WO2024041155A1 - 用于电动助力转向系统的蜗杆压紧支撑机构 - Google Patents

用于电动助力转向系统的蜗杆压紧支撑机构 Download PDF

Info

Publication number
WO2024041155A1
WO2024041155A1 PCT/CN2023/102276 CN2023102276W WO2024041155A1 WO 2024041155 A1 WO2024041155 A1 WO 2024041155A1 CN 2023102276 W CN2023102276 W CN 2023102276W WO 2024041155 A1 WO2024041155 A1 WO 2024041155A1
Authority
WO
WIPO (PCT)
Prior art keywords
compression
component
worm
support
rubber
Prior art date
Application number
PCT/CN2023/102276
Other languages
English (en)
French (fr)
Inventor
胡少雄
杨景元
董行
李山
Original Assignee
博世华域转向系统有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 博世华域转向系统有限公司 filed Critical 博世华域转向系统有限公司
Publication of WO2024041155A1 publication Critical patent/WO2024041155A1/zh

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D3/00—Steering gears
    • B62D3/02—Steering gears mechanical
    • B62D3/04—Steering gears mechanical of worm type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
    • 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
    • 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
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere

Definitions

  • the present invention relates to the technical field of electric power steering systems, specifically a worm compression support mechanism for electric power steering systems.
  • Automobile steering systems generally include steering wheels, steering columns, intermediate shafts, steering gears, tie rods and other components.
  • Column electric power steering system (hereinafter referred to as EPSc), double pinion electric power steering system (hereinafter referred to as EPSdp), single pinion electric power steering system (hereinafter referred to as EPSp), etc. all belong to automobile electric power steering
  • EPSc Column electric power steering system
  • EPSdp double pinion electric power steering system
  • EPSp single pinion electric power steering system
  • the main function of the system (hereinafter referred to as EPS) is to convert the rotation of the steering wheel into the left and right swing of the wheels, thereby realizing the power steering function of the car.
  • EPSc provides assist torque through the assist motor installed at the steering column
  • EPSdp provides assist torque through the assist motor installed at the second pinion of the steering gear
  • EPSp provides assist torque through the assist motor installed at the first pinion.
  • the deceleration mechanism decelerates and increases torque to provide corresponding power assist torque to the steering system, thereby realizing the designed power assist function.
  • the reduction mechanism uses a worm gear reduction mechanism. This type of reduction mechanism can provide a large reduction ratio and take up little space.
  • the current EPS worm gear mechanism has problems such as excessive friction torque or excessive free clearance due to parts manufacturing tolerances and installation errors. This ultimately leads to excessive rotational friction torque that affects the steering feel or the worm gear appears when driving on bad roads. Worm knocking noise and worm housing knocking noise. In order to reduce the rotational friction torque and eliminate knocking noise, it is necessary to control the clearance of the worm gear reduction mechanism to zero clearance and not make the worm gear fit too tightly, and provide certain damping in the radial movement direction of the worm. Generally, the worm needs to be supported by two ball bearings on the left and right.
  • the solutions that provide zero clearance include the bracket bearing solution and the solution of adding a separate spring plunger at one end of the worm.
  • the large force fluctuation range results in the inability to effectively eliminate the clearance of the worm gear reduction mechanism and insufficient bearing capacity.
  • the present invention provides a worm pressing support mechanism for an electric power steering system.
  • the radial gap of the worm gear reduction mechanism can be eliminated and the steering feel can be improved. Reduce knocking noise.
  • a worm pressing support mechanism for an electric power steering system including a worm, a worm gear, a big end bearing, a small end bearing, and a casing.
  • the characteristic is: a worm gear and a worm are provided in the casing.
  • the upper end of the worm is connected to the worm, one end of the worm is equipped with a big-end bearing, the other end of the worm is equipped with a small-end bearing, and a pressing component is located on the outer edge of the small-end bearing, and the pressing component is close to the
  • the outer ring of the small end bearing and the upper side of the small end bearing are provided with a support component.
  • the support component is located above the compression component, and the lower surface of the support component is close to the compression component.
  • the pre-tightening force is provided by the compression component, the support component is arranged above the compression component, and the lower surface of the support component presses the compression component to limit the compression component in the vertical direction.
  • the pressing assembly provides top damping and hard limits on the top of the worm, and side damping and hard limits on the sides of the worm to support and limit the swing of the worm and absorb the impact of the worm, thereby eliminating the gap in the worm gear mechanism and reducing the impact of the worm.
  • Reduce noise and improve hand feel reduce the number of machined surfaces of the housing, simplify installation, and reduce costs; reduce the outer size of the housing and occupy less installation space.
  • the pressing component provides pre-tightening force for the up and down swing motion, thereby eliminating the gap in the worm gear reduction mechanism; the pressing component provides vertical buffering of the worm to avoid noise caused by up and down impacts; the pressing component provides a left and right swing buffer surface, Avoid noise caused by left and right swing impact; provide vertical compression spring feature, that is, provide vertical compression elastic force through the compression assembly, which can easily adjust the required vertical compression stiffness, thereby providing the required vertical compression
  • the direct pressing force controls the clearance of the worm gear reduction mechanism to zero to avoid noise caused by the clearance of the reduction mechanism; the appropriate vertical pressing force is provided by the pressing assembly to avoid excessive friction torque of the reduction mechanism and improve steering. Feel.
  • a worm compression support mechanism for electric power steering system including a worm, a worm gear, a big end bearing, a small end bearing, a shell, a compression nut, and a worm gear hub, which is characterized by: the shell There is a worm gear and a worm in the body. The upper end of the worm gear is connected to the worm. One end of the worm is equipped with a big-end bearing and a worm gear hub. The outer side of the big-end bearing is equipped with a compression nut; the other end of the worm is equipped with a small end.
  • the bearing is provided with a pressing component on the outer edge side of the small end bearing, and a support component is provided on the upper side of the small end bearing.
  • the described pressing component is one of pressing component one, pressing component two, pressing component three, pressing component four, and pressing component five;
  • the supporting component is one of supporting component one, supporting component two, and One of support component three, support component four, and support component five;
  • the pressing component one matches the supporting component one;
  • the pressing component two matches the supporting component two;
  • the pressing component four is matched with the supporting component four;
  • the pressing component five is matched with the supporting component five.
  • the pressing assembly 1 includes a leaf spring 1 and a preload rubber 1.
  • the leaf spring 1 is set on the upper part of the outer edge of the small end bearing, and the preload rubber 1 is set on the lower part of the outer edge of the small end bearing.
  • the leaf spring 1 has a butterfly-shaped structure.
  • the top of the leaf spring 1 is an arc-shaped middle end face.
  • the tops of the left and right ends of the middle end face are respectively connected to spring buckles.
  • the bottoms of the left and right ends of the middle end face are respectively connected to one end of the spring arm.
  • the other end of the spring arm is connected to the pressing boss one; a spring waist-shaped hole is provided in the middle of the middle end face;
  • the spring arm is composed of two inwardly inclined bent panels, and the cross-section of the spring arm is C Font structure.
  • the preloaded rubber has a U-shaped structure, the left and right sides of the upper part of the preloaded rubber are respectively connected to convex ribs, and the preloaded rubber located on the lower side of the convex ribs is connected to a semi-cylindrical protrusion.
  • the support component 1 includes an adjusting bolt 1 and a compression pin 1.
  • the top of the small end bearing is provided with the bottom of the compression pin 1, and the top of the compression pin 1 is provided with an adjustment bolt 1.
  • the outer edge of the adjustment bolt 1 is provided with external threads, the bottom of the adjustment bolt 1 is a flat surface, and the top of the adjustment bolt 1 is connected to an internal hexagonal groove.
  • the upper part of the compression pin one is a cylindrical structure, the lower part of the compression pin one is a waist column structure, the lower part of the compression pin one is embedded with soft rubber; and the upper part of the compression pin one and the compression pin one
  • the lower part is an integrated structure; there is a positioning square hole on the top of the pressing pin one, and the bottom of the pressing pin one is an arc-shaped structure.
  • the second pressing component includes a second leaf spring and a second preload rubber.
  • the second preload rubber is sleeved on the outer edge of the small end bearing.
  • the rear side of the second preload rubber is snap-connected to the second leaf spring.
  • the second leaf spring has a U-shaped structure.
  • the top of the second leaf spring is an arc structure.
  • the left and right sides of the second leaf spring are respectively provided with square holes.
  • the leaf spring 2 on the upper side of the hole is provided with an inwardly bent trapezoidal hypotenuse, the bottom of the trapezoidal hypotenuse is connected to the leaf spring 2, and the top of the trapezoidal hypotenuse is connected to the pressing boss 2.
  • the second preload rubber is an annular structure, which is located on the inner side of the top of the second preload rubber and connected to the slot.
  • the inner sides of the left and right sides of the middle part of the second preload rubber are respectively connected to arc columns.
  • the inner sides of the arc columns are connected to each other.
  • the side is a flat surface, and the inner side of the arc column is connected to a boss.
  • the front end faces of the two preload rubbers located at the connection between the arc column and the two preload rubbers are respectively provided with a number of protrusions.
  • the second support component includes an adjustment bolt two and a compression pin two.
  • the top of the small end bearing is provided with the bottom of the compression pin two, and the top of the compression pin two is provided with an adjustment bolt two; the two adjustment bolts and the compression pin are
  • the structure of tightening pin two is consistent with that of adjusting bolt one and compression pin one.
  • the compression component 3 includes a leaf spring 3 and a preload rubber 3.
  • the leaf spring 3 is located on the outer edge of the small end bearing, and the rear side of the leaf spring 3 is engaged with the preload rubber 3.
  • the leaf spring 3 has an " ⁇ "-shaped structure, the top of the leaf spring 3 is a flat surface, the bottom sides of the leaf spring 3 are tilted outward respectively, and the ends tilted outward are connected to the pressing boss 3. .
  • the preload rubber 3 is a semicircular arc ring structure.
  • the rear ends located on the left and right sides of the preload rubber 3 are respectively connected to semi-cylinders.
  • the rear ends located at the top of the preload rubber 3 are connected to the top rubber.
  • the center of the top rubber is provided with Center hole.
  • the support component three includes an adjustment bolt three, and the top of the small end bearing is provided with an adjustment bolt three.
  • the structure of the adjustment bolt three is that a small cylinder is connected to the bottom plane of the adjustment bolt one, and the small cylinder of the adjustment bolt three is embedded in it. It is located in the center hole of the top rubber of the three tops of the preload rubber.
  • the pressing assembly 4 includes a preloading rubber 4, and the preloading rubber 4 is located at the lower part of the outer edge of the small end bearing; the preloading rubber 4 is a semicircular arc annular structure, and is located on the lower part of the preloading rubber 4.
  • the left and right end surfaces of the top are respectively connected to the outer protruding structure, and the inner side of the outer protruding structure is a rectangular plane.
  • the support component four includes a support bushing one, a coil spring one, a rubber pad, and an adjusting screw one.
  • the top of the small end bearing is provided with an adjusting screw one.
  • the lower part of the adjusting screw one is provided with a coil spring one.
  • the coil spring one is
  • the outer sleeve is provided with a support bushing one, which is located on the support bushing.
  • the adjusting screw on the top of the sleeve is provided with a rubber pad, and the bottom of the supporting bushing is connected to the top end face of the small end bearing.
  • the adjusting screw 1 has a T-shaped structure.
  • the upper outer edge of the adjusting screw 1 is provided with external threads.
  • the middle part of the adjusting screw 1 is covered with a rubber pad.
  • the lower part of the adjusting screw 1 is covered with a coil spring.
  • the cylindrical structure of the support bushing 1 is located at the top of the support bushing 1 and is provided with a groove that is connected to the lower part of the adjustment screw.
  • the bottom of the support bushing 1 is an arc surface.
  • the pressing assembly 5 includes a preloading rubber 5, which is respectively set on the upper and lower parts of the outer edge of the small end bearing; the preloading rubber 5 is a rubber ring.
  • the support component five includes a support bushing two, a coil spring two, and an adjustment screw two.
  • the top of the small end bearing is provided with an adjustment screw two.
  • the lower part of the adjustment screw two is provided with a coil spring two, and the outside of the coil spring two is provided with a coil spring two.
  • the structure of the second adjusting screw is consistent with that of the adjusting screw one; the structure of the second spiral spring is consistent with the structure of the first spiral spring; the structure of the second supporting bushing is consistent with the structure of the supporting bushing one.
  • the first pressing component and the supporting component 1 are arranged in a housing that matches the pressing component 1 and the supporting component 1; the pressing component 2 and the supporting component 2 are arranged in the housing together with the pressing component 2 and the supporting component.
  • the second component is matched with the housing two; the pressing component three and the supporting component three are arranged in the housing three which is matched with the pressing component three and the supporting component three; the pressing component four and the supporting component are 4 is arranged in the housing 4 that matches the pressing component 4 and the supporting component 4; the pressing component 5 and the supporting component 5 are arranged in the housing 5 matching the pressing component 5 and the supporting component 5.
  • the positive and progressive effect of the present invention is that the pre-tightening force is provided through the compression component, the support component is arranged above the compression component, and the lower surface of the support component presses the compression component, which plays a role in the vertical direction of the compression component.
  • the pressing component provides top damping and hard limit at the top of the worm.
  • the side of the worm relies on the pressing component to provide side damping and hard limit to support and limit the swing of the worm and absorb the impact of the worm, thereby eliminating the problem of the worm gear mechanism. Clearance, reduce noise, improve feel; reduce the number of machined surfaces of the shell, simplify installation, reduce costs; reduce the outer size of the shell, occupying less installation space.
  • the pressing component provides pre-tightening force for the up and down swing motion, thereby eliminating the gap in the worm gear reduction mechanism; the pressing component provides vertical buffering of the worm to avoid noise caused by up and down impacts; the pressing component provides a left and right swing buffer surface, Avoid noise caused by left and right swing impacts; the vertical compression spring feature is provided through the compression assembly, which can easily adjust the required vertical compression stiffness, thereby providing the required vertical compression force and controlling the worm gear reduction mechanism
  • the clearance is zero to avoid noise caused by the clearance of the reduction mechanism; the compression assembly provides appropriate vertical pressing force to avoid excessive friction torque of the reduction mechanism and improve the steering feel.
  • Figure 1 is a cross-sectional view of the structure of the present invention.
  • Figure 2 and Figure 3 are structural cross-sectional views of the first solution of the present invention.
  • Figures 4 and 5 are structural schematic diagrams of leaf spring one in scheme one.
  • Figure 6 is a schematic structural diagram of pre-tensioned rubber 1 in solution 1.
  • Figure 7 is a schematic structural diagram of adjusting bolt 1 in Scheme 1.
  • Figures 8 and 9 are structural schematic diagrams of compression pin 1 in scheme 1.
  • Figure 10 is a schematic structural diagram of shell one in scheme one.
  • Figures 11 and 12 are structural cross-sectional views of the second solution of the present invention.
  • Figure 13 is a schematic diagram of the connection structure of the second leaf spring and the second preload rubber in the second solution.
  • Figure 14 is a schematic structural diagram of the second leaf spring in the second solution.
  • Figure 15 is a schematic structural diagram of the second preload rubber in the second solution.
  • Figure 16 is a schematic structural diagram of the second middle housing.
  • Figures 17 and 18 are structural cross-sectional views of the third solution of the present invention.
  • Figure 19 is a schematic diagram of the connection structure of leaf spring three and preload rubber three in scheme three.
  • Figure 20 is a schematic structural diagram of leaf spring three in solution three.
  • Figure 21 is a schematic structural diagram of preload rubber three in scheme three.
  • Figure 22 is a schematic structural diagram of adjusting bolt three in solution three.
  • Figure 23 is a schematic structural diagram of middle housing three.
  • Figures 24 and 25 are structural cross-sectional views of the fourth solution of the present invention.
  • Figure 26 is a schematic structural diagram of the pre-tightened rubber four in the fourth solution.
  • Figure 27 is a schematic structural diagram of the adjustment screw in Scheme 4.
  • Figure 28 is a schematic structural diagram of the support bushing in Scheme 4.
  • Figure 29 is a schematic structural diagram of the middle housing 4.
  • Figures 30 and 31 are structural cross-sectional views of the fifth solution of the present invention.
  • Figure 32 is a schematic diagram of the connection structure between the small end bearing and the preloaded rubber in Scheme 5.
  • Figure 33 is a schematic diagram of the structure of the present invention installed in the EPSc steering system.
  • Figure 34 is a schematic diagram of the structure of the present invention installed in the EPSdp steering system.
  • Figure 35 is a schematic diagram of the structure of the present invention installed in the EPSp steering system.
  • This embodiment provides a worm compression support mechanism for an electric power steering system, including a worm 5, a worm gear 6, a big end bearing 3, a small end bearing 7, a housing 1, a compression nut 2, and a worm gear hub 4.
  • the casing 1 is provided with a worm gear 6 and a worm 5.
  • the upper part of the worm gear 6 The end of the worm 5 is connected with the worm 5.
  • One end of the worm 5 is equipped with a big end bearing 3 and a worm gear hub 4.
  • a compression nut 2 is installed on the outside of the big end bearing 3; the other end of the worm 5 is equipped with a small end bearing 7.
  • a pressing component is provided on the outer edge side of the small end bearing 7, and the pressing component is close to the outer ring of the small end bearing 7.
  • a support component is provided on the upper side of the small end bearing 7, and the support component is located on the pressing component. above, and the lower surface of the support component is in close contact with the compression component. The pre-tightening force is provided by the compression component, the support component is arranged above the compression component, and the lower surface of the support component presses the compression component to limit the compression component in the vertical direction.
  • the pressing assembly provides top damping and hard limiting at the top of the worm 5, and the sides of the worm 5 rely on the pressing assembly to provide side damping and hard limiting to support and limit the swing of the worm 5 and absorb the impact of the worm 5, thereby eliminating
  • the clearance of the worm gear 5 mechanism reduces noise and improves hand feel; reduces the number of machined surfaces of the housing, simplifies installation and reduces costs; reduces the outer dimensions of the housing and takes up less installation space.
  • the pressing assembly provides a pre-tightening force for the up and down swing movement, thereby eliminating the gap in the worm gear reduction mechanism; the pressing assembly provides vertical buffering of the worm 5 to avoid noise caused by up and down impacts; the pressing assembly provides a left and right swing buffer surface , to avoid noise caused by left and right swing impacts; the vertical spring feature is provided by the compression assembly, which can easily adjust the required vertical compression stiffness, thereby providing the required vertical compression force and controlling the worm gear 5 reduction mechanism
  • the clearance is zero to avoid noise caused by the clearance of the reduction mechanism; the compression assembly provides appropriate vertical pressing force to avoid excessive friction torque of the reduction mechanism and improve the steering feel.
  • the output shaft of the power assist motor of the steering system is connected to the worm gear hub 4 through a coupling.
  • the worm gear hub 4 and the worm 5 are connected through splines, thereby applying the assist force of the motor output shaft to the worm 5.
  • the outer ring of the big end bearing 3 is placed in the bearing hole of the housing with a clearance fit.
  • the compression nut 2 is connected to the housing 1 through threads to compress the bearing end face in the bearing hole of the housing.
  • the inner ring of the big end bearing 3 is an interference fit. Installed on the big-end bearing seat of the worm 5, the big-end bearing 3 allows the worm 5 to produce a small swing motion in the circumferential direction around the center of the bearing.
  • the inner ring of the small end bearing 7 is installed on the small end bearing seat of the worm 5 through an interference fit, and the outer ring clearance is placed in the housing cavity.
  • the worm gear 6 is integrated with the output shaft and is supported in the casing 1 through bearings.
  • the worm gear 6 and the worm 5 are driven by helical gear meshing.
  • the limit pin is inserted into the waist-shaped hole of the casing 1 with a clearance fit.
  • the leaf spring The buckle is clamped on the housing groove, that is, the pressing assembly is clamped on the housing groove through the buckle connection.
  • the pressing component is pressing component one, which includes a leaf spring 11 and a preload rubber 12, located on the outer edge of the small end bearing 7
  • the upper part is provided with a leaf spring 11, and the lower part of the outer edge of the small end bearing 7 is provided with a preload rubber 12.
  • the pre-tightening force is provided by the compression component 1.
  • the leaf spring 11 provides top damping and hard limit at the top of the worm 5.
  • the side of the worm 5 relies on the leaf spring 11 and the preload rubber 12 to provide side damping and hard limit to support and limit the swing and absorption of the worm 5.
  • the impact of the worm 5 can thereby eliminate the gap in the worm gear 5 mechanism, reduce noise, and improve the feel; reduce the number of machined surfaces of the housing, simplify installation, and reduce costs; reduce the outer size of the housing and occupy less installation space.
  • the pressing component 1 provides a pre-tightening force for the up and down swing movement, thereby eliminating the gap in the worm gear reduction mechanism; the pressing component 1 provides vertical buffering of the worm 5 to avoid noise caused by up and down impacts; the pressing component 1 provides left and right The swing buffer surface avoids the noise caused by the left and right swing impact; the vertical compression spring feature is provided through the leaf spring 11, that is, the elastic force in the vertical direction is provided through the leaf spring 1, which can easily adjust the required vertical pressure.
  • Tight stiffness thereby providing the required vertical pressing force, and controlling the clearance of the worm gear reduction mechanism to zero clearance to avoid noise caused by the clearance of the reduction mechanism; by providing appropriate vertical pressing force through the pressing assembly 1, excessive friction torque of the reduction mechanism can be avoided and the steering feel can be improved.
  • the leaf spring 11 has a butterfly-shaped structure.
  • the top of the leaf spring 11 is an arc-shaped middle end surface 11-1.
  • the tops of the left and right ends are respectively connected to the spring buckles 11-2, the bottoms of the left and right ends of the middle end surface 11-1 are respectively connected to one end of the spring arm 11-3, and the other end of the spring arm 11-3 is connected to the pressing boss 11-4.
  • the spring arm 11-3 is composed of two inwardly inclined bent panels, and the cross-section of the spring arm 11-3 has a C-shaped structure .
  • the spring buckle 11-2 of the leaf spring 11 is symmetrically designed and is clamped on the spring groove of the casing through interference.
  • the middle end surface 11-1 of the top of the leaf spring 11 is fit with the casing for the use of the leaf spring 11.
  • the spring arm 11-3 is placed in the installation cavity of the housing with a gap, the pressing boss 11-4 is in pressing contact with the outer ring of the small end bearing 7, the pressing boss 11-4 is arranged symmetrically , the pre-tightening forces in the horizontal direction cancel each other out, and the pre-tightening force is provided to the top of the worm 5 in the vertical direction;
  • the vertical buffer of the worm 5 is provided through the leaf spring 11 to avoid the noise caused by the up and down impact;
  • the worm gear deceleration is controlled
  • the clearance of the mechanism is zero to avoid noise caused by the clearance of the reduction mechanism; it can avoid excessive friction torque of the reduction mechanism and improve the steering feel.
  • the leaf spring 11 has a butterfly-shaped structure, which is conducive to simplifying the structural arrangement of the leaf spring 11.
  • the cross-section of the spring arm 11-3 is a C-shaped structure, which is conducive to simplifying the structural arrangement of the spring arm 11-3.
  • the above arrangement is beneficial to The integral arrangement of the leaf spring 11 is realized, which facilitates the production and manufacture of the leaf spring 11 .
  • the preload rubber 12 has a U-shaped structure.
  • the left and right sides of the upper part of the preload rubber 12 are respectively connected to the convex ribs 12-1 and are located under the convex ribs 12-1.
  • a semi-cylindrical protrusion 12-2 is connected to the preload rubber 12 on the side.
  • the convex ribs 12-1 of the preloading rubber 12 are interference-compressed between the outer ring of the small end bearing 7 and the side soft rubber support surface and generate side preloading force.
  • the preloading rubber 12 provides a buffer surface for the left and right swing of the worm 5.
  • the semi-cylindrical protrusion 12-2 is clearance matched with the casing to ensure that the preload rubber 12 can be assembled in the casing.
  • the support assembly includes an adjusting bolt and a compression pin.
  • the top of the small end bearing 7 is provided with the bottom of the compression pin 10.
  • the top of the compression pin 10 is provided with Adjust bolt 19.
  • the compression pin 10 is inserted into the waist-shaped hole of the housing 8, and the adjustment bolt 9 is pressed tightly against the compression pin 10, which is beneficial to the relationship between the adjustment bolt 9, the compression pin 10, and the small end bearing 7. It is fixed without any gap and limits the position of the small end bearing 7 in the axial direction and provides preload force.
  • the outer edge of the adjustment bolt 9 is provided with external threads
  • the bottom of the adjustment bolt 9 is a flat surface
  • the top of the adjustment bolt 9 is connected to a hexagon socket Slot 9-1.
  • the external thread of the adjusting bolt 9 is connected to the threaded hole of the housing 8 through a threaded fit.
  • the bottom plane of the adjusting bolt 9 is pressed against the top plane of the compression pin 10 to provide an internal hexagonal groove 9- 1. It is convenient to adjust the screwing-in angle of the thread, ensuring that there is no gap between the adjusting bolt 19, the pressing pin 10, and the small end bearing 7.
  • the small end bearing 7 is limited in the axial direction and provides preload force.
  • the upper part of the compression pin 10 is a cylindrical structure, and the lower part of the compression pin 10 is a waist-shaped column structure; the lower part of the compression pin 10 is A soft glue 10-1 is embedded; and the upper part of the pressing pin 10 and the pressing pin 10
  • the lower part is an integrated structure; the top of the pressing pin 10 is provided with a positioning square hole 10-2, and the bottom of the pressing pin 10 is an arc-shaped structure.
  • the waist-shaped cylindrical clearance of the compression pin 10 is inserted into the waist-shaped hole of the housing 8 and the spring waist-shaped hole 11-5 of the leaf spring 11.
  • the cylindrical clearance of the compression pin 10 is inserted into the housing.
  • the matching length allows the compression pin 10 to move up and down in the housing 8.
  • the cylindrical surface presses and fits the small end bearing 7, limiting the small end bearing 7 in the axial direction and providing preload force.
  • the soft rubber cambered surface of the soft rubber 10-1 is pressed against the outer ring of the small end bearing 7, limiting the small end bearing 7 in the vertical direction and providing preload force.
  • the upper part of the pressing pin 10 and the lower part of the pressing pin 10 are integrated structures, which simplifies the structure of the pressing pin 10 and facilitates the production and manufacture of the pressing pin 10 .
  • the worm 5 When the worm gear 6 and the worm 5 engage in meshing transmission, the worm 5 will drive the small end bearing 7 to produce radial swing motion.
  • the spring force of the small end preload mechanism presses the worm 5 against the worm gear 6 , thereby eliminating the tooth gap between the worm gear 6 and the worm 5, and the soft rubber compression force of the small end side buffer mechanism eliminates the gap between the small end bearing 7 and the housing 8; when the meshing force is large, the small end preload force
  • the hard base material arc surface of the mechanism is in contact with the outer ring of the small end bearing 7, thereby limiting the vertical position of the small end bearing 7.
  • the small end bearing 7 of the small end side buffer mechanism is in contact with the small end of the housing 18
  • the sides of the bearing 7 are in hard limit contact, thereby limiting the left and right positions of the small end bearing 7 .
  • the support component is support component one.
  • the support component one cooperates with the pressing component one.
  • the pressing component one and the supporting component one are arranged in a shell that matches the pressing component one and the supporting component one.
  • the housing one 8 cooperates with the supporting component one and the pressing component one to facilitate the installation of the supporting component one and the pressing component one.
  • the supporting component one and the pressing component one are limited through the housing one 8, thereby facilitating the support.
  • the pressing component 1 plays a limiting role in the vertical direction, and is conducive to the pressing component 1 to provide top damping and hard limiting on the top of the worm 5, and to provide side damping and hard limiting on the side of the worm 5. , to support and limit the swing of the worm 5 and absorb the impact of the worm, thereby eliminating the gap in the worm gear mechanism, reducing noise, and improving the feel.
  • the worm compression support mechanism for the electric power steering system also includes a compression nut 2 and a worm gear hub 4.
  • One end of the worm 5 is covered with the worm gear hub 4.
  • the compression nut 2 is connected to the housing 1 through threads, pressing the bearing end face into the bearing hole of the housing.
  • the worm gear hub 4 and the worm 5 are connected through splines, thereby applying the assist force of the motor output shaft to the worm 5.
  • This embodiment provides a worm compression support mechanism for an electric power steering system, including a worm 5, a worm gear 6, a big end bearing 3, a small end bearing 7, a housing 1, a compression nut 2, and a worm gear hub 4.
  • a worm gear 6 and a worm 5 inside the housing 1.
  • the upper end of the worm gear 6 is connected to the worm 5.
  • One end of the worm 5 is covered with a big-end bearing 3 and a worm gear hub 4.
  • the outer side of the big-end bearing 3 is covered with a Compression nut 2; the other end of the worm 5 is equipped with a small end bearing 7, and a compression component is located on the outer edge side of the small end bearing 7.
  • the compression component is close to the outer ring of the small end bearing 7, and the small end A support component is provided on the upper side of the bearing 7.
  • the support component is located above the compression component, and the lower surface of the support component is close to the compression component.
  • the compression component is compression component 2.
  • Compression component 2 includes leaf spring 16 and preload rubber 17.
  • the sleeve located on the outer edge of the small end bearing 7 is equipped with preload rubber 17.
  • the rear side of the pre-tightened rubber 2 17 is snap-connected to the leaf spring 2 16 .
  • the leaf spring 16 provides top damping and hard limit at the top of the worm 5.
  • the side of the worm 5 relies on the leaf spring 16 and the preload rubber 17 to provide side damping and hard limit to support and limit the swing and absorption of the worm 5. Impact of worm 5, This can eliminate the gap in the worm gear mechanism, reduce noise, and improve the feel; reduce the number of machined surfaces of the housing, simplify installation, and reduce costs; reduce the outer size of the housing and occupy less installation space.
  • the pressing component 1 provides a pre-tightening force for the up and down swing movement, thereby eliminating the gap in the worm gear reduction mechanism; the pressing component 1 provides vertical buffering of the worm 5 to avoid noise caused by up and down impacts; the pressing component 1 provides left and right The swing buffer surface avoids the noise caused by the left and right swing impact; the vertical compression spring feature is provided through the leaf spring 2 16, that is, the elastic force in the vertical direction is provided through the leaf spring 2 16, which can easily adjust the required vertical The compression stiffness is provided to provide the required vertical compression force, and the clearance of the worm gear reduction mechanism is controlled to be zero clearance to avoid noise caused by the clearance of the reduction mechanism; by providing the appropriate vertical compression force through the compression assembly, the Avoid excessive friction torque of the deceleration mechanism and improve steering feel.
  • the second leaf spring 16 has a U-shaped structure, the top of the second leaf spring 16 is an arc structure, and a spring waist-shaped hole 16 is provided at the top of the second leaf spring 16.
  • the left and right sides of the leaf spring 16 are respectively provided with square holes 16-2, and the leaf spring 16 located on the upper side of the square hole 16-2 is provided with an inwardly bent trapezoidal hypotenuse 16-3.
  • the bottom of the edge 16-3 is connected to the leaf spring 16, and the top of the trapezoidal hypotenuse 16-3 is connected to the pressing boss 2 16-4.
  • the arc surface at the top of leaf spring 2 16 fits the spring support round surface of casing 2 13 , the trapezoidal hypotenuse 16 - 3 is placed in the spring installation cavity of the casing, and the boss 2 16 - 4 is pressed against the small end.
  • the outer rings of bearing 7 are in compressive contact.
  • the first pressing boss 11-4 is in pressing contact with the outer ring of the small end bearing 7.
  • the second pressing boss 16-4 is arranged symmetrically. The preload forces in the horizontal direction cancel each other out and the top of the worm 5 in the vertical direction. Provides preload.
  • the vertical buffering of the worm 5 is provided through the leaf spring 216 to avoid noise caused by up and down impacts; the clearance of the worm gear reduction mechanism is controlled to be zero clearance to avoid noise caused by the clearance of the reduction mechanism; excessive friction torque of the reduction mechanism can be avoided , improve steering feel.
  • the second pre-tightening rubber 17 is an annular structure, located inside the top of the second pre-tightening rubber 17 and connected to the slot 17-1.
  • the inner sides of the left and right sides of the middle part are respectively connected to the arc column 17-2.
  • the inner side of the arc column 17-2 is a plane.
  • the inner side of the arc column 17-2 is connected to the boss 2, which is located on the arc column 17-2.
  • a number of protrusions 17-4 are respectively provided on the front end surface of the pre-tension rubber 2 17 at the connection point with the pre-tension rubber 2 17.
  • the arc column 17-2 of the pre-tightening rubber 2 17 is closely matched with the casing, so that it is compressed between the outer ring of the small end bearing 7 and the casing through interference compression of the casing and generates side pre-tightening force.
  • the boss 17-3 of the preload rubber 17 is inserted into the square hole 16-2 of the leaf spring 2 16, and the arc surface of the top of the leaf spring 16 is close to the slot 17-1 of the preload rubber 17.
  • the end face of the protrusion 17-4 so that the preload rubber 17 and the leaf spring 2 16 are assembled into a small assembly, and then inserted into the cavity of the housing 13 until the arc-shaped end face of the preload rubber 17 It is close to the soft rubber supporting end surface of housing 213.
  • the support component 2 includes an adjustment bolt 2 and a compression pin 2.
  • the top of the small end bearing is provided with the bottom of the compression pin 2.
  • the compression pin 2 is There is an adjusting bolt two on the top; the structure of the adjusting bolt two 14 and the pressing pin two 15 is consistent with the structure of the adjusting bolt one 9 and the pressing pin one 10 in Embodiment 1.
  • the support component is support component two; the support component two cooperates with the pressing component two, and the pressing component two and the supporting component two are arranged with the pressing component 2 and the supporting component 2 are matched with the housing 2.
  • the arc column 17-2 of the preload rubber 2 17 is closely matched with the side soft rubber supporting surface of the housing 2 13, so that the outer ring of the small end bearing 7 and the housing 2 are compressed through the interference compression of the boss of the housing 2 13. 13 between the soft rubber assembly holes and generate side pre-tightening force.
  • Shell two 13, support component two and compression group The two parts cooperate to facilitate the installation of the support component 2 and the compression component 2.
  • the support component 2 and the compression component 2 are limited through the housing 2 13, thereby facilitating the pair of the support component 2 and the compression component 2 in the vertical position. It plays a limiting role in the direction and is conducive to the compression component 2. It provides top damping and hard limiting on the top of the worm 5, and provides side damping and hard limiting on the side of the worm 5 to support and limit the swing and movement of the worm 5. Absorbs the impact of the worm, thereby eliminating the gap in the worm gear mechanism, reducing noise, and improving the feel.
  • the worm 5 When the worm gear 6 and the worm 5 engage in meshing transmission, the worm 5 will drive the small end bearing 7 to produce radial swing motion.
  • the spring force of the small end preload mechanism presses the worm 5 against the worm gear 6 , thereby eliminating the tooth gap between the worm gear and the worm, and the soft compression force of the small end side buffer mechanism eliminates the gap between the small end bearing 7 and the housing 2 13; when the meshing force is large, the hard force of the small end preload mechanism
  • the arc surface of the base material is in contact with the outer ring of the small end bearing 7, thereby limiting the vertical position of the small end bearing 7.
  • the small end bearing 7 of the small end side buffer mechanism is in contact with the side of the small end bearing of the housing 213. The hard limit contact limits the left and right position of the small end bearing.
  • This embodiment provides a worm compression support mechanism for an electric power steering system, including a worm 5, a worm gear 6, a big end bearing 3, a small end bearing 7, a housing 1, a compression nut 2, and a worm gear hub 4.
  • a worm gear 6 and a worm 5 inside the housing 1.
  • the upper end of the worm gear 6 is connected to the worm 5.
  • One end of the worm 5 is covered with a big-end bearing 3 and a worm gear hub 4.
  • the outer side of the big-end bearing 3 is covered with a Compression nut 2; the other end of the worm 5 is equipped with a small end bearing 7, and a compression component is located on the outer edge side of the small end bearing 7.
  • the compression component is close to the outer ring of the small end bearing 7, and the small end A support component is provided on the upper side of the bearing 7.
  • the support component is located above the compression component, and the lower surface of the support component is close to the compression component.
  • the compression assembly is compression assembly three.
  • the compression assembly three includes leaf spring three 20 and preload rubber three 21.
  • the outer edge of the small end bearing 7 is sleeved with leaf spring three 20.
  • the rear side of the leaf spring 20 is engaged with the preload rubber 21 .
  • Leaf spring three 20 provides top damping and hard limit at the top of worm 5.
  • the side of worm 5 relies on leaf spring three 20 and preload rubber three 21 to provide side damping and hard limit to support and limit the swing and absorption of worm 5.
  • the impact of the worm 5 can thereby eliminate the gap in the worm gear 5 mechanism, reduce noise, and improve the feel; reduce the number of machined surfaces of the housing, simplify installation, and reduce costs; reduce the outer size of the housing and occupy less installation space.
  • the compression component three provides a preload force for the up and down swing movement, thereby eliminating the gap in the worm gear reduction mechanism; the compression component three provides vertical buffering of the worm 5 to avoid noise caused by up and down impacts; the compression component three provides left and right The swing buffer surface avoids the noise caused by the left and right swing impact; the leaf spring 320 provides a vertical compression spring feature, that is, the leaf spring 320 provides elastic force in the vertical direction, which can easily adjust the required vertical
  • the compression stiffness is provided to provide the required vertical compression force, and the clearance of the worm gear reduction mechanism is controlled to be zero clearance to avoid noise caused by the clearance of the reduction mechanism; by providing the appropriate vertical compression force through the compression assembly three, the Avoid excessive friction torque of the deceleration mechanism and improve steering feel.
  • the leaf spring 320 has an " ⁇ "-shaped structure, the top of the leaf spring 320 is flat, and the two sides of the bottom of the leaf spring 320 are tilted outwards. , and the outwardly tilted end is connected to the pressing boss three 20-1.
  • the front and rear ends of the top of the leaf spring three 20 are respectively provided with spring buckles, and the two spring buckles are symmetrically designed. They are stuck in the middle of the small end bearing 7 in the width direction, and the boss three 20-1 is pressed against the shell.
  • the upper surface of the spring support hole of the body 318 is pressed and contacted to provide preload force on the top of the worm 5 in the vertical direction; the leaf spring 20 is used to provide vertical buffering of the worm 5 to avoid noise caused by up and down impacts. Sound; control the clearance of the worm gear reduction mechanism to zero clearance to avoid noise caused by the clearance of the reduction mechanism; it can avoid excessive friction torque of the reduction mechanism and improve the steering feel.
  • the top, side and bottom of the leaf spring 320 are tangent to the outer ring of the small end bearing 7, forming five positions of line contact at the same time.
  • the spring arm gap is placed in the spring installation cavity of the housing, and the boss 3 is pressed.
  • the vertical buffer avoids noise caused by up and down impacts; it controls the clearance of the worm gear reduction mechanism to zero to avoid noise caused by the clearance of the reduction mechanism; it avoids excessive friction torque of the reduction mechanism and improves the steering feel.
  • the preload rubber 3 21 has a semicircular arc annular structure.
  • the rear ends located on the left and right sides of the preload rubber 3 21 are connected to semi-cylinders 21-3 respectively.
  • the rear end of the top of the tight rubber 21 is connected to the top rubber 21-1, and the center of the top rubber is provided with a center hole 21-2.
  • the semi-cylinder 21-3 of the pre-tightened rubber 21 is interference-compressed between the side planes of the leaf spring 20 and generates side pre-tightening force to avoid noise caused by the left and right swing impact; the semi-cylindrical protrusion 12-2 and
  • the clearance fit of the housing ensures that the preload rubber 12 can be assembled in the housing.
  • support component three includes an adjustment bolt three 19.
  • the top of the small end bearing 7 is provided with an adjustment bolt three 19.
  • the structure of the adjustment bolt three 19 is the bottom of the adjustment bolt three 19.
  • the small cylinder 19-1 is connected on the plane, and the small cylinder of the adjusting bolt three 19 is embedded in the center hole 21-2 of the top rubber 21-1 on the top of the preload rubber three 21.
  • the external thread of the adjusting bolt three 19 is connected with the threaded hole of the housing three 18 through a threaded fit.
  • the bottom plane of the adjusting bolt three 19 is pressed against the upper plane of the top rubber 21-1 of the preloading rubber three 21.
  • the preloading rubber The lower plane of the top rubber 21-1 of the three 21 is pressed against the top plane of the leaf spring three 20.
  • the small cylinder 19-1 of the adjusting bolt three 19 is inserted into the center hole 21-2 of the preload rubber three 21.
  • the small cylinder The end face of 19-1 forms a small gap with the top plane of leaf spring 320; half the length of the outer ring of the small end bearing 7 clamps the side of the leaf spring 320 with the side hard limit of the small end bearing 7 of the housing 318 within the gap space formed by the position.
  • the support component is support component three; support component three is matched with pressing component three, and pressing component three and support component three are arranged in a shell that matches with pressing component three and support component three.
  • the housing three 18 cooperates with the support component three and the compression component three to facilitate the installation of the support component three and the compression component three.
  • the support component three and the compression component three are limited through the housing three 18, thereby facilitating support.
  • Component three pairs of pressing component three play a limiting role in the vertical direction, and are conducive to pressing component three to provide top damping and hard limiting on the top of worm 5 and provide side damping and hard limiting on the side of worm 5 , to support and limit the swing of the worm 5 and absorb the impact of the worm, thereby eliminating the gap in the worm gear mechanism, reducing noise, and improving the feel.
  • the worm 5 When the worm gear 6 and the worm 5 engage in meshing transmission, the worm 5 will drive the small end bearing 7 to produce radial swing motion.
  • the spring force of the small end preload mechanism presses the worm 5 against the worm gear 6 , thereby eliminating the tooth gap between the worm gear and the worm, and the soft rubber compression force of the small end side preload mechanism eliminates the gap between the small end bearing 7 and the housing 318; when the meshing force is large, the small end preload mechanism adjusts
  • the small cylinder 19-1 of the bolt 19 is in flat contact with the top of the leaf spring 20, thereby limiting the vertical position of the small end bearing 7, and the side plane of the leaf spring 20 of the small end side buffer mechanism is in contact with the shell.
  • the sides of the small end bearing 7 of body three 18 are in hard limiting contact, thereby limiting the left and right positions of the small end bearing 7 .
  • This embodiment provides a worm compression support mechanism for an electric power steering system, including a worm 5, a worm gear 6, a big end bearing 3, a small end bearing 7, a housing 1, a compression nut 2, and a worm gear hub 4.
  • a worm gear 6 and a worm 5 inside the housing 1.
  • the upper end of the worm gear 6 is connected to the worm 5.
  • One end of the worm 5 is covered with a big-end bearing 3 and a worm gear hub 4.
  • the outer side of the big-end bearing 3 is covered with a Compression nut 2; the other end of the worm 5 is equipped with a small end bearing 7, and a compression component is located on the outer edge side of the small end bearing 7.
  • the compression component is close to the outer ring of the small end bearing 7, and the small end A support component is provided on the upper side of the bearing 7.
  • the support component is located above the compression component, and the lower surface of the support component is close to the compression component.
  • the pressing assembly is the pressing assembly 4.
  • the pressing assembly 4 includes a preloading rubber 27.
  • the lower part of the outer edge of the small end bearing 7 is equipped with a preloading rubber 27;
  • the preloading rubber Four 27 is a semi-circular arc annular structure.
  • the left and right end surfaces located at the top of the preloaded rubber four 27 are respectively connected to the outer protruding structure 27-1.
  • the inner side of the outer protruding structure 27-1 is a rectangular plane.
  • the preload rubber 27 provides side damping and hard limit on the side of the worm 5 to support and limit the swing of the worm 5 and absorb the impact of the worm 5, thereby eliminating the gap in the worm gear 5 mechanism, reducing noise, and improving the feel; reduce
  • the number of machined surfaces of the shell simplifies installation and reduces costs; the outer dimensions of the shell are reduced, occupying less installation space.
  • the pressing assembly four provides a preload force for the up and down swing movement, thereby eliminating the gap in the worm gear reduction mechanism; the pressing assembly four provides vertical buffering of the worm 5 to avoid noise caused by up and down impacts; the pressing assembly four provides left and right The swing buffer surface avoids noise caused by left and right swing impacts; the compression assembly 4 provides appropriate vertical pressing force to avoid excessive friction torque of the deceleration mechanism and improve steering feel.
  • the support assembly 4 includes a support bushing 26, a coil spring 25, a rubber pad 23, an adjustment screw 23, and a small end bearing 7
  • a support bushing 26 is set on the top.
  • a spiral spring 25 is set on the lower part of the adjusting screw 23.
  • a support bushing 26 is set on the outer side of the spiral spring 25.
  • the adjusting screw 23 is located on the top of the supporting bushing 26.
  • the sleeve is provided with a rubber pad 24, and the bottom of the support bushing 26 is connected to the top end surface of the small end bearing 7.
  • the support bushing 26 is installed in the housing 22.
  • the waist-shaped side of the supporting bushing 26 matches the waist-shaped ring of the housing 22.
  • the supporting bushing 26 can move up and down.
  • the bottom of the supporting bushing 26 is round.
  • the arc surface is in contact with the outer ring of the small end bearing 7.
  • the coil spring 25 is installed in the hole of the support bushing 26.
  • the bottom of the coil spring 25 is supported by the annular surface of the support bushing 26.
  • the adjusting screw 23 has The threaded section, the housing 22 has a threaded hole, the rubber pad 24 is installed on the adjusting screw 23 and then screwed into the housing 22 together.
  • the top of the coil spring 25 is supported by the shoulder of the adjusting screw 23.
  • the bottom of the rubber pad 24 fits the top surface of the support bushing 26, the side of the rubber pad 24 matches the round hole wall of the housing 22, and the cylindrical surface of the adjusting screw 23 is used to limit the position of the coil spring 25.
  • the adjusting screw 23 has a T-shaped structure, the upper outer edge of the adjusting screw 23 is provided with external threads, and the middle part of the adjusting screw 23 is covered with a rubber pad 24.
  • the lower part of the adjusting screw 23 is provided with a coil spring 25.
  • the adjusting screw 23 has a threaded section, and the housing 22 has a threaded hole.
  • the rubber pad 24 is installed on the adjusting screw 23 and then screwed into the housing 22 together.
  • the top of the coil spring 25 is fixed by the adjusting screw 23 shoulder support. The above arrangement facilitates the connection of the adjustment screw 23, the rubber pad 24 and the coil spring 25.
  • the cylindrical structure of the support bushing 26 is provided with a groove on the top of the support bushing 26 that is connected to the lower part of the adjustment screw 23.
  • the support bushing The bottom of 126 is an arc surface. The above arrangement is beneficial to pre-positioning the bottom of the adjusting screw 23 and the supporting bushing 26 .
  • the bottom of the support bushing 26 is an arc surface, so that the bottom of the support bushing 26 can better fit and compress the small end bearing 7 .
  • the supporting component is the supporting component four; the supporting component four matches the pressing component four, and the pressing component four and the supporting component four are arranged in a shell that matches the pressing component four and the supporting component four.
  • the housing 422 cooperates with the support component 4 and the compression component 4 to facilitate the installation of the support component 4 and the compression component 4.
  • the support component 4 and the compression component 4 are limited through the housing 422, thereby facilitating support.
  • the preload rubber 27 is installed between the housing 22 and the small end bearing 7.
  • the rectangular planes of the outer protruding structures 27-1 on both sides of the preload rubber 27 are in contact with the small end bearing 7.
  • the outer surfaces of the preload rubber 27 are in contact with the small end bearing 7.
  • the side surface is in contact with the arc surface of the housing 22, and the housing 422 is also provided with hard limiting surfaces on both sides for hard limiting of the small end bearing 7.
  • This embodiment provides a worm compression support mechanism for an electric power steering system, including a worm 5, a worm gear 6, a big end bearing 3, a small end bearing 7, a housing 1, a compression nut 2, and a worm gear hub 4.
  • a worm gear 6 and a worm 5 inside the housing 1.
  • the upper end of the worm gear 6 is connected to the worm 5.
  • One end of the worm 5 is covered with a big-end bearing 3 and a worm gear hub 4.
  • the outer side of the big-end bearing 3 is covered with a Compression nut 2; the other end of the worm 5 is equipped with a small end bearing 7, and a compression component is located on the outer edge side of the small end bearing 7.
  • the compression component is close to the outer ring of the small end bearing 7, and the small end A support component is provided on the upper side of the bearing 7.
  • the support component is located above the compression component, and the lower surface of the support component is close to the compression component.
  • the compression assembly is compression assembly five.
  • the compression assembly five includes pre-tensioning rubber five.
  • the upper and lower parts of the outer edge of the small end bearing 7 are respectively covered with pre-tensioning rubber five 31;
  • the tight rubber 5 is a rubber ring 31.
  • the rubber ring 31 can provide damping in the radial direction of the entire circumference of the bearing, that is, provide a buffering effect on the top and sides.
  • the rubber ring 31 is elastic and can provide damping and limiting effects in the radial direction of the entire circumference of the worm 5 to support it. And limit the swing of the worm 5 and absorb the impact of the worm 5, thereby eliminating the gap in the worm gear 5 mechanism, reducing noise, and improving the feel; reducing the number of machined surfaces of the housing, simplifying installation, and reducing costs; reducing the outer dimensions of the housing , occupying less installation space.
  • the support component 5 includes a support bushing 2 30 , a coil spring 29 , and an adjustment screw 28 .
  • the top of the small end bearing 7 is provided with an adjustment screw 28
  • the lower part of the adjustment screw 28 is provided with a coil spring 29 .
  • the outer side of the coil spring 29 is provided with a support bushing 230
  • the bottom of the support bushing 230 is connected to the top end surface of the small end bearing 7.
  • the structure of the adjusting screw two 28 is consistent with the structure of the adjusting screw one 23
  • the structure of the two coil springs 29 is consistent with the structure of the coil spring one 25
  • the structure of the supporting bushing two 30 is consistent with the structure of the supporting bushing one 26.
  • the supporting component is the supporting component five; the supporting component five matches the pressing component five, and the pressing component five and the supporting component five are arranged in the housing five 32 that matches the pressing component five and the supporting component five.
  • the housing five 32 cooperates with the support component five and the compression component five to facilitate the installation of the support component five and the compression component five.
  • the support component five and the compression component five are limited through the housing five 32, thereby facilitating support.
  • Component five pairs of pressing component 5 play a limiting role in the vertical direction, and are conducive to pressing component 5 to provide top damping and hard limiting on the top of worm 5 and provide side damping and hard limiting on the side of worm 5 , to support and limit the swing of the worm 5 and absorb the impact of the worm, thereby eliminating the gap in the worm gear mechanism, reducing noise, and improving the feel.
  • the steering wheel and the input shaft of the EPSc steering system are connected through splines.
  • torque hereinafter referred to as manual force to turn the steering wheel
  • the input shaft will be driven to rotate.
  • the input shaft is connected to the steering column through splines.
  • the steering column and the output shaft are connected through splines, which transmit hand force to the output shaft.
  • the torque sensor installed on the output shaft reads the torque signal and transmits this signal to the control unit.
  • the boost motor After calculation by the control unit, the boost motor outputs corresponding torque, which is referred to as boost and speed below. After decelerating and increasing torque through the deceleration mechanism, the boost is applied to the output shaft.
  • the torque output by the output shaft is the total torque of hand force plus boost.
  • the total torque is connected through the output shaft and the intermediate shaft through splines.
  • the intermediate shaft and the steering gear are connected through splines and then transmitted to the steering gear.
  • the steering gear can convert the rotation of the steering wheel into the left and right movement of the rack. This movement is passed through the rack and pinion mechanism.
  • the output is sent to the left and right tie rods, thereby converting the rotational motion of the steering wheel into the left and right swing of the wheels, thus realizing the power steering function of the car.
  • FIG. 34 it is an EPSdp steering system.
  • the steering wheel and the input shaft are connected through splines.
  • the input shaft is connected to the steering column and the steering column through splines. It is connected to the intermediate shaft through splines.
  • the hand force is transmitted to the first pinion of the steering gear, so that the steering gear can convert the rotation of the steering wheel into the left and right movement of the rack.
  • This movement is passed through The rack and pinion mechanism outputs to the left and right tie rods, thereby converting the rotational motion of the steering wheel into left and right oscillation of the wheels.
  • the torque sensor installed on the steering gear reads the hand torque signal and transmits this signal to the control unit.
  • the power-assisted motor After calculation by the control unit, the power-assisted motor outputs corresponding power.
  • the power After decelerating and increasing torque through the reduction mechanism, the power is applied to the output shaft.
  • the torque output by the output shaft is transmitted to the second pinion of the steering gear, and then interacts with the gear of the steering gear.
  • the rack generates a gear and rack meshing motion, which can convert the rotation of the steering wheel into the left and right movement of the rack. This movement is output to the left and right tie rods through the rack and pinion mechanism.
  • the motor assist and the steering wheel hand force act on the rack at the same time. Thereby realizing the power steering function of the car.
  • FIG. 35 it is an EPSp steering system.
  • the steering wheel and the input shaft are connected through splines.
  • the input shaft is connected to the steering column and the steering column through splines. It is connected to the intermediate shaft through splines.
  • the hand force is transmitted to the first pinion of the steering gear, so that the steering gear can convert the rotation of the steering wheel into gears.
  • the left and right movement of the bar is output to the left and right tie rods through the rack and pinion mechanism, thereby converting the rotational motion of the steering wheel into the left and right oscillation of the wheel.
  • the torque sensor installed on the steering gear reads the hand torque signal and transmits this signal to the control unit.
  • the power-assisted motor After calculation by the control unit, the power-assisted motor outputs corresponding power.
  • the power After decelerating and increasing torque through the reduction mechanism, the power is applied to the output shaft.
  • the torque output by the output shaft is transmitted to the first pinion of the steering gear, and then interacts with the gear of the steering gear.
  • the rack generates a gear and rack meshing motion, which can convert the rotation of the steering wheel into the left and right movement of the rack. This movement is output to the left and right tie rods through the rack and pinion mechanism.
  • the motor assist and the steering wheel hand force act on the rack at the same time. Thereby realizing the power steering function of the car.
  • the invention relies on leaf springs or coil springs to provide preloading force
  • the top relies on the combination of compression pins and locking bolts, or the combination of rubber pads, support bushings and adjusting screws to provide top damping and hard limiting
  • the side relies on rubber and shells.
  • the machined surface of the body provides side damping and hard limits to support and limit the swing of the worm and absorb the impact of the worm, thereby eliminating the gap in the worm gear mechanism, reducing noise, and improving the feel; reducing the number of machined surfaces of the shell and simplifying Install and reduce costs; reduce the outer size of the shell and occupy less installation space; provide up and down swing motion preload to eliminate the gap in the worm gear reduction mechanism; provide vertical damping of the worm to avoid noise caused by up and down impacts ; Provide left and right damping of the worm to avoid noise caused by left and right swing impacts; Provide vertical compression spring features to easily adjust the required vertical compression stiffness, thereby providing the required vertical compression force to control the worm gear
  • the clearance of the worm reduction mechanism is zero to avoid noise caused by the clearance of the reduction mechanism; providing appropriate vertical pressing force can avoid excessive friction torque of the reduction mechanism and improve the steering feel.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Power Steering Mechanism (AREA)

Abstract

一种用于电动助力转向系统的蜗杆压紧支撑机构，包括壳体（1），壳体（1）内设有蜗杆（5）及蜗轮（6），蜗轮（6）的上端配合连接蜗杆（5），蜗杆（5）的一端套设有大端轴承（3），另一端套设有小端轴承（7），位于小端轴承（7）的外缘侧设有压紧组件，压紧组件贴紧小端轴承（7）的外圈，小端轴承（7）的上侧设有支撑组件，支撑组件位于压紧组件的上方，且支撑组件的下表面贴紧压紧组件。通过压紧组件提供预紧力，支撑组件设置在压紧组件的上方，且支撑组件的下表面压紧压紧组件，对压紧组件在竖直方向上起到限位作用，压紧组件在蜗杆（5）的顶部和侧面提供阻尼和硬限位，来支撑和限制蜗杆（5）的摆动和吸收蜗杆（5）的冲击。

Description

用于电动助力转向系统的蜗杆压紧支撑机构
本申请要求申请日为2022/8/26的中国专利申请2022110290429的优先权。本申请引用上述中国专利申请的全文。
技术领域
本发明涉及电动助力转向系统技术领域，具体地说是一种用于电动助力转向系统的蜗杆压紧支撑机构。
背景技术
汽车转向系统一般包括方向盘、转向管柱、中间轴、转向机、横拉杆等部分组成。管柱式电动助力转向系统(下述为EPSc)、双小齿轮式电动助力转向系统(下述为EPSdp)、单小齿轮式电动助力转向系统(下述为EPSp)等均属于汽车电动助力转向系统(下述为EPS)，主要功能是将方向盘的旋转运动转换成车轮的左右摆动，从而实现汽车的助力转向功能。EPSc通过安装在转向管柱处的助力电机提供助力扭矩，EPSdp通过安装在转向机第二小齿轮处的助力电机提供助力扭矩，EPSp通过安装在第一小齿轮处的助力电机提供助力扭矩，经减速机构减速增扭，为转向系统提供相应的助力扭矩，从而实现设计的助力功能。一般的，减速机构采用蜗轮蜗杆减速机构，该类型减速机构能提供大减速比且占用空间小。
目前EPS的蜗轮蜗杆机构，由于零件制造存在公差和安装误差等原因，存在摩擦扭矩过大或自由间隙过大等问题，最终导致转动摩擦扭矩过大而影响转向手感或驾驶过坏路时出现蜗轮蜗杆敲击噪音及蜗杆壳体敲击噪音。为降低转动摩擦扭矩及消除敲击噪音，需要控制蜗轮蜗杆减速机构的间隙为零间隙且不能使蜗轮蜗杆贴合过紧，蜗杆径向运动方向提供一定阻尼。一般蜗杆需要由左右两个球轴承提供支撑，由于零件装配后两个轴承同轴度累积误差，导致轴承受力不良，会带来降低轴承承载能力下降、承载转动不畅产生滚动噪音、轴承使用寿命降低及滚动摩擦力矩过大等问题。目前提供零间隙的方案有支架轴承方案、在蜗杆一端增加单独的弹簧柱塞方案等，但均存在诸多缺点，如：零件过多导致的公差累积大、成本过高及安装困难、弹簧压紧力波动范围大导致不能很好的消除蜗轮蜗杆减速机构的间隙、轴承承载能力不足。
发明内容
本发明为克服现有技术的不足，提供一种用于电动助力转向系统的蜗杆压紧支撑机构，通过五种不同结构的方案，从而能消除蜗轮蜗杆减速机构的径向间隙，提升转向手感，降低敲击噪音。
为实现上述目的，设计一种用于电动助力转向系统的蜗杆压紧支撑机构，包括蜗杆、蜗轮、大端轴承、小端轴承、壳体，其特征在于：壳体内设有蜗轮及蜗杆，蜗轮的上端配合连接蜗杆，蜗杆的一端套设有大端轴承，蜗杆的另一端套设有小端轴承，位于小端轴承的外缘侧设有压紧组件，所述压紧组件贴紧所述小端轴承的外圈，小端轴承的上侧设有支撑组件，支撑组件位于压紧组件的上方，且所述支撑组件的下表面贴紧所述压紧组件。
在本方案中，通过压紧组件提供预紧力，支撑组件设置在压紧组件的上方，且支撑组件的下表面压紧压紧组件，对压紧组件在竖直方向上起到限位作用。压紧组件在蜗杆的顶部提供顶部阻尼和硬限位，在蜗杆的侧面提供侧面阻尼和硬限位，来支撑和限制蜗杆的摆动和吸收蜗杆的冲击，从而能消除蜗轮蜗杆机构的间隙、降低噪音、改善手感；减少壳体的机加工面数量、简化安装、降低成本；减小壳体外廓尺寸，占用更小的安装空间。通过压紧组件提供上下摆动运动预紧力，从而消除蜗轮蜗杆减速机构的间隙；通过压紧组件提供蜗杆的竖直缓冲，避免由上下冲击产生的噪音；通过压紧组件提供左右摆动缓冲面，避免由左右摆动冲击产生的噪音；提供竖直压紧弹簧特征，即通过压紧组件提供竖直压紧的弹性力，可方便调节出所需的竖直压紧刚度，从而提供所需的竖直压紧力，控制蜗轮蜗杆减速机构的间隙为零间隙，避免由减速机构间隙产生的噪音；通过压紧组件提供合适的竖直压紧力，可避免减速机构的摩擦扭矩过大，提升转向手感。
为实现上述目的，设计一种用于电动助力转向系统的蜗杆压紧支撑机构，包括蜗杆、蜗轮、大端轴承、小端轴承、壳体、压紧螺母、蜗杆齿毂，其特征在于：壳体内设有蜗轮及蜗杆，蜗轮的上端配合连接蜗杆，蜗杆的一端套设有大端轴承及蜗杆齿毂，位于大端轴承的外侧套设有压紧螺母；蜗杆的另一端套设有小端轴承，位于小端轴承的外缘侧设有压紧组件，小端轴承的上侧设有支撑组件。
所述的压紧组件为压紧组件一、压紧组件二、压紧组件三、压紧组件四、压紧组件五中的一种；所述的支撑组件为支撑组件一、支撑组件二、支撑组件三、支撑组件四、支撑组件五中的一种；所述的压紧组件一与支撑组件一相配合；压紧组件二与支撑组件二相配合；压紧组件三支撑组件三相配合；压紧组件四与支撑组件四相配合；压紧组件五与支撑组件五相配合。
所述的压紧组件一包括叶片弹簧一、预紧橡胶一，位于小端轴承外缘的上部套设有叶片弹簧一，小端轴承外缘的下部套设有预紧橡胶一。
所述的叶片弹簧一呈蝴蝶状结构，叶片弹簧一的顶部为圆弧形的中间端面，中间端面的左右两端的顶部分别连接弹簧卡扣，中间端面的左右两端的底部分别连接弹簧臂的一端，弹簧臂的另一端连接压紧凸台一；位于中间端面的中部设有弹簧腰型孔一；所述的弹簧臂由两个向内倾斜的弯折面板组成，并且弹簧臂的截面呈C字型结构。
所述的预紧橡胶一呈U型结构，预紧橡胶一上部的左右两侧分别连接凸筋，位于凸筋下侧的预紧橡胶一上连接半圆柱凸起。
所述的支撑组件一包括调整螺栓一、压紧销一，小端轴承的顶部设有压紧销一的底部，压紧销一的顶部设有调整螺栓一。
所述的调整螺栓一的外缘周设有外螺纹，调整螺栓一的底部为平面，调整螺栓一的顶部连接内六角凹槽。
所述的压紧销一的上部为圆柱形结构，压紧销一的下部为腰型柱结构，压紧销一的下部嵌设有软胶；并且压紧销一的上部及压紧销一的下部为一体结构；位于压紧销一的顶部设有定位方孔，压紧销一的底部为圆弧形结构。
所述的压紧组件二包括叶片弹簧二、预紧橡胶二，位于小端轴承外缘的套设有预紧橡胶二，预紧橡胶二的后侧卡扣连接叶片弹簧二。
所述的叶片弹簧二为U型结构，叶片弹簧二的顶部为圆弧结构，位于叶片弹簧二的顶部设有弹簧腰型孔二，叶片弹簧二的左右两侧分别设有方孔，位于方孔上侧的叶片弹簧二上设有向内弯折的梯形斜边，梯形斜边的底部与叶片弹簧二连接，梯形斜边的顶部连接压紧凸台二。
所述的预紧橡胶二为圆环形结构，位于预紧橡胶二顶部内侧连接卡槽，预紧橡胶二的中部左右两侧的内侧面分别连接圆弧柱，所述的圆弧柱的内侧面为平面，位于圆弧柱的内侧面连接凸台，位于圆弧柱与预紧橡胶二连接处的预紧橡胶二前端面上分别设有若干凸起。
所述的支撑组件二包括调整螺栓二、压紧销二，小端轴承的顶部设有压紧销二的底部，压紧销二的顶部设有调整螺栓二；所述的调整螺栓二及压紧销二的结构与调整螺栓一及压紧销一的结构一致。
所述的压紧组件三包括叶片弹簧三、预紧橡胶三，位于小端轴承的外缘套设有叶片弹簧三，叶片弹簧三的后侧卡接预紧橡胶三。
所述的叶片弹簧三呈“Ω”状结构，叶片弹簧三顶部为平面，叶片弹簧三的底部两侧分别向外翘起，并且所述的向外翘起的端部连接压紧凸台三。
所述的预紧橡胶三为半圆弧环状结构，位于预紧橡胶三左右两侧的后端分别连接半圆柱，位于预紧橡胶三顶部的后端连接顶部橡胶，顶部橡胶的中心设有中心孔。
所述的支撑组件三包括调整螺栓三，小端轴承的顶部设有调整螺栓三，所述的调整螺栓三的结构为调整螺栓一的底部平面上连接小圆柱，并且调整螺栓三的小圆柱嵌设在预紧橡胶三顶部的顶部橡胶的中心孔内。
所述的压紧组件四包括预紧橡胶四，位于小端轴承外缘的下部套设有预紧橡胶四；所述的预紧橡胶四为半圆弧环状结构，位于预紧橡胶四的顶部左右两侧端面分别连接外侧凸起结构，所述的外侧凸起结构的内侧面为矩形平面。
所述的支撑组件四包括支撑衬套一、螺旋弹簧一、橡胶垫、调整螺钉一，小端轴承的顶部设有调整螺钉一，调整螺钉一的下部套设有螺旋弹簧一，螺旋弹簧一的外侧套设有支撑衬套一，位于支撑衬 套一顶部的调整螺钉一上套设有橡胶垫，支撑衬套一的底部与小端轴承的顶部端面连接。
所述的调整螺钉一呈T型结构，调整螺钉一的上部外缘设有外螺纹，调整螺钉一的中部套设有橡胶垫，调整螺钉一的下部套设有螺旋弹簧一。
所述的支撑衬套一的圆柱形结构，位于支撑衬套一的顶部设有与调整螺钉一下部配合连接的凹槽，支撑衬套一的底部为圆弧面。
所述的压紧组件五包括预紧橡胶五，位于小端轴承外缘的上部及下部分别套设有预紧橡胶五；所述的预紧橡胶五为橡胶圆环。
所述的支撑组件五包括支撑衬套二、螺旋弹簧二、调整螺钉二，小端轴承的顶部设有调整螺钉二，调整螺钉二的下部套设有螺旋弹簧二，螺旋弹簧二的外侧套设有支撑衬套二，支撑衬套二的底部与小端轴承的顶部端面连接。
所述的调整螺钉二的结构与调整螺钉一的结构一致；螺旋弹簧二的结构与螺旋弹簧一的结构一致；支撑衬套二的结构与支撑衬套一的结构一致。
所述的压紧组件一及支撑组件一设置在与压紧组件一及支撑组件一相配合的壳体一内；所述的压紧组件二及支撑组件二设置在与压紧组件二及支撑组件二相配合的壳体二内；所述的压紧组件三及支撑组件三设置在与压紧组件三及支撑组件三相配合的壳体三内；所述的压紧组件四及支撑组件四设置在与压紧组件四及支撑组件四相配合的壳体四内；所述的压紧组件五及支撑组件五设置在与压紧组件五及支撑组件五相配合的壳体五内。本发明的积极进步效果在于：通过压紧组件提供预紧力，支撑组件设置在压紧组件的上方，且支撑组件的下表面压紧压紧组件，对压紧组件在竖直方向上起到限位作用。压紧组件在蜗杆的顶部提供顶部阻尼和硬限位，蜗杆的侧面依靠压紧组件提供侧面阻尼和硬限位，来支撑和限制蜗杆的摆动和吸收蜗杆的冲击，从而能消除蜗轮蜗杆机构的间隙、降低噪音、改善手感；减少壳体的机加工面数量、简化安装、降低成本；减小壳体外廓尺寸，占用更小的安装空间。通过压紧组件提供上下摆动运动预紧力，从而消除蜗轮蜗杆减速机构的间隙；通过压紧组件提供蜗杆的竖直缓冲，避免由上下冲击产生的噪音；通过压紧组件提供左右摆动缓冲面，避免由左右摆动冲击产生的噪音；通过压紧组件提供竖直压紧弹簧特征，可方便调节出所需的竖直压紧刚度，从而提供所需的竖直压紧力，控制蜗轮蜗杆减速机构的间隙为零间隙，避免由减速机构间隙产生的噪音；通过压紧组件提供合适的竖直压紧力，可避免减速机构的摩擦扭矩过大，提升转向手感。
附图说明
图1为本发明结构剖面图。
图2，图3为本发明方案一结构剖视图。
图4，图5为方案一中叶片弹簧一的结构示意图。
图6为方案一中预紧橡胶一的结构示意图。
图7为方案一中调整螺栓一的结构示意图。
图8，图9为方案一中压紧销一的结构示意图。
图10为方案一中壳体一的结构示意图。
图11，图12为本发明方案二结构剖视图。
图13为方案二中叶片弹簧二和预紧橡胶二连接结构示意图。
图14为方案二中叶片弹簧二的结构示意图。
图15为方案二中预紧橡胶二的结构示意图。
图16为中壳体二的结构示意图。
图17，图18为本发明方案三结构剖视图。
图19为方案三中叶片弹簧三和预紧橡胶三连接结构示意图。
图20为方案三中叶片弹簧三的结构示意图。
图21为方案三中预紧橡胶三的结构示意图。
图22为方案三中调整螺栓三的结构示意图。
图23为中壳体三的结构示意图。
图24，图25为本发明方案四结构剖视图。
图26为方案四中预紧橡胶四的结构示意图。
图27为方案四中调整螺钉的结构示意图。
图28为方案四中支撑衬套的结构示意图。
图29为中壳体四的结构示意图。
图30，图31为本发明方案五结构剖视图。
图32为方案五中小端轴承与预紧橡胶五连接结构示意图。
图33为本发明结构安装在EPSc转向系统中的示意图。
图34为本发明结构安装在EPSdp转向系统中的示意图。
图35为本发明结构安装在EPSp转向系统中的示意图。
具体实施方式
下面根据附图对本发明做进一步的说明。
实施例1
本实施例提供一种用于电动助力转向系统的蜗杆压紧支撑机构，包括蜗杆5、蜗轮6、大端轴承3、小端轴承7、壳体1、压紧螺母2、蜗杆齿毂4.其中，壳体1内设有蜗轮6及蜗杆5，蜗轮6的上 端配合连接蜗杆5，蜗杆5的一端套设有大端轴承3及蜗杆齿毂4，位于大端轴承3的外侧套设有压紧螺母2；蜗杆5的另一端套设有小端轴承7，位于小端轴承7的外缘侧设有压紧组件，压紧组件贴紧所述小端轴承7的外圈，小端轴承7的上侧设有支撑组件，支撑组件位于压紧组件的上方，且支撑组件的下表面贴紧压紧组件。通过压紧组件提供预紧力，支撑组件设置在压紧组件的上方，且支撑组件的下表面压紧压紧组件，对压紧组件在竖直方向上起到限位作用。压紧组件在蜗杆5的顶部提供顶部阻尼和硬限位，蜗杆5的侧面依靠压紧组件提供侧面阻尼和硬限位，来支撑和限制蜗杆5的摆动和吸收蜗杆5的冲击，从而能消除蜗轮蜗杆5机构的间隙、降低噪音、改善手感；减少壳体的机加工面数量、简化安装、降低成本；减小壳体外廓尺寸，占用更小的安装空间。通过压紧组件提供上下摆动运动预紧力，从而消除蜗轮蜗杆减速机构的间隙；通过压紧组件提供蜗杆5的竖直缓冲，避免由上下冲击产生的噪音；通过压紧组件提供左右摆动缓冲面，避免由左右摆动冲击产生的噪音；通过压紧组件提供竖直弹簧特征，可方便调节出所需的竖直压紧刚度，从而提供所需的竖直压紧力，控制蜗轮蜗杆5减速机构的间隙为零间隙，避免由减速机构间隙产生的噪音；通过压紧组件提供合适的竖直压紧力，可避免减速机构的摩擦扭矩过大，提升转向手感。
如图1所示，转向系统的助力电机的输出轴通过联轴器与蜗杆齿毂4连接，蜗杆齿毂4与蜗杆5通过花键连接，从而将电机输出轴的助力施加到蜗杆5上。大端轴承3外圈间隙配合放置在壳体轴承孔内，压紧螺母2与壳体1通过螺纹连接，将轴承端面压紧在壳体轴承孔内，大端轴承3内圈通过过盈配合安装在蜗杆5的大端轴承座上，大端轴承3允许蜗杆5绕轴承中心产生圆周方向的小幅度摆动运动。小端轴承7内圈通过过盈配合安装在蜗杆5的小端轴承座上，外圈间隙放置在壳体腔内。蜗轮6与输出轴包塑成一体，并通过轴承支撑在壳体1内，蜗轮6和蜗杆5通过螺旋斜齿啮合传动，限位销间隙配合插在壳体1的腰形孔内，叶片弹簧的卡扣卡紧在壳体槽上，即压紧组件通过卡扣的连接方式卡紧在壳体槽上。
作为一种较佳的实施方式，如图2-图10所示，压紧组件为压紧组件一，压紧组件一包括叶片弹簧一11、预紧橡胶一12，位于小端轴承7外缘的上部套设有叶片弹簧一11，小端轴承7外缘的下部套设有预紧橡胶一12。通过压紧组件一提供预紧力。叶片弹簧一11在蜗杆5的顶部提供顶部阻尼和硬限位，蜗杆5的侧面依靠叶片弹簧一11和预紧橡胶一12提供侧面阻尼和硬限位，来支撑和限制蜗杆5的摆动和吸收蜗杆5的冲击，从而能消除蜗轮蜗杆5机构的间隙、降低噪音、改善手感；减少壳体的机加工面数量、简化安装、降低成本；减小壳体外廓尺寸，占用更小的安装空间。通过压紧组件一提供上下摆动运动预紧力，从而消除蜗轮蜗杆减速机构的间隙；通过压紧组件一提供蜗杆5的竖直缓冲，避免由上下冲击产生的噪音；通过压紧组件一提供左右摆动缓冲面，避免由左右摆动冲击产生的噪音；通过叶片弹簧一11提供竖直压紧弹簧特征，即通过叶片弹簧一提供竖直方向上的弹性力，可方便调节出所需的竖直压紧刚度，从而提供所需的竖直压紧力，控制蜗轮蜗杆减速机构的间隙为零 间隙，避免由减速机构间隙产生的噪音；通过压紧组件一提供合适的竖直压紧力，可避免减速机构的摩擦扭矩过大，提升转向手感。
作为一种较佳的实施方式，如图4和图5所示，叶片弹簧一11呈蝴蝶状结构，叶片弹簧一11的顶部为圆弧形的中间端面11-1，中间端面11-1的左右两端的顶部分别连接弹簧卡扣11-2，中间端面11-1的左右两端的底部分别连接弹簧臂11-3的一端，弹簧臂11-3的另一端连接压紧凸台一11-4；位于中间端面11-1的中部设有弹簧腰型孔一11-5；弹簧臂11-3由两个向内倾斜的弯折面板组成，并且弹簧臂11-3的截面呈C字型结构。叶片弹簧一11的弹簧卡扣11-2为对称设计，通过过盈卡紧在壳体的弹簧卡槽上，叶片弹簧一11顶部的中间端面11-1与壳体贴合用于叶片弹簧一11的轴向定位，弹簧臂11-3间隙放置在壳体的安装空腔内，压紧凸台一11-4与小端轴承7的外圈压紧接触，压紧凸台一11-4对称设置，水平方向上的预紧力相互抵消，竖直方向上对蜗杆5的顶部提供预紧力；通过叶片弹簧一11提供蜗杆5的竖直缓冲，避免由上下冲击产生的噪音；控制蜗轮蜗杆减速机构的间隙为零间隙，避免由减速机构间隙产生的噪音；可避免减速机构的摩擦扭矩过大，提升转向手感。叶片弹簧一11呈蝴蝶状结构，有利于简化叶片弹簧一11的结构设置，弹簧臂11-3的截面呈C字型结构，有利于简化弹簧臂11-3的结构设置，通过上述设置有利于实现叶片弹簧一11的一体设置，便于叶片弹簧一11的生产制造。
作为一种较佳的实施方式，如图6所示，预紧橡胶一12呈U型结构，预紧橡胶一12上部的左右两侧分别连接凸筋12-1，位于凸筋12-1下侧的预紧橡胶一12上连接半圆柱凸起12-2。预紧橡胶一12的凸筋12-1过盈压缩在小端轴承7外圈与侧面软胶支撑面之间并产生侧边预紧力，预紧橡胶一12提供蜗杆5左右摆动缓冲面，避免由左右摆动冲击产生的噪音；半圆柱凸起12-2与壳体间隙配合，保证预紧橡胶一12能够装配在壳体内。
作为一种较佳的实施方式，所述的支撑组件一包括调整螺栓一、压紧销一，小端轴承7的顶部设有压紧销一10的底部，压紧销一10的顶部设有调整螺栓一9。压紧销一10插入到壳体一8的腰形孔内，调整螺栓一9压紧贴合压紧销一10，有利于调整螺栓一9、压紧销一10、小端轴承7之间无间隙固定，在轴向上对小端轴承7进行限位并提供预紧力。
作为一种较佳的实施方式，如图7所示，所述的调整螺栓一9的外缘周设有外螺纹，调整螺栓一9的底部为平面，调整螺栓一9的顶部连接内六角凹槽9-1。调整螺栓一9的外螺纹与壳体一8的螺纹孔通过螺纹配合连接，调整螺栓一9的底部平面压紧贴合在压紧销一10的顶部平面上，提供设置内六角凹槽9-1便于调节螺纹旋入角度，保证调整螺栓一9、压紧销一10、小端轴承7之间无间隙固定，在轴向上对小端轴承7进行限位并提供预紧力。
作为一种较佳的实施方式，如图8和图9所示，压紧销一10的上部为圆柱形结构，压紧销一10的下部为腰型柱结构；压紧销一10的下部嵌设有软胶10-1；并且压紧销一10的上部及压紧销一10 的下部为一体结构；位于压紧销一10的顶部设有定位方孔10-2，压紧销一10的底部为圆弧形结构。压紧销一10的腰形柱面间隙插入到壳体一8的腰形孔内和叶片弹簧一11的弹簧腰型孔一11-5内，压紧销一10的圆柱面间隙插入到壳体一8的圆孔内，配合长度允许压紧销一10在壳体一8内上下移动，底部的圆弧形结构与小端轴承7的外圈有间隙，有利于压紧销一10的圆柱面压紧贴合小端轴承7，在轴向上对小端轴承7进行限位并提供预紧力。软胶10-1的软胶弧面贴合压紧在小端轴承7的外圈，在竖直方向上对小端轴承7进行限位并提供预紧力。压紧销一10的上部及压紧销一10的下部为一体结构，简化了压紧销一10的结构，便于压紧销一10的生产制造。
当蜗轮6和蜗杆5产生啮合传动时，蜗杆5将带动小端轴承7产生径向的摆动运动，当啮合力较小时，小端预紧力机构的弹簧力将蜗杆5压紧在蜗轮6上，从而消除蜗轮6与蜗杆5之间的齿隙，小端侧边缓冲机构的软胶压缩力消除小端轴承7与壳体一8的间隙；当啮合力较大时，小端预紧力机构的硬质基材弧面与小端轴承7的外圈接触，从而将小端轴承7的竖直位置限制住，小端侧边缓冲机构的小端轴承7与壳体一8的小端轴承7侧边硬限位接触，从而将小端轴承7的左右位置限制住。
作为一种较佳的实施方式，支撑组件为支撑组件一，支撑组件一与压紧组件一相配合，压紧组件一及支撑组件一设置在与压紧组件一及支撑组件一相配合的壳体一8内。壳体一8与支撑组件一和压紧组件一相配合，便于支撑组件一和压紧组件一的安装，通过壳体一8对支撑组件一和压紧组件一进行限位，从而有利于支撑组件一对压紧组件一在竖直方向上起到限位作用，且有利于压紧组件一在蜗杆5的顶部提供顶部阻尼和硬限位，在蜗杆5的侧面提供侧面阻尼和硬限位，来支撑和限制蜗杆5的摆动和吸收蜗杆的冲击，从而能消除蜗轮蜗杆机构的间隙、降低噪音、改善手感。
作为一种较佳的实施方式，用于电动助力转向系统的蜗杆压紧支撑机构还包括压紧螺母2和蜗杆齿毂4，蜗杆5的一端套设有蜗杆齿毂4。压紧螺母2与壳体1通过螺纹连接，将轴承端面压紧在壳体轴承孔内，蜗杆齿毂4与蜗杆5通过花键连接，从而将电机输出轴的助力施加到蜗杆5上。
实施例2
本实施例提供一种用于电动助力转向系统的蜗杆压紧支撑机构，包括蜗杆5、蜗轮6、大端轴承3、小端轴承7、壳体1、压紧螺母2、蜗杆齿毂4.其中，壳体1内设有蜗轮6及蜗杆5，蜗轮6的上端配合连接蜗杆5，蜗杆5的一端套设有大端轴承3及蜗杆齿毂4，位于大端轴承3的外侧套设有压紧螺母2；蜗杆5的另一端套设有小端轴承7，位于小端轴承7的外缘侧设有压紧组件，压紧组件贴紧所述小端轴承7的外圈，小端轴承7的上侧设有支撑组件，支撑组件位于压紧组件的上方，且支撑组件的下表面贴紧压紧组件。如图11-图16所示，压紧组件为压紧组件二，压紧组件二包括叶片弹簧二16、预紧橡胶二17，位于小端轴承7外缘的套设有预紧橡胶二17，预紧橡胶二17的后侧卡扣连接叶片弹簧二16。叶片弹簧二16在蜗杆5的顶部提供顶部阻尼和硬限位，蜗杆5的侧面依靠叶片弹簧二16和预紧橡胶二17提供侧面阻尼和硬限位，来支撑和限制蜗杆5的摆动和吸收蜗杆5的冲击， 从而能消除蜗轮蜗杆5机构的间隙、降低噪音、改善手感；减少壳体的机加工面数量、简化安装、降低成本；减小壳体外廓尺寸，占用更小的安装空间。通过压紧组件一提供上下摆动运动预紧力，从而消除蜗轮蜗杆减速机构的间隙；通过压紧组件一提供蜗杆5的竖直缓冲，避免由上下冲击产生的噪音；通过压紧组件一提供左右摆动缓冲面，避免由左右摆动冲击产生的噪音；通过叶片弹簧二16提供竖直压紧弹簧特征，即通过叶片弹簧二16提供竖直方向上的弹性力，可方便调节出所需的竖直压紧刚度，从而提供所需的竖直压紧力，控制蜗轮蜗杆减速机构的间隙为零间隙，避免由减速机构间隙产生的噪音；通过压紧组件一提供合适的竖直压紧力，可避免减速机构的摩擦扭矩过大，提升转向手感。
作为一种较佳的实施方式，如图14所示，叶片弹簧二16为U型结构，叶片弹簧二16的顶部为圆弧结构，位于叶片弹簧二16的顶部设有弹簧腰型孔二16-1，叶片弹簧二16的左右两侧分别设有方孔16-2，位于方孔16-2上侧的叶片弹簧二16上设有向内弯折的梯形斜边16-3，梯形斜边16-3的底部与叶片弹簧二16连接，梯形斜边16-3的顶部连接压紧凸台二16-4。叶片弹簧二16顶部的弧面与壳体二13的弹簧支撑圆面贴合，梯形斜边16-3间隙放置在壳体的弹簧安装空腔内，压紧凸台二16-4与小端轴承7的外圈压紧接触。压紧凸台一11-4与小端轴承7的外圈压紧接触，压紧凸台二16-4对称设置，水平方向上的预紧力相互抵消，竖直方向上对蜗杆5的顶部提供预紧力。通过叶片弹簧二16提供蜗杆5的竖直缓冲，避免由上下冲击产生的噪音；控制蜗轮蜗杆减速机构的间隙为零间隙，避免由减速机构间隙产生的噪音；可避免减速机构的摩擦扭矩过大，提升转向手感。
作为一种较佳的实施方式，如图13-图15所示，预紧橡胶二17为圆环形结构，位于预紧橡胶二17顶部内侧连接卡槽17-1，预紧橡胶二17的中部左右两侧的内侧面分别连接圆弧柱17-2，圆弧柱17-2的内侧面为平面，位于圆弧柱17-2的内侧面连接凸台2，位于圆弧柱17-2与预紧橡胶二17连接处的预紧橡胶二17前端面上分别设有若干凸起17-4。预紧橡胶二17的圆弧柱17-2与壳体贴紧配合，从而通过壳体过盈压缩在小端轴承7外圈与壳体之间并产生侧边预紧力。预紧橡胶二17的凸台17-3间隙插入到叶片弹簧二16的方孔16-2内，叶片弹簧二16的顶部的弧面贴紧在预紧橡胶二17的卡槽17-1内以及凸起17-4的端面上，从而预紧橡胶二17与叶片弹簧二16装配成小总成，再插入到壳体二13的空腔内，直到预紧橡胶二17的圆弧形端面与壳体二13的软胶支撑端面贴紧。
作为一种较佳的实施方式，如图11-图16所示，支撑组件二包括调整螺栓二、压紧销二，小端轴承的顶部设有压紧销二的底部，压紧销二的顶部设有调整螺栓二；所述的调整螺栓二14及压紧销二15的结构与实施例1中的调整螺栓一9及压紧销一10的结构一致。
作为一种较佳的实施方式，如图11-图16所示，支撑组件为支撑组件二；支撑组件二与压紧组件二相配合，压紧组件二及支撑组件二设置在与压紧组件二及支撑组件二相配合的壳体二内。预紧橡胶二17的圆弧柱17-2与壳体二13的侧面软胶支撑面贴紧配合，从而通过壳体二13的凸台过盈压缩在小端轴承7外圈与壳体二13的软胶装配孔之间并产生侧边预紧力。壳体二13与支撑组件二和压紧组 件二相配合，便于支撑组件二和压紧组件二的安装，通过壳体二13对支撑组件二和压紧组件二进行限位，从而有利于支撑组件二对对压紧组件二在竖直方向上起到限位作用，且有利于压紧组件二在蜗杆5的顶部提供顶部阻尼和硬限位，在蜗杆5的侧面提供侧面阻尼和硬限位，来支撑和限制蜗杆5的摆动和吸收蜗杆的冲击，从而能消除蜗轮蜗杆机构的间隙、降低噪音、改善手感。
当蜗轮6和蜗杆5产生啮合传动时，蜗杆5将带动小端轴承7产生径向的摆动运动，当啮合力较小时，小端预紧力机构的弹簧力将蜗杆5压紧在蜗轮6上，从而消除蜗轮蜗杆之间的齿隙，小端侧边缓冲机构的软胶压缩力消除小端轴承7与壳体二13的间隙；当啮合力较大时，小端预紧力机构的硬质基材弧面与小端轴承7的外圈接触，从而将小端轴承7的竖直位置限制住，小端侧边缓冲机构的小端轴承7与壳体二13的小端轴承侧边硬限位接触，从而将小端轴承的左右位置限制住。
实施例3
本实施例提供一种用于电动助力转向系统的蜗杆压紧支撑机构，包括蜗杆5、蜗轮6、大端轴承3、小端轴承7、壳体1、压紧螺母2、蜗杆齿毂4.其中，壳体1内设有蜗轮6及蜗杆5，蜗轮6的上端配合连接蜗杆5，蜗杆5的一端套设有大端轴承3及蜗杆齿毂4，位于大端轴承3的外侧套设有压紧螺母2；蜗杆5的另一端套设有小端轴承7，位于小端轴承7的外缘侧设有压紧组件，压紧组件贴紧所述小端轴承7的外圈，小端轴承7的上侧设有支撑组件，支撑组件位于压紧组件的上方，且支撑组件的下表面贴紧压紧组件。如图17-图23所示，压紧组件为压紧组件三，压紧组件三包括叶片弹簧三20、预紧橡胶三21，位于小端轴承7的外缘套设有叶片弹簧三20，叶片弹簧三20的后侧卡接预紧橡胶三21。叶片弹簧三20在蜗杆5的顶部提供顶部阻尼和硬限位，蜗杆5的侧面依靠叶片弹簧三20和预紧橡胶三21提供侧面阻尼和硬限位，来支撑和限制蜗杆5的摆动和吸收蜗杆5的冲击，从而能消除蜗轮蜗杆5机构的间隙、降低噪音、改善手感；减少壳体的机加工面数量、简化安装、降低成本；减小壳体外廓尺寸，占用更小的安装空间。通过压紧组件三提供上下摆动运动预紧力，从而消除蜗轮蜗杆减速机构的间隙；通过压紧组件三提供蜗杆5的竖直缓冲，避免由上下冲击产生的噪音；通过压紧组件三提供左右摆动缓冲面，避免由左右摆动冲击产生的噪音；通过叶片弹簧三20提供竖直压紧弹簧特征，即通过叶片弹簧三20提供竖直方向上的弹性力，可方便调节出所需的竖直压紧刚度，从而提供所需的竖直压紧力，控制蜗轮蜗杆减速机构的间隙为零间隙，避免由减速机构间隙产生的噪音；通过压紧组件三提供合适的竖直压紧力，可避免减速机构的摩擦扭矩过大，提升转向手感。
作为一种较佳的实施方式，如图19和图20所示，叶片弹簧三20呈“Ω”状结构，叶片弹簧三20顶部为平面，叶片弹簧三20的底部两侧分别向外翘起，并且向外翘起的端部连接压紧凸台三20-1。叶片弹簧三20顶部的前后两端分别设有弹簧卡扣，并且两个弹簧卡扣为对称设计，在小端轴承7宽度方向上将其卡在中间，压紧凸台三20-1与壳体三18的弹簧支撑孔上平面压紧接触，竖直方向上对蜗杆5的顶部提供预紧力；通过叶片弹簧三20提供蜗杆5的竖直缓冲，避免由上下冲击产生的噪 音；控制蜗轮蜗杆减速机构的间隙为零间隙，避免由减速机构间隙产生的噪音；可避免减速机构的摩擦扭矩过大，提升转向手感。叶片弹簧三20的顶部、侧边、底部与小端轴承7的外圈相切，同时形成五个位置的线接触，弹簧臂间隙放置在壳体的弹簧安装空腔内，压紧凸台三20-1与壳体三18的弹簧支撑孔上平面压紧接触，水平方向上的预紧力相互抵消，竖直方向上对蜗杆5的顶部提供预紧力；通过叶片弹簧三20提供蜗杆5的竖直缓冲，避免由上下冲击产生的噪音；控制蜗轮蜗杆减速机构的间隙为零间隙，避免由减速机构间隙产生的噪音；可避免减速机构的摩擦扭矩过大，提升转向手感。
作为一种较佳的实施方式，如图21所示，预紧橡胶三21为半圆弧环状结构，位于预紧橡胶三21左右两侧的后端分别连接半圆柱21-3，位于预紧橡胶三21顶部的后端连接顶部橡胶21-1，顶部橡胶的中心设有中心孔21-2。预紧橡胶三21的半圆柱21-3过盈压缩在叶片弹簧三20的侧边平面之间并产生侧边预紧力，避免由左右摆动冲击产生的噪音；半圆柱凸起12-2与壳体间隙配合，保证预紧橡胶一12能够装配在壳体内。
作为一种较佳的实施方式，如图22所示，支撑组件三包括调整螺栓三19，小端轴承7的顶部设有调整螺栓三19，调整螺栓三19的结构为调整螺栓三19的底部平面上连接小圆柱19-1，并且调整螺栓三19的小圆柱嵌设在预紧橡胶三21顶部的顶部橡胶21-1的中心孔21-2内。调整螺栓三19的外螺纹与壳体三18的螺纹孔通过螺纹配合连接，调整螺栓三19的底部平面压紧贴合在预紧橡胶三21的顶部橡胶21-1的上平面，预紧橡胶三21的顶部橡胶21-1的下平面压紧在叶片弹簧三20的顶部平面，调整螺栓三19的小圆柱19-1间隙插入到预紧橡胶三21的中心孔21-2内，小圆柱19-1的端面与叶片弹簧三20的顶部平面形成小间隙；小端轴承7外圈的一半长度将叶片弹簧三20的侧面夹在与壳体三18的小端轴承7的侧边硬限位形成的间隙空间内。
作为一种较佳的实施方式，支撑组件为支撑组件三；支撑组件三与压紧组件三相配合，压紧组件三及支撑组件三设置在与压紧组件三及支撑组件三相配合的壳体三内。壳体三18与支撑组件三和压紧组件三相配合，便于支撑组件三和压紧组件三的安装，通过壳体三18对支撑组件三和压紧组件三进行限位，从而有利于支撑组件三对压紧组件三在竖直方向上起到限位作用，且有利于压紧组件三在蜗杆5的顶部提供顶部阻尼和硬限位，在蜗杆5的侧面提供侧面阻尼和硬限位，来支撑和限制蜗杆5的摆动和吸收蜗杆的冲击，从而能消除蜗轮蜗杆机构的间隙、降低噪音、改善手感。
当蜗轮6和蜗杆5产生啮合传动时，蜗杆5将带动小端轴承7产生径向的摆动运动，当啮合力较小时，小端预紧力机构的弹簧力将蜗杆5压紧在蜗轮6上，从而消除蜗轮蜗杆之间的齿隙，小端侧边预紧机构的软胶压缩力消除小端轴承7与壳体三18的间隙；当啮合力较大时，小端预紧力机构调整螺栓三19的小圆柱19-1与叶片弹簧三20的顶部平面形接触，从而将小端轴承7的竖直位置限制住，小端侧边缓冲机构的叶片弹簧三20的侧边平面与壳体三18的小端轴承7的侧边硬限位接触，从而将小端轴承7的左右位置限制住。
实施例4
本实施例提供一种用于电动助力转向系统的蜗杆压紧支撑机构，包括蜗杆5、蜗轮6、大端轴承3、小端轴承7、壳体1、压紧螺母2、蜗杆齿毂4.其中，壳体1内设有蜗轮6及蜗杆5，蜗轮6的上端配合连接蜗杆5，蜗杆5的一端套设有大端轴承3及蜗杆齿毂4，位于大端轴承3的外侧套设有压紧螺母2；蜗杆5的另一端套设有小端轴承7，位于小端轴承7的外缘侧设有压紧组件，压紧组件贴紧所述小端轴承7的外圈，小端轴承7的上侧设有支撑组件，支撑组件位于压紧组件的上方，且支撑组件的下表面贴紧压紧组件。如图24-图29所示，压紧组件为压紧组件四，压紧组件四包括预紧橡胶四27，位于小端轴承7外缘的下部套设有预紧橡胶四27；预紧橡胶四27为半圆弧环状结构，位于预紧橡胶四27的顶部左右两侧端面分别连接外侧凸起结构27-1，外侧凸起结构27-1的内侧面为矩形平面。预紧橡胶四27在蜗杆5的侧面提供侧面阻尼和硬限位，来支撑和限制蜗杆5的摆动和吸收蜗杆5的冲击，从而能消除蜗轮蜗杆5机构的间隙、降低噪音、改善手感；减少壳体的机加工面数量、简化安装、降低成本；减小壳体外廓尺寸，占用更小的安装空间。通过压紧组件四提供上下摆动运动预紧力，从而消除蜗轮蜗杆减速机构的间隙；通过压紧组件四提供蜗杆5的竖直缓冲，避免由上下冲击产生的噪音；通过压紧组件四提供左右摆动缓冲面，避免由左右摆动冲击产生的噪音；通过压紧组件四提供合适的竖直压紧力，可避免减速机构的摩擦扭矩过大，提升转向手感。
作为一种较佳的实施方式，如图24、图27和图28所示，支撑组件四包括支撑衬套一26、螺旋弹簧一25、橡胶垫23、调整螺钉一23，小端轴承7的顶部设有调整螺钉一23，调整螺钉一23的下部套设有螺旋弹簧一25，螺旋弹簧一25的外侧套设有支撑衬套一26，位于支撑衬套一26顶部的调整螺钉一23上套设有橡胶垫24，支撑衬套一26的底部与小端轴承7的顶部端面连接。支撑衬套一26装在壳体四22中，支撑衬套一26的腰形侧面与壳体四22的腰形环配合，支撑衬套一26可上下运动，支撑衬套一26的底部圆弧面与小端轴承7的外圈接触配合，螺旋弹簧一25装在支撑衬套一26的孔中，螺旋弹簧一25的底部被支撑衬套一26的环面支撑，调整螺钉一23具有螺纹段，壳体四22具有螺纹孔，橡胶垫24装到调整螺钉一23上后一起旋入装入到壳体四22中，螺旋弹簧一25的顶部被调整螺钉一23的肩部支撑，橡胶垫24的底部与支撑衬套一26的顶面贴合，橡胶垫24的侧部与壳体四22的圆孔壁配合，调整螺钉一23的圆柱面用于螺旋弹簧一25的限位，装配完成后，将调整螺钉一23拧到到合适位置，螺旋弹簧一25被压缩提供的弹力用于蜗轮蜗杆配合预紧，调整螺钉一23的底部与支撑衬套一26内部的凸台有一定间隙，当小端轴承7向上移动时，初始阶段螺旋弹簧一25与橡胶垫24被压缩提供阻尼，最终支撑衬套一26的凸台与调整螺钉一23的底部接触即达到硬限位。通过调整螺钉一23与壳体四22的螺纹连接，对支撑衬套一26在竖直方向上进行限位，且通过螺旋弹簧一25调节支撑衬套一26在蜗杆5的顶部施加的预紧力，从而提供所需的竖直压紧力，控制蜗轮蜗杆减速机构的间隙为零间隙，避免由减速机构间隙产生的噪音。
作为一种较佳的实施方式，如图27所示，调整螺钉一23呈T型结构，调整螺钉一23的上部外缘设有外螺纹，调整螺钉一23的中部套设有橡胶垫24，调整螺钉一23的下部套设有螺旋弹簧一25。调整螺钉一23具有螺纹段，壳体四22具有螺纹孔，橡胶垫24装到调整螺钉一23上后一起旋入装入到壳体四22中，螺旋弹簧一25的顶部被调整螺钉一23的肩部支撑。通过上述设置便于调整螺钉一23、橡胶垫24和螺旋弹簧一25的连接。
作为一种较佳的实施方式，如图28所示，支撑衬套一26的圆柱形结构，位于支撑衬套一26的顶部设有与调整螺钉一23下部配合连接的凹槽，支撑衬套一26的底部为圆弧面。上述设置有利于对调整螺钉一23的底部与支撑衬套一26进行预定位。支撑衬套一26的底部为圆弧面，使得支撑衬套一26的底部能够更好地贴合压紧小端轴承7。
作为一种较佳的实施方式，支撑组件为支撑组件四；支撑组件四与压紧组件四相配合，压紧组件四及支撑组件四设置在与压紧组件四及支撑组件四相配合的壳体四22内。壳体四22与支撑组件四和压紧组件四相配合，便于支撑组件四和压紧组件四的安装，通过壳体四22对支撑组件四和压紧组件四进行限位，从而有利于支撑组件四对压紧组件四在竖直方向上起到限位作用，且有利于压紧组件四在蜗杆5的顶部提供顶部阻尼和硬限位，在蜗杆5的侧面提供侧面阻尼和硬限位，来支撑和限制蜗杆5的摆动和吸收蜗杆的冲击，从而能消除蜗轮蜗杆机构的间隙、降低噪音、改善手感。
预紧橡胶四27装在壳体四22与小端轴承7中间，预紧橡胶四27两侧的外侧凸起结构27-1的矩形平面与小端轴承7接触，预紧橡胶四27的外侧面与壳体四22的圆弧面接触，壳体四22中两侧还设有硬限位面，用于小端轴承7的硬限位。当小端轴承7产生水平的摆动运动时可吸收水平方向冲击力。
实施例5
本实施例提供一种用于电动助力转向系统的蜗杆压紧支撑机构，包括蜗杆5、蜗轮6、大端轴承3、小端轴承7、壳体1、压紧螺母2、蜗杆齿毂4.其中，壳体1内设有蜗轮6及蜗杆5，蜗轮6的上端配合连接蜗杆5，蜗杆5的一端套设有大端轴承3及蜗杆齿毂4，位于大端轴承3的外侧套设有压紧螺母2；蜗杆5的另一端套设有小端轴承7，位于小端轴承7的外缘侧设有压紧组件，压紧组件贴紧所述小端轴承7的外圈，小端轴承7的上侧设有支撑组件，支撑组件位于压紧组件的上方，且支撑组件的下表面贴紧压紧组件。如图30-图32所示，压紧组件为压紧组件五，压紧组件五包括预紧橡胶五，位于小端轴承7外缘的上部及下部分别套设有预紧橡胶五31；预紧橡胶五为橡胶圆环31。橡胶圆环31可为轴承整周径向方向提供阻尼即为顶部和侧边提供缓冲作用，橡胶圆环31具有弹性，能够在蜗杆5的整周径向方向提供阻尼和限位作用，来支撑和限制蜗杆5的摆动和吸收蜗杆5的冲击，从而能消除蜗轮蜗杆5机构的间隙、降低噪音、改善手感；减少壳体的机加工面数量、简化安装、降低成本；减小壳体外廓尺寸，占用更小的安装空间。
较佳地，支撑组件五包括支撑衬套二30、螺旋弹簧二29、调整螺钉二28，小端轴承7的顶部设有调整螺钉二28，调整螺钉二28的下部套设有螺旋弹簧二29，螺旋弹簧二29的外侧套设有支撑衬套二30，支撑衬套二30的底部与小端轴承7的顶部端面连接。其中，调整螺钉二28的结构与调整螺钉一23的结构一致；螺旋弹簧二29的结构与螺旋弹簧一25的结构一致；支撑衬套二30的结构与支撑衬套一26的结构一致。
较佳地，支撑组件为支撑组件五；支撑组件五与压紧组件五相配合，压紧组件五及支撑组件五设置在与压紧组件五及支撑组件五相配合的壳体五32内。壳体五32与支撑组件五和压紧组件五相配合，便于支撑组件五和压紧组件五的安装，通过壳体五32对支撑组件五和压紧组件五进行限位，从而有利于支撑组件五对压紧组件五在竖直方向上起到限位作用，且有利于压紧组件五在蜗杆5的顶部提供顶部阻尼和硬限位，在蜗杆5的侧面提供侧面阻尼和硬限位，来支撑和限制蜗杆5的摆动和吸收蜗杆的冲击，从而能消除蜗轮蜗杆机构的间隙、降低噪音、改善手感。
如图33所示，为EPSc转向系统方向盘与输入轴通过花键连接，当驾驶员施加扭矩以下称为手力转动方向盘时，会带动输入轴转动，输入轴通过花键与转向管柱连接、转向管柱与输出轴通过花键连接，将手力传到输出轴，同时安装在输出轴上的扭矩传感器读取扭矩信号，将此信号传递给控制单元。通过控制单元计算后助力电机输出相应的扭矩以下称为助力和转速，再通过减速机构减速增扭后，助力施加到输出轴上，此时输出轴输出的扭矩为手力加上助力的总扭矩。总扭矩通过输出轴与中间轴通过花键连接，中间轴与转向机通过花键连接后传递到转向机，转向机可将方向盘的转动转化为齿条的左右移动，该移动通过齿轮齿条机构输出到左右的横拉杆，从而将方向盘的旋转运动转换成车轮的左右摆动，从而实现汽车的助力转向功能。
如图34所示，为EPSdp转向系统，方向盘与输入轴通过花键连接，当驾驶员施加手力转动方向盘时，会带动输入轴转动，输入轴通过花键与转向管柱连接、转向管柱与中间轴通过花键连接，中间轴与转向机通过花键连接后将手力传递到转向机的第一小齿轮，从而转向机可将方向盘的转动转化为齿条的左右移动，该移动通过齿轮齿条机构输出到左右的横拉杆，从而将方向盘的旋转运动转换成车轮的左右摆动。与EPSc不同的是，安装在转向机上的扭矩传感器读取手力扭矩信号，将此信号传递给控制单元。通过控制单元计算后助力电机输出相应的助力，再通过减速机构减速增扭后，将助力施加到输出轴上，输出轴输出的扭矩传到转向机的第二小齿轮，再与转向机的齿条产生齿轮齿条啮合运动，可将方向盘的转动转化为齿条的左右移动，该移动通过齿轮齿条机构输出到左右的横拉杆，此时电机助力和方向盘手力同时作用在齿条上，从而实现汽车的助力转向功能。
如图35所示，为EPSp转向系统，方向盘与输入轴通过花键连接，当驾驶员施加手力转动方向盘时，会带动输入轴转动，输入轴通过花键与转向管柱连接、转向管柱与中间轴通过花键连接，中间轴与转向机通过花键连接后将手力传递到转向机的第一小齿轮，从而转向机可将方向盘的转动转化为齿 条的左右移动，该移动通过齿轮齿条机构输出到左右的横拉杆，从而将方向盘的旋转运动转换成车轮的左右摆动。与EPSc不同的是，安装在转向机上的扭矩传感器读取手力扭矩信号，将此信号传递给控制单元。通过控制单元计算后助力电机输出相应的助力，再通过减速机构减速增扭后，将助力施加到输出轴上，输出轴输出的扭矩传到转向机的第一小齿轮，再与转向机的齿条产生齿轮齿条啮合运动，可将方向盘的转动转化为齿条的左右移动，该移动通过齿轮齿条机构输出到左右的横拉杆，此时电机助力和方向盘手力同时作用在齿条上，从而实现汽车的助力转向功能。
本发明依靠叶片弹簧或螺旋弹簧提供预紧力、顶部依靠压紧销与锁紧螺栓组合，或橡胶垫、支撑衬套与调整螺钉组合的方式提供顶部阻尼和硬限位、侧面依靠橡胶和壳体机加工面提供侧面阻尼和硬限位，来支撑和限制蜗杆的摆动和吸收蜗杆的冲击，从而能消除蜗轮蜗杆机构的间隙、降低噪音、改善手感；减少壳体的机加工面数量、简化安装、降低成本；减小壳体外廓尺寸，占用更小的安装空间；提供上下摆动运动预紧力，从而消除蜗轮蜗杆减速机构的间隙；提供蜗杆的竖直阻尼，避免由上下冲击产生的噪音；提供蜗杆的左右阻尼，避免由左右摆动冲击产生的噪音；提供竖直压紧弹簧特征，可方便调节出所需的竖直压紧刚度，从而提供所需的竖直压紧力，控制蜗轮蜗杆减速机构的间隙为零间隙，避免由减速机构间隙产生的噪音；提供合适的竖直压紧力，可避免减速机构的摩擦扭矩过大，提升转向手感。
虽然以上描述了本发明的具体实施方式，但是本领域的技术人员应当理解，这些仅是举例说明，在不背离本发明的原理和实质的前提下，可以对这些实施方式做出多种变更或修改。因此，本发明的保护范围由所附权利要求书限定。

Claims (16)

  1. 一种用于电动助力转向系统的蜗杆压紧支撑机构，包括蜗杆、蜗轮、大端轴承、小端轴承、壳体，其特征在于：壳体(1)内设有蜗轮(6)及蜗杆(5)，蜗轮(6)的上端配合连接蜗杆(5)，蜗杆(5)的一端套设有大端轴承(3)，蜗杆(5)的另一端套设有小端轴承(7)，位于小端轴承(7)的外缘侧设有压紧组件，所述压紧组件贴紧所述小端轴承(7)的外圈，小端轴承(7)的上侧设有支撑组件，所述支撑组件位于所述压紧组件的上方，且所述支撑组件的下表面贴紧所述压紧组件。
  2. 根据权利要求1所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：所述压紧组件为压紧组件一，所述的压紧组件一包括叶片弹簧一、预紧橡胶一，位于小端轴承(7)外缘的上部套设有叶片弹簧一(11)，小端轴承(7)外缘的下部套设有预紧橡胶一(12)。
  3. 根据权利要求2所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：叶片弹簧一(11)的顶部为圆弧形的中间端面(11-1)，中间端面(11-1)的左右两端的顶部分别连接弹簧卡扣(11-2)，中间端面(11-1)的左右两端的底部分别连接弹簧臂(11-3)的一端，弹簧臂(11-3)的另一端连接压紧凸台一(11-4)；位于中间端面(11-1)的中部设有弹簧腰型孔一(11-5)；所述的弹簧臂(11-3)由两个向内倾斜的弯折面板组成；
    优选地，所述的叶片弹簧一(11)呈蝴蝶状结构；
    优选地，弹簧臂(11-3)的截面呈C字型结构；
    和/或，所述的预紧橡胶一(12)呈U型结构，预紧橡胶一(12)上部的左右两侧分别连接凸筋(12-1)，位于凸筋(12-1)下侧的预紧橡胶一(12)上连接半圆柱凸起(12-2)。
  4. 根据权利要求2所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：所述支撑组件为支撑组件一，所述支撑组件一与所述压紧组件一相配合，所述的压紧组件一及支撑组件一设置在与压紧组件一及支撑组件一相配合的壳体一(8)内；
    优选地，所述的支撑组件一包括调整螺栓一、压紧销一，小端轴承(7)的顶部设有压紧销一(10)的底部，压紧销一(10)的顶部设有调整螺栓一(9)。
  5. 根据权利要求4所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：所述的调整螺栓一(9)的外缘周设有外螺纹，调整螺栓一(9)的底部为平面，调整螺栓一(9)的顶部连接内六角凹槽(9-1)；
    和/或，所述的压紧销一(10)的上部为圆柱形结构，压紧销一(10)的下部为腰型柱结构；位于压紧销一(10)的顶部设有定位方孔(10-2)，压紧销一(10)的底部为圆弧形结构；
    优选地，压紧销一(10)的下部嵌设有软胶(10-1)；并且压紧销一(10)的上部及压紧销一(10)的下部为一体结构；
    优选地，所述用于电动助力转向系统的蜗杆压紧支撑机构还包括压紧螺母和蜗杆齿毂，所述蜗杆(5)的一端套设有蜗杆齿毂(4)。
  6. 根据权利要求1所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：所述压紧组件为压紧组件二，所述的压紧组件二包括叶片弹簧二、预紧橡胶二，位于小端轴承(7)外缘的套设有预紧橡胶二(17)，预紧橡胶二(17)的后侧卡扣连接叶片弹簧二(16)。
  7. 根据权利要求6所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：所述的叶片弹簧二(16)为U型结构，叶片弹簧二(16)的顶部为圆弧结构，位于叶片弹簧二(16)的顶部设有弹簧腰型孔二(16-1)，叶片弹簧二(16)的左右两侧分别设有方孔(16-2)，位于方孔(16-2)上侧的叶片弹簧二(16)上设有向内弯折的梯形斜边(16-3)，梯形斜边(16-3)的底部与叶片弹簧二(16)连接，梯形斜边(16-3)的顶部连接压紧凸台二(16-4)；
    和/或，所述的预紧橡胶二(17)为圆环形结构，位于预紧橡胶二(17)顶部内侧连接卡槽(17-1)，预紧橡胶二(17)的中部左右两侧的内侧面分别连接圆弧柱(17-2)，所述的圆弧柱(17-2)的内侧面为平面，位于圆弧柱(17-2)的内侧面连接凸台(17-3)，位于圆弧柱(17-2)与预紧橡胶二(17)连接处的预紧橡胶二(17)前端面上分别设有若干凸起(17-4)。
  8. 根据权利要求6所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：所述支撑组件为支撑组件二；所述支撑组件二与所述压紧组件二相配合，所述的压紧组件二及支撑组件二设置在与压紧组件二及支撑组件二相配合的壳体二(13)内；
    优选地，所述的支撑组件二包括调整螺栓二、压紧销二，小端轴承(7)的顶部设有压紧销二(15)的底部，压紧销二(15)的顶部设有调整螺栓二(14)。
  9. 根据权利要求1所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：所述压紧组件为压紧组件三，所述的压紧组件三包括叶片弹簧三、预紧橡胶三，位于小端轴承(7)的外缘套设有叶片弹簧三(20)，叶片弹簧三(20)的后侧卡接预紧橡胶三(21)。
  10. 根据权利要求9所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：叶片弹簧三(20)顶部为平面，叶片弹簧三(20)的底部两侧分别向外翘起，并且所述的向外翘起的端部连接压紧凸台三(20-1)；
    优选地，所述的叶片弹簧三(20)呈“Ω”状结构；
    和/或，所述的预紧橡胶三(21)为半圆弧环状结构，位于预紧橡胶三(21)左右两侧的后端分别连接半圆柱(21-3)，位于预紧橡胶三(21)顶部的后端连接顶部橡胶(21-1)，顶部橡胶(21-1)的中心设有中心孔(21-2)。
  11. 根据权利要求9所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：所述支撑组件为支撑组件三；所述支撑组件三与所述压紧组件三相配合，所述的压紧组件三及支撑组件三设 置在与压紧组件三及支撑组件三相配合的壳体三(18)内；
    优选地，所述的支撑组件三包括调整螺栓三，小端轴承(7)的顶部设有调整螺栓三(19)，所述的调整螺栓三(19)的结构为调整螺栓一(9)的底部平面上连接小圆柱(19-1)，并且调整螺栓三(19)的小圆柱(19-1)嵌设在预紧橡胶三(21)顶部的顶部橡胶(21-1)的中心孔(21-2)内。
  12. 根据权利要求1所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：所述压紧组件为压紧组件四，所述的压紧组件四包括预紧橡胶四，位于小端轴承(7)外缘的下部套设有预紧橡胶四(27)；所述的预紧橡胶四(27)为半圆弧环状结构，位于预紧橡胶四(27)的顶部左右两侧端面分别连接外侧凸起结构(27-1)，所述的外侧凸起结构(27-1)的内侧面为矩形平面。
  13. 根据权利要求12所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：所述支撑组件为支撑组件四；所述支撑组件四与所述压紧组件四相配合，所述的压紧组件四及支撑组件四设置在与压紧组件四及支撑组件四相配合的壳体四(22)内；
    优选地，所述的支撑组件四包括支撑衬套一、螺旋弹簧一、橡胶垫、调整螺钉一，小端轴承(7)的顶部设有调整螺钉一(23)，调整螺钉一(23)的下部套设有螺旋弹簧一(25)，螺旋弹簧一(25)的外侧套设有支撑衬套一(26)，位于支撑衬套一(26)顶部的调整螺钉一(23)上套设有橡胶垫(24)，支撑衬套一(26)的底部与小端轴承(7)的顶部端面连接。
  14. 根据权利要求13所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：所述的调整螺钉一(23)呈T型结构，调整螺钉一(23)的上部外缘设有外螺纹，调整螺钉一(23)的中部套设有橡胶垫(24)，调整螺钉一(23)的下部套设有螺旋弹簧一(25)；
    和/或，所述的支撑衬套一(26)的圆柱形结构，位于支撑衬套一(26)的顶部设有与调整螺钉一(23)下部配合连接的凹槽，支撑衬套一(26)的底部为圆弧面。
  15. 根据权利要求1所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：所述压紧组件为压紧组件五，所述的压紧组件五包括预紧橡胶五，位于小端轴承(7)外缘的上部及下部分别套设有预紧橡胶五(31)；所述的预紧橡胶五(31)为橡胶圆环。
  16. 根据权利要求15所述的一种用于电动助力转向系统的蜗杆压紧支撑机构，其特征在于：所述支撑组件为所述支撑组件五；所述支撑组件五与所述压紧组件五相配合，所述的压紧组件五及支撑组件五设置在与压紧组件五及支撑组件五相配合的壳体五(32)内；
    优选地，所述的支撑组件五包括支撑衬套二、螺旋弹簧二、调整螺钉二，小端轴承(7)的顶部设有调整螺钉二(28)，调整螺钉二(28)的下部套设有螺旋弹簧二(29)，螺旋弹簧二(29)的外侧套设有支撑衬套二(30)，支撑衬套二(30)的底部与小端轴承(7)的顶部端面连接。
PCT/CN2023/102276 2022-08-26 2023-06-26 用于电动助力转向系统的蜗杆压紧支撑机构 WO2024041155A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202211029042.9A CN117657281A (zh) 2022-08-26 2022-08-26 一种用于电动助力转向系统的蜗杆压紧支撑机构
CN202211029042.9 2022-08-26

Publications (1)

Publication Number Publication Date
WO2024041155A1 true WO2024041155A1 (zh) 2024-02-29

Family

ID=90012385

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2023/102276 WO2024041155A1 (zh) 2022-08-26 2023-06-26 用于电动助力转向系统的蜗杆压紧支撑机构

Country Status (2)

Country Link
CN (1) CN117657281A (zh)
WO (1) WO2024041155A1 (zh)

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011157034A (ja) * 2010-02-03 2011-08-18 Jtekt Corp 電動パワーステアリング装置
CN102398628A (zh) * 2010-09-09 2012-04-04 株式会社捷太格特 电动动力转向装置
JP2014101071A (ja) * 2012-11-21 2014-06-05 Jtekt Corp 電動パワーステアリング装置
CN207111910U (zh) * 2017-08-31 2018-03-16 长城汽车股份有限公司 蜗轮蜗杆传动机构的间隙补偿结构、转向系统和车辆
CN207683593U (zh) * 2018-01-05 2018-08-03 浙江吉利汽车研究院有限公司 一种电动助力转向系统的蜗轮蜗杆机构
CN209521756U (zh) * 2018-12-20 2019-10-22 博世华域转向系统有限公司 一种改进的蜗杆预紧结构
CN210000393U (zh) * 2019-06-12 2020-01-31 长城汽车股份有限公司 用于转向器的间隙补偿机构
CN210919979U (zh) * 2019-07-25 2020-07-03 长城汽车股份有限公司 间隙补偿传动组件及具有其的电动转向助力系统
CN211918817U (zh) * 2019-12-31 2020-11-13 博世华域转向系统有限公司 一种汽车转向管柱蜗杆预紧结构
CN212890573U (zh) * 2020-07-29 2021-04-06 坤泰车辆系统（常州）有限公司 一种新型电动助力转向系统的蜗轮蜗杆传动间隙补偿机构
CN216045224U (zh) * 2021-09-18 2022-03-15 奇瑞汽车股份有限公司 蜗轮蜗杆间隙调整机构
CN216789124U (zh) * 2021-12-29 2022-06-21 国太阳科技有限公司 一种用于蜗轮蜗杆的弹性补偿机构

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011157034A (ja) * 2010-02-03 2011-08-18 Jtekt Corp 電動パワーステアリング装置
CN102398628A (zh) * 2010-09-09 2012-04-04 株式会社捷太格特 电动动力转向装置
JP2014101071A (ja) * 2012-11-21 2014-06-05 Jtekt Corp 電動パワーステアリング装置
CN207111910U (zh) * 2017-08-31 2018-03-16 长城汽车股份有限公司 蜗轮蜗杆传动机构的间隙补偿结构、转向系统和车辆
CN207683593U (zh) * 2018-01-05 2018-08-03 浙江吉利汽车研究院有限公司 一种电动助力转向系统的蜗轮蜗杆机构
CN209521756U (zh) * 2018-12-20 2019-10-22 博世华域转向系统有限公司 一种改进的蜗杆预紧结构
CN210000393U (zh) * 2019-06-12 2020-01-31 长城汽车股份有限公司 用于转向器的间隙补偿机构
CN210919979U (zh) * 2019-07-25 2020-07-03 长城汽车股份有限公司 间隙补偿传动组件及具有其的电动转向助力系统
CN211918817U (zh) * 2019-12-31 2020-11-13 博世华域转向系统有限公司 一种汽车转向管柱蜗杆预紧结构
CN212890573U (zh) * 2020-07-29 2021-04-06 坤泰车辆系统（常州）有限公司 一种新型电动助力转向系统的蜗轮蜗杆传动间隙补偿机构
CN216045224U (zh) * 2021-09-18 2022-03-15 奇瑞汽车股份有限公司 蜗轮蜗杆间隙调整机构
CN216789124U (zh) * 2021-12-29 2022-06-21 国太阳科技有限公司 一种用于蜗轮蜗杆的弹性补偿机构

Also Published As

Publication number Publication date
CN117657281A (zh) 2024-03-08

Similar Documents

Publication Publication Date Title
CN203005508U (zh) 车辆的转向装置
CN101607551A (zh) 车辆中的卡钳连接型电子停车制动器
CN203727461U (zh) 转向装置
CN102616269B (zh) 齿条转向装置和装有齿条转向装置的伺服转向系统
WO2024041155A1 (zh) 用于电动助力转向系统的蜗杆压紧支撑机构
WO2023077702A1 (zh) 一种可摇摆的轴传动三轮车
US10981592B2 (en) Ball nut assembly for a power steering assembly of a vehicle
WO2012093713A1 (ja) ステアリング装置
US6749040B1 (en) Electric power assisted rack and pinion system
CN109973500A (zh) 一种防松螺母及其使用方法
US20210381544A1 (en) Shaft device capable of sensing torque
CN201515289U (zh) 一种电机传动系统
CN213705696U (zh) 一种集成式电动助力自行车双驱动组件
KR20110125513A (ko) 감속기 및 이를 구비한 전동식 동력 보조 조향장치
CN213705695U (zh) 一种集成式电动助力自行车双驱动组件
CN210919979U (zh) 间隙补偿传动组件及具有其的电动转向助力系统
CN213705697U (zh) 一种集成式电动助力自行车双驱动组件
WO2012093712A1 (ja) ステアリング装置
CN211918816U (zh) 一种用于管柱式电动助力转向系统的蜗杆压紧结构
CN111319711A (zh) 中置驱动机构和助力自行车
CN201231673Y (zh) 用于电动车辆的驱动机构
CN1325319C (zh) 车辆转向机构用的贯通式锁位器
KR20130008693A (ko) 전동식 동력 보조 조향장치의 벨트 장력 조절기 및 이를 구비한 전동식 동력 보조 조향장치
JPH11182637A (ja) ウォームギヤ伝動装置及び電動パワーステアリング装置
CN112224329A (zh) 一种集成式电动助力自行车双驱动组件及其安装方法

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 23856247

Country of ref document: EP

Kind code of ref document: A1