CN111457056A - Cold air damper - Google Patents
Cold air damper Download PDFInfo
- Publication number
- CN111457056A CN111457056A CN201910089782.3A CN201910089782A CN111457056A CN 111457056 A CN111457056 A CN 111457056A CN 201910089782 A CN201910089782 A CN 201910089782A CN 111457056 A CN111457056 A CN 111457056A
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- China
- Prior art keywords
- gear
- shaft
- cold air
- rotation
- air damper
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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- 230000000903 blocking effect Effects 0.000 claims abstract description 51
- 230000002093 peripheral effect Effects 0.000 claims description 22
- 230000002159 abnormal effect Effects 0.000 abstract description 17
- 239000004519 grease Substances 0.000 abstract description 9
- 230000004048 modification Effects 0.000 description 12
- 238000012986 modification Methods 0.000 description 12
- 230000005540 biological transmission Effects 0.000 description 10
- 230000000694 effects Effects 0.000 description 4
- 230000002401 inhibitory effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 2
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
- F16H1/206—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members characterised by the driving or driven member being composed of two or more gear wheels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/028—Gearboxes; Mounting gearing therein characterised by means for reducing vibration or noise
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Chemical & Material Sciences (AREA)
- Thermal Sciences (AREA)
- Combustion & Propulsion (AREA)
- Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
- Gear Transmission (AREA)
- Air-Flow Control Members (AREA)
- Gears, Cams (AREA)
- General Details Of Gearings (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Abstract
A cold air damper capable of preventing or suppressing abnormal sound generated in a gear mechanism without using grease. A cold air damper (1) is provided with: a first shutter (7) for opening and closing a first opening (5) provided in the first frame (3); a first output shaft (17) connected to the first baffle plate (7); a motor (21); a motor pinion (24) fixed to the rotating shaft of the motor (21); and a gear mechanism (25) that transmits the rotation of the motor pinion (24) to the first output shaft (17). The cold air damper (1) further comprises a rotation blocking mechanism (26), and the rotation blocking mechanism (26) biases a first gear (27) of the plurality of gears constituting the gear mechanism (25) to block the rotation of the first gear (27). When the motor (21) is driven, the first gear (27) rotates against the biasing force (F) of the rotation blocking mechanism (26).
Description
Technical Field
The present invention relates to a cold air damper that opens and closes an opening that forms a part of a cold air passage of a refrigerator by a shutter.
Background
Patent document 1 describes a cold air damper that opens and closes an opening portion constituting a part of a cold air passage of a refrigerator by a damper. The cold air damper of this document includes: a shutter for opening and closing the opening; an output shaft connected to the baffle; a motor; and a gear mechanism that transmits rotation of the motor to the output shaft. The gear mechanism has a plurality of gears.
In the gear mechanism, when rotation is transmitted, collision noise in which the teeth of one gear collide with the teeth of the other gear may be continuously generated at the meshing portion of the two gears.
In order to suppress the generation of such abnormal sound, a scheme of coating grease at the meshing portion of the two gears is considered. But the cold air damper is provided in an environment where temperature variation inside the refrigerator is large. That is, the cold air damper is provided in an environment where the temperature changes from-40 ° to 40 °, for example. Therefore, in the case where grease is applied to the meshing portions of the two gears, if a low-temperature environment is created, the viscosity of the grease increases, and a large load is applied to the rotation of the gears. On the other hand, when the environment is a high temperature environment, the viscosity of the grease decreases, and therefore the grease flows out from the meshing portion of the two gears. Once the grease flows out, the generation of abnormal noise cannot be suppressed.
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open No. 2018-25286
Disclosure of Invention
In view of the above-described problems, it is an object of the present invention to provide a cold air damper that can prevent or suppress abnormal sound generated in a gear mechanism regardless of a change in temperature environment.
In order to solve the above technical problems, the cold air damper of the present invention comprises; a shutter for opening and closing an opening provided in the frame; an output shaft connected to the baffle; a motor; a motor pinion fixed to a rotating shaft of the motor; a gear mechanism that transmits rotation of the motor pinion to the output shaft; and a rotation blocking mechanism that blocks rotation of at least one target gear among the plurality of gears constituting the gear mechanism by biasing the target gear, wherein when the motor is driven, the target gear rotates against biasing of the rotation blocking mechanism.
According to the present invention, the target gear, which is one of the gears constituting the gear mechanism, transmits the rotation of the motor, but the rotation of the target gear is inhibited by the urging force of the rotation inhibiting mechanism. Therefore, the target gear is not moved in a state where the gear mechanism does not transmit the rotation of the motor. This prevents the teeth of the target gear from repeatedly colliding with the teeth of the other gear multiple times when the target gear meshes with the other gear during transmission of rotation. That is, when the rotation of the target gear is not inhibited by the rotation inhibiting mechanism, if the teeth of the target gear come into contact with the teeth of the other gear when the target gear meshes with the other gear, the target gear rotates in one direction around its own rotation center line in reaction to the contact, and the teeth of the target gear collide with the teeth of the other gear. Further, when a collision occurs, the subject gear rotates in the other direction around its own rotation center line in reaction to the collision, so that the teeth of the subject gear collide with the other teeth of the other gear. Subsequently, the subject gear repeats the above-described collision until the engagement of the subject gear with the other gears becomes reliable. On the other hand, if the target gear is not moved by the biasing force of the rotation blocking mechanism, even if the teeth of the target gear come into contact with the teeth of the other gear when the target gear is meshed with the other gear, the target gear is prevented or suppressed from rotating around its rotation center axis due to the reaction of the contact. This prevents or suppresses the repeated occurrence of collision between the teeth of the subject gear and the teeth of the other gear, and thus prevents or suppresses the generation of abnormal sound from the gear mechanism. Further, since no grease is used, generation of abnormal sound from the gear mechanism can be prevented or suppressed regardless of a change in the temperature environment.
In the present invention, the gear mechanism may be a reduction gear mechanism, and the target gear may be a gear that rotates first among the plurality of gears constituting the gear mechanism. The first rotating gear is liable to generate abnormal sound when meshing with other gears. Therefore, if the gear is set as the target gear to inhibit the rotation, the effect of suppressing the generation of the abnormal sound is excellent.
In the present invention, the gear mechanism may include a first gear and a second gear, the first gear may be engaged with the motor pinion, the second gear may be engaged with the first gear, the first gear may include a large diameter gear portion engaged with the motor pinion, and a small diameter gear portion engaged with the second gear, an outer diameter of the small diameter gear portion may be smaller than an outer diameter of the large diameter gear portion, and the target gear may be the first gear. Thus, the effect of suppressing the generation of abnormal sounds is excellent.
The following modes can be adopted in the invention, namely: a support shaft that rotatably supports the target gear; and a contact portion that contacts the counter gear from one side in an axial direction of the support shaft, wherein the rotation blocking mechanism includes a biasing member that is disposed on the other side in the axial direction of the counter gear and biases the counter gear toward the contact portion. In this way, the target gear is pressed against the contact portion by the urging force of the urging member, and therefore, the rotation of the target gear can be inhibited.
In the present invention, a support shaft may be provided, the support shaft rotatably supporting the target gear, the target gear may include a gear portion including a gear portion, a shaft portion coaxial with the gear portion, and a shaft hole through which the gear portion and the shaft portion are inserted, the support shaft may penetrate the shaft hole, and the rotation blocking mechanism may include a biasing member that biases the shaft portion toward the support shaft. In this way, the target gear is pressed against the support shaft by the urging force of the urging member, and therefore, the rotation of the target gear can be inhibited.
In the present invention, an embodiment may be adopted in which the rotation preventing mechanism includes a support shaft that rotatably supports the target gear, the target gear includes a gear portion including a gear portion, a shaft portion coaxial with the gear portion, and a shaft hole that penetrates the gear portion and the shaft portion, the support shaft penetrates the shaft hole, and the rotation preventing mechanism includes a cylindrical portion that surrounds the shaft portion from an outer peripheral side, and an urging member that is compressed between the shaft portion and the cylindrical portion in a direction intersecting an axial direction of the support shaft and urges the shaft portion. In this way, the rotation of the target gear can be inhibited by the biasing force of the biasing member.
In the present invention, an embodiment may be adopted in which the target gear includes a gear portion including a tooth portion and a shaft portion coaxial with the gear portion, and a bearing rotatably supporting the shaft portion and including a contact portion contacting the target gear from one side in an axial direction of the shaft portion, the rotation blocking mechanism includes an urging member disposed on an opposite side of the bearing in the axial direction and urging the target gear toward the contact portion. In this way, the target gear is pressed against the contact portion of the bearing by the urging force of the urging member, and therefore, the rotation of the target gear can be inhibited.
In the present invention, an embodiment may be adopted in which the target gear includes a gear portion, a main body portion, and a shaft portion, the gear portion includes a toothed portion, the main body portion is coaxial with the gear portion, the shaft portion is coaxial with the gear portion, the bearing rotatably supports the shaft portion and includes a contact portion that contacts an outer peripheral surface of the shaft portion, and the rotation blocking mechanism includes a biasing member that biases the main body portion from a direction intersecting an axial direction of the shaft portion toward the contact portion. In this way, the target gear is pressed against the contact portion of the bearing by the urging force of the urging member, and therefore, the rotation of the target gear can be inhibited.
In the present invention, an embodiment may be adopted in which the rotation blocking mechanism includes a cylindrical portion that surrounds the shaft portion from an outer peripheral side, and an urging member that is compressed between the shaft portion and the cylindrical portion in a direction intersecting an axial direction of the shaft portion and urges the shaft portion, the bearing supporting the target gear rotatably about a predetermined axis, the target gear including a gear portion and a shaft portion, the gear portion including a toothed portion, the shaft portion being coaxial with the gear portion, the bearing supporting the shaft portion rotatably, and the rotation blocking mechanism including a bearing that compresses the target gear between the shaft portion and the cylindrical portion in a direction intersecting the axial direction of the shaft portion. In this way, the rotation of the target gear can be inhibited by the biasing force of the biasing member.
In the present invention, it is possible to adopt a mode in which the motor is a stepping motor. In the case of using a stepping motor as a motor, abnormal sound is easily generated at the meshing portion of the two gears, as compared with the case of using a servo motor as a motor. In contrast, in the present invention, even when the motor is a stepping motor, the generation of abnormal sound can be prevented or suppressed.
According to the present invention, the rotation of the target gear, which is one of the gears constituting the gear mechanism, is inhibited by the urging force of the rotation inhibiting mechanism. Therefore, the target gear is not moved in a state where the gear mechanism does not transmit the rotation of the motor. Thus, when the target gear meshes with another gear during rotation transmission, the teeth of the target gear can be prevented from repeatedly colliding with the teeth of the other gear.
Drawings
Fig. 1 is a perspective view of the cold air damper as viewed from the side where the baffle is disposed.
Fig. 2 is an exploded perspective view of the cold air damper.
Fig. 3 is a plan view of the driving device with the cover removed, as viewed from the + X direction.
Fig. 4 is an exploded perspective view of the drive device with the cover removed, as viewed from the + X direction.
Fig. 5 is an exploded perspective view of the drive device with the casing removed, as viewed from the-X direction.
Fig. 6 is a perspective view of the motor, the driving force transmission mechanism, the first output shaft, and the second output shaft.
Fig. 7 is an exploded perspective view of the fourth gear, the first output gear, the second output gear, the first output shaft, and the second output shaft when viewed from the + X direction.
Fig. 8 is an exploded perspective view of the fourth gear, the first output gear, the second output gear, the first output shaft, and the second output shaft as viewed from the-X direction.
Fig. 9 is a sectional view of the vicinity of the first gear and the first spindle.
Fig. 10 is an explanatory diagram of the operation of the cold air damper.
Fig. 11 is an explanatory view of the rotation blocking mechanism according to modification 1 or 2.
Fig. 12 is an explanatory view of a rotation blocking mechanism according to modification 3.
Fig. 13 is an explanatory view of a rotation blocking mechanism according to modification 4.
Fig. 14 is an explanatory view of a rotation blocking mechanism according to modification 5.
(symbol description)
1 cold air damper, 2 drive device, 3 first frame, 4 second frame, 5 first opening, 6 second opening, 7 first baffle, 8 second baffle, 11 housing, 12 box, 13 cover, 15 end plate portion, 16 square tube portion, 17 first output shaft, 18 second output shaft, 21 motor, 22 driving force transmission mechanism, 24 motor pinion, 25 gear mechanism, 26A-26E rotation blocking mechanism, 27 first gear, 27a large diameter gear portion, 27b gear portion, 28 second gear, 28a large diameter gear portion, 28b small diameter gear portion, 29 third gear, 29a large diameter gear portion, 29b small diameter gear portion, 30 fourth gear, 31 first output gear, 32 second output gear, 35 first shaft, 36 motor housing, 37 end plate, 38 second shaft, 39 third shaft, 40 support column, 41 first gear member, 41a large diameter gear portion, 41b small diameter gear portion, 41c, 41d, 41E gear portion, 42 contact portion, 42 second shaft portion, 54 b contact force applying portion, 50 b force applying portion, 52 b applying portion, 52 b, 70 b contact force applying portion, 70 b, 70 b, 70.
Detailed Description
Hereinafter, a cold air damper to which the present invention is applied will be described with reference to the accompanying drawings.
(Overall Structure)
Fig. 1 is a perspective view of a cold air damper to which the present invention is applied, as viewed from a side where a baffle is disposed, fig. 2 is an exploded perspective view of the cold air damper, and as shown in fig. 1 and 2, the cold air damper 1 of the present example includes a drive device 2, and a first frame 3 and a second frame 4, wherein the first frame 3 and the second frame 4 are disposed on both sides of the drive device 2, the first frame 3 includes a rectangular first opening 5, the second frame 4 includes a rectangular second opening 6, the cold air damper 1 further includes a first baffle 7 and a second baffle 8, wherein the first baffle 7 opens and closes the first opening 5, the second baffle 8 opens and closes the second opening 6, the first baffle 7 abuts the first frame 3 from a direction orthogonal to an arrangement direction of the first frame 3, the drive device 2, and the second frame 4 to close the first opening, the second baffle 8 abuts the second frame 4 from the orthogonal direction to the arrangement direction of the first frame 3, the drive device 2, and the second baffle 7 is arranged to extend around a second rotation axis 352, and the second baffle 638 is arranged to rotate around a second rotation axis L, which is arranged around a second rotation axis L, which is arranged around the drive device 352.
In the following description, directions orthogonal to each other are defined as an X direction, a Y direction, and a Z direction, the X direction is an arrangement direction, and the Y direction is an orthogonal direction, and in the X direction, a side where the first frame 3 is located is defined as a + X direction, and a side where the second frame 4 is located is defined as a-X direction, and in the Y direction, a side where the first shutter 7 is located is defined as a + Y direction and an opposite side thereof is defined as a-Y direction with respect to the first frame 3, and in addition, one side in the Z direction is defined as a + Z direction, and the other side in the Z direction is defined as a-Z direction, and the first rotation axis L1 of the first shutter 7 is located at an end portion in the-Z direction of the first shutter 7, and the second rotation axis L2 of the second shutter 8 is located at an end portion in the-Z direction of the second shutter 8.
In fig. 1, the first shutter 7 is disposed at an open position where the first opening portion 5 is released. The second shutter 8 is disposed at a closed position where the second opening 6 is closed. The first shutter 7 rotates between an open position shown in fig. 1 and a closed position standing along the first frame 3. The second shutter 8 rotates between the closed position shown in fig. 1 and the open position lying down in the + Y direction. Here, the cold air damper 1 can arrange both the first damper 7 and the second damper 8 at the open position by the driving of the driving device 2. Further, the cold air damper 1 can dispose both the first damper 7 and the second damper 8 at the closed position by the driving of the driving device 2. Further, the cold air damper 1 can be driven by the driving device 2 to place one of the first flap 7 and the second flap 8 in the closed position and place the other in the open position.
As shown in fig. 1, the drive device 2 includes a rectangular parallelepiped housing 11, as shown in fig. 2, the housing 11 includes a rectangular case 12 having an opening portion directed in the + X direction in the case 12, and a lid 13 closing the opening portion of the case 12, the case 12 includes a rectangular end plate portion 15 extending perpendicular to the X direction, and a square tube portion 16 extending in the + X direction from an outer peripheral edge of the end plate portion 15, the lid 13 is plate-shaped and provided integrally with the first frame 3 at an end portion in the-X direction of the first frame 3, the lid 13 covers the square tube portion 16 in the + X direction from the + X direction, the first output shaft 17 protrudes in the + X direction from the lid 13, the first baffle 7 is coupled to the first output shaft 17, an axis of the first output shaft 17 coincides with a first rotation axis L1 of the first baffle 7, the second output shaft 18 protrudes in the-X direction from the end plate 15, the second baffle 8 is coupled to the second output shaft L2 of the second output shaft 18.
As shown in fig. 2, a motor 21 and a driving force transmission mechanism 22 are housed in the case 11, and the driving force transmission mechanism 22 transmits rotation of the motor 21 to the first output shaft 17 and the second output shaft 18. The motor 21 is a stepping motor. The motor 21 rotates in the forward direction or the reverse direction. A servomotor can also be used as the motor 21.
(Driving force transmitting mechanism)
Fig. 3 is a plan view of the drive device 2 with the cover 13 removed, as viewed from the + X direction. Fig. 4 is an exploded perspective view of the drive device 2 with the cover 13 removed, as viewed from the + X direction. Fig. 5 is an exploded perspective view of the drive device 2 with the casing 12 removed, as viewed from the-X direction. Fig. 6 is a perspective view of the motor 21, the driving force transmission mechanism 22, the first output shaft 17, and the second output shaft 18. Fig. 7 is an exploded perspective view of the fourth gear, the first output gear, the second output gear, the first output shaft 17, and the second output shaft 18 when viewed from the + X direction. Fig. 8 is an exploded perspective view of the fourth gear, the first output gear, the second output gear, the first output shaft 17, and the second output shaft 18 when viewed from the-X direction. Fig. 9 is a sectional view of the vicinity of the first gear and the first spindle.
The driving force transmission mechanism 22 includes: a motor pinion 24, the motor pinion 24 being fixed to a rotating shaft of the motor 21; and a gear mechanism 25, the gear mechanism 25 transmitting rotation of the motor pinion 24 to the first output shaft 17 and the second output shaft 18. The gear mechanism 25 is a reduction gear mechanism that reduces the rotation of the motor 21, that is, the rotation of the motor pinion 24, and transmits the reduced rotation. The driving force transmission mechanism 22 includes a rotation blocking mechanism 26, and the rotation blocking mechanism 26 blocks rotation of the target gear by using at least one of the plurality of gears constituting the gear mechanism 25 as the target gear and biasing the target gear.
The gear mechanism 25 includes a first gear 27, a second gear 28, a third gear 29, a fourth gear 30, a first output gear 31, and a second output gear 32. As shown in fig. 6, the first gear 27 has: a large diameter gear part 27a, the large diameter gear part 27a meshing with the motor pinion 24; and a small diameter gear portion 27b, the outer dimension of the small diameter gear portion 27b being smaller than the outer dimension of the large diameter gear portion 27 a. The large diameter gear portion 27a is coaxial with the small diameter gear portion 27 b. The first gear 27 is rotatably supported by a first support shaft 35 inserted into a shaft hole through which the large-diameter gear portion 27a and the small-diameter gear portion 27b are inserted. The end portion of the first support shaft 35 in the + X direction is supported by the cover 13, and the end portion in the-X direction is supported by an end plate 37 on the output side of the motor case 36. An end plate 37 (contact portion) on the output side of the motor case 36 contacts the first gear 27 supported by the first spindle 35 from the-X direction side. The end plate 37 of the motor case 36 is a contact portion that contacts the first gear 27 from the-X direction side.
As shown in fig. 5, the second gear 28 has: a large diameter gear portion 28a, the large diameter gear portion 28a meshing with the small diameter gear portion 27b of the first gear 27; and a small-diameter gear portion 28b, the outer dimension of the small-diameter gear portion 28b being smaller than the outer dimension of the large-diameter gear portion 28 a. The large diameter gear portion 28a is coaxial with the small diameter gear portion 28 b. The second gear 28 is rotatably supported by a second support shaft 38 inserted into a shaft hole through which the large-diameter gear portion 28a and the small-diameter gear portion 28b are inserted. The second support shaft 38 is supported at the end in the + X direction by the cover 13, and at the end in the-X direction by the end plate 15 of the case 12. The third gear 29 has: a large diameter gear portion 29a, the large diameter gear portion 29a meshing with the small diameter gear portion 28b of the second gear 28; and a small diameter gear part 29b, the outer dimension of the small diameter gear part 29b being smaller than the outer dimension of the large diameter gear part 29 a. The large diameter gear portion 29a is coaxial with the small diameter gear portion 29 b. The third gear 29 is rotatably supported by a third support shaft 39 inserted into a shaft hole through which the large-diameter gear portion 29a and the small-diameter gear portion 29b are inserted. The end portion of the third support shaft 39 in the + X direction is supported by the cover 13, and the end portion in the-X direction is supported by the end plate 15 of the case 12.
As shown in fig. 3 and 4, the fourth gear 30 is rotatably supported by a support column 40 projecting in the + X direction from the end plate portion 15 of the housing 12. As shown in fig. 6, the fourth gear 30 includes: the first gear member 41; and a second gear member 42, the second gear member 42 overlapping with the-X direction of the first gear member 41.
As shown in fig. 7, the first gear member 41 has: a large diameter gear portion 41a, the large diameter gear portion 41a meshing with the small diameter gear portion 29b of the third gear 29; and a small diameter gear portion 41b, the small diameter gear portion 41b having an outer diameter smaller than that of the large diameter gear portion 41 a. The large diameter gear portion 41a is coaxial with the small diameter gear portion 41 b. The small-diameter gear portion 41b has a tooth portion 41c in a part of the circumferential direction. A circular arc peripheral wall 41d is provided on the outer peripheral surface of the small-diameter gear portion 41b except for the gear 41 c. As shown in fig. 8, the first gear member 41 has a contact portion 41e on an end surface (end surface in the (-X direction)) on the opposite side to the side where the small-diameter gear portion 41b is formed.
As shown in fig. 7, the second gear member 42 includes: a base portion 42a having an end surface on which the first gear member 41 is placed; and a protruding portion 42b, the protruding portion 42b protruding in the + X direction from a part of the outer peripheral edge of the base portion 42a in the circumferential direction. Teeth 42c are provided on the outer peripheral surface of the protruding portion 42b and the outer peripheral surface of the base portion 42a, at a portion located in the-X direction of the protruding portion 42 b. Further, the second gear member 42 includes a contacted portion 42d, and the contacting portion 41e of the first gear member 41 can abut against the contacted portion 42d from the circumferential direction. The contacted portion 42d is a protrusion protruding from the base portion 42a in the + X direction, and is provided on the opposite side of the tooth portion 42c so as to sandwich the pillar 40 (the rotation center line of the fourth gear 30). The second gear member 42 is in contact with the contacted portion 42d through the contact portion 41e of the first gear member 41, and the contacted portion 42d is pressed in the rotation direction by the contact portion 41e, thereby rotating with the rotation of the first gear member 41.
Here, the plate spring 45 is disposed on the outer peripheral side of the second gear member 42. The plate spring 45 biases the outer peripheral surface portion of the base portion 42a on the side opposite to the tooth portion 42c toward the support post 40. The base portion 42a is biased by the leaf spring 45, so that the second gear member 42 is prevented from rotating together with the first gear member 41 except for a state in which the contact portion 41e of the first gear member 41 presses the contacted portion 42 d.
As shown in fig. 8, an arc groove 46 is provided on the end surface of the base portion of the second gear member 42 in the-X direction. As shown in fig. 4, a rotation restricting portion 47 protruding from the end plate portion 15 of the case 12 is inserted into the circular arc groove 46. Here, the arc groove 46 and the rotation restricting portion 47 restrict the rotation range of the second gear member 42. That is, the rotation range of the second gear member 42 ranges from the angular position at which the rotation restricting portion 47 abuts on one end wall in the circumferential direction of the arc groove 46 to the angular position at which the rotation restricting portion 47 abuts on the other end wall.
As shown in fig. 7 and 8, the first output gear 31 is a sector gear, the first output gear 31 can mesh with the tooth portion 41c of the first gear member 41 of the fourth gear 30, the first output shaft 17 is attached to the rotation center of the first output gear 31, the first output shaft 17 protrudes from the first output gear 31 in the + X direction, and here, the first output shaft 17 rotates integrally with the first output gear 31, and therefore, the rotation of the motor 21 is transmitted to the first output shaft 17 via the motor pinion 24 and the gear mechanism 25, and the first flapper 7 coupled to the first output shaft 17 rotates about the first rotation axis L1 by the driving of the motor 21.
The second output gear 32 is a sector gear, the second output gear 32 can mesh with the tooth portion 42c of the second gear member 42 of the fourth gear 30, the second output shaft 18 is attached to the rotation center of the second output gear 32, the second output shaft 18 protrudes from the second output gear 32 in the-X direction, and here, the second output shaft 18 and the second output gear 32 rotate integrally, and therefore, the rotation of the motor 21 is transmitted to the second output shaft 18 via the motor pinion 24 and the gear mechanism 25, and the second baffle plate 8 coupled to the second output shaft 18 rotates about the second rotation axis L2 by the driving of the motor 21.
Then, the rotation blocking mechanism 26 biases the first gear 27 as a target gear to block the rotation. As shown in fig. 3 and 6, the rotation blocking mechanism 26 includes an urging member 50, and the urging member 50 is disposed in the + X direction of the first gear 27 in the axial direction (X direction) of the first support shaft 35 supporting the first gear 27, and urges the first gear 27 toward the end plate 37 (contact portion) of the motor case 36.
The urging member 50 is a plate spring. The urging member 50 is made of metal. As shown in fig. 6, the urging member 50 includes: an annular portion 51, the annular portion 51 including a center hole through which the first spindle 35 passes; and a pair of arm portions 52, the pair of arm portions 52 protruding from the annular portion 51 to one side and the other side in the radial direction. The pair of arm portions 52 extend from the annular portion 51 to be inclined in the + X direction toward the outer peripheral side. As shown in fig. 9, the urging member 50 is disposed between the first gear 27 (large diameter gear portion 27a) and the lid 13 of the housing 11, elastically deforms, and presses the first gear 27 against the end plate 37 of the motor housing 36. Thus, the first gear 27 is not moved in a state where the gear mechanism 25 does not transmit the rotation of the motor 21. On the other hand, when the motor 21 is driven, the first gear 27 rotates against the biasing force F of the rotation blocking mechanism 26 (the biasing force of the biasing member 50 pressing the first gear 27 to the end plate 37).
(operation of Cold air damper)
Fig. 10 is an explanatory diagram of the operation of the cold air damper 1. The upper views of fig. 10(a) to (f) are plan views of the first gear member 41, the first output gear 31, and the first output shaft 17 of the fourth gear 30, respectively, as viewed from the + X direction. The lower views of fig. 10(a) to (f) are plan views of the second gear member 42, the second output gear 32, and the second output shaft 18 of the fourth gear 30, respectively, as viewed from the + X direction. In the lower drawings of fig. 10(a) to (f), a part of the second gear member 42 is shown in a perspective view in order to understand the structure of the rotation restricting portion 47.
Fig. 10(a) shows the closed-closed origin position where both the first shutter 7 and the second shutter 8 are in the closed position. At the close-close origin position, the tooth portion 41c of the small-diameter gear portion 41b of the first gear member 41 is located on the opposite side with respect to the first output gear 31 across the strut 40. In this state, the second gear member 42 is in a position where the tooth portion 42c is rotated 120 ° in the clockwise direction CW with respect to the tooth portion 41c of the small-diameter gear portion 41b of the first gear member 41. Here, the arrangement of the first output gear 31 at the closed-closed origin position is the arrangement in which the first shutter 7 is at the closed position. The configuration of the second output gear 32 at the closed-close origin position is a configuration in which the second shutter 8 is in the closed position.
When the motor 21 is driven from the close-close origin position and the first gear member 41 is rotated 120 ° in the clockwise direction CW, the close-close stop position shown in fig. 10(b) is reached. During the period from the close-close origin position to the close-close stop position, the tooth portion 41c of the small-diameter gear portion 41b of the first gear member 41 is not meshed with the first output gear 31. Further, during the period from the close-close origin position to the close-close stop position, the contact portion 41e of the first gear member 41 is not in contact with the contacted portion 42d of the second gear member 42, and the second gear member 42 does not rotate. Therefore, during the period from the close-close origin position to the close-close stop position, the first output gear 31 and the second output gear 32 do not rotate, and the first shutter 7 and the second shutter 8 are maintained at the closed position.
When the motor 21 is driven from the close-close stop position and the first gear member 41 is rotated 120 ° in the clockwise direction CW, the open-close stop position shown in fig. 10(c) is reached. During the period from the close-close stop position to the open-close stop position, the tooth portion 41c of the small-diameter gear portion 41b of the first gear member 41 meshes with the first output gear 31, so that the first output gear 31 rotates in the counterclockwise direction CCW. Thereby, the first shutter 7 moves from the closed position to the open position. On the other hand, during the period from the close-close stop position to the open-close stop position, the contact portion 41e of the first gear member 41 is not in contact with the contacted portion 42d of the second gear member 42. Therefore, the second gear member 42 does not rotate. Thereby, the second output shaft 18 does not rotate, and the second shutter 8 is maintained at the closed position.
When the motor 21 is further driven from the open-close stop position and the first gear member 41 is rotated by 120 ° in the clockwise direction CW, the open-open home position shown in fig. 10(d) is reached. During the period from the opening/closing stop position to the opening/opening origin position, the tooth portion 41c of the small-diameter gear portion 41b of the first gear member 41 is not meshed with the first output gear 31. Therefore, the first output shaft 17 does not rotate, and the first shutter 7 is maintained at the open position. On the other hand, the contact portion 41e of the first gear member 41 contacts the contacted portion 42d of the second gear member 42 during the period from the opening-closing stop position to the opening-opening origin position. Therefore, the second gear member 42 rotates together with the first gear member 41 and rotates in the clockwise direction CW. Thereby, the tooth portion 42c of the second gear member 42 meshes with the second output gear 32, and the second output gear 32 rotates in the counterclockwise direction CCW. Thereby, the second output shaft 18 rotates, and the second shutter 8 moves from the closed position to the open position. At the opening-opening origin position, both the first flap 7 and the second flap 8 are disposed at the opening position.
Next, when the motor 21 is driven in the reverse direction from the opening-opening origin position and the rotation is transmitted to the fourth gear 30 so that the first gear member 41 rotates 120 ° in the counterclockwise direction CCW, the opening-opening stop position shown in fig. 10(e) is reached. During the period from the opening-opening origin position to the opening-opening stop position, the tooth portion 41c of the small-diameter gear portion 41b of the first gear member 41 is not meshed with the first output gear 31. Therefore, the first output shaft 17 does not rotate, and the first shutter 7 is maintained at the open position. Further, the contact portion 41e of the first gear member 41 and the contacted portion 42d of the second gear member 42 do not contact during the period from the opening-opening origin position to the opening-closing stop position. Therefore, the second output shaft 18 does not rotate, and the second shutter 8 is maintained at the open position.
When the motor 21 is driven further in the reverse direction from the open-open stop position and the rotation is transmitted to the fourth gear 30 to rotate the first gear member 41 by 120 ° in the counterclockwise direction CCW, the closed-open stop position shown in fig. 10(f) is reached. During the period from the open-close stop position to the close-open stop position, the tooth portion 41c of the small-diameter gear portion 41b of the first gear member 41 meshes with the first output gear 31, so that the first output gear 31 rotates in the clockwise direction CW. Accordingly, the first output shaft 17 rotates, and the first shutter 7 moves from the open position to the closed position. On the other hand, the contact portion 41e of the first gear member 41 is not in contact with the contacted portion 42d of the second gear member 42 during the period from the open-close stop position to the close-open stop position. Further, the contact portion 41e of the first gear member 41 and the contacted portion 42d of the second gear member 42 do not contact during the period from the opening-opening origin position to the opening-opening stop position. Therefore, the second output shaft 18 does not rotate, and the second shutter 8 is maintained at the open position.
Here, when the motor 21 is driven further in the reverse direction from the close-open stop position and the first gear member 41 is rotated by 120 ° in the counterclockwise direction CCW, the close-close origin position is reached. During the period from the close-open stop position to the close-close origin position, the tooth portion 41c of the small-diameter gear portion 41b of the first gear member 41 is not meshed with the first output gear 31. Therefore, the first output shaft 17 does not rotate, and the first shutter 7 is maintained at the closed position. On the other hand, during the period from the close-open stop position to the close-close origin position, the contact portion 41e of the first gear member 41 contacts the contacted portion 42d of the second gear member 42. Thus, the second gear member 42 rotates together with the first gear member 41 and rotates in the counterclockwise direction CCW. Thereby, the tooth portion 42c of the second gear member 42 meshes with the second output gear 32, and therefore, the second output gear 32 rotates in the clockwise direction CW. Thus, the second shutter 8 moves from the open position to the closed position. Thus, at the closing-closing origin position, both the first flap 7 and the second flap 8 are disposed at the open position.
(effective effect)
According to this example, the first gear 27 of the gear mechanism 25 transmits the rotation of the motor 21, but is pressed against the motor case 36 by the urging force of the rotation blocking mechanism 26 to block the rotation. Therefore, the first gear 27 is not moved in a state where the gear mechanism 25 does not transmit the rotation of the motor 21. This prevents the teeth of the first gear 27 and the teeth of the second gear 28 from repeatedly colliding with each other a plurality of times when the first gear 27 and the second gear 28 mesh with each other during rotation transmission.
That is, when the rotation of the first gear 27 is not inhibited by the rotation inhibiting mechanism 26, if the teeth of the first gear 27 come into contact with the teeth of the motor pinion 24 when the first gear 27 is meshed with the motor pinion 24, the first gear 27 rotates in one direction around its own rotation center line by reaction of the contact, so that the teeth of the first gear 27 collide with the teeth of the motor pinion 24. Further, when a collision occurs, the first gear 27 rotates in the other direction around its own rotation center line in reaction to the collision, and causes the teeth of the first gear 27 to collide with the other teeth of the motor pinion 24. Subsequently, the first gear 27 repeats the above-described collision until the engagement between the first gear 27 and the motor pinion 24 becomes reliable. On the other hand, if the first gear 27 is not moved by the urging force of the rotation blocking mechanism 26, even if the teeth of the first gear 27 come into contact with the teeth of the motor pinion 24 when the first gear 27 is meshed with the motor pinion 24, the first gear 27 is prevented or suppressed from rotating around its own rotation center line due to the reaction of the contact. This prevents or suppresses the repeated occurrence of collision between the teeth of the first gear 27 and the teeth of the motor pinion 24, and therefore prevents or suppresses the generation of abnormal sound from the gear mechanism 25. Further, since no grease is used, generation of abnormal sound from the gear mechanism 25 can be prevented or suppressed regardless of a change in the temperature environment.
In this example, the gear mechanism 25 is a reduction gear mechanism, and the first gear 27 is a gear that rotates first among a plurality of gears constituting the gear mechanism 25. Here, the first gear to rotate is likely to generate abnormal sound when meshing with another gear. Therefore, if the first gear 27 that rotates first is urged to resist its rotation, the effect of suppressing the generation of abnormal sound is good.
In this example, the driving device 2 includes: a first shaft 35, the first shaft 35 rotatably supporting the first gear 27; and an end plate 37 of the motor housing 36 that contacts the first gear 27 from one side in the axial direction of the first spindle 35. The rotation blocking mechanism 26 includes an urging member 50, and the urging member 50 is disposed on the other side of the first gear 27 in the axial direction of the first shaft 35, and urges the first gear 27 toward the end plate 37 of the motor housing 36. Therefore, the rotation of the first gear 27 can be inhibited by the urging force of the urging member 50.
Also, in this example, the motor 21 is a stepping motor. In the case of using a stepping motor as the motor 21, abnormal sound is easily generated at the meshing portion of the two gears, as compared with the case of using a servo motor as the motor 21. On the other hand, in the present embodiment, since the rotation blocking mechanism 26 that blocks the rotation of the first gear 27 is provided, it is possible to prevent or suppress the generation of abnormal sound from the gear mechanism 25.
In the above example, the first gear 27 is the target gear for which the rotation of the rotation blocking mechanism 26 blocks the rotation, but the rotation of any gear may be blocked if the target gear is the gear constituting the gear mechanism 25. The rotation blocking mechanism 26 may block the rotation of a plurality of gears constituting the gear mechanism 25 by applying a force thereto.
The biasing member 50 of the rotation blocking mechanism 26 may be disposed between the first gear 27 and the motor case 36, and may bias the first gear 27 toward the holding portion 55 (see fig. 5) of the first support shaft 35 of the lid 13. Here, the end surface of the holding portion 55 in the-X direction is a contact portion 41e that contacts the first gear 27. In this way, the rotation of the first gear 27 can be also hindered.
(modification of rotation blocking mechanism)
Next, modifications 1 to 5 of the rotation blocking mechanism 26 will be described with reference to fig. 11 to 13. The rotation blocking mechanism according to the modification 1 to 5 can be used as a mechanism for blocking the rotation of each gear of the gear mechanism 25 of the cold air damper 1.
Fig. 11(a) is an explanatory view of the rotation blocking mechanism of modification 1. As shown in fig. 11(a), the target gear 61 to be biased by the rotation blocking mechanism 26A of the present example is rotatably supported by a support shaft 60. One end of the support shaft 60 is supported by the cover 13, and the other end is supported by the end plate 15 of the case 12. The rotation blocking mechanism 26A biases the counter gear 61 from a direction intersecting the axis of the support shaft 60 to block the rotation of the counter gear 61.
Specifically, the target gear 61 includes a gear portion 62 (a large-diameter gear portion 62a and a small-diameter gear portion 62b) having a gear portion, a shaft portion 63 coaxial with the gear portion 62, and a shaft hole 64 penetrating the gear portion 62 and the shaft portion 63, the shaft hole 64 is penetrated by the support shaft 60, the rotation blocking mechanism 26A includes a biasing member 65 that biases the shaft portion 63 toward the support shaft 60, the biasing member 65 is, for example, a plate spring, the target gear 61 is pressed against the support shaft 60 by a biasing force F1 of the biasing member 65, and rotation thereof is blocked, and here, the shaft portion 63 may be provided between the large-diameter gear portion 62a and the small-diameter gear portion 62b in a direction along the axis line L of the target gear 61.
Fig. 11(b) is an explanatory view of the rotation blocking mechanism of modification 2. As shown in fig. 11(B), the target gear 61 to be biased by the rotation blocking mechanism 26B of the present example is rotatably supported by a support shaft 60. One end of the support shaft 60 is supported by the cover 13, and the other end is supported by the end plate 15 of the case 12. The rotation blocking mechanism 26B biases the counter gear 61 toward the inner peripheral side to block the rotation thereof.
Specifically, the target gear 61 includes a gear portion 62 (a large-diameter gear portion 62a and a small-diameter gear portion 62B) having a toothed portion, a shaft portion 63 coaxial with the gear portion 62, and a shaft hole 64 through which the gear portion 62 and the shaft portion 63 are inserted, the support shaft 60 penetrates the shaft hole 64, the rotation blocking mechanism 26B includes a cylindrical portion 68 surrounding the shaft portion 63 from the outer peripheral side, and an urging member 69 compressed between the shaft portion 63 and the cylindrical portion 68 in a direction intersecting the direction along the axis L of the support shaft 60 and urging the cylindrical portion 68, the cylindrical portion 68 is provided in the case 12, for example, and the urging member 69 is an annular elastic member, for example, an O-ring, and the target gear 61 is pressed toward the inner peripheral side by the urging force F2 of the urging member 69 and rotation of the target gear 61 is blocked, and here, the shaft portion 63 may be provided between the large-diameter gear portion 62a and the small-diameter gear portion 62B in the direction.
Fig. 12(a) and (b) are a perspective view and a sectional view of a rotation preventing mechanism 26C of modification 3, in this example, a target gear 70 to be urged by the rotation preventing mechanism 26C is rotatably supported by a bearing 71, more specifically, the cold air damper 1 includes a bearing 71, the bearing 71 supports the target gear 70 on an end plate portion 15 of a case 12 so that the target gear 70 can rotate about a predetermined axis L, a support 72 coaxial with the bearing 71 is provided on a lid 13, the target gear 70 includes a gear portion 74, a shaft portion 75, the shaft portion 75 and the gear portion 74 being coaxial, and a body portion 76, the shaft portion 76 and the shaft portion 74 being coaxial, the gear portion 74 includes a large-diameter gear portion 74a and a small-diameter gear portion 74b, the body portion 76 is positioned between the large-diameter gear portion 74a and the gear portion 74b, the 75 is provided on one end of the target gear 70 opposite to the large-diameter gear portion 74a, the shaft portion 74 is provided with a recess 77 of the target gear portion 75, the bearing 71 is provided on the shaft portion 74, the bearing 71 is capable of coaxially supporting the target gear 70, and the support portion is provided on the side where the support post 71a contacts the target gear portion 3571 is inserted from the axis 75 along the axis of the target gear portion 71.
The rotation blocking mechanism 26C includes a biasing member 78, which is disposed on the opposite side of the bearing 71 from the bearing 71 in the direction along the axis L of the bearing 71 of the target gear 70, and which biases the target gear 70 toward the contact portion 71a, the biasing member 78 is, for example, a plate spring, the biasing member 78 includes a ring portion 78a having a hole through which the support 72 passes, an arm portion 78b extending from the ring portion 78a toward the outer peripheral side and in the direction away from the target gear 70, and a fixing portion 78C provided at the tip of the arm portion 78b, the ring portion 78a abuts against the large diameter gear portion 74a, the fixing portion 78C is fixed to the lid body 13, the plate spring is disposed between the large diameter gear portion 74a and the lid body 13 in an elastically deformed state, and the target gear 70 is pressed against the contact portion 71a of the bearing 71 by the biasing force F3 of the biasing member 78, and rotation of the target gear 70 is blocked.
Fig. 13(a) and (b) are a perspective view and a sectional view of a rotation preventing mechanism 26D according to modification 4, in this example, a target gear 70 to be urged by the rotation preventing mechanism 26D is rotatably supported by a bearing 71, and more specifically, the cold air damper 1 includes a bearing 71, and the bearing 71 supports the target gear 70 on an end plate portion 15 of the case 12 so that the target gear 70 can rotate about a predetermined axis L, and the cover 13 includes a support 72 coaxial with the bearing 71, the target gear 70 includes a gear portion 74, a shaft portion 75, which is coaxial with the gear portion 74, and a body portion 76, which is coaxial with the shaft portion 74, the shaft portion 76 includes a large-diameter gear portion 74a and a small-diameter gear portion 74b, the body portion 76 is positioned between the large-diameter gear portion 74a and the gear portion 74b, and the target gear 70 is provided with a recess 77 of the target gear portion 75, the bearing 71 is coaxially supported, and the support portion 71 is in contact with the small-diameter gear portion 77, and the support portion 71 is inserted into the outer peripheral surface of the target gear portion 71, and the support portion 71 is inserted into the recess 77 of the target gear portion 75.
The rotation preventing mechanism 26D includes an urging member 80 that urges the shaft portion 75 toward the contact portion 71b from a direction intersecting the direction along the axis L. the urging member 80 is, for example, a leaf spring, and the leaf spring includes an abutting portion 80a that abuts against the shaft portion 75, an inclined portion 80b that extends obliquely from the abutting portion 80a in a direction away from the shaft portion 75, and a fixed portion 80c that is provided on the opposite side of the inclined portion 80b from the abutting portion 80 a. the urging member 80 fixes the fixed portion 80c to the inner wall surface of the housing in an elastically deformed state, and the target gear 70 is pressed by the urging force F4 of the urging member 80 to the abutting portion 80a of the bearing 71 and rotation thereof is prevented, and the target gear 70 is pressed by the urging force F4 of the urging member 80 to the support post 72 and rotation thereof is prevented.
Fig. 14 is a sectional view of a rotation preventing mechanism 26E of modification 5, in this example, a target gear 70 to be urged by the rotation preventing mechanism 26E is rotatably supported by a bearing 71, more specifically, the cold air damper 1 includes a bearing 71, the bearing 71 supports the target gear 70 on an end plate portion 15 of the case 12 so that the target gear 70 can rotate about a predetermined axis L, the lid 13 includes a support 72 coaxial with the bearing 71, the target gear 70 includes a gear portion 74 including a gear portion 74, a shaft portion 75 coaxial with the gear portion 74, and a body portion 76 coaxial with the gear portion 74, the shaft portion 74 includes a large-diameter gear portion 74a and a small-diameter gear portion 74b, the body portion 76 is positioned between the large-diameter gear portion 74a and the small-diameter gear portion 74b, the shaft portion 75 is provided at one end of the target gear 70 opposite to the large-diameter gear portion 74a, the target gear 70 includes a recess 77 coaxial with the shaft portion 75, the bearing 71 rotatably supports the support 75 to the recess 77 of the target gear 70.
The rotation blocking mechanism 26E includes a cylindrical portion 85 surrounding the body portion 76 from the outer peripheral side, and an urging member 86 that is compressed between the body portion 76 and the cylindrical portion 85 in a direction intersecting the direction along the axis L of the shaft portion 75 and urges the body portion 76, the urging member 86 being an annular elastic member such as an O-ring, and the target gear 70 is pressed toward the inner peripheral side by an urging force F5 of the urging member 86 and is blocked from rotating.
Claims (10)
1. A cold air damper, comprising:
a shutter for opening and closing an opening provided in the frame;
an output shaft coupled to the baffle;
a motor;
a motor pinion fixed to a rotation shaft of the motor;
a gear mechanism that transmits rotation of the motor pinion to the output shaft; and
a rotation blocking mechanism that blocks rotation of at least one target gear among the plurality of gears constituting the gear mechanism by applying a force to the target gear,
when the motor is driven, the target gear rotates against the urging force of the rotation blocking mechanism.
2. The cold air damper as claimed in claim 1,
the gear mechanism is a reduction gear mechanism,
the target gear is a gear that rotates first among the plurality of gears constituting the gear mechanism.
3. The cold air damper according to claim 1 or 2,
the gear mechanism includes a first gear and a second gear, wherein the first gear is engaged with the motor pinion, the second gear is engaged with the first gear,
the first gear includes a large diameter gear portion and a small diameter gear portion, wherein the large diameter gear portion is engaged with the motor pinion, the small diameter gear portion is engaged with the second gear, and an outer diameter of the small diameter gear portion is smaller than an outer diameter of the large diameter gear portion,
the subject gear is the first gear.
4. The cold air damper as claimed in any one of claims 1 to 3, wherein the cold air damper comprises:
a fulcrum shaft that rotatably supports the target gear; and
a contact portion that contacts the target gear from one side in an axial direction of the spindle,
the rotation blocking mechanism includes an urging member that is disposed on the other side of the counter gear in the axial direction and that urges the counter gear toward the contact portion.
5. The cold air damper as claimed in any one of claims 1 to 3,
the cold air damper has a support shaft for rotatably supporting the target gear,
the target gear includes a gear portion, a shaft portion, and a shaft hole, wherein the gear portion includes a tooth portion, the shaft portion is coaxial with the gear portion, and the shaft hole penetrates the gear portion and the shaft portion,
the fulcrum shaft penetrates through the shaft hole,
the rotation blocking mechanism includes a biasing member that biases the shaft portion toward the support shaft.
6. The cold air damper as claimed in any one of claims 1 to 3,
the cold air damper has a support shaft for rotatably supporting the target gear,
the target gear includes a gear portion, a shaft portion, and a shaft hole, wherein the gear portion includes a tooth portion, the shaft portion is coaxial with the gear portion, and the shaft hole penetrates the gear portion and the shaft portion,
the fulcrum shaft penetrates through the shaft hole,
the rotation blocking mechanism includes a cylindrical portion that surrounds the shaft portion from an outer peripheral side, and an urging member that is compressed between the shaft portion and the cylindrical portion in a direction intersecting the axial direction of the support shaft and urges the shaft portion.
7. The cold air damper as claimed in any one of claims 1 to 3,
the cold air damper has a bearing for rotatably supporting the target gear around a predetermined axis,
the object gear includes a gear portion including a tooth portion and a shaft portion coaxial with the gear portion,
the bearing rotatably supports the shaft portion and includes a contact portion that contacts the target gear from one side of the shaft portion in the axial direction,
the rotation blocking mechanism includes an urging member that is disposed on the opposite side of the bearing in the axial direction and that urges the target gear toward the contact portion.
8. The cold air damper as claimed in any one of claims 1 to 3,
the cold air damper has a bearing for rotatably supporting the target gear around a predetermined axis,
the object gear includes a gear portion, a body portion, and a shaft portion, wherein the gear portion includes a tooth portion, the body portion is coaxial with the gear portion, the shaft portion is coaxial with the gear portion,
the bearing rotatably supports the shaft portion and includes a contact portion that contacts an outer peripheral surface of the shaft portion,
the rotation blocking mechanism includes an urging member that urges the main body portion toward the contact portion from a direction intersecting an axial direction of the shaft portion.
9. The cold air damper as claimed in any one of claims 1 to 3,
the cold air damper has a bearing for rotatably supporting the target gear around a predetermined axis,
the object gear includes a gear portion including a tooth portion and a shaft portion coaxial with the gear portion,
the bearing rotatably supports the shaft portion,
the rotation blocking mechanism includes a cylindrical portion that surrounds the shaft portion from an outer peripheral side, and an urging member that is compressed between the shaft portion and the cylindrical portion in a direction intersecting an axial direction of the shaft portion and urges the shaft portion.
10. The cold air damper as claimed in any one of claims 1 to 9,
the motor is a stepper motor.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2019008174A JP2020118194A (en) | 2019-01-22 | 2019-01-22 | Cold air damper |
| JP2019-008174 | 2019-01-22 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111457056A true CN111457056A (en) | 2020-07-28 |
Family
ID=68821554
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910089782.3A Pending CN111457056A (en) | 2019-01-22 | 2019-01-30 | Cold air damper |
| CN201920162146.4U Active CN209800640U (en) | 2019-01-22 | 2019-01-30 | Cold air damper |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201920162146.4U Active CN209800640U (en) | 2019-01-22 | 2019-01-30 | Cold air damper |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2020118194A (en) |
| CN (2) | CN111457056A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2020118194A (en) * | 2019-01-22 | 2020-08-06 | 日本電産サンキョー株式会社 | Cold air damper |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1439941A (en) * | 2002-02-18 | 2003-09-03 | 株式会社三协精机制作所 | Driving power transferring mechanism and its damper device |
| CN1583439A (en) * | 2003-07-30 | 2005-02-23 | 阿斯莫有限公司 | Actuator device |
| JP2014200458A (en) * | 2013-04-04 | 2014-10-27 | 日本電産サンキョー株式会社 | Lid body opening/closing device |
| WO2015133444A1 (en) * | 2014-03-04 | 2015-09-11 | 日本電産サンキョー株式会社 | Drain valve driving device |
| CN107620788A (en) * | 2016-07-14 | 2018-01-23 | 日本电产三协株式会社 | Torque limiter and open and close member drive device |
| CN209800640U (en) * | 2019-01-22 | 2019-12-17 | 日本电产三协株式会社 | Cold air damper |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2549356Y2 (en) * | 1991-02-28 | 1997-09-30 | 狭山精密工業株式会社 | Geared motor noise reduction structure |
| JP2002115754A (en) * | 2000-10-06 | 2002-04-19 | Oriental Motor Co Ltd | Reduction gear |
| JP5697932B2 (en) * | 2010-09-24 | 2015-04-08 | 株式会社ミツバ | Motor device with reduction mechanism and electric seat device for vehicle |
| JP2012122704A (en) * | 2010-12-10 | 2012-06-28 | Hitachi Appliances Inc | Refrigerator |
-
2019
- 2019-01-22 JP JP2019008174A patent/JP2020118194A/en active Pending
- 2019-01-30 CN CN201910089782.3A patent/CN111457056A/en active Pending
- 2019-01-30 CN CN201920162146.4U patent/CN209800640U/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1439941A (en) * | 2002-02-18 | 2003-09-03 | 株式会社三协精机制作所 | Driving power transferring mechanism and its damper device |
| CN1583439A (en) * | 2003-07-30 | 2005-02-23 | 阿斯莫有限公司 | Actuator device |
| JP2014200458A (en) * | 2013-04-04 | 2014-10-27 | 日本電産サンキョー株式会社 | Lid body opening/closing device |
| WO2015133444A1 (en) * | 2014-03-04 | 2015-09-11 | 日本電産サンキョー株式会社 | Drain valve driving device |
| CN107620788A (en) * | 2016-07-14 | 2018-01-23 | 日本电产三协株式会社 | Torque limiter and open and close member drive device |
| CN209800640U (en) * | 2019-01-22 | 2019-12-17 | 日本电产三协株式会社 | Cold air damper |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2020118194A (en) | 2020-08-06 |
| CN209800640U (en) | 2019-12-17 |
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