Gear shift mechanism and feed box

Abstract

The present invention relates to a transmission device with an operating mechanism and a feed gearbox. The operating mechanism consists of a control panel on which a speed disc is used to adjust the speed of the basic gear set. The device also includes a tower gear shaft, a power input shaft, and a guide shaft with parallel axis lines. A transmission mechanism is provided between the speed disc and the guide frame to drive the guide frame to move along the direction defined by the guide shaft. A positioning plate is located above the stroke slider. A drive mechanism is provided between the handle on the speed disc and the stroke slider to drive the stroke slider to move to the upper section of the connecting rod to engage or disengage with the positioning groove. The meshing of the oscillating gear with each unit gear in the tower gear set is controlled by the speed disc and the handle on it, eliminating the problems of mutual interference and misoperation when selecting different speed ratios, and achieving precise positioning and reliable meshing of the oscillating gear with the tower gear set.

Description

Technical Field

[0001] This invention relates to the operating mechanism of a speed change device and a lathe feed box. Background Technology

[0002] Speed ​​change mechanisms are crucial transmission mechanisms in the mechanical field, converting the speed input from the power input shaft into multi-speed power output. For example, the feed gearbox is a core functional component of a lathe, enabling feed rate conversion and thread lead control. In light-duty lathes, due to the limited internal space of the feed gearbox, traditional structures struggle to maximize coverage of metric, imperial, module, and diametral pitch thread machining specifications while minimizing the number of external gear changes. This results in issues such as limited applicable specifications and cumbersome operation.

[0003] The invention titled "Horizontal Lathe Feed Box" (Document No. CN2471454Y, hereinafter referred to as Document 1) discloses a feed box in which the basic group consists of a drive shaft I and a driven shaft II equipped with double triple sliding gears 1 and 7, and two sets of four fixed gears 2, 3, 4, 5, 8, 9, 10, and 11, forming a total of 14 gears with 7 meshing groups. The driven shaft II is used to transmit 7 different speeds to the multiplier group. The scheme disclosed in Document 1 requires two sets of shift fork mechanisms to drive the two triple sliding gears 1 and 7 to move, which is complex to operate, difficult to arrange, and occupies space in the axial direction. To address this, the invention titled "Horizontal Lathe Feed Box Operating Mechanism" (Document No. CN2471453Y, hereinafter referred to as Document 2) provides a scheme to control two triple sliding gears with a single handle. The problem is that Document 2 requires the installation of upper and lower racks, which significantly increases the component cost, and requires the two gear rack transmission mechanisms to work alternately to drive the corresponding triple sliding gear displacement. Furthermore, it did not solve the problem of inefficiency caused by 14 gears forming 7 sets of meshing transmission ratios.

[0004] The invention is titled "Horizontal Lathe Feed Box" (Document No. CN2304502Y, hereinafter referred to as Document 3). In Document 3, the drive shaft I is equipped with four sliding gears 4, 3, 2, and 1, and four gears 5, 6, 7, and 8 are fixed, distributed, and correspondingly arranged on the driven shaft II. A total of 8 gears can only obtain 4 speed ratios, which is too few to meet the requirements. In addition, the length required fork linkage 16 between the handle 15 and the fork 17 is too long. This means that the feed box must have enough space in the vertical direction, otherwise it will be difficult to realize the sliding operation of the four sliding gears 4, 3, 2, and 1.

[0005] The common problem in the above-mentioned conventional sliding multi-gear transmission structures is that although the total number of gears is large, they only constitute half of the total number of gears in terms of transmission ratio.

[0006] To avoid the above problems, the Norton mechanism provides another basic solution. In order to solve the shortcomings of the open solution of the basic Norton mechanism, the technicians further improved the sealing and oil storage of the housing. The lubrication conditions and appearance of the moving parts during operation were improved. Based on the complexity and cumbersome operation structure of the improved Norton mechanism, and the difficulties in processing, assembly, disassembly and maintenance caused by the large number of workpieces, the invention entitled "Speed ​​Change Operation Mechanism of Contained Feed Box Tower Gear of Horizontal Lathe" (Document No. CN 201960399U, hereinafter referred to as Document 4) provides a corresponding solution. In Document 4, the Norton frame gear 15 cooperates with the tower gear 13 fixed on the I axis 12 to obtain the transmission ratio of the number of gears of the tower gear 13.

[0007] In Reference 4, rotating the outer handle 20 and the outer handle seat 1 drives the rotating shaft 18 and cam 4 to rotate together via the pin, causing the lower positioning plate 8 to swing up and down around the fixed end, applying and releasing the constraint to the positioning pin 17; rotating the inner handle 19 and the inner handle seat 2 drives the gear sleeve 3 to rotate via the flat key 21. Since the gear sleeve 3 meshes with the rack 5 mounted on the lever 7, and the lever 7 is also locked on the Norton frame 6, it drives the sliding gear 11 and the Norton frame gear 15 to move axially along the II axis 10 and the III axis 16. At the same time, since the positioning pin 17 is clamped between the upper positioning plate 9 and the lower positioning plate 8, it can only move tilted along the direction of the round hole 22. Therefore, the Norton frame 6 moves and swings at the same time, and keeps the distance between the tip of the Norton frame gear 15 and the corresponding tower gear 13 unchanged.

[0008] The solution provided in Reference 4 has the following main problems: First, the two control components, inner handle 19 and inner handle seat 2 and outer handle 20 and outer handle seat 1, are coaxially arranged. Operators are not only prone to confusing the control objects of inner handle 19 and inner handle seat 2 and outer handle 20 and outer handle seat 1, making misoperation difficult to avoid, but the mutual interference caused by their coaxial arrangement is also inevitable, making normal operation difficult. Second, the rotating mating surfaces between the coaxially arranged rotating shaft 18 and gear sleeve 3, and between gear sleeve 3 and housing, need to be sealed. Once one of the seals fails, lubricating oil leakage is unavoidable. Third, an upper positioning plate 9 and a lower positioning plate 8 need to be set, and a circular hole 22 needs to be formed between the upper and lower positioning plates 9 and 8. This requires not only high machining accuracy but also high assembly accuracy; otherwise, the meshing accuracy of the corresponding gears on the Norton frame gear 15 and the tower gear 13 will be difficult to achieve. Fourth, the positioning pin 17 moves along the Norton frame gear 15 along the II axis 10 and the III axis 16. When the axial movement of the positioning pin 17 is to different positions, the angle between the core direction of the positioning pin 17 and the horizontal plane is different. Therefore, the core direction of each hole 22 formed between the upper and lower positioning plates 9 and 8 needs to be set to different directions, which increases the processing difficulty and cost of the upper and lower positioning plates 9 and 8. Summary of the Invention

[0009] The primary objective of this invention is to provide a control mechanism for a transmission device, which aims to achieve simple and convenient operation by separately engaging a set of pulleys and a single gear through a compact structural design, thereby avoiding misoperation.

[0010] To achieve the above objectives, the present invention adopts the following technical solution:

[0011] A control mechanism for a transmission device includes a control panel on the housing with a speed dial for adjusting the speed of the basic gear set, and a transmission mechanism for the basic gear set arranged inside the housing. The transmission mechanism comprises a sprocket shaft, a power input shaft, and a guide shaft with parallel shaft cores. A sprocket gear set is fixedly connected to the sprocket shaft. A guide hole at the rear of the guide frame forms a sliding guide fit with the guide shaft. The power input shaft is a splined shaft, and the input gear forms a spline sliding fit with the power input shaft. A swing gear hinged to the swing end of the swing frame always meshes with the input gear on the power input shaft. A transmission mechanism is provided between the speed dial and the guide frame to drive the guide frame to move along the direction defined by the guide shaft. A stroke slider mounted on the guide frame moves vertically... The travel slider has a guide hole for the connecting rod to pass through, and the two form a sliding guide fit. The lower end of the connecting rod located below the travel slider is hinged to the swing frame by a cylindrical pin parallel to the power input shaft. A positioning plate is provided above the travel slider. The edge of the positioning plate facing the upper section of the connecting rod exposed above the travel slider has a toothed positioning groove. A drive mechanism is provided between the handle on the speed dial and the travel slider to drive the travel slider to move to the upper section of the connecting rod to engage or disengage with the positioning groove. When the upper section of the connecting rod and the positioning groove are in the engaged position, the swing gear meshes with a unit gear in the tower gear set. The rotation axis of the speed dial is perpendicular to the axis direction of the power input shaft and the guide shaft.

[0012] In the above scheme, the meshing of the oscillating gear and the unit gears in the tower gear set is controlled by the speed dial and the handle set on it. That is to say, it forms the same number of speed ratios as the number of unit gears. It can be completed simply by rotating the speed dial and coordinating with the lever's flicking action. The operation is extremely simple. It overcomes the problems of mutual interference and misoperation when multiple speed dials and multiple handles control the oscillating gear and tower gear set to select each speed ratio. It achieves precise positioning and reliable meshing of the oscillating gear and tower gear set. This invention is applicable to the basic group transmission device and its operating mechanism of the feed box of machine tools such as lathes, which simplifies the structure and facilitates operation.

[0013] Another objective of this invention is to provide a feed box that improves the ease of operation of the feed box while reducing misoperation.

[0014] The technical solution adopted to achieve the above-mentioned objectives is as follows:

[0015] A feed box, characterized in that: a control panel of the box body is provided with a speed dial for adjusting the speed of the basic group, a handle seat for adjusting the speed of the multiplier group, and an adjustment handle connected to a torque switching mechanism that selects the torque output to the lead screw or the guide rod; a basic group transmission mechanism is arranged in the basic group chamber of the box body, and a multiplier group transmission mechanism is arranged in the multiplier group chamber of the box body; the power output end of the basic group transmission mechanism is connected to the input end of the multiplier group transmission mechanism; the power input end of the torque switching mechanism is connected to the power output end of the multiplier group transmission mechanism; and the power output end of the torque switching mechanism is selectively connected to the power input end of the lead screw or the guide rod.

[0016] The above technical solution controls the degree of freedom of the guide rod movement, facilitates the adjustment of the basic gear speed in the feed box, achieves precise positioning and reliable meshing of the gear set, effectively eliminates mutual interference and the possibility of misoperation during operation, and the feed box adopts a closed structure, which is conducive to the lubrication of transmission components, effectively reduces working noise, and extends the service life of the mechanism. Attached Figure Description

[0017] Figure 1 , 2 These are schematic diagrams of the three-dimensional structure of the feed box;

[0018] Figure 3 yes Figure 1 Sectional view in;

[0019] Figure 4 This is a three-dimensional structural schematic diagram of the present invention;

[0020] Figure 5 yes Figure 4 A schematic diagram with some components hidden;

[0021] Figure 6 , 7 They are Figure 4 , 5 Sectional view in;

[0022] Figure 8 , 9 These are three-dimensional structural diagrams showing the speed dial and handle in two different adjustment states.

[0023] Figure 10 , 11 These are the 3D view and the front view of the rack shaft, respectively.

[0024] Figure 12 It is a 3D diagram of the connecting rod;

[0025] Figure 13 , 14 These are 3D images of the positioning plate from two different upward viewing angles. Detailed Implementation

[0026] Example 1

[0027] Combination Figures 1-9 The transmission mechanism includes a control panel on the housing 10 with a speed dial 20 for adjusting the basic gear speed. The housing 10 contains a basic gear transmission mechanism, which includes a sprocket shaft 31 with parallel shafts, a power input shaft 3, and a guide shaft 6. A sprocket gear set 30 is fixedly connected to the sprocket shaft 31. A guide hole 221 at the rear of the guide frame 22 forms a sliding guide fit with the guide shaft 6. The power input shaft 3 is a spline shaft, and the input gear 25 forms a spline sliding fit with the power input shaft 3. A swing gear 27, hinged to the swing end of the swing frame 29, always meshes with the input gear 25 on the power input shaft 3. A transmission mechanism is provided between the speed dial 20 and the guide frame 22 to drive the guide frame 22 to move along the direction defined by the guide shaft 6. A stroke slider 50 on the guide frame 22 moves in a direction perpendicular to the guide frame 22. The stroke slider 50 has a guide hole for the connecting rod 52 to pass through, and the two form a sliding guide fit. The lower end of the connecting rod 52 located below the stroke slider 50 is hinged to the swing frame 29 by a cylindrical pin 28 parallel to the power input shaft 3. A positioning plate 40 is provided above the stroke slider 50. The edge of the positioning plate 40 facing the upper section of the connecting rod 52 exposed above the stroke slider 50 has a toothed positioning groove 41. A drive mechanism is provided between the handle 21 on the speed disk 20 and the stroke slider 50 to drive the stroke slider 50 to move to the upper section of the connecting rod 52 to engage or disengage with the positioning groove 41. When the upper section of the connecting rod 52 and the positioning groove 41 are in the engaged position, the swing gear 27 meshes with a unit gear 32 in the tower gear set 30. The rotation axis of the speed disk 20 is perpendicular to the axis direction of the power input shaft 3 and the guide shaft 6.

[0028] In the above scheme, the vertical direction of the connecting rod 52 is positioned so that it is directly in front of the observer's line of sight when facing the power input shaft 3 and the guide shaft 6 in a horizontal manner. Of course, in actual use, the control panel of the housing 10 can be arranged at an angle, vertically, or horizontally. When the rotation axis of the speed dial 20, the power input shaft 3, and the guide shaft 6 are all in the horizontal direction, the length of the connecting rod 52 is arranged vertically. The illustrations show examples of this arrangement. The rotation axis of the speed dial 20 is arranged at an angle to the horizontal direction to accommodate the fact that the control panel can also be arranged vertically at a small angle, while the rotation axis of the speed dial 20 remains perpendicular to the control panel.

[0029] In fact, depending on the requirements of the application environment, the power input shaft 3 and the guide shaft 6 can be arranged in a vertical position, while the connecting rod 52 is arranged in a horizontal position. In this case, the two ends of the connecting rod 52 can be referred to as the inner end and the outer end or the left end and the right end.

[0030] The present invention needs to transmit the rotational torque of the power input shaft 3 at a certain speed to the tower wheel shaft 31, and then output the transmitted torque downstream by the tower wheel shaft 31 at the same speed ratio as the number of unit gears 32 in the tower wheel gear set 30. For this purpose, it is necessary to adjust the swing gear 27 to mesh with a certain unit gear 32 in the tower wheel gear set 30. The above technical solution relies on the speed plate 20 and the handle 21 to achieve the selection of the torque transmission path.

[0031] When the rotating disc 20 is rotated, the transmission mechanism between the disc 20 and the guide frame 22 drives the guide frame 22 to move in the direction defined by the guide shaft 6. When the guide frame 22 is at a certain position in the axial direction of the guide shaft 6, the swing gear 27 and a certain unit gear 32 in the tower gear set 30 are in the same position in the axial direction. At this time, the driving mechanism between the handle 21 and the stroke slider 50 drives the stroke slider 50 to move to the position where the upper section of the connecting rod 52 mates with the positioning groove 41. During the process of the upper section of the connecting rod 52 entering the positioning groove 41, the connecting rod 52 moves downward. The lower end of the connecting rod 52 presses down on the swing frame 29, causing the swing end to swing downward to the swing gear. Wheel 27 meshes with a unit gear 32 that is axially aligned with the tower wheel shaft 31. If it is necessary to adjust the output speed of the tower wheel shaft 31, the drive mechanism drives the stroke slider 50 to move until the upper section of the connecting rod 52 separates from the positioning groove 41. During the process of the upper section of the connecting rod 52 disengaging from the positioning groove 41, the connecting rod 52 moves upward, and the lower end of the connecting rod 52 pulls the swing frame 29 upward, causing the swing end to swing upward until the swing gear 27 separates from the unit gear 32 that is axially aligned with the tower wheel gear set 30. In the state where the swing gear 27 is separated from the tower wheel gear set 30, the displacement of the guide frame 22 can be completed again by operating the rotating speed disk 20, so that the adjustment of the next target speed can be implemented. In the above scheme, the upper section of the connecting rod 52 is used to cooperate with the positioning groove 41 to achieve accurate and reliable axial positioning of the guide frame 22, the lower end of the connecting rod 52 is used to drive the swing of the swing frame 29, and the middle section of the connecting rod 52 and the guide hole in the middle of the stroke slider 50 form an up-and-down sliding cooperation during the synchronous displacement with the stroke slider 50.

[0032] like Figures 3-7 As shown, the rotation axis of the speed disk 20 is perpendicular to the axis direction of the power input shaft 3 and the guide shaft 6. The above scheme is beneficial to simplifying the transmission mechanism between the speed disk 20 and the guide frame 22 to drive the guide frame 22 to move along the direction defined by the guide shaft 6. On the other hand, it is beneficial to set up a drive mechanism controlled by the handle 21 to drive the stroke slider 50 to move to the upper section of the connecting rod 52 to engage or disengage with the positioning groove 41.

[0033] Combination Figure 4 , 6 See also Figure 13 , 14In the preferred embodiment, the inclined direction of the surface where the positioning groove 41 is located is consistent with the cone direction of the tower gear set 30. This ensures that the positioning of the connecting rod 52 and the positioning groove 41 corresponds to the increase or decrease of the output speed when the speed disk 20 rotates in both directions. Furthermore, the inclined direction of the surface where the positioning groove 41 is located, consistent with the cone direction of the tower gear set 30, ensures that the rotation angle of the speed disk 20 and the swing stroke range of the handle 21 are basically the same for the up and down movement of the connecting rod 52 and the displacement movement of the sliding block 50 along with the stroke, corresponding to the adjustment of adjacent speed positions. This significantly facilitates the actual operation for the operator and also allows for the arrangement of a reasonable number of unit gears 32 within the reasonable rotation range of the speed disk 20. It should be briefly explained here that... Figure 4 , 6 As shown in Figures 13 and 14, the positioning groove 41 has an arc-shaped interface that is smaller than a semicircle. This solves multiple problems at the same time, such as accurate positioning, guiding the connecting rod 52 into the positioning groove 41, and reasonably selecting the thickness of the unit gear 32.

[0034] The driving mechanism for the horizontal displacement of the stroke slider 50 includes a handle 21 on the speed disk 20. The handle 21 is hinged to the speed disk 20 by a threaded cylindrical pin 212, and the threaded cylindrical pin 212 is perpendicular to the rotation axis of the speed disk 20. When the handle 21 swings around the threaded cylindrical pin 212, it drives the rack shaft 26, which is coaxially arranged in the hole of the speed disk 20, to move inward and outward along the direction of the disk axis of the speed disk 20. The axis of the camshaft 60 is parallel to the axis of the power input shaft 3. When the rack shaft 26 moves inward and outward, it drives the camshaft 60 to rotate around its own axis. When the camshaft 60 rotates, the unit cam 611 in the cam tower group 61 set on its shaft abuts or separates from the stroke slider 50. The radial direction of the camshaft 60 is consistent with the radial direction of the cam tower group 61. In this scheme, when the handle 21 swings around the threaded cylindrical pin 212, it drives the rack shaft 26 to move inward and outward along the rotation axis of the speed disk 20, that is, the rack shaft 26 itself. Here, inward and outward refers to the control panel of the housing 10. The rack shaft 26, which is controlled by the handle 21 to move inward and outward, drives the cam shaft 60 to rotate around its own axis. Since the radial direction of the cam tower assembly 61, that is, the radial direction of the unit cam 611, is consistent with the radial direction of the cam shaft 60, when the cam shaft 60 rotates, the rim of the unit cam 611 at the major diameter is in different positions in the circumferential direction, thus forming a state of contact or separation between the unit cam 611 and the stroke slider 50. This realizes the displacement of the stroke slider 50 on the guide frame 22 in a straight line direction perpendicular to the moving direction of the guide frame 22, thereby ensuring that the connecting rod 52 moves up and down when it moves with the stroke slider 50.

[0035] like Figures 5-8Furthermore, one end of the camshaft 60 has a spur gear 62, the core of which coincides with the core of the camshaft 60. The inner section of the horizontal rack shaft 26 is an annular tooth segment 261 with tooth tips and tooth valleys extending in a circumferential direction. The outer section of the rack shaft 26 is a strip-shaped hole or U-shaped groove 262. The handle 21, which is placed in the strip-shaped hole or U-shaped groove 262, is hinged to the rack shaft 26 by a handle pin 213. The handle pin 213 is perpendicular to the core of the strip-shaped hole or U-shaped groove 262 and the core of the rack shaft 26. The other end of the handle 21, relative to the gripping end, is hinged to the speed disk 20 by a threaded cylindrical pin 212. The threaded cylindrical pin 212 is set parallel to the handle pin 213.

[0036] In the above scheme, the inner section of the rack shaft 26 is set as an annular toothed section 261. The width of each tooth on the annular toothed section 261 is independently occupied within a specific range in the axial direction of the rack shaft 26. It can also be understood that the tooth valleys between adjacent teeth form a circumferential annular groove. The adjacent teeth or annular grooves have completely different shapes from threaded teeth or threaded grooves. The size of the circumferential range covered by each tooth corresponds to the rotation range of the speed dial 20 when adjusting the speed. Of course, for ease of processing, the teeth on the annular toothed section 261 can be directly machined into a complete circle, that is, machined into a complete annular groove. In other words, the teeth or grooves are connected end to end in the circumferential range. In addition, the handle 21 is hinged to the rack shaft 26 by the handle pin 213. During operation, when the handle 21 is held and the handle head of the handle 21 is moved away from the housing 10, the rack shaft 26 is displaced outward, the annular toothed section 261 is displaced outward and drives the spur gear 62 meshing with it to press... Figure 8 The posture shown is rotated counterclockwise to Figure 4 , 6 In the state shown, it appears as Figure 4 , 6 The long-diameter rim of the unit cam 611 shown extends towards the stroke slider 50 and engages with it. The direct result of this control is that the rack shaft 26 and the handle 21 move inward or outward synchronously. This allows the operator to subconsciously lock the action of pushing the handle 21 outward; conversely, pushing the handle 21 inward subconsciously unlocks it. At this point, the handle 21 and the core of the speed dial 20 are in a naturally relaxed, perpendicular relationship. Power transmission is interrupted to facilitate rotation of the speed dial 20 and adjustment of the corresponding gear ratio. Therefore, this scheme aligns with the operator's general thinking habits, allowing for quick familiarization with the equipment's operation and further minimizing the possibility of misoperation.

[0037] Combination Figure 3 , 9As shown, the end of the handle 21 away from the gripping end is detachably connected to the shift fork 211. The middle section of the shift fork 211 is placed in the strip hole 262 and is hinged by the handle pin 213. The other end of the shift fork 211 is a fork and a threaded cylindrical pin 212 is placed in the fork. The two ends of the threaded cylindrical pin 212 are connected to the pin seat 20B provided on the outer wall of the convex section 20A of the speed disk 20. Setting the end of the handle 21 away from the gripping end to the shift fork 211 as a detachable connection reduces the machining difficulty of the operating handle and simplifies the assembly process. The fork of the shift fork 211 is pinned to the threaded cylindrical pin 212 fixed to the pin seat 20B on the outer wall of the convex section 20A of the speed disk 20. This increases the distance between the threaded cylindrical pin 212 and the handle pin 213, which can minimize the radial and axial dimensions of the convex section 20A of the speed disk 20 and meet the basic requirements of the inward and outward displacement stroke of the rack shaft 26 while ensuring that the shifting angle of the handle 21 is appropriate.

[0038] like Figure 3 , 9 As shown, the central hole of the rotating disk 20 is a stepped hole with a larger outer diameter and a smaller inner diameter. The optical axis of the middle section of the rack shaft 26 slides and engages with the small diameter section of the central hole of the rotating disk 20. The outer section of the rack shaft 26 is a square block shape and is placed in the large hole section of the convex column section 20A. The convex column section 20A has a through hole 20C with the through direction consistent with the through direction of the strip hole 262.

[0039] The small-diameter section of the central hole in the speed disc 20 serves to center the optical shaft section of the rack shaft 26 and guide its axial displacement. When the square block-shaped inner end face of the rack shaft 26 abuts against the variable-diameter platform of the central hole in the speed disc 20, the core of the handle 21 is in a position perpendicular to the rack shaft 26. At this time, the handle 21 is in a stable state, which corresponds to the state where the camshaft 60 and the stroke slider 50 are completely separated, i.e., the torque transmission chain is interrupted, i.e., the unlocked state. The handle 21 corresponds to... Figure 8 As shown in the diagram, the protruding column section 20A has a through hole 20C whose through direction is consistent with that of the strip hole 262, which is beneficial for arranging the handle 21 and provides a suitable swing space for the swing of the handle 21.

[0040] like Figures 4-7 As shown, the transmission mechanism that drives the guide frame 22 to move along the direction defined by the guide shaft 6 includes a shift gear 24 coaxially connected to the inner end of the speed disk 20. The shift gear 24 meshes with the rack 23. The rack 23 is parallel to the power input shaft 3 and is mounted on the guide frame 22 with its tooth surface facing upward.

[0041] With the help of the meshing of the shift gear 24 and the rack 23, when the turntable 20 rotates, it drives the guide frame 22 to move in the direction defined by the guide shaft 6. The displacement of the guide frame 22 realizes the axial displacement of the swing gear 27 on the guide frame 22, so that the swing gear 27 is moved to the corresponding position that is axially aligned with a certain unit gear 32 of the tower gear set 30, which is in advance for the next step of meshing the swing gear 27 and the unit gear 32.

[0042] The above only describes the displacement of the guide frame 22 along the direction defined by the guide shaft 6. In fact, the posture of the guide frame 22 during the movement process is determined, that is, the parallel guide shaft 6 and the power input shaft 3 simultaneously provide constraints on the guide frame 22.

[0043] See Figures 3-7 9. The shift gear 24 is coaxially connected to the inner end of the speed plate tube 20D at the inner end of the speed plate 20. A positioning sleeve 20E is provided between the speed plate 20, the speed plate tube 20D and the mounting hole of the control panel of the housing 10. The annular tooth section 261 of the inner section of the rack shaft 26, which is exposed outside the speed plate tube 20D, meshes with the spur gear 62 on the camshaft 60. The speed plate tube 20D and the speed plate 20 are concentric and the rotation shaft is located in the horizontal direction.

[0044] See Figure 8 , 9 Furthermore, the unit cams 611 are arranged in a stepped manner on the same side of the circumference of the camshaft 60. The axial arrangement positions of the large and small diameter unit cams 611 are opposite to the axial arrangement positions of the large and small diameter unit gears 32 in the tower gear set 30. The top edge of the unit cam 611 is respectively in the upper position separated from the wedge-shaped adjusting block 53 and the suspended position where the top edge abuts against the wedge-shaped adjusting block 53. The upper position and the suspended position of the unit cam 611 correspond to the vertical position of the handle 21 and the internal position and the external oblique position, respectively.

[0045] like Figure 4 , 5 As shown in Figures 7 and 8, when handle 21 is in Figure 8 When the handle 21 is perpendicular to the rotating shaft of the speed disk 20, the top edge of the unit cam 611 on the camshaft 60 is in the upper position, the camshaft 60 and the stroke slider 50 are completely separated. When the speed disk 20 rotates, the tooth peak of the annular tooth segment 261 in the inner section of the rack shaft 26 can slide freely in the tooth valley of the spur gear 62 on the camshaft 60. The circumferential rotation of the annular tooth segment 261 in the inner section of the rack shaft 26 will not cause the rotation of the camshaft 60 and the spur gear 62. That is, at this time, the meshing transmission between the shift gear 24 and the rack 23 can realize the displacement adjustment of the guide frame 22.

[0046] See Figures 3-7The guide seat 70 and the stroke slider 50 are respectively in sliding fit with the guide key 222 and the linear guide rail 223 provided on the top surface of the guide frame 22. The guide direction of the guide key 222 and the linear guide rail 223 is horizontal and perpendicular to the axial direction of the guide shaft 6. A spring 54 is provided between the guide seat 70 and the stroke slider 50 to drive them to separate. The bottom surface of the positioning plate 40 and the top of the guide seat 70 and the stroke slider 50 form a limiting fit to restrict the separation distance between them.

[0047] The guide seat 70 and the stroke slider 50 form a sliding fit with the guide key 222 and the linear guide rail 223 set on the top surface of the guide frame 22, respectively. The guide key 222 and the linear guide rail 223 define the direction parallel to each other. This ensures that the guide seat 70 and the stroke slider 50 move synchronously with the guide frame 22 along the axial direction of the guide shaft 6, and also move relative to the guide frame 22. The displacement of the guide seat 70 and the stroke slider 50 in the direction defined by the guide key 222 and the linear guide rail 223 is intended to drive the displacement of the connecting rod 52. The movement of the connecting rod 52 includes three component movements: first, the axial displacement along the guide shaft 6 with the guide frame 22; second, the displacement along the linear guide rail 223 with the stroke slider 50 when driven by the stroke slider 50; and third, the vertical displacement under the joint constraint of the guide hole on the cylindrical pin 28 and the stroke slider 50 through which the connecting rod 52 passes. The second and third movements are performed simultaneously, and the combined movement of the second and third movements constitutes the oscillating gear 27 to mesh or disengage with a certain unit gear 32 of the tower gear set 30 in a translational and oscillating manner.

[0048] Whether the oscillating gear 27 meshes with the unit gear 32 is actually determined by the position of the connecting rod 52, which determines the fit between the connecting rod 52 and the positioning plate 40. The preceding text has detailed the working state corresponding to the meshing torque transmission of the swing gear 27 and the unit gear 32 when the connecting rod 52 and the positioning groove 41 on the positioning plate 40 are engaged. This working state can be regarded as the positioning groove 41 on the positioning plate 40 providing a positioning function for the connecting rod 52. During the adjustment of the meshing of the swing gear 27 with a certain unit gear 32 and in the non-working state, the swing gear 27 and any unit gear 32 are in a disengaged state. At this time, the separation position of the connecting rod 52 and the positioning groove 41 on the positioning plate 40 needs to be stable and certain. For this reason, the present invention gives the positioning plate 40 a new additional task, namely, to provide a limiting function for the connecting rod 52, ensuring that the connecting rod 52 can quickly and reliably reach the positioning position that mates with the positioning groove 41. The solution to this problem is that a spring 54 is provided between the guide seat 70 and the stroke slider 50 to drive them to separate. The bottom surface of the positioning plate 40 and the top of the guide seat 70 and the stroke slider 50 form a limiting fit that restricts the separation distance between them. Therefore, it can be seen that under the action of spring 54, the guide seat 70 and the stroke slider 50 always tend to move away from each other. Under the limiting constraint applied by the positioning plate 40 to both the guide seat 70 and the stroke slider 50, the guide seat 70 and the stroke slider 50 can only maintain a certain distance of separation. In fact, this sets a boundary for the connecting rod 52 to move away from the positioning groove 41 on the positioning plate 40. That is, when the guide seat 70 and the stroke slider 50 are separated to the maximum distance, it is also the maximum distance between the connecting rod 52 and the positioning groove 41 on the positioning plate 40. This distance is stable and certain. On the one hand, it ensures that the distance between the stroke slider 50 and the camshaft 60 is stable and reliable. On the other hand, it ensures that the maximum distance between the stroke slider 50 and the positioning groove 41 is sufficient to ensure the safe separation of the swing gear 27 and the tower gear set 30, and avoids the camshaft 60 and the tower gear set 30 interfering with the displacement of the guide frame 22 and hindering the displacement of the guide frame 22.

[0049] Furthermore, the spring 54 is sleeved on the spring guide rod 55, and both ends of the spring guide rod 55 are connected to the guide seat 70 and the stroke slider 50 respectively, with at least one of the guide seat 70 and the stroke slider 50 forming a sliding engagement with the spring guide rod 55. The spring 54 being sleeved on the spring guide rod 55 prevents torsional deformation when the spring 54 is subjected to force, ensuring the uniformity of spring deformation and the consistency of elastic force release. The spring guide rod 55 also restricts the smoothness and consistency of the relative movement of the guide seat 70 and the stroke slider 50 towards or away from each other.

[0050] For details, see Figure 5 , 67, 13, 14, The bottom surface of the positioning plate 40 has a cavity 42. The first cavity wall 43 and the second cavity wall 44 of the cavity 42 are arranged opposite to each other and their walls are parallel to the surface where the positioning groove 41 is located. The distance between the first cavity wall 43 and the surface where the positioning groove 41 is located is greater than that between the second cavity wall 44 and the surface where the positioning groove 41 is located. The first cavity wall 43 and the second cavity wall 44 respectively form a limiting fit with the top of the guide seat 70 and the stroke slider 50 to limit the maximum distance between the two. As can be seen from the above scheme, the first cavity wall 43 and the second cavity wall 44 of the concave cavity 42 provide constraint and limit to the guide seat 70 and the stroke slider 50. The maximum separation distance between the guide seat 70 and the stroke slider 50 is determined by the distance between the first cavity wall 43 and the second cavity wall 44. Therefore, the maximum separation distance between the guide seat 70 and the stroke slider 50 is stable and reliable. At the same time, since the first cavity wall 43 and the second cavity wall 44 are parallel to the surface where the groove opening or bottom of the positioning groove 41 is located, the maximum distance between the guide seat 70 and the stroke slider 50 when they are separated from the positioning groove 41 on the positioning plate 40 is basically the same, regardless of the position to which the connecting rod 52 is displaced. For the operation of the handle 21, the range of the handle 21 turning angle corresponding to the process of the connecting rod 52 engaging and disengaging from the positioning groove 41 on the positioning plate 40 is the same each time.

[0051] Further, see Figure 5 , 6 7, 13, 14. A slider 71 is hinged to the top of the guide seat 70. The rotary shaft is located on the planar vertical surface of the slider 71 facing the plumb line, which slides and engages with the first cavity wall 43. When the connecting rod 52 engages with the positioning groove 41 on the positioning plate 40, the spring 54 contracts and the elastic force increases, thereby increasing the force transmitted between the slider 71 and the first cavity wall 43. The design of the planar vertical surface of the slider 71 engaging with the first cavity wall 43 can reduce pressure and avoid scratch damage to the contact surface of the slider 71 and the first cavity wall 43. This ensures that the planar vertical surface of the slider 71 and the first cavity wall 43 can reliably and smoothly contact each other at any position, avoiding step-like unstable contact at the contact point between the slider 71 and the first cavity wall 43, and eliminating interference with the positioning of the connecting rod 52 and the positioning groove 41, thus eliminating the impact on the positioning accuracy of the connecting rod 52.

[0052] The top of the stroke slider 50 has a bearing 56 with its shaft located in the vertical direction. The bearing 56 and the second cavity wall 44 form a separation or rolling contact fit. When the connecting rod 52 separates from the positioning groove 41 on the positioning plate 40, the spring 54 releases its elastic force and extends. When the bearing 56 contacts the second cavity wall 44, the pressure between them is very small, and the contact between the bearing 56 and the second cavity wall 44 can be regarded as a line contact. However, there will be no pressure damage between the bearing 56 and the second cavity wall 44.

[0053] In the above scheme, the first cavity wall 43 and the second cavity wall 44 of the bottom surface of the positioning plate 40 constituting the cavity 42, and the constraint cooperation between the slider 71 on the top of the guide seat 70 and the bearing 56 on the top of the stroke slider 50, not only restrict the maximum distance between the guide seat 70 and the stroke slider 50, but also provide the motion form of the stroke slider 50 floating relative to the guide seat 70, and also realize the displacement of the stroke slider 50 and the guide seat 70 along the area where the first cavity wall 43 and the second cavity wall 44 are located, which is consistent with the direction of the cone slope of the tower gear set 30.

[0054] To facilitate the installation of bearing 56 and reduce the size of stroke slider 50, a trapezoidal block 51 is provided on the side of stroke slider 50 facing guide seat 70. The trapezoidal block 51 is arranged between springs 54, thus reasonably completing the arrangement of each component.

[0055] See Figure 6 , 7 The connecting rod 52 is arranged vertically, with a gap between the plumb surface of the cylindrical pin 28 and the plumb surface of the power input shaft 3. The vertical arrangement of the connecting rod 52 has many advantages, such as the vertical extension direction of the positioning groove 41 on the positioning plate 40, the guide hole on the stroke slider 50, and the vertical arrangement of the first cavity wall 43 and the second cavity wall 44. This simplifies the machining process of many components and ensures high machining accuracy. The gap between the plumb surface of the cylindrical pin 28 and the plumb surface of the power input shaft 3 avoids the cylindrical pin 28 and the power input shaft 3 being in a dead angle position relative to the plumb surface, thus ensuring that the rotational torque of the connecting rod 52 with the power input shaft 3 as its rotation axis is greater than zero.

[0056] Referring to points 3, 5, 6, 7, and 12, the lower section of connecting rod 52 is a cylindrical shape with a constant diameter. The radius of the cylindrical surface section facing the positioning groove 41 on the upper section of connecting rod 52 is smaller than the radius of the cylindrical surface section facing away from the positioning groove 41. The cylindrical surfaces on both sides transition smoothly circumferentially. The lower section of connecting rod 52 is a cylindrical shape with a constant diameter, and the diameter of the lower section needs to meet certain dimensions to facilitate the machining of connecting rod 52 and its mating guide holes. Figure 6 , 7In this design, the connecting rod 52 passes through a copper sleeve installed on the stroke slider 50. This reduces wear and improves the flexibility of the vertical displacement of the connecting rod 52. The lower end of the connecting rod 52 also bears the responsibility of pressing against the swing frame 29 to maintain the stable and reliable meshing of the swing gear 27 and the unit gear 32. The lower section of the connecting rod 52 with a suitable cylinder diameter has appropriate bending strength. Once the lower section of the connecting rod 52 is bent and deformed under force, the vertical displacement of the connecting rod 52 will be hindered. If the connecting rod 52 is a cylinder with equal upper and lower diameters, the cavity diameter of the positioning groove 41 that mates with it must be correspondingly increased. The increase in the cavity diameter of the positioning groove 41 further requires an increase in the axial thickness of the unit gear 32, an overall increase in the shaft length of the tower gear set 30, and a thickening of the swing gear 27, among other issues. To solve the above problems, the solution of this invention is that the radius of the cylindrical cross-section facing the positioning groove 41 on the upper section of the connecting rod 52 is smaller than the radius of the cylindrical cross-section facing away from the positioning groove 41, and the cylindrical surfaces on both sides are circumferentially extended. In other words, by machining the upper section of the connecting rod 52 into a small cross-section shape on the cylindrical surface facing the positioning groove 41, the strength and vertical displacement of the lower section of the connecting rod 52 are satisfied, while avoiding the need for proper matching between the cavity diameter of the positioning groove 41 and the thickness of the unit gear 32.

[0057] A wedge-shaped adjusting block 53 is provided on one side of the stroke slider 50 facing the cam tower assembly 61. The upper inclined surface of the wedge-shaped adjusting block 53 is parallel to the wheel core of the camshaft 60, and the distance between it and the plumb surface passing through the wheel core of the camshaft 60 gradually approaches from top to bottom. The lower vertical surface of the wedge-shaped adjusting block 53 is parallel to the plumb surface passing through the wheel core of the camshaft 60. When the wedge-shaped adjusting block 53 is set to cooperate with the camshaft 60, under the guidance of the upper inclined surface, the wheel rim of the unit cam 611 on the camshaft 60 gradually contacts the upper inclined surface of the wedge-shaped adjusting block 53, avoiding abrupt impact. When the wheel rim of the unit cam 611 contacts the lower vertical surface of the wedge-shaped adjusting block 53, it corresponds to the fully engaged position of the upper section of the connecting rod 52 and the positioning groove 41. At this time, it is also the stable and reliable meshing state of the oscillating gear 27 and the unit gear 32, ensuring the reliability and stability of torque transmission.

[0058] Example 2

[0059] When the operating mechanism of the speed change device provided in Example 1 is applicable to mechanical equipment such as lathes, it can serve as the basic transmission mechanism of the feed box, thereby forming a new scheme for the feed box of a lathe:

[0060] The feed box has a control panel on its housing 10 with a speed dial 20 for adjusting the speed of the basic group, a handle seat 1 for adjusting the speed of the multiplier group, and an adjustment handle 2 connected to a torque switching mechanism that selects the torque output to the lead screw or the guide rod. The basic group transmission mechanism is arranged in the basic group chamber 10A inside the housing 10, and the multiplier group transmission mechanism is arranged in the multiplier group chamber 10A inside the housing 10. The power output end of the basic group transmission mechanism is connected to the input end of the multiplier group transmission mechanism, and the power input end of the torque switching mechanism is connected to the power output end of the multiplier group transmission mechanism. The power output end of the torque switching mechanism is selectively connected to the power input end of the lead screw 4 or the guide rod 5.

[0061] The basic group has 6 to 12 unit gears 32 in the tower gear set 30, and the multiplier group has 4 speed ratios.

[0062] The feed box constructed by the above scheme makes almost no improvement to the existing multiplier gear transmission mechanism and torque switching mechanism. It only requires that the operating device of the speed change mechanism provided by this invention be used as the transmission and operating mechanism for the basic group speed of the feed box. As shown in the figure, when 8 unit gears 32 are selected and the multiplier gear has 4 speed ratios, the feed box can provide up to 24 speed ratios. The arrangement of the lead screw 4, guide rod 5, and operating lever connecting shaft 7 continues to adopt the existing arrangement scheme, undoubtedly meeting the basic requirements for shaft or thread machining. If 10 unit gears 32 are selected and the multiplier gear has 4 speed ratios, the feed box can provide up to 40 speeds. Of course, the number of unit gears 32 in the tower gear set 30 can be appropriately increased or decreased, i.e., set to meet the basic requirements for shaft or thread machining.

Claims

1. A control mechanism of a variable speed device, a speed dial (20) for adjusting the speed of a basic group is arranged on the control panel of a box (10), a basic group transmission mechanism is arranged in the box (10), characterized in that: The basic transmission mechanism includes a tower wheel shaft (31) with parallel shaft cores, a power input shaft (3), and a guide shaft (6). The tower wheel gear set (30) is fixedly connected to the tower wheel shaft (31). The guide frame (22) has a guide hole (221) at the rear, which forms a sliding guide fit with the guide shaft (6). The power input shaft (3) is a spline shaft, and the input gear (25) forms a spline sliding fit with the power input shaft (3). The swing gear (27) hinged to the swing end of the swing frame (29) always meshes with the input gear (25) on the power input shaft (3). A transmission mechanism is provided between the speed disk (20) and the guide frame (22) to drive the guide frame (22) to move along the direction defined by the guide shaft (6). The stroke slider (50) set on the guide frame (22) moves in a straight line direction perpendicular to the moving direction of the guide frame (22). The stroke slider (50) has a guide hole for the connecting rod (52) to pass through. Furthermore, the two form a sliding guide fit. The lower end of the connecting rod (52) located below the stroke slider (50) is hinged to the swing frame (29) by a cylindrical pin (28) parallel to the power input shaft (3). A positioning plate (40) is provided above the stroke slider (50). The edge of the positioning plate (40) facing the upper section of the connecting rod (52) exposed above the stroke slider (50) has a toothed positioning groove (41). A drive mechanism is provided between the handle (21) on the speed disk (20) and the stroke slider (50) to drive the stroke slider (50) to move to the upper section of the connecting rod (52) to engage or disengage with the positioning groove (41). When the upper section of the connecting rod (52) and the positioning groove (41) are in the engagement position, the swing gear (27) meshes with a unit gear (32) in the tower gear set (30). The rotation axis of the speed disk (20) is perpendicular to the axis direction of the power input shaft (3) and the guide shaft (6).

2. The shift device operating mechanism according to claim 1, characterized by: The inclined direction of the groove opening of the positioning groove (41) is consistent with the cone direction of the tower gear set (30).

3. The shift device operating mechanism according to claim 1, characterized by: The shaft cores of the power input shaft (3) and guide shaft (6) are located in the horizontal direction, and the rotation shaft core of the speed disk (20) is located in the horizontal direction or the rotation shaft core of the speed disk (20) is arranged at an angle to the horizontal direction.

4. The shift device operating mechanism according to claim 1 or 2 or 3, characterized by: The driving mechanism of the horizontal displacement drive stroke slider (50) includes a handle (21) on the turntable (20). The handle (21) and the turntable (20) are hinged by a threaded cylindrical pin (212), and the threaded cylindrical pin (212) is perpendicular to the rotation axis of the turntable (20). When the handle (21) swings around the threaded cylindrical pin (212), it drives the rack shaft (26) arranged in the hole of the turntable (20) to move inward and outward along the turntable (20) axis. The axis of the camshaft (60) is parallel to the axis of the power input shaft (3). When the rack shaft (26) moves inward and outward, it drives the camshaft (60) to rotate around its own axis. When the camshaft (60) rotates, the unit cam (611) in the cam tower group (61) set on its shaft abuts or separates from the stroke slider (50). The radial direction of the camshaft (60) is consistent with the radial direction of the cam tower group (61).

5. The gearshift operating mechanism according to claim 4, characterized in that: One end of the camshaft (60) has a spur gear (62), the core of the spur gear (62) coincides with the core of the camshaft (60), the inner section of the horizontal rack shaft (26) is an annular tooth segment (261) with the tooth tip and tooth valley extending in the circumferential direction, and the outer section of the rack shaft (26) is a strip hole or U-shaped groove (262). The handle (21) placed in the strip hole or U-shaped groove (262) is hinged to the rack shaft (26) by the handle pin (213). The handle pin (213) is perpendicular to the core of the strip hole or U-shaped groove (262) and the core of the rack shaft (26). The other end of the handle (21) relative to the gripping end is hinged to the speed disk (20) by a threaded cylindrical pin (212). The threaded cylindrical pin (212) and the handle pin (213) are set parallel to each other.

6. The shift device operating mechanism according to claim 4, characterized by: The end of the handle (21) away from the gripping end is detachably connected to the shift fork (211). The middle section of the shift fork (211) is placed in the strip hole (262) and is hinged by the handle pin (213). The other end of the shift fork (211) is a fork and a threaded cylindrical pin (212) is placed in the fork. The two ends of the threaded cylindrical pin (212) are connected to the pin seat (20B) provided on the outer wall of the convex section (20A) of the speed disk (20).

7. The shift device operating mechanism according to claim 5, characterized by: The central hole of the rotating disk (20) is a stepped hole with a larger outer diameter and a smaller inner diameter. The optical axis of the middle section of the rack shaft (26) slides and engages with the small diameter section of the central hole of the rotating disk (20). The outer section of the rack shaft (26) is a square block shape and is placed in the large hole section of the convex column section (20A). The convex column section (20A) has a through hole (20C) with the through direction consistent with the through direction of the strip hole (262).

8. The shift apparatus according to claim 1, wherein: The transmission mechanism that drives the guide frame (22) to move along the direction defined by the guide shaft (6) includes a shift gear (24) coaxially connected to the inner end of the turntable (20). The shift gear (24) meshes with the rack (23). The rack (23) is parallel to the power input shaft (3) and its tooth surface is facing upward on the guide frame (22).

9. A gear shift device operating mechanism according to claim 8, characterized in that: The shift gear (24) is coaxially connected to the inner end of the speed plate tube (20D) at the inner end of the speed plate (20). A positioning sleeve (20E) is provided between the speed plate (20), the speed plate tube (20D) and the mounting hole of the control panel of the feed box (10). The annular tooth section (261) of the inner section of the rack shaft (26) is exposed outside the speed plate tube (20D) and meshes with the spur gear (62) on the camshaft (60). The speed plate tube (20D) and the speed plate (20) are concentric and the rotation shaft is located in the horizontal direction.

10. The shift apparatus according to claim 4, wherein: The guide seat (70) and the stroke slider (50) are respectively in sliding fit with the guide key (222) and the linear guide rail (223) provided on the top surface of the guide frame (22). The guide direction of the guide key (222) and the linear guide rail (223) is horizontal and perpendicular to the axial direction of the guide shaft (6). A spring (54) is provided between the guide seat (70) and the stroke slider (50) to drive them to separate. The bottom surface of the positioning plate (40) and the top of the guide seat (70) and the stroke slider (50) form a limiting fit to restrict the separation distance between them.

11. The gearshift operating mechanism according to claim 10, characterized in that: The spring (54) is sleeved on the spring guide rod (55). The two ends of the spring guide rod (55) are respectively connected to the guide seat (70) and the stroke slider (50), and at least one of the guide seat (70) and the stroke slider (50) forms a sliding fit with the spring guide rod (55).

12. The shift apparatus according to claim 10, wherein: The bottom surface of the positioning plate (40) has a cavity (42). The first cavity wall (43) and the second cavity wall (44) of the cavity (42) are arranged opposite to each other and their walls are parallel to the surface where the positioning groove (41) is located. The distance between the first cavity wall (43) and the surface where the positioning groove (41) is located is greater than that between the second cavity wall (44) and the surface where the positioning groove (41) is located. The first cavity wall (43) and the second cavity wall (44) respectively form a limiting fit with the top of the guide seat (70) and the stroke slider (50) to limit the maximum distance between the two.

13. The operating mechanism of the transmission device according to claim 12, characterized in that: The top of the guide seat (70) is hinged to a slider (71), and the rotary shaft is located on the planar vertical surface of the slider (71) in the plumb direction and slides in cooperation with the first cavity wall (43).

14. The operating mechanism of the transmission device according to claim 12, characterized in that: The top of the stroke slider (50) has a bearing (56) with the shaft located in the vertical direction. The bearing (56) and the second cavity wall (44) form a separation or rolling contact fit.

15. The operating mechanism of the transmission device according to claim 4, characterized in that: The connecting rod (52) is arranged vertically and the vertical surface of the cylindrical pin (28) is spaced apart from the vertical surface of the power input shaft (3).

16. The operating mechanism of the transmission device according to claim 4, characterized in that: The lower section of the connecting rod (52) is a cylindrical shape with equal diameter. The upper section of the connecting rod (52) has a cylindrical cross-section facing the positioning groove (41) with a radius smaller than the cylindrical cross-section facing away from the positioning groove (41). The cylindrical surfaces on both sides are circumferentially extended and transitioned.

17. The operating mechanism of the transmission device according to claim 4, characterized in that: The stroke slider (50) is provided with a wedge-shaped adjustment block (53) on one side of the cam tower assembly (61). The upper inclined surface of the wedge-shaped adjustment block (53) is parallel to the camshaft (60) wheel core and the distance between it and the plumb surface of the camshaft (60) wheel core gradually approaches from top to bottom. The lower vertical surface of the wedge-shaped adjustment block (53) is parallel to the plumb surface of the camshaft (60) wheel core.

18. The operating mechanism of the transmission device according to claim 17, characterized in that: The unit cams (611) are arranged in a stepped manner on the same side of the circumference of the camshaft (60). The axial arrangement of the large and small diameter unit cams (611) is opposite to that of the large and small diameter unit gears (32) in the tower gear set (30). The top edge of the unit cam (611) is in the upper position separated from the wedge adjustment block (53) and the suspended position where the top edge abuts against the wedge adjustment block (53). The top edge of the unit cam (611) is in the upper position and the suspended position corresponding to the vertical position of the handle (21) and the built-in vertical position and the external inclined position, respectively.

19. A feed gearbox comprising the operating mechanism of the transmission device according to claims 1 to 18, characterized in that: The control panel of the housing (10) is equipped with a speed dial (20) for adjusting the speed of the basic group, a handle seat (1) for adjusting the speed of the multiplier group, and an adjustment lever handle (2) connected to the torque switching mechanism that selects the torque output to the lead screw or the guide rod. The basic group transmission mechanism is arranged in the basic group chamber (10A) inside the housing (10), and the multiplier group transmission mechanism is arranged in the multiplier group chamber (10A) inside the housing (10). The power output end of the basic group transmission mechanism is connected to the input end of the multiplier group transmission mechanism, and the power input end of the torque switching mechanism is connected to the power output end of the multiplier group transmission mechanism. The power output end of the torque switching mechanism is selected to be connected to the power input end of the lead screw or the guide rod.

20. The feed box according to claim 19, characterized in that: The basic group has 6 to 12 unit gears (32) in the tower gear set (30), and the multiplier group has 4 speed ratios.

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