JP2007112247A - Air passage opening/closing device, and air-conditioner for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To satisfy both of the constant application of a spring load to a door, and the incorporation of the spring under a free state. <P>SOLUTION: A fork-like spring 41 is arranged in such a manner that the first arm section 41b and the second arm section 41c may be placed under a free state from an arm section deforming means 39b and an arm section return-preventing means 40c. After arranging the fork-like spring 41, by rotating second air passage opening/closing doors 26 and 260, the arm section deforming means 39b which is combined with the second air passage opening/closing doors 26 and 260 elastically deforms the second arm section 41c from the free state at a specified angle θ2 only. When the second arm section 41c is elastically deformed at the specified angle θ2 only, the second arm section 41c is fastened to the arm section return preventing means 40c. At the same time, the first arm section 41b presses first rotary shafts 25a, 25b and 252 side, and the spring load of the fork-like spring 41 is applied to the first air passage opening/closing doors 25 and 250 in a manner to cancel a door load by the door's self weight or an air pressure. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an air passage opening and closing device that opens and closes an air passage by a rotatable door and a vehicle air conditioner using the same, and more particularly, is suitable as a blowing mode switching mechanism in a vehicle air conditioning device. is there.

  The present inventor has previously proposed a vehicle air conditioner provided with a blowing mode switching mechanism shown in FIG. 17 in a patent application (hereinafter referred to as a prior application example) of Japanese Patent Application No. 2004-217112. In this prior application example, two rotary doors 25 and 26 are provided in the blowing mode switching mechanism that opens and closes the defroster opening 20, the face opening 21, and the foot opening 22.

  The two rotary doors 25 and 26 rotate about the rotation shafts 25b and 26b, respectively, and the outer door surface is located at a predetermined distance from the center of the rotation shafts 25b and 26b to the radially outward side. 25e and 26e are arranged, and both end portions in the axial direction of the outer peripheral door surfaces 25e and 26e are connected to the rotary shafts 25b and 26b.

  Thereby, the outer peripheral door surfaces 25e and 26e rotate integrally with the rotating shafts 25b and 26b. Of the two rotary doors 25 and 26, the first rotary door 25 located on the upstream side of the air flow opens and closes the inlet flow paths of the front foot opening 22 and the rear foot opening (not shown).

  Further, the defroster opening 20 and the face opening 21 are opened and closed by the second rotary door 26 located on the downstream side of the air flow. Further, the first rotary door 25 opens and closes the communication passage opening 27 in the upstream portion of the second rotary door 26 in conjunction with the opening and closing of the foot opening 22.

  FIG. 17 shows the face mode, and the first rotary door 25 fully closes the inlet passage of the foot opening 22 and simultaneously opens the communication passage opening 27. The second rotary door 26 fully closes the defroster opening 20 and simultaneously opens the face opening 21. As a result, the blown air in the case 11 passes through the communication passage opening 27 and the face opening 21 as indicated by the arrow Y, and blows out toward the passenger's upper body side in the passenger compartment.

  By the way, the gravity center positions at the rotational positions of the first and second rotary doors 25 and 26 shown in FIG. 17 are G1 and G2, respectively, and the loads W1 and W2 of the door's own weight are below the gravity center positions G1 and G2, respectively. Acts on. As a result, axial moments M1 and M2 centering around the first and second rotary shafts 25b and 26b act on the first and second rotary doors 25 and 26, respectively.

  Accordingly, when the first and second rotary doors 25 and 26 are rotated in the directions K and N opposite to the directions of the axial moments M1 and M2, the door operating force increases due to the influence of the axial moments M1 and M2. The problem arises.

  In order to solve this problem, in the prior application example, a bifurcated spring 41 that contacts the drive levers 38 and 39 coupled to the first and second rotating shafts 25b and 26b of the doors 25 and 26 is disposed. As a result, spring loads P1 and P2 in opposite directions to the axial moments M1 and M2 are applied to the doors 25 and 26, respectively.

  The spring loads P1 and P2 cancel the shaft moments M1 and M2 based on the influence of the door's own weight, thereby suppressing an increase in the door operating force.

  FIG. 18 is a graph for explaining the relationship between the door self-weight canceling action and the blowing mode switching according to the prior application example. In FIG. 18, the “total load due to the door's own weight” indicated by the two-dot chain line is the total value of the loads W1 and W2 due to the door's own weight, and the spring total load indicated by the broken line is the total value of the aforementioned spring loads P1 and P2 The “canceling load of the spring load and the door's own weight” indicated by is a load after the offset between the total load due to the door's own weight and the spring total load.

  In the prior application example, as shown by the solid line in FIG. 18, the load after cancellation of the total load due to the door's own weight and the total spring load can be suppressed to a small value (half or very small amount) through the full blowing mode.

  In the example of the prior application, as shown by a point Z in FIG. 18, when the blowing mode is the foot mode, the spring is in a free state and the total spring load is zero. For this reason, the spring can be easily assembled by assembling the spring in the foot mode state.

  In the example of the prior application, the driving force from one manual operation mechanism is transmitted to the two rotary doors 25 and 26 via the link device shown in FIG. It is designed to rotate.

  Specifically, two drive groove portions 42d and 42e are formed in one link plate 42 that is rotated by an occupant's operation force applied via a manual operation mechanism, and two drive groove portions 42d and 42e are provided with 2 The drive pins 38c and 39c of the two drive levers 38 and 39 are slidably fitted, and the rotational displacements of the two drive levers 38 and 39 are transmitted to the two rotary doors 25 and 26, respectively. The two rotary doors 25 and 26 are rotated.

  However, according to the detailed examination by the present inventors, it has been found that the door operating force cannot be sufficiently reduced in the prior application example for the following reason.

  That is, in the prior application example, for the purpose of realizing a predetermined operation of one rotary door 25, the distance D1 between the portion corresponding to the foot mode (point e) in one drive groove and the rotation axis 42a of the link plate is as follows. It is getting shorter. In other words, the distance from the fulcrum to the action point in the lever principle is shortened.

  For this reason, in the foot mode, a large driving force must be applied to the link plate 42 in order to counteract the load after the total load due to the door's own weight and the spring total load cancel each other, so that the door operating force increases.

  In FIG. 19 of the prior application example, the total load due to the weight of the door in the bi-level mode and the load after the cancellation of the spring total load are larger than in the foot mode, but the drive groove corresponds to the bi-level mode. The distance D3 between the portion (point i) and the rotation axis 42a of the link plate is longer than the distance D1. In other words, since the distance from the fulcrum to the action point in the lever principle is long, the door operating force does not increase.

  In order to solve this problem, the above-described distance D1 may be increased. However, in the prior application example, the above-described distance D1 cannot be increased for the purpose of realizing a predetermined operation of the rotary door 25.

  Therefore, a measure to suppress the load after offsetting the total load due to the door's own weight in the foot mode and the spring total load to a smaller value can be considered, but in the prior application example, as described above, in the foot mode, the total spring There is a problem that the load is zero and the weight of the door cannot be offset.

  Therefore, a measure to apply the spring load even in the foot mode can be considered. However, according to this measure, the spring cannot be assembled in a free state, and the spring is bent while receiving the reaction force of the spring. Since it must be assembled, there arises a problem that the assemblability of the spring deteriorates.

  Moreover, when the assembly | attachment property of a spring deteriorates, since the complicated installation is needed at the time of automatic assembly | attachment, the problem that automatic assembly | attachment becomes difficult also arises.

  In FIG. 17, since the rotary doors 25 and 26 whose outer peripheral door surfaces 25e and 26e rotate in a direction orthogonal to the air flow are used as door means for opening and closing the air passage, the door operating force is caused by the wind pressure of the air flow. There is no increase.

  On the other hand, when using a cantilever plate door with a rotating shaft at the end of the plate door body as door means for opening and closing the air passage, the plate door body is rotated against the wind pressure of the air flow. There is a problem that the door operating force is increased due to wind pressure.

  In view of the above points, an object of the present invention is to satisfy both of the fact that a spring load always acts on a door and that the spring is assembled in a free state.

In order to achieve the above object, the present invention includes a plurality of air passages (20 to 23, 27),
First and second winds configured to be rotatable about first and second rotation shafts (25a, 25b, 26a, 26b, 252 and 262), respectively, and open and close a plurality of air passages (20 to 23 and 27). Road opening and closing doors (25, 26, 250, 260);
A bifurcated spring means disposed near the intermediate position of the first and second rotating shafts (25a, 25b, 26a, 26b, 252, 262) and having a first arm part (41b) and a second arm part (41c) (41)
Arm deformation means (39b) coupled to the second rotation shaft (26a, 26b, 262);
Arm position return prevention means (40c) that does not move,
The bifurcated spring means (41) is such that the first arm part (41b) and the second arm part (41c) are in a free state with respect to the arm part deforming means (39b) and the arm part return preventing means (40c). Placed in
After the bifurcated spring means (41) is arranged, the second air passage opening / closing door (26, 260) is rotated so that the arm deforming means (39b) causes the second arm part (41c) to move from the free state to a predetermined angle ( It is elastically deformed by θ2)
When the second arm portion (41c) is elastically deformed by a predetermined angle (θ2), the second arm portion (41c) is locked to the arm portion return prevention means (40c),
In a state where the second arm portion (41c) is elastically deformed by a predetermined angle (θ2), the first arm portion (41b) presses the first rotating shaft (25a, 25b, 252) side to open and close the first air path. The spring load of the bifurcated spring means (41) acts on the door (25, 250) so as to cancel the door load due to the door's own weight or wind pressure.

  According to this, since the first arm portion (41b) and the second arm portion (41c) of the bifurcated spring means (41) are arranged in a free state, the bifurcated spring means (41) can be easily assembled. it can.

  Then, after the bifurcated spring means (41) is arranged, when the second air passage opening / closing door (26, 260) is rotated, the second arm part (41c) is moved by a predetermined angle (θ2) by the arm part deforming means (39b). Since the second arm portion (41c) is locked to the arm portion return prevention means (40c), the second arm portion (41c) is held elastically deformed by a predetermined angle (θ2). Can do. For this reason, the spring load by the bifurcated spring means (41) can always be generated.

  Of the bifurcated spring means (41), the first arm portion (41b) presses the first rotating shaft (25a, 25b, 252) side to the first air passage opening / closing door (25, 250). Since the spring load of the bifurcated spring means (41) acts so as to cancel the door load due to the door's own weight or wind pressure, the spring load can always be applied to the first air passage opening / closing door (25, 250). it can.

  As a result, it is possible to achieve both a constant spring load acting on the door and the assembly of the spring in a free state.

Specifically, in the present invention, when the rotational operation position of the first air passage opening / closing door (25, 250) at which the door load of the first air passage opening / closing door (25, 250) is minimum is set as the minimum door load position. ,
The bifurcated spring means (41) may be arranged in a free state in a state where the first airway opening / closing door (25, 250) is arranged at the minimum door load position.

  Further, according to the present invention, when the first airway opening / closing door (25, 250) is rotated at the minimum door load position, the spring load due to the elastic deformation of the second arm portion (41c) is changed to the first door load position at the minimum door load position. The door load of one airway opening / closing door (25, 250) is offset.

  As a result, when the first airway opening / closing door (25, 250) is rotated to the minimum door load position, the load after the cancellation of the spring load and the door load can be made substantially zero.

The present invention specifically includes a case (11) in which a plurality of air passages (20 to 23, 27) are formed and the first and second air passage opening / closing doors (25, 26, 250, 260) are incorporated. )
The bifurcated spring means (41) is arranged on the outer surface side of the case (11),
A second lever (39) that is coupled to the second rotation shaft (26a, 26b, 262) and rotationally drives the second air passage opening / closing door (26, 260) is disposed on the outer surface side of the case (11),
A second arm pressing portion (39b) that forms an arm deforming means is provided on the second lever (39),
A stopper (40c) that forms an arm return prevention means is formed so as to protrude from the outer surface of the case (11) in a direction substantially perpendicular to the rotation surface of the second lever (39),
An inclined surface (40d) is formed on the tip surface of the stopper (40c),
The inclined surface (40d) is formed so that the protruding height on the side approaching the second arm portion (41c) is low and the protruding height on the side far from the second arm portion (41c) is high.
After the bifurcated spring means (41) is arranged, the second arm pressing portion (39b) presses the second arm (41c) toward the stopper (40c) as the second lever (39) rotates,
By this pressing, the second arm portion (41c) abuts on the inclined surface (40d), then projects the inclined surface (40d) and slides from the lower side to the higher side to stop the stopper (40c). It is also possible to get over the front end side of the stopper and to be engaged with the outer peripheral surface of the stopper (40c) while being elastically deformed by a predetermined angle (θ2).

In the present invention, the bifurcated spring means (41) is arranged such that the second arm portion (41c) in a free state is in contact with or close to the second arm portion pressing portion (39b),
When the second arm pressing portion (39b) presses the second arm portion (41c) toward the stopper (40c) with the rotation of the second lever (39), the second arm pressing portion (39b) It slides against the two arms (41c),
When the second arm part (41c) is locked to the stopper (40c), the second arm part has a relief part (39d) for separating the second arm part pressing part (39b) and the second arm part (41c). It forms in a part press part (39b).

  According to this, when the second arm portion (41c) is locked to the stopper (40c), the second arm portion pressing portion (39b) and the second arm portion (41c) are separated from each other. ) Is locked to the stopper (40c), the second arm portion pressing portion (39b) can be swung without contacting the second arm portion (41c).

  Therefore, after the second arm portion (41c) is locked to the stopper (40c), the second arm portion (41c) is kept in the same position without being deformed in accordance with the rotation operation of the second lever (39). While being able to hold | maintain, it can avoid that a 2nd arm part press part (39b) interferes with a 2nd arm part (41c), and prevents rotation of a 2nd lever (39).

Further, in the present invention, the second arm pressing portion (39b) is formed so as to protrude from the second lever (39) in substantially the same direction as the stopper (40c),
A protruding portion (39e) that protrudes in a direction substantially perpendicular to the protruding direction is formed at the tip of the second arm portion pressing portion (39b),
When the second arm portion pressing portion (39b) presses the second arm portion (41c) toward the stopper (40c), the protruding portion (39e) passes through the tip end side of the stopper (40c).

  According to this, when the 2nd arm part press part (39b) presses the 2nd arm part (41c) to the stopper (40c) side, the 2nd arm flipped up by the inclined surface (40d) of the stopper (40c) Since the portion (41c) abuts on the protruding portion (39e), the second arm portion (41c) gets over the second arm portion pressing portion (39b) and comes off the second arm portion pressing portion (39b). Can be prevented.

In the present invention, specifically, on the outer surface side of the case (11), the first air passage opening / closing door (25, 250) coupled to the first rotation shaft (25a, 25b, 252) is rotationally driven. Place one lever (38)
The first lever (38) is provided with a first arm portion pressing portion (38b),
As the first lever (38) rotates, the first arm pressing portion (38b) rotates, so that the first arm (41b) is pressed by the first arm pressing portion (38b) and elastically deforms. It may be.

Further, in the present invention, when the rotational operation position of the first airway opening / closing door (25, 250) that maximizes the door load is set as the maximum door load position,
When the first air passage opening / closing door (25, 250) is rotated at the maximum door load position, in addition to the elastic deformation of the second arm portion (41c), the first arm portion (41b) is elastically deformed, The spring load due to the elastic deformation of the first arm portion (41b) and the second arm portion (41c) cancels the door load of the first airway opening / closing door (25, 250) at the maximum door load position. .

  As a result, when the first airway opening / closing door (25, 250) is rotated at the maximum door load position, the load after canceling out the spring load and the door load can be made substantially zero.

Further, the present invention provides a link plate (42) that is disposed on the outer surface side of the case (11) and is rotated about the rotation shaft (42a),
A first drive groove (42d) and a second drive groove (42e) provided in the link plate (42);
A first drive pin (38c) provided on the first lever (38) is slidably fitted into the first drive groove (42d),
A second drive pin (39c) provided on the second lever (39) is slidably fitted into the second drive groove (42e).

  According to this, when the link plate (42) is rotated, the rotational driving force can be transmitted to both the first lever (38) and the second lever (39). Therefore, the door operating force is transmitted to the first air passage opening / closing door (25, 250) and the second air passage opening / closing door (26, 260), and the first air passage opening / closing door (25, 250) and the second air passage opening / closing door. The air passage opening / closing doors (26, 260) can be operated in conjunction with each other.

  In the present invention, the minimum distance (D2) between the second drive groove (42e) and the rotation shaft (42a) is the minimum distance between the first drive groove (42d) and the rotation shaft (42a) ( It is set larger than D1).

  According to this, on the second drive groove (42e) side, the distance from the fulcrum to the action point in the lever principle can be increased as compared with the first drive groove (42d) side. For this reason, the driving force applied to the link plate (42) may be small in order to counter the load of the second air passage opening / closing door (26, 260) due to its own weight or wind pressure.

  In other words, the influence of the load of the second air passage opening / closing door (26, 260) due to its own weight or wind pressure on the door operating force is small, and the load of the first air passage opening / closing door (25, 250) due to its own weight or wind pressure is small. The influence of has become dominant.

  As a result, the door operating force is increased by the spring load of the bifurcated spring means (41) acting on only the first airway opening / closing door (25, 250) so as to cancel the load due to the door's own weight or wind pressure. Can be suppressed.

Further, in the present invention, one end side in the axial direction of the circular coil portion (41a) of the bifurcated spring means (41) is disposed on the outer surface side of the case (11),
On the other end side in the axial direction of the circular coil portion (41a), a spring pressing portion (42c) formed integrally with the link plate (42) is disposed,
A gap (43) having a predetermined dimension is formed between the other axial end of the circular coil portion (41a) and the spring pressing portion (42c).

  According to this, when the second arm portion (41c) rides on the stopper (40c) while sliding on the inclined surface (40d), the circular coil portion (41a) also has the same direction as the riding direction of the second arm portion (41c). Since the spring pressing portion (42c) is disposed on the other end side in the axial direction of the circular coil portion (41a), that is, the side on which the circular coil portion (41a) is to be lifted, the circular coil portion (41a) is circular. The coil part (41a) contacts the spring pressing part (42c).

  As a result, the movement of the circular coil portion (41a) is restricted, and the second arm portion (41c) is elastically deformed in the riding-up direction, so that a spring reaction force is generated in the second arm portion (41c). Therefore, when the second arm portion (41c) gets over the stopper (40c), the second arm portion (41c) can be accommodated on the base side of the stopper (40c) by its own spring reaction force. As a result, the second arm portion (41c) can be reliably locked to the stopper (40c).

  Further, since the spring pressing portion (42c) is formed on the link plate (42), the link plate (42) can also be used as the spring pressing means of the bifurcated spring means (41). Therefore, the dedicated spring pressing means for the bifurcated spring means (41) can be eliminated.

  Further, since a gap (43) having a predetermined dimension is formed between the spring pressing portion (42c) and the other axial end of the circular coil portion (41a), the second arm portion (41c) is provided as a stopper (40c). After the locking, the spring pressing portion (42c) and the bifurcated spring means (41) can be prevented from coming into contact with each other when the link plate (42) rotates, thereby generating sliding resistance.

In the present invention, the first lever (38) is integrally formed with the first arm pressing portion (38b) and the first drive pin (38c).
The second lever (39) is integrally formed with a second arm pressing portion (39b) and a second drive pin (39c),
The integrated first lever (38) and the integrated second lever (39) have the same shape.

  Thereby, parts can be shared by the first lever (38) and the second lever (39), and the cost can be reduced.

  Further, the present invention provides an outer periphery in which the first and second air passage opening / closing doors are located at a site separated by a predetermined amount from the center of the first and second rotating shafts (25a, 25b, 26a, 26b) radially outward. It can be comprised with the rotary door (25, 26) which has a door surface (25e, 26e), and an outer peripheral door surface (25e, 26e) rotates in the direction orthogonal to an air flow.

  When the airway opening / closing door is constituted by the rotary doors (25, 26) whose outer door surfaces (25e, 26e) rotate in a direction orthogonal to the air flow in this way, the operation by the weight of the first rotary door (25) is performed. The increase in force can be effectively suppressed by the bifurcated spring means (41).

  Further, according to the present invention, the first and second airway opening / closing doors are cantilever plate doors in which the first and second rotating shafts (252, 262) are arranged at end portions of the plate door main body portions (251, 262) 250, 260).

  When a cantilever door is used in this way, the door operating force increases due to the influence of both wind pressure and the door's own weight as illustrated in FIG. 16 described later, but the door operating force increases due to both the wind pressure and the door's own weight. Can be effectively suppressed by the bifurcated spring means (41).

Further, the present invention includes the above-described air passage opening and closing device according to the present invention,
As a plurality of air passages, a plurality of outlet openings (20 to 23) for blowing out air to different parts in the passenger compartment are included,
The first and second air passage opening / closing doors are configured as blowing mode doors that open and close a plurality of blowing openings (20 to 23).

  Thereby, the increase in the operating force of the blowing mode door of the vehicle air conditioner can be effectively suppressed by the bifurcated spring means (41).

  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)
The first embodiment of the present invention will be described below. FIG. 1 shows an air conditioning unit 10 that houses a heat exchanger part among the indoor unit parts in the vehicle air conditioner of the first embodiment. FIG. 1 is a cross-sectional view showing only the blowing mode switching mechanism.

  The air conditioning unit 10 is disposed at a substantially central portion in the vehicle left-right (width) direction inside an instrument panel (not shown) at the front of the vehicle interior. Note that the up and down arrows in FIG. 1 indicate directions in a vehicle-mounted state.

  The indoor unit portion of the vehicle air conditioner is roughly divided into the air conditioning unit 10 at the substantially central portion and a blower unit (not shown) that is offset on the passenger seat side inside the instrument panel.

  The blower unit includes an inside / outside air switching box that switches and introduces outside air (outside air in the passenger compartment) or inside air (air inside the cabin), and a centrifugal blower that blows air introduced into the inside / outside air switching box. The blown air from the blower unit flows into the lowermost air inflow space 12 in the case 11 of the air conditioning unit 10.

  The case 11 is formed of a resin having elasticity like polypropylene and high mechanical strength. Specifically, the case 11 is divided into a plurality of divided cases for the convenience of die cutting for molding, the reasons for assembling the air conditioner in the case, and the like. It is configured to be fastened.

  In the case 11 of the air conditioning unit 10, an evaporator 13 that forms a cooling heat exchanger is disposed substantially horizontally with a small inclination angle above the air inflow space 12. Accordingly, the blown air of the blower unit flows into the air inflow space 12 and then passes from the space 12 through the evaporator 13 from below to above. As is well known, low-pressure refrigerant decompressed by a decompression device such as an expansion valve of a refrigeration cycle for vehicle air conditioning flows into the evaporator 13, and the low-pressure refrigerant absorbs heat from the blown air and evaporates.

  An air mix door 14 and a hot water heater core 15 serving as a heating heat exchanger are disposed above the evaporator 13 (on the downstream side of the air flow). Here, the air mix door 14 is configured by a cantilever plate door that rotates about a rotation shaft 14a.

  As is well known, the heater core 15 heats air using warm water (cooling water) of the vehicle engine as a heat source, and the heater core 15 is also arranged in a substantially horizontal direction, that is, substantially parallel to the evaporator 13.

  However, the heater core 15 is smaller than the passage cross-sectional area in the case 11 and is disposed in the case 11 so as to be biased toward the vehicle front side. As a result, a cool air passage 16 is formed on the vehicle rear side of the heater core 15 (part near the passenger seat) to bypass the heater core 15 and through which air (cold air) flows.

  The air mix door 14 rotates in the vehicle front-rear direction between the evaporator 13 and the heater core 15 to open and close the inlet air passage 15 a and the cold air passage 16 of the heater core 15. As a result, the air volume ratio between the warm air (arrow A) heated through the heater core inlet air passage 15a and the cold air (arrow B) passing through the cool air passage 16 is adjusted, and the temperature of the air blown into the vehicle interior is adjusted. Can be adjusted. Therefore, the air mix door 14 constitutes temperature adjusting means for the air blown into the vehicle interior.

  The rotary shaft 14a of the air mix door 14 is rotatably supported by bearing holes (not shown) on the left and right side wall portions of the case 11, and one end of the rotary shaft 14a protrudes outside the case 11 to allow air mixing. Connected to the door operation mechanism. As the air mix door operation mechanism, either a manual operation mechanism manually operated by a passenger or an actuator mechanism using a motor may be used.

  A hot air guide wall 17 is formed integrally with the case 11 at a predetermined interval above the heater core 15, and a hot air passage 18 is formed between the hot air guide wall 17 and the upper surface of the heater core 15. . The warm air that has passed through the heater core 15 is guided by the warm air guide wall 17 and flows in the warm air passage 18 toward the rear side of the vehicle as indicated by an arrow A.

  An air mixing unit 19 that mixes the warm air A flowing through the warm air passage 18 toward the rear side of the vehicle and the cool air B rising through the cold air passage 16 is formed in the upper portion of the cold air passage 16.

  A defroster opening 20 is opened in a vehicle front side portion of the upper surface portion of the case 11, and a face opening portion 21 is opened in a vehicle rear side portion of the defroster opening portion 20 in the upper surface portion of the case 11. Both the defroster opening 20 and the face opening 21 have a rectangular shape. More specifically, the defroster opening 20 and the face opening 21 have a rectangular shape having a long side in the vehicle left-right direction and a short side in the vehicle front-rear direction.

  Here, the defroster opening 20 is for blowing the conditioned air from the air mixing unit 19 toward the inner surface of the vehicle front glass through a defroster duct (not shown). The face opening 21 is for blowing out the conditioned air from the air mixing unit 19 toward the upper body of the occupant through a face duct (not shown).

  Front foot openings 22 are opened in side walls on the left and right sides of the case 11. More specifically, the front foot opening 22 is located at a position adjacent to the vehicle rear side wall surface 11a in the left and right side wall portions of the case 11 and in the vicinity of the air mixing portion 19 in the vehicle vertical direction. It is open. The front foot openings 22 on the left and right sides are for blowing the conditioned air from the air mixing unit 19 toward the feet of the front seat occupants (driver and passenger occupants).

  A rear foot opening 23 is disposed on the wall 11 a below the front foot opening 22 and on the vehicle rear side of the case 11. The rear foot opening 23 blows out the conditioned air from the air mixing unit 19 toward the feet of the rear seat occupant.

  The rear foot opening 23 and the front foot opening 22 are always connected by a rear foot passage 24. The rear foot passage 24 is formed between a wall surface 11a on the vehicle rear side of the case 11 and a cold air passage wall surface 11b located on the inner side (vehicle front side) of the wall surface 11a.

  In the present embodiment, the blowing mode switching mechanism is constituted by the first and second rotary doors 25 and 26. The first rotary door 25 opens and closes the inlet passages of the front foot opening 22 and the rear foot opening 23, and the second rotary door 26 opens and closes the defroster opening 20 and the face opening 21.

  In the case 11, a communication path opening 27 is formed adjacent to the front side of the front foot opening 22 in the vehicle, and the defroster opening 20 and the face opening 21 are connected via the communication path opening 27. It communicates with the air mixing section 19. The first rotary door 25 opens and closes the communication passage opening 27 as the inlet passages of both foot openings 22 and 23 open and close.

  Although the first and second rotary doors 25 and 26 have different external dimensions, the door configuration is basically the same. Accordingly, a specific example of the rotary door configuration will be described with reference to FIG. 2 taking the first rotary door 25 as an example. In FIG. 2, the reference numeral of the second rotary door 26 is shown in parentheses, and a specific description of the second rotary door 26 is omitted. The first rotary door 25 integrally includes left and right first rotary shafts 25a and 25b, left and right fan-shaped side plate portions 25c and 25d, and an outer peripheral door surface 25e.

  The left and right first rotating shafts 25a and 25b are formed so as to protrude outward in the left and right at the fan-shaped key positions of the left and right side plate portions 25c and 25d, and are rotatably supported by the left and right side wall portions 11c of the case 11.

  Then, by joining the outer peripheral door surface 25e to the outer peripheral end portions of the left and right fan-shaped side plate portions 25c, 25d, the left and right fan-shaped side plate portions 25c, 25d and the outer peripheral door surface 25e are gate-shaped (U-shaped). ). Since the inner space of this gate shape is always open to the space in the case 11 as it is, air can freely flow through the inner space of the gate shape in the direction of arrow C (direction perpendicular to the rotation axis direction). It has become.

  The outer peripheral door surface 25e is located at a position away from the center of the first rotary shafts 25a and 25b by a predetermined amount in the radial direction (radially outward side) of the first rotary shafts 25a and 25b, and extends in the door rotating direction. A predetermined wall area is formed. More specifically, the outer peripheral door surface 25e of the present embodiment has an arcuate cross-sectional shape (see FIG. 1) centered on the first rotation shafts 25a and 25b, and the upper surface shape of the outer peripheral door surface 25e is The vehicle left-right direction has a long side and the vehicle front-rear direction has a short side.

  The passage opening / closing function can be exhibited even if the outer peripheral door surface 25e is formed in a flat plate shape instead of an arc shape.

  The first rotary door 25 has an overall shape including the above-described first rotary shafts 25a and 25b, fan-shaped side plate portions 25c and 25d, and an outer peripheral door surface 25e. It is integrally formed with a resin having elasticity.

  Next, the seal structure in the first rotary door 25 will be described. The door seal structure is a lip seal type to reduce door operation force. And the 1st seal | sticker part 25f is provided in the site | part by the side of the front foot opening part 22 among the peripheral surface of the outer peripheral door surface 25e and the side-plate parts 25c and 25d which comprise a door board | substrate part, and the site | part by the side of the communicating path opening part 27 side. The second seal portions 25g are fixed to each other.

  Both the seal portions 25f and 25g are made of an elastic body, and protrude in a lip shape (thin plate shape) with a substantially V-shaped cross-section from the door peripheral surface to the outside. As shown in FIG. 2, when viewed from the air flow direction C inside the rotary door, the overall shape of both seal portions 25 f and 25 g constitutes a portal shape (a U-shape) similar to the overall shape of the rotary door 25. To do.

  Further, as a specific material of both the seal portions 25f and 25g, the door of the first rotary door 25 can be formed by using a thermoplastic elastomer that can be molded like a thermoplastic resin at a high temperature and has rubber elasticity at a normal temperature. Both seal portions 25f and 25g can be integrally formed when the substrate portion is formed.

  The second rotary door 26 of the present embodiment also has second rotary shafts 26 a and 26 b and parts 26 c to 26 g corresponding to the parts 25 a to 25 g of the first rotary door 25 described above, and has the same configuration as the first rotary door 25. It has become.

  Next, the case-side seal surfaces 28 to 35 where the seal portions 25f, 25g, 26f, and 26g of the first and second rotary doors 25 and 26 are in pressure contact will be described. Of the inner wall of the case 11, foot-side seal surfaces 28 and 29 are provided at positions above and below the front foot opening 22, and communication path-side seal surfaces 30 and 31 are provided at positions before and after the communication path opening 27. It has been.

  Further, in the inner wall of the case 11, defroster side seal surfaces 32 and 33 are provided at positions before and after the defroster opening 20, and face side seal surfaces 34 and 35 are provided at positions before and after the face opening 21. ing.

  The above-described seal surfaces 28, 29, 30, 31 on the foot side and the communication path side are formed in a portal shape corresponding to the portal shape of the seal portions 25f, 25g of the first rotary door 25. ˜31, the seal portions 25f and 25g of the first rotary door 25 are elastically deformed to come into pressure contact.

  Similarly, the defroster side and face side seal surfaces 32, 33, 34, and 35 are formed in a gate shape corresponding to the gate shape of the seal portions 26f and 26g of the second rotary door 26, and the seal surfaces 32- 35, the seal portions 26f and 26g of the second rotary door 26 are elastically deformed to be in pressure contact with each other.

  Next, a specific configuration of the blowing mode switching mechanism that characterizes the present embodiment will be described with reference to FIGS. 3 is an exploded perspective view of the blowing mode switching mechanism, FIG. 4 is a perspective view of the assembled state of the main part of FIG. 3, and FIG. 5 is a sectional view of the assembled state of the blowing mode switching mechanism.

  The side wall 11c of the case 11 shown in FIGS. 3 and 5 is the side wall 11c on the right side of the vehicle shown in FIG. 1. The case side wall 11c includes first and second rotary doors 25 and 26. Bearing holes 36 and 37 are formed corresponding to the second rotating shafts 25b and 26b, respectively. The first and second rotating shafts 25b and 26b are rotatably supported in the bearing holes 36 and 37, respectively, and the tip ends of the first and second rotating shafts 25b and 26b protrude to the outside of the case side wall portion 11c. Yes.

  The same anti-rotation shape which consists of non-circular shape is formed in the front-end | tip part of the 1st, 2nd rotating shaft 25b, 26b, respectively. The first and second levers 38 and 39 are provided with non-circular shaft fixing holes 38a and 39a corresponding to the anti-rotation shapes of the first and second rotating shafts 25b and 26b. The first and second rotary shafts 25b and 26b and the first and second levers 38 and 39 are fixed to the shaft fixing holes 38a and 39a by rotating the tip portions of the first and second rotary shafts 25b and 26b. Are fixed together.

  The first and second levers 38 and 39 are both resin members having a triangular plate shape. In this example, the first and second levers 38 and 39 are formed in the same shape. The first and second levers 38 and 39 are formed with shaft fixing holes 38a and 39a near one vertex in the triangular plate shape, and the first and second spring pressing portions 38b and 39b near the other two vertexes. The first and second drive pins 38c and 39c are integrally formed. Among these, the first and second drive pins 38c and 39c are formed so as to protrude from the first and second levers 38 and 39 toward the outside of the case side wall 11c, respectively.

  The first and second spring pressing portions 38b and 39b are formed in a substantially flat plate shape protruding from the first and second levers 38 and 39 toward the outer side of the case side wall portion 11c. In addition, the 2nd spring press part 39b corresponds to the arm part deformation | transformation means in this invention.

  Part of the substantially flat plate-like first and second spring pressing portions 38b, 39b is arranged so as to protrude outward from the triangular plate-like side of the first and second levers 38, 39.

  Of the first and second spring pressing portions 38b and 39b, the first and second spring pressing portions 38b and 39b are portions that protrude outward from the first and second levers 38 and 39. In the base side portion, inclined surfaces 38d, 39d are formed which are inclined toward the first and second levers 38, 39 side. Of the inclined surfaces 38d and 39d, the inclined surface 39d of the second spring pressing portion 39b corresponds to a relief portion in the present invention.

  Further, of the first and second spring pressing portions 38b and 39b, a portion that protrudes outward from the first and second levers 38 and 39, and is a front end portion in the outer side direction of the case side wall portion 11c. Are formed with projecting portions 38e and 39e that project further outward from the first and second levers 38 and 39, respectively.

  On the other hand, in the case side wall portion 11c, a mounting boss 40 is provided in the vicinity of an intermediate position between the two bearing holes 36 and 37 (first and second rotating shafts 25b and 26b). The mounting boss 40 has a cylindrical shape and is integrally formed with the case side wall portion 11c so as to protrude outward from the case side wall portion 11c.

  The mounting boss 40 serves both as a mounting portion for the bifurcated spring 41 and as a mounting portion for the blowing mode link plate 42.

  The bifurcated spring 41 is composed of a circular coil portion 41a fitted to the cylindrical outer peripheral surface of the mounting boss 40, and first and second arm portions 41b and 41c for pin holding. The first and second arm portions 41b and 41c protrude from the circular coil portion 41a in opposite directions. One first arm portion 41b is linearly drawn in the tangential direction of the circular coil portion 41a, while the other second arm portion 41c is drawn out in a bent shape with a step portion 41d described later. Yes.

  On the outer peripheral surface of the mounting boss 40, a large number of ribs 40a extending in the axial direction of the cylindrical shape are formed uniformly in the circumferential direction of the cylindrical shape. The plurality of ribs 40a are for setting the inner diameter of the circular coil portion 41a to a value larger by a predetermined amount than the outer diameter of the mounting boss 40. The recesses between the plurality of ribs 40a are resin-molded stealing spaces. Form. The rib 40a is formed in an L shape, and an axial end portion (the lower end portion in FIGS. 4 and 5) of the circular coil portion 41a is supported by an L-shaped base portion (base portion) 40b.

  In the case side wall 11c, a stopper 40c is provided in the vicinity of an intermediate position between the mounting boss 40 and the second rotating shaft 26b. The stopper 40c has a pillar shape protruding outward from the case side wall 11c, and is integrally formed with the case side wall 11c.

  An inclined surface 40d is formed at the distal end surface of the stopper 40c, and the inclined surface 40d has a low protruding height on the side closer to the second arm portion 41c of the bifurcated spring 41 and moves away from the second arm portion 41c. It is formed so that the protruding height on the side is increased. The stopper 40c corresponds to the arm return prevention means in the present invention.

  The circular coil portion 41a of the bifurcated spring 41 is fitted onto the cylindrical outer peripheral surface of the mounting boss 40 from the position of the two-dot chain line in FIG. At this time, the first and second arm portions 41b and 41c at both ends of the circular coil portion 41a are opposed to the outer peripheral surfaces of the first and second spring pressing portions 38b and 39b of the first and second levers 38 and 39. Just touch (hit).

  This allows the contact positions of the first and second spring pressing portions 38b and 39b and the first and second arm portions 41b and 41c to be changed with the rotational displacement of the first and second levers 38 and 39. Because.

  On the other hand, the blowing mode link plate 42 is a resin-made disk-shaped member, and a rotation shaft 42a is integrally formed at the center thereof, and the rotation shaft 42a is rotatably fitted to the inner periphery of the cylindrical mounting boss 40. It is supposed to be.

  A plurality of (for example, three) locking claws 42b protrude from the distal end portion of the rotating shaft 42a, and the locking claw 42b is elastically locked to the hole end surface 40e of the mounting boss 40 to blow out the air. The mode link plate 42 is attached to the attachment boss 40.

  Further, in the blowing mode link plate 42, an annular spring pressing portion 42c having an outer diameter larger than that of the rotating shaft 42a is integrally formed at the base portion of the rotating shaft 42a. A gap 43 having a predetermined size is set between the annular spring pressing portion 42c and the other axial end portion (the upper end portion in FIGS. 4 and 5) of the circular coil portion 41a of the bifurcated spring 41. This prevents the bifurcated spring 41 from falling off and reduces the sliding resistance generated when the bifurcated spring 41 rotates.

  Therefore, the bifurcated spring 41 can be attached to the attachment boss 40 using the blowing mode link plate 42 itself without requiring a dedicated attachment member.

  In the bifurcated spring 41, the drawing position of the right second arm portion 41c is lower than the drawing position of the left first arm portion 41b depending on the axial dimension of the circular coil portion 41a as shown in FIG. Therefore, a step portion 41d that corrects (eliminates) the displacement of the drawing position is formed in the second arm portion 41c on the right side, and the positions of the distal end sides of the left and right first and second arm portions 41b and 41c are set in the spring axis direction. To the same position. Thereby, the 1st, 2nd levers 38 and 39 can be made into the same shape.

  The blow mode link plate 42 has first and second drive grooves 42d and 42e. As shown in FIG. 5, the first and second drive groove portions 42d and 42e have a concave cross-sectional shape that opens toward the case side wall portion 11c. Further, as shown in FIG. 3, the first and second drive groove portions 42d and 42e are formed to extend in the vicinity of the outer edge portion of the blowing mode link plate 42 in a substantially circumferential direction.

  The first drive pin 38c of the first lever 38 is slidably fitted inside the first drive groove 42d, and the second drive pin 39c of the second lever 39 slides inside the second drive groove 42e. It is possible to fit. At the bases of the first and second drive pins 38c and 39c, columnar support portions 38g and 39g having a larger outer diameter than the first and second drive pins 38c and 39c are formed. The blowing mode link plate 42 is supported on the support portions 38g and 39g and rotates.

  Here, the first and second spring pressing portions 38b and 39b of the first and second levers 38 and 39 are slightly lower in height than the support portions 38g and 39g as shown in FIG. The first and second spring pressing portions 38b and 39b do not hinder the rotation of the blowing mode link plate 42.

  A gear 42 f is formed on the outer peripheral edge of the blowing mode link plate 42. A gear of a blow mode door operation mechanism (not shown) is engaged with the gear 42f to give a rotation operation force to the blow mode link plate 42. In this example, a manual operation mechanism is used as the blow-out mode door operation mechanism, in which an operation force is given by a passenger's manual operation. An actuator mechanism using a motor may be used as the blowout mode door operation mechanism instead of the manual operation mechanism.

  FIG. 6 shows a state immediately after the component parts are assembled to the case 11. The first rotary door 25 and the second rotary door 26 are assembled to the case 11 at the position in the face mode.

  Specifically, the first and second seal portions 25f and 25g of the first rotary door 25 are in contact with the case-side seal surfaces 29 and 31, respectively. On the other hand, the first and second seal portions 26f and 26g of the second rotary door 26 are in contact with the case-side seal surfaces 35 and 33, respectively.

  In this state, the first arm portion 41 b of the bifurcated spring 41 is only in contact (striking) with the outer peripheral surface of the first spring pressing portion 38 b of the first lever 38. The second arm portion 41 c only comes into contact with (subjects to) the substantially flat plate surface of the second spring pressing portion 39 b of the second lever 39.

  That is, since the first and second arm portions 41b and 41c of the bifurcated spring 41 are both in a free state, they can be easily assembled without bending the spring.

  The arrangement position of the bifurcated spring 41 in this state is a temporary arrangement position for facilitating the assembly of the bifurcated spring 41, and the effect of the bifurcated spring 41 is obtained when the vehicle air conditioner is operated. In order to exhibit, it is necessary to elastically deform the bifurcated spring 41 from a free state to a predetermined state.

  The predetermined state of the bifurcated spring 41 is a state in which the second arm portion 41c of the bifurcated spring 41 is caught by the stopper 40c as shown in FIG.

  Therefore, in this example, in order to hook the second arm portion 41c of the bifurcated spring 41 to the stopper 40c, the above-described components are assembled to the case 11, and then the blowing mode link plate 42 is rotated from the outside to rotate the second rotary. The door 26 is rotated to the position in the face mode shown in FIG.

  The operation of rotating the blowing mode link plate 42 from the outside may be performed manually in the state of the air conditioning unit 10 alone, or may be automatically performed by an industrial machine or the like. Moreover, you may perform by operation of the blowing mode door operation mechanism in the state which mounted the air conditioning unit 10 in the vehicle.

  In the face mode, the second rotary door 26 rotates clockwise by a predetermined angle from the position of FIG. 6, and the first and second seal portions 26f, 26g of the second rotary door 26 are respectively placed on the case-side seal surfaces 34, 32. It comes in pressure contact.

  At this time, with the rotational displacement of the second lever 39, the second spring pressing portion 39b rotates from the solid line position to the broken line position as indicated by an arrow H in FIG. Accordingly, the second arm portion 41c of the bifurcated spring 41 is pressed by the second spring pressing portion 39b and gets over the stopper 40c as indicated by an arrow J.

  The operation when the second arm portion 41c gets over the stopper 40c will be described more specifically. At the beginning of the rotation of the second spring pressing portion 39b, the second arm portion 41c and the flat plate surface of the second spring pressing portion 39b are substantially parallel, so the second arm portion 41c is pressed by the substantially flat plate surface of the second spring pressing portion 39b. Is done.

  As the second spring pressing portion 39b rotates, the second arm portion 41c slides on the inclined surface 40d of the stopper 40c and gradually rides on the inclined surface 40d, so that the second arm portion 41c in the second spring pressing portion 39b and The contact position moves. Specifically, the contact position of the second spring pressing portion 39b with the second arm portion 41c gradually moves from the root side to the tip side of the second spring pressing portion 39b.

  Further, at the time of initial assembly, the flat plate surface of the second spring pressing portion 39b is substantially parallel to the second arm portion 41c, but as the second spring pressing portion 39b rotates, the flat plate surface of the second spring pressing portion 39b The angle with the second arm portion 41c increases. For this reason, as the second spring pressing portion 39b rotates, the second arm portion 41c protrudes from the second lever 39 of the second spring pressing portion 39b (the side on which the inclined surface 39d and the protruding portion 39e are formed). ) Will be pressed at the end.

  FIG. 8 shows a state where the second arm portion 41c is riding on the vicinity of the uppermost portion of the stopper 40c. At this time, the second arm portion 41c comes into contact with the protruding portion 39e of the second spring pressing portion 39b. Thereby, the 2nd arm part 41c is flipped up above the 2nd spring press part 39b, and the 2nd spring press part 39b is prevented from swinging idly.

  Here, when the second arm portion 41c rides on the stopper 40c, the circular coil portion 41a of the bifurcated spring 41 tends to move in the riding direction. At this time, the circular coil portion 41a of the bifurcated spring 41 is also moved. A gap 43 between the upper end portion of the circular coil portion 41a and the spring pressing portion 42c is set so that the upper end portion of the circular coil portion 41a contacts the spring pressing portion 42c. That is, the gap 43 is a minute gap.

  For this reason, the movement of the circular coil portion 41a is restricted, and the second arm portion 41c is elastically deformed in the riding direction, so that a reaction force is generated in the second arm portion 41c to return to the case 11 side. At this time, since the inclined surface 39d is formed at the base portion of the second spring pressing portion 39b, the second arm portion 41c trying to return to the base side of the stopper 40c is not caught by the second spring pressing portion 39b. I can escape.

  For this reason, the 2nd arm part 41c which got over the stopper 40c can be successfully stored in the base side of the stopper 40c by own reaction force.

  FIG. 9 shows a state in which the second arm portion 41c gets over the stopper 40c. The second arm portion 41c is elastically deformed from the free state toward the stopper 40c by a predetermined angle θ2 (FIG. 7). For this reason, the spring load from the 2nd arm part 41c acts on the stopper 40c, and the 2nd arm part 41c is hooked on the stopper 40c.

  The inclined surface 39d formed on the second spring pressing portion 39b serves as a so-called escape portion so that the second spring pressing portion 39b does not come into contact with the second arm portion 41c stored on the base side of the stopper 40c. For this reason, after the 2nd arm part 41c is hooked on the stopper 40c, the 2nd spring press part 39b swings idle.

  As a result, in use, the second arm portion 41c can be held at the same position without being deformed in accordance with the rotation operation of the second rotary door 26, and the second spring pressing portion 39b can be held by the second arm portion 41c. Can be prevented from interfering with the rotation of the second rotary door 26.

  In this example, the first rotary door 25 and the second rotary door 26 are rotated to the position in the face mode in order to hook the second arm portion 41c of the bifurcated spring 41 to the stopper 40c. Even if the bi-level mode is operated, the second rotary door 26 has the same rotational operation, so that the second arm portion 41c of the bifurcated spring 41 can be hooked on the stopper 40c.

  Further, when the first rotary door 25 and the second rotary door 26 are rotated to a position other than the face mode and the bi-level mode, that is, the foot defroster mode and the defroster mode (detailed later), the second rotary door 26 is rotated. Since only the first rotary door 25 is in the same position as in the foot mode, the second arm 41c of the bifurcated spring 41 is maintained in a free state.

  Next, the operation of the first embodiment in the above configuration will be described. First, an outline of the operation of the air conditioning unit 10 as a whole will be described. 1 and FIG. 10 to be described later show the face mode, and the first and second seal portions 25f and 25g of the first rotary door 25 are elastically pressed against the case-side seal surfaces 28 and 30, respectively.

  As a result, the communication between the portal-shaped inner space of the first rotary door 25 and the outer space of the first rotary door 25 is blocked, so that both foot openings 22 and 23 are located upstream of the door by the first rotary door 25. It will be in a blocking state with the flow path.

  At this time, the first rotary door 25 fully opens the communication passage opening 27, and the portal-shaped inner space of the first rotary door 25 communicates the space on the air mixing portion 19 side with the communication passage opening 27. Also fulfills.

  On the other hand, in the second rotary door 26, the first and second seal portions 26f and 26g are elastically pressed against the seal surfaces 34 and 32 on the case side, respectively. Thereby, the defroster opening 20 is fully closed by the second rotary door 26 and the face opening 21 is fully opened.

  As described above, the air on the air mixing unit 19 side (cooling air of the evaporator 13) flows directly into the communication path opening 27, passes through the inner space of the first rotary door 25, and flows into the communication path opening 27. . Then, the conditioned air in the communication passage opening 27 blows out only from the face opening 21 to the passenger's upper body side in the passenger compartment. In the face mode, the vehicle interior is cooled by blowing the cool air cooled by the evaporator 13 toward the upper body of the passenger.

  Next, FIG. 11 shows the bi-level mode, in which the first rotary door 25 rotates clockwise by a predetermined angle from the position of FIGS. 1 and 10, and the inlet channels of both foot openings 22 and 23 Both of the communication passage openings 27 are opened simultaneously. On the other hand, the second rotary door 26 is maintained at the same position as in the face mode and opens only the face opening 21.

  Accordingly, the air on the air mixing unit 19 side can be blown out to the passenger's foot side in the vehicle compartment through both foot openings 22 and 23, and at the same time, the air can be blown out to the passenger's upper body side through the face opening 21.

  FIG. 12 shows the foot mode. FIG. 12 shows a state after the second arm 41c of the bifurcated spring 41 is caught by the stopper 40c, and therefore the position of the second arm 41c of the bifurcated spring 41 is different from FIG. .

  In this foot mode, the first rotary door 25 is further rotated clockwise from the position of FIG. 11 by a predetermined angle, and the first and second seal portions 25f, 25g of the first rotary door 25 are sealed on the case-side seal surface 29. , 31 are elastically pressed against each other. As a result, the first rotary door 25 fully opens the inlet passages of both foot openings 22 and 23 and fully closes the communication passage opening 27.

  Accordingly, the entire amount of air on the air mixing unit 19 side can be blown out to the passenger's foot side in the vehicle compartment through both foot openings 22 and 23. In the foot mode, the vehicle interior is heated by blowing warm air heated by the heater core 15 toward the passenger's feet.

  In the foot mode, the second rotary door 26 rotates counterclockwise by a predetermined angle from the position of FIGS. 1, 10, and 11, and the first and second seal portions 26f, 26g of the second rotary door 26 are in the case. The seal surfaces 35 and 33 on the side are elastically pressed against each other. Thereby, the face opening 21 is fully closed by the second rotary door 26 and the defroster opening 20 is fully opened. However, since the communication passage opening 27 is fully closed, air does not blow out from the defroster opening 20.

  Next, FIG. 13 shows the foot defroster mode, and the first rotary door 25 rotates counterclockwise by a predetermined angle from the position of FIG. 12 and returns to the same position as FIG. Thereby, both the inlet flow path of both foot opening parts 22 and 23 and the communicating path opening part 27 are opened simultaneously.

  On the other hand, since the 2nd rotary door 26 maintains the same position as FIG. 12, the face opening 21 is fully closed and the defroster opening 20 is fully opened.

  Accordingly, air on the air mixing unit 19 side, specifically, warm air heated by the heater core 15 is blown out to the passenger's foot side in the passenger compartment through both foot openings 22 and 23, and at the same time through the defroster opening 20. Can blow out to the inside of the window glass. As a result, in the foot defroster mode, the vehicle interior can be heated and, at the same time, the vehicle front window glass can be prevented from fogging.

  Next, FIG. 14 shows the time in the defroster mode, and the first rotary door 25 further rotates counterclockwise by a predetermined angle from the position of FIG. 13 and returns to the same position as in FIGS. As a result, the inlet channels of both foot openings 22 and 23 are fully closed, and the communication passage opening 27 is fully opened. On the other hand, since the 2nd rotary door 26 maintains the same position as FIG. 12, FIG. 13, the face opening part 21 is fully closed and the defroster opening part 20 is fully opened.

  Therefore, the entire amount of air on the air mixing unit 19 side can be blown out through the defroster opening 20 to the inside of the vehicle front window glass. This blown air is dehumidified air cooled by the evaporator 13 or warm air heated by the heater core 15. As a result, the anti-fogging action of the vehicle front window glass can be maximized.

  Note that, in any of the above-described air blowing modes, the vehicle interior air temperature can be arbitrarily adjusted by adjusting the rotational position of the air mix door 14 and adjusting the air volume ratio between warm air and cold air.

  The blowing mode switching between the face mode and the defroster mode described above can be performed by selecting the rotation position of the blowing mode link plate 42 by a blowing mode door operation mechanism (not shown). That is, as the rotational position of the blowing mode link plate 42 changes, the fitting position between the first drive groove 42d and the first drive pin 38c of the first lever 38 and the second drive groove 42e and the second lever 39 are changed. The fitting position with the second drive pin 39c is changed, whereby the rotational positions of the first and second levers 38 and 39, and hence the rotational positions of the first and second rotary doors 25 and 26 are changed. The blowing mode can be switched as described above.

  In the present embodiment, an increase in door operation force due to the weight of the first rotary door 25 can be satisfactorily suppressed by the bifurcated spring 41. Hereinafter, the action of suppressing the door operating force by the bifurcated spring 41 will be described in detail with reference to FIGS. 10 (a) and 10 (b).

  FIG. 10A is a view showing the relationship between the load W1 due to the weight of the first rotary door 25 and the load P1 of the bifurcated spring 41 in the face mode shown in FIG. 1, and FIG. It is a figure which expands and shows only the relationship between the load W1 by the door weight of 10 (a), and the spring load P1.

  As shown in FIG. 10 (b), the central position of the circular coil portion 41a of the bifurcated spring 41 is in the vicinity of the intermediate position between the first and second rotary shafts 25b and 26b of the first and second rotary doors 25 and 26. a is set, and the vicinity of the tip end portion of the first arm portion 41 b of one end portion of the bifurcated spring 41 is brought into contact with the first spring pressing portion 38 b of the first lever 38. Further, the second arm 41c at the other end of the bifurcated spring 41 is in contact with the stopper 40c.

  In FIG. 10B, the solid line positions of the first and second spring pressing portions 38b and 39b are the positions in the face mode, and the center of gravity position of the first rotary door 25 is G1 in the face mode. A load W1 due to the weight of the door acts on the door.

  Therefore, an axial moment M1 is generated in the first rotary door 25 due to the horizontal distance L1 from the rotation axis center b to the gravity center position G1. Therefore, when the first rotary door 25 rotates in the direction K opposite to the axial moment M1, the door operating force increases due to the influence of the axial moment M1.

  Therefore, by setting a spring load that acts on the first rotary door 25 in a direction opposite to the axial moment M1, the axial moment M1 based on the influence of the door's own weight is canceled out, and an increase in the door operating force is suppressed. Can do.

  10 (b) and 12 (b), the two-dot chain line position of the bifurcated spring 41 is the position of the bifurcated spring 41 immediately after assembly, and the first, second levers 38, 39 have first, The two-dot chain line positions of the second spring pressing portions 38b and 39b are positions in the foot mode, and c is a contact point (spring action point) between the first arm portion 41b and the first spring pressing portion 38b at this time.

  Immediately after assembly, the bifurcated spring 41 is in a free state, so that the spring load is zero at the contact c.

  In FIG. 10B, the solid line position of the bifurcated spring 41 is the position of the bifurcated spring 41 in the face mode, and d is the contact point between the first arm portion 41b and the first spring pressing portion 38b in the face mode. (Spring action point).

  In the face mode, the first spring pressing portion 38b rotates by a predetermined angle θ1 from the two-dot chain line position to the solid line position, so that the contact point c shifts to the contact point d, and the first arm pressing portion 38b causes the first arm portion 41b. Is pressed and elastically deformed by a predetermined angle θ1. That is, the deformation angle θ3 of the bifurcated spring 41 at this time is the sum (θ3 = θ1 + θ2) of the respective deformation angles θ1 and θ2 of the first and second arm portions 41b and 41c.

  As a result, the bifurcated spring 41 generates a spring load P1 at the contact point d. For this reason, an axial moment M0 is generated in the first rotary door 25 depending on the distance from the rotational axis center b to the contact d.

  Since the axial moment M1 is canceled by the axial moment M0 based on the spring load P1, an increase in the door operating force can be suppressed.

  By the way, in this embodiment, since the center of the circumferential direction of the 1st rotary door 25 is located in the vertical line vicinity of the rotating shaft center b at the time of foot mode (refer FIG. 12), from the rotating shaft center b to the gravity center position G1. The horizontal distance L1 becomes smaller. For this reason, in the foot mode, the axial moment M1 based on the influence of the door's own weight is reduced.

  That is, the axial moment M1 decreases as the first rotary door 25 rotates in the direction K opposite to the axial moment M1, but does not become zero.

  At this time, since the first spring pressing portion 38b returns from the position in the face mode to the position in the foot mode, the deformation of the first arm portion 41b of the bifurcated spring 41 becomes smaller and finally the deformation. Although it becomes zero, since the other second arm portion 41c is caught by the stopper 40c, it remains elastically deformed by a predetermined angle θ2.

  For this reason, the spring load P1 decreases as the first rotary door 25 rotates in the direction K opposite to the axial moment M1, but does not become zero. Along with this, the axial moment M0 generated in the first rotary door 25 by the spring load P1 also decreases, but does not become zero.

  Accordingly, the axial moment M1 decreases as the first rotary door 25 rotates in the direction K opposite to the axial moment M1, but the axial moment M0 that cancels the axial moment M1 also decreases correspondingly, so the axial moment M1 is reduced. It can cancel well, and the increase in door operation force can be suppressed.

  Furthermore, since the spring load P1 and the axial moment M0 always act and do not become zero, it is possible to always suppress an increase in the door operating force in the process of shifting from the face mode to the foot mode.

  As described above, by using the bifurcated spring 41, an increase in the door operating force due to the weight of the first rotary door 25 can be suppressed satisfactorily.

  At this time, the first and second arm portions 41b and 41c at both ends of the bifurcated spring 41 are in contact with (striking) the first spring pressing portion 38b of the first lever 38 and the outer peripheral surface of the stopper 40c. Just not fixed.

  Accordingly, relative sliding contact between the first spring pressing portion 38b and the stopper 40c and the first and second arm portions 41b and 41c becomes possible along with the rotational displacement of the first lever 38. The position can be changed. Accordingly, the first and second arm portions 41b and 41c can be smoothly offset without causing excessive deformation of the first and second arm portions 41b and 41c with the rotational displacement of the first lever 38.

  FIG. 15 is a graph for explaining the relationship between the door self-weight canceling action and the blowing mode switching according to the present embodiment, in which the horizontal axis is the above-described face mode or defroster blowing mode, and the vertical axis is the load.

  In FIG. 15, “door load” indicated by a two-dot chain line is a load F <b> 1 that acts on the first arm 41 b from the first spring pressing portion 38 b due to the axial moment M <b> 1 based on the door's own weight, and switches the blowing mode. And the door load changes.

  That is, since the axial moment M1 changes depending on the rotational operation position of the first rotary door 25, the load F1 applied to the first arm 41b from the first spring pressing portion 38b by the axial moment M1 is also the rotational operation of the first rotary door 25. Varies with position.

  In FIG. 15, the “spring load” indicated by a broken line is a spring load P1 that acts on the first spring pressing portion 38b from the first arm portion 41b.

  Further, in FIG. 15, “the load after the cancellation of the spring load and the door load” indicated by the solid line is a load after the cancellation of the spring load P1 and the door load F1, and the load after the cancellation is small. As a result, the axial moment after the cancellation of the first rotary door 25 becomes smaller, and the door operating force is reduced.

  In the face mode and the defroster mode, the center of gravity position G1 of the first rotary door 25 moves to the position closest to the horizontal plane and the axial moment M1 is maximized, so the door load is also maximized. In the foot mode, as described above, the center of gravity position G1 of the first rotary door 25 moves to a position near the vertical line of the rotation axis center b and the axial moment M1 is minimized, so the door load F1 is also minimized.

  Therefore, the rotational operation position of the first rotary door 25 in the face mode and the defroster mode corresponds to the maximum door load position in the present invention, and the rotational operation position of the first rotary door 25 in the foot mode is in the present invention. Corresponds to the minimum door load position.

  Therefore, in this embodiment, the spring load is set so that the load after canceling out the spring load and the door load is substantially zero in the face mode, the defroster mode, and the foot mode.

  Specifically, the spring load P1 of the bifurcated spring is given by the product of the spring constant k and the deformation angle θ of the bifurcated spring (in other words, the sum of the deformation angles of the first and second arm portions). (P1 = k · θ), the spring load is set by setting the spring constant k and the above-described spring deformation angles θ2 and θ3 as follows.

  That is, the product (k · θ3) of the spring constant k and the deformation angle θ3 (θ3 = θ1 + θ2) in the face mode and the defroster mode is the same as the door load (maximum door load: F1MAX) in the face mode and the defroster mode. And the product of the spring constant k and the deformation angle θ2 in the foot mode is the same value as the door load in the foot mode (minimum door load: F1MIN) (k · θ3 = F1MAX and k · θ2) = F1MIN), the spring constant k and the deformation angles θ2, θ3 are set.

  In the present embodiment, for the purpose of realizing a predetermined operation of the first rotary door 25, the portion corresponding to the foot mode (point e in FIG. 3) of the first drive groove portion 42d and the rotation shaft 42a of the blowing mode link plate 42. The distance D1 between is smaller. For this reason, in the foot mode, a large driving force must be applied to the link plate 42 in order to counter the door load caused by the door's own weight, which increases the door operating force.

  Therefore, in this embodiment, the spring load of the bifurcated spring 41 is zero immediately after assembly (point f in FIG. 15), but the second arm portion 41c is hooked on the stopper 40c, so that the first load can be obtained even in the foot mode. A spring load can be applied to one rotary door 25 (point g in FIG. 15).

  For this reason, the load after cancellation of the spring load and the door load in the foot mode can be made substantially zero, and is not affected by the distance D1 between the first drive groove 42d and the rotation shaft 42a of the blow-out mode link plate 42. The door operating force can be suppressed.

  In the bi-level mode and the foot defroster mode, the rotational position of the rotary door 25 is an intermediate position between the face mode, the defroster mode, and the foot mode, and accordingly, the door load is also an intermediate value. In these blowing modes, the spring load is also an intermediate value, so that the door load can be offset well.

  As a result, as shown by the solid line in FIG. 15, a spring load substantially equal to the door load can be applied through the full blow mode, and the load after cancellation of the door load and the spring load is sufficiently small through the full blow mode ( (Small amount).

  Furthermore, in this embodiment, since there is no region where the spring load becomes zero, the load after the cancellation of the door load and the spring load between the region where the spring load acts and the region where the spring load becomes zero suddenly increases. Fluctuation can be avoided.

  In other words, the load after cancellation of the door load and the spring load can be made substantially uniform in any blowing mode. For this reason, the rapid fluctuation | variation of door operation force can be suppressed and a passenger | crew's operation feeling can be improved.

  By the way, in this embodiment, although the spring load is not acting on the 2nd rotary door 26, the problem that door operating force increases with the dead weight of the 2nd rotary door 26 does not arise. This is due to the following reason.

  That is, in a series of blowing mode switching operations from the face mode to the defroster mode (FIGS. 10 to 14), the first rotary door 25 is moved to the fully opened position of the communication passage opening 27 shown in FIGS. It reciprocates once between the communication path opening 27 shown in the fully closed position. On the other hand, the second rotary door 26 only rotates once from the fully closed position of the defroster opening 20 shown in FIGS. 10 and 11 to the fully open position of the defroster opening 20 shown in FIGS.

  Therefore, as shown in FIG. 3, the shape of the second drive groove 42e can be simplified as compared with the first drive groove 42d, and therefore, from the rotating shaft 42a of the blowing mode link plate 42 to the second drive groove 42e. Can be made larger than the maximum distance D1 from the rotating shaft 42a to the first drive groove 42d.

  Here, the maximum distance D1 is the distance between the portion corresponding to the foot mode (point e) in the first drive groove portion 42d and the rotation axis 42a of the link plate, and the minimum distance D2 is in the second drive groove portion 42e. This is the distance between the portion corresponding to the bi-level mode (point h) and the rotation axis 42a of the link plate.

  For this reason, on the second drive groove portion 42e side, the distance from the fulcrum to the action point in the lever principle is larger than that on the first drive groove portion 42d side, so that it counters the door load due to the weight of the second rotary door 26. Therefore, the driving force applied to the link plate 42 may be small.

  In other words, the influence of the door load due to the weight of the second rotary door 26 is small with respect to the door operating force, and the influence of the door load due to the weight of the first rotary door 25 is dominant.

  As a result, in this embodiment, by applying a spring load only to the first rotary door 25, it is possible to suppress an increase in door operating force due to the door's own weight.

(Second Embodiment)
In the first embodiment, the outer peripheral door surfaces 25e and 26e are arranged at a predetermined distance from the center of the first and second rotary shafts 25a, 25b, 26a, and 26b to the radially outer side, and the outer peripheral door surfaces 25e, Although the blowout mode door is constituted by the rotary doors 25 and 26 that rotate the direction 26e in the direction orthogonal to the air flow, in the second embodiment, the blowout mode door is constituted by the cantilever plate doors 250 and 260 as shown in FIG. It is composed.

  The cantilever plate doors 250 and 260 have plate-like plate door main body portions 251 and 261, and rotary shafts 252 and 262 are integrally formed at the ends of the plate door main body portions 251 and 261. The door main body 251 and the rotary shaft 252 and the plate door main body 261 and the rotary shaft 262 can be integrally formed with resin.

  The first cantilever plate door 250 corresponds to the first rotary door 25 of the first embodiment, and opens and closes the inlet flow paths and the communication passage openings 27 of both foot openings 22 and 23. The second cantilever plate door 260 corresponds to the second rotary door 26 of the first embodiment, and opens and closes the face opening 21 and the defroster opening 20.

  Since the cantilever plate doors 250 and 260 rotationally displace the plate-like plate door main body portions 251 and 261 against the air flow around the rotation shafts 252 and 262, the influence of the wind pressure compared to the rotary doors 25 and 26. There is a characteristic of receiving a lot.

  In FIG. 16, the first cantilever plate door 250 fully closes the inlet channels of both foot openings 22 and 23 and the communication passage opening 27 is fully opened, and the second cantilever plate door 260 opens the defroster opening 20. Is fully closed and the face opening 21 is fully opened. That is, FIG. 16 shows the face mode.

  In FIG. 16, the solid line position of the bifurcated spring 41 indicates the position after the second arm portion 41 c of the bifurcated spring 41 is caught by the stopper 40 c, and the two-dot chain line position indicates the bifurcated spring. The position immediately after the assembly of 41 is shown.

  Also in the present embodiment, as in the first embodiment, the cantilever plate doors 250 and 260 are assembled at the foot mode position (two-dot chain line position) and the bifurcated spring 41 is assembled in a free state. Then, by switching to the face mode state after the air conditioning unit 10 is assembled, the bifurcated spring 41 gets over the stopper 40c and is caught on the outer peripheral surface of the stopper 40c.

  In this face mode state, the pressing load W1 acts on the first cantilever plate door 250 by the wind pressure Va of the air flow from the air mixing portion 19 toward the face opening portion 21. Therefore, an axial moment M1 is generated in the first cantilever plate door 250 by the pressing load W1 and the door length L1.

  Therefore, when the first cantilever plate door 250 is rotated from the solid line position in FIG. 16 toward the two-dot chain line position, the axial moment M1 acts in the direction opposite to the rotation direction of the first cantilever plate door 250. The operating force of the single cantilever plate door 250 is increased.

  Therefore, the bifurcated spring 41 is moved by the first spring pressing portion 38b of the first lever 38 (equivalent to the first lever 38 of the first embodiment) coupled to the rotating shaft 252 of the first cantilever plate door 250. The first arm portion 41b is pressed and elastically deformed, and a spring load P1 in the direction opposite to the pressing load W1 is generated at the contact point d of the first arm portion 41b.

  For this reason, the first cantilever plate door 250 generates an axial moment M0 based on the spring load P1. Since the axial moment M1 is canceled by the axial moment M0 based on the spring load P1, the influence of the wind pressure Va on the operating force of the first cantilever plate door 250 can be canceled by the spring load P1.

  When the first cantilever plate door 250 is operated to the two-dot chain line position that fully closes the communication passage opening 27, the first spring pressing portion 38b of the first lever 38 is moved to the two-dot chain line position (contact c side). To the position). At this door position, the pressing load due to the wind pressure acting on the first cantilever plate door 250 and the load due to the door's own weight are offset.

  Accordingly, the axial moment M1 decreases as the first cantilever plate door 250 rotates from the solid line position to the two-dot chain line position. Accordingly, the first arm portion 41b of the bifurcated spring 41 returns from the solid line position to the two-dot chain line position, and the deformation of the first arm portion 41b becomes zero, so the spring load P1 is also reduced. At this time, since the other second arm portion 41c of the bifurcated spring 41 remains caught by the stopper 40c, the spring load P1 does not become zero.

  Accordingly, when the axial moment M1 is reduced, the axial moment M0 based on the spring load P1 is also reduced correspondingly, so that the axial moment M1 can be canceled well and an increase in door operating force can be suppressed.

  Furthermore, since the spring load P1 acts through the full blow mode and does not become zero, an increase in the door operation force can be suppressed through the full blow mode, and a rapid fluctuation in the door operation force can be suppressed. Operation feeling can be improved.

  As described above, in the second embodiment, as the blow mode door is configured by the cantilever doors 250 and 260, the influence of both the wind pressure and the door's own weight on the door operation force is canceled by the spring load, and the door operation force Can be reduced.

  By the way, the second cantilever plate door 260 is disposed on the downstream side of the air flow with respect to the first cantilever plate door 250, and the second cantilever plate door 260 and the plate surface of the second cantilever plate door 260 at the operation position in the face mode of FIG. The air flow is substantially parallel to the second cantilever plate door 260, and the wind pressure does not affect the second cantilever plate door 260.

  For this reason, in this embodiment, an increase in the door operating force due to wind pressure can be suppressed by applying a spring load only to the first cantilever plate door 250.

(Other embodiments)
(1) You may apply this invention with respect to the structure which combines the rotary doors 25 and 26 of 1st Embodiment, and the cantilever plate doors 250 and 260 of 2nd Embodiment.

  (2) In the first and second embodiments, the present invention is applied to the blowing mode door that opens and closes the blowing opening in the vehicle air conditioner. However, the present invention is an air having a plurality of air passage opening / closing door means. The passage opening / closing device can be applied to various uses without being limited to the vehicle air conditioner.

FIG. 2 is a cross-sectional view showing only an external view of a part of the air conditioning unit showing the first embodiment of the present invention, and shows a face mode. It is a perspective view which illustrates the rotary door structure in a 1st embodiment. It is a disassembled perspective view of the blowing mode switching mechanism part in 1st Embodiment. FIG. 4 is a perspective view of the main part of FIG. 3 in an assembled state. It is sectional drawing of the assembly | attachment state of the blowing mode switching mechanism part in 1st Embodiment. It is a principal part side view of the air-conditioning unit part which shows the time of the assembly | attachment of 1st Embodiment. In FIG. 4, it is a perspective view which shows a mode that a bifurcated spring is fixed. It is a perspective view of the principal part of Drawing 7, and shows a state where a bifurcated spring got on a stopper. FIG. 9 is a perspective view showing a state in which the bifurcated spring climbs over the stopper in FIG. 8. (A) is explanatory drawing which shows the relationship between the load and spring load by the rotary door own weight at the time of face mode shown in FIG. 1, (b) expands only the relationship between the load and spring load by the door own weight of (a). It is explanatory drawing shown in figure. It is a principal part side view of the air-conditioning unit part which shows the time of bilevel mode of 1st Embodiment. (A) is a principal part side view of the air-conditioning unit part which shows the time of the foot mode of 1st Embodiment, (b) is explanatory drawing which expands and illustrates the relationship between the load by the door dead weight of (a), and a spring load. . It is a principal part side view of the air-conditioning unit part which shows the time of the foot defroster mode of 1st Embodiment. It is a principal part side view of the air-conditioning unit part which shows the time of the defroster mode of 1st Embodiment. It is a graph which shows the door weight cancellation effect by 1st Embodiment. It is principal part sectional drawing of the air-conditioning unit part by 2nd Embodiment, and the time at the time of face mode is shown. It is principal part sectional drawing of the air-conditioning unit part in a prior application example. It is a graph which shows the door weight cancellation effect by a prior application example. It is a perspective view which illustrates the rotary door structure in a prior application example.

Explanation of symbols

20 ... defroster opening (air passage), 21 ... face opening (air passage),
22: Foot opening (air passage),
25, 26 ... first and second rotary doors (first and second airway opening / closing doors),
25b, 26b ... 1st, 2nd rotating shaft, 39b ... 2nd spring press part (arm part deformation | transformation means),
40c ... stopper (arm part return preventing means) 41 ... bifurcated spring (bifurcated spring means),
41b, 41c ... 1st, 2nd arm part.

Claims (15)

A plurality of air passages (20-23, 27);
The first and second rotating shafts (25a, 25b, 26a, 26b, 252, 262) are configured to be rotatable about the first and second rotating shafts (25a, 25b, 26a, 26b, 252, 262), and open and close the plurality of air passages (20-23, 27) Airway doors (25, 26, 250, 260);
A bifurcated spring having a first arm portion (41b) and a second arm portion (41c) disposed near the intermediate position of the first and second rotation shafts (25a, 25b, 26a, 26b, 252, 262). Means (41);
Arm deforming means (39b) coupled to the second rotating shaft (26a, 26b, 262);
Arm position return prevention means (40c) that does not move,
The bifurcated spring means (41) is such that the first arm part (41b) and the second arm part (41c) are opposed to the arm part deforming means (39b) and the arm part return preventing means (40c). Placed in a free state,
After the bifurcated spring means (41) is arranged, the arm part deforming means (39b) causes the second arm part (41c) to be moved freely by rotating the second air passage opening / closing door (26, 260). Elastically deform from the state by a predetermined angle (θ2),
When the second arm portion (41c) is elastically deformed by the predetermined angle (θ2), the second arm portion (41c) is locked to the arm portion return prevention means (40c),
In a state where the second arm portion (41c) is elastically deformed by the predetermined angle (θ2), the first arm portion (41b) presses the first rotating shaft (25a, 25b, 252) side, and The air passage opening and closing device, wherein the spring load of the bifurcated spring means (41) acts on the first airway opening and closing door (25, 250) so as to cancel the door load due to the door weight or wind pressure. When the rotational operation position of the first air passage opening / closing door (25, 250) at which the door load of the first air passage opening / closing door (25, 250) is minimized is the minimum door load position,
The bifurcated spring means (41) is disposed in a free state in a state where the first air passage opening / closing door (25, 250) is disposed at the minimum door load position. The air passage opening and closing device according to 1. When the first airway opening / closing door (25, 250) is rotated to the minimum door load position, the spring load due to elastic deformation of the second arm portion (41c) is the first load at the minimum door load position. The air passage opening and closing device according to claim 2, wherein the door load of one air passage opening and closing door (25, 250) is offset. A case (11) that forms the plurality of air passages (20 to 23, 27) and incorporates the first and second air passage opening / closing doors (25, 26, 250, 260);
The bifurcated spring means (41) is disposed on the outer surface side of the case (11),
A second lever (39) that is coupled to the second rotating shaft (26a, 26b, 262) and rotationally drives the second air passage opening / closing door (26, 260) is disposed on the outer surface side of the case (11). And
A second arm pressing portion (39b) that constitutes the arm deforming means is provided on the second lever (39);
A stopper (40c) that constitutes the arm part return preventing means is formed so as to protrude from the outer surface of the case (11) in a direction substantially perpendicular to the rotation surface of the second lever (39),
An inclined surface (40d) is formed on the tip surface of the stopper (40c),
The inclined surface (40d) is formed such that the protruding height closer to the second arm portion (41c) is lower and the protruding height away from the second arm portion (41c) is higher. And
After the bifurcated spring means (41) is arranged, the second arm portion pressing portion (39b) pushes the second arm portion (41c) to the stopper (40c) side as the second lever (39) rotates. Press to
By this pressing, the second arm portion (41c) is brought into contact with the inclined surface (40d), and then slides on the inclined surface (40d) from the protruding side to the higher side. 2. The vehicle according to claim 1, wherein the stopper (40 c) is moved over the front end side and is further elastically deformed by the predetermined angle (θ 2) to be engaged with the outer peripheral surface of the stopper (40 c). 4. The air passage opening and closing device according to any one of 3 to 3. The bifurcated spring means (41) is arranged such that the second arm part (41c) in the free state is in contact with or close to the second arm part pressing part (39b),
When the second arm portion pressing portion (39b) presses the second arm portion (41c) toward the stopper (40c) with the rotation of the second lever (39), the second arm portion pressing portion. (39b) slides relative to the second arm (41c),
A relief part (39d) for separating the second arm part pressing part (39b) and the second arm part (41c) when the second arm part (41c) is locked to the stopper (40c). The air passage opening and closing device according to claim 4, wherein the air passage opening and closing device is formed in the second arm portion pressing portion (39 b). The second arm pressing portion (39b) is formed so as to protrude from the second lever (39) in substantially the same direction as the stopper (40c),
A projecting portion (39e) projecting in a direction substantially perpendicular to the projecting direction is formed at the tip of the second arm portion pressing portion (39b),
When the second arm pressing portion (39b) presses the second arm (41c) toward the stopper (40c), the projecting portion (39e) passes through the distal end side of the stopper (40c). The air passage opening and closing device according to claim 4 or 5, wherein A first lever (38) that is coupled to the first rotating shaft (25a, 25b, 252) and rotationally drives the first air passage opening / closing door (25, 250) is disposed on the outer surface side of the case (11). And
The first lever (38) is provided with a first arm pressing portion (38b),
As the first lever (38) is rotated, the first arm pressing portion (38b) is rotated so that the first arm (41b) is pressed by the first arm pressing portion (38b). The air passage opening and closing device according to claim 4, wherein the air passage opening and closing device is elastically deformed. When the rotational operation position of the first airway opening / closing door (25, 250) at which the door load is maximum is the maximum door load position,
When the first airway opening / closing door (25, 250) is rotated at the maximum door load position, the first arm (41b) is elastically deformed in addition to the elastic deformation of the second arm (41c). By doing so, the spring load due to the elastic deformation of the first arm portion (41b) and the second arm portion (41c) causes the first air passage opening / closing door (25, 250) at the maximum door load position to be The air passage opening and closing device according to claim 7, wherein the door load is offset. A link plate (42) disposed on the outer surface side of the case (11) and rotated about the rotation axis (42a);
A first drive groove (42d) and a second drive groove (42e) provided in the link plate (42);
A first drive pin (38c) provided on the first lever (38) is slidably fitted into the first drive groove (42d),
The air passage according to claim 7 or 8, wherein a second drive pin (39c) provided on the second lever (39) is slidably fitted into the second drive groove (42e). Switchgear. The minimum distance (D2) between the second drive groove (42e) and the rotation shaft (42a) is the minimum distance (D1) between the first drive groove (42d) and the rotation shaft (42a). The air passage opening and closing device according to claim 9, wherein the air passage opening and closing device is set larger than the air passage. One end side in the axial direction of the circular coil portion (41a) of the bifurcated spring means (41) is disposed on the outer surface side of the case (11),
On the other end side in the axial direction of the circular coil portion (41a), a spring pressing portion (42c) formed integrally with the link plate (42) is disposed,
The clearance gap (43) of a predetermined dimension is formed between the axial direction other end side of the said circular coil part (41a), and the said spring holding | suppressing part (42c), The Claim 9 or 10 characterized by the above-mentioned. Air passage opening and closing device. In the first lever (38), the first arm pressing portion (38b) and the first drive pin (38c) are integrally formed,
In the second lever (39), the second arm pressing portion (39b) and the second drive pin (39c) are integrally formed,
The air passage opening and closing device according to any one of claims 9 to 11, wherein the integral first lever (38) and the integral second lever (39) have the same shape. The first and second air passage opening / closing doors are outer door surfaces (25e) positioned at a predetermined distance from the center of the first and second rotating shafts (25a, 25b, 26a, 26b) to the radially outward side. 26e), and the outer peripheral door surfaces (25e, 26e) are first and second rotary doors (25, 26) rotating in a direction perpendicular to the air flow. The air passage opening and closing device according to any one of the above. The first and second airway opening / closing doors are cantilever plate doors (250, 260) in which the first and second rotating shafts (252, 262) are arranged at end portions of the plate door main body portions (251, 262). The air passage opening and closing device according to any one of claims 1 to 13, wherein An air passage opening and closing device according to any one of claims 1 to 14,
The plurality of air passages include a plurality of blowing openings (20 to 23) for blowing air to different parts in the vehicle interior,
The first and second air passage opening / closing doors are configured as blowing mode doors that open and close the plurality of blowing openings (20 to 23).

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