JP2001317853A - Double damper device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce a dead space and extend the distance between two openings in a double damper device. SOLUTION: The double damper device is provided with two opening/closing boards 5, 5 for two openings 4, 4. A driving part 2 for driving both boards 5, 5 is provided between the openings 4, 4. In this case, driving shafts are provided to the respective boards 5, 5, side walls 3a, 3a supporting the driving shafts are provided to frames 3, 3 in which opening 4, 4 are formed, and the driving part 2 may be provided between the central both side-walls 3a, 3a adjacent to each other.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a double damper device which uses a motor or the like as a drive source and operates an opening / closing plate such as a baffle with respect to two openings, and particularly controls the intake of cool air in a refrigerator. The present invention relates to a suitable double damper device.

[0002]

2. Description of the Related Art A conventional damper device having a single opening, particularly a motor type damper device 70 for a refrigerator,
As shown in FIG. 22 and FIG.
(See Japanese Patent Laid-Open No. 6-109354), a baffle 72 and a drive mechanism 73 such as a motor are disposed therebetween.
Reference). Then, the baffle 72 and the driving mechanism 73
While the backlash between the members in the
A leaf spring (not shown) that is constantly pressed in the closing direction of the baffle 72 to increase the degree of sealing between the baffle 72 and the frame 74 is disposed at the rear. In order to further improve the degree of sealing, a soft tape 75 is applied to the contact surface of the baffle 72 with the frame 74 so that the frame 74 is sunk, and the opening 76 is completely closed by the baffle 72. I have.

[0003] Such a conventional motor type damper device 7
At 0, the rotational torque of the motor is converted into the thrust torque of the spindle. The baffle 72 is rotated by the spindle thrust torque in the thrust direction.
Is driven so as to rotate about the center. As described above, since the rotational direction torque is changed to the thrust direction torque, it is necessary to provide rattling when the baffle 72 is closed in consideration of the accuracy of each component. Moreover,
Because of this rattling, it is necessary to press down the baffle 72 with a leaf spring or the like.

A motor type damper device 70 having such a structure is used in a refrigerator 80 as shown in FIG. That is, the refrigerator 80 is
And a refrigerator compartment 82 and a vegetable compartment 83,
An evaporator 84 is provided at the bottom of the evaporator. A fan motor 85 is arranged at the rear of the evaporator 84 to circulate the obtained cool air through the freezing room 81 and the refrigeration room 82.

[0005] A partition slope 86 is provided between the evaporator 84 and the refrigerating chamber 82 to block the cool air of the evaporator 84 from flowing directly to the refrigerating chamber 82. On the other hand, a cool air flow passage 87 is formed between the rear part of the partition slope 86 and the rear inner wall of the refrigerator 80, and a motor type damper device 70 is disposed in the cool air flow passage 87. When the baffle 72 of the motor-type damper device 70 is in an open state, the cool air flow passage 87, which is a passage of the cool air, is in a crank state. The motor-type damper device 70 is installed so as to be held by a partition wall 88 that forms a part of the cool air flow passage 87.

[0006] In recent years, with the mid-freezer of the refrigerator, a type of refrigerator in which the cool air obtained at the central evaporator portion is circulated to a refrigerator room at an upper position and a distant position has appeared.

The motor type damper device 70 is of a type orthogonal to the cold air flow passage 87 as described above, and can be used only for bending the flow of the cold air at a right angle. Moreover,
In the refrigerator 80 using such a motor-type damper device 70, since the cold air flow passage 87 has a crank shape, the cold air flow passage 87 becomes long, and loss occurs in terms of cold air transmission. This loss is extremely disadvantageous for a recent mid-freezer refrigerator due to its long cool air flow passage 87. In addition, since the cold air flow passage 87 has a crank shape, as shown in FIG.
8, the protrusion width M into the interior of the refrigerator 80 is increased,
This contributes to reducing the volume of the refrigerator 80.

Further, the opening operation of the baffle 72 does not open to a position parallel to the flow of cold air,
As shown in FIG. 7, since the baffle 72 opens only up to the oblique position, the baffle 72 becomes resistant to the flow of cool air, which is not preferable for rapid diffusion of cool air.

Further, such a motor type damper device 7
In a damper device used for a refrigerator or the like, including 0, when the baffle 72 is in the closed position, it is required to completely shut off cold air and the like. In addition, baffle 7
In the closed position 2, it is necessary to prevent the baffle 72 and the like from freezing and locking with other parts. Further, the pressing by the leaf spring has a strong force and is preferable for completely shutting off the cool air. Is not preferred.

Further, recently, there are increasing the number of refrigerators in which the interior of the refrigerator is divided into more than the refrigerators 80 shown in FIG. For this reason, the opening 76 shown in FIG. 22 and FIG.
As shown in FIG. 25, a double damper device 77 having two openings 76 is used. In the double damper device 77, two openings 76, 76 are formed in a frame 74, and a drive mechanism 73 such as a motor is disposed so as to be located on a lower side of a back surface. 22 and FIG.
Are provided and driven by one synchronous motor (not shown) in the drive mechanism 73 to open and close the openings 76, 76. The operation of the baffles 72, 72 is such that both are in the open position, both are in the closed position, one is in the open position and the other is in the closed position,
The four modes are set such that the other is in the open position and the other is in the closed position.

[0011]

In the conventional motor type damper device 70 and double damper device 77 shown in FIGS. 22, 23 and 25, the width N of the drive mechanism 73 is large and the portion is large. It is dead space.

Further, in the conventional double damper device 77 shown in FIG. 25, the output is obtained from one synchronous motor in the drive mechanism 73 and the baffles 72, 72 disposed on the upper side are moved, so that the drive mechanism is provided. In consideration of the miniaturization of the portion 73, the distance P between the openings 76 tends to be small. Distance P between both openings 76, 76
Is smaller, the heat insulation between the cool air flow passages 87 connected to the openings 76, 76 becomes insufficient, and the cold air flow passage 8
7 will appear in the other cool air flow passage 87. For this reason, severe temperature control for each room is difficult.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and has as its object to provide a double damper device capable of reducing dead space and increasing the distance between two openings.

[0014]

In order to achieve the above object, according to the first aspect of the present invention, there is provided a frame having two open / close plates which open and close two openings by rotating independently. In the double damper device,
A drive unit for driving the two opening / closing plates is housed in the case body between the two openings, and the center of rotation of each of the two opening / closing plates is set on both sides of the case body in which the driving unit is housed. Provided on the surface, the frame is fitted into the duct so as to form a part of a duct serving as a fluid passage, an opening / closing plate is housed inside the frame, and the frame is integrated with the case body. .

In addition, according to the second aspect of the present invention, in the double damper device according to the first aspect, the opening forming portion formed so as to surround the periphery of the opening of the opening is projected toward the opening / closing plate. A protrusion is provided.

According to the third aspect of the present invention, there is provided the second aspect.
In the double damper device described above, the opening forming portion is provided inside the frame, and the opening forming portion is formed in a cylindrical shape.

Further, according to the present invention, in a double damper device having a frame having two opening / closing plates for opening and closing two openings by rotating independently of each other, a space between the two openings is provided. A drive unit for driving the two open / close plates, a center of rotation of each of the two open / close plates is provided on both opposite sides of the drive unit, and the drive unit includes one motor serving as a drive source; One reduction gear train meshing with a fixed shaft serving as an output shaft of the motor, and drive shafts driven by the common reduction gear train and provided on two opening / closing plates, respectively, and having regulating guides on both surfaces. An operating lever having a single cam body, a pin fitted into the regulating guide portion and following the movement of the regulating guide portion, and having an engaging portion engaged with the drive shaft. ing

In this double damper device, the power of a driving source such as a motor is transmitted to a baffle serving as an opening / closing plate, and the baffle opens and closes an opening provided in a frame. And this opening is provided in parallel with the frame,
A drive unit such as a drive source is disposed between the openings. Thus, the two openings are each tightly closed by a baffle and the distance between the openings is automatically ensured by the presence of the drive. In addition, since the driving section is disposed between the openings, a wide dead space unlike the related art does not occur. Moreover, the place where the drive unit is disposed is a place where sufficient heat insulation is required, and if the drive unit is provided so as to fit in the minimum necessary space for the heat insulation, no dead space is generated. It will be.

When a frame is formed with an opening, a side wall is provided, the side wall supports a drive shaft of an opening / closing plate, and a driving section is provided between two central side walls. And the function of supporting the drive shaft at the same time. Therefore, the configuration is simplified and the size can be reduced.

[0020]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a double damper device according to the present invention will be described with reference to FIGS. In addition,
The double damper device of this embodiment is used for a refrigerator and is a motor-driven damper device driven by a motor.

This double damper device comprises a drive unit 2 having a stepping motor 1 disposed at the center, two cylindrical frames 3 and 3 open at both ends disposed on both sides of the drive unit 2, It mainly comprises two openings 4, 4 formed inside the frames 3, 3, and baffles 5, 5, which open and close the openings 4, 4, respectively. Note that the stepping motor 1 is a driving source,
Each of the baffles 5 and 5 is an opening / closing plate.

As shown in FIGS. 7 and 8, the stepping motor 1 in the driving section 2 has a fixed shaft 6, on which a rotor 7 having a pinion 7a is rotatably fitted. I have. The pinion 7a meshes with the gear portion 8a of the first gear 8, and the pinion portion 8b of the first gear 8
Are engaged with the gear portion 9a of the second gear 9. The pinion 9b of the second gear 9 meshes with the cam gear 10c of the cam body 10. This gear train reduces the rotation of the stepping motor 1 in this manner,
Tells 0.

As shown in FIG. 10, U-shaped cam grooves 10a and 10b serving as regulating guides are provided on both surfaces of the cam body 10. The operating levers 11, 11 are engaged with the cam grooves 10a, 10b. This operating lever 1
Reference numeral 1 denotes a lever portion 11a projecting to one side around a rotation fulcrum 12, a sector gear portion 11b serving as an engaging portion that opens 90 degrees from the lever portion 11a and projects to the other side,
Projecting pin 11c provided at the tip of lever portion 11a
And The pin 11c is connected to the cam grooves 10a and 10b.
And moves in the cam grooves 10a and 10b while being guided and guided.

The sector gear 11b is engaged with a drive shaft 5a formed on the baffle 5, and transmits the rotation of the operation lever 11 to the baffle 5. This engagement is performed when the gear 5b provided on the drive shaft 5a meshes with the sector gear 11b. Since the distance from the rotation fulcrum 12 to the tip of the sector gear 11b is shorter than the distance from the rotation fulcrum 12 to the pin 11c, the movement of the sector gear 11b is smaller than the movement of the lever 11a. Have been. Therefore, similar to the principle of leverage, the force for moving the gear 5b increases even though the force for moving the operation lever 11 is small. on the other hand,
Since the diameter of the sector gear 11b is larger than the diameter of the gear 5b provided on the drive shaft 5a and the number of teeth is increased, the rotation transmission from the sector gear 11b to the gear 5b is performed by a speed increasing gear train. It has become.

A case body 13 made of ABS resin covers these driving mechanisms for rotating the baffle 5. The case body 13 includes a case 13a and a main plate 13b. The frames 3 and 3 are attached to the side surface of the case body 13 with a plurality of screws 14 and the case 14 a
3b is firmly integrated. Both ends of the drive shaft 5 a of the baffle 5 are supported by side walls 3 a provided on both sides of the frame 3. Further, the pinion 7a, the first gear 8, the second gear 9, the cam body 10, the operation lever 11, and the gear 5b constitute transmission means. The operating range of the sector gear 11b is about 45 degrees.

The detailed configuration of the stepping motor 1 is shown in FIG.
It is as shown in. That is, the rotor 7 is urged to one side by the spring 15 to prevent vibration. The rotor 7 has a magnet 16 in addition to the pinion 7a, a bobbin 18 provided with a magnet wire 17 and a protruding pin 19 so as to face the magnet 16 and surround the rotor, and two cores 20 and 2. A stator composed of two stator cases 21 is provided.
A side plate 22 and a mounting plate 23 are provided so as to sandwich the stator cases 21 and 21. In addition, the board 25 is attached to the bracket 26, and the protruding pins 19 are connected to the printed circuit on the surface of the board 25. On the other hand, a lead wire 27 for supplying electric power from the outside to the stepping motor 1 is connected to the board 25. This lead 2
7 is taken out from the deepest part of the notch 50 (see FIG. 13) of the case 13a, that is, substantially at the center of the thickness Q of the drive unit 2.

The side plate 22 is placed on a circular support 30 projecting inward from the case 13a, and the mounting plate 23
Is fixed by the screws 29 mounted on the column 31, whereby the stepping motor 1 is attached to the case 13a. The fixed shaft 6 is connected to the fitting support 32 of the main plate 13b.
It is inserted in. Further, the dish-shaped spring 15 is
The rotor 7 is biased toward the case 13a by being sandwiched between the circular spring support portion 33b and the pinion 7a.

Each frame 3 is made of ABS resin, and in this embodiment, has a rectangular column shape with a small thickness. An opening 4 is formed inside the frame 3, and a drive shaft 5 a of the baffle 5 is housed in the frame 3. On both sides of the frame 3, there are formed side walls 3a, 3a for supporting the drive shaft 5a, and a gear 5b.
The portion supporting the drive shaft 5a on the side is a notch-shaped engagement hole 3b. On the other hand, the other end of the drive shaft 5a is fitted into a fitting hole 3c provided in the side wall 3a, and is rotatably supported.

On the other hand, the opening 4 is formed by an opening forming portion 4a projecting in parallel with the frame 3 surrounding the opening 4b. The portion of the opening forming portion 4a facing the opening 4b is formed by a projecting portion 4c that contacts the baffle 5.
, Forming a contact surface. The opening 4
Is formed integrally with the frame 3, but may be formed as a separate member. In this embodiment, the length of the protrusion 4c is made different as shown in FIG.
Are made to abut in an oblique position.

The baffle 5 is formed from polycarbonate. On the opening 4 side of the baffle 5, a soft tape 28 serving as a cushioning member is fixed and forms a part of the baffle 5. A rib may be provided on the back side of the baffle 5 in order to maintain the strength of the baffle 5. The baffle 5 is rotatable about the drive shaft 5a, and opens and closes in the direction indicated by the arrow in FIG. In addition, as the soft tape 28, the protrusion 4
Although the foamed polyurethane is used so that the amount of sink when contacted with c is large, other elastic members, for example, a foamed polyethylene or a rubber member may be used.

The drive shaft 5a of the baffle 5 is provided with a radial projection 5c in addition to the gear 5b.
As shown in FIG. 9, the gear 5 is inserted into the fitting hole 34 of the case 13a.
When "b" penetrates, it comes into contact with the case 13a and is positioned. The drive shaft 5a is rotatably supported by a bearing 35 surrounding the fitting hole 34. On the other hand, the base plate 13b is also provided with a fitting hole 36 so that the other gear 5b can penetrate. And
Similarly, the drive shaft 5 a is provided with a bearing 37 surrounding the fitting hole 36.
It is rotatably supported by.

The first gear 8 is made of resin made of polyacetal. Further, one end is fixed to the mounting plate 23 and the other end is rotatably supported by a shaft fixed to the base plate 13b. The second gear 9 is also made of polyacetal, and is rotatably supported by a support shaft 38 formed integrally with the case 13a. The tip of the support shaft 38 is
3b is fitted to the cylindrical support 39.

The cam body 10 is made of polyacetal resin and is formed in a disk shape. Then, as shown in FIG. 10, the support pillar 4 fixed to the case 13a and the base plate 13b.
The leading ends 40a, 40a of the 0, 40 are rotatably supported by fitting into the concave portions at the center of the cam body 10.
The cam grooves 10a and 10b provided on both surfaces thereof correspond to FIG.
As shown in the figure, each is formed in an arc shape, but the shapes are different. That is, the cam body 1
As 0 rotates, the baffles 5 and 5 move from the closed / closed position to the closed / open position, then to the open / open position, and finally to the open / close position.

The relationship between the rotation angle of the cam body 10 (hereinafter referred to as the groove cam angle) and the open and closed positions of the baffles 5 and 5 will be described in detail with reference to FIG. Here, the cam form A of the cam groove 10a with which one baffle 5 (hereinafter referred to as baffle A) is engaged is indicated by an arrow A in FIG. The cam form B of the cam groove 10b with which the other baffle 5 (hereinafter referred to as baffle B) is engaged is indicated by an arrow B in FIG. The cam groove 10a is provided from minus several degrees to 275 degrees in terms of the groove cam angle. The cam form A has a groove cam angle of 0 to 100.
Degree is the same low height, gradually increases from 100 degrees to 160 degrees, and has the same height from 160 degrees to 275 degrees. Here, the 0-degree position is an initial position described later, and the cam baffle A is in the closed position from 0 to 100 degrees, and the movement range between the closed and open positions of the baffle A is from 100 to 160 degrees. , 160 to 275 degrees is the open position of the baffle A.

Similarly, the cam groove 10b is also moved from minus several degrees to 2 degrees.
It is provided up to 75 degrees. The cam form B has the same low height from 0 to 20 degrees,
From 80 degrees to 80 degrees, it gradually increases, and from 80 degrees to 18
The height is the same high up to 0 degrees, gradually lowers from 180 degrees to 240 degrees, and the same low height again from 240 degrees to 275 degrees. Here, the 0-degree position is an initial position described later, and the baffle B is in the closed position from 0 to 20 degrees, and the baffle B is from 20 to 80 degrees.
In the range of movement between the closed and open positions of
Degree is the open position of baffle B, from 180 degrees to 24 degrees
Up to 0 degree is the movement range between the open position and the closed position of baffle B,
The closed position of the baffle B is from 240 degrees to 275 degrees.

The initial position is a so-called initialization position, where each sector gear portion 11b abuts against the case body 13 and is in a mechanically locked state. This position is a position used for defining the origin when the positions of the baffles 5 and 5 are unknown at the time of initial assembly, a power failure, or the like.

Both the baffles A and B have a groove cam angle of 10
It is driven so as to stop at four places of degrees, 90 degrees, 170 degrees, and 250 degrees. In addition, you may make it provide a stop position freely besides these four places. That is, by controlling the number of pulses of the stepping motor 1,
The stop positions of the baffles 5 and 5 may be freely set.

The position where the groove cam angle is 0 degrees is the initial position (see FIG. 15). The position at 10 degrees is a closed position where both the baffles A and B are closed (see FIG. 16). At the 90-degree position, the baffle A is in the closed position and the baffle B is in the open position in the closed position (see FIG. 17). The 170-degree position is the open position where both the baffles A and B are open (see FIG. 18). At the position of 250 degrees, the baffle A is the open position and the baffle B is the closed position where the baffle B is the closed position (see FIG. 19).

The operating lever 11 is made of resin made of polyacetal, and includes a lever portion 11a, a sector gear portion 11b, a pin 11c, and a rotating fulcrum 12 provided on a case 13a.
The through-hole 11d through which is provided a rotation support portion 11e. Then, a sleeve 41 is fitted between the rotation support portions 11e, 11e, and the two operation levers 11, 11
Is held.

The rotation fulcrum 12 is provided integrally with the case 13a, and is fitted to the cylindrical projection 42 of the base plate 13b.
The case 13a constituting the case body 13 is
2, has a fitting hole 34 and a support shaft 38, and is formed in a bottomed cylindrical shape as shown in FIGS. Then, as shown in FIG. 6 and FIG.
The tips of the four corners on the side facing are formed as cylindrical portions 43.
At the center of each cylindrical portion 43, a screw hole 43a with which the screw 14 is engaged is provided. Also, the case 13a
Is provided with a cylindrical base 44 for supporting one end of the fixed shaft 6 and a column 46 substantially at the lower center in FIG. The support 46 is fixed to the main plate 1 by screws 45.
It has a screw hole 46a for integration with 3b.
On the other hand, the base plate 13b is formed in a flat plate shape, and has the above-described insertion hole 36. Further, through holes 51 into which the cylindrical portion 43 of the case 13a is fitted and engaged are provided at four corners.

The circuit configuration of the stepping motor 1 is as shown in FIG. That is, it is composed of two windings 47, eight transistors 48, and eight diodes 49, and each element is symmetrically arranged so as to be bipolar-driven. The stepping motor 1 has a step angle of 7.5 degrees, a power supply voltage of 12 V DC, an operating frequency of 400 pps, a torque during rotation of about 30 g.cm, and a detent torque of about 4 g.
g.cm. The rotation of the stepping motor 1 is reduced to 1/120 by the gear train and transmitted to the cam body 10. On the other hand, the sector gear portion 11b of the lever 11 engaged with the cam body 10 and the gear 5b of the drive shaft 5a
The speed is increased five times. Although the detent torque of the stepping motor 1 is small, the detent torque is reduced by the cam groove 10 as described later.
This is because a and 10b have a structure that mechanically locks the movement of each of the operation levers 11 and 11, so that even if the detent torque is small, the baffles A and B can sufficiently hold the closed position and the open position.

The assembling of the double damper device configured as described above is performed as follows. First, the drive unit 2 is assembled. In this assembly, the stepping motor 1 and the cam body 10 are inserted into the case 13a and the base plate 13b, and the screws 45 are used.
To integrate. Next, one end of the drive shaft 5a of the baffle 5 is made to penetrate into the fitting hole 3c of the side wall 3a of one of the frames 3 (outside when completed). At this time, the side where the gear 5b is located is inserted into the notch-shaped engagement hole 3b from its open end. Then, the portion of the gear 5 b is inserted into the fitting hole 34. Similarly, the gear 5b of the other frame 3 and the baffle 5 integrated into the fitting hole 36 is inserted. Thereafter, the frames 3 and 3 are fixed to the drive unit 2 with the screw 14 with the drive unit 2 at the center. In this way,
The double damper device is assembled. In addition, the fitting hole 3
After inserting the gear 5b into each of the frames 4, 36, the frame 3,
3 may be positioned with respect to the baffles 5 and 5.

This double damper device is, for example, shown in FIG.
As shown in FIG. Here, the same members as those shown in FIG. 24 are denoted by the same reference numerals, and description thereof will be omitted. This refrigerator 60
A mid-freezer refrigerator with a freezer 81 in the center
Are provided, and a refrigerator compartment 82 is provided at an upper portion, and a vegetable compartment 83 is provided at a lower portion. A duct 61 for blowing cool air to the refrigerator compartment 82 is formed.
The double damper device is fitted in a portion communicating with the freezing room 81 and the refrigerating room 82. That is, the frame 3 of the double damper device is fitted so as to form a part of the duct 61, and the double damper device itself also serves as the duct 61. In addition, as shown in FIG.
You may make it attach to the part which leads to 2. Further, the double damper device may be provided at the entrance of the duct 81, in other words, at the exit of the room of the evaporator 84.

Next, the operation of the double damper device will be described. After assembling into the refrigerator 60, initialization is performed, and then the baffles A and B are held at the closed / closed position (see FIG. 16), that is, at a position at a groove cam angle of 10 degrees. At this time, as shown in FIG. 14, from the initial position (groove cam angle 0 °) to the groove cam angle 20 ° including the closing position, both cam forms A and B keep maintaining the same height, ie, The radius of each of the cam grooves 10a and 10b keeps the same state.
For this reason, the position from the initial position to be initialized to 20 degrees is the same position for the baffles 5 and 5 as the initialized state, but the lock state that occurs at the conventional initialized position does not occur. That is, the same complete abutment as at the time of initialization can be obtained when the groove cam angle is 10 degrees, but the noise which has conventionally occurred at the time of initialization does not occur in this double damper device. Further, since the radius of the cam groove 10a is the same from 0 to 100 degrees and the radius of the cam groove 10b is the same from 0 to 20 degrees, both the baffles A and B are mechanically maintained at the closed position. It will be.

A CPU or the like that controls the temperature in the refrigerator 60 by operating the refrigerator 60 issues a command to the double damper device to introduce cold air into the room where the baffle B is involved. Then, the rotor 7 of the stepping motor 1 is driven, and the rotation is performed by the pinion 7a, the first gear 8, the second gear 9, the cam body 10, the operating levers 11, 11, the gears 5a, 5
b, transmitted to the baffles 5, 5 via the drive shafts 5a, 5a. As a result, the baffle 5 driven by the cam groove 10b
Moves from the opening 4 to an open position that is parallel to the frame 3.

That is, when the number of steps of the stepping motor 1 becomes a predetermined number from the position of the groove cam angle of 10 degrees, that is, 1,280 in this embodiment, the cam body rotates 80 degrees and the groove cam angle becomes 90 degrees. And the baffle B rotates 45 degrees and comes to the open position. On the other hand, the baffle A maintains the closed position. In this closed / open position, the operating lever 11 on the cam groove 10a side is locked in the closed position, as shown in FIG. 17A, and the operating lever 11 on the cam groove 10b side is also locked in FIG.
As shown in (B), it is locked in the open position. In addition to this mechanical lock, the baffles 5 and 5 are driven by the current holding force or detent torque of the stepping motor 1 so that
The closed position state and the open position state are maintained.

When the CPU or the like in the refrigerator 60 issues a command to introduce cold air into the room in which the baffles A and B are involved from the state where the baffles A and B are in the closed position, the cam body 10 is driven by the stepping motor 1. 10 to 170 in groove cam angle
Rotate to a degree. Then, the operation lever 11 on the cam groove 10a side moves from FIG. 16A to FIG.
8 (A), and the baffle A is in the open position. On the other hand, the operation lever 11 on the cam groove 10b side is shown in FIG.
18B through FIG. 17B, and the baffle B is also in the open position. Also at this time, the two operation levers 11 and 11 are in the locked state, and mechanically maintain the open position.

When the CPU or the like in the refrigerator 60 issues a command to introduce cold air into the room in which the baffle A is involved from the state in which the baffles A and B are in the closed position, the cam body 10 is driven by the stepping motor 1 to cause the groove to move. The cam rotates from 10 degrees to 250 degrees. Then, while the baffle A is in the open position,
After the baffle B temporarily reaches the open position, it comes to the closed position and stops. The baffle A is in the open position and the baffle B is in the closed position. Also at this time, the operation lever 11,
11 is locked by the cam grooves 10a and 10b, and the open position and the closed position are held, respectively.

At this time, the drive of the stepping motor 1 is stopped after the soft tape 28 fixed to the baffle B has moved to some extent even after coming into contact with the projection 4c of the opening 4. That is, the baffle B is moved to the projecting portion 4c.
At about 235 degrees in the groove cam angle, but after contact, the cam body 10 moves about 5 degrees, the baffle B further rotates, and the protruding portion 4c is As shown in FIG. Thereafter, the stepping motor 1 further continues to rotate, and the cam body 10 also rotates, but the same height portion of the cam form B is moved to the pin 11c.
Moves, so that the biting state does not change. For this reason, a complete contact position as shown in FIG. 2 can be reliably held. Then, the stepping motor 1 stops at the position of 250 degrees.

This operation is the same when the cam body 10 rotates in the reverse direction from the time when the baffle B is at the open position and returns to the closed position at a groove cam angle of 10 degrees. That is, the soft tape 28 comes into contact with the protruding portion 4c at about 25 degrees, and then the cam body 10 further moves about 5 degrees, and the bite state shown in FIG. 2 is obtained. Then, the stepping motor 1 stops at the position of the groove cam angle of 10 degrees. On the other hand, the baffle A performs the same operation. That is, when returning from the open position to the closed position, the projecting portion 4c and the soft tape 28 come into contact with each other at a position where the groove cam angle is about 105 degrees. Then, at a position where the position is further returned by about 5 degrees (about 100 degrees), the state shown in FIG. 2 is obtained. After that,
Even if the cam body 10 rotates further in the reverse direction, the state of FIG. 2 is maintained. Then, at the position of 90 degrees, which is the closed / open position, the stepping motor 1 stops. When returning to the closed position, the stepping motor 1 is stopped at 10 degrees.

As described above, the baffles A and B have the protrusions 4c.
After that, the stepping motor 1 is driven to rotate the cam body 10 to rotate the baffles A and B. For this reason, the torque of the stepping motor 1 is applied to the baffles A and B, and the soft tape 28 having elasticity is pressed, so that the protruding portion 4c bites into the soft tape 28 and makes firm contact with the soft tape 28 without any gap. In this contact, if the protrusion amount of the protrusion 4c of the opening 4 and the shape of the baffles A and B vary, or if there is a backlash in the sector gear 11b or the like, the contact is completely performed. However, in this double damper device, the stepping motor 1 is driven and the baffles A and B are rotated even after the soft tape 28 comes into contact with the protruding portion 4c.
Since the projection 4c is digged into the inside, even if there is such a variation or backlash, it can be brought into contact with no gap.

Here, the movement between the four positions, such as the transition of the baffles A and B from the open / close position to the closed / open position and the transition from the open / close position to another position, is performed by detecting the number of steps and the rotation direction and controlling the movement. By doing so, it can be done freely.

When the pins 11c move to both ends of the cam grooves 10a and 10b, the baffles A and B hit the protruding portion 4c, and the cam body 10 is set to a groove cam angle of 10 degrees or 250 degrees.
After that, power supply to the stepping motor 1 may be continued without interrupting power supply.
In this case, the operation lever 11 comes into contact with the case body 13 and the like, so that the stepping motor 1 is made unrotatable so as to be out of step. In this case, the out-of-step condition is changed to the refrigerator 60.
The microcomputer in the inside can detect and confirm the origin. That is, the closed position and the open position are the origins of the movement of the baffle 4. In this embodiment, normally, initialization is not performed, and the origin is confirmed by the above-mentioned step-out state at a groove cam angle of 0 degrees as initialization at the time of assembling or startup after a power failure. .

When the power supply to the stepping motor 1 is cut off with the protruding portion 4c biting into the soft tape 28, the elastic repulsive force of the soft tape 28 is transmitted through the drive shaft 5a to the gear. 5b and the sector gear 11b. However, the cam grooves 10a and 10b are
c is firmly locked, and the cam body 10 does not rotate. Therefore, backlash in the gear 5b and the sector gear 11b is eliminated. Even if the cam body 10 moves, the stepping motor 1 has the detent torque as described above, and the rotor 7 does not rotate. For this reason, when the cam body 10 moves, the backlash of the first gear 8, the second gear 9, and the like is also eliminated, and
There is no backlash in the transmission mechanism from the rotor 7 of the stepping motor 1 to the baffles A and B, which is preferable. The backlash of the gear 5b and the like in this embodiment is about 0.05 mm in distance, which is extremely small. However, eliminating this backlash is advantageous in preventing backlash.

Here, the movement time of the baffles A and B from the open position to the closed position and the movement time in the opposite direction are controlled by the pulse generation rate. In this example, since the speed is set to 400 pps, the cam body 10 rotates at a groove cam angle of 80 degrees in about 3 seconds. However, other pulse rates can be used as appropriate. Further, the baffles A and B can be stopped at an intermediate position between the open position and the closed position instead of the fully opened position. That is, in FIG. 14, in addition to the positions of 10, 90, 170, and 250 degrees, the positions of 50, 130, and 210 degrees can be set. In addition, although the movement angle from the open position to the closed position is set to about 45 degrees in this embodiment,
Other angles may be employed as appropriate.

In this embodiment, since the opening 4 is formed perpendicular to the frame 3, the thickness of the frame 3 can be reduced. For this reason, the entire device including the frame 3 is reduced in size, and the double damper device can be easily attached to another device, for example, a refrigerator. Further, since the open positions of the baffles 5 and 5 are substantially parallel to the frames 3 and 3, the cool air flowing along the frames 3 and 3 when the baffles 5 and 5 are open is in the open state. There is almost no obstruction by the parts 4 and 4 and it flows straight. For this reason, the transmission loss of the cold air is eliminated, and the refrigerator has high efficiency of the cold air transmission and the cold air diffusion. Further, since the movement of the operation lever 11 is transmitted to the gear 5b at an increased speed, the slight movement of the cam grooves 10a, 10b can be transmitted to the gear 5b, and the operation angle of the baffles 5, 5 can be increased. In addition, since the operation lever 11 abuts against the case body 13 or the like to cope with an operation failure such as runaway of the stepping motor 1, a double damper device with stable operation can be provided. In addition, since the stepping motor 1 is used as a driving source, forward and reverse rotation is possible, and the baffles 5 and 5 can be accurately controlled.

The above embodiment is an example of a preferred embodiment of the present invention, but the present invention is not limited to this, and various modifications can be made without departing from the spirit of the present invention. is there. For example, instead of one stepping motor 1 as a driving source, two baffles 5 may be driven as two. Also, instead of a stepping motor, another motor such as a synchronous motor,
Other driving sources may be used. However, when a DC motor or the like is used, the position is detected using a position detecting means of the baffles 5 and 5, for example, a magnet is fixed to the cam body 10 and a Hall element for detecting the position of the magnet is used. It may be necessary to control the operation time of the motor and the like.

In the above-described embodiment, the soft tape 28 is used. However, if the tightness is not strictly required, the soft tape 28 may be omitted. In both cases where the soft tape 28 is attached and not attached, the openings 4, 4 and the baffle 5,
The stepping motor 1 may be immediately stopped in a state where the stepping motor 5 is in contact.

Further, in the above-described embodiment, the reduction gear train is used, but the reduction gear train is not necessarily required. As a driving method of the stepping motor 1, other driving methods such as a bipolar driving and a unipolar driving can be appropriately adopted, and various specifications such as a step angle and a torque can be various values according to the usage form. Can be adopted. Also, the pin 11 of the operation lever 11
c may be a two-pronged shape, while the regulating guide on the cam body 10 side may be a projection, and the projection may enter a cross-section of the bifurcated pin 11c to regulate the position of the operation lever 11.

Although the frames 3 and 3 are duct-shaped dampers in the above-described embodiment, the present invention can be applied to dampers having other configurations. Further, the present invention can be applied to various damper devices for controlling other fluids, such as a ventilation duct, instead of a refrigerator. Further, the frames 3 and 3 are attached to a frame on a side to which the damper device is attached, for example, a duct 61 for blowing cool air of a refrigerator 60 shown in FIG.
May be used. Opening 4
When three or more are installed side by side, this double damper device can be used for a part of them.

[0061]

As described above, in the double damper device of the present invention, the drive section is provided between the two openings, and the rotation centers of the two opening / closing plates are provided on both sides of the drive section opposite to each other. Therefore, the dead space on both sides of the drive unit can be reduced. Moreover, by arranging the driving unit, 2
Since the distance between the two openings can be increased, the heat insulating effect is enhanced and severe temperature control can be performed. In addition, since the drive section is located between the openings, the operation can be easily transmitted to the respective open / close plates, and the distance between the openings can be set more freely than in the past. For this reason, the mechanism of the drive unit can be simplified, design can be made easily in accordance with the heat insulating effect, and air path design becomes easy. Further, since the frame is fitted into the duct so as to form a part of the duct, the duct portion does not become thick, and the equipment in which this device is incorporated does not increase in size.

According to the second aspect of the present invention, by forming the projecting portion, rigidity is generated in the opening forming portion, the opening forming portion can be made thinner, and the device can be reduced in size and weight. Further, the formation of the protruding portion makes it possible to enhance the adhesion to the opening / closing plate.

Further, according to the third aspect of the present invention, since the cylindrical opening forming portion is provided in the frame, the fluid smoothly passes through the opening forming portion.

In addition, according to the fourth aspect of the present invention, one motor, one common reduction gear train, and one cam body are provided as drive sources, so that the drive unit can be downsized. At the same time, the number of parts can be reduced and the price can be reduced.

[Brief description of the drawings]

FIG. 1 is a front view of a double damper device according to an embodiment of the present invention.

FIG. 2 is a sectional view taken along line II-II of FIG.

FIG. 3 is a side view as viewed from a direction indicated by an arrow III in FIG. 1;

FIG. 4 is a view of the left side of the plan view seen from the direction of arrow IV in FIG. 3;

FIG. 5 is a plan view of the plan view of FIG. 4 excluding an upper frame of a right portion.

FIG. 6 is a partially cutaway rear view as viewed from the direction indicated by an arrow VI in FIG. 3;

FIG. 7 is a view showing a state in which a ground plate is removed from a driving unit of the double damper device of FIG. 1;

FIG. 8 is a cross-sectional view of a stepping motor portion of a drive unit of the double damper device of FIG.

9 is a sectional view of a drive shaft and a second gear portion of a drive unit of the double damper device of FIG.

FIG. 10 is a partial cross-sectional view of a cam body and an operation lever of a drive unit of the double damper device of FIG. 1;

11 is a side view as seen from the direction of arrow XI in FIG. 10;

FIG. 12 is a side view as seen from the direction of arrow XII in FIG. 10;

FIG. 13 is a bottom view as seen from the direction of arrow XIII in FIG. 10;

FIG. 14 is a view showing a cam foam provided on a cam body in a drive section of the double damper device of FIG. 1;

15A and 15B are diagrams showing a relationship between the cam body and the operation lever when the cam body of the double damper device of FIG. 1 has a groove cam angle of 0 °, wherein FIG. 15A shows the baffle A side, and FIG. It is a figure showing the baffle B side.

16A and 16B are diagrams showing the relationship between the cam body and the operation lever when the cam body of the double damper device of FIG. 1 has a groove cam angle of 10 degrees, wherein FIG. 16A shows the baffle A side, and FIG. It is a figure showing the baffle B side.

17A and 17B are diagrams showing a relationship between the cam body and the operation lever when the cam body of the double damper device of FIG. 1 has a groove cam angle of 90 degrees, wherein FIG. 17A shows the baffle A side, and FIG. It is a figure showing the baffle B side.

18A and 18B are diagrams showing a relationship between the cam body and the operation lever when the cam body of the double damper device of FIG. 1 has a groove cam angle of 170 degrees, where FIG. 18A shows the baffle A side, and FIG. It is a figure showing the baffle B side.

19A and 19B are diagrams showing the relationship between the cam body and the operation lever when the cam body of the double damper device of FIG. 1 has a groove cam angle of 250 degrees, wherein FIG. 19A shows the baffle A side, and FIG. It is a figure showing the baffle B side.

20 is a drive circuit diagram of the double damper device of FIG.

FIG. 21 is a view for explaining a state in which the double bumper device of FIG. 1 is incorporated in a refrigerator.

FIG. 22 is a rear view of a conventional motor type damper device.

FIG. 23 is a partial cross-sectional side view of a conventional motor type damper device.

FIG. 24 is a view for explaining a state in which a conventional motor type damper device or double damper device is incorporated in a refrigerator.

FIG. 25 is a front view of a conventional double damper device.

[Explanation of symbols]

 Reference Signs List 1 stepping motor (drive source) 2 drive unit 3 frame 3a side wall 4 opening 4c protrusion 5 baffle (opening / closing plate) 5a drive shaft 5b gear 7 rotor 7a pinion 8 first gear 9 second gear 10 cam body 10a, 10b cam Groove (Regulation guide) 11 Operating lever 11a Lever 11b Sector gear 11c Pin 28 Soft tape

Claims (4)

[Claims] 1. An independent rotation of each
In a double damper device having a frame having two opening and closing plates for opening and closing two openings, a driving unit for driving the two opening and closing plates is provided between the two openings and provided in a case body. The center of rotation of each of the two opening / closing plates is provided on opposing side surfaces of the case body in which the driving unit is housed, and the frame is formed in a duct so as to form a part of a duct serving as a fluid passage. Wherein the opening / closing plate is housed inside the frame, and the frame is integrated with the case body. 2. The double according to claim 1, wherein an opening forming portion formed so as to surround the periphery of the opening of the opening is provided with a projecting portion projecting toward the opening / closing plate. Damper device. 3. The double damper device according to claim 2, wherein said opening forming portion is provided inside said frame, and said opening forming portion is formed in a cylindrical shape. 4. The rotation by independently rotating each other
In a double damper device having a frame having two open / close plates for opening and closing two openings, a drive unit for driving the two open / close plates is provided between the two openings, and the two open / close plates are provided. Are provided on opposite sides of the drive unit, the drive unit includes one motor serving as a drive source, and one reduction gear train that meshes with a fixed shaft serving as an output shaft of the motor. One cam body which is driven by the common reduction gear train and drives the respective drive shafts provided on the two opening / closing plates, and has a regulating guide portion on both sides, is further fitted into the regulating guide portion. An operation lever having a pin that follows the movement of the leverage guide portion and having an engagement portion that engages with the drive shaft;
A double damper device comprising: