A synchronous gap-eliminating helical gear transmission

Abstract

The utility model discloses a kind of helical gear transmission devices of synchronous elimination gap, belong to transmission gear technical field, including two groups of linkage cooperation driven transmission shaft and driving transmission shaft, the middle part of driven transmission shaft is fixedly installed with driven helical gear, driving transmission shaft is movably installed with the positive driving helical gear and reverse driving helical gear meshing with driven helical gear on it;The middle part of driving transmission shaft is equipped with anti-backlash spring, and the inner wall of positive driving helical gear and reverse driving helical gear is connected respectively at both ends of anti-backlash spring;Positive driving helical gear and reverse driving helical gear are movably installed on driving transmission shaft by axial slider;The utility model uses self-adapting axial motion, so anti-backlash function is not influenced by transmission force and the elastic force of anti-backlash spring.This scheme can be applied in all traditional gear transmission structure with anti-backlash requirement, so that traditional mechanical equipment is adjusted minimum, most economic condition is realized gear anti-backlash transmission, and the design improves practicability.

Description

Technical Field

[0001] This utility model relates to the field of transmission gear technology, specifically a helical gear transmission device for synchronously eliminating backlash. Background Technology

[0002] In industrial manufacturing, gear drives are commonly used. Ordinary gears mesh at point contact, resulting in backlash during gear transmission. This backlash can cause abnormal noise, and even small gaps can be amplified at the end of the machine, causing noticeable vibration. Currently available backlash-eliminating gears can eliminate tooth flank backlash in gear drives. This is achieved by making the driven gear of a pair of gears into two thin plates, one fixed to the shaft and the other fitted onto the hub of a gear sleeve. A tension spring is placed between the gear sleeve and the gear disc. This structure utilizes the tension of the spring to ensure that the left side of the gear disc's teeth and the right side of the gear sleeve's teeth are tightly pressed against the left and right sides of the tooth groove of the driving gear, respectively. This staggered tooth structure eliminates tooth flank backlash and prevents backlash errors during reverse rotation.

[0003] Chinese utility model patent application CN214367681U discloses a gear transmission device for eliminating gear backlash. It includes forward-facing and reverse-facing backlash-eliminating gears with equal number of teeth and diameter, a target gear, a gear shaft, a forward-facing flywheel, and a reverse-facing flywheel. The forward-facing and reverse-facing flywheels are spaced apart on the gear shaft. The forward-facing backlash-eliminating gear is mounted on the forward-facing flywheel, and the reverse-facing backlash-eliminating gear is mounted on the reverse-facing flywheel. A tension spring is provided between the forward-facing and reverse-facing backlash-eliminating gears to encourage them to rotate in opposite directions. This utility model uses the tension spring between the forward-facing and reverse-facing backlash-eliminating gears to clamp the target gear. The tension spring keeps two adjacent teeth of the forward-facing and reverse-facing backlash-eliminating gears in close contact with the two sides of the same tooth of the target gear. Regardless of whether the gear shaft rotates forward or reverse, one gear is always in contact with the target gear, thereby eliminating backlash in the gear transmission.

[0004] However, the circumferential structural space of the gear transmission device disclosed above is relatively large, and the backlash elimination effect is limited by the magnitude of the spring elastic force. After long-term use, as the spring elasticity decays, the backlash elimination effect is greatly reduced, and the transmission stiffness is limited by the magnitude of the transmitted power. Utility Model Content

[0005] The purpose of this utility model is to provide a helical gear transmission device that synchronously eliminates backlash, in order to solve the problems that existing gear transmission devices have large circumferential structural space dimensions, the backlash elimination effect is limited by the size of the spring elastic force, the backlash elimination effect is greatly reduced after long-term use as the spring elasticity decays, and the transmission stiffness is limited by the size of the transmitted power.

[0006] To achieve the above objectives, the technical solution of this utility model is: a helical gear transmission device for synchronously eliminating backlash, comprising two sets of linked driven transmission shafts and a driving transmission shaft. A driven helical gear is fixedly installed in the middle of the driven transmission shaft, and a forward driving helical gear and a reverse driving helical gear are movably installed on the driving transmission shaft, meshing with the driven helical gear. A backlash-eliminating spring is sleeved in the middle of the driving transmission shaft, and the two ends of the backlash-eliminating spring are respectively connected to the inner walls of the forward driving helical gear and the reverse driving helical gear. The backlash-eliminating spring is axially arranged and applies axial elastic force. The forward driving helical gear and the reverse driving helical gear maintain overall linkage through the backlash-eliminating spring, and the relative positional relationship between the forward driving helical gear and the reverse driving helical gear is adjusted by adaptive axial movement to eliminate the transmission backlash between the driven helical gear and the forward driving helical gear and the reverse driving helical gear.

[0007] As a further embodiment of this utility model: a groove is provided on the outer wall of the drive shaft, and grooves are provided on the inner walls of the forward drive helical gear and the reverse drive helical gear. An axial sliding member is movably installed in the groove, and the forward drive helical gear and the reverse drive helical gear are movably installed on the drive shaft through the axial sliding member.

[0008] As a further embodiment of this utility model, the axial sliding member is one of a single key, a double key, a spline, a linear guide motion unit, a cross roller guide, or a linear sleeve.

[0009] As a further improvement of this utility model: a connecting cavity is provided on the inner wall of both the forward active helical gear and the reverse active helical gear, and the backlash-eliminating spring is located in the connecting cavity.

[0010] As a further embodiment of this invention: the starting angle of the teeth of the positive driving helical gear is γ1, and the starting angle of the teeth of the negative driving helical gear is γ2, the relationship between γ1 and γ2 is as follows:

[0011] γ2=γ1+ .

[0012] As a further improvement of this utility model, the driven helical gear, the forward driving helical gear, and the reverse driving helical gear are all helical gears.

[0013] Compared with the prior art, the present invention has the following beneficial effects:

[0014] 1. This utility model achieves the backlash elimination function of gear transmission by adopting an axial relative motion constraint method. That is, on the same transmission shaft, forward and reverse rotation are driven by different gears, and the two gears are arranged on the same shaft. Utilizing the concept of force closure, while power is transmitted through different transmission paths, a constraint relationship is established between the two paths of forward and reverse power transmission, so that the helical gear tooth profiles on the two power transmission paths always remain meshed. This eliminates the transmission backlash during the forward and reverse rotation switching process. This design improves the stability and backlash elimination effect of the helical gear transmission device that synchronously eliminates backlash.

[0015] 2. This utility model achieves the backlash elimination function independently outside the power transmission path. Due to the adoption of adaptive axial motion, the backlash elimination function is unaffected by the transmitted force (torque) and the elastic force of the backlash elimination spring. This design ensures reliability while force-sealing the gear transmission mechanism, enabling backlash-free gear transmission even with gears of ordinary machining precision. This maintains the same transmission stiffness as traditional gear transmissions, is no longer limited by spring elastic force, and fully inherits the advantages of traditional gear transmissions. This solution can be applied to all traditional gear transmission structures requiring backlash elimination, directly updating traditional mechanical equipment. It allows traditional mechanical equipment to achieve backlash-free gear transmission with minimal and economical adjustments, improving the practicality of this synchronous backlash elimination helical gear transmission device. Attached Figure Description

[0016] The present invention will be further explained below with reference to the accompanying drawings and embodiments:

[0017] Figure 1 This is a three-dimensional structural diagram of the present invention;

[0018] Figure 2 This is a cross-sectional view of the present invention along the direction of the drive shaft;

[0019] Figure 3 This is a cross-sectional view of the positive driving helical gear in this utility model;

[0020] Figure 4 This is a cross-sectional view of the reverse driving helical gear in this utility model;

[0021] Figure 5 This is a top view of the present invention;

[0022] Figure 6 This is a schematic diagram of the motion and power transmission of this utility model. Figure 1 ;

[0023] Figure 7 This is a schematic diagram of the motion and power transmission of this utility model. Figure 2 .

[0024] Explanation of reference numerals in the attached figures:

[0025] 1. Driven drive shaft; 2. Driven drive shaft; 3. Driven helical gear; 4. Forward driving helical gear; 5. Reverse driving helical gear; 6. Slide groove; 7. Slot; 8. Axial sliding component; 9. Connecting cavity; 10. Backlash-eliminating spring. Detailed Implementation

[0026] The following will be combined with the appendix Figures 1 to 7 The technical solution of this utility model has been clearly and completely described. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.

[0027] This utility model provides an improved helical gear transmission device for synchronously eliminating backlash, such as... Figures 1-7 As shown, the drive shaft includes two sets of driven drive shafts 1 and 2 that are linked together. A driven helical gear 3 is fixedly installed in the middle of the driven drive shaft 1. A forward driving helical gear 4 and a reverse driving helical gear 5 that mesh with the driven helical gear 3 are movably installed on the drive drive shaft 2. A backlash-eliminating spring 10 is sleeved in the middle of the drive drive shaft 2. The two ends of the backlash-eliminating spring 10 are connected to the inner walls of the forward driving helical gear 4 and the reverse driving helical gear 5, respectively. The backlash-eliminating spring 10 is axially arranged and applies axial elastic force. The forward driving helical gear 4 and the reverse driving helical gear 5 maintain overall linkage through the backlash-eliminating spring 10. The relative positional relationship between the forward driving helical gear 4 and the reverse driving helical gear 5 is adjusted by adaptive axial movement to eliminate the transmission backlash between the driven helical gear 3 and the forward driving helical gear 4 and the reverse driving helical gear 5.

[0028] This invention employs a coaxial, synchronous, parallel transmission concept, differing from existing technologies that use rotational methods to eliminate backlash. This invention uses axial relative motion constraints to achieve backlash elimination in gear transmission. Even on the same transmission shaft, forward and reverse rotation are driven by different gears, both arranged on the same shaft. Utilizing the concept of force closure, a constraint relationship is established between the two power transmission paths while power is transmitted through different paths. By rigidly constraining the relative positional relationship of the different transmission components in forward and reverse rotation, the backlash of the gear transmission is eliminated. Furthermore, this invention implements the backlash elimination function independently outside the power transmission path, ensuring reliability while force-closing the gear transmission mechanism. This allows for backlash-free gear transmission even when using gears with ordinary machining precision, maintaining the same transmission stiffness as traditional gear transmissions and no longer being limited by spring elasticity.

[0029] The coaxial parallel transmission concept adopted in this utility model can be implemented on the driving shaft of a gear transmission or on the driven shaft of a gear transmission. However, in order to reduce the spatial structure size, it is recommended to implement it on the driving shaft of a gear transmission.

[0030] See appendix Figure 1 - Appendix Figure 2 The outer wall of the drive shaft 2 is provided with a groove 6, and the inner walls of the positive drive helical gear 4 and the negative drive helical gear 5 are both provided with grooves 7. An axial sliding member 8 is movably installed in the groove 6. The positive drive helical gear 4 and the negative drive helical gear 5 are movably installed on the drive shaft 2 through the axial sliding member 8.

[0031] In this embodiment: In order to facilitate the installation of the forward active helical gear 4 and the reverse active helical gear 5 and ensure their adaptive axial adjustment, a mutually cooperating sliding groove 6 and slotted structure 7 are designed.

[0032] See appendix Figure 2 Both the forward driving helical gear 4 and the reverse driving helical gear 5 have a connecting cavity 9 on their inner walls, and the backlash-eliminating spring 10 is located in the connecting cavity 9.

[0033] In this embodiment: during adaptive circumferential adjustment, in order to reduce the relative distance between the positive driving helical gear 4 and the negative driving helical gear 5, improve the fit, and place the backlash-eliminating spring 10 inside it, a connecting cavity 9 structure is provided, and the backlash-eliminating spring 10 is axially arranged and applies axial elastic force.

[0034] See appendix Figure 3 - Appendix Figure 5 The initial angle of the teeth of the forward driving helical gear 4 is γ1, and the initial angle of the teeth of the reverse driving helical gear 5 is γ2. The relationship between γ1 and γ2 is as follows:

[0035] γ2=γ1+ .

[0036] In this embodiment, the tooth positions of the forward driving helical gear 4 and the reverse driving helical gear 5 must ensure a certain geometric relationship in order to successfully achieve a geometrically closed structure. If the starting angle of the teeth of the forward driving helical gear 4 is γ1, then the starting angle of the teeth of the reverse driving helical gear 5 is obtained by the above formula and marked as γ2.

[0037] The starting angle is defined as the angle between the positioning surface of the axial sliding member 8, or the torque transmission plane, which is defined as zero degrees, and the center line of the first tooth of the helical gear at the twelve o'clock direction.

[0038] Let the helix angle of the helical gear be α, the tooth width of the positive driving helical gear 4 be b, the distance between the end faces of the positive driving helical gear 4 and the negative driving helical gear 5 be δ, and the pitch circle diameter of the end faces of the positive driving helical gear 4 and the negative driving helical gear 5 be r.

[0039] See appendix Figure 1 - Appendix Figure 2 The driven helical gear 3, the forward driving helical gear 4, and the reverse driving helical gear 5 are all helical gears.

[0040] In this embodiment: in order to maintain the meshing relationship of linkage, and to make the forward driving helical gear 4 and the reverse driving helical gear 5 achieve the gear transmission backlash elimination function by means of "axial movement", and to constrain the axial movement of the forward driving helical gear 4 and the reverse driving helical gear 5, and finally cooperate with the driven helical gear 3 to form a geometric force closed structure by using the helical tooth surface, the driven helical gear 3, the forward driving helical gear 4 and the reverse driving helical gear 5 are all helical gear structures.

[0041] See appendix Figure 2 The axial sliding element 8 is one of the following: single key, double key, spline, linear guide motion unit, cross roller guide or linear sleeve.

[0042] The recommended structural forms and fit tolerances for the axial sliding element 8 are shown in the table below:

[0043]

[0044] The working principle of this utility model is as follows: When an external power source is connected to the drive shaft 2 and the drive shaft 2 rotates clockwise, power flows in through the drive shaft 2, passes through the axial sliding member 8, and is transmitted to the positive drive helical gear 4. Then, through the meshing of the positive drive helical gear 4 and the driven helical gear 3, the motion and power are transmitted to the driven helical gear 3. Since the driven helical gear 3 is fixed to the driven drive shaft 1, the motion and power are thus transmitted from the drive shaft 2 to the driven drive shaft 1.

[0045] During this period, the reverse driving helical gear 5 does not participate in the transmission of motion and power, but the elastic force F of the backlash-eliminating spring 10 is... k Under the action of the reverse driving helical gear 5, the tooth profile of the reverse driving helical gear 3 on the non-transmission side remains engaged with the tooth profile of the driven helical gear 3, so as to be ready to transmit motion and power when the driving shaft 2 rotates counterclockwise.

[0046] At this time, the elastic force F of the gap-eliminating spring 10 kTogether with the transmission tooth profile (green dashed line) of the positive driving helical gear 4 and the non-transmission tooth profile (red dashed line) of the reverse driving helical gear 5, a geometric force closed structure is formed, so that while the transmission tooth profile of the positive driving helical gear 4 meshes with the driven helical gear 3 to transmit motion and power, the tooth profile of the reverse driving helical gear 5 and the non-transmission side tooth profile of the driven helical gear 3 are always meshed.

[0047] When an external power source is connected to the drive shaft 2 and the drive shaft 2 rotates counterclockwise, power transmission is as follows: Figure 7 As shown by the green arrow in the middle. Power flows in through the drive shaft 2, passes through the axial sliding member 8 and is transmitted to the reverse drive helical gear 5. Then, through the meshing of the reverse drive helical gear 5 and the driven helical gear 3, the motion and power are transmitted to the driven helical gear 3. Since the driven helical gear 3 is fixed to the driven drive shaft 1, the motion and power are thus transmitted from the drive shaft 2 to the driven drive shaft 1.

[0048] At this point, the forward-driving helical gear 4 does not participate in the transmission of motion and power, but the elastic force F of the backlash-eliminating spring 10... k Under the action of the driving helical gear 4, the tooth profile of the driving helical gear 3 on the non-transmission side always remains meshed, so as to be ready at all times to transmit motion and power when the driving shaft 2 rotates clockwise.

[0049] At this time, the elastic force F of the gap-eliminating spring 10 k The reverse active helical gear 5, along with the transmission tooth profile (green dashed line) and the non-transmission tooth profile (red dashed line) of the forward active helical gear 4, forms a geometrically closed structure. This allows the transmission tooth profile of the reverse active helical gear 5 to mesh with the driven helical gear 3 to transmit motion and power, while the tooth profile of the forward active helical gear 4 meshes with the non-transmission side tooth profile of the driven helical gear 3.

[0050] The above description of the disclosed embodiments enables those skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and inventive features disclosed herein.

Claims

1. A synchronous gear transmission with a clearance-free helical gearing, comprising two sets of interlocking driven transmission shafts (1) and driving transmission shafts (2), characterized in that: The middle part of the driven transmission shaft (1) is fixedly provided with a driven bevel gear (3), and the driven bevel gear (3) is meshed with a positive driven bevel gear (4) and a reverse driven bevel gear (5) movably arranged on the driving transmission shaft (2); The middle part of the driving transmission shaft (2) is sleeved with an anti-backlash spring (10), the two ends of the anti-backlash spring (10) are connected with the inner walls of the positive driven bevel gear (4) and the reverse driven bevel gear (5) respectively, and the anti-backlash spring (10) is arranged in an axial direction and exerts an axial elastic force. The positive driven bevel gear (4) and the reverse driven bevel gear (5) are kept in overall linkage through the anti-backlash spring (10), the relative position relationship between the positive driven bevel gear (4) and the reverse driven bevel gear (5) is adjusted through self-adaptive axial movement, and the transmission backlash between the driven bevel gear (3) and the positive driven bevel gear (4) and the reverse driven bevel gear (5) is eliminated. The starting angle of the gear teeth of the positive driven bevel gear (4) is γ1, and the starting angle of the gear teeth of the reverse driven bevel gear (5) is γ2.

2. A synchronous backlash-free helical gear transmission according to claim 1, characterized in that A sliding groove (6) is formed in the outer wall of the driving transmission shaft (2), and a slot (7) is formed in the inner wall of each of the positive driven bevel gear (4) and the reverse driven bevel gear (5), an axial sliding member (8) is movably arranged in the sliding groove (6), and the positive driven bevel gear (4) and the reverse driven bevel gear (5) are movably arranged on the driving transmission shaft (2) through the axial sliding member (8).

3. A synchronous backlash-cancelling helical gear transmission according to claim 2, characterised in that: The axial sliding member (8) is one of a single key, a double key, a spline, a linear guide rail movement unit, a cross roller guide rail, and a linear sliding sleeve.

4. A synchronous backlash-free helical gearing according to any one of claims 1-3, characterized in that: A connecting cavity (9) is formed in the inner wall of each of the positive driven bevel gear (4) and the reverse driven bevel gear (5), and the anti-backlash spring (10) is located in the connecting cavity (9).

5. A synchronous backlash-free helical gear transmission according to any one of claims 1-3, characterized in that: γ1 and γ2 are related as follows: γ2 = γ1 + 0.5 ; If the starting angle of the gear teeth of the positive driven bevel gear (4) is γ1 and the starting angle of the gear teeth of the reverse driven bevel gear (5) is obtained from the above formula and marked as γ2, the helix angle of the bevel gear is α, the tooth width of the positive driven bevel gear (4) is b, the distance between the end faces of the positive driven bevel gear (4) and the reverse driven bevel gear (5)) is δ, and the diameter of the pitch circle of the bevel gear end faces of the positive driven bevel gear (4) and the reverse driven bevel gear is r.

6. A synchronous backlash-free helical gear transmission according to claim 1, characterized in that: The driven bevel gear (3), the positive driven bevel gear (4), and the reverse driven bevel gear (5) are all bevel gears.

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