US1948468A - Honing machine - Google Patents

Description

Feb. 20, 1934.

Filed Nov. 18, 192

J. P. FERRIS HONING MACHINE 2 Sheets-Shefl 1 INVENTOR L/bHNFF'EEHJE.

ATTORNEY Patented Feb. 20, 1934 UNITED STATES 1,948,468 HONING momma- John P. Ferris, Milwaukee, Wis., assignor to The Ollgear Company, Milwaukee, Win, a corporation of Wisconsin Application November 18, 1926 Serial No. 149,052

9 Claim.

This invention relates primarily to honing machines although certain of the novel features thereof may be applied to advantage in other types of reciprocating machines such as grinders and the like.

One object of the present invention is the provision in a hydraulic reciprocating drive mechanism of improved control means for eifecting a continuous reciprocation of the driven part between certain prescribed limits within a normal working rangeg and adjustable to effect withdrawal of said part out of said range and to bring said part to rest automatically after withdrawing the same.

Another object is the provision of means for use with a control mechanism of the character mentioned by which the operator may at any time bring the reciprocating part to rest and by which the speed of the driven part may be 20 reduced to a very slow rate. This latter function is important, particularly in honing machines, in order to provide an exceedingly slow motion, commonly called inching, and commonly used when lining up the machine for a fresh piece of work.

Other objects and advantages will appear from the following description of an illustrative embodiment of the present invention.

In the drawings:--

Figure 1 is a fragmentary view in front elevation of a honing machine embodying the present invention.

Fig. 2 is a fragmentary view on a larger scale of the control mechanism shown in Figure 1, including sectional views of the valves.

Fig. 3 is a side elevation of a rocker element shown in Figures 1 and 2.

Fig. 4 is a sectional view of a honing tool illustrating means for expanding and contracting the same.

The honing machine selected for illustration includes a head casting fixed to the upper ends of a pair of parallel supporting columns 11 which rise from a base 12. A vertically reciproeating cross-head 13, mounted upon and guided by the columns 11, carries the honing tool 14, to be hereinafter described. The tool is shown fixed to the lower end of a shaft 15 journaled at its upper end within the cross-head l3, and driven from a shaft 16 through appropriate gearing housed within the cross-head. Shaft 16 is journalled within the cross-head, so as to reciprocate therewith and projects loosely through the head casting 10. A drive shaft 17, connected in driving relation with shaft 16 through appropriate gearing 18, carries a loose drive pulley 19. A clutch of any approved design, such for instance as shown at 20, is employed for releasably connecting the pulley in driving relation with the shaft. The clutch shown includes a movable collar 21 splined to the shaft 1'7 and cooperating with a similar clutch element 22 fixed to the pulley. An appropriate hand lever 23 pivoted at 24 and connected with the collar 21 is provided for opening and closing the clutch.

The cross-head 13 is reciprocated hydraulically. In the machine shown a piston 25 and cylinder 26 is provided for this purpose, the cylinder being anchored in the casting 10 and the piston being connected to the cross-head through a rod 2'7. The piston is actuated in either direction by liquid supplied froman appropriate source preferably from a variable displacement pump 28. The pump shown is fully described in Patent No. 1,798,198, issued March 31, 1931 to Walter Ferris and John P. Ferris. It will suflice here to state that the pump is driven at constant speed through appropriate means such as a pulley 29, and the displacement of the pump is regulated and controlled by a handle 30. Provision is also made in the pump for automatically-reducing pump displacement when the pressure in the pump delivery line exceeds a predetermined maximum, so that when the delivery line is blocked pump displacement is automatically reduced substantially to zero.

In the machine shown the pump is adjusted so as to deliver'liquid at a predetermined rate through pipe 31 and to receive liquid through pipe 32. A reversing valve 33 of appropriate form controls communication between these pipes and pipes 34 and 35, respectively connected to the upper and lower ends of the cylinder 26. The valve 33 is shown in section in Figure 2. It comprises a piston having two heads 36 and 3'7, connected by a reduced portion 38, and closely fitted for lengthwise reciprocation within the bore of a substantially cylindrical housing 39. The pump delivery pipe 31 communicates with the housing intermediate the heads 36 and 37, and the return pipe 32 communicates through branch pipes 32' with the opposite ends of the housing. An annular groove 40, controlled by head 36, communicates with pipe 34; and an annular groove 41, controlled by head 3'7, communicates with pipe 35. The arrangement is such that when the piston is in the lower full line position of Figure 2 pipe 31 communicates with pipe 35, leading to the lower end of cylinder 26, so that the piston 25, and consequently the cross-head 13 travel upwardly, the liquid from the upper end of the cylinder escaping through pipes 34 and 32 back to the return side of the pump. With the piston in the upper dotted line position of this figure, pipe 31 communicates with pipe 34 and pipe 35 communicates with pipe 32, so that the piston and cross-head travel downwardly. In an intermediate position of the valve, piston head 36 covers groove 40 and head 37 covers groove 41, so that pipes 34 and 35 are both blocked and the piston and cross-head are held stationary.

In the machine shown two separate means are shown for operating valve 33, one responding directly to the motion of the cross-head 13 by which the valve is shifted into intermediate position, and the other including valve actuating means, controlled by motion of the cross-head by which the valve is completely reversed. For these purposes the piston is provided with end plun'gers 42 and 43, closely fitted for reciprocation in cylinders 44 and 45, respectively, formed in the opposite ends of the housing. The valve housing 39 is fixed to the head casting 10 and the lower plunger 43 is provided with a reduced extension 46 forming a push rod aligned with a cooperating stop 4'7 fixed to the cross-head 13, so that as the cross-head approaches the upper limit of its stroke, the stop 47 acts against the rod 46 to force the piston of the valve into intermediate position. The stop 47 is preferably in the form of a screw, threaded in an appropriate lug 48 in order to afford adjustment of the coacting parts. The cylinders 44 and 45 are connected through pipes 49 and 50, respectively, to an appropriate pilot valve 51, also mounted on the head casting, through which fluid pressure is applied to one or the other of the cylinders, to thereby shift the reversing valve 33 from either extreme position to the other. A valve well suited for the purpose is shown in section in Figure 2.

As therein shown this valve includes a piston having two heads 52 and 53 closely fitted for reciprocation within a cylindrical housing 54. A groove 55 within the housing, controlled by head 52, communicates with pipe 49; and a similar groove 56, controlled by head 53, communicates with pipe 50. A pipe 57, leading from an appropriate fluid pressure source, communicates with the housing intermediate the heads 52 and 53, and discharge pipes 58 leading from the opposite ends of the housing communicate with a drain pipe 58. In this instance the pipe 57 is shown connected to the pump delivery pipe 31, and in order to insure sufiicient operating pressure in the pipe 31, a spring loaded valve 57' is interposed within this pipe between pipe 57 and the valve 33. The drain pipe 58 is ordinarily led back to the pump casing. The functioning of this valve is similar to that of valve 33. With the piston in the lower full line position of Figure 2, supply pipe 57 communicates with pipe 50, leading to end cylinder 44 of valve 33 thereby forcing the valve piston into the lower full line position, liquid escaping from end cylinder 45 through pipe 49 to drain pipe 58. Then when the piston is shifted into the upper dotted line position, supply pipe 5'? is connected with pipe 49, and pipe 50 is connected with drain pipe 58, so that the piston of valve 33 is elevated into the dotted line position shown.

The pilot valve 51 is placed under the control of the reciprocating cross-head 13 so as to effect the automatic reversal of valve 33. This may be accomplished in various ways, but the mechanism shown is well adapted to effect a continuous reciprocation of the cross-head within certain predetermined limits. a rod 59 supported by the piston of valve 51 and paralleling the path of reciprocation of the crosshead. A pair of stops 60 and 61 adjustably fixed to the cross-head cooperate with a stop 62 fixed to the lower end of this rod. The rod 59 is provided at its upper end with a substantially cylindrical head 63 guided within an appropriate bracket 64 fixed to the head casting 10. Any appropriate form of detent, such as a spring loaded ball 65 within the bracket and cooperating with annular grooves 66 and 6'7 in the head 63, serves to yieldably retain and position the rod 59 in either of two positions. The rod is connected to the lower end of the valve piston preferably through a yieldable connection 68, carried by the head 63, and a rod 69. The normal operation is such that, during the down stroke of the crosshead, stop 60 thereon strikes stop 62 on rod 59, thereby forcing the rod 59 downwardly into the position shown in Figure 2, and lowering the piston of valve 51 accordingly. This causes the valve 33 to assume the lower full line position of Figure 2, with the result that the lower end of cylinder 26 is open to the supply pipe 31 and the cross-head 13 rises. The cross-head continues to rise until stop 61 thereon strikes stop 62 on the rod 59, causing the rod to rise, and thereby reversing valves 51 and 33 and causing the crosshead to lower. The cross-head thus reciprocates continuously through a range determined by the setting of the stops 60 and 61, and this range may be varied by adjusting either or both of these stops.

During each upward stroke the lower stop 61 normally strikes the stop 62 on the rod 59 before the stop 4'7 strikes the rod 46. Provision is made by which the operator may so adjust the stop 62 as to clear the stop 61, to thereby permit the cross-head to rise until stop 47 strikes rod 46. In the machine shown this is accomplished by the use of a collar 70 fixed to the rod 59-through which the rod 59 is rotated sufficiently to cause stop 62 to clear stop 61.- The collar 70 is actuated and controlled by an element 71 pivotally supported upon a stud 72 fixed in the bracket 64, and provided with a depending fork '73 engaged with a pin '74 projecting laterally from the collar. A control rod 75, connected to an arm '76 projecting from the rocker element 71, extends down- Wardly within convenient reach of the operator, where it is connected to an appropriate hand lever '77. A spring '78, interposed between the casting 10 and the rocker element, normally retains the element and associated parts in the position shown in Figures 1, 2 and 3, with the stop 62 in the path of movement of the stop 61. By depressing the hand lever 77 the element '71 is rocked clockwise (Fig. 3) causing the rod 59 to be rotated in such direction as to swing stop 62 clear of stop 61. This permits the cross-head 13 to continue its upward stroke until stop 47 strikes rod 46 and shifts the piston of valve 33 into intermediate position. As above pointed out, the valve 33, in this position, blocks 'both pipes 34 and 35 and the piston 25 and cross-head come to rest.

It will be noted that during the upward stroke of the cross-head the piston of valve 51 is in the lower full line position of Figure 2, and that this valve remains in this position as the piston of valve 33 is forced upwardly into intermediate po- This mechanism includes sition by the advance of stop 47. The piston of valve 51 is thus in lower position when the crosshead comes to rest. In order to again start the cross-head on a down stroke the piston of this valve is shifted by the operator into the upper dotted line position. Various means may be provided for placing this valve under the control of the operator, but the mechanism herein shown is well adapted for the purpose. This mechanism includes a control rod '79, connected at its lower endto an appropriate hand lever 80 and at its upper end to an appropriate shifting lever 81, rockably supported upon a fixed pivot 82 and engaged through the usual trunnion, and groove connection 83 with the collar 70. The arrangement is such that when the hand lever 80 is depressed the shifting lever 81 is swung clockwise and the rod 59 and piston of valve 51 is elevated. This causes the piston of valve 33 to be elevated, as hereinabove described, and the cross-head 13 starts downwardly.

A brief description of the operation of the machine, thus far described, will now be given. Let it be assumed that the drive pulleys 19 and 29 are both in operation; that the clutch 20 is closed so that the tool 14 is rotating; that the pump control handle 30 is properly set; and that crosshead 13 is at the upper limit of its stroke with the piston of valve 33 in intermediate position and the piston of valve 51 in the lower ful line position of Figure 2. The cross-head is of course at rest. To lower the cross-head into its lower normal operating range the operator depresses the handle 80 to thereby lift the piston of valve 51. Fluid under pressure is thus admitted to end cylinder of valve 33, through pipes 49 and 57, and the piston of this valve is immediately elevated.

. Liquid is thus supplied to the upper end of cylinder 26 through pipes 34 and 31 and the piston 25 and cross-head start downwardly. During this initial down stroke the operator holds handle 30 depressed in order to permit the stop 62 to clear stop 61. After stop 61 has passed stop 62 the operator releases handle 80 and the cross-head continues downwardly until stop 60 strikes stop 62 and lowers the piston of valve 51 into the full line position of Figure 2. When this occurs the end cylinder 44 of valve 33 receives liquid under pressure through pipes and 57, valve 33 is reversed and liquid, admitted through pipes 35 and 31 to the lower end of the cylinder 26, causes the piston 25 and cross-head to travel upwardly. This upward travel continues until stop 61 strikes stop 62 to again reverse valves 51 and 33 causing a reversal of movement of the cross-head. Thereafter the cross-head continues to reciprocate through a definite range, as determined by the stops and 61, resulting in a corresponding reciprocation of the honing tool 14. When the honing operation is completed the operator depresses the handle 77 so as to swing the stop 62 clear of the stop 61, thereby permitting the crosshead and tool to rise, this upward movement continuing until the valve 33 has been adjusted into neutral position by the upward advance of stop 4'7 against the rod 46. During the continuous reciprocation of the cross-head and tool within the range determined by the stops 60 and 61, the tool is engaged within the work, the extended movement beyond this range being pro vided to advance the tool into and retract the same from the work.

The machine illustrated is designed primarily for use in honing the cylinder walls of internal combustion engines and the tool 14 is of an expansible type commonly employed for this purpose. In such operations it has been found desirable to contract the tool prior to insertion and extraciion from the work and provision is therefore made in the machine shown for automatically performing this function. Mechanism well adapted for this purpose is shown in Figures 1 and 4. The tool shown comprises a hollow cylindrical head 84 removably fixed to the lower end of shaft 15 for rotation therewith. A series of shoes 85, each having a facing 86 of abrasive material, are symmetrically disposed about the head and extend parallel to the axis thereof. Each shoe is carried by a stem 87 closely fitted in the wall of the head for lengthwise movement radially of the head. Each shoe is guided by appropriate studs 88 similarly fitted in the wall of the head and provided with appropriate means, such as nuts 89, for limiting outward movement of the shoes. Appropriate springs 90 yieldably urge the shoes outwardly. An appropriate form of cam mechanism serves to contract the shoes toward the head. The cam mechanism shown comprises a spider 91 having a plurality of wedge shaped elements 92 projecting upwardly'therefrom, each wedge 92 being engaged within a slot 93 formed in a stem 87. The spider 91 is fixed to a rod 94 closely fitted for lengthwise adjustment within a bore 95 formed in the lower end of shaft 15. A wedge 96 projecting through slots 97 and 98 formed in the shaft 15 and rod 94 is operative to adjust the rod with the shaft. The wedge 96 is yieldably retained in the retracted position shown in Figure 4 by any appropriate means such as a spring 99, and, in this position, the rod 94, spider 91 and wedges 92 are lowered and the shoes 85 are free to move outwardly under the action of springs 90. By forcing the Wedge 96 inwardly against the pressure of spring 99, the rod 9 is lifted and the wedges 92 acting on the stems 87 draw the shoes 35 inwardly to thereby contract the tool. In the machine shown the wedge 96 is automatically operated by a ring 100 surrounding the shaft 15 and adjustably fixed to one of the columns 11 of the machine. The ring 100 is provided with an inernal cam surface 100 and is so positioned as to clear the wedge 96 during normal reciprocation of the tool within its normal working range, but so as to engage the wedge immediately prior to entry of the tool in the work and to exfraction of the tool from the work. Thus during the entry and extraction of the tool the wedge 96 is forced inwardly and so held by the ring, thereby contracting and holding the tool in contracted condition during these periods.

Provision is also made in the machine shown for stopping the reciprocation of the cross-head 13 and tool 14 at any instant, or for effecting an exceeding slow movement of the par s, such as has been found desirable when setting up the machine for a fresh piece of work. Mechanism for this purpose is preferably so combined with the tool roating mechanism, as to effect non-rotation of the tool during this slow motion or inching process. In the machine shown this mechanism includes a valve 101 interposed within the main supply pipe 31 leading from the pump. This valve comprises a piston having two heads 102 and 103 connected by a reduced portion 104 and closely fitted for reciprocation in a cylindrical housing 105. The liquid in the pipe 31 is normally free to pass around the reduced portion 104 to the valves 51 and 33. By adjusting the piston lengthwise however the head 102 thereof may be so positioned with respect to pipe 31 as to throttle this flow to any extent desired, even to the extent 01' completely blocking the flow. The piston is connected through a rod 106 with the clutch control lever 23 so as to respond to movement thereof. The connection is such and the reduced portion 104 of the piston so proportioned, that the clutch may be opened completely by the action of lever 23 without disturbing the flow through pipe 31. Thus the valve may be adjusted from the full-line position into the dotted line position of Figure 1 while the lever 23 is being swung sumciently to open the clutch. Thereafter further movement of the lever causes the head 102 of the valve to throttle the pipe 31 to any degree desired, during which adjustment the clutch 20 remains open and the tool 14 is not rotated.

Various changes may be made in the embodiment of the invention hereinabove specifically described without departing from the invention as defined in the appended claims.

I claim:

1. In a honing machine the combination of a reciprocating member, a honing tool movable therewith, means for rotating said tool, a variable displacement pump, means actuated by said pump for driving said member at a rate corresponding to pump displacement, control mechanism for said driving means normally responsive to movement of said member for reversing the same to thereby efiect continuous reciprocation of said member and tool within a predetermined range, means for adjusting said control mechanism during reciprocation of said member to effect withdrawal of said member and tool from said range at said predetermined rate, and means automatically operable to stop the movement of said member at a predetermined point beyond said range.

2. In a honing machinev the combination of a reciprocating member, a honing tool movable therewith, means for rotating said tool, a variable displacement pump, means actuated by said pump for driving said member at a rate corresponding to pump displacement, control mechanism for said driving means, cooperating stops associated with said member and control mechanism automatically operable to reverse said member to thereby effect continuous reciprocation of said member and tool within a predetermined range, means for rendering one of said stops inactive without actuating said control mechanism to efiect withdrawal of said member and tool from said range at said rate, and means responsive to movement of said member beyond said range for arresting movement thereof.

3. In a honing machine the combination of a reciprocating member, a honing tool movable therewith, means for rotating said tool, a variable displacement pump, means actuated by said pump for driving said member at a rate corresponding to pump displacement, valve mechanism for controlling said driving means, means normally responsive to movement of said member for shifting said valve mechanism to effect continuous reciprocation of said member and tool within a predetermined range, means for adjusting said last named means to effect withdrawal of said member and tool from said range without operating said valve mechanism, and means responsive to movement of said member beyond said range for shifting said valve mechanism into neutral position to arrest the movement of said member and tool.

4. In a machine having a reciprocating member, the combination of a variable displacement pump, hydraulic means driven by said pump for driving said member, means for regulating pump displacement to thereby regulate the movement oi. said member, a valve for controlling said driving means, means normally responsive to movement of said member for shifting said valve to efiect continuous reciprocation of said member within a predetermined range, means for adjusting said last named means to eflect withdrawal of said member from said range without operating said valve, and means responsive to movement of said member beyond said range for shifting said valve into neutral position to thereby arrest movement of said member.

5. In a machine having a reciprocating member, the combination of hydraulic driving means therefor, a valve for controlling said driving means, hydraulic means for operating said valve, a pilot valve controlled by movement of said member for controlling said valve operating means, means under the control of the attendant for operating said pilot valve to render said driving means active, and means actuated by movement of said member for operating said first named valve to render said driving means inactive.

6. In a machine having a reciprocating member, the combination of hydraulic driving means therefor, a valve for controlling said driving means, hydraulic means for operating said valve, a pilot valve normally responsive to movement of said member for controlling said valve operating means to reverse said valve and member, means actuated by said member for operating said first named valve to arrest movement of said member, and means controlled by the operator for operating said pilot valve.

7. In a machine of the character described the combination of a reciprocating member, hydraulically actuated means for driving said member at a predetermined rate, a reversing valve for controlling the direction of movement of said member, a pilot valve for controlling said reversing valve, automatic control means coacting with said pilot valve to effect continuous reciprocation of said member between predetermined limits, means under the control of the operator for operating said pilot valve independently of said control means, and means under the control of the operator for rendering said automatic control means ineffective to thereby efiect movement of said member beyond said limits at said predetermined rate.

8. In a machine of the character described the combination of a reciprocating member, hydraulically actuated means for driving said member at a predetermined rate, a reversing valve for controlling the direction of operation of movement of said member, a pilot valve for controlling said reversing valve, automatic control means coacting with said pilot valve to effect continuous reciprocation of said member between predetermined limits, means under the control of the operator for operating said pilot valve, independently of said control means, means under the control of the operator for rendering said automatic control means ineffective to thereby effect movement of said member beyond said limits at said predetermined rate, and means automatically operable to stop the movement of said member at a predetermined point beyond said limits.

9. A honing machine, comprising a support for supporting the work in a stationary position during the honing operation, a tool head reciprovalve in response to the movement of said toolhead to effect continuous reciprocation of said tool head within a predetermined range, means for adjusting said valve operating means to effect withdrawal of said tool head beyond said range without changing the speed of said motor, and means responsive to the movement of said tool head beyond said range for operating said control valve independently of said pilot valve to arrest the movement of said tool head.

JOHN P. FER-BIS.

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