CN220905088U - Steering gear and vehicle - Google Patents

Abstract

The present application relates to a steering gear and a vehicle. The steering gear comprises a direction control device, a transmission device and a steering device, wherein the transmission device comprises a worm wheel and a worm, the direction control device is in transmission connection with the worm, the steering device is in transmission connection with the worm wheel, and the direction control device drives the steering device to rotate through the cooperation of the worm and the worm wheel so as to realize a steering function; the transmission device further comprises a support and a bearing, the support is sleeved at the end part of the worm through the bearing, the support is further provided with a limiting part, and the limiting part is propped against the outer ring of the bearing along the direction of the rotating shaft of the worm so as to limit the radial displacement of the worm. According to the steering gear disclosed by the application, the limiting part capable of propping against the bearing is arranged in the support, so that the relative position relationship between the worm and the worm wheel can be ensured by the limiting part when the worm wheel and the worm are in matched transmission, the matching clearance between the worm and the worm wheel is ensured, the transmission precision of the transmission device is improved, and the steering efficiency of the steering gear is further improved.

Description

Steering gear and vehicle

Technical Field

The present application relates to the field of steering gears, and in particular to a steering gear, and a vehicle comprising the steering gear.

Background

In the transmission field, in the transmission process of the worm wheel and the worm, the interaction between the worm wheel and the worm easily causes the fit clearance between the worm wheel and the worm to be enlarged, thereby influencing the transmission precision of the worm wheel and the worm.

Disclosure of utility model

In view of the above-described deficiencies of the prior art, an object of the present application is to provide a steering gear that improves steering efficiency, and a vehicle including the steering gear. The method specifically comprises the following technical scheme:

In a first aspect, an embodiment of the present application provides a steering gear, including a steering device, a transmission device, and a steering device, where the transmission device includes a worm wheel and a worm, the steering device is in transmission connection with the worm, and the steering device is in transmission connection with the worm wheel, and the steering device is driven to rotate by the cooperation of the worm and the worm wheel to implement a steering function;

The transmission device further comprises a support and a bearing, the support is sleeved at the end part of the worm through the bearing, the support is further provided with a limiting part, and the limiting part is propped against the outer ring of the bearing along the direction of the rotating shaft of the worm so as to limit the radial displacement of the worm.

The steering device is connected with the worm in a transmission way, and the steering device is connected with the worm wheel in a transmission way, so that the steering device can control the worm wheel to rotate by controlling the worm to rotate and drive the steering device to rotate, thereby realizing the steering function of the steering device.

According to the steering gear, the end part of the worm is sleeved on the bearing, and the limiting part is arranged on the support, so that when the direction control device rotates and the worm generates eccentric moment, the limiting part can convert the force of the worm wheel on the worm into reverse eccentric moment through the supporting action of the bearing, and offset the eccentric moment on the worm, so that the fit clearance between the worm and the worm wheel is ensured, the transmission precision of the transmission device is improved, and the steering efficiency of the steering gear is further improved.

In one embodiment, the limiting portion includes a first limiting portion and a second limiting portion, in the direction of the rotation axis of the worm, the first limiting portion and the second limiting portion are located on opposite sides of the outer ring of the bearing respectively, the first limiting portion is close to the worm wheel relative to the second limiting portion, and the first limiting portion and the second limiting portion are propped against two opposite end faces of the bearing respectively to limit radial displacement of the worm.

In this embodiment, the first limiting portion and the second limiting portion are disposed on two opposite sides of the bearing, and the first limiting portion and the second limiting portion are made to abut against corresponding end faces of the bearing respectively, so that limitation of axial displacement of the bearing is achieved. Meanwhile, based on the limitation of the limiting part on the radial displacement of the worm, the first limiting part and the second limiting part are matched to further limit the radial displacement of the worm.

In one embodiment, the first limit portion is closer to the rotation axis of the worm wheel with respect to the rotation axis of the worm and/or the second limit portion is farther from the rotation axis of the worm wheel with respect to the rotation axis of the worm in the arrangement direction of the worm wheel and the worm.

In this embodiment, the first limiting portion is disposed on a side, close to the rotation axis of the worm, of the rotation axis of the worm, so that when the bearing abuts against the first limiting portion, an axial force acting on the worm by the worm wheel can cooperate with the first limiting portion to form a reverse eccentric moment, so as to offset the eccentric moment formed by the worm acting on the worm by the worm wheel, limit radial displacement of the worm, and ensure a fit gap between the worm and the worm wheel.

The second limiting part is arranged on one side of the rotation axis of the worm, far away from the rotation axis of the worm wheel, so that when the bearing is propped against the second limiting part, the axial force of the worm wheel acting on the worm can be matched with the second limiting part to form a reverse eccentric moment, so that the eccentric moment formed by the worm wheel acting on the worm is counteracted, the radial displacement of the worm is limited, and the fit clearance between the worm and the worm wheel is ensured.

In one embodiment, the first limit portion is closer to the steering device than the second limit portion in an arrangement direction of the worm wheel and the worm.

In this embodiment, through setting up first spacing portion and second spacing portion in the range direction of worm wheel and worm for the axial force that the worm received can form reverse eccentric moment under the effect of first spacing portion and/or second spacing portion, and this reverse eccentric moment can offset the eccentric moment that the worm wheel acted on the worm and forms, thereby restriction worm produces radial displacement, guarantees the fit clearance between worm and the worm wheel.

In one embodiment, a first spacing portion is provided between the first spacing portion and the rotational axis of the worm, a second spacing portion is provided between the second spacing portion and the rotational axis of the worm, and the first spacing portion is less than or equal to the second spacing portion.

In this embodiment, since the second limiting portion is farther from the rotation axis of the worm wheel than the first limiting portion, by setting the second spacing that is relatively greater than or equal to the first spacing, the difference between the eccentric moment formed by the second limiting portion and the axial force fit and the eccentric moment formed by the first limiting portion and the axial force fit is reduced, so that the limiting effect of the second limiting portion on the radial displacement of the worm is ensured, and the fit gap between the worm and the worm wheel is ensured.

In one embodiment, the limiting portion is of a circular ring structure, and the limiting portion comprises an axial protruding piece, and the axial protruding piece extends towards the end face of the bearing along the rotation axis of the bearing and abuts against the end face of the outer ring of the bearing to limit radial displacement of the worm.

In the embodiment, the limiting part is in a circular ring structure, and the axial protruding part extending towards the end face of the bearing along the rotation axis direction of the bearing is arranged, so that when the direction control device rotates, the axial protruding part can limit radial displacement of the worm through abutting action with the bearing, fit clearance between the worm and the worm wheel is ensured, transmission precision of the transmission device is improved, and steering efficiency of the steering gear is further improved.

In one embodiment, two axial protruding parts are arranged, along the arrangement direction of the worm wheel and the worm, the two axial protruding parts are positioned on the same side of the rotation axis of the bearing, and the distance between the two bearing protruding parts and the rotation axis of the bearing is equal.

In this embodiment, the two axial protruding members are disposed on the same side of the rotation axis of the bearing, and the distances between the two axial protruding members and the rotation axis of the bearing are equal, so that when the directional control device rotates, the forces applied to the bearing by the two axial protruding members can ensure that the stress of the bearing is relatively uniform. Meanwhile, the direction of the deflection moment formed by the matching of the axial protruding piece and the bearing can be guaranteed, and the direction of the deflection moment generated by the worm wheel acting on the worm is opposite to that of the deflection moment generated by the worm wheel.

In one embodiment, the axial projections are arcuate and are circumferentially arranged about the axis of rotation of the bearing.

In this embodiment, by setting the axial protrusion to be arc-shaped, the axial protrusion is located on one side of the rotation axis of the bearing, and the axial protrusion is circumferentially arranged around the rotation axis of the bearing, so that the stress on the side of the bearing end face close to the axial protrusion is relatively uniform. Meanwhile, the direction of the moment formed by the matching of the axial protruding piece and the bearing can be guaranteed, and the direction of the moment is opposite to the direction of the deflection moment generated by the worm wheel acting on the worm.

In one embodiment, the limiting part further comprises a radial protruding part protruding in the radial direction of the bearing, the support is further provided with a mounting groove, the mounting groove is arranged in the radial direction of the bearing, and the radial protruding part is accommodated in the mounting groove so as to fix the position of the support to the limiting part.

In the embodiment, the radial protruding piece protruding along the radial direction of the bearing is arranged, and the mounting groove is formed in the support, so that the radial protruding piece can be contained in the mounting groove, and the position of the support and the position limiting portion are fixed.

In one embodiment, the transmission further comprises a buffer member filled between the bearing and the support, the buffer member being for absorbing vibrations between the bearing and the support.

In this embodiment, the buffer member filled between the bearing and the support is provided to absorb the vibration generated between the bearing and the support when the direction control device rotates, thereby reducing the noise generated by the vibration between the bearing and the support during the operation of the steering gear of the present application.

In one embodiment, the steering control device comprises a steering wheel, a sensor and a motor, wherein a rotating shaft of the steering wheel is fixed relative to the transmission device, the sensor is in communication connection with the motor, the sensor is used for collecting rotation information of the steering wheel and converting the rotation information into a steering signal to be transmitted to the motor, the motor is in transmission connection with a worm, and the motor drives the worm to rotate based on the steering signal.

In this embodiment, the steering wheel is rotated by a user operation by fixing the rotation shaft of the steering wheel with respect to the transmission device. And the sensor is in communication connection with the motor, so that the sensor can convert collected rotation information of the steering wheel into a steering signal, and then the steering signal is transmitted to the motor, and the worm is driven to rotate by the motor. Therefore, the force required by the user to rotate the steering wheel is reduced, and the user experience is improved.

In one embodiment, the direction control device further comprises a controller, the controller is communicatively connected between the sensor and the motor, and the controller is used for processing the steering signal output by the sensor and transmitting the processed steering signal to the motor.

In this embodiment, the controller is communicatively connected to the sensor and the motor, so that the steering signal output by the sensor can be processed by the controller and then sent to the motor. Therefore, the force required by the user to rotate the steering wheel is reduced, and the user experience is improved.

In a second aspect, embodiments of the present application provide a vehicle including wheels and a steering gear for controlling wheel deflection to change a direction of travel of the vehicle.

It will be appreciated that the vehicle according to the second aspect of the present application is provided with the steering gear according to the first aspect of the present application, and the steering gear according to the first aspect of the present application has the advantage of improving steering efficiency. The vehicle of the application thus also has a higher steering efficiency.

Drawings

FIG. 1 is a schematic view of a vehicle according to an embodiment of the present application;

FIG. 2 is a schematic diagram of a steering gear according to an embodiment of the present application;

FIG. 3 is a schematic view of a steering gear according to an embodiment of the present application;

FIG. 4 is a schematic diagram of a transmission device according to an embodiment of the present application;

FIG. 5 is a top view of a transmission provided in one embodiment of the present application;

FIG. 6 is a force analysis diagram of a transmission according to an embodiment of the present application;

FIG. 7 is a schematic diagram illustrating another force analysis of a transmission according to an embodiment of the present application;

FIG. 8 is a schematic diagram of a prior art diverter;

FIG. 9 is a schematic view of a partial cross-sectional structure of a steering gear in the prior art;

FIG. 10 is a force analysis schematic of a transmission in a prior art steering gear;

FIG. 11 is a schematic view of a partial cross-sectional structure of a transmission device according to an embodiment of the present application;

FIG. 12 is a schematic diagram illustrating yet another force analysis of a transmission provided in an embodiment of the present application;

FIG. 13 is a schematic diagram illustrating still another stress analysis of a transmission according to an embodiment of the present application;

FIG. 14 is a partial front view of a transmission provided in one embodiment of the present application;

FIG. 15 is a partially exploded schematic illustration of a transmission provided in one embodiment of the application;

FIG. 16 is another partially exploded view of a transmission provided in one embodiment of the present application;

FIG. 17 is a schematic view of another partial cross-sectional configuration of a transmission provided in an embodiment of the application;

FIG. 18 is an enlarged partial schematic view of a transmission provided in an embodiment of the application;

Fig. 19 is a schematic view showing a partial cross-sectional structure of a transmission device according to an embodiment of the present application.

Detailed Description

In order that the application may be readily understood, a more complete description of the application will be rendered by reference to the appended drawings. The drawings illustrate preferred embodiments of the application. This application may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete.

The following description of the embodiments refers to the accompanying drawings, which illustrate specific embodiments in which the application may be practiced. The numbering of the components itself, e.g. "first", "second", etc., is used herein merely to distinguish between the described objects and does not have any sequential or technical meaning. The term "coupled" as used herein includes both direct and indirect coupling (coupling), unless otherwise indicated. Directional terms, such as "upper", "lower", "front", "rear", "left", "right", "inner", "outer", "side", etc., in the present application are merely referring to the directions of the attached drawings, and thus, directional terms are used for better, more clear explanation and understanding of the present application, rather than indicating or implying that the apparatus or element being referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present application.

In the description of the present application, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; may be a mechanical connection; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present application will be understood in specific cases by those of ordinary skill in the art. It should be noted that the terms "first," "second," and the like in the description and claims of the present application and in the drawings are used for distinguishing between different objects and not for describing a particular sequential order. Furthermore, the terms "comprises," "comprising," "includes," "including," or "having," when used in this specification, are intended to specify the presence of stated features, operations, elements, etc., but do not limit the presence of one or more other features, operations, elements, etc., but are not limited to other features, operations, elements, etc. Furthermore, the terms "comprises" or "comprising" mean that there is a corresponding feature, number, step, operation, element, component, or combination thereof disclosed in the specification, and that there is no intention to exclude the presence or addition of one or more other features, numbers, steps, operations, elements, components, or combinations thereof.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used herein in the description of the application is for the purpose of describing particular embodiments only and is not intended to be limiting of the application.

Referring to FIG. 1, a schematic diagram of a vehicle 200 according to an embodiment of the present application is shown.

As shown in fig. 1, the vehicle 200 provided by the present application includes wheels 201 and a steering gear 100. Wherein the steering gear 100 is used to control the deflection of the wheels 201 to change the traveling direction of the vehicle 200.

Referring to fig. 2, a schematic diagram of a steering gear 100 according to an embodiment of the present application is shown.

As shown in fig. 2, the steering gear 100 provided by the present application includes a direction control device 10, a transmission device 20, and a steering device 30. The transmission 20 comprises a worm wheel 21 and a worm 22 in driving connection. The worm wheel 21 is in transmission connection with the steering device 30, and the worm 22 is in transmission connection with the directional control device 10. The direction control device 10 can output a turning moment having a turning signal and transmit the turning moment to the worm wheel 21 through the worm 22.

Since the transmission device 20 adopts a transmission mode that the worm wheel 21 and the worm 22 are matched with each other, and the transmission ratio of the worm wheel 21 and the worm 22 is relatively large. It will be appreciated that when the directional control device 10 controls the rotation of the worm 22, the worm wheel 21 is able to output a greater torque outwardly than the torque output by the directional control device 10. The steering device 30 receives the torque increased through the transmission 20 through the worm wheel 21 and outputs it to the outside to realize the steering function of the steering gear 100 of the present application.

It will be appreciated that in another embodiment, the directional control device 10 may also be in driving connection with the worm wheel 21, and the steering device 30 correspondingly in driving connection with the worm 22. When the directional control device 10 rotates, the torque output by the corresponding worm 22 is relatively small, and the rotation speed is relatively fast, so as to be suitable for different working conditions.

Referring to fig. 3, a schematic partial structure of a steering gear 100 according to an embodiment of the present application is shown, and a schematic structure of a transmission 20 according to an embodiment of the present application is shown in fig. 4.

As shown in fig. 3 and 4, the transmission 20 further includes a support 23 and a bearing 24. The bearing 24 is embedded in the support 23, and the support 23 is sleeved at the end of the worm 22 through the bearing 24, so that the bearing 24 is relatively fixed in the support 23.

Specifically, as shown in fig. 4, the support 23 has an inner hole 231, an outer ring 242 of the bearing 24 is embedded in the inner hole 231 of the support 23, and an inner ring 243 of the bearing 24 is sleeved at one end of the worm 22, so that the support 23 supports the worm 22 and simultaneously enables the worm 22 to rotate relative to the support 23. Meanwhile, as shown in fig. 4, the third rotation axis L3 of the bearing 24 coincides with the first rotation axis L1 of the worm 22.

The other end of the worm 22 is in driving connection with the worm wheel 21 and fixes the second rotation axis L2 of the worm wheel 21 with respect to the support 23. As shown in fig. 5, an included angle is formed between the first rotation axis L1 and the second rotation axis L2. It will be appreciated that in another embodiment, the first and second axes of rotation L1, L2 are perpendicular to each other.

It will be appreciated that the drive connection of the worm 22 and worm gear 21 causes the worm 22 to rotate under the influence of the directional control device 10 and drive the worm gear 21 to rotate, thereby effecting the drive function of the drive 20 of the steering gear 100 of the present application.

The support 23 is further provided with a limiting portion 25, and the limiting portion 25 abuts against an end face 241 of the bearing 24 along the direction of the first rotation axis L1 and abuts against an outer ring 242 of the bearing 24 to limit radial displacement of the worm 22.

Specifically, please refer to fig. 6, which illustrates a force analysis diagram of the transmission 20 according to an embodiment of the present application, and fig. 4. Fig. 6 is a schematic diagram of the stress analysis of fig. 4. For ease of description, the description of the support 23 is omitted from fig. 6 and the subsequent force analysis schematic diagram, and the bearing 24, worm 22 and worm wheel 21 are simplified. Meanwhile, the limit portion 25 is also simplified so as to describe the positional relationship between the limit portion 25 and the first rotation axis L1.

As shown in fig. 4 and 6, the stopper 25 is disposed on a side of the bearing 24 relatively far from the worm wheel 21, and abuts against the end face 241 of the corresponding bearing 24. As shown in fig. 4, when the direction control device 10 rotates, the worm 22 and the worm wheel 21 also rotate synchronously. Based on the worm 22 being fixed at only one end. It will be appreciated that during the co-operation of the worm 22 and worm wheel 21, the worm wheel 21 will exert a force on the worm 22 and cause the worm 22 to generate an eccentric moment. Wherein the eccentric moment causes axial displacement of the worm 22. At the same time, the eccentric moment also cooperates with the bearing 24 to cause radial displacement of the worm 22.

There is a space between the line of action of the force based on the axial displacement of the drive worm 22 and the setting position of the stopper 25. It will be appreciated that the force causing axial displacement of the worm 22 is transmitted to the bearing 24 and in cooperation with the stop 25 and bearing 24, a counter-eccentric moment is created to counteract the eccentric moment on the worm 22. Thereby limiting the radial displacement of the worm 22, ensuring the fit clearance between the worm 22 and the worm wheel 21, and improving the transmission precision of the transmission device 20. Thereby improving the steering efficiency of the steering gear 100 of the present application.

On the other hand, the arrangement of the limiting portion 25 makes it unnecessary to provide a structure for providing a supporting force at the distal end of the worm 22 facing away from the limiting portion 25, thereby reducing the space occupation of the transmission 20 in the steering gear 100 of the present application and making the steering gear 100 of the present application more compact.

Specifically, as shown in fig. 6, when the worm 22 and the worm wheel 21 are cooperatively driven, the worm wheel 21 has a radial force F1 and an axial force F2 acting on the worm 22. Based on the fact that only one side of the worm 22 protrudes into the seat 23, a limitation of the radial displacement of the worm 22 is achieved under the action of the seat 23. It will be appreciated that under the action of the radial force F1, the worm 22 has a tendency to rotate about the abutment 23 in a direction away from the worm wheel 21 and to undergo a radial displacement, resulting in an increase in the fit clearance between the worm wheel 21 and the worm 22. When the fit clearance between the worm wheel 21 and the worm 22 is excessively large, the transmission between the worm 22 and the worm wheel 21 may be affected, and even when the worm 22 or the worm wheel 21 rotates, the corresponding worm wheel 21 or worm 22 may not be driven to rotate. The radial force F1 can be converted into a first eccentric torque T1 which is applied to the worm 22 and which rotates in a direction away from the worm wheel 21.

Based on the limit portion 25 abutting against the outer ring 242 of the bearing 24, the worm 22 extends into the inner ring 243 of the bearing 24. It will be appreciated that there is a spacing between the stop 25 and the first axis of rotation L1 of the worm 22. As shown in fig. 6, the axial force F2 applied to the worm 22 by the worm wheel 21 is transmitted to the stopper 25 along the first rotation axis L1, and the axial displacement of the bearing 24 is limited, and the second eccentric moment T2 for rotating the worm 22 in the direction approaching the worm wheel 21 can be formed in cooperation with the stopper 25. And the second eccentric moment T2 is greater than or equal to the first eccentric moment T1.

As shown in fig. 6, the directions of the first eccentric moment T1 and the second eccentric moment T2 are opposite, so that the second eccentric moment T2 can offset the first eccentric moment T1, thereby ensuring that the radial force F1 does not affect the fit gap between the worm 22 and the worm wheel 21 in the fit transmission with the worm wheel 21. Thereby improving the transmission accuracy of the transmission 20 of the present application.

In another embodiment, as shown in fig. 7, when the limiting portion 25 may be disposed on a side of the bearing 24 near the worm wheel 21 and abuts against the end face 241 of the corresponding bearing 24. The axial force F2 generated by the worm wheel 21 acting on the worm 22 is directed along the first rotation axis L1 and away from the limiting portion 25, and the radial force F1 generated by the worm wheel 21 acting on the worm 22 can cause the worm 22 to have a tendency to generate radial displacement away from the worm wheel 21. It will be appreciated that the axial force F2 can also cooperate with the stop 25 to create a second eccentric moment T2 that rotates the worm 22 in a direction towards the worm wheel 21 to counteract the first eccentric moment T1 created by the radial force F1 cooperating with the abutment 23. Ensuring a fit clearance between the worm 22 and the worm wheel 21.

Therefore, the transmission device 20 is provided with the limit part 25 which can prop against the outer ring 242 of the bearing 24, so that when the worm 22 and the worm wheel 21 are matched for transmission and generate a deflection moment, the limit part 25 can be matched with the bearing 24 to generate a reverse deflection moment so as to limit the radial displacement of the worm 22, thereby ensuring the matching gap between the worm 22 and the worm wheel 21 and improving the transmission precision of the transmission device 20. Thereby improving the steering efficiency of the steering gear 100 of the present application.

Meanwhile, the arrangement of the limiting part 25 in the transmission device 20 also makes the far end of the worm 22 away from the limiting part 25 unnecessary to be provided with a structure for providing supporting force, thereby reducing the space occupation ratio of the transmission device 20 in the steering gear 100 of the application and enabling the steering gear 100 of the application to be more compact in structure.

Referring to fig. 8, a schematic structural diagram of a prior art steering gear 100', a schematic partial cross-sectional structure of the prior art steering gear 100' shown in fig. 9, and a schematic stress analysis of a transmission 20 'in the prior art steering gear 100' shown in fig. 10 are shown.

As shown in fig. 8 to 10, in the related art, a steering gear 100 'includes a direction control device 10', a transmission 20', and a steering device 30'. The transmission 20' comprises a worm wheel 21' and a worm 22' in driving connection. The worm wheel 21 'is connected with the steering device 30' in a driving way, and the worm 22 'is connected with the direction control device 10' in a driving way. The steering device 10 'drives the steering device 30' to rotate through the cooperation of the worm 22 'and the worm wheel 21' so as to realize the steering function.

As shown in fig. 9, the transmission 20 'further includes a first mount 231', a second mount 232', a first bearing 241', a second bearing 242', and a spring 25'. Wherein, the first bearing 241 'is embedded in the first support 231', and the second bearing 242 'is embedded in the second support 232'. Opposite ends of the worm 22' extend into the first bearing 241' and the second bearing 242', respectively. The worm wheel 21 'is located between the first bearing 241' and the second bearing 242 'and is in driving connection with the worm 22'. The spring 25' is disposed in the second support 232', and disposed on a side of the worm 22' away from the worm wheel 21', and abuts against the worm 22 '.

Specifically, as shown in fig. 10, in the prior art, when the worm wheel 21' and the worm 22' are cooperatively driven, the radial force F1' applied to the worm 22' by the worm wheel 21' causes the worm 22' to turn over with respect to the first bearing 241 '. The spring 25' applies an elastic force F2' to the worm 22' in a direction opposite to the radial force F1' to cancel the radial force F1'.

However, in the prior art, in order to adapt to different working conditions, there may be a situation that the rotation moment transmitted by the directional control device 10' has a large variation range. The spring 25' is limited by the elastic force range, and cannot provide reliable elastic force feedback under all working conditions, so that the force of the worm wheel 21' acting on the worm 22' is not matched with the force of the spring 25' acting on the worm 22' under part of working conditions, and the worm 22' can move in a direction away from or close to the worm wheel 21', so that the fit clearance between the worm 22' and the worm wheel 21' is increased or reduced, and the transmission precision of the worm wheel 21' and the worm 22' is affected. Thereby affecting the steering efficiency of the steering gear 100'.

Therefore, when the steering gear 100 of the present application rotates with the direction control device 10 and the worm 22 generates a yaw moment by providing the stopper 25 that abuts against the outer ring 242 of the bearing 24 along the direction of the first rotation axis L1 of the worm 22, the stopper 25 can convert the force of the worm wheel 21 acting on the worm 22 into a reverse eccentric moment by abutting against the bearing 24 and counteract the yaw moment of the worm 22 to ensure a fit gap between the worm 22 and the worm wheel 21.

Since the first and second eccentric moments T1 and T2 of the inventive steering gear 100 acting on the worm 22 are provided by the radial force F1 and the axial force F2, respectively, the magnitudes of the radial force F1 and the axial force F2 are related to the rotational moment of the worm wheel 21. It will be appreciated that as the rotational torque of the directional control device 10 changes, the rotational torque of the worm gear 21 will also change. Correspondingly, the magnitudes of the radial force F1 and the axial force F2 will also vary. So that the first and second eccentric moments T1 and T2 also vary. And the second eccentric moment T2 is synchronously changed with the change of the first eccentric moment T1.

It will be appreciated that the eccentric moment provided by the spring force of the spring 25' is compared to the prior art. The limiting part 25 of the steering gear 100 ensures that the second eccentric moment T2 can also change along with the change of the first eccentric moment T1 when the rotation moment of the direction control device 10 changes, and can offset the first eccentric moment T1, thereby limiting the radial displacement of the worm 22. Thereby ensuring the fit clearance between the worm 22 and the worm wheel 21 and improving the transmission precision of the transmission device 20. Thereby improving the steering efficiency of the steering gear 100 of the present application.

Meanwhile, compared with the prior art, the arrangement of the limiting portion 25 of the steering gear 100 reduces the arrangement of the second support 232 'and the second bearing 242', thereby reducing the space occupation ratio of the transmission 20 in the steering gear 100, and further making the steering gear 100 more compact.

Referring to FIG. 11, a schematic partial cross-sectional view of a transmission 20 according to an embodiment of the present application is shown.

As shown in fig. 11, the stopper 25 includes a first stopper 251 and a second stopper 252. The bearing 24 has a first end face 2411 and a second end face 2412 in the direction of the third rotation axis L3, and the first end face 2411 is closer to the worm wheel 21 (not shown in the drawings) than the second end face 2412. The first limiting portion 251 abuts against the first end surface 2411 of the bearing 24, and the second limiting portion 252 abuts against the second end surface 2412 of the bearing 24, so that the bearing 24 is limited between the first limiting portion 251 and the second limiting portion 252 in the direction of the third rotation axis L3. Thereby effecting a restriction of the axial displacement of the bearing 24.

As shown in fig. 11, the first stopper 251 is closer to the second rotation axis L2 (not shown) of the worm wheel 21 (not shown) than the second stopper 252 in the arrangement direction of the worm wheel 21 and the worm 22.

Since the worm 22 and the bearing 24 are both of a solid of revolution construction. It will be appreciated that when the position of the worm wheel 21 is changed in the circumferential direction of the worm 22, there may be caused a case where the first limit portion 251 or the second limit portion 252 coincides with the first rotation axis L1 in the arrangement direction of the worm wheel 21 and the worm 22.

Thus, the first stopper 251 and the second stopper 252 having different distances from the second rotation axis L2 are provided in the arrangement direction of the worm wheel 21 and the worm 22, and it is possible to avoid the first stopper 251 and the second stopper 252 overlapping the first rotation axis L1 at the same time when the arrangement direction of the worm wheel 21 changes.

The stopper 251 abuts against the outer ring 242 of the bearing 24. It is understood that the first limit portion 251 and the second limit portion 252 can each cooperate with the axial force F2 to form a second eccentric moment T2. Therefore, the first and second stopper portions 251 and 252 are provided at intervals in the arrangement direction of the worm wheel 21 and the worm 22, so that the formation of the second eccentric moment T2 can be ensured to cancel the first eccentric moment T1 formed by the radial force F1 of the worm wheel 21 acting on the worm 22. Thereby preventing the worm 22 from turning around the bearing 24, ensuring a fit clearance between the worm 22 and the worm wheel 21.

Specifically, please refer to fig. 12 for a further force analysis diagram of the transmission 20 according to an embodiment of the present application, and fig. 13 for a further force analysis diagram of the transmission 20 according to an embodiment of the present application, in conjunction with fig. 11. Fig. 12 and fig. 13 are schematic diagrams of force analysis of the steering gear 100 according to the present application, which is made by adopting the structures of the first limiting portion 251 and the second limiting portion 252 shown in fig. 11.

As shown in fig. 11 to 13, in the arrangement direction of the worm wheel 21 and the worm 22, the first limiting portion 251 is closer to the second rotation axis L2 (not shown) with respect to the first rotation axis L1, and the second limiting portion 252 is farther from the second rotation axis L2 with respect to the first rotation axis L1.

As shown in fig. 12, the rotation direction of the worm wheel 21 and the worm 22 may be changed during the mating transmission. It will be appreciated that as the directional control device 10 rotates, the direction of the axial force F2 exerted by the worm wheel 21 on the worm 22 will also change.

When the axial force F2 of the worm wheel 21 acting on the worm 22 is directed away from the bearing 24, the axial force F2 causes the outer ring 242 of the bearing 24 to press the first limiting portion 251. That is, the outer ring 242 of the bearing 24 mainly receives the reaction force from the first stopper 251 in the direction along the third rotation axis L3 of the bearing 24.

Since the first stopper 251 is relatively close to the worm wheel 21, there is a space between it and the third rotation axis L3. The axial force F2 will cause the worm 22 to have a tendency to turn towards the direction of approach to the worm wheel 21. That is, the worm 22 has the second eccentric moment T2 turned toward the direction approaching the worm wheel 21 by the axial force F2 and the first stopper 251.

The second eccentric moment T2 can offset the influence of the first eccentric moment T1 on the worm 22, so that a fit clearance between the worm 22 and the worm wheel 21 is ensured, and the steering efficiency of the steering gear 100 is improved.

On the other hand, as shown in fig. 13, when the direction of the axial force F2 of the worm wheel 21 acting on the worm 22 is the direction toward the bearing 24, the axial force F2 can cause the outer ring 242 of the bearing 24 to press the second stopper 252. It will be appreciated that outer race 242 of bearing 24 is primarily subjected to forces from second limiter 252 in a direction along third rotational axis L3 of bearing 24.

Since the second limiting portion 252 is relatively far from the worm wheel 21, a space exists between the second limiting portion and the third rotation axis L3. The axial force F2 will cause the worm 22 to have a tendency to turn towards the direction of approach to the worm wheel 21. That is, the worm 22 also has the second eccentric moment T2 turned over in the direction approaching the worm wheel 21 by the axial force F2 and the second stopper 252.

The second eccentric moment T2 can offset the influence of the first eccentric moment T1 on the worm 22, so that a fit clearance between the worm 22 and the worm wheel 21 is ensured, and the steering efficiency of the steering gear 100 is improved.

Thus, in the steering gear 100 of the present application, the first stopper 251 and the second stopper 252 are provided on opposite sides of the first rotation axis L1, so that even when the rotation direction of the worm wheel 21 is changed, the fit clearance between the worm 22 and the worm wheel 21 can be ensured. Thereby enhancing the applicable operating conditions of the steering gear 100 of the present application.

In another embodiment, when the rotation direction of the direction control device 10 is unchanged and the direction of the axial force F2 of the worm wheel 21 acting on the worm 22 is a direction away from the bearing 24, the first limiting portion 251 and the second limiting portion 252 are both closer to the second rotation axis L2 than the first rotation axis L1 in the arrangement direction of the worm wheel 21 and the worm 22. Correspondingly, the axial force F2 of the worm wheel 21 acting on the worm 22 can cause the first stopper 251 to abut against the first end surface 2411. The second limiting portion 252 is configured to cooperate with the first limiting portion 251 to limit an axial position of the bearing 24.

Meanwhile, in another embodiment, when the rotation direction of the direction control device 10 is unchanged and the direction of the axial force F2 acting on the worm 22 by the worm wheel 21 is the direction toward the bearing 24, in the arrangement direction of the worm wheel 21 and the worm 22, the first limiting portion 251 and the second limiting portion 252 are both further away from the second rotation axis L2 than the first rotation axis L1. The applicant does not particularly limit this.

In one embodiment, as shown in fig. 12 and 13, a first distance D1 is between the first limiting portion 251 and the third rotation axis L3 of the bearing 24, a second distance D2 is between the second limiting portion 252 and the third rotation axis L3 of the bearing 24, and the first distance D1 is less than or equal to the second distance D2.

In the direction of the first rotation axis L1, since the distance between the second limiting portion 252 and the second rotation axis L2 is longer than the distance between the first limiting portion 251 and the second rotation axis L2, the magnitude of the rotation moment is related to not only the magnitude of the force but also the perpendicular distance between the force line and the rotation axis.

It will be appreciated that, under the same radial force F1, the first eccentric moment T1 generated by the worm 22 about the first limit portion 251 is smaller than the first eccentric moment T1 generated by the worm 22 about the second limit portion 252. Correspondingly, the second eccentric moment T2 generated by the cooperation of the axial force F2 and the first limiting portion 251 should be smaller than the second eccentric moment T2 generated by the cooperation of the axial force F2 and the second limiting portion 252.

Since the magnitude of the axial force F2 is synchronized with the magnitude change of the radial force F1. Therefore, the second distance D2 that is greater than or equal to the first distance D1 is provided, so that the second eccentric moment T2 generated by the cooperation of the axial force F2 and the second limiting portion 252 can be ensured to cancel the corresponding first eccentric moment T1. Thereby ensuring the limiting effect of the second limiting part 252 on the radial displacement of the worm 22 and ensuring the fit clearance between the worm 22 and the worm wheel 21.

Referring to FIG. 14, a partial front view of the transmission 20 according to one embodiment of the present application is shown, and referring to FIG. 15, a partial exploded view of the transmission 20 according to one embodiment of the present application is shown, together with FIG. 11.

As shown in fig. 11, the first limiting part 251 may be detachably connected with the support 23, so that the first limiting part 251 may be separately manufactured in the process of manufacturing the support 23, thereby reducing the manufacturing complexity of the support 23. The first stopper 251 includes a first axial protrusion 251a and a first radial protrusion 251b. As shown in fig. 14 and 15, the first limiting portion 251 has a circular ring structure, and the first axial protrusion 251a extends along the third rotation axis L3 toward the first end surface 2411 of the bearing 24 for abutting against the first end surface 2411. The first radial protrusion 251b protrudes in the radial direction.

The support 23 is provided with a mounting groove 23a which cooperates with the first radial protrusion 251 b. The first stopper 251 is fixed in position by receiving the first radial protrusion 251b in the mounting groove 23a.

In one embodiment, as shown in fig. 15, two first axial protruding pieces 251a are provided, and in the arrangement direction of the worm wheel 21 and the worm 22, the two first axial protruding pieces 251a are located on the same side of the third rotation axis L3, and the two first axial protruding pieces 251a are equally spaced from the third rotation axis L3.

It will be appreciated that the provision of the two first axial protrusions 251a, as shown in fig. 15, enables the force exerted by the two first axial protrusions 251a on the first end face 2411 of the bearing 24 to be relatively uniform as the directional control device 10 is rotated. On the other hand, when the worm wheel 21 and the worm 22 cooperate to drive and generate an eccentric moment, the mutual cooperation of the two first axial protruding members 251a can prevent the eccentric moment formed by the cooperation of the axial force F2 and the single first axial protruding member 251a from facing other directions, thereby ensuring the limiting effect of the first limiting portion 251 on the radial displacement of the worm 22.

Another partially exploded view of the transmission 20, please refer to another partially cross-sectional view of the transmission 20 provided in one embodiment of the present application shown in fig. 17, and partially enlarged view of the transmission 20 provided in one embodiment of the present application shown in fig. 18.

As shown in fig. 16 to 18, the first axial protrusion 251a is of an arc-shaped structure and circumferentially arranged about the third rotation axis L3. To increase the contact area with the outer ring 242 of the bearing 24, thereby ensuring the contact effect of the first limiting portion 251 with the outer ring 242 of the bearing 24. As shown in fig. 18, the first axial protrusion 251a has a first distance D1 from the third rotation axis L3.

It will be appreciated that in other embodiments, as shown in fig. 19, the second limiting portion 252 may be detachably connected to the support 23. Correspondingly, the second limiting portion 252 also includes a second axial protrusion 252a and a second radial protrusion 252b. The second axial protrusion 252a extends toward the bearing 24 and abuts against the bearing 24, and the second radial protrusion 252b cooperates with a mounting location (not shown) on the support 23 to achieve a relative fixation of the second stopper 252.

The second axial protrusion 252a may be disposed in a similar manner to the first axial protrusion 251a shown in fig. 15, 16 and 17, which is not particularly limited by the applicant.

In one embodiment, referring back to FIG. 17, the transmission 20 also includes a bumper 26. Wherein the buffer 26 is filled between the bearing 24 and the support 23. When the worm 22 and the worm wheel 21 are cooperatively driven, the worm 22 may generate vibration, which may be transmitted to the bearing 24, and the bearing 24 and the support 23 may rub against each other due to the vibration, thereby generating noise.

The buffer member 26 can absorb the vibration between the bearing 24 and the support 23, thereby avoiding the phenomenon of mutual friction between the bearing 24 and the support 23 caused by the vibration, reducing the noise generated in the working process of the transmission device 20 and improving the use experience of users.

In one embodiment, referring back to FIG. 1, directional control device 10 includes a steering wheel 11, a sensor 12, and a motor 13. The rotation axis of the steering wheel 11 is fixed relative to the transmission device 20, and the sensor 12 is disposed in the steering wheel 11 for acquiring rotation information of the steering wheel 11. The motor 13 is in driving connection with the worm 22 and in communication with the sensor 12.

When the steering wheel 11 is rotated by a user, the sensor 12 collects rotation information of the steering wheel 11 and converts the rotation information into a steering signal to be transmitted into the motor 13. The motor 13 drives the worm 22 to rotate based on the steering information, thereby realizing the driving of the worm 22 by the directional control device 10.

In one embodiment, the directional control device 10 further includes a controller (not shown) in communication with the sensor 12 and the motor 13. When the steering wheel 11 rotates, the sensor 12 converts the collected rotation information of the steering wheel 11 into a steering signal and transmits the steering signal to the controller, and the controller processes the steering signal and then transmits the steering signal to the motor 13, so that the driving of the worm 22 by the direction control device 10 is realized.

It should be appreciated that the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more of the described features. In the description of the embodiments of the present application, the meaning of "plurality" is two or more, unless explicitly defined otherwise.

In the description of the present specification, reference to the terms "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present application. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

It is to be understood that the utility model is not limited in its application to the examples described above, but is capable of modification and variation in light of the above teachings by those skilled in the art, and that all such modifications and variations are intended to be included within the scope of the appended claims. Those skilled in the art will recognize that the full or partial flow of the embodiments described above can be practiced and equivalent variations of the embodiments of the present utility model are within the scope of the appended claims.

Claims (13)

1. The steering gear is characterized by comprising a direction control device, a transmission device and a steering device, wherein the transmission device comprises a worm wheel and a worm, the direction control device is in transmission connection with the worm, the steering device is in transmission connection with the worm wheel, and the direction control device drives the steering device to rotate through the cooperation of the worm and the worm wheel so as to realize a steering function;

The transmission device further comprises a support and a bearing, the support is sleeved at the end part of the worm through the bearing, the support is further provided with a limiting part, and the limiting part is propped against the outer ring of the bearing along the direction of the rotating shaft of the worm so as to limit the radial displacement of the worm.

2. The steering gear according to claim 1, wherein the limit portion includes a first limit portion and a second limit portion, the first limit portion and the second limit portion are located on opposite sides of the bearing, respectively, in a direction of a rotation axis of the worm, and the first limit portion is close to the worm wheel with respect to the second limit portion, and the first limit portion and the second limit portion are abutted against opposite end surfaces of the bearing outer race, respectively, to limit radial displacement of the worm.

3. The steering gear according to claim 2, wherein the first stopper portion is closer to the rotation axis of the worm wheel with respect to the rotation axis of the worm and/or the second stopper portion is farther from the rotation axis of the worm wheel with respect to the rotation axis of the worm in the arrangement direction of the worm wheel and the worm.

4. The steering gear according to claim 2, wherein the first stopper portion is closer to the steering device than the second stopper portion in an arrangement direction of the worm wheel and the worm.

5. The diverter of claim 4, wherein a first spacing is provided between the first spacing and the axis of rotation of the worm, and a second spacing is provided between the second spacing and the axis of rotation of the worm, the first spacing being less than or equal to the second spacing.

6. The steering gear according to claim 1, wherein the limiting portion is of a circular ring structure, and the limiting portion includes an axial protruding member that extends toward an end face of the bearing along a rotation axis of the bearing and abuts against an end face of the bearing outer ring to limit radial displacement of the worm.

7. The steering gear according to claim 6, wherein two of the axial protrusions are provided, the two axial protrusions are located on the same side of the rotational axis of the bearing in the arrangement direction of the worm wheel and the worm screw, and the two axial protrusions are equally spaced from the rotational axis of the bearing.

8. The steering gear according to claim 6, wherein the axial projection is arcuate, the axial projection being located on one side of the rotational axis of the bearing and being circumferentially arranged about the rotational axis of the bearing.

9. The steering gear according to claim 6, wherein the limiting portion further comprises a radial protruding member protruding in a radial direction of the bearing, the support is further provided with a mounting groove, the mounting groove is disposed in the radial direction of the bearing, and the radial protruding member is accommodated in the mounting groove so as to fix the position of the support to the limiting portion.

10. The steering gear according to claim 1, wherein the transmission further comprises a buffer member filled between the bearing and the support, the buffer member being for absorbing vibrations between the bearing and the support.

11. A steering gear according to any one of claims 1-10, wherein the steering control device comprises a steering wheel, a sensor and a motor, the rotation axis of the steering wheel is fixed relative to the transmission device, the sensor is in communication connection with the motor, the sensor is used for collecting rotation information of the steering wheel and converting the rotation information into a steering signal to be transmitted to the motor, the motor is in transmission connection with the worm, and the motor drives the worm to rotate based on the steering signal.

12. The steering gear of claim 11, wherein the directional control device further comprises a controller communicatively coupled between the sensor and the motor, the controller configured to process the steering signal output by the sensor and to transmit the processed steering signal to the motor.

13. A vehicle comprising wheels, and a steering gear as claimed in any one of claims 1 to 12 for controlling deflection of the wheels to change the direction of travel of the vehicle.