Helical gear transmission device capable of synchronously eliminating clearance

Abstract

The invention discloses a bevel gear transmission device capable of synchronously eliminating a gap, which belongs to the technical field of transmission gears and comprises a driven transmission shaft and a driving transmission shaft which are in linkage fit, and a driven bevel gear is fixedly mounted in the middle of the driven transmission shaft. A forward driving bevel gear and a reverse driving bevel gear which are meshed with the driven bevel gear are movably mounted on the driving transmission shaft; the middle of the driving transmission shaft is sleeved with an anti-backlash spring, and the two ends of the anti-backlash spring are connected with the inner wall of the forward driving bevel gear and the inner wall of the reverse driving bevel gear respectively. The forward driving bevel gear and the reverse driving bevel gear are movably installed on the driving transmission shaft through an axial sliding piece. Self-adaptive axial movement is adopted, so that the anti-backlash function is not affected by transmission force and elastic force of the anti-backlash spring. The scheme can be applied to all traditional gear transmission structures with anti-backlash requirements, gear anti-backlash transmission is achieved under the condition that traditional mechanical equipment is minimum in adjustment and most economical, and practicability is improved through the design.

Description

Technical Field

[0001] The invention relates to the technical field of transmission gears, in particular to a helical gear transmission device capable of synchronously eliminating backlash. Background Art

[0002] Gear transmission is often used in industrial manufacturing. Ordinary gears mesh with point contact, which creates gaps during gear transmission. These gaps can cause abnormal noises, and even small gaps can be amplified when transmitted to the end of the machine, causing noticeable vibration. Currently available anti-backlash gears can eliminate the tooth side clearance in gear transmission. The driven wheel of a pair of gears is made into two thin pieces, one of which is fixed to the shaft and the other is mounted on the hub of the gear sleeve. A tension spring is installed between the gear sleeve and the gear disc. This structure utilizes the tension of the tension spring to make the left side of the gear disc teeth and the right side of the gear sleeve teeth close to the left and right sides of the tooth groove of the driving gear, respectively. This staggered tooth structure eliminates tooth side clearance, and no backlash error occurs during reverse rotation.

[0003] Chinese utility model patent application CN214367681U discloses a gear transmission device for eliminating gear backlash. The device comprises a forward and reverse anti-backlash gear with equal teeth and diameter, a target gear, a gear shaft, a forward flywheel, and a reverse flywheel. The forward and reverse flywheels are spaced apart and sleeved on the gear shaft. The forward anti-backlash gear sleeves onto the forward flywheel, while the reverse anti-backlash gear sleeves onto the reverse flywheel. A tension spring is provided between the forward and reverse anti-backlash gears to induce the forward and reverse anti-backlash gears to rotate in opposite directions. The utility model utilizes a tension spring disposed between the forward and reverse anti-backlash gears to clamp the forward and reverse anti-backlash gears against the target gear. The tension spring pulls two adjacent teeth of the forward and reverse anti-backlash gears against the sides of the same tooth on the target gear. Regardless of whether the gear shaft rotates forward or reverse, one gear always engages the target gear, thereby eliminating backlash in the gear transmission.

[0004] However, the circumferential structural space size of the gear transmission device disclosed above is large, and the anti-backlash effect is limited by the size of the spring elastic force. After long-term use, as the spring elasticity decays, the anti-backlash effect is greatly reduced, and the transmission stiffness is limited by the size of the transmitted power. Summary of the Invention

[0005] The purpose of the present invention is to provide a helical gear transmission device with synchronous clearance elimination in order to solve the problems that the circumferential structural space size of the existing gear transmission device is large, the clearance elimination effect is limited by the size of the spring elastic force, the clearance elimination effect is greatly reduced as the spring elasticity decays after long-term use, and the transmission stiffness is limited by the size of the transmitted power.

[0006] To achieve the above-mentioned purpose, the technical solution of the present invention is: a helical gear transmission device for synchronously eliminating clearance, comprising two groups of driven transmission shafts and active transmission shafts that cooperate with each other, the middle part of the driven transmission shaft being fixedly mounted with a driven helical gear, the active transmission shaft being movably mounted with a forward driving helical gear and a reverse driving helical gear that mesh with the driven helical gear; the middle part of the active transmission shaft is sleeved with an anti-backlash spring, the two ends of the anti-backlash spring are respectively connected to the inner walls of the forward driving helical gear and the reverse driving helical gear, the anti-backlash 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 anti-backlash spring, and the relative position relationship between the forward driving helical gear and the reverse driving helical gear is adjusted by adaptive axial movement to eliminate transmission side clearance between the driven helical gear and the forward driving helical gear and the reverse driving helical gear.

[0007] As a further solution of the present invention: a slide groove is provided on the outer wall of the active transmission shaft, and a groove is provided on the inner wall of the forward active helical gear and the reverse active helical gear. An axial sliding member is movably installed in the slide groove, and the forward active helical gear and the reverse active helical gear are movably installed on the active transmission shaft through the axial sliding member.

[0008] As a further solution of the present invention: 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 solution of the present invention: a connecting cavity is formed on the inner wall of the forward driving helical gear and the reverse driving helical gear, and the anti-backlash spring is located in the connecting cavity.

[0010] As a further solution of the present invention: the starting angle of the gear teeth of the forward driving helical gear is γ1, and the starting angle of the gear teeth of the reverse driving helical gear is γ2. The relationship between γ1 and γ2 is: γ2=γ1+ .

[0011] As a further solution of the present invention, the driven helical gear, the forward driving helical gear and the reverse driving helical gear are all helical gears.

[0012] Compared with the prior art, the present invention has the following beneficial effects: 1. The present invention realizes the gear transmission backlash elimination function by adopting the method of axial relative motion constraint. That is to say, on the same transmission shaft, the forward and reverse rotations are driven by different gears, and the two gears are arranged on the same shaft. By utilizing the force closure concept, while the power is transmitted through different transmission paths, a constraint relationship is established between the two paths of positive and reverse power transmission. This ensures that the tooth profiles of the helical gears on the two power transmission paths always remain in meshing, thereby eliminating the occurrence of transmission side clearance during the forward and reverse switching process of the gears. This design improves the stability and backlash elimination effect of the helical gear transmission device with synchronous backlash elimination.

[0013] 2. The present invention implements the backlash elimination function independently outside the power transmission path. Due to the use of adaptive axial motion, the backlash elimination function is unaffected by the transmission force (torque) and the elastic force of the backlash elimination spring. This design ensures reliability while also sealing the gear transmission mechanism. This allows for gear backlash elimination using gears of standard machining precision, maintaining transmission stiffness consistent with traditional gear transmissions and freeing them from the constraints of spring elastic force, thus fully inheriting the advantages of traditional gear transmissions. This solution can be applied to all traditional gear transmission structures requiring backlash elimination, enabling direct upgrades to traditional mechanical equipment, enabling gear backlash elimination with minimal and most economical adjustments. This design enhances the practicality of this synchronous backlash elimination helical gear transmission. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] The present invention will be further explained below in conjunction with the accompanying drawings and examples: Figure 1 It is a three-dimensional structural diagram of the present invention; Figure 2 is a cross-sectional view of the present invention along the active transmission shaft direction; Figure 3 is a cross-sectional view of the forward driving helical gear of the present invention; Figure 4 is a cross-sectional view of the reverse driving helical gear of the present invention; Figure 5 is a top view of the present invention; Figure 6 This is a schematic diagram of the motion and power transmission of the present invention Figure 1 ; Figure 7 This is a schematic diagram of the motion and power transmission of the present invention Figure 2 .

[0015] Description of reference numerals: 1. Driven transmission shaft; 2. Driving transmission shaft; 3. Driven helical gear; 4. Forward driving helical gear; 5. Reverse driving helical gear; 6. Slide; 7. Slot; 8. Axial sliding member; 9. Connecting cavity; 10. Anti-backlash spring. DETAILED DESCRIPTION

[0016] The following will be combined with the Figures 1 to 7 The technical solutions of the present invention are clearly and completely described. Obviously, the embodiments described are only some embodiments of the present invention, not all embodiments. All other embodiments derived by persons of ordinary skill in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0017] The present invention provides a helical gear transmission device with synchronous clearance elimination through improvement. Figure 1-Figure 7 As shown, it includes two groups of driven transmission shafts 1 and driving transmission shafts 2 that are linked and matched. A driven bevel gear 3 is fixedly installed in the middle of the driven transmission shaft 1, and a forward driving bevel gear 4 and a reverse driving bevel gear 5 that are engaged with the driven bevel gear 3 are movably installed on the driving transmission shaft 2; an anti-backlash spring 10 is sleeved in the middle of the driving transmission shaft 2, and the two ends of the anti-backlash spring 10 are respectively connected to the inner walls of the forward driving bevel gear 4 and the reverse driving bevel gear 5. The anti-backlash spring 10 is axially arranged and applies axial elastic force; the forward driving bevel gear 4 and the reverse driving bevel gear 5 maintain overall linkage through the anti-backlash spring 10, and the relative position relationship between the forward driving bevel gear 4 and the reverse driving bevel gear 5 is adjusted through adaptive axial movement to eliminate the transmission side clearance between the driven bevel gear 3 and the forward driving bevel gear 4 and the reverse driving bevel gear 5.

[0018] This invention adopts the transmission concept of coaxial synchronous parallel connection. Different from the prior art that uses rotation to eliminate backlash, the present invention adopts the method of axial relative motion constraint to realize the gear transmission backlash elimination function. Even on the same transmission shaft, the forward and reverse rotations are driven by different gears, and the two gears are arranged on the same shaft. By utilizing the force closure concept, while the power is transmitted through different transmission paths, a constraint relationship is established between the two paths of positive and reverse power transmission. By rigidly constraining the relative position relationship of different transmission parts for forward and reverse rotations, the function of eliminating the side clearance of the gear transmission is realized. At the same time, this invention realizes the backlash elimination function independently outside the power transmission path, ensuring reliability while making the gear transmission mechanism force-closed, so that when using ordinary processing precision gears, gear backlash elimination transmission can be realized, so that the transmission stiffness is consistent with the traditional gear transmission and is no longer limited by the spring elastic force.

[0019] The coaxial parallel transmission concept adopted by this invention can be implemented on the driving shaft of the gear transmission or on the driven shaft of the gear transmission. However, in order to reduce the spatial structure size, it is recommended to implement it on the driving shaft of the gear transmission.

[0020] See attached Figure 1 -Attached Figure 2A slide groove 6 is provided on the outer wall of the active transmission shaft 2, and a groove 7 is provided on the inner wall of the forward active helical gear 4 and the reverse active helical gear 5. An axial sliding member 8 is movably installed in the slide groove 6, and the forward active helical gear 4 and the reverse active helical gear 5 are movably installed on the active transmission shaft 2 through the axial sliding member 8.

[0021] In this embodiment, in order to facilitate the installation of the forward driving helical gear 4 and the reverse driving helical gear 5 and ensure their adaptive axial adjustment, mutually cooperating sliding grooves 6 and slots 7 are designed.

[0022] See attached Figure 2 A connecting cavity 9 is provided on the inner wall of the forward driving helical gear 4 and the reverse driving helical gear 5 , and the anti-backlash spring 10 is located in the connecting cavity 9 .

[0023] In this embodiment: during adaptive circumferential adjustment, in order to reduce the relative distance between the forward driving helical gear 4 and the reverse driving helical gear 5, improve the fit and allow the anti-backlash spring 10 to be located therein, a connecting cavity 9 structure is provided, and the anti-backlash spring 10 is axially arranged and applies an axial elastic force.

[0024] See attached Figure 3 -Attached Figure 5 , the starting angle of the gear teeth of the forward driving helical gear 4 is γ1, and the starting angle of the gear teeth of the reverse driving helical gear 5 is γ2. The relationship between γ1 and γ2 is: γ2=γ1+ .

[0025] In this embodiment, the teeth of the forward driving helical gear 4 and the reverse driving helical gear 5 must maintain a certain geometric relationship to ensure 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 using the above formula and is labeled γ2.

[0026] The definition of the starting angle is the angle between the positioning surface of the axial sliding member 8, or the torque transmission plane, which is set to zero degrees, and the center line of the first tooth in the twelve o'clock direction of the helical gear.

[0027] Assume that the helical angle of the helical gear is α, the tooth width of the forward driving helical gear 4 is b, the end face distance between the forward driving helical gear 4 and the reverse driving helical gear 5 is δ, and the pitch circle diameter of the helical gear end faces of the forward driving helical gear 4 and the reverse driving helical gear 5 is r.

[0028] See attached Figure 1 -Attached Figure 2 , the driven helical gear 3, the forward driving helical gear 4 and the reverse driving helical gear 5 are all helical gears.

[0029] In this embodiment, in order to maintain the linked meshing relationship, the forward driving helical gear 4 and the reverse driving helical gear 5 are made to achieve the gear transmission backlash elimination function by means of "axial movement", and the axial movement of the forward driving helical gear 4 and the reverse driving helical gear 5 is mutually constrained, and finally cooperates with the driven helical gear 3 to form a geometric force-sealed structure using the helical tooth surfaces. Therefore, the driven helical gear 3, the forward driving helical gear 4 and the reverse driving helical gear 5 are all helical gear structures.

[0030] See attached Figure 2 The axial sliding member 8 is one of a single key, a double key, a spline, a linear guide motion unit, a cross roller guide or a linear sleeve.

[0031] The structural forms and recommended tolerances of the axial sliding member 8 are as follows:

[0032] The working principle of the present invention is as follows: When an external power source is connected to the driving transmission shaft 2 and the driving transmission shaft 2 rotates clockwise, power flows through the driving transmission shaft 2, is transmitted to the forward driving helical gear 4 via the axial slide 8, and then, through the meshing transmission of the forward driving helical gear 4 and the driven helical gear 3, the motion and power are transmitted to the driven helical gear 3. Because the driven helical gear 3 is fixed to the driven transmission shaft 1, the motion and power are transmitted from the driving transmission shaft 2 to the driven transmission shaft 1.

[0033] During this period, the reverse driving helical gear 5 does not participate in the transmission of motion and power, but under the elastic force F of the anti-backlash spring 10 k Under the action of the reverse driving helical gear 5, the tooth profile of the driven helical gear 3 on the non-transmission side is always kept in meshing, so as to prepare for the transmission of motion and power when the driving transmission shaft 2 rotates counterclockwise.

[0034] At this time, the elastic force F of the anti-backlash spring 10 k , forming a geometric force-enclosed structure with the transmission tooth profile (green dotted line) of the forward driving helical gear 4 and the non-transmission tooth profile (red dotted line) of the reverse driving helical gear 5, so that while the transmission tooth profile of the forward driving helical gear 4 is meshing with the driven helical gear 3 to transmit motion and power, the tooth profile of the reverse driving helical gear 5 is always meshing with the non-transmission side tooth profile of the driven helical gear 3.

[0035] When the external power source is connected to the active transmission shaft 2 and the active transmission shaft 2 rotates counterclockwise, the power transmission is as follows Figure 7 As shown by the green arrow in the middle, power flows in through the driving transmission shaft 2, is transmitted to the reverse driving helical gear 5 through the axial slide 8, and then the reverse driving helical gear 5 and the driven helical gear 3 are meshed and transmitted, transmitting motion and power to the driven helical gear 3. Since the driven helical gear 3 is fixed to the driven transmission shaft 1, the motion and power are transmitted from the driving transmission shaft 2 to the driven transmission shaft 1.

[0036] At this time, the positive driving helical gear 4 does not participate in the transmission of motion and power, but under the elastic force F of the anti-backlash spring 10 k Under the action of the positive driving helical gear 4, the tooth profile of the driven helical gear 3 on the non-transmission side is always kept in meshing, so as to prepare for the transmission of motion and power when the active transmission shaft 2 rotates clockwise.

[0037] At this time, the elastic force F of the anti-backlash spring 10 k , forming a geometric force-enclosed structure with the transmission tooth profile of the reverse driving helical gear 5 (green dotted line) and the non-transmission tooth profile of the forward driving helical gear 4 (red dotted line), so that while the transmission tooth profile of the reverse driving helical gear 5 is meshing with the driven helical gear 3 to transmit motion and power, the tooth profile of the forward driving helical gear 4 remains meshing with the non-transmission side tooth profile of the driven helical gear 3.

[0038] The above description of the disclosed embodiments will enable one skilled in the art to implement or use the present invention. Various modifications to these embodiments will be readily apparent to one 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 limited to the embodiments shown herein but is to be construed in the widest manner consistent with the principles and inventive features disclosed herein.

Claims

1. A helical gear transmission device for synchronously eliminating backlash, comprising two sets of linked driven transmission shafts (1) and active transmission shafts (2), characterized in that: A driven helical gear (3) is fixedly mounted on the middle portion of the driven transmission shaft (1), and a forward driving helical gear (4) and a reverse driving helical gear (5) meshing with the driven helical gear (3) are movably mounted on the driving transmission shaft (2); The middle part of the active transmission shaft (2) is sleeved with an anti-backlash spring (10), and the two ends of the anti-backlash spring (10) are respectively connected to the inner walls of the forward active helical gear (4) and the reverse active helical gear (5), and the anti-backlash spring (10) is axially arranged and applies an axial elastic force; The forward driving helical gear (4) and the reverse driving helical gear (5) maintain overall linkage through the anti-backlash spring (10), and the relative position relationship between the forward driving helical gear (4) and the reverse driving helical gear (5) is adjusted through adaptive axial movement to eliminate transmission side clearances between the driven helical gear (3) and the forward driving helical gear (4) and the reverse driving helical gear (5).

2. The helical gear transmission device with synchronous clearance elimination according to claim 1, characterized in that: A slide groove (6) is provided on the outer wall of the active transmission shaft (2), and a groove (7) is provided on the inner wall of each of the forward active helical gear (4) and the reverse active helical gear (5). An axial sliding member (8) is movably installed in the slide groove (6), and the forward active helical gear (4) and the reverse active helical gear (5) are movably installed on the active transmission shaft (2) via the axial sliding member (8).

3. The helical gear transmission device with synchronous backlash elimination according to claim 2, characterized in that: The axial sliding member (8) is one of a single key, a double key, a spline, a linear guide motion unit, a cross roller guide or a linear sleeve.

4. A helical gear transmission device with synchronous backlash elimination according to any one of claims 1 to 3, characterized in that: A connecting cavity (9) is provided on the inner walls of the forward driving helical gear (4) and the reverse driving helical gear (5), and the backlash eliminating spring (10) is located in the connecting cavity (9).

5. A helical gear transmission device with synchronous backlash elimination according to any one of claims 1 to 3, characterized in that: The starting angle of the gear teeth of the forward driving helical gear (4) is γ1, and the starting angle of the gear teeth of the reverse driving helical gear (5) is γ2. The relationship between γ1 and γ2 is: γ2=γ1+ 。 6. The helical gear transmission device with synchronous backlash elimination according to claim 1, characterized in that: The driven helical gear (3), the forward driving helical gear (4) and the reverse driving helical gear (5) are all helical gears.

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