KR100221449B1 - Damper device - Google Patents

Abstract

The task is to reduce the dead space and increase the distance between the two openings. As a solution, the double damper device has two opening and closing plates 5 and 5 for opening and closing the two openings 4 and 4. ) Is added. And the drive part 2 which drives two open / close boards 5 and 5 between two opening parts 4 and 4 is provided. At this time, the drive shafts are formed on the two opening and closing plates 5 and 5, respectively, and the side walls 3a and 3a supporting the drive shafts are provided in the frames 3 and 3 where the openings 4 and 4 are formed, respectively. The drive part 2 may be provided between two adjacent side wall 3a, 3a among the side wall 3a.

Description

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

2 is a II-II cross-sectional view of FIG.

3 is a side view seen from the direction III of the arrow of FIG.

4 is a view of the left part of the plan view seen in the direction IV in the arrow of FIG.

5 is a plan view of the right side of the top view of FIG. 4 without the upper frame.

FIG. 6 is a back view of the rear view seen from the direction VI of the arrow of FIG. 3; FIG.

7 is a view of a state in which the fingerboard is removed from the drive unit of the double damper device of 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 cross-sectional view of the drive shaft and the second gear part of the drive unit of the double damper device of FIG.

10 is a partial cross-sectional view of the cam body and the operating lever portion of the drive unit of the double damper device of FIG.

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

12 is a side view as seen from the XII direction at the arrow of FIG.

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

FIG. 14 is a view showing a camform provided in a cam body in a driving part of the double damper device of FIG.

Fig. 15 is a diagram showing the relationship between the cam body and the operation lever when the cam body of the double damper device of Fig. 1 is 0 degrees from the home cam angle, in which a shows the baffle A side and b shows the baffle B side.

FIG. 16 is a diagram showing the relationship between the cam body and the operation lever when the cam body of the double damper device of FIG. 1 is 10 degrees from the home cam angle, a showing the baffle A side, and b showing the baffle B side.

FIG. 17 is a diagram showing the relationship between the cam body and the operation lever when the cam body of the double damper device of FIG. 1 is 90 degrees from the home cam angle, a showing the baffle A side, and b showing the baffle B side.

18 is a diagram showing the relationship between the cam body and the operating lever when the cam body of the double damping device of FIG. 1 is 170 degrees from the home cam angle, in which a shows the baffle A side and b shows the baffle B side.

FIG. 19 is a diagram showing the relationship between the cam body and the operating lever when the cam body of the double damper device of FIG. 1 is 250 degrees from the home cam angle, in which a shows the baffle A side and b is the baffle B side.

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

FIG. 21 is a view for explaining the state incorporated into the refrigerator of the double damper device of FIG. 1. A is a sectional view showing the front baffle and the cold air flow path, and B is a sectional view showing the inside baffle and the cold air flow path. .

Fig. 22 is a diagram showing a first modification of the double damper device of the present invention, in which a shows a cam body portion and b is a front view of the whole apparatus.

Fig. 23 is a view showing a second modification of the double damper device of the present invention, in which a shows a cam body portion and b is a front view of the whole apparatus.

24 is a partial cross-sectional side view of a conventional motor damper device.

25 is a view for explaining a state in which a conventional motor damper or double damper device is incorporated into the refrigerator.

26 is a front view of a conventional double damper device.

[Name of invention]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a damper device for operating an opening and closing plate such as a baffle with respect to an opening by using a motor or the like as a drive source, and more particularly, to a damper device suitable for controlling cold air from entering a refrigerator.

Conventionally, as a motor damper device for a refrigerator, the device disclosed in US Pat. No. 5,398,910 (Japanese Patent Laid-Open No. 6-109354) is known. This is shown in FIG.

The motor damper device 70 of such a structure is used for the refrigerator 80 of the shape as shown in FIG. 25, for example. The refrigerator 80 is divided into a freezer compartment 81 and a refrigerating compartment 82, and an evaporator 84 is provided at the bottom of the freezer compartment 81. In the rear part of the evacuator 84, the cold air obtained by having the fan motor 85 disposed is blown and circulated to the freezing chamber 81 and the refrigerating chamber 82.

A partition plate 86 is provided between the evacuator 84 and the refrigerating chamber 82 to prevent cold air from the evacuator 84 from flowing directly into the refrigerating chamber 82. On the other hand, a cold air flow passage 87 is formed between the rear portion of the partition plate 86 and the rear inner wall of the refrigerator 80, and the motor-type damper device 70 in the cold air flow passage 87 is disposed.

The motor damper device 70 has a structure in which a baffle 72 and a drive mechanism 73 such as a synchronous motor are disposed between the rotation point shafts 71. The drive mechanism 73 outputs the rotational torque of the air motor as a force in the thrust direction by the rack & pinion mechanism, and the baffle 72 is driven about the rotation point axis 71 by the force in the thrust direction. Is rotated.

Temperature control in the refrigerator is achieved by completely blocking cold air when the baffle 72 is in a closed position, and introducing cold air into each room such as a refrigerator compartment when the baffle 72 is opened.

However, in such a motor damper device 70, the torque in the rotational direction is changed to the torque in the thrust direction. Therefore, in consideration of the precision of each component, it is necessary to provide a backlash in the coupling between the members in the baffle 72 or the driver section 73. On the other hand, in order to ensure temperature control, it is necessary to completely block the cold air at the position where the baffle 72 is closed.

Thus, in the motor damper device 70, the sealing member of the baffle 72 and the frame 74 is increased to completely close the opening 76 with the baffle 72, so that the spring coil is pressed in the direction in which the baffle 72 is closed. (Not shown), the soft tape 75 is attached to the contact surface between the baffle 72 and the frame 74 so as to lower the frame 74.

However, the crimp in the plate spring is so strong that it is preferable to completely block the cold air, but since the crimp force of the spring varies greatly depending on the opening and closing position of the baffle 72, it is preferable for the safe operation of the drive mechanism 73 such as a synchronous motor. Can not.

In addition, since the motor damper device 70 uses a rack & pinion mechanism, the operation of opening the baffle 72 does not open to a position parallel to the flow of cold air, but only to an inclined position as shown in FIG. The structure does not open. For this reason, the baffle 72 interrupts the flow of cold air and is not preferable for the rapid diffusion of cold air. In addition, the angle at which such a baffle 72 opens is likely to be smaller in relation to the bending performance of the plate spring.

In addition, by using the rack & pinion mechanism, the pole (N) of the drive mechanism portion 73 is required for a certain time or more, and the portion is causing a large dead space.

In recent years, refrigerators have been divided into several rooms such as a refrigerator compartment, a freezer compartment, a vegetable compartment, and a chilled compartment to control the temperature of each room, and a large number of refrigerators of the type which controls the temperature in each part of the large room separately. In such a refrigerator, a dedicated cold air flow passage 87 is formed in each chamber or each portion to individually control the amount of cold air flowing into each room. For this reason, the double damper device 77 which uses many apparatuses, such as the motor damper apparatus 70 shown in FIG. 24, or has two opening parts corresponding to each cold air flow path as shown in FIG. I use it.

In the double damper device 77, two openings 76a and 76b are formed in the frame 74, and drive mechanisms 73 such as a motor are disposed below the rear surface. Each of the openings is provided with two baffles 72a and 72b which are the same as the above-described motor damper device 70, and these baffles 72a and 72b are introduced into the respective cold air flow passages 87 and 87. Is in control. In addition, the baffles 72a and 72b are driven by one synchronous motor (not shown) in the drive mechanism 73, and both are open, both are closed, one is open, the other is closed, and the other is closed. The side is open and is configured to take four modes: one side closes.

In the double damper device 77, the baffle 72a, 72b disposed above the drive mechanism 73 is moved by obtaining an output from the single synchronous motor in the drive mechanism 73 through the rack & pinion. For this reason, there arises a problem that the drive mechanism 73 containing a rack & pinion becomes large. In particular, since the racks collide with each other at the base of each central portion of the baffles 72a and 72b, the distance R between the racks is increased, thereby increasing the drive mechanism 73.

On the other hand, considering the miniaturization of the drive mechanism 73, the distance P between the openings 76a and 76b is small. If the distance P of both openings 76a and 76b becomes small, the heat insulation between each cold air flow path 87 following two opening 76a and 76b will become inadequate, and the influence of the temperature of one cold air flow path 87 will be inadequate. This cold air flow path 87 is shown on the other side. For this reason, exact temperature control with respect to each room becomes difficult.

Also known is a damper device that uses a direct current motor, a stepping motor, or the like as a drive source, rather than a synchronous motor. Such motors often control the opening and closing of the baffle by energizing time or number of pulses without using a position sensor for low price. In this case, the baffle may not operate for a moment due to the wandering time of the stepping motor or the like and the freezing of the baffle. This prevents the baffle from closing securely, resulting in cold leakage.

It is to provide a damper device that has addressed the problems of the prior art as described above. That is, an object of the present invention is to provide a damper device for a refrigerator having a high efficiency by reducing a space by having a plurality of baffles corresponding to a refrigerator for individually controlling the temperature of a plurality of rooms or parts individually.

An embodiment of the double damper device of the present invention will be described based on FIG. 1 to FIG. In addition, the double damper device of the present embodiment is used in a refrigerator and is a motor damper device driven by a motor.

The double damper device comprises a drive unit 2 having a stepping motor 1 disposed at its center, two cylindrical frames 3 and 3 having open ends at both sides of the drive unit 2 and the frame ( It consists of two opening parts 4 and 4 which are formed inside 3 and 3, respectively, and the baffles 5 and 5 which open and close the openings 4 and 4, respectively. In addition, the stepping motor 1 is a driving source, and the baffles 5 and 5 are opening and closing plates, respectively.

The stepping motor 1 in the drive unit 2 has a fixed shaft 6 as shown in Figs. 7 and 8, in which the rotor 7 having a pinion 7a rotates. It is possible to fit. In addition, the pinion 7a meshes with the cogwheel portion 8a of the first cogwheel 8, and the pinion 8b of the first cogwheel 8 is the cogwheel of the second cogwheel 9. The parts 9a are meshed with each other. The pinion portion 9b of the second gear 9 is engaged with the cam gear 10c of the cam body 10. In this way, the gear wheel heat is decelerated in the rotation of the stepping motor 1 and transmitted to the cam body 10.

On both sides of the cam body 10, as shown in FIG. 10, U-shaped cam grooves 10a and 10b serving as regulation guides are provided. In addition, the operation levers 11 and 11 are coupled to the cam grooves 10a and 10b. The operating lever 11 is a lever 11a which protrudes to one side about the pivot point 12 and a fan-shaped gear 11b which is engaged with the lever 11a by 90 degrees. ) And a projection pin 11c provided at the tip of the lever portion 11a. The pin 11c is inserted into the cam grooves 10a and 10b and moves in the cam grooves 10a and 10b while the position thereof is regulated and guided.

The fan-shaped gear part 11b is coupled to the drive shaft 5a formed in the baffle 5, and transmits the rotation of the operation lever 11 to the baffle 5. This engagement is performed by engaging the gear 5b provided in the drive shaft 5a with the fan-shaped gear part 11b. In addition, since the distance from the rotation point 12 to the tip of the fan-shaped gear part 11b is shorter than the distance from the rotation point 12 to the pin 11c, the movement of the fan-shaped gear part 11b is performed. It is reduced compared with the movement of the lever part 11a. For this reason, similarly to the principle of lever, even if the force which moves the operation lever 11 is small, the force which moves the gear 5b becomes large. On the other hand, the diameter of the fan gear 11b is increased by the diameter of the gear 5b provided on the drive shaft 5a and the number of teeth increases, so that the rotational transmission from the fan gear 11b to the gear 5b increases. It's becoming Yoonyeol.

The case body 13 covers these drive mechanisms for rotating the baffle 5. This case body 13 is comprised from the case 13a and the fingerboard 13b. The frames 3 and 3 are attached to the side of the case body 13 with a plurality of screws 14. Both ends of the drive shaft 5a of the baffle 5 are supported by side walls 3a and 3b provided on both sides of the frame 3. The pinion 7a, the first cogwheel 8, the second cogwheel 9, the cam body 10, the operating lever 11 and the gear 5b constitute a transmission means. In addition, the operating range of the fan gear 11b is about 45 degrees.

The detailed configuration of the stepping motor 1 is as shown in FIG. That is, the rotor 7 is urged inward by the spring 15, and vibration is prevented. The rotor 7 also has a magnet 16 in addition to the pinion 7a and a bobbin 18 provided with a magnet wire 17 and a protruding pin 19 so as to surround the rotor against the magnet 16. The stator which consists of the core 20 and the two stator cases 21 is provided. The side plate 22 and the mounting plate 23 are provided to sandwich the stator cases 21 and 21 therebetween. In addition, the board | substrate 25 is attached to the bracket 26, and the protrusion pin 19 is connected with the printed circuit of the surface of the board | substrate 25. As shown in FIG. On the other hand, a lead wire 27 for supplying electric power to the stepping motor 1 is connected to the substrate 25. This lead wire 27 is taken out at the deepest part of the ablation 50 (see FIG. 13) of the case 13a, that is, about the center position of the thickness Q of the drive unit 2.

In addition, the side plate 22 is mounted on the circular support portion 30 protruding inwardly of the case 13a, and the mounting plate 23 is fixed with the screw 29 mounted on the support pillar 31 to thereby stepping motors. (1) is attached to the case 13a. And the fixed shaft 6 is fitted in the fitting support part 32 of the fingerboard 13b. In addition, a plate-shaped spring 15 is sandwiched between the circular spring support 33 of the fingerboard 13b and the pinion 7a, and the rotor 7 is urged toward the case 13a.

Each frame 3 has a thin rectangular pillar shape in this embodiment. The opening 4 is formed inside the frame 3, and the drive shaft 5a is accommodated in the frame 3 at the same time as the baffle 5. Side portions 3a and 3a for supporting the drive shaft 5a are formed on both sides of the frame 3, and a portion for supporting the drive shaft 5a on the side of the gear 5b is an ablation coupling hole 3b. . On the other hand, the drive shaft 5a and the other end side are rotatably supported in the insertion hole 3c provided in the side wall 3a.

On the other hand, the opening part 4 is formed by the opening formation part 4a which protruded in parallel with the frame 3 surrounding the periphery of the opening 4b. And this opening formation part 4a has the protrusion part 4c which contacts the baffle 5, and forms the contact surface. In addition, although the opening part 4 is formed integrally with the frame 3, it is good also as another member. Moreover, in this embodiment, the protrusion length of the protrusion part 4c is made to contact in the inclined position state so that it may differ in the figure as shown in FIG.

A soft tape 28 made of a cushioning member is fixed to the opening 4 side of the baffle 5 to form a part of the baffle 5. In addition, a rib may be provided on the back side of the baffle 5 to maintain the strength of the baffle 5. Further, the baffle 5 is rotatable with the drive shaft 5a as a point, and opens and closes in the direction of the arrow in FIG. The soft tape 28 is made of foamed polyurethane so that the amount of falling down when it comes in contact with the protruding portion 4c may be made of another elastic member such as foamed polyethylene or rubber.

As shown in FIG. 9, the driving shaft 5a of the baffle 5 is provided with a contacting protrusion 5c protruding in the radial direction in addition to the gear 5b, and the gear (3) in the fitting hole 34 of the case 13a. When it penetrates 5b), it hits or positions the case 13a. The drive shaft 5a is rotatably supported by the shaft bearing portion 35 surrounding the fitting hole 34. On the other hand, a hole 36 is also provided in the fingerboard 13b to allow the other gear 5b to penetrate. Similarly, the drive shaft 5a is rotatably supported by the shaft bearing portion 37 surrounding the fitting hole 36.

The first cog wheel 8 is made of resin as shown in FIG. The first cogwheel 8 is rotatably supported on an axis, one end of which is fixed to the mounting plate 23 and the other end of which is fixed to the fingerboard 13b. As shown in FIG. 9, the second cogwheel 9 is rotatably supported by the support shaft 38 formed integrally with the case 13a. Moreover, the tip of this support shaft 38 is fitted to the cylindrical support part 39 provided in the finger board 13b.

The cam body 10 is made of resin and is formed in a disc shape. As shown in FIG. 10, the support pillars 40 and 40 fixed to the case 13a and the fingerboard 13b are rotatably supported by being inserted into the recessed part of the center part of the cam body 10. As shown in FIG. The cam grooves 10a and 10b provided on both surfaces thereof are formed in an arc shape as shown in FIG. As the cam body 10 rotates, the baffles 5 and 5 move from the closed position to the closed position, then to the individual position, and finally to the open / close position.

The relationship between the rotation angle (referred to as the next home cam angle) of this cam body 10 and the opening position and closing position of the baffles 5 and 5 is demonstrated in detail based on FIG. Here, the camform A of the cam groove 10a to which the one baffle 5 (referred to as the next baffle A) is shown by the arrow A of FIG. The camform B of the cam groove 10b to which the other baffle 5 (called the next baffle B) is shown by the arrow B of FIG. The cam groove 10a is provided from minus a few degrees to 275 degrees in terms of the home cam angle. And Camform A has the same low height at home cam angles from 0 to 100 degrees and gradually rises from 100 to 160 degrees to the same high height from 160 to 275 degrees. Here, the position of 0 degrees is the initial position described later, and the cambaffle A position is closed from 0 degrees to 100 degrees, and the range of 100 degrees to 160 degrees is the moving range between the closing position of the baffle A and the open position. Is the open position of baffle A.

Similarly, the cam groove 10b is provided from minus several degrees to 275 degrees. And Campform B has the same low height from 0 degrees to 20 degrees, and gradually increases from 20 degrees to 80 degrees, becoming the same high height from 80 degrees to 180 degrees, and gradually lowers from 180 degrees to 240 degrees and 240 degrees to 275 degrees. Up to the same low height. Here, the position of 0 degrees is the initial position described later, and the position of baffle B is closed from 0 degrees to 20 degrees, and the range of movement between the position of closing and opening of baffle B from 20 degrees to 80 degrees, at 80 degrees Baffle B is in the open position up to 180 degrees, and baffle B is in the closed position from 240 degrees to 275 degrees as a movement between the open and closed positions from 180 degrees to 240 degrees.

The initial position is the position of the so-called initial rise, and each of the fan-shaped cogwheel portions 11b collides with the case body 13 or becomes a mechanically locked state. This position is used to define the origin when the position of the baffles A and B is unclear at the time of initial assembly or power failure.

The baffles A and B are driven to stop at four places of 10 degrees, 90 degrees, 170 degrees and 250 degrees from the home cam angle. Alternatively, the stop positions may be freely provided in addition to these four locations. In other words, the stop positions of the baffles A and B may be freely set by controlling the number of pulses of the stepping motor 1.

The position where the home cam angle is 0 degrees becomes the initial position (see FIG. 15). The position of 10 degrees is the closed position of the position where both the baffles A and B are closed (refer FIG. 16). The 90 degree position is the position where baffle A is closed and the closing position of the position where baffle B is opened (see FIG. 17). The position of 170 degrees is an individual state of the position where both the baffles A and B open (see FIG. 18). The position of 250 degrees is the position where the baffle A opens and the opening and closing position of the position where the baffle B closes (see FIG. 19).

The operating lever 11 is made of resin, and rotates with the through hole 11d through which the pivot point 12 provided in the case 13a, in addition to the lever part 11a, the fan-shaped gear part 11b, and the pin 1c. The support part 1e is provided. The sleeve 41 is fitted between the rotation support portions 11e and 11e to maintain the positions of the two operation levers 11 and 11.

The pivot point 12 is integrally provided in the case 13a, and the cylindrical protrusion 42 of the finger board 13b fits inward. The case 13a constituting the case body 13 has a pivoting point 12, an insertion hole 34, and a support shaft 38, and at the same time a bottomed cylinder as shown in FIGS. It is formed into a shape. As shown in FIG. 6 and FIG. 7, the tip of the four corners of the side which faces the finger board 13b is the cylindrical part 43. As shown in FIG. In the center of each cylindrical portion 43, a screw hole 43a to which the screw 14 is coupled is provided. Moreover, the case 13a is provided with the cylindrical support part 44 which supports the one end of the fixed shaft 6, and the support column 46 located about the center lower part in FIG. This support column 46 has a screw hole 46a for integrating with the fingerboard 13b by the screw 45. On the other hand, the fingerboard 13b is formed in a flat plate shape and has the above-described insertion hole 36. In addition, a through hole 51 through which the cylindrical portion 43 of the case 13a is press-fitted is provided at four corners.

The circuit configuration of the stepping motor 1 is as shown in FIG. That is, it consists of two windings 47, eight transistors 48, and eight diodes 49, and each element is symmetrically arranged to be bipolar driven. Such rotation of the stepping motor 1 is transmitted to the deceleration door cam body 10 by one-120th by gear wheel heat. On the other hand, the relationship between the fan-shaped gear part 11b of the lever 11 couple | bonded with this cam body 10, and the gear 5b of the drive shaft 5a is 5 times speed-up. In addition, the detent torque of the stepping motor 1 is small, but this has a structure in which the cam grooves 10a and 10b described later lock the movement of each of the operating levers 11 and 11 mechanically. Even the smallest one can keep the position where the baffles A and B are closed or open.

This double damper device is incorporated in the mid-flush type refrigerator 60 shown in FIGS. 21A and 21B, for example. Here, the same members as those shown in FIG. 25 are denoted by the same reference numerals and description thereof is omitted. The refrigerator 60 is provided with a freezer compartment 81 at the center, a refrigerating compartment 82 at the top, and a vegetable compartment 83 at the bottom, and simultaneously blows cold air into the freezer compartment 81, the refrigerating compartment 82, and the vegetable compartment 83. A duct 61 is provided and a cold air passage 87 is formed. The double damper device is fitted in the duct 61 in the middle of the cold air flow passage 87. In addition, the cold air flow passage 87 on the side of the opening 4 of the double damper device, which communicates with the freezing chamber 81, the refrigerating chamber 82, and the vegetable chamber 83, passes through each room blocked by a partition wall made of a heat insulating material or the like. Branched to the independent cold air flow passage 87, each has a door to separately control the inflow of cold air into a predetermined room. The refrigerator 60 controls the inflow of cold air into the upper double damper device 60A and the freezer compartment 81 and the inflow of cold air into the vegetable chamber 83 that controls the inflow of cold air into the upper portion of the refrigerating chamber 82 and the inflow of cold air into the lower portion of the refrigerator compartment 82. Two of the lower double damper devices 60B are mounted. That is, the cold air flow passage 87 is formed at the front and the inside of the refrigerator 60 shown in FIGS. 21A and 21B to communicate with each part or room. The frame 3 of the double damper device 60A, 60B is fitted to form a part of the duct 61. In addition, the location of the double damper device 60A, 60B may be a position close to the exit of the evacuator 84 room or a position away from it in accordance with the design of the refrigerator.

The following describes the operation of this double damper device. In addition, after it is squeezed into the refrigerator 60, initialization is performed, and the baffles A and B are then kept at a closed position (see FIG. 16), that is, at a position of 10 degrees from the home cam angle. At this time, both camforms A and B continue to maintain the same height from the initial position shown in FIG. 14 (the home cam angle of 0 degrees) to the home cam angle of 20 degrees including the closed position. That is, the radii of the cam grooves 10a and 10b all keep the same state. For this reason, the initializing degree is 20 degrees from the initial position, and the position is the same position as the initializing state in baffles A and B. In addition, since the radius of the cam groove 10a is equal to 0 degrees to 100 degrees, and the radius of the cam groove 10b is equal to 0 degrees to 20 degrees, the baffles A and B are both mechanically maintained in the closed position.

By the operation of the refrigerator 60, a CPU or the like that controls the temperature in the refrigerator 60 commands the air intake into the chamber in which the baffle B is involved to the double damper device. Then, the lock 7 of the stepping motor 1 is driven, and the rotation thereof is the pinion 7a, the first cog wheel 8, the second cog wheel 9, the cam body 10, and the operating levers 11 and 11. ), The gears 5a and 5b and the drive shafts 5a and 5a are transferred to the baffles A and B. As a result, the baffle B driven by the cam groove 10b moves away from the opening 4 to the open position, which is a position parallel to the frame 3.

That is, when the number of steps of the stepping motor 1 becomes a predetermined number at this position of 10 degrees from the home cam angle, in this embodiment, the cam body rotates by 80 degrees, the home cam angle becomes 90 degrees, and the baffle B rotates by 45 degrees. . Baffle A, on the other hand, remains in the closed position. In this closed 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 shown in Fig. 17b. It is locked in the open position. In addition to this mechanical lock, the baffle A and B are kept in the closed position and the open position state by the energization holding force or detent torque of the stepping motor 1.

When the baffles A and B instruct the CPU in the refrigerator 60 to enter the cold air into the chambers in which both the baffles A and B are involved from the closed position, the cam body 10 is driven from the home cam angle by the driving of the stepping motor 1. Rotate from 10 degrees to 170 degrees. Then, the operating lever 11 on the cam groove 10a side is in the state of FIG. 18a via FIGS. 16a through 17a, and the baffle A is in the open position. On the other hand, the operating lever 11 on the cam groove 10b side is in the state of FIG. 18B via the FIGs. 16B to 17B, and the baffle B is also in the open position. At this time, both of the operation levers 11 and 11 are locked and maintain their open positions mechanically.

When the baffles A and B instruct the CPU in the refrigerator 60 to enter the air into the chamber in which the baffle A is involved from the closed position, the cam body 10 is driven from the angle of 10 degrees from the home cam angle by the driving of the stepping motor 1. Rotate to 250 degrees Then baffle A is in the open position while baffle B is in the open position and then closed. Then, the opening and closing positions of the position where the baffle A opens and the position where the baffle B closes. At this time, the operation levers 11 and 11 are locked to the cam grooves 1a and 10b, respectively, to maintain the open and closed positions.

At this time, the driving stop of the stepping motor 1 stops after moving to some extent even after the soft tape 28 stuck to the baffle B comes into contact with the protrusion 4c of the opening 4. That is, the contact of the baffle B with the protrusion 4c is about 235 degrees from the home cam angle, but even after the contact, the cam body 10 moves about 5 degrees, and the baffle B is also rotated so that the protrusion 4c is placed on the soft tape 28. As shown in FIG. 2, it becomes the shape which penetrates. Thereafter, the stepping motor 1 continues to rotate, and the cam body 10 also rotates, but the pin 11c moves in the same height portion of the camform B, so that the recessed state does not change. This makes it possible to reliably maintain the complete contact position as shown in FIG. The stepping motor 1 stops at the 250 degree position.

This operation is also the same when the cam body 10 rotates backward from the position where the baffle B is open and returns to the closed position of 10 degrees from the home cam angle. In other words, the soft tape 28 is in contact with the protruding portion 4c at a position of about 25 degrees, and then the cam body 10 moves about 5 degrees and is in a recessed state shown in FIG. Then, the stepping motor 1 stops at the home cam angle of 10 degrees. On the other hand, baffle A performs the same operation. That is, when returning from the open position to the closed position, the protrusion 4c and the soft tape 28 contact each other at about 105 degrees from the home cam angle. Moreover, it will be in the state shown in FIG. 2 in the place which returned about 5 degree | times (about 100 degree | times). After that, even if the cam body 10 further rotates in reverse, the state of FIG. 2 is maintained. Then, the stepping motor 1 stops at the 90 position which becomes the closing position. In addition, when returning to the closed position, the stepping motor 1 is stopped at 10 degrees.

In this manner, even after the baffles A and B come into contact with the protrusions 4c, the stepping motor 1 is driven and the cam body 10 is rotated to rotate the baffles A and B. For this reason, the torque of the stepping motor 1 is added to the baffles A and B, and the soft tape 8 which has elasticity is crimped | bonded, and the protrusion part 4c comes into tight contact with the gap without the gap. In addition, if there is an unbalance in the protrusion amount of the protrusion 4c of the opening part 4 or the shape of the baffles A and B or the backlash in the fan-shaped gear part 11b, the contact may not be completed completely. In the double damper device, even after the soft tape 28 is in contact with the protrusion 4c, the stepping motor 1 is driven to rotate the baffles A and B, and the protrusion 4c is penetrated into the soft tape 28. Even with the same imbalance or backlash, contact can be made seamlessly.

Here, the movement between the four positions, such as the transition from the open / close position of the baffles A and B to the closed position or the shift from the open / close position to another position, can be freely detected by detecting and controlling the number of steps and the rotation direction.

In addition, when the pins 11c are moved to both ends of the cam grooves 10a and 10b, the baffles A and B collide with the protrusions 4c or the cam body 10 becomes 10 degrees or 250 degrees from the home cam angle. The power supply may be continued without interrupting the power supply to the furnace. In this case, the operation lever 11 hits the case body 13 or the stepping motor 1 is incapable of rotation so that the operating lever 11 is in the state of being out of step. In this way, the microcomputer in the refrigerator 60 detects this state of disassembly and can confirm as origin. In other words, this closing position or opening position becomes the origin of the baffle 4 movement. In this embodiment, the origin check is performed by the above-mentioned step-out state at the place where the home cam angle is 0 degrees as the initialization at the time of incorporation without initializing or at start-up after power failure.

In addition, when the power supply to the stepping motor 1 is cut off while the protrusion 4c is penetrated by the soft tape 28, the elastic repulsive force of the soft tape 28 passes through the drive shaft 5a and the gear 5b or fan shape. It is conveyed to the shape gear part 11b etc. However, the cam grooves 10a and 10b lock the pin 11c firmly, so that the cam body 10 does not rotate. For this reason, backlash in the gear 5b and the fan gear 11b is eliminated. In addition, even if the cam body 10 moves temporarily, the stepping motor 1 has the detent torque as mentioned above, and the rotor 7 does not rotate. For this reason, when the cam body 10 moves, the backlash of the first cogwheel 8 and the second cogwheel 9 is also eliminated, and the backlash of the transmission mechanism from the rotor 7 to the baffles A and B of the stepping motor 1 is eliminated. It disappears and becomes a preferable thing. Further, in the embodiment, the backlash of the gear 5b is extremely small as a distance of about 0.05 mm, but it is advantageous in terms of preventing the backlash when this backlash is eliminated.

Here, the position where the baffles A and B are closed and the movement time in the opposite direction are controlled by the generation rate of the pulse. In this example, since it is set to 400pps, the cam body 10 rotates 80 degrees from the home cam angle in about 3 seconds. However, other pulse rates may be used as appropriate. It is also possible to stop the baffles A and B in the middle of opening and closing, not in the fully open position. That is, in addition to the positions of 10 degrees, 90 degrees, 170 degrees, and 250 degrees in FIG. 14, the positions of 50 degrees, 130 degrees, and 210 degrees can also be set. Moreover, although the moving angle from the open position to the closed position is about 45 degrees in this embodiment, other angles can also be appropriately employed.

In this embodiment, since the drive part 2 is provided between two opening parts 4 and 4, dead space can be reduced. In addition, since the distance between the two opening parts 4 and 4 can be lengthened by arrange | positioning the drive part 2, a heat insulation effect becomes high and it becomes possible to perform sibian temperature control. In addition, since the drive unit 2 is located between the openings 4 and 4, the operation transfer to each of the baffles 5 and 5 can be easily performed, and the distance setting between the openings 4 and 4 can be set freely. For this reason, the mechanism of the drive part 2 can be simplified, the design suitable for the heat insulation effect becomes easy, and the air path design becomes easy. Moreover, since the opening part 4 is formed perpendicular | vertical with respect to the frame 3, the thickness of the frame 3 can be made thin. For this reason, the whole apparatus including the frame 3 becomes small and it becomes easy to mount this double damper apparatus to another apparatus, for example, a refrigerator.

Also, in this embodiment, since the position where the baffles 5 and 5 are opened is slightly parallel to the frames 3 and 3, the cold air flowing along the frames 3 and 3 when it is open is the baffles 5 and 5 ) And the openings 4 and 4 are almost never blocked and flow straight. As a result, the transfer loss of cold air is eliminated, resulting in a refrigerator having good effects of cold air diffusion and cold air diffusion. In addition, since the movement of the operating lever 11 is increased and transmitted to the gear 5b, the slight movement of the cam grooves 10a and 10b can be increased to be transmitted to the gear 5b and the baffles 5 and 5 are operated. The angle can be increased. In addition, by hitting the operation lever 11 against the case body 13 or the like, it is possible to cope with an operation failure such as congestion of the stepping motor 1, so that a double damper device with stable operation can be provided. In addition, since the stepping motor 1 is used as the driving source, forward and reverse rotation is possible, and the baffles 5 and 5 can be precisely controlled.

In addition, although embodiment mentioned above is an example of the suitable embodiment of this invention, it is not limited to this, A various deformation | transformation is possible in the range which does not deviate from the summary of this invention. For example, the damper device of one baffle may be used, in which the frame 3 and the baffle 5 are one each. In addition, not only one stepping motor 1 but also two may be used to drive each baffle 5 as a drive source. It is also possible to use a different motor such as a synchronous motor instead of a stepping motor or a different driving source. However, when a DC motor or the like is used, the position detection means of the baffles 5 and 5, for example, the position detection is performed by using a Hall element or the like which fixes the magnet to the cam body 10 and detects the position of the magnet or the DC motor or the like. There is also the possibility of needing to control the operating time of the.

In addition, although the soft tape 28 was used in embodiment mentioned above, when the sealing degree is not strictly required, the soft tape 28 may be abbreviate | omitted. In addition, in either the case where the soft tape 28 is mounted or not, the stepping motor 1 may be immediately stopped while the openings 4 and 4 and the baffles 5 and 5 are in contact with each other. . Although the number of slabs from the open position to the closed position, for example, 10 to 90 degrees is 1260 steps, the number of slabs from the open position to the closed position may be 1440 steps. . This makes it possible to more reliably close the opening 4 with the baffle 5 in the closed position where cold air leakage should not occur.

Moreover, although the deceleration lubrication heat is used in embodiment mentioned above, deceleration lubrication heat is not necessarily required. As the driving method of the stepping motor 1, other driving methods such as unipolar driving as well as bipolar driving can be appropriately adopted, and various methods such as step angle and torque can be adopted with various values according to the usage type. Can be. In addition, the pin 11c of the operating lever 11 is made into two upper right corners, and the restriction guide portion on the cam body 10 side is turned so that the projection is further formed by the two right upper pins 11c. The position may be entered to restrict the position of the operation lever 11.

Moreover, in the above-mentioned embodiment, although the frames 3 and 3 are a duct-shaped damper apparatus, it is applicable also to the damper apparatus of another structure. It is also applicable to various damper devices that control other fluids, such as ducts for ventilation, not in refrigerators. Further, the frames 3 and 3 may be configured using a frame on the side where the damper device is mounted, for example, a duct 61 for cold air blowing of the refrigerator 60 shown in FIG. Moreover, even when three or more opening parts 4 are provided together, this damper apparatus can be employ | adopted for the one part.

In the double damper device of the present invention described above, the angle of opening and closing of the opening and closing plate can be increased by utilizing the cam mechanism and the ring mechanism, and the driving portion can be miniaturized. In addition, since the opening and closing plate is driven through the cam mechanism and the ring mechanism, the positional maintenance of the opening and closing plate can be achieved mechanically, achieving a stable opening and closing operation, thereby making it possible to securely block the opening with the baffle. In addition, since the driving portion is provided between the two openings, the dead space can be reduced. In addition, by arranging the driving unit, the distance between the two openings can be increased, so that the thermal insulation effect is increased and the Sibian temperature control can be performed. In addition, the drive portion makes it easy to transfer the operation to the respective opening and closing plates in the opening portion, and at the same time, the distance setting of the opening portion is freer than in the prior art. This simplifies the mechanism of the drive unit, facilitates the design according to the insulation effect, and facilitates the design of the air path.

Damper device

Claims (5)

In a damper device comprising two openings through which fluid flows out and two opening and closing plates for opening and closing each of the two openings, a driving unit for driving the two opening and closing plates is provided between the two openings. Damper device, characterized in that for opening and closing the opening and closing plate to control the outflow of the fluid. 2. The drive shaft according to claim 1, wherein drive shafts are formed on the two opening and closing plates, respectively, and side walls supporting each of the drive shafts are provided in a frame in which the openings are formed, respectively, and the drive portion is formed between two adjacent side walls of the side walls. Damper device characterized in that provided. 2. The driving unit according to claim 1, wherein the driving unit is driven by the driving source and the driving source and at the same time has a cam body having a regulation guide for causing the opening and closing operation of the opening and closing plate; A pin and an operating lever including an engaging portion coupled to the drive shaft of the opening and closing plate, wherein the operating lever moves the pin by the regulation guide part when the cam body is driven by the driving source, and at the same time the movement amount of the pin is moved. The drive shaft is driven by the coupling portion corresponding to the damper device, characterized in that for opening and closing the opening and closing operation. 2. The cam unit according to claim 1, wherein the driving unit includes one motor serving as a driving source, a deceleration lubrication heat engaged with the output shaft of the motor, and a cam groove each driven by the deceleration lubrication heat, and at the same time, a cam groove formed of a restriction guide part. A damper device, characterized in that it has two operating lever coupled to the cam groove to transfer the operation to the drive shaft formed in the opening and closing plate. The damper device of claim 1, wherein the driving shaft formed on the opening and closing plate is driven directly by a driving source.

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