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Publication numberUS3380198 A
Publication typeGrant
Publication dateApr 30, 1968
Filing dateFeb 24, 1966
Priority dateMay 20, 1965
Also published asDE1577494A1
Publication numberUS 3380198 A, US 3380198A, US-A-3380198, US3380198 A, US3380198A
InventorsTakada Susumu
Original AssigneeTakada Susumu
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Parallel plane honing equipment
US 3380198 A
Abstract  available in
Images(3)
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Claims  available in
Description  (OCR text may contain errors)

5 Sheets-*Sheet 1 Filed Feb. 24. 1966 INVENTOR. WW

April 30, 968 susuMu TAKADA 3,380,198

PARALLEL PLANE HQNING EQUIPMENT Filed Feb. 24. 1966 3 Sheets-Sheet 2 MENTOR.

We. M1444,

April 1968 susuMu TAKADA 3,380,198

PARALLEL PLANE HONING EQUIPMENT Filed Feb. 24, 1966 5 Sheets-Sheet 3 INVENTOR.

United States Patent 3,380,198 PARALLEL PLANE HONING EQUIPMENT Snsunm Takada, 53-1 Shirasagi-cho, Fukuoka-sin, Japan Filed Feb. 24, 1966, Ser. No. 529,864 Claims priority, application Japan, May 20, 1965, 40/29,713 4 Claims. (CI. 5154) The present invention relates to a parallel plane honing equipment for grinding works precisely by pressing a grinding wheel to surfaces of the works eccentrically.

In accordance with the conventional plane honing machine, the grinding operation has been achieved by rotating honing wheels at a single position, while the works are rotatably moved. Accordingly, more complicated mechanical construction was necessary for treating the works which naturally causing more expenses in manufacturing the conventional equipment.

Moreover, said conventional equipment has other fatal defects as that a volume of grinding productivity is limited and in addition, said equipment was not suflicient to achieve precision operation due to such mechanical construction in which works are moved rotatingly during the grinding process.

Particularly, in the conventional lapping machine, an extra high precision machine for tracing out the standard surface which is provided in the machine was needed.

Main object of the present invention is, therefore, to avoid such defects as aforementioned and that more precision grinding at a lower cost could be realized.

At the same time, the particularly designed mechanical construction having same dimensional area to the conventional honing machine otters more volume of works.

Furthermore, the present invention also features for non-necessity of the high engineering techniques in operating machine but simply treating the eccentric movement to the grinding wheel having two surfaces with the three surfaces combination system between the works and the surface of the grinding wheel.

It will be featured again that the present mechanism employs the particular honing performance having two step torque process.

It will be now described in detail of the present disclosure with the accompanying drawings below.

Drawings show one of the examples according to the present invention.

FIGURE 1 is a transversial view of the present invention.

FIGURE 2 shows a side view of a part cut according to FIG. 1.

FIGURE 3 is a side sectional view of the essential part for rotating movement of the grinding wheels.

FIGURE 4 is a partial plane view according to FIG. 3.

FIGURE 5 is a front view of the sliding part of the grinding wheels according to FIG. 3.

FIGURE 6 is an explanatory drawing of the rotation of the aforesaid sliding part of the grinding wheels.

FIGURE 7 is a side sectional view of the power transmission device which rotates the rotating member of the grinding wheels shown in FIG. 3.

FIGURE 8 is a plane sectional view of the pressing device of the grinding wheels facing each other.

Referring now to the drawing, and in particular to FIG. 1, sliding arms 1, 1' having wheel grinders a, a move up and down through the rotation of a turn buckle 4 being conducted by guide poles 3 provided on a bed 2.

A rotating axis 5 is rotated by a motor m provided within the bed 2 and the rotating axis 5, guide poles 3 and turn buckle 4 are respectively supported the front end of a flame 6 provided in the rear part of the bed 2.

Between the sliding arms 1, 1 which are conducted by the guide poles 3, a holder 8 between the grinders a, a is removably maintained through a bracket 7.

In the holder 8, holes 9 for holding works b are provided and proper scale of holder may be used depends on the sizes and shapes of the works b.

The grinders a, a are respectively secured on surfaces of desks 10, 10' and each surface is maintained in flanges 11, 11 with a passage. The flanges 11, 11' are respectively fitted to the sliding arms 1, 1 facing in opposite and that the rotating movement of the grinders a, a of the above is constituted, however, said constitution is respectively common to both blocks. Accordingly, it will be further described for the mechanical operation of the rotating movement effected by a block of the sliding arm 1 and the wheel grinder a referring to drawings basing FIG. 3 to FIG. 6.

The flange 11 is secured in the sliding arm 1 through a cylindrical axis 13 connecting to an upper pulley 12 and thrust blocks 14. In the flange 11 and the cylindrical axis 13, a center axis 15 is inserted and a flange 16 forming in the lower end of the center axis 15 is provided within the flange 11, while on the upper end of the center axis 15, a pulley 17 is secured.

Within the center axis 15, a control axis 18 is further inserted and a disk 19 provided in the lower end of the axis 18 is fitted within the flange 16. The upper part of the control axis 18 is screwed into a disk 21 having a passage hole 20. The disk 21 is fixedly secured to the center axis 15 by tightening of a screw 22 which combined with the center axis 15 through the passage hole 20.

Accordingly, the control axis 18 simultaneously rotates within the cylindrical axis 13 with the center axis 15 through the disk 21. On the lower surface of the disk 19 provided within the flange 16, a pin 23 is projected at an eccentric-position to the control axis 18. The pin 23 is inserted into a side-long passage hole 24 of the disk 14) positioned in the lower surface of the flange 16 I and the disk 19. Accordingly, the disk 1% moves as much as an eccentric amount of the center axis 15 of the pin 23 provided by the rotation of the center axis 15 being along with a passage 25 of the flange 11.

In FIG. 6 a locus x shows a rotation of the control axis 18 inserted into the center axis 15, while another locus y shows a transfer of the pin 23 which may be controled by the control axis 18. Accordingly, the rotating movement of the grinder a illustrated an optimum eccentricity amount when the pin axis 2: is settled in the most distant place from the central point x of the cylindrical axis 13 and the center axis 15.

A device for the rotating movement of the grinder a of the sliding arm 1' is also the same to the grinder a of the sliding arm 1 in the mechanical construction, accordingly, a signal marked with a point shows symmetrically a signal without any mark.

In this connection, if a motor m is normally operated for rotating the turn buckle 4 by fitting the works b with the holder 8, both surfaces of the works b are ground by the grinders a, a being cfi'ected by the sliding arms 1, 1. And thus, the desired honing process is achieved on the both surfaces of the works b by operating the grinder a with belts 26, 27 and the grinder a with belts 26, 27'. In this case, the belts 26, 27' are hung in cross-shape and the rotating direction of the grinder a is made to be opposite to the direction of the grinder a in order to prevent the skidding of the works b in the holder 3, at the same time, to increasing grinding efiiciency.

In accordance with the present example, the sliding arms 1, 1' are, however, moved symmetrically, only the sliding arm 1 can be moved up and down by securing the sliding arm 1.

In FIG. 7, a pulley 28 is for operating the belt 26 and a cylindrical axis 29 of the pulley 28 is inserted into the rear part of the sliding arm 1 having a thrust block 30 therein. Within the cylindrical axis 29, a cylindrical axis 33 having a passage 32 in which pins 31 which are driven from the both sides of the cylindrical axis 29 is provided. Further, within the cylindrical axis 33, the rotating axis 5 penetrates therethrough and a knock pin 35 of a pulley 34 positioned on the upper surface of the pulley 28 meets a key passage 36 of the rotating axis 5 so that the pulley 34 is supported by a bracket 38 which is held in the surface of sliding arm 1 through thrust blocks 37. Accordingly, the belt 27 is rotated with the rotation of the pulley 34. In the middle part of the cylindrical axis 33, a gear 39 is fixedly secured and the pulleys 28, 28' are rotated by gearing with a pinion 40 which transmits the rotation of a motor 111 On the cylindrical axis 33, a stopper screw 41 is secured and the front end thereof combines to a passage 42 of the rotating axis 5 so that the cylindrical axis 33 maintains the constant position.

The construction mechanism mentioned in the above is common to the construction mechanism of the pulleys 28', 34' provided in the rear part of the sliding arm 1'.

In this connection, the rotation of the cylindrical axis 33 is transmitted to the pulleys 28, 28 and the movement of the rotating axis 5 is transmitted to the pulleys 34, 34' respectively even if the sliding arms 1, 1 may move up and down at the turn buckle 4.

In FIG. 8, a worm 43 is combined with a worm wheel 44 which is fixedly secured on the turn buckle 4 and said worm 43 is built together with an axis 46 having a gear 45. The front end of the axis 46 supported by a casing 47 is held by a bar 49 which presses a spring 48. At this sense, if the overload is generated on the turn buckle 4 which rotates by the transmission of a pinion 50, only the worm 43 rotates for the advancement without having rotated the worm wheel 44. A flange 51 secured on the axis 46 contacts with a switch 52 which cuts the power source at off position in case the axis 46 accidently advances. Accordingly, the motor m is for stopping the rotation of the turn buckle 4 when the grinders a, a contact with the works b with a proper friction being approached by the sliding arms 1, 1'. Further, between the motor m and the pinion 50, a clutch 53 is provided. Also,

in the front side of the equipment, a control disk 54 is provided.

In short, the aforesaid parallel plane honing equipment is particularly featured in the works maintained in the proper position and the movement of the grinder surface is rotated in a meandering movement having an eccentric amount being combined with circularity and reciprocation movements, at the same time, it is further characterized in realizing a pressure system to the grinder surface and the works.

Namely, the disk 10 which rotates with the flange 11 may tend to rotate with the central axis x of the flange 11, however, the disk 10 operates the meandering rotation movement along with the center axis x as the eccentric amount of the pin 23 provided in the flange 16 is multiplied to the rotation of the flange 11 with the rotation having diameter consisting of the length of the flanges 11, 16 of the center axis x and the axis point z.

In this connection, by setting the position of the pin 23 with proper adjustment of the disk 21 so that the surface of the works d is contacted with the two surfaces d and d of the grinder surface, the rotating grinder surface may constitute with the double movement comprising circular movement by the flange and reciprocation movement by the pin 23 and the passage 25. Accordingly, the present construction is based on the unique mechanism for assuring more precision grinding in which supplemental grinding surface d is particularly provided for amending errors to be generated from the grinding operation executed by the grinding surface d and the surface of the works d. Such a grinding method may be thus, called three surfaces contact system. At this sense, the relation between the grinder surfaces d 0' and the surface of works at will be represented by d d, and the grinder surfaces a and d are equal.

In this case, on the surface of the works, the grinder surfaces d d having a certain amount of eccentricity of sin curve always contact with the surface of the works in such a route of d d dz d Accordingly, the present honing equipment can provide an etficient honing process and precise result without having any inconveniency effected by non-uniformity of the grinder surface as appeared in the conventional honing equipment.

Now, it will be described for the press-process of the grinder surface when the turn buckle 4 is operated by the pinion 50 of the motor m as shown by an arrow mark in FIG. 8, the axis 46 having the worm 43 moves ahead with rotation (right side in the drawing) against the spring force of the spring 48, as the worm wheel 44 is in static-state receiving the load from the sliding arms 1, 1 of the turn buckle 4. However, intermediate space between the grinder surfaces may be approached if the worm wheel 44 rotates to the arrow direction which causes the axis 46 to have larger torque than the load of the worm wheel 44 because of an effect of excess shrinkage of the spring 48. Namely, the grinding operation will be sufficiently achieved by an appropriate approach of the grinder surface and the works, however, the worm wheel 44 stops rotation thereof if the approach becomes too heavy beyond over certain pressure.

In this connection, the worm 43 still maintains rotating operation by the motor m and therefore, said worm 43 further proceeds by pressing the spring 48. At this state, the operation of the motor m is suspended by the limit switch 52 controlled by the flange 51 having the axis 46. Accordingly, the rotating torque opposite direction to the above effects to the worm wheel 44 as the worm 43 is forced to move backwardly by the energy reserved in the spring 48.

As described in the aforesaid statement, in the present grinder surface press-device, a continuous honing operation to be operated each other by the motor and the spring for supplying the torque to the worm Wheel can be realized. Consequently, if the limit switch 52 controlled by the flange 51 releases the circuit being effected from the counter action of the spring 48, the motor m is operated again. Further, the worm 43 and the gear 45 are, of course, made to gear with the counter gear with the proper width.

The pressure torque of the present device will be adjusted by the manipulation of the pin 49 of the spring 48, whereby an eflicient honing result will be obtained.

What I claim is:

1. A parallel plane honing equipment, comprising a bed,

a threaded spindle rotatably mounted in said bed,

guide poles secured in said bed and disposed parallel with said threaded spindle, two sliding arms movable toward and from each other, respectively, by rotation of said threaded spindle and guided in the movements by said guide poles,

rotating members having a flange disposed in said sliding arms and having a passage,

disks including a wheel grinder slidably disposed in said passage,

eccentric means for reciprocating said disks in said passage,

means for turning said rotating members,

means for adding pressing torque to the surfaces of said Wheel grinder, and

a holder secured in said bed and adapted to support a workpiece to be ground.

2. The honing equipment, as set forth in claim 1, wherein said disks move in said passage in diametrical direction.

3. The honing equipment, as set forth in claim 1, wherein said eccentric means comprises a pin projecting eccentrically from one of said disks,

a reciprocating plate securing said wheel grinders thereto and receiving said pin, so that upon rotation of said one of said disks, said plate performs a reciprocating movement.

4. The honing equipment, as set forth in claim 1,

wherein said threaded spindle includes a worm wheel,

a worm meshing said Worm wheel,

spring means forcing said Worm backwardly, said worm tending to move ahead with said Worm wheel, thereby rotating said threaded spindle, and

said worm having a shaft,

said shaft carrying a flange moving axially with said shafts,

a limit switch engaging said last mentioned flange and operated upon axial movement of said flange, and a motor operatively connected with and turning said threaded spindle.

References Cited UNITED STATES PATENTS OTHELL M. SIMPSON, Primary Examiner.

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US1257046 *Jan 2, 1918Feb 19, 1918Edward A SuverkropLapping-machine.
US1486345 *Dec 9, 1922Mar 11, 1924William E HokeLapping machine
US1491103 *Jul 8, 1919Apr 22, 1924Pratt & Whitney CoMethod of and machine for making gauges and other articles
US2195065 *Nov 5, 1938Mar 26, 1940Chrysler CorpFinishing apparatus and method
US2291123 *Mar 24, 1937Jul 28, 1942Chrysler CorpLapping apparatus
US3000148 *Dec 28, 1959Sep 19, 1961Bovensiepen Hans FriedrichTwo-lap lapping machine
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3653160 *Apr 23, 1969Apr 4, 1972Ind Micronics IncLapping machine and method
US3782042 *Jul 3, 1972Jan 1, 1974Strasbaugh RLens grinding and polishing units
US4205489 *Dec 8, 1977Jun 3, 1980Balabanov Anatoly SApparatus for finishing workpieces on surface-lapping machines
US5287658 *Jun 11, 1993Feb 22, 1994SevaPolishing machine having combined alternating translational and rotational tool motion
Classifications
U.S. Classification451/158, 451/262
International ClassificationB24B37/04, B24B7/16
Cooperative ClassificationB24B37/08, B24B7/162
European ClassificationB24B37/08, B24B7/16B