Method for calculating transmission ratio of driving mechanism, and air conditioner and driving mechanism

Abstract

A method for calculating a transmission ratio of a driving mechanism, and an air conditioner and a driving mechanism. The driving mechanism comprises a driving gear and a driven member engaged with the driving gear, wherein the driving gear is a non-circular gear; and when a transmission ratio of the driving gear to the driven member is a non-constant value, there is a preset function relationship between the transmission ratio and a rotation angle of the driving gear. The function comprises a monotonically increasing interval and / or a monotonically decreasing interval, an absolute value of a derivative at the maximum value and / or the minimum value of the monotonically increasing interval is less than a preset value, and an absolute value of a derivative at the maximum value and / or the minimum value of the monotonically decreasing interval is less than the preset value.

Description

Calculation method of transmission ratio of drive mechanism, air conditioning, drive mechanism

[0001] This application is based on Chinese patent application No. 202310780139.1, filed on June 28, 2023, Chinese patent application No. 202310779185.X, filed on June 28, 2023, Chinese patent application No. 202310777014.3, filed on June 28, 2023, Chinese patent application No. 202310777067.5, filed on June 28, 2023, and Chinese patent application No. 202310777054.8, filed on June 28, 2023, and claims the priority of these Chinese patent applications. The entire contents of these Chinese patent applications are hereby incorporated into this application by reference. Technical Field

[0002] The present application relates to the technical field of air conditioning, for example, to a method for calculating a transmission ratio of a driving mechanism, an air conditioner, and a driving mechanism. Background Art

[0003] At present, in the related art, when the wind guide plate swings, the rotation center is fixed, which cannot realize various wind guide functions and cannot meet the use needs of users.

[0004] In the related technology, a flippable wind guide plate is provided so that the wind guide plate can move between a closed position, a first open position with the wind guide surface facing downward, and a second open position with the wind guide surface facing upward. The setting of the first open position and the second open position enables the wind guide plate to have a variety of wind-guiding functions, thereby meeting the user's usage needs.

[0005] The air deflector can be turned over, which makes the movement of the air deflector more complicated. Therefore, the driving mechanism for driving the air deflector to turn over is more complicated. How to design the driving mechanism is an urgent problem to be solved.

[0006] It should be noted that the information disclosed in the above background technology section is only used to enhance the understanding of the background of this application, and therefore may include information that does not constitute prior art known to ordinary technicians in this field.

[0007] Summary of the Invention

[0008] In order to provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. The summary is not an extensive review, nor is it intended to identify key / critical elements or delineate the scope of protection of these embodiments, but rather serves as a prelude to the detailed description that follows.

[0009] The embodiments of the present disclosure provide a method for calculating the transmission ratio of a drive mechanism, an air conditioner, and a drive mechanism to implement the design of the drive mechanism.

[0010] An embodiment of the first aspect of the present invention provides a driving mechanism, comprising a driving gear and a driven member meshing with the driving gear, wherein the driving gear is a non-circular gear, the transmission ratio between the driving gear and the driven member is a non-constant value, and there is a preset functional relationship between the transmission ratio and the rotation angle of the driving gear; wherein the function comprises a monotonically increasing interval and / or a monotonically decreasing interval, the absolute value of the derivative at the maximum value and / or minimum value of the monotonically increasing interval is less than a preset value, and the absolute value of the derivative at the maximum value and / or minimum value of the monotonically decreasing interval is less than a preset value.

[0011] Optionally, the functional relationship includes a sine function relationship, a cosine function relationship, or a quadratic function relationship.

[0012] Optionally, the transmission ratio Where β is the rotation angle of the driving gear, A≠0, ω≠0; A, B and the radius of the driving gear and the driven member satisfy the first constraint relationship, ω, There is a second constraint relationship between the starting value and the ending value of the rotation angle of the driving gear corresponding to i.

[0013] Optionally, when the initial value of the rotation angle of the driving gear is β1 and the end value is β1+β2, and i increases during the rotation of the driving gear from β1 to β1+β2, the first constraint relationship includes:

[0014] The second constraint relationship includes:

[0015] Among them, r1 is the radius of the driving gear corresponding to β1, r2 is the radius of the driving gear corresponding to β1+β2, R1 is the radius of the driven member corresponding to β1, R2 is the radius of the driven member corresponding to β1+β2, and k is an integer.

[0016] Optionally, when the initial value of the rotation angle of the driving gear is β1 and the end value is β1+β2, and i decreases during the rotation of the driving gear from β1 to β1+β2, A and B satisfy:

[0017] ω、 satisfy:

[0018] Among them, r1 is the radius of the driving gear corresponding to β1, r2 is the radius of the driving gear corresponding to β1+β2, R1 is the radius of the driven member corresponding to β1, R2 is the radius of the driven member corresponding to β1+β2, and k is an integer.

[0019] Optionally, the transmission ratio i=a*β2+b*β+c, where β is the rotation angle of the driving gear, a≠0, and a, b, c and the starting value and ending value of the rotation angle of the driving gear corresponding to i, and the radii of the driving gear and the driven member satisfy a third constraint relationship.

[0020] Optionally, when i increases, a>0; when i decreases, a<0.

[0021] Optionally, the initial value of the rotation angle of the driving gear is β1, the end value is β1+β2, and i increases or decreases during the rotation of the driving gear from β1 to β1+β2. The third constraint relationship includes:

[0022] Among them, r1 is the radius of the driving gear corresponding to β1, r2 is the radius of the driving gear corresponding to β1+β2, R1 is the radius of the driven member corresponding to β1, and R2 is the radius of the driven member corresponding to β1+β2.

[0023] An embodiment of the second aspect of the present invention provides an air conditioner, comprising: an indoor unit, comprising a shell and an air guide plate, the shell defining an air outlet duct and being provided with an air outlet connected to the air duct, and the air guide plate movably arranged at the air outlet; a driving mechanism as described in any one of the above embodiments, the driving gear comprising a first design gear and a second design gear, the driven member comprising a first design connecting rod engaged with the first design gear and a second design connecting rod engaged with the second design gear, the first design connecting rod and the second design connecting rod are both drivingly connected to the air guide plate to realize the opening and closing of the air guide plate.

[0024] An embodiment of the third aspect of the present invention provides a method for calculating the transmission ratio of a drive mechanism, which is used to calculate the transmission ratio of a driving gear and a driven member in a drive mechanism as described in any one of the above embodiments. The calculation method includes: using a mathematical function to represent the transmission ratio function when the transmission ratio is not a constant, the mathematical function has a monotonically increasing interval and / or a monotonically decreasing interval, the absolute value of the derivative at the maximum value and / or minimum value of the monotonically increasing interval is less than a preset value, and the absolute value of the derivative at the maximum value and / or minimum value of the monotonically decreasing interval is less than a preset value; wherein, the variable of the transmission ratio function is the rotation angle of the driving gear.

[0025] The method for calculating the transmission ratio of a drive mechanism, the air conditioner, and the drive mechanism provided by the embodiments of the present disclosure can achieve the following technical effects:

[0026] A specific functional relationship is selected. Specifically, the function satisfies the following conditions: a monotonically increasing interval and / or a monotonically decreasing interval; the absolute value of the derivative at the maximum and / or minimum of the monotonically increasing interval is less than a preset value; and the absolute value of the derivative at the maximum and / or minimum of the monotonically decreasing interval is less than a preset value. A derivative's absolute value less than the preset value indicates a slow rate of change at that derivative. Using this function to characterize the transmission ratio can prevent sudden changes in the transmission ratio and achieve smooth transmission.

[0027] The above general description and the following description are exemplary and explanatory only and are not intended to limit the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] One or more embodiments are exemplarily described by corresponding drawings. These exemplary descriptions and drawings do not limit the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements. The drawings do not constitute a scale limitation. In addition,

[0029] FIG1 is a schematic structural diagram of a driving mechanism from a first perspective when an air deflector is in a closed position, provided by an embodiment of the present disclosure;

[0030] FIG2 is a schematic structural diagram of a driving mechanism from a second perspective when an air deflector is in a closed position, provided by an embodiment of the present disclosure;

[0031] FIG3 is a structural diagram of an assembly structure of a first gear, a second gear, and a fourth gear from a first perspective when an air deflector is in a closed position according to an embodiment of the present disclosure;

[0032] FIG4 is a structural diagram of an assembly structure of a first gear, a second gear, and a fourth gear from a second perspective when an air deflector provided by an embodiment of the present disclosure is in a closed position;

[0033] FIG5 is a schematic structural diagram of a driving mechanism from a first perspective when an air deflector provided by an embodiment of the present disclosure is in a first open position;

[0034] FIG6 is a schematic structural diagram of a driving mechanism from a second perspective when an air deflector provided by an embodiment of the present disclosure is in a first open position;

[0035] FIG7 is a schematic structural diagram of a driving mechanism from a first perspective when an air deflector provided by an embodiment of the present disclosure is in a second open position;

[0036] FIG8 is a structural schematic diagram of a driving mechanism from a second perspective when an air deflector provided by an embodiment of the present disclosure is in a second open position;

[0037] FIG9 is a schematic diagram of a design method provided by an embodiment of the present disclosure;

[0038] FIG10 is a schematic diagram of another design method provided by an embodiment of the present disclosure;

[0039] FIG11 is a schematic diagram of another design method provided by an embodiment of the present disclosure;

[0040] FIG12 is a diagram illustrating a solution of a first arc provided by an embodiment of the present disclosure;

[0041] FIG13 is a solution diagram of the first connecting rod provided in an embodiment of the present disclosure;

[0042] FIG14 is a diagram illustrating a solution of a second arc provided by an embodiment of the present disclosure;

[0043] FIG15 is a solution diagram of the second connecting rod provided in an embodiment of the present disclosure;

[0044] FIG16 is a schematic diagram showing a first gear design and a first connecting rod design provided in an embodiment of the present disclosure being tangent to a pitch curve;

[0045] FIG17 is a schematic diagram showing a second gear design and a second connecting rod design provided in an embodiment of the present disclosure being tangent to a pitch curve;

[0046] FIG18 is a schematic diagram of angle division of a first design gear provided by an embodiment of the present disclosure;

[0047] FIG19 is a schematic diagram of angle division of a second gear design provided by an embodiment of the present disclosure;

[0048] FIG20 is a schematic diagram of another design method provided by an embodiment of the present disclosure;

[0049] FIG21 is a schematic diagram of another design method provided by an embodiment of the present disclosure;

[0050] FIG22 is a schematic diagram of another design method provided by an embodiment of the present disclosure;

[0051] FIG23 is a schematic diagram of another design method provided by an embodiment of the present disclosure;

[0052] FIG24 is a schematic diagram of another design method provided by an embodiment of the present disclosure;

[0053] FIG25 is a schematic diagram of another design method provided by an embodiment of the present disclosure;

[0054] FIG26 is a schematic diagram of another design method provided by an embodiment of the present disclosure;

[0055] FIG27 is a schematic diagram of a pitch curve of a non-circular gear provided by an embodiment of the present disclosure;

[0056] FIG28 is a schematic diagram of a pitch curve of a follower provided by an embodiment of the present disclosure;

[0057] FIG29 is a schematic diagram of a pitch curve of a non-circular gear and a driven member provided by the disclosed embodiment;

[0058] FIG30 is a schematic diagram of a tooth blank profile and an offset profile provided by an embodiment of the present disclosure;

[0059] FIG31 is a schematic diagram of a tool and a non-circular gear provided by an embodiment of the present disclosure;

[0060] FIG32 is a schematic diagram of a tool profile trajectory provided by an embodiment of the present disclosure;

[0061] FIG33 is a schematic diagram of a Boolean operation between an offset profile and a tool provided by an embodiment of the present disclosure;

[0062] FIG34 is a schematic diagram of a non-circular gear provided by an embodiment of the present disclosure;

[0063] FIG35 is a schematic structural diagram of a driving gear and a driven member in meshing state provided by an embodiment of the present disclosure.

[0064] Reference numerals:

[0065] 10. First connecting rod; 101. First front drive unit; 102. First recess; 103. Second protrusion; 104. First gear tooth; 105. Sliding shaft; 20. Second connecting rod; 201. Second front drive unit; 202. First protrusion; 203. Second recess; 204. Second gear tooth; 30. Air guide plate; 301. Air guide surface; 302. Protrusion; 303. Slide groove; 40. Power source; 401. Driving member; 402. Transmission member; 4021. Third gear; 4022. Fourth gear; 403. Transmission shaft; 50. First gear Wheel; 60, second gear; 100, housing; 1001, air outlet; 01, first connection point; 02, second connection point; 03, third connection point; 04, fourth connection point; 05, fifth connection point; 06, sixth connection point; 07, first arc; 08, second arc; A1, motion trajectory of the first designed connecting rod; B1, motion trajectory of the second designed connecting rod; 200, pitch curve of non-circular gear; 201, tooth blank profile; 202, offset profile; 203, pitch curve of follower; 204, tool; 205, non-circular gear. DETAILED DESCRIPTION

[0066] In order to be able to understand the features and technical content of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure is described in detail below in conjunction with the accompanying drawings. The accompanying drawings are for reference only and are not used to limit the embodiments of the present disclosure. In the following technical description, for the sake of convenience of explanation, a full understanding of the disclosed embodiments is provided through multiple details. However, one or more embodiments can still be implemented without these details. In other cases, to simplify the drawings, well-known structures and devices can be simplified for display.

[0067] In the description and claims of the embodiments of the present disclosure, as well as in the accompanying drawings, the terms "first," "second," and the like are used to distinguish similar items and are not necessarily used to describe a particular order or precedence. It should be understood that the terms used in this manner are interchangeable where appropriate to describe the embodiments of the present disclosure. Furthermore, the terms "including," "having," and any variations thereof are intended to cover non-exclusive inclusions.

[0068] In the embodiments of the present disclosure, the terms "upper", "lower", "inside", "middle", "outside", "front", "back" and the like indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. These terms are mainly intended to better describe the embodiments of the present disclosure and their embodiments, and are not intended to limit the indicated devices, elements or components to having a specific direction, or to be constructed and operated in a specific direction. Moreover, in addition to being used to indicate directions or positional relationships, some of the above terms may also be used to indicate other meanings. For example, the term "upper" may also be used to indicate a certain dependency or connection relationship in certain circumstances. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0069] Furthermore, the terms "disposed," "connected," and "fixed" should be interpreted broadly. For example, "connected" can mean a fixed connection, a removable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection, an indirect connection through an intermediary, or an internal connection between two devices, elements, or components. Those skilled in the art will understand the specific meanings of these terms in the embodiments of this disclosure based on the specific circumstances.

[0070] Unless otherwise stated, the term "plurality" means two or more.

[0071] In the embodiment of the present disclosure, the character " / " indicates that the preceding and following objects are in an "or" relationship. For example, A / B means: A or B.

[0072] The term "and / or" describes an association between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or A and B.

[0073] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present disclosure can be combined with each other.

[0074] 1-8 , an embodiment of the present disclosure provides a driving mechanism for an air guide plate 30 of an air conditioner.

[0075] The air conditioner includes an indoor unit and an outdoor unit, which are connected by a connecting pipe to realize the circulation of refrigerant between the indoor unit and the outdoor unit.

[0076] The indoor unit includes a housing 100, which defines an air duct and includes an air inlet and an air outlet 1001 connected to the duct. A heat exchanger and a fan are located within the duct. Driven by the fan, air enters through the air inlet, exchanges heat with the heat exchanger, and is then blown out through the air outlet 1001.

[0077] The indoor unit further includes an air guide plate 30 , which is movably disposed at the air outlet 1001 for opening or closing the air outlet 1001 .

[0078] The driving mechanism is connected to the air guide plate 30 for driving the air guide plate 30 to move relative to the air outlet 1001 to open or close the air outlet 1001 .

[0079] As shown in FIG. 1 and FIG. 2 , the driving mechanism includes a first connecting rod 10 , a second connecting rod 20 , a first gear 50 and a second gear 60 .

[0080] The first connecting rod 10 is configured to be movably connected to the air guide plate 30 and to perform telescopic movement along the length direction of the air duct. The first connecting rod 10 is provided with a first recess 102, and the first recess 102 is provided with a first gear tooth 104; the second connecting rod 20 is configured to be movably connected to the air guide plate 30 and to perform telescopic movement along the length direction of the air duct, and the second connecting rod 20 is provided with a first protrusion 202, and the first protrusion 202 is provided with a second gear tooth 204. The first gear 50 is engaged with the first gear tooth 104 to drive the first connecting rod 10 to perform telescopic movement along the length direction of the air duct. The second gear 60 is engaged with the second gear tooth 204 to drive the second connecting rod 20 to perform telescopic movement along the length direction of the air duct; as shown in Figures 1 and 2, when the air guide plate 30 is in the closed position, the first recess 102 corresponds to the first protrusion 202, so that the first connecting rod 10 and the second connecting rod 20 can have different movement speeds to realize the movement of the air guide plate 30.

[0081] The surface of the first connecting rod 10 facing the first gear 50 is recessed to form a first recessed portion 102 , and the surface of the second connecting rod 20 facing the second gear 60 is protruded to form a first protruding portion 202 .

[0082] A first recess 102 is provided on the first connecting rod 10, and a first protrusion 202 is provided on the second connecting rod 20. When the air deflector 30 is in the closed position, the first recess 102 corresponds to the first protrusion 202, i.e., the first connecting rod 10 and the second connecting rod 20 have different shapes. Thus, when the first gear 50 engages with the first recess 102 and the second gear 60 engages with the first protrusion 202, the first connecting rod 10 and the second connecting rod 20 can achieve different telescopic movement speeds. Both the first connecting rod 10 and the second connecting rod 20 are movably connected to the air deflector 30. When the first connecting rod 10 and the second connecting rod 20 have different telescopic movement speeds, the air deflector 30 can be positioned in a variety of different air guide positions, thereby achieving a variety of different air outlet modes.

[0083] The air deflector 30 can be opened to a first open position as shown in Figures 5 and 6, and can be opened to a second open position as shown in Figures 7 and 8. In the first open position, the air deflector surface 301 of the air deflector 30 faces downward, allowing hot air to blow downward; in the second open position, the air deflector surface 301 of the air deflector 30 faces upward, allowing cold air to blow upward, preventing cold air from blowing directly.

[0084] Optionally, the first connecting rod 10 further comprises a second protrusion 103. The second protrusion 103 and the first recess 102 are sequentially arranged along the direction in which the first connecting rod 10 extends out of the air duct, i.e., the first recess 102 is located between the second protrusion 103 and the air deflector 30. The first protrusion 202 is provided with first gear teeth 104. The second connecting rod 20 further comprises a second recess 203. The second recess 203 and the first protrusion 202 are sequentially arranged along the direction in which the second connecting rod 20 extends out of the air duct, i.e., the first protrusion 202 is located between the second recess 203 and the air deflector 30. The second recess 203 is provided with second gear teeth 204. When the air deflector 30 is in the closed position, the second protrusion 103 and the second recess 203 correspond to each other, enabling the first connecting rod 10 and the second connecting rod 20 to have different movement speeds when the first gear 50 engages with the second protrusion 103 and the second gear 60 engages with the second recess 203.

[0085] The surface of the first connecting rod 10 facing the first gear 50 is convex toward the first gear 50 to form a second convex portion 103 , and the surface of the second connecting rod 20 facing the second gear 60 is concave to form a second concave portion 203 .

[0086] As shown in FIG1 and FIG2 , when the air guide plate 30 is in the closed position, the first concave portion 102 corresponds to the first convex portion 202 , and the second convex portion 103 corresponds to the second concave portion 203 , so that the corresponding portions of the first connecting rod 10 and the second connecting rod 20 have different shapes.

[0087] During the opening process of the air deflector 30, the first gear 50 first meshes with the first recess 102, at which point the second gear 60 meshes with the first protrusion 202. Subsequently, the first gear 50 meshes with the second protrusion 103, at which point the second gear 60 meshes with the second recess 203. The arrangement of the first recess 102, the first protrusion 202, the second recess 203, and the second protrusion 103 allows the first connecting rod 10 and the second connecting rod 20 to have different shapes. This allows the first connecting rod 10 and the second connecting rod 20 to have different movement speeds when the first connecting rod 10 meshes with the first gear 50 and the second connecting rod 20 meshes with the second gear 60. Both the first connecting rod 10 and the second connecting rod 20 are movably connected to the air deflector 30, so the differential movement of the first connecting rod 10 and the second connecting rod 20 enables the air deflector 30 to have multiple air guide positions, allowing the air conditioner to achieve multiple air outlet modes.

[0088] The first recess 102 and the second protrusion 103 are both driven by the first gear 50. When the first recess 102 is engaged with the first gear 50, the distance between the first recess 102 and the rotation axis of the first gear 50 is greater than the distance between the second protrusion 103 and the rotation axis of the first gear 50 when the second protrusion 103 is engaged with the first gear 50. The radius of the first gear 50 that is engaged with the first recess 102 is greater than the radius of the first gear 50 that is engaged with the second protrusion 103. When the angular velocity of the first gear 50 is equal, the movement speed of the first connecting rod 10 when the first recess 102 is engaged with the first gear 50 is greater than the movement speed of the first connecting rod 10 when the second protrusion 103 is engaged with the first gear 50.

[0089] The first protrusion 202 and the second recess 203 are both driven by the second gear 60. When the first protrusion 202 is engaged with the second gear 60, the distance between the rotation axis of the first protrusion 202 and the second gear 60 is smaller than the distance between the rotation axis of the second recess 203 and the second gear 60 when the second recess 203 is engaged with the second gear 60. The radius of the part on the second gear 60 that is engaged with the first protrusion 202 is smaller than the radius of the part on the second gear 60 that is engaged with the second recess 203. When the angular velocity of the second gear 60 is equal, the movement speed of the second connecting rod 20 when the first protrusion 202 is engaged with the second gear 60 is smaller than the movement speed of the second connecting rod 20 when the second recess 203 is engaged with the second gear 60.

[0090] In a specific embodiment, when the first recess 102 is engaged with the first gear 50, the movement speed of the first connecting rod 10 is greater than the movement speed of the second connecting rod 20 when the first protrusion 202 is engaged with the second gear 60, and when the second protrusion 103 is engaged with the first gear 50, the movement speed of the first connecting rod 10 is less than the movement speed of the second connecting rod 20 when the second recess 203 is engaged with the second gear 60, so that the air guide plate 30 can be flipped in different directions.

[0091] Optionally, the first connecting rod 10 is further provided with a first front-drive portion 101, and the first recess 102 and the first front-drive portion 101 are arranged in sequence along the direction in which the first connecting rod 10 extends out of the air duct, that is, the first front-drive portion 101 is located between the first recess 102 and the air guide plate 30, and the first front-drive portion 101 is provided with a first gear tooth 104; the second connecting rod 20 is further provided with a second front-drive portion 201, and the first convex portion 202 and the second front-drive portion 201 are arranged in sequence along the direction in which the second connecting rod 20 extends out of the air duct, that is, the second front-drive portion 201 is located between the first convex portion 202 and the air guide plate 30, and the second front-drive portion 201 is provided with a second gear tooth 204; wherein, when the air guide plate 30 is in the closed position, the first front-drive portion 101 and the second front-drive portion 201 correspond to each other.

[0092] The absolute value of the difference between the movement speed of the first connecting rod 10 when the first front drive part 101 is engaged with the first gear 50 and the movement speed of the second connecting rod 20 when the second front drive part 201 is engaged with the second gear 60 is less than the preset difference, that is, the movement speed of the first connecting rod 10 when the first front drive part 101 is engaged with the first gear 50 and the movement speed of the second connecting rod 20 when the second front drive part 201 is engaged with the second gear 60 are close.

[0093] When the movement speed of the first connecting rod 10 when the first front drive part 101 is engaged with the first gear 50 is equal to the movement speed of the second connecting rod 20 when the second front drive part 201 is engaged with the second gear 60, the air guide plate 30 is pushed out in the direction away from the air outlet 1001, and there is no flipping movement, which can prevent the air guide plate 30 from flipping and interfering with the side wall of the air duct or the shell 100.

[0094] When the absolute value of the difference between the movement speed of the first connecting rod 10 when the first front drive part 101 is engaged with the first gear 50 and the movement speed of the second connecting rod 20 when the second front drive part 201 is engaged with the second gear 60 is greater than zero and less than the preset difference, the air guide plate 30 is pushed toward the direction away from the air outlet 1001 and flipped at the same time. Since the air guide plate 30 is pushed toward the direction away from the air outlet 1001 while flipping, it can also avoid interference between the air guide plate 30 and the side wall of the air duct or the shell 100 during movement.

[0095] Among them, the absolute value of the difference between the movement speed of the first connecting rod 10 when the first recess 102 is engaged with the first gear 50 and the movement speed of the second connecting rod 20 when the first protrusion 202 is engaged with the second gear 60 is greater than the preset difference, so that when the first recess 102 is engaged with the first gear 50 and the first protrusion 202 is engaged with the second gear 60, the speed difference between the first connecting rod 10 and the second connecting rod 20 is large, which can realize the flipping of the air guide plate 30 and realize multiple air-guiding positions of the air guide plate 30.

[0096] The absolute value of the difference between the movement speed of the first connecting rod 10 when the second protrusion 103 is engaged with the first gear 50 and the movement speed of the second connecting rod 20 when the second recess 203 is engaged with the second gear 60 is greater than the preset difference, so that when the second protrusion 103 is engaged with the first gear 50 and the second recess 203 is engaged with the second gear 60, the speed difference between the first connecting rod 10 and the second connecting rod 20 is large, which can realize the flipping of the air guide plate 30 and realize multiple air-guiding positions of the air guide plate 30.

[0097] For example, at least one of the first front-drive portion 101 and the second front-drive portion 201 is straight. For another example, both the first front-drive portion 101 and the second front-drive portion 201 are curved, but the curvature of the first front-drive portion 101 is smaller than the curvature of the first concave portion 102, and the curvature of the second front-drive portion 201 is smaller than the curvature of the first convex portion 202. The shapes of the first gear 50 and the second gear 60 are conveniently designed so that the absolute value of the difference between the movement speed of the first connecting rod 10 when the first front-drive portion 101 is engaged with the first gear 50 and the movement speed of the second connecting rod 20 when the second front-drive portion 201 is engaged with the second gear 60 is smaller than a preset difference.

[0098] Optionally, the first gear 50 and the second gear 60 are both non-circular, so that the first gear 50 can engage with the first precursor 101, the first recess 102, and the second protrusion 103, and the second gear 60 can engage with the second precursor 201, the first protrusion 202, and the second recess 203.

[0099] As shown in Figures 3 and 4, the first gear 50 has different radii at the meshing locations with the first precursor portion 101, the first recess 102, and the second convex portion 103; the second gear 60 has different radii at the meshing locations with the second precursor portion 201, the first convex portion 202, and the second recess 203.

[0100] Optionally, the rotation axes of the first gear 50 and the second gear 60 coincide with each other, so that the first gear 50 and the second gear 60 can be driven by one power source 40 , thereby simplifying the structure of the driving mechanism.

[0101] The first gear 50 and the second gear 60 rotate synchronously. On the one hand, it is convenient for the first gear 50 and the second gear 60 to be driven by a power source 40. On the other hand, the first gear 50 and the second gear 60 have the same angular velocity. The first gear 50 and the second gear 60 are designed to have different radii, so that the differential motion of the first connecting rod 10 and the second connecting rod 20 can be realized, thereby simplifying the structure of the driving structure.

[0102] Optionally, as shown in Figures 1 to 4, the driving mechanism also includes a power source 40, which is driven and connected to the first gear 50 and the second gear 60. The power source 40 includes a driving member 401 and a transmission member 402. The driving member 401 is driven and connected to the transmission member 402, and the transmission member 402 cooperates with the first gear 50 and the second gear 60 so that the driving member 401 drives the first gear 50 and the second gear 60 to move synchronously through the transmission member 402.

[0103] The transmission member 402 cooperates with the first gear 50 and the second gear 60 at the same time, so that the power source 40 can simultaneously drive the first gear 50 and the second gear 60 to move through the transmission member 402, thereby achieving synchronous movement of the first gear 50 and the second gear 60.

[0104] Optionally, the transmission member 402 includes a third gear 4021 and a fourth gear 4022 .

[0105] The third gear 4021 is drivingly connected to the driving member 401 ; the fourth gear 4022 is meshed with the third gear 4021 , and is connected to both the first gear 50 and the second gear 60 .

[0106] The driving member 401 includes a single motor. The motor is drivingly connected to the third gear 4021 to drive the third gear 4021 to rotate. The third gear 4021 meshes with the fourth gear 4022 to drive the fourth gear 4022 to rotate. The first gear 50 and the second gear 60 are both connected to the fourth gear 4022, so that the fourth gear 4022 drives the first gear 50 and the second gear 60 to rotate.

[0107] It can be understood that the number of motors can also be multiple, and the number of corresponding third gears and fourth gears can also be multiple.

[0108] The rotation axes of the first gear 50, the second gear 60 and the fourth gear 4022 are parallel or coincident. On the one hand, this makes the overall structure composed of the first gear 50, the second gear 60 and the fourth gear 4022 compact and occupies little space; on the other hand, it is convenient for the fourth gear 4022 to drive the first gear 50 and the second gear 60 to rotate synchronously.

[0109] In a specific embodiment, the drive mechanism also includes a transmission shaft 403, which passes through the first gear 50, the second gear 60 and the fourth gear 4022 to achieve the connection between the first gear 50, the second gear 60 and the fourth gear 4022, and the transmission shaft 403 forms the rotation axis of the first gear 50, the second gear 60 and the fourth gear 4022.

[0110] Optionally, as shown in FIG. 4 and FIG. 5 , the first gear 50 and the second gear 60 are respectively located on opposite sides of the fourth gear 4022 , or the first gear 50 and the second gear 60 are located on the same side of the fourth gear 4022 .

[0111] Optionally, the first gear 50 and the second gear 60 are both eccentrically arranged on the power source 40, so that when the first gear 50 is respectively engaged with the first precursor 101, the first recess 102 and the second protrusion 103, the first connecting rod 10 can have different movement speeds, and when the second gear 60 is respectively engaged with the second precursor 201, the first protrusion 202 and the second recess 203, the second connecting rod 20 can have different movement speeds.

[0112] Optionally, one of the first link 10 and the second link 20 is configured to be slidably connected to the wind deflector 30, and the other is configured to be rotatably connected to the wind deflector 30, so that the first link 10 and the second link 20 cooperate to enable the wind deflector 30 to have a first open position and a second open position;.

[0113] The following describes the opening process of the air deflector 30 by taking the example that the first connecting rod 10 is slidably connected to the air deflector 30 and the second connecting rod 20 is rotatably connected to the air deflector 30 .

[0114] During the opening process of the air deflector 30, the motor rotates in the forward direction, driving the third gear 4021. The third gear 4021 drives the fourth gear 4022, which in turn drives the first gear 50 and the second gear 60 to rotate synchronously. The first gear 50 meshes with the first gear teeth 104 on the first front drive unit 101, and the second gear 60 meshes with the second gear teeth 204 on the second front drive unit 201. The extension speed of the first connecting rod 10 is close to or equal to the extension speed of the second connecting rod 20, and the air deflector 30 is pushed outward or flipped while being pushed out. Subsequently, the first gear 50 engages with the first gear teeth 104 on the first recess 102, and the second gear 60 engages with the second gear teeth 204 on the first protrusion 202. The movement speed of the first connecting rod 10 is greater than the movement speed of the second connecting rod 20, and the air guide plate 30 flips downward to reach the first open position, with the air guide surface 301 facing downward; subsequently, the first gear 50 engages with the first gear teeth 104 on the second protrusion 103, and the second gear 60 engages with the second gear teeth 204 on the second recess 203. The movement speed of the first connecting rod 10 is less than the movement speed of the second connecting rod 20, and the air guide plate 30 flips upward to reach the second open position, with the air guide surface 301 facing upward.

[0115] One of the first connecting rod 10 and the air deflector 30 is provided with a protrusion 302 having a slide groove 303 formed therein, and the other is provided with a sliding shaft 105, which is located within and slidably connected to the slide groove 303 to achieve a sliding connection between the first connecting rod 10 and the air deflector 30. As shown in FIG1 , the first connecting rod 10 is provided with the sliding shaft 105, and the air deflector surface 301 is provided with a protrusion 302 having a slide groove 303 formed therein. The slide groove 303 extends along the width direction of the air deflector surface 301.

[0116] 9 , an embodiment of the present disclosure provides a method for designing a drive mechanism for opening and closing an air deflector. The method includes:

[0117] Step S901, determining the closed position, the first open position, and the second open position of the air deflector;

[0118] Step S902: determining a first connection point 01, a second connection point 02, and a third connection point 03, wherein the first connection point 01 is located at the same position relative to the air deflector in the closed position, the second connection point 02 is located at the same position relative to the air deflector in the first open position, and the third connection point 03 is located at the same position relative to the air deflector in the second open position;

[0119] Step S903, connect the first connection point 01, the second connection point 02 and the third connection point 03 in sequence, and determine the motion trajectory A1 of the first designed connecting rod according to the connection line of the first connection point 01, the second connection point 02 and the third connection point 03, wherein one of the first designed connecting rod and the second designed connecting rod below is the first connecting rod, and the other is the second connecting rod, and one of the first designed gear and the second designed gear below is the first gear, and the other is the second gear, but it is necessary to satisfy that when the first designed connecting rod is the first connecting rod, the first designed gear is the first gear, and when the first designed connecting rod is the second connecting rod, the second designed gear is the second gear, so as to satisfy that the first gear is engaged with the first connecting rod and the second gear is engaged with the second connecting rod.

[0120] In a specific embodiment, as shown in FIG13 , step S902 determines the first connection point 01, the second connection point 02, and the third connection point 03 by: setting the first connection point 01 inside the closed position of the air deflector, setting the second connection point 02 inside the first open position of the air deflector, and setting the third connection point 03 inside the second open position of the air deflector. The first connection point 01, the second connection point 02, and the third connection point 03 are connected to the first and second points on their respective corresponding air deflectors via two line segments, respectively. The first point is located at the same position relative to the air deflector in the closed position, the second point is located at the same position relative to the air deflector in the first open position, and the third point is located at the same position relative to the air deflector in the second open position. The second point is located at the same position relative to the closed position, the second point is located at the same position relative to the air deflector in the first open position, and the second point is located at the same position relative to the air deflector in the second open position. Line segments A11, A12, A13, B11, B12, and B13 are obtained. Adjust the positions of the first connection point 01, the second connection point 02 and the third connection point 03 until A11=A12=A13, B21=B22=B23 are satisfied, and the distances from the first connection point 01, the second connection point 02 and the third connection point 03 to their respective corresponding air guide plates are equal, that is, the distance from the first connection point 01 to the air guide plate in the closed position, the distance from the second connection point 02 to the air guide plate in the first open position, and the distance from the third connection point 03 to the air guide plate in the second open position are all equal, thereby determining the first connection point 01, the second connection point 02 and the third connection point 03.

[0121] Taking the sliding connection between the first design link and the wind deflector as an example, the end of the first design link rotates relative to the first connection point 01, the second connection point 02, and the third connection point 03, and slides along the slide groove. The first connection point 01, the second connection point 02, and the third connection point 03 are designed to be points on the inner side of the wind deflector in their corresponding positions to prevent direct contact between the first design link and the wind deflector surface. This allows for the provision of a protrusion on the wind deflector surface, with the slide groove located above the protrusion.

[0122] It should be noted that the first connection point 01, the second connection point 02 and the third connection point 03 can also be points on the air guide plate in the corresponding positions, that is, the first connection point 01 is a point on the air guide plate in the closed position, the second connection point 02 and the third connection point 03 are points on the air guide plate in the first open position and the second open position respectively. At this time, the air guide surface is concave to form a slide groove, which is suitable for situations where the air guide plate is thicker.

[0123] Taking the first design's connecting rod's pivoting connection to the wind deflector as an example, the first design's connecting rod's end A10 pivots relative to the first connection point 01, the second connection point 02, and the third connection point 03. The first connection point 01, the second connection point 02, and the third connection point 03 are designed to be points on the inner side of the wind deflector in their corresponding positions to prevent direct contact between the first design's connecting rod and the wind deflector surface. This allows for the provision of a boss on the wind deflector surface, which pivots with the first design's connecting rod.

[0124] It should be noted that the first connection point 01, the second connection point 02 and the third connection point 03 can also be points on the air guide plate in the corresponding positions, that is, the first connection point 01 is a point on the air guide plate in the closed position, the second connection point 02 and the third connection point 03 are points on the air guide plate in the first open position and the second open position respectively. At this time, the air guide surface is concave, and the first designed connecting rod is rotatably connected to the concave part, which is suitable for situations where the air guide plate has a larger thickness.

[0125] After obtaining the first connection point 01, the second connection point 02, and the third connection point 03, a connecting line is obtained by sequentially connecting the first connection point 01, the second connection point 02, and the third connection point 03. The first designed connecting rod drives the air deflector from the closed position to the first open position or the second open position. Based on the shape of the connecting line, the motion trajectory A1 of the first designed connecting rod can be obtained. Based on the motion trajectory A1 of the first designed connecting rod, the first designed connecting rod can be obtained.

[0126] Step S903, determining the motion trajectory A1 of the first designed connecting rod according to the connection line of the first connection point 01, the second connection point 02 and the third connection point 03, includes:

[0127] As shown in Figures 12 and 13, if the first connection point 01, the second connection point 02 and the third connection point 03 are all located on the first arc 07, the first arc 07 is used to sequentially connect the first connection point 01, the second connection point 02 and the third connection point 03;

[0128] The motion trajectory A1 of the first designed connecting rod is determined to be an arc shape and has the same center as the first arc O7.

[0129] The line connecting the first connection point 01, the second connection point 02 and the third connection point 03 is the first arc 07, indicating that when the first design connecting rod drives the air guide plate from the closed position to the first open position and then to the second open position, the motion trajectory is an arc. Therefore, the motion trajectory A1 of the first design connecting rod is determined to be arc-shaped and concentric with the first arc 07.

[0130] Optionally, after determining that the motion trajectory A1 of the first designed connecting rod is arc-shaped and has the same center as the first arc O7, the design method further includes:

[0131] The position of the first designed connecting rod is determined, wherein the first designed connecting rod is located on one side of the first arc 07 . As shown in FIG. 13 , the first designed connecting rod can be located on the upper side of the first arc 07 or on the lower side of the first arc 07 .

[0132] Step S903, determining the motion trajectory A1 of the first designed connecting rod according to the connection line of the first connection point 01, the second connection point 02 and the third connection point 03, includes:

[0133] If the first connection point 01, the second connection point 02 and the third connection point 03 are all located on the first straight line, the first straight line is used to sequentially connect the first connection point 01, the second connection point 02 and the third connection point 03;

[0134] The motion trajectory A1 of the first designed connecting rod is determined to be linear and parallel to the first straight line.

[0135] The line connecting the first connection point 01, the second connection point 02 and the third connection point 03 is the first straight line, indicating that when the first design connecting rod drives the air guide plate from the closed position to the first open position and then to the second open position, the motion trajectory is a straight line. Therefore, the motion trajectory A1 of the first design connecting rod is determined to be straight and parallel to the first straight line.

[0136] After determining that the motion trajectory A1 of the first designed connecting rod is linear and parallel to the first straight line, the design method further includes:

[0137] The position of the first designed connecting rod is determined, wherein the first designed connecting rod is located on one side of the first straight line. Taking the horizontal extension of the first straight line as an example, the first designed connecting rod can be located on the upper side of the first straight line or on the lower side of the first straight line.

[0138] As shown in FIG10 , an embodiment of the present disclosure provides a design method for a drive mechanism for opening and closing an air deflector. The design method includes:

[0139] Step S1001, determining the closed position, the first open position, and the second open position of the air deflector;

[0140] Step S1002: determining a first connection point 01, a second connection point 02, and a third connection point 03, wherein the first connection point 01 is located at the same position relative to the air deflector in the closed position, the second connection point 02 is located at the same position relative to the air deflector in the first open position, and the third connection point 03 is located at the same position relative to the air deflector in the second open position;

[0141] Step S1003: If the first connection point 01, the second connection point 02 and the third connection point 03 are all located on the first arc 07, the first arc 07 is used to sequentially connect the first connection point 01, the second connection point 02 and the third connection point 03;

[0142] Step S1004, determining that the motion trajectory A1 of the first designed connecting rod is an arc shape and has the same center as the first arc O7;

[0143] Step S1005, determining the position of the first designed connecting rod, the first designed connecting rod is located on one side of the first arc 07;

[0144] Step S1006: If the first connection point 01, the second connection point 02, and the third connection point 03 are all located on the first straight line, the first straight line is used to sequentially connect the first connection point 01, the second connection point 02, and the third connection point 03;

[0145] Step S1007, determining that the motion trajectory A1 of the first designed connecting rod is linear and parallel to the first straight line;

[0146] Step S1008, determining the position of the first designed connecting rod, the first designed connecting rod being located on one side of the first straight line;

[0147] Step S1009, verifying the position of the first designed connecting rod according to the spatial dimensions inside the air conditioner;

[0148] Step S1010, if the position of the first designed connecting rod does not meet the requirements of the space size, that is, the movement of the first designed connecting rod is restricted by the space size and cannot be implemented, adjust the position of the first designed connecting rod, and / or adjust the positions of the first connection point 01, the second connection point 02 and the third connection point 03 relative to the corresponding wind guide plate.

[0149] Step S1011: If the position of the first designed connecting rod meets the requirements of the space size, that is, the movement of the first designed connecting rod is not restricted by the space size and the first designed connecting rod can move freely, the design of the first designed connecting rod is completed.

[0150] The driving mechanism further includes a second designed connecting rod, and the design method further includes a design method for the second designed connecting rod. The design method for the second designed connecting rod includes:

[0151] Determine a fourth connection point 04, a fifth connection point 05, and a sixth connection point 06, wherein the fourth connection point 04 is located at the same position relative to the wind deflector in the closed position, the fifth connection point 05 is located at the same position relative to the wind deflector in the first open position, and the sixth connection point 06 is located at the same position relative to the wind deflector in the second open position;

[0152] The fourth connection point 04 , the fifth connection point 05 and the sixth connection point 06 are connected, and the motion trajectory B1 of the second designed connecting rod is determined according to the connection line of the fourth connection point 04 , the fifth connection point 05 and the sixth connection point 06 .

[0153] In a specific embodiment, as shown in FIG14 , the method for determining the fourth connection point 04, the fifth connection point 05, and the sixth connection point 06 is as follows: the fourth connection point 04 is set inside the closed position of the air deflector, the fifth connection point 05 is set inside the first open position of the air deflector, and the sixth connection point 06 is set inside the second open position of the air deflector. The fourth connection point 04, the fifth connection point 05, and the sixth connection point 06 are respectively connected to the third and fourth points on their respective corresponding air deflectors via two line segments, wherein the third point is at the same position relative to the air deflector in the closed position, the fourth point is at the same position relative to the air deflector in the first open position, and the third point is at the same position relative to the air deflector in the second open position, and the fourth point is at the same position relative to the air deflector in the closed position, the fourth point is at the same position relative to the air deflector in the first open position, and the fourth point is at the same position relative to the air deflector in the second open position, thereby obtaining line segments C11, C12, C13, D11, D12, and D13. Adjust the positions of the fourth connection point 04, the fifth connection point 05 and the sixth connection point 06 until C11=C12=C13, D21=D22=D23 are satisfied, and the distances from the fourth connection point 04, the fifth connection point 05 and the sixth connection point 06 to their respective corresponding air guide plates are equal, that is, the distance from the fourth connection point 04 to the air guide plate in the closed position, the distance from the fifth connection point 05 to the air guide plate in the first open position, and the distance from the sixth connection point 06 to the air guide plate in the second open position are all equal, thereby determining the fourth connection point 04, the fifth connection point 05 and the sixth connection point 06.

[0154] Taking the sliding connection between the second design link and the wind deflector as an example, the end of the second design link rotates relative to the fourth connection point 04, the fifth connection point 05, and the sixth connection point 06, and slides along the slide groove. The fourth connection point 04, the fifth connection point 05, and the sixth connection point 06 are designed to be points on the inner side of the wind deflector in their corresponding positions to prevent the second design link from directly contacting the wind deflector surface. This allows for the provision of a protrusion on the wind deflector surface, with the slide groove located on the protrusion.

[0155] It should be noted that the fourth connection point 04, the fifth connection point 05 and the sixth connection point 06 can also be points on the wind guide plate in the corresponding positions, that is, the fourth connection point 04 is a point on the wind guide plate in the closed position, the fifth connection point 05 and the sixth connection point 06 are points on the wind guide plate in the first open position and the second open position respectively. At this time, the wind guide surface is concave to form a slide groove, which is suitable for situations where the wind guide plate is thicker.

[0156] Taking the second design's connecting rod's pivoting connection to the wind deflector as an example, the end of the second design's connecting rod pivots relative to the fourth connection point 04, the fifth connection point 05, and the sixth connection point 06. Designing the fourth, fifth, and sixth connection points 04, 05, and 06 to be points on the inner side of the wind deflector in their corresponding positions prevents direct contact between the second design's connecting rod and the wind deflector surface. This allows for the provision of a boss on the wind deflector surface, which pivots with the second design's connecting rod.

[0157] It should be noted that the fourth connection point 04, the fifth connection point 05 and the sixth connection point 06 can also be points on the wind guide plate in the corresponding positions, that is, the fourth connection point 04 is a point on the wind guide plate in the closed position, the fifth connection point 05 and the sixth connection point 06 are points on the wind guide plate in the first open position and the second open position respectively. At this time, the wind guide surface is concave, and the second design connecting rod is rotatably connected to the concave part, which is suitable for situations where the wind guide plate has a larger thickness.

[0158] After obtaining the fourth connection point 04, the fifth connection point 05, and the sixth connection point 06, a connecting line is formed by sequentially connecting the fourth connection point 04, the fifth connection point 05, and the sixth connection point 06. The second designed connecting rod drives the air deflector from the closed position to the first open position or the second open position. Based on the shape of the connecting line, the motion trajectory B1 of the second designed connecting rod can be obtained. Based on the motion trajectory B1 of the second designed connecting rod, the second designed connecting rod can be obtained.

[0159] The motion trajectory B1 of the second designed connecting rod is determined according to the connection line of the fourth connecting point 04, the fifth connecting point 05 and the sixth connecting point 06, including:

[0160] As shown in Figures 14 and 15, if the fourth connection point 04, the fifth connection point 05 and the sixth connection point 06 are all located on the second arc 08, the second arc 08 is used to sequentially connect the fourth connection point 04, the fifth connection point 05 and the sixth connection point 06;

[0161] The motion trajectory B1 of the second designed connecting rod is determined to be an arc shape and has the same center as the second arc O8.

[0162] The line connecting the fourth connection point 04, the fifth connection point 05 and the sixth connection point 06 is the second arc 08, indicating that when the second design connecting rod drives the air guide plate from the closed position to the first open position and then to the second open position, the motion trajectory is an arc. Therefore, the motion trajectory B1 of the second design connecting rod is determined to be arc-shaped and concentric with the second arc 08.

[0163] Optionally, after determining that the motion trajectory B1 of the second designed connecting rod is arc-shaped and has the same center as the second arc O8, the design method further includes:

[0164] The position of the second designed connecting rod is determined, wherein the second designed connecting rod is located on one side of the second arc 08 , as shown in FIG15 , and can be located on the upper side of the second arc 08 or on the lower side of the second arc 08 .

[0165] Alternatively, the motion trajectory B1 of the second designed connecting rod is determined according to the connection line of the fourth connecting point 04, the fifth connecting point 05, and the sixth connecting point 06, including:

[0166] If the fourth connection point 04, the fifth connection point 05 and the sixth connection point 06 are all located on the second straight line, the second straight line is used to sequentially connect the fourth connection point 04, the fifth connection point 05 and the sixth connection point 06;

[0167] The motion trajectory B1 of the second designed connecting rod is determined to be linear and parallel to the second straight line.

[0168] The line connecting the fourth connection point 04, the fifth connection point 05 and the sixth connection point 06 is the second straight line, indicating that when the second design connecting rod drives the air guide plate from the closed position to the first open position and then to the second open position, the motion trajectory is a straight line. Therefore, the motion trajectory B1 of the second design connecting rod is determined to be straight and parallel to the second straight line.

[0169] After determining that the motion trajectory B1 of the second designed connecting rod is linear and parallel to the second straight line, the design method further includes:

[0170] Determine the position of the second designed connecting rod, wherein the second designed connecting rod is located on one side of the second straight line. Taking the second straight line extending horizontally as an example, the second designed connecting rod can be located on the upper side of the second straight line or on the lower side of the second straight line.

[0171] After determining the position of the second design link, it also includes:

[0172] Verify the position of the second design link according to the space size of the air conditioner;

[0173] If the position of the second designed connecting rod does not meet the requirements of the space size, that is, the movement of the second designed connecting rod cannot be implemented due to the limitation of the space size, adjust the position of the second designed connecting rod, and / or adjust the positions of the fourth connection point 04, the fifth connection point 05 and the sixth connection point 06 relative to the air deflector;

[0174] If the position of the second designed connecting rod meets the requirements of the space size, that is, the movement of the second designed connecting rod is not restricted by the space size and the second designed connecting rod can move freely, the design of the second designed connecting rod is completed.

[0175] FIG11 shows a specific design method.

[0176] The present application also includes a driving mechanism designed using the design method of a driving mechanism for opening and closing an air guide plate as described in any one of the above embodiments.

[0177] As shown in FIG20 , an embodiment of the present disclosure provides a design method for a drive mechanism for opening and closing an air deflector. The design method includes:

[0178] Step S2001, dividing the opening process of the air deflector into multiple stages according to the movement speed or movement stroke of the first designed connecting rod and the second designed connecting rod during the opening process of the air deflector;

[0179] Step S2002 : determining the radius of the first designed gear and the second designed gear, and the connecting rod parameters of the first designed connecting rod and the second designed connecting rod at each stage.

[0180] To achieve the flipping of the air deflector, the movement speeds of the first and second design connecting rods are not constant during the opening process of the air deflector. That is, the movement speeds of the first and second design connecting rods vary, resulting in changes in the movement strokes of the first and second design connecting rods per unit time. Based on the movement speeds or strokes of the first and second design connecting rods, the opening process of the air deflector is divided into multiple stages. The radii of the first and second design gears and the connecting rod parameters of the first and second design connecting rods are determined for each stage, thereby obtaining the radii of the first and second design gears and the connecting rod parameters of the first and second design connecting rods for the entire process.

[0181] Optionally, step S2001 divides the opening process of the air deflector into multiple stages according to the movement speeds or movement strokes of the first designed connecting rod and the second designed connecting rod during the opening process of the air deflector, including:

[0182] When the difference between the movement speed or movement stroke of the first design connecting rod and the second design connecting rod is less than the preset difference, the air deflector is in the first stage, and the air deflector moves from the closed position to the extended position;

[0183] When the movement speed of the first design connecting rod is greater than the movement speed of the second design connecting rod, and the difference between the movement speed or movement stroke of the first design connecting rod and the second design connecting rod is greater than the preset difference, the air deflector is in the second stage, and the air deflector moves from the extended position to the first open position;

[0184] When the movement speed of the second design connecting rod is greater than the movement speed of the first design connecting rod, and the difference in movement speed or movement stroke between the second design connecting rod and the first design connecting rod is greater than the preset difference, the air deflector is in the third stage, and the air deflector moves from the first open position to the second open position.

[0185] Step S2002 determines the radius of the first design gear and the second design gear, and the connecting rod parameters of the first design connecting rod and the second design connecting rod at each stage, including:

[0186] When the air guide plate is in the first stage, the radii of the first design gear, the second design gear, the first design connecting rod and the second design connecting rod are determined to be constant values;

[0187] When the air guide plate is in the second stage, the radii of the first design gear, the second design gear, the first design connecting rod and the second design connecting rod are determined to be variable values;

[0188] When the air guide plate is in the third stage, the radii of the first design gear, the second design gear, the first design connecting rod and the second design connecting rod are determined to be constant values.

[0189] In the first and third stages, setting the radii of the first and second design gears to constant values ​​simplifies the design process and transforms complex non-uniform speed ratio transmissions into uniform speed ratio transmissions. Generally speaking, the rate of change in the transmission ratio for irregular speed motion, from uniform speed ratio to non-uniform speed ratio transmission, can be easily adapted to the curve variation of trigonometric functions. Therefore, setting the radii of the first and second design gears to constant values ​​in the first stage, along with the corresponding radii of the first and second design connecting rods, allows for a smooth transition from constant speed transmission to non-uniform speed transmission from the first stage to the second stage, utilizing trigonometric functions.

[0190] Optionally, when the air deflector is in the second stage, determining the radii of the first design gear, the second design gear, the first design connecting rod, and the second design connecting rod as variable values ​​includes:

[0191] The second stage is divided into a first sub-stage and a second sub-stage, and the air guide plate goes through the first sub-stage and the second sub-stage in sequence during the opening process;

[0192] When the air deflector is in the first sub-stage and the second sub-stage, the radius change trends of the first design gear and the second design gear are opposite, thereby realizing the differential movement of the first design connecting rod and the second design connecting rod, and then realizing the flipping movement of the air deflector (from the closed position to the first open position).

[0193] Optionally, when the air guide plate is in the first sub-stage and the second sub-stage, the radius change trends of the first design gear and the second design gear are opposite, including:

[0194] When the air deflector is in the first sub-stage, the radius of the first design gear decreases and the radius of the second design gear increases;

[0195] When the air deflector is in the second sub-stage, the radius of the first design gear increases and the radius of the second design gear decreases. That is, in the second stage, the radius of the first design gear first decreases and then increases, while the radius of the second design gear first increases and then decreases.

[0196] If the radius of the first design gear continues to increase in the second stage, the rotation angle of the first design connecting rod increases under the drive of the first design gear, and the first design gear and the second design gear rotate synchronously, resulting in an increase in the rotation angle of the second design gear. When the difference in the movement stroke of the first design connecting rod and the second design connecting rod is certain, the second design connecting rod requires a larger rotation angle, which will cause the second design connecting rod to be limited by the spatial dimensions.

[0197] Optionally, determining the radii of the first-design gear and the second-design gear, and the connecting rod parameters of the first-design connecting rod and the second-design connecting rod at each stage includes:

[0198] Design the rotation axes of the first design gear and the second design gear to coincide with each other;

[0199] In the closed position, the first design gear is tangent to the pitch curve of the first design connecting rod (as shown at E in FIG16 ), and the second design gear is tangent to the pitch curve of the second design connecting rod (as shown at F in FIG17 ).

[0200] Optionally, determining the radii of the first-design gear and the second-design gear, and the connecting rod parameters of the first-design connecting rod and the second-design connecting rod at each stage includes:

[0201] Determining the radius of the first design gear, the radius of the first design connecting rod, and the rotation angle of the first design connecting rod according to the transmission ratio and center distance of the first design gear and the first design connecting rod;

[0202] The radius of the second design gear, the radius of the second design connecting rod and the rotation angle of the second design connecting rod are determined according to the transmission ratio and the center distance of the second design gear and the second design connecting rod.

[0203] As shown in Figures 12 and 14, the air deflector opens from the closed position to the first open position: the first gear drives the first design connecting rod to rotate about the center of the first arc 07 by an arc length L11 or an angle θ11; the second gear drives the second design connecting rod to rotate about the center of the second arc 08 by an arc length L21 or an angle θ21. The air deflector moves from the first open position to the second open position: the first gear drives the first design connecting rod to rotate about the center of the second arc 08 by an arc length L12 or an angle θ12; the first gear drives the second design connecting rod 2 to rotate about the center of the second arc 08 by an arc length L22 or an angle θ22.

[0204] In the closed position, the pitch curves of the first gear and the first connecting rod, and the second gear and the second connecting rod are tangent to each other. The transmission ratio of the first gear and the first connecting rod is m, and the center distance is a. The transmission ratio of the second gear and the second connecting rod is n, and the center distance is b. Analyzing the rotation angles of the first and second connecting rods, to achieve the first and second open positions, as shown in Figures 18 and 19, the motor needs to rotate by three angles: α1, α2, and α3.

[0205] Within the range of α1: Since the air deflector is an outward-turning deflector, if it rotates directly, it will interfere with the duct frame. Therefore, it is necessary to extend the air deflector a certain distance before rotating it, or to extend it while rotating. By adjusting the transmission ratios m and n, the air deflector can be extended and rotated simultaneously without interfering with the duct frame. In this case, the first and second design gears are designed to have the same initial radius. In this case, the first and second design connecting rods rotate about their respective centers while extending horizontally by a similar distance. This allows the air deflector to extend and rotate simultaneously without interfering with the duct frame.

[0206] Within the range of α2: After the air deflector extends and rotates a certain distance, the first design link and the second design link can perform a large differential motion. At this time, the first design link extends slower and the second design link extends faster, so that the air deflector extends and flips to the first open position within the angle of α2;

[0207] Within the range of α3: the air guide plate moves from the first open position to the second open position, and the first design connecting rod and the second design connecting rod also need to perform a large differential movement. At this time, the first design connecting rod extends faster and the second design connecting rod extends slower, so that they can extend and flip to the second open position within the α3 angle.

[0208] L11<L21,L12> L22 and L11 are close to L12, and L21 and L22 are quite different. For example, if L12=1.1*L11;L21=1.5*L11;L22=0.5*L11, the diameters of the first design gear and the second design gear are controlled within The diameter of the first design gear is within the range of First reduce to Increase to The diameter of the second design gear is First increase to Reduce to

[0209] The diameters of the first and second design gears are controlled within The above is to increase the strength of the gear and increase stability; control Within, it is to reduce the space occupied by the driving mechanism. The larger the diameter, the greater the transmission torque required.

[0210] The motor drives the first design gear and the second design gear to rotate through three angles (α1, α2, α3), and the corresponding transmission parameters are as follows:

[0211] Within the range of α1: The radius r11 of the first design gear is a constant value, the radius R11 of the first design connecting rod is a constant value, the transmission ratio between the first design gear and the first design connecting rod is m11, the radius r21 of the second design gear is a constant value, the radius R21 of the second design connecting rod is a constant value, and the transmission ratio between the second design gear and the second design connecting rod is n21. At this time, r11 = r21, and R11 > R21 (it can also be R11 ≤ R21). Within the range of α2: Set the angle α21 to divide α2 (the second stage) into a first sub-stage and a second sub-stage. The radius of the first design gear is a variable value, and the radius of the first design connecting rod changes with the first design gear. Within the angle range from α1 to α21, the radius of the first design gear decreases from r11 to r12 first, and the transmission ratio between the first design gear and the first design connecting rod is the function m12. Within the angle range from α21 to α2, the radius of the first design gear increases from r12 to r13, and the transmission ratio between the first design gear and the first design connecting rod is the function m13. The radius of the second design gear is a variable value, and the radius of the second design connecting rod changes with the second design gear. Within the angle range from α1 to α21, the radius of the second design gear increases from r21 to r22 first, and the transmission ratio between the second design gear and the second design connecting rod is the function n22. Within the angle range from α21 to α2, the radius of the second design gear decreases from r22 to r23, and the transmission ratio between the second design gear and the second design connecting rod is the function n23. Since L11 < L21, r12 < r22; since L12 > L22, r13 > r23. Within the range of α3: The radius r13 of the first design gear is a constant value, the radius R13 of the first design connecting rod is a constant value, the transmission ratio between the first design gear and the first design connecting rod is m14, the radius r23 of the second design gear is a constant value, the radius R23 of the second design connecting rod is a constant value, and the transmission ratio between the second design gear and the second design connecting rod is n24.

[0212] Taking the internal meshing of the first design connecting rod and the first design gear and the internal meshing of the second design connecting rod and the second design gear as an example, the polar coordinate function equation of the pitch curve of the first design gear is:

[0213] The polar coordinate function equation of the pitch curve of the first design connecting rod is: [[ID=十六]]

[0214] The rotation angle θ1 of each stage of the first design connecting rod is:

[0215] The polar coordinate function equation of the pitch curve of the second design gear is:

[0216] The polar coordinate function equation of the pitch curve of the second design connecting rod is:

[0217] The rotation angle θ2 of the second design link at each stage is:

[0218] After determining the radius of the first design gear and the second design gear, and the connecting rod parameters of the first design connecting rod and the second design connecting rod at each stage, including:

[0219] The rotation angles of the first designed link and the second designed link are compared with the target angle, and the adjustment of the rotation angle is determined according to the comparison result.

[0220] The rotation angles of the first design link and the second design link are θ1 and θ2 respectively. The target angle refers to the target position of the corresponding air deflector. The angles to which the first design link and the second design link should rotate, that is, when the first design link and the second design link are opened to the target angle, the air deflector should be located at the corresponding target position.

[0221] After calculating the rotation angle according to the above formula, the rotation angle is compared with the target angle. If the difference is small, the rotation angle does not need to be adjusted. If the difference is large, the rotation angle needs to be adjusted. During adjustment, at least one of the radius of the first design gear, the center distance between the first design gear and the first design connecting rod, the radius of the second design gear, the center distance between the second design gear and the second design connecting rod, α1, α2, and α3 can be adjusted.

[0222] Optionally, after determining the radii of the first design gear and the second design gear and the connecting rod parameters of the first design connecting rod and the second design connecting rod at each stage, or after determining that no adjustment is required for the rotation angle based on a comparison result of the rotation angles of the first design connecting rod and the second design connecting rod with a target angle, the design method further includes:

[0223] Verify the interference between the air deflector and the shell during opening;

[0224] If the air guide plate interferes with the housing during opening, adjust at least one of the center distance between the first design gear and the first design connecting rod, the center distance between the second design gear and the second design connecting rod, α1, α2, and α3.

[0225] If there is no interference with the shell during the opening of the air deflector, the design is complete.

[0226] The present application also provides a method for calculating the transmission ratio of a drive mechanism, the drive mechanism comprising a driving gear and a driven member meshing with the driving gear. The driving gear may be a first design gear or a second design gear, and the corresponding driven member may be a first design connecting rod meshing with the first design gear or a second design connecting rod meshing with the second design gear. The driven member may also be a first driven gear meshing with the first design gear or a second driven gear meshing with the second design gear.

[0227] The first design gear and the second design gear are both non-circular gears. As shown in Figure 21, the calculation method includes:

[0228] Step S2101, using a mathematical function to represent a transmission ratio function when the transmission ratio is not a constant, the mathematical function having a monotonically increasing interval and / or a monotonically decreasing interval, the absolute value of the derivative at the maximum value and / or the minimum value of the monotonically increasing interval being less than a preset value, and the absolute value of the derivative at the maximum value and / or the minimum value of the monotonically decreasing interval being less than a preset value; wherein the variable of the transmission ratio function is the rotation angle of the driving gear.

[0229] If the radius of the driving gear decreases linearly, the transmission ratio will initially change suddenly, preventing smooth transmission. Selecting a specific mathematical function satisfies the following requirements: a monotonically increasing interval and / or a monotonically decreasing interval, the absolute value of the derivative at the maximum and / or minimum of the monotonically increasing interval being less than a preset value, and the absolute value of the derivative at the maximum and / or minimum of the monotonically decreasing interval being less than a preset value. A derivative's absolute value being less than a preset value indicates that the function's rate of change at that derivative is slow. Using this function to represent the transmission ratio can prevent sudden changes in the transmission ratio and achieve smooth transmission.

[0230] Optionally, the absolute value of the derivative at the maximum value and / or minimum value of the monotonically increasing interval is less than a preset value, and the absolute value of the derivative at the maximum value and / or minimum value of the monotonically decreasing interval is less than a preset value, including: the derivative at the maximum value and / or minimum value of the monotonically increasing interval is zero, and the derivative at the maximum value and / or minimum value of the monotonically decreasing interval is zero, which can further prevent sudden changes in the transmission ratio.

[0231] Optionally, the mathematical function is a trigonometric function or a quadratic function, and the trigonometric function includes a sine function or a cosine function.

[0232] The sine function, cosine function and quadratic function all have monotonically increasing intervals and monotonically decreasing intervals, and the derivatives at the maximum and minimum values ​​of the monotonically increasing intervals and monotonically decreasing intervals of the sine function and cosine function are both zero. The quadratic function has a monotonically increasing interval and a monotonically decreasing interval, and the derivative at one of the maximum and minimum values ​​of the monotonically increasing interval and monotonically decreasing interval is zero.

[0233] Optionally, step S2101, using a mathematical function to represent a transmission ratio function when the transmission ratio is not a constant value, includes:

[0234] According to the change of the transmission ratio, the transmission ratio is divided into an interval in which the transmission ratio increases and an interval in which the transmission ratio decreases;

[0235] In the range where the transmission ratio increases, the transmission ratio function uses a function corresponding to a monotonically increasing range in the mathematical function, so that the monotonicity of the mathematical function is consistent with the transmission ratio, so that the mathematical function can represent the transmission ratio;

[0236] In the transmission ratio decreasing interval, the transmission ratio function selects the function corresponding to the monotonically decreasing interval in the mathematical function, so that the monotonicity of the mathematical function is consistent with the transmission ratio, so that the mathematical function can represent the transmission ratio.

[0237] For example, if the transmission ratio of the driving gear increases throughout the entire [P1-P2] range, the entire [P1-P2] range can be divided into a range with increasing transmission ratios, and the transmission ratio function can be represented by a function corresponding to a monotonically increasing range in a mathematical function. Alternatively, the [P1-P2] range can be divided into multiple ranges, and each range can be represented by a function corresponding to a monotonically increasing range in a mathematical function. For example, if [P1-P2] is divided into two ranges, [P1-P11] and [P11-P2], the transmission ratio function of each range can be represented by a function corresponding to a monotonically increasing range, where P1 < P11 < P2.

[0238] For example, if the transmission ratio of the driving gear decreases throughout the entire [P1-P2] range, the entire [P1-P2] range can be divided into a range with a decreasing transmission ratio, and the transmission ratio function can be represented by a function corresponding to a monotonically decreasing range in a mathematical function. Alternatively, the [P1-P2] range can be divided into multiple ranges, and each range can be represented by a function corresponding to a monotonically decreasing range in a mathematical function. For example, if [P1-P2] is divided into two ranges, [P1-P11] and [P11-P2], the transmission ratio function of each range can be represented by a function corresponding to a monotonically decreasing range, where P1 < P11 < P2.

[0239] Optionally, in the interval where the transmission ratio increases, the transmission ratio function selects a function corresponding to a monotonically increasing interval in a mathematical function, including:

[0240] When the derivatives at the maximum value and the minimum value of the monotonically increasing interval are both zero, in the interval where the transmission ratio increases, the transmission ratio function selects the monotonically increasing interval including the maximum value and the minimum value in the mathematical function.

[0241] For example, when the mathematical function is a sine function or a cosine function, the derivatives at the maximum and minimum values ​​of the monotonically increasing interval are both zero. Taking the sine function as an example, in the interval where the transmission ratio increases, the transmission ratio function uses a monotonically increasing interval that includes the maximum and minimum values ​​of the mathematical function, such as the interval [-π / 2, π / 2]. Of course, any other monotonically increasing interval that includes the maximum and minimum values ​​can also be selected, such as [3π / 2, 5π / 2]. Taking the cosine function as an example, the interval [-π, 0] can be selected, or any other monotonically increasing interval that includes the maximum and minimum values, such as [π / 2, 2π].

[0242] For example, consider the driving gear's rotation angles, which are divided into β1, β2, and β3. Within β1, the driving gear operates with a fixed radius, r1; within β2, it operates with a variable radius, decreasing from r1 to r2; and within β3, it operates with a variable radius, increasing from r2 to r3. The corresponding parameters for the driven element are: within β1, the radius is fixed, R1, and the transmission ratio i1 = R1 / r1; within β2, the radius is variable, decreasing from R1 to R2, increasing the transmission ratio i2 and slowing the angular velocity of Gear 2; within β3, the radius is variable, increasing from R2 to R3, decreasing the transmission ratio i3 and accelerating the angular velocity of Gear 2.

[0243] Take the mathematical function as a sine function, and select the interval [-π / 2, π / 2], and the first design connecting rod is meshed with the first design gear, and the second design connecting rod is meshed with the second design gear. For example, let the transmission ratio function be Let the y-axis be the transmission ratio i and the x-axis be the rotation angle β of the driving gear. Taking the two end values ​​and writing equations, we get the following four equations:

[0244] Based on this, we can obtain A, B, ω, The value of is used to obtain the transmission ratio function i2.

[0245] Optionally, in the transmission ratio decreasing interval, the transmission ratio function is selected from a mathematical function corresponding to a monotonically decreasing interval, including:

[0246] When the derivatives at the maximum value and the minimum value of the monotonically decreasing interval are both zero, the transmission ratio function selects the monotonically decreasing interval including the maximum value and the minimum value in the mathematical function.

[0247] For example, in the range where the transmission ratio decreases, the transmission ratio function uses a monotonically decreasing interval with both a maximum and a minimum value, such as the interval [π / 2, 3π / 2]. Of course, any other monotonically decreasing interval with both a maximum and a minimum value can also be selected, such as [5π / 2, 7π / 2]. For example, in the range where the transmission ratio decreases, the transmission ratio function uses a monotonically decreasing interval with both a maximum and a minimum value, such as [2π, 3π].

[0248] Within β3, the transmission ratio decreases. The X-axis is [π / 2, 3π / 2], and the transmission ratio function is i3 = Csin(σβ + τ) + D. Taking the two end values ​​and formulating the equations, we get the following four equations:

[0249] By respectively obtaining the values ​​of C, D, σ and τ, the transmission ratio function i3 can be obtained.

[0250] In another embodiment, when the derivative at one of the maximum and minimum values ​​of the monotonically increasing interval is zero, in the interval where the transmission ratio increases, the transmission ratio function selects the function corresponding to the monotonically increasing interval in the mathematical function, including: selecting the value corresponding to the independent variable at which the derivative is zero as the starting value of the driving gear rotation angle corresponding to the interval where the transmission ratio increases. When the derivative at one of the maximum and minimum values ​​of the monotonically increasing interval is zero, in the interval where the transmission ratio decreases, the transmission ratio function selects the function corresponding to the monotonically decreasing interval in the mathematical function, including:

[0251] The value of the independent variable corresponding to the point where the derivative is zero is selected as the starting value of the driving gear rotation angle corresponding to the transmission ratio reduction interval.

[0252] A quadratic function has a monotonically increasing interval where its derivative is zero at one of its maximum and minimum values, but a non-zero derivative at the other.

[0253] The rotation angle of the driving gear is divided into γ1 and γ2. In γ1, the driving gear is a fixed radius r1 transmission; in γ2, it is a variable radius transmission, and the radius decreases or increases from r1 to r2; the corresponding parameters of the driven member are: in γ1, it is a fixed radius R1, at this time the transmission ratio i1 = R1 / r1; in γ2, it is a variable radius, and the radius decreases or increases from R1 to R2, at this time the transmission ratio i2 increases or decreases, and the angular velocity of the driven member should slow down or speed up accordingly.

[0254] Within γ2, the transmission ratio can be increased or decreased. The calculation method for i2 is the same whether it increases or decreases. Let the transmission ratio function i2 = a*x 2+b*x+c, the x-axis is [-b / (2a), -b / (2a)+γ2], where if i2 is increasing, a>0, and if i2 is decreasing, a<0. Taking the values ​​of both ends and writing the equation, we can get:

[0255] By finding the values ​​of a, b and c, we can find the transmission ratio function i2.

[0256] In conjunction with FIG22 , the present disclosure also provides another design method for a drive mechanism. The drive mechanism includes a non-circular gear and a driven member. The non-circular gear can be a first gear or a second gear. Correspondingly, the driven member can be a first connecting rod or a second connecting rod. This design method specifically relates to a design method for a non-circular gear tooth profile. The design method includes:

[0257] Step S2201, obtaining a pitch curve 200 of the non-circular gear, as shown in FIG27 , and a pitch curve 203 of the follower, as shown in FIG28 ;

[0258] Step S2202, generating a tooth blank profile 201 according to the pitch curve, as shown in FIG30;

[0259] Step S2203, shifting the tooth blank profile along the pitch curve toward the tooth top by the tooth top height to obtain an offset profile 202, as shown in FIG30;

[0260] S2204: Obtain the tooth profile of the non-circular gear according to the tool path profile and the offset profile.

[0261] The tooth blank profile is offset along the pitch curve toward the tooth tip, with the offset amount being the tooth tip height. This creates an offset profile, which allows the tooth tip to be easily machined using a tool, ultimately producing a non-circular gear. If the tooth blank profile is not offset, the offset profile and tooth tip location cannot be determined, requiring additional operations to produce a non-circular gear, which is tedious and complex.

[0262] In step S2204, the tooth profile of the non-circular gear is obtained according to the tool trajectory profile and the offset profile, including: obtaining the tool trajectory profile; performing a Boolean subtraction operation on the tool trajectory profile and the offset profile to obtain the gear tooth profile.

[0263] Optionally, obtaining the tool trajectory profile includes:

[0264] Draw a tool 204 in 3D software. The tool may be a gear shaping cutter, as shown in FIG31 .

[0265] The tool trajectory profile is generated by motion simulation in 3D software, as shown in Figure 32.

[0266] Optionally, after obtaining the pitch curve of the non-circular gear, the method further includes:

[0267] Import the node curve into the 2D software and enlarge it to 1:1 to obtain a 2D software file; import the 2D software file into the 3D drawing software to obtain Figure 29.

[0268] Import the pitch curve into 2D software, such as CAD or Photoshop. The 2D software must be able to magnify the pitch curve, and the saved 2D software file must be openable in 3D software, meaning it can be imported into 3D drawing software such as Unigraphics NX (UG NX), Pro / Engineer (Pro / Engineer), or SolidWorks. Generate the gear blank contour in the 3D drawing software.

[0269] By enlarging the pitch curve to 1:1, the true pitch curve can be obtained, and the true gear blank contour can be obtained later, which is convenient for tool processing.

[0270] Optionally, before obtaining the pitch curve of the non-circular gear, the method further includes:

[0271] Determine the transmission ratio function of the non-circular gear and obtain the pitch curve based on the transmission ratio function.

[0272] The method for obtaining the transmission ratio function is detailed in step S2101 above. After obtaining the transmission ratio function, the pitch curve of the non-circular gear can be solved using the mathematical software Maple.

[0273] 23 , a design method for a non-circular gear tooth profile is shown, including:

[0274] Step S2301, determining the transmission ratio function of the non-circular gear and the driven member;

[0275] Step S2302, using the mathematical software Maple to solve the pitch curve of the non-circular gear;

[0276] Step S2303, importing the two-dimensional image of the node curve into CAD, scaling it up, and obtaining a CAD file;

[0277] Step S2304: import the CAD file into 3D drawing software (e.g., UG NX), as shown in FIG29;

[0278] Step S2305, generating a gear blank profile according to the pitch curve, and offsetting the gear blank profile along the pitch curve toward the tooth top by the tooth top height distance to obtain an offset profile;

[0279] Step S2306, drawing a tool in 3D software;

[0280] Step S2307, generating a tool contour trajectory by motion simulation in 3D software;

[0281] Step S2308, performing a Boolean subtraction operation on the entire contour of the tool and the offset contour, as shown in FIG33;

[0282] Step S2309, obtaining the tooth profile of the non-circular gear, as shown in FIG34 .

[0283] In conjunction with FIG24 , the present application also discloses another method for designing a drive mechanism, wherein the drive mechanism includes a first design gear, a second design gear, a first design connecting rod meshing with the first design gear, and a second design connecting rod meshing with the second design gear. The first design connecting rod and the second design connecting rod are both connected to a driven member, which may be an air deflector. The first design connecting rod may be a first connecting rod, in which case the first design gear is the first gear, the second design connecting rod is the second connecting rod, and the second design gear is the second gear; or the first design connecting rod may be a second connecting rod, in which case the first design gear is the second gear, the second design connecting rod is the first connecting rod, and the second design gear is the first gear. The design method includes:

[0284] Step S2401, determining actual displacements of the first designed connecting rod and the second designed connecting rod during the movement of the driven member from the initial position to the target position, wherein the initial position may be the closed position, and the target position may be the extended position, the first open position, or the second open position; the initial position may also be the extended position, and the target position may be the first open position or the second open position; the initial position may also be the first open position, and the target position may be the second open position;

[0285] Step S2402, setting the parameters of the driving mechanism as the set parameters, and obtaining the transmission ratio function of the second designed gear and the second designed connecting rod according to the set parameters and the actual displacement of the first designed connecting rod;

[0286] Step S2403, using mathematical software, calculating the calculated displacement of the second designed connecting rod according to the transmission ratio function of the second designed connecting rod;

[0287] Step S2404: Determine the adjustment of the set parameters based on the magnitude relationship between the calculated displacement and the actual displacement of the second designed connecting rod.

[0288] According to the magnitude relationship between the calculated displacement and the actual displacement of the second design connecting rod, it is judged whether the setting parameters are reasonable, so that reasonable setting parameters are obtained by continuously adjusting the setting parameters, thereby obtaining a driving mechanism.

[0289] Optionally, step S2404, determining the adjustment of the set parameters based on the magnitude relationship between the calculated displacement and the actual displacement of the second designed connecting rod, includes:

[0290] If the absolute value of the difference between the calculated displacement and the actual displacement of the second designed connecting rod is greater than or equal to the specified difference, it means that the calculated displacement is significantly different from the actual displacement and the set parameters are unreasonable, and the set parameters are adjusted.

[0291] If the absolute value of the difference between the calculated displacement and the actual displacement of the second design connecting rod is less than the specified difference, it means that the difference between the calculated displacement and the actual displacement is small and the setting parameters are reasonable, then the setting parameters do not need to be adjusted.

[0292] Optionally, the setting parameters include the radius r1 of the first designed gear, the center distance a1 between the first designed gear and the first designed connecting rod, and the center distance a2 between the second designed gear and the second designed connecting rod.

[0293] The setting parameters need to satisfy the requirement that the transmission ratio function of the second design gear and the second design connecting rod can be obtained according to the setting parameters and the actual displacement of the first design connecting rod, thereby obtaining the actual displacement of the second design connecting rod according to the transmission ratio function.

[0294] Optionally, an increasing segment of the radius of the second design gear is selected, and the setting parameters include a radius starting value r21 and a radius ending value r22 of the increasing segment, wherein the radius r1 of the first design gear corresponds to the radius starting value of the second design gear, that is, when the radius r1 portion of the first design gear meshes with the first design connecting rod, the radius initial value of the second design gear meshes with the second design connecting rod. Adjusting the setting parameters includes:

[0295] End point radius value for the second designed gear.

[0296] The radius r1 of the first gear design is set appropriately. Since the radius r1 of the first gear design corresponds to the starting radius value of the second gear design, the starting radius value of the second gear design is also appropriate. Therefore, when adjusting the set parameters, adjust the ending radius value of the second gear design first.

[0297] The first designed gear can be a circular gear, in which case r1 is a constant value; or it can be a non-circular gear, in which case r1 is the radius of the first designed gear at a position corresponding to the starting value of the radius of the second designed gear.

[0298] If the end value of the radius of the second design gear is adjusted but the absolute value of the difference between the calculated displacement and the actual displacement of the second design connecting rod cannot be less than the specified difference, r1 and the starting value of the radius of the second design gear can be adjusted.

[0299] In conjunction with FIG25 , an embodiment of the present disclosure provides a design method, including:

[0300] Step S2501, determining actual displacements of the first designed connecting rod and the second designed connecting rod during the process of the driven member moving from the initial position to the target position, where the target position may be the first open position or the second open position;

[0301] Step S2502: Setting the parameters of the driving mechanism as the set parameters, and obtaining the transmission ratio function of the second designed gear and the second designed connecting rod according to the set parameters and the actual displacement of the first designed connecting rod;

[0302] Step S2503, using mathematical software, calculating the calculated displacement of the second designed connecting rod according to the transmission ratio function of the second designed connecting rod;

[0303] Step S2504: determining the adjustment of the set parameters based on the magnitude relationship between the calculated displacement and the actual displacement of the second designed connecting rod;

[0304] Step S2505: If the absolute value of the difference between the calculated displacement and the actual displacement of the second design connecting rod is greater than or equal to the specified difference, then the adjusted radius endpoint value is set to belong to the interval (r211, r222), wherein when the radius endpoint value is r211, the actual displacement of the second design connecting rod is greater than the calculated displacement of the second design connecting rod, and when the radius endpoint value is r222, the actual displacement of the second design connecting rod is less than the calculated displacement of the second design connecting rod;

[0305] Step S2506, using mathematical software to solve the calculated displacement of the second designed connecting rod corresponding to the interval (r211, r222);

[0306] Step S2507 , the radius endpoint value corresponding to the absolute value of the difference between the calculated displacement and the actual displacement of the second designed connecting rod in the selected interval ( r211 , r222 ) being less than the specified difference is selected as the feasible radius.

[0307] Step S2508: determining the actual feasibility of the feasible radius according to the size of the space where the driving mechanism is located.

[0308] When adjusting the radius midpoint value in step S2505, the radius midpoint value r22, which was originally a fixed value, is expanded to the interval (r211, r222). When the radius endpoint value is r211, the actual displacement of the second design connecting rod is greater than the calculated displacement of the second design connecting rod. When the radius endpoint value is r222, the actual displacement of the second design connecting rod is less than the calculated displacement of the second design connecting rod. Therefore, when r22 takes values ​​within the interval (r211, r222), there exists a value (i.e., a feasible radius) such that the actual displacement of the second design connecting rod is equal to the calculated displacement of the second design connecting rod. In other words, the absolute value of the difference between the calculated displacement and the actual displacement of the second design connecting rod is less than the specified difference.

[0309] The calculated and actual displacements of the second-design connecting rod can be expressed to several decimal places. More decimal places provide greater accuracy. If the absolute value of the difference between the calculated and actual displacements of the second-design connecting rod to six decimal places is less than the specified difference, the calculated and actual displacements of the second-design connecting rod are considered equal.

[0310] Step S2508, determining the actual feasibility of the feasible radius according to the size of the space where the driving mechanism is located, includes:

[0311] If the feasible radius does not conform to the size of the space where the drive mechanism is located, reset the setting parameters of the drive mechanism;

[0312] If the feasible radius is consistent with the size of the space where the drive mechanism is located, there is no need to reset the setting parameters of the drive mechanism and the design is completed.

[0313] When the motion trajectory of the first design link is an arc, the actual displacement of the first design link is the actual rotation angle, and the calculated displacement is the calculated rotation angle. When the motion trajectory of the second design link is an arc, the actual displacement of the second design link is the actual rotation angle, and the calculated displacement is the calculated rotation angle. As shown in Figure 12, when the target position is the first open position, the actual rotation angle of the first design link is θ11, and the actual rotation angle of the second design link is θ21.

[0314] When the motion trajectory of the first design link is a straight line, the actual displacement of the first design link is the actual movement length, and the calculated displacement is the calculated movement length. When the motion trajectory of the second design link is a straight line, the actual displacement of the second design link is the actual movement length, and the calculated displacement is the calculated movement length.

[0315] In conjunction with FIG26 , an embodiment of the present disclosure provides a design method, including:

[0316] Step S2601, determining the actual rotation angle θ1 of the first design link and the actual rotation angle θs of the second design link during the process of the air deflector moving from the initial position to the target position;

[0317] Step S2602, setting the radius r1 of the first design gear, the radius starting value r21 and the radius ending value r22 of the second design gear, the center distance a1 between the first design gear and the first design connecting rod, and the center distance a2 between the second design gear and the second design connecting rod;

[0318] Step S2603, calculating the rotation angle α1 of the first designed gear according to r1, a1, and θ1;

[0319] Step S2604, obtaining a transmission ratio function i2 of the second designed gear and the second designed connecting rod according to α1, r21, and r22;

[0320] Step S2605, using the mathematical software Maple, calculate the calculated rotation angle θj of the second designed connecting rod according to α1, r21, r22, and i2;

[0321] Step S2606, comparing θs and θj to see if they are equal, where the precision of θs and θj is taken to six decimal places;

[0322] Step S2607, if they are not equal, adjust the value of r22 and set r22 to change within the interval (r211, r222) (with an accuracy of six decimal places), wherein when r22 is r211, θs>θj; when r22 is r222, θs<θj;

[0323] Step S2608, using Maple mathematical software and programming, solve the corresponding value of θs when the radius r22 changes in the interval (r211, r222);

[0324] Step S2609, obtaining the value of r22 when θs and θj are equal as the feasible radius, where the accuracy of θs and θj is taken to six decimal places;

[0325] Step S2610, determining whether the space where the driving mechanism is located can accommodate the driving mechanism;

[0326] Step S2611: If it can be accommodated, the design is completed;

[0327] Step S2612: If it cannot be accommodated, adjust r1, r21, r22, a1 and a2.

[0328] In step S2603, α1 is calculated according to the following formula:

[0329] r1*α1=R1*θ1, R1 is the radius of the first design connecting rod at the point where it meshes with r1. When the first design gear is internally meshed with the first design connecting rod, R1=a1+r1; when the first design gear is externally meshed with the first design connecting rod, R1=a1-r1.

[0330] The calculation method of i2 in step S2604 is detailed in step S2101.

[0331] An embodiment of the present disclosure provides a computer program, which, when executed by a computer, enables the computer to implement the above-mentioned calculation method.

[0332] An embodiment of the present disclosure provides a computer program product, which includes computer instructions stored on a computer-readable storage medium. When the program instructions are executed by a computer, the computer is enabled to implement the above-mentioned calculation method.

[0333] The above description and the accompanying drawings sufficiently illustrate the embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Unless expressly required, individual components and functions are optional, and the order of operations may vary. Portions and features of some embodiments may be included in or replace portions and features of other embodiments. The embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A driving mechanism, characterized in that: It includes a driving gear and a driven member meshing with the driving gear, the driving gear is a non-circular gear, and when the transmission ratio between the driving gear and the driven member is a non-constant value, there is a preset functional relationship between the transmission ratio and the rotation angle of the driving gear; wherein the function includes a monotonically increasing interval and / or a monotonically decreasing interval, the absolute value of the derivative at the maximum value and / or the minimum value of the monotonically increasing interval is less than the preset value, and the absolute value of the derivative at the maximum value and / or the minimum value of the monotonically decreasing interval is less than the preset value.

2. The driving mechanism according to claim 1, characterized in that: The functional relationship includes a sine function relationship, a cosine function relationship, or a quadratic function relationship.

3. The driving mechanism according to claim 2, characterized in that: Gear Ratio Among them, β is the rotation angle of the driving gear, A≠0, ω≠0; Among them, A, B and the radius of the driving gear and the driven member satisfy the first constraint relationship, ω, There is a second constraint relationship between the starting value and the ending value of the rotation angle of the driving gear corresponding to i.

4. The driving mechanism according to claim 3, characterized in that: When the initial value of the rotation angle of the driving gear is β1, the end value is β1+β2, and i increases during the rotation of the driving gear from β1 to β1+β2, the first constraint relationship includes: The second constraint relationship includes: Among them, r1 is the radius of the driving gear corresponding to β1, r2 is the radius of the driving gear corresponding to β1+β2, R1 is the radius of the driven member corresponding to β1, R2 is the radius of the driven member corresponding to β1+β2, and k is an integer.

5. The driving mechanism according to claim 3, characterized in that: When the initial value of the rotation angle of the driving gear is β1 and the end value is β1+β2, and i decreases during the rotation of the driving gear from β11 to β1+β2, A and B satisfy: oh, satisfy: Among them, r1 is the radius of the driving gear corresponding to β1, r2 is the radius of the driving gear corresponding to β1+β2, R1 is the radius of the driven member corresponding to β1, R2 is the radius of the driven member corresponding to β1+β2, and k is an integer.

6. The driving mechanism according to claim 2, characterized in that: Transmission ratio i = a*β2+b*β+c, where β is the rotation angle of the driving gear, a≠0, a, b, c and i correspond to the driving gear The starting value and the end value of the rotation angle of the wheel, and the radius of the driving gear and the driven member satisfy the third constraint relationship.

7. The driving mechanism according to claim 6, characterized in that: When i increases, a>0; when i decreases, a<0.

8. The driving mechanism according to claim 7, characterized in that: The initial value of the rotation angle of the driving gear is β1, the end value is β1+β2, and i increases or decreases during the rotation of the driving gear from β11 to β1+β2. The third constraint relationship includes: Among them, r1 is the radius of the driving gear corresponding to β1, r2 is the radius of the driving gear corresponding to β1+β2, R1 is the radius of the driven member corresponding to β1, and R2 is the radius of the driven member corresponding to β1+β2.

9. An air conditioner, characterized in that: include: The indoor unit comprises a housing and an air guide plate, wherein the housing defines an air outlet passage and is provided with an air outlet connected to the air outlet passage, and the air guide plate is movably arranged at the air outlet; According to the driving mechanism as described in any one of claims 1 to 8, the driving gear includes a first designed gear and a second designed gear, the driven member includes a first designed connecting rod meshed with the first designed gear and a second designed connecting rod meshed with the second designed gear, and the first designed connecting rod and the second designed connecting rod are both connected to the driving of the air guide plate to realize the opening and closing of the air guide plate.

10. The air conditioner according to claim 9, characterized in that: One of the first design connecting rod and the second design connecting rod is slidably connected to the wind deflector, and the other of the first design connecting rod and the second design connecting rod is rotatably connected to the wind deflector.

11. A method for calculating the transmission ratio of a driving mechanism, used for calculating the transmission ratio of a driving gear and a driven member in a driving mechanism according to any one of claims 1 to 8, characterized in that: The calculation methods include: A transmission ratio function when the transmission ratio is not a constant is represented by a mathematical function, the mathematical function having a monotonically increasing interval and / or a monotonically decreasing interval, the absolute value of the derivative at the maximum value and / or the minimum value of the monotonically increasing interval is less than a preset value, and the absolute value of the derivative at the maximum value and / or the minimum value of the monotonically decreasing interval is less than a preset value; Among them, the variable of the transmission ratio function is the rotation angle of the driving gear.

12. The calculation method according to claim 11, characterized in that: The absolute value of the derivative at the maximum value and / or minimum value of the monotonically increasing interval is less than a preset value, and the absolute value of the derivative at the maximum value and / or minimum value of the monotonically decreasing interval is less than a preset value, including: The derivative at the maximum and / or minimum value of a monotonically increasing interval is zero, and the derivative at the maximum and / or minimum value of a monotonically decreasing interval is zero.

13. The calculation method according to claim 11, characterized in that: The mathematical functions are either trigonometric or quadratic.

14. The calculation method according to claim 13, characterized in that: Trigonometric functions include sine and cosine functions.

15. The calculation method according to any one of claims 11 to 14, characterized in that: The transmission ratio function when the transmission ratio is not a constant value is represented by a mathematical function, including: In the range where the transmission ratio increases, the transmission ratio function uses the function corresponding to the monotonically increasing range in the mathematical function; In the interval where the transmission ratio decreases, the transmission ratio function uses a function corresponding to a monotonically decreasing interval in a mathematical function.

16. The calculation method according to claim 15, characterized in that: In the range where the transmission ratio increases, the transmission ratio function uses the function corresponding to the monotonically increasing interval in the mathematical function, including: When the derivatives at the maximum and minimum values ​​of the monotonically increasing interval are both zero, in the interval where the transmission ratio increases, the transmission ratio function selects the monotonically increasing interval including the maximum and minimum values ​​in the mathematical function.

17. The calculation method according to claim 15, characterized in that: In the range where the transmission ratio increases, the transmission ratio function uses the function corresponding to the monotonically increasing interval in the mathematical function, including: When the derivative at one of the maximum value and the minimum value of the monotonically increasing interval is zero, the value corresponding to the independent variable at which the derivative is zero is selected as the starting value of the driving gear rotation angle corresponding to the transmission ratio increasing interval.

18. The calculation method according to claim 15, characterized in that: In the range where the transmission ratio decreases, the transmission ratio function uses the function corresponding to the monotonically decreasing range in the mathematical function, including: When the derivatives at the maximum value and the minimum value of the monotonically decreasing interval are both zero, the transmission ratio function selects the monotonically decreasing interval including the maximum value and the minimum value in the mathematical function.

19. The calculation method according to claim 15, characterized in that: In the range where the transmission ratio decreases, the transmission ratio function uses the function corresponding to the monotonically decreasing range in the mathematical function, including: When the derivative at one of the maximum value and the minimum value of the monotonically decreasing interval is zero, the value corresponding to the independent variable at which the derivative is zero is selected as the starting value of the driving gear rotation angle corresponding to the transmission ratio reduction interval.

20. An air conditioner, characterized in that: include: The indoor unit comprises a housing and an air guide plate, wherein the housing defines an air outlet passage and is provided with an air outlet connected to the air outlet passage, and the air guide plate is movably arranged at the air outlet; A drive mechanism designed using the method for calculating the transmission ratio of a drive mechanism as described in any one of claims 11 to 19, wherein the driving gear includes a first designed gear and a second designed gear, the driven member includes a first designed connecting rod meshed with the first designed gear and a second designed connecting rod meshed with the second designed gear, and the first designed connecting rod and the second designed connecting rod are both connected to the driving force of the air guide plate to realize the opening and closing of the air guide plate.

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