CN113586667A - Worm gear mechanism and electric power steering system - Google Patents
Worm gear mechanism and electric power steering system Download PDFInfo
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- CN113586667A CN113586667A CN202110874996.9A CN202110874996A CN113586667A CN 113586667 A CN113586667 A CN 113586667A CN 202110874996 A CN202110874996 A CN 202110874996A CN 113586667 A CN113586667 A CN 113586667A
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- worm
- bearing
- gear mechanism
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
- F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
- F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/50—Photovoltaic [PV] energy
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Power Steering Mechanism (AREA)
- Gear Transmission (AREA)
Abstract
The invention discloses a worm gear mechanism and an electric power steering system, and belongs to the technical field of vehicles. The worm and gear mechanism comprises a shell, a worm and a worm wheel which are rotatably arranged in the shell, and a supporting assembly, wherein the supporting assembly comprises a worm supporting unit and an axial elastic piece, one end of the axial elastic piece is elastically abutted against the input end of the worm, and the other end of the axial elastic piece is used for supporting an output shaft of a motor; the worm support unit comprises a self-aligning bearing, a floating bearing and an elastic support assembly, axial pretightening force is provided for the worm by the aid of the axial elastic piece, floating support is provided for the floating bearing by the aid of the elastic support assembly, and the worm can be adjusted in position adaptability relative to the worm wheel in radial and axial directions. The electric power steering system comprises the driving gear shaft and the worm gear mechanism, and friction torque loss between a worm gear and a worm is reduced and noise is reduced by applying the worm gear mechanism.
Description
Technical Field
The invention relates to the technical field of vehicles, in particular to a worm gear mechanism and an electric power steering system.
Background
The double-pinion electric power-assisted steering system adopts a worm gear structure for transmission, and can reduce carbon emission by more than 6% compared with a hydraulic power-assisted steering system; compared with the existing single-gear electric power steering system and the like, the driving force has great advantages, and the boundary of 12KN can be broken through; compared with the existing belt type electric power steering system and the like, the cost price can be reduced by more than 20%, and the belt type electric power steering system has a wide application prospect and is increasingly applied to the field of intelligent driving.
In the existing double-pinion electric power steering system, the worm is mostly installed in a fixed mode, on one hand, the meshing force between the worm wheel and the worm is fixed in the fixed installation mode, assembly stress is easy to generate, on the other hand, an assembly gap is easy to occur between the worm wheel and the worm, and along with the increase of the service time of the worm wheel and the worm, the gap between the worm wheel and the worm can also be increased. The excessive assembly stress can cause the pressure between the worm and the gear and the loss of transmission friction torque to be increased, and even the phenomenon of self-locking and locking of the transmission of the worm and the gear can occur; and too large clearance can lead to the unstable transmission of the worm gear and the worm, and noise and torque fluctuation are easy to generate.
To this end, in the prior art, the worm is supported by the self-aligning bearing and the deep groove ball bearing, and the deep groove ball bearing on the worm is supported by the bearing seat with the C-shaped structure, so that the worm is installed in a floating manner, and the above problems are improved to a certain extent. However, due to the floating installation of the worm, the contact between the worm and the output shaft of the motor is unstable, the meshing between the worm and the worm wheel is further influenced, the problems of transmission friction torque increase and noise still exist, and the performance of the electric power steering system after durability is influenced.
Disclosure of Invention
The invention aims to provide a worm and gear mechanism which is beneficial to reducing the transmission friction torque loss between worm and gears, reducing noise and improving the durable performance of the worm and gear.
Another object of the present invention is to provide an electric power steering system, which reduces friction torque loss between worm gears and worm gears by applying the above worm gear mechanism, and simultaneously reduces noise and also improves durability of the worm gears and worm gears.
In order to realize the purpose, the following technical scheme is provided:
in one aspect, a worm and gear mechanism is provided, comprising:
a housing;
the worm and the worm wheel are rotatably arranged in the shell and are meshed with each other, and the worm is provided with an input end which is in transmission connection with an output shaft of the motor;
and a support assembly comprising:
the worm supporting unit comprises a self-aligning bearing, a floating bearing and an elastic supporting assembly, an inner ring of the self-aligning bearing and an inner ring of the floating bearing are fixed on the worm at intervals, an outer ring of the self-aligning bearing is supported on the shell, and the elastic supporting assembly is mounted on the shell, is used for supporting the floating bearing and allows the floating bearing to float relative to the shell;
the support assembly further comprises:
one end of the axial elastic piece is elastically abutted to the input end of the worm, and the other end of the axial elastic piece is used for being supported on an output shaft of the motor; the self-aligning bearing is closer to the axial elastic member than the floating bearing.
As an alternative of the worm and gear mechanism, a first mounting hole is formed in the end face of the input end of the worm, and the axial elastic piece abuts against the bottom wall of the first mounting hole.
As an alternative of the worm gear mechanism, the axial elastic member is a spring, the worm gear mechanism further includes an axial pressing block, and the axial pressing block includes:
the first block part is inserted with an output shaft of the motor;
the axial elastic piece is sleeved on the first columnar portion and abuts against the first blocky portion.
As an alternative of the worm gear mechanism, a coupler is further arranged at the input end of the worm, and the input end of the worm and the output shaft of the motor are respectively inserted at two ends of the coupler.
As an alternative to the worm gear mechanism, the elastic support assembly includes a flexible washer, and the flexible washer is mounted to the housing and sleeved on the outer ring of the floating bearing.
As an alternative to the worm gear mechanism, the elastic support assembly further includes a bearing knock pin passing through the flexible washer and abutting against an outer ring of the floating bearing, and a radial elastic member having one end elastically abutting against the bearing knock pin and the other end supported against the housing, and capable of driving the bearing knock pin to move so as to bias the worm gear in a direction approaching the worm wheel.
As an alternative of the worm gear mechanism, the elastic support assembly further comprises a pretightening force adjusting piece, the pretightening force adjusting piece is screwed with the shell, and the radial elastic piece is elastically abutted to the bearing ejector pin and the pretightening force adjusting piece respectively.
As an alternative to the worm gear mechanism, the bearing knock pin comprises:
the first end of the pin head is inserted with the pretightening force adjusting piece;
the pin column is connected to the second end of the pin head, the diameter of the pin column is smaller than that of the pin head, the pin column penetrates through the flexible gasket and is abutted to the outer ring of the floating bearing, and the flexible gasket can be abutted to the pin head.
As an alternative to the worm gear mechanism, the pin head is at least partially inserted into the pretension adjusting piece, and a groove is formed in the outer peripheral surface of the part of the pin head located in the pretension adjusting piece.
As an alternative of the worm gear mechanism, a second mounting hole is formed in the first end face of the pin head, and one end of the radial elastic piece abuts against the bottom wall of the second mounting hole.
As an alternative to the worm gear mechanism, the radial elastic member is a spring, and the elastic support assembly further includes a radial pressing block, and the radial pressing block includes:
the second block-shaped part is abutted against the pretightening force adjusting piece;
the second columnar part is connected with the second block-shaped part, and the radial elastic piece is sleeved on the second columnar part and abutted against the second block-shaped part.
As an alternative to the worm gear mechanism, the bearing knock pin is made of hard plastic; the flexible gasket is made of rubber materials.
As an alternative to the worm gear mechanism, the flexible gasket is provided with a first plug structure, the housing is provided with a second plug structure, and the first plug structure can be plugged with the second plug structure to restrict the flexible gasket from rotating in a circumferential direction thereof.
On the other hand, still provide an electric power assisted steering system, including drive gear axle and as above any the worm gear mechanism, worm wheel fixed mounting be in drive gear axle, drive gear axle still is equipped with shaft shoulder, support bearing and clamp groove, the clamp inslot is equipped with bearing inner circle clamp, the shaft shoulder with bearing inner circle clamp is followed respectively drive gear axle's axial with support the inner circle butt of bearing.
As an alternative of the electric power steering system, the bearing inner race clamp is configured to be filled in the clamp groove after being deformed by extrusion, and an inner diameter of the bearing inner race clamp before being deformed is not smaller than an outer diameter of the drive gear shaft.
As an alternative scheme of the electric power steering system, the side wall of the clamp groove far away from the supporting bearing is provided with a first guide inclined surface, and when the bearing inner ring clamp is extruded and deformed by adopting an extrusion process, the first guide inclined surface is used for providing thrust towards the supporting bearing to the bearing inner ring clamp.
As an alternative of an electric power steering system, the inner wall of the support bearing is provided with a second guide inclined plane, the second guide inclined plane is larger than an included angle between the axes of the bearing inner ring hoop and the first guide inclined plane is larger than an included angle between the axes of the drive gear shaft, and after the bearing inner ring hoop deforms, the second guide inclined plane deforms and is attached to the first guide inclined plane.
As an alternative to an electric power assisted steering system,
an included angle alpha between the first guide inclined plane and the axis of the drive gear shaft, and if the friction coefficient of the first guide inclined plane is mu 1, the angle alpha/mu 1 is greater than or equal to 386.7 degrees and less than or equal to 1240 degrees;
before the bearing inner ring hoop deforms, an included angle between the second guide inclined plane and the axis of the bearing inner ring hoop is beta, the friction coefficient of the second guide inclined plane is mu 2, and beta/mu 2 is larger than or equal to 480 degrees and smaller than or equal to 1560 degrees.
As an alternative to the electric power steering system, the drive gear shaft includes a plain shaft section and a spline shaft section that are simultaneously interference-fitted with the worm wheel, the plain shaft section is located in front of the spline shaft section in the assembling direction of the worm wheel, and the spline shaft section is engaged with the worm wheel.
As an alternative to the electric power steering system, the surface hardness of the clamp groove is greater than the hardness of the bearing inner race clamp.
Compared with the prior art, the invention has the beneficial effects that:
the worm gear mechanism comprises a shell, a worm and a worm wheel which are rotatably arranged in the shell, and a supporting component, wherein the worm and the worm wheel are mutually meshed, and the worm is provided with an input end which is in transmission connection with an output shaft of a motor; the support assembly comprises a worm support unit, the worm support unit comprises a self-aligning bearing, a floating bearing and an elastic support assembly, an inner ring of the self-aligning bearing and an inner ring of the floating bearing are fixed on the worm at intervals, an outer ring of the self-aligning bearing is supported on the shell, the elastic support assembly is installed on the shell and used for supporting the floating bearing, and the floating bearing is allowed to float relative to the shell; the support assembly further comprises an axial elastic piece, one end of the axial elastic piece is elastically abutted to the input end of the worm, and the other end of the axial elastic piece is used for being supported on an output shaft of the motor; the self-aligning bearing is closer to the axial elastic member than the floating bearing. The axial elastic piece is utilized to provide axial pretightening force for the worm, so that the meshing force between the worm and the worm wheel can be adaptively adjusted, and the assembly stress can be avoided; utilize elastic support component to provide the floating support to floating bearing, can make the worm can wind self-aligning bearing to the direction swing of being close to or keeping away from the worm wheel, but make clearance self-adaptation regulation between worm and the worm wheel, the too big phenomenon in clearance can not appear, make on radial and axial two directions, but the worm is adjusted for the position adaptability of worm wheel, be favorable to reducing the transmission friction torque loss between the worm gear, reduce the noise simultaneously, promote the performance after the worm gear is durable, can guarantee the driven stationarity of system.
The electric power steering system comprises the driving gear shaft and the worm gear mechanism, and friction torque loss between the worm gear and the worm is reduced by applying the worm gear mechanism, noise is reduced, and the durability of the worm gear is improved.
Drawings
FIG. 1 is an exploded view of an electric power steering system in accordance with an embodiment of the present invention;
FIG. 2 is a schematic cross-sectional view of a worm gear mechanism in an embodiment of the invention;
FIG. 3 is a schematic view showing the assembly relationship between a worm and a worm wheel according to an embodiment of the present invention;
FIG. 4 is a schematic view of the connection between the output shaft of the motor and the worm gear in the embodiment of the present invention;
FIG. 5 is an enlarged view of portion A of FIG. 4;
FIG. 6 is an exploded view of a flexible support assembly in accordance with an embodiment of the present invention;
FIG. 7 is an exploded view of a flexible support assembly according to another embodiment of the present invention;
FIG. 8 is a schematic view of the construction of a drive gear shaft in an embodiment of the present invention;
FIG. 9 is an enlarged view of portion B of FIG. 8;
FIG. 10 is a schematic view of the assembled relationship of the drive gear shaft and the support bearing in an embodiment of the present invention;
FIG. 11 is a schematic view of the assembly of the drive gear shaft and the bearing inner race clamp before press fitting in the embodiment of the present invention;
FIG. 12 is an enlarged view of section C of FIG. 11;
FIG. 13 is a schematic view of the assembled relationship between the drive gear shaft and the bearing inner race clamp after press fitting in the embodiment of the present invention;
fig. 14 is an enlarged view of a portion D of fig. 13.
Reference numerals:
100. a coupling;
200. an output shaft of the motor; 201. inserting a block;
300. a bearing fastening nut;
1. a drive gear shaft; 11. a light axis segment; 12. a splined shaft section; 13. a clamp groove; 131. a first guide slope; 14. a shaft shoulder;
2. a housing; 21. an end cap;
3. a worm; 31. a first mounting hole;
4. a worm gear;
5. an axial elastic member;
6. a worm support unit; 61. a self-aligning bearing; 62. a floating bearing; 63. an elastic support member; 631. a flexible gasket; 6311. a limiting boss; 6312. a through hole; 632. a bearing knock pin; 6321. a pin head; 6322. a pin; 6323. a groove; 6324. a second mounting hole; 633. a pre-tightening force adjusting piece; 6331. a wrench jack; 634. a radial elastic member;
7a, axial pressing blocks; 7a1, first block; 7a2, a first columnar portion; 7b, radial briquetting; 7b1, second block; 7b2, second cylindrical portion;
8. a support bearing; 81. a bearing outer ring snap ring;
9. a bearing inner ring hoop; 91. a second guide slope.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all, embodiments of the present invention. The components of embodiments of the present invention generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations.
Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, it need not be further defined and explained in subsequent figures.
In the description of the present invention, it should be noted that the terms "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings or orientations or positional relationships that are conventionally placed when the products of the present invention are used, and are used only for convenience of describing the present invention and simplifying the description, but do not indicate or imply that the devices or elements to be referred to must have specific orientations, be constructed in specific orientations, and operate, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," "third," and the like are used solely to distinguish one from another and are not to be construed as indicating or implying relative importance. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
In the description of the present invention, it should also be noted that, unless otherwise explicitly specified or limited, the terms "disposed" and "connected" are to be interpreted broadly, e.g., as being either fixedly connected, detachably connected, or integrally connected; either mechanically or electrically. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.
An input shaft of the electric power steering system is connected with the intermediate shaft, and is used for receiving torque input from a steering wheel of a driver and outputting the torque input to a wheel end. Taking a double-pinion electric power steering system as an example, an existing double-pinion electric power steering system generally includes a worm wheel and a worm, a motor drives the worm to rotate, the worm drives the worm wheel to rotate, and finally, torque is output to a wheel end through a driving gear shaft, so that an auxiliary steering function of the electric power steering system is realized. However, in the existing double-pinion electric power steering system, the worm is supported by arranging the self-aligning bearing and the deep groove ball bearing, and the deep groove ball bearing on the worm is supported by the bearing seat with the C-shaped structure, so that the worm is installed in a floating manner, the loss of pressure between the worm wheel and the worm and the loss of transmission friction torque are increased easily, and even the phenomenon of self-locking and clamping of worm wheel and worm transmission can occur; meanwhile, the worm gear and worm transmission is not stable, and noise and torque fluctuation are easily generated.
In order to solve the above problem, the present embodiment further provides a worm and gear mechanism and an electric power steering system, as shown in fig. 1 to 14, the electric power steering system includes a worm and gear mechanism and a driving gear shaft 1, the worm and gear mechanism includes a housing 2, a worm 3 and a worm wheel 4 rotatably disposed in the housing 2, and a support assembly, the worm 3 and the worm wheel 4 are engaged with each other, and the worm 3 has an input end for being in transmission connection with an output shaft 200 of a motor. The support assembly comprises an axial elastic piece 5 and a worm support unit 6, one end of the axial elastic piece 5 is elastically abutted to the input end of the worm 3, and the other end of the axial elastic piece 5 is used for being supported on an output shaft 200 of the motor; the worm support unit 6 comprises a self-aligning bearing 61, a floating bearing 62 and an elastic support component 63, wherein the inner ring of the self-aligning bearing 61 and the inner ring of the floating bearing 62 are fixed on the worm 3 at intervals, and the self-aligning bearing 61 is closer to the axial elastic piece 5 than the floating bearing 62; the outer race of the self-aligning bearing 61 is supported by the housing 2, and the elastic support member 63 is attached to the housing 2 and used for supporting the floating bearing 62 and allowing the floating bearing 62 to float with respect to the housing 2. Illustratively, the floating bearing 62 is a deep groove ball bearing.
The axial elastic piece 5 is used for providing axial pretightening force for the worm 3, so that the meshing force between the worm 3 and the worm wheel 4 can be adaptively adjusted, and the assembling stress can be avoided; utilize elastic support assembly 63 to provide floating support to floating bearing 62, can make worm 3 can wind self-aligning bearing 61 to the direction swing of being close to or keeping away from worm wheel 4, but make clearance self-adaptation regulation between worm 3 and the worm wheel 4, the too big phenomenon in clearance can not appear, make on radial and axial two directions, but worm 3 is for worm wheel 4's position adaptability adjusts, be favorable to reducing the transmission friction torque loss between worm wheel 4 and the worm 3, reduce the noise simultaneously, promote worm gear mechanism durability, can guarantee the driven stationarity of system.
Specifically, the outer ring of the self-aligning bearing 61 is fixedly mounted on the housing 2, the inner ring of the self-aligning bearing 61 is in interference fit with one end of the worm 3, and the outer ring of the self-aligning bearing 61 is fixed on the housing 2 through a bearing fastening nut 300; the outer ring of the floating bearing 62 is fixed in a floating mode through an elastic supporting assembly 63, and the inner ring of the floating bearing 62 is in interference fit with the other end of the worm 3; in the process of meshing transmission of the worm gear and worm mechanism, the worm 3 can swing at a small angle around the self-aligning bearing 61, and exemplarily, as shown in fig. 3, the worm 3 can swing 5 degrees in the direction close to the worm wheel 4 and also can swing 5 degrees in the direction far away from the worm wheel 4, so that self-adaptive pre-tightening between the worm wheel 4 and the worm 3 can be realized, the assembly stress between the worm wheel and the worm 3 can be reduced, and the occurrence of the phenomenon of jamming of meshing transmission can be avoided.
Further, as shown in fig. 1 and fig. 4, the input end of the worm 3 is further provided with a coupler 100, the input end of the worm 3 and the output shaft 200 of the motor are respectively inserted at two ends of the coupler 100, the input end of the worm 3 is connected with the output shaft 200 of the motor through the coupler 100, and the jamming caused by the misalignment between the axis of the output shaft 200 of the motor and the axis of the worm 3 can be eliminated through the coupler 100. Specifically, the motor drives the worm 3 to rotate, the worm 3 drives the worm wheel 4 to rotate, and the worm wheel 4 transmits the torque to the driving gear shaft 1. In this embodiment, the input end of the driving gear shaft 1 is located in the housing 2 and the worm wheel 4 is fixedly mounted at the input end of the driving gear shaft 1, and the output end of the driving gear shaft 1 is located outside the housing 2 and is used for outputting torque. In other embodiments, the output shaft 200 of the motor and the worm 3 can also be connected through a key for power transmission.
Furthermore, the housing 2 is further provided with an end cover 21, the end cover 21 is covered above the worm wheel 4, and in addition, sealing gaskets are respectively arranged between the portions of the worm 3 and the drive gear shaft 1 extending out of the housing 2 and the housing 2, so that the housing 2 forms a closed structure.
Furthermore, because the worm wheel 4 is fixedly arranged on the driving gear shaft 1, the worm 3 is stressed greatly, and in order to ensure the strength of the worm 3, the worm 3 is made of metal materials; the worm wheel 4 is made of engineering plastics, and compared with a worm wheel made of metal materials in the prior art, meshing impact noise between the worm wheel 4 and the worm 3 can be eliminated. Specifically, the material of the worm wheel 4 may be nylon, or nylon plus fiber made of glass, steel, or the like, so that the worm wheel 4 has high strength and has characteristics of lubrication, wear resistance, and corrosion resistance. Wherein, lubricants such as grease can be added between the worm wheel 4 and the worm 3 to further reduce the coefficient of friction between the worm wheel 4 and the worm 3, improve the mechanical transmission efficiency of the worm wheel 4 and the worm 3 kinematic pair, still can reduce the meshing impact noise between the worm wheel 4 and the worm 3, still can take away the heat of friction accumulation between the worm wheel 4 and the worm 3, play the refrigerated effect. Specifically, as shown in fig. 4 to 5, a first mounting hole 31 is provided on an end surface of the input end of the worm 3, one end of the axial elastic member 5 abuts against a bottom wall of the first mounting hole 31, and the other end of the axial elastic member 5 abuts against an output shaft 200 of the motor. Further, an axial pressing piece 7a is interposed between the axial elastic member 5 and the output shaft 200 of the motor. Further, the axial pressing block 7a is made of non-metal materials such as plastics, and the axial pressing block 7a is clamped between the axial elastic piece 5 and the output shaft 200 of the motor, so that noise caused by direct contact of metal and metal between the axial elastic piece and the output shaft can be avoided.
Further, the axial elastic piece 5 is a spring, the axial pressing block 7a includes a first block part 7a1 and a first column part 7a2, and a slot for inserting the output shaft 200 of the motor is opened on the first end face of the first block part 7a 1; the first column portion 7a2 is connected to the second end of the first block portion 7a1, the axial elastic element 5 is sleeved on the first column portion 7a2, and the axial elastic element 5 abuts against the first block portion 7a1, so that the axial elastic element 5 is not bent or deflected when the axial elastic element 5 is compressed. Specifically, the end of the output shaft 200 of the motor is provided with the insertion block 201, the insertion block 201 can be inserted into the slot of the first block-shaped portion 7a1, and the insertion block 201 is inserted into the slot, so that the output shaft 200 of the motor can be ensured to be stably contacted with the axial pressing block 7 a. In the working process, the position of the worm 3 relative to the worm wheel 4 can generate slight change along the axial direction of the worm 3, and the output shaft 200 of the motor can tightly abut against the worm 3 by compressing the axial elastic piece 5 to realize real-time meshing pre-tightening of the worm wheel 4 and the worm 3. In order to further reduce the friction Noise, a lubricant such as grease may be applied between the axial pressing block 7a and the axial elastic member 5, so as to improve NVH (Noise, Vibration, and Harshness) performance of the double-pinion electric power steering system during operation.
Specifically, as shown in fig. 6 to 7, the elastic support member 63 includes a flexible washer 631, the flexible washer 631 has elasticity, and the flexible washer 631 is mounted to the housing 2 and sleeved on the outer ring of the floating bearing 62. Illustratively, the flexible gasket 631 is made of a rubber material. The worm 3 can press the flexible washer 631 through the floating bearing 62 to deform the flexible washer 631, so that the worm 3 can slightly swing in a direction close to or away from the worm wheel 4, thereby alleviating the problem of excessive assembly stress or excessive clearance between the worm 3 and the worm wheel 4. In addition, the flexible gasket 631 can deform, has the functions of damping vibration attenuation and noise reduction, and improves the NVH performance of the double-pinion electric power steering system in the operation process.
Further, in the present embodiment, the flexible gasket 631 is provided with a first insertion structure, and the housing 2 is provided with a second insertion structure, wherein the first insertion structure can be inserted into the second insertion structure to limit the rotation of the flexible gasket 631 along the circumferential direction thereof. Specifically, in this embodiment, the first inserting structure is at least one limiting boss 6311 disposed on the outer wall of the flexible gasket 631; correspondingly, the second inserting structure is a boss limiting groove arranged on the shell 2, the boss limiting groove and the limiting boss 6311 are arranged in a one-to-one correspondence manner, and when the flexible gasket 631 is assembled, the limiting boss 6311 and the boss limiting groove are aligned and inserted, so that the flexible gasket 631 can be limited to rotate along the circumferential direction. In other embodiments, the first insertion structure is at least one boss limiting groove disposed on the outer wall of the flexible gasket 631; correspondingly, the second inserting structure is a limit boss 6311 disposed on the housing 2. In other embodiments, as shown in FIG. 7, the flexible gasket 631 may also be a simple ring-like structure to facilitate machining.
Further, the elastic support assembly 63 further includes a bearing knock pin 632 and a radial elastic member 634, the bearing knock pin 632 passes through the flexible washer 631 and abuts against the outer ring of the floating bearing 62, one end of the radial elastic member 634 elastically abuts against the bearing knock pin 632, the other end of the radial elastic member 634 is supported on the housing 2, and the radial elastic member 634 can drive the bearing knock pin 632 to move so as to bias the worm screw 3 to a direction close to the worm wheel 4. The radial elastic member 634 can provide radial pretightening force to the floating bearing 62 through the bearing knock pin 632, so as to provide floating support for the worm 2, so that the clearance between the worm 2 and the worm wheel 3 can be adjusted in a self-adaptive manner, and the phenomenon of overlarge clearance is avoided.
Further, in order to reduce noise generated by the contact between the bearing pin 632 and the floating bearing 62, reduce the weight of the bearing pin 632, and control the cost, the bearing pin 632 is made of hard plastic.
Further, the elastic support assembly 63 further includes a preload adjusting element 633, the preload adjusting element 633 is screwed to the housing 2, and the radial elastic element 634 elastically abuts against the bearing pin 632 and the preload adjusting element 633 respectively. Specifically, the pre-tightening force adjusting element 633 is a nut, the outer wall of the nut is provided with an external thread and is screwed to the housing 2, and the deformation of the radial elastic element 634 can be adjusted by rotating the pre-tightening force adjusting element 633, so that the radial pre-tightening force is adjustable. In order to facilitate the rotation of the preload adjusting element 633, a wrench socket 6331 is further disposed at an end of the preload adjusting element 633, and the position of the preload adjusting element 633 can be adjusted by rotating the preload adjusting element 633 with a wrench, so as to control the preload of the radial elastic element 634.
Specifically, the bearing knock pin 632 includes a pin head 6321 and a pin column 6322, and a first end of the pin head 6321 is inserted into the preload adjuster 633; a pin 6322 is attached to the second end of the pin head 6321, the pin 6322 has a diameter smaller than the pin head 6321, the pin 6322 passes through the flexible washer 631 and abuts the outer race of the floating bearing 62, and the flexible washer 631 can abut the pin head 6321. Specifically, the side wall of the flexible washer 631 is provided with a through hole 6312, and the pin 6322 passes through the through hole 6312 and abuts against the outer ring of the floating bearing 62. In addition, the limiting boss 6311 of the flexible gasket 631 is aligned with the boss limiting groove of the housing 2, so that the pin 6322 is aligned with the through hole 6312, and assembly is facilitated.
Further, the pin head 6321 is at least partially inserted into the preload adjusting element 633, and the outer peripheral surface of the pin head 6321 located in the preload adjusting element 633 is provided with a groove 6323. Specifically, the pin head 6321 is inserted into the pretension adjuster 633 and is movable relative to the pretension adjuster 633, and the groove 6323 is always located in the pretension adjuster 633 regardless of the amount of movement of the pin head 6321. The groove 6323 is an annular groove formed along the outer peripheral surface of the pin head 6321, the pin head 6321 is formed into a thin waist-shaped structure by the arrangement of the groove 6323, so that the two ends of the bearing ejector pin 632 are in contact with the inner wall of the pretightening force adjusting piece 633 and are in contact with the stressed part, the groove 6323 cannot be in contact with the stressed part, the contact stability of the bearing ejector pin 632 can be improved on one hand, the machining precision of the groove 6323 is not required to be guaranteed on the other hand, and the machining difficulty can be reduced. Optionally, groove 6323 may be filled with grease. In other embodiments, the groove 6323 may be a helical groove, as shown in FIG. 7, and the bearing pin 632 may be a simple cylindrical structure.
Specifically, a second mounting hole 6324 is formed in a first end surface of the pin head 6321, one end of the radial elastic element 634 abuts against a bottom wall of the second mounting hole 6324, and the other end of the radial elastic element 634 abuts against the preload adjuster 633. Further, a radial pressing block 7b is clamped between the radial elastic element 634 and the preload adjusting element 633. Optionally, the radial pressing block 7b is made of a non-metallic material such as plastic, and the radial pressing block 7b is sandwiched between the radial elastic member 634 and the pre-tightening force adjusting member 633, so that noise generated by direct metal-to-metal contact between the two members can be avoided.
Further, the radial elastic element 634 is a spring, the radial pressing block 7b comprises a second block part 7b1 and a second column part 7b2, and a first end of the second block part 7b1 abuts against the preload adjuster 633; the second column portion 7b2 is connected to the second end of the second block portion 7b1, and the radial elastic element 634 is sleeved on the second column portion 7b2 and abuts against the second block portion 7b1, so that the radial elastic element 634 does not bend or deflect when the radial elastic element 634 is compressed.
Further, as shown in fig. 8 to 9, the drive gear shaft 1 includes an optical axis section 11 and a spline shaft section 12 which are interference-fitted with the worm wheel 4 at the same time, the optical axis section 11 is located in front of the spline shaft section 12 in the assembling direction of the worm wheel 4, and the spline shaft section 12 is engaged with the worm wheel 4. The matching of the inner holes of the driving gear shaft 1 and the worm wheel 4 adopts the modes of partial optical axis press fit and partial spline press fit, and the holding force of the driving gear shaft 1 and the worm wheel 4 can be ensured. When the worm wheel 4 is assembled, the worm wheel 4 is sleeved on the optical shaft section 11, the optical shaft section 11 is used for guiding, and the smooth press fitting of the worm wheel 4 can be ensured.
Further, the spline shaft section 12 is processed by adopting a heat treatment process, and the hardness of the spline shaft section 12 can be improved by carrying out heat treatment on the spline shaft section 12, so that the matching part of the spline shaft section 12 and the worm wheel 4 cannot be deformed, and the teeth of the spline shaft section 12 can be ensured to be embedded into the inner hole of the worm wheel 4, so that sufficient circumferential holding force is provided.
Further, as shown in fig. 8-14, the driving gear shaft 1 is further provided with a clamp groove 13, a support bearing 8 and a shoulder 14, a bearing inner ring clamp 9 is arranged in the clamp groove 13, the shoulder 14 and the bearing inner ring clamp 9 are respectively abutted with the inner ring of the support bearing 8 along the axial direction of the driving gear shaft 1, and the other side of the shoulder 14 is abutted with the inner ring of the support bearing 8.
The bearing inner ring hoop 9 is filled in the hoop groove 13 after being extruded and deformed by adopting an extrusion process, the inner diameter of the bearing inner ring hoop 9 before being deformed is not smaller than the outer diameter of the driving gear shaft 1 (the bearing inner ring hoop 9 can be sleeved into the hoop groove 13 from one end of the driving gear shaft 1 at least), one end of the bearing inner ring hoop 9 after being deformed is abutted against the inner ring of the supporting bearing 8, and the outer diameter of the bearing inner ring hoop 9 after being deformed is larger than the inner diameter of the inner ring of the supporting bearing 8. Specifically, the outer race of the support bearing 8 is fixedly mounted to the housing 2, and the outer race of the support bearing 8 may be positioned, illustratively, using a bearing outer race snap ring 81, with the inner race of the support bearing 8 interference fit with the drive gear shaft 1. The axial movement of the drive gear shaft 1 can be limited by the support bearing 8 and the bearing inner ring hoop 9, namely the drive gear shaft 1 is limited to slide downwards by the support bearing 8, and the drive gear shaft 1 is limited to slide upwards by the bearing inner ring hoop 9. Because the teeth of the driving gear shaft 1 are designed to be helical teeth with the inclination angle of 20-22 degrees, and the torque transmitted by the driving gear shaft 1 can exceed 80Nm in the working process, the axial force borne by the driving gear shaft 1 can exceed 4000N, and therefore, a common snap ring gasket cannot meet the fastening requirement of the driving gear shaft 1 and a bearing inner ring, the bearing inner ring clamp 9 provided by the embodiment is filled in the clamp groove 13 after being extruded and deformed, the strength is high, the positioning of the supporting bearing 8 and the driving gear shaft 1 can be met, and the inner ring play of the driving gear shaft 1 and the supporting bearing 8 in the working process is avoided. Illustratively, the bearing inner ring clamp 9 is made of 45# steel, the hardness of the material is HRC45, the surface roughness is controlled to be Ra3.2, the outer diameter of the bearing inner ring clamp 9 is 28.2mm, the inner diameter of the bearing inner ring clamp 9 is 25.4mm (the inner diameter of the bearing inner ring clamp 9 needs to be larger than the diameter of an optical axis part of the driving gear shaft 1 by 25mm), the height of the bearing inner ring clamp 9 is 3.2mm, and the wall thickness of the bearing inner ring clamp 9 is 1.4 mm.
Further, the side wall of the clamp groove 13 away from the support bearing 8 is provided with a first guide inclined surface 131, and when the bearing inner ring clamp 9 is extruded and deformed by an extrusion process, the first guide inclined surface 131 is used for providing thrust towards the support bearing 8 for the bearing inner ring clamp 9, so that the bearing inner ring clamp 9 can be deformed towards the direction close to the support bearing 8 and can be tightly pressed against the inner ring of the support bearing 8.
Further, the inner wall of the bearing inner ring clamp 9, which is far away from the support bearing 8, is provided with a second guide inclined surface 91, and an included angle between the second guide inclined surface 91 and the axis of the bearing inner ring clamp 9 is larger than an included angle between the first guide inclined surface 131 and the axis of the drive gear shaft 1. When the bearing inner ring hoop 9 is extruded and deformed by an extrusion process, the second guide inclined surface 91 can be matched with the first guide inclined surface 131, so that the bearing inner ring hoop 9 is further promoted to deform towards the direction close to the support bearing 8 and push against the inner ring of the support bearing 8.
Further, as shown in fig. 11 to 12, the angle α between the first guide slope 131 and the axis of the drive gear shaft 1 is such that the coefficient of friction of the first guide slope 131 is μ 1, and 386.7 ° ≦ α/μ 1 ≦ 1240 °. Wherein the angle α between the first guide slope 131 and the axis of the drive gear shaft 1 in this embodiment is in the range of 58 ° to 62 °, the coefficient of friction of the first guide slope 131 is μ 1 in the range of 0.05 to 0.15, the upper limit of α/μ 1 is calculated to be 62 °/0.05 to 1240 °, and the lower limit of α/μ 1 is calculated to be 58 °/0.15 to 368.7, and 386.7 ° ≦ α/μ 1 ≦ 1240 °. By adopting the arrangement, on one hand, the bearing inner ring hoop 9 is beneficial to press-mounting deformation and plays a role in deformation guiding, on the other hand, after the bearing inner ring hoop 9 is formed, the second guide inclined plane 91 is matched with the first guide inclined plane 131 to form self-locking, and the performance of the double-pinion electric power steering system after being fatigue and durable is improved. Specifically, the angle between the first guide slope 131 and the axis of the drive gear shaft 1 may be any one of 58 °, 59 °, 60 °, 61 °, and 62 °. Preferably, the angle between the first guide slope 131 and the axis of the drive gear shaft 1 is 60 °.
Further, before the bearing inner ring hoop 9 deforms, an included angle between the second guide inclined plane 91 and the axis of the bearing inner ring hoop 9 is beta, the friction coefficient of the second guide inclined plane 91 is mu 2, and beta/mu 2 is larger than or equal to 480 degrees and smaller than or equal to 1560 degrees. In the present embodiment, before the bearing inner race yoke 9 is deformed, the angle β between the second guide slope 91 and the axis of the bearing inner race yoke 9 is in the range of 72 ° to 78 °, the friction coefficient of the second guide slope 91 is in the range of 0.05 to 0.15, the upper limit of β/μ 2 is calculated to be 78 °/0.05-1560 °, the lower limit of β/μ 2 is 72 °/0.15-480 °, and then β/μ 2 is not less than 480 ° -1560 °. The second guide slope 91 is beneficial to material flowing, and is convenient for extrusion forming of the bearing inner ring clamp 9. Specifically, the angle between the second guide slope 91 and the axis of the bearing cone yoke 9 ranges from any one of 72 °, 73 °, 74 °, 75 °, 76 °, 77 °, and 78 °. Preferably, the angle between the second guiding inclined surface 91 and the axis of the bearing inner ring clamp 9 is 75 °, so that the self-locking effect generated between the first guiding inclined surface 131 and the second guiding inclined surface 91 is optimal.
It should be noted that, as shown in fig. 11-12, when the bearing inner ring clip 9 is assembled, the bearing inner ring clip 9 is in clearance fit with the driving gear shaft 1, the bearing inner ring clip 9 can be easily sleeved on the driving gear shaft 1 and slid into the clip groove 13 by manual operation, and then the bearing inner ring clip 9 is compressed and deformed by external force to be filled in the clip groove 13. As shown in fig. 13-14, after the bearing inner race clip 9 is deformed, the second guiding inclined surface 91 is deformed and attached to the first guiding inclined surface 131, so as to form self-locking, and prevent the support bearing 8 from moving axially relative to the driving gear shaft 1.
Further, the surface hardness of the clip groove 13 is greater than the hardness of the bearing inner race clip 9. Since the bearing inner race yoke 9 is attached by means of press deformation, in order to ensure the assembly accuracy, it is necessary to perform carburizing and hardening treatment on the yoke groove 13 portion of the drive gear shaft 1, and it is necessary to make the surface hardness of the yoke groove 13 to be more than HRC55 (in order to make the bearing inner race yoke 9 easily deform, the surface hardness of the yoke groove 13 needs to be more than HRC10 higher than the hardness of the bearing inner race yoke 9).
It is to be noted that the foregoing is only illustrative of the preferred embodiments of the present invention and the technical principles employed. It will be understood by those skilled in the art that the present invention is not limited to the particular embodiments described herein, but is capable of various obvious changes, rearrangements and substitutions as will now become apparent to those skilled in the art without departing from the scope of the invention. Therefore, although the present invention has been described in greater detail by the above embodiments, the present invention is not limited to the above embodiments, and may include other equivalent embodiments without departing from the spirit of the present invention, and the scope of the present invention is determined by the scope of the appended claims.
Claims (20)
1. A worm gear mechanism comprising:
a housing (2);
the worm (3) and the worm wheel (4) are rotatably arranged in the shell (2), the worm (3) and the worm wheel (4) are meshed with each other, and the worm (3) is provided with an input end which is in transmission connection with an output shaft (200) of a motor;
and a support assembly comprising:
the worm supporting unit (6) comprises a self-aligning bearing (61), a floating bearing (62) and an elastic supporting assembly (63), an inner ring of the self-aligning bearing (61) and an inner ring of the floating bearing (62) are fixed to the worm (3) at intervals, an outer ring of the self-aligning bearing (61) is supported on the shell (2), and the elastic supporting assembly (63) is installed on the shell (2) and used for supporting the floating bearing (62) and allowing the floating bearing (62) to float relative to the shell (2);
characterized in that, the supporting component still includes:
one end of the axial elastic piece (5) is elastically abutted to the input end of the worm (3), and the other end of the axial elastic piece (5) is used for being supported on an output shaft (200) of the motor; the self-aligning bearing (61) is closer to the axial elastic member (5) than the floating bearing (62).
2. The worm-and-gear mechanism according to claim 1, characterized in that the end face of the input end of the worm (3) is provided with a first mounting hole (31), and the axial elastic member (5) abuts against the bottom wall of the first mounting hole (31).
3. The worm-gear mechanism according to claim 2, characterized in that the axial elastic member (5) is a spring, the worm-gear mechanism further comprising an axial pressing piece (7a), the axial pressing piece (7a) comprising:
a first block (7a1), the first block (7a1) being inserted into the output shaft (200) of the motor;
the first columnar portion (7a2), the first columnar portion (7a2) is connected to the first block-shaped portion (7a1), the axial elastic member (5) is sleeved on the first columnar portion (7a2), and the axial elastic member (5) abuts against the first block-shaped portion (7a 1).
4. The worm and gear mechanism according to claim 1, characterized in that the input end of the worm (3) is further provided with a coupling (100), and the input end of the worm (3) and the output shaft (200) of the motor are respectively inserted at two ends of the coupling (100).
5. The worm-gear mechanism according to claim 1, characterized in that the elastic support assembly (63) comprises a flexible washer (631), the flexible washer (631) being mounted to the housing (2) and being sleeved on the outer ring of the floating bearing (62).
6. The worm-gear mechanism according to claim 5, characterized in that the elastic support assembly (63) further comprises a bearing knock pin (632) and a radial elastic member (634), the bearing knock pin (632) passes through the flexible washer (631) and abuts against the outer ring of the floating bearing (62), one end of the radial elastic member (634) elastically abuts against the bearing knock pin (632), the other end of the radial elastic member (634) is supported on the housing (2), and the radial elastic member (634) can drive the bearing knock pin (632) to move to bias the worm gear (3) to a direction close to the worm wheel (4).
7. The worm-gear mechanism according to claim 6, characterized in that the elastic support assembly (63) further comprises a preload adjuster (633), the preload adjuster (633) is screwed to the housing (2), and the radial elastic member (634) elastically abuts against the bearing knock pin (632) and the preload adjuster (633), respectively.
8. The worm-gear mechanism according to claim 7, characterized in that the bearing knock pin (632) comprises:
a pin head (6321), a first end of the pin head (6321) is inserted into the pretension adjusting element (633);
a pin (6322), the pin (6322) connected to the second end of the pin head (6321), the pin (6322) having a diameter less than the diameter of the pin head (6321), the pin (6322) passing through the flexible washer (631) and abutting the outer race of the floating bearing (62), and the flexible washer (631) capable of abutting the pin head (6321).
9. The worm-gear mechanism according to claim 8, characterized in that the pin head (6321) is at least partially inserted into the pretension adjuster (633), and the outer circumference of the portion of the pin head (6321) located inside the pretension adjuster (633) is provided with a groove (6323).
10. The worm-gear mechanism according to claim 8, wherein a second mounting hole (6324) is opened on the first end face of the pin head (6321), and one end of the radial elastic member (634) abuts against the bottom wall of the second mounting hole (6324).
11. The worm-gear mechanism according to claim 10, characterized in that the radial elastic member (634) is a spring, the elastic support assembly (63) further comprises a radial pressing piece (7b), the radial pressing piece (7b) comprising:
a second block (7b1), the second block (7b1) abutting against the pretension adjuster (633);
a second cylindrical portion (7b2), the second cylindrical portion (7b2) being connected to the second block portion (7b1), the radial elastic member (634) being sleeved on the second cylindrical portion (7b2) and abutting against the second block portion (7b 1).
12. The worm-gear mechanism according to claim 6, characterized in that the bearing knock pin (632) is made of hard plastic; the flexible gasket (631) is made of a rubber material.
13. The worm-and-gear mechanism according to claim 5, characterized in that the flexible washer (631) is provided with a first plug-in structure and the housing (2) is provided with a second plug-in structure, the first plug-in structure being able to plug-in with the second plug-in structure to restrict the flexible washer (631) from rotating in its circumferential direction.
14. An electric power steering system, characterized by, including drive gear axle (1) and the worm gear mechanism of any one of claims 1-13, worm wheel (4) fixed mounting is in drive gear axle (1), drive gear axle (1) still is equipped with shaft shoulder (14), support bearing (8) and clamp groove (13), be equipped with bearing inner circle clamp (9) in clamp groove (13), shaft shoulder (14) with bearing inner circle clamp (9) are followed respectively the axial of drive gear axle (1) with support the inner circle butt of bearing (8).
15. An electric power steering system according to claim 14, characterized in that the inner race clamp (9) is arranged to be deformed by extrusion to fill the clamp groove (13), and the inner diameter of the inner race clamp (9) before deformation is not smaller than the outer diameter of the drive gear shaft (1).
16. An electric power steering system according to claim 15, characterized in that the side wall of the yoke groove (13) remote from the support bearing (8) is provided with a first guide slope (131), the first guide slope (131) being adapted to provide the inner race yoke (9) with a thrust force towards the support bearing (8) when the inner race yoke (9) is deformed by extrusion using an extrusion process.
17. The electric power steering system according to claim 16, wherein the inner wall of the bearing inner ring clamp (9) away from the support bearing (8) is provided with a second guide inclined surface (91), an included angle between the second guide inclined surface (91) and the axis of the bearing inner ring clamp (9) is larger than an included angle between the first guide inclined surface (131) and the axis of the drive gear shaft (1), and after the bearing inner ring clamp (9) deforms, the second guide inclined surface (91) deforms and is attached to the first guide inclined surface (131).
18. The electric power steering system according to claim 17, characterized in that the angle α between the first guide ramp (131) and the axis of the drive gear shaft (1), the coefficient of friction of the first guide ramp (131) being μ 1, 386.7 ° ≦ α/μ 1 ≦ 1240 °;
before the bearing inner ring hoop (9) deforms, an included angle between the second guide inclined plane (91) and the axis of the bearing inner ring hoop (9) is beta, the friction coefficient of the second guide inclined plane (91) is mu 2, and beta/mu 2 is larger than or equal to 480 degrees and smaller than or equal to 1560 degrees.
19. The electric power steering system according to claim 14, characterized in that the drive gear shaft (1) comprises a plain shaft section (11) and a splined shaft section (12) which are simultaneously interference-fitted with the worm wheel (4), the plain shaft section (11) being located in front of the splined shaft section (12) in the assembling direction of the worm wheel (4), and the splined shaft section (12) being engaged with the worm wheel (4).
20. Electric power steering system according to claim 14, characterized in that the surface hardness of the clamp groove (13) is greater than the hardness of the bearing inner ring clamp (9).
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| CN202110874996.9A CN113586667B (en) | 2021-07-30 | 2021-07-30 | Worm gear mechanism and electric power steering system |
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| CN202110874996.9A CN113586667B (en) | 2021-07-30 | 2021-07-30 | Worm gear mechanism and electric power steering system |
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| CN114131311A (en) * | 2021-11-30 | 2022-03-04 | 中汽创智科技有限公司 | Coaxiality adjusting device, worm and gear steering machine and assembling device |
| CN114321604A (en) * | 2021-12-31 | 2022-04-12 | 北京有竹居网络技术有限公司 | Worm gear transmission assembly, driving device, holder and image acquisition device |
| CN114475771A (en) * | 2022-01-20 | 2022-05-13 | 北京汽车股份有限公司 | Electric power steering system capable of adjusting clearance between worm and gear and automobile |
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| CN113586667B (en) | 2023-05-26 |
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