JP2007186036A - Rotation operation mechanism and air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce a rotation operation force of a rotary type heat exchanger for heating, in an air conditioner controlling a blowing-out air temperature by using the rotary type heat exchanger for heating. <P>SOLUTION: The air conditioner comprises: an air-conditioning case 11 in which air flows; and the heat exchanger 15 rotatably disposed in the case 11 and heating the air in the air-conditioning case 11. By changing the rotational position of the air conditioner 15 for heating, the air conditioner adjusts proportions of the volume of hot air passing through the heat exchanger 15 and the volume of cold air bypassing the heat exchanger 15 so as to control the blowing-out air temperature. The heat exchanger 15 is rotated around a rotational shaft 16 by a drive force from a drive unit and the air conditioner is provided with spring members 28, 32 whose spring loads P act on the heat exchanger 15, so that the spring load and a load W the by dead weight of the heat exchanger 15 are canceled with each other. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a rotation operation mechanism that reduces a rotation operation force on a heavy rotating body, and is particularly effective when applied to a rotation operation mechanism of a rotary heating heat exchanger in an air conditioner.

  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 the position where it does not become the draft resistance of the cold air flow, that is, the side position 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).
JP 2001-47845 A Japanese Patent Laid-Open No. 2001-246922

  However, in these prior arts, in addition to the weight of the hot water heating heat exchanger itself, the total weight of the hot water heating heat exchanger is very large due to the weight of the hot water in the hot water heating heat exchanger. It will be heavy.

  For this reason, when the rotation center axis of the hot water heating heat exchanger is set in the horizontal direction and the rotation direction of the hot water heating heat exchanger is set in the vertical direction, the hot water heating heat exchanger is There is a problem that the rotational operation force becomes very large because the rotational operation must be performed against its own weight.

  In view of the above points, an object of the present invention is to reduce the rotational operating force of a rotary heating heat exchanger in an air conditioner that adjusts the blown air temperature using the rotary heating heat exchanger.

  Another object of the present invention is to provide a rotation operation mechanism that can reduce a rotation operation force on a heavy rotating body in view of the above points.

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,
The heating heat exchanger (15) is configured to rotate around the rotating shaft (16) by a driving force from a driving device,
Furthermore, it has spring members (28, 32) that apply a spring load (P) to the heat exchanger (15) for heating,
The first feature is that the spring load (P) cancels out the load (W) due to the weight of the heating heat exchanger (15).

  According to this, the spring load (P) of the spring members (28, 32) cancels the load (W) due to the weight of the heat exchanger (15) for heating, so that the canceled load can be made close to zero. For this reason, the rotational operating force of the heat exchanger for heating (15) can be reduced, and the rotational operating force can be made substantially uniform.

  Note that “cancel” in the present invention does not only mean completely canceling out to zero, but also means close to zero by canceling a part of the amount before canceling.

Specifically, when the heat exchanger for heating (15) is rotated to a position where the load (W) is maximized, the present invention relates to the center (B) of the rotating shaft (16) and the spring load (P The angle (θ) formed by the line segment (S) connecting the point of action (D) and the direction of action of the spring load (P) is maximized,
When the heating heat exchanger (15) is rotated in a direction in which the load (W) decreases, the angle (θ) changes in a direction to decrease.

  According to this, when the heating heat exchanger (15) is rotated to a position where the load (W) due to the weight of the heating heat exchanger (15) is maximized, the center of the rotating shaft (16) (B ) And the point of action (D) of the spring load (P) and the angle (θ) formed by the direction of action of the spring load (P) is maximized. Of these, the ratio of the load acting to cancel the load (W) can be maximized.

  On the other hand, when the heating heat exchanger (15) is rotated in the direction in which the load (W) decreases, the angle (θ) changes in the direction in which the load (W) decreases. It is possible to reduce the ratio of loads acting so as to cancel out.

  For this reason, since the load (W) which fluctuates with rotation operation of the heat exchanger (15) for heating can be offset well by the spring load (P), the rotation operation force of the heat exchanger for heating (15) can be further increased. It can be made uniform.

  More specifically, according to the present invention, when the heating heat exchanger (15) is rotated to a position where the load (W) is minimized, the angle (θ) becomes a predetermined angle greater than 0 degrees. In addition, spring members (28, 32) are formed.

  Here, when the angle (θ) is 0 degree, that is, when the line segment (S) and the acting direction of the spring load (P) are completely parallel, the total load of the spring load (P) is converted into a heat exchanger for heating ( 15) acts so as to press against the rotation support portion, so that the sliding friction force generated between the heat exchanger for heating (15) and the rotation support portion increases.

  In view of this point, the spring member is set such that the angle (θ) when the heating heat exchanger (15) is rotated to a position where the load (W) is minimum is a predetermined angle greater than 0 degrees. Since (28, 32) is comprised, the load which acts so that the heat exchanger for heating (15) may be pressed against a rotation support part among spring loads (P) can be reduced.

  As a result, the sliding friction force generated between the heating heat exchanger (15) and the rotation support portion can be reduced.

More specifically, the present invention relates to a lever (26) that is coupled to the rotating shaft (16) and rotates as the heating heat exchanger (15) rotates.
A bifurcated spring means (28) in which the first arm (30) is pressed by the lever (26) and the second arm (31) is supported by the air conditioning case (11);
The spring member comprises bifurcated spring means (28);
The point of action of the spring load (P) is the contact (D) between the first arm (30) and the lever (26),
The direction of action of the spring load (P) is the direction in which the first arm (30) presses the lever (26).

  According to this, the load (W) due to the own weight of the heat exchanger (15) for heating can be obtained only by using the bifurcated spring means (41) having the first arm portion (30) and the second arm portion (31). Can be offset. Accordingly, an increase in the rotational operation force of the heating heat exchanger (15) due to the influence of the weight of the heating heat exchanger (15) can be suppressed with a simple configuration. The practical effect such as reduction is great.

More specifically, the present invention relates to a lever (26) that is coupled to the rotating shaft (16) and rotates as the heating heat exchanger (15) rotates.
One end (34a) is pulled by the lever (26), and the other end (35a) is provided with tension spring means (32) supported by the air conditioning case (11),
The spring member is composed of tension spring means (32),
The point of action of the spring load (P) is the contact (D) between the one end (34a) and the lever (26),
The acting direction of the spring load is the direction in which the one end (34a) pulls the lever (26).

  Thereby, the load (W) by the dead weight of the heat exchanger (15) for heating can be offset only by using the tension spring means (32).

  In addition, the tension spring means (32) in this invention can be comprised with elastic materials, such as a metal coiled spring and rubber | gum, for example.

The present invention also provides a rotating body (15) that rotates about a rotating shaft (16) by a driving force from a driving device;
A spring member (28, 32) for applying a spring load (P) to the rotating body (15),
The second feature is that the spring load (P) cancels the load (W) due to the weight of the rotating body (15).

  Thereby, the rotational operation force with respect to a rotary body (15) can be reduced effectively.

Specifically, according to the present invention, when the rotating body (15) is rotated to a position where the load (W) due to the weight of the rotating body (15) becomes maximum, the center (B) of the rotating shaft (16) is obtained. The angle (θ) formed by the line segment (S) connecting the spring and the action point (D) of the spring load (P) and the action direction of the spring load (P) is maximized,
When the rotating body (15) is rotated in a direction in which the load (W) is reduced, the angle (θ) is changed in a direction to be reduced.

  Thereby, the load (W) which fluctuates with rotation operation of a rotary body (15) can be canceled well by a spring load (P).

  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 is a schematic 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, showing a maximum cooling state.

  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. One end portion 15a of the rectangular outer shape, more specifically, the rotary shaft 16 is set at the upper end portion 15a. The air-conditioning case 11 is rotatably supported.

  In the example of FIG. 1, the rotating shaft 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 15 a of the heater core 15. 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 of the wind shielding wall 17 and the lower end of the heater core 15 (the end opposite to the rotation shaft 16) 15b and the bottom surface of the air conditioning case 11, and the predetermined gap An air passage 18 on the upstream side of the heater core is formed. 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 the present embodiment, the lower end portion 15b of the heater core 15 approaches the upwind air passage 18 formed on the lower end side of the windshield wall 17, and the upper end portion 15a of the heater core 15 extends from the upwind air passage 18. Since the heater core 15 is disposed so as to move away, the lower end portion 15b of the heater core 15 serves as the windward side end portion, and the upper end portion 15a of the heater core 15 serves as the leeward side end portion.

  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).

  FIG. 2 is a side view of the main part of the air conditioning unit shown in FIG. 1 as viewed from the outside of the air conditioning case, and shows the maximum heating state. FIG. 3 is a side view of the main part of the air conditioning unit shown in FIG. 1 viewed from the outside of the air conditioning case, and shows the maximum cooling state.

  Both end portions in the axial direction of the rotating shaft 16 of the heater core 15 are slidably fitted in through holes (not shown) on the left and right side walls of the air conditioning case 11 and protrude to the outside of the air conditioning case 11. The end portion is connected to a hot water inlet / outlet mechanism (not shown) outside the air conditioning case 11.

  Further, the other end portion (right end portion) of the rotation shaft 16 is connected to the rotation drive mechanism 25 outside the air conditioning case 11 as shown in FIG. Thereby, the rotating shaft 16 is rotatably supported with respect to the air conditioning case 11.

  The hot water inlet / outlet mechanism includes a hot water inlet side pipe (not shown) and a hot water outlet side pipe (not shown) connected to the rotary shaft 16 side, and a fixed hot water inlet fixed to the air conditioning case 11 side. Side piping (not shown) and hot water outlet side piping (not shown), and these pipings are coaxially fitted so that the rotating side piping can rotate with respect to the fixed side piping. Consists of a coaxial double piping mechanism. Hot water circulates in the heater core 15 through the hot water inlet / outlet mechanism and the hot water passage portion of the rotating shaft 16.

  In this example, the rotation drive mechanism 25 is a manual mechanism that is operated by the manual operation force of the passenger. Specifically, the rotation drive mechanism 25 is configured by a substantially fan-shaped lever 26, a drive side gear 27, and the like.

  The rotary shaft 16 is fitted in the fan-shaped key position of the lever 26. A gear portion 26 a is formed along the arc shape of the lever 26. A pin portion 26b for supporting a bifurcated spring 28, which will be described later, is formed integrally with the lever 26 in the vicinity of one end portion (the lower end portion in FIG. 2) of the gear portion 26a.

  The drive side gear 27 is rotatably supported so as to be rotatable about the rotation shaft 27a with respect to the air conditioning case 11 at the vehicle rear side and the lower side of the rotation shaft 16. The drive side gear 27 is engaged with the gear portion 26 a of the lever 26.

  One end of a control cable (not shown) is connected to the drive side gear 27, and the other end side of the control cable is connected to a blow mode switching lever provided on an air conditioning operation panel (not shown) in the passenger compartment. Yes. The blowing mode switching lever and the control cable correspond to the driving device in the present invention.

  Thereby, the drive side gear 27 is rotationally driven based on the manual operation of the blowing mode switching lever. The lever 26 is rotationally displaced about the rotation shaft 16 as the drive side gear 27 rotates.

  In addition, you may comprise the drive device in this invention by the actuator mechanism using a servomotor. Specifically, the drive side gear 27 may be rotationally driven by a servo motor or the like.

  The bifurcated spring 28 includes a circular coil portion 29 and first and second arm portions 30 and 31 protruding from the circular coil portion 29. The two-dot chain line position in FIG. 2 indicates the free state of the bifurcated spring 28.

  In this free state, the first arm portion 30 protrudes in the tangential direction of the circular coil portion 29, and the second arm portion 31 is a direction substantially perpendicular to the tangential direction of the circular coil portion 29 and the protruding direction of the first arm portion 30. Protruding to

  The distal end portion 30a of the first arm portion 30 is formed in an annular shape, and the pin portion 26b of the lever 26 is slidably fitted to the inner peripheral side of the annular distal end portion 30a. Thus, the first arm portion 30 of the bifurcated spring 28 is supported so as to be rotatable with respect to the lever 26.

  This is because the first arm portion 30 can be deformed without difficulty by changing the contact position between the lever 26 and the distal end portion 30a as the lever 26 rotates.

  The second arm portion 31 of the bifurcated spring 28 is coupled to the air conditioning case 11 below the rotating shaft 16. Specifically, the tip end portion 31a of the second arm portion 31 of the bifurcated spring 28 is formed in an annular shape. And the pin part 11a integral with the air-conditioning case 11 is fitted in the inner peripheral side of the annular front-end | tip part 31a so that sliding is possible.

  Accordingly, the second arm portion 31 of the bifurcated spring 28 is supported so as to be rotatable with respect to the air conditioning case 11. This is because the second arm portion 31 can be deformed without difficulty when the contact position between the pin portion 11a and the tip portion 31a varies with the rotational displacement of the lever 26.

  Next, the operation of this embodiment will be described. Now, when the occupant manually operates the blow mode switching lever of the air conditioning operation panel (not shown), the rotation shaft 16 of the heater core 15 is rotated in the rotational direction via the control cable (not shown), the drive side gear 27 and the lever 26. Power is added. As a result, the heater core 15 is rotationally displaced about the rotation shaft 16.

  Thus, since the heater core 15 rotates around the rotation shaft 16 by manual operation of the blowing mode switching lever, the occupant can arbitrarily adjust the rotational position of the heater core 15 by adjusting the blowing mode switching lever. The temperature in the passenger compartment 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 this embodiment, by using the bifurcated spring 28, an increase in the heater core rotating operation force due to the dead weight of the heater core 15 can be satisfactorily suppressed. Hereinafter, the effect of suppressing the heater core rotating operation force by the bifurcated spring 27 will be described in detail with reference to FIGS.

  As shown in FIG. 2, the center position A of the circular coil portion 29 of the bifurcated spring 27 is set on the rotation tip side of the lever 26. The pin portion 26b of the lever 26 is slidably fitted to the tip portion 30a of the first arm portion 30 of the bifurcated spring 27, and the air conditioning case 11 is fitted to the tip portion 31a of the second arm portion 31 of the bifurcated spring 27. The pin portion 11a is slidably fitted.

  In FIG. 2, the broken line position of the heater core 15 is the position at the time of maximum heating, and the center of gravity position of the heater core 15 is G at the time of maximum heating, and the load W due to the weight of the heater core acts on this center of gravity position G.

  Therefore, an axial moment M is generated in the heater core 15 due to the horizontal distance L between the rotation axis center B (the center of the rotation axis 16) and the gravity center position G. Therefore, when the heater core 15 rotates in the direction opposite to the axial moment M, the heater core rotating operation force increases under the influence of the axial moment M.

  Therefore, by setting a spring load P acting in the opposite direction to the axial moment M for the heater core 15, the axial moment M based on the influence of the heater core's own weight is offset, and an increase in the heater core rotational operation force is suppressed. be able to.

  That is, at the time of maximum heating, the tip portion 30a of the first arm portion 30 of the bifurcated spring 28 is pressed against the pin portion 26b of the lever 26, so that the bifurcated spring 28 is elastic from the free state indicated by the two-dot chain line position. Since it is deformed, the spring load P acts on the lever 26 from the first arm portion 30.

  In FIG. 2, a point D is a contact point (spring action point) between the distal end portion 30 a of the first arm portion 30 and the pin portion 26 b of the lever 26 during the maximum heating, and a line segment S is a rotation axis center B of the heater core 15. And a spring segment D.

  During this maximum heating, the lever 26 is rotated to a position where the gear portion 26a faces in the horizontal direction (left direction in FIG. 2), and the first arm portion 30 becomes substantially parallel to the line segment S. For this reason, since the angle θ formed by the line segment S and the acting direction of the spring load P is substantially perpendicular, the spring moment P can effectively cancel the axial moment M based on the influence of the heater core's own weight.

  In the present embodiment, as shown in FIG. 3, the center-of-gravity position G of the heater core 15 is positioned vertically below the rotation axis center B during maximum cooling. For this reason, at the time of maximum cooling, the axial moment M based on the influence of the heater core's own weight becomes substantially zero.

  On the other hand, as can be seen from FIG. 3, at the time of maximum cooling, the bifurcated spring 28 is more elastically deformed than at the time of maximum heating, so that a larger spring load P acts on the lever 26 from the first arm portion 30 than at the time of maximum heating. To do.

  During this maximum cooling, the lever 26 is rotated to a position where the gear portion 26a faces downward, and the first arm portion 30 is substantially orthogonal to the line segment S, so that the direction of action of the line segment S and the spring load P is substantially the same. Become parallel.

  For this reason, although a larger spring load P acts on the lever 26 from the first arm portion 30 than at the time of maximum heating, the spring load P hardly contributes to the axial moment of the heater core 15. As a result, the axial moment after cancellation can be made substantially zero during maximum cooling.

  By the way, at the time of maximum cooling, the acting direction of the line segment S and the spring load P is not completely parallel, and the bifurcated spring so that the angle θ formed by the line segment S and the acting direction of the spring load P becomes a minute angle. 28 is arranged.

  Thereby, compared with the case where the acting direction of the line segment S and the spring load P is completely parallel, the rotating shaft 16 is pressed against the through hole (not shown) on the air conditioning case 11 side by the spring load P. Suppressed. For this reason, compared with the case where the action direction of the line segment S and the spring load P is completely parallel, the sliding frictional force generated between the rotating shaft 16 and the through hole on the air conditioning case 11 side is reduced. .

  Since the spring load P is determined according to the deformation angle and spring constant of the bifurcated spring 27, the deformation angle and spring of the bifurcated spring 27 are set so that the spring load P and the load W of the heater core are substantially equal to each other. Determine the constant.

  As described above, an increase in the heater core rotating operation force due to the dead weight of the heater core 15 can be satisfactorily suppressed with a simple configuration in which only the bifurcated spring 28 is used.

  At this time, the tip portions 30 a and 31 a of the first and second arm portions 30 and 31 of the bifurcated spring 28 slide with respect to the outer peripheral surface of the pin portion 26 b of the lever 26 and the pin portion 11 a of the air conditioning case 11. It is supposed to be.

  Accordingly, the contact position between the pin portions 26b and 11a and the tip portions 30a and 31a of the first and second arm portions 30 and 31 can be changed with the rotational displacement of the lever 26. Thereby, the first and second arm portions 30 and 31 can be smoothly canceled without causing excessive deformation of the first and second arm portions 30 and 31 with the rotational displacement of the lever 26.

  FIG. 4 is a graph for explaining the effect of reducing the heater core rotational operation force according to the present embodiment, in which the horizontal axis represents the heater core opening, and the vertical axis represents the heater core rotational operation force (operation torque). Here, the heater core opening is set to 0 degree at the maximum cooling time and 40 degrees at the maximum heating time.

  In FIG. 4, the solid line e is the heater core rotation operation force when the heater core 15 is rotated from the maximum cooling side to the maximum heating side in the present embodiment, and the solid line f is the heater core 15 from the maximum heating side in the present embodiment. This is the heater core rotation operating force when rotating to the maximum cooling side.

  The two-dot chain lines g and h are comparative examples, and the two-dot chain line g is a heater core rotating operation force when the heater core 15 is rotated from the maximum cooling side to the maximum heating side without the bifurcated spring 28. A two-dot chain line h is a heater core rotating operation force when the bifurcated spring 28 is eliminated and the heater core 15 is rotated from the maximum heating side to the maximum cooling side.

  At the time of maximum cooling, the center of gravity position G of the heater core 15 moves vertically below the rotation axis center B as described above, and the load W due to the weight of the heater core is minimized. Therefore, at the time of maximum cooling, the line segment S and the direction of action of the spring load P are made substantially parallel as described above so that the spring load P hardly contributes to the axial moment of the heater core 15.

  At the time of maximum heating, the gravity center position G of the heater core 15 moves to the horizontal direction side of the rotation axis center B, and the load W due to the heater core's own weight becomes maximum. In view of this, the angle θ formed by the line segment S and the direction of action of the spring load P is set to a maximum during maximum heating so that the load W due to the heater core's own weight can be effectively offset by the spring load P.

  At the time of temperature control, the rotation position of the heater core 15 is an intermediate position between the maximum cooling and the maximum heating, and accordingly, the total load W due to the heater core's own weight also becomes an intermediate value. In this temperature control, the angle θ formed by the line segment S and the acting direction of the spring load P is also an intermediate value, so that the load due to the heater core's own weight can be offset well by the spring load P.

  As a result, as shown by the solid line e in FIG. 4, in the present invention, the heater core rotating operation force when the heater core 15 is rotated from the maximum cooling side to the maximum heating side is compared with the comparative example (two-dot chain line g). It can be reduced to a small value through the entire heater core opening.

  Furthermore, since the heater core rotation operating force can be made to be a substantially uniform value through the entire heater core opening, the operation feeling of the occupant can be improved without the heater core rotating operation force changing rapidly.

  Further, as shown by the solid line f in FIG. 4, in the present invention, the heater core rotating operation force when the heater core 15 is rotated from the maximum heating side to the maximum cooling side is increased with respect to the comparative example (two-dot chain line h). However, the heater core rotation operating force (solid line e) when rotating from the maximum cooling side to the maximum heating side substantially coincides.

  For this reason, since the heater core 15 can be controlled to rotate from the maximum heating side to the maximum cooling side, and when the heater core 15 is rotated from the maximum cooling side to the maximum heating side, it is possible to prevent the heater core rotational operation force from fluctuating rapidly. The occupant's operational feeling can be improved.

(Second Embodiment)
In the first embodiment, the use of the bifurcated spring 28 suppresses an increase in the heater core rotation operating force due to the weight of the heater core 15, but in this embodiment, as shown in FIGS. By using the coiled spring 32 instead of the bifurcated spring 28, an increase in the heater core rotating operation force due to the dead weight of the heater core 15 is suppressed.

  FIG. 5 is a side view of the main part of the air conditioning unit according to the present embodiment as viewed from the outside of the air conditioning case, and shows the maximum heating state of the rotation drive mechanism of the rotary heating heat exchanger. FIG. 6 is a side view of the main part of the air conditioning unit according to the present embodiment as viewed from the outside of the air conditioning case, and shows the maximum cooling state of the rotation drive mechanism of the rotary heating heat exchanger.

  The coiled spring 32 includes a circular coil portion 33 and first and second arm portions 34 and 35 protruding from the circular coil portion 33. The first arm portion 34 protrudes in the axial direction of the circular coil portion 33, and the second arm portion 35 protrudes in the axial direction of the circular coil portion 29 and in a direction opposite to the protruding direction of the first arm portion 34.

  The distal end portion 34a of the first arm portion 34 is formed in an annular shape, and the pin portion 26b of the lever 26 is slidably fitted in the annular distal end portion 34a. Thus, the first arm portion 34 of the coiled spring 32 is supported so as to be rotatable with respect to the lever 26.

  The second arm portion 35 of the coiled spring 32 is coupled to the air conditioning case 11 above the rotating shaft 16. Specifically, the tip 35a of the second arm portion 35 of the coiled spring 32 is formed in an annular shape. And the pin part 11a integral with the air-conditioning case 11 is fitted in the annular front-end | tip part 35a so that sliding is possible.

  5 and 6, the circular coil portion 29 of the coiled spring 32 is in a state of being extended in the axial direction with respect to the free state.

  In FIG. 5, the broken line position of the heater core 15 is a position at the time of maximum heating, and the center of gravity position of the heater core 15 is G at the time of maximum heating, and a load W due to the weight of the heater core acts on this center of gravity position G.

  Therefore, an axial moment M is generated in the heater core 15 due to the horizontal distance L between the rotation axis center B and the gravity center position G. Therefore, when the heater core 15 rotates in the direction opposite to the axial moment M, the heater core rotating operation force increases under the influence of the axial moment M.

  Therefore, by setting a spring load P acting in the opposite direction to the axial moment M for the heater core 15, the axial moment M based on the influence of the heater core's own weight is offset, and an increase in the heater core rotational operation force is suppressed. be able to.

  That is, at the time of maximum heating, the tip end portion 34a of the first arm portion 34 of the coiled spring 32 is pulled by the pin portion 26b of the lever 26 so that the coiled spring 32 is extended with respect to the free state. Therefore, the spring load P acts on the lever 26 from the coiled spring 32.

  In FIG. 5, a point D is a contact point (spring action point) between the distal end portion 34 a of the first arm portion 34 and the pin portion 26 b of the lever 26 at the time of maximum heating, and a line segment S is a rotation axis center B of the heater core 15. And a spring segment D.

  During this maximum heating, the lever 26 is rotated to a position where the gear portion 26a faces in the horizontal direction (left direction in FIG. 2), and between the axial direction of the circular coil portion 33 of the coiled spring 32 and the line segment S. A predetermined angle occurs. For this reason, since the angle θ formed by the line segment S and the acting direction of the spring load P has a predetermined angle, the axial moment M based on the influence of the weight of the heater core can be offset by the spring load P.

  In the present embodiment, as shown in FIG. 6, the center-of-gravity position G of the heater core 15 is positioned vertically below the rotation axis center B during maximum cooling. For this reason, at the time of maximum cooling, the axial moment M based on the influence of the heater core's own weight becomes substantially zero.

  On the other hand, as can be seen from FIG. 6, at the time of maximum cooling, the distance between the pin portion 26b of the lever 26 and the pin portion 11a of the air conditioning case 11 is longer than that at the time of maximum heating. The amount of displacement of the portion 33 is greater than that during maximum heating. For this reason, a larger spring load P is applied from the coiled spring 32 to the lever 26 than during maximum heating.

  During this maximum cooling, the lever 26 is rotated to a position where the gear portion 26a faces downward, and the axial direction of the circular coil portion 33 of the coiled spring 32 is parallel to the line segment S. The direction of action of the load P becomes parallel.

  For this reason, although a larger spring load P is applied to the lever 26 from the coiled spring 32 than at the time of maximum heating, the spring load P does not contribute to the axial moment of the heater core 15. As a result, the axial moment after cancellation can be made substantially zero during maximum cooling.

  Here, since the spring load P is determined according to the displacement amount and the spring constant of the coiled spring 32, the displacement amount and the spring constant are set so that the spring load P and the load W of the heater core weight substantially coincide with each other. decide.

  As described above, the use of the coiled spring 32 instead of the bifurcated spring 28 can also suppress an increase in the heater core rotating operation force due to the weight of the heater core 15.

  In this embodiment, the coiled spring 32 is disposed so that the line segment S and the direction of action of the spring load P are parallel at the maximum cooling, but the line segment S and the spring load P are at the maximum cooling. The coiled spring 32 may be arranged so that the angle θ formed by the direction of action of the coil becomes a minute angle.

  Specifically, by setting the position of the pin portion 11a of the air conditioning case 11 on the vehicle rear side (left side in FIG. 6) with respect to the position in the second embodiment, the line segment S and the spring at the maximum cooling time. The angle θ formed by the acting direction of the load P may be a minute angle. In this case, the sliding frictional force generated between the rotating shaft 16 and the through hole on the air conditioning case 11 side can be reduced as in the first embodiment.

(Other embodiments)
(1) In each of the above embodiments, the rotation axis center B of the heater core 15 is set in the vehicle left-right direction (horizontal direction), but the setting direction of the rotation axis center B is not limited to the horizontal direction.

  That is, if the rotation axis center B is slightly tilted from the vertical direction, the rotational operation force becomes heavy due to the influence of the load W due to the heater core's own weight. However, by applying the present invention, the load W due to the heater core's own weight is offset. The rotational operation force can be reduced.

  (2) In the first embodiment, the bifurcated spring 28 is arranged so that the angle θ formed by the line segment S and the direction of action of the spring load P at the time of maximum cooling is a minute angle. The bifurcated spring 28 may be disposed so that the line segment S and the direction of action of the spring load P are completely parallel to each other.

  Specifically, by setting the position of the pin portion 11a of the air conditioning case 11 above the position in the first embodiment, the line segment S and the direction of action of the spring load P are completely parallel at the time of maximum cooling. It may be.

  (3) In each of the above embodiments, the rotary shaft 16 is set at the upper end portion 15a of the heater core 15, but the rotary shaft 16 may be set at an intermediate position in the vertical direction of the heater core 15.

  (4) 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.

  (5) In each of the above embodiments, the example in which the present invention is applied to the rotation operation mechanism of the heater core 15 in the vehicle air conditioner has been described. However, the present invention can be widely applied to various uses other than the vehicle air conditioner. Is.

It is a schematic longitudinal cross-sectional view of the indoor air-conditioning unit which shows 1st Embodiment of this invention. It is a principal part side view of the air-conditioning unit part which shows the time of the maximum heating of 1st Embodiment. It is a principal part side view of the air-conditioning unit part which shows the time of the maximum cooling of 1st Embodiment. It is a graph which shows the heater core rotational operation force reduction effect by 1st Embodiment. It is a principal part side view of the air-conditioning unit part which shows the time of the maximum heating of 2nd Embodiment. It is a principal part side view of the air-conditioning unit part which shows the time of the maximum cooling of 2nd Embodiment.

Explanation of symbols

15 ... heater core (heat exchanger for heating), 16 ... rotary shaft, 26 ... lever,
28 ... Bifurcated spring, 30 ... First arm, 31 ... Second arm, B ... Center of rotation axis,
D: contact (point of action), P: spring load, W: load due to the weight of the heater core, θ: angle.

Claims (7)

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,
The heating heat exchanger (15) is configured to rotate around the rotation axis (16) by a driving force from a driving device,
Furthermore, it has spring members (28, 32) that apply a spring load (P) to the heating heat exchanger (15),
The air conditioner characterized in that the spring load (P) cancels the load (W) due to the weight of the heating heat exchanger (15). When the heating heat exchanger (15) is rotated to a position where the load (W) is maximized, the center (B) of the rotating shaft (16) and the action point of the spring load (P) ( The angle (θ) formed by the line segment (S) connecting D) and the direction of action of the spring load (P) is maximized,
The air conditioner according to claim 1, wherein when the heating heat exchanger (15) is rotated in a direction in which the load (W) decreases, the angle (θ) changes in a direction in which the load (W) decreases. . When the heating heat exchanger (15) is rotated to a position where the load (W) is minimized, the spring member (28) is set so that the angle (θ) becomes a predetermined angle larger than 0 degrees. 32). The air conditioner according to claim 2, wherein the air conditioner is configured. A lever (26) coupled to the rotating shaft (16) and rotating in accordance with the rotation of the heating heat exchanger (15);
A bifurcated spring means (28), wherein the first arm (30) is pressed by the lever (26) and the second arm (31) is supported by the air conditioning case (11);
The spring member comprises the bifurcated spring means (28);
The action point of the spring load (P) is a contact point (D) between the first arm (30) and the lever (26),
The rotation operation mechanism according to claim 2 or 3, wherein the direction of action of the spring load (P) is a direction in which the first arm (30) presses the lever (26). A lever (26) coupled to the rotating shaft (16) and rotating in accordance with the rotation of the heating heat exchanger (15);
One end (34a) is pulled by the lever (26), and the other end (35a) is provided with a tension spring means (32) supported by the air conditioning case (11),
The spring member comprises the tension spring means (32);
The action point of the spring load (P) is a contact (D) between the one end (34a) and the lever (26),
The rotation operation mechanism according to claim 2 or 3, wherein the direction of action of the spring load (P) is a direction in which the one end (34a) pulls the lever (26). A rotating body (15) that rotates about a rotating shaft (16) by a driving force from a driving device;
A spring member (28, 32) that applies a spring load (P) to the rotating body (15);
The rotary operation mechanism, wherein the spring load (P) cancels a load (W) caused by the weight of the rotating body (15). When the rotating body (15) is rotated to a position where the load (W) due to the weight of the rotating body (15) becomes maximum, the center (B) of the rotating shaft (16) and the spring load (P The angle (θ) formed by the line segment (S) connecting the action point (D) and the action direction of the spring load (P) is maximized,
The rotation operation mechanism according to claim 6, wherein when the rotating body (15) is rotated in a direction in which the load (W) is decreased, the angle (θ) is decreased.

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