TWI824906B - Single power source wavelet low-frequency radial wave milling tool holder composite mechanism - Google Patents

Abstract

This creation includes input shaft, coupling, first reduction group, planetary reduction group, radial cam group, offset transmission group and output shaft. The input shaft is driven by a single power source. The input gear of the input shaft mainly drives the transmission gear of the offset transmission group to drive the output shaft to rotate at high speed. In addition, the driving gear of the input shaft drives the first reduction group to cause the internal gear to decelerate. It rotates in the opposite direction, and connects the internal gear and the ring gear of the planetary reduction group through the coupling piece, and then engages the planetary gear with the sun gear of the input shaft through a two-degree-of-freedom differential, so that the planetary gear revolution drives the planet carrier to rotate at a low speed; and then through the planet carrier Combined with the radial cam group, it drives the offset transmission group to make the output shaft move repeatedly in the radial low-frequency wavelet. The output shaft is allowed to perform high-speed rotation and radial wavelet reciprocating motion at the same time, providing a mechanical solution to the problems caused by interruption of continuous chips when processing equipment cuts highly viscous materials.

Description

Single power source wavelet low-frequency radial wave milling tool holder composite mechanism

This invention relates to a driving device, specifically a single power source wavelet low-frequency radial wave milling tool holder composite mechanism that can mechanically interrupt continuous cutting chips.

When the workpiece is processed, continuous strip-shaped cutting chips will inevitably be produced. Continuous strips of cutting chips will not only wrap around the workpiece or tool, causing the workpiece to be unable to be processed, reducing the machining accuracy of the workpiece, damaging the tool, blocking the cutting fluid, or damaging the tool, etc.

In order to process highly viscous materials such as aluminum alloys, which are metals that are more likely to produce continuous strip-shaped cutting chips, existing processing equipment needs to purchase a controller to control the movement of the tool with software to interrupt the continuous strip-shaped cutting chips. to interrupt the continuous strip of chips. Only using software to control tool movement requires money to purchase controllers and software, which increases the cost of production and processing equipment.

Therefore, in order to improve the existing processing equipment and reduce the production cost of the processing equipment, it is necessary to improve the structure of the existing processing equipment.

In order to solve various problems caused by the interruption of continuous cutting chips by software control in existing processing equipment, this creation provides a single power source wavelet low-frequency radial wave milling tool holder composite mechanism, which can achieve the purpose of mechanically interrupting continuous cutting chips.

The single power source wavelet low-frequency radial wave milling tool holder composite mechanism proposed by this creation to solve the technical problem includes: a casing with a hollow interior; An input shaft, which can rotate through the casing and includes a shaft body, a driving gear, a sun gear and an input gear; the shaft body is rod-shaped; the driving gear, the sun gear, the input gear Coaxially fixed with the shaft body and capable of rotating together; a coupling member located in the casing, coaxially mounted on the input shaft and capable of rotating with the input shaft as the axis; a first reduction group , which is located in the casing and includes a plurality of intermediate gears and an internal gear; the plurality of intermediate gears surround the driving gear, and each intermediate gear can rotate at a fixed position and meshes with the driving gear; the internal gear It is annular, surrounds the plurality of intermediate gears, meshes with each of the intermediate gears and can rotate around the plurality of intermediate gears; a planetary reduction group, which is located in the casing and includes a planet carrier, a plurality of planetary gears and A ring gear; the planet carrier can rotate with the input shaft as the axis; the plurality of planet gears surround the sun gear, and each planet gear is rotatably combined with the planet carrier and meshes with the sun gear; the ring gear revolve around the plurality of planetary gears, mesh with each of the planetary gears and be able to rotate around the plurality of planetary gears; the internal gear and the ring gear are fixed on opposite sides of the coupling, and the internal gear and the ring gear Can rotate together with the coupling piece; an offset transmission group, which includes a gear frame and two index transmission parts; the interior of the gear frame is hollow; the two index transmission parts are spaced apart and can rotate through In the gear frame, each index transmission member includes an index gear and a transmission gear that are coaxially fixed and can rotate together. The index gear is a negative index gear, and the input gear is between two The index transmission member is between two index gears and meshes with the two index gears; a radial cam group includes a cam and two rollers; the cam is rotatably placed on the shaft body and coaxially It is fixed to the planet carrier and can rotate together with the planet carrier; the two rollers can roll and are combined with the gear frame, and each roller can roll along the cam and drive the offset transmission group along the a radial reciprocating motion perpendicular to the input axis; and An output shaft includes an output gear, which is between the two transmission gears of the two indexing transmission members and meshes with the two transmission gears; wherein the input shaft is driven by a single power source, and the output shaft is driven by a single power source. The input gear of the input shaft drives the output shaft to rotate through two index transmission parts; each planetary gear of the planetary reduction group inputs power with two degrees of freedom from the sun gear of the input shaft and the ring gear; the planet carrier and the cam Driven by the plurality of planetary gears to decelerate and rotate relative to the input shaft, the cam drives the gear frame and the output shaft to reciprocate radially.

The single power source wavelet low-frequency radial wave milling tool holder composite mechanism, wherein the casing includes an output housing, and two guide holes are respectively provided on opposite sides of the output housing; the offset transmission The set is located in the output housing and includes two guide members combined with the gear frame. Each guide member includes a guide post. The two guide posts of the two guide members face opposite directions respectively, and the two guide members The guide posts are inserted into the two guide holes respectively and can move radially.

In the single power source wavelet low-frequency radial wave milling cutter holder composite mechanism, a sliding bearing is placed between each of the guide posts and a corresponding guide hole.

The single power source wavelet low-frequency radial wave milling tool seat composite mechanism, wherein the radial cam group includes an output roller seat, the output roller seat is combined with the gear frame, and the two rollers can roll The cam is disposed on the output roller seat and is combined with the gear frame through the output roller seat; the cam is provided with a plurality of radial convex portions at equal angles.

The efficiency improvement that can be obtained by the technical means of this invention lies in the single power source wavelet low-frequency radial wave milling tool holder composite mechanism of this invention, which uses the coupling to combine the internal gear of the first reduction group and the ring of the planetary reduction group. The gear makes the ring gear and the input shaft rotate in reverse. The planetary reduction group simultaneously inputs power to the planetary gear from the sun gear and the ring gear to have two degrees of freedom, and makes the sun gear and the ring gear reversely rotate. The planetary gear is differentially driven to perform a large deceleration revolution, and the planetary gear drives the planet carrier to rotate at a low speed, so that the planet carrier drives the radial cam to rotate together at a relatively low speed. rotate, and then drive the offset transmission group, change the center distance through the positive and negative offset of the two sets of negative shift gears, and perform low-frequency and small fluctuation reciprocating motion along the radial direction of the input shaft, so that the output shaft can perform high-speed It can also reciprocate radially during rotational machining, which can interrupt continuous and strip-shaped cutting chips.

10:Chassis

11: Ring shell

12:Input end cover

121: Input end bearing cap

13:Output housing

131:Guide hole

20:Input shaft

21: Shaft body

21C:Axis

22:Driving gear

23:Sun gear

24:Input gear

30:Connecting parts

301: First side

302: Second side

40: First reduction group

41:Intermediate gear

42: Internal gear

50:Planetary reduction group

51:Planet carrier

52: ring set

53:Planetary gear

54: Ring gear

60: Radial cam group

61:Cam

611:convex circle

62:Output roller seat

63:Roller

70: Offset transmission group

71:Gear rack

72: Index transmission parts

721, 721A, 721B: indexing gear

722,722A,722B: transmission gear

73: Guide parts

731:Guide column

80:Output shaft

81:Output gear

81C:Axis

D1: first center distance

D2: Second center distance

Figure 1 is a schematic three-dimensional view of the appearance of a preferred embodiment of this invention.

Figure 2 is a schematic cross-sectional view of a preferred embodiment of this invention.

Figure 3 is a simple schematic diagram of a preferred embodiment of this invention.

Figure 4 is an exploded schematic diagram of the preferred embodiment of the present invention.

Figure 5 is a partial cross-sectional schematic diagram of the components of the preferred embodiment of the present invention.

Figure 6 is an exploded schematic diagram of the preferred embodiment of the present invention.

Figure 7 is a schematic cross-sectional view of the radial cam group according to the preferred embodiment of the present invention.

Figure 8 is a schematic plan view of the radial cam group according to the preferred embodiment of the present invention.

Figure 9 is a schematic cross-sectional view of the offset transmission group according to the preferred embodiment of this invention.

Figure 10 is a schematic plan view of the offset transmission group according to the preferred embodiment of the present invention.

11A to 11C are schematic plan views of the operation of the offset transmission group according to the preferred embodiment of the present invention.

In order to understand the technical features and practical effects of this invention in detail, and to realize it according to the content of the invention, the preferred embodiment as shown in the drawings is further described in detail as follows: As shown in Figures 1 to 4, this invention The preferred embodiment of the single power source wavelet low-frequency radial wave milling tool holder composite mechanism includes a casing 10, an input shaft 20, a coupling 30, a first reduction group 40, and a planetary reduction group 50 , a radial cam group 60, an offset transmission group 70 and an output shaft 80.

As shown in FIGS. 1 and 2 , the casing 10 is hollow inside and includes an annular shell 11 , an input end cover 12 and an output housing 13 . Among them, the ring shell 11 includes two opposite ends; the input end cover 12 is plate-shaped and is combined with one end of the ring shell 11. The input end cover 12 includes an input end bearing cover 121. A bearing is provided in the bearing cover 121; the output housing 13 is located at the other end of the ring housing 11; two guide holes 131 are respectively formed on opposite sides of the output housing 13.

As shown in FIGS. 1 to 5 and 9 , the input shaft 20 is rotatably inserted into the casing 10 and includes a radial direction perpendicular to the input shaft 20 , a shaft body 21 , a driving gear 22 , A sun gear 23 and an input gear 24; the shaft 21 is rod-shaped; the driving gear 22, the sun gear 23, the input gear 24 and the shaft 21 are coaxially fixed and can rotate together. In a preferred embodiment of the present invention, the shaft body 21 is divided into two sections and can be connected by a rigid coupling (not shown).

As shown in FIGS. 2 to 6 , the coupling member 30 includes a first side 301 and a second side 302 that are opposite to each other. The coupling member 30 is located in the casing 10 and is coaxially mounted on the input shaft 20 And it can rotate with this input shaft 20 as an axis|shaft. In a preferred embodiment of the invention, the coupling member 30 is sleeved on the input shaft 20 , and at least one bearing is provided between the coupling member 30 and the input shaft 20 to provide radial rigidity for the coupling member 30 Support; preferably, two bearings can be provided between the coupling member 30 and the input shaft 20 .

As shown in FIGS. 2 , 5 and 6 , the first reduction group 40 is located in the casing 10 and between the coupling member 30 and the input end cover 12 . The first reduction group 40 includes two intermediate gears 41 and an internal gear 42; in application, the first reduction group 40 can include multiple intermediate gears 41. The two intermediate gears 41 surround the driving gear 22. Each intermediate gear 41 is rotatably coupled to the input end cover 12 and supported by the input end cover 12; therefore, each intermediate gear 41 can rotate at a fixed position. , that is, each intermediate gear 41 can only rotate in place and cannot revolve relative to the driving gear 22; and each intermediate gear 41 meshes with the driving gear 22 and rotates in the opposite direction. The internal gear 42 is annular and surrounds the two intermediate gears 41, meshes with each of the intermediate gears 41, and can rotate around the two intermediate gears 41; in this invention , the internal gear 42 is fixed to the first side 301 of the coupling member 30 and can rotate together with the coupling member 30 , and the internal gear 42 and the driving gear 22 rotate in opposite directions.

As shown in FIGS. 2 , 5 and 6 , the planetary reduction group 50 is located in the casing 10 , and the planetary reduction group 50 and the first reduction group 40 are separated by the coupling 30 . The planetary reduction group 50 includes a planet carrier 51 , a ring sleeve 52 , a plurality of planetary gears 53 and a ring gear 54 . The planet carrier 51 can rotate with the input shaft 20 as its axis. The ring sleeve 52 is placed on the planet carrier 51 . The ring sleeve 52 is between the planet carrier 51 and the ring shell 11 so as to be able to radiate. The planet carrier 51 is supported toward the ground.

As shown in FIG. 2 , FIG. 5 and FIG. 6 , the plurality of planetary gears 53 are arranged around the sun gear 23 . Each of the planetary gears 53 is rotatably coupled to the rotatable planet carrier 51 and meshes with the sun gear 23 . ; Therefore, each of the planet gears 53 can revolve around the sun gear 23 along with the planet carrier 51 . The ring gear 54 surrounds the plurality of planetary gears 53 , meshes with each of the planetary gears 53 , and can rotate around the plurality of planetary gears 53 ; in this invention, the ring gear 54 is fixed to the second portion of the coupling 30 The side 302 can rotate together with the coupling member 30 and the internal gear 42 . The main function of the coupling 30 in this invention is to connect the internal gear 42 of the first reduction group 40 and the ring gear 54 of the planetary reduction group 50 so that the three are combined into a rigid body that rotates together.

As shown in FIGS. 2 , 4 , 7 and 8 , the radial cam group 60 includes a cam 61 , an output roller seat 62 and two rollers 63 . Among them, the cam 61 is rotatably sleeved on the shaft body 21 of the input shaft 20 through a through hole and is coaxially fixed to the planet carrier 51 and can rotate together with the planet carrier 51. Since the shaft body 21 is divided into It is two sections and connected by the rigid coupling, so that the cam 61 can be sleeved on the shaft body 21; in application, the shaft body 21 can also be a rod extending directly to the input gear 24. In the preferred embodiment of the present invention, the cam 61 includes an alignment convex circle 611 and is provided with a plurality of radial convex portions at equal angles; the alignment convex circle 611 of the cam 61 can be recessed on the planet carrier. The alignment grooves of the cam 61 and the planet carrier 51 are engaged so that the cam 61 and the planet carrier 51 can rotate coaxially. The output roller seat 62 is connected to the eccentric roller by bolts. Bit transmission group 70. The two rollers 63 can roll on the output roller seat 62, and each roller 63 can roll along the cam 61 to drive the offset transmission group 70 to linearly reciprocate along the radial direction.

As shown in Figures 2, 4, 9 and 10, the offset transmission group 70 is located in the output housing 13 of the casing 10. The offset transmission group 70 includes a gear frame 71, two index transmissions 72 and two guide parts 73. Among them, the gear frame 71 is hollow inside, and the output roller seat 62 is combined with the gear frame 71 of the offset transmission group 70; the two rollers 63 are connected to the gear frame 71 through the output roller seat 62. combined. The two indexing transmission parts 72 are spaced apart and rotatably inserted through the gear frame 71. Each of the indexing transmission parts 72 includes an indexing gear 721 and a transmission gear that are coaxially fixed and can rotate together. 722, the input gear 24 is between the two index gears 721 of the two index transmission members 72 and meshes with the two index gears 721. Since the offset transmission group 70 is driven by the radial cam group 60 to reciprocate radially; in order to allow the indexing gears 721 of each indexing transmission member 72 to remain in mesh with the input gear 24 without interfering with each other, downward, moving radially relative to the input gear 24; in this creation, the index gear 721 of each index transmission member 72 is a negative index gear. Each guide member 73 includes a guide post 731. The two guide members 73 are respectively coupled to opposite sides of the gear frame 71. The two guide posts 731 of the two guide members 73 face opposite directions respectively, and The two guide posts 731 are respectively and radially movably inserted into the two guide holes 131 of the output housing 13 . Specifically, a sliding bearing is disposed between each guide post 731 and a corresponding guide hole 131 and is sleeved on the guide post 731 .

As shown in Figures 2, 9 and 10, the output shaft 80 includes an output gear 81, which is between the two transmission gears 722 of the two index transmission members 72, and the output gear 81 is connected to the two transmission gears 722. The transmission gear 722 is in mesh.

As shown in Figure 2, one end of the input shaft 20 can be coupled with a power source. When the power source inputs power through the input shaft 20, the power is divided into two flow directions.

One is that the input gear 24 of the input shaft 20 directly drives the two index gears 721 of the two index transmission members 72 at high speed, and then the two transmission gears 722 of the two index transmission members 72 drive the output shaft 80 The output gear 81 drives the output shaft 80 to rotate at high speed. The processing equipment of the present invention can be used to install a cutter on the output shaft 80 and drive the high-speed rotating cutter to process the workpiece.

The second is transmitted to the ring gear 54 through the driving gear 22, the two intermediate gears 41, the internal gear 42 and the coupling member 30 in sequence. As shown in FIG. 2 , the ring gear 54 and the sun gear 23 drive a plurality of planet gears 53 with two degrees of freedom and then drive the planet carrier 51 . Since the sun gear 23 and the ring gear 54 rotate in opposite directions and have opposite tangential speeds, the tangential speed of each planet gear 53 revolving around the sun gear 23 is slowed down, so that the planet carrier 51 rotates at a relatively low speed. The cam 61 rotates at a high speed and slowly drives the cam 61 to rotate, and the cam 61 slowly drives the output roller seat 62 , the offset transmission group 70 and the output shaft 80 along the radial low-frequency wavelet ground perpendicular to the transmission shaft 20 Reciprocating linear motion.

For convenience of explanation, as shown in FIG. 10 and FIGS. 11A to 11C , the two index transmission members 72 of the offset transmission group 70 are further divided into a first transmission member 72A and a second transmission member 72B. The member 72A and the second transmission member 72B reciprocate linearly with low frequency in the radial direction, and the index gear 721A of the first transmission member 72A and the index gear 721B of the second transmission member 72B mesh with the input gear 24 .

First, as shown in FIG. 11A , a first center distance D1 is defined between the index gear 721A of the first transmission member 72A and the center of the input gear 24; the index gear 721B of the second transmission member 72B and the input gear A second center distance D2 is defined between the centers of 24. In FIG. 11A , the first center distance D1 is equal to the second center distance D2.

Then, as shown in FIG. 11B , when the gear frame 71 of the offset transmission group 70 drives the first transmission member 72A and the second transmission member 72B to move toward the right side of FIG. 11B , because the first transmission member 72A The index gear 721A and the index gear 721B of the second transmission member 72B are both negative index gears; therefore, the index gear 721A of the first transmission member 72A can move toward the input while maintaining meshing and non-interference. Gear 24; and the indexing gear 721B of the second transmission member 72B can move away from the input gear 24 while maintaining meshing. In FIG. 11B , the index gear 721A of the first transmission member 72A is smaller than the index gear 721A of the second transmission member 72A. The index gear 721B of the transmission member 72B is close to the input gear 24 and has a large working depth, and the first center distance D1 is smaller than the second center distance D2.

Finally, as shown in FIG. 11C , when the gear frame 71 of the offset transmission group 70 drives the first transmission member 72A and the second transmission member 72B to move toward the left side of FIG. 11C , similarly, due to the indexing Gears 721A and 721B are both negative indexing gears; therefore, in FIG. 11B , the indexing gear 721B of the second transmission member 72B is closer to the input gear 24 and has a larger diameter than the indexing gear 721A of the first transmission member 72A. working depth, and the first center distance D1 is greater than the second center distance D2.

As shown in FIG. 11B , the index gear 721A on the left is closer to the input gear 24 of the input shaft 20 than the index gear 721B on the right and has a larger working depth. The first center distance D1 is smaller than the second center distance. D2; then, as shown in Figure 11A, the two indexing gears 721A/B are at the same distance from the input gear 24; finally, as shown in Figure 11C, the indexing gear 721B on the right side is closer to the indexing gear 721A on the left side. The input gear 24 of the input shaft 20 has a larger working depth, and the first center distance D1 is greater than the second center distance D2.

The operation of this creation is divided into four stages.

The first stage: the first reduction group 40 drives the ring gear 54 of the planetary reduction group 50 to reversely rotate.

Second stage: The sun gear 23 and the ring gear 54 input power to each planetary gear 53 of the planetary reduction group 50 with two degrees of freedom, causing each planetary gear 53 to perform a decelerated revolution with a large reduction ratio. That is, the sun gear 23 and the ring gear 54 drive each planet gear 53 in reverse direction to rotate at high speed and revolve around the sun gear 23 at a large speed.

The third stage: the planetary gears 53 drive the planetary carrier 51 and the cam 61 of the radial cam group 60 to rotate slowly, and the radial cam group 60 drives the offset transmission group 70 and the output shaft 80 repeatedly Low frequency radial motion.

The fourth stage: the input gear of the input shaft drives the output shaft 80 through the two index transmission members 72, so that the output shaft 80 can rotate at high speed while repeating low-frequency radial motion.

In this creation, the output shaft 80 is directly driven by the input shaft 20 and can rotate at high speed; the cam 61 of the radial cam group 60 is driven by the planet carrier 51 to rotate slowly, and the cam 61 drives the output roller seat 62. Only when the offset transmission group 70 and the output shaft 80 reciprocate slowly along the radial direction can the offset transmission group 70 and the output shaft 80 reciprocate along the radial direction with low-frequency micro fluctuations; in this way Therefore, when processing with this invention, the cutting state can be slightly changed to interrupt the continuous strip-shaped cutting chips, and thus various problems caused by the continuous strip-shaped cutting chips can be avoided.

As shown in Figure 10, the offset of the axis center 81C of the output shaft 80 relative to the axis center 21C of the shaft body 21 is greater than the thickness of the cutting chips, so that the invention can interrupt continuous strip-shaped cutting chips and is suitable for rough machining. occasion.

The above are only preferred embodiments of the present invention and do not impose any formal restrictions on the present invention. Anyone with ordinary knowledge in the technical field can use the present invention without departing from the scope of the technical solution proposed by the present invention. Equivalent embodiments with partial changes or modifications to the technical content disclosed in the creation, and which do not deviate from the content of the technical solution of this creation, still fall within the scope of the technical solution of this creation.

10:Chassis

11: Ring shell

12:Input end cover

121: Input end bearing cap

13:Output housing

131:Guide hole

20:Input shaft

21: Shaft body

22:Driving gear

23:Sun gear

24:Input gear

30:Connecting parts

301: First side

302: Second side

40: First reduction group

41:Intermediate gear

42: Internal gear

50:Planetary reduction group

51:Planet carrier

52: ring set

53:Planetary gear

54: Ring gear

60: Radial cam group

61:Cam

62:Output roller seat

63:Roller

70: Offset transmission group

71:Gear rack

72A, 72B: First and second index transmission parts

73: Guide parts

731:Guide column

80:Output shaft

81:Output gear

Claims (7)

A single power source wavelet low-frequency radial wave milling cutter holder composite mechanism, which includes: a casing with a hollow interior; an input shaft that can rotate through the casing and includes a shaft body, a driving gear, A sun gear and an input gear; the shaft body is rod-shaped; the driving gear, the sun gear, the input gear and the shaft body are coaxially fixed and can rotate together; a coupling member is located in the casing , coaxially installed on the input shaft and capable of rotating with the input shaft as the axis; a first reduction group, which is located in the casing and includes a plurality of intermediate gears and an internal gear; the plurality of intermediate gears Around the drive gear, each intermediate gear can rotate at a fixed position and mesh with the drive gear; the internal gear is annular, surrounds the plurality of intermediate gears, meshes with each of the intermediate gears, and can surround the plurality of intermediate gears. The intermediate gear rotates; a planetary reduction group is located in the casing and includes a planet carrier, a plurality of planet gears and a ring gear; the planet carrier can rotate with the input shaft as the axis; the plurality of planet gears revolve around the A sun gear, each of the planet gears is rotatably coupled to the planet carrier and meshes with the sun gear; the ring gear surrounds the plurality of planet gears, meshes with each of the planet gears, and can rotate around the plurality of planet gears; The internal gear and the ring gear are fixed on opposite sides of the coupling, and the internal gear and the ring gear can rotate together with the coupling; an offset transmission group including a gear frame and two indexes Transmission parts; the gear frame is hollow inside; two index transmission parts are spaced apart and rotatably penetrated through the gear frame, and each index transmission part includes a coaxially bonded and rotatable part. An index gear and a transmission gear. The index gear is a negative index gear. The input gear is between the two index gears of the two index transmission parts and meshes with the two index gears; A radial cam group, which includes a cam and two rollers; the cam is rotatably mounted on the shaft and is coaxially fixed to the planet carrier and can rotate together with the planet carrier; the two rollers can Rolling and combined with the gear frame, each roller can roll along the cam to drive the offset transmission group to reciprocate in a radial direction perpendicular to the input shaft; and an output shaft, which includes an output Gear, the output gear is between the two transmission gears of the two index transmission parts and meshes with the two transmission gears; wherein the input shaft is driven by a single power source, and the input gear of the input shaft passes through the two transmission gears. The indexing transmission member drives the output shaft to rotate; each planetary gear of the planetary reduction group inputs power with two degrees of freedom from the sun gear of the input shaft and the ring gear; the planet carrier and the cam are driven by the plurality of planetary gears The cam then drives the gear frame and the output shaft to reciprocate in a radial direction relative to the decelerated rotation of the input shaft. The single power source wavelet low-frequency radial wave milling tool holder composite mechanism as described in claim 1, wherein the casing includes an output housing, and two guide holes are respectively provided on opposite sides of the output housing; The offset transmission group is located in the output housing and includes two guide members combined with the gear frame. Each guide member includes a guide post, and the two guide posts of the two guide members face opposite directions respectively. , and the two guide posts are inserted into the two guide holes respectively and can move radially. The single power source wavelet low-frequency radial wave milling cutter holder composite mechanism as described in claim 2, wherein there is a guide post placed between each guide post and a corresponding guide hole. Sliding bearings. The single power source wavelet low-frequency radial wave milling tool seat composite mechanism as described in claim 3, wherein the radial cam group includes an output roller seat, the output roller seat is combined with the gear frame, and the two The roller can roll on the output roller seat and is combined with the gear frame through the output roller seat; the cam is provided with a plurality of radial protrusions at equal angles. The single power source wavelet low-frequency radial wave milling tool holder composite mechanism as described in claim 1, wherein the frame of the offset transmission group is driven by the radial cam group to perform radial low-speed wavelet repetitive motion, and then passes through the internal The two index gears and the input gear of the input shaft perform forward and reverse offset transmission to reduce and increase the center distance, driving the two transmission gears to drive the output gear, causing the output shaft to perform low-frequency wavelet repeated motions. The single power source wavelet low-frequency radial wave milling tool holder composite mechanism as described in claim 1, wherein the two-degree-of-freedom star gear reduction mechanism uses the first reduction group to reversely rotate the internal gear and drive Each planetary gear rotates, and each planetary gear passes through the speed difference between the sun gear and the ring gear, so that each planetary gear drives the planet carrier to rotate at a large deceleration and low speed, and its differential speed ratio is driven by the first reduction group The reverse rotation of the ring gear and the sun gear are combined with the tooth number ratio to obtain the required large reduction ratio. The single power source wavelet low-frequency radial wave milling tool holder composite mechanism as described in claim 1, wherein the radial cam group movement drives the offset transmission group wavelet repeated movement and the offset movement amount needs to be greater than the cutting chip thickness, and The offset amount of the center distance between the input gear and each index gear in the offset transmission group needs to be determined by the shift coefficient of the two index gears.

Images