outlet tank 15 a of the heater core 15 through the link mechanism 52 by the rotation output of the motor 51. As a result, the heater core 15 is rotationally displaced about the rotation center axis O.

  Thus, since the heater core 15 rotates about the rotation center axis O by the rotation of the motor 51, the rotation position of the heater core 15 can be arbitrarily controlled by controlling the rotation direction and the rotation amount (operation angle) of the motor 51. As a result, the temperature of the air blown into the vehicle interior can be adjusted.

  Moreover, since the heater core 15 is rotated to the broken line position MC in FIG. 1 during maximum cooling, the entire passage area in the air conditioning case 11 can be configured as a passage 18 through which cool air flows, as indicated by an arrow c in FIG.

  Further, at the time of maximum heating, the heater core 15 is rotated to the one-dot chain line position MH in FIG. 1, so that the entire passage area in the air conditioning case 11 is a passage through which hot air flows as shown by the arrow d ′ in FIG. Can be configured.

  Therefore, compared with a normal indoor air-conditioning unit with an air mix door, the maximum cooling performance and maximum heating performance can be achieved by increasing the amount of cool air blown air and hot air blown air by reducing the ventilation resistance during maximum cooling and maximum heating. Can be improved.

  In addition to this, in this embodiment, the coaxial double pipe portion 16 for warm water in / out is configured at one end of the heater core 15 (the end on the hot water outlet tank 15a side), and the central axis O of the coaxial double pipe portion 16 is The heater core 15 is rotated as the center, and the configuration of the coaxial double pipe portion 16 is effectively used to provide the inlet channel opening / closing mechanism 39 that blocks the hot water flowing into the heater core 15. Can demonstrate.

  That is, when the heater core 15 is rotated to the maximum cooling position, as shown in FIG. 4 (a), the rotation side openings 41b and 42b move to a position away from the fixed side opening 40b to open and close the inlet channel. The mechanism 39 is in a fully closed blocking state.

  Here, the first lip portion 48 of the elastic seal member 42 is in close contact with the fixed-side opening-attached wall portion 40, and the elastic seal member 42 is disposed around the entire periphery of the rotation-side opening portion 41 b of the rotation-side opening-attached wall portion 41. The second lip portion 42d is in close contact. Furthermore, the outer peripheral surface 42e of the annular elastic seal member 42 is in close contact with the inner peripheral surface of the outer rotary pipe 33, and the inner peripheral surface 42f of the annular elastic seal member 42 is in close contact with the outer peripheral surface of the inner rotary pipe 32. Yes.

  Therefore, the flow of hot water from the outer fixed pipe 26 of the fixed part 16a to the outer rotary pipe 33 of the rotating part 16b is blocked, and the inflow of hot water to the heater core 15 is blocked.

  Thereby, since the heat of the hot water is not released to the air flow from the heater core 15 at the maximum cooling, the temperature rise of the air flow c (see FIG. 1) flowing bypassing the heater core 15 can be avoided, and the maximum cooling performance is more effectively achieved. Can demonstrate.

  9 and 10 are graphs showing effects in the present embodiment. FIG. 9 shows the flow rate of hot water flowing through the heater core 15 side hot water passage (arrow W in FIG. 3) during maximum cooling. FIG. 10 shows the relationship between the flow rate of hot water flowing through the heater core 15 side hot water passage and the temperature rise of the air flow c flowing bypassing the heater core 15 during maximum cooling.

  9 and 10, as Comparative Example 1, an example in which the inlet channel opening / closing mechanism 39 and the bypass passage mechanism 44 of the present embodiment are omitted is shown. Further, as an example corresponding to the prior application example (Comparative Example 2), an example in which the inlet flow path opening / closing mechanism 39 is abolished and only the bypass passage mechanism 44 is provided is shown.

  In the first comparative example, at the time of maximum cooling, since the entire amount of hot water flowing into the inlet pipe 28 that is the inlet portion of the coaxial double pipe structure 16 flows through the heater core 15 side hot water passage, the air flowing by bypassing the heater core 15 The temperature of stream c will increase by about 2.5 ° C.

  On the other hand, in the comparative example 2, at the time of maximum cooling, a part of the hot water flowing into the inlet pipe 28 that is the inlet portion of the coaxial double piping structure 16 passes through the bypass passage mechanism 44 and flows to the outlet pipe 30 side in a short circuit. However, since the remaining hot water flows through the heater core 15 side hot water passage, the temperature of the air flow c flowing by bypassing the heater core 15 rises.

  Specifically, when the vehicle engine is in an idle state, the flow of about 1 L / min flows through the heater core 15 side hot water passage, and the temperature of the air flow c increases by about 2.2 ° C. When the vehicle engine is 4000 rpm, the number of rotations of a water pump (not shown) that circulates and supplies hot water increases, and the flow rate of circulating hot water increases. For this reason, about 4 L / min flows through the heater core 15 side hot water passage, and the temperature of the air flow c rises by about 2.5 ° C.

  In contrast, in the present embodiment, the flow rate of hot water flowing through the heater core 15 side hot water passage can be 0 L / min regardless of whether the vehicle engine is in an idle state or 4000 rpm, and the temperature of the air flow c The rise can be 0 ° C.

  On the other hand, when the heater core 15 is rotated to the maximum heating position, as shown in FIG. 5 (a), the rotation side openings 41b and 42b are superimposed on the fixed side opening 40b, and the inlet channel opening / closing mechanism 39 is Fully open communication.

  In the present embodiment, the opening on the rotation side is such that the opening area when the inlet channel opening / closing mechanism 39 is fully opened (in this example, the total area of the fixed side opening 40b) is larger than the channel area of the inner rotary pipe 32. The shapes and positions of 41b and 42b and the fixed side opening 40b are set. For this reason, it is possible to suppress an increase in water flow resistance by the inlet channel opening / closing mechanism 39 at the maximum heating position.

  As a result, the entire amount of hot water flowing into the outer fixed pipe 26 of the fixed portion 16a flows through the heater core 15 side hot water passage shown by the arrow W in FIG. 3, so that the air heating action by the heater core 15 can be exhibited without any trouble.

  When the heater core 15 is rotated to a temperature control state (intermediate rotation position) of a predetermined rotation angle or more, as shown in FIG. 6A, the rotation side openings 41b and 42b halve the fixed side opening 40b. The inlet channel opening / closing mechanism 39 moves to a position where it is opened to a certain extent, and is in a communication state with an intermediate opening.

  For this reason, the inlet channel opening / closing mechanism 39 can adjust the flow rate of the hot water passing through the heater core 15 side hot water passage in accordance with the rotation angle of the heater core 15. Therefore, the inlet channel opening / closing mechanism 39 can exhibit the function of a so-called hot water valve.

  In the present embodiment, four fixed-side openings 40b and rotation-side openings 41b and 42b are provided at equal intervals in the circumferential direction of the fixed-side opening-equipped wall 40, the rotation-side opening-equipped wall 41, and the elastic seal member 42. Separated one by one. This ensures a large opening area of the inlet channel opening / closing mechanism 39 when the rotation angle of the heater core 15 is small as compared to the case where only one fixed side opening 40b and one rotation side opening 41b, 42b are provided. ing.

  For this reason, when the rotation angle of the heater core 15 is small, the flow rate of the warm water passing through the heater core 15 side warm water passage can be ensured by a predetermined amount or more.

  Further, in the present embodiment, the bypass double-pass mechanism 44 that directly communicates between the hot water inlet / outlet portions of the coaxial double pipe structure 16 is provided by effectively utilizing the configuration of the coaxial double pipe section 16, so that the following effects are obtained. The effect can be demonstrated.

  That is, when the heater core 15 is rotated to the maximum cooling position, the bypass hole opening / closing part 46 moves to a position away from the bypass hole 45 as shown in FIG. It becomes a state.

  Therefore, the inlet pipe 28 that is the inlet portion of the coaxial double piping structure 16 and the outlet pipe 30 that is the outlet portion are directly communicated by the bypass passage mechanism 44. As a result, the hot water that has flowed into the inlet pipe 28 does not flow to the outer fixed pipe 26 side of the fixed portion 16a, but flows through the bypass passage mechanism 44 and to the outlet pipe 30 side as indicated by an arrow Z in FIG. .

  Thereby, it is possible to prevent hot water from staying in the outer fixed pipe 26 of the fixed portion 16a when the inlet channel opening / closing mechanism 39 is shut off during maximum cooling. For this reason, it is possible to avoid the problem that foreign matter (cast sand or the like adhering during manufacture of the vehicle engine) mixed in the hot water accumulates in the outer fixed pipe 26 and bites into the inlet channel opening / closing mechanism 39.

  In addition to this, since the hot water flow is blocked and the hot water pressure is prevented from rising when the inlet channel opening / closing mechanism 39 is shut off during maximum cooling, the coaxial double piping structure 16 including the inlet channel opening / closing mechanism 39 is provided. Can be reduced, and an increase in product cost can be suppressed.

  On the other hand, when the heater core 15 is rotated to the maximum heating position, as shown in FIG. 5B, the bypass hole opening / closing portion 46 is superposed on the bypass hole 45 so that the bypass passage mechanism 44 is fully closed. It becomes a cut-off state.

  For this reason, since the whole amount of hot water flowing into the inlet pipe 28 flows through the heater core 15 side hot water passage shown by the arrow W in FIG. 3, the air heating action by the heater core 15 can be exhibited without any trouble.

  When the heater core 15 is rotated to a temperature control state (intermediate rotation position) in which the rotation angle is equal to or greater than a predetermined value, the bypass hole opening / closing section 46 opens the bypass hole 45 as shown in FIG. The bypass passage mechanism 44 moves to a position where the opening is about half and the intermediate opening degree is in a communicating state.

  For this reason, the flow rate of the hot water passing through the bypass passage mechanism 44 can be adjusted in accordance with the rotation angle of the heater core 15. In other words, the flow rate of the hot water passing through the heater core 15 side hot water passage can be adjusted according to the rotation angle of the heater core 15.

  Here, when the rotation angle of the heater core 15 is a minute angle, that is, when the flow rate of the hot water flowing through the inlet channel opening / closing mechanism 39 is large when the inlet channel opening / closing mechanism 39 has a small opening degree, the inlet channel opening / closing mechanism 39. Since the flow rate of the hot water is increased at the minute opening of the water, a running sound is generated.

  Therefore, the present inventor has made a trial study on the relationship between the diameter of the bypass hole 45 and the generation of running water noise. The result is shown in FIG.

  As can be seen from the chart shown in FIG. 11, by setting the bypass hole 45 to a diameter of 3 mm or more, the flow rate of the hot water passing through the bypass passage mechanism 44 is increased when the rotation angle of the heater core 15 is a minute angle, and the inlet flow is increased. The flow rate of the hot water flowing through the road opening / closing mechanism 39 can be suppressed. For this reason, it turned out that it can prevent that a flowing water sound generate | occur | produces in the micro opening part of the entrance flow-path opening-closing mechanism 39. FIG.

  Furthermore, by setting the bypass hole 45 to a diameter of 3 mm or more, it is possible to suppress an increase in the flow rate of hot water passing through the bypass hole 45. For this reason, it turned out that it can also prevent that a flowing water sound generate | occur | produces in bypass hole 45 itself.

  At the time of temperature control, the opening degree of the inlet channel opening / closing mechanism 39 is increased, so that the flow rate of hot water passing through the bypass hole 45 is reduced. For this reason, even if the bypass hole 45 is closed about half by the bypass hole opening / closing part 46 at the time of temperature control, the flow rate of the warm water passing through the bypass hole 45 does not increase, so that a running sound is generated in the bypass hole 45. There is nothing.

  By the way, if the position of the bypass hole 45 is a position that directly receives the dynamic pressure of the hot water flowing into the outer fixed pipe 26 from the inlet pipe 28, the heater core 15 is rotated to the maximum heating position and the bypass passage mechanism 44 is fully closed. Therefore, the hot water is likely to leak from the bypass passage mechanism 44.

  FIG. 12 is a graph showing the flow rate of hot water flowing through the heater core 15 side hot water passage shown by the arrow W in FIG. 3 at the maximum heating position. In FIG. 12, Comparative Example 3 is an example in which the bypass hole 45 is opened at a portion (the lower portion in FIG. 3) facing the inlet pipe 28 in the inner fixed pipe 25.

  In this comparative example 3, since the bypass hole 45 is disposed at a position that directly receives the dynamic pressure of the hot water flowing into the outer fixed pipe 26 from the inlet pipe 28, the hot water of the heater core 15 with respect to the total flow rate of 6 L / min of hot water. The flow rate is about 4 L / min.

  On the other hand, the comparative example which has arrange | positioned the bypass hole 45 in the site | part opposite to the inlet pipe 28 (upper side of FIG. 3) with respect to the central axis O of the coaxial double piping part 16 among the inner side fixed piping 25. 4, the hot water flow rate of the heater core 15 is about 4.4 L / min, which is higher than that of the comparative example 3.

  Therefore, in the present embodiment, the bypass hole 45 is disposed in a portion of the inner fixed pipe 25 opposite to the inlet pipe 28 with respect to the central axis O of the coaxial double pipe portion 16. It is possible to avoid the bypass hole 45 directly receiving the dynamic pressure of the hot water flowing into the outer fixed pipe 26 from the outside.

  For this reason, it is possible to suppress the leakage of hot water from the bypass passage mechanism 44 when the heater core 15 is rotated to the maximum heating position and the bypass passage mechanism 44 is in the fully closed blocking state.

  Further, in the present embodiment, the inlet throttle mechanism 37 that adjusts the flow rate of the hot water flowing into the outer fixed pipe 26 of the fixed part 16a by effectively utilizing the configuration of the coaxial double pipe part 16 is provided. The effect can be demonstrated.

  That is, when the heater core 15 is rotated to the maximum cooling position, as shown in FIG. 4B, the inlet opening / closing part 38 of the rotating part 16b is superposed on the inlet pipe 28, and the inlet throttle mechanism 37 opens and closes the inlet. Only the hot water circulation part 38a formed in the part 38 is in a communicating state.

  For this reason, the flow rate of the hot water flowing into the outer fixed pipe 26 from the inlet pipe 28 can be suppressed. As a result, it is possible to further prevent the hot water flow from being blocked and the hot water pressure from rising when the inlet flow path opening / closing mechanism 39 is shut off during maximum cooling, so that the coaxial double piping structure 16 including the inlet flow path opening / closing mechanism 39 is provided. Can be further reduced, and an increase in product cost can be further suppressed.

  Here, if the area of the hot water circulation part 38a of the inlet opening / closing part 38 is too small, the flow rate of the hot water is increased in the hot water circulation part 38a, so that running water sounds are generated in the hot water circulation part 38a. Therefore, the present inventor has confirmed through trial manufacture that the running water sound in the hot water circulation portion 38a can be prevented by making the hot water circulation portion 38a a circular hole having a diameter of 3 mm or more.

  On the other hand, when the heater core 15 is rotated to the maximum heating position, the inlet opening / closing portion 38 moves to a position away from the inlet pipe 28 and the inlet throttle mechanism 37 is fully opened as shown in FIG. It becomes.

  For this reason, since the whole amount of hot water flowing into the inlet pipe 28 flows through the heater core 15 side hot water passage shown by the arrow W in FIG. 3, the air heating action by the heater core 15 can be exhibited without any trouble.

  When the heater core 15 is rotated to a temperature control state (intermediate rotation position) where the rotation angle is equal to or greater than a predetermined value, the inlet opening / closing portion 38 halves the inlet pipe 28 as shown in FIG. The inlet throttling mechanism 37 moves to a position where it is opened to a certain extent, and is in a communication state with an intermediate opening.

  For this reason, the flow rate of the hot water passing through the inlet throttle mechanism 37 can be adjusted in accordance with the rotation angle of the heater core 15. In other words, the flow rate of the hot water passing through the heater core 15 side hot water passage can be adjusted according to the rotation angle of the heater core 15.

  By the way, in the present embodiment, the inner rotating pipe 32 is fitted to the inner peripheral side of the inner fixed pipe 25 in the inner pipe section of the coaxial double pipe section 16. Thereby, as shown in FIG. 8, the fitting front end portion 32 b of the inner rotary pipe 32 is located in the space 25 a in the inner fixed pipe 25.

  In other words, it is possible to avoid the fitting tip 32b of the inner rotating pipe 32 from being located in the space 26a between the outer peripheral side of the outer fixed pipe 26 and the inner peripheral side of the inner fixed pipe 25.

  For this reason, since it can avoid that the fitting front-end | tip part 32b of the inner side rotation piping 32 receives the dynamic pressure of inflow side warm water directly, it can prevent that warm water flows in into the fitting part of the inner side rotation piping 32 and the inner side fixed piping 25. Can be suppressed.

  On the other hand, although the fitting front end 25b of the inner fixed pipe 25 is positioned in the space 26a, the fitting front end 25b of the inner fixed pipe 25 faces the downstream side of the inflow-side hot water. For this reason, since it can avoid that the fitting front-end | tip part 25b of the inner side fixed piping 25 receives the dynamic pressure of inflow side warm water directly, it can be said that warm water flows in into the fitting part of the inner side rotation piping 32 and the inner side fixed piping 25. Can be suppressed.

  As a result, it is possible to suppress leakage of hot water at the fitting portion between the inner rotating pipe 32 and the inner fixed pipe 25.

  Furthermore, in this embodiment, the inner rotary pipe 32 and the inner fixed pipe are formed by setting the minute gap 35 existing between the outer peripheral face of the inner rotary pipe 32 and the inner peripheral face of the inner fixed pipe 25 to 0.3 mm or less. The hot water leakage in the fitting part with 25 is suppressed effectively.

  In FIG. 12, the comparative example 5 is an example in which the minute gap 35 is set to 0.5 mm or less in the comparative example 4 described above. In Comparative Example 5, the hot water flow rate of the heater core 15 is about 4.5 L / min with respect to the total hot water flow rate of 6 L / min.

  In contrast, in the present embodiment, the outer diameter of the inner rotary pipe 32 and the inner diameter of the inner fixed pipe 25 are set so that the dimension of the minute gap 35 is 0.3 mm or less. Thereby, as shown in FIG. 12, it turned out that the warm water flow rate of the heater core 15 can be made into about 5.6 L / min, and can be significantly increased rather than the comparative example 5. FIG.

  Comparative Example 6 is an example in which the minute gap 35 is 0.1 mm or less with respect to Comparative Example 4. Thereby, the hot water flow rate of the heater core 15 can be set to about 5.8 L / min.

  However, if the minute gap 35 is reduced from 0.3 mm to 0.1 mm or less, high processing accuracy and assembly accuracy are required, which causes an increase in product cost. On the other hand, even if the minute gap 35 is 0.3 mm to 0.1 mm or less, the increase in the hot water flow rate of the heater core 15 is as small as 0.2 L / min. For this reason, in this embodiment, the minute gap 35 is set to 0.3 mm or less.

  Thus, in this embodiment, the warm water leak in the fitting part of the inner side rotation piping 32 and the inner side fixed piping 25 is suppressed favorably without using an elastic sealing material. For this reason, generation | occurrence | production of the sliding frictional force by using an elastic sealing material for the said fitting part can be avoided.

  As a result, it is possible to prevent hot water leakage at the fitting portion between the inner rotary pipe 32 and the inner fixed pipe 25 without increasing the rotational operation force of the heater core 15.

  By the way, in this embodiment, in the inlet channel opening / closing mechanism 39, sliding frictional force is generated by sliding between the first lip portion 42c of the elastic seal member 42 and the flat plate surface of the fixed-side opening-equipped wall portion 40. Since the film 43 (such as a sheet made of Teflon (registered trademark)) having a small friction coefficient is attached to the first lip portion 42c of the elastic seal member 42, generation of sliding frictional force can be suppressed.

  As a result, it is possible to suppress an increase in the rotational operation force of the heater core 15 due to the provision of the inlet channel opening / closing mechanism 39.

(Second Embodiment)
In the first embodiment, the elastic seal member 42 is laminated on the wall portion 41 with the rotation side opening. However, in this embodiment, as shown in FIG. 13, the elastic seal member 42 and the wall portion 41 with the rotation side opening are provided. Are integrally molded.

  FIG. 13 is a cross-sectional view of a main part in the present embodiment. In the present embodiment, the elastic seal member 42 and the rotation-side opening-attached wall portion 41 are integrally formed by insert-molding the elastic seal member 42.

  More specifically, the elastic seal member 42 is formed so as to cover the flat plate surfaces on both the front and back sides of the rotation-side opening-attached wall 41 and the inner peripheral surface of the rotation-side opening 41b. Then, similarly to the first embodiment (see FIG. 7), four protrusions 41a protruding in the outer diameter direction are equidistantly arranged in the circumferential direction on the outer peripheral surface of the annular rotation-side opening-equipped wall portion 41. The protrusions 41 a are inserted into the four recesses 33 b on the front end surface of the outer rotary pipe 33 so as to be spaced apart.

  As a result, the integrally formed rotation-side opening-equipped wall portion 41 and the elastic seal member 42 are fixed to the distal end portion of the outer rotary pipe 33, and rotate with the rotation of the rotation portion 16b.

  Further, by providing a step on the outer peripheral surface of the inner rotary pipe 32 of the rotating portion 16b, the contact surface 32c facing the second lip portion 42d side of the elastic seal member 42 is formed. Similarly, a contact surface 33c facing the second lip portion 42d side of the elastic seal member 42 is formed by providing a step on the inner peripheral surface of the outer rotating pipe 33 of the rotating portion 16b.

  In the present embodiment, at the maximum cooling time, the first lip portion 48 of the elastic seal member 42 is in close contact with the fixed-side opening-attached wall portion 40, and the second lip portion 42d of the elastic seal member 42 is the contact surface 32c of the rotating portion 16b. , 33c. Furthermore, the outer peripheral surface 42 e of the annular elastic seal member 42 is in close contact with the inner peripheral surface of the outer rotary pipe 33, and the inner peripheral surface 42 f of the annular elastic seal member 42 is in close contact with the outer peripheral surface of the inner rotary pipe 32. Yes.

  Therefore, the flow of hot water from the outer fixed pipe 26 of the fixed part 16a to the outer rotary pipe 33 of the rotating part 16b is blocked, and the inflow of hot water to the heater core 15 is blocked.

  Thereby, the effect similar to 1st Embodiment can be exhibited.

(Third embodiment)
In each of the above embodiments, the coaxial double pipe portion 16 is disposed on the vehicle rear side of the evaporator 13 and the wind shielding wall 17 covering the entire windward surface of the heater core 15 is disposed. As shown in FIG. 14, the coaxial double pipe portion 16 is disposed in close contact with the vehicle rear side wall surface of the air conditioning case 11 and the wind shielding wall 17 is eliminated.

  FIG. 14 is a schematic cross-sectional view of the indoor air conditioning unit according to this embodiment. In the present embodiment, at the time of maximum cooling, the heater core 15 is rotated to a broken line position in FIG. 13 (a position extending substantially in the vertical direction along the vehicle rear side wall surface of the air conditioning case 11) MC. As shown, the entire passage area in the air conditioning case 11 can be configured as a passage 18 through which cold air flows.

  At this time, in the vicinity of the core portion of the heater core 15, the flow rate of the air flow c that bypasses the heater core 15 is high, so that the heat transfer rate increases. However, the inlet flow opening / closing mechanism 39 causes the warm water to flow into the heater core 15. Since it is interrupted, the heat of the hot water is not released from the heater core 15 into the air flow.

  For this reason, similarly to the above-described embodiments, it is possible to avoid the temperature rise of the air flow c that flows by bypassing the heater core 15 and to effectively exhibit the maximum cooling performance.

  Further, at the time of maximum heating, the heater core 15 is rotated to the one-dot chain line position MH in FIG. 14, so that the entire passage area in the air conditioning case 11 is a passage through which hot air flows, as indicated by an arrow d ′ in FIG. Can be configured.

  Furthermore, in this embodiment, the aeration resistance by the wind shielding wall 17 can be reduced by eliminating the wind shielding wall 17. Therefore, compared with the above embodiments, the maximum cooling performance and the maximum heating performance can be improved by increasing the amount of cool air blown air and the amount of hot air blown air by reducing the ventilation resistance during maximum cooling and maximum heating.

(Other embodiments)
(1) In each of the above embodiments, in the coaxial double pipe section 16 for hot water in / out, the outer pipes 26 and 33 constitute a hot water inlet side flow path, and the inner pipes 25 and 32 constitute a hot water outlet side flow path. However, conversely, the outer pipes 26 and 33 may constitute a hot water outlet side flow path, and the inner pipes 25 and 32 may constitute a hot water inlet side flow path. That is, the configuration may be such that the hot water flow direction W is reversed in FIG.

  2 and 3, the upper hot water outlet tank 15a in FIGS. 2 and 3 becomes a hot water inlet tank, the lower hot water inlet tank 15b in FIGS. 2 and 3 becomes a hot water outlet tank, and the hot water inlet pipe 28 It becomes a hot water outlet pipe, and the hot water outlet pipe 30 becomes a hot water inlet pipe. Therefore, the coaxial double pipe portion 16 is disposed on the hot water inlet tank side.

  In this embodiment, the inlet channel opening / closing mechanism 39 configured by the fixed opening side wall portion 40, the rotation side opening wall portion 41 and the elastic seal member 42 may be disposed in the inner pipes 25 and 32.

  Also in this embodiment, the bypass passage mechanism 44 including the bypass hole 45 and the bypass hole opening / closing part 46 can be similarly configured. However, the flow direction of the bypass hot water passing through the bypass passage mechanism 44 flows in the direction opposite to the arrow Z.

  In this embodiment, if the inlet opening / closing part 38 is formed in the inner rotary pipe 32, the inlet throttle mechanism 37 can be constituted by the outlet pipe 30 and the inlet opening / closing part 38.

  In this embodiment, the inner rotary pipe 32 is fitted on the outer peripheral side of the inner fixed pipe 25 by reversing the internal and external positional relationship in the fitting of the inner fixed pipe 25 and the inner rotary pipe 32 to the above embodiments. What is necessary is just to make it match.

  Thereby, since it can avoid that the fitting front-end | tip part 25b of the inner side fixed piping 25 receives the dynamic pressure of inflow side warm water directly, it fits with the inner side fixed piping 25 and the outer side fixed piping 26 similarly to said each embodiment. Warm water leakage at the part can be suppressed.

  (2) In each of the above embodiments, the bypass hole 45 of the bypass passage mechanism 44 and the hot water circulation part 38a of the inlet opening / closing part 38 of the inlet throttle mechanism 37 are both circular holes having a diameter of 3 mm or more. The shape is not limited to a circle, and may be, for example, an oval or a rectangle.

  In this way, when the bypass hole 45 and the hot water circulation part 38a are formed in a hole shape other than a circle, the holes in the inlet channel opening / closing mechanism 39 and the hot water circulation part 38a are made to have a size of an equivalent circular diameter of 3 mm or more. Generation of running water noise can be prevented.

  Furthermore, the hot water circulation part 38a of the inlet opening / closing part 38 can be not only a hole shape but also a notch shape. In this way, when the hot water circulation portion 38a is formed in a notch shape, the hot water circulation portion 38a is formed by making the overlapping portion of the warm water circulation portion 38a and the hot water inlet pipe 28 at the time of maximum cooling have an equivalent circular diameter of 3 mm or more. The generation of running water noise can be prevented.

  (3) In each of the above embodiments, the hot water inlet pipe 28 and the hot water outlet pipe 30 are both coupled to the outer diameter direction of the coaxial double pipe portion 16 (direction perpendicular to the axial direction). One or both of the hot water outlet pipe 30 and the hot water outlet pipe 30 may be coupled in the axial direction of the coaxial double pipe portion 16.

  In this embodiment, the inlet throttling mechanism 37 or the bypass passage mechanism 44 may be constituted by a wall portion with a rotation-side opening and a wall portion with a fixed-side opening, similarly to the inlet channel opening / closing mechanism 39.

  (4) In each of the above-described embodiments, the inlet throttle mechanism 37 or the coaxial double pipe portion 16 for entering and exiting hot water is disposed on one end side (on the hot water outlet tank 15a side) of the heater core 15, and the rotation center axis O of the heater core 15 is The heater core 15 is set on one end side (on the warm water outlet tank 15a side), but the coaxial double pipe portion 16 for warm water in / out is arranged in the intermediate portion in the longitudinal direction of the connecting pipe 15f of the heater core 15 so that the heater core 15 The rotation center axis O may be set at an intermediate position between the hot water inlet tank 15b and the hot water outlet tank 15a.

  (5) In each of the above embodiments, the rotating portion 16b of the coaxial double pipe portion 16 is integrated with the heater core 15 by brazing, but mechanical connecting means such as caulking the rotating portion 16b of the coaxial double pipe portion 16 is used. Thus, the seal may be fixed to the heater core 15 side with a sealing material interposed therebetween.

  (6) In each of the above embodiments, as the heater core 15, a so-called all-pass type (one-way flow type) is used in which hot water passes from the hot water inlet tank 15b through all the tubes 15c toward the hot water outlet tank 15a. However, as the heater core 15, a front / rear U-turn type that makes a U-turn of the hot water flow in the front / rear direction of the air flow direction may be used, and the present invention may be applied to the front / rear U-turn type heater core 15.

  Similarly, as the heater core 15, a left and right U-turn type that makes a U-turn of the hot water flow in the left-right direction of the heater core (the left-right direction in FIGS. 4 and 5) is used, and the present invention is applied to the left-right U-turn type heater core 15. May be.

  (7) In each of the above embodiments, the fixing portion 16a of the coaxial double pipe portion 16 is formed separately from the air conditioning case 11, but both the fixing portion 16a and the air conditioning case 11 are resin members. The fixing portion 16a may be integrally formed with the air conditioning case 11 with resin.

  (8) In each of the above embodiments, the example in which the hot water of the vehicle engine is circulated to the heater core 15 has been described. However, the hot water heated by the in-vehicle heat source device such as a combustion heater or a fuel cell is supplied to the heater core 15. You may make it circulate.

  Further, hydraulic oil for hydraulic equipment or the like may be used as the heat source fluid to be circulated through the heater core 15 instead of hot water.

It is a schematic longitudinal cross-sectional view of the indoor air-conditioning unit which shows 1st Embodiment of this invention. It is sectional drawing which shows the warm water flow path in the maximum cooling state of the heat exchanger for rotary heating by the 1st Embodiment of this invention, and a coaxial double piping part. It is sectional drawing which shows the warm water flow path | route in the maximum heating state of the heat exchanger for rotary heating by the 1st Embodiment of this invention, and a coaxial double piping part. (A) is an AA expanded sectional view in FIG. 2, (b) is a BB expanded sectional view in FIG. (A) is CC expanded sectional view in FIG. 3, (b) is DD expanded sectional view in FIG. (A), (b) is sectional drawing in the temperature control state of the coaxial double piping part shown in FIG. 1, (a) respond | corresponds to Fig.4 (a), Fig.5 (a), (b) is This corresponds to FIGS. 4B and 5B. It is a perspective view of the wall part with a fixed side opening and outer side fixed piping by 1st Embodiment of this invention. It is sectional drawing which shows the flow-path interruption | blocking mechanism by 1st Embodiment of this invention. It is a graph which shows the warm water flow rate in the maximum cooling state of the heat exchanger for rotary heating by 1st Embodiment of this invention, and the hot water flow rate in the maximum cooling state of the heat exchanger for rotary heating by a comparative example. It is a graph which shows the cold wind temperature rise in the maximum cooling state of the rotary heating heat exchanger by 1st Embodiment of this invention, and the cold wind temperature rise in the maximum cooling state of the rotary heating heat exchanger by a comparative example. It is a graph which shows the relationship between the diameter of the bypass hole by 1st Embodiment of this invention, and the presence or absence of generation | occurrence | production of a flowing water sound. It is a graph which shows the hot water flow rate in the maximum heating state of the rotary heating heat exchanger according to the first embodiment of the present invention and the hot water flow rate in the maximum cooling state of the rotary heating heat exchanger according to the comparative example. It is sectional drawing which shows the flow-path interruption | blocking mechanism by 2nd Embodiment of this invention. It is a schematic longitudinal cross-sectional view of the indoor air conditioning unit which shows 3rd Embodiment of this invention.

Explanation of symbols

11 ... air conditioning case, 15 ... rotary heater core (heat exchanger for heating),
16 ... Coaxial double pipe part, 25 ... Inner fixed pipe, 25a ... Space (exit flow path),
26 ... Outer fixed pipe (fixed side pipe), 26a ... Space (inlet flow path),
28 ... Inlet pipe (inlet part), 30 ... Outlet pipe (outlet part), 32 ... Inside rotary pipe,
32a ... space (exit flow path), 33 ... outside rotary pipe (rotary side pipe),
33a ... space (inlet flow path), 35 ... minute gap, 37 ... inlet throttle mechanism,
39 ... Inlet channel opening / closing mechanism, 45 ... Bypass hole, 46 ... Bypass hole opening / closing part,
O: Center axis of rotation.

Claims (17)

An air conditioning case (11) through which air flows;
A heating heat exchanger (15) that is rotatably arranged in the air conditioning case (11) and heats the air in the air conditioning case (11);
By changing the rotational position of the heating heat exchanger (15), the air volume ratio between the hot air passing through the heating heat exchanger (15) and the cold air bypassing the heating heat exchanger (15) is changed. In the air conditioner that adjusts the blown air temperature by adjusting,
A pipe forming an inlet channel (26a, 33a) for allowing a heat source fluid to flow into the heating heat exchanger (15), and an outlet channel (25a, 32a) for allowing the heat source fluid to flow out of the heating heat exchanger (15). ) With a coaxial double pipe structure (16),
The heating heat exchanger (15) is configured to be rotatable about the central axis (O) of the coaxial double pipe structure (16), and
When the heating heat exchanger (15) is rotated to the maximum cooling position, an inlet channel opening / closing mechanism (39) for closing the inlet channel (26a, 33a) is provided in the coaxial double pipe structure (16). Configure
When the heating heat exchanger (15) is rotated from the maximum cooling position to the maximum heating position, the inlet channel opening / closing mechanism (39) changes in a direction to open the inlet channels (26a, 33a). An air conditioner characterized by that. The inlet channel (26a, 33a) includes a rotating side pipe (33) that rotates integrally with the heating heat exchanger (15), and a fixed side pipe (26) that communicates with the rotating side pipe (33). Consisting of
A wall portion (41) with a rotation side opening having a rotation side opening (41b) is part of the inlet channel (26a, 33a) at the upstream side portion of the heat source fluid flow in the rotation side pipe (33). It is arranged to close
In the fixed side pipe (26), a fixed side opening wall portion (40) having a fixed side opening portion (40b) is disposed so as to face and closely contact the rotation side opening wall portion (41). ,
When the heating heat exchanger (15) is in the maximum cooling position, the rotating side opening (41b) is located away from the fixed side opening (40b), and the heating heat exchanger (15 ) Is rotated from the maximum cooling position to the maximum heating position, the rotation side opening (41b) and the rotation side opening (41b) are overlapped with the fixed side opening (40b). The fixed side opening (40b) is formed,
2. The air conditioner according to claim 1, wherein the inlet channel opening / closing mechanism (39) includes the rotation-side opening-equipped wall portion (41) and the fixed-side opening-equipped wall portion (40). . The air conditioner according to claim 2, wherein the rotation-side opening wall portion (41) and the fixed-side opening wall portion (40) are in close contact via an elastic seal member (42). The air conditioner according to claim 3, wherein the elastic seal member (42) is formed integrally with the wall portion (41) with the rotation side opening. A plurality of the rotation side openings (41b) are provided in the rotation direction of the wall portion with rotation side opening (41),
The air conditioner according to any one of claims 2 to 4, wherein a plurality of the fixed side openings (40b) are provided in correspondence with the rotation side openings (41b). When the heating heat exchanger (15) is rotated to the maximum heating position, a polymerization area of the rotation side opening (41b) and the fixed side opening (40b) is set to the outlet flow path (25a, 32a). The rotation side opening (41b) and the fixed side opening (40b) are formed so as to be larger than the area of (1). Air conditioner. The outer pipe of the coaxial double pipe structure (16) includes an outer rotary pipe (33) that rotates integrally with the heating heat exchanger (15), and an outer fixed pipe (33) that communicates with the outer rotary pipe (33). 26), and
The inner pipe of the coaxial double pipe structure (16) includes an inner rotating pipe (32) rotating integrally with the heating heat exchanger (15) and an inner fixed pipe (32) communicating with the inner rotating pipe (32). 25) and
The outer rotating pipe (33) constitutes the rotating side pipe,
The air conditioner according to any one of claims 2 to 6, wherein the outer fixed pipe (26) constitutes the fixed side pipe. The air conditioner according to claim 7, wherein the inner rotating pipe (32) is fitted to an inner peripheral side of the inner fixed pipe (25). The inner rotary pipe (32) so that a minute gap (35) existing between the outer peripheral surface of the inner rotary pipe (32) and the inner peripheral face of the inner fixed pipe (25) is 0.3 mm or less. The air conditioner according to claim 8, wherein an outer diameter of the inner fixed pipe and an inner diameter of the inner fixed pipe (25) are set. The outer fixed pipe (26) is formed with an inlet part (28) of the coaxial double pipe structure (16),
The inner fixed pipe (25) is formed with an outlet part (30) of the coaxial double pipe structure (16),
The inner fixed pipe (25) is formed with a bypass hole (45) for directly communicating the inlet portion (28) and the outlet portion (30),
The inner rotary pipe (32) is provided with a bypass hole opening / closing part (46) that opens and closes the bypass hole (45) in accordance with the rotation operation of the heating heat exchanger (15).
When the heating heat exchanger (15) is rotated to the maximum cooling position, the bypass hole opening / closing part (46) opens the bypass hole (45),
When the heating heat exchanger (15) is rotated from the maximum cooling position to the maximum heating position, the bypass hole opening / closing part (46) changes in a direction to close the bypass hole (45). The air conditioner according to any one of claims 7 to 9, wherein The inlet portion (28) is formed on the outer radial direction side of the outer fixed pipe (26),
The said bypass hole (45) is formed in the site | part on the opposite side to the said inlet part (28) with respect to the said center axis | shaft (O) among the said inner side fixed piping (25). 10. The air conditioner according to 10. The air conditioner according to claim 10 or 11, wherein the bypass hole (45) has an equivalent circular diameter of 3 mm or more. When the heating heat exchanger (15) is rotated to the maximum cooling position, an inlet throttle mechanism (37) that minimizes the opening of the inlet (28) is formed in the outer rotary pipe (33). Has been
The inlet throttle mechanism (37) is configured such that the opening degree increases when the heating heat exchanger (15) is rotated from the maximum cooling position to the maximum heating position. The air conditioner according to any one of claims 7 to 12. The inlet throttle mechanism (37) is configured so that the opening of the inlet part (28) has an equivalent circular diameter of 3 mm or more when the opening is at a minimum. Item 14. The air conditioner according to Item 13. An air conditioning case (11) through which air flows;
A heating heat exchanger (15) that is rotatably arranged in the air conditioning case (11) and heats the air in the air conditioning case (11);
By changing the rotational position of the heating heat exchanger (15), the air volume ratio between the hot air passing through the heating heat exchanger (15) and the cold air bypassing the heating heat exchanger (15) is changed. In the air conditioner that adjusts the blown air temperature by adjusting,
A pipe forming an inlet channel (26a, 33a) for allowing a heat source fluid to flow into the heating heat exchanger (15), and an outlet channel (25a, 32a) for allowing the heat source fluid to flow out of the heating heat exchanger (15). ) With a coaxial double pipe structure (16),
The heating heat exchanger (15) is configured to be rotatable about the central axis (O) of the coaxial double pipe structure (16),
The inner pipe of the coaxial double pipe structure (16) is rotatably fitted with the inner rotary pipe (32) that rotates integrally with the heating heat exchanger (15) and the inner rotary pipe (32). It consists of an inner fixed pipe (25),
In the fitting portion between the inner rotary pipe (32) and the inner fixed pipe (25), the inner rotary pipe (32) is located on the outlet flow path (25a, 32a) side, and the inner fixed pipe (25 ) Is located on the inlet channel (26a, 33a) side. Out of the inner rotating pipe (32) and the inner fixed pipe (25), the outer peripheral surface of the inner peripheral pipe (32) disposed on the inner peripheral side in the fitting portion and the outer peripheral side disposed on the outer peripheral side. The outer diameter of the inner peripheral side pipe (32) and the inner diameter of the outer peripheral side pipe (25) so that the minute gap (35) existing between the inner peripheral surface of the pipe (25) is 0.3 mm or less. The air conditioner according to claim 15, wherein the air conditioner is set. The outer pipe of the coaxial double pipe structure (16) includes an outer rotary pipe (33) that rotates integrally with the heating heat exchanger (15), and an outer fixed pipe (33) that communicates with the outer rotary pipe (33). 26), and
The outer fixed pipe (26) is formed with an inlet part (28) of the coaxial double pipe structure (16),
The air conditioner according to claim 15 or 16, wherein an outlet (30) of the coaxial double pipe structure (16) is formed in the inner fixed pipe (25).

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