Speed reducer and multi-stage gear transmission module thereof

Abstract

The utility model belongs to the technical field of speed reducer equipment, specifically relates to a speed reducer and multistage gear transmission module thereof, and the speed reducer comprises: a box body, at least four mutually parallel transmission shafts rotatably arranged in the box body, and the at least four transmission shafts comprising an input shaft and an output shaft, and at least one end of the input shaft and the output shaft extending to outside the box body, a plurality of pairs of gear pairs arranged on the transmission shafts, the plurality of pairs of gear pairs being sequentially meshed to form at least three-stage transmission, the total transmission ratio of the multistage transmission being not less than 80:1, and in the plurality of pairs of gear pairs, the first-stage gear pair driven by the input shaft being a helical gear pair.

Description

Technical Field

[0001] This utility model belongs to the technical field of speed reducer equipment, and in particular relates to a speed reducer and its multi-stage gear transmission module. Background Technology

[0002] A speed reducer is a power transmission mechanism widely used in industrial machinery, automated equipment, and transportation vehicles. Its core function is to reduce speed and increase output torque through gear meshing.

[0003] Currently, in operating conditions requiring a large transmission ratio (≥50:1), single-stage gear transmissions suffer from inherent drawbacks such as significant size differences between the driving and driven gears, excessive concentration of meshing stress, and susceptibility to severe vibration and high-frequency noise. Therefore, those skilled in the art generally employ multi-stage transmission mechanisms. However, even with multi-stage transmission schemes, when dealing with extreme conditions of ultra-large speed ratios (≥80:1) and high torque output, the linear velocity of the high-speed gears is extremely high to achieve the ultra-large speed ratio, and their meshing impact remains the main source of noise, resulting in significant vibration and noise problems.

[0004] Therefore, how to solve the problem of excessive vibration and noise in reducers under ultra-high speed ratio conditions is a technical problem that urgently needs to be solved by those skilled in the art.

[0005] It should be noted that the information disclosed in this background section is only for understanding the background technology of the present application concept, and therefore, the above description is not considered to constitute prior art information. Utility Model Content

[0006] This disclosure provides at least one speed reducer and its multi-stage gear transmission module.

[0007] In a first aspect, embodiments of this disclosure provide a speed reducer, comprising: Box; At least four parallel drive shafts are rotatably disposed within the housing; and each drive shaft includes an input shaft and an output shaft, with at least one end of the input shaft and the output shaft extending outside the housing. Multiple pairs of gears are respectively mounted on the drive shaft; The multiple pairs of gears mesh sequentially to form at least three stages of transmission, and the total transmission ratio of the at least three stages of transmission is not less than 80:1; Among the multiple pairs of gear pairs, the first-stage gear pair driven by the input shaft is a helical gear pair.

[0008] In one alternative implementation, all of the multiple gear pairs are helical gear pairs.

[0009] In one alternative embodiment, the helical gear pairs have opposite helix angles between adjacent gear pairs.

[0010] In one alternative embodiment, the helix angle of the helical gear pair is 8° to 15°.

[0011] In one alternative implementation, the diameter of the output shaft is larger than the diameter of the input shaft.

[0012] In one alternative embodiment, the drive shaft is supported on the housing by rolling bearings, which are either angular contact ball bearings or tapered roller bearings.

[0013] In one alternative embodiment, the output shaft and / or input shaft are connected to the housing via a flange, and an annular vibration damping pad is provided at the connection between the flange and the housing.

[0014] Secondly, embodiments of this disclosure also provide a multi-stage gear transmission module for a speed reducer, comprising: At least four parallel drive shafts, including an input shaft for receiving power and an output shaft for outputting power; Multiple pairs of gears are respectively mounted on the drive shaft; The multiple pairs of gears mesh sequentially to form at least three stages of transmission, and the total transmission ratio of the at least three stages of transmission is not less than 80:1; Among the multiple pairs of gear pairs, the first-stage gear pair driven by the input shaft is a helical gear pair.

[0015] In one optional implementation, all of the multiple pairs of gears are helical gear pairs; Alternatively, the helix angle of the helical gear pair is 8° to 15°; Alternatively, the diameter of the output shaft is larger than the diameter of the input shaft.

[0016] In one alternative embodiment, the helical gear pairs have opposite helix angles between adjacent gear pairs.

[0017] The beneficial effect of this utility model is that the gear pair driven by the input shaft of this reducer (i.e., the high-speed gear pair) adopts a helical gear pair structure. By utilizing the high meshing overlap of helical gears, the impact force of meshing and disengaging is effectively reduced, thereby reducing transmission noise.

[0018] Other features and advantages of this invention will be set forth in the description which follows, and will be apparent in part from the description, or may be learned by practicing the invention. The objectives and other advantages of this invention are realized and obtained through the structures particularly pointed out in the description and drawings.

[0019] To make the above-mentioned objectives, features and advantages of this utility model more apparent and understandable, preferred embodiments are described in detail below with reference to the accompanying drawings. Attached Figure Description

[0020] To more clearly illustrate the specific embodiments of this utility model or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0021] Figure 1 This is an internal structural diagram of a speed reducer provided in an embodiment of the present disclosure; Figure 2 This is a perspective view of a speed reducer provided in an embodiment of the present disclosure.

[0022] In the picture: 100. Housing; 200. Drive shaft; 210. Input shaft; 220. Output shaft; 230. First intermediate shaft; 240. Second intermediate shaft; 300. Gear pair; 310. First stage pinion; 320. First stage gear; 330. Second stage pinion; 340. Second stage gear; 350. Third stage pinion; 360. Third stage gear; 400. Rolling bearing; 500. Annular vibration damping pad; 600. Flange. Detailed Implementation

[0023] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.

[0024] In this document, when it is mentioned that a first component is located on a second component, this can mean that the first component can be directly formed on the second component, or that a third component can be inserted between the first and second components. Furthermore, in the accompanying drawings, the thickness of the components may be exaggerated or reduced for the purpose of effectively describing the technical content.

[0025] In this document, when an element or layer is referred to as “located,” “joined to,” “connected to,” “attached to,” or “coupled to” another element or layer, it may be directly located, joined, connected, attached to, or coupled to the other element or layer, or there may be intermediate elements or layers present. Conversely, when an element is referred to as “directly on another element or layer,” “directly joined to,” “directly connected to,” “directly attached to,” or “directly coupled to” another element or layer, there may be no intermediate elements or layers present. Other terms used to describe relationships between elements should be interpreted in a similar manner (e.g., “between” versus “directly between,” “adjacent” versus “directly adjacent,” etc.). As used herein, the term “and / or” includes any and all combinations of one or more of the related listed items.

[0026] In this document, exemplary embodiments of the present disclosure will be described in more detail with reference to the accompanying drawings. As used herein, expressions such as “at least one of…” modify the entire list of elements when following a list of elements, rather than individual elements in the list. For example, the expression “at least one of a, b, and c” should be understood to include only a, only b, only c, both a and b, both a and c, both b and c, or all of a, b, and c.

[0027] The terminology used herein is for the purpose of describing specific exemplary configurations only and is not intended to be limiting. As used herein, the singular articles “a,” “an,” and “the” may also be intended to include plural forms unless otherwise clearly stated herein. The terms “comprising,” “including,” and “having” are inclusive and thus specify the presence of features, steps, operations, elements, and / or components, but do not preclude 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 should not be construed as requiring them to be performed in the specific order discussed or shown, unless specifically identified as such. Additional or alternative steps may be employed.

[0028] As used herein, the phrases “in one embodiment,” “according to one embodiment,” “in some embodiments,” etc., generally refer to the fact that a particular feature, structure, or characteristic following the phrase can be included in at least one embodiment of this disclosure. Therefore, a particular feature, structure, or characteristic can be included in more than one embodiment of this disclosure, such that these phrases do not necessarily refer to the same embodiment. As used herein, the terms “example,” “exemplary,” etc., are used to “serve as an example, instance, or illustration.” Any implementation, aspect, or design described herein as “example” or “exemplary” is not necessarily to be construed as preferred or superior to other implementations, aspects, or designs. Rather, the use of the terms “example,” “exemplary,” etc., is intended to present concepts in a specific manner.

[0029] Research has revealed the following drawbacks of existing technologies: Currently, under operating conditions requiring a large transmission ratio (≥50:1), single-stage gear transmissions suffer from inherent defects such as significant size differences between the driving and driven gears, excessive concentration of meshing stress, and susceptibility to severe vibration and high-frequency noise. Therefore, those skilled in the art generally employ multi-stage transmission mechanisms. However, even with multi-stage transmission schemes, when dealing with extreme conditions of ultra-large speed ratios (≥80:1) and high torque output, the linear velocity of the high-speed gears is extremely high to achieve the ultra-large speed ratio, and their meshing impact remains the main source of noise, resulting in significant vibration and noise problems.

[0030] Based on the above research, this disclosure provides a speed reducer that uses a helical gear pair in the high-speed stage, which effectively overcomes the defect of severe meshing impact of spur gears during high-speed transmission and solves the above-mentioned problems.

[0031] The shortcomings of the above solutions are the result of the inventor's practical experience and careful research. Therefore, the discovery process of the above problems and the solutions proposed in this disclosure should be considered as the inventor's contribution to this disclosure.

[0032] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0033] The following detailed description, with reference to the accompanying drawings, describes some embodiments of the present invention. Unless otherwise specified, the following embodiments and features can be combined with each other.

[0034] See Figure 2 This disclosure provides a speed reducer, including: a housing 100, which is typically made of cast iron and has an internal cavity for accommodating transmission components. The outer wall of the housing 100 is provided with multiple mounting bosses and bolt holes for securely mounting the entire speed reducer to a device base.

[0035] See Figure 1The housing 100 contains at least four parallel drive shafts 200. In this embodiment, the number of drive shafts 200 is four, namely, an input shaft 210, a first intermediate shaft 230, a second intermediate shaft 240, and an output shaft 220. One end of the input shaft 210 extends outside the housing 100 and is connected to the output shaft 220 of the motor. Similarly, one end of the output shaft 220 extends outside the housing 100 and is used to connect the load. Multiple pairs of gears 300 are fixedly mounted on the drive shafts 200, and the gears 300 mesh sequentially to form a three-stage transmission. Specifically: the first-stage gear pair 300 consists of a first-stage pinion 310 fixedly mounted on the input shaft 210 and a first-stage gear 320 fixedly mounted on the first intermediate shaft 230 meshing with each other. The second-stage gear pair 300 consists of a second-stage pinion 330 fixedly mounted on the first intermediate shaft 230 and a second-stage gear 340 fixedly mounted on the second intermediate shaft 240 meshing with each other. The third-stage gear pair 300 consists of a third-stage pinion 350 fixedly mounted on the second intermediate shaft 240 and a third-stage large gear 360 fixedly mounted on the output shaft 220, which mesh with each other. By rationally configuring the number of teeth in each gear pair 300, the overall transmission ratio of the above three-stage transmission is not less than 80:1, thereby achieving significant deceleration and torque increase. Among the multiple gear pairs 300, the first-stage gear pair 300 driven by the input shaft 210 (i.e., the first-stage pinion 310 and the first-stage large gear 320) is a helical gear pair. Since the first-stage transmission operates at high speed, its rotational speed is the highest, making it the main source of gear meshing impact and noise. Using a helical gear pair can take advantage of its high overlap ratio and smooth meshing characteristics to significantly reduce high-speed meshing impact and noise directly from the noise source, thereby reducing the overall machine operating noise.

[0036] See also Figure 1 In some embodiments, all gear pairs 300 in this embodiment, namely the first-stage gear pair 300, the second-stage gear pair 300, and the third-stage gear pair 300, adopt a helical gear pair 300 structure. The first-stage gear pair 300, driven by the input shaft 210, operates at its highest speed and is the main source of meshing impact and air noise. Using helical gears here can utilize their high overlap ratio and smooth meshing characteristics to directly suppress noise at the source. Although the speeds of the second-stage and third-stage gear pairs 300 decrease progressively, the torque they transmit is enormous. Due to their meshing characteristics, the helical gear pair 300 has a larger contact area and a more uniform stress distribution, which not only helps to further reduce noise during low- and medium-speed operation but also significantly improves the load-bearing capacity and durability of the gears.

[0037] See also Figure 1 In some embodiments, the helix angle of the helical gear pair 300 is optimized to be in the range of 8° to 15°, preferably 12°.

[0038] See also Figure 1 In some embodiments, in multiple pairs of helical gear pairs 300, the helix angles of adjacent gear pairs are opposite. Specifically, the gears mounted on the first intermediate shaft 230 (i.e., the first-stage large gear 320 and the second-stage small gear 330) have the same helix direction; while the gears mounted on the second intermediate shaft 240 (i.e., the second-stage large gear 340 and the third-stage small gear 350) have the opposite helix direction. Thus, two pairs of gear pairs 300 with opposite helix directions are formed. Since helical gears generate axial force during transmission, the opposite helix direction of the gears on the aforementioned different shafts results in the axial forces on the first intermediate shaft 230 and the second intermediate shaft 240 being in opposite directions. These axial forces in opposite directions are transmitted to the housing 100 through the shafts and bearings, and can partially cancel each other out, thereby greatly reducing the load on the bearing housing of the housing 100, effectively suppressing the deformation and vibration of the housing 100 that may be caused by the imbalance of axial forces, and thus reducing the noise caused by the vibration of the housing 100.

[0039] See also Figure 1 In some embodiments, the diameter of the output shaft 220 is larger than the diameter of the input shaft 210. In the reduction gear transmission, the rotational speed decreases step by step, while the torque increases step by step. As the final power output end, the output shaft 220 bears the largest torque value, which is much higher than the initial torque borne by the input shaft 210. Using a larger diameter for the output shaft 220 ensures that it has sufficient torsional strength to effectively resist the bending deformation caused by gear meshing forces, thereby maintaining a relatively precise meshing position between the third-stage large gear 360 and the third-stage small gear 350, which are fixedly connected to it. By increasing the diameter of the output shaft 220, vibration, impact, and wear noise caused by meshing misalignment due to shaft deformation are avoided.

[0040] See also Figure 1 In some embodiments, the drive shaft 200 is supported on the housing 100 by rolling bearings 400, preferably angular contact ball bearings or tapered roller bearings. Angular contact ball bearings and tapered roller bearings are ideal bearings specifically designed to withstand combined loads. Their unique raceway design enables them to withstand pure axial loads from one or both directions, while also supporting heavy combined loads, providing axial preload to the drive shaft 200, and contributing to improved axial and radial stiffness of the entire shaft system.

[0041] See Figure 2In some embodiments, an annular damping pad 500 is provided at the flange 600 connection between the output shaft 220 and the input shaft 210 and the housing 100. Vibrations generated by the meshing of gears inside the reducer are transmitted through the shaft system to the output flange 600, and then through the rigid connection to the housing 100, radiating noise outwards. Preferably, the annular damping pad 500 is made of rubber, polyurethane, or other polymer damping materials, with an elastic modulus much lower than that of the metal housing 100. The annular damping pad 500 forms a highly damped elastic vibration isolation layer at the flange 600 connection, effectively attenuating the transmission of vibration energy along this path.

[0042] The above is merely a preferred embodiment of this utility model (three-stage transmission). Those skilled in the art will readily recognize that the number of transmission stages can be increased to achieve a larger overall transmission ratio or more optimized load distribution. For example, five transmission shafts can be used to achieve four-stage transmission, or six transmission shafts can be used to achieve five-stage transmission. This can be achieved simply by increasing the number of intermediate shafts and the number of gear pairs according to the same design principles described above.

[0043] See also Figure 1 Some embodiments also provide a multi-stage gear transmission module for a speed reducer, comprising: at least four parallel transmission shafts 200, including an input shaft 210 for receiving power and an output shaft 220 for outputting power; multiple pairs of gear pairs 300, respectively disposed on the transmission shafts 200; the multiple pairs of gear pairs 300 meshing sequentially to form at least three stages of transmission, the total transmission ratio of the multi-stage transmission being not less than 80:1; among the multiple pairs of gear pairs 300, the first stage gear pair 300 driven by the input shaft 210 is a helical gear pair 300.

[0044] In summary, the gear pair 300 driven by the input shaft 210 of this reducer (i.e., the high-speed gear pair 300) adopts a helical gear pair 300 structure. By utilizing the high meshing overlap of helical gears, the impact force of meshing and disengaging is effectively reduced, thereby reducing transmission noise.

[0045] In the description of the embodiments of this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0046] In the description of this utility model, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model. Furthermore, terms such as "first," "second," and other numerical terms used herein do not imply order or sequence unless expressly indicated herein. Therefore, without departing from the teachings of the exemplary embodiments, the first element, component, region, layer, or segment discussed above may be referred to as the second element, component, region, layer, or segment.

[0047] Spatially relative terms, such as “inside,” “outside,” “below,” “below,” “down,” “above,” “up,” etc., may be used herein to describe the relationship between one element or feature illustrated in the figures and another element or feature. In addition to the orientations depicted in the figures, spatially relative terms may be intended to cover different orientations of the device in use or operation. For example, if the device in the figure is flipped, an element described as “below” or “below” other elements or features would be oriented as “above” other elements or features. Thus, the example term “below” can cover both above and below orientations. The device may be oriented in other ways (rotated 90 degrees or in other orientations), and the spatially relative descriptors used herein are interpreted accordingly.

[0048] In the above discussion, unless otherwise stated, when used to describe numerical values, the terms “about,” “approximately,” “basically,” etc., indicate a change of + / - 10% in that value.

[0049] Based on the above-described preferred embodiments of this utility model, and through the foregoing description, those skilled in the art can make various changes and modifications without departing from the technical concept of this utility model. The technical scope of this utility model is not limited to the contents of the specification, but must be determined according to the scope of the claims.

Claims

1. A speed reducer, characterized in that, include: Box (100); At least four parallel drive shafts (200) are rotatably disposed within the housing (100); The drive shaft (200) includes an input shaft (210) and an output shaft (220), at least one end of the input shaft (210) and the output shaft (220) extending outside the housing (100); Multiple pairs of gears (300) are respectively disposed on the drive shaft (200); The multiple pairs of gears (300) mesh sequentially to form at least three levels of transmission, and the total transmission ratio of the at least three levels of transmission is not less than 80:1; Among the multiple pairs of gear pairs (300), the first-stage gear pair driven by the input shaft (210) is a helical gear pair.

2. The speed reducer as described in claim 1, characterized in that, All of the multiple gear pairs (300) are helical gear pairs (300).

3. The speed reducer as described in claim 2, characterized in that, In the helical gear pair (300), the helix angles of adjacent gear pairs are opposite.

4. The speed reducer as described in claim 1, characterized in that, The helix angle of the helical gear pair (300) is 8° to 15°.

5. The speed reducer as described in claim 1, characterized in that, The diameter of the output shaft (220) is larger than the diameter of the input shaft (210).

6. The speed reducer as described in claim 1, characterized in that, The drive shaft (200) is supported on the housing (100) by a rolling bearing (400), which is an angular contact ball bearing or a tapered roller bearing.

7. The speed reducer as described in claim 1, characterized in that, The output shaft (220) and / or input shaft (210) are connected to the housing (100) via a flange (600), and an annular damping pad (500) is provided at the connection between the flange (600) and the housing (100).

8. A multi-stage gear transmission module for a speed reducer, characterized in that, include: At least four parallel drive shafts (200), including an input shaft (210) for receiving power and an output shaft (220) for outputting power. Multiple pairs of gears (300) are respectively disposed on the drive shaft (200); The multiple pairs of gears (300) mesh sequentially to form at least three levels of transmission, and the total transmission ratio of the at least three levels of transmission is not less than 80:1; Among the multiple pairs of gear pairs (300), the first-stage gear pair driven by the input shaft (210) is a helical gear pair.

9. The multi-stage gear transmission module as described in claim 8, characterized in that, All of the multiple pairs of gears (300) are helical gear pairs; Alternatively, the helix angle of the helical gear pair (300) is 8° to 15°; Alternatively, the diameter of the output shaft (220) is larger than the diameter of the input shaft (210).

10. The multi-stage gear transmission module as described in claim 9, characterized in that, In the helical gear pair (300), the helix angles of adjacent gear pairs are opposite.

Images