JPS6018275Y2 - Crankshaft phase indexing device - Google Patents

Description

[Detailed description of the invention] In order to perform processing such as turning and grinding the crank pin of the crankshaft, this invention uses phase indexing to align the axis of the crank pin with the rotation center axis of the main shaft that rotates the workpiece. Regarding the equipment for performing.

As is well known, the journal portion of a crankshaft is located on the same axis that is the rotation center of the crankshaft, but the crank pin is located at an eccentric position with respect to the axis, and in a crankshaft having a plurality of crank pins, each The crankbins are at different angular positions with respect to the axis.

For example, in a crankshaft for a two-cylinder internal combustion engine, each crank pin has a phase difference of 180 degrees.

Therefore, in order to perform processing such as turning or grinding a crank bottle, a chuck is provided on the rotating main shaft with the clamp center eccentric by the amount of eccentricity of the crank pin, and the chuck is made to hold the journal portion of the crankshaft. According to
It is necessary to determine the central axis of the crank pin so that it coincides with the rotation center of the main shaft.

Conventionally, as a device for accurately determining the phase of a crankpin, as in the crankshaft indexing and holding device described in Japanese Patent Publication No. 51-48716, a device is mounted on a slider at the tip of the main shaft and eccentrically disposed a predetermined distance from its center of rotation. Bushes corresponding to the phase of the crank pins of the crankshaft are fitted into the mounted chuck in the same number as the crank pins, and dowel pins provided on the slider so as to be retractable are inserted into the slider when the desired crank pin is indexed. The phase of the chuck is determined by fitting the bushing corresponding to the phase of the chuck.

In such a phase indexing device, the accuracy of phase indexing is low due to the play that occurs between the dowel pin and the bushing, and the cylinder for operating the dowel pin and the clamp for clamping the chuck to the main shaft are attached to the tip of the main shaft. Because it is necessary to install a device, it is not possible to shorten the distance between the bearing that supports the spindle and the chuck, and the weight of the tip of the spindle becomes large, which may cause the crankshaft to swing during machining. It was not suitable for machining crankshafts.

The purpose of this invention is to provide a crankshaft phase indexing device that improves the accuracy of phase indexing and can support the crankshaft with high rigidity. The center of rotation of the chuck is eccentric from the center of rotation of the main shaft by a predetermined distance equal to the amount of eccentricity from the journal of the crank pin at the front of the main shaft to be driven, so that the chuck can rotate and move in the axial direction with respect to the main shaft. A movable shaft whose front end is fixed to the rotation center of the chuck is provided inside the main shaft at the waist of the device, and gear couplings are formed on opposing surfaces of the rear part of the chuck and the front part of the main shaft to connect the movable shaft to the cylinder. By moving the gear coupling forward and backward in the axial direction using a device, the gear coupling is engaged and disengaged.When determining the phase, the movable shaft is moved forward and the gear coupling is disengaged, and the crank pin is rotated by the rotation of the movable shaft. When the desired crank pin is indexed, the movable shaft is moved back to engage the gear coupling, and the phase relative to the main shaft of the chuck is determined. High-precision phasing and ease of high-precision finishing with little backlash allow for high-precision indexing, and the distance between the bearing that supports the main spindle and the chuck can be shortened as much as possible. be.

The drawing shows an embodiment of the present invention for determining the phase of a crankshaft having two crank pins with a phase difference of 180 degrees between P□ and P2. Two spindle heads are formed, a left spindle head and a left spindle head 3. Inside these spindle cylinders 2 and 3, spindles 4 and 5 are coaxially and rotatably supported by bearings 6 and 6, respectively. The main motor 7 attached to the main shaft 4,
The main shafts 4 and 5 are configured to rotate synchronously by gears 9 and 9 fixed concentrically to the main shafts 4 and 5.

A thick main shaft body 10 having a substantially disc shape is formed at the end (front part) of the right main shaft 4 facing the left main shaft 5.
A bottomed cylindrical hole 11 is bored in the end face of the chuck 1, and the cylindrical hole 11 is eccentric from the rotation center of the main shaft 2 by a predetermined distance and has an axis parallel to the rotation center of the main shaft 2.
A cylindrical protrusion 14 formed on the chuck body 13 of No. 2 is fitted to support the chuck 12 on the spindle body 10 so as to allow relative rotation and axial movement.

The chuck body 13 is provided with a receiver 15 having an arcuate receiving surface centered on the axis of the cylindrical projection 14, and a clamp arm 16 holds the journal J of the crankshaft W concentrically with the cylindrical projection 14. It is configured to tightly grip onto the receiver 15.

The clamp device 17 including the receiver 15 and the clamp arm 16 is a conventionally known device in which the clamp arm 16 is moved by a cylinder device.

On the other hand, a substantially disc-shaped flange 18 is formed at the end of the left main shaft 5 facing the right main shaft 4, and a chuck 21 provided with a receiver 19 and a clamp arm 20 is provided on the end surface of the flange 18. Receiver 19 and clamp arm 2
The rotation center of the journal J of the crankshaft W supported by the crankshaft 0 is fixed by a bolt 23 such that it is eccentric from the rotation center of the left main shaft 5 by the predetermined distance.

The clamping device 22, including the receiver 19 and the clamping arm 20, is identical to the clamping device 17 described above.

The eccentricity of the chuck 12.21 corresponds to the eccentricity between the journal J of the crankshaft W and each crank pin P, P2.
, J are tightly gripped by the chucks 12.21 by the respective clamping devices 17.22, the axis of at least one crank pin P□ or P2 is aligned with the left and right main shafts 4.
, 5, and machining such as turning or grinding is performed at the aligned position.

At the other end (rear part) of the right main shaft 4, an indexing plate 25 and a gear housing 26, which are rotatable on the main shaft head 2 via the bearing 6, are provided.
is fixed, and a shaft hole 27 having a diameter smaller than the diameter of the cylindrical hole 11 is bored concentrically with the bottomed cylindrical hole 11 inside the main shaft 4. A movable shaft 28 whose tip end is fixed to the chuck body 13 and whose rear end is supported by a gear housing 26 and projects into the moat 26 is arranged parallel to the rotation center axis of the main shaft 4.

A bottomed cylindrical hole 29 concentric with the rotation center of the main shaft 4 is bored at the other end (rear part) of the gear housing 26.
A universal joint device 30 having a cylindrical outer shape is assembled inside the cylindrical hole 29, and is configured to move forward and backward in the axial direction within the cylindrical hole 29, and the open end of the cylindrical hole 29 is coaxial with the center of rotation of the main shaft 4. The bearing sleeve 32 of the intermediate shaft 31 having the center of rotation is fixed and closed.

As shown in FIGS. 2 and 5, the universal joint device 30 includes an external gear 33 concentrically fixed to the rear end of the movable shaft 28 and a cylindrical hole 29 on the outer peripheral surface. an internal gear 36 that is rotatably fitted and meshes with the external gear 33; and a shaft 31 at the tip of the intermediate shaft 31;
and an external gear 37 that is concentrically fixed to the internal gear 36 and meshes with the internal gear 36.

As will be described later, the external gears 33, 37 and the internal gear 36 are incorporated into a piston body constituted by piston end plates 35, 40, and regardless of the axial movement of the piston body, The positions and meshing relationships between the gears do not change.

In the universal joint device 30, when the external gear 37 rotates due to the rotation of the intermediate shaft 31, the rotation of the gear 37 is caused by the rotation of the internal gear 3.
6 to the external gear 33, which rotates the movable shaft 28 and rotates the chuck 7.12 in its eccentric position.

The piston end plates 35 and 40 of the piston body each have an outer peripheral surface fitted into the cylindrical hole 29 to perform a piston action, and one piston end plate 35 is connected to the movable shaft 2.
8 is rotatably supported, and the piston end plate 3 of the gear 33 is held between the shaft 28 and the external gear 33ε.
Movement in the axial direction with respect to S is restricted.

The other piston end plate 40 rotatably supports the intermediate shaft 31, and also fixes a spacing piece 34 that is concentrically with the external gear 37 and integrally formed with the one piston end plate 35. This fixes to the piston end plate 35, determines the positional relationship of the external gears 33, 37, and rotatably sandwiches the internal gear 36 between the piston end plates 35, 40.

In this way, the external gear 33, 37 and the internal gear 33
The positional relationship and meshing relationship are maintained by a piston body constituted by piston end plates 35 and 40.

A cylinder chamber 41 is formed between the piston end plate 35 and the bottom surface of the cylindrical hole 29, and a cylinder chamber 42 is formed between the piston end plate 40 and the end surface of the bearing tube 32. Guide bin 4 protruding from gear housing 26
3 is guided through a guide hole 44 formed in the piston end plate 35 to prevent the piston end plates 35, 40 from rotating.

Therefore, by supplying pressure hydraulic oil to either one of the cylinder chambers 41, 42, the universal joint device 30 can
It is movable in the axial direction together with the piston body consisting of piston end plates 35 and 40, the movable shaft 28, and the intermediate shaft 31.

The bearing tube 32 has its outer circumferential surface slidably in contact with the inside of a distributor 46 supported by a suitable support 45 on the machine base 1, and is connected to the cylinder via oil passages 47 and 48 in the distributor 46. Pressure hydraulic oil is distributed between the chambers 41 and 42, and the piston body containing the universal joint device 30 is inserted into the bottomed cylindrical hole 29.
Allows for reciprocating movement inside.

A gear coupling 50 consisting of coupling members 51 and 52 is formed on the surface of the spindle body 10 of the left spindle 4 facing the chuck body 13 and the surface of the chuck body 13 facing the spindle body 10, respectively.

The coupling members 51 and 52 each have an annular shape, and ridges 53 and 54 each having a tooth-like cross-section of a gear whose longitudinal direction extends in the radial direction are formed in an annular shape on the same circumference on the opposite surfaces thereof. The ridges 53 and 54 have a shape having the same central angle, and are arranged in large numbers at equal intervals with the same central angle as the central angle.

Such coupling members 51 and 52 are connected to the main shaft body 10.
, are fixed by fitting into stepped portions 38 and 39 formed on the opposing surface of the chuck body 13 around the central axis of rotation of the chuck 12, that is, the central axis of rotation of the movable rod 28, and have protruding ridges 53 and 5.
4 are facing each other.

When the movable shaft 28 is retracted by the pressure of the pressurized hydraulic oil introduced into the cylinder chamber 41, the gear coupling 50 engages the ridges 53 and 5 of the coupling members 51 and 52.
4 is fitted into the gap between the ridges of the opposing coupling members, the phase difference between the main shaft 4 and the chuck 12 is determined by the ridges 53 and 54, and the chuck 12 is integrally coupled when the main shaft 4 rotates. Let it rotate.

When pressurized hydraulic oil is introduced into the cylinder chamber 42, the movable shaft 28 is moved forward and the coupling members 51, 52 are disengaged, allowing the chuck 12 to rotate relative to the main shaft 4 by the movable shaft 28.

One end plate 56 of a cylindrical lock-shaped clutch casing 55 is fixed to the other end (rear end) of the intermediate shaft 31, and the other end plate 57 of the casing has a A drive shaft 60 of a deceleration drive device 59 operated by a phase indexing motor 58 is loosely passed through the intermediate shaft 31 coaxially with the inner wall of the end plate 57 and the front end of the drive shaft 60. Tooth-shaped ridges 62 and 63 similar to the ridges of the gear coupling are provided on the opposite surface of the fixed engagement plate 61.
are disposed in an annular manner at the same central angle, forming a clutch 64 that is engaged and disengaged by the reciprocating motion of the intermediate shaft 31 in the axial direction.

Reference numeral 65 in FIG. 2 is a fixed position stop device, and the index plate 25 has at least one tooth groove 66 carved on its circumference, and the index plate 25 is stopped by a cylinder device 67. When a piece 69 formed at the free end of a piston rod 68 that is moved forward and backward in the diametrical direction of the chuck 12 engages with the tooth groove 66, the chuck 12 is stopped at a predetermined angular position.

In addition, reference numerals 71 and 72 in FIG. 2 indicate oil grooves that distribute hydraulic oil to the cylinder devices of the clamp device 17, and 73 in FIG. 1 indicates a distributor that distributes hydraulic oil to the cylinder devices of the clamp device 22. be.

In the device of this embodiment configured as described above, when the main shaft 4 is stopped by the fixed position stop device 65,
As in normal crankshaft turning and grinding equipment, the main shafts 4 and 5 are indexed to angular positions suitable for carrying in and out the crankshaft W, and in this state, the clamping devices 17 and 22 of the chuck 12.21 When the journal J of the crankshaft W is gripped, the crank pin P1 of the crankshaft W. P
2, for example, P□, is indexed on the axis of the main shafts 4 and 5.

When stopped at the fixed position, hydraulic oil is introduced into the cylinder chamber 41 at the bottom of the bottomed cylindrical hole 29 of the gear housing 26 by the oil groove 47 of the distributor 46, and moves the movable shaft 28 to the right end of movement in FIG. It is assumed that the coupling members 51, 52 of the positioning gear coupling 50 are engaged.

At the right moving end position (retracted position) of the movable shaft 28, the universal joint device 30, the intermediate shaft 31, and the clutch casing 55 are all in the retracted position, and the clutch 64 is disengaged.

When the main motor 7 is driven in this state, the main motor 7
is rotated by the left and right main shafts 4, 5 through a synchronous shaft 8 and gears 9, 9.
Since the pin P1 of the crankshaft W is indexed on the axis of the main shafts 4 and 5, the crankshaft W
is rotated about the pin P1 as the center of rotation, and machining such as turning and grinding of the crank pin P1 is performed.

When the machining of the crank pin P is completed, the rotation of the main shaft 4°5 is stopped, and the oil is supplied to the cylinder chamber 42 between the piston 40 of the universal joint device 30 and the end face of the bearing sleeve 32 via the oil groove 48 of the distributor 46. Pressurized hydraulic oil is sent to drain the hydraulic oil in the cylinder chamber 41, and the movable shaft 28 is moved to the leftward movement end (forward end) position in FIG.

In this case, the coupling members 51, 52 of the gear coupling 50 are disengaged, while the clutch 64 is engaged by the advancement of the intermediate shaft 31.

At the same time, the clamping force of the clamping device 22 of the chuck 21 provided on the left main shaft 5 is weakened, allowing relative rotation of the journal J of the crankshaft W with respect to the clamping device 22.

After that, when the phase indexing motor 58 is rotated by a certain rotation angle, the deceleration drive device 59, the drive shaft 60, the intermediate shaft 31,
Chuck body 1 via universal joint device 30 and movable shaft 28
3 is rotated 180 degrees relative to the main axis 4,
The crank pin P2 is indexed to a position coaxial with the main shafts 4 and 5.

For this phase indexing, there is no need to stop the main shaft 4 at a fixed position by the fixed position stopping device 65.

When the crank pin P2 is indexed, the hydraulic oil is sent to the cylinder chamber 41 again and the hydraulic oil in the cylinder chamber 42 is drained, the movable shaft 28 is moved to the retreat position, and the gear coupling 50 is When engaged, the main shaft 4 and the chuck 12 are angularly positioned, and at the same time, the clamping device 22 of the chuck 21 of the left main shaft 5 is tightened tightly.

As the movable shaft 28 moves to the retracted position, the clutch 64 disengages and disconnects the intermediate shaft 31 and the drive shaft 60, so the main shaft drive motor 7 is started again and the main shaft 4.
is rotated to process the pin P2.

In the present invention, the chuck is eccentrically set a predetermined distance from the main shaft rotatably supported by the main shaft head of the machine base, and the chuck is rotated relative to the main shaft and moved in the axial direction about the rotation center parallel to the rotation center of the main shaft. A movable shaft is fixed along the rotation center of the chuck and is mounted inside the main shaft so as to be movable in the axial direction by a cylinder device. Since the gear coupling, which engages and disengages as the chuck moves in the axial direction, is formed around the axis of the movable shaft, the angular positioning of the chuck with respect to the main shaft after determining the phase of the crank pin is easy. This is achieved with high precision by the engagement of the gear coupling, and since the gear coupling is made up of a pair of coupling members in which a large number of tooth-shaped ridges engage with each other as is well known, the movable shaft can be When the gear coupling is moved in the axial direction and engaged, there is no play between the coupling members, and since the gear coupling itself is centripetal, even if there is play between the chuck and the main shaft, the crank will not move. It has the great feature of not affecting the rotation accuracy of the shaft.

In addition, in this invention, since the chuck is directly attached to the front of the main spindle, the distance between the chuck and the bearing that supports the main spindle can be made as short as possible, and the crankshaft does not swing during machining. The drawbacks of conventional devices of this type can be overcome.

In addition, in the present invention, since the rotary drive device for phase indexing is connected to the rear end of the movable shaft via a clutch, the movable shaft is moved in the axial direction by the cylinder device to disengage the engagement of the gear coupling. After that, the crank pin of the crankshaft on the chuck can be indexed by the clutch and the rotational drive device,
This invention simplifies the structure of the phase indexing device and enables highly accurate indexing and angular positioning, so it can be said to be an extremely useful device.

In the present invention, the clutch between the rear end of the movable shaft and the rotational drive device for phase indexing is engaged by utilizing the axial movement (forward movement) of the movable shaft to disengage the gear coupling. The gear coupling and clutch can be engaged and disengaged at the same time if the engagement is made using the axial movement (retreat) of the movable shaft to engage the gear coupling. .

[Brief explanation of the drawing]

The drawings show one embodiment of the present invention, in which Fig. 1 is a front view thereof, Fig. 2 is a cross-sectional view of the main part of the part related to the right main axis, and Fig. 3 is a cross-sectional view of Fig. 2. 4 is a cross-sectional view of a main part of a portion related to the right main axis, and FIG. 5 is a cross-sectional view taken along a broken line V--V in FIG. 2. In the figure, 1 is the base, 2 and 3 are the spindle head, 4 and 5 are the spindle,
12.21 is a chuck, 17.22 is its clamp device, 28 is a movable shaft, 30 is a universal joint device, 35.40 is a piston end plate, 41.42 is a cylinder chamber, 46 is a distributor,
58 is a phase indexing motor, 59 is a reduction drive device, 64 is a clutch, W is a crankshaft, J is a journal, Pl, P
2 indicates a crank bin.

Claims (2)

[Scope of utility model registration request] (1) A machine base to which a main motor is attached, a main shaft that is rotatably supported by the main shaft head of the machine base and rotationally driven by the main motor, and a rotation center of the main shaft that is eccentric by a predetermined distance from the center of rotation of the main shaft. a chuck provided at the front part of the main shaft and having a rotation center parallel to the main shaft and capable of relative rotation and axial movement with respect to the main shaft; and a front part provided inside the main shaft on the rotation center of the chuck. a movable shaft that is fixed to the chuck and can rotate and move back and forth in the axial direction with respect to the main shaft together with the chuck; A gear coupling configured to be engaged and disengaged by movement; a cylinder device that causes the movable shaft to move forward and backward in the axial direction inside the main shaft to engage and disengage the gear coupling; and a clutch connected to the rear end of the movable shaft. A crankshaft phase determining device comprising a rotational drive device for determining a phase, which is detachably associated with a crankshaft and rotates the movable shaft. (2) The gear coupling extends at a predetermined central angle in the radial direction from the rotation center of the movable shaft in a relative plane perpendicular to the axis of the movable shaft at the rear of the chuck and the front of the main shaft. The clutch has a protruding ridge extending from a pair of coupling members disposed annularly around the rotation center of the movable shaft with a predetermined center angle apart, and one engagement plate constituting the clutch is The other engagement plate, which is fixed to the intermediate shaft rotatably connected to the rear end of the movable shaft via a universal joint, and which faces the retaining plate, is connected to the rotary drive device, which is disposed coaxially with the intermediate shaft. It is fixed to a drive shaft, and when the coupling member of the gear coupling is released from the coupling member by forward movement of the movable shaft, the engagement plate of the clutch is engaged, and by the rearward movement of the movable shaft, the engagement plate of the gear coupling is released. The crankshaft phase indexing device according to claim 1, which is configured to release the engagement plate of the clutch when the coupling member of the clutch is engaged.