JPS643630Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Field of Industrial Application) The present invention relates to an improvement of a device for loading and unloading an annular workpiece in a grinding machine.

(Prior Art) Japanese Utility Model Publication No. 17268/1983 discloses a grinding machine in which a single loading arm is used to carry an annular workpiece into and out of its processing position. In the device described in this publication,
It looks like this: That is, a loading arm having an annular fitting portion for the workpiece is attached to a loading shaft that is freely displaceable in the axial direction, and the workpiece is moved between a standby position and a processing position according to forward and reverse rotation of the loading shaft. A clutch shaft is arranged in series with the loading shaft, and a cam is provided on one of the loading shaft and the clutch shaft, and a cam is provided on the other. A cam follower is provided that comes into contact with the cam from the axial direction, and the cam displaces the loading shaft in a direction away from the clutch shaft while the loading arm is returning from the processing position to the standby position to move the workpiece. It is designed to emit

In this way, by the action of the cam, the loading arm that holds (fits) the workpiece at the standby position is swung and conveyed to the processing position, and the workpiece is processed at that processing position. On the way back from the machine position to the standby position, the machined workpiece is released, and the workpiece is held at the standby position again. Of course, this ejected workpiece will be dropped onto the chute and recovered at a predetermined position.

(Problems to be Solved by the Invention) By the way, it is conceivable to apply such a conveying device to workpieces having different thicknesses (axial lengths). In this case, if a cam that is optimally set for a thick workpiece is used as is and applied to a small workpiece, the workpiece will be ejected from the loading arm before the specified position, and after machining. Not only is it impossible to retrieve the workpiece to a predetermined position, but the released workpiece is likely to fall onto the bed of the grinder, causing the grinder to stop.

To explain this point in more detail, the shape of the cam (the height of the cam surface) has an inclined surface so that the loading arm (fitting part) gradually comes out of the workpiece on the way back from the processing position to the standby position. The holding action (fitting) of the loading arm on the workpiece is completely released at the release position between the processing position and the standby position. In this way, in order to hold (fit) and release (unfit) a thick workpiece, a large axial displacement of the loading shaft is required. The height difference due to the slope is relatively large.

Therefore, if the above cam is used as is for a workpiece with a small internal thickness, the amount of axial displacement of the loading shaft used for ejecting the workpiece will be smaller than that of a workpiece with a large thickness, so that the workpiece will reach the predetermined ejection position. Relatively small displacements of the previous loading axis resulted in a loss of the holding effect of the loading arm on the workpiece.

SUMMARY OF THE PRESENT EMBODIMENT An object of the present invention is to provide an annular workpiece loading and unloading device for a grinding machine which is capable of reliably discharging workpieces of different thicknesses at predetermined discharge positions using the same cam.

(Means and actions for solving the problems) In order to achieve the above-mentioned object, the present invention has the following configuration. That is, a loading arm having an annular fitting portion for the workpiece is attached to a loading shaft that is freely displaceable in the axial direction, and the workpiece is moved between a standby position and a processing position according to forward and reverse rotation of the loading shaft. A clutch shaft, which can freely swing between the two positions and is only allowed to rotate in a direction corresponding to the swinging of the loading arm from the processing position to the standby position by a one-way clutch, is connected to the loading shaft. A cam is provided on one of the loading shaft and the clutch shaft, and a cam follower is provided on the other that contacts the cam from the axial direction, and a spring causes the cam and the cam follower to come into contact with each other. The loading shaft is urged rearward so as to be in contact with each other,
In an annular workpiece unloading device for a grinding machine, the cam displaces the loading shaft in a direction away from the clutch shaft and releases the workpiece while the loading arm is returning from the processing position to the standby position, An operating rod is provided that passes through the clutch shaft in the axial direction and is screwed onto the clutch shaft so that its front end can come into contact with the loading shaft from the axial direction. By changing the screwing position of the clutch shaft, the stroke end position of the loading shaft in the approaching direction with respect to the clutch shaft is adjusted.

With this configuration, even if the cam shape is set to the largest thickness among multiple types of workpieces with different thicknesses, it can be used for small-thickness workpieces. By changing the screwing position of the operating rod with respect to the clutch shaft and displacing the operating rod further to the front side, the stroke end position of the loading shaft in the approach direction with respect to the clutch shaft can be adjusted according to the thickness of the workpiece. By adjusting the position more toward the front (in the direction in which the cam and the cam follower are separated), it is possible to eject the workpiece at a predetermined ejection position even for a workpiece having a small thickness.

In other words, with the above adjustment, the timing at which the loading arm starts displacing in the workpiece ejecting direction is delayed compared to when the loading arm starts displacing the workpiece in the workpiece discharge direction. The loading arm will hold it securely until it reaches the release position. At the same time, the amount of displacement of the loading arm required for this ejection is also small, corresponding to the workpiece having a small thickness.

(Embodiments) Examples of the present invention will be described below with reference to the attached drawings.

In FIG. 1, reference numeral 1 denotes a base of a grinding machine, and a loading shaft 3 is rotatably mounted on a first bearing portion 2 integrally provided on the base 1 in the axial direction (horizontal direction in FIG. 1). It is held so that it can be freely displaced. The base end of a loading arm 4 is integrated with the front end (right end in FIG. 1) of the loading shaft 3 by a bolt 5, and the loading shaft 3 is connected to the rear end of the tip of the loading arm 4. A pin 6 serving as a workpiece fitting portion extending parallel to the workpiece is detachably attached using a bolt 7. Of course, this pin 6
The outer diameter of the annular workpiece W is smaller than the inner diameter of the annular work W.

A Geneva cam 8 is integrated into the rear end of the loading shaft 3, and a groove 8a extending in the radial direction of the loading shaft 3 is formed in the Geneva cam as shown in FIG. This Geneva cam 8 (groove 8a) is connected to a drive unit 21 that rotates the loading shaft 3 forward and backward to swing the loading arm 4 back and forth.
This is the part that receives the driving force from the To explain this drive unit 21, the base 1 has a second
The bearing part 22 is integrally constructed, and a pinion shaft 23 extending parallel to the loading shaft 3 is rotatably held in the second bearing part 22 . A rack 24 is attached to the pinion 23a of this pinion shaft 23.
The pinion shaft 23 is rotated forward and backward by reciprocating the rack 24 by a cylinder device (not shown). An arm 25 is integrated into the front end of the pinion shaft 23 as shown in FIG.
It is slidably fitted inside a. As a result, in response to the reciprocating movement of the rack 24, the Geneva cam 8, that is, the loading shaft 3, is rotated in the forward and reverse directions via the pinion shaft 23, arm 25, and roller 26.

The base 1 further includes a base plate located on the same axis as the first bearing part 2 on the rear side thereof.
The third bearing portion 31 is integrally constructed. A clutch shaft 32 is held in this third bearing portion 31 so as to be rotatable but not displaceable in the axial direction. This clutch shaft 32 is equipped with a one-way clutch 33 and can only rotate in the direction of arrow A in FIG. A cam 34 is integrated into the front end of the clutch shaft 32, and a cam follower 9 made of a roller is attached to the boss portion of the Geneva cam 8, facing the cam 34.
Then, in order to bring the cam follower 9 into contact with this cam 34 without rattling, the loading shaft 3
is urged rearward by a spring 10.

The clutch shaft 32 is provided with a position adjustment mechanism. This position adjustment mechanism
The operating rod 35 is provided with an operating rod 35 which passes through the operating member 2 in the axial direction and is screwed thereto.
is opposed to the rear end surface of the loading shaft 3 so as to be able to come into contact with it. Further, the rear end portion of the operating rod 35 has an extension portion 35b extending outside the clutch shaft 32.
A threaded portion 35c formed on the extension portion 35b is screwed into a threaded portion 32d at the rear end of the clutch shaft 32, and a lock nut 36 is screwed onto the threaded portion 35c. Relative rotation of the operating rod 36 with respect to the clutch shaft 32 is restricted. In this way, as the operating rod 35 is moved forward, the loading shaft 3 is urged backward by the spring 10.
The rear stroke end position of is displaced forward.

As shown in FIG. 3, the loading arm 4 moves between a standby position S1 and a processing position S2 as well as a discharge position S3 between the two positions S1 and S2. In the embodiment, the swing angle of the loading arm 4 between the standby position S1 and the processing position S2 is set to 90 degrees. A loading plate 41 is provided on the base 1 to face the rear end surface of the loading arm 4. An insute 42 and a side plate 43 are attached to the plate 41 for transporting the work W to the standby position S1, and a stopper 44 is rotatably attached to the downstream end of both 42 and 43 by a pin 45. It is being This stopper 44 is always in the rotating position shown in FIG. 3 in which it is in contact with a bolt 47 as a stopper by a leaf spring 46, so that the workpiece W is held stationary in a predetermined posture at the standby position S1. There is. Also,
The loading plate 41 has an inclined outshoot 4 for discharging the workpiece W from the grinding machine.
8 and a presser plate 49 are attached, and the upper end of the outshoot 48 is located directly below the discharge position S2.

In FIG. 3, numeral 50 is a pair of shoes, and 51 is a grinding wheel. The shoe 50 supports the workpiece W at the processing position S2, and the grinding wheel 51 is supported by the shoe 5 and is at the processing position. The workpiece W in S2 is to be ground.

Next, the operation of the above configuration will be explained. First of all,
The workpiece W at the standby position S1 is held by the loading arm 4 by being fitted with the pin 6 as a fitting part of the loading arm 4, as in the conventional art. Thereafter, due to the swinging of the loading arm 4, the workpiece W is carried over the stopper 44 and sliding on the loading plate 41 to the processing position S2. Then, the workpiece W is at this processing position S2
Then, it is ground by a grinding wheel while being supported by a shoe 50. Thereafter, the loading arm 4 swings in the opposite direction, releases the work W at an intermediate release position S3, returns to the standby position S1 again, and repeats the same process as described above. Of course,
The workpiece W is discharged at the discharge position S3 by the loading arm 4, that is, the loading shaft 3, moving forward (rightward movement in FIG. 1), and the workpiece W discharged from the loading arm 4 is
It will fall onto the outshoot 48 due to its own weight.

The above-mentioned swinging and back-and-forth movement of the loading arm 4 is performed by the above-mentioned cam 34.
In the figure, a development of the cam surface 34a of the cam 34 is shown together with the movement path α of the cam follower 9 in correspondence with one cycle of the movement of the loading arm 4.

In addition, in FIG. 4, for ease of understanding, the cam surface including the area from the standby position S1 to the machining position S2 is shown, but this portion originally does not exist due to the one-way rotation setting by the one-way clutch 33. (This also applies to FIG. 5, which will be described later). As is clear from FIG. 4, the lift amount L ₁ of the cam follower 9 by the cam surface 34a
In other words, the loading arm 4 for the work W
The amount of displacement when the fitting part is inserted and removed is the cam surface 34
The size is determined according to the difference in level of the inclined surface 34b that connects the bottom and top surfaces of a. That is,
The one shown in FIG. 4 utilizes the greatest height difference between the highest and lowest surfaces of the cam surface 34a.
This corresponds to a workpiece W having a large thickness.

If the thickness of the workpiece W is smaller than that shown in FIG. 1, as shown in FIG. 6, loosen the lock nut 36 of the position adjustment mechanism and tighten the operating rod 3.
5 is rotated and moved forward, the lock nut 36 is tightened again, and the rear stroke end position of the loading shaft 3 is moved forward than in the case of FIG.
The diagram corresponding to Figure 4 in this case is Figure 5,
The lift amount of the cam follower 9 at this time is _L2 , which is smaller than _L1 . As is clear from FIG. 5, the longitudinal motion relationship at each position S1, S2, and S3 of the loading arm 4 is the first.
Although it is the same as the one in the figure, the amount of displacement of the forward movement of the loading arm 4, which is the direction in which the workpiece W is discharged, is small, and this displacement starts later than in the case of FIG. Ru. As a result, even if the workpiece W is small in thickness, the holding action by the loading arm 4 will not be released inadvertently until it reaches the discharge position S3 from the processing position S2, and the workpiece will be placed at the predetermined discharge position. Work W only in S3
is released from the loading arm 4. Of course,
Based on the difference in the thickness and inner diameter of the work W, the protruding position and outer diameter of the pin 6 from the loading arm 4, which serves as the fitting part, are changed as appropriate, and when the outer diameter of the work W is different, the side plate 43 , the mounting position of the presser plate 49 is changed.

Note that while the cam 34 is provided on the loading shaft 3, the cam follower 9 may be provided on the clutch shaft 32.

(Effects of the invention) As is clear from the above, the invention has the following effects:
The cam can be used in common for workpieces of different thicknesses without having to be replaced, and the versatility of the loading/unloading device for annular workpieces in this type of grinding machine can be increased.

Further, since it is only necessary to screw the operating rod into the existing clutch shaft, the structure is simple and can be implemented at low cost.

Furthermore, by adjusting the screwing position of the operating rod with respect to the clutch shaft, the initial position of the loading shaft, that is, the stroke end position in the approach direction with respect to the clutch shaft, can be adjusted while compensating for wear on the contact portion between the operating rod and the loading shaft. It can always be whatever you want.

[Brief explanation of the drawing]

FIG. 1 is a side sectional view showing an embodiment of the present invention.
FIG. 2 is a front view showing a mechanism for rotating the loading shaft in forward and reverse directions. FIG. 3 is a diagram showing the rocking positional relationship of the loading arm. Figures 4 and 5 are developed views of the cam surface. FIG. 6 is a side sectional view of a main part when applied to a workpiece having a different thickness from the workpiece shown in FIG. 1. 3: Loading shaft, 4: Loading arm, 6: Pin (fitting part), 8: Geneva cam, 8
a: groove, 9: cam follower, 23: pinion shaft,
23a: pinion, 24: rack, 25: arm, 26: roller, 32: clutch shaft, 32d:
Threaded portion, 33: One-way clutch, 34: Cam, 34a: Cam surface, 35: Operation rod, 35
c: threaded part, 36: lock nut, 42: insitu, 48: outrat, 51: grinding wheel,
S1: Standby position, S2: Processing position, S3: Release position, α, β: Cam follower movement trajectory, L ₁ ,
L ₂ : Lift amount, W: Workpiece.

Claims (1)

[Claims for Utility Model Registration] A loading arm having an annular fitting portion for a workpiece is attached to a loading shaft that is freely displaceable in the axial direction, and the workpiece is placed on standby according to the forward and reverse rotation of the loading shaft. a clutch shaft that can freely swing between the processing position and the processing position, and is only allowed to rotate in a direction corresponding to the swinging of the loading arm from the processing position to the standby position by a one-way clutch; is arranged in series with the loading shaft, a cam is provided on one of the loading shaft and the clutch shaft, and a cam follower is provided on the other that contacts the cam from the axial direction, and The loading shaft is urged rearward so that the cam and the cam follower come into contact with each other,
In an annular workpiece unloading device for a grinding machine, the cam displaces the loading shaft in a direction away from the clutch shaft and releases the workpiece while the loading arm is returning from the processing position to the standby position, An operating rod is provided that passes through the clutch shaft in the axial direction and is screwed onto the clutch shaft so that its front end can come into contact with the loading shaft from the axial direction. A loading/unloading device for an annular workpiece in a grinding machine, characterized in that the stroke end position of the loading shaft in the approaching direction with respect to the clutch shaft is adjusted by changing the screwing position of the loading shaft.