JPS62152634A - Clamp device of turret head for machining tool - Google Patents

Abstract

PURPOSE:To aim at ensuring the fixation of a turret head to a frame, by locating one of spindles at a machining position and the other spindle at a tool exchanging position, and thereafter, by making clamp pieces approach together so that a pair of outer peripheral flanges are fastened at a radially outward position. CONSTITUTION:One 16 of a pair of spindle heads is located at a machining position while the other spindle head 66 is simultaneously located at a tool exchanging position, and thereafter, when a clamp actuating cylinder is operated to make the forward end parts of clamp pieces 19 approach together, the clamp pieces 19 fasten a pair of outer peripheral flanges 11f, 17f at a radially outside positions in a such a condition they are fitted onto the tapered surfaces 11t, 17t of the flanges 11f, 17f. In this phase, wedging action is effected between the clamp pieces 19 and the flange taper surfaces 11t, 17t, and therefore, a turret 17 is stably and surely secured to a frame 11. During machining or upon completion of tool exchange, the clamp pieces 19 are pressed by the clamp actuating cylinder in the direction in which the forward end parts of the clamp pieces 19 are separated from each other, and then the turret 17 is turned.

Description

Detailed Description of the Invention A1 Objective of the Invention (11 Industrial Field of Application) The present invention is directed to a system in which a leaning tower type turret head rotatably supports a plurality of tool rotation spindles and is rotatably supported with respect to a frame body. This invention relates to a clamping device for a turret head of a machine tool of the type described above.

(2) Prior Art A machine tool of the type in which a leaning tower type turret head rotatably supports a plurality of tool rotation spindles is rotatably supported on a frame body is disclosed in Japanese Patent Application Laid-Open No. 52-122976. This is already known as seen in the official gazette.

(3) Problems to be Solved by the Invention When the turret head is rotated to position one of the plurality of spindles at the machining position, at the same time, one of the other spindles (one of the spindles is positioned at the tool exchange position). rear,
Conventionally, when fixing the turret head to the frame, it was fixed using an index pin that responds to a detection signal of the rotation position of the turret head. However, fixing with an indexing bin does not sufficiently fix the turret head to the frame, so vibrations are likely to occur in the turret head, especially during high-speed cutting, making it difficult to perform highly accurate machining.

Therefore, the main object of the present invention is to obtain a clamping device for a turret head for a machine tool, which can securely fix the turret head to a frame, has a simple structure, and is reliable in operation. It is.

B0 Configuration of the Invention +11 Means for Solving Problems According to the present invention, a leaning tower type turret head that rotatably supports a plurality of tool rotation spindles is rotatably supported on a frame. A clamping device for a turret head of a machine tool according to the above-mentioned type, comprising: an outer peripheral flange formed on the outer peripheral side of the end edge of the cylindrical support part of the frame body and an outer peripheral side of the end edge of the cylindrical connecting part of the turret head. The formed outer peripheral flanges face each other on the same axis, and the back sides of each of the outer peripheral flanges are formed as tapered surfaces so as to form an annular wedge with each other. A pair of semicircular clamp pieces are pivotally supported at the proximal end of each clamp piece so as to fit into the tapered surface portion of each of the outer peripheral flanges, and the position between the tip ends of the pair of clamp pieces is determined. A clamping device for a turret head for a machine tool is obtained, characterized in that a clamp operation cylinder is supported for swinging the tip of each of the clamp pieces in a plane parallel to each of the outer peripheral flanges. .

(2) For production.

At the same time, the turret head is rotated to position one of the plurality of spindles at the machining position, and at the same time, after positioning one of the other spindles (one of them at the tool change position),
When the clamp operation cylinder is actuated to draw the tips of the clamp pieces together, each clamp piece tightens the outer flanges from the outside in the radial direction while being fitted into the tapered surface portions of the pair of outer flanges. At this time, a wedge action occurs between each clamp piece and the tapered surface of each outer periphery flange, and the turret nozzle is securely fixed to the frame in a stable state. When machining and tool exchange are completed and the turret head is rotated relative to the frame, the clamp operation cylinder is actuated to press and move the tips of each clamp piece away from each other. Since the turret head is separated from the tapered surface of the outer peripheral flange, the turret head can freely rotate relative to the frame.

(3) Examples An embodiment of the present invention will be described below with reference to the drawings.

First, in FIGS. 1 and 2, a left-right moving table 3 is mounted on the head 1 of the machine tool, and the left-right moving table 3 is moved in the left-right direction by a feed motor 2.
Mounted on the top is a back-and-forth moving table 7 that is moved back and forth along a pair of guide rails 5.6 by a feed motor 4.

A column 8 is erected on this longitudinally moving table 7, and an elevating frame 11 of the tool drive unit A, which is raised and lowered by a feed screw 10 rotationally driven by a feed motor 9, is vertically mounted on the front side of the column. The column 8 is moved up and down relative to the column 8 along a pair of left and right guide rails 12 and 13 extending from the left to the right. A leaning tower turret rad 17 is supported on the front side of the elevating frame 11 and is rotated around an axis in a direction inclined with respect to the front-rear direction in a horizontal plane. Head 16.
66 is formed. Each spindle head 16.66
The central axes of the tool drive unit A are twisted to each other as shown in Fig. 1 to avoid interference between the internal mechanisms of the tool drive unit A, and as shown in Fig. 2, the spindle The central axis of the head faces in the front-back direction with respect to the column 8, and the central axis of the spindle head runs in the left-right direction with respect to the column 8 as the rad 17 rotates toward the turret during tool exchange.

In FIG. 2, spindle head 16 is in the cutting position and spindle head 66 is in the tool change position. Further, as shown in FIG. 2, the guide rail 13 is disposed in front of the guide rail 12, and each guide rail 12.
The distances from 13 to turret head 17 are both short.

In FIG. 3, the outer circumferential side of the cylindrical connecting part 18 of the turret head 17 is rotatably supported on the inner circumferential side of the cylindrical support part 14 of the lifting frame 11 via a bearing 15. The opposing surfaces of the outer circumferential flange 11r of the lifting frame 11 and the outer circumferential flange 17f of the turret rod 17 are configured to be able to freely come into sliding contact with each other. and each outer peripheral flange 11 f.

The back side of 17f is formed as a tapered surface 11t, 17t, respectively, so as to cooperate with each other to form an annular wedge, and these pair of outer peripheral flanges 11f, 17
The outer surface of r is surrounded by an annular clamp 19 to prevent the turret head 17 from pivoting as required.

A gear 20 is integrally fixed to the end face side of the cylindrical connecting part 18, and a turret rotation motor 21 mounted on the elevating frame 11 is attached to the gear 20. Bevel gear 23, bearing 24.2 on the cylindrical support 14
A gear 28 on the other end of the gear shaft 26, which is rotatably driven via a bevel gear 27 on one end of the gear shaft 26, is in mesh with the gear shaft 26.

The rotational driving force of the tool rotation motor 29 mounted on the lifting frame 11 is transmitted by an output shaft 30 and a bearing 31 by the lifting frame 11.
．． 32, a gear 34 on a gear shaft 33 rotatably supported by a gear shaft 32, a gear 38 on a gear shaft 37 rotatably supported by an elevator frame 11 via bearings 35, 36, and a gear 38 on a gear shaft 37 rotatably supported by an elevator frame 11. The signal is transmitted to the spline 43 on the outer circumferential surface of the forward protrusion of the gear shaft 41 via the gear 42 on the gear shaft 41 which is rotatably supported via bearings 39 and 40.

The spline 43 has a drive side engagement member 4 of the clutch 44.
The spline on the inner peripheral surface of 4a is engaged. The driving-side engaging member 44a has a cylindrical shape as a whole, and has a retaining portion on its front end edge that engages with the driven-side engaging member 44b, and has a retaining portion on its outer peripheral surface near the rear end. A clutch operation wheel 45 having an annular groove 46 formed on the outer peripheral surface side is fixed.

A proximal end of a rod 47 that protrudes forward in parallel with the spline 43 is fixed to the elevating frame 11, and a fixed piston 48 formed in the center of the rod 47 has a
A clutch operation cylinder 49 is fitted. Both end walls of the clutch operating cylinder 49 are slidable along the outer circumferential surface of the loft 47, and a clutch operating pawl 50 fixed on the outer circumferential surface near the rear end of the clutch operating cylinder 49 is fitted into an annular groove of the clutch operating wheel 45. 46. As shown in FIG. 4, a base end portion of a sliding contact member 73 that protrudes in a direction perpendicular to the axial direction of the clutch operation cylinder 49 is fixed on the upper surface of the rear end portion of the clutch operation cylinder 49. The sliding member 73 is slidably fitted into a guide rail 74 parallel to the loft 47 whose base end is fixed on the elevating frame 11 and a stopper nut 75 is screwed onto the distal end. ing. The sliding contact member 73 (FIG. 4) slides along this guide rail 74, so that the clutch operation cylinder 4
9 slides along the rod 47 while always maintaining a constant orientation. When the pressure fluid is conducted to the pressure fluid path 51 in the rod 47, the clutch operation cylinder 49 is moved back and the clutch 44 is disengaged, and when the pressure fluid is conducted to the pressure fluid path 52 in the loft 47. , the clutch operation cylinder 49 moves forward and the clutch 44 becomes engaged.

In FIG. 3, the inner circumference 17 of the spindle head 16 is
A hollow spindle 55 is rotatably supported via a bearing 53 and a bearing group 54, and an annular driven-side engagement member 44b constituting the clutch 44 is fixed on the outer peripheral surface of the rear end of the hollow spindle 55. has been done. Therefore, when the clutch 44 is in the engaged state, the rotational driving force on the spline 43 side is transmitted to the hollow spindle 55 via the clutch 44.

A tapered surface 55t that expands toward the front is formed on the inner circumferential surface side of the front end of the hollow spindle 55, and a tapered surface 57t formed on the outer circumference of the tool holder 57 is in close contact with this tapered surface 55t. It is supposed to be done. When the tool holder 57 is fitted into the tapered surface 55, the rotational driving force of the hollow spindle 55 is applied to the retaining pin 56 fixed to the front end of the hollow spindle 55 on the outer peripheral surface side of the front end of the tool holder 57. The tool holder 57 is engaged with the engagement recess formed in the tool holder 57 via the retaining pin 56.
transmitted to.

A tool holder shaft 58 having an enlarged portion at the rear end protrudes rearward from the rear end surface of the tool holder 57, and this tool holder shaft 58 extends in the axial direction within the hollow portion of the hollow spindle 55. It is adapted to fit into a cylindrical portion 60 formed at the front end of the drawbar 59. Cylindrical part 60
A plurality of, for example three, ball holding holes penetrating in the radial direction are formed at intervals in the circumferential direction, and a ball 61 is held in each ball holding hole so as not to come off. A cylindrical member 62 having a tapered surface that expands forward is held at a position corresponding to the cylindrical portion 60 in the hollow portion of the hollow spindle 55 on the inner periphery of the front end. A nut 63 is screwed to the rear end of the drawbar, and the spring biasing force of a large number of annular leaf springs 64 interposed between the nut 63 and the shoulder on the inner peripheral side of the hollow spindle 55 causes The drawbar 59 is constantly receiving a rearward tensile force, and due to this spring biasing force, each ball 61 moves along the tapered surface on the inner circumference side of the cylindrical member 62, tightens the tool holder shaft 58, and tightens the tool holder. 57 to securely hold the tapered surface 55 within the part.

When removing the tool holder 57 from the hollow spindle 55, rotate the turret head 17 and remove the tool holder 57 from the spindle head 1.
6 to the tool exchange position, then move the drawbar 59
The proximal end surface of the tool holder 57 is pressed against the biasing force of the spring by a bush rod (described later), and the gripping claw is engaged with an annular retaining groove 65 formed on the outer peripheral surface of the distal end of the tool holder 57 to hold the tool holder 57 in the hollow state. The tool holder 57 can be removed from the hollow spindle 55 by pulling the spindle 55 outwards.

A pressurized air introduction hole 59C is formed in the drawbar 59 to penetrate in the axial direction, and when the tool holder 57 is removed from the hollow spindle 55 during tool exchange, pressurized air is introduced into the pressure air introduction hole 59C. By doing so, the tapered surface 55t can be cleaned by blowing pressurized air toward the tapered surface 55.

In FIGS. 4 to 7, the spindle nozzle 16 is in the machining position, and the tool 124, the tool shaft 125 of which is held by the tool holder 57, is in a cutting operation state. In contrast, the spindle head 66 is in the tool change position. A hollow spindle 69 is rotatably supported on the inner peripheral side of the spindle head 66 via a bearing 67 and a bearing group 68, and the hollow spindle 69 holds a tool holder 71 that holds a tool shaft 70. There is.

The hollow spindle 69 has exactly the same structure as the hollow spindle 55, and the driven side engagement member 72 of the clutch 44 is fixed on the outer peripheral surface of the base end of the hollow spindle 69, and the driven side An engagement groove 83 is formed adjacent to the engagement member 72. On the other hand, a placket 79 protruding from the proximal end of the hook 80 is pivotally supported on a pivot portion 78 of a bracket 77 fixed to the elevating frame 11 .

An engagement groove 8 for the hollow spindle 69 is provided at the tip of the hook 80.
A two-pronged engagement claw 82 that engages with the hook 80 is formed in the center of the hook 80, and an elongated long hole 81 is formed in the center of the hook 80 from the proximal end to the distal end of the hook 80. An engagement pin 76 protruding from the upper surface of the outer peripheral portion of the clutch operation cylinder 49 is loosely fitted into the elongated hole 81 . Therefore, while the clutch operation cylinder 49 is retracted and the clutch 44 is placed in the disengaged state when the turret head 17 is rotated by the operation of the turret rotation motor 21, the hook 80 is rotated around the pivot portion 78 and the lifting frame 11 is rotated. Although the engaging pawl 82 is disengaged from the engaging groove 83 by swinging toward the other side, one of the spindles, for example, the spindle head 16, is positioned at the processing position and simultaneously the other spindle head, for example, When the spindle head 66 is positioned at the tool exchange position and the clutch operating cylinder 49 moves forward to engage the clutch 44, the hook 80 swings forward about the pivot 78 and the engagement pawl 82 engages. In particular, in FIGS. 6 and 7, the hook 80 counteracts the force applied in the axial direction of the hollow spindle 69 by engaging the groove 83 and prevents the bearing 67 and the bearing group 68 from being subjected to excessive force. A cylinder 90 is integrally formed inside the cylinder 90.
The tip of a bushing rod 92 that is integral with the piston rod of the piston 91 that slides therein can protrude toward the tip of the hook 80 .

A flow path 93 is formed in the bush rod 92,
When four pressure fluids are supplied to the port 95 as shown in FIG. When pressurized fluid is introduced into the boat 94 with the hook 80 engaged with the proximal end of the spindle 69, the piston 91 moves toward the distal end of the hook 80, and the bushing rod 92 moves along the proximal end of the drawbar 97. By pressing the drawbar 97 against the spring force of the leaf spring 98, the spindle 69
Move it to the tip side. At the same time, the channel 93 is connected to the boat 96
A pressurized air introduction hole 97C formed by the boat 96, the flow path 93, and the hollow part of the drawbar 97 communicates with the pressurized air.
is introduced into the annular gap between the tapered surface 69t of the tip of the spindle 69 and the tapered surface 711 of the tool holder 71.

As a result, the engagement between the drawbar 97 and the tool holder 71 is released, and the tool holder 71 can be removed from the spindle 69, and the tapered surface 69t of the spindle 69 is cleaned by the pressurized air.

During this time, since the hook 80 is engaged with the base end of the spindle 690, the spindle 69 is not pushed toward the distal end, and no unreasonable force is applied to the bearings 67, 68.

In FIGS. 8 to 10, the annular clamp 19 is composed of a pair of semicircular clamp pieces 19a and 19b, each of which has its base end pivoted on a pivot 99 on the lifting frame 11. . A clamp operation cylinder 100 supported by the elevating frame 11 is disposed between the tips of the clamp pieces 19a and 19b. The piston rods 103a and LQ3b of the pistons 102a and 102b that slide in the pair of cylinder chambers Iota and 101b formed to face each other in the clamp operation cylinder 100 extend in opposite directions and correspond to each other. Pivotal supports 105 of brackets 104a, 104b formed at the tips of clamp pieces 19a, 19b
a and 105b. Each piston 102a,
The opposite surface side of 1Q2b is a pressure fluid chamber communicating with a common boat 106, and each piston 102a.

A temporary spring 107 is interposed between each end wall 102b and the end wall through which the piston 07 doors 103a and 103b pass.

Therefore, each piston 102a, 102b is always biased by the corresponding leaf spring 107 in the direction of approaching each other, and during machining and tool exchange, pressure fluid is not introduced from the boat 106, and each piston 1
02a and 102b are each subjected to a force in the direction of approaching each other by the spring biasing force of the corresponding leaf spring 107, and the inner peripheral surface of each clamp piece 19a and 19b is attached to each outer peripheral flange as shown in FIGS. 3 and 4. It is pressed against the tapered surfaces 11t and 17t of ILf and 17f, and securely fixes the turret head 17 to the elevating frame 11 by a wedge action.

When the turret head 17 turns, the boat 106
By introducing more pressure fluid, each piston 10
2a, 102b move away from each other, and as a result, each clamp piece 19a, 19b swings outward around the pivot portion 99 to move away from the outer peripheral flanges 11f, 17f, respectively, so that the turret head 17 can be raised and lowered. It can rotate relative to the frame 11.

C0 Effects of the Invention As described above, according to the present invention, the outer peripheral flange of the cylindrical support portion of the frame body and the outer peripheral flange of the cylindrical connecting portion of the turret head cooperate with each other to form an annular wedge. The tapered surfaces are formed as tapered surfaces, and a pair of semicircular clamp pieces are configured to swing around the pivot portion and press into contact with these tapered surfaces, so that the outer peripheral flange of the turret head is The fastening can be reliably fixed over a long section in the direction (rust action), and the mechanical rigidity of the connection between the turret head and the frame can be maintained high, so the turret head can be tightened even during high-speed cutting. It is possible to prevent the occurrence of vibration and perform highly accurate machining.

In addition, a clamp operation cylinder for swinging the tip of each clamp piece is provided between the tips of the pair of clamp pieces, so the clamp can be operated reliably with a simple configuration. I can do it.

[Brief explanation of drawings]

FIG. 1 is a front view showing an example of a machine tool equipped with a support device for a tool drive unit according to an embodiment of the present invention, FIG. 2 is a plan view of the machine tool shown in FIG. 1, and FIG. Figure III
-I A side view of the main part seen along the line, Figure 6 is the 4th
Figure 7 is a cross-sectional view of the main part similar to Figure 6 in an operating state different from Figure 6, Figure 8 is a cross-sectional view of the main part of Figure 3.
Figure 9 is a cross-sectional view of the main part taken along line -■.
■A side view of the main part taken along the line, Figure 10 is the X-
FIG. 3 is a sectional view of a main part taken along an X-ray. 11... Frame, 11f... Outer flange, 11t.
...Tapered surface, 14...Cylindrical support part, 17...To turret, 7 do, 17f...Outer periphery flange, 17t...
・Tapered surface, 18...Cylindrical connecting portion, 19a, 19b・
... Clamp piece, 55.69 ... Spindle, 100
・・・Clamp operation cylinder

Claims (1)

[Claims] A leaning tower type turret head (17) that rotatably supports a plurality of tool rotation spindles (55, 69) is attached to the frame (1).
1) A clamping device for a turret head of a machine tool which is rotatably supported relative to the frame (
11) and the outer peripheral flange (11f) formed on the outer peripheral side of the end edge of the cylindrical support part (14) and the turret head (17).
) are opposed to each other on the same axis with the outer peripheral flanges (17f) formed on the outer peripheral side of the end edge of the cylindrical connecting portion (18), and the back side of each of the outer peripheral flanges (11f, 17f) is They are formed as tapered surfaces (11t, 17t) so as to cooperate with each other to form an annular wedge, and each of the outer peripheral flanges (11f, 17t) is formed on the frame (11).
A pair of semicircular clamp pieces (19a, 19b) are pivotally supported at the proximal end of each clamp piece (19a, 19b) so as to fit into the tapered surface (11t, 17t) of the clamp piece (17f), These pair of clamp pieces (19a, 19
b) At the position between the tips of each of the clamp pieces (1
9a, 19b) to each outer peripheral flange (11f).
, 17f). A clamp device for a turret head for a machine tool, characterized in that a clamp operation cylinder (100) is supported for swinging operation in a plane parallel to .