Reverse buckling mechanism of turning and milling composite main shaft

Abstract

The utility model belongs to the field of turning and milling machining equipment, and particularly relates to a turning and milling composite spindle reverse buckling mechanism which comprises an end tooth piston, a gear ring set, a mandrel, a hydraulic cylinder, an outer sleeve and a casing pipe, the gear ring set comprises an outer positioning gear ring and an inner rotating gear ring, and the outer positioning gear ring surrounds the outer portion of the inner rotating gear ring. The end tooth piston is located on the upper side of the gear ring set, and the end tooth piston can be pressed towards the gear ring set under pressure so that the lower end face of the end tooth piston can be fixedly meshed with the upper end face of the gear ring set. And the spiral spring on the sleeve is compressed to absorb the pressure, so that the effect of buffering the pressure is achieved, and the situation that the bearing is damaged due to long-term compression caused by the fact that the pressure of the inner rotating gear ring is directly pressed to the bearing is avoided.

Description

Technical Field

[0001] This utility model belongs to the field of turning and milling machining equipment, specifically relating to a turning and milling composite spindle reverse coupling mechanism. Background Technology

[0002] Mill-turn machining is one of the most popular machining processes internationally. It is an advanced manufacturing technology. Mill-turn machining combines several different machining processes on a single machine tool, essentially a combination of a CNC lathe and a machining center.

[0003] In the initial state, there is a gap between the end-tooth piston and the gear ring assembly in the spindle axial direction. When turning is required, the end-tooth piston is subjected to the pressure of the oil pressure above, and the end-tooth piston presses against the gear ring assembly so that the lower end face of the end-tooth piston meshes and is fixed with the upper end face of the gear ring assembly. The pressure of the gear ring assembly will press against the bearing. The bearing is easily damaged by long-term pressure, which increases maintenance costs and requires frequent replacement, causing frequent work interruptions. Utility Model Content

[0004] Therefore, the technical problem to be solved by this utility model is to overcome the fact that the bearings of the milling and turning spindle are subjected to oil pressure every time they are switched from milling mode to turning mode, which makes the bearings easy to be damaged, increases maintenance costs, and requires frequent replacement, causing frequent interruptions to work.

[0005] To solve the above-mentioned technical problems, this utility model provides a reverse-clamping mechanism for a milling and turning composite spindle, including an end-tooth piston, a gear ring assembly, a spindle, a hydraulic cylinder, an outer sleeve, and a bushing. The gear ring assembly includes an outer positioning gear ring and an inner rotating gear ring. The outer positioning gear ring surrounds the outer side of the inner rotating gear ring. The end-tooth piston is located on the upper side of the gear ring assembly and can be pressed against the gear ring assembly so that the lower end face of the end-tooth piston meshes and is fixed with the upper end face of the gear ring assembly.

[0006] The sleeve includes a radially distributed mounting portion and a reverse-threaded portion. Along the axial direction of the main shaft, the sleeve is located between the outer sleeve and the hydraulic cylinder. The mounting portion has a through hole near its outer edge, and the outer sleeve has a threaded blind hole near its outer edge. The through hole and the threaded blind hole can be simultaneously inserted by an internal hexagon screw. The internal hexagon screw includes an axially distributed locking portion and a rod portion. The locking portion has threads on its exterior and is located inside and threadedly connected to the threaded blind hole. The axial length of the threaded blind hole is greater than the axial length of the locking portion. The rod portion is located inside the through hole, which is stepped and includes a large-diameter portion and a small-diameter portion distributed vertically. A helical spring is fitted on the upper half of the rod portion. The helical spring is located in the large-diameter portion, and the lower end of the helical spring can abut against the lower wall of the large-diameter portion. The lower end of the inner rotating toothed ring and the upper end of the outer sleeve can form a receiving cavity, and the reverse-threaded portion is located inside the receiving cavity.

[0007] Preferably, the inner diameter of the threaded blind hole is smaller than the inner diameter of the through hole, and the diameter of the shank is equal to the inner diameter of the through hole.

[0008] Preferably, the outer wall of the inner rotating gear ring is three-step shaped, including a first step, a second step, and a third step from bottom to top along the main shaft axis, and the radial height of the first step, the second step, and the third step gradually increases. The upper end face of the outer sleeve is provided with a lower groove, the outer wall of the second step and the side wall of the third step form an upper groove, and the lower groove and the upper groove surround the receiving cavity.

[0009] Preferably, the upper end face of the hydraulic cylinder is provided with a pressure supply hole and a pressure release hole, and the circumferential surface of the hydraulic cylinder is provided with a pressure release channel and a pressure release channel. The upper end of the pressure release channel is connected to the pressure supply hole, and the lower end opening of the pressure release channel is located on the upper side of the end tooth piston. The upper end of the pressure release channel is connected to the pressure release hole, and the lower end opening of the pressure release channel is located on the lower side of the end tooth piston.

[0010] The technical solution of this utility model has the following beneficial effects:

[0011] When the end-tooth piston is subjected to the pressure of the oil pressure above, it presses against the gear ring assembly, so that the lower end face of the end-tooth piston meshes and is fixed with the upper end face of the gear ring assembly. This causes the inner rotating gear ring and the spindle to move forward until the lower end face of the inner rotating gear ring hits the reverse engagement part. The reverse engagement part then acts on the outer sleeve, and the pressure of the outer sleeve then acts on the sleeve (that is, from bottom to top along the main shaft axis), causing the sleeve to press over from the back of the helical spring, compressing the helical spring and allowing the helical spring to reach its maximum load, thus playing a role in buffering pressure and preventing the pressure of the inner rotating gear ring from directly pressing on the bearing. Attached Figure Description

[0012] To more clearly illustrate the specific embodiments of this utility model or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0013] Figure 1 This is a perspective view of the appearance of this utility model;

[0014] Figure 2 This is a side view of the present invention;

[0015] Figure 3 for Figure 2 A cross-sectional view along the AA direction;

[0016] Figure 4 for Figure 2 A cross-sectional view along the BB direction;

[0017] Figure 5 This is a three-dimensional sectional view of the present invention;

[0018] Figure 6 for Figure 5 Enlarged schematic diagram of part A;

[0019] Figure 7 for Figure 5 Enlarged diagram of part A (and) Figure 6 The parts labeled are different.

[0020] Explanation of reference numerals in the attached drawings: 1. End-tooth piston; 2. Gear ring assembly; 21. Positioning gear ring; 22. Inner rotating gear ring; 221. First step; 222. Second step; 223. Third step; 3. Mandrel; 4. Hydraulic cylinder; 5. Outer sleeve; 51. Threaded blind hole; 52. Lower slot; 6. Sleeve; 61. Mounting part; 611. Through hole; 611a. Large diameter part; 611b. Small diameter part; 62. Reverse thread part; 7. Socket head cap screw; 71. Locking part; 72. Rod part; 8. Helical spring; 9. Upper slot; 10. Pressure supply hole; 11. Pressure release hole; 12. Lower pressure channel; 13. Pressure release channel. Detailed Implementation

[0021] The technical solution of this utility model will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this utility model. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this utility model.

[0022] In the description of this utility model, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings and are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or component referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0023] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0024] Furthermore, the technical features involved in the different embodiments of this utility model described below can be combined with each other as long as they do not conflict with each other.

[0025] This utility model provides a reverse-threading mechanism for a milling and turning composite spindle, including an end-tooth piston 1, a gear ring assembly 2, a spindle 3, a hydraulic cylinder 4, an outer sleeve 5, and a sleeve 6. The gear ring assembly 2 includes an outer positioning gear ring 21 and an inner rotating gear ring 22, with the outer positioning gear ring 21 surrounding the outer side of the inner rotating gear ring 22. The sleeve 6 includes a radially distributed mounting portion 61 and a reverse-threading portion 62. Along the spindle axis, the sleeve 6 is located between the outer sleeve 5 and the hydraulic cylinder 4. The mounting portion 61 has a through hole 611 near its outer edge, and the outer sleeve 5 has a threaded blind hole 51 near its outer edge. The through hole 611 and the threaded blind hole 51 can be simultaneously inserted by a hexagon socket screw 7. The hexagon socket screw 7 includes axially distributed... The locking part 71 and the rod part 72 are provided. The locking part 71 is threaded on the outside. The locking part 71 is located in the threaded blind hole 51 and is threadedly connected to the threaded blind hole 51. The axial length of the threaded blind hole 51 is greater than the axial length of the locking part 71. The rod part 72 is located in the through hole 611. The through hole 611 is stepped and includes a large diameter part 611a and a small diameter part 611b distributed vertically. The upper half of the rod part 72 is fitted with a helical spring 8. The helical spring 8 is located in the large diameter part 611a. The lower end of the helical spring 8 can abut against the lower wall surface of the large diameter part 611a. The lower end of the inner rotating toothed ring 22 and the upper end of the outer sleeve 5 can form a receiving cavity. The reverse buckle part 62 is located in the receiving cavity.

[0026] The mounting part 61 of the sleeve 6 in this utility model is mainly used to insert the internal hexagon screw 7. The main function of the internal hexagon screw 7 is to connect the sleeve 6 and the outer sleeve 5 together, but the two are not completely fixed. In the initial state, there is a gap between the end-tooth piston 1 and the toothed ring assembly 2 in the axial direction of the main shaft. When the end-tooth piston 1 is subjected to the pressure of the upper oil pressure, it presses against the toothed ring assembly 2, so that the lower end face of the end-tooth piston 1 meshes and fixes with the upper end face of the toothed ring assembly 2. This causes the inner rotating toothed ring 22 and the spindle 3 to move forward until the lower end face of the inner rotating toothed ring 22 hits the reverse engagement part 62. The reverse engagement part 62 then acts on the outer sleeve 5, and the pressure of the outer sleeve 5 then acts on the sleeve 6 (that is, from bottom to top along the axial direction of the main shaft), so that the sleeve 6 presses over from the back side of the helical spring 8, compressing the helical spring 8, so that the helical spring 8 reaches the maximum load and plays a role in buffering pressure. If the reverse engagement function is designed, the oil pressure of the hydraulic cylinder 4 will be directly transmitted to the bearing through the end-tooth piston 1, which will reduce the bearing life and performance.

[0027] In order to prevent interference with the locking part 71 when the pressure of the outer sleeve 5 acts on the sleeve 6 (that is, from bottom to top along the main shaft axis) as the outer sleeve 5 moves from bottom to top, there is a buffer gap between the end face of the locking part 71 and the lower wall of the threaded blind hole 51 in the initial state.

[0028] To ensure accurate positioning of the socket head cap screw 7 when it is inserted into the threaded blind hole 51, the inner diameter of the threaded blind hole 51 is smaller than the inner diameter of the through hole 611, and the diameter of the shank 72 is equal to the inner diameter of the through hole 611. When the lower end face of the shank 72 abuts against the upper end face of the outer sleeve 5, the socket head cap screw 7 is installed in the threaded blind hole 51 and the through hole 611.

[0029] The outer wall of the inner rotating gear ring 22 is three-step in shape, including a first step 221, a second step 222 and a third step 223 from bottom to top along the main axis, and the radial height of the first step 221, the second step 222 and the third step 223 gradually increases. The upper end face of the outer sleeve 5 is provided with a lower groove 52. The outer wall of the second step 222 and the side wall of the third step 223 form an upper groove 9. The lower groove 52 and the upper groove 9 form a receiving cavity.

[0030] When the end-tooth piston 1 engages with both the outer positioning gear ring 21 and the inner rotating gear ring 22, the spindle and the outer sleeve 5 are relatively fixed, and the milling-turning spindle is used for turning. When the end-tooth piston 1 moves upward and resets, it disengages from the outer positioning gear ring 21 and the inner rotating gear ring 22. Then, when the motor drives and rotates the pulley, the spindle 3 rotates within the outer sleeve 5, and the milling-turning spindle is used for milling.

[0031] The upper end face of the hydraulic cylinder 4 is provided with a pressure supply hole 10 and a pressure release hole 11. The circumferential surface of the hydraulic cylinder 4 is provided with a pressure release channel 12 and a pressure release channel 13. The upper end of the pressure release channel 12 is connected to the pressure supply hole 10, and the lower end opening of the pressure release channel 12 is located above the end tooth piston 1. The upper end of the pressure release channel 13 is connected to the pressure release hole 11, and the lower end opening of the pressure release channel 12 is located below the end tooth piston 1. When the spindle needs to perform turning, hydraulic oil is introduced into the pressure supply hole 10. The hydraulic oil is input into the pressure release channel 12 and then comes out from the lower end of the pressure release channel 12, pressing down the end tooth piston 1. When the spindle needs to perform milling, hydraulic oil or gas is introduced into the pressure release hole 11. The hydraulic oil or gas is input into the pressure release channel 13 and then comes out from the lower end of the pressure release channel 13, causing the end tooth piston 1 to move upward and reset.

[0032] Obviously, the above embodiments are merely illustrative examples for clear explanation and are not intended to limit the implementation. Those skilled in the art will recognize that other variations or modifications can be made based on the above description. It is neither necessary nor possible to exhaustively list all possible implementations here. However, obvious variations or modifications derived therefrom are still within the protection scope of this invention.

Claims

1. A reverse clamping mechanism for a turning-milling composite spindle, comprising an end-toothed piston (1), a toothed ring set (2), a mandrel (3), a hydraulic cylinder (4) and an outer sleeve (5), the toothed ring set (2) comprising an outer positioning toothed ring (21) and an inner rotating toothed ring (22), the outer positioning toothed ring (21) being wrapped outside the inner rotating toothed ring (22), the end-toothed piston (1) being located on the upper side of the toothed ring set (2), the end-toothed piston (1) being capable of being pressed towards the toothed ring set (2) so that the lower end surface of the end-toothed piston (1) is engaged and fixed with the upper end surface of the toothed ring set (2), characterized in that, it further comprises a sleeve (6) comprising a mounting portion (61) and a reverse clamping portion (62) distributed in the radial direction, along the axial direction of the spindle, the sleeve (6) being located between the outer sleeve (5) and the hydraulic cylinder (4), the mounting portion (61) being provided with a through hole (611) near the outer edge position, the outer sleeve (5) being provided with a threaded blind hole (51) near the outer edge position, the through hole (611) and the threaded blind hole (51) being capable of being penetrated by a hexagonal socket head cap screw (7) at the same time, the hexagonal socket head cap screw (7) comprising a locking portion (71) and a rod portion (72) distributed in the axial direction, the locking portion (71) being provided with a thread on the outside, the locking portion (71) being located in the threaded blind hole (51) and being threadedly connected with the threaded blind hole (51), and the axial length value of the threaded blind hole (51) being greater than the axial length value of the locking portion (71), the rod portion (72) being located in the through hole (611), the through hole (611) being stepped, comprising a large-diameter portion (611a) and a small-diameter portion (611b) distributed in the upper and lower directions, the upper half of the rod portion (72) being sleeved with a coil spring (8), the coil spring (8) being located in the large-diameter portion (611a), the lower end of the coil spring (8) being capable of abutting against the lower wall surface of the large-diameter portion (611a), the lower end of the inner rotating toothed ring (22) and the upper end of the outer sleeve (5) being capable of being enclosed to form an accommodating cavity, the reverse clamping portion (62) being located in the accommodating cavity. The inner diameter of the threaded blind hole (51) is smaller than the inner diameter of the through hole (611), and the diameter of the rod portion (72) is equal to the inner diameter of the through hole (611).

2. The turn-mill-composite spindle counter-buckle mechanism according to claim 1, characterized in that, The outer wall surface of the inner rotating toothed ring (22) is three-stepped, comprising a first step (221), a second step (222) and a third step (223) from the lower to the upper along the axial direction of the spindle, and the radial height of the first step (221), the second step (222) and the third step (223) gradually increases, the upper end surface of the outer sleeve (5) is provided with a lower clamping groove (52), the outer wall surface of the second step (222) and the side wall surface of the third step (223) form an upper clamping groove (9), and the lower clamping groove (52) and the upper clamping groove (9) enclose the accommodating cavity.

3. The turn-mill-composite spindle counter-buckle mechanism according to claim 1, characterized in that, ​ 4. The turn-mill-composite spindle counter-buckle mechanism according to claim 1, characterized in that, The upper end surface of the hydraulic cylinder (4) is provided with a pressure supply hole (10) and a pressure relief hole (11), the circumferential surface of the hydraulic cylinder (4) is provided with a pressure channel (12) and a pressure relief channel (13), the upper end of the pressure channel (12) is communicated with the pressure supply hole (10), the lower end of the pressure channel (12) is opened on the upper side of the end-toothed piston (1), the upper end of the pressure relief channel (13) is communicated with the pressure relief hole (11), and the lower end of the pressure channel (12) is opened on the lower side of the end-toothed piston (1).

Images