AUTOMATIC TOOL CHANGER

Abstract: An automatic tool changer for a machine tool which is provided with a first cam (C S ) which cooperates with a first cam roller (21) fixed to the rear surface of a turret (38) to swing the turret (38), a second cam (C L ) used to move the turret (38) vertically and relatively to a spindle head in the direction parallel to the axis of the main shaft of the machine tool, and links (6, 8, 14, 16) which have a second cam roller (22) cooperating with the second cam (C L ), and which is adapted to move the turret (38) vertically and relatively to the main shaft of the machine tool when the turret (38) is swung in accordance with the cooperation of the first cam (C S ) with the first cam roller (21), whereby a relative speed of the turret (38) with respect to the spindle head (34) is reduced, so that a shock occurring in the main shaft and turret (38) during a tool changing operation is lessened.

Description: Technical Field This invention relates to a machine tool according to the preamble of claim 1. Background Art Machine tools comprising an automatic tool changer, in particular CNC drills, are widely used. Such machine tools and in particular automatic tool changers are known, for example, from the US-A-5,020,210 as well as from the Japanese unexamined patent publication No. 2-15935 and from the Japanese unexamined patent Publication No. 2-48146. A prior art automatic tool changer, as shown in Figure 16, comprises a turret 74 holding a plurality of tools positioned on its peripheral. When a tool-change command is executed, firstly, orientation is carried out. In orientation, the angular position of a key on a spindle, on which a tool (or tool holder) 70 is mounted, is adjusted to a given angular position. Sequentially, a spindle head 60 is raised with the angular position of the spindle maintained. As the spindle head is raised, a cam 62 is engaged with a lever 64, then the lever 64 is rotated by the cam 62. The rotation of the lever 64 is transmitted to a crank 68 through a link 66 provided on an end of the lever 64. Thus, the crank 68 rotates (in the following, the rotation of the crank and the turret is referred to as a swing movement), and a grip 72 arranged on the periphery of the turret 74 approaches the tool holder 70 mounted on the spindle. Then, the grip 72 engages with the tool holder 70 and grasps it. Thereafter, the spindle head 60 is further raised so that the tool holder 70 is removed from the spindle. When the tool holder 70 removed from the spindle, an indexing of the turret 74 is carried out by the rotation of the spindle with a spindle gear 76 being engaged with a turret gear 78. Thus, a desired tool is selected from among the tools held on the turret 74. Sequentially, the spindle head 60 is lowered and the turret gear 78 is disengaged from the spindle gear 76, during which another orientation is carried out in order to correct the discrepancy of the angular position of the spindle, since the angular position of the spindle may be different from the given angular position due to the rotation of the spindle for indexing the turret. When the spindle head 60 is lowered, the tool holder grasped by the grip 72 is mounted on the spindle and the tool change operation is completed. The conventional automatic tool changer generates shock due to the swing movement of the turret 74 when the grip 72 grasps the tool holder mounted on the spindle or the tool holder grasped by the grip 72 is mounted on the spindle. In order to reduce the shock, in the conventional automatic tool changer, the feed velocity of the vertical movement of the spindle head is reduced when the shock is generated. Thus, the conventional automatic tool changer has a disadvantage that it takes long time for a tool change because of the reduction of the feed velocity. Furthermore, in order to remove the tool holder from the spindle, in the conventional automatic tool changer, the spindle head 60 must be raised higher until the tool holder is completely removed after the grip grasps the tool holder mounted on the spindle. On the other hand, the spindle head must be lowered until the tool holder is completely mounted on the spindle when the tool holder is mounted on the spindle. Therefore, a long feed length is required in the conventional automatic tool changer. Thus, the conventional automatic tool changer has the further disadvantages that the machine tool is high and the time for tool change is long. In the prior art, the turret is driven by the spindle, the speed of which is reduced to about 30 rpm without a speed reducer between the turret and the spindle. However, the electric motor, typically a spindle motor, used as an drive source for such an automatic tool changer has a characteristic that the generated power is proportional to the speed of the motor when the motor rotates at a speed under 1500 rpm, that is, the generated torque is constant under 1500 rpm. Therefor, if the turret is driven by the spindle which is rotating at 30 rpm then the power is not enough for a high-speed tool change. It is obvious that this problem can be solved by providing a compact speed reducer within the turret. The speed reducer within the turret does not require high accuracy or high transmission efficiency for indexing the turret during a tool change. There are various known speed reducers, such as a multiple gear box, a worm gear device, a bevel gear device, a planetary gear (epicyclic gear) device, a roller gear cam device, and the others. The multiple gear box has high transmission efficiency. However, it has a plurality of gears. The worm gear device has high reduction ratio. However, it has an input axis and an output axis arranged at right angle to each other. Thus, the above two devices tend to have relatively large dimensions. A device having a combination of bevel gears and a device using planetary gears cannot provide the high reduction ratio required for the automatic tool changer. The roller cam gear device can provide a high reduction ratio and high accuracy without back-lash. However, it is a large and expensive device since it has a plurality of axes and complicated roller grooves must be formed on the drive axis thereof. Therefore, conventional speed reducers are too complicated and large to be arranged within the turret. It is also difficult to reduce the time required for a tool change by providing the desired reduction ratio. That is, it is difficult to increase the velocity of the turret during a tool change by the conventional speed reducer. Furthermore, from a viewpoint of a cost, because of the high quality, the conventional speed reducer is not suitable as a speed reducer adapted to drive the turret of an automatic tool changer. Disclosure of the Invention Thus, the object of the invention is to provide a machine tool comprising an automatic tool changer which is constructed so as to eliminate, or to reduce as much as possible, the shock generated during a tool change while using a relatively high velocity of the spindle head, and to change tools with a shorter travel of the spindle head than the conventional automatic tool changer, whereby to provide an automatic tool changer which can change tools quickly. A further object of the invention is to provide a machine tool comprising an automatic tool changer which can change tools quickly, the turret thereof comprising a compact speed reducer with reduction ratio of 6:1 or so, which can manufactured with relatively easily and is inexpensive while its transmission efficiency is not high. Yet further object of the invention is to provide a machine tool comprising a compact speed reducer with reduction ratio of 6 or so which can be manufactured with relatively easily and is inexpensive while its transmission efficiency is not high. In accordance with the present invention there is provided a machine tool comprising a spindle head and an automatic tool changer comprising a turret holding a plurality of tools by means of grips arranged on the periphery thereof and supported for rotation about a rotation axis, said automatic tool changer selecting the desired tool by indexing said turret and changing tools between said desired tool and a tool mounted on a spindle of said machine tool by said turret swinging toward and away from the spindle. said automatic tool changer comprising: a first cam means provided on a spindle head of said machine tool for swinging said turret in cooperation with a first cam roller means mounted on a back face of said, turret for rotation about an axis, which is characterized by a second cam means provided on said spindle head for raising and lowering said turret with respect to said spindle head in a direction along the central axis of said spindle of said machine tool; and a link means having a second cam roller means cooperating with said second cam means, when said spindle head is raised or is lowered and said turret swings based on said cooperation between said first cam means and said first cam roller, said link means receiving a force generated by the cooperation between said second cam means and said second cam roller means and raising or lowering said turret with respect to said spindle in the direction along said central axis of said spindle whereby the relative velocity between said turret and said spindle head is reduced. The first cam means may be extended parallel to the central axis of the spindle and comprise first and second flat bearing faces and a third bearing face arranged between the first and the second bearing faces and having externally convex configuration. The first and second bearing faces may be integrally formed or separately formed each other. The second cam means may be of a type having a hook-shaped groove composed of a straight portion extended generally parallel to the central axis of the spindle and a curved portion. Furthermore, the turret may comprise a rotating shaft provided with a coaxial-type speed reducer having a reduction ratio of a integral number of 2:1 or more. A speed reducer used in the machine tool may comprise: a plurality of ball means transmitting the driving force, the number of the ball means corresponding to the number of the reduction ratio plus one; a driving cam means containing a first cam groove which engages with the ball means and has a circular configuration, the center of the circle being eccentrically positioned with respect to the axis of the speed reducer; a follower cam means containing a second cam means having a plurality of convex and concave portions, the number of the convex portions corresponding to the reduction ratio; a holder means provided with a plurality of equally spaced radial grooves, the number of which corresponds to the number of the reduction ratio plus one, each of the grooves allowing the respective ball means to move in the radial direction; and the driving cam means and the follower cam means connected to each other with the holder means therebetween, the sides of each the cam means formed with the respective grooves facing each other whereby the rotation of the driving cam means is transmitted to the follower cam means, and reduced, through the ball means. Brief Description of the Drawings Figure 1 is a side elevation of an automatic tool changer, in accordance with the invention, used for a CNC drill. Figure 2 is a plan view of an automatic tool changer in accordance with the invention, used for a CNC drill viewed from the arrow II in Figure 1. Figure 3 illustrates the arrangement of cams of an automatic tool changer, in accordance with the invention, with the spindle head of the CNC drill of Figure 1 lowered to the lowest point. Figure 4 is enlarged view of the swing cam and the lift cam used for an automatic tool changer in accordance with the invention. Figure 5 illustrates the relationship between the swing cam and the swing movement of the turret. Figure 6 illustrates the relationship between the lift cam and the lift movement of the turret. Figure 7 is sectional view of the speed reducer in accordance with the invention. Figure 8(a), 8(b) and 8(c) are front view of the follower cam, the holder and the driving cam of the speed reducer shown in Figure 7 respectively. Figure 9 schematic representation to explain the arrangement of the cam groove of the driving cam of the speed reducer shown in Figure 7. Figure 10 schematic representation to explain the number of the slot required in the holder of the speed reducer shown in Figure 7. Figure 11(a), 11(b) and 11(c) are front views of the follower cam, the holder and the driving cam of the speed reducer with the reduction ratio of 4:1 in accordance with the invention respectively. Figure 12(a), 12(b) and 12(c) are front views of the follower cam, the holder and the driving cam of the speed reducer with the reduction ratio of 9:1 in accordance with the invention respectively. Figure 13 is a schematic representation to explain the pressure angle. Figure 14 is a graph illustrating variation of the pressure angle. Figure 15 is a schematic representation to explain the relation between the rotational center of the driving ball and respective contact points. Figure 16 is a side elevation of the conventional automatic tool changer. Best Mode for carrying Out the Invention Referring to Figures 1 and 2, a CNC drill provided with an automatic tool changer in accordance with the invention comprises a spindle head 34 rotationally holding a spindle on which a tool for machining is mounted. The spindle head 34 is arranged so as to be raised or lowered in the vertical direction on guide rails 1. The automatic tool changer in accordance with the invention has a generally U-shaped arm member 2, and a turret 38 having a plurality of grips 28 on periphery thereof. Each tool is held in a respective grip 28. The turret 38 can rotate about an axis "a" in order to select the desired tool. The turret also comprises a speed reducer 39 of the coaxial type. The speed reducer 39 is mounted within the turret coaxially with the axis "a". Rotation of the spindle of the CNC drill is transmitted to the speed reducer 39 through a turret gear 30 and a spindle gear 32. The speed reducer 39 reduces and transmits this rotation to the turret 38. In the following, a description is made of one embodiment of the invention in which the turret 38 can hold 10 tool holders on its periphery. In Figure 1 and 2, the automatic tool changer is mounted on the spindle head 34 which can move in the vertical direction. The automatic tool changer comprises a first cam (in the following, referred to as a swing cam) C S for swinging a crank 4 about a shaft 18 in a direction indicated by an arrow SS and a second cam (in the following, referred to as a lift cam) C L for moving the crank 4 in a direction indicated by an arrow LL. The crank 4 is secured on a back face of the turret 38 holding tool holders 36 through grips 28. Thus, the turret 38 can move in the both directions indicated by arrows SS and LS. A first cam roller (in the following, referred to as a swing roller) 21 is rotationally mounted on the crank 4 about a shaft 20 at the opposite end to the shaft 18. The swing roller 21 cooperates with the swing cam C S . A spring means 26 is attached to the crank 4 at the generally center portion thereof by a pin 19. The crank 4 is biased by the spring means 26 in a direction indicated by an arrow SP about the shaft 18. That is, the swing roller 21 is pressed onto a bearing face of the swing cam C S by the spring means 26. The above arrangement allows turret 38 to swing in the direction of the arrow SS in accordance with the configuration of the swing cam C S when the swing roller 21 is moved relatively to the swing cam C S which bears on the bearing face. The shaft 18 is connected to a lift slider 16. The lift slider 16 can move in the vertical direction, indicated by an arrow LS, along a linear guide 40 attached to the arm member 2. A lift link 14 is attached to the lift slider 16 at the opposite end to the shaft 18. The lift link 14 can move in the direction of the arrow LS with the lift slider 16. A lift lever is attached to the lift link 14 at the opposite end to a bolt 15 by a pin 12. The lift lever comprises two arm members 8, 6 and can rotate about shaft 10. The shaft 10 is attached to the arm member 2 horizontally. The lift lever 6, 8 is attached to the shaft and can rotate in the direction of an arrow LL shown in Figure 3 (referring to Figure 3). A second cam roller 22 (in the following, referred to as a lift roller) is attached to the arm member 6 of the lift lever at the opposite end to the shaft 10. The lift roller 22 engages with the lift cam C L and can rotate about a shaft 24. The above arrangement allows lift link 14 and lift slider 16 to be raised and lowered in the direction of the arrow LS which leads to a movement of the turret 38 in the direction of the arrow LS (in the following, this movement of the turret 38 is referred to as a lift movement) when the lift roller 22 is moved in the direction LL by the engagement with the lift cam C L , that is, the lift link 6, 8 rotates in the direction of the arrow LL about the shaft 10. In the following, a description is made of the two cams C S and C L used for the automatic tool changer in accordance with the invention (referring to Figure 4). The swing cam C S comprises first and second bearing faces C Sa and C Sb which are arranged at two levels and extended parallel to the center axis of the spindle of the CNC drill (in the following, referred to as Z-axis), and a third bearing face C Sc which has convex configuration and substantially regulates the movement of the turret 38 as can be understand from Figure 4. In the following, a description is made of the movement of the turret 38 by the cooperation between the swing cam C S and the swing roller 21. At first, turret 38 does not move and is kept in a waiting position while the swing roller 21 is on the bearing face C Sa (referring to Figure 3). Once the swing roller 21 reaches the starting point (C S1 ) of the cam surface C Sc , the turret 38 starts swinging toward the spindle of the CNC drill about the shaft 18 corresponding to the movement of the swing roller 21 along the cam surface C Sc . In the following, the assumption is made that the the origin of the Z-axis is defined when the swing roller 21 is at C S1 . When the swing roller 21 is abutted to the cam surface C Sb (the center of the swing roller 21 is indicated by C S2 ) after moving along the cam surface C Sc , the swing movement of the turret 38 toward the spindle of the CNC drill is stopped. At this time, the grip 28 engages sufficiently with the V-shaped groove 35 of the tool holder 36 and grasps the tool holder 36. It is apparent that the two bearing face C Sa and C Sb can be formed as one body although they are shown as separated bodies in Figure 4. On the other hand, the lift cam C L is a hook-shaped groove cam having a straight portion C La and a curved portion C Lb . The lift roller 22 contacts the inner surface of the groove and rolls in the groove. In the following, a description is made of the relationship between the movements of the lift cam C L and the turret 38. When the lift roller 22 is in the straight portion C La of the lift cam C L , the lift lever 6, 8 does not move, therefore the turret 38 does not lift. When the lift roller 22 reaches the first portion (C L1 to C L2 ) of the curved portion C Lb , the arm member 6 of the lift lever starts to rotate in a clockwise direction which raises the lift link 14 and the lift slider 16 in the direction of the arrow LS. Thus, the turret 38 moves in the up-ward direction. When, the lift roller 22 reaches to the second portion (C L2 to C L3 ) of the curved portion C Lb , the arm member 6 of the lift lever rotates in the counter-clockwise direction which lowers the lift link 14 and the lift slider 16. Thus, the turret 38 is lowered. That is, the turret 38 moves in the down-ward direction. When the swing roller 21 reaches C S1 , the lift roller 22 is at C L1 shown in Figure 4. In the following, a description is made of the tool change action of the automatic tool changer in accordance of the invention, with reference to Figure 3, in which the spindle head 34 is shown at the lowest position, for understanding the configuration of the cams. The description is also made with reference to Figure 5 and 6 showing the relationship of the respective cams to the displacement, the displacement velocity, and the displacement acceleration of the swing and lift movements. Firstly, the orientation of the spindle is carried out when the tool change command is executed from a CNC drill controller (not shown). At the same time, the spindle head 34 is quickly raised. The swing roller 21 approaches the starting position C S1 of the swing movement, that is, the origin of the Z-axis along the first bearing face C Sa of the swing cam C S . When the swing roller 21 reaches C S1 , the spindle head 34 stops and waits for the end of the spindle orientation. When the spindle orientation is completed, the spindle head 34 is raised again. During this operation, the lift roller 22 is on the straight portion C Ls of the lift cam C L extending parallel to the Z-axis and the lift movement is not carried out (shown by a portion L 1 in Figure 6). Thereafter, the spindle head 34 is further raised and the swing roller 21 approaches the third bearing face C Sc of the cam C S . At this time, the turret 38 starts swinging in the clockwise direction about the rotation shaft 18. The third bearing face C Sc is formed so that the free ends of the grip 28 approach the V-shaped groove 35 of the tool holder 36 without contacting the spindle gear 32 and then rollers (not shown) provided at the free ends of the grip 28 trace accuracy along the V-shaped groove 35 after the rollers engage with the groove. Futhermore, it is desired that the configuration of the third bearing face of the swing cam C S is such that the free ends of the grip 28 swing along a shortest path. Then, the spindle head 34 is raised at a displacement velocity and is accelerated linearly as the swing roller 21 moves from C S2 to C S1 . During this operation, the acceleration of the swing movement of the turret 38 (indicated by S 1 , S 2 in Figure 5) is an acceleration defined by the configuration of the swing cam and the linear acceleration of the spindle head 34. It is apparent from the construction of the turret 38 and the swing cam C S shown in Figure 1, that the velocity of the movement of the turret 38 is defined by the configuration of the swing cam C S and the relative velocity between the swing cam C S and the swing roller 21. Therefore, the swing movement of the turret 38 is decelerated if the turret 38 moves in the same direction of the movement of the spindle head 34 just before the end of the swing movement (indicated by S 5 in Figure 5), which leads the reduction in relative velocity therebetween. This allows the swing movement to be completed without shock being generated on the grip 28 and tool holder 34 and without the velocity of the spindle head 34 being reduced. To realize this, during the deceleration of the swing movement (S 3 in Figure 5 and between C L4 and C L2 in Figure 6), the lift lever 6, 8 is rotated in the counter-clockwise direction about the shaft 10 by the engagement between the lift roller 22 and a portion from C L4 to C L2 . The rotation results in a rising movement of the lift link 14 and the lift slider 16 and in the acceleration of the crank 4, that is, of the turret 38 in the same direction as the rising movement of the spindle head 34 (indicated by L 6 in Figure 6). Thus, relative velocity of the turret 38 to the spindle head 34 rising in the Z-axis is substantially 0 (the velocity of the turret 34 is indicated by L P and the spindle head 34 also moves at a velocity indicated by L P ) at the end of the swing movement, that is when the swing roller 21 is at C S2 (also indicated by C S2 in Figure 5) and the lift roller 22 is at C L2 (also indicated by C L2 in Figure 6). Thus, the shock described above is considerably reduced or removed. This is an important advantage of the invention. After the end of the swing movement, the spindle head 34 is rapidly raised to a point where the turret carries out the indexing. At the same time, the turret 38 starts a further movement in the downward direction to draw out the tool holder 36 from the spindle. During this operation, the swing roller 21 moves from C S2 to C S3 and the lift roller 22 moves from C L2 to C L3 . That is, the direction of the acceleration of the lift movement is reversed to the movement in the Z-axis (the acceleration becomes negative) and the lifting movement is decelerated after the lift roller 22 is beyond the point C L2 in Figure 6. The crank, firstly, is raised (L 2 in Figure 6), then starts to move in downward direction (L 3 in Figure 6) since the crank has a velocity in the same direction as the rising movement of the spindle head 34. During this operation, the acceleration of the crank 4 is a linear acceleration in order to minimize the variations in the acceleration (L 8 and L 9 ). It is an important advantage of the invention that the automatic tool changer can draw out the tool holder 36 from the spindle in a shorter distance than the conventional automatic tool changer since the crank 4 and the turret 38 carry out the lift movement in a downward direction related to the spindle head 34. After the end of the rising movement of the spindle head 34 (shown in Figure 1), indexing is carried out by rotating the spindle, for selecting the desired tool, with the spindle gear 32 of the CNC drill engaged with the turret gear 30 of the speed reducer 39. The angular position of the spindle corresponds to the orientation of the spindle when the indexing of the turret is completed since one indexing is carried out by one rotation of the spindle through the speed reducer 39 as described later. After the end of the indexing of the turret, the spindle head 34 is lowered to the origin of the Z-axis following a sequence opposite to that described above. Thus, the relative velocity of the turret 38 to the velocity of the lowering movement of the spindle head 34 is substantially 0, when the spindle receives the tool holder 36 from the grip 28. The spindle head 34 returns to the origin at the same time that the reverse swing movement of the turret 38, and thus the operation of the tool change, is completed. In the following, a description is made of the speed reducer 39 with reference to Figure 7. The speed reducer 39 comprises a driving cam 44, a follower cam 42 and a holder 46 between the driving cam 44 and the follower cam 42. The driving cam 44 and the follower cam 42 are rotatably connected to the holder 46 about a common axis by a bearing means such as a ball bearing. Referring to Figure 8, a second cam groove 52 is formed on the follower cam 42. A first cam groove 58 is formed on the driving cam. The holder 46 contains ball slots 54. One ball 48 is held in each of the ball slots 54. The speed reducer is assembled so that the balls 48 engage with the first and the second grooves. The rotation of the driving cam 44 is reduced and is transmitted to the follower cam 42 through the movement of the balls 48 as described below. The driving cam 44 comprises a generally circular member with the turret gear 30 on its periphery as shown in Figure 8 (c). The turret gear 30 engages with the spindle gear 32 on the spindle. The driving cam contains the first cam groove 58 which engages with the balls 48. The first cam groove 58 is a generally a circular groove with a radius "r" and a center eccentrically positioned from the axis of the driving cam 44 by a distance Q. The formula representing the configuration of the first cam groove with respect to an angle  about the axis of the speed reducer will be described later. In Figure 8 (b), the holder 46 comprises a generally circular member provided with an island 56 having a means 41 for mounting onto a given position of the turret 38 so as to prevent the rotation of the holder 46. The holder 46 has n+1 ball slots 54 while the reduction ratio is n:1 (n=2,3,4,..). The ball slots 54 is radially extended and equally positioned. Figure 8 (b) illustrates the holder when the reduction ratio is 6:1 as one embodiment of the invention. The ball slot 54 has an axial length substantially twice the distance Q between the axis O of the driving cam 44, that is, the axis of the speed reducer, and the center point O' of the eccentrically positioned circle of the first cam groove 54. A ball 48 is held in each of the ball slots 54. The movement of the ball 48 relative to the movement of the driving cam 44 is constrained in the radial direction by the ball slot 54. That is, each of the balls 48 reciprocates once in the respective ball slots 54 for each rotation of the driving cam 44. In Figure 8 (a), the follower cam 42 comprises a generally circular member provided with the second cam groove 52 a plurality of radial convex and concave portions of which the number corresponds to the reduction ratio n. In Figure 8 (a), the reduction ratio of the speed reducer containing the cam is 6. The formula representing the configuration of the second cam groove with respect to an angle  about the axis will be described later. In the following, a description is made of the principle of the operation of the speed reducer 39. As can be seen from the description for the construction of the speed reducer, during one rotation of the driving cam 44, each ball held in the respective ball slots 54 of the holder 46 reciprocates once in the respective ball slots 54, in the radial direction, while engaging with the first cam groove 58 of the driving cam 44 and the second cam groove 52 of the follower cam 42. This movement of each ball 48 in the respective ball slot 54 is converted into a partial rotation of the follower cam with respect to the central angle  in the formula representing the configuration of the second cam groove 52, for example, one of the balls 48 moves from peak to peak of the second cam groove. That is, since the second groove contains n convex and concave portions, one rotation of the driving cam is converted into 2 π/n rotation of the follower cam. For example, in the particular embodiment illustrated, since n=6, the follower cam 42 rotates 1/6 rotation for one rotation of the driving cam 44. Thus, reduction of 1/6 is obtained. Furthermore, if the reduction ratio between the spindle gear 32 and the turret gear 30 is 1:1.6667 when 10 tool holders are held on the peripheral of the turret, then one tool is selected with one rotation of the spindle during the indexing. Consequently, the angular position of the spindle corresponds to that of before the indexing. In the following, a description is made of the formula representing the configuration of the first cam groove 58 with respect to the angle  about the axis of the speed reducer with reference to Figure 9. If a perpendicular line is drawn from a center point O' of the first cam groove 58 to M, it may be seen that the formula representing the first cam groove, that is, a radial position R1 of the respective balls 48 is shown as follow, R1 = Q cos  + r cos(sin -1 (Q sin ) / r) On the other hand, the configuration of the second cam groove 52 corresponds to a configuration illustrated by the radial movement of one of the balls 48. Each of balls 48 reciprocate n times in the respective ball slots 54 during one rotation of the follower cam 42. Thus, the formula representing the configuration of the second cam groove 52, that is a radial position R2 of the respective balls 48 is shown as follow, R2 = Q cos  + r cos(sin -1 (Q sin n ) / r) It may be seen that if the rotational angle  of the follower cam 42 is as follows with respect to the rotational angle  of the driving cam 44,  = n  then, always R1 = R2 thus, the radial positions of the respective cam grooves, at which the respective balls 48 are positioned. correspond to each other. In the following, it is shown that there are always n+1 points where the radial positions, at which the respective balls 48 are positioned, of the respective cam grooves correspond to each other with reference to Figure 10. Figure 10 schematically illustrates the combination of the driving cam 44, holder 46 and the follower cam 48, in which the first and second cam groove 58, 52 are shown by a dotted line. In Figure 10, an assumption is made that the radial positions of the respective cam grooves, at which the respective balls 48 are positioned, correspond to each other, i.e. R1 = R2, at the angle  on the driving cam 44 and at the angle  on the follower cam 42 (this angular position is identified by m). A further assumption is made that the radial positions of the respective cam grooves, at which the respective balls 48 are positioned, correspond to each other again when the driving cam 44 rotates a further angle β about the axis of the speed reducer. It can be seen that the angular position of the follower cam 42 is represented by  - β at this time since the follower cam 42 rotates in the reverse direction with respect to the rotation of the driving cam 44. In order to comply with the equation (3) it is necessary that,  + β = n · ( - β ) that is,  -n  = -(n+1) · β if  is represented by the general angle  =  ± 2mπ (m=1, 2, 3, ...) and the equation (3) is substituted for the equation (6) then, β = ± 2mπ/(n+1) that is, there are always n+1 points where the radial positions of the respective cam grooves, at which the respective balls 48 are positioned, correspond each other with respect to the reduction ratio of n. In the following table, the variation of the radial position R2 of one of the balls 48 in the second cam groove 52 and the variation of the pressure angle α described below with respect to the rotational angle  with the assumptions of the distance Q =14mm, the radii r=72mm.  (deg) R2(mm) α (deg) 0.0 86.00 90.0 5.0 83.78 59.6 10.0 77.97 44.3 15.0 70.63 40.1 20.0 63.97 44.3 25.0 59.53 59.6 30.0 58.00 90.0 35.0 59.53 120.4 40.0 63.97 135.7 45.0 70.63 139.9 50.0 77.97 135.7 55.0 83.78 120.4 60.0 86.00 90.0 Figures 11 and 12 illustrate follower cams, holders and driving cams of speed reducers 39 with the reduction ratios 4:1 and 9:1 respectively formed by the same manner described above. In the following, a description is made of the pressure angle with reference to Figure 13. Figure 13 is a enlarged view of the ball slot 54 of the holder 46 in which the ball 48 is pressed in downward direction by the second cam groove 52 of the driving cam 44 and the ball presses the second cam groove 52 of the follower cam 44 at a tangent point T. In Figure 13, the ball 48 acts on the second cam groove 52 of the follower cam 42 at the tangent point T with pressure F1 in the longitudinal direction of the ball slot 54. The pressure angle is defined as an angle between a tangential line at the tangent point T and a longitudinal axis of the ball slot. It can be seen from Figure 13, pressure F2 perpendicular to the radial direction of the follower cam 42 is applied onto the follower cam 42 and is represented below. The follower cam 42 is driven by the pressure F2. F2=(F1 · sin α) / cos(π/2- α) If α =90(deg) then F2 = 0. Thus, the no driving pressure is applied onto the follower cam 42. In practice, the experiments shows that if 60° ≦ α ≦ 90° then the pressure angle is excessively large and substantial driving pressure is not generated. Figure 14 illustrates a graph of the relation between the pressure angle α and the rotation angle  of the follower cam 42 shown in TABLE 1. Figure 14 is shown with respect to one cycle of the rotational angle , that is, 0° ≦  ≦ 60° and the corresponding positions of the balls are indicated by #1 to #7 respectively. It can be seen from Figure 14, three balls are within the angular region defined by the equation (9) and four balls drive the follower cam 42. The four balls are out of the angular region defined by the equation (9) and act on the follower cam 42 with driving pressure. Thus, the rotation of the driving cam 44 is transmitted to the follower cam 42. On the other hand, when an external force is applied onto the follower cam 42, the rotational torque which is generated by the balls 48 moving in the radial direction is not transmitted to the driving cam 44 since the pressure angle of the first cam groove 58 is always more than 70° Futhermore, the longer eccentric distance Q of the first cam groove 58 of the driving cam 44 results in the smaller minimum pressure angle. However, if the distance Q is made excessively long then a undercut portion appears in the second cam groove 52 of the follower cam 42. In the undercut portion, the balls 48 transmitting the driving pressure do not move continuously which leads to an inhibition of the smooth movement of the speed reducer 39. Therefore, the it is desired that the eccentric distance Q is as long as possible within the region in which the undercut portion does not appear. As described above, the speed reducer in accordance with the invention transmits the rotation of the driving cam 44 to the follower cam 42. For this purpose, the balls 48 rotate between the first cam groove 58 of the driving side and the second cam groove 52 of the follower side which leads friction due to the difference of the peripheral velocity therebetween. This problem, however, can be considerably reduced by an arrangement in which the ratio of the distances δ1 and δ2 shown in Figure 15 corresponds to reverse ratio of the length along the second cam groove 52 and the first cam groove 58. The distance δ1 corresponds to a distance between the rotational center of the ball 48 and the point at which it contacts the first cam groove 52. The distance δ2 corresponds to a distance between the rotational center of the ball 48 and the point at which it contacts the second cam groove 58. It is apparent from the above description that the automatic tool changer in accordance with the invention can reduce the shock generated by the swing movement of the turret without reducing the velocity of the movement of the spindle head since the turret moves in the vertical direction relative to the spindle head when the turret swings for tool change and the movement of the turret reduces the relative velocity between the turret and the spindle head as much as possible. Thus, the tool change movement is ensured and the time for the tool change is reduced. Furthermore, the automatic tool changer of the invention can change tools with reduced movement compared with the prior art when the turret draws out the tool holder from the spindle or mounts the tool holder on the spindle since the turret moves in the vertical direction with respect to the spindle head. This results in the time for tool change being reduced and in the dimensions of the automatic tool changer being reduced. The invention provides a speed reducer which is compact and inexpensive. The speed reducer is suitable for mounting within a turret of an automatic tool changer. The speed reducer suitably rotates the turret without reducing the speed of the motor for the spindle of a machine tool, such as a CNC drill, excessively. This results in increasing the speed for indexing the turret. Furthermore, sufficient tolerance for driving the spindle is ensured. The speed reducer provided within the turret of the automatic tool changer has a relatively high reduction ratio. The reduction ratio is an integral number and may be, for example 6 while the number of the tools held on the automatic tool changer may be, for example 10. Thus, the automatic tool changer in accordance with the invention can index one tool for one rotation of the spindle by appropriately selecting the number of teeth on the turret gear and on the spindle gear. This allows the automatic tool changer to avoid the orientation of the spindle which is carried out, in the prior art, after the indexing of the turret for matching the angular positions of the key on the spindle and of the key groove on the tool. Therefore, the automatic tool changer can reduce the time required for the tool change. Furthermore, in the speed reducer in accordance with the invention, rotation is not transmitted from the follower cam to the driving cam when an external force is applied to the follower cam. Therefore, even if an external force is applied to the turret during the tool change operation, the turret driven by the speed reducer does not rotate. This ensures the safety of the automatic tool changer.

Claims: A machine tool comprising a spindle head and an automatic tool changer comprising a turret (38) holding a plurality of tools by means of grips (28) arranged on the periphery thereof and supported for rotation about a rotation axis (18), said automatic tool changer selecting the desired tool by indexing said turret (38) and changing tools between said desired tool and a tool mounted on a spindle of said machine tool by said turret swinging toward and away from the spindle, said automatic tool changer comprising: a first cam means (C S ) provided on a spindle head (34) of said machine tool for swinging said turret (38) in cooperation with a first cam roller means (21) mounted on a back face of said turret (38) for rotation about an axis, characterized by a second cam means (C L ) provided on said spindle head (34) for raising and lowering said turret (38) with respect to said spindle head (34) in a direction along the central axis of said spindle of said machine tool; and a link means (6, 8, 14, 16) having a second cam roller means (22) cooperating with said second cam means (C L ), when said spindle head (34) is raised or is lowered and said turret (38) swings based on said cooperation between said first cam means (C S ) and said first cam roller (21), said link means (6, 8, 14, 16) receiving a force generated by the cooperation between said second cam means (C L ) and said second cam roller means (22) and raising or lowering said turret (38) with respect to said spindle in the direction along said central axis of said spindle whereby the relative velocity between said turret (38) and said spindle head (34) is reduced. The machine tool according to claim 1 wherein said first cam means (C S ) is extended parallel to said central axis of said spindle and comprises first and second flat bearing faces (C Sa , C Sb ) and a third bearing face (C Sc ) arranged between said first and said second bearing faces (C Sa , C Sb ) and having externally convex configuration. The machine tool according to claim 2 wherein said first and second bearing faces (C Sa , C Sb ) are integrally formed. The machine tool according to claim 2 wherein said first and second bearing faces (C Sa , C Sb ) are separately formed each other. The machine tool according to claim 1 wherein said second cam means (C L ) is of a type having a hook-shaped groove composed of a straight portion (C La ) extended generally parallel to said central axis of said spindle and a curved portion (C Lb ). The machine tool according to claim 5 wherein said turret (38) comprises a rotational shaft provided with a coaxial type speed reducer (39) having a reduction ratio of an integral number of 2 or more. A machine tool according to claim 1 wherein said turret (38) comprising a rotational shaft provided with a coaxial type speed reducer (39) having a reduction ratio of a integral number of 2 or more. The machine tool according to claims 6 or 7 wherein said speed reducer (39) comprises: a plurality of ball means (48) transmitting the driving force, the number of said ball means (48) corresponds to the number of said reduction ratio plus one. a driving cam means (44) containing a first cam groove (58) which engages with said ball means and has a circular configuration, the center of the circle is eccentrically positioned with respect to the axis of said speed reducer; a follower cam means (42) containing a second cam means (52) having a plurality of convex and concave portions, the number of convex portions corresponding to said reduction ratio; a holder means (46) provided with a plurality of equally spaced radial grooves the number of which corresponds to said number of said reduction ratio plus one. each of said grooves allowing said respective ball means to move in the radial direction: and said first cam means (44) and said second cam means (42) connected to each other with said holder means (46) therebetween, the sides of each said cam means (44, 42) formed with said respective grooves (58, 52) facing each other whereby the rotation of said driving cam means (44) being transmitted to said follower cam means (42), and reduced, through said ball means (48). The machine tool according to claim 8 wherein said driving cam means (44) comprises a generally circular member with a turret gear means (30) on the periphery, said turret gear means (30) engaging with a spindle gear means (32) said machine tool whereby said driving cam means (42) obtains a driving force.

Inventors: FUJIMOTO AKIHIKO, ISHII HISAO, OKAMOTO SHINYA, SATO NAOKI, FUJIMOTO, AKIHIKO, ISHII, HISAO, OKAMOTO, SHINYA, SATO, NAOKI, FUJIMOTO, AKIHIKO, FANUC MANSION HARIMOMI 6-109, OKAMOTO, SHINYA, FANUC DAI-3 VIRA-KARAMATSU, SATO, NAOKI, FANUC DAI-3 VIRA-KARAMATSU
Applicants: FANUC LTD, FANUC LTD.
Application year: 1993
Main classification: B23Q3
IPC codes: B23Q3