Gear box, rocker arm assembly and window

Abstract

The gear box comprises a shell and a driving part, an inner cavity is formed in the shell, the driving part is arranged in the inner cavity, and the gear box comprises a transmission assembly arranged in the inner cavity and meshed with the driving part and an external rocker arm; the planetary gear set is formed by meshing a plurality of first gears in a surrounding mode, and the transmission assembly extends into the planetary gear and is meshed with each first gear at the same time to be used for being matched with the transmission assembly to transmit the driving force of the driving part to the external rocker arm. On the basis that the torque and the first gears form a parallel and circumferentially distributed force flow path in the inner cavity through the transmission assembly, the load borne by a single meshing pair is remarkably reduced, the situation that the load is improved by increasing the size of the gear matched with the external rocker arm is avoided, and therefore the problem that the size of the gearbox is too large due to the fact that the torque is guaranteed is avoided.

Description

Technical Field

[0001] This application relates to the field of construction, and more particularly to a gearbox, rocker arm assembly, and window. Background Technology

[0002] Planetary gear drives are a common type of coaxial transmission, typically consisting of a sun gear, multiple planet gears, a planet carrier, and an internal / external ring gear that meshes with the planet gears. Their characteristics include the simultaneous meshing of multiple planet gears, enabling a large transmission ratio and high load-bearing capacity within a relatively small volume. Furthermore, the force can be distributed among multiple meshing pairs, making them widely used in various reduction mechanisms and actuators.

[0003] In automated curtain / window / door opening devices, the drive components (such as the motor output and its fixed-axis gear stage) and gearbox are typically concealed within the narrow interior cavity of the window or door frame. Power is output to an external rocker arm (or sector gear segment) via gear transmission to drive the window sash to open and close. Existing devices mostly employ multi-stage fixed-axis gear reduction, with some designs incorporating a planetary gear transmission stage to improve the reduction ratio and load-bearing capacity. However, the final output to the rocker arm still relies on a single, large external meshing output gear engaging with the rocker arm. Due to limitations in the frame's cross-sectional dimensions and installation space, the number and tooth width of the planetary gears are often constrained, and the number of contact teeth between the final output and the rocker arm is limited, with the load primarily concentrated on a few tooth surfaces.

[0004] In the field of automated curtains, to ensure the torque required for normal opening and closing of the window sash, existing technologies typically increase the load-bearing capacity by increasing the module and diameter of the output gear meshing with the rocker arm, thereby meeting the output torque requirements. However, this approach significantly increases the overall size and cross-sectional height of the gearbox, making it difficult to arrange the gearbox within the window frame cavity or forcing an increase in the window frame size. This leads to the problem of "excessively large gearbox volume, resulting in enlarged door / window frame sizes," affecting assembly and appearance, and limiting its application in narrow frames. Summary of the Invention

[0005] In view of this, it is necessary to provide a gearbox, a rocker arm assembly, and a window to solve the above problems.

[0006] An embodiment of this application provides a gearbox, including a housing and a drive member. The housing has an inner cavity, and the drive member is disposed in the inner cavity. The gearbox further includes a transmission assembly disposed in the inner cavity, and the transmission assembly is respectively engaged with the drive member and an external rocker arm. The planetary gear set is composed of multiple first gears meshing around each other. The transmission component extends into the planetary gears and meshes with each first gear simultaneously, in order to cooperate with the transmission component to transmit the driving force of the drive member to the external rocker arm.

[0007] In at least one embodiment of this application, the transmission assembly includes a second gear and a third gear; The second gear extends into the planetary gear set and simultaneously meshes with each of the first gears, and the third gear meshes with the second gear and is connected to the drive unit for transmission.

[0008] In at least one embodiment of this application, a plurality of the first gears are arranged at equal angular intervals around the second gear in the circumferential direction, and the number is at least three.

[0009] In at least one embodiment of this application, each of the first gears is a spur gear and they all have the same module, and the second gear has the same module as the first gear.

[0010] In at least one embodiment of this application, the transmission assembly further includes a first transmission member and a second transmission member; The first transmission component meshes with the driving component, and the second transmission component meshes with the first transmission component and the third gear, respectively.

[0011] In at least one embodiment of this application, the driving member includes a motor and a driving part disposed on the motor drive shaft, the driving part engaging with the first transmission member.

[0012] In at least one embodiment of this application, the driving part is a helical gear, the first transmission member and the second transmission member are a gear set, and the driving part meshes with the first transmission member to drive the first transmission member to move.

[0013] In at least one embodiment of this application, the planetary gear set further includes a planet carrier, each of the first gears being rotatably mounted on the planet carrier via a rotating shaft, the planet carrier being fixed to the housing.

[0014] In at least one embodiment of this application, a rocker arm assembly includes a rocker arm and the gearbox, the rocker arm being connected to the transmission assembly.

[0015] In at least one embodiment of this application, a window includes the aforementioned rocker arm assembly.

[0016] The gearbox described above houses the transmission assembly within the internal cavity of the housing, which meshes with both the drive component and the external rocker arm. The planetary gear set consists of multiple first gears meshing around each other, and the transmission assembly extends into the planetary gear set and meshes with each of the first gears simultaneously. Based on this configuration, torque flows through the internal cavity via the transmission assembly and the multiple first gears, forming a parallel, circumferentially distributed force flow path. This significantly reduces the load borne by a single meshing pair, avoiding the need to increase the gear size at the engagement point with the external rocker arm to improve load capacity. This avoids the problem of an excessively large gearbox size due to insufficient torque. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] in: Figure 1 This is a perspective view of the gearbox in Embodiment 1 of this application; Figure 2 This is a first-view perspective view of the gearbox in Embodiment 1 of this application; Figure 3 This is a perspective view of the gearbox in Embodiment 1 of this application from a second viewpoint; Figure 4 This is an exploded view of the gearbox in Embodiment 1 of this application from a first perspective; Figure 5 This is an exploded view of the gearbox in Embodiment 1 of this application from a second perspective.

[0019] Explanation of key component symbols: 100. Gearbox; 10. Housing; 10a. Inner cavity; 20. Drive component; 21. Motor; 22. Drive unit; 30. Transmission assembly; 31. Second gear; 32. Third gear; 33. First transmission component; 34. Second transmission component; 40. Planetary gear set; 41. First gear; 50. Planet carrier. Detailed Implementation

[0020] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.

[0021] It should be noted that when a component is considered to be "connected" to another component, it can be directly connected to the other component or may also have an intervening component. When a component is considered to be "placed" on another component, it can be directly placed on the other component or may also have an intervening component. The terms "top," "bottom," "upper," "lower," "left," "right," "front," "back," and similar expressions used in this article are for illustrative purposes only.

[0022] Example 1 Please see Figures 1-4 This embodiment provides a gearbox, including a housing, a drive component, a transmission assembly, and a planetary gear set. The housing has an inner cavity, the drive component is disposed in the inner cavity, the transmission assembly is disposed in the inner cavity, and the transmission assembly is respectively meshed with the drive component and an external rocker arm. The planetary gear set is formed by multiple first gears meshing around each other. The transmission assembly extends into the planetary gears and meshes with each first gear simultaneously, for cooperating with the transmission assembly to transmit the driving force of the drive component to the external rocker arm.

[0023] The gearbox 100 of this embodiment includes a housing 10, within which an inner cavity 10a is formed. A drive member 20 is disposed at one end of the inner cavity 10a and is used to provide driving force to the inner cavity.

[0024] In one specific embodiment, the drive member 20 is a motor 21, whose drive section 22 meshes with the first transmission member 33 of the transmission assembly 30. The first transmission member 33 is a coaxial compound gear of one large and one small. The drive section 22 preferably meshes with its larger gear to achieve initial reduction. The smaller gear of 33 meshes with the larger gear of the second transmission member 34 to achieve secondary reduction and wheelbase transition. The second transmission member 34 is also a coaxial compound gear of one large and one small. The smaller gear of 34 meshes with the third gear 32. The third gear 32 acts as a transition gear to change the transmission direction and meshes with the second gear 31. The second gear 31 is located at the center of the planetary gear set 40 and extends into the set. As a central meshing member, it meshes with multiple first gears 41 simultaneously. The multiple first gears 41 are rotatably supported by the planet carrier 50 and are distributed equiangularly around the second gear 31 in the circumferential direction. Their outer sides are configured to mesh with the tooth segments of the external rocker arm, thereby outputting torque to the external rocker arm.

[0025] Based on the above connections and positional relationships, the force flow can be clearly defined as follows: driving component 20 → first transmission component 33 → second transmission component 34 → third gear 32 → second gear 31 → multiple first gears 41 → external rocker arm.

[0026] It should be noted that, since the second gear 31 is located at the center of the planetary gear set 40 and meshes with each of the first gears 41 simultaneously, the driving force is distributed in parallel by multiple meshing pairs in the circumferential direction, and the contact and bending loads of a single meshing pair are significantly reduced; the first gears 41 are distributed around the perimeter, and their radial reaction forces on the inner cavity 10a are geometrically canceled out, thereby reducing the off-center load and bending moment that the bearings and housing 10 need to bear; under the premise of meeting the same output torque and life, the second gear 31 and its cooperating support do not need to increase the outer diameter to improve the load-bearing capacity, and can complete the driving of the peripheral rocker arm, which is conducive to compressing the shape of the part that cooperates with the peripheral rocker arm and reducing the outer contour of the gearbox 100 in the inner cavity direction, making it suitable for embedded installation in the limited space of the window frame.

[0027] In one specific embodiment, the transmission assembly includes a second gear and a third gear; the second gear extends into the planetary gear set and simultaneously meshes with each of the first gears, and the third gear meshes with the second gear and is connected to the drive member for transmission.

[0028] It should be noted that, in this embodiment, the transmission assembly 30 includes at least a second gear 31 and a third gear 32. The second gear 31 is disposed within the inner cavity 10a of the housing 10, near the center of the planetary gear set 40, and extends axially into the envelope of the planetary gear set 40, so that its tooth surface is located in the common meshing area of ​​the plurality of first gears 41, thereby meshing with each of the first gears 41 simultaneously in the circumferential direction; the plurality of first gears 41 are distributed at equal angles around the second gear 31, and are preferably rotatably supported by the planet carrier 50.

[0029] The third gear 32 is arranged in the inner cavity 10a and is adjacent to the second gear 31. The two are stably meshed at the designed center distance. The other side of the third gear 32 is connected to the drive member 20 for transmission.

[0030] In one specific embodiment, the driving component 20 is a motor 21, and the driving part 22 of the motor directly meshes with the third gear 32.

[0031] In another embodiment, the drive unit 22 transmits torque through a connecting member coaxially fixed with the third gear. From the above connection and positional relationship, the actuation chain can be deduced as follows: after the drive unit 20 outputs torque, it first drives the third gear 32 to rotate, and the third gear 32 transmits power to the second gear 31 that meshes with it; since the second gear 31 extends into the planetary gear set 40 and meshes with all the first gears 41 at the same time, it distributes the torque from the third gear 32 in a circumferential "parallel" manner to multiple first gears 41, and each first gear 41 transmits the torque to the external rocker arm to complete the external output.

[0032] It should be noted that the beneficial effects of the "third gear 32 → second gear 31 → multiple first gears 41" arrangement are as follows: First, the second gear 31 meshes with each of the first gears 41 simultaneously, so that the total torque is shared by multiple meshing pairs, significantly reducing the load on a single meshing pair. Therefore, it is not necessary to increase the load-bearing capacity by increasing the outer diameter of the gear that mates with the external rocker arm. Second, the first gears 41 are distributed around the perimeter, and the radial forces acting on the second gear 31 are geometrically canceled out. This reduces the requirements for eccentric loads and bending moments on the bearings and housing 10, making it easier to ensure assembly clearance and lifespan. Third, the second gear 31 extends into the planetary gear set 40, causing the force flow to close within the inner cavity 10a and shortening the path. The third gear 32, as a transition gear, provides center distance and arrangement freedom, facilitating coaxial or parallel axis arrangement and controlling the overall profile within the narrow inner cavity 10a. In summary, the above solution can meet the predetermined output torque while helping to reduce the size of the components that mate with the external rocker arm and shrink the profile of the gearbox 100.

[0033] In one specific embodiment, a plurality of the first gears are arranged at equal angular intervals around the second gear in the circumferential direction, and the number is at least three.

[0034] In one specific embodiment, each of the first gears is a spur gear and they all have the same module, and the second gear has the same module as the first gear.

[0035] Furthermore, the transmission assembly also includes a first transmission member and a second transmission member. The first transmission member meshes with the driving member, and the second transmission member meshes with both the first transmission member and the third gear.

[0036] It should be noted that, in this embodiment, in addition to the second gear 31 and the third gear 32, the transmission assembly 30 also includes a first transmission member 33 and a second transmission member 34. All four are arranged in the inner cavity 10a of the housing 10 and are arranged sequentially along the length of the housing to adapt to the narrow space. The first transmission member 33 is a coaxial large / small compound gear, with its large teeth located on the side close to the drive member 20 to mesh with the drive member 20.

[0037] In one specific embodiment, the drive unit 22 of the motor meshes with the large teeth of the first transmission member 33, thereby completing the initial speed ratio within the inner cavity 10a and "introducing" power from the drive member 20 to the transmission assembly 30. The small teeth of the first transmission member 33 mesh with the large teeth of the second transmission member 34, which is also a coaxial large / small compound gear. This meshing relationship further completes the transition of speed ratio and wheelbase. The small teeth of the second transmission member 34 mesh with the third gear 32, which meshes stably with the second gear 31 at the designed center distance. The second gear 31 is located at the center of the planetary gear set 40 and extends into its envelope, thereby simultaneously meshing with multiple first gears 41 and sending power to the external rocker arm.

[0038] In summary, the drive component 20 first drives the large tooth of the first transmission component 33, and the power of 33 is transmitted to the large tooth of the second transmission component 34 through its small tooth. 34 then drives the third gear 32 with its small tooth, and the third gear 32 drives the second gear 31. The second gear 31 meshes with each of the first gears 41 in the planetary gear set 40 and distributes the torque in parallel to each point in the circumference. Finally, the output is completed by meshing with the external rocker arm.

[0039] In this embodiment, through a two-stage composite transmission of "33→34", the drive component 20 can obtain the required wheelbase conversion and speed ratio accumulation within the inner cavity 10a. The third gear 32 only provides transition and arrangement freedom, while the second gear 31 is positioned closest to the planetary gear set 40 to shorten the power flow path. Since the second gear 31 meshes with multiple first gears 41 simultaneously, the torque is distributed at multiple points in the circumferential direction, reducing the load on a single meshing pair. Therefore, it is not necessary to enlarge the outer diameter of a single gear at the point of engagement with the external rocker arm to achieve the predetermined output torque. Overall, it is more conducive to achieving a small outline, low noise, and reliable embedded arrangement within a narrow window frame.

[0040] It is understandable that the first transmission component 33 and the second transmission component 34 can be a gear set structure consisting of large and small gears, or other structures such as chains or crank-slider blocks that can transmit the driving force of the drive component 20.

[0041] Furthermore, the driving component includes a motor and a driving part disposed on the motor drive shaft, the driving part being engaged with the first transmission component.

[0042] It should be noted that, in this embodiment, the drive unit 20 is composed of a motor 21 and a drive part 22 disposed at the end of the drive shaft of the motor 21. The motor 21 is arranged at one end of the inner cavity 10a of the housing 10, and the drive shaft extends out along the length direction of the inner cavity 10a. The drive part 22 is coaxially fixed to the drive shaft and acts as the driving member, meshing only with the large gear of the first transmission member 33 to introduce power into the transmission assembly 30.

[0043] In this embodiment, the drive unit 20 consists of a motor 21 and a drive part 22 disposed at the end of the drive shaft of the motor 21. The motor 21 is fixed to one end of the inner cavity 10a of the housing 10, and the drive shaft extends into the inner cavity 10a along its length. The drive part 22 is coaxially fixed to the end of the drive shaft and acts as the driving member, cooperating with the first transmission member 33. The first transmission member 33 is a coaxial compound gear, with its "large gear portion" facing the drive unit 20 to mesh with the drive part 22, and its "small gear portion" facing the subsequent stage (the subsequent stage will not be described further).

[0044] Specifically, the drive unit 22 and the large gear portion of the first transmission member 33 are arranged opposite each other under the condition that the center distance is parallel to the shaft, and both are located in the inner cavity 10a to form the first-stage transmission pair. The motor 21 outputs speed / torque, which drives the large gear portion of the first transmission member 33 to rotate via the drive unit 22, completing the initial force introduction and deceleration. Subsequently, the small gear portion of the first transmission member 33 transmits the power to the subsequent stages.

[0045] In this embodiment, the drive unit 22 is located at the drive shaft end of the motor 21 and is in the form of a helical gear. The first transmission member 33 and the second transmission member 34 are both gear sets (coaxial large and small compound gears). All three are arranged in the inner cavity 10a of the housing 10 and are arranged sequentially along the length direction. The drive unit 22 and the "large gear part" of the first transmission member 33 are externally meshed under the design center distance and parallel axis conditions, and are positioned opposite each other to form a primary transmission pair.

[0046] Specifically, the motor 21 drives the drive unit 22 to rotate, and the drive unit 22 meshes with the large gear portion of the first transmission member 33, introducing power into the first transmission member 33 and causing the first transmission member 33 to move around its own axis; then the small gear portion of the first transmission member 33 meshes with the large gear portion of the second transmission member 34, further transmitting power to the second transmission member 34.

[0047] In summary, by using a helical gear drive unit 22 to engage with the large gear portion of the first transmission component 33, a high degree of meshing overlap and continuous meshing characteristics can be obtained within the confined cross section of the inner cavity 10a. The first-stage transmission is smoother, and the unit tooth surface load and torque pulsation are lower, providing a larger design margin for subsequent speed ratio accumulation and wheelbase transition achieved by gear sets 33 and 34. The axial component force generated by the helical gear meshing is absorbed by the support system within the inner cavity 10a, and the force flow is closed within the housing 10, thereby achieving effective driving of the first transmission component 33 without increasing the size of the exposed gears, and laying the foundation for the miniaturization and noise control of subsequent stages of the transmission assembly 30.

[0048] In one specific embodiment, the planetary gear set further includes a planet carrier, and each of the first gears is rotatably mounted on the planet carrier via a rotating shaft, the planet carrier being fixed to the housing.

[0049] In this embodiment, the planetary gear set 40 is provided with a planet carrier 50, and a plurality of first gears 41 are respectively mounted on the planet carrier 50 in a rotatable manner through their respective shafts. The planet carrier 50 is fixed in the inner cavity 10a of the housing 10 and does not rotate relative to the housing 10.

[0050] Specifically, the planet carrier 50 is arranged around the second gear 31, and the first gear 41 is distributed at equal angles along the circumference of the planet carrier 50. Its axis is parallel to the axis of the second gear 31 and opposite to the tooth width area of ​​the second gear 31, so as to ensure that after the second gear 31 extends axially into the planet gear set 40, it can stably mesh with each of the first gears 41 in the same meshing zone.

[0051] Furthermore, the second gear 31 rotates after being driven by the third gear 32, causing all the first gears 41 to rotate on their own axis. Since the planet carrier 50 is fixed to the housing 10, the first gear 41 only rotates on its own axis and does not revolve with the planet carrier 50. The reaction force from the meshing with the second gear 31 is transmitted to the planet carrier 50 through the shaft of the first gear 41, and then transmitted from the planet carrier 50 to the housing 10 to complete the closed force flow.

[0052] In summary, the planetary carrier 50 serves as the common support reference for the first gear 41, locking the center distance and axial position between each first gear 41 and the second gear 31 on the same geometric reference, thereby ensuring that the condition of "the second gear 31 simultaneously meshing with each first gear 41" is continuously met during assembly and operation. Furthermore, the first gear 41 is circumferentially surrounded and is angularly positioned by the planetary carrier 50. The radial forces acting on the second gear 31 cancel each other out in the circumferential direction, reducing the requirements for off-center load and bending moment, which is beneficial for maintaining a miniaturized bearing and housing structure within the inner cavity 10a.

[0053] Furthermore, each of the first gears 41 rotates independently via its shaft, causing the torque output by the second gear 31 to be shared in parallel across multiple meshing pairs. This reduces the load on a single pair and, in conjunction with the meshing action of the outer side and the external rocker arm, achieves stable output and a compact size arrangement.

[0054] Example 2 This second embodiment provides a rocker arm assembly, including a gearbox and a rocker arm (not shown) as in the first embodiment, wherein the rocker arm is connected to the transmission assembly.

[0055] It should be noted that the gearbox in this second embodiment is exactly the same as the gearbox in the first embodiment, and therefore has the same beneficial effects, which will not be repeated here.

[0056] Example 3 This third embodiment provides a window, including a rocker arm assembly as in embodiment two.

[0057] It should be noted that the rocker arm assembly in this second embodiment is exactly the same as the rocker arm assembly in the first embodiment, and therefore has the same beneficial effects, which will not be repeated here.

[0058] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0059] The embodiments described above are merely illustrative of several implementation methods of this application, and while the descriptions are specific and detailed, they should not be construed as limiting the scope of this patent application. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this application, and these all fall within the protection scope of this application. Therefore, the protection scope of this patent application should be determined by the appended claims.

Claims

1. A gearbox, comprising a housing and a drive component, wherein the housing has an inner cavity, and the drive component is disposed within the inner cavity, characterized in that, The gearbox also includes: A transmission assembly is disposed in the inner cavity, and the transmission assembly is respectively engaged with the driving member and the external rocker arm; The planetary gear set is composed of multiple first gears meshing around each other. The transmission component extends into the planetary gears and meshes with each first gear simultaneously, in order to cooperate with the transmission component to transmit the driving force of the drive member to the external rocker arm.

2. The gearbox according to claim 1, characterized in that, The transmission assembly includes a second gear and a third gear; The second gear extends into the planetary gear set and simultaneously meshes with each of the first gears, and the third gear meshes with the second gear and is connected to the drive unit for transmission.

3. The gearbox according to claim 2, characterized in that, Multiple first gears are arranged at equal angular intervals around the second gear in the circumferential direction, and the number is at least three.

4. The gearbox according to claim 2, characterized in that, Each of the first gears is a spur gear and has the same module, and the second gear has the same module as the first gear.

5. The gearbox according to claim 2, characterized in that, The transmission assembly further includes a first transmission component and a second transmission component. The first transmission component meshes with the driving component, and the second transmission component meshes with the first transmission component and the third gear, respectively.

6. The gearbox according to claim 5, characterized in that, The driving component includes a motor and a driving part disposed on the motor drive shaft, the driving part being engaged with the first transmission component.

7. The gearbox according to claim 6, characterized in that, The driving part is a helical gear, and the first transmission member and the second transmission member are a gear set. The driving part meshes with the first transmission member and is used to drive the first transmission member to move.

8. The gearbox according to claim 1, characterized in that, The planetary gear set also includes a planet carrier, and each of the first gears is rotatably mounted on the planet carrier via a rotating shaft, the planet carrier being fixed to the housing.

9. A rocker arm assembly, characterized in that, It includes a rocker arm and a gearbox as described in any one of claims 1-8, wherein the rocker arm is connected to the transmission assembly.

10. A window, characterized in that, Includes the rocker arm assembly as described in claim 9.

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