JP3285776B2 - Crank pin phase indexing device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a crank pin phase indexing equipment embodied in the crank pin grinding machine for performing machining of grinding or polishing or the like crankpin of the crankshaft.

[0002]

2. Description of the Related Art Generally, in this kind of crank pin phase indexing device,
The main shafts are rotatably supported on the same axis line by a pair of headstocks, and chucks for holding both end journals of the crankshaft at positions separated from the axis line of the main shaft are attached to opposite ends of both main shafts. . A spindle drive motor is connected to each of the pair of spindle heads, and the spindles are rotationally driven by the spindle drive motors, and a crankshaft is rotated around a crankpin located on the same axis as the spindle. Is processed for grinding or polishing by a rotating grindstone.

On one chuck side, a phase indexing motor and a crank pin phase indexing device having a phase indexing shaft are provided, and the crankshaft is rotated by indexing rotation of the phase indexing shaft by the phase indexing motor. Crankpins which are rotated about the journal and have different phases on the crankshaft are selectively arranged at machining positions on the axis of the main shaft.

In such a crankpin phase indexing device, only the phase indexing shaft is rotated while the main shaft is stopped at the time of phase indexing. Further, during the machining operation, it is necessary to rotate the phase index axis together with the main axis so that the phase index axis maintains a fixed relation with the main axis.

[0005] Therefore, the conventional phase indexing apparatus, for example, as disclosed in JP-A-7-606 1 3 JP-mediated complex planetary gear mechanism between the spindle and the phase indexing shaft The two modes of the phase indexing and the machining operation of the phase indexing shaft can be selected by the operation of the planetary gear mechanism.

However, in this conventional phase indexing device, there is a problem that the planetary gear mechanism composed of a large number of gears has a complicated structure, the entire device becomes large, and the manufacturing cost increases. Also, since the gears in the planetary gear mechanism generate rattling noise, etc., the noise is large and not only deteriorates the working environment of the crankpin processing,
There has been a problem that accuracy is reduced due to wear of the gears, and maintenance such as lubrication of the gears is required.

When the crankshaft is changed to one having a different half-stroke, in other words, to one having a different length of the crank arm, the chuck is moved and adjusted, and the axis of the main shaft and the axis of the chuck are adjusted. The distance between is changed. An extendable joint, for example, a Schmitt coupling 201 as shown in FIG. 11, is provided between the spindle and the chuck so as to allow this change in distance.

The Schmitt coupling 201 rotates integrally with the drive shaft on the same axis as the main shaft, a drive coupling plate 202, an intermediate coupling plate 203, and the chuck on the same axis as the main shaft. Driven coupling plate 204
And The intermediate coupling plate 203 is connected on one side to a drive coupling plate 202 via a link 205 and on the other side to a driven coupling plate 204 via a link 206.

Then, as shown in FIG. 12, the center α of the driving coupling plate 202 and the center β of the driven coupling plate 204 connected to the driving coupling plate 202 via the intermediate coupling plate 203. , On the vertical line γ in the direction of expansion and contraction of the Schmidt coupling 201.

Normally, in such a Schmidt coupling 201, a minimum specified value δ is set as an unstable region in the approach distance between the centers α and β,
β does not become shorter than this value δ. Therefore, in the conventional configuration as shown in FIG. 12, when the center distance ε between the main shaft and the chuck is expanded or contracted in response to a change in the half stroke of the crankshaft, the Schmitt coupling 201 Is limited in the range that can follow.

That is, the first axis α which is the axis of the main shaft
And a second axis β which is the axis of the chuck cannot be smaller than a value corresponding to the minimum specified value δ. For this reason, the driven coupling plate 204 is
The limit is the approach movement to the position θ indicated by the two-dot chain line in FIG. 12, and the crankshaft whose half stroke is smaller than the value δ cannot cope with the stroke change.

In this type of crankshaft grinding machine, since the rigidity of a crankpin as a work is generally low, it is necessary to rotate the crankshaft so that the crankshaft is not twisted during machining. For this reason, a synchronous drive device has been proposed in which both main shafts are operatively connected by a synchronous shaft and the two main shafts are synchronously rotated via the synchronous shaft.

However, in this conventional synchronous drive device, since it is necessary to accurately rotate both main shafts via the synchronous shaft, it is necessary to perform a troublesome adjustment operation such as removing backlash of the rotary connecting portion. It is necessary to use a large-diameter synchronous shaft that does not cause twisting of the synchronous shaft itself. In addition, with the long-term use of the device, there is a possibility that rattling occurs in the rotary drive system due to wear or the like, and the two spindles do not accurately rotate synchronously. "

In order to cope with such a situation, there has been proposed a synchronous drive device in which motors are separately connected to the two spindles so as to control the synchronous rotation of the motors. However, in this conventional device, there is a possibility that a synchronous rotation abnormality may occur between the two motors due to modulation of the control system of one of the motors. Thus, when the synchronous rotation abnormality occurs, the crankshaft is twisted, and the machining accuracy is reduced.

[0015] have been proposed such order to solve the problems, for example, the actual fair 7-1 synchronous drive apparatus having a configuration as shown in 3945 JP also conventionally. In this conventional configuration, both main shafts are configured to be synchronously rotated by a pair of motors, and a security shaft is connected between the two main shafts on an axis different from the axis of the main shaft so as to be able to rotate interlockingly. If an abnormality occurs in the synchronous control due to a failure of the motor or the like, the rotation is transmitted from one main shaft to the other main shaft via the security shaft to prevent the crankshaft from being excessively twisted. It has become.

That is, in this conventional synchronous drive device,
When a synchronization shift occurs between the two spindles due to the modulation of the motor control system, the rotational force of one of the spindles forcibly rotates the other spindle via the security axis, and the synchronization between the two spindles is mechanically performed. To ensure. Therefore, when a synchronization shift occurs, the security shaft is responsible for torque transmission, and a thick and strong security shaft is required. For this reason,
Even during normal times when the security shaft becomes excessively heavy and the security shaft does not perform its function, the heavy security shaft wastes the power of the motor and causes energy loss.

Further, if a synchronization shift occurs between the two main shafts due to modulation of the control system of one of the motors, different values of drive torque act on both ends of the crankshaft, and security in this state is increased. The crankshaft is twisted by the forced rotation by the shaft. If the processing is continued in this twisted state, there is a possibility that the processing accuracy is significantly reduced.

The present invention has been made in view of such problems existing in the prior art. Its purpose is to simplify the structure, reduce the size of the entire device, reduce the manufacturing cost,
In addition, it is an object of the present invention to provide a crank pin phase indexing device and a phase indexing method that can suppress noise, maintain high-precision machining, and facilitate maintenance.

[0019]

In order to achieve the above object, according to the invention of a crank pin phase indexing device according to the first aspect, the crank pin phase indexing device is disposed on a first axis so as to be spaced apart from each other and synchronously controlled with each other. A pair of spindles respectively rotated by a pair of spindle drive motors, a chuck body provided at the tip of each spindle, and a first axis provided on each chuck body and separated from the first axis. A chuck portion for gripping journals at both ends of a crankshaft on a second axis parallel to the crankshaft; and a crank provided on the second axis of at least one chuck body so as to be rotatable and engaged with an end surface of the crankshaft. Rotating a shaft, and a phase conversion axis for indexing a phase of a crankpin having a different phase angle on the first axis; and a concentric arrangement with the main axis connected to the phase conversion axis, In crankpin grinding machine and a phase indexing shaft being rotated by a phase indexing motor, a first mode in which said phase conversion shaft is rotated synchronously with the pair of spindle and the same speed, the phase conversion shaft pair as a second mode, which is synchronously rotated with a relative speed difference with respect to the spindle is performed, the control means for controlling the phase indexing motor and both the spindle drive motor is provided, wherein the phase conversion shaft and phase split
Expansion and contraction that can change the distance between the axes between the extension axis
A joint is interposed, and the expansion joint is
Plates, driven coupling plates and their
The intermediate coupling plate located between
Schmidt including a link interposed between the switching plates
And a drive coupling plate.
Gear coupling with the phase indexing shaft
From the center of the phase index axis to the coupling position.
In a direction perpendicular to the direction of extension and contraction .

According to a second aspect of the present invention, in the crank pin phase indexing device according to the first aspect, at least one main shaft has a hollow shape, and the phase indexing shaft is disposed in the main shaft. It is.

According to a third aspect of the present invention, in the crank pin phase indexing device according to the first or second aspect, a plurality of positioning portions corresponding to the indexing angle are provided on the phase conversion shaft, and the chuck body is provided on the chuck body. There is provided a holding member which is detachably engaged with a positioning portion of the phase conversion shaft and holds the phase conversion shaft at a predetermined indexing angle.

According to a fourth aspect of the present invention, in the crank pin phase indexing device according to the third aspect, in the first mode, when the phase indexing motor is stopped, the phase conversion shaft is moved via the holding member. In this manner, the chuck is rotated integrally with the chuck body together with the rotation of the spindle.

[0023] In the invention described in claim 5, in the crank pin phase indexing apparatus in claim 1 serial <br/> mounting chuck present
The body is the one where the distance between the first axis and the second axis expands and contracts
The main shaft is provided so as to be adjustable with respect to the main shaft .

According to the sixth aspect of the present invention, the first to fifth aspects are provided.
In the crank pin phase indexing device according to any one of the above, a detection shaft is connected and arranged between the motor shafts of both spindle drive motors.
And the detection axis has a rotational synchronization deviation between both motor axes.
When it occurs, it detects it and stops both spindle drive motors
This is provided with a detecting means for causing the detection .

According to a seventh aspect of the present invention, in the crank pin phase indexing device according to the sixth aspect , the detection axis is:
On another axis parallel to the axis of the spindle and the axis of the chuck body
It is arranged in .

According to the eighth aspect of the present invention, there is provided the sixth aspect of the present invention.
In the crank pin phase indexing apparatus according to 7, before
The detection axis is divided into two parts, and the divided part
Slip occurs when synchronization is lost between both spindles during
And a detecting means detects clutch slippage.
The motor is brought out to stop the motor .

[0027]

[0028]

[0029]

[0030]

[0031]

[0032]

[0033]

Therefore, according to the first aspect of the present invention,
Processing operation and indexing can be performed by switching modes without using a complicated planetary gear mechanism, and the configuration is simplified. In addition, the expansion joint is
It is possible to respond to a change in the amount of one stroke.
Without being restricted by the minimum specified value of the unstable region of
Its Schmitt coupling can be stretched
You.

According to the second aspect of the present invention, since the phase indexing shaft is located within the main shaft, the size can be reduced. According to the third and fourth aspects of the present invention, the positioning of the phase conversion shaft can be directly performed by mechanical engagement.

[0036]

According to the fifth aspect of the present invention, the distance between the center of the chuck of the chuck body and the axis of the spindle can be adjusted. According to the invention described in claim 6 , when abnormalities occur in the synchronous rotation of the motor shafts due to modulation of the control system of the two spindle drive motors, the rotation of the two spindle drive motors can be stopped immediately. .

According to the seventh aspect of the present invention, since the detection axis extends in the same direction as the main axis or the like, the configuration can be reduced in size. According to the eighth aspect of the invention, when an abnormality occurs in the synchronous rotation of the pair of main shafts, the clutch slips and the connection of the divided portions of the detection shaft is released.

[0039]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below in detail with reference to FIGS. 1 to 5 and FIGS.

As shown in FIG. 1, a pair of headstocks 21 and
Numerals 2 are arranged oppositely on a table (not shown) at a predetermined interval. The hollow main shafts 23 and 24 are rotatably supported by the respective headstocks 21 and 22 via bearings 25 so as to be positioned on the first axis α.

The chuck bodies 26 and 27 are provided with mounting members 28,
At the front ends of the spindles 23 and 24, grippers 32 and 33 are provided at opposite ends of the spindles 23 and 24 as chucks including a holder 30 and a clamp arm 31. The journals 35, 3 at both ends of the crankshaft 34 are formed by the gripping portions 32, 33.
6 is held on a second axis β parallel to the first axis α. The distance ε between the second axis β and the first axis α is, as shown in FIG. 2, the distance between the centers of the journals 35 and 36 of the crankshaft 34 and the centers of the pins 40 to 42. Distance (half stroke)
It is set according to κ.

In addition, the chuck bodies 26 and 27 move relative to the mounting members 28 and 29 in a direction in which the distance ε between the second axis β and the first axis α expands and contracts, that is, the first axis α Is mounted so as to be adjustable in a direction perpendicular to the direction. Then, by turning the adjustment screw 39 with a nut runner (not shown) or the like, the chuck main bodies 26 and 27 are rotated.
To adjust the distance ε between the axes α and β.

Further, in a state where the crankshaft 34 is held between the chuck bodies 26 and 27, any one of the crankpins 40 to 42, for example, the crankpins 40 on both sides is connected to the first axis α of the main shafts 23 and 24. They are arranged on the same axis.

A pair of main shaft drive motors 51 and 52 composed of servo motors are provided corresponding to the main shafts 23 and 24, respectively, and their motor shafts are connected to the main shafts 23 and 24 via a pair of gears 53 and 54, respectively. It is operatively connected. Then, by the synchronous rotation of the spindle drive motors 51 and 52, the two spindles 23 and 24 are synchronously rotated in the same direction at the same speed, and the crankshaft 34 held between the grippers 32 and 33 is rotated by the spindles 23 and 24. Is rotated about any one of the crankpins 40 to 42 located on the same axis as the first axis α. Therefore, both end journals 35 and 36 of the crankshaft 34 revolve around the crankpins 40 to 42 together with the chuck bodies 26 and 27. In this revolving state, the grinding wheel 20 is brought into contact with any one of the crank pins 40 to 42 on the first axis α while being rotationally driven, and the outer peripheral surfaces of the crank pins 40 to 42 are processed for processing or polishing. Is done.

As shown in FIG. 1 and FIG.
Is rotatably supported by one chuck body 26 so as to be located on the same axis as the second axis β. The indexing plate 56 is fixed to the phase conversion shaft 55, and a pin 58 that can be engaged with an eccentric hole 57 on one end surface of the crankshaft 34 protrudes from the end surface thereof, and a plurality of positioning portions as an outer periphery is provided. The engagement grooves 59 are formed at predetermined intervals identical to the arrangement phase of the crank pins 40 to 42.

The cylinder 60 is disposed on one of the chuck bodies 26 so as to face the peripheral surface of the index plate 56, and its piston rod has an engagement groove 59 of the index plate 56.
An engagement body 61 as a detachable holding member is attached to the main body. When the engaging body 61 engages with one of the engagement grooves 59 on the indexing plate 56, the indexing plate 56
And the phase conversion shaft 55 is held at the selected indexing angle, and any of the crankpins 40 to 42 is
3 and 24 are positioned and held in a state where they are arranged on the first axis α.

The pusher 62 is disposed in the indexing plate 23 and the phase conversion shaft 55, and is protruded outward by the urging force of the spring 63 to support one end surface of the crankshaft 34. ing. The cylinder 64 is disposed on the chuck body 27 on the opposite side of the pusher 62, and the piston rod of the cylinder 64 causes the crankshaft 3
The crankshaft 34 is connected to the pin 58 of the index plate 56 by pressing the other end surface of the fourth shaft 4.

The phase indexing shaft 65 is inserted and supported at the center of the one main shaft 23 via a bearing (not shown) so as to be relatively rotatable. A Schmitt coupling 66 as an expansion joint is interposed between the phase indexing shaft 65 and the phase conversion shaft 55, and the two shafts 23, 65 are connected via the Schmitt coupling 66 and a pair of gears 69, 70 to each other. They are operatively connected at a rotation transmission ratio of one to one. The phase indexing motor 67 is mounted on one headstock 21, and its motor shaft is directly connected to a phase indexing shaft 65 via a coupling 68.

As shown in FIGS. 1, 4 and 5, the Schmidt coupling 66 includes a drive coupling plate 71, an intermediate coupling plate 72, and a driven coupling plate 73. The drive coupling plate 71 is attached to the mounting member such that the center η thereof is offset by a predetermined distance κ in a direction orthogonal to a perpendicular γ connecting the first axis α and the second axis β. 26 is rotatably supported.

The driven coupling plate 73
Are concentrically fixed to the phase conversion shaft 55. The intermediate coupling plate 72 has three links 74 on one side.
And the other side is connected to the driven coupling plate 73 via three links 75. The center ω of the driven coupling plate 73 is located on the second axis β.

The predetermined distance κ corresponds to at least the unstable region of the Schmidt cup link 66, that is, the minimum specified value δ of the approach distance between the center η of the drive coupling plate 71 and the center ω of the driven cup link plate 73. It is set to the size or more. Then, when the half stroke of the crankshaft 34 to be processed changes due to the change of the work to be processed, the second axis β of the phase conversion shaft 55 is shifted with respect to the first axis α of the phase indexing shaft 65. The chuck bodies 26 and 27 are moved in the radial direction in the approaching and separating directions to adjust the distance between the first axis α and the second axis β. At this time, as shown in FIGS.
The corresponding positional relationship of each of the plates 71, 72, 73 changes. Note that FIG. 5 is schematically illustrated for easy understanding.

The control device 76 constituting the control means includes the phase indexing motor 67 and the two spindle drive motors 51 and 52.
Two modes for controlling the operation of are executed. That is, during the machining operation, the first mode for machining is executed by the operation of the control device 76, and the phase index motor 67
And the two spindle drive motors 51 and 52 are synchronously controlled at the same speed, and the phase conversion shaft 55 is integrally rotated with the spindles 23 and 24 in the same direction via the phase indexing shaft 65 and the Schmitt coupling 66. It has become so. Further, at the time of phase indexing of the pins 40 to 42 of the crankshaft 34, a second
The mode is executed. And, both spindle drive motors 51,
In a stopped state or a rotating state of 52, the phase indexing motor 67 is synchronously controlled with a relative speed difference between the two spindle drive motors 51 and 52. This allows
The phase conversion shaft 55 is rotated relative to the main shafts 23 and 24 via the phase indexing shaft 65 and the Schmitt coupling 66 for phase indexing.

As shown in FIGS. 1 and 7, the detection shaft 81 is rotatably supported between the headstocks 21 and 22, and both ends of the detection shaft 81 are driven by gears 82 and 83, respectively.
It is operatively connected to 1,52 motor shafts. The detection axis 81 is arranged at a position different from the first axis α and the second axis β and on an axis parallel to the axes α and β. The detection shaft 81 is divided into two parts 86 and 87 near one headstock 21, and a clutch 88 is interposed in the divided part.

As shown in FIGS. 7 and 8, the clutch 88 has a pair of clutch plates 95 and 96 which are arranged so as to face divided portions of the detection shaft 81. The first clutch plate 95 is fitted and supported on a clutch plate support 97 fixed to one part 86 of the detection shaft 81 so as to be movable in the axial direction. On the other hand, the second clutch plate 96 is fitted and fixed to the other portion 87 of the detection shaft 81.

A plurality of receiving holes 90 for receiving and holding the balls 89 are formed in the first clutch plate 95.
The clutch plate 96 has a plurality of engagement recesses 98 in which the balls 89 are slidably engaged. Further, a detection flange 91 is integrally formed on the outer peripheral edge of the first clutch plate 95 so as to protrude.

The plurality of coil springs 99 are interposed between the ring member 92 fixed to the clutch plate support 97 and the first clutch plate 95, and move the first clutch plate 95 toward the second clutch plate 96. To move. Normally, as shown in FIG. 9, the urging force of the coil spring 99 causes the ball 89 in the accommodation hole 90 of the first clutch plate 95 to move.
Are engaged with the concave portion 98a of the second clutch plate 96, and the two clutch plates 95, 96 are held in a connected state.

The detector 93 as a detecting means comprising a proximity switch is provided on the detecting flange 9 of the first clutch plate 95.
1 is attached to one headstock 21 via a bracket 94 so as to face the headstock 1. In a state where the clutch plates 95 and 96 are connected to each other via the ball 89 by the urging force of the coil spring 99, the both sides 8 of the detection shaft 81 are normally rotated by the synchronous rotation of the two spindle drive motors 51 and 52.
6, 87 are integrally rotated.

On the other hand, when a synchronization deviation exceeding a predetermined amount occurs between the motor shafts of the two spindle drive motors 51 and 52, a torsional force is generated at the divided portion of the detection shaft 81. As a result, as shown by a two-dot chain line in FIG. 9, each ball 89 separates from the engagement recess 98 against the urging force of the coil spring 99 and rides on the end face of the second clutch plate 96, and The connections 95 and 96 are opened, causing slippage.

The ball 89 moves from the engagement recess 98 to the second
When riding on the end face of the clutch plate 96, the coil spring 99
As a result, the first clutch plate 95 is moved leftward from the state shown in FIG. 8 to the state shown in FIG. As a result, the detection flange 91 approaches the detector 93,
The detector 93 outputs a detection signal to the control device 76. Then, the control device 76 stops the rotation of the two spindle drive motors 51 and 52 based on the detection signal from the detector 93.

Next, the operation of the phase indexing device configured as described above will be described. Now, in this phase indexing device, when performing the phase indexing of the crankpins 40 to 42, the second mode is executed by the operation of the control device 76. At the time of execution of the second mode, in a state where both spindle drive motors 51 and 52 are stopped, both gripping portions 32 and 33 are brought into a semi-clamped state by moving means (not shown), and an index plate 56 is engaged. In a state where the engaging body 61 is detached from the groove 59, the phase indexing shaft 65 is rotated by a predetermined angle by the phase indexing motor 67. That is,
A relative speed difference occurs between the main shafts 23, 24 and the phase indexing shaft 65.

Thus, the phase indexing shaft 65, the phase conversion shaft 55, and the indexing plate 56 are indexed and rotated with respect to the chuck bodies 26 and 27. The crankshaft 34 is indexed and rotated about the second axis β integrally with the indexing rotation of the indexing plate 56, and one of the crankpins 40 to 42 having a different phase on the crankshaft 34 is rotated by the main shaft. 23 and 24 are indexed and arranged at processing positions on the same axis as the first axis α.

When the indexing is completed, the engaging body 61 of the cylinder 60 engages with the engaging groove 59 of the indexing plate 56, and the indexing plate 56 is held at a predetermined indexing angle. Next, the journals 35, 36 at both ends of the crankshaft 34 are clamped by the grippers 32, 33, and are set to a required indexing position.

On the other hand, during the machining operation, the control device 76 executes the first mode. During the execution of the first mode, the phase indexing motor 67 is driven by the two spindle drive motors 5.
The synchronous rotation is controlled in the same direction at the same speed as that of the main shafts 23 and 24 and the chuck body 2 via the phase indexing shaft 65 and the Schmidt coupling 66.
6 and 27 are integrally rotated. Thereby, the crankshaft 34 is moved to the first axis α concentric with the main shafts 23 and 24.
The crank pin 4 is rotated about any one of the crank pins 40 to 42 located above and
The peripheral surfaces 0 to 42 are processed by the grinding wheel 20.

During the processing of the crank pins 40 to 42, the clutch 88 on the detection shaft 81 is normally connected via the ball 89 by the urging force of the coil spring 58. For this reason, the motors 51 and 52 for driving both spindles are provided.
, The spindles 23 and 24 are synchronously rotated,
When a normal machining operation is performed, both side portions 86 and 87 of the detection shaft 81 are integrally rotated via the clutch 88.

During the machining operation, if a synchronous shift of the synchronous rotation of the motor shaft occurs due to modulation of one of the control systems of the spindle drive motors 51 and 52, a torsional force acts on the clutch 88 of the detection shaft 81. . When the synchronization deviation between the motor shafts exceeds a predetermined amount, the clutch 8 of the detection shaft 81
When a torsional force greater than a predetermined value acts on the motor 8, a speed difference is generated between the two side portions 51 a and 51 b of the detection shaft 81, and relative slippage occurs between the clutch plates 95 and 96.

Then, due to the slippage of the clutch plates 95 and 96, the ball 89 rides out of the concave portion 98 of the second clutch plate 96, thereby causing the first clutch plate 95 to move as shown in FIG.
Then, the detection flange 91 is moved to the left from the state shown in FIG. For this reason, the abnormal state of the motor shaft synchronization deviation is detected by the detector 93, and the rotation of the spindle drive motors 51 and 52 is immediately stopped under the control of the control device 76. Therefore, the spindle 2
The crankshaft 34 does not continue to rotate while the synchronous rotation shift occurs in the gears 3 and 24, and the machining operation is not continued.

When the crankshaft 34 is changed to one having a different half-stroke, the chuck bodies 26 and 27 are moved and adjusted via an adjusting screw by a nut runner or the like (not shown) to adjust the axis α. , Distance between β and ε
Change the settings. Then, with this change, the Schmitt coupling 66 expands and contracts. That is, FIG.
As shown in (a), (b) and (c), in response to the change of the distance ε between the axes α and β, the driven coupling plate 7
3 is moved in a direction of expansion and contraction by a distance ε on a perpendicular γ. Therefore, it is possible to sufficiently follow a relatively large crankshaft 34 having a half stroke and a relatively small crankshaft 34 having a half stroke, and to cope with a wide range of stroke change. .

That is, in this embodiment, FIG.
As shown in the figure, the drive coupling plate 71 is set at a minimum specified value that is at least an unstable region of the Schmidt coupling 66 so that its center η is at least one side in a direction orthogonal to the perpendicular γ in the direction of expansion and contraction of the Schmitt coupling 66. The stroke of δ is offset from the beginning by a predetermined distance κ and offset. The gears 33 and 34 directly connect the phase indexing shaft 65 and the drive coupling plate 71 to each other.

Thus, when the second axis β approaches the first axis α, the center η of the driven coupling plate 73 moves on the perpendicular γ. For this reason, as shown by a two-dot chain line in FIG. 5, the driven coupling plate 73 passes by the side of the drive coupling plate 71, and can move further in the same direction even after passing therethrough. At this time, since the driven coupling plate 73 does not approach the drive coupling plate 71 beyond the distance between the centers thereof, the expansion and contraction operation of the Schmitt coupling 27 is performed without difficulty. Therefore, regardless of the minimum stroke δ of the Schmidt coupling 66, the half-stroke of the crankshaft 34 is not affected by the Schmitt coupling 66 regardless of the minimum value.
Is allowed.

In this embodiment, as shown in FIG. 5, the center η of the drive coupling plate 71 is offset from the perpendicular γ by a predetermined distance κ in a direction perpendicular to the perpendicular γ, and the phase indexing shaft 65 Perpendicular from the position of
It is arranged at a position offset a predetermined distance λ upward in the direction. Thereby, as compared with the conventional configuration shown in FIG.
The restriction on the contraction direction of the Schmitt coupling 66 is eliminated, and the length can be further increased in the extension direction by the offset of the distance λ. Therefore, the same device can easily handle a half stroke of the crankshaft with various types of crankshafts 34, from those with a large stroke εmax which could not be handled conventionally to those with a small stroke ε less than the minimum specified value δ. become.

The effects exerted by the above embodiment will be described below. (1) In this phase indexing device, the relative rotation of the phase indexing motor 67 and the two spindle drive motors 51 and 52 during machining operation and phase indexing is performed under synchronous rotation control. , 24 and the phase indexing shaft 65 do not require a complicated planetary gear mechanism. Therefore, the structure of the apparatus can be simplified, the whole apparatus can be reduced in size, and the manufacturing cost can be reduced. Further, since a planetary gear mechanism is not required, not only noise caused by gear rattle and the like can be eliminated, but also replacement due to gear wear and maintenance such as lubrication are not required.

(2) Since the indexing plate 56 is provided on the phase conversion shaft 55, the positioning and holding of the phase conversion shaft 55 at a predetermined indexing angle are directly performed by mechanical engagement. It is possible to improve the positioning and position holding accuracy.

(3) Phase indexing axis 65 and phase conversion axis 5
5 is a Schmidt coupling 66
Therefore, a large amount of expansion and contraction between the two shafts 65 and 55 can be secured, and it is possible to easily cope with a large change of the crankshaft 34 by a half stroke.

(4) In particular, in the Schmitt coupling 66 of this embodiment, FIGS.
As shown in (c), in response to the change in the distance ε between the axes α and β, the center ω of the driven coupling plate 73 is moved on the perpendicular γ in the direction of expansion and contraction of the distance ε. I have. Therefore, as described above, even for a relatively large half-stroke crankshaft 34 (FIG. 4).
(Case (a)), a relatively small half-stroke,
For example, even when the Schmitt coupling 66 slightly exceeds the minimum specified value δ (in the case of FIG. 4C), it can sufficiently follow up, and can easily cope with a wide range of stroke change.

(5) Since the phase indexing shaft 65 is inserted into the hollow main shaft 23, the size of those shafts can be reduced, and the size of the entire apparatus can be reduced. (6) A detector 93 is provided as detecting means for detecting a rotational synchronization deviation between the motor shafts of the two spindle drive motors 51 and 52. Therefore, when an abnormality occurs in the synchronous rotation between the two motor shafts, the abnormality can be detected and the rotation of the two spindle drive motors 51 and 52 can be immediately stopped. Therefore, no twist is applied to the crankshaft 34 held between the chuck bodies 26, 27 at the tips of the main spindles 23, 24, and the machining operation is continued with the torsional force acting on the crankshaft 34. It is possible to prevent the possibility that the processing accuracy of the work is reduced beforehand.

(7) Since the detection shaft 81 extends in the same direction as the main shafts 23, 24, etc., the overall configuration can be reduced in size. (8) When the main spindles 23 and 24 are out of synchronization, the clutch 88 is caused to slip, causing the main spindles 23 and 24 to slip.
Is stopped. Therefore, the power transmission function is not provided to the detection shaft 81, and a thin and lightweight detection shaft 81 can be employed, and the detection shaft 81 can be rotated with a small torque, thereby suppressing energy loss.

(9) In addition, when the main shafts 23 and 24 are out of synchronization, the clutch 88 slips.
Even if an excessive torque difference occurs between both side portions 86 and 87 of the first shaft 1, damage to the detection shaft 81 can be prevented.

The present invention can be embodied with the following modifications. (1) A pair of phase indexing mechanisms such as a phase indexing shaft 65 and a phase indexing motor 67 are provided for each of the main spindles 23 and 24. This configuration is suitable for phase determination of a crankshaft having a large overall length.

(2) The connection between the drive coupling plate 71 and the phase indexing shaft 65 is performed by using a toothed belt instead of the gear connection. With this configuration, the displacement distance κ can be increased, and the design flexibility is improved.

(3) As shown in FIG. 6, instead of the configuration of FIG. 5, a configuration in which a predetermined distance λ offset in the perpendicular γ direction is omitted. (4) Both spindle drive motors 51 and 52 are built-in motors.

(5) In this case, for both main shafts 23 and 24, for example, both detection shafts 81 are provided between the shafts of a timing pulley connected to a belt. (6) The indexing plate 56 serves as a positioning portion and a holding member.
Use a toothed coupling between the chuck body 26 and the chuck body 27.

Even with such a configuration, the effects as in the above-described embodiment can be enjoyed. (7) Under the first mode, the phase index motor 67
Is not driven, the engagement groove 59 of the index plate 56 and the engagement body 61 of the chuck bodies 26 and 27 are connected, and the phase conversion shaft 55 is integrated with the chuck bodies 26 and 27 with the rotation of the main shafts 23 and 24. To rotate.

(8) In the second mode, when the spindle drive motors 51 and 52 rotate, the phase indexing motor 67 is rotated synchronously at a different rotation speed from the rotation of the spindle drive motors 51 and 52 so that the phase indexing shaft 65 is rotated. 24 is rotated with a relative speed difference to perform phase indexing. In this case, the control device 76 may be configured to change the rotation speed of only the spindle drive motors 51 and 52, may be configured to change the rotation speed of only the phase index motor 67, or Drive motors 51 and 52
The object can also be achieved by changing the rotation speed of both the phase index motor 67 and the phase index motor 67. Then, in this manner, the motors 51, 52, 67
Can be determined without stopping the operation.
For this reason, processing efficiency can be improved.

[0084]

The present invention is configured as described above, and has the following effects. According to the first aspect of the present invention, a complicated planetary gear mechanism is not required, the structure of the apparatus can be simplified, and the entire apparatus can be reduced in size.
Manufacturing costs can be reduced, noise can be suppressed, and maintenance is facilitated. In addition, phase indexing can be performed even during rotation of the main shaft, and machining efficiency is improved. Also, the half stroke S1 of the crankshaft is
Easy to handle, from relatively large to small
Not only can contribute to the miniaturization of equipment
You.

According to the second aspect of the present invention, since the phase indexing shaft is located within the main shaft, the size can be reduced. According to the invention described in claims 3 and 4, the positioning of the phase conversion shaft can be directly performed by mechanical engagement, whereby the crank pin is accurately positioned at a required indexing position, It can contribute to high precision processing.

[0086]

According to the fifth aspect of the invention, the distance between the chuck center of the chuck body and the axis of the main shaft can be adjusted, and it is possible to easily cope with a change in the half stroke of the crankshaft.

According to the sixth aspect of the invention, when an abnormality occurs in the synchronous rotation of the motor shafts due to the modulation of the control system of the two spindle drive motors, the rotation of the two spindle drive motors is immediately stopped. be able to.

According to the seventh aspect of the present invention, since the detection axis extends in the same direction as the main axis and the like, the configuration can be reduced in size. According to the eighth aspect of the invention, when an abnormality occurs in the synchronous rotation of the pair of main shafts, the clutch slips and the connection of the divided portions of the detection shaft is released. Therefore, damage to the detection shaft can be prevented.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a crankpin grinding machine embodying the present invention.

FIG. 2 is an explanatory diagram for explaining phase determination of a crankpin.

FIG. 3 is a partially enlarged cross-sectional view showing a positioning configuration of a phase indexing shaft.

FIG. 4 is an explanatory diagram for explaining the operation of a Schmitt coupling.

FIG. 5 is an explanatory diagram for explaining the operation of the Schmidt coupling.

FIG. 6 is an explanatory view showing another embodiment of the Schmidt coupling.

FIG. 7 is an enlarged front view showing a detection mechanism.

FIG. 8 is a partially enlarged longitudinal sectional view showing the clutch mechanism of FIG. 7;

FIG. 9 is a partially enlarged transverse sectional view showing the clutch mechanism of FIG. 7;

FIG. 10 is an enlarged sectional view showing a part of FIG. 9;

FIG. 11 is a perspective view showing a conventional Schmidt coupling.

FIG. 12 is an explanatory diagram for explaining the operation of a conventional Schmitt coupling.

[Explanation of symbols]

21, 22 ... headstock, 23, 24 ... spindle, 26, 27 ...
Chuck body, 32, 33 ... gripping part as chuck part, 34 ... crankshaft, 35, 36 ... journal, 40, 41, 42 ... crankpin, 51, 52 ... spindle drive motor, 55 ... phase conversion shaft, 56 ... Indexing plate, 5
9 ... engaging groove as positioning part, 61 ... engaging body as holding member, 65 ... phase indexing shaft, 66 ... Schmitt coupling, 67 ... phase indexing motor, 71 ... drive coupling plate, 72 ... intermediate cup Ring plate, 7
3: driven coupling plate, 76: control device as control means, 81: detection shaft, 86, 87 ... part, 88 ...
Clutch, 89: ball, 93: detector as detecting means, α: first axis, β: second axis.

──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Yukio Okaji 100, Fukuno-cho, Higashi-Tonami-gun, Toyama Pref. 2-292148 (JP, A) JP-A-3-19757 (JP, A) JP-B-4-51301 (JP, B2) (58) Fields investigated (Int. Cl. ⁷ , DB name) B24B 5/42

Claims (8)

(57) [Claims] 1. A device according to claim 1, further comprising:
A pair of spindles respectively rotated by a pair of spindle drive motors controlled synchronously with each other; a chuck body provided at the tip of each spindle; and a chuck body provided on each chuck body and separated from the first axis. A chuck portion for gripping both end journals of the crankshaft on a second axis parallel to the first axis; and a rotatably provided on the second axis of at least one of the chuck bodies, engaging with an end face of the crankshaft. A crankshaft is rotated to determine the phase of the crankpin having a different phase angle on the first axis; and a phase conversion shaft connected to the phase conversion shaft and arranged concentrically with the main shaft;
Bei a phase indexing shaft being rotated by a phase indexing motor
A first mode in which the phase conversion shaft is synchronously rotated at the same speed as the pair of main shafts, and a second mode in which the phase conversion shaft is synchronously rotated with a relative speed difference with respect to the pair of main shafts. as the modes are executed, a control means for controlling the phase indexing motor and both the spindle drive motor is provided, between the phase conversion shaft and the phase indexing shaft, the axes
An expansion joint that can change the distance is interposed, and the expansion joint
The drive side coupling plate and the driven side coupling
Plate and intermediate coupling located between them
Plate and the plate interposed between each coupling plate.
And a Schmidt coupling that includes
Gear coupling between the coupling plate and the phase indexing shaft
To determine the center position of the drive coupling plate
From the center of the shaft to the direction perpendicular to the coupling expansion and contraction direction
A crank pin phase indexing device arranged to be deviated by a predetermined amount . 2. At least one main shaft has a hollow shape,
2. The crankpin phase indexing device according to claim 1, wherein the phase indexing shaft is disposed within the main shaft. 3. The phase conversion shaft is provided with a plurality of positioning portions corresponding to the indexing angle, and the chuck main body is releasably engaged with the positioning portion of the phase conversion shaft to index the phase conversion shaft to a predetermined index. The crank pin phase indexing device according to claim 1 or 2, further comprising a holding member for holding the position at an angle. 4. The crank pin phase according to claim 3, wherein in the first mode, the phase conversion shaft is rotated integrally with the chuck body together with the rotation of the main shaft via the holding member when the phase indexing motor is stopped. Indexing device. 5. The chuck body has a first axis and a second axis.
Adjustable with respect to the main axis in the direction in which the distance between
2. The crank pin phase split according to claim 1, wherein
Out device. 6. Detection between motor shafts of both spindle drive motors
The shaft is connected and the detection shaft is rotated between both motor shafts.
When a synchronizing error occurs, it is detected and the
A detecting means for stopping the data.
The crank pin phase indexing device according to any one of the above. 7. The detection axis includes a spindle axis and a chuck body.
7 is arranged on another axis parallel to the axis of
The crank pin phase indexing device as described in the above. 8. The detection axis is divided into two parts.
However, there was a synchronization error between the two spindles between the divided parts.
Sometimes a slipping clutch is interposed, and the detecting means
Detects slippage of latch and stops motor
The crank pin phase indexing device according to claim 6 or 7.
Place.