US1969063A

US1969063A - Grinding machine

Info

Publication number: US1969063A
Application number: US321198A
Authority: US
Inventors: Ernst Hans; Herman R Isler
Original assignee: Cincinnati Grinders Inc
Current assignee: Cincinnati Grinders Inc
Priority date: 1928-11-22
Filing date: 1928-11-22
Publication date: 1934-08-07
Anticipated expiration: 1951-08-07

Description

Aug. 7,1934. H. ERNST Er A1. 1,969,063

GRINDING MACHINE Filed Nov. 22. 1928 5 Sheets-Sheet 1 7i 5g, 7 z. 31

2, J..- azi a 10 /76 1M 416 36 as A o 1e i W A 55 6 e.

sa 141 U5 .of 67 2. v Z5 '"iililliliiiiiiiul@il Jl 1 l v :YE

l *if K4 Mnlgm i? iE- Q14. aw

Aug. 7, 1934. H. ERNST Er AL GRINDING MACHINE Filed Nov.

5V Sheets-Sheet 2 Allg. 7,; 1934. H. ERNST ET AL 1,969,063

I 'GRINDING MACHINE Filed Nov. 22, 1928 5 sheets-sheet s wz: d i 105 i04- iz da: 404 i056,

A N y gwomtoc .A5 E HANS ERNsr I su* HERMAN R. SLER.. 45 g MM 1 g: i I amm ab 44K: I

Aug. 7, 1934. H. 4ERNST ET Al. 1,969,063

' i GRINDING MACHINE File@ Nov. 22, 1928 5 Sheets-Sheet 4 l z y Swanton:

HAMsE/M'sr HER/vl A NA. I'sLfR FJ accom,

Aug- 7, 1934 H. ERNST Er Al. v1,969,063

GRINDING MACHINE Filed Nov. 22. 1928" 5 sheets-sheet 5 `IIIIIHIlHIIllIIIIHIIIIHIIIII u l HA/vs ER NST, HERMA/v RISLER,

Patented ug. 7, 1934 n UNITED sTATEs GRINDING MACHINE Hans Ernst and Herman R. Isler, Cincinnati,-

Ghio

Ohio, assgnors to Cincinnati Grinders Incorporated, Cincinnati, Ohio, a corporatioxrof Application November 22, 1928, Serial No. 321,198

37 Claims.

This invention relates to improvements in grinding machines/and particularly to that type of grinding machine in which the work is held between centers in opposition to a grinding 5 member for removal of stock therefrom.

In the performance of grinding of this nature there are two general methods of grinding employed, one in" which the grinding wheel is fed directly into the work and commonly known Al as plunge cut grinding and the other in which a relative transverse movement is imparted to the work and grinding wheel to cover work of greater length than the width of the wheel and in which the feeding action takes place only at l the end of the stroke or strokes of movement.

One of the principal objects of the present invention is the provision of an improved automatic machine of universal application and capable of utilization for either of said types of grinding.

A furtherv object of the invention is the provision of novel and improved automatic or semiautomatic control mechanism for effecting the various desired movements of the parts of the machine.

An additional object of the invention is the provision of a machine which obviates the necessity for a large number of gears, clutch members and the like for accomplishing the various desired feeding movements and adjustment of the speed thereof and which will satisfactorily accomplish the results hitherto attained by gear mechanisms through the utilization of a novel hydraulic control system therefor.

Further objects of the invention include the provision of improved hydraulic circuits and control mechanisms therefor for operation of the grinding wheel head slide and for operation of the grinding wheel table to insure properly timed and sequential movements of the several' parts.

Other objects and advantages of the present invention should be readily apparent by reference to the following specification taken in connection with the accompanying drawings, forming a part thereof, and it will be understood that we may make any modifications in the structural details or combination and arrangement of parts hereinafter described within the scope of the appended claims without departing from or exceeding the spirit of the invention.

Figure l is a front elevation of a machine embodying the present improvements.

Figure 2 is a transverse Vertical sectional view thereof, taken as on the line 2-2 of Figure 1.

Figure 3 is a diagrammatic view illustrating the several control systems for the machine.

Figure 4 is a fragmentary view partially in section illustrating the connections for imparting reciprocating movement to a long table member. e

Figure 5 is a fragmentary end viewwith parts in section illustrating the arrangement of the electrical and mechanical starting and stopping system.

Figure A6 is a sectional View as on line 6--6 of Figure 1 illustrating the pump drive and speeding up mechanisms.

Figure 7 is a fragmentary view illustrating the manual adjustment of the variable displacement pump.

Figure 8 is a fragmentary section of the view as on line 8--8 of Figure. 7.

Figure 9 is a fragmentary transverse section as on line 9--9 of Figure 1 showing the manual table adjustment mechanism.

Figure 10 is a horizontal section as on line 10-10 of Figure 1 showing the hydraulic table drive control valve mechanism.

' Figure 11 is a similar view showing a different adjustment of the valve with respect of the several ports controlled thereby.

Figure 12 is a fragmentary view of the valve control lever for shifting the parts shown in Figures 10 and 11.

Figure 13 is a fragmentary section through the intermittent table feed flutter valve indicated in Figure 3v of the drawings, and

Figure 14 is a section as on line 14-14 of Figure 10.

In the drawings in which similar characters of reference are employed to denote corresponding parts throughout the several views the number 25 designates the main bed of the machine formed with the longitudinally extending ways 26 and 27 which slidably support the Work table 28 for movement longitudinally of the bed to tra-verse the Work with respect to the grinding wheel. The bed is further formed with a rearward extension 29 having the Ways 30 slidably supporting the grinding wheel carriage 31 which has journaled therein the counter-shaft 32 Iand grinding Wheelspindle 33 bearing the grinding wheel 34.

'I'he main power for driving the grinding wheel and imparting the various movements to the table and wheel slide is preferably furnished from a suitable prime mover such as the motor 35 having a shaft 36 provided with a drive pinion 37 which through chain 38 drives shaft 39, from which a belt 40 transmits power to the shaft 32. 'Ihe coupling between shafts 32 and 39 is such that the necessarily limited back and forth movement may be given the wheel slide Without effecting the drive of the parts, due to the swinging of belt 40 about shaft 39 as a center during such adjusting movement. In addition a chain or other drive connection 41 extends forwardly into the bed 25, driving sprocket lo-the constant displacement pump 53.

42 for actuation of the pump members, which control the hydraulic .actuating circuits for the respective slides. This drive includes a coupling clutch 43 by which power is transmitted from pinion 42 to shaft 44 provided with the drive pinion 45 and the clutch face 46. Drive pinion 45 in turn actuates gear 47 of sleeve 48 journaled on the stub shaft 49 and having a pinion 50 normally in mesh with gear 51 on shaft 52 of Disposed coaxially with shaft 44 is shaft 55 of the variable displacement pump 56 which controls the movement of the table at a variable rate dependingV upon the rate of flow through said pump. This shaft has a splined portion on which is slidably mounted gear 54 having a spool 58 engaged by shifter yoke 57 actuable by handle 57 on the front of the machine. When shifted to the left clutch face 59 on gear 54 inter-engages with clutch face 46 on shaft 44 to drive the variable displacement pump at its normal rapid rate. To enable the rate of actuation of the pump to be slowed down and thus permit a ne adjustment of slow table traverse movements such as desirable for example, in performing 'truing operations, gear 54 may be shifted to the right as indicated in Figure 6 to mesh with pinion 50. It will be understood the variable displacement pump may be of any standard commercial type and preferably such that a lateral displacement or variation in ecoentricity of the rotor will serve A to vary the rate of flow therethrough. This displacement may be controlled by a rotary actuating cam 60 operated through miter gears 61 and knurled Wheel 62 projecting from the front of the machine, and provided with an indicator point 63 cooperating with a dial 64 on the control plate of the machine for indicating the adjustment thereof.

'projecting fromthe front of the machine and is carried by-sleeve 68 pivoted to one arm of the bell crank lever 69 secured as at 70 to the control plate 71. The other arm of the bell crank carries a roller 72 riding in slot 73 of plunger 74 which projects upwardly from control plate 71 adjacent the edge of the table and is adapted to be depressed by the reversing dogs 75 just prior to the engagement of the reverse dog with the table reverse lever 76.

The general normal cycle of operation of the table should be best understood by reference to diagrammatic view in Figure 3 considered in conjunction with the valve structural details particularly brought out in Figures 10, 11 and 12.

'I'he table itself is shown as provided with the rack 77 on its under surface having eshing therewith the drive gear 78 which isselectively rotatable either manually by pinion 79 or power actuated by cooperative engagement of piston rack 80 with gear pinion 81. Rack 80 is carried by the ends of the double piston rodv 82 intermediately provided with piston 83 movable in cylinder 84. The purpose of this specic construction is to multiply the movement imparted to the table so that the mechanism may satisfactorily be employed on long beds requiring maximum stroke of the grinding table, in

that a limited movement of piston 83 transmitted through rack 80 and pinion 81 to4 gear 78 will cause a much greater degree of movement of the grinder table.

It will of course be understood that while this multiplying mechanism has been shown as most advantageous, if a lesser degree of movement of the table is desired, the piston may be coupled direct with the grinder table and the cylinder 84 carried by the bed of the machine.

In either event the hydraulic actuation is the same in that the.

hydraulic conduits

85 and 86 are coupled with theI respective ends of the cylinder, the hydraulic circuit extending through valve casing 87 including reversing valve 88 to the lower supplemental portion of the casing containing starting and stopping valve 89 controlling pressure conduit 90-k and exhaust 91. In the normal operation of the machine, pressure of the desired amount is created by the constant displacement pump 53 and -is transmitted through conduit 90 to control valve 89. When in the position shown in Figure 11 this valve. will short circuit the pressure flow back through line 91 and an equalized pressure will act through

lines

85 and 86 against opposite ends of the piston. When the valve is moved to starting position, however, as shown in Figure 10 and diagrammatically illustrated in Figure 3, the pressure ilow from the constant displacement pump will be through conduit 90 valve 89 and conduit 86 to the right hand end of the piston cylinder creating an urge of the piston toward the left. At the same time conduit 85 will be coupled through valve 88 and valve 89 with conduit 91 leading to the variable displacement pump 56, the rate of discharge from the left hand end of the cylinder being therefore positivelycontrolled by the rate of passage of fluid through the variable displacement pump providing a locked system positively and definitely controlling the table movement of the machine.

It will of course be understood that suitable provision is made to prevent building up of undue pressure in either side of the hydraulic circuit. 'I'his may be accomplished by introduction of relief valve 92 in the pressure side of the circuit and a corresponding emergency relief valve 93 in the branch conduit 94 extending to the oil or hydraulic fluid reservoir 95 from a point in the return line ahead of the variable displacement pump.

It will be noted that in normal operation the variable displacement pump transfers the liquid from the discharge side 91 to the pressure side 90 thus causing a continuous circulation of oil within the closed system and with a pressure on the actuating or urge side in excess of that on the opposite side due to the action of the constant displacement pump. The reversal of direction of actuation, as has been mentioned, is determined by contact of the table dog 75 with the reversing lever 76 while the slowing down at the end of the table stroke prior to said -reversal is effected as by actuation of plunger 74, operating shift screw 65 to shift the variable displacement pump to a more nearly neutral position, thus reducing the flow through the discharge line.

Considering now the mechanism for producing proper feeding of the grinding wheel toward the work piece 95 when held between the head stock 96 and tail stock 97 on the work supporting slide or table, reference is made to diagrammatic view Figure 3 considered particularly in conjunction with the sectional view, Figure 2. From these views it will be noted that the grinding wheel head or slide 31 has a depending arm 98 provided with a bushing 99 in threaded engagement with screw 100. This screw has pinned thereon piston 101 movable in cylinder 102 in anaxial direction and also capable of rotation with the screw as effected through the series of gears 103 operable from the front of the machine by hand adjusting wheel 104 and shaft 105. This rotation serves to move the grinding wheel slide back and forth with respect to the piston in compensation for wheel wear and the like and to vary the position of the grinding wheel slide for reciprocations of a given amplitude as determined by the stroke of the piston 101. The hydraulic actuating system for the piston includes a conduit or passage 106 for conducting the actuating fluid to the front of the piston to retract the wheel and slide and a second conduit 107 to conduct the actuating fluid into the rear of cylinder 102 to forwardly urge the piston therein. .The actuating fluid for this urge is supplied from the general pressure line 90 fed by pump 53 through the pipe 108 as shown in Figure 2. A control valve casing 109 regulates the distribution of the actuating fluid to one end of the cylinder and its escape or discharge from the opposite end thereof. For example with the valve in the position shown diagrammatically in Figure 3 and in full lines in Figure 2, the

pressure side of the system is coupled through conduit 108, valve 110 and conduit 107 with the rear of cylinder 102 forwardly urging the piston. At the same time the front or relief side is coupled through conduit 106, valve 110 and pipe line 111 with the throttle valve 112 allowing discharge of the fluid through discharge line 113 to reservoir 95. 'I'he setting of the throttle valve determines the rate of escapement of the fluid and thus the speed of movement of the wheel toward the work. As an alternative proposition the valve 110 may be moved one step toward the right coupling line 106`direct with line 113 and thus permitting of rapid escape of the iiuid at the front of the piston cylinder and consequent rapid movement of the wheel toward the work. Similarly a complete forward or left-hand movement of the valve will couple pressure line 108 with the right hand branch 106' of passage 106 introducing the actuating fluid to the front of the piston to retract the wheel and at the same time couple line 107 direct with discharge passage 113 permitting this movement to be rapidly effected. Considering specifically the mechanism for automatic control of these several movements of the grinding wheel attention is invited to the fact that valve 110 has a forwardly extending operating rod 114 adjustably coupled by link 115 with the control handle 116 pivoted to the front plate 71 of the machine.

Handle 116 has the inwardly extending bell crank arm 117 carrying the pawl 118 for securing the lever in desired adjusted position. A spring 119 urges the bell crank arm downwardly and thus the main portion of the handle inwardly toward the bed of the machine. In its most inward position the link 115 and thus rod 114 and valve 110 are moved toward the lrear coupling pressure line 108 through the valve with passage 106 and thence through 106 directing the actuating fluid toward the forward side of piston 101. This pressure tends to rearwardly actuate the piston and consequently the wheel head slide. At the same time passage 107 is coupled through the valve 110 with the direct return line 113 permitting rapid rearward movement of the piston and wheel slide. This movement continues until flange or disc 120 on screw 100 contacts with the upper end of the intermediately pivoted lever 121 having a lost motion connection as at 122 with valve rod 114. As the parts inter-engage the continued rearward movement of flange 120 will transmit forward movement through rod 114 to valve 110 shifting the valve to such a point that the control pistons or flanges thereon simultaneously shut off the flow of fluid under pressure to the front of the piston and the discharge from the rear. In other words the valve will occupy a stop position preventing movement of the'wheel head slide in either direction and at the same time lever 116 will be rocked slightly forward. At this time 'the operator can withdraw4 the completed Work piece from the worksupporting slide for table and insert a newv work piece. This operation having been performed, by manual grasping and forward rocking of lever 116 the valve is moved to its extreme forward position. In this position the valve couples the pressure line 108 with passage 107 for forward actuation of the piston and wheel slide. At the same time the passage 106 is coupled with the open return line 113 permitting rapid inward feeding of the grinding wheel 34. As the handle is so moved, locking pawl 118 is retracted permitting latch member 123 under urge of spring pressed plunger 124 to move into a position over-lying stop 125 when the pawl 118 will inter-engage with shoulder 126 on the latch, locking the lever in this forward position against the action of spring 119.

It will be noted that the keeper is coupled by link 127 with the'lower endof intermediately pi'voted lever 128 whose upper end extends into the path of movement of the adjustable abutment 129 on the forward end of screw 100. Consequently as the wheel head slide and screw move forward the abutment will contact with the upper end of the lever swinging the lower end toward the rear of the machine and through link 127 withdrawing the keeper from engagement with the handle locking pawl. When this takes place the pawl will drop down on its stop 125, occupying the position shown in Figure 2 of the drawings. It is to be understood that a corresponding movement of the lever 116 takes place, shifting the valve 110 sufliciently to the rear to shut oil' flow through pipe 113 and directing same through line 111 containing the throttle valve 112 reducing the amount of flow so that the proper slow feed of the grinding wheel now ensues. The wheel will then be fed into the Work to the limit of movement of the slide as determined by interengagement of the end of the screw with stop bracket 130 where the parts will remain until handle 116 is manually shifted to reverse the valve and cause the retraction of the wheel head slide as previously described. It will be noted that abutment 129 is adjustable with respect to screw as for initial positioning of the machine to cause the tripping out action slowing down from rapid advance to feed to take place a predetermined distance before the grinding wheel slide reaches its limit of movesupporting pivot and thus the point at which upper end of lever 128 will contact with abutment 129 andv become effective to automatically change the wheel head speed from rapid advance to slow feeding action.

'I'he complete cycle of wheel head control mechanism just described is particularly adapted for in-feed grinding, which is to say grinding in which the work is stationary and the wheel is continuously fed directly into the work for the desired depth of cut. When the machine is utilized for traverse grinding or grinding in which the work or Work table reciprocates a different system of feed is required in that the wheel head is preferably given a limited amount of inward feed at each end of the table stroke and held in this position during the traverse of the work so that an equal amount of stock is removed circumferentially of the work throughout its length at each table stroke. To control the inward feed in this system ofgrind ing, line 111 is provided with a two Way cock 136 which in one position directs the flow through throttling valve 112 into the exhaust or reservoir line 113 and in its other position directs the flow through conduit 137 which discharges into supplemental valve casing 138 containing valve 139, preferably as an integral continuation of valve 88. Casing 138 has

ports

139 and 140 communicating through

lines

141 and 142 with the termini of escapement cylinder 143. This cylinder contains the shuttle piston or flutter valve 144 whose stroke is limited by abutment 145 on adjusting screw 146 having a knurled -operating head 147 projecting on the front plate 7l. The head is further provided with a dial 148 cooperating with a micrometer indicator 149 for determining the effective adjustment of abutment 145. Valve casing 138 is further provided with a port communicating with pipe 149 and a second port communicating with its branch 149 pipe 149 being continued over and discharging -into line 113.

In the operation of this mechanism Valve `88, being coupled with the table reverse lever 76, is reciprocated at each end of the table stroke. This correspondingly reciprocates valve 139 to alternately couple pressure inlet 137 with ports- 139' and 140 and at the same time to alternatively couple discharge line 149-149 with the other of these ports. Considering the back pressure or discharge fluid from the forward end of cylinder 102 as entering cylinder 143 through pipe 142, shuttle piston 144 will be forced toward the left as indicated to an amount limited by the position of abutment 145, thus allowing a predetermined amount of said fluid to enter the right hand end of the cylinder. -When the valve is reversed 142 will then be coupled with discharge line 149-149 and the pressure oppositely admitted through 141. As line 149 is under atmospherical pressure against the duid in the reservoir only, the measured amount of fluid previously admitted to the right i of cylinder 143 will be forced therefrom by movement of piston144 to the right and a corresponding amount will be permitted to enter the left hand end of the cylinder. The wheel head can then advance toward the work to the extent of the reduction in amount of uid thus escaping from the forward end of cylinder 102. I'his operation -is repeated at eachA reversal of the table until the wheel reaches its forward limit of movement. It will thus be seen that the piston 144 by its movement in the cylinder measures out the back pressure fluid from the main wheel head shifting cylinder, allowing the wheel to advance toward the work by prescribed increments whose amount is determined by the adjustment given to abutment 145 and that consequently there is a forwarding movement of desired amount imparted to the `wheel at each reversal of the table controlling valve.

It will of course be understood that the -reversal of the table may be effected either manually, or automatically by actuation of lever 76 on rock shaft 150 which is provided with the double end detent cam 151 cooperating with the

notches

152, 153 in the pair of actuating arms 154 which are urged together by the spring 155 and serve as the lever is rocked to snap it from one position to another and lock it in desired adjusted position. The connection between the lever and the valve proper 88 includes the rock arm 156 and actuator 157 engaged in slot 158 of head 159 on rock shaft 150. There is a lost motion between these parts permitting of initial movement of -the lever under influence of the appropriate table dog without shifting of the Valve coupled with a sudden impact positively throwing the valve from one position to the other if the lever and associate parts are swung under the influence.

control arm 161, movement of member 161 in one direction initiating the table traverse and in theI opposite direction producing a balanced pressure condition as previously described holding the table against movement for direct infeed grinding. In addition, the entire movement of the table and wheel-head slide as well as rotation of the work may be stopped through the use of the combined starting control lever 162 on rock shaft 163 which extends into the bed and carries the shifter arm 164 operating clutch shifter yoke 165 engaging spool 166 of clutch 43 for shifting same for disconnecting the drive to the parts from main drive sprocket 42 as particularly illustrated in Figure 6. Rock shaft 163 in addition carries the actuating arms 167-168 for the starting and stopping

switch plungers

169 and 170 respectively. 4These plungers control the circuit of motor 171 which drives the head stock 96 so that on shifting of the lever in one direction the motive power for the head stock will be stopped by breaking of the electric circuit therefor and simultaneously therewith power drive will be disconnected from the constant and variable delivery pumps preventing further hydraulic actuation of the machine. Under these conditions it will be evident that the main Vdrive motor 35 may be left in operation or that the circuit therefor may also be coupled with the

switch plungers

169 and 170 for complete control of the actuation of the machine from the single lever. as may be preferred.

As was mentioned above the work table 28 may be reciprocated manually when the pinion 79 is shifted into engagement with gear '1 8.

vThe pinion 79 is provided with a groove 175 in which is received a shifting shoe 176 carried by control arm 161. This control arm 161 is pivotally connected to lever 177 which controls the movement of the starting and stopping valve -89 as well as the shifting of gear pinion '79 on shaft '78 into and out of engagement with gear 78. Shaft 178 has a gear connection 179 with hand wheel 180 whereby the table may be manually shifted across the face of the grinding wheel.

From the drawings it will be noted that the manual means and the power means for reciprocating the table are never simultaneously in operating connection, but that when the lever 177 is actuated about its pivot 181 toward the bed of the machine the manual means are disconnected and the power means connected, and conversely, when the lever is moved away from the bed manual means is connected and the power means disconnected.

From the foregoing description the general operation of the present improved hydraulically controlled grinding machine should be readily understood and it will be seen that there has been provided a machine particularly adapted for either traverse or plunge cut grinding purposes in which the maximumv length of table movement may be effected with minimum length of piston or piston rod parts; in which the rate of traverse of the table when utilized for traverse grinding may be readily varied within wide limits and with a smooth and uniform movement in which extreme smoothness of reversal of the table may be effected due to the automatic slowing down of the rate of table movement prior to actuation of the automatic re-E versing mechanism therefor; and in which the rate of relative feeding movement between the grinding wheel and work may be automatically hydraulically controlled and properly accurately effected at the end of each relative traversing stroke of the parts.

It will further be noted that an improved semi-automatic cycle of grinding Wheel movement has been provided which is equally adapted for use in conjunction with both forms of grinding and which serves to cause a rapid relative approach of the grinding wheel and work, followed by a slow feeding movement of properly controlled nature and an ultimate limitation of the feeding movement suceeded if desired by an automatic rapid separating of the parts when the prescribed grinding has been completed. Y

It will further be noted that the various unitary portions of the machine such as the feeding and retraction of the grinding wheel, the trav- 1 ersing movement of the table, the rotation or drive of the head stock may be independently controlled and 'started or stopped as desired or in which the functioning of all of said parts and the drive of the grinding wheel itself as Well may g be started or stopped by a single controlling member therefor.

-It is also to be noted that a machine has been provided in which the essential operations such as the relative feeding and retraction of work and grinding wheel in a direction controlling the amount and rate of stock remdval, and the relative traversing of the parts to control the extent of surface operated upon are all"hydraulically effected by a single pressure pump or source of power while individual rate .controlling means are provided governing the action of the ,several parts under impulse received from the common source of power. l

We claim:l

1. A- grinding machine including a bed and a wheel slide movable on the bed, hydraulically actuable means for shifting the slide on the bed. a control valvefor determining the rate and direction of movement of the slide on the bed,

a trip actuable means for automatically shifting the valve to reduce the rate of movement of the wheel slide in one direction, a manual means for additionally shifting the valve to reverse the dircction of movement of the slide, and additional trip controlled means actuable on said reverse movement of the slide for automatically shifting the valve to check all movements of the slide.

2. A grinding machine including a bed and a wheel slide movable on the bed, hydraulically actuable means for shifting the slide on the bed, a control valve for determining the rate vsaid reverse movement of the slide for automatically shifting the valve to. check all movements of the slide, and manually operable means for adjusting the position of the slide with respect to the hydraulic actuating means and trip controls therefor, whereby 'the position of Athe slide is varied for trip controlled reciprocations of the same amplitude.

3. A grinding machine including a bed, a work supporting table translatable on the bed, a grinding wheel slide movable on the bed in a direction toward and from the table, hydraulically operated means for imparting a reciprocating movement to the table, additional hydraulically operable means for moving the wheel slide in a direction toward and from the table, common means for supplying actuating fluid to said hydraulically actuable mechanisms, a variable displacement pump in the table hydraulic circuit for controlling the rate of discharge of said circuit and consequently the rate of movement of the table, and independent throttling means in the grinding wheel slide hydraulic circuit for variably determining the maximum rate of discharge of said circuit and consequently the rate of movement of the grinding wheel slide.

4. A grinding machine including a bed, a work supporting table translatable on the bed, a grinding wheel slide movable on the bed in a direction toward and from the table, hydraulically operated means for imparting a reciprocating movement to the table, additional hydraulically operable means for moving the wheel slide in a direction toward and from the table, means for supplying actuating fluid to said hydraulically actuable mechanisms, a variable displacement pump in the table hydraulic circuit` for co'ntrolling the rate of movement of the" table, an independent throttling means in vthe grinding wheel slide hydraulic circuit for variably determining the maximum rate of movement of the of, and additional means for varying the speedv grinding wheel slide, a supplemental hydraulic return line 4for the grinding wheel circuit and meansA for selectively completing the circuit inclusive or exclusive of the throttling device to vary the rate of movement of said slide.`

5. A grinding machine including a bed and table reciprocably mounted thereon, a grinding wheel on the bed, means for imparti relative feeding movement to the grinding w el and table to determine the rate of stock removal from a work piece on the table, an hydraulically operable mechanism for .effecting said relative movement including acylinder and contained piston one of said partsA being secured to the bed and the other to a movable member, a'hydraulic circuit for introducing actuating uid into one end of the cylinder and conducting it from the opposite end of the cylinder, an escapement mechanism in the discharge line, and means for eiecting actuation of the escapement mechanism as the table reaches a prescribed limit by movement in one direction.

6. An hydraulically actuated grinding machine including a bed, a table reciprocable thereon, means for hydraulically reciprocating the table including a cylinder and piston intermediately f movable in the cylinder, one of said parts being rigidly secured to the bed and the other operatively associated with the table, and means for controlling the relative movement of piston and cylinder and thus movement of the table on the bed comprising a hydraulic circuit including a constant delivery pump for supplying actuatingr iluid to one end of the cylinder and a variable delivery pump controlling the flow of fluid from the opposite end of the cylinder, means for varying the rate of flow of iiuid through the variable delivery pump at a given speed of rotation thereo! rotation of said variable delivery pump.

'7. An hydraulically actuated grinding machine including a bed, a table reciprocable to decelerate the rate of translation of the movable member. prior to reversal thereof.

10. A grinding machine mechanism including a bed or support and a slide movable thereon, a piston rod coupled with the slide for a'ctuation thereof, a piston coupled with the-rod, a rate and direction determining valve for controlling the movement of the piston, releasable means-for locking the valve in position for rapid actuation of the piston in one direction, means for shifting the valve to decelerate the rate of movement of the slide and a controlling device extending into the path of movement of the piston rod and engageable thereby to render said valve shifting means operative.

11. In a machine of the character described, the combination with a bed or support, of a wheel head carriage slidably mounted thereon, a piston coupled with the carriage, an hydraulic system for actuating the piston in reverse directions including a single control valve for varying the rate and direction of movement of the carriage, means for shifting the valve to initiate the movement of the piston in a given direction at a given rate, means for resiliently actuating the valve to reduce the rate of movement of the carriage in said given direction means for locking the valve against said resilient actuation, release mechanism operable by thereon, means for hydraulically reciprocating rmovement 0f the carriage to disengage the lockthe table including a cylinder and piston intermediately movable in the cylinder, one of said parts being rigidly secured to the bed and the other operatively associated with the table, and means for controlling the relative movement of piston and cylinder and thus movement of the table on the bed comprising an hydraulic circuit including a constant delivery pump for supplying fluid to one end of the cylinder and a variable delivery pump controlling the ilow of fluid from the opposite end of the cylinder, means for automatically reversing the coupling of the constant and variable delivery pumps with the cylinder to reverse the direction of movement of the table, and means for automatically decreasing the flow of fluid through the variable delivery pump prior to the action of said reversing means.

8.` A grinding machine of the character described including a bed, a table reciprocable on 4the bed, a grinding wheel movable toward and ing mechanism whereby resilient actuation of the valve is effected, adjustable means for determining the timing of said release with respect to the movement of the carriage, and means for shifting said valve to reverse the direction of movement of the piston and carriage.

12. In agrinding machine, the combination with a bed or support, of a Work supporting member, a wheel supporting member, said parts being mounted for relative feeding movement to produce proper stock removal from the Work piece, and means for controlling said relative feeding movement comprising an hydraulic system including a piston intermediately mounted in a double end cylinder, means for supplying an actuating medium to one end of the cylinder, a discharge conduit extending from the opposite end of the cylinder, and a measuring device for controlling the escape of actuating medium through the conduit, including a cylinder, a shuttle member therein, and means for alternately directing the escaping iluid to the opposite ends of the cylinder whereby the cubical displacement o'f the shuttle member determines the increments of escape of the iiuid through the conduit.

13. In a grinding machine, the combination with a bed or support, of a work supporting member, a wheel supporting member, said parts being mounted for relative feeding movement to produce proper stock removal from the work piece, and means for controlling said relative gfeding movement comprising an hydraulic system including a piston intermediately mounted in a double end cylinder, means for supplying an actuating medium to one end of the cylinder, a discharge conduit extending from the opposite end of the cylinder, a measuring device for controlling the escape of actuating medium through the conduit, including a cylinder, a 'shuttle member therein, and means for alternately directing the escaping uid to the opposite ends of the cylinder whereby the cubical displacement of the shuttle. member determines the increments of escape of the fluid through the conduit, and means for variably determining the amount of movement of the shuttle member to vary the amplitude of individual feeding movements as controlled thereby.

14. A cylindrical grinding machine including a. bed or support, a work holding table mounted on the support for translation relative thereto, a grinding wheel carriage slidably mounted on the support for feeding movement toward and from the work support, and an hydraulic control system for said parts including a common source of actuating uid for the slide and table, a variable displacement return pump for controlling return of actuating fluid and thus the rate of movement of the table transversely of the grinding wheel, an actuating piston for the grinding wheel carriage, and a plurality of selectively couplable control mechanisms for said rpiston including a fluid escapement conduit, a lthrottle controlled conduit and an escapement mechanism, whereby rapid advance or return of the grinding wheel, slow or intermittent movement thereof may be effected.

15. A cylindrical grinding machine comprising a work support, a rotatable grinding wheel, a grinding wheel slide therefor, a cross feed screw operatively connected to the slide, manually operable mechanism for turning the cross feed screw to feed the grinding wheel into the work, a fluid pressure mechanism including a motor operatively connected to move the screw bodily endwise and quickly move the wheel towards the work, and a stop to locate the wheel adjacent to the work.

16. A cylindrical grinding machine comprising a work support, a rotatable grinding wheel,

-a grinding wheel slide therefor, a cross feed screw operatively connected to the slide, manually operable mechanism for turning the cross feed screw to feed the grinding wheel into the work, a fluid pressure mechanism including a, motor operatively connected to move the screw bodily endwise and thereby quickly position the wheel adjacent to the work, said motor having a movable part connected to the screw, means including a stop for limiting the endwise movement of said screw in one direction, and means for so controlling said fluid pressure mechanism as to maintain a constant pressure on said stop to hold the feed screw against endwise movevment while the same is being turned to effect the grinding feed.

17. In a machine tool organization the. combination of a bed, a tool carriage mounted thereon for movement relative thereto including a screw rod, means for rotating the screw for effecting adjustment of the carriage, hydraulic means for axially shifting the screw rod for adjusting the position of the carriage relative to the bed, said hydraulic means being adapted to shift the carriage at rapid and slow rates in sequential order, and trip means for changing the rate of movement of the carriage.

18. In a grinding machine of the class described the combination with a bed, and a grinding wheel carriage mounted thereon for movement relative thereto, of hydraulic means for effecting said movement of the carriage at rapid and slow rates including a piston operatively connected with the carriage, an hydraulic medium for shifting the piston, a conduit for the medium, a valve for alternately directing the medium from the conduit to opposite ends of the piston and for connecting the other end of the piston with a throttled or an unthrottled return conduit, and trip controlled means operable by the slide for shifting the valve to direct the exhaust medium successively through the unthrottled and throttled discharge conduits.

19. In a grinding machine of the class described the combination with a bed, and a grinding wheel carriage mounted thereon for movement relative thereto, of hydraulic means for effecting said movement of the carriage at rapid and slow` rates includingl a piston operatively connected with the carriage, an hydraulic medium for shifting the piston, a conduit for the medium, a valve for alternately directing the medium from the conduit to opposite ends of the piston and for connecting the other end of the piston with'a throttled or an unthrottled return conduit, and trip controlled means operable by the slide for shifting the valve to direct the exhaust medium successively through the unthrottled and throttled discharge conduits, comprising a valve stem extending from the valve, a lever connected with the stem, yielding means tending to actuate the lever in one direction and shift the valve, a latch tensioning the yielding means, and means operable by the slide for releasing the latch and thereby the yielding means.

20. In a grinding machine of the class described the combination with a bed, and a carriage mounted thereon for movement relative thereto, of hydraulic means for effecting said movement including a piston operatively coupled With the carriage, an hydraulic medium, means for circulating the medium under pressure for actuating the piston, a valve for connecting the medium alternately with opposite sides of the piston for reversely actuating the same, the valve connecting the idle side of the piston when moving in one direction for selective discharge through an unthrottled or a throttled conduit, means for automatically shifting the valve to direct the exhaust medium sequentially through the unthrottled and throttled conduits including yieldable means for shifting the valve, a latch normally preventing movement of the valve by the yieldable means, a trip operable by the carriage for releasing the latch and the yieldable means. and means for varying the point at which the automatic shifting of the valve takes place including a screw shaft, a nut on 4the shaft to which the latch is pivoted, and means for rotating the screw.

21. In a grinding machine of the class described the combination with a bed, and a carriage mounted thereon for movement relative thereto, of hydraulic means for effecting said movement including a piston operatively coupled with the carriage, an hydraulic medium, means for circulating the medium under pressure for actuating the piston, a valve for connecting the medium alternately with opposite sides of the piston for reversely actuating the same, the valve connecting the idle side of the shifting the valve to direct the exhaust medium sequentially through the unthrottled and throttled conduits including yieldable means for 1 shifting the valve,.a latch normally preventing lmovement of the valve by the yieldable means,

a trip operable by the carriage for releasing the latch and the yieldable, means, means for varying the point at which the automatic shifting of the valve takes place including a screw shaft, a nut on the shaft to which the latch is pivoted, means for rotating the screw, and indicating means for accurately positioning the latch.

22. In a grinding machine of the class described the combination with a bed, and a Work supporting tablemounted thereon "for movement relative thereto, of hydraulic means for effecting the translation of the table comprising a piston and cylinder mechanism one of which is movable and the other fixed, a rack adjustingv the rate of discharge of the variable delivery pump for thereby varying the rate of movement of the table.

23. In afgrinding machine of the class described the combination With abed, and a work supporting table mounted thereon for movement relative thereto, of hydraulic means for effecting the translation of the table comprising a piston and cylinder mechanism one of which is movable and the other fixed, a rack movable with said movable member of the piston and cylinder mechanism, a rack on the table, transmission gearing between the racks whereby the movement of the piston and cylinder rack is increased as table movement, an hydraulic pump connected with one end of said piston and cylinder mechanism for creating an hydraulic urge on the movable member, a variable displacement pump connected with the other end of said mechanism for determining the rate of actuation thereof, means projecting beyond the forward wall of the bed for adjusting the rate of discharge of the variable delivery pump for thereby varying the rate of movement of the table, means for reversing the connections of the pumps for reversing the movement of the table, and means for temporarily reducing the discharge from the variable liplacement pump prior to each reversal of the 24. In a grinding machine of the class described the combination with a bed, and a Work supporting table mounted thereon for movement relative thereto, of hydraulic means for effecting the translation of the table comprising a piston and cylinder mechanism one of which is movable and the other fixed, a rack movable' with said movable member of the piswhereby the movement of the piston and cylinder rack is increased as table movement, an

hydraulic pump connected with one end of said piston and cylinder mechanism for creating an hydraulic urge on the movable member, a variable displacement pump connected with the other end of said mechanism for determining the rate of actuation thereof, means projecting beyond the forward wall ofthe bed for adjusting the rate of discharge of the variable delivery pump for thereby varying the rate of movement of the table, means for reversing the connections of the pumps for reversing the movement of the table, and means for temporarily reducing the discharge from the variable displacement pump. prior to each reversal of the table, said means comprising a depressible plunger operable by the table, and a pump adjuster operatively connected with the plunger.

25. A grinding machine comprising a base, a slidable table thereon, a piston and cylinder mechanism arranged to move said table, a fluid pressure system to admit fluid under pressure to either end of said cylinder, a valve mechanism in said system arranged to control the rate of fluid flow in said system, and means actuated by movement of said table to operate said valve to diminish the fluid flow from said cylinder when the table has'reached a predetermined position and thereby cause the table to move thereafter at a definite but slower speed.

26. In a grinding machine the combination of a bed, a work supporting table carried thereby and translatable longitudinally thereof, agrinding wheel carriage carried by the bed and movable transversely thereof toward and from the Work supporting table, means for effecting said translation including an hydraulic reciprocating motor, an hydraulic medium for actuating the motor, means controlling the flow of the mediiun to effect a movement of the carriage at a rapid rate, means controlling the flow of the medium to actuate the carriage at a constant slow rate, means for controlling the flow of the medium to actuate the carriage intermittently at a slow rate, means to automatically direct the flow of the medium from the rapid rate controlling means to either of the slow rate controlling means, and means for determining which of the slow rate controlling means is to be used.

27. In a grinding machine thev combination of a bed, a grinding wheel carriage carried therebyv and movable transversely thereof, an hydraulically actuated reciprocating motor for effecting said movement of the carriage, an hydraulic medium for the motor, a valve controlling the flow of the medium, manual means for shifting the valve to initiate a movement of the carriage at a rapid rate in one direction, means operable by the Acarriage for shifting the valve to slow down the movement thereof in the said direction and minutely adjustable means for determining the point at which the change in movement of the carriage from the rapid rate to the slow rate takes place.

28. In a grinding machine the combination of a bed, a grinding wheel carriage carried thereby and movable transversely thereof, an hydraulically actuated reciprocating motor for effecting said movement of the carriage, an hydraulic medium for the motor, a valve controlling the flow of the medium, manual means for Vshifting the valve to initiate a movement of the carriage at a rapid rate in one direction, means operable by the carriage for shifting the valve to slow down the movement thereof in the said direction, minutely adjustable means for determining the point at which the change in movementl of the carriage from the rapid rate to the slow rate takes place, and means for varying the slow feeding rate of movement whereby the grinding wheel may be fed into the work at dierential rates.

`29. In a grinding machine the combination of a bed, a reciprocating work supporting table carried thereby, a grinding wheel carriage carried by the bed movable transversely thereof toward and from the work supporting table at a rapid rate and a slow feed rate, means for controlling the actuation of the carriage toward the table to feed the grinding wheel into the work at a constant slow feeding rate, means for controlling the actuation of the carriage toward the table to intermittently feed the grinding wheel into the work, and means for simultaneously connecting one of said feed controlling means with and disconnecting the other from the carriage.

30. In a grinding machine the combination of a bed, a reciprocating work supporting table carried thereby, a grinding wheel carriage carried by the bed movable transversely thereof toward and from the work supporting table at a rapid rate and a slow feed rate, means for controlling the actuation of the carriage toward the table to feed the grinding wheel into the work at a constant slow feeding rate, means for controlling the actuation of the carriage toward the table to intermittently feed the grinding wheel into the work, means for simultaneously connecting one of said feed controlling means with and disconnecting the other from. the carriage, and additional means for determining the rate of the slow feed movement of the carriage when being constantly fed and the amount of movement of the carriage when being intermittently fed.

31. In a grinding machine of the class described the combination of a bed, a slide mounted thereon for movement relative thereto at fast and slow rates in a given direction, hydraulic means for effecting the movement of the slide including a valve for controlling the speed thereof, a trip member carried by and movable with the slide, latch means in the path of movement of the trip member for holding the valve in one position, and yielding means for shifting the valve to a second position upon release thereof by the trip mechanism.

32. In a grinding machine of the class described the combination of a bed, a grinding wheel carriage movable thereon at rapid and feeding rates through a given zone, hydraulic means including a valve for effecting the movement of the carriage, latch means for holding the valve in one position to effect the rapid movement of the carriage, yielding means for shifting the valve to a second position upon release of the latch means to eiIect the movement of the slide at a slow rate, trip means carried by the slide for releasing the latch, means for varying the effectiveness of the latch means and thereby varying the point at which the change from rapid to slow takes place, and stop meansl for limiting the reverse movement of the carriage.

33. In a grinding machine of the class de- :scribed the combination of a bed, agrinding wheel carriage movable thereon at rapid and feeding rates through a given zone, hydraulic means including a valve for effecting the move- .lease of the latch means to effect the movement ment of the carriage, latch means for holding the valve in one position to effect the rapid movement of the carriage, 'yielding' means .for shifting the valve to a second position upon reof the slide at a slow rate, trip means carried by the slide for releasing the latch, means for varying the effectiveness of the latch means and thereby varying the point at which the change from rapid to slow takes place, stop means for limiting the reverse movement of the carriage, and means for changing the zone through which' the movement of the slide takes place without changing the point in said zone at which the change in movement occurs.

34. In a grinding machine of the class described the combination of a bed, a grinding wheel carriage mounted thereon for movement relative thereto at a continuous slow rate or at an incremental intermittent rate, hydraulic means for eiectingsaid movement of the carriage, a work supporting table mounted on the bed for reverse translation relative thereto and for controlling the incremental intermittent feed of the carriage, a valve in the hydraulic means 1N for determining whether the continuous infeed or intermittent feed is to be employed, a valve in the hydraulic circuit for determining the rate of the continuous feed, a valve in the circuit for determining the amount of incremental feed, means for effecting and determining the adjustment of each of said valves, and a valve casing carried by the bed for containing said valves.

35. In a grinding machine the combination of a bed, a grinding wheel carriage carried thereby and shiftable relative thereto, an adjusting screw having a threaded engagement with the carriage, the screw having a splined portion thereon,

a gear connected with the screw through the i splined portion whereby the screw is rotated with the gear while the'screw may be axially shifted relative to the gear, a piston on the screw, and means for rotating the gear for adjusting the slide at a slow rate and for shifting the piston for moving the slide at a rapid rate independent of the movement thereof by the gear.

36. In a grinding machine the combination of a bed, a slide carried thereby and movable relative thereto at a slow rate and at a rapid traverse ratefa screw rod having a threaded connection with the slide adapted to be rotatably actuated for moving the slide at a slow rate, a piston carried by the screw rod adapted to be axially shifted for moving the slide at a rapid rate, and means for actuating the screw rod rotatably and axially 1m at the proper rates.

37. In a grinding machine of the class described the combination of a bed, a grinding wheel carriage mounted thereon for movement relative thereto, a work supporting table on the bed for supporting a work piece in the line of movement of the carriage, hydraulic means for effecting thev movement of the carriage at rapid and feeding rates toward the table, and means for determining the point of change in speed of the carriage comprising a member movable within the carriage, a trip mechanism in the line of movement of the member, latch means normally holding the trip mechanism against operation, and yieldable means operable upon the operation of the trip mechanism to render the latch mechanism inoperative.

HANS ERNST. HERMAN R. IBLER. l.