Double-station combined tilting grinder

Abstract

The application relates to the technical field of grinding processing, and discloses a double-station combined inclined knife grinder. In order to solve the problem that a single grinding head cannot guarantee the grinding precision of two angle surfaces of the same workpiece, two face-to-face rotatable grinding heads are installed on the same machine tool, so that the design purpose is to simultaneously grind different V-shaped surfaces. The knife grinder can complete the required angle surface of the workpiece in the same reference clamping, and feeds according to the required angle based on intelligent control, so that the goal of improving the work efficiency by two times is achieved, and the effect of double-station inclined grinding is achieved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of grinding processing, and particularly relates to a double-station combined inclined knife grinder. BACKGROUND

[0002] The inclined knife grinder is mainly used for processing special-shaped cutters such as inclined grooves and V-shaped grooves. These special-shaped cutters have a wide range of applications in industrial production. For example, in the field of metal processing, inclined groove and V-shaped groove cutters can be used for cutting, punching, milling and other operations to improve production efficiency and quality.

[0003] The current knife grinding technology usually adopts the mode of installing a grinding head in a single direction to grind the surface of a workpiece. However, in actual application, this single-inclined grinding head mode has some limitations. First, a single inclined grinding head can only grind the surface in one angle direction, so for a workpiece that needs to be ground in multiple angle directions, the grinding head angle needs to be changed multiple times, resulting in low grinding efficiency. Second, when the precision requirements of two angle surfaces of the same workpiece are high, the single-inclined grinding head mode often cannot meet the processing requirements, and errors and deviations are prone to occur. SUMMARY

[0004] The present application provides a double-station combined inclined knife grinder, which has the advantages of double-station inclined grinding and effectively solves the problem that a single grinding head cannot guarantee the grinding precision of two angle surfaces of the same workpiece.

[0005] To achieve the above-mentioned purpose, the present application adopts the following technical scheme: a double-station combined inclined knife grinder, comprising: a machine base, the surface of which is provided with two facing transverse sliding blocks, the transverse sliding blocks move back and forth on the surface of the machine base, a vertical sliding block moves up and down on the transverse sliding block, a horizontal sliding seat moves left and right on the vertical sliding block, a control box is fixed on the side of the machine base for electrical control; a guide sliding block is movably installed at the bottom of the horizontal sliding seat, one end of the guide sliding block is fixed with a power support, and the top end of the power support is fixedly installed with a power motor; a power guide rod is fixed at the top end of the power motor and is fixedly connected with a grinding head at the bottom end, and a driving gear is threadedly connected to the outer side of the middle part of the power guide rod; a transposition support is fixed on the side of the power support, a transfer shaft is movably installed on the side of the transposition support, a middle transmission gear is arranged on the top of the transfer shaft and is in external gear meshing with the driving gear, and the middle transmission gear and the transfer shaft are in one-way transmission, a driving bevel gear is arranged on the bottom of the transfer shaft, and a driven bevel gear is movably installed on the other side of the transposition support and is in external gear meshing with the driving bevel gear, and the shaft of the driven bevel gear is fixedly connected with a transposition gear; a positioning gear is arranged on the inner side of the horizontal sliding seat and is in meshing with the transposition gear.

[0006] Further, a position detection grating is movably installed on the surface of the horizontal sliding seat, and the guide sliding block is located on the outer side of the position detection grating.

[0007] Further, the intermediate transmission gear is sleeved on the transfer shaft, the side of the transfer shaft movably mounts a limiting column, a limiting spring is arranged between the limiting column and the transfer shaft, and the inner side middle part of the intermediate transmission gear is fixedly connected with a one-way rotation tooth.

[0008] Further, the power guide rod is provided with a transposition screw groove for threadedly connecting with the driving gear, the power guide rod is sleeved with a transposition ring sleeve located below the driving gear, the bottom of the transposition ring sleeve movably mounts an intermediate transmission rod, and the bottom end of the intermediate transmission rod movably mounts a lock tooth head, a limiting spring is arranged between the lock tooth head and the transposition ring sleeve.

[0009] Further, the top end of the intermediate transmission rod is located above the intermediate transmission gear after penetrating through the driving bevel gear, the transfer shaft and the intermediate transmission gear, and the top end of the intermediate transmission rod is fixedly connected with a return ball; the top of the horizontal sliding seat is provided with a reset groove, the inner side of the horizontal sliding seat movably mounts a return baffle located at the end of the reset groove, and a tension spring is arranged between the return baffle and the horizontal sliding seat; the inner side of the horizontal sliding seat is provided with a return protruding tooth located at the end of the positioning tooth row, the other end of the positioning tooth row is provided with a return groove, the cross section of the return protruding tooth is tapered, and the return protruding tooth is higher than the positioning tooth row; the inner top of the intermediate transmission gear movably mounts a disengagement spring.

[0010] Further, the return baffle located at one end of the reset groove is higher than the other end of the reset groove.

[0011] Further, a speed limiting mechanism is arranged in the intermediate transmission gear to avoid the power support from returning too fast.

[0012] Further, the speed limiting mechanism comprises an increased resistance tooth arranged in the inner side of the intermediate transmission gear, the increased resistance tooth is located below the one-way rotation tooth, and any one of the one-way increased resistance tooth protrudes outward.

[0013] Further, the speed limiting mechanism comprises a speed reduction rubber ring arranged at the end of the intermediate transmission gear.

[0014] Further, the middle part of the intermediate transmission rod is a cuboid; the inner side of the intermediate transmission rod movably mounts a force adding rod, the top end of the force adding rod movably connects with a forced top return rod, and a forced return top spring is arranged between the bottom end of the force adding rod and the intermediate transmission rod; one end of the limiting column is fixedly connected with a speed reduction top rod located at one side of the force adding rod, and the top end of the intermediate transmission gear is provided with an inclined angle.

[0015] The present application has the following beneficial effects:

[0016] The double-station combined inclined grinding machine provided by the application comprises two facing rotatable grinding heads installed on the same machine tool, which can simultaneously grind different V-shaped surfaces. The grinding machine can complete the required angle surface of the workpiece in the same reference clamping and feed the required angle according to intelligent control, thereby achieving the goal of doubling the work efficiency and realizing the effect of double-station inclined grinding.

[0017] The double-station design means that two surfaces of the workpiece can be ground simultaneously during processing. Such design not only improves production efficiency, but also ensures the precision of the workpiece. Because of the simultaneous processing of two surfaces, the deformation and distortion of the workpiece can be reduced, thereby avoiding the precision error caused by single-surface processing. BRIEF DESCRIPTION OF DRAWINGS

[0018] The accompanying drawings, which form a part of the specification, illustrate the embodiments of the present application and serve to explain the principles of the present application.

[0019] The present application can be more clearly understood by referring to the following detailed description in conjunction with the accompanying drawings, in which:

[0020] Figure 1 is a schematic diagram of the overall three-dimensional structure of the outer shape;

[0021] Figure 2 is a schematic diagram of the overall three-dimensional structure of the side surface;

[0022] Figure 3 is a schematic diagram of the front three-dimensional structure of the horizontal slide;

[0023] Figure 4 is a schematic diagram of the back three-dimensional structure of the horizontal slide;

[0024] Figure 5 is a schematic diagram of the back plane of the horizontal slide;

[0025] Figure 6 is a schematic diagram of the overall cross-sectional structure of the middle part of the horizontal slide;

[0026] Figure 7 is a schematic diagram of the overall cross-sectional structure of the middle part of the horizontal slide; Figure 6

[0027] is a schematic diagram of the overall cross-sectional structure of the middle part of the horizontal slide; Figure 8

[0028] is a schematic diagram of the overall cross-sectional structure of the middle part of the horizontal slide; Figure 9

[0029] is a schematic diagram of the overall cross-sectional structure of the middle part of the horizontal slide; Figure 10

[0030] ​In the figure: 1, base; 2, control box; 3, fixed table; 4, transverse sliding block; 5, vertical sliding block; 6, horizontal sliding seat; 7, power motor; 8, grinding head; 9, power guide rod; 900, transposition chute; 10, guide sliding block; 11, position detection grating; 12, power support; 120, transposition support; 13, drive gear; 14, return baffle; 15, reset channel; 16, transposition gear; 17, intermediate transmission gear; 170, one-way rotating tooth; 171, resistance increasing tooth; 18, return ball; 19, deceleration rubber ring; 20, driving bevel gear; 21, driven bevel gear; 22, positioning tooth row; 220, return groove; 221, return convex tooth; 23, limit spring; 24, locking tooth head; 25, transposition ring sleeve; 26, intermediate transmission rod; 27, intermediate shaft; 28, disengagement spring; 29, forced return rod; 30, force amplification rod; 31, limiting column; 310, limiting spring; 311, deceleration ejector rod; 32, forced return spring. DETAILED DESCRIPTION

[0031] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by a person of ordinary skill in the art without creative work fall within the scope of protection of the present application.

[0032] Embodiment one

[0033] Please refer to Figure 1 and Figure 2 It can be seen that two transverse sliding blocks 4 are arranged on the slide rails on the surface of the base 1, and the transverse sliding blocks 4 and the base 1 are connected by means of servo motors and lead screws, so that the transverse sliding blocks 4 can move forward and backward on the surface of the base 1. Since the two transverse sliding blocks 4 are arranged face to face, the two transverse sliding blocks 4 can move close to or away from each other by driving the lead screws by the servo motors. Similarly, vertical sliding blocks 5 capable of moving up and down are arranged on the transverse sliding blocks 4, and horizontal sliding seats 6 capable of moving left and right are arranged on the vertical sliding blocks 5. The movement of the vertical sliding blocks 5 on the transverse sliding blocks 4 and the movement of the horizontal sliding seats 6 on the vertical sliding blocks 5 are both driven by servo motors and lead screws. In order to control the movement, a control box 2 is fixed to the side of the base 1 by bolts, so that the precise movement of the transverse sliding blocks 4, the vertical sliding blocks 5 and the horizontal sliding seats 6 can be realized by intelligent control of the control box 2.

[0034] In order to simultaneously machine two angle surfaces of the same workpiece and ensure the machining precision, in combination with Figure 3 and Figure 4The bottom of the horizontal slide 6 is movably mounted with a guide sliding block 10, which can only move back and forth along the path of the bottom of the horizontal slide 6, and one end of the guide sliding block 10 is fixedly mounted with a power support 12 located at the middle of the horizontal slide 6, and the power support 12 is movably mounted with a power guide rod 9, and the other end of the power guide rod 9 is fixedly mounted with a grinding head 8. Figure 4 As can be clearly seen from the figure, the top end of the power support 12 is fixedly mounted with a power motor 7 for providing power, and the power guide rod 9 is fixed on the output shaft of the power motor 7, and the grinding head 8 is fixed on the end of the power guide rod 9, so that the grinding head 8 is driven to rotate by the power motor 7 through the power guide rod 9, and the workpiece can be ground by the grinding head 8.

[0035] The outer side of the power guide rod 9 is threadedly connected with a drive gear 13, and the drive gear 13 is fixedly connected with a transmission gear 14. Figure 4 And Figure 6 As can be clearly seen from the figure, the side of the power support 12 is fixedly connected with a transposition support 120, and the transposition support 120 is in the shape of L, and the side of the transposition support 120 is movably mounted with a transfer shaft 27 parallel to the central axis of the power guide rod 9, and the top of the transfer shaft 27 is provided with an intermediate transmission gear 17 engaged with the outer gear of the drive gear 13, and the intermediate transmission gear 17 and the transfer shaft 27 are in one-way transmission, so that when the power motor 7 is reversed, the intermediate transmission gear 17 is not reversed synchronously with the drive gear 13, and the bottom of the transfer shaft 27 is fixedly connected with a driving bevel gear 20, and the other side of the transposition support 120 is movably mounted with a driven bevel gear 21 engaged with the outer gear of the driving bevel gear 20, so that when the intermediate transmission gear 17 rotates with the drive gear 13, the driving bevel gear 20 and the driven bevel gear 21 rotate synchronously through the transmission of the transfer shaft 27, and the rotating shaft of the driven bevel gear 21 is fixedly connected with a transposition gear 16, and the inner side of the horizontal slide 6 is provided with a positioning tooth row 22 engaged with the transposition gear 16, so that when the transposition gear 16 rotates on the positioning tooth row 22, the power support 12 and the guide sliding block 10 will be deflected on the horizontal slide 6, so as to change the grinding angle of the grinding head 8.

[0036] In order to make the two grinding heads 8 easy to build the deflection angle of the V-shaped groove, the Figure 2 And Figure 5 As can be clearly seen from the figure, the positioning tooth row 22 is in the shape of an arc, and the center point of the positioning tooth row 22 is at the top vertex of the bottom side of the grinding head 8 (the black dot in the figure is the rotating point), so that when the guide sliding block 10 rotates according to the positioning tooth row 22, the grinding head 8 can rotate around the rotating point, so as to Figure 2 As can be clearly seen from the figure, when the rotating points of the two grinding heads 8 overlap, the angle between the two grinding heads 8 can be adjusted only by the movement of the guide sliding block 10 on the horizontal slide 6, so that the angle between the two grinding heads 8 can be quickly determined.

[0037] In order to make the two grinding heads 8 easy to build the deflection angle of the V-shaped groove, the Figure 3 And Figure 6As can be seen, the surface of the horizontal sliding seat 6 is movably provided with a position detection grating 11, and the guide sliding block 10 is located outside the position detection grating 11. In actual application, the position of the guide sliding block 10 is detected by the position detection grating 11, so that the deflection angle of the grinding head 8 can be quickly known, and the accurate control of the deflection angle of the grinding head 8 is ensured.

[0038] In actual application, the workpiece is fixed on the fixed table 3 inside the base 1, and the workpiece is stably placed by the clamping component on the fixed table 3. When the V-shaped chute needs to be machined on the workpiece, the control box 2 is used to control the horizontal sliding block 4 to move forward and backward, so that the horizontal sliding blocks 4 are close to each other. Then, the vertical sliding block 5 and the horizontal sliding seat 6 are controlled to make the rotation points of the grinding heads 8 coincide, as shown in Figure 2 .

[0039] Finally, the power motor 7 is reversely rotated, so that the driving gear 13 drives the intermediate transmission gear 17 to rotate. Since the intermediate transmission gear 17 and the intermediate shaft 27 are in one-way transmission, when the intermediate transmission gear 17 reversely rotates with the power motor 7, the intermediate transmission gear 17 can drive the intermediate shaft 27 to rotate. Then, the driving bevel gear 20 is rotated by the intermediate shaft 27, so that the driven bevel gear 21 drives the transposition gear 16 to rotate on the positioning tooth row 22. Thus, according to the rotation of the transposition gear 16 on the positioning tooth row 22, the guide sliding block 10 is deflected, and finally the included angle between the grinding heads 8 is deflected. When the included angle between the grinding heads 8 is consistent with the required machining angle of the workpiece, the power motor 7 is forwardly rotated, so that the intermediate transmission gear 17 no longer drives the intermediate shaft 27 to rotate, and the angle adjustment is no longer performed. Then, according to the synchronous movement of the two horizontal sliding blocks 4 and the height adjustment of the vertical sliding block 5, the grinding of the workpiece is realized.

[0040] Embodiment Two

[0041] On the basis of the embodiment one, further improvement is made. In order to prevent the guide sliding block 10 from being deviated on the horizontal sliding seat 6 during the grinding of the workpiece by the grinding head 8, so that the grinding angle of the grinding head 8 is changed, the grinding head 8 is locked on the horizontal sliding seat 6 during the grinding of the workpiece, please refer to Figure 4 and Figure 6 As can be seen, the power guide rod 9 is provided with a transposition screw channel 900 outside for threadedly connecting with the driving gear 13, and the length of the transposition screw channel 900 is 2-4 times the thickness of the driving gear 13, so that the driving gear 13 has a tendency of reciprocating along the center line of the power guide rod 9 during the rotation of the power guide rod 9.

[0042] The outer side of the power guide rod 9 is sleeved with a transposition ring sleeve 25 below the driving gear 13, and the bottom of the transposition ring sleeve 25 is movably installed with an intermediate transmission rod 26 through an "L" shaped frame, and the bottom end of the intermediate transmission rod 26 is movably installed with a locking tooth head 24, a limiting spring 23 is arranged between the locking tooth head 24 and the "L" shaped frame of the transposition ring sleeve 25, so that the locking tooth head 24 is clamped on the positioning tooth row 22 through the elastic force of the limiting spring 23, thereby limiting the movement of the power support 12.

[0043] In actual application, when the power motor 7 drives the power guide rod 9 to rotate forward, at this time, the grinding head 8 is in a working state, in order to prevent the power support 12 from deviating on the horizontal sliding seat 6, in combination with Figure 6 It can be seen that when the power guide rod 9 rotates forward, the transposition ring sleeve 25 is clamped below the driving gear 13 by the elastic force of the limiting spring 23, so that when the driving gear 13 and the transposition screw track 900 relatively rotate, the driving gear 13 has a downward movement trend according to the transposition screw track 900, and since the intermediate transmission gear 17 and the intermediate shaft 27 are in one-way transmission at this time, the transposition gear 16 will not rotate.

[0044] After the driving gear 13 continuously moves downward, it will be separated from the intermediate transmission gear 17, at the same time, the limiting spring 23 is compressed by the downward pressure of the driving gear 13, so that the strength of the locking tooth head 24 clamped on the positioning tooth row 22 is increased, thereby forcing the power support 12 not to deviate on the horizontal sliding seat 6 during work, ensuring the stability of work.

[0045] When the power motor 7 reversely rotates, at this time, it is necessary to change the position, as described above, when the power motor 7 drives the power guide rod 9 to reversely rotate, the driving gear 13 moves upward along the transposition screw track 900, the transposition ring sleeve 25 moves upward with the driving gear 13, and the compression of the limiting spring 23 is reduced, but at this time, the locking tooth head 24 is still clamped on the positioning tooth row 22, thereby preventing the power support 12 from deviating, as the driving gear 13 moves upward and gradually engages with the intermediate transmission gear 17, since the intermediate transmission gear 17 and the intermediate shaft 27 are in transmission state when the driving gear 13 reversely rotates, the transposition gear 16 is forced to rotate on the positioning tooth row 22, since the rotation of the transposition gear 16 drives the power support 12 to overcome the movement limitation of the power support 12 by the locking tooth head 24, so that the locking tooth head 24 moves with the power support 12, until the transposition gear 16 stops, the locking tooth head 24 is always clamped on the positioning tooth row 22 by the elastic force of the limiting spring 23, so that after the transposition gear 16 stops moving, the power support 12 still maintains the state of not deviating, finally, the limiting spring 23 is compressed again by the forward rotation of the power motor 7, so as to ensure the stability of the grinding head 8 during grinding.

[0046] Example three

[0047] On the basis of the first and second embodiments, in order to further disclose the one-way transmission between the intermediate transmission gear 17 and the intermediate shaft 27, please refer to Figure 8 and Figure 9 As can be seen, the intermediate transmission gear 17 is sleeved on the intermediate shaft 27, the side of the intermediate shaft 27 is movably mounted with a limiting column 31, and a limiting spring 310 is arranged between the limiting column 31 and the intermediate shaft 27, so that the limiting column 31 is always forced to move towards the inside of the intermediate transmission gear 17 according to the elasticity of the limiting spring 310, and the inside middle of the intermediate transmission gear 17 is fixedly connected with a one-way rotation tooth 170, so that the intermediate transmission gear 17 and the intermediate shaft 27 can only be one-way transmission from Figure 8 As can be seen from the figure, the cross-sectional shape of the one-way rotation tooth 170 is a right triangle, so that when the limiting column 31 is pushed out by the elastic force of the limiting spring 310, it is limited by the one-way rotation tooth 170, so that the intermediate transmission gear 17 and the intermediate shaft 27 can only be one-way transmission.

[0048] As can be seen from the figure, the number of limiting columns 31 is seven, which can be adjusted as needed in actual production, and the seven limiting columns 31 are arranged in a ring shape, and the angle between adjacent two limiting columns 31 gradually increases, which can avoid all limiting columns 31 contacting the one-way rotation tooth 170 at the same time, so that axial movement is not easy to occur. Figure 8 As can be seen from the figure, the number of limiting columns 31 is seven, which can be adjusted as needed in actual production, and the seven limiting columns 31 are arranged in a ring shape, and the angle between adjacent two limiting columns 31 gradually increases, which can avoid all limiting columns 31 contacting the one-way rotation tooth 170 at the same time, so that axial movement is not easy to occur.

[0049] As can be seen from the figure, the number of limiting columns 31 is seven, which can be adjusted as needed in actual production, and the seven limiting columns 31 are arranged in a ring shape, and the angle between adjacent two limiting columns 31 gradually increases, which can avoid all limiting columns 31 contacting the one-way rotation tooth 170 at the same time, so that axial movement is not easy to occur. Figures 4-6 As can be seen from the figure, the top end of the intermediate transmission rod 26 is located above the intermediate transmission gear 17 after passing through the driving bevel gear 20, the intermediate shaft 27 and the intermediate transmission gear 17, and the top end of the intermediate transmission rod 26 is fixedly connected with a return ball 18, and the return ball 18 is a smooth spherical shape, in combination with Figure 4 As can be seen from the figure, the top of the horizontal sliding seat 6 is provided with a reset channel 15, and the inside of the horizontal sliding seat 6 is movably mounted with a return baffle 14 located at the end of the reset channel 15, and a tension spring is arranged between the return baffle 14 and the horizontal sliding seat 6, so that the return baffle 14 is always consistent with the curvature of the reset channel 15 according to the tension spring force, and the return baffle 14 is always consistent with the curvature of the reset channel 15 from Figure 5 As can be seen from the figure, the length of the return baffle 14 from the rotation point of the grinding head 8 is greater than the length of the other end of the reset channel 15 from the rotation point of the grinding head 8, that is, it is ensured that one end of the return baffle 14 is gradually higher than the other end of the reset channel 15.

[0050] As can be seen from the figure, the length of the return baffle 14 from the rotation point of the grinding head 8 is greater than the length of the other end of the reset channel 15 from the rotation point of the grinding head 8, that is, it is ensured that one end of the return baffle 14 is gradually higher than the other end of the reset channel 15. Figure 5As can be seen, the inner side of the horizontal slide 6 is provided with a return tooth 221 at the end of the positioning tooth row 22, and the cross-sectional shape of the return tooth 221 is tapered, with a height greater than that of the positioning tooth row 22. The return tooth 221 is located below the reset baffle 14, so that when the lock tooth head 24 is moved to the return tooth 221 by the position changing gear 16, the lock tooth head 24 is blocked by the return tooth 221, forcing the height of the upward movement of the lock tooth head 24 to increase, and prompting the return ball 18 to move upward and push the reset baffle 14 to open. As the lock tooth head 24 continuously pushes the intermediate transmission rod 26 upward, after the return ball 18 passes through the reset baffle 14, the reset baffle 14 is closed under the force of the tension spring. At this time, the reset baffle 14 is located below the return ball 18, so that when the return ball 18 moves downward again, it is blocked by the return ball 18, preventing the return ball 18 from completing the downward movement.

[0051] In combination Figure 7 As can be seen, the inner side of the intermediate transmission gear 17 is movably mounted with a disengagement spring 28 above the intermediate transmission shaft 27. When the intermediate transmission rod 26 rises, the side of the intermediate transmission rod 26 will push on the disengagement spring 28 and compress it.

[0052] In actual application, as the lock tooth head 24 is moved by the position changing gear 16 to the return tooth 221, the lock tooth head 24 is pushed upward by the return tooth 221, and at the same time, the intermediate transmission rod 26 is compressed by the disengagement spring 28 as it moves upward. When the intermediate transmission rod 26 moves upward, the top return ball 18 lifts the reset baffle 14. When the return ball 18 passes through the reset baffle 14, the reset baffle 14 is reset and blocked below the return ball 18 by the force of the tension spring. Then, as the compression force of the disengagement spring 28 increases continuously, the intermediate transmission gear 17 moves upward, because: Figures 7-9 As can be seen, since the limiting column 31 is pushed out to the middle of the intermediate transmission gear 17, the axial movement between the intermediate transmission shaft 27 and the intermediate transmission gear 17 is reduced by the blocking of the limiting column 31. However, since the two rely on the outward pushing force of the limiting spring 310, when the compression force of the disengagement spring 28 increases continuously and reaches the strength at which the limiting column 31 can disengage from the intermediate transmission gear 17, the limiting column 31 moves away from the one-way rotating tooth 170 and is located below the one-way rotating tooth 170. At this time, power transmission cannot be achieved.

[0053] Afterwards, due to the upstroke of the lock tooth head 24 on the return convex tooth 221, the limiting spring 23 will be further compressed, and the bottom of the lock tooth head 24 will be higher than the positioning tooth row 22. When there is no power transmission between the intermediate transmission gear 17 and the intermediate shaft 27, the lock tooth head 24 has a tendency to pull the intermediate transmission rod 26 downward due to the elastic force of the limiting spring 23, which in turn pulls the return ball 18 to be close to the reset groove 15. As mentioned above, the return baffle 14 at one end of the reset groove 15 is higher than the other end of the reset groove 15, so when the return ball 18 presses the reset groove 15, it will move along the reset groove 15 until it moves to the lowest end of the reset groove 15.

[0054] From Figure 5 It can be seen that one end of the positioning tooth row 22 is provided with a return groove 220 below the lowest end of the reset groove 15, and the return groove 220 is a V-shaped groove. When the lock tooth head 24 moves to the lowest end of the reset groove 15, the return ball 18 is separated from the reset groove 15, and the elastic force of the limiting spring 23 will make the lock tooth head 24 continuously move into the return groove 220, and pull the return ball 18 downward through the intermediate transmission rod 26. After the return ball 18 moves downward, it will press the intermediate transmission gear 17 to move downward synchronously until the limiting column 31 moves to the one side of the one-way rotating tooth 170 again, and the working cooperation between the one-way rotating tooth 170 and the limiting column 31 is realized again.

[0055] Example Four

[0056] Further improvement for example three, although the power support 12 can be reset in example three, but during the reset process, there is no speed limiting device according to the movement of the return ball 18 in the reset groove 15, which leads to the power support 12 directly colliding with the horizontal sliding seat 6 due to the excessive speed after the return ball 18 moves to the lower end of the reset groove 15, which is easy to cause damage to the parts. In order to avoid the excessive speed of the power support 12 during return, please refer to Figures 7-9 It can be seen that the speed limiting mechanism is arranged in the intermediate transmission gear 17 to avoid the excessive speed of the power support 12 during return. In example four, the speed limiting mechanism has two kinds:

[0057] The first kind is combined Figure 9It can be seen that the inner side of the intermediate transmission gear 17 is provided with a circle of resistance teeth 171, and the resistance teeth 171 are located below the one-way rotation tooth 170, so that when the intermediate shaft 27 moves axially relative to the intermediate transmission gear 17, the limiting column 31 on the intermediate shaft 27 will be separated from the one-way rotation tooth 170 and enter the resistance tooth 171, and as the limiting column 31 rotates in the resistance tooth 171, the rotation of the intermediate shaft 27 has a certain resistance, which is transmitted to the transposition gear 16 through the driving bevel gear 20 and the driven bevel gear 21, so that the movement speed of the transposition gear 16 is reduced, thereby reducing the return speed of the power support 12.

[0058] Second combination Figure 4 、 Figure 6 and Figure 9 It can be seen that the end of the intermediate transmission gear 17 is provided with a speed reduction rubber ring 19, and it can be known from the third embodiment that when the intermediate transmission gear 17 and the intermediate shaft 27 move axially, the disengaging spring 28 is excessively compressed, and the disengaging spring 28 after being compressed will push the intermediate transmission gear 17 upward, so that the speed reduction rubber ring 19 at the top of the intermediate transmission gear 17 contacts the inner top of the horizontal sliding seat 6, that is, the peripheral part of the reset channel 15, thereby reducing the movement speed of the power support 12 through the sliding friction between the speed reduction rubber ring 19 and the horizontal sliding seat 6.

[0059] In summary of the above, the above two ways can slow down the return speed of the power support 12, and the limiting way is similar to applying a fixed movement resistance, so that when the applied resistance is too large, the movement of the power support 12 is slowed down or stopped, and for the same reason, when the applied resistance is too small, the purpose of speed reduction cannot be achieved. In order to further optimize the speed reduction effect, in combination with Figure 7 and Figure 10 It can be seen that the middle part of the intermediate transmission rod 26 is a cuboid, so that the intermediate transmission rod 26 can always rotate with the intermediate shaft 27, and the inner side of the intermediate transmission rod 26 movably installs a force adding rod 30, and the resistance end of the force adding rod 30 movably connects a forced return rod 29, and the power end of the force adding rod 30 and the intermediate transmission rod 26 are provided with a forced return spring 32, so that when the forced return spring 32 pushes the force adding rod 30 by the elastic force, according to the lever principle, the force adding rod 30 will push the forced return rod 29 outward, and the strength of the outward pushing is enhanced, in combination with Figure 7 It can be seen that the end of the forced return rod 29 is designed with a ball, and the forced return rod 29 is attached to the inner side of the intermediate transmission gear 17, so that when the forced return spring 32 pushes the forced return rod 29 outward due to the elastic force, the ball on the forced return rod 29 is attached to the inner side of the intermediate transmission gear 17.

[0060] One end of the limiting column 31 is fixedly connected with a speed reduction top rod 311 located on one side of the force adding rod 30, so that when the limiting column 31 is excessively retracted into the middle shaft 27, the force adding rod 30 is pushed through the speed reduction top rod 311, and the speed reduction rubber ring 19 is pushed to the inner top of the horizontal sliding seat 6 through the force adding rod 30 and the speed reduction top rod 311, so that the movement resistance of the power support 12 is further increased to achieve speed reduction. Figure 9 As can be seen from the drawings, the top end of the intermediate transmission gear 17 is provided with an inclined angle, and when the intermediate transmission rod 26 is pushed outwards, the forced return rod 29 also moves upwards relative to the intermediate transmission gear 17, so that the upward movement of the intermediate transmission gear 17 is limited by the extended forced return rod 29.

[0061] As can be seen from the drawings, the top end of the limiting column 31 is fixedly connected with a speed reduction top rod 311 located on one side of the force adding rod 30, so that when the limiting column 31 is excessively retracted into the middle shaft 27, the force adding rod 30 is pushed through the speed reduction top rod 311, and the speed reduction rubber ring 19 is pushed to the inner top of the horizontal sliding seat 6 through the force adding rod 30 and the speed reduction top rod 311, so that the movement resistance of the power support 12 is further increased to achieve speed reduction. Figure 8 As can be seen from the drawings, any one-way resistance increasing tooth 171 protrudes outward, Figure 8 As can be seen from the drawings, the top end of the limiting column 31 is fixedly connected with a speed reduction top rod 311 located on one side of the force adding rod 30, so that when the limiting column 31 is excessively retracted into the middle shaft 27, the force adding rod 30 is pushed through the speed reduction top rod 311, and the speed reduction rubber ring 19 is pushed to the inner top of the horizontal sliding seat 6 through the force adding rod 30 and the speed reduction top rod 311, so that the movement resistance of the power support 12 is further increased to achieve speed reduction.

[0062] In actual application, when the lock tooth head 24 moves to the return protruding tooth 221, causing the return ball 18 to move upwards to the reset groove 15, at the same time, the limiting column 31 is separated from the one-way rotating tooth 170 and enters the resistance increasing tooth 171 to work at a reduced speed, and the intermediate transmission gear 17 also moves upwards due to the elastic force of the separation spring 28, but at this time, since the intermediate transmission rod 26 moves upwards first, the separation spring 28 is compressed and pushes the intermediate transmission gear 17 upwards, and the forced return rod 29 is pushed outwards by the elastic force of the forced return spring 32, and when the subsequent intermediate transmission gear 17 moves upwards under the elastic force of the separation spring 28, the intermediate transmission gear 17 cannot continue to move upwards due to the blocking of the forced return rod 29, and the speed reduction rubber ring 19 will not contact the top of the horizontal sliding seat 6.

[0063] After that, with the rotation of the middle shaft 27 in the intermediate transmission gear 17, the movement of the power support 12 is slowed down through the relative sliding between the limiting column 31 and the resistance increasing tooth 171, and when the limiting column 31 contacts the extended resistance increasing tooth 171, the movement stroke of the limiting column 31 into the middle shaft 27 is increased, thereby pushing the force adding rod 30 and compressing the forced return spring 32. Since the forced return rod 29 is locked into the intermediate transmission rod 26 after the speed reduction top rod 311 presses the force adding rod 30, the forced return rod 29 is released from the limitation of the intermediate transmission gear 17, and then the elastic force of the separation spring 28 on the intermediate transmission gear 17 causes the speed reduction rubber ring 19 to be pressed to the inner top of the horizontal sliding seat 6, further increasing the movement resistance to achieve speed reduction. Although the intermediate transmission gear 17 continues to move upwards, the forced return rod 29 is still at the top inclined surface of the intermediate transmission gear 17.

[0064] Finally, when the limiting column 31 passes the highest resistance tooth 171, the forced return top spring 32 exerts an elastic force to push the forced return rod 29 outward, which is in contact with the top inclined surface of the intermediate transmission gear 17, thereby forcing the intermediate transmission gear 17 to drive the speed reduction rubber ring 19 to disengage from the top of the horizontal sliding base 6 again, so as to remove the frictional resistance between the speed reduction rubber ring 19 and the horizontal sliding base 6, and avoid the phenomenon that the frictional resistance is too large to cause the power support 12 to fail to return normally.

[0065] The advantage of the fourth embodiment is that the frequency of the speed reduction rubber ring 19 is related to the relative rotation speed between the intermediate transmission gear 17 and the intermediate shaft 27. If the rotation is too fast, it indicates that the power support 12 moves too fast, and the intermediate transmission gear 17 intervenes more frequently, thereby avoiding the power support 12 from moving too fast. Conversely, when the rotation speed between the intermediate transmission gear 17 and the intermediate shaft 27 is slow, the intervention of the intermediate transmission gear 17 is relatively slow, and the extension speed of the intermediate transmission gear 17 is also relatively slow.

Claims

1. A two-station combination bevel sharpening machine comprising: The machine base (1) has two facing transverse sliders (4) on its surface. The transverse sliders (4) move back and forth on the surface of the machine base (1). A vertical slider (5) that moves up and down is provided on the transverse sliders (4). A horizontal slide (6) that moves left and right is provided on the vertical sliders (5). The machine base (1) is characterized in that... The control box (2) is fixed to the side of the base (1) for electrical control; The guide slider (10) is movably installed at the bottom of the horizontal slide (6), and a power bracket (12) is fixed at one end of the guide slider (10), and a power motor (7) is fixedly installed at the top of the power bracket (12). The power guide rod (9) is fixed at the top end to the power motor (7), and a grinding head (8) is fixedly connected at the bottom end. A drive gear (13) is threadedly connected to the outer side of the middle part. The shift bracket (120) is fixed to the side of the power bracket (12). A central shaft (27) is movably installed on the side. An intermediate transmission gear (17) is provided on the top of the central shaft (27) and meshes with the external teeth of the drive gear (13). The intermediate transmission gear (17) and the central shaft (27) have unidirectional transmission. An active bevel gear (20) is provided at the bottom of the central shaft (27). A driven bevel gear (21) that meshes with the external teeth of the active bevel gear (20) is movably installed on the other side of the shift bracket (120). The shaft of the driven bevel gear (21) is fixedly connected to the shift gear (16). The positioning gear (22) is arc-shaped and is located on the inner side of the horizontal slide (6), and the positioning gear (22) meshes with the shift gear (16); The power guide rod (9) is provided with a shifting thread (900) for threaded connection with the drive gear (13) on the outside. The power guide rod (9) is fitted with a shifting ring sleeve (25) located below the drive gear (13) on the outside. An intermediate transmission rod (26) is movably installed at the bottom of the shifting ring sleeve (25), and a locking tooth head (24) is movably installed at the bottom end of the intermediate transmission rod (26). A limiting spring (23) is provided between the locking tooth head (24) and the shifting ring sleeve (25). The top end of the intermediate transmission rod (26) passes through the active bevel gear (20), the central shaft (27) and the intermediate transmission gear (17) and is located above the intermediate transmission gear (17), and the top end of the intermediate transmission rod (26) is fixedly connected to the return ball (18). A reset channel (15) is provided on the top of the horizontal slide (6), and a return baffle (14) located at the end of the reset channel (15) is movably installed on the inner side of the horizontal slide (6). A tension spring is provided between the return baffle (14) and the horizontal slide (6). The inner side of the horizontal slide (6) is provided with a return protrusion (221) located at the end of the positioning tooth row (22), and the other end of the positioning tooth row (22) is provided with a return groove (220). The cross-sectional shape of the return protrusion (221) is conical, and the return protrusion (221) is higher than the positioning tooth row (22). A release spring (28) is movably mounted on the top inner side of the intermediate transmission gear (17).

2. The two-station combination bevel sharpener of claim 1 wherein, A position detection grating (11) is movably mounted on the surface of the horizontal slide (6), and the guide slider (10) is located outside the position detection grating (11).

3. The dual position combination bevel sharpener of claim 1 wherein, The intermediate transmission gear (17) is sleeved on the transfer shaft (27), the side of the transfer shaft (27) is movably installed with a limiting column (31), a limiting spring (310) is arranged between the limiting column (31) and the transfer shaft (27), and the inner side middle part of the intermediate transmission gear (17) is fixedly connected with a one-way rotation tooth (170).

4. The dual position combination bevel sharpener of claim 1 wherein, The return baffle (14) at one end of the reset channel (15) is higher than the other end of the reset channel (15).

5. The dual position combination bevel sharpener of claim 1 wherein, A speed limiting mechanism is arranged in the intermediate transmission gear (17) to avoid the return speed of the power support (12) being too fast.

6. The two-station combination bevel sharpener of claim 5 wherein, The speed limiting mechanism comprises resistance increasing teeth (171) arranged on the inner side of the intermediate transmission gear (17), and the resistance increasing teeth (171) are located below the one-way rotation tooth (170), and any one resistance increasing tooth (171) protrudes outward.

7. The dual position combination bevel sharpener of claim 5 wherein, The speed limiting mechanism comprises a speed reducing rubber ring (19) arranged at the end of the intermediate transmission gear (17).

8. The dual position combination bevel sharpener of claim 5 wherein, The middle part of the intermediate transmission rod (26) is a cuboid; The inner side of the intermediate transmission rod (26) movably installs a force adding rod (30), the top end of the force adding rod (30) movably connects a forced top return rod (29), and the bottom end of the force adding rod (30) and the intermediate transmission rod (26) are provided with a forced return top spring (32); One end of the limiting column (31) is fixedly connected with a speed reducing top rod (311) located on one side of the force adding rod (30), and the top end of the intermediate transmission gear (17) is provided with an inclined angle.

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