US2437530A

US2437530A - Means for effecting reciprocatory motion

Info

Publication number: US2437530A
Application number: US578843A
Authority: US
Inventors: Penrose R Hoopes
Original assignee: SUPER SPEED PRESS CORP
Current assignee: SUPER SPEED PRESS Corp
Priority date: 1945-02-20
Filing date: 1945-02-20
Publication date: 1948-03-09
Anticipated expiration: 1965-03-09

Description

March 9, 1948. P. R. HOOPES MEANS FOR EFFECTING RECIPROGATORY Filed Feb. 20, 1945 3 Sheets-Sheet l INVENTOR:

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WI TN ESSES woo P. R. HOOPES MEANS FOR EFFECTING RECIPROCATORY Filed Feb. 20,1945

3 Sheets-Sheei 2 INVENTOR: Pen/rose Rfioo ves,

ATTORNEYS.

March 9, 1948. HOOPES 2,437,530

MEANS FOR EFFECTING RECIPROCATORY Filed Feb. 20, 1945 3 Sheets-Sheet 3 WITNESSES INVENTOR:

PenmsefiHoqpes,

Chum/z ATTORNEYS.

Patented Mar. 9, i948 MEANS FOR EFFECTING RECIPROCATORY MOTION Penrose It. Hoopes, Philadelphia, Pa, assignor to Super Speed Press Corporation, Bridgeton, N. J a corporation of Delaware Application February 20, 1945, Serial No. 578,843

5 Claims.

This invention relates to means useful in machines of various kinds for imparting motion to a member which is to be reciprocated. In connection with such means, it is the chief aim of my invention to make it possible to vary the throw of the reciprocated element between zero and the maximum for which the means is designed, with maintenance of a perfect balance in the parts in all positions of adjustment so that the machines in which my invention is incorporated can be operated at much higher speeds than heretofore with absence of vibration and with corresponding increase in productive output.

One way in which the foregoing and other objects and advantages may be readily realized in practice will appear from the following detailed description of the attached drawings, wherein Fig. 1 is a fragmentary view in sectional elevation of a punching or stampin press conveniently embodying the reciprocating means of myinvention.

Figs. 2 and 3 are detail sections on a larger scale taken as indicated by the angled arrows IIII and III--III in Fig. 1, showing the recip- 1igrcating means adjusted to impart the maximum Fig. 4 is a detail sectional view likewise on a larger scale taken as indicated by the angled arrows IV-IV in Fig. 1.

Figs. 5 and 6 are views like Fig. 4 showing the parts in different positions of adjustment.

Figs. '7, 8 and 9 are diagrammatic views, respectively corresponding to Figs. 4, 5 and 6.

With more detailed reference first more particularly to Fig. 1 of these illustrations, the press therein shown for convenience of exemplifying my invention has a frame with spaced rigid standards or columns l and H which are connected at the top by a bridging member l2. Disposed in the space between the standards or columns. I 0 and II of the frame is the vertically reciprocative member l3 of the press which has the form of a yoke with side members l and I6 and a connecting cross member I! at the top.

The adjustable means provided for reciprocating the yoke l3 in accordance with my invention includes a rotary shaft with a journal portion I 8 at one end, and with an integrally-formed laterally-ofl'set crank extension 19 at the other end. The journal portion l8 of the shaft is rotatively supported in a bearing 20 suitably mounted in the standard III, while the crank extension I 9 is engaged and held within the eccentric bore of a bushing 2| which is rotative in a bearing 22 in the standard I l in line with the main bearing 20. In the illustrated instance, the shaft is driven through a clutch generally designated by the numeral 23 by a fly wheel 2t having belt grooves at 25; and an automatic brake comprehensively designated 26 is relied upon to stop the shaft upon disconnection of said clutch. The last described devices and other parts of the press except those about to be referred to, do not form any part of the present invention and do not therefore need further mention.

Mounted on the crank extension [9 of the shaft with capacity for rotative adjustment thereon in a manner later on explained is a sleeve 21. Ad jacent its ends, this sleeve 21 is formed with contiguously-arranged integral

eccentric enlargements

28, 29 and 23a, 29a, of which the latter arediametrically opposed to and counterbalance the former about the axis B of the crank portion IQ of. the shaft I8. As shown, the eccentric enlargements 28 and 29 are centered on an axis C and extend through

bearings

30 and 3| in the side portions l5 and N5 of the reciprocated member, while the eccentric enlargements 23a. and 29a are centered on the shaft-bushing axis A. The sleeve 21 is moreover formed at its very ends with integral, flanges 32 and 3'! which are centered on the crank axis B. As further shown, the sleeve flange 32 abuts an eccentric flange 33 integrallyformed medially of the drive shaft l8 and corn tered in the crank axis B. The shaft flange 33 is made with a conical peripher for wedging ac tion with a surrounding clamp ring 34 and has a shouldered portion 33a which snugly fits into a recess in the contiguous face of the sleeve flange 32. The shaft flange 33 is moreover provided with a circumferential series of tapped holes to receive the shanks of headed screws 35 passed through screw holes in the sleeve flange 32. The other sleeve flange 31 in turn abuts a concentric conical flange 38 on the bushing 2|, the latter flange being provided with a shouldered portion 2 la which snugly fits into a recess in the contiguous face of the flange 38. A clamp ring 39 surrounding the flange 38 is provided with a circumferential series of tapped holes for engagement by the shanks of headed screws 40 passed, as before stated, through the screw holes of the sleeve flange 31. Attention is directed to the fact that the eccentricity of the enlarged portions 28, 29 of the sleeve 21 relative to the crank 19 is equal to the eccentricity of said crank extension [9 relative to the shaft; that is to say, the axis C is 01iset from the axis B by the same distance as the axis B is offset from the axis A. Secured by screws 4| and 42 to the shaft and bushing flanges 33 and 38 respectively are weighted annular elements 43 and 44 which counterbalance said flanges and the crank portion IQ of the shaft 18. As shown the elements 43 and 44 are centered on the shaft-bushing axis'A and have openings centered on the crank axis B to snugly receive the sleeve flanges 32 and 31.

With the sleeve 21 set as shown in Figs. 1-4, it will be seen that the eccentricity f the portions 28 and 29 of the sleeve 21 is added to that of the crank I9 so that maximum movement is imparted to the reciprocated element l3, the effective crank radius being as indicated by the arrow R in Fig. 7. To change the adjustment, the screws 35 and 40 are backed off to relieve the clamp rings crank axis; a bushing coaxial with the journal portion of the drive shaft, said bushing having an eccentric bore in which the end of the crank extension is engaged, and an eccentric flange centered on the crank axis; bearings respectively for the journal portion of the shaft and the bushing; a sleeve mounted with capacity for rotative adjustment about the crank between the shaft flange and the bushing, said sleeve having an eccentric enlargement for actuating a member which is to be reciprocated, and end flanges centered on the crank axis and respectively abutting the shaft and bushing flanges; clamp means operative to connect the sleeve flanges with the shaft and bushing flanges to secure the sleeve in adjusted positions; and means whereby the sleeve 34 and. 39 so that the sleeve 21 may be rotated in either direction about the crank I9 until the desired adjustment is had, whereupon said screws are re-tightened to hold such adjustment. The adjustment may be effected by means of a spanner wrench inserted into holes provided for that purpose in flanges 36 and 31. By turning the sleeve 2! through 180 from the position of Figs. 1, 3, 4 and 7 to the position of Figs. 5 and 8, the axis C is brought into coincidence with the shaftbushing axis A with the result that the effective crank radius will be zero. Again, by turning the sleeve 21 through a smaller angle as exemplified in Figs. 6 and 9, the effective crank radius will be shortened to the distance R and the movement of the member [5 correspondingly reduced.

Since, by reason of the described construction, the sleeve 21 is perfectly balanced about the crank axis B by the counterweighting at 28c and 29a, and the sleeve mass together with the crank extension I9 is perfectly balanced about the shaft axis A by the counterweighting at 43 and 44, it follows that the rotation of the drive shaft will be unattended by vibration for positions of adjustment of the crank throw. Accordingly machines in which the reciprocating means of my invention are employed can be safely operated at much higher speeds than heretofore possible and their output in turn correspondingly increased. Moreover due to the coaction between the shouldered portions 33a and 38a of the shaft and bushing flanges 33 and 38 and the recesses in the collar flanges 32 and 31, it will be seen that the crank extension l9 of said shaft and the sleeve 21 are effectively stiffened to withstand any forces tending to flex or bend them incident to high speed operation of the machines.

Having thus described my invention, I claim:

1. Means for effecting reciprocatory motion including an integrally-formed drive shaft element with a journal portion at one end, a laterallyoffset crank extension at the other end, and a medially-located eccentric flange centered on the is dynamically balanced about the crank axis, and whereby the crank and the sleeve are dynamically balanced about the shaft-bushing axis for all rotatively-adjuste'd positions of said sleeve.

2. The invention definedin claim 1, wherein the displacement of the eccentric portion of the sleeve relative to the crank axis is equal to the displacement of said crank axis relative to the shaft-bushing axis.

3. The invention defined in claim 1, wherein the drive shaft and the bushing flanges have shouldered portions concentric with the crank axis which snugly fit into recesses in the contiguous faces of the corresponding sleeve flanges.

4. The invention defined in claim 1, wherein the peripheries of the shaft and bushing flanges are conical; wherein correspondingly bored clamp rings fit over said flanges; and wherein the shanks of headed screws are passed through screw holes in the sleeve flanges and threadedly engage tapped'holes in said clamp rings.

5. The invention defined in claim 1, wherein the balancing means include an integral eccentric portion on the sleeve disposed diametrically opposite the eccentric enlargement for actuating the reciprocated member, and counterweight e1e-1 merits centered on a shaft axis and secured'to the shaft and the bushing flanges, said elements having circular openings centered on the crank axis and fitting over said sleeve flanges.

PENROSE R. HOOPES.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,137,877 Manly et a1. May 4, 1915 FOREIGN PATENTS Number Country Date 115,219 Great Britain May 2,1918