CN101704134B - Variable-angle reversing mechanism on face gear shaping machine dividing tooth transmission chain - Google Patents

Abstract

The invention provides a variable-angle reversing mechanism on face gear shaping machine dividing tooth transmission chain, belonging to the technical field of mechanical transmission. The included angle between the output shaft of the variable-angle reversing mechanism and the gear shaping cutter axis of rotation can be changed between 0 degree to 90 degrees, thus solving the problem of the realization of gear shaping machining under the condition of not changing the reversing mechanism of the orthogonal unbiased face gear and nonorthogonal unbiased face gear with different angles. In the invention, in the premise of not increasing manufacturing cost, not changing the cutter and not increasing the manufacturing difficulty, the problem of the manufacturing of the orthogonal unbiased face gear and nonorthogonal unbiased face gear with different angles by the same reversing mechanism in the processing of the gear shaping, thus having dramatic substantial characteristics and prominent improvement.

Description

Variable Angle Reversing Mechanism on Split Gear Transmission Chain of Face Gear Shaping Machine Tool

technical field

The invention relates to a variable-angle reversing mechanism on a split-tooth transmission chain of a face gear shaping machine tool, which is one of the key transmission mechanisms of a face gear shaping machine tool and belongs to the field of mechanical transmission.

Background technique

Face gear transmission refers to the meshing of cylindrical gear and bevel gear to realize the transmission between spatially intersecting or interlaced axes. According to the relationship between the two axes of the cylindrical gear and the face gear, the face gear transmission can be divided into four types: orthogonal non-offset, non-orthogonal non-offset, orthogonal offset and non-orthogonal offset.

When the rotation axis of the cylindrical gear intersects and is perpendicular to the rotation axis of the face gear, the face gear transmission is called an orthogonal non-offset face gear transmission, as shown in Figure 1; when the rotation axis of the cylindrical gear and the rotation axis of the face gear When they intersect but are not perpendicular, the face gear transmission is called non-orthogonal non-offset face gear transmission, as shown in Figure 2; It is an orthogonal offset face gear transmission, as shown in Figure 3; when the rotational axis of the cylindrical gear and the rotational axis of the face gear intersect and are not perpendicular, the face gear transmission is called a non-orthogonal offset face gear transmission. As shown in Figure 4.

Compared with bevel gear transmission, face gear transmission has the following advantages:

(1) Since the gear meshing with the face gear is an involute cylindrical gear, its axial movement error has no influence on the transmission performance, and the influence of other directions is also very small, so there is no need for error-proof design. In the bevel gear transmission, the axial error will cause serious partial load, so the important bevel gear transmission must be designed for error prevention.

(2) When the gear meshing with the face gear is a spur gear, there is no axial force on the spur gear, the support is simple, and the structure occupies a small space. In the bevel gear transmission, the support is complicated due to the axial force, and the structure takes up a lot of space.

(3) The coincidence degree of face gear transmission is larger than that of bevel gear transmission, which can reach 1.6-1.8 under no load, and its coincidence degree will be even greater under load.

(4) Point contact surface gear transmission is still fixed ratio transmission, while the transmission ratio of point contact bevel gear transmission fluctuates within a certain range, so the vibration and noise of surface gear transmission are smaller than bevel gear transmission.

Face gear machining method is one of the main contents of face gear transmission research. Gear shaping is one of the main contents of research on face gear cutting. The principle of gear shaping processing of face gears is the same as that of face gear meshing transmission, that is, the cylindrical gear in the face gear meshing transmission is replaced by a gear shaping tool, and the gear shaping processing of face gears can be realized. As shown in Fig. 1 orthogonal non-offset face gear transmission and Fig. 2 non-orthogonal non-offset face gear transmission, when the orthogonal non-offset and non-orthogonal non-offset face gears are processed, the axis of rotation and the inserting The axis angles of the rotary axes of the gear cutters are different. When the existing face gear shaping machine tool processes orthogonal non-offset and non-orthogonal non-offset face gears with different angles, the reversing angle must be changed according to the angle between the rotation axis of the face gear and the rotation axis of the gear shaping tool. mechanism, so as to realize the machining of non-offset face gears with different angles. At present, it has not been realized that the gear shaping process of non-offset face gears with different angles can be performed without replacing the reversing mechanism. The function of the variable-angle reversing mechanism on the split-tooth transmission chain of the face gear shaping machine tool in the present invention is to realize the gear shaping process of non-offset face gears with different angles without changing the reversing mechanism. The main difficulty of the variable angle reversing mechanism is to realize the angle change between the axis of rotation of the gear workpiece on the machined surface and the axis of gear shaper without splitting the transmission chain.

Contents of the invention

The present invention is a variable-angle reversing mechanism on the split-tooth transmission chain of a face gear shaping machine tool, which mainly solves the problem of using orthogonal non-offset face gears and non-orthogonal non-offset face gears with different angles on a gear shaping machine tool without the need In the case of replacing the reversing mechanism with different shaft angles, the problem of realizing gear shaping processing.

The technical scheme of the variable angle reversing mechanism on the split gear transmission chain of the face gear shaping machine tool is composed of the main input shaft, the main input cylindrical gear, the first split input shaft, the first split cylindrical gear, the first split bevel gear, the first Reversing shaft, first reversing bevel gear, first converging bevel gear, second splitting input shaft, second splitting cylindrical gear, second splitting bevel gear, second reversing shaft, second reversing bevel gear, second Combination bevel gear, confluence output bevel gear, confluence shaft, output bevel gear, output reversing bevel gear and output shaft;

The first split input shaft and the second split input shaft are respectively parallel to the main input shaft, the first commutation shaft and the second commutation shaft are respectively perpendicular to the main input shaft, and the first commutation shaft and the second commutation shaft are collinear , the merging axis can be changed between 0° and 90° around the axis of the first reversing shaft or the second reversing shaft, and the output shaft and the merging axis are perpendicular to each other;

Wherein the first split cylindrical gear and the first split bevel gear are installed on the first split input shaft, the first reversing bevel gear and the first converging bevel gear are installed on the first reversing shaft, the main input cylindrical gear and the second A shunt cylindrical gear meshes, and the first shunt bevel gear meshes with the first reversing bevel gear;

Wherein the second split cylindrical gear and the second split bevel gear are installed on the second split input shaft, the second reversing bevel gear and the second converging bevel gear are installed on the second reversing shaft, the main input cylindrical gear and the first The second shunt cylindrical gear meshes, and the second shunt bevel gear meshes with the second reversing bevel gear;

Wherein the confluence output bevel gear and the output bevel gear are both installed on the confluence shaft, and the confluence output bevel gear meshes with the first confluence bevel gear and the second confluence bevel gear at the same time;

The output reversing bevel gear is installed on the output shaft, and the output reversing bevel gear meshes with the output bevel gear to realize the rotation of the output shaft;

Wherein the transmission ratio i ₂₄ of the main input cylindrical gear and the first split cylindrical gear is equal to the transmission ratio i ₂₁₀ of the main input cylindrical gear and the second split cylindrical gear; the transmission ratio i of the first split bevel gear and the first reversing bevel gear ₅₆ is equal to the transmission ratio i ₁₁₁₂ of the second split bevel gear and the second reversing bevel gear; the transmission ratio i ₈₁₅ of the first confluence bevel gear and the confluence output bevel gear is equal to the transmission ratio of the second confluence bevel gear and the confluence output bevel gear i ₁₄₁₅ are equal; the transmission ratio i ₂₄ of the main input cylindrical gear and the first split cylindrical gear, the transmission ratio i ₅₆ of the first split conical gear and the first reversing bevel gear, and the transmission of the first confluent bevel gear and the confluent output bevel gear The product of the ratio i ₈₁₅ and the transmission ratio i ₁₇₁₈ of the output bevel gear and the output reversing bevel gear is 1.

Utilizing the variable-angle reversing mechanism on the split-tooth transmission chain of the face gear shaper machine tool, it is possible to realize the shaping of orthogonal non-offset face gears and non-orthogonal non-offset face gears with different angles without changing the reversing mechanism Processing, get rid of the problem that the corresponding shaft angle reversing mechanism needs to be replaced when the non-offset face gears with different angles are processed in the past.

Description of drawings

Figure 1 is a schematic diagram of orthogonal non-offset face gear transmission.

Fig. 2 is a schematic diagram of non-orthogonal non-offset face gear transmission.

Fig. 3 is a schematic diagram of orthogonal offset face gear transmission.

Fig. 4 is a schematic diagram of non-orthogonal offset face gear transmission.

Fig. 5 is a schematic diagram when the output shaft of the variable-angle reversing mechanism is perpendicular to the rotation axis of the gear shaping tool. Among them, Figure 5-1 is the front view of the vertical output, and Figure 5-2 is the right sectional view of the vertical output.

Fig. 6 is a schematic diagram when the angle between the output shaft of the variable-angle reversing mechanism and the rotation axis of the gear shaping tool is γ. Figure 6-1 is a front view when the included angle is γ, and Figure 6-2 is a right sectional view when the included angle is γ.

Fig. 7 is a schematic diagram when the output shaft of the variable-angle reversing mechanism is parallel to the rotation axis of the gear shaping tool. Fig. 7-1 is a front view of parallel output, and Fig. 7-2 is a right sectional view of parallel output.

Label names in the figure: 1. Main input shaft, 2. Main input cylindrical gear, 3. First split input shaft, 4. First split cylindrical gear, 5. First split bevel gear, 6. First reversing cone Gear, 7. The first reversing shaft, 8. The first converging bevel gear, 9. The second splitting input shaft, 10. The second splitting cylindrical gear, 11. The second splitting bevel gear, 12. The second reversing bevel gear , 13 second reversing shaft, 14. second confluence bevel gear, 15. confluence output bevel gear, 16. confluence shaft, 17. output bevel gear, 18. output reversing bevel gear, 19. output shaft, 20. plug Tooth cutter axis.

Detailed ways

As shown in Fig. 5-Fig. 7, the equipment composed of the variable angle reversing mechanism on the split tooth transmission chain of the face gear shaping machine tool is as follows:

The main input cylindrical gear 2 is assembled on the main input shaft 1, and the rotation of the main input shaft 1 drives the main input cylindrical gear 2 to rotate; the main input cylindrical gear 2 meshes with the first split cylindrical gear 4 and the second split cylindrical gear 10, and the The main input cylindrical gear 2 drives the first split cylindrical gear 4 and the second split cylindrical gear 10 to rotate; the first split cylindrical gear 4 and the first split bevel gear 5 are installed on the first split input shaft 3 at the same time, and the second split cylindrical gear 10 and the second split bevel gear 11 are installed on the second split input shaft 9 at the same time, the rotation of the first split cylindrical gear 4 drives the first split input shaft 3 to rotate, thereby pushing the first split bevel gear 5 to rotate, and the second The rotation of the diverter cylindrical gear 10 drives the second diverter input shaft 9 to rotate, thereby pushing the second diverter bevel gear 11 to rotate; the first diverter bevel gear 5 meshes with the first reversing bevel gear 6, and the first diverter bevel gear 5 drives the second A reversing bevel gear 6 rotates; the second diverting bevel gear 11 meshes with the second reversing bevel gear 12, and the second diverting bevel gear 11 promotes the rotation of the second reversing bevel gear 12; the first reversing bevel gear 6 and the second reversing bevel gear A confluence bevel gear 8 is installed on the first reversing shaft 7 at the same time, because the rotation of the first reversing bevel gear 6 pushes the first reversing bevel gear 7 to rotate, thereby driving the first reversing bevel gear 8 to rotate; the second reversing bevel gear The gear 12 and the second converging bevel gear 14 are installed on the second reversing shaft 13 at the same time, because the rotation of the second reversing bevel gear 12 pushes the second reversing shaft 13 to rotate, thereby driving the second converging bevel gear 14 to rotate; A confluence bevel gear 8 and a second confluence bevel gear 14 mesh with the confluence output bevel gear 15 at the same time to push the confluence output bevel gear 15 to rotate; The rotation of the bevel gear 15 drives the confluence shaft 16 to rotate, thereby pushing the output bevel gear 17 to rotate; the output reversing bevel gear 18 is installed on the output shaft 19, and the output bevel gear 17 meshes with the output reversing bevel gear 18 to drive the output reversing The bevel gear 18 rotates; the motion output of the output shaft 19 is finally realized.

The first reversing shaft 7 is collinear with the second reversing shaft 13, and the confluent output bevel gear 15 can rotate around the common axis of the first reversing shaft 7 and the second reversing shaft 13, and the converging output conical gear 15 and the first Changes in the installation positions of the converging bevel gear 8 and the second converging bevel gear 14 realize the change of the angle between the output shaft 19 and the axis of the gear shaping tool, so as to meet the requirements of orthogonal non-offset face gears and non-orthogonal non-offsets at different angles Shaping processing requirements for face gears.

In order to realize this institution, the following conditions must be met:

1. The transmission ratio i ₂₄ of the main input spur gear 2 and the first split spur gear 4 is equal to the transmission ratio i ₂₁₀ of the main input spur gear 2 and the second split spur gear 10;

2. The transmission ratio i ₅₆ of the first splitting bevel gear 5 and the first reversing bevel gear 6 is equal to the transmission ratio i ₁₁₁₂ of the second splitting bevel gear 11 and the second reversing bevel gear 12;

3. The first reversing shaft 7 and the second reversing shaft 13 must be collinear;

4. The transmission ratio i ₈₁₅ of the first confluence bevel gear 8 and the confluence output bevel gear 15 is equal to the transmission ratio i ₁₄₁₅ of the second confluence bevel gear 14 and the confluence output bevel gear 15;

5. The transmission ratio i ₂₄ of the main input cylindrical gear 2 and the first split cylindrical gear 4, the transmission ratio i ₅₆ of the first split bevel gear 5 and the first reversing bevel gear 6, and the first converging bevel gear 8 and converging output conical gear The transmission ratio i ₈₁₅ of the gear 15 and the product of the transmission ratio i ₁₇₁₈ of the output bevel gear 17 and the output reversing bevel gear 18 are 1, namely

i ₂₄ i ₅₆ i ₈₁₅ i ₁₇₁₈ = 1

Under the condition that the transmission ratio i ₂₄ i ₅₆ i ₈₁₅ i ₁₇₁₈ = 1, the design steps of a certain variable angle reversing mechanism

1. Design the transmission ratio of the main input spur gear 2 and the first shunt spur gear 4, and determine its modulus, number of teeth, pressure angle and other parameters according to the gear transmission design method;

2. Determine the geometric parameters of the second split spur gear 10, and get the same geometric parameters as the first split spur gear 4;

3. Take the transmission ratio of the first shunting bevel gear 5 and the first reversing bevel gear 6 as the transmission ratio of the first shunting cylindrical gear 4 and the main input cylindrical gear 2, and determine its modulus and number of teeth according to the gear transmission design method , pressure angle and other parameters;

4. Get the geometric parameter of the second split bevel gear 11 to be identical with the first split bevel gear 5, get the geometric parameter of the second reversing bevel gear 12 to be identical with the first reversing bevel gear 6;

5. Take the transmission ratio as 1, and determine the parameters such as the modulus, number of teeth, and pressure angle of the first confluent bevel gear 8 and confluent output bevel gear 15 according to the gear transmission design method;

6. Get the geometric parameters of the second converging bevel gear 14 to be identical with the first converging bevel gear 8;

7. Take the transmission ratio as 1, and determine the parameters such as the modulus, the number of teeth, and the pressure angle of the output bevel gear 17 and the output reversing bevel gear 18 according to the gear transmission design method;

8. Design and select the center shaft and bearings of the reversing mechanism;

9. Design the parts structure, box body, lubrication and sealing in the reversing mechanism.

Embodiment one

The transmission ratio i ₂₄ of the main input spur gear 2 and the first split spur gear 4 =1/2, the modulus m=4, the pressure angle α=20°, the number of teeth z 2 of the main input spur gear ₂ =36, the first split spur gear The number of teeth z 4 of the cylindrical gear ₄ =18; the geometric parameters of the second split cylindrical gear 10 are the same as the cylindrical gear 4; the transmission ratio i ₅₆ of the first split bevel gear 5 and the first reversing bevel gear 6 =2, the modulus m =2, pressure angle α=20°, the number of teeth z 5 of the first split bevel gear ₅ =18, the number of teeth z 6 of the first reversing bevel gear ₆ =36; the geometric parameters of the second split bevel gear 11 and the first split Bevel gear 5 is identical, and the geometric parameter of the second reversing bevel gear 12 is the same as that of the first reversing bevel gear 6; the modulus m=1 of the first converging bevel gear 8, the second converging bevel gear 14 and converging output bevel gear 15, Pressure angle α=20°, number of teeth z ₈ =z ₁₄ =z ₁₅ =16; output conical gear 17 and output reversing bevel gear 18 with modulus m=2, pressure angle α=20°, number of teeth z ₁₇ =z ₁₈ =20.

Embodiment two

The transmission ratio i ₂₄ of the main input spur gear 2 and the first split spur gear 4 =1/3, the modulus m=6, the pressure angle α=25°, the number of teeth z 2 of the main input spur gear ₂ =60, the first split spur gear The number of teeth z 4 of the cylindrical gear ₄ =20; the geometric parameters of the second split cylindrical gear 10 are the same as the cylindrical gear 4; the transmission ratio i ₅₆ of the first split bevel gear 5 and the first reversing bevel gear 6 =3, the modulus m =3, pressure angle α=25°, the number of teeth z 5 of the first split bevel gear ₅ =17, the number of teeth z 6 of the first reversing bevel gear ₆ =51; the geometric parameters of the second split bevel gear 11 and the first split Bevel gear 5 is identical, and the geometric parameter of the second reversing bevel gear 12 is the same as that of the first reversing bevel gear 6; the modulus m=1.5 of the first converging bevel gear 8, the second converging bevel gear 14 and converging output bevel gear 15, Pressure angle α=25°, number of teeth z ₈ =z ₁₄ =z ₁₅ =18; output conical gear 17 and output reversing bevel gear 18 with modulus m=3, pressure angle α=25°, number of teeth z ₁₇ =z ₁₈ =22.

In a word, according to Fig. 5-7, since the confluent output bevel gear 15 can rotate around the common axis of the first reversing shaft 7 and the second reversing shaft 13, the rotation axis of the converging output bevel gear 15 and the first reversing shaft can be changed. The angle between the common axis of the steering shaft 7 and the second reversing shaft 13 is used to realize the change of the angle between the output shaft 19 and the axis 20 of the gear shaping tool. When processing orthogonal non-offset face gears or non-orthogonal non-offset face gears at a certain angle, first adjust the rotation axis of the confluent output bevel gear 15 to be coaxial with the first reversing shaft 7 and the second reversing shaft 13 The angle between them is the same as the angle of the orthogonal non-offset face gear or non-orthogonal non-offset face gear that is required to be processed, and then the position of the confluent output bevel gear 15 is fixed to achieve orthogonal non-offset Shaping of face gears or non-orthogonal non-offset face gears of corresponding angles.

Claims (1)

1. A variable-angle reversing mechanism on a face gear shaper machine tool split-tooth drive chain, characterized in that: The main input shaft (1), the main input cylindrical gear (2), the first split input shaft (3), the first split cylindrical gear (4), the first split bevel gear (5), the first reversing shaft (7 ), the first reversing bevel gear (6), the first converging bevel gear (8), the second splitting input shaft (9), the second splitting cylindrical gear (10), the second splitting bevel gear (11), the second Commutation shaft (13), second reversing bevel gear (12), second confluence bevel gear (14), confluence output bevel gear (15), confluence shaft (16), output bevel gear (17), output reversing Bevel gear (18) and output shaft (19) form; Wherein the first split input shaft (3), the second split input shaft (9) are respectively parallel to the main input shaft (1), the first reversing shaft (7), the second reversing shaft (13) are respectively parallel to the main input shaft (1) vertical, the first reversing shaft (7) and the second reversing shaft (13) are collinear, and the confluence axis (16) can be around the first reversing shaft (7) or the second reversing shaft (13) The axis varies from 0° to 90°, and the output shaft (19) and the confluence shaft (16) are perpendicular to each other; Wherein the first split cylindrical gear (4) and the first split bevel gear (5) are installed on the first split input shaft (3), the first reversing bevel gear (6) and the first converging bevel gear (8) are both Installed on the first reversing shaft (7), the main input cylindrical gear (2) meshes with the first diverter cylindrical gear (4), and the first diverter bevel gear (5) meshes with the first reversing bevel gear (6); Wherein the second split cylindrical gear (10) and the second split bevel gear (11) are all installed on the second split input shaft (9), the second reversing bevel gear (12) and the second converging bevel gear (14) are both Installed on the second reversing shaft (13), the main input cylindrical gear (2) meshes with the second diverter cylindrical gear (10), and the second diverter bevel gear (11) meshes with the second reversing bevel gear (12); Wherein the confluence output bevel gear (15) and the output bevel gear (17) are all installed on the confluence shaft (16), and the confluence output bevel gear (15) is connected with the first confluence bevel gear (8) and the second confluence bevel gear (14) at the same time ) engagement; Wherein the output reversing bevel gear (18) is installed on the output shaft (19), and the output reversing bevel gear (18) meshes with the output bevel gear (17) to realize the rotation of the output shaft; Wherein the transmission ratio i ₂₄ of the main input spur gear (2) and the first split spur gear (4) is equal to the transmission ratio i ₂₁₀ of the main input spur gear (2) and the second split spur gear (10); the first split cone The transmission ratio i ₅₆ of the gear (5) and the first reversing bevel gear (6) is equal to the transmission ratio i ₁₁₁₂ of the second split bevel gear (11) and the second reversing bevel gear (12); the first converging bevel gear (8) and the transmission ratio i ₈₁₅ of the converging output bevel gear (15) are equal to the transmission ratio i ₁₄₁₅ of the second converging bevel gear (14) and the converging output bevel gear (15); the main input cylindrical gear (2) and the first The transmission ratio i ₂₄ of the split cylindrical gear (4) and the transmission ratio i ₅₆ of the first split conical gear (5) and the first reversing bevel gear (6) and the first converging bevel gear (8) and converging output bevel gear ( The product of the transmission ratio i ₈₁₅ of 15) and the transmission ratio i ₁₇₁₈ of the output bevel gear (17) and the output reversing bevel gear (18) is 1.

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