JP6770220B2 - Air conditioning register - Google Patents

Description

The present invention relates to an air-conditioning register that blows out air-conditioning air sent from an air-conditioning device from an air outlet of a ventilation passage, and more particularly to an air-conditioning register provided with a shut damper that opens and closes the ventilation passage.

The instrument panel of the vehicle incorporates an air-conditioning register that blows out the air-conditioning air sent from the air-conditioning device from the air outlet of the air passage. As one form of this air conditioning register, fins and shut dampers arranged in order from the outlet at the downstream end of the ventilation passage to the upstream, and an operation knob, a transmission shaft, and a rotation direction changing mechanism for operating them are provided. Those provided are known (see, for example, Patent Document 1).

The shut damper includes a pair of damper plates that are tilted in opposite directions between the open position and the closed position with the damper shaft on the same line as a fulcrum by the force transmitted from the rotation direction changing mechanism.

The transmission shaft extends in the flow direction of the air conditioning air. The rotation direction changing mechanism changes the rotation direction of the transmission shaft and transmits the transmission to the shut damper, and is provided between the upstream end of the transmission shaft and the shut damper. In Patent Document 1, a bevel gear mechanism is used as this rotation direction changing mechanism. The transmission shaft and the operation knob, and the transmission shaft and the rotation direction changing mechanism are connected by a cardan joint such as a universal joint and a ball joint, respectively.

German Patent Application Publication No. 1021014100441

According to the conventional air-conditioning register, the fins can be tilted by moving the operation knob in the left-right direction or the up-down direction to change the direction in which the air-conditioning air is blown out from the air outlet. Further, by rotating the operation knob, the shut damper can be tilted between the open position where the ventilation path is opened and the closed position where the ventilation path is closed.

By the way, it is possible that a force is applied to a shut damper that is stationary at a position different from the closed position, for example, at the open position, in the thickness direction of both damper plates. In this case, both damper plates may tilt with the damper shaft as a fulcrum, and the rotation direction may not be properly converted by the rotation direction conversion mechanism. Therefore, it is necessary to restore the rotation direction conversion mechanism to an appropriate state, but the conventional air-conditioning register does not take any particular measures for this restoration.

The present invention has been made in view of such circumstances, and an object of the present invention is to keep the rotation direction changing mechanism in an appropriate state even if both damper plates are tilted by applying a force in the thickness direction to the shut damper. The purpose is to provide an air conditioning register that can be restored to.

The air conditioning register that solves the above problems has a rotation direction changing mechanism that changes the direction of rotation of the operation knob transmitted through the transmission shaft extending in the flow direction of the air conditioning air in the ventilation path and transmits it to the shut damper. The shut damper includes a pair of damper plates that are tilted in opposite directions between the open position and the closed position with the damper axis on the same line as a fulcrum by the force transmitted from the rotation direction conversion mechanism. The rotation direction changing mechanism includes a pair of arm portions having a sliding end portion at the tip, which extends from each damper plate and moves along an arc-shaped path centered on the damper axis as the damper plate tilts. A cam member having a cam groove on the outer surface on which each sliding end is slidably engaged is provided, and both sliding ends are a pair of sliding regions facing each other with an axis of the cam member interposed therebetween. In the cam member which is engaged with the cam groove and has both sliding ends engaged with both sliding regions, the cam member includes the axis of the cam member and passes through both sliding ends. The cross section has a curved portion that curves along the arc-shaped path between the most upstream portion in the cross section and the portion where each sliding end portion of each sliding region is engaged.

According to the above configuration, when the operation knob is rotated, the rotation is transmitted to the shut damper via the transmission shaft and the rotation direction changing mechanism. In the rotation direction changing mechanism, the cam member rotates around its own axis. As the cam member rotates, the cam groove having a pair of sliding regions also rotates around the axis of the cam member. As the cam groove rotates, the position where the sliding end of each arm portion engages in the sliding region of the cam groove changes along the arcuate path. As both engagement positions change, each damper plate is tilted in opposite directions between the open position and the closed position with the damper shaft as a fulcrum. The rotation direction and tilt direction of the operation knob and both damper plates are different from each other, but the rotation direction of the operation knob is changed and transmitted to each damper plate by passing through the rotation direction conversion mechanism, and the damper plate is transmitted to each damper plate. Each is tilted.

By the way, it is possible that a force is applied in the thickness direction to a shut damper in which both damper plates are stationary at a position different from the closed position, for example, in the open position. In this case, when both damper plates tilt with the damper shaft as a fulcrum, the sliding end portion of one damper plate comes off from the cam groove. In this case, both damper plates are tilted with the damper shaft as a fulcrum, and the rotation direction is not properly converted by the rotation direction conversion mechanism.

However, the sliding end of the other damper plate continues to engage the cam groove. This is because the sliding end moves along the arcuate path along with the tilting of the other damper plate, the engagement position of the sliding end with the cam groove changes, and the cam member rotates. Is.

When the operation knob is rotated from this state to the side that tilts both damper plates to the open position, the cam member rotates, and the other damper plate whose sliding end is engaged with the cam groove tilts. .. The damper plate pushes one of the damper plates whose sliding end is out of the cam groove. One of the damper plates tilts along an arcuate path with the damper axis as a fulcrum.

Here, if there is a portion between the sliding end portion and the cam groove that hinders the movement of the sliding end portion, it is difficult to engage the sliding end portion with the cam groove. For example, the outer peripheral surface of the cam member has a cylindrical shape centered on the axis of the cam member, and the upstream end surface of the cam member has a planar shape orthogonal to the axis, and the cam groove is the outer peripheral surface. When formed in, the corner portion between the outer peripheral surface and the upstream end surface hinders the movement of the sliding end portion. From the state where the movement of the sliding end is hindered in this way, when a force for further rotating the operation knob is applied, even the sliding end engaged with the cam groove is also applied. May come off from the cam groove.

In this regard, in the above configuration, in the cam member in which both sliding ends are engaged with both sliding regions, the cross section including the axis of the cam member and passing through both sliding ends is the same cross section. It has a curved portion between the most upstream portion in the above and the portion where each sliding end portion of each sliding region is engaged. This curved portion is curved along an arcuate path. Therefore, there is no portion between the sliding end portion and the cam groove that hinders the movement of the sliding end portion, or a state close to it. Therefore, when the one damper plate pushed by the other damper plate tilts along the arcuate path with the damper axis as a fulcrum, the sliding end portion moves along the curved portion and re-enters the cam groove. Engage. Both sliding ends are in a state of being engaged with the cam groove, and the rotation direction can be properly converted by the rotation direction conversion mechanism.

In the air conditioning register, the curved portion is preferably formed of an arc having a constant radius.
As described above, when the curved portion is formed of an arc having a constant radius, the sliding end portion is formed when one of the damper plates tilts along the arc-shaped path with the damper axis as a fulcrum. The force required to move the vehicle along the curved portion is substantially constant at any portion of the curved portion. Therefore, the sliding end portion can be moved more smoothly and can be engaged with the cam groove.

In the air conditioning register, the cam groove is formed so that the center of the cam groove is located on a spherical surface, and the curved portion is formed of an arc having the center of the spherical surface as its own center. Is preferable.

According to the above configuration, in the cam member in which the cam groove is formed so that its center is located on the spherical surface, the curved portion is composed of an arc whose center is the center of the spherical surface. The curved portion is composed of an arc having a constant radius.

According to the above-mentioned air conditioning register, even if both damper plates are tilted by applying a force in the thickness direction to the shut damper, the rotation direction conversion mechanism can be returned to an appropriate state.

A perspective view of an air conditioning register. The perspective view which shows a part component of the air-conditioning register. Similarly, a perspective view showing some components of the air conditioning register. The perspective view which shows the shut damper and the cam member. It is a figure which shows the cam member, (a) is a rear view, (b) is a plan view, (c) is a side view. A plan sectional view of an air conditioning register. A partial plan sectional view of an air conditioning register having a cross section different from that of FIG. Side sectional view of the air conditioning register. A partial side sectional view of an air conditioning register having a cross section different from that of FIG. A partial side sectional view of an air conditioning register having a cross section different from that of FIGS. 8 and 9. It is a figure which shows the state when both damper plates are tilted to a closed position, (a) is a front view of the operation knob, (b) is a partial side sectional view of a shut damper and a peripheral part. It is a figure which shows the state when both damper plates are tilted to an open position, (a) is a front view of the operation knob, (b) is a partial side sectional view of a shut damper and a peripheral part. It is a figure explaining by comparing the state which the sliding end portion of the upper damper plate is detached from a cam groove, (a) is the partial side sectional view of the comparative example, and (b) is the partial side sectional view of embodiment.

Hereinafter, an embodiment embodied in an air-conditioning register for a vehicle will be described with reference to the drawings.
In the following description, the traveling direction (forward direction) of the vehicle will be the front, the reverse direction will be the rear, and the height direction will be the vertical direction. Further, regarding the vehicle width direction (horizontal direction), the direction is defined based on the case where the vehicle is viewed from the rear.

In the passenger compartment, an instrument panel is provided in front of the front seats (driver's seat and passenger's seat) of the vehicle, and air conditioning registers are incorporated in the central portion, side portions, etc. in the left-right direction (vehicle width direction). There is. The main functions of this air-conditioning register are to change the direction of the air-conditioning air sent from the air-conditioning device and blow out from the air outlet into the vehicle interior, and to adjust the amount of the air-conditioning air blown out. Adjusting the blowout amount includes blocking the blowout.

As shown in FIGS. 1, 6 and 8, the air conditioning register includes a retainer 10, a downstream fin group, an upstream fin group, a shut damper 40 and an operation knob 55. Note that in FIG. 1, the bezel 12 in the retainer 10 is not shown. Next, the configuration of each part constituting the air conditioning register will be described.

<Retainer 10>
As shown in FIGS. 6 and 8, the retainer 10 is for connecting the air duct (not shown) of the air conditioner and the opening (not shown) provided in the instrument panel, and is for connecting the retainer main body 11 and the bezel. It has twelve.

The internal space of the retainer 10 constitutes a flow path of the air conditioning air A1 (hereinafter referred to as "ventilation passage 13"). Here, regarding the flow direction of the air conditioning air A1, the side closer to the air conditioner is referred to as "upstream", "upstream side", etc., and the side far from the air conditioner is referred to as "downstream", "downstream side", etc. ..

The ventilation passage 13 is surrounded by four walls of the retainer 10. These four wall portions are composed of a pair of side wall portions 14 facing each other in the left-right direction, and an upper wall portion 15 and a bottom wall portion 16 facing each other in the vertical direction.

The bezel 12 is a member that constitutes the most downstream portion of the retainer 10. In the bezel 12, an air outlet 17 from which the air conditioning air A1 is blown out is formed at a location at the downstream end of the ventilation passage 13. The downstream end surface of the bezel 12 and the portion around the air outlet 17 constitutes the design surface of the air conditioning register.

<Downstream fin group>
As shown in FIGS. 2 and 8, the downstream fin group consists of a plurality of (two) downstream fins 18 and 19 arranged so as to be separated in the vertical direction. The downstream fins 18 and 19 are used to change the blowing direction of the air conditioning air from the air outlet 17 up and down. The main parts of the downstream fins 18 and 19 are formed of plate-like bodies extending in the left-right direction and the flow direction of the air conditioning air A1 in the ventilation passage 13, respectively.

As shown in FIGS. 2 and 6, downstream fin shafts 21 extending in the same direction are provided on both end faces of the downstream fins 18 and 19 in the left-right direction. Each downstream fin shaft 21 is located at the downstream end of the downstream fins 18 and 19 in the flow direction of the air conditioning air A1. The downstream fin shafts 21 for each of the downstream fins 18 and 19 are supported by the bearing portions 22 on both side wall portions 14.

In each of the downstream fins 18 and 19, a connecting pin 23 extending parallel to the downstream fin shaft 21 is provided at a portion deviated upstream from one of the downstream fin shafts 21 (on the right in the present embodiment). The connecting pins 23 for each of the downstream fins 18 and 19 are connected to each other by a vertical connecting rod 24 extending substantially in the vertical direction. The upper and lower downstream fins 18 and 19 are mechanically connected by the connecting pin 23 and the vertical connecting rod 24, and the lower downstream fin 19 has the same tendency as the upper downstream fin 18 so as to have the same inclination as the upper downstream fin 18. A link mechanism LM1 that tilts in synchronization with the fin 18 is configured.

A tubular portion 25 having both an upstream end and a downstream end open is integrally formed in an intermediate portion in the left-right direction of the upper downstream fin 18 (see FIG. 8). The tubular portion 25 has a flat shape having a large horizontal dimension with respect to the vertical dimension.

<Upstream fin group>
The upstream fin group consists of a plurality of upstream fins arranged on the upstream side of the downstream fin group in the ventilation passage 13. Each upstream fin is used to change the blowing direction of the air conditioning air A1 from the air outlet 17 to the left or right. Each upstream fin is formed of a plate-like body extending in the vertical direction and the flow direction of the air conditioning air A1 in the ventilation passage 13. Most of the plurality of upstream fins are arranged in a state of being substantially parallel to each other at substantially equal intervals in the left-right direction.

Here, in order to distinguish a plurality of upstream fins, those adjacent to each other in the central portion in the left-right direction are referred to as "center upstream fins 28", and those other than that are referred to as "upstream fins 29". When it is not necessary to distinguish a plurality of upstream fins, it may be simply referred to as upstream fins 28 and 29.

As shown in FIGS. 2 and 9, upstream fin shafts 31 extending in the same direction are provided on both end faces of the upstream fins 28 and 29 in the vertical direction. Both upstream fin shafts 31 for each of the upstream fins 28 and 29 are located substantially at the center of the upstream fins 28 and 29 in the flow direction of the air conditioning air A1. Both upstream fin shafts 31 for each of the upstream fins 28 and 29 are supported by the bearing portion 32 so as to be tiltable with respect to the upper wall portion 15 and the bottom wall portion 16.

As shown in FIGS. 2, 6 and 9, each of the upstream fins 28 and 29 is provided with a notch 33 and a connecting pin 34, respectively. Each notch 33 is located downstream of the upstream fins 28 and 29 in the flow direction of the air conditioning air A1. Further, each notch portion 33 is located at the central portion of the upstream fins 28 and 29 in the vertical direction. Each connecting pin 34 extends in the vertical direction at a portion of the notch 33 that is biased toward the downstream side from the upstream fin shaft 31. The connecting pins 34 for each of the upstream fins 28 and 29 are connected to each other by a horizontal connecting rod 35 extending substantially in the left-right direction. The link mechanism LM2 is configured by the connecting pin 34 and the lateral connecting rod 35 to tilt all the upstream fins 28 and 29 in a synchronized state so as to have the same inclination.

<Shut damper 40>
As shown in FIGS. 3 and 6, the shut damper 40 is for opening and closing the ventilation passage 13 on the upstream side of the upstream fin group in the retainer 10. The shut damper 40 includes a pair of upper and lower damper plates 41 and 46. Each of the damper plates 41 and 46 has an elongated plate shape in the left-right direction with respect to the flow direction of the air conditioning air A1. Seal portions 41a and 46a, which are thinner and more flexible than the other parts of the damper plates 41 and 46, are formed around the damper plates 41 and 46.

Damper shafts 42 extending in the same direction are provided at both ends of the upper damper plate 41 in the left-right direction. In the upper damper plate 41, a pair of bearing portions 43 are provided between the two damper shafts 42 and at locations separated from each other in the left-right direction. Damper shafts 47 extending in the same direction are provided at both ends of the lower damper plate 46 in the left-right direction. In the lower damper plate 46, a pair of bearing portions 48 are provided between the two damper shafts 47 and at locations separated from each other in the left-right direction. The damper shafts 42, 47 and the bearing portions 43, 48 are located on the same straight line at the downstream ends of both damper plates 41, 46.

The upper damper plate 41 is supported by the bearing portion 51 on the right side wall portion 14 on the right damper shaft 42, and is supported on the lower damper plate 46 by the bearing portion 48 on the left damper shaft 42. Has been done.

The lower damper plate 46 is supported by the bearing portion 52 on the left side wall portion 14 on the left damper shaft 47, and is supported on the upper damper plate 41 by the bearing portion 43 on the right damper shaft 47. Has been done.

Each of the damper plates 41 and 46 can tilt in opposite directions between the open position and the closed position with both damper shafts 42 and 47 as fulcrums. In the open position, each of the damper plates 41 and 46 is a substantially central portion between the upper wall portion 15 and the bottom wall portion 16, as shown in FIGS. 8 and 12 (b), and the upper wall portion 15 and the bottom thereof. It is substantially parallel to the wall portion 16 and greatly opens the ventilation passage 13. In the closed position, the shut damper 40 contacts the upper wall portion 15 and the bottom wall portion 16 in a greatly inclined state as shown in FIG. 11B, and closes the ventilation passage 13.

<Operation knob 55>
As shown in FIGS. 1, 6 and 8, the operation knob 55 is a member operated by an occupant when tilting the downstream fins 18, 19, the upstream fins 28, 29 and the shut damper 40, respectively. The operation knob 55 is configured by assembling a plurality of members. These members are broadly composed of a member that constitutes the knob body 56 and a member that constitutes the rotating portion 61. The knob body 56 is slidably mounted in the left-right direction with respect to the tubular portion 25 of the upper downstream fin 18.

As shown in FIGS. 3, 6 and 8, the rotating portion 61 includes a knob portion 62 and a shaft portion 63. The knob portion 62 is rotatably attached to the knob body 56. Between the knob body 56 and the knob 62, the knob 62 is opened at the closing instruction position shown in FIG. 11A and the rotation phase shifted by 90 ° from that position as shown in FIG. 12A. A stopper (not shown) is provided that allows rotation within an angle range between the designated position and prevents rotation beyond that angle range.

The shaft portion 63 is rotatably inserted through the knob body 56, and is rotatably connected to the knob portion 62 at the downstream end thereof.
Further, the following configuration is adopted to transmit the movement of the operation knob 55 to each of the two central upstream fins 28 and the shut damper 40 and tilt them.

As shown in FIGS. 2 and 6, a transmission portion 36 having a transmission hole 37 extending in the flow direction of the air conditioning air A1 is integrally formed in a portion of the horizontal connecting rod 35 located between the two central upstream fins 28. It is formed.

As shown in FIGS. 6 and 8, a transmission shaft 65 extending along the flow direction of the air conditioning air A1 is inserted through the transmission unit 36. A disk-shaped contact 66 having a diameter larger than the diameter of the transmission shaft 65 is formed at the insertion point of the transmission shaft 65 into the transmission hole 37.

The transmission hole 37 is formed in a vertically long hole shape. This is because the inner wall surface of the transmission hole 37 in the transmission unit 36 swings in the left-right direction with the transmission shaft 65 as a fulcrum as the operation knob 55 slides. This is to convey to.

Between the transmission shaft 65 and both damper plates 41 and 46, the rotation direction of the operation knob 55 transmitted via the transmission shaft 65 is changed to change the rotation direction to transmit to the damper plates 41 and 46. The mechanism TM1 is provided. As shown in FIGS. 4 and 8, the rotation direction changing mechanism TM1 includes an arm portion 44 provided on the upper damper plate 41, an arm portion 49 provided on the lower damper plate 46, and a cam member 76. It has.

The upper arm portion 44 extends from the intermediate portion in the left-right direction to the downstream side in the upper damper plate 41. The arm portion 44 is curved so as to bulge upward, and has a sliding end portion 44a having a spherical surface at a downstream end portion which is its own tip portion. The lower arm portion 49 extends from the intermediate portion in the left-right direction to the downstream side in the lower damper plate 46. The arm portion 49 is curved so as to bulge downward, and has a sliding end portion 49a having a spherical surface at a downstream end portion which is its own tip portion. As shown in FIGS. 11 (b) and 12 (b), both sliding end portions 44a and 49a have an arcuate path centered on the damper shafts 42 and 47 as the damper plates 41 and 46 tilt. Move along T1.

As shown in FIGS. 3 and 6, a cylindrical outer cylinder member 74 is used to support the cam member 76 on both damper plates 41 and 46. The outer cylinder member 74 includes a pair of shafts 75 that project in the left-right direction. The left shaft 75 is supported by the left bearing 43 in the upper damper plate 41. The right shaft 75 is supported by the right bearing 48 on the lower damper plate 46. In this way, the outer cylinder member 74 is supported by both damper plates 41 and 46.

The cam member 76 is rotatably mounted in the outer cylinder member 74. As shown in FIG. 4, the cam member 76 has a cam groove 77 on the outer surface on which the sliding end portions 44a and 49a are slidably engaged with each other. In the present embodiment, the cam groove 77 is formed on the outer surface of the cam member 76 over the entire circumference and has an endless shape. As shown in FIGS. 4 and 5 (a) to 5 (c), the cam groove 77 has sliding end portions 44a and 49a when the damper plates 41 and 46 are tilted between the open position and the closed position, respectively. Has a pair of sliding regions 78 on which the Both sliding regions 78 are located at locations facing each other across the axis L1 of the cam member 76. Each sliding region 78 is set in an angle range of 90 ° around the axis L1.

Free running regions 78b are set at both ends of each sliding region 78. In each idle region 78b, when the cam member 76 rotates by a certain angle, the amount of movement in the direction along the arcuate path T1 (see FIG. 12B) at the engagement position with the sliding end portions 44a and 49a is large. This is a region that is smaller than the general region 78a that constitutes the intermediate portion of the sliding region 78.

Each idle region 78b has the arcuate path T1 (FIG. 12) around the damper shafts 42 and 47 when the sliding end portions 44a and 49a slide from one end to the other end of the idle region 78b. (See (b)) It is formed so as to move 3 ° to 5 ° above. Due to such formation, one end portion and the other end portion of each idle region 78b are located at locations separated from each other in the direction along the arcuate path T1.

On the outer surface of the cam member 76, a recess 81 is formed in a part of the region sandwiched between the sliding regions 78.
As shown in FIGS. 12 (b) and 13 (b), in the cam member 76 in a state where the sliding ends 44a and 49a are engaged with both sliding regions 78, the cam member 76 includes the axis L1 and both slides. The cross section 82 passing through the moving end portions 44a and 49a has a curved portion 84. The curved portion 84 has an arcuate path T1 (see FIG. 12B) between the most upstream portion 83 in the cross section 82 and the portion where the sliding end portions 44a and 49a of the sliding regions 78 are engaged. ) Is curved. The curved portion 84 is located between the recess 81 and the cam groove 77. In the present embodiment in which the cam member 76 is provided with the recess 81, the boundary portion between the recess 81 and the curved portion 84 is the most upstream portion 83. Further, in the present embodiment, the curved portion 84 is formed of an arc having a constant radius R1. Specifically, the cam groove 77 is formed so that the center of the cam groove 77 is located on the spherical surface S1, and the curved portion 84 is formed by an arc having the center C2 of the spherical surface S1 as its own center. ing.

As shown in FIGS. 3 and 8, the downstream end portion of the transmission shaft 65 is flexibly and rotationally transmitted to the rotating portion 61 of the operation knob 55 by a cardan joint J1 on the downstream side. More specifically, at the downstream end of the transmission shaft 65, a pair of arm portions 67 sandwiching the axis of the transmission shaft 65 are formed. On the other hand, the upstream end of the rotating portion 61 is composed of the support member 57. The support member 57 has a support shaft 58 extending in a direction orthogonal to the direction in which both arm portions 67 face each other. Both arms 67 and the support shaft 58 are connected by a connecting member 68. The connecting member 68 is formed with transmission pins 69 projecting in opposite directions. The connecting member 68 is rotatably supported by both arm portions 67 at these transmission pins 69. Further, the connecting member 68 has an engaging recess 71, and is rotatably supported by the support shaft 58 in the engaging recess 71. Then, the cardan joint J1 on the downstream side is configured by the both arm portions 67, the support member 57, and the connecting member 68.

The upstream end of the transmission shaft 65 is flexibly and rotationally transmitted to the cam member 76 by a cardan joint J2 on the upstream side. The cam member 76 is formed with an engaging recess 85 that opens at the downstream end surface thereof. The engaging recess 85 has a substantially cylindrical inner surface. A pair of engaging groove portions 86 (see FIG. 6) extending along the coaxial line L1 are formed on the inner surface of the engaging recess 85 at locations facing each other with the axis L1 of the cam member 76 interposed therebetween.

On the other hand, a disk-shaped engaging convex portion 72 is formed on the outer periphery of the upstream end portion of the transmission shaft 65. A transmission pin 73 is formed on the engaging convex portion 72 so as to project in the radial direction and in opposite directions (see FIG. 6). The engaging convex portion 72 is slidably engaged with the cam member 76 in a state where the outer surface thereof is in contact with the cylindrical inner surface of the engaging concave portion 85. Both transmission pins 73 are engaged with the corresponding engaging grooves 86 of the cam member 76. The cardan joint J2 on the upstream side is formed by the engaging groove portion 86, the engaging convex portion 72, and both transmission pins 73. In the cardan joint J2 on the upstream side, the transmission shaft 65 can swing with respect to the cam member 76 with the engaging convex portion 72 as a fulcrum. Further, the rotation of the transmission shaft 65 can be transmitted to the cam member 76 by both transmission pins 73. Further, each transmission pin 73 can move in the flow direction of the air conditioning air A1 along the corresponding engaging groove portion 86.

Next, the operation and effect of the present embodiment configured as described above will be described.
FIG. 11B shows a state when both damper plates 41 and 46 are in the closed position. In this state, the ventilation passage 13 is closed by both damper plates 41 and 46. The flow of the air conditioning air A1 is cut off downstream of both damper plates 41 and 46 of the ventilation passage 13, and the blowing of the air conditioning air A1 from the air outlet 17 is stopped.

On the other hand, FIGS. 8 and 12 (b) show the state when both damper plates 41 and 46 are in the open position. In this state, the ventilation passage 13 is fully opened, and the air conditioning air A1 flows separately to the upper side of the damper plate 41 and the lower side of the damper plate 46. The air-conditioning air A1 that has passed through both damper plates 41 and 46 flows along the upstream fin group, the downstream fin group, and the like, and then blows out from the air outlet 17.

Switching from the closed position to the open position and switching from the open position to the closed position of the shut damper 40 is performed by rotating the knob 62 on the operation knob 55, as shown in FIGS. 11 (a) and 12 (a). It is done through. When the knob 62 is rotated by an occupant, the rotation of the knob 62 is performed via the downstream cardan joint J1, the transmission shaft 65, and the upstream cardan joint J2, as shown in FIGS. 6 and 8. It is transmitted to the cam member 76. The cam member 76 rotates about its own axis L1, and the cam groove 77 having a pair of sliding regions 78 also rotates about the coaxial line L1.

As the cam groove 77 rotates, the positions where the sliding end portions 44a, 49a of each of the arm portions 44, 49 are engaged in each sliding region 78 are located on the arcuate path T1 centered on the damper shafts 42, 47. Each changes along. With the change of both engaging positions, the damper plates 41 and 46 are tilted in opposite directions between the open position and the closed position, respectively, with the damper shafts 42 and 47 as fulcrums. The rotation direction and the tilt direction of the rotating portion 61 of the operation knob 55 and both damper plates 41 and 46 are different from each other, but the rotation direction of the rotating portion 61 is changed by passing through the rotation direction conversion mechanism TM1 as described above. Then, it is transmitted to the damper plates 41 and 46, and the damper plates 41 and 46 are tilted, respectively. Due to these tilts, the opening degree of the ventilation passage 13 changes.

When the knob 62 is rotated to the closing instruction position shown in FIG. 11A, both the upper damper plate 41 and the lower damper plate 46 reach the closing position as shown in FIG. 11B. The upper damper plate 41 is in an inclined state so as to be higher toward the upstream portion, and comes into contact with the upper wall portion 15 at the seal portion 41a. The lower damper plate 46 is in an inclined state so as to be lower toward the upstream portion, and comes into contact with the bottom wall portion 16 at the seal portion 46a. In this way, both damper plates 41 and 46 are bent with the damper shafts 42 and 47 as fulcrums, and the ventilation passage 13 is closed.

Contrary to the above, when the knob portion 62 is rotated to the open instruction position shown in FIG. 12 (a), the upper damper plate 41 reaches the open position and becomes substantially parallel to the upper wall portion 15. Further, the lower damper plate 46 reaches the open position and becomes substantially parallel to the bottom wall portion 16. Both damper plates 41 and 46 are overlapped in the vertical direction, and the ventilation passage 13 is greatly opened.

As described above, the opening degree of the ventilation passage 13 can be changed by rotating the knob portion 62, and the amount of air conditioning air A1 passing through the shut damper 40 in the ventilation passage 13 can be adjusted.

Further, when the transmission shaft 65 is rotated as described above, the rotation is not transmitted to the upstream fins 28 and 29. This is because, as shown in FIGS. 6 and 8, the contactor 66 rotates in the transmission hole 37 with the rotation, and the force is not transmitted between the contactor 66 and the transmission unit 36. Therefore, the upstream fins 28 and 29 do not tilt. Further, the force is not transmitted between the operation knob 55 and the tubular portion 25. Therefore, the downstream fins 18 and 19 do not tilt either.

The following description is based on the premise that the shut damper 40 is in the open position.
6 and 8 show air conditioning registers when both downstream fins 18 and 19 are in the neutral state and all the upstream fins 28 and 29 are in the neutral state. At this time, both downstream fins 18 and 19 are substantially parallel to the upper wall portion 15 and the bottom wall portion 16. Further, the upstream fins 28 and 29 are made substantially parallel to the left and right side wall portions 14.

Therefore, the air-conditioning air A1 that has passed through the shut damper 40 flows along the upstream fins 28, 29, the side wall portion 14, and then along the downstream fins 18, 19, the upper wall portion 15, the bottom wall portion 16, and the like. It flows and blows straight out from the outlet 17.

At this time, the operation knob 55 is located at the central portion of the upper downstream fin 18 in the left-right direction of the tubular portion 25. The axis of the shaft portion 63 in the rotating portion 61 is substantially parallel to the upper wall portion 15 and the bottom wall portion 16 as in the downstream fins 18 and 19. The transmission shaft 65 is substantially parallel to both the upper wall portion 15 and the bottom wall portion 16 and both side wall portions 14.

When a force is applied to the operation knob 55 in the vertical direction, for example, downward from both neutral states, the upper downstream fin 18 is tilted clockwise with the downstream fin shaft 21 as a fulcrum. .. This tilt is transmitted to the lower downstream fin 19 via the link mechanism LM1 (see FIG. 6). Due to this transmission, the lower downstream fin 19 is tilted toward the operated side of the operation knob 55 in synchronization with the upper downstream fin 18. Both the operation knob 55 and the downstream fins 18 and 19 are tilted so as to be lower toward the downstream side. The air-conditioning air A1 flows along the downstream fins 18 and 19 tilted as described above, so that the air can be turned and blown diagonally downward from the outlet 17.

The tilt of the operation knob 55 is transmitted to the transmission shaft 65 via the cardan joint J1 on the downstream side. Therefore, the transmission shaft 65 swings in the vertical direction with the shaft 75 of the outer cylinder member 74 engaged with the damper plates 41 and 46 as a fulcrum. For example, when a downward force is applied to the operation knob 55 as described above, the shaft portion 63 is inclined so as to be higher toward the upstream side. The transmission shaft 65 is in an inclined state so as to be higher toward the downstream side.

However, the swing of the transmission shaft 65 is not transmitted to the upstream fins 28 and 29. This is because the contact 66 of the transmission shaft 65 moves in the above direction (upward) in the transmission hole 37 due to the swing, and the force is not transmitted between the contact 66 and the transmission unit 36. is there. Both the upper and lower inner wall surfaces of the transmission hole 37 do not come into contact with the contactor 66 or a portion different from the contactor 66 of the transmission shaft 65. As a result, all the upstream fins 28 and 29 do not tilt.

When a force is applied to the operation knob 55 in the left-right direction, for example, to the left from both neutral states, the operation knob 55 is in the same direction with the cardan joint J1 on the downstream side, as shown in FIG. Slide to. Therefore, the transmission shaft 65 swings in the above direction (leftward) with the engaging convex portion 72 as a fulcrum.

The swing of the transmission shaft 65 is transmitted to the lateral connecting rod 35. This is because the contactor 66 of the transmission shaft 65 comes into contact with the left and right inner wall surfaces of the transmission hole 37 in the transmission portion 36 due to the swing, and the force is transmitted between the contactor 66 and the transmission portion 36. is there. The transmission portion 36 moves to the left together with the other portion of the lateral connecting rod 35. This movement is transmitted to the upstream fins 28 and 29. As a result, the upstream fins 28 and 29 tilt in the clockwise direction as shown in FIG. 7 with the upstream fin shaft 31 as a fulcrum.

The air-conditioning air A1 flows along the upstream fins 28 and 29 tilted as described above, so that the air can be turned and blown to the left from the outlet 17.
The above is an action when the operation knob 55 is tilted or slid from the neutral state based on the neutral states of the upstream fins 28 and 29 and the downstream fins 18 and 19, but the neutral state. Even when the operation knob 55 is tilted or slid from a state different from the above, each part of the air conditioning register operates in the same manner as described above. Further, in the operation of rotating the knob portion 62 to tilt the shut damper 40, even if the upstream fins 28 and 29 are tilted with respect to the side wall portions 14, the downstream fins 18 and 19 are inclined to the upper wall portion 15 and the bottom. It is possible even if the wall portion 16 is inclined. This is because the downstream end of the transmission shaft 65 is connected to the rotating portion 61 by the cardan joint J1 on the downstream side, and the upstream end is connected to the cam member 76 by the cardan joint J2 on the upstream side. Even if the axis of the transmission shaft 65 and the axis of the rotating portion 61 intersect, the force is transmitted. Further, even if the axis of the transmission shaft 65 and the axis L1 of the cam member 76 intersect, the force is transmitted.

By operating the operation knob 55 having the rotating portion 61 in this way, the downstream fins 18, 19, the upstream fins 28, 29, and the shut damper 40 can be tilted, respectively.
Here, it is assumed that when the cam member 76 rotates by a certain angle, the amount of movement of the engagement position of the cam groove 77 with the sliding end portions 44a and 49a in the direction along the arcuate path T1 is uniform. .. Then, when the operation knob 55 is rotated in a state where the intersection angle between the axis of the operation knob 55 and the axis of the transmission shaft 65 is large, or when the intersection angle between the axis of the transmission shaft 65 and the axis L1 of the cam member 76 is large. , The rotation deviation that occurs between the operation knob 55 and the cam member 76 becomes large.

In this regard, in the present embodiment, as shown in FIGS. 5A to 5C, free running regions 78b are set at both end portions of each sliding region 78 in the cam groove 77. In each idle region 78b, when the cam member 76 rotates by a certain angle, the amount of movement in the direction along the arcuate path T1 (see FIG. 12B) at the engagement position with the sliding end portions 44a and 49a is , Less than the general area 78a. Specifically, when the sliding end portions 44a and 49a slide from one end to the other end of the free running region 78b, the sliding end portions 44a and 49a are 3 ° to 3 ° on the arcuate path T1 around the damper shafts 42 and 47. Move 5 °. The sliding end portions 44a and 49a are located at locations separated from each other in the direction along the arcuate path T1 when they are located at one end of the free running region 78b and when they are located at the other end. To do.

Therefore, when the sliding end portions 44a and 49a of each of the damper plates 41 and 46 slide in the idle region 78b, the tilt angle of the damper plates 41 and 46 with the damper shafts 42 and 47 as fulcrums is determined. The number of sliding ends 44a and 49a is smaller than that when sliding in the general region 78a. In other words, when the sliding end portions 44a and 49a slide in the corresponding idle region 78b, the damper plates 41 and 46 tilt more gently than when sliding in the general region 78a.

Therefore, in each idle region 78b, the rotational deviation caused by the intersection angle of the two axes of the transmission shaft 65 and the operation knob 55 and the intersection angle of the two axes of the transmission shaft 65 and the cam member 76 is absorbed, and the deviation is absorbed. The phenomenon caused by is eliminated.

For example, when the knob portion 62 is rotated to the closing instruction position shown in FIG. 11A, it is possible to prevent both damper plates 41 and 46 from tilting beyond the closing position, respectively. Interference with the upper wall portion 15 of the damper plate 41 is suppressed, interference with the bottom wall portion 16 of the damper plate 46 is suppressed, and the operation knob 55, the rotation direction changing mechanism TM1, and the parts arranged between them are used. It is possible to suppress the application of a load.

Contrary to the above, both damper plates 41 and 46 do not tilt to the closed positions, the ventilation passage 13 is not closed, a gap is created between the damper plate 41 and the upper wall portion 15, and the damper plate 46 and It is possible to prevent the air-conditioning air A1 from leaking from the gap between the bottom wall portion 16 and the bottom wall portion 16.

Further, for example, when the knob portion 62 is rotated to the open instruction position shown in FIG. 12A, both damper plates 41 and 46 do not tilt to the open position, but tilt with respect to the flow direction of the air conditioning air A1. It is possible to suppress the situation in which the air conditioner is formed. Both damper plates 41 and 46 serve as resistance to the flow of the air conditioning air A1 and can suppress a decrease in the amount of blowout.

By the way, the above-mentioned effect that each free-running region 78b absorbs the rotation deviation is maximized when the free-running region 78b is located at the same place on the arcuate path T1 at any place. This is because when the sliding end portions 44a and 49a slide on the cam groove 77 in the idle region 78b, both damper plates 41 and 46 do not tilt.

However, as in the present embodiment, even if one end and the other end of the idling region 78b are separated from each other in the direction along the arcuate path T1, 3 ° to 3 ° on the arcuate path T1. If the distance is about 5 °, the effect of absorbing the above-mentioned rotation deviation can be obtained.

In the above air-conditioning register, both damper plates 41 and 46 are at positions different from the closed position, for example, as shown in FIG. 12B, with respect to both damper plates 41 and 46 which are both stationary in the open position. It is possible that forces are applied in their thickness direction. For example, when a downward force is applied, both damper plates 41 and 46 tilt downward with the damper shafts 42 and 47 as fulcrums. As shown in FIG. 13A, the sliding end portion 44a of the upper damper plate 41 is disengaged from the cam groove 77. Then, the rotation direction conversion mechanism TM1 does not properly convert the rotation direction.

However, the sliding end 49a of the lower damper plate 46 continues to engage the cam groove 77. This is because the sliding end portion 49a moves along the arcuate path T1 as the lower damper plate 46 with the damper shaft 47 as a fulcrum tilts, and the sliding end portion 49a engages with the cam groove 77. This is because the mating position changes and the cam member 76 rotates.

From this state, when the operation knob 55 is rotated to the open instruction position side, that is, the side that tilts both damper plates 41 and 46 to the open position, the cam member 76 rotates and the cam groove 77 at the sliding end portion 49a. The lower damper plate 46 that is engaged tilts. The upper damper plate 41 whose sliding end 44a is detached from the cam groove 77 is pushed upward by the lower damper plate 46. The upper damper plate 41 tilts upward along the arcuate path T1 with the damper shaft 42 as a fulcrum.

Here, if there is a portion between the sliding end portion 44a and the cam groove 77 that hinders the movement of the sliding end portion 44a, it is difficult to engage the sliding end portion 44a with the cam groove 77. .. For example, as shown in FIG. 13A, the outer peripheral surface of the cam member 76 has a cylindrical shape with the axis L1 as its center, and the upstream end surface of the cam member 76 has a planar shape orthogonal to the axis L1. When the cam groove 77 is formed on the outer peripheral surface, the corner portion 76a between the outer peripheral surface and the upstream end surface hinders the movement of the sliding end portion 44a. In the state where the movement of the sliding end portion 44a is hindered in this way, when a force is applied to the operation knob 55 to further rotate it toward the opening instruction position side, it engages with the cam groove 77. Even the sliding end portion 49a may come off from the cam groove 77.

In this respect, in the present embodiment, as shown in FIG. 13B, in the cam member 76, the cross section 82 including the axis L1 and passing through both sliding end portions 44a and 49a is the most upstream portion 83 and the cross section 82. A curved portion 84 is provided between the sliding end portions 44a and 49a of the sliding region 78 and the engaging portion. The curved portion 84 is curved along the arcuate path T1. Therefore, there is no portion between the sliding end portion 44a and the cam groove 77 that hinders the movement of the sliding end portion 44a, or a state close to the sliding end portion 44a. Therefore, when the upper damper plate 41 pushed by the lower damper plate 46 tilts upward along the arcuate path T1 with the damper shaft 42 as a fulcrum, the sliding end portion 44a moves along the curved portion 84. Then, as shown in FIG. 12B, the cam groove 77 is engaged again. Both sliding ends 44a and 49a are in a state of being engaged with the cam groove 77.

In particular, in the present embodiment, the curved portion 84 is formed by a constant arc having a radius R1. Therefore, when the upper damper plate 41 tilts upward along the arcuate path T1 with the damper shaft 42 as a fulcrum, the force required to move the sliding end portion 44a along the curved portion 84 is , It becomes substantially constant at any position of the curved portion 84. Therefore, the sliding end portion 44a can be moved more smoothly and can be engaged with the cam groove 77.

When an upward force is applied to both damper plates 41 and 46 in FIG. 12B and the sliding end portion 49a is disengaged from the cam groove 77, the operation knob 55 is moved to the opening instruction position side. By being rotated, the sliding end portion 49a is engaged with the cam groove 77 again in the same manner as described above.

As a result, the rotation direction conversion mechanism TM1 can properly convert the rotation direction.
In addition, the above-described embodiment can also be implemented as a modified example in which this is modified as follows.

The cardan joint J1 on the downstream side may connect the rotating portion 61 of the operation knob 55 and the transmission shaft 65 so that the angle at which their axes intersect can be freely changed. Therefore, as the cardan joint J1 on the downstream side, a so-called universal joint as described above may be adopted, but a joint of a different type, for example, a ball joint may be used.

In the above embodiment, the cam groove 77 includes a region that does not participate in the sliding of the sliding end portions 44a and 49a, but the region that does not participate in the sliding is omitted, and the cam is provided only by the sliding region 78. The groove 77 may be configured. In this case, the cam grooves 77 are provided at two positions facing each other with the axis L1 in between.

The free running region 78b may be omitted from the sliding region 78 of the cam groove 77, and the sliding region 78 may be composed of only the general region 78a.
The shape of the curved portion 84 in the cross section 82 of the cam member 76 can be changed to a shape different from that of the above embodiment on condition that the curved portion 84 is curved along the arcuate path T1. For example, the curved portion 84 in the cross section 82 of the cam member 76 may be composed of a plurality of arcs having different radii.

-In the above embodiment, a configuration is adopted in which the rotation of the rotating portion 61 on the operation knob 55 is restricted between the closing instruction position and the open instruction position. Therefore, the rotating portion 61 is rotated (rotated) in the forward and reverse directions between the closing instruction position and the opening instruction position, so that both damper plates 41 and 46 are tilted between the opening position and the closing position, respectively. To. However, the limitation of the rotation region is not essential and may be lifted. In this case, the rotating portion 61 is rotated in only one direction. Even if it is changed in this way, if the cam groove 77 is formed over the entire circumference of the outer peripheral surface of the cam member 76 and has an endless shape as in the above embodiment, both damper plates 41 and 46 are opened. It is possible to tilt between the position and the closed position respectively.

In the above embodiment, the cam member 76 is rotated by 90 ° by rotating the rotating portion 61 of the operation knob 55 by 90 ° between the closing instruction position and the opening instruction position, and both damper plates 41 and 46. Is tilted between the closed position and the open position. Instead, the cam member 76 is different from 90 ° by rotating the rotating portion 61 of the operation knob 55 at an angle different from 90 °, for example, 180 °, between the closing instruction position and the open instruction position. It may be rotated by an angle (180 °) so that both damper plates 41, 46 are tilted between the closed position and the open position.

The recess 81 in the cam member 76 may be omitted.
-The numbers of the downstream fins 18, 19 and the upstream fins 28, 29 may be changed to different numbers from those in the above embodiment.

The downstream fins 18 and 19 may be formed of plate-like bodies extending in the vertical direction and the flow direction of the air conditioning air A1 in the ventilation passage 13, respectively. Further, the upstream fins 28 and 29 may be formed of plate-like bodies extending in the left-right direction and the flow direction of the air conditioning air A1 in the ventilation passage 13, respectively.

-The above-mentioned air-conditioning register can also be applied to an air-conditioning register provided in a place different from the instrument panel in the vehicle interior.
The air-conditioning register changes the direction of the air-conditioning air A1 sent from the air-conditioning device by the upstream fins 28 and 29 and the downstream fins 18 and 19 and blows it into the room, and shuts off the blown air by the shut damper 40. As long as it can be used, it can be widely applied not only to vehicles.

13 ... Ventilation path, 40 ... Shut damper, 41,46 ... Damper plate, 42,47 ... Damper shaft, 44,49 ... Arm part, 44a, 49a ... Sliding end part, 55 ... Operation knob, 65 ... Transmission shaft, 76 ... cam member, 77 ... cam groove, 78 ... sliding region, 82 ... cross section, 83 ... most upstream part, 84 ... curved part, A1 ... air conditioning air, C1, C2 ... center, L1 ... cam member axis, R1 ... radius, S1 ... spherical surface, T1 ... arcuate path, TM1 ... rotation direction conversion mechanism.

Claims (3)

It is equipped with a rotation direction conversion mechanism that changes the direction of rotation of the operation knob transmitted through the transmission shaft extending in the flow direction of the air conditioning air in the ventilation path and transmits it to the shut damper.
The shut damper includes a pair of damper plates that are tilted in opposite directions between an open position and a closed position with a damper axis on the same line as a fulcrum by a force transmitted from the rotation direction changing mechanism.
The rotation direction changing mechanism includes a pair of arm portions having a sliding end portion at the tip that extends from each damper plate and moves along an arcuate path centered on the damper axis as the damper plate tilts. A cam member having a cam groove on the outer surface to which each sliding end is slidably engaged is provided.
Both sliding ends are engaged with the cam groove in a pair of sliding regions facing each other across the axis of the cam member, and both sliding ends are engaged with both sliding regions. In the cam member in the state, the cross section including the axis of the cam member and passing through both sliding ends is a portion where the most upstream portion in the same cross section and each sliding end of each sliding region are engaged. An air conditioning register having a curved portion curved along the arcuate path between the and. The air-conditioning register according to claim 1, wherein the curved portion is formed of an arc having a constant radius. The cam groove is formed so that the center of the cam groove is located on a spherical surface.
The air-conditioning register according to claim 2, wherein the curved portion is formed of an arc having the center of the spherical surface as its own center.