US2058782A - High speed planing machine with hydraulic ram drive - Google Patents

Description

Oct. 27, 1936. H FElLKAs 2,058,782

HIGH SPEED PLANING MACHINE WITH HYDRAULIC RAM DRIVE Filed Jan. 21, 1935 I5 Sheets-Sheet l fly] 7// r A Oct. 27, 1936.. 2,058,782

HIGH SPEED PLANING MACHiNE WITH HYDRAULIC RAM DRIVE.

-H, FEILKAS Filed Jan. 21, 1935 3 Sheets-Sheetv 2 lNl/E/VTUR 1935- H. FEILKAS 2,053,732

i-IIGH SPEED PLANING MACHINE WITH HYDRAULIC RAM DRIVE Filed Jan. 21, 1935 3 Sheets-Sheet 3 Fly? - 50' w x1: F .9 40 g 3/1? I 722 zrsn for:

Patented Oct. 27, 1936 j HIGH SPEED PLANHNG MACHINE WITH HYDRAULEQ RAM DRIVE Heinrich Feilkas, @iienbach-on-the-Main,

Germany Application llanuary 21, 1935, Serial No. 2,710 in Genny January 24, 193i 7 @laims.

This invention relates to a high speed planing machine with hydraulic ram drive by a pump with uniformly variable delivery quantity, which, controlled by a reversing element, acts on a piston arranged in a working cylinder and mounted on the end of a piston rod.

The known machines of this type are open to the objection that all the working speeds necessary for rough and smooth work'cannot be governed by a single delivery pump of small dimensions, without special auxiliary arrangements.

I The primary object of the invention is to overcome this objection. This is attained in that the reversing element cooperating with a reversing cock controls conduits deliveringto both ends of the working cylinder so that merely by adjusting the reversing cock for roughing only the full piston side, for smoothing for the purpose of increasing the working speed both piston sides and for the accelerated return movement only the oil-set side of the piston can be subjected to pressure, whereas, when the reversing element is in its intermediate 'position, the loading of the piston is interrupted.

In order to effect the return movement in any working position at the-highest possible constant speed, the reversing element is'connected with the delivery pump by clutch members which, when the reversing element is set for the return movement, adjust the pump for maximum raising.

By interposing an idle movement in the clutch members between the pump and the reversing element, provision is made for the shock-free reversal of the piston.

The displacement of the reversing element is effected by an auxiliary pump, the pressure oil of which can be employed for pressure lubrication after the reversal. The reversing element is also directly connected with a shaft effecting the travel of the table, this shaft, when disengaged, enabling a uniform driving of the table.

The planing machine consists substantially of a base plate serving as oil container, a ram shiftablymounted on a bed and driven by a power cylinder situated thereunder, a pressure oil pump with reversing valve and the necessary conduits, and a table with feed mechanism for carrying the'work.

In the accompanying drawings those arrangements which are essential for the invention are illustrated, by way of example, partly diagrammatically.

Fig. 1 shows the hydraulicdrive and the reversin'g device fol-"the piston actuating the ram (oi. air-38) and the drive for the table travel connected therewith.

Fig. 2 is a section on line Iii-II of Fig. 1. Figs. 3 to 6 show the reversing valve in section on line IIIIII of Fig. 1, with thecontrolling it member in different positions.

Fig. 7 shows in section and on a larger scale the ratchet clutch for intermittently feeding the work table.

Fig. 8 is a sectional view showing the other end of the driving shaft of the ratchet clutch with the neighbouring bearing parts equipped with a claw clutch, the claw clutch being completely engaged for'obtaining maximum table feed.

Fig. 9' shows the same arrangement as Fig. 8 with half engaged claw'clutch for obtaining smallest table feed.

Fig. 10 shows the arrangement of recesses in one of the bearing parts serving for accommodating the clutch teeth, viewed in the direction of the arrow I of Fig. 8.

Fig. 11 shows the arrangement of the teeth on the clutch part, viewed in the direction of. the arrow II of Fig. 8.

Fig. 12 is a horizontal part section through the control box taken at the height of the axis of I the reversing cook.

The planing machine is driven for example by an electric motor 0 which drives a hydraulic pump 2 with oscillatable casing 3. When the casing assumes the horizontal position shown in Fig.'1,'the delivery is zero. By oscillating the casing 3 upwards into the position a indicated in dot-dash lines, the delivering quantity can be uniformly varied up to a maximum. The oil is '35 taken from an oil tank it through a suction pipev 5 supplied from. the-pressure side of the hydraulic pump through a pressure pipe 6 to a reversing element i, from which it is fed through conduits 8 and 9 respectively to the power cylinder id. In this cylinder moves a piston l i which on one side. carries a piston rod i l rigidly connected in the usual manner with the ram of the planing machine which is not shown on the drawings. During the outward movement of the ram the full face Ila. of the piston is operative, whereas during its return movement only the annular surface lib is operative. The ratio between the two piston surfaces is about 2: 1.

The reversing valve l3 consists of a housing I with a rotaryfyalve I! mounted therein, in the bore Bar of which valve a shaft I4 is axially shiftable. The bores and milled out portions necessary for conducting the pressure oil to the pressure conduits 8 and Q'are provided in the housing I and in the valve l2. The pressure conduits 8 and 9 and a discharge conduit 15 extend in the section plane III-III up to the slide valve bore Ila. At this point the valve l3 has two chambers l6 and I1 open towards the bore l3a. A shut off or reversing cock I8 is fitted in the pressure conduit 9 in the housing 1 transversely to the valve l2, said cock enabling the conduit 9 to be brought into communication with a by-pass conduit [9 terminating in the slide valve bore l3a opposite the conduit 8. All channels communicating with the bore I3a are mutually displaced through an angle of 90.

The pressure oil is supplied through a channel 20 extending from the pressure conduit 6 and leading to the chamber IS in the valve l2. Diametrically opposite this channel 20 a bypass 2l is arranged in the housing 1, which by-pass leads from the pressure chamber It to the outer end of the housing. This by-pass 2| is closed by a portion of the reversing cock l8 which is -not hollow, but is opened when the reversing cock is in a predetermined position by means of a bore 22 in this cock, so that the oil can flow off freely from the pressure chamber through this by-pass into the collecting tank 4. The rotary slide valve is adjusted by hydraulic means through the intermediary of a gear driven auxiliary pump 24 driven from the shaft M by gear wheels, drawing oil out of the tank 4 through a suction pipe 25 and forcing it through a pressure pipe 26 into a chamber 21 arranged in a cover 28 placed on one side of the housing I. This cover covers a semi-annular space29 in the housing 1, half filled by a blade 30 fixed on the rotary slide valve. Channels 31 and 32 extend from the chamber 2'! to each end of the semi-annular space 29. A stepped piston valve 33 is mounted in the chamber 21 and adjusted by adjustable abutments influenced by the piston II or the ram through the intermediary of transmission members not shown in the drawings. This stepped piston valve conducts, according to its position, the pressure oil to the one or the other side of the blade 30, so that the rotary slide valve I2 is rotated through an angle of 90 in the one or other direction (Fig. 2). The stroke movement is limited by the blade striking against the housing.

The oil delivered by the auxiliary pump 24, does not return, after every rotation of the rotary slide valve, directly into the oil tank, but is forced into tubes 34, 35 serving for lubricating the whole machine, the tubes 35 being, during the reversing movement, alternatively connected with the portion of the semi-annular space 29 actually filled with oil.

The table travel is derived from the shaft l4 journalled in the rotary slide valve, said shaft acting on the usual feeding mechanism of the table through the intermediary of a ratchet clutch 30 operating in one direction and of a bevel wheel gearing 31, 38.. The ratchet clutch comprises a sleeve 3! slidable in the hollow hub of the toothed wheel 31 and provided at one end with teeth 38' bevelled on one side which engage in the corresponding tooth gaps of a toothed ring 31' inserted and fixed in the hub bore owing to the fact that the sleeve 31 is pressed against the ring I! by the pressure of a spring 34". In the sleeve It wedge grooves 41 are provided in which the wedges 48 fixed on the shaftv l4 slide when this shaft-is shifted. When the'shaft I4 is driven in one direction. the teeth 3C cause the toothed ring 31' to rotate, whereas they slide 'valve l2, which shaft carries on its periphery four conically tapered projections 40. These projections engage in corresponding recesses 50 in the rotary valve l2. When the shaft is in the position shown in Fig. 8, the shaft is rotated during a swinging movement so that the maximum table feed is attained. By pulling the shaft back into the position shown in Fig. 9, there is .idle movement between the projections 40 and the recesses 50 so that in this position for example the shaft carries out only half the swinging movement and consequently reduces the table feed by one half as compared with the position according to Fig. 8. The table feed can be regulated by different intermediate positions.

In order to obtain a uniform table movement, it requires, for example for bringing it quickly into its initial position when setting up a fresh workpiece, a clutch member 39 is fitted on the shaft l4 and when the shaft I4 is shiftedfurther to the left, this member is brought into engagement with the axle of one of the wheels of the pump 24 through the intermediary of a suitable gearing. Thus, the shaft is uniformly driven when the clutch between it and the rotary valve l2 has been disengaged.

The shaft I4 is always shifted the desired distance in longitudinal direction by hand, through the intermediary of an adjusting lever 4|.

A lever 43 is fixed on the end of the rotary slide valve I2 extending through the cover 28, and connected to the housing 3 of the hydraulic gear by a wire rope 44. Consequently,- if the rotary slide valve i2 is rotated in one direction, the lever 43 lifts the housing 3 and adjusts the main pump 2 to maximum delivery.

The housing 3 of the main pump can further be adjusted by a toe cam 45 to a certain delivering quantity determining the forward speed.

The arrangement above described is operated and operates-in the following manner:-

It is supposed that the main pump 2, 3 adiusted by the toe cam to a certain delivery to be conducted through the pipe 8 to the face Ila of the piston ll, produces the desired forward speed for the ram.

(a) Rough planing It the machine is to carry out rough planing, the controlling elements assume the positions shown in Figs. 2 to 4, Figs. 2 and 3 particularly show the position of the controlling parts during the return movement of the piston II. The chamber it, into which the pressure oil is fed through the conduit 0 andchannel 2i, communicates with the conduit 9 through the by-pass conduit I! and reversing 0001: I8, so that the pressure oil cannot onthe annular face llb of the piston II and push the piston towards the. left. When the rotary slide valve I2 is in this position, its lever 43 raises the housing I of the main pump and adjusts this pump for maximum delivery. The return movement of the piston is therefore considerably accelerated as compared with its forward movement. not only on ac aoaavsa ment abutments of the piston slide valve 33- infiuenced by the ram are shifted out of the position indicated in Fig. 2 towards the left by a distance b. Thus, the pressure 011 delivered by auxiliary pump 44 is then fed through the channel 32 in front of the blade 39 which is thus turned through an angle of 90 in clockwise direction. During, the shifting of the blade 30 "the oil in the-space 29 is forced through the channel till into the lubricating conduit 35 which is now opened. After reversal the pressure oil can flow back to the auxiliary pump through the ,lubricatlng conduit 34.

"By. the rotation of the rotary slide valve if the lever 33 has likewise been lowered so that the housing 3 of the main pump again bears on the toe cam t5 and the main pump is adjusted to the forward speed.

as shown in Fig. 4 the pressure chamber it, during the forward movement, communicates with the pressure conduit 8 through which the piston face Ilia of the piston i II is loaded, so that the forward movement of the cam is effected.

The oil on the rear side of the piston can flow to the discharge pipe it through the conduit 9, reversing cook it, by-pass conduit it and channel ill. I

(b) Smooth planing To enable the same equipment to be also em.-

ployed for smoothingwork requiring increased speed, it is only necessary to adjust therotary slide valve so that, during the forward moveconduits d and 9 are connected with thepressure chamber it. The oil behind the piston ill is then, during the forward movement, pressed.

through the conduit 9 into the pressure chamber it and thence through the conduit t together with the oil delivered by the main pump through the conduit 8 in front of the piston it. Thus, the quantity of oil acting on the front'of the piston will be enlarged by the quantity displaced from behind the piston and the speed of the forward movement is correspondingly increased.

For the return movement the rotary slide valve I2 is turned into the position shown in Fig. 5, in which the pressure chamber I B is connected with the-conduit t by the reversing cock, whereas the oil in front of the piston H can flow off through the conduit 8, channel l1 and pipe i5. In this position the pump 3 is likewise set formaximum delivery.

(c) Stopping position In order to stop the cam immediately in any position it is only necessary to bring .into its middle position the hand lever 46 which actuates the reversing cock l8. Thus, the channel 2i hitherto shut off by the reversing cock and which connects the pressure chamber with the external space, is uncovered by the bore 22 in 1 er distance.

the reversing cock, so that the oil delivered by the pump 3 fiows back into the oil .tank free from pressure.

From the above described operations it will be clear that the adjusting of the machine for roughingand smoothing-work and for stopping can be effected'by a lever 46. The duration of the returnmovement is reduced as far as possible by simultaneous adjusting of the pump 3 for maximum delivery and maintained constant at all speeds of forward movement.

In order to attain a gentle reversing movement of the piston it an idle movement is provided in the clutch members which connect the rotary slide valve it with the adjustable part of the delivery pump. This may be attained, for example, by making the angle of rotation of the rotary slide valve 112 and therefore of the lever dd twice as large as the angle of rotation of the pump housing 3. Thus, the pump, when changing over from forward to reverse movement, is only raised after the rotary slide valve has already performed half of its movement,- so that oil can already pass to the other side of the piston through the conduit 9 shortly before the reversal of the piston. Consequently, the acceleration takes place gently, that is any pressure impulses which might otherwise occur during the reversal of the whole quantity of oil are avoided.

On the other hand, during the reversing of the piston from reverse to forward movement, the delivery of the pump during,the first half of the rotation of travel of the rotary slide valve is first reduced and only thereafter is the oil flow reversed. Consequently, the most favorable effect is attained with the very simple means.

(d) Feed and quick travel The periodical travel of the table is efiected, as already mentioned, by the control valve it in that by throwing over the lever ti to the right (Fig. l), the control valve is coupled with the shaft it journalled therein, so that this shaft actuates the feeding mechanism by means of a ratchet clutch 36 operating in one direction during the return movement of the piston. If the shaft it is then moved to the left bythe lever ii, the wedge-shaped noses tit on the catch 39 will be gradually pulled out of the corresponding wedge grooves of the rotary slide valve, so that, according to the distance the shaft is shifted, there will be more or less play between the noses and grooves which represents more or less great idle movement between the shaft and the rotary valve. Consequently the full rotary movement of the valve is no longer transmitted to the shaft it and consequently the table travels for a short- Thus, the table travel can be regulated within certain limits by the lever it.

In order to reduce the idle running periods it must be possible to continuously move the table not only by hand but also mechanically. The continuous movement must, however, only take place after the disengagement of the intermittent movement. This is attained by entirely uncoupling the shaft i l from the rotary slide valve stroke, the feed from zero to maximum, and the feed and quick travel can be carried out whilst the machine is running. Moreover, it has been possible by the reversing valve which unites everything, to reduce the number of operating levers to a minimum and to arrange these on a small area of the outer wall where they are easily accessibleh The invention is not restricted to high-speed planing machines but it may also be applied to other machine-tools wherein the toolor the work carries out a reciprocating movement.

The pump with variable. delivery may likewise be of any suitable construction.

I claim:-

I. High-speed planing machine with hydraulic ram drive, comprising in combination a working cylinder, a piston reciprocable in said cylinder, 9. piston rod on one side of said piston reducing the operative surface on this side of the piston, a main pump with uniformly variable delivery, a pressure pipe leading from this pump, a control element at the other end of said delivery pipe, a control housing accommodating said control element, said control element rotatable in both directions in said housing, a second pump with constant speed of rotation, a blade servomotor connected with said control element, a pivot control valve between said servo-motor and said control element, said second pump in conjunction with said servo-motor adapted to alternately shift said control element into its two extreme positions through the intermediary of said pivot control valve, by-passes in said housing leading to said control element, a hand operated reversing cock arranged in the control housing and adapted to control said by-passeaa conduit leading from said control element to one end of said working cylinder, and a conduit leading from said reversing cock to the other end of said working cylinder, said control element and said reversing cock being mutually adjustable to control said by-passes and conduits and place the large surface of said piston under pressure during the outward movement, the small surface of the piston during the return movement and in the case of high working speed, such as for smoothing, both surfaces of the pistons during the outward run and the small surface of the piston during the return motion.

2. In a high-speed planing machine as claimed in claim 1 coupling members connecting the rotatable selector valve with the portion of the variable main pump adjusting the delivery of the pump, said coupling members adapted to set the main pump for maximum delivery when said selector valve is set for reverse motion.

3. A high-speed planing machine as specified in claim 1, comprising abutments on the ram adapted to indirectly influence the control element, and clutch members between said element and the main pump adapted to adjust said pump for maximum delivery when said element is adjusted to return movement by said abutments, said clutch members having an idle movement to prevent the production of shocks during the reversal.

4. In a high speed planing machine as specified in claim 1 an oscillatable main pump casing, a pull element attached at one end to said casing, a lever fixed on the control element and attached to the other end of said pull element so that during the rotation of said pull element said casing is oscillated at an angle of. rotation smaller than that of said pull element.

5. In a highspeed planing machine as specified in claim 1 the control element having a central bore, a table feed driving shaft longitudinally shiftable in said bore, a part driven by the auxiliary pump, and clutch members between said part and said shaft adapted to transmit the movement of said part to said shaft to effect the table feed.

6. In a high speed planing machine as specified in claim 1 the control element having a central bore, a table feed driving shaft longitudinally shiftable in said bore, a part driven by the auxiliary pump, and conical, clutch-members between said part and said shaft adapted to transmit the movement of said part to said shaft to effect the Y table feed.

'7. In a high speed planing machine as specified in claim'l a table feeding mechanism connected to 'the control element, and a blade servo-motor connected with the auxiliary pump and adapted to adjust said control element to actuate said mechanism, and pressure lubricating conduits connectedto said motor and adapted to lead oi! the oil from the auxiliary pump to lubricate the machine.

- HEINRICH FEILKAB.

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