CN211599510U - Gear mechanism for gear shifting actuating mechanism and gear shifting actuating mechanism - Google Patents

Abstract

The utility model relates to a gear mechanism for a gear shifting actuating mechanism, which comprises an upper shell, a lower shell and a gear arranged between the upper shell and the lower shell, wherein the gear comprises a first end facing the upper shell and a second end facing the lower shell; the gear further includes a lower opening extending from the second end in a direction toward the first end, the lower opening being open to the lower housing. A blocking member is disposed in the lower opening, an end of the blocking member facing the lower housing being capable of protruding from the gear beyond the second end, the blocking member being configured in the lower opening relative to the gear to block any displacement of the gear toward the lower housing. And, still relate to a gear shift actuating mechanism including this gear mechanism. Through this gear mechanism and actuating mechanism that shifts, avoided the slip of gear in longitudinal direction.

Description

Gear mechanism for gear shifting actuating mechanism and gear shifting actuating mechanism

Technical Field

The present invention relates to a gear mechanism for a gear shift actuator, and in particular to a gear mechanism with a blocking member for blocking the displacement of a gear in a longitudinal direction. The utility model discloses still relate to an actuating mechanism that shifts including this gear mechanism.

Background

In the prior art, a gear mechanism is used as a main transmission mechanism of a gear shifting actuating mechanism of a vehicle. The present shift actuators are subject to longitudinal acceleration during operation. In general, in order to simulate operating conditions in operation, it is necessary in vibration tests to apply a high acceleration to the shift actuator and therefore to the gear mechanism thereof in order to detect the operating conditions of the shift actuator and possible problems.

At present, due to the clearance after the gear mechanism is assembled, and due to the acceleration in the longitudinal direction which is received in the vibration test, the gear is caused to slide in the longitudinal direction, and such gear sliding causes the efficiency of the transmission system to be reduced, noise to be generated, and even the service life of the gear mechanism to be reduced.

Accordingly, there remains a need for further improvements in the gear mechanisms of prior shift actuators.

SUMMERY OF THE UTILITY MODEL

The utility model discloses a technical problem that will solve is: a gear mechanism for a shift actuator is provided that ensures stable position of a gear in a longitudinal direction.

In order to solve the above problems, the present invention provides a gear mechanism for a gear shift actuator, comprising an upper housing, a lower housing, and a gear disposed between the upper housing and the lower housing, the gear comprising a first end facing the upper housing and a second end facing the lower housing; the gear further includes a lower opening extending from the second end in a direction toward the first end, the lower opening being open to the lower housing. In the lower opening, a blocking element is arranged, whose one end facing the lower housing can project from the gear beyond the second end of the gear. The blocking member is configured within the lower aperture relative to the gear to block any displacement of the gear toward the lower housing. By providing the blocking member at a predetermined position on the lower housing, the gear is supported in the longitudinal direction.

According to one aspect of the present invention, the blocking member includes an elastic member whose rigidity is designed to be in a pre-compression state after being installed in the lower opening, and is not further compressed in response to an impact force applied to the elastic member by the gear mechanism. The stop member is advantageously mounted using a pre-compressed resilient member without the lower housing failing to mount to the upper housing due to dimensional interference or the like mismatch.

According to an aspect of the invention, the elastic member is configured as a coil spring, the coil spring comprises an arc-shaped portion at an end portion, and/or the gear is configured as a face gear. The coil spring is commercially available and inexpensive, and the curved portions at both ends are advantageous in reducing friction with the gear and with the lower case. The face gear can then be adapted to a conventional spindle drive of the shift actuator.

According to an aspect of the invention, the lower opening is a blind hole, and the blocking member comprises a further end portion which is remote from the lower housing, which further end portion abuts against the bottom of the blind hole in the blind hole, so that the blocking member can be easily constructed with one end abutting against the bottom of the blind hole to support the gear without additionally providing an element such as a bar in the hole.

According to the utility model discloses an aspect, the one end of gear is directly supported and is leaned on in last casing to make the gear can not take place any displacement towards last casing, make the gear like this can not upwards also can not the downward displacement on longitudinal direction.

According to an aspect of the present invention, the gear mechanism further includes a sensor for detecting a movement of the gear, the sensor being disposed above the upper case. A preset position is reserved above the upper shell, and a sensor to be detected, a PCB and the like are arranged in the preset position.

According to an aspect of the invention, the gear further comprises an upper opening extending from the first end in a direction towards the second end, in which upper opening the magnet is fixed, and wherein the sensor is configured as a magnetic sensor to detect the movement of the gear by detecting the magnetic lines of force of the magnet, and the sensor is spaced from the magnet by a fixed distance, which depends on the sensing range of the magnetic sensor used.

According to the utility model discloses an aspect, gear mechanism still includes the inner support of fixing in the space between last casing and lower casing, and the gear is arranged to rotatably arrange the inner support in, so arrange can make things convenient for the gear at last casing, installation and location between the casing down to can add emollient in order to do benefit to the gear rotation between inner support and gear.

According to an aspect of the invention, the inner support is arranged at the first end and the second end of the gear, respectively. The inner support adopts a plurality of inner supports to limit the gear instead of a single inner support to surround the whole gear, so that the installation is convenient.

According to the utility model discloses a shift actuating mechanism, wherein, shift actuating mechanism includes any one of the gear mechanism in the above aspect.

Compared with the existing gear mechanism, the gear mechanism of the utility model can be realized only by adding a blocking piece with lower cost, has good universality, and has no modification requirement; only the blocking piece is required to be arranged in the existing lower opening hole, the assembly process is easy to realize, and the requirement of additional installation is avoided; the commercial spring can meet the supporting requirement and the noise reduction requirement, is suitable for the original working environment of the gear mechanism, and has strong universality and no need of additional design cost.

Drawings

FIG. 1 is an elevational view of a shift actuator and its gear mechanism according to a preferred embodiment of the present invention;

fig. 2 is a partial enlarged view of a gear mechanism according to a preferred embodiment of the present invention;

fig. 3a is a front view of a coil spring of a gear mechanism according to a preferred embodiment of the present invention; and

fig. 3b is a side view of the coil spring of the gear mechanism according to the preferred embodiment of the present invention.

List of reference numerals

10 upper shell

20 lower casing

30-face gear

31 first end

32 second end

33 is provided with a hole

34 lower open hole

34a bottom of hole

35 helical spring

35a (of the coil spring) at the other end

35b (of a helical spring) of one end

40 magnetic force sensor

50 magnet

61 inner support

62 inner support

100 gear mechanism

1000 shift actuator.

Detailed Description

The present invention will be further described with reference to the following embodiments and drawings, and more details will be set forth in the following description in order to provide a thorough understanding of the present invention, but it is obvious that the present invention can be implemented in various other ways different from those described herein, and those skilled in the art can make similar generalizations and deductions according to the actual application without departing from the spirit of the present invention, and therefore, the scope of the present invention should not be limited by the contents of the embodiments.

In the embodiment of the present invention, the "longitudinal direction" is defined as the upper-lower casing direction, and the direction toward the upper casing is the positive longitudinal direction.

In embodiments of the present invention, the gears include, but are not limited to, gears having straight teeth, helical teeth, face teeth (crown teeth), ring gears, and the like.

In an embodiment of the present invention, the gear mechanism includes an upper housing, a lower housing, and a gear between the upper housing and the lower housing. Wherein the upper and lower housings are pre-configured in a suitable shape to fit within a shift actuator. The upper and lower housings include a space therebetween for operatively transmitting gears. At the end of the installation process, the lower housing may be secured to the upper housing by bolting, welding, riveting, or the like.

The gear mechanism also includes a gear disposed between the upper and lower housings, the gear including a first end facing the upper housing and a second end facing the lower housing. The gear is preferably cast and has a lower opening at the second end facing the lower housing. The lower opening allows the gear to be controlled to have a uniform wall thickness during casting. The lower opening can be a blind hole or a through hole and the like according to the working requirement.

The gear mechanism preferably comprises inner housings mounted within the upper and lower housings, the first and second ends of the gears being rotatably disposed within the respective inner housings by a form fit. The structure, number and location of the internal supports are not particularly limited and may vary according to design and application requirements. Lubricating fluid such as oil is present at the position where the inner carrier contacts the gear to reduce friction in the circumferential direction when the gear rotates. The portion of the inner bracket that is in shape fit with the first end and the second end of the gear respectively comprises, but is not limited to, a cylinder shape of a through hole, a cylinder shape of a blind hole and the like, and the outer diameter of the first end and the second end of the gear is slightly smaller than the aperture of the corresponding hole of the inner bracket.

In order to ensure the position stability of the gear in the longitudinal direction, it is necessary to provide an effective supporting force to the gear in the longitudinal direction, and therefore a stopper may be provided in the lower opening of the gear. The end of the blocking element facing the lower housing can project beyond the second end of the gear wheel, wherein the length of the projection of the blocking element is slightly greater than the assembly clearance of the gear wheel mechanism, and directly abuts against the lower housing, or alternatively against an inner support corresponding to the second end, the blocking element being arranged in the lower opening by means of an interference fit so as to block any displacement of the gear wheel towards the lower housing. The other end of the blocking piece, which is far away from the lower shell, is abutted against the lower opening of the gear. For example, when the lower opening hole is a blind hole, the other end of the blocking member abuts against the bottom of the lower opening hole, and when the lower opening hole is a through hole, the other end of the blocking member abuts against a stopper such as a stopper strip disposed inside the lower opening hole.

The stop includes a resilient member to facilitate overcoming the stress of the interference fit during the installation step. The elastic member is in a pre-compressed state after being mounted in the lower opening, and the rigidity of the elastic member is designed not to be further compressed in response to an impact force applied thereto by the gear mechanism, and therefore its length is not further shortened, thereby preventing any displacement of the gear toward the lower housing in the longitudinal direction. The elastic member includes, but is not limited to, a coil spring, a reed, a telescopic support rod, etc., and is preferably a coil spring. Both ends of the coil spring are preferably configured in an arc shape, i.e., an arc-shaped portion, and the equivalent stiffness of such a coil spring also needs to satisfy the aforementioned conditions. The arc top of the arc-shaped portion makes the contact area of the one end facing the lower casing and the other end facing the lower opening smaller, and therefore receives less frictional force. It is of course easily conceivable that the structure of both ends of the coil spring is not limited thereto and may vary according to design and application requirements. On the other hand, the coil spring is inexpensive in the elastic member, enabling cost reduction.

In order to ensure a stable position of the gear wheel in the longitudinal direction, it is also necessary to configure the gear wheel such that no further approaching movement relative to the upper housing is possible. Preferably, the first end of the gear directly abuts the upper housing to prevent displacement thereof towards the upper housing. Alternatively, in the case of a non-direct abutment, i.e. the inner support in which the gear is placed is not provided with a through hole but with a blind hole, the first end of the gear abuts against the bottom of the corresponding blind hole of the inner support to prevent an approaching movement with respect to the upper housing. Alternatively, the gear may also have an upper aperture facing the upper housing at the first end and include another blocking member therein, as previously described, such that the blocking member is disposed within the upper aperture to block any displacement of the gear towards the upper housing.

The gear mechanism may also include various sensors to monitor various operating conditions of the gears, including but not limited to rotational speed, temperature, noise, etc. The sensor may be disposed at a predetermined position above the upper case and electrically connected to a PCB board provided in advance, so as to transmit detected data to an operation and control chip of a computer of the vehicle.

The gear mechanism preferably includes a magnetic force sensor, and the gear has an upper opening facing the upper housing at the first end, and a magnet is mounted in the upper opening, the magnet being fixed in the upper opening so as to rotate with the gear. The magnetic force sensor can detect the magnetic induction line of the magnet and thus detect the rotation angle, angular velocity, angular acceleration, and other related data of the gear. In this case, but not limited thereto, the magnetic force sensor needs to be spaced apart from the magnet by a fixed distance depending on the requirements of the magnetic force sensor to effectively detect the magnetic force lines of the magnet.

The gear mechanisms used in shift actuators are configured to transmit operating forces to the transmission, gearbox, etc. by means such as gear sets, face gears, worms, etc.

The present invention will be further described with reference to the following embodiments and drawings, and more details will be set forth in the following description in order to provide a thorough understanding of the present invention, but it is obvious that the present invention can be implemented in various other ways different from those described herein, and those skilled in the art can make similar generalizations and deductions according to the actual application without departing from the spirit of the present invention, and therefore, the scope of the present invention should not be limited by the contents of the embodiments.

Fig. 1 shows a shift actuator 1000 and its gear mechanism 100 configured to drive through a face gear worm set in accordance with a preferred embodiment of the present invention. The gear mechanism 100 includes an upper case 10, a lower case 20, and a face gear 30 provided between the upper case 10 and the lower case 20. The face gear 30 includes a first end 31 facing the upper housing 10 and a second end 32 facing the lower housing 20.

As shown in fig. 2, at the second end 32, there is a lower opening 34 facing the lower housing 20, wherein the lower opening 34 is a blind hole design, and a bottom 34a of the lower opening 34 is at a distance L2 from the lower housing.

The gear mechanism 1 comprises inner supports 61, 62 mounted in the upper and lower housings 10, 20, the first and second ends 31, 32 of the face gear 30 being rotatably disposed in the respective inner supports 61, 62 by a form fit. The corresponding inner support and the first end and the second end of the gear are matched in shape, the corresponding inner support and the first end and the second end of the gear are cylindrical, and the outer diameter of the first end and the second end of the gear is slightly smaller than the aperture of the corresponding inner support.

A coil spring 35 is provided in the lower opening hole 34, one end 35b of the coil spring 35 facing the lower case 20 can protrude from the face gear 30 beyond the second end 32 thereof, and the protruding length of the coil spring 35 is slightly larger than the fitting clearance of the gear mechanism 100 and directly abuts against the lower case 20. The other end 35a of the coil spring 35 abuts against the bottom 34a of the lower opening 34.

The gear mechanism 100 also includes a magnetic sensor 40 to monitor the speed of rotation of the face gear 30, among other operating conditions. The magnetic force sensor 40 may be disposed at a predetermined position above the upper case 10 and electrically connected to a PCB board provided in advance, so as to transmit detected data to a computing and control chip of a computer of the vehicle. And the face gear 30 has an upper opening 33 facing the upper case 10 at the first end 31 of the face gear 30, and a magnet 50 is installed therein, the magnet 50 being fixed in the upper opening 33 so as to rotate following the face gear 30. The magnetic force sensor 40 is capable of detecting magnetic lines of force of the magnet 50 and thus detecting data of the angle, angular velocity, and angular acceleration of the rotation of the face gear 30. In the present embodiment, the magnetic force sensor 40 is commercially available, and needs to be spaced apart from the magnet 50 by a fixed distance to effectively detect the line of magnetic induction of the magnet 50.

Fig. 3a, 3b show a coil spring of a gear mechanism according to a preferred embodiment of the present invention, and the curvature of the arc portion at both ends thereof is exaggerated for easy illustration. In the preferred embodiment, the coil spring 35 is pre-compressed after being installed in the lower opening 34, and the two ends of the coil spring are preferably curved arcs, i.e., arc-shaped portions, as shown in fig. 3 a. End 35b abuts lower housing 20 and end 35a abuts blind hole bottom 34 a. The arc tips of the arc portions make the contact area smaller and thus receive less friction when the face gear rotates.

The coil spring 35 used in the preferred embodiment is commercially available and has a diameter R that is slightly smaller than the diameter of the lower opening 34 of the face gear 30. The spring rate of the coil spring 35 is K (as shown in fig. 3a, the original length of the coil spring 35 is known as L0, and the compressed length when subjected to a force F1 becomes L1, where L1 is smaller than L0, the difference between which may be on the order of millimeters, for example).

When the coil spring 35 is placed in the lower opening 34 and compressed to a compressed length (i.e., the distance L2 between the bottom 34a of the lower opening 34 and the lower housing, the difference between L2 and L1 being, for example, 1 mm or less), i.e., the working length L2, the pre-compression force F2 is received as:

F2＝K*ΔX＝K*(L0-L2)

wherein,

f2 is the precompression force (in newtons, for example);

k is the stiffness coefficient (in units such as newtons/mm);

Δ X is the amount of compression;

l0 is the original length (in units of, for example, millimeters); and

l2 is the working length (in units of millimeters, for example).

Therefore, the pre-compression force of the coil spring 35, i.e., the supporting force of the coil spring 35 against the face gear 30 is F2, and it is not further compressed in the case where the impact force of the face gear against it is received less than F2.

The impact force applied to the coil spring 35 by the face gear 30 and the magnet 50 therein due to the acceleration effect of the vibration test is calculated below. In the present preferred embodiment, the vibration test applies an acceleration of a (e.g., on the order of several tens of g) and the sum of the weights of the face gear 30 and the magnet 50 is m, so that the impact force applied to the coil spring 35 is:

F3＝m*a

wherein,

f3 is the impact force applied to the coil spring;

m is the total mass of the relevant components;

a is the acceleration.

Therefore, in the vibration test, the impact force applied to the coil spring 35 by the face gear 30 and the magnet 50 of the gear mechanism 100 due to the acceleration is F3.

As long as the coil spring 35 is designed to satisfy the above-described impact force F3 smaller than the supporting force of the coil spring 35 against the face gear 30 (i.e., F3< F2), the coil spring 35 does not generate further compression in response to the impact force, thereby preventing any displacement of the face gear 30 in the longitudinal direction toward the lower housing 20.

When the gear mechanism of the preferred embodiment is installed in a gear shifting actuating mechanism, the following steps are carried out:

first, the magnetic force sensor 40 is mounted to a predetermined position of the shift actuator 1000 and electrically connected with a pre-mounted PCB board. Next, the upper case 10 is mounted to a predetermined position in the shift actuator 1000 and fixed with bolts. The corresponding inner support 61 is then installed in the upper housing 10 and the lubricating oil is spread in the inner support.

The magnet 50 is then installed into the upper opening 33 of the first end 31 of the face gear 30, and the first end 31 of the face gear 30 is then rotatably disposed in the inner bracket 61.

Then, the corresponding inner bracket 62 is installed in the lower case 20 and the lubricating oil is smeared in the inner bracket. And, a coil spring 35 is disposed in the lower opening 34 of the second end 32 of the face gear 30.

Finally, the lower housing is mounted to the upper housing such that the second end 32 of the face gear 30 is rotatably disposed within the inner bracket 62 with the end 35a of the coil spring abutting the bottom 34a of the lower opening 34 and the end 35b of the coil spring abutting the lower housing 20. Next, the lower case 20 is fixed to the upper case 10 with bolts.

While various embodiments have been described above, it should be understood that they have been presented by way of example only, and not limitation. It will be apparent to those skilled in the relevant art that the disclosed information and content can be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are, therefore, to be considered in all respects as illustrative and not restrictive, and not as a basis for any limitation on the invention.

Claims (10)

1. A gear mechanism (100) for a shift actuator (1000), the gear mechanism (100) comprising:

an upper case (10);

a lower case (20);

a gear (30), the gear (30) being disposed between the upper housing (10) and the lower housing (20), the gear (30) comprising a first end (31) facing the upper housing (10) and a second end (32) facing the lower housing (20),

characterized in that the gear (30) further comprises a lower aperture (34) extending from the second end (32) in a direction towards the first end (31), the lower aperture (34) being open towards the lower housing (20), a stop being arranged in the lower aperture (34), one end (35b) of the stop facing the lower housing (20) being projectable from the gear (30) beyond the second end (32), the stop being configured in the lower aperture (34) relative to the gear (30) to stop any displacement of the gear (30) towards the lower housing (20).

2. The gear mechanism (100) of claim 1 wherein said stop comprises a resilient member having a stiffness designed to be pre-compressed after installation in said lower aperture (34) and not to be further compressed in response to an impact force applied to said resilient member by said gear (30).

3. Gear mechanism (100) according to claim 2, characterised in that the elastic element is configured as a helical spring (35), that the helical spring (35) comprises an arc-shaped portion at the end (35a, 35b), and/or that the gear wheel (30) is configured as a face gear wheel (30).

4. Gear unit (100) according to claim 1, characterised in that the lower aperture (34) is a blind hole and the stop comprises a further end (35a) facing away from the lower housing (20), the further end (35a) resting against its bottom (34a) in the blind hole.

5. Gear mechanism (100) according to claim 1, characterised in that the first end (31) of the gear wheel (30) is directly against the upper housing (10) so that no displacement of the gear wheel (30) towards the upper housing (10) can take place.

6. The gear mechanism (100) according to claim 1, wherein the gear mechanism (100) further comprises a sensor (40) for detecting the movement of the gear (30), the sensor (40) being disposed above the upper housing (10).

7. The gear mechanism (100) according to claim 6, wherein the gear (30) further comprises an upper opening (33) extending from the first end (31) of the gear (30) in a direction towards the second end (32), a magnet (50) being fixed in the upper opening (33), and wherein the sensor (40) is configured as a magnetic sensor (40) to detect the movement of the gear (30) by detecting magnetic lines of force of the magnet (50), and the sensor (40) is spaced from the magnet (50) by a fixed distance.

8. Gear mechanism (100) according to claim 1, characterised in that the gear mechanism (100) further comprises an inner support (61, 62) fixed in the space between the upper housing (10) and the lower housing (20), the gear wheel (30) being arranged to be rotatably placed in the inner support (61, 62).

9. Gear mechanism (100) according to claim 8, characterised in that said inner brackets (61, 62) are provided at said first end (31) and said second end (32) of said gear wheel (30), respectively.

10. A shift actuator (1000), characterized in that the shift actuator (1000) comprises a gear mechanism (100) according to any one of claims 1-9.

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