CN106871549B - Air supply device for air-cooled refrigerator and air supply method using same - Google Patents

Air supply device for air-cooled refrigerator and air supply method using same Download PDF

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Publication number
CN106871549B
CN106871549B CN201710233785.0A CN201710233785A CN106871549B CN 106871549 B CN106871549 B CN 106871549B CN 201710233785 A CN201710233785 A CN 201710233785A CN 106871549 B CN106871549 B CN 106871549B
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Prior art keywords
damper
air supply
drive
post
driving
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CN106871549A (en
Inventor
丁维超
王富冈
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Jiangsu Leili Motor Co Ltd
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Jiangsu Leili Motor Co Ltd
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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
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
    • F25D17/062—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators
    • F25D17/065—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators with compartments at different temperatures
    • 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
    • F25D17/042—Air treating means within refrigerated spaces
    • F25D17/045—Air flow control arrangements
    • 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
    • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
    • F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
    • F25D2317/068—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans
    • F25D2317/0681—Details thereof

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)

Abstract

The invention relates to an air supply device for an air-cooled refrigerator, which comprises: a frame body including an airflow circulating part and a driving mechanism receiving part; a fan received in the airflow circulating part for drawing the airflow from the cold air forming device and guiding the airflow to the airflow passage; a first damper mounted at one end of the frame in a lateral direction, switchable between an open position and a closed position to control the circulation of the air flow through the first outlet; a second damper, which is installed at the other end of the frame body opposite to the first damper in the transverse direction and can be switched between an open position and a closed position to control the circulation of the air flow through the second outlet; a drive mechanism for driving the switching of the first damper and the second damper between the open position and the closed position, and the drive mechanism is received in the drive mechanism receiving portion; wherein the drive mechanism receiving portion and the airflow circulating portion are separated from each other. The invention also relates to a refrigerator comprising the air supply device and an air supply method applying the air supply device.

Description

Air supply device for air-cooled refrigerator and air supply method using same
Technical Field
The invention relates to an air supply device for an air-cooled refrigerator and an air supply method for the refrigerator by using the air supply device.
Background
The air-cooled refrigerator generates cold air through a built-in evaporator, and the cold air circularly flows to the storage space of the refrigerator through an air duct to realize refrigeration. In order to supply cold energy to two refrigerating chambers in the three-door refrigerator and ensure that food is not rotten, a double-door air supply device is required to be designed to supply cold energy. The large air supply opening is corresponding to the large refrigerating chamber to supply or block cold air, and the small air supply opening is corresponding to the small refrigerating chamber to supply or block cold air. The traditional single-door air supply device cannot supply air to the refrigerator with two refrigerating chambers at the same time. Therefore, there is a need for an air supply device that meets the above requirements.
The above information is presented as background information only to aid in understanding the present invention. No determination is made as to whether any of the above information is likely to be appropriate as prior art with respect to the present invention, and no assertion is made.
Disclosure of Invention
The invention relates to an air supply device for an air-cooled refrigerator, which comprises: a frame body including an airflow circulating part and a driving mechanism receiving part; a fan received in the airflow circulating part for drawing the airflow from the cold air forming device and guiding the airflow to the airflow passage; a first damper, which is installed at one end of the frame body along the transverse direction and can be switched between an opening position and a closing position so as to control the circulation of the air flow through the first outlet; a second damper, which is installed at the other end of the frame body opposite to the first damper in the transverse direction and can be switched between an open position and a closed position to control the circulation of the air flow through the second outlet; a drive mechanism for driving the switching of the first damper and the second damper between the open position and the closed position, and the drive mechanism is received in the drive mechanism receiving portion; wherein the drive mechanism receiving portion and the airflow circulating portion are separated from each other.
In an alternative embodiment, the first damper includes a first panel and a compressible first seal disposed on a surface of the first panel, and/or the second damper includes a second panel and a compressible second seal disposed on a surface of the second panel.
In an alternative embodiment, the frame includes a first raised edge at one end thereof in the transverse direction that defines the shape of the first airflow outlet, the first raised edge engaging the first seal and compressing the first seal to close the first airflow outlet in the closed position of the first damper, and/or the frame includes a second raised edge at the other end thereof in the transverse direction that defines the shape of the second airflow outlet, the second raised edge engaging the second seal and compressing the second seal to close the second airflow outlet in the closed position of the second damper.
In an alternative embodiment, each of the first and second dampers is arranged such that, when it is transitioned from the closed position to the open position, each of the first and second dampers rotates inward of the frame without extending beyond the frame.
In an optional embodiment, the transmission mechanism includes a driving motor, a reduction transmission pair, a first damper driving wheel, a first damper driving rod and a first damper driving piece for driving the first damper, a second damper driving rod and a second damper driving piece for driving the second damper, and the reduction transmission pair includes at least one stage of reduction transmission.
In an alternative embodiment, the first damper drive wheel, the first damper drive rod and the first damper drive member for driving the first damper, and the second damper drive rod, the second damper drive rod and the second damper drive member for driving the second damper, are mirror images with respect to a longitudinal axis of the air-moving device.
In an alternative embodiment, the reduction gear pair is a gear pair and includes a power source input in the form of a pinion gear, and a first power source output and a second power source output for driving the first damper and the second damper, respectively, the first power source output and the second power source output being in the form of reduction gears, a first damper drive wheel for driving the first damper, a first damper drive rod, a first damper drive member, and a first power source output, and a second damper drive rod for driving the second damper, a second damper drive rod, a second damper drive member, and a second power source output, mirror symmetric with respect to a longitudinal axis of the air supply device.
In an alternative embodiment, the first damper drive wheel is provided at a side thereof with a first groove track, and the second damper drive wheel is provided at a side thereof with a second groove track, the first damper drive lever is provided with a first post that mates with the first groove track, the second damper drive lever is provided with a second post that mates with the second groove track, the first groove track is arranged to vary in radius in a circumferential direction of the first damper drive wheel such that when the first damper drive wheel is rotated via a torque output by the drive motor, the first groove track is drivingly coupled with the first post for translation to further drive movement of the first damper, the second groove track is arranged to vary in radius in a circumferential direction of the second damper drive wheel such that when the second damper drive wheel is rotated via a torque output by the drive motor, the second groove track is drivingly coupled with the second post for translation, thereby further driving movement of the second damper.
In an alternative embodiment, the first damper drive lever further includes a first rack engaging the sector gear of the first damper drive lever to convert the translational movement of the first damper drive lever into rotational movement of the first damper, and the second damper drive lever further includes a second rack engaging the sector gear of the second damper drive lever to convert the translational movement of the second damper drive lever into rotational movement of the second damper.
In an alternative embodiment, the angle of engagement of the sector gear of the first damper driver is greater than the angle of rotation of the first damper between the open and closed positions, and/or the angle of engagement of the sector gear of the second damper driver is greater than the angle of rotation of the second damper between the open and closed positions.
In an alternative embodiment, the axis of rotation of the first groove track coincides with the axis of rotation of the first damper drive wheel and/or the axis of rotation of the second groove track coincides with the axis of rotation of the second damper drive wheel.
In an alternative embodiment, the first damper drive lever includes a first guide slot that cooperates with a first guide slot stop disposed in the drive mechanism receiving portion to guide the first damper drive lever for translation in the lateral direction, and/or the second damper drive lever includes a second guide slot that cooperates with a second guide slot stop disposed in the drive mechanism receiving portion to guide the second damper drive lever for translation in the lateral direction.
In an alternative embodiment, the first damper drive lever includes a first motion bypass portion that receives an end of the rotational shaft of the first damper drive wheel, and/or the second damper drive lever includes a second motion bypass portion that receives an end of the rotational shaft of the second damper drive wheel.
In an alternative embodiment, when the first damper is in the closed position, the first post is located at a first radius in the first groove track, the first post is positioned at a second radius in the first groove track when the first damper is in the open position, the first radius being greater than the second radius, such that, the force exerted on the first post when the first damper is in the closed position is less than the force exerted on the first post when the first damper is in the open position, and/or when the second damper is in the closed position, the second post is positioned at a third radius in the second groove track, the second post is positioned within the second groove track at a fourth radius when the second damper is in the open position, the third radius being greater than the fourth radius, such that, the force exerted on the second post when the second damper is in the closed position is less than the force exerted on the second post when the second damper is in the open position.
In an alternative embodiment, when the first damper is in the closed position, the first post is located at a first radius in the first groove track, the first post is positioned at a second radius in the first groove track when the first damper is in the open position, the first radius being less than the second radius, such that, the force exerted on the first post when the first damper is in the closed position is greater than the force exerted on the first post when the first damper is in the open position, and/or when the second damper is in the closed position, the second post is positioned at a third radius in the second groove track, the second post is positioned at a fourth radius in the second groove track when the second damper is in the open position, the third radius being less than the fourth radius, such that, the force exerted on the second post when the second damper is in the closed position is greater than the force exerted on the second post when the second damper is in the open position.
In an alternative embodiment, the damper group of the first and second dampers has a plurality of different operating states, and the first and second groove tracks are arranged in different shapes so that switching between the plurality of operating states of the damper group is achieved by the drive motor driving rotation of the first and second damper drive wheels.
In an alternative embodiment, the first and second damper drive wheels each rotate through the same angle as the damper groups switch between each two states.
In an alternative embodiment, both the first and second damper drive wheels rotate through the same angle each time the damper group is switched between the two states.
In an alternative embodiment, the drive motor may be programmed and programmed to change direction of rotation during a state switch of the damper group such that the first damper drive wheel rotates in a different direction each time and the second damper drive wheel rotates in a different direction each time during a plurality of state switches of the damper group.
In an alternative embodiment, only one damper is actuated each time the damper group switches from one operating condition to the next operating condition from the first operating condition of the damper group, and only one of the first groove track of the first damper drive wheel and the second groove track of the second damper drive wheel corresponding to the first damper and the second damper in the damper group changes in radius during the switching of the operating conditions.
In an alternative embodiment, the drive mechanism receiving portion of the frame is closed by the front cover such that the drive mechanism is substantially completely enclosed in the drive mechanism receiving portion.
In an alternative embodiment, an upper portion of the airflow circulation part of the frame is coupled with a damper blower cover having an opening corresponding in shape and size to the shape of the open upper portion of the blower so that the airflow flows into the airflow circulation part via the open upper portion of the blower.
In an alternative embodiment, the fan is fixed to the airflow circulating part of the frame by one or more mounting parts, and a shock-absorbing pad is provided at each of the one or more mounting parts.
The invention also relates to an air-cooled refrigerator which comprises the air supply device according to the embodiment of the invention.
The invention also relates to a method for supplying air or cooling by using the air supply device according to the embodiment of the invention.
Drawings
FIG. 1A is a schematic top perspective view of an air-moving device according to a preferred embodiment of the present invention;
FIG. 1B is a schematic bottom perspective view of an air supply arrangement according to a preferred embodiment of the present invention;
FIG. 2 shows an exploded view of the blower of FIGS. 1A and 1B;
fig. 3A shows a view of the drive mechanism viewed in the direction a in fig. 2;
fig. 3B shows a view of the drive mechanism as viewed in the direction B in fig. 2;
FIG. 4 shows a front perspective view of a frame of an air supply apparatus according to a preferred embodiment of the present invention;
FIG. 5A shows three views of a first damper drive lever of a blower device in accordance with a preferred embodiment of the present invention;
FIG. 5B is a three-dimensional view of a second damper drive lever of the air supply apparatus in accordance with the preferred embodiment of the present invention;
FIG. 6A shows top and front views of a first damper drive wheel of an air supply arrangement in accordance with a preferred embodiment of the present invention;
FIG. 6B shows top and front views of a second damper drive wheel of an air supply apparatus in accordance with a preferred embodiment of the present invention;
FIG. 7 is a view showing respective states of first and second damper driving levers and first and second damper driving wheels when a plurality of states of a first damper and a second damper are combined in a blower device according to a preferred embodiment of the present invention;
FIG. 8 schematically illustrates a side view of the open and closed positions of the first and second dampers in accordance with a preferred embodiment of the present invention;
FIG. 9A shows two perspective views and three plan views of a first damper drive lever of a blower apparatus according to another embodiment of the present invention;
FIG. 9B shows two perspective views and three plan views of a second damper drive lever of a blower device in accordance with another embodiment of the present invention;
FIG. 10A shows top and front views of a first damper drive wheel of an air supply arrangement in accordance with another embodiment of the present invention;
FIG. 10B shows top and front views of a second damper drive wheel of an air supply arrangement in accordance with another embodiment of the present invention;
FIG. 11 is a view showing the states of the first and second damper driving levers and the first and damper driving wheels when a plurality of states of the first and second dampers of the air-blowing device according to another embodiment of the present invention are combined;
fig. 12A and 12B schematically show forces applied to the first column moving to different positions in the first groove track in the air blowing device according to another embodiment of the present invention.
Detailed Description
The following description is provided with reference to the accompanying drawings to assist in a comprehensive understanding of various embodiments of the invention as defined by the claims. It includes various specific details to assist in this understanding, but these details should be construed as merely exemplary. Accordingly, those of ordinary skill in the art will recognize that changes and modifications of the various embodiments described herein can be made without departing from the scope of the invention, which is defined by the appended claims. Moreover, descriptions of well-known functions and constructions may be omitted for clarity and conciseness.
It will be apparent to those skilled in the art that the following descriptions of the various embodiments of the present invention are provided for illustration only and not for the purpose of limiting the invention as defined by the appended claims.
Throughout the description and claims of this specification, the words "comprise" and variations of the words, for example "comprising" and "comprises", mean "including but not limited to", and are not intended to (and do not) exclude other components, integers or steps.
Features, integers or characteristics described in conjunction with a particular aspect, embodiment or example of the invention are to be understood to be applicable to any other aspect, embodiment or example described herein unless incompatible therewith.
It is to be understood that the singular forms "a," "an," and "the" include plural referents unless expressly specified otherwise. The expression "comprising" and/or "may comprise" as used in the present invention is intended to indicate the presence of corresponding functions, operations or elements, and is not intended to limit the presence of one or more functions, operations and/or elements. Furthermore, in the present invention, the terms "comprises" and/or "comprising" are intended to indicate the presence of the features, amounts, operations, elements, and components disclosed in the specification, or combinations thereof. Thus, the terms "comprising" and/or "having" should be understood as presenting additional possibilities for one or more other features, quantities, operations, elements, and components, or combinations thereof.
In the present invention, the expression "or" comprises any and all combinations of the words listed together. For example, "a or B" may comprise a or B, or may comprise both a and B.
Although expressions such as "1 st", "2 nd", "first" and "second" may be used to describe the respective elements of the present invention, they are not intended to limit the corresponding elements. For example, the above expressions are not intended to limit the order or importance of the corresponding elements. The above expressions are used to distinguish one element from another. For example, the first damper and the second damper are both damper devices and represent different damper devices. For example, a first damper may be referred to as a second damper, and similarly, a second damper may be referred to as a first damper, without departing from the scope of the present invention.
References herein to "upper", "lower", "left", "right", etc. are merely intended to indicate relative positional relationships, which may change accordingly when the absolute position of the object being described changes.
The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. Singular references include plural references unless there is a significant difference in context, scheme or the like between them.
Unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and the present specification and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.
Figures 1 through 12, discussed below, and the various embodiments used to describe the principles of the present invention in this patent document are by way of illustration only and should not be construed in any way to limit the scope of the invention. Those skilled in the art will appreciate that the principles of the present invention may be implemented in any suitably arranged air supply arrangement and refrigerator incorporating the same. The terminology used to describe various embodiments is exemplary. It should be understood that these are provided solely to aid in the understanding of this specification and their use and definition do not limit the scope of the invention in any way. Unless explicitly stated otherwise. A group is defined as a non-empty group containing at least one element.
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the drawings of the embodiments of the present invention. It is to be understood that the embodiments described are only a few embodiments of the present invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the described embodiments of the invention without any inventive step, are within the scope of protection of the invention. It should be understood that the exemplary embodiments described herein should be considered in descriptive sense only and not for purposes of limitation. Descriptions of features or aspects within each exemplary embodiment should generally be considered as available for similar features or aspects in other exemplary embodiments.
Fig. 1-8 show various views of an air-moving device 100 in accordance with a preferred embodiment of the present invention.
Fig. 1A is a schematic top perspective view of air supply device 100, and fig. 1B is a schematic bottom perspective view of air supply device 100. In particular, the air supply device serves to draw an air flow from a cold air forming device (e.g. an evaporator) and to guide and appropriately distribute the air flow to one or more storage spaces of the refrigerator in order to achieve an appropriate distribution of cold in the refrigerator.
In the air blowing device 100 shown in fig. 1A, the air blowing device 100 is oriented with respect to a longitudinal direction X, a lateral direction Y, and a vertical direction Z that are perpendicular to each other. In fig. 1A, the vertical direction Z extends parallel to the direction of gravity. However, it should be understood that the embodiments described herein are not limited to having a particular orientation with respect to gravity. For example, in other applications, the longitudinal direction X or the transverse direction Y may extend parallel to the direction of gravity. Specifically, the relative orientation of air supply device 100 depends on its particular arrangement in the refrigerator.
Fig. 2 shows an exploded view of the air blowing device 100 in fig. 1A and 1B. Fig. 2 shows the respective components of the air blowing device 100.
In the embodiment shown in fig. 1A, 1B and 2, air-moving device 100 includes two air-flow passages. In the illustrated embodiment, the airflow channel refers to a channel from the fan 500 to the corresponding airflow outlet 101A, 101B, and is used for allowing airflow to flow therein; in particular, the number of airflow passages is equal to the number of dampers 140. In alternative embodiments, the air supply arrangement may also include only one air flow passage or more than two air flow passages, and a corresponding only one damper or more than two dampers.
In the illustrated embodiment, the two air flow passages of the air blowing device 100 are arranged so that the air flow flows in the lateral direction Y. The two air flow channels have the same width in the longitudinal direction X and the same height in the vertical direction Z; in alternative embodiments, the two air flow channels may also have different widths in the longitudinal direction X or different heights in the vertical direction Z. In the illustrated embodiment, the two air flow passages of the air blowing device 100 are arranged so that the air flows in opposite directions; in alternative embodiments, the two air flow channels may also be arranged such that the air flows flow in the same direction or in directions at an angle to each other.
Air supply device 100 includes dampers 140A and 140B for opening and/or closing respective air flow passages. Specifically, when the dampers 140A, 140B are in the open position, the respective airflow passages allow airflow or chilled air to circulate therethrough; when the dampers 140A, 140B are in the closed position, airflow or cold air is not able to flow through the respective airflow passages. During operation of blower apparatus 100, dampers 140A and 140B may be in any state or combination of states.
The blower device 100 includes a housing 110, and the housing 110 includes an airflow circulating section 111 and a drive mechanism receiving section 112. The airflow vent 111 is for receiving the fan 500 and the dampers 140A, 140B therein and defines a path along which the airflow flows. The drive mechanism receiving portion 112 is for receiving a drive mechanism that transmits power to the dampers 140A and 140B to drive the respective dampers between open and closed positions. In the illustrated embodiment, the airflow circulation portion 111 and the drive mechanism receiving portion 112 are arranged and spaced apart in the longitudinal direction X. In alternative embodiments, the airflow circulation portion and the driving mechanism receiving portion may be arranged in other directions, such as in a vertical direction Z, for example, to meet the arrangement requirements in a refrigerator or other refrigeration device.
The structure of the air blowing device 100 according to the present invention is described in detail below with reference to the embodiment shown in fig. 1A, 1B, and 2. The air blowing device having other arrangements of the airflow circulating part 111 and the driving mechanism receiving part 112 can also be realized by a similar principle, and will not be described in detail below.
The airflow circulating part 111 receives the blower 500 therein. The fan 500 is generally cylindrical and includes a circular outer periphery 502 and a plurality of blades extending from a central portion 503 of the fan to the outer periphery 502. The outer periphery 502 is connected to the plurality of blades and rotates with the rotation of the plurality of blades. The fan 500 is opened at the upper and circumferential sides to form a continuous air flow path, thereby drawing air flow from the cold air forming device (e.g., evaporator), and guiding the air flow into the air flow path at both sides of the fan 500, and flowing through the air flow outlets 101A, 101B and reasonably distributing to one or more storage spaces of the refrigerator, thereby achieving reasonable distribution of cold in the refrigerator. The damper hood 600 is disposed above the airflow circulation part 111 and has an opening 601 therein. The shape and size of the opening 601 correspond to the shape of the open upper portion of the fan 500 so as not to obstruct the flow of air to the upper portion of the fan 500.
The fan 500 includes three mounting portions 501 uniformly distributed in the circumferential direction of the fan 500, and is fixed to the frame body 110 by the three mounting portions 501. In alternative embodiments, the fan 500 may include more or less than three mounts; or a plurality of mounting portions of the fan 500 are non-uniformly distributed along the circumference thereof, so as to better adapt to the arrangement of other components and avoid interference. In the mounted state of the fan 500, the upper surface of the fan 500 is flush with the damper fan cover 600 or slightly lower than the damper fan cover 600, so that the fan 500 is completely received in the frame 110 (particularly in the airflow circulating section 111) in its mounted state. Such an arrangement contributes to further reducing the volume of the air blowing device, particularly the height in the vertical direction Z.
The air door fan cover 600 comprises a corresponding number of mounting elements 602 therein and a corresponding number of mounting seats 113 on the bottom surface of the airflow circulation 111 (only 1 is shown in fig. 2, the other two being hidden from view). A corresponding number of fasteners 603 secure the damper fan cover 600, fan 500, and frame 110 (particularly the airflow communication portion 111) together, such as by a threaded connection, an adhesive connection, or an interference fit, for example.
In a preferred embodiment, a shock pad is mounted at each mounting 501 of the fan 500. The vibration generated when the impeller rotates to suck gas is at least partially or completely absorbed by the shock absorption pad, so that the vibration is reduced, the noise is reduced, and the energy loss is further reduced.
The airflow circulation portion 111 has airflow outlets 101A, 101B on opposite sides thereof in the lateral direction Y, respectively. The damper 140A controls the opening and closing of the airflow outlet 101A, and the damper 140B controls the opening and closing of the airflow outlet 101B. The dampers 140A, 140B have coupling portions 141A, 142A and 141B, 142B at both ends of their rotational axes, respectively. A coupling portion 141A of the damper 140A remote from the drive mechanism receiving portion 112 is rotatably connected with an element 114A on the rear plate of the airflow circulating portion 111 opposite the drive mechanism receiving portion 112, so that the damper 140A can freely rotate about the element 114A. Similarly, the coupling portion 141B of the damper 140B remote from the drive mechanism receiving portion 112 is rotatably connected with the element 114B on the rear plate of the airflow circulation portion 111 opposite the drive mechanism receiving portion 112, so that the damper 140B can freely rotate about the element 114B. Preferably, the elements 114A, 114B may be formed in a cylindrical or pin shape, or may be formed in a hollow cylindrical shape.
The coupling portions 142A, 142B of the dampers 140A, 140B, which are adjacent to the drive mechanism receiving portion 112, receive power from the drive mechanism and drive the dampers 140A, 140B to rotate so as to switch between the open and closed positions.
The drive mechanism for driving the dampers between the open and closed positions includes a drive motor 130, a reduction gear pair, damper drive wheels 150A, 150B for driving the two dampers, respectively, damper drive rods 160A, 160B, and damper drive members 170A, 170B. The underdrive gear set is used to convert the higher rotational speed of the output of the motor 130 to a lower rotational speed suitable for driving the state transition of the damper. In the illustrated embodiment, the reduction gear set includes a power source input 131 in the form of a pinion gear and power source outputs 132A, 132B in the form of reduction gears. The power source input portion 131 is connected to an output shaft of the motor 130, and is gear-coupled to the power source output portions 132A, 132B, thereby outputting torque from the motor 130 to the power source output portions 132A, 132B on both sides. In the illustrated embodiment, a primary output wheel is used for primary reduction. Reducing the number of intermediate transition wheels not only simplifies the overall structure and saves cost, but also reduces the overall size of the air supply device 100, particularly the size in the transverse direction Y.
However, in alternative embodiments, the speed reduction transmission pair may include more than one step of speed reduction transmission, i.e., include multiple power source outputs; or in another embodiment, the torque output from the drive motor is transmitted directly to the damper drivers 150A, 150B via the power source output 131 without including any speed reduction gear set therebetween. In other embodiments, the reduction gear pair may also be formed in other forms, for example in the form of a worm gear pair.
Further, in the illustrated embodiment, the rotational axis of the drive motor 130 is arranged parallel to the rotational axis of the damper drive wheels 150A, 150B, i.e., parallel to the longitudinal direction X. In alternative embodiments, the drive motors are not limited to being arranged in the longitudinal direction X (as shown in fig. 2), but may instead be arranged in the vertical direction Z or the longitudinal direction X, and the direction of the rotational axis may be changed using a bevel gear drive or a worm gear drive.
During operation of the blower, torque output by the drive motor 130 is transmitted to the respective damper drive wheels 150A, 150B via the speed reduction gear pair (power source input 131 and power source outputs 132A, 132B). The side surfaces in each of the damper drive wheels 150A, 150B are respectively provided with groove tracks arranged so that the distance in the radial direction varies in the circumferential direction (a specific structure can be seen from fig. 6A-6B). The groove tracks provided on the surfaces of the damper drive wheels 150A, 150B mate with posts 161A and 161B (shown in fig. 5A-5B) on the damper drive levers 160A and 160B, respectively, and convert rotational movement of the damper drive wheel 150 into translational movement of the damper drive levers 160A and 160B, respectively, in the lateral direction Y.
The racks 162A, 162B on the damper drive bars 160A, 160B engage the sector gears 171A, 171B on the damper drives 170A, 170B, respectively, such that the translational movement of the damper drive bars 160A, 160B is converted into rotational movement of the damper drives 170A, 170B. The damper drivers 170A, 170B include bosses 172A, 172B at one end thereof, respectively, the bosses 172A, 172B being fitted into (in particular, inserted into) the coupling portions 142A, 142B at one end of the rotational shafts of the dampers 140A, 140B, so that the damper drivers 170A, 170B can drive the dampers 140A, 140B to rotate between the open and closed positions, respectively. In the embodiment shown in fig. 2, the damper drivers 170A, 170B are formed as separate components from the dampers 140A, 140B, and the couplings 142A, 142B of the dampers 140A, 140B receive the lobes 172A, 172B of the damper drivers 170A, 170B, respectively, such that the damper drivers 170A, 170B drive the respective dampers 140A, 140B to rotate; in an alternative embodiment, the damper driver is formed with a recess and the coupling portions 142A, 142B are formed in the form of projections such that the coupling portions 142A, 142B are received in the recess of the damper driver. In the embodiment shown in fig. 2, the dampers 140A, 140B are rotated between open and closed positions, respectively, about axes parallel to the longitudinal direction X; in alternative embodiments, the dampers 140A, 140B may rotate between open and closed positions about axes in other directions (e.g., in the vertical direction Z or the lateral direction Y); in another alternative embodiment, the transition of the damper between the open and closed positions may be accomplished by other means of movement (e.g., translational movement).
As can be seen in the embodiment shown in fig. 2, the drive mechanism that transfers torque from the output of the motor 130 to the rotation of the dampers 140A, 140B has a plurality of power transfer means, including gear drives, post-groove track drives, and rack and pinion drives. In order to facilitate power transmission and reduce frictional resistance, a lubricant such as lubricating oil or grease is provided at the plurality of power transmission devices, thereby reducing loss and improving transmission efficiency.
It should be understood by those skilled in the art that the embodiment shown in FIG. 2 illustrates only one possible embodiment of a drive mechanism that drives the rotation of the dampers 140A, 140B. In alternate embodiments, any other drive mechanism capable of driving the rotation of the damper may be employed, such as, but not limited to, including additional one or more transmissions, omitting one or more transmissions, or replacing one or more of the power transfer devices shown in FIG. 2 with other transmissions.
The drive mechanism as a whole is received in the drive mechanism receiving portion 112. The drive mechanism receiving portion 112 is formed in the form of a recess, and the front end thereof is closed by the front cover 200, thereby substantially completely closing the drive mechanism in the drive mechanism receiving portion 112 without being exposed to the outside or to the airflow. In the illustrated embodiment, the front cover 200 is secured to the body portion of the frame 110 by a plurality of fasteners. The plurality of fasteners are formed in the form of a plurality of fastening screws. In other embodiments, the fasteners may be formed in other forms, such as adhesives, snap-fit connections, and the like.
Fig. 3A and 3B respectively show side views of air-blowing device 100 as viewed in a direction opposite to longitudinal direction X of air-blowing device 100. Specifically, fig. 3A shows a view of the drive mechanism viewed in the a direction in fig. 2; fig. 3B shows a view of the drive mechanism as viewed in direction B in fig. 2, with the front cover 200 removed to better illustrate the structure of the drive mechanism.
In the views of fig. 3A and 3B, the dampers 140A, 140B are both in an open state. However, dampers 140A, 140B may be in any state or combination of states during operation of blower apparatus 100.
Specifically, the drive mechanism that drives the dampers 140A, 140B between the open and closed positions is shown in fig. 3B and includes a drive motor 130, a power source input 131 (not shown in fig. 3B), power source outputs 132A, 132B, damper drive wheels 150A, 150B, damper drive rods 160A, 160B, and damper drives 170A, 170B. Specifically, the torque output by the drive motor 130 is transmitted to the damper drive wheels 150A, 150B via gear transmission of the power source input portion 131 and the power source output portions 132A, 132B. The damper drive wheels 150A, 150B have grooved tracks 151A, 151B formed on one side thereof, respectively, for receiving posts 161A, 161B (fig. 5A-5B) of the damper drive levers 160A, 160B to convert rotational movement of the damper drive wheels 150A, 150B into translational movement of the damper drive levers 160A, 160B in the lateral direction Y (fig. 2). The racks 162A, 162B on the damper drive bars 160A, 160B cooperate with the sector gears 171A, 171B of the damper drivers 170A, 170B to convert the translational movement of the damper drive bars 160A, 160B in the lateral direction Y into rotational movement of the damper drivers 170A, 170B. The rotational movement of the damper drivers 170A, 170B further drives the rotation of the dampers 140A, 140B such that the dampers 140A, 140B rotate between the open and closed positions.
Fig. 4 shows a front perspective view of the frame body 110, which shows the structure of the drive mechanism receiving portion 112. The drive mechanism receiving portion 112 is formed as a recess having a bottom plate, and the recess substantially accommodates the drive mechanism therein. A driving motor mounting portion for arranging the driving motor 130 and a driving motor fixing member 115 for fixing the driving motor 130 in place are provided on a bottom plate of the driving mechanism receiving portion 112. The bottom plate of the drive mechanism receiving portion 112 is also provided with shafts 116A, 116B for fixing the power source output portions 132A, 132B. In the embodiment shown in fig. 2, the reduction gear train comprises only one reduction, i.e. only one power source output 132A or 132B (i.e. reduction gear) for each damper, and thus only two shafts 116A, 116B for receiving the two power source outputs 132A, 132B are included in the drive mechanism receiving portion 112. In alternative embodiments, the speed reduction gear set may include multiple speed reductions, or other forms of speed reduction gear sets, in which case the components for securing the speed reduction gear sets in the speed reduction gear set may be adaptively located in the drive mechanism receptacle 112. Further, the drive mechanism receiving portion 112 includes fixing holes 120A, 120B for receiving the rotation shafts of the damper drive wheels 150A, 150B. Of course, the arrangement of the fixation holes 120A, 120B and the shafts 116A, 116B may be arranged in other ways.
Disposing the shafts 116A, 116B and the drive motor fixing member 115 on the bottom plate of the drive mechanism receiving portion 112 in the form of the recess can make the mounting process of the air blowing device 100 easier. Specifically, when the power source output portions 132A, 132B are mounted to the shafts 116A, 116B, respectively, and the motor 130 is fixed to the drive motor mounting portion by one or more drive motor fixing members 115, the entire drive mechanism is substantially accommodated in the recess and is not easily dropped out of the drive mechanism receiving portion 112; the substantially planar bezel 200 need only be simply secured to the drive mechanism receiving portion upon subsequent installation, thereby simplifying the operational complexity of the installation process.
In the illustrated embodiment, the front cover 200 is generally planar in shape, but includes a cylindrical protrusion. The shape of the projection is adapted to receive the motor 130 therein, so that the motor 130 can be accommodated with a certain height without making the length of the drive mechanism in the longitudinal direction X too large.
With continued reference to fig. 4, the drive mechanism receiving portion 112 is provided with holes 119A, 119B. The damper drivers 170A, 170B, and in particular the lobes 172A, 172B, extend through the apertures 119A, 119B and engage the couplings in the form of the recesses of the dampers 140A, 140B to thereby further transfer the torque output by the drive motor 130 to the dampers 140A, 140B, driving them to rotate between the open and closed positions. Optionally, a seal is provided between the holes 119A, 119B and the projections 172A, 172B to avoid leakage of cold air flow into the vicinity of the drive mechanism, affecting the drive efficiency.
The drive mechanism receiving portion 112 is also provided with guide groove stoppers 121A and 121B. In the assembled state of the air blowing device 100, the guide groove stopper portions 121A, 121B are engaged with guide grooves 163A, 163B (fig. 5A-5B) provided on the damper drive levers 160A, 160B to guide the translational movement of the damper drive levers 160A, 160B in the lateral direction Y.
Fig. 5A shows three views of the damper drive rod 160A. As can be seen from fig. 5A, two projections 165A are formed on the side of the damper drive lever 160A facing the airflow circulating portion 111, the two projections 165A being arranged to form a guide groove 163A therebetween, the guide groove 163A cooperating with the guide groove stopper portion 121A provided in the drive mechanism receiving portion 112, thereby defining the degree of freedom of movement of the damper drive lever 160A so that it can be translated only in the lateral direction Y to enable precise control of the rotational angle of the damper 140A. In the illustrated embodiment, the guide slot 163A extends partially through the damper drive lever 160A in the thickness direction thereof, forming a blind slot.
The damper drive lever 160 is further formed with another guide groove 163A' on the side facing away from the airflow passage 111. The other guide groove 163A' cooperates with another guide groove stopper portion (not shown) disposed on the front cover to further restrict the degree of freedom of movement of the drive lever 160A. The other guide groove 163A' is also formed in the form of a blind groove. In an alternative embodiment, the guide slots 163A and/or 163A' may extend completely through the damper drive rod 160A in the thickness direction, forming a through slot; in another alternative embodiment, there may be only one guide slot 163A or 163A' formed in the form of a blind slot.
Further, the damper drive lever 160A has a movement avoiding portion 164A at an end opposite to the guide groove 163A, the movement avoiding portion 164A serving to accommodate an end portion of the rotational shaft of the damper drive wheel 150A in the operating state of the air blowing device 100, so that the damper drive lever 160A can move in the lateral direction Y relative to the damper drive wheel 150A without interfering with the rotational shaft of the damper drive wheel 150A. Specifically, the movement avoiding portion 164A is in the form of an elongated groove such that, when the damper drive lever 160A moves in the lateral direction Y, an end portion of the rotation shaft of the damper drive wheel 150A moves in the elongated groove formed by the movement avoiding portion 164A. In the illustrated embodiment, the motion bypass portion 164A is formed in the form of a through hole that extends through the damper drive lever 160A; alternatively, the movement avoiding portion 164A may be formed in the form of a blind hole. Preferably, the height of the movement bypass portion 164A in the vertical direction Z is slightly larger than the diameter of the end of the rotation shaft of the damper drive wheel 150A so that when the end can move in the movement bypass portion 164A without hindrance; alternatively, the height of the movement bypass portion 164A in the vertical direction Z is substantially equal to the diameter of the end of the rotational shaft of the damper drive wheel 150A, so that the cooperation of the end and the movement bypass portion 164A can further contribute to the guidance of the damper drive lever 160A in the lateral direction Y.
Fig. 5B shows three views of the damper drive rod 160B. The damper drive rod 160B is of a substantially symmetrical construction to the damper drive rod 160A and cooperates with corresponding components in a similar manner and will not be described in detail herein.
The cooperation of the guide slots 163A, 163B and the guide slot stoppers 121A, 121B, and/or the cooperation of the further guide slots 163A ', 163B' and the further guide slot stoppers, in addition to facilitating the guiding of the damper drive levers 160A, 160B in the transverse direction Y, also facilitates a further reduction in the length of the drive mechanism in the longitudinal direction X. Further, providing the movement escape portions 164A, 164B on the damper drive levers 160A, 160B for receiving the ends of the rotary shafts of the damper drive wheels helps to further reduce the length of the drive mechanism in the longitudinal direction X, thereby further reducing the longitudinal length and overall size of the entire air blowing device 100.
Fig. 6A shows a top view and a front view of the damper drive wheel 150A. The damper drive wheel 150A has a recessed track 151A for receiving and driving a post 161A of the damper drive lever 160A. In the illustrated embodiment, the center of rotation of the groove track 151A coincides with the axis of rotation of the damper drive wheel 150A. Specifically, groove track 151A has two different track radii R1 and R2. When the post 161A of the damper drive lever 160A is at a position of track radius R1 in the pocket track 151A, the damper 140A is in the closed position; when the post 161A of the damper drive lever 160A is at a position of track radius R2 in the pocket track 151A, the damper 140A is in the open position.
Similarly, fig. 6B shows a top view and a front view of the damper drive wheel 150B. The damper drive wheel 150B has a recessed track 151B for receiving and driving a post 161B of the damper drive lever 160B. Specifically, the notched tracks 151A and 151B have different shapes, so that when the damper drive wheels 150A, 150B are driven to rotate, the damper 140A and the damper 140B are driven in different ways, achieving a plurality of state combinations. The center of rotation of the groove track 151B coincides with the axis of rotation of the damper drive wheel 150B. Specifically, groove track 151B has two different track radii R3 and R4. When the post 161B of the damper drive lever 160B is at the position of the track radius R3 in the groove track 151B, the damper 140B is in the closed position; when the post 161B of the damper drive lever 160B is at the position of the track radius R4 in the groove track 151B, the damper 140B is in the open position.
In the preferred embodiment, the radii R1 are equal to R3, the radii R2 are equal to R4, and the drive mechanisms that drive the dampers 140A and 140B are arranged symmetrically with respect to the longitudinal direction X as a whole with respect to the motor 130 and the power source input gear 131, so that the dampers 140A and 140B rotate through the same angle when switching between the open and closed positions.
The table set forth in FIG. 7 shows the condition of the damper drive levers 160A, 160B and the damper drive wheels 150A, 150B when the conditions of the dampers 140A and 140B are combined. In fig. 7, the frame 110 is omitted to specifically show the relative states of the damper drive wheel, the damper drive lever, and the damper.
Fig. 7 shows a view from the front to the rear in the longitudinal direction X, showing a plurality of states in which the notched rail 151A of the damper drive wheel 150A is engaged with the damper drive lever 160A, and showing a plurality of states in which the notched rail 151B of the damper drive wheel 150B is engaged with the damper drive lever 160B. In the view of FIG. 7, although the posts 161A, 161B on the damper drive levers 160A, 160B are not visible between the damper drive levers and the damper drive wheels, the positions of the posts 161A, 161B in the groove tracks are schematically illustrated in bold circles for clarity of illustration of the mating relationship. It should be understood that the illustrated posts 161A, 161B are for illustrative purposes only, and are in no way limiting as to the size and/or location of the posts.
A plurality of state combinations of the dampers 140A and 140B are described below with reference to fig. 7.
In the first state, both the damper drive wheels 150A, 150B are in the initial state, i.e., the damper drive wheels 150A, 150B are rotated by an angle of 0 ° with respect to the initial position. The initial position described herein refers to the position of the posts 161A, 161B at the initial end in the groove tracks 151A, 151B. At this time, the post 161A is at a position of radius R1 in the groove track 151A, the post 161B is at a position of radius R3 in the groove track 151B, and both dampers 140A, 140B are in the closed position, so that no airflow exits via the airflow outlets 101A, 101B.
In the second state, the damper drive wheel 150A is rotated by α 1 with respect to the first state, i.e., the damper drive wheel 150A is rotated by an angle α 1 with respect to the initial position; the damper drive wheel 150B rotates by β 1 with respect to the first state, i.e., the damper drive wheel 150B rotates by an angle β 1 with respect to the initial position. At this time, the post 161A transitions from a position of radius R1 to a position of radius R2 in the groove track 151A, and the post 161B remains at a position of radius R3 in the groove track 151B; the damper 140A thus transitions from the closed position to the open position, with the damper 140B still in the closed position, with airflow exiting through the airflow outlet 101A.
In the third state, the damper drive wheel 150A is rotated by α 2 with respect to the second state, i.e., the damper drive wheel 150A is rotated by an angle α 1+ α 2 with respect to the initial position; the damper drive wheel 150B rotates by β 2 with respect to the second state, i.e., the damper drive wheel 150B rotates by an angle β 1+ β 2 with respect to the initial position. At this point, post 161A is still at radius R2 in groove track 151A, and 161B transitions from radius R3 to radius R4 in groove track 151B; the damper 140A is thus still in the open position and the damper 140B transitions from the closed position to the open position, at which point the airflow exits via the airflow outlets 101A, 101B.
In the fourth state, the damper drive wheel 150A is rotated by α 3 with respect to the third state, i.e., the damper drive wheel 150A is rotated by an angle α 1+ α 2+ α 3 with respect to the initial position; the damper drive wheel 150B rotates by β 3 with respect to the third state, i.e., the damper drive wheel 150B rotates by an angle β 1+ β 2+ β 3 with respect to the initial position. At this time, the post 161A transitions from the position of radius R2 to the position of radius R1 in the groove track 151A, and the post 161B remains at the position of radius R4 in the groove track 151B; the damper 140A thus transitions from the open position to the closed position, and the damper 140B remains in the closed position, with airflow exiting through the airflow outlet 101B.
Table 1 summarizes the relevant parameters for the four operating states of air supply device 100 and the states of the various dampers according to the embodiment shown in fig. 7.
TABLE 1 four operating states of the blower 100
Figure BDA0001267398000000201
FIG. 7 illustrates a plurality of alternative states for the damper groups 140A, 140B. In accordance with the summary of table 1, and with reference to the multiple-state embodiment shown in fig. 7, the damper sets 140A, 140B change from one state to another for each angular rotation of the damper drive wheel sets 150A, 150B. In a preferred embodiment, when the damper group is switched between each two states, each of the damper drive wheels 150A, 150B rotates through the same angle, i.e., α 1, α 2, α 3 are the same angle, and β 1, β 2, β 3 are the same angle, respectively; in a preferred embodiment, the power source outputs 132A, 132B, and the damper drive wheels 150A, 150B are symmetrically arranged with respect to the rotational axis of the motor 130 such that both damper drive wheels 150A, 150B rotate through the same angle, i.e., α 1 is the same as β 1, α 2 is the same as β 2, and α 3 is the same as β 3, each time the damper group is switched between the two states. In alternative embodiments, the angle through which the damper groups are rotated when switching between different states may not be fixed, i.e., α 1, α 2, α 3 may not be the same, or β 1, β 2, β 3 may not be the same; alternatively, the damper drive wheels 150A, 150B rotate through different angles when the damper groups are switched between different states, i.e., α 1 is not the same as β 1, or α 2 is not the same as β 2, or α 3 is not the same as β 3.
In the illustrated embodiment, only one damper is actuated and the other damper remains in place during each switching of the damper group. For example, when the damper group switches from the first state to the second state, only damper 140A is actuated; when the damper group is switched from the second state to the third state, only the damper 140B is actuated; when the damper group is switched from the third state to the fourth state, only the damper 140A is actuated. Therefore, when the state of the air door group is switched each time, the radius of the groove track where only one column is located is changed, and the radius of the groove track where the other column is located is not changed. Therefore, according to the sequential change of the radius of the groove track where the two columns are located, four working states of the air door group of the air supply device 100 are realized. Only one air door acts (namely the state is changed) when the state of the air door group is switched every time, so that the torque loss output by the motor is small. Thus, a motor with smaller power and smaller volume can be adopted for driving the state switching of the air door group, so that the whole volume of the air supply device 100 is more compact; meanwhile, the torque for driving the state change of the air door is small, and the torque born by the driving mechanism for outputting the torque of the motor 130 to the rotation of the air doors 140A and 140B is low, so that the driving mechanism is not easy to damage, and the service life is prolonged.
In an alternative embodiment, a scheme may be employed in which simultaneous actuation of the two dampers 140A, 140B is achieved for each state switching. The scheme can more flexibly configure the sequence among various air door states of the air supply device; however, this will cause the power consumed by the opening and closing of the two dampers to increase, thereby increasing the power required to be output by the motor, potentially increasing the cost and size of the motor.
In the aspect of the present invention, in the air blowing device 100, the two damper drive wheels 150A, 150B are symmetrically arranged with respect to the drive motor 130, and are driven by the only one drive motor 130. The single motor is adopted to simultaneously control the state combination of the two air doors, so that the cost can be reduced, and a simpler refrigerator control program can be realized.
During rotation of the damper drive wheels 150A, 150B driving the damper drive levers 160A, 160B, and thus the dampers 140A, 140B, the notched tracks 151A, 151B of the damper drive wheels 150A, 150B will exert a component of force on the posts 161A, 161B in the vertical direction Z, thereby causing the damper drive levers 160A, 160B to have a tendency to move away from the lateral direction Y. The cooperation of the guide slots 163A, 163B on the damper drive levers 160A, 160B with the guide slot stops 121A, 121B on the frame 110, and/or the cooperation of the other guide slot 163A ', 163B' on the damper drive levers 160A, 160B and the other guide slot stop on the front cover 200 further helps to resist the tendency of the damper drive levers to move away from the lateral direction Y to maintain proper operation of the damper drive levers.
Referring again to fig. 7, in the first state, the dampers 140A, 140B are both in the closed position, and the posts 161A, 161B are both in the initial end position in the recessed tracks 151A, 151B. The starting end is optionally designed so that the posts 161A, 161B can self-lock in place (e.g., hook radially inward), preventing the damper from automatically rotating toward the open position. In particular, this initial end achieves the self-locking function of the post by limiting the translation of the damper drive rod in the transverse direction Y.
With continued reference to FIG. 7, as the damper drive wheel 150A controls the closing and opening of the damper 140A, the groove track 151A varies between radii R1 and R2. The damper drive wheel 150A receives torque from the drive motor 130, and outputs the torque to the damper 140A via the damper drive lever 160A. The torque output by the damper drive wheel 150A is constant and R1> R2, so that as the post 161A on the damper drive lever moves closer to radius R2, the shorter the moment arm of the post from the center of the damper drive wheel 150A, and thus the greater the force generated; as the post 161A on the damper drive lever moves closer to the radius R1, the longer the moment arm of the post from the center of the damper drive wheel 150A, and thus the less force generated.
Similarly, the damper drive wheel 150B controls the closing and opening of the damper 140B, the groove track 151B varies between radii R3 and R4. The damper drive wheel 150B receives torque from the motor 130 and outputs the torque to the damper 140B via the damper drive lever. The torque output by the damper drive wheel 150B is constant and R3> R4, so that as the post 161B on the damper drive lever moves closer to radius R4, the shorter the moment arm of the post from the center of the damper drive wheel 150B, and thus the greater the force generated; as the post 161B on the damper drive lever moves closer to the radius R3, the longer the moment arm of the post from the center of the damper drive wheel 150B and thus the less force is generated.
Thus, as the dampers 140A, 140B approach the closed position, the less force is transferred to the posts 161A, 161B; the greater the force transferred to the posts 161A, 161B as the dampers 140A, 140B approach the open position.
Fig. 8 schematically illustrates a side view of the open and closed positions of the dampers 140A, 140B, showing the drive mechanism from a rear-to-front view along the longitudinal direction X (along direction a in fig. 2). The damper 140A is rotated between the open and closed positions by an angle θ A The damper 140B is rotated between the open and closed positions by an angle θ B . In a preferred embodiment, θ A And theta B Are equal. As shown in fig. 8, θ A /θ B Is an acute angle of less than 90 deg.. Preferably, θ A /θ B In the range of 70 to 90. More preferably, θ A /θ B Set at an angle of 80 deg.. If the rotation angle theta of the air door is changed A /θ B If the air flow is too small (for example, less than 70 °), the length of the air door increases, the self weight of the air door increases, and the increase in the length of the air door increases the moment of the driving part required for opening and closing the air door when the air door is pushed by wind power; further, as the length of the door panel increases, the overall distance of the air supply device in the flow direction of the air current increases, resulting in an increase in volume, there may be a problem of material waste in the actual production process, and the force transmitted to the end of the damper may be small due to the long length of the door panel, making it difficult to ensure a good seal of the damper at the end. If the rotation angle theta of the air door is changed A /θ B Selection of an oversize (e.g., greater than 90 °) may result in increased engagement travel between the transmissions (e.g., the damper drive rod 160A and the damper drive 170A, and the damper drive rod 160B and the damper drive 170B) in the drive mechanism (e.g., the damper drive wheels 150A, 150B and/or the damper drive rods 160A, 160B may be sized to provide forLarger), further leading to an increase in the overall volume of the air-blowing device 100, particularly in the length in the lateral direction Y. When the rotation angle of the air door is too large, the moving distance of the air door driving rod (and the rack on the air door driving rod) is lengthened, and meanwhile, the radius change rate of the groove track on the surface of the air door driving wheel changes steeply due to the increase of the moving distance of the rack, so that the torque loss of the motor is increased when the door panel is in a switching state. Thus, the damper rotates by an angle θ A /θ B The reasonable selection of the motor can realize the minimum torque loss of the motor and reduce the volume of the air supply device 100.
With continued reference to fig. 8, the damper 140A includes a panel 143A and a seal 144A disposed on a surface of the panel 143A. The surface of the panel 143A opposite to the seal 144A is optionally provided with a recess structure having a bead, so that it is possible to reduce the material required to manufacture the damper 140A, reduce the weight of the damper 140A, and thus reduce the power/torque required to rotate the damper, while securing the strength of the damper 140A. The frame body 110 includes a convex edge 122A defining the shape of the air flow outlet 101A at the side where the air flow outlet 101A is formed. As can be seen in fig. 2, the raised edge 122A is generally rectangular in shape, thereby defining a generally rectangular shaped airflow outlet 101A. Under the closed position of the damper 140A, the seal 144A engages the generally rectangular shaped raised edge 122A and is partially compressed by the raised edge 122A, thereby completely closing the airflow passage 101A.
Similarly, the damper 140B, and the engagement of the damper 140B with the raised edge 122B, may also be accomplished in a similar manner and will not be described in further detail herein. However, in alternative embodiments, the damper 140B may be a different size or shape than the damper 140A.
In the illustrated embodiment, when the dampers 140A, 140B are switched from the closed position to the open position, both dampers rotate inwardly of the frame 110, without extending beyond the frame 110, when the airflow blows against the panels 143A, 143B tending to resist opening of the dampers; and as the damper transitions from the open position to the closed position, the airflow tends to press the damper further toward the corresponding raised edge, which helps to effect a seal between the damper and the corresponding raised edge when in the closed position. As described above, the engagement of the notched tracks 151A, 151B of the damper drive wheels 150A, 150B and the posts 161A, 161B of the damper drive levers 160A, 160B is achieved as follows: the less force is transferred to the posts 161A, 161B as the dampers 140A, 140B approach the closed position; the greater the force transferred to the posts 161A, 161B as the dampers 140A, 140B approach the open position. Thus, as the damper tends to transition to the open position, the greater force transferred to the posts 161A, 161B helps overcome the resistance to airflow; while the air flow tends to urge the damper toward the closed position as it tends to transition toward the closed position, further facilitating the closing and sealing of the damper, the simultaneous transfer of less force from the posts 161A, 161B prevents the damper from striking the corresponding raised edges with a greater impact force, somewhat reducing noise.
In an alternative embodiment, the damper may be arranged such that when the damper is in the closed condition, the airflow tends to urge the damper towards the open position. In such an embodiment, the meshing angle of the sector gears 171A, 171B may be set to be greater than the angle θ through which the dampers 140A, 140B rotate when closed A /θ B So that the sector gear can further drive the damper to press towards the closing direction after the damper reaches the closed position, thereby realizing tighter sealing.
In the air blowing device 100 according to the exemplary embodiment of the present invention, the driving mechanism for driving the dampers 140A, 140B to switch between the open position and the closed position is completely received in the recess of the driving mechanism receiving portion 112, and the recess is closed by the front cover 200, so that the driving mechanism is accommodated in the substantially closed space and is completely isolated from the airflow circulating portion 111 for airflow circulation, thereby avoiding the airflow from directly blowing toward the driving mechanism.
Such an arrangement of the air supply device 100 achieves complete separation of the air flow circulating portion from the driving mechanism, thereby preventing the driving mechanism from being exposed to the flow of the cool air. As described above, at the plurality of power transmission devices of the drive mechanism and the joints thereof, a lubricant such as lubricating oil or grease may be provided to facilitate the transmission of power and reduce friction, improving efficiency; the power transmission mechanism is prevented from being exposed in cold airflow so that the lubricant cannot be volatilized too fast due to the direct blowing of the airflow, thereby avoiding the unsmooth operation or the generation of noise of the power transmission mechanism caused by the lack of the lubricant and maintaining good lubricating conditions of the driving mechanism and the efficient transmission of the power. Therefore, such an arrangement can improve the working efficiency of the air supply device 100 and prolong the service life thereof.
In the illustrated embodiment, the elements in the drive mechanism of the air blowing device 100 are mostly symmetrical members arranged symmetrically. In the actual production process, the production, manufacturing and processing processes of the symmetrical components are simple, and the manufacturing time and cost can be greatly shortened. In addition, the installation process of the symmetrical part is simpler, and errors are not easy to occur.
Fig. 9-11 show various views of a drive mechanism for an air-moving device in accordance with another embodiment of the invention.
Specifically, fig. 9A shows two perspective views and three plan views of the damper drive lever 1160A, specifically illustrating the structure of the damper drive lever 1160A; FIG. 9B shows two perspective and three plan views of the damper drive lever 1160B, specifically illustrating the structure of the damper drive lever 1160B.
As can be seen from fig. 9A, two projections 1165A are formed on the side of the damper drive lever 1160A facing the airflow circulating portion 111, the two projections 1165A are arranged to form a guide groove 1163A therebetween, and the guide groove 1163A cooperates with the guide groove stopper portion 121A provided in the drive mechanism receiving portion 112, thereby defining the degree of freedom of movement of the damper drive lever 1160A so that it can be translated only in the lateral direction Y to enable precise control of the rotation angle of the damper 1140A. In the illustrated embodiment, the guide groove 1163A extends partially through the damper drive lever 1160A in the thickness direction thereof, in the form of a blind groove.
The damper drive lever 1160 is further formed with another guide groove 1163A' on a side surface facing away from the airflow passing portion 111. The other guide groove 1163A' cooperates with another guide groove stopper portion (not shown) provided on the front cover to further restrict the degree of freedom of movement of the drive lever 1160A. The other guide groove 1163A' is also formed in the form of a blind groove. In an alternative embodiment, the guide slots 1163A and/or 1163A' may extend entirely through the damper drive bar 1160A in the thickness direction, forming a through slot; in another alternative embodiment, there may be only one guide groove 1163A or 1163A' formed in the form of a blind groove.
Further, the damper drive lever 1160A also has a motion avoidance portion 1164A for accommodating an end portion of the rotational shaft of the damper drive wheel 1150A in an operating state of the air blowing device 100, so that the damper drive lever 1160A can move in the lateral direction Y with respect to the damper drive wheel 1150A without interfering with the rotational shaft of the damper drive wheel 1150A. Specifically, the motion avoiding portion 1164A is in the form of an elongated groove, so that when the damper drive lever 1160A moves in the lateral direction Y, an end portion of the rotation shaft of the damper drive wheel 1150A moves in the elongated groove formed by the motion avoiding portion 1164A. In the illustrated embodiment, the motion bypass portion 1164A is formed as a through-hole through the damper drive lever 1160A; alternatively, the movement avoiding portion can also be formed in the form of a blind hole. Preferably, the height of the motion avoiding portion 1164A in the vertical direction Z is slightly larger than the diameter of the end portion of the rotation shaft of the damper drive wheel 1150A so that when the end portion can move in the motion avoiding portion 1164A without hindrance; alternatively, the height of the motion bypass portion 1164A in the vertical direction Z is substantially equal to the diameter of the end of the rotational shaft of the damper drive wheel 1150A, so that the cooperation of the end and the motion bypass portion 1164A can further contribute to the guidance of the damper drive lever 1160A in the lateral direction Y.
Fig. 9B shows three views of the damper drive lever 1160B. The damper drive lever 1160B is of a substantially symmetrical configuration to the damper drive lever 1160A and cooperates with corresponding components in a similar manner and will not be described in detail herein.
The damper drive levers 1160A, 1160B of fig. 9A-9B have changed positions of the posts 1161A, 1161B as compared to the damper drive levers 160A, 160B shown in fig. 5A-5B.
Taking the damper drive levers 160A, 1160A as an example, specifically, in the view of fig. 5A, the post 161A is located between the rack 162A and the motion bypass 164A, such that when the damper 140A is in the closed position, the post 161A is further from the rotational axis of the damper drive wheel, i.e., the radius (R1) is larger at the notched track 151A where the post 161A is located, and when the damper 140A is in the open position, the post 161A is closer to the rotational axis of the damper drive wheel, i.e., the radius (R2) is smaller at the notched track 151A where the post 161A is located. In contrast, in the view of fig. 9A, the post 1161A and the rack 1162A are located at both ends of the movement avoiding portion 1164A, respectively. Referring to FIG. 11, it can be seen that when damper 1140A is in the closed position, post 1161A is closer to the axis of rotation of the damper drive wheel, i.e., the radius (R11) at notch track 1151A of post 1161A is smaller, and when damper 1140A is in the open position, post 1161A is further from the axis of rotation of the damper drive wheel, i.e., the radius (R12) at notch track 1151A of post 1161A is larger.
The same is true for the arrangement of the posts 1161B and the motion bypass 1164B on the damper drive wheel 1150B. Specifically, in the view of fig. 9B, the column 1161B and the rack 1162B are located at both ends of the movement avoiding portion 1164B, respectively. Referring to FIG. 11, it can be seen that when the damper 1140B is in the closed position, the post 1161B is closer to the axis of rotation of the damper drive wheel, i.e., the radius (R13) at the notch track 1151B where the post 1161B is located, is smaller, and when the damper 1140B is in the open position, the post 1161B is further from the axis of rotation of the damper drive wheel, i.e., the radius (R14) at the notch track 1151B where the post 1161B is located, is larger.
Fig. 10A shows a top view and a front view of the damper drive wheel 1150A. The damper drive wheel 1150A has a recessed track 1151A for receiving and driving the post 1161A of the damper drive lever 1160A. In the illustrated embodiment, the center of rotation of the groove track 1151A coincides with the axis of rotation of the damper drive wheel 1150A. Specifically, groove track 1151A has two different track radii R11 and R12. When the post 1161A of the damper drive lever 1160A is at a position with a track radius R11 in the groove track 1151A, the damper 1140A is in the closed position; when the post 1161A of the damper drive lever 1160A is at a position with a track radius R12 in the groove track 1151A, the damper 1140A is in the open position.
Similarly, fig. 10B shows a top view and a front view of the damper drive wheel 1150B. The damper drive wheel 1150B has a recessed track 1151B for receiving and driving the post 1161B of the damper drive lever 1160B. Specifically, the groove tracks 1151A and 1151B have different shapes so that as the damper drive wheels 1150A, 1150B are driven to rotate, the damper 1140A and the damper 1140B are driven in different ways, enabling multiple state combinations. The center of rotation of the groove track 1151B coincides with the axis of rotation of the damper drive wheel 1150B. Specifically, groove track 1151B has two different track radii R13 and R14. When the post 1161B of the damper drive lever 1160B is at a position in the groove track 1151B with a track radius R13, the damper 1140B is in the closed position; when the post 1161B of the damper drive lever 1160B is at a position with a track radius R14 in the groove track 1151B, the damper 1140B is in the open position.
In a preferred embodiment, radii R11 are equal to R13, radii R12 are equal to R14, and the drive mechanism that drives dampers 1140A and 1140B is symmetrically arranged with respect to the longitudinal direction X as a whole relative to motor 1130 and power source input gear 1131 so that dampers 1140A and 1140B rotate through the same angle when transitioning between open and closed positions.
The table set forth in FIG. 11 shows the condition of the damper drive levers 1160A, 1160B and the damper drive wheels 1150A, 1150B for a combination of conditions for the dampers 1140A and 1140B. In the drawings, the frame body is omitted to specifically show the relative states of the damper drive wheel, the damper drive lever, and the damper.
A view from the front to the rear in the longitudinal direction X is shown in fig. 11, showing a plurality of states in which the groove rail 1151A of the damper drive wheel 1150A is engaged with the damper drive lever 1160A, and showing a plurality of states in which the groove rail 1151B of the damper drive wheel 1150B is engaged with the damper drive lever 1160B. In the view of FIG. 11, although the posts 1161A, 1161B on the damper drive levers 1160A, 1160B are not visible between the damper drive lever and the damper drive wheel, the positions of the posts 1161A, 1161B in the groove tracks are schematically illustrated in bold circles for clarity of illustration of the mating relationship. It should be understood that the posts 1161A, 1161B shown are for illustrative purposes only and are not intended to limit the size and/or location of the posts in any way.
During the transition of the multiple state combinations of dampers 1140A and 1140B shown in fig. 11, the motor 130 drives the damper drive wheels 1150A, 1150B to rotate in different directions (e.g., may rotate clockwise and counterclockwise). Specifically, during each state switching of the damper group, the damper drive wheel 1150A rotates through a different angle, and the damper drive wheel 1150B rotates through a different angle; it is preferred that the damper drive wheel 1150A and the damper drive wheel 1150B rotate through the same angle each time the damper group is switched between the two states. In an alternative embodiment, the damper drive wheel 1150A may rotate in a different direction and the damper drive wheel 1150B may also rotate in a different direction during multiple state transitions of the damper group. For example, when the damper groups 1140A, 1140B are switched from the first state to the second state, the damper drive wheel 1150A rotates counterclockwise (as viewed in direction B in fig. 2, the same applies below), and the damper drive wheel 1150B rotates counterclockwise; when the damper groups 1140A, 1140B are switched from the second state to the third state, the damper drive wheel 1150A rotates clockwise and the damper drive wheel 1150B rotates clockwise; when the damper groups 1140A, 1140B are switched from the third state to the fourth state, the damper drive wheel 1150A rotates clockwise and the damper drive wheel 1150B rotates clockwise. Accordingly, the motor control program may be programmed to cause the motor to operate in a desired manner to achieve a desired manner of rotation of the damper drive wheel, and a corresponding desired change in state of the damper.
In such an embodiment, the shape of the grooved tracks may be more flexibly configured and the manner in which the dampers 1140A, 1140B of the blower device may be changed in position, although the motor programming may be more complex. In particular, the program of the motor can be modified according to the actual need, so that the motor driving program can be modified without changing the structure of the driving mechanism, in particular without changing the shape of the groove tracks 1151A, 1151B, so as to realize different state change sequences of the damper groups.
With continued reference to fig. 11, as the damper drive wheel 1150A controls the closing and opening of the damper 1140A, the groove track 1151A varies between radii R11 and R12. The damper drive wheel 1150A receives torque from the drive motor and outputs the torque to the damper 1140A via the damper drive lever. The torque output by the damper drive wheel 1150A is constant and R11< R12, so that as the post 1161A on the damper drive lever moves closer to the radius R11, the shorter the moment arm of the post from the center of the damper drive wheel 1150A, and thus the greater the force generated; as the post 1161A on the damper drive lever moves closer to the radius R12, the longer the moment arm of the post from the center of the damper drive wheel 1150A and thus the less force generated.
Similarly, the damper drive wheel 1150B controls the closing and opening of the damper 1140B, the groove track 1151B varies between radii R13 and R14. The damper drive wheel 1150B receives torque from the drive motor and outputs the torque to the damper 1140B via the damper drive lever. The torque output by the damper drive wheel 1150B is constant and R13< R14, so that as the post 1161B on the damper drive lever moves closer to the radius R13, the shorter the moment arm of the post from the center of the damper drive wheel 1150B, and thus the greater the force generated; as the post 1161B on the damper drive lever moves closer to the radius R14, the longer the moment arm of the post from the center of the damper drive wheel 1150B and thus the less force generated.
Thus, the greater the force transferred to the posts 1161A, 1161B as the dampers 1140A, 1140B approach the closed position; as the dampers 1140A, 1140B approach the open position, less force is transferred to the posts 1161A, 1161B. The air door structure has the advantages that large force is applied when the air door is closed, the air door can be guaranteed to be tightly pressed with the raised edge of the air door frame, and the air door and the raised edge are guaranteed to be well sealed under the closed position of the air door.
Fig. 12A and 12B schematically illustrate the forces applied to the post 1161A at different positions as it moves in the groove track 1151A. The plurality of different positions are indicated at L1-L6, and the trend of the force applied to the post 1161A at the plurality of different positions L1-L6 is shown in FIG. 12B. The trend of the force applied to the post 1161A described above as a function of the position of the post in the groove track 1151A can be seen in fig. 12A-12B.
The above description is intended to be illustrative of the present invention and not to limit the scope of the invention, which is defined by the claims appended hereto.
Those skilled in the art will appreciate that various features of the various embodiments of the invention described hereinabove may be omitted, added to, or combined in any manner, respectively. For example, the alternative embodiment of the drive mechanism for driving the damper described with reference to FIGS. 9-12 may be used in conjunction with the preferred embodiment of air supply apparatus 100 described with reference to FIGS. 1-8; the sequence of changing the state of the damper groups 1140A, 1140B driven by the damper drive wheels 1150A, 1150B may be applied to the air-supplying apparatus 100 of fig. 1-8 instead of the sequence of changing the state of the damper groups driven by the damper drive wheels 150A, 150B, or vice versa. Any combination of these aspects is not beyond the scope of the present invention.
While the invention has been shown and described with reference to various embodiments, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the scope of the invention as defined by the appended claims.

Claims (24)

1. An air supply device (100) for an air-cooled refrigerator,
it is characterized in that the preparation method is characterized in that,
the air supply device (100) comprises:
a frame body (110) including an airflow circulation part (111) and a drive mechanism receiving part (112),
a fan (500) received at the airflow circulating part (111) for drawing an airflow from the cold air forming device and guiding the airflow to the airflow passage,
a first damper (140A) mounted at one end of the frame (110) in the transverse direction (Y) and switchable between an open position and a closed position to control the passage of the air flow through the first outlet (101A),
a second damper (140B) mounted on the other end of the frame (110) opposite the first damper in the transverse direction (Y) and switchable between an open position and a closed position to control the passage of the air flow through the second outlet (101B),
a drive mechanism for driving the switching of the first and second dampers between the open and closed positions, and the drive mechanism is received in the drive mechanism receiving portion (112),
the drive mechanism receiving part (112) and the airflow circulating part (111) are separated from each other,
the drive mechanism includes a first damper drive wheel (150A) for driving the first damper (140A), and a first damper drive lever (160A), a second damper drive wheel (150B) for driving the second damper (140B), and a second damper drive lever (160B),
wherein the content of the first and second substances,
the first damper drive lever (160A) includes a first motion bypass portion (164A), the first motion bypass portion (164A) receiving one end of a rotational shaft of the first damper drive wheel (150A), and/or,
the second damper drive lever (160B) includes a second motion avoidance portion (164B), and the second motion avoidance portion (164B) receives one end of the rotation shaft of the second damper drive wheel (150B).
2. Air supply arrangement (100) according to claim 1,
the first damper (140A) includes a first panel (143A) and a compressible first seal (144A) disposed on a surface of the first panel, and/or
The second damper (140B) includes a second panel (143B) and a compressible second seal (144B) disposed at a surface of the second panel.
3. An air supply arrangement (100) according to claim 2,
the frame (110) comprises, at one end thereof in the transverse direction (Y), a first raised edge (122A) defining the shape of a first airflow outlet (101A), said first raised edge (122A) engaging and compressing, in the closed position of the first damper, the first seal (144A) to close the first airflow outlet, and/or
The frame (110) comprises, at its other end in the transverse direction (Y), a second raised edge (122B) defining the shape of a second airflow outlet (101B), said second raised edge (122B) engaging and compressing said second seal (144B) in the closed position of the second damper to close said second airflow outlet.
4. Air supply arrangement (100) according to claim 1,
each of the first damper (140A) and the second damper (140B) is arranged such that, when it is switched from a closed position to an open position, each of the first damper and the second damper rotates inward of the frame without extending out of the frame.
5. Air supply arrangement (100) according to claim 1,
the driving mechanism also comprises a driving motor (130), a speed reduction transmission pair, a first air door driving piece (170A) used for driving the first air door (140A), a second air door driving piece (170B) used for driving the second air door (140B),
the reduction transmission pair comprises at least one stage of reduction transmission.
6. An air supply arrangement (100) according to claim 5,
the first damper driving wheel (150A), the first damper driving rod (160A) and the first damper driving piece (170A) for driving the first damper (140A), and the second damper driving wheel (150B), the second damper driving rod (160B) and the second damper driving piece (170B) for driving the second damper (140B) are mirror-symmetrical relative to the longitudinal axis (X) of the air supply device (100).
7. An air supply arrangement (100) according to claim 5,
the reduction gear train is a gear train and includes a power source input (131) in the form of a pinion gear, and a first power source output (132A) and a second power source output (132B) for driving the first damper (140A) and the second damper (140B), respectively, the first power source output (132A) and the second power source output (132B) being in the form of reduction gears,
used for driving first throttle drive wheel (150A), first throttle actuating lever (160A), first throttle driving piece (170A) and first power supply output (132A) of first throttle (140A), and be used for the drive second throttle drive wheel (150B), second throttle drive pole (160B), second throttle driving piece (170B) and second power supply output (132B) of second throttle (140B), for longitudinal axis (X) mirror symmetry of air supply arrangement (100).
8. An air supply arrangement (100) according to claim 5,
the first damper driving wheel (150A) is provided at a side thereof with a first groove rail (151A), and the second damper driving wheel (150B) is provided at a side thereof with a second groove rail (151B),
the first damper drive lever (160A) is provided with a first post (161A) that mates with the first groove track,
the second damper actuation lever (160B) is provided with a second post (161B) which mates with the second groove track,
the first groove track (151A) is arranged to vary in radius in a circumferential direction of the first damper drive wheel (150A) such that when the first damper drive wheel (150A) is rotated via torque output by a drive motor, the first groove track (151A) drivingly engages the first post (161A) for translation, thereby further driving movement of the first damper (140A),
the second groove track (151B) is arranged to vary in radius in a circumferential direction of the second damper drive wheel (150B) such that when the second damper drive wheel (150B) is rotated via a torque output by a drive motor, the second groove track (151B) drivingly engages the second post (161B) for translation, thereby further driving movement of the second damper (140B).
9. An air supply arrangement (100) according to claim 8,
the first damper drive lever (160A) further includes a first rack gear (162A), the first rack gear (162A) engaging a sector gear (171A) of a first damper drive member (170A) to convert translational movement of the first damper drive lever (160A) into rotational movement of the first damper (140A), and
the second damper drive lever (160B) further includes a second rack gear (162B), the second rack gear (162B) engaging a sector gear (171B) of a second damper drive member (170B) to convert translational movement of the second damper drive lever (160B) into rotational movement of the second damper (140B).
10. An air supply arrangement (100) according to claim 9,
the meshing angle of the sector gear (171A) of the first damper driver (170A) is greater than the angle of rotation of the first damper between the open and closed positions, and/or
The meshing angle of the sector gear (171B) of the second damper driver (170B) is greater than the angle of rotation of the second damper between the open and closed positions.
11. An air supply arrangement (100) according to claim 8,
the axis of rotation of the first groove track (151A) coincides with the axis of rotation of the first damper drive wheel (150A), and/or
The rotational axis of the second groove track (151B) coincides with the rotational axis of the second damper drive wheel (150B).
12. Air supply arrangement (100) according to claim 5,
the first damper drive lever (160A) includes a first guide groove (163A) that cooperates with a first guide groove stopper (121A) disposed in the drive mechanism receiving portion (112) to guide translation of the first damper drive lever (160A) in a lateral direction (Y), and/or
The second damper drive lever (160B) includes a second guide groove (163B) that cooperates with a second guide groove stopper portion (121B) disposed at the drive mechanism receiving portion (112) to guide translation of the second damper drive lever (160B) in the lateral direction (Y).
13. An air supply arrangement (100) according to claim 8,
the first post (161A) is positioned at a first radius (R1) in the first groove track (151A) when the first damper (140A) is in a closed position, the first post (161A) is positioned at a second radius (R2) in the first groove track (151A) when the first damper (140A) is in an open position, the first radius being greater than the second radius such that a force exerted on the first post (161A) when the first damper is in a closed position is less than a force exerted on the first post (161A) when the first damper is in an open position, and/or
The second post (161B) is positioned at a third radius (R3) in the second groove track (151B) when the second damper (140B) is in the closed position, and the second post (161B) is positioned at a fourth radius (R4) in the second groove track (151B) when the second damper (140B) is in the open position, the third radius being greater than the fourth radius such that a force exerted on the second post (161B) when the second damper is in the closed position is less than a force exerted on the second post (161B) when the second damper is in the open position.
14. An air supply arrangement (100) according to claim 8,
the first post (1161A) is located at a first radius (R11) in the first groove track (1151A) when the first damper (1140A) is in the closed position, the first post (1161A) is located at a second radius (R12) in the first groove track (1151A) when the first damper (1140A) is in the open position, the first radius being less than the second radius such that a force exerted on the first post (1161A) when the first damper is in the closed position is greater than a force exerted on the first post (1161A) when the first damper is in the open position, and/or
The second post (1161B) is located at a third radius (R13) in the second pocket track (1151B) when the second damper (1140B) is in the closed position, the second post (1161B) is located at a fourth radius (R14) in the second pocket track (1151B) when the second damper (1140B) is in the open position, the third radius being less than the fourth radius such that a force exerted on the second post (1161B) when the second damper is in the closed position is greater than a force exerted on the second post (1161B) when the second damper is in the open position.
15. An air supply arrangement (100) according to claim 8,
the damper group composed of the first damper (140A) and the second damper (140B) has a plurality of different operating states, and the first groove rail (151A) and the second groove rail (151B) are arranged in different shapes so that switching between the plurality of operating states of the damper group is achieved by driving the first damper drive wheel (150A) and the second damper drive wheel (150B) to rotate by the drive motor.
16. An air supply arrangement (100) according to claim 15,
when the damper group is switched between each two states, the first damper drive wheel (150A) and the second damper drive wheel (150B) each rotate by the same angle, respectively.
17. An air supply arrangement (100) according to claim 15,
when the damper group is switched between the two states each time, both the first damper drive wheel (150A) and the second damper drive wheel (150B) rotate through the same angle.
18. An air supply arrangement (100) according to claim 15,
the drive motor may be programmed and programmed to change direction of rotation during a state switch of the damper group such that when the damper group is switched between states a plurality of times, the first damper drive wheel (150A) rotates in a different direction each time and the second damper drive wheel (150B) rotates in a different direction each time.
19. An air supply arrangement (100) according to claim 17,
from a first operating state of the group of dampers, only one damper is activated each time the group of dampers switches from one operating state to the next, and
during this operational state switching, only one of the first groove track (151A) of the first damper drive wheel and the second groove track (152B) of the second damper drive wheel, which correspond to the first damper and the second damper in the damper group, changes in radius.
20. Air supply arrangement (100) according to claim 1,
the drive mechanism receiving portion (112) of the frame (110) is closed by a front cover (200) such that the drive mechanism is substantially completely enclosed in the drive mechanism receiving portion (112).
21. Air supply arrangement (100) according to claim 1,
an upper portion of an airflow circulation part (111) of the frame body (110) is coupled with a damper fan cover (600), the damper fan cover (600) having an opening (601) having a shape and size corresponding to a shape of an open upper portion of the fan (500) such that an airflow flows into the airflow circulation part via the open upper portion of the fan.
22. Air supply arrangement (100) according to claim 1,
the fan (500) is fixed to an airflow circulating section (112) of the frame body (110) by one or more mounting sections (501), and a cushion pad is provided at each of the one or more mounting sections (501).
23. An air-cooled refrigerator comprising the air supply apparatus (100) of any one of claims 1 to 22.
24. A method of supplying air or cooling with an air supply arrangement (100) according to any of claims 1-22.
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CN107621119B (en) * 2017-10-16 2020-10-30 合肥华凌股份有限公司 Air door device and refrigerator with same
CN108050751A (en) * 2017-12-29 2018-05-18 青岛海尔股份有限公司 Branch air-supply arrangement and refrigerator
CN108302893A (en) * 2018-01-04 2018-07-20 合肥美的电冰箱有限公司 Blast volume controller, refrigerating plant and its control method
CN110822791A (en) * 2018-08-07 2020-02-21 松下知识产权经营株式会社 Air supply device and refrigerator

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