Gear structure, air door device and refrigeration equipment

Abstract

The utility model relates to the field of household appliances, in particular to a gear structure, an air door device and refrigeration equipment. The gear structure comprises a gear body and an anti-skid piece, a shaft hole is formed in the gear body, a positioning shaft penetrates through the shaft hole, the anti-skid piece is matched with the shaft hole, the anti-skid piece has elasticity in the radial direction of the shaft hole, and the anti-skid piece is used for abutting against the positioning shaft. According to the gear structure, the anti-skid piece is attached to the positioning shaft through the elastic effect in the radial direction, friction force can be increased, the gear is effectively prevented from sliding in the rotating process, stable friction force and mechanical limiting can be established between the positioning shaft and the gear body through the elastic design of the anti-skid piece, and the gear structure is simple in structure and convenient to use. And the slippage problem caused by factors such as gravity and rotating torque in a traditional gear structure is avoided.

Description

Technical Field

[0001] This utility model relates to the field of home appliances, specifically to a gear structure, a damper device, and a refrigeration equipment. Background Technology

[0002] Frost-free air-cooled refrigerators are widely used in modern homes. They achieve internal cooling through an air-cooling system, avoiding the frost problems that are common in traditional direct-cooling refrigerators. The air damper, an important component of frost-free air-cooled refrigerators, is used to regulate the distribution and flow of cold air, ensuring temperature uniformity and optimized energy efficiency throughout the refrigerator's interior.

[0003] In existing damper devices, gear systems are typically used to control the opening and closing of the damper. However, in practical use, slippage is prone to occur during gear rotation. Especially when the damper is open, the damper, under the influence of gravity, may slip circumferentially and axially along the positioning axis or rotate uncontrollably, leading to unstable friction between the gear and the damper, thus causing slippage. This slippage not only affects the stability of the damper but may also cause noise problems in the system, reducing user experience and overall product reliability. Therefore, it is urgent to improve the gear structure to avoid slippage, thereby improving the damper's working efficiency and durability. Utility Model Content

[0004] The purpose of this invention is to at least solve the problem of how to prevent slippage during gear rotation. This purpose is achieved through the following technical solution:

[0005] The first aspect of this utility model provides a gear structure, comprising:

[0006] A gear body, wherein the gear body is provided with a shaft hole for a positioning shaft to pass through;

[0007] An anti-slip component is provided, which is connected to the gear body and fits into the shaft hole. The anti-slip component is elastic along the radial direction of the shaft hole and is used to press against the positioning shaft.

[0008] According to the gear structure of this utility model, the gear body is provided with a shaft hole for a positioning shaft to pass through, providing a support structure for gear rotation. An anti-slip component is fitted into the shaft hole and has elasticity in the radial direction. This anti-slip component, through its radial elasticity, forms a close fit with the shaft hole and the positioning shaft, increasing friction and ensuring that the gear structure can rotate synchronously relative to the positioning shaft when subjected to driving force. It also effectively prevents slippage of the gear structure during rotation and avoids slippage due to the weight of the transmission structure when the gear structure needs to be fixed. This utility model, through the elastic design of the anti-slip component, can establish stable friction and mechanical restraint between the positioning shaft and the gear body, avoiding slippage problems caused by gravity, rotational torque, and other factors in traditional gear structures. Furthermore, this anti-slip design requires no complex processing technology or additional components, solving the slippage problem during gear rotation while ensuring the simplicity of the gear structure and controllable cost.

[0009] In addition, the gear structure according to this utility model may also have the following additional technical features:

[0010] In some embodiments of this utility model, the anti-slip component includes an anti-slip pressure plate, which is formed by the inner wall or edge of the shaft hole extending toward one side of the shaft hole along the axial direction, and the anti-slip pressure plate is used to press against the positioning shaft.

[0011] In some embodiments of this utility model, the shaft hole includes a first shaft hole and a second shaft hole coaxially arranged, the inner diameter of the second shaft hole is larger than the inner diameter of the first shaft hole, a step is formed between the first shaft hole and the second shaft hole, the anti-slip pressure plate is disposed on the step and extends away from the step, and the anti-slip pressure plate is spaced apart from the second shaft hole.

[0012] In some embodiments of this utility model, the anti-slip pressure plate is formed by the circumferential edge of the shaft hole extending towards the outer side of the shaft hole along the axial direction. The anti-slip pressure plate has an annular sheet structure, and a cut is provided on the circumferential sidewall of the annular sheet structure along the radial direction of the annular sheet structure.

[0013] In some embodiments of this utility model, the anti-slip component includes an anti-slip protrusion, which is disposed on the inner wall of the shaft hole and is used to press against the positioning shaft.

[0014] In some embodiments of this utility model, along the axial direction of the shaft hole, the middle part of the anti-slip protrusion protrudes towards the center of the shaft hole relative to both sides.

[0015] In some embodiments of this utility model, the anti-slip component includes an anti-slip pressure plate and an anti-slip protrusion. The anti-slip pressure plate is formed by the inner wall or edge of the shaft hole extending towards one side of the shaft hole along the axial direction. The anti-slip protrusion is located on the side of the anti-slip pressure plate facing the center of the shaft hole and is used to press against the positioning shaft.

[0016] The second aspect of this utility model provides a damper device, comprising:

[0017] A damper mechanism, comprising a door frame and a door panel, wherein the door frame has an opening defined thereon, and the door panel is pivotally connected to the door frame to open or close the opening;

[0018] The driving mechanism includes a driving component and a positioning shaft. The driving component includes the gear structure described above. The positioning shaft is disposed in the shaft hole and presses against the anti-slip component. The driving component drives the door panel to pivot relative to the door frame.

[0019] In some embodiments of this utility model, the damper mechanism is configured as two damper mechanisms, namely a first damper mechanism and a second damper mechanism. The first damper mechanism and the second damper mechanism are respectively disposed on opposite sides of the drive mechanism, and the drive mechanism is configured to drive the first damper mechanism and the second damper mechanism to open and close.

[0020] A third aspect of this utility model provides a refrigeration device, including the aforementioned damper mechanism. Attached Figure Description

[0021] Various other advantages and benefits will become apparent to those skilled in the art upon reading the following detailed description of preferred embodiments. The accompanying drawings are for illustrative purposes only and are not intended to limit the scope of the invention. Furthermore, the same reference numerals denote the same parts throughout the drawings. In the drawings:

[0022] Figure 1 A schematic diagram of the gear structure according to an embodiment of the present invention is shown.

[0023] Figure 2 A first-view view of a gear structure according to an embodiment of the present invention is shown schematically;

[0024] Figure 3 for Figure 2 A cross-sectional view of the AA plane;

[0025] Figure 4 for Figure 3 A magnified view of a section at point B in the middle;

[0026] Figure 5 An exploded view of a portion of the drive mechanism according to an embodiment of the present invention is shown schematically.

[0027] Figure 6 A schematic diagram of the damper device according to an embodiment of the present invention is shown.

[0028] Figure 7 A schematic diagram of the structure of the first driven intermittent tooth and the first drive shaft according to an embodiment of the present invention is shown.

[0029] The attached figures are labeled as follows:

[0030] 10. Gear structure; 101. First shaft hole; 102. Second shaft hole; 103. Clearance; 11. Gear body; 12. Anti-slip component; 121. Anti-slip pressure plate; 1211. Cutout; 122. Anti-slip protrusion; 13. Stop block; 14. Annular structure; 15. Annular groove; 16. Step;

[0031] 1. Drive mechanism; 20. Driving intermittent gear; 21. Protrusion; 30. First drive shaft; 31. First driven intermittent gear; 311. First half-tooth region; 312. Second half-tooth region; 40. Second drive shaft; 41. Second driven intermittent gear; 50. Driven gear;

[0032] 100. Damper device; 2. First damper mechanism; 201. First door frame; 202. First door panel; 3. Bolt; 4. Second damper mechanism; 401. Second door frame; 402. Second door panel; 4011. Opening. Detailed Implementation

[0033] Exemplary embodiments of the present disclosure will now be described in more detail with reference to the accompanying drawings. While exemplary embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure may be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.

[0034] It should be understood that the terminology used herein is for the purpose of describing particular exemplary embodiments only and is not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms “a,” “an,” and “described” as used herein may also include the plural forms. The terms “comprising,” “including,” “containing,” and “having” are inclusive and therefore indicate the presence of the stated features, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The method steps, processes, and operations described herein are not construed as requiring them to be performed in a particular order described or illustrated unless the order of performance is explicitly indicated. It should also be understood that additional or alternative steps may be used.

[0035] Although terms such as first, second, third, etc., may be used in this document to describe multiple elements, components, regions, layers, and / or segments, these elements, components, regions, layers, and / or segments should not be limited by these terms. These terms may be used only to distinguish one element, component, region, layer, or segment from another. Unless the context clearly indicates otherwise, terms such as "first," "second," and other numerical terms used herein do not imply order or sequence. Therefore, the first element, component, region, layer, or segment discussed below may be referred to as the second element, component, region, layer, or segment without departing from the teachings of the exemplary embodiments.

[0036] For ease of description, spatial relative terms may be used in the text to describe the relationship of one element or feature relative to another element or feature, as shown in the figure. These relative terms include, for example, "inside," "outside," "middle," "outer," "below," "below," "above," "over," etc. Such spatial relative terms are intended to include different orientations of the device in use or operation, other than those depicted in the figure. For example, if the device in the figure is flipped, an element described as "below other elements or features" or "below other elements or features" would subsequently be oriented "above other elements or features" or "above other elements or features." Therefore, the example term "below" can include both upper and lower orientations.

[0037] like Figures 1 to 4 As shown, according to an embodiment of the present invention, a gear structure 10 is proposed. The gear structure 10 includes a gear body 11 and an anti-slip member 12. The gear body 11 is provided with a shaft hole for a positioning shaft to pass through. The anti-slip member 12 extends toward one side of the shaft hole along the axial direction of the shaft hole and is elastic along the radial direction of the shaft hole. The anti-slip member 12 is used to press against the positioning shaft.

[0038] According to the gear structure 10 of this utility model, the gear body 11 is provided with a shaft hole for a positioning shaft to pass through, providing a support structure for gear rotation. An anti-slip member 12 extends along the edge of the shaft hole and has an elastic design. This anti-slip member 12, through its radial elasticity, forms a close fit with the positioning shaft, increasing friction and ensuring that the gear structure 10 can rotate synchronously relative to the positioning shaft when subjected to driving force. It also effectively prevents slippage of the gear structure 10 during rotation and avoids slippage due to the weight of the transmission structure when the gear structure 10 needs to be fixed. Through the elastic design of the anti-slip member 12, this utility model can establish stable friction and mechanical restraint between the positioning shaft and the gear body 11, avoiding slippage problems caused by gravity or rotational torque in traditional gear structures 10. Furthermore, this anti-slip design requires no complex processing technology or additional components, solving the problem of gear slippage during rotation while ensuring structural simplicity and cost control.

[0039] In the first embodiment, the anti-slip component 12 includes an anti-slip pressure plate 121. The anti-slip pressure plate 121 is formed by extending the inner wall or edge of the shaft hole along the axial direction of the shaft hole towards one side. The anti-slip pressure plate 121 is used to press against the positioning shaft. The anti-slip pressure plate 121 extends along the inner wall or edge of the shaft hole and presses against the positioning shaft, which can provide additional friction and effectively prevent the positioning shaft from sliding or displacing due to external forces during use, thus ensuring the stability of equipment operation.

[0040] It is understood that the anti-slip pressure plate 121 is provided on the inner wall of the shaft hole and extends towards one side of the shaft hole along the axial direction of the shaft hole. The anti-slip pressure plate 121 extends out of the shaft hole and can abut against the positioning shaft.

[0041] It is understood that the anti-slip pressure plate 121 is formed by the circumferential edge of the shaft hole extending towards one side of the shaft hole along the axial direction of the shaft hole. The anti-slip pressure plate 121 has an annular sheet structure, and along the radial direction of the annular sheet structure, a notch 1211 is provided on the circumferential sidewall of the annular sheet structure.

[0042] Specifically, the anti-slip pressure plate 121 is an annular sheet structure with a radial cut 1211 on its circumference. The cut 1211 penetrates the circumferential sidewall of the annular sheet structure, from its outer edge to its inner edge. The cut 1211 is relatively narrow, thus maintaining the integrity of the annular sheet structure. This cut 1211 allows the annular anti-slip pressure plate 121 to expand or contract in the radial direction. When a positioning shaft is inserted into the shaft hole, the anti-slip pressure plate 121 can conform to the surface of the positioning shaft due to deformation.

[0043] Specifically, the annular sheet structure of the anti-slip pressure plate 121 can have multiple radial cuts 1211 evenly distributed on it. Each cut 1211 extends from the outer periphery to the inside, but does not completely penetrate the inner periphery edge, forming flexible segments. The multiple cuts 1211 divide the annular sheet structure into several independent segments, allowing each segment to deform independently in the radial direction, thereby improving the overall elastic adaptability of the anti-slip pressure plate.

[0044] Specifically, the annular sheet structure of the anti-slip pressure plate 121 can be provided with radial cuts 1211 that are staggered on the inner and outer peripheries. The inner peripheral cuts 1211 extend outward from the inner edge of the ring, and the outer peripheral cuts 1211 extend inward from the outer edge of the ring. The positions of the cuts 1211 are staggered. The staggered distribution of the cuts 1211 makes the elasticity of the anti-slip pressure plate more uniform. The inner and outer cuts 1211 complement each other, which can avoid stress concentration caused by a single cut 1211 direction, and further improve elasticity and anti-slip stability.

[0045] Specifically, the cut 1211 of the anti-slip pressure plate 121 can be designed as a radial V-shaped groove, extending from the outer edge to the inner periphery. The width of the cut 1211 gradually decreases with depth, forming a flexible area. The V-shaped cut 1211 gradually expands or contracts under force, providing non-linear radial elasticity, effectively absorbing large deformations while maintaining the strength of the overall structure. This embodiment is used in scenarios subject to large radial forces, such as when the positioning shaft operates under dynamic loads.

[0046] In the second embodiment, the anti-slip member 12 includes an anti-slip protrusion 122, which is disposed on the inner wall of the shaft hole and is used to press against the positioning shaft.

[0047] Specifically, the anti-slip protrusion 122 can be made of hard plastic or rubber.

[0048] Understandably, along the axial direction of the shaft hole, the center of the anti-slip protrusion 122 protrudes towards the center of the shaft hole relative to the two sides, and the height of the anti-slip protrusion 122 gradually decreases from the center to the sides. Firstly, the gradual decrease in height from the center to the sides of the anti-slip protrusion 122 forms a transitional curved surface, which better conforms to the surface of the positioning shaft. This design increases the contact area, effectively disperses contact pressure, and thus significantly enhances friction and improves anti-slip performance. The gradually decreasing protrusion design avoids stress concentration that may be caused by sharp edges or abrupt transitions, reducing frictional wear between the anti-slip protrusion 122 and the positioning shaft, and extending the service life of the anti-slip component 12. Furthermore, the gradually decreasing anti-slip protrusion 122 can effectively buffer the impact force generated by the positioning shaft during dynamic operation, reducing noise and vibration during gear rotation and improving the smoothness of gear system operation. Finally, the anti-slip protrusion 122 can deform uniformly under force, accommodating slight deviations of the positioning shaft while providing sufficient friction, thereby improving the adaptability and stability of the anti-slip component 12.

[0049] Furthermore, the maximum height of the anti-slip protrusion 122 facing the shaft hole ranges from 0.1mm to 0.5mm. This maximum height setting ensures that the anti-slip protrusion 122 has adequate fit allowance within the shaft hole. The highest point of the anti-slip protrusion 122 does not completely abut against the circumferential edge of the shaft hole, but maintains a certain distance. This provides buffer space during installation, preventing excessive compression of the protrusion and ensuring anti-slip performance while extending its lifespan.

[0050] Specifically, the first distance of the anti-slip protrusion 122 is 0.2mm. This small distance ensures high-precision fit, reduces free slippage, and improves the operational stability of the gear.

[0051] Specifically, the distance between the highest point of the anti-slip protrusion 122 and the circumferential edge is 0.3mm. This distance is moderate, taking into account both ease of installation and anti-slip performance, and is suitable for equipment with medium tolerance range.

[0052] In the third embodiment, the anti-slip component 12 includes an anti-slip pressure plate 121 and an anti-slip protrusion 122. The anti-slip pressure plate 121 is connected to the edge of the shaft hole along the shaft hole, and the anti-slip protrusion 122 is connected to the side of the anti-slip pressure plate 121 facing the center of the shaft hole. The projection of the anti-slip protrusion 122 along the axial direction is located inside the shaft hole, for pressing against the positioning shaft. After the anti-slip protrusion 122 extends through the anti-slip pressure plate 121, its deformation capability and contact performance are optimized. A more stable contact state can reduce noise and vibration caused by slippage or loosening, further improving the smoothness of the gear system operation and user experience. At the same time, the anti-slip component 12 distributes the load from a single contact point to a larger area through the anti-slip pressure plate 121, which reduces the wear caused by the anti-slip protrusion 122 directly rubbing against the shaft hole or positioning shaft, thereby significantly extending the service life of the anti-slip component 12. Furthermore, the anti-slip component 12 includes an anti-slip protrusion 122 disposed on the side facing the shaft hole, and the projection of the anti-slip protrusion 122 along the axial direction is located within the shaft hole. This protrusion can provide additional mechanical contact points during gear rotation, further enhancing the anti-slip effect and limiting slippage.

[0053] Specifically, the anti-slip pressure plate 121 is formed by extending the circumferential edge of the shaft hole towards the outer side of the shaft hole along the axial direction of the shaft hole. The anti-slip pressure plate 121 has an annular sheet structure, and the radial direction of the annular sheet structure is reversed. A cut 1211 is provided on the circumferential sidewall of the annular sheet structure. The anti-slip pressure plate 121 is an annular sheet structure with multiple radial cuts 1211 on its circumference. The cuts 1211 penetrate the circumferential sidewall of the annular sheet structure, that is, from the outer edge to the inner edge of the annular sheet structure. The width of the cuts 1211 is small, so that the integrity of the annular sheet structure is basically maintained. This cut 1211 allows the annular anti-slip pressure plate 121 to expand or contract in the radial direction. When the positioning shaft is inserted into the shaft hole, the anti-slip pressure plate 121 can conform to the surface of the positioning shaft due to deformation.

[0054] Specifically, there are four cuts 1211, and the four cuts 1211 are evenly spaced along the circumference of the shaft hole. Each cut 1211 covers 20° of the circumference of the shaft hole, and the interval between two adjacent cuts 1211 is 70°.

[0055] It is understandable that, along the axial direction of the shaft hole, the anti-slip pressure plate 121 has a first height (e.g., Figure 3 As shown in a1), the first height ranges from 1mm to 10mm. The first height, within the range of 1mm to 10mm, provides sufficient extension distance, enabling the anti-slip pressure plate 121 to provide stable support when under force, avoiding structural loosening due to insufficient height or increased assembly difficulty due to excessive height.

[0056] Specifically, the anti-slip pressure plate 121 has a height of 5mm, and the anti-slip part 12 adopts a multi-cut design 1211, with the depth of the cut 1211 being 50% of the height of the anti-slip pressure plate 121.

[0057] In some embodiments, the shaft hole includes a first shaft hole 101 and a second shaft hole 102 coaxially arranged, and the inner diameter of the second shaft hole 102 is larger than the inner diameter of the first shaft hole 101. A step 16 is formed between the first shaft hole 101 and the second shaft hole 102. An anti-slip pressure plate 121 is disposed on the step 16 and extends away from the step 16. The anti-slip pressure plate 121 is spaced apart from the second shaft hole 102. This gap 103 allows the anti-slip member 12 to generate elastic deformation.

[0058] Understandably, the height of step 16 is adapted to the thickness of anti-slip component 12 along the axial direction, allowing anti-slip component 12 to be stably housed within step 16, while the gap 103 allows anti-slip component 12 to undergo elastic deformation. The design of step 16 provides a stable embedding space for anti-slip component 12, preventing it from shifting or loosening during gear operation, and ensuring that anti-slip component 12 always maintains an effective anti-slip function.

[0059] Furthermore, the second shaft hole 102 is formed as the inner wall of the annular structure 14, and the annular structure 14 forms a support at one end of the first shaft hole 101, which disperses the stress when the gear rotates and reduces the risk of local structural fatigue.

[0060] In some embodiments, the gear body 11 is provided with an annular groove 15 along the axial direction of the shaft hole. Specifically, the annular groove 15 is provided such that the circumferential edge of the gear body extends to form the outer peripheral wall of the annular groove 15, and the outer peripheral wall of the annular structure 14 coincides with the inner peripheral wall of the annular groove 15. That is, the annular groove 15 is a groove formed between the circumferential sidewall of the gear body and the annular structure 14.

[0061] Furthermore, an annular groove 15 is provided between the circumferential sidewalls of the annular structure 14 and the gear body 11, and a reinforcing rib is provided within the annular groove 15, which connects the annular structure 14 and the gear body 11 respectively. The annular groove 15 between the annular structure 14 and the gear body 11 provides stress buffer space for the gear, while the addition of the reinforcing rib further enhances the overall rigidity while ensuring the design of the annular groove 15, thus balancing flexibility and strength and significantly improving the fatigue resistance of the gear structure 10.

[0062] like Figure 5 and Figure 6As shown, this embodiment also provides a damper device 100, which specifically includes a damper mechanism and a drive mechanism 1. The damper mechanism includes a door frame and a door panel. The door frame defines an opening 4011. The door panel is pivotally connected to the door frame to open or close the opening 4011. The drive mechanism 1 includes a drive shaft and a drive assembly. The drive shaft is driven to the door panel. The drive assembly drives the door panel to pivot relative to the door frame via the drive shaft. The drive assembly includes the aforementioned gear mechanism, power component, drive gear, driven gear 50, and positioning shaft. The power component is driven to the drive gear. The drive gear and driven gear 50 mesh with each other. The driven gear 50 is driven to the gear structure 10. The drive assembly drives the door panel to pivot relative to the door frame.

[0063] In some embodiments, there are two damper mechanisms, namely a first damper mechanism 2 and a second damper mechanism 4. The first damper mechanism 2 and the second damper mechanism 4 are respectively disposed on opposite sides of the drive mechanism 1. The drive mechanism 1 is configured to drive the first damper mechanism 2 and the second damper mechanism 4 to open and close.

[0064] Specifically, the first damper mechanism 2 includes a first door frame 201 and a first door panel 202, and the second damper mechanism 4 includes a second door frame 401 and a second door panel 402. Furthermore, in some embodiments, the damper mechanisms are detachably connected to the drive mechanism 1 via bolts 3.

[0065] Furthermore, the drive assembly also includes a driving gear, a driven gear 50, and a motor. The motor is connected to the driving gear, and the driven gear 50 is connected to the driving intermittent gear 20. The driving gear and driven gear 50 mesh with each other. First, the motor is the core power source of the drive assembly, providing power to the entire system through the rotation of its output shaft. The motor is mounted with bearings to ensure smooth operation. The motor has both forward and reverse rotation modes. The driving gear is directly connected to the motor's output shaft, transmitting the motor's power to the driven gear 50. The number of teeth and size of the driving gear are designed according to the transmission ratio to match the requirements of the driven gear 50. The driven gear 50 meshes with the driving gear to receive the power transmitted by the driving gear. The shaft of the driven gear 50 is connected to the driving intermittent gear 20, further transmitting power to the driving intermittent gear 20. The transmission design of the driving gear and driven gear 50 improves power transmission efficiency, ensuring that the motor's power can be smoothly transmitted to the driving intermittent gear 20, avoiding power loss.

[0066] Specifically, the drive assembly includes a first driven intermittent gear 31, a driving intermittent gear 20, a second driven intermittent gear 41, and a gear structure 10. The gear structure 10 is driven by a positioning shaft. The first driven intermittent gear 31 is mounted on the first drive shaft 30, and the second driven intermittent gear 41 is mounted on the second drive shaft 40. The driving intermittent gear 20 is driven by the first driven intermittent gear 31 and the motor to drive the first door panel 202 to pivot. The gear structure 10 is driven by the second driven intermittent gear 41 and the driving intermittent gear 20 to drive the second door panel 402 to pivot. The driving intermittent gear 20 can drive the gear structure 10 to rotate. The first drive shaft 30 is driven by the first driven intermittent gear 31, and transmits power through the driving intermittent gear 20 to achieve the rotation of the first door panel 202. The second drive shaft 40 is driven by the second driven intermittent gear 41, and transmits power through the gear structure 10 to achieve the rotation of the second door panel 402.

[0067] Specifically, gear structure 10 and driving intermittent gear 20 have the same structure, and the first driven intermittent tooth 31 and the second driven intermittent tooth 41 have the same structure. Therefore, this embodiment uses driving intermittent gear 20 and first driven intermittent tooth 31 as examples. Driving intermittent gear 20 is a circular gear with partial gear teeth and a sliding engagement portion. The gear portion is located in a local area of ​​the circular gear's circumference, forming a toothed area for meshing with the first driven intermittent tooth 31. The arc length of the toothed area determines the intermittent meshing time period. The number and tooth profile of the gear match the first driven intermittent tooth 31 to ensure reliable power transmission during meshing. The sliding engagement portion is located on the remaining part of the circular gear's circumference and is used to contact the limiting engagement portion of the first driven intermittent tooth 31. It is usually designed as a smooth arc surface or a fan-shaped arc surface and does not have a transmission function. The function of the sliding engagement portion and the limiting engagement portion is to guide the driving intermittent gear 20 to rotate smoothly while preventing the first driven intermittent tooth 31 from being subjected to force and rotating. The first driven intermittent gear 31 is a structure with arc-shaped gear teeth, which mesh with the toothed area of ​​the driving intermittent gear 20. The number of teeth on the arc-shaped gear matches the number of teeth on the driving intermittent gear 20, and the tooth profile corresponds to that of the driving gear. The length of the arc-shaped gear typically corresponds to the length of the toothed area of ​​the driving intermittent gear 20, ensuring precise intermittent meshing. The engagement relationship between the driving intermittent gear 20 and the first driven intermittent gear 31 is such that when the driving intermittent gear 20 rotates until its toothed area aligns with the arc-shaped teeth of the first driven intermittent gear 31, the two begin to mesh. Power is transmitted from the driving intermittent gear 20 to the first driven intermittent gear 31, driving the first drive shaft 30 and its connected door plate to rotate. When the gear portion of the driving intermittent gear 20 disengages from the arc-shaped teeth of the driven gear 50, the gear enters a sliding engagement state. The sliding engagement portion of the driving intermittent gear 20 contacts the limiting engagement portion of the first driven intermittent gear 31, ensuring smooth rotation of the driving intermittent gear 20, but without transmitting power.

[0068] Furthermore, the active intermittent gear 20 and the gear structure 10 are coaxially arranged, and the active intermittent gear 20 has a protrusion on the end face facing the gear structure 10, and the gear structure 10 has a stop on the rotation trajectory of the protrusion on the end face facing the active intermittent gear 20. The protrusion and the stop cooperate to enable the gear structure 10 to rotate in both directions relative to the positioning shaft under the drive of the active intermittent gear 20.

[0069] like Figure 7 As shown, further, the first driven intermittent gear 31 has a first half-tooth region 311 and a second half-tooth region 312 respectively on both sides of the arc-shaped gear teeth in the circumferential direction. The first half-tooth region 311 and the second half-tooth region 312 are smooth transition areas and have limiting teeth on both sides extending in the circumferential direction, thus forming a limiting fit part, which is used to match the sliding fit part of the driving intermittent gear 20 to achieve a smooth sliding connection. When the driving intermittent gear 20 contacts the first half-tooth region 311 of the first driven intermittent gear 31, the limiting tooth on one side of the first half-tooth region 311 abuts against the side surface of the driving intermittent gear 20, limiting the first driven intermittent gear 31. Similarly, when the driving intermittent gear 20 contacts the second half-tooth region 312 on the other side, the limiting tooth on one side of the second half-tooth region 312 abuts against the side surface of the driving intermittent gear 20, limiting the first driven intermittent gear 31.

[0070] It is understandable that the active intermittent gear 20 and the gear structure 10 cooperate to give the damper device 100 a first state, a second state, a third state, and a fourth state. Specifically, in the first state, the first damper mechanism 2 is open, and the second damper mechanism 4 is open; in the second state (e.g.... Figure 6 As shown), the first damper mechanism 2 is closed, and the second damper mechanism 4 is open; in the third state (the drive mechanism is as shown), Figure 5 As shown, in the first state, the first damper mechanism 2 is closed, and the second damper mechanism 4 is closed; in the fourth state, the first damper mechanism 2 is open, and the second damper mechanism 4 is closed. Through precise control of these four damper states, the damper device 100 can flexibly adjust the airflow in each storage space of the refrigeration equipment, optimizing cold air distribution and temperature uniformity. For example, in the first state, both the first damper mechanism 2 and the second damper mechanism 4 are open, increasing the cold air flow and effectively maintaining a balanced temperature within the refrigeration equipment. This prevents certain storage spaces from becoming too hot or too cold, thus improving the refrigeration efficiency of the equipment.

[0071] like Figure 5 As shown, when the drive mechanism 1 is in the third state, the first damper mechanism 2 is closed, the second damper mechanism 4 is closed, and the working principle of the active intermittent gear 20 and the gear structure 10 to switch the damper device 100 to the first, second, and fourth states are as follows:

[0072] Switching from the third state to the fourth state, the driving intermittent gear 20 rotates counterclockwise, and its toothed area meshes with the first driven intermittent gear 31, driving the first driven intermittent gear 31 to rotate clockwise. The first damper mechanism 2 opens, and at this time, the sliding engagement part of the driving intermittent gear 20 abuts against the second half-tooth area 312 of the first driven intermittent gear 31. However, the protrusion 21 has not yet contacted the stop 13 of the gear structure 10.

[0073] Switching from the fourth state to the first state, the active intermittent gear 20 continues to rotate counterclockwise. The second side of the protrusion 21 contacts the second side of the stop 13 of the gear structure 10, transmitting power to make the gear structure 10 rotate counterclockwise. The gear structure 10 meshes with the second driven intermittent gear 41, driving the second driven intermittent gear 41 to rotate clockwise, opening the second damper mechanism 4. At this time, both damper mechanisms are in the open state simultaneously.

[0074] When switching from the first state to the second state, the active intermittent gear 20 rotates clockwise, and its toothed area meshes with the first driven intermittent gear 31, causing the first driven intermittent gear 31 to rotate counterclockwise, driving the first damper mechanism 2 to close. At this time, the active intermittent gear 20 idles, and the protrusion 21 has not yet contacted the stop 13 of the gear structure 10, and the second damper mechanism 4 remains open. At this time, the sliding engagement part of the active intermittent gear 20 abuts against the first half-tooth area 311 of the first driven intermittent gear 31. When the second damper mechanism 4 remains open, under the gravity of the second door panel 402, the second driven intermittent gear 41 and the gear structure 10 may rotate relative to the positioning shaft. This application provides an anti-slip component 12 to prevent the gear structure 10 from slipping due to the gravity of the transmission structure itself.

[0075] Switching from the second state to the third state, the active intermittent gear 20 continues to rotate clockwise, and the first side of the protrusion 21 contacts the first side of the stop 13 of the gear structure 10, transmitting power to make the gear structure 10 rotate clockwise. The gear structure 10 drives the second driven intermittent gear 41 to rotate counterclockwise, closing the second damper mechanism 4. At this time, both damper mechanisms are simultaneously in the closed state.

[0076] It is understandable that, as described above, when the first state is switched to the second state, the second damper mechanism 4 remains open, but the protrusion 21 has not yet contacted the stop 13 of the gear structure 10. At this time, the gear structure 10 may slip due to the weight of the second door panel 402. Therefore, the gear structure 10 is provided with an anti-slip member 12. The friction generated by the anti-slip member 12 can counteract the weight of the second door panel 402 and prevent the second door panel 402 from closing.

[0077] It is understood that the first damper mechanism 2 has a first opening 4011, and the second damper mechanism 4 has a second opening 4011, wherein there is a difference between the area of ​​the first opening 4011 of the first damper mechanism 2 and the area of ​​the second opening 4011 of the second damper mechanism 4. This difference in the opening area 4011 of the first damper mechanism 2 and the second damper mechanism 4 allows airflow to be distributed according to the needs of the storage space. For example, a larger damper opening 4011 area can deliver more cold air to meet the cooling needs of a large-capacity storage space, while a smaller damper opening 4011 area can reduce the amount of cold air delivered, avoiding energy waste. This differential design can precisely match the cooling needs of the storage space and improve the efficiency of cold air utilization inside the refrigerator.

[0078] This embodiment also provides a refrigeration device, including the aforementioned damper device 100. The refrigeration device further includes a casing, a refrigerator compartment, a freezer compartment, a refrigeration system, and a temperature control system. The damper device 100 is disposed at a partition or air duct between the refrigerator compartment and the freezer compartment. Through a damper controller, the damper can adjust the flow or blockage of cold air according to changes in temperature within the refrigeration device, ensuring that the refrigerator compartment and the freezer compartment are respectively at a set temperature.

[0079] The above description is merely a preferred embodiment of this utility model, but the protection scope of this utility model is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this utility model should be included within the protection scope of this utility model. Therefore, the protection scope of this utility model should be determined by the scope of the claims.

Claims

1. A gear structure, characterized in that, include: The gear body has a shaft hole for passing through a positioning shaft. The shaft hole includes a first shaft hole and a second shaft hole arranged coaxially. The inner diameter of the second shaft hole is larger than the inner diameter of the first shaft hole. A step is formed between the first shaft hole and the second shaft hole. An anti-slip component is provided, which is connected to the gear body and fits into the shaft hole. The anti-slip component is elastic along the radial direction of the shaft hole and is used to press against the positioning shaft. The anti-slip component includes an anti-slip pressure plate, which is formed by the inner wall or edge of the shaft hole extending towards one side of the shaft hole along the axial direction of the shaft hole. The anti-slip pressure plate is used to press against the positioning shaft. The anti-slip pressure plate is disposed on the step and extends away from the step. The anti-slip pressure plate is spaced apart from the second shaft hole. The anti-slip pressure plate has an annular sheet structure. Along the radial direction of the annular sheet structure, there is a cut on the circumferential sidewall of the annular sheet structure. Each cut covers 20° of the circumferential direction of the shaft hole, and the depth of the cut is 50% of the height of the anti-slip pressure plate.

2. The gear structure according to claim 1, characterized in that, The anti-slip component includes an anti-slip protrusion, which is disposed on the inner wall of the shaft hole and is used to press against the positioning shaft.

3. The gear structure according to claim 2, characterized in that, Along the axial direction of the shaft hole, the middle part of the anti-slip protrusion protrudes towards the center of the shaft hole relative to both sides.

4. The gear structure according to claim 1, characterized in that, The anti-slip component includes an anti-slip pressure plate and an anti-slip protrusion. The anti-slip pressure plate is formed by the inner wall or edge of the shaft hole extending towards one side of the shaft hole along the axial direction of the shaft hole. The anti-slip protrusion is located on the side of the anti-slip pressure plate facing the center of the shaft hole and is used to press against the positioning shaft.

5. A damper device, characterized in that, include: A damper mechanism, comprising a door frame and a door panel, wherein the door frame has an opening defined thereon, and the door panel is pivotally connected to the door frame to open or close the opening; A driving mechanism, comprising a driving component and a positioning shaft, wherein the driving component includes a gear structure according to any one of claims 1 to 4, the positioning shaft is disposed in the shaft hole and press-fits with the anti-slip member, and the driving component drives the door panel to pivot relative to the door frame.

6. The damper device according to claim 5, characterized in that, The damper mechanism is configured as two damper mechanisms, namely a first damper mechanism and a second damper mechanism. The first damper mechanism and the second damper mechanism are respectively disposed on opposite sides of the drive mechanism. The drive mechanism is configured to drive the first damper mechanism and the second damper mechanism to open and close.

7. A refrigeration device, characterized in that, Includes the damper device according to claim 5 or 6.

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