US703032A - Steam-engine. - Google Patents

Description

No. 703,032. Patented 'June 24, I902... C. C. WUBTHINGTIJN.

STEAM ENGINE. (Application filed Nov. 27, 1899.)

7 Sheets-Sheet I.

(No Model.)

17111671207": WW i WQ It Patented lune -24, I902;

0. c. womnmmon.

STEAM ENGINE.

(Application fihd Nov. 27, 1899.]

7 Sheeir-Sheet 2.

(No Model.) 7

6 a a a a W Isl THE mars PETER c0. moYau'r No. 703,032. Patented June 24, I902. C. .8. WORTHINGTDN.

STE All ENGINE.

(Application filed Nov. 27, 1898.) (Hp Model.) 7 Sheets-S het 3.

Q ma I'll ref No. 703,032. Patented June 24, I902. C. B. WOBTHINGTON.

STEAM ENGINE.

(Application filed Nov. 27, 1899.)

7 Sheets- Sheet 4,

(No Model.)

THE nofims PETERS cu, pnmoumnv. WASHINGTON, u. c,

- Patented June 24, I902.,

C. C. WDRTHINGTUN.

STEAM ENGINE.

(Aplication filed Nov. 27, 1899.)

(No Model.)

III.

7 Sheets-Sheet 5.

"m: Noam FEIERS co, PHOTO-LITHQ, WASHINGTON, 01c.

No. 703,032. Patented Ju e 24; I902. c. c, wunmmmou STEAM ENGINE.

(Application filed Nov 27, 899., No Model.) 7 Sheets$heet 6:

Ewe/175i" n4: NORRIIS runs 00.. wmo-Lrruu. wxsmum'ox, u. c.

No. 203,032: Patented June 24, I902.

C. C. WORTHINGTON.

STEAM ENGINE.

(Application filed Nov. 27. 1899. r (No Model.) 7 Sheets-Sheet 7.

UNITED STATES PATENT @FFICE.

CHARLES C. \VORTHINGTON, OF DUNNFIELD, NE\V JERSEY.

STEAM-ENGINE.

PECIFICATION forming part of Letters Patent No. 703,032, dated June 24, 1902.

Application filed November 27, 1899. Serial No. 738,367- (No model.)

To all whom it may concern:

Be it known that 1, CHARLES C. WORTHING- TON, a citizen of the United States, residing at Dunnfield, county of Warren, and State of New Jersey, have invented certain new and usefullmprovementsin Steam-Engines, fully described and represented in the following specification and the accompanying drawings, forming a part of the same. I

The especial object of the present invention is to provide a double-cylinder singleacting vertical pump especially adapted for air or gas, with the steam-valves controlled by the pistons on the opposite sides so as to secure a uniform action and constant suction without employing a beam, as in such pumps heretofore in use; but the broader features of myinvention may be applied also in other classes of engines employing a plurality of steam-cylinders with the pistons timed differently.

In double-cylinder single-acting air-pumps, which are used largely in connection wit-h condensers and in similar service, when a substantially constant withdrawal of the fluid is desirable it is important that as one plunger goes down and does little or no work the other plunger should be making an upstroke and doing full work and that the two plungers should be controlled so as to assure the desired relative timing. Heretofore this result has been secured by the use of a heavy beam pivoted between and connecting the piston-rods on the two sides of the pump, thus rigidly connecting the opposite plungers and assuring their accurate timing. Such constructions are objectionable, however, especially because a heavy strong beam must be used, with journals and links of sufficient size and strength to bear the whole load, so that the construction is necessarily heavy, cumbersome, and wasteful of power, and on account of friction and of the side thrust and resulting strain upon the parts of the pump as the beam passes its center. I obtain substantially the operation of such apnmp, while at the same time avoiding all side thrust and the use of heavy parts connecting the opposite sides of the pump, by providing means for operating the valves of the steamcylinders in such a manner that one of the pistons shifts or causes the shifting of the valve on the opposite side at or near the end of the stroke of this piston, as in various classes of double-cylinder engines now well known, while the other piston shifts or causes the shifting of the valve on the opposite side at or near the commencement of the stroke of the piston, and each piston shifts or causes the shifting of the valve on the opposite side, so as to start the engine on that side on its stroke in the opposite direction to that in which the piston that shifts or causes the shifting of the valve will be moving during the greater part of its corresponding stroke.

Many different forms of valve-movements may be used for securing the desired operation of the valves of the two cylinders; but I preferably employ connections between each of the pistons and the valves on the opposite side of the engine by which the valves are directly operated by the movement of the pistons on the opposite sides and providing lost motion between the pistons and the valves, so that one piston takes up the lost motion between it and the opposite valve during the first part of the stroke of'the piston, and the other piston takes up the lost motion between it and the opposite valve during the latter part of the stroke of the piston, the operation of the lost-motion connections thus being reversed on opposite sides. With such a construction it is obvious that the connections between the opposite sides of the pump need be only of such size and weight as to secure the movement of the steam-valves and that no side strains need be caused,so that such connections may be very light, with corresponding economy in construction and operation. Such constructions also secure this important advantage over beam constructions: that the valves are directly and positively operated instead of being thrown-by the pressure of the steam or other fluid or by weights or springs, as in beam-pumps. While I prefer, however, that the valves shall be connected to moving parts on the opposite sides of the pump, so as to be actuated directly by the pistons on the opposite sides, as I thus secure a more positive control of the operation of each side of the engine and greater accuracy and certaintyin the timing of the two sides relatively to each other, I may use means by which the valves on one or both sides of the pump are controlled but not actuated directly by the pistons of the opposite sidesas, for instance, by the use of fluid-pressure for operating the valves controlled by the opposite side of the pump.

As a full understanding of the invention can best be given by a detailed description of constructions embodying the same, such a description will now be given in connection with the accompanying drawings, forming a part of this specification and showing means of the preferred form for carrying out my invention and certain modified forms thereof, and the features forming the invention will then be specifically pointed out in the claims.

In the drawings, Figure 1 is a front elevation of avertical air-pump embodying the invention with the preferred form of means for actuating the valve of one side at the beginning of the stroke of the piston on the other side. Fig. 2 is a side elevation of the same. Figs. 3 and 1 are enlarged central sections of the steam-cylinders on the opposite sides, showing the parts in-the same position as in Figs. 1 and 2. Figs. 3 and 3 are detail side views of the valve-movement of valve in different positions, Fig. 3 corresponding in position to Fig. 3. Figs. 4: and P are similar views of the valve-movementof valve 0', Fig. 1 corresponding in position to Fig. 1, but looking in the opposite direction. Figs. 5 and 6 are views similar to Figs. 3 and 4, but showing the pistons and valves of the two cylinders at the commencement of the next stroke after that on which they are moving in Figs. 3 and 4. Fig. 7is a plan view of the valve-movement in the position shown in detail in Figure 4. Fig. 8 is a detail horizontal section on the line 8 of Fig. 9. Fig. 9 is an end view of the valve-movement of Figs. 4 and 4 with the parts shown in central position as the crank passes the center in moving the valve in either direction. Fig. 10 is a partial view similar to Fig. 1, on an enlarged scale, showing a modified construction with a friction-disk for actuating the valve at the beginning of the stroke. Fig. 11 is a side elevation of the same with parts broken away to show the construction. Fig. 12 is a detail side elevation of one of the cylinders, looking to the left from theline 12 of Fig. 10, but showingthe parts in their position at the beginning of the next stroke after that on which the pistons are movin'gin Figs. 10 and 11. Fig. 13 is a detail end view ofthe friction-disk valve-movement, lookingin the same direction as Fig. 12. Fig. 14 is a central horizontal section on the line let of Fig. 13. Fig. 15 is a vertical section on the line 15 of Fig. 14. Fig. 16 is a front elevation of one of the cylinders,simi1ar to Fig. 10, show ing a modification in which a friction-roller construction is used for operating the valve at the beginning of the stroke. Fig. 17 is a view of this modification similar to Fig. 12 and with the parts in the same position. Fig.

18 is a view similar to Fig. 17, but showing the parts in the position they occupy at the shown in Fig. 18.

beginning of the next stroke after that on which the pistons are moving in Figs. 16 and 17. Fig. 19 is an enlarged end view of this friction-roller valve-movement'in the position Fig. 20 is a plan view of the same. Fig. 21 is a horizontal section of the same on the line 21 of Fig. 19. Fig. 22 is a front elevation showing a construction in which fluid-pressure controlled by the piston on the opposite side is used to actuate the valve at the beginning of the stroke, the parts being shown in the position they occupy as the piston on one side starts and the valve on the other side is about to be actuated to start the opposite side. Fig. 23 is a view similar to Fig. 22, but showing the parts in corresponding position in connection with the next stroke of the pistons.

Referring now particularly to the construction shown in Figs. 1 to 9, A A are the steamcylinders, and B B the corresponding pump cylinders on opposite sides of a vertical directacting air pump or compressor; 0, the induction-pipe, and D the exhaust-pipe, for the steam-cylinders, and E F, respectively, the suction and delivery of the pump, it being understood that the plunger on each side of the pump is single-acting, so as to deliver only on the upstroke of the pump, as usual in such constructions. The steam cylinders A A have the respective pistons G G connected directly to the plnngers by piston-rods g g. The respective steam-cylinders A A are provided with the usual induction and exhaust ports a b and a b, communicating, through the oscillating steam-valves c c, with the induction-pipe O for the admission ofsteam and with the exhaust-coves d d for the exhaust. It will be understood that the steam-valves c 0 may be valves of any suitable form and movement, but are shown as oscillating valves of a common construction.

As stated above,the valve on one side of the pump is actuated at the end of the stroke of the piston on the opposite side and the valve on the other side of the pump actuated at the beginning of the stroke of the first-mentioned side, so that the piston upon one side of the engine completes its stroke as it reverses the valve of the cylinder on the other side, and the piston on the other side then starts upon its stroke in the return direction and shifts the valve of the opposite side, so as to start the piston on that side in the return direction, the pistons on the opposite sides thus moving in opposite directions and one of the pistons starting slightly before the other, so as to reverse the piston on the other side as it commences its movement. I secure this result by the use of connections between the pistons and the valves on the opposite side of the engine provided with lost motion, respectively, during the first part and during the latter part of the stroke of the respective pistons, so that one piston shifts the valve on the opposite side at or near the end of the piston-stroke and the other piston shifts the valve on the side opposite to it at or near the beginning of the piston-stroke. In the construction shown the piston G of the cylinder A shifts the lever c of cylinder A at or near the end of the stroke of piston G and the piston Gr of the cylinder Ashifts the valve of cylinder A at or near the beginning of the stroke of piston G. This result is secured by the following means: The piston-rods g g on the opposite sides engage levers 1O 11 on rockshafts 12 13, mounted in the frame and provided with crank-arms 14 15, which are connected by links h h to cranks 2' 1', through which the respective valve-movements are actuated. The connections between the crankarms t 2' and the valves 0 c are the same in construction on both sides of the engine, except for the omission of a spring, as hereinafter pointed out, so as to secure the operation of the valve 0 at the beginning of the stroke of piston G and the operation of valve 0 at the end of the stroke of piston G, so that a single description of the construction will apply generally to both, and the same references will be used for corresponding parts on opposite sides of the engine.

Referring particularly to the detail views, Figs. 7 to 9, which show the construction in connection with valve 0, which is actuated at the beginning of the stroke of the piston Gr, and shown in section in Figs. at and 6, and with the valve-movement in end elevation in Figs. a and 4, the crank z" is pivotally mounted by stud 16 upon a second crank 17, which is mounted upon the hub or bracket 18, in which the valve-stem 19 turns, this crank 17 being keyed or otherwise secured to the valve-stem 19, so as to actuate the latter. The crank t is also pivotally connected by pin 20 to a sliding bar 21, which is secured to or formed into a casing 22 at one end and threaded upon the reduced end of the valvestem 19 by slot 1, which permits the movement of the bar 21 transversely to the valvestem. Within the casing 22 is a coiled spring 23, which bears against an adjustable screwplug 24 in the outer end of the casing and against an abutment 25, which rests against the side of the reduced end of the valve-stem 19, so that this spring acts to press the bar 21 transversely to the valve-stem to the right in the drawings, and thus tends to pull the crank t" in either direction from the central position (shown in Fig. 9) and hold it on either side of the central position, as shown in Fig. at or i", and the spring 23 is compressed in moving the crank "0 past the center from either of the positions shown in these figures. The crank 17 is provided with an arm 26 on the opposite side of the valve-stem from the crank i, which plays between abutments 27 28 on the fixed hub or bracket 18, these acting as stops to limit the movement of the crank 17 as it moves in opposite directions. This valve-movement acts as follows: As the crank t" is moved toward the center in either direction by the link h from its extreme positions the first movement of the crank tends to move the pin 20 away from the valve-stem 19 or to the left in Figs. at 4", which can be done only by drawing the bar 21 also to the left. This is resisted by the spring 23, and the resistance of this spring is suflicient so that instead of the spring being compressed the crank 4) will be held by the bar 21 in the position shown in Figs. 4 and 4 relatively to its pivot 16iand will move the crank 17 with it, the cranks t" and 17 pivoting upon the hub or bracket 18. This movement of the crank 17 shifts the valve 0 through its stem 19, to which the crank 17 is secured, and this movement continues until the valve has been fully shifted, when the arm 26 Will strike one of the abutments 27 or 28, thus positively stopping the movement of the crank17 and valve-stem 19, after which the continued movement of the piston G on the opposite side for the rest of the stroke will act through the link It only to rock the crank 2" upon its pivot 16, the spring 23 being compressed to permit this movement as the crank t" moves toward the central position, (shown in Fig. 9,) the bar 21 then moving to the left from the position shown in Fig. 4 or 4) to that shown in Fig. 9, and the spring 23 and bar 21 returning to one or the other of the extreme positions as the crank t completes its movement after passing the center, so that the parts are in position to repeat the action for moving the valve in the opposite direction at the beginning of the next stroke of the piston G.

As shown in Fig. 4, the valve 0 has been shifted into the position shown in Fig. 4 by the piston G as it commences its downstroke, and is now fully open for the upstroke of the piston G, the arm 26 having been brought into contact with the upper abutment 28, so as to stop the further movement of the valve, and the crank 2" will now move downward without operating the valve during the rest of the downstroke of piston G and at the end of this stroke be brought to the limit of its movement on the opposite side of the central position. As shown in Fig. 4", the crankarm t has commenced to move upward from its extreme lower position, the piston G having just started on its upstroke, and the crank t" is about to shift the valve 0 for the downstroke of the piston G, which shifting movement will be stopped by the arm 26 engaging the lower abutment 27, after which the crank-arm 2" will move onward without actuating the valve until it has reached its extreme upper position at the end of the upstroke of the piston G.

There is nothing peculiar in the action of the piston G upon the valve 0 in shifting the latter at or near the end of the stroke of piston G, and any suitable connection providing for lost motion at the beginning of the stroke of this piston may be used, many of which are now well known in connection with duplex and tappet motion pumps. For uni= &

formity of appearance and the cheapness and convenience resulting from duplicate parts, however, I have shown both sides of the pump illustrated in Figs. 1 to 9 as provided with the same valve-movement connections, as above stated, except that for securing the lost motion at the beginning of the stroke of the piston G, and the operation of the valve 0 at or near the end of the stroke of piston G, instead ofatornear the beginning ofits stroke, as above described, in connection with piston Gand valve 0 I omit from the valve-movement the spring 23 and abutment 25, by which is secured the resistance to the movement of the bar 21, which is required to move this valve 0 at the beginning of the movement of crank t in either direction. WVith this spring 23 and abutment 25 omitted the action is as follows in connection with the crank 't' and in operating the valve 0: As the crank 71 moves in either direction from its extreme position on either side of its central position the crank first moves the pin 20 away from the valvestem 10 or to the left in Figs. 3 and 3 which is permitted without strain on the valve-stem 19 by the slot 1, by which the bar 21 is threaded upon the valve-stem 19, so that the crank 71 is thus moved by the piston G at the beginning of the stroke of the piston without moviug the valve 0. This movement of the crank '5 without actuating the valve continues as the crank 1i approaches and passes the center, after passing which, of course, the crank moves the pin 20 toward the valve-stem 19 and the bar 21 to the right in the figures; but as the crank i approaches the limit of its movement as the piston G approaches the end of its stroke the end of the slot 1 next the pin 20 engages the end of the valvestem 19, so that the bar 21 cannot move any farther to the right upon the valve-stem, but is locked thereto by the engagement of the end of the slot 1 with the valve-stem, and the further movement of the crank '21 carries with it the crank 17 and valve-stem 19, so as to shift the valve at the end of the stroke of piston G. The arm 26 and abutments 27 28 are used also in this construction with valve 0, so as to assure the stopping of the valve 0 in proper position, although it will be understood that the arm and abutments are not absolutely essential in connection with this construction.

As shown in Fig. 3, the crank t has been moved into its extreme lower position by the piston G, which has now reached the end of its downstroke, as shown in Fig. 4, and the valve 0 has been shifted into the position shown in Fig. 3 and fully opened for the downstroke of piston G by the engagement of the end of the slot 1 with the valve-stem 19 and the resulting movement of the crank 17 and valve 0 with the crank 2'. As shown in Fig. 3 the crank 7 has been moved upward nearly to its extreme position by the piston G on its upstroke and has moved the bar 21 to the right, so that the end of the slot 1 bears against the end of the valve-stem 19, and the further movement of the crank t' as the piston G completes its stroke will shift the valve 0 from its position shown in Fig. 3 to that shown in Fig. 5 for the upstroke of the piston G. In both Figs. 3 and 3", therefore, the end of the slot 1 is shown as bearing against the end of the valve-stem 19; but in Fig. 3 the valve has been shifted at the end of the downstroke of piston G, while in Fig. 3 it is about to be shifted at the end of the next upstroke of piston G.

The general operation of the pump will be understood from a brief description in connection with the above description of the valve movement. As shown in the general views and Figs. 3 and 4, the piston G of cylinder A has just completed its downstroke, during the latter part of which it has shifted the valve 0 of cylinder A into the position shown in Fig. 3 for the downstroke of piston G, and the piston G has started on its downstroke and shifted the valve 0 of cylinder A into the position shown in Fig. 4, reversing the piston G for the upstroke, whichit is now starting upon. As the valve 0 of cylinderA is shifted so as to fully open the induction-port a to the upper end of the cylinder Abefore the piston G completes it downstroke, the piston G starts upon its downstroke, so that the pistons G G are moving for a short time in the same direction with the pistons G and G as, respectively, the leading and following pistons. It will be seen, however, that this movement of the pistons in the same direction is small, as the piston G completes its stroke immediately after or on fully opening the port ct of cylinder A, so that the movement of the two pistons G G is practically the movement of the pistons in a beam-engine that is, in opposite directions and simultaneously, so that a practically constant delivery is secured. The position of the parts of the valve movement corresponding to Figs. 3 and 4 is shown in Figs. 3 and 4, both valves 0 and 0 having just been shifted by their respective cranks 2' t" through the links and from the piston-rods g g on the opposite sides through levers 10 11, rock-shafts 12 13, crankarms 14 15, and links 7t 7t. As the pump continues its operation from the position shown in Figs. 1 to 4 the plunger in cylinder B delivers through the delivery F during the upstroke of the piston G, while the plunger in cylinder B takes suction during the downstroke of the piston G in cylinder A, the piston G starting on its upstroke almost immediately upon the termination of the upstroke of the piston G, so that there is little or practically no intermission in the delivery. As the piston G approaches the end of its upstroke it shifts the valve 0 of cylinder A from the position shown in Fig. 3 to that shown in Fig. 5, so as to open the port a at the lower end of the cylinder for the upstroke of the piston G, and as the piston G starts upon its upstroke at or just slightly before the piston G stops it commences to shift the valve c of cylinder A from the position shown in Fig. i to that shown in Fig. 6, so as to open the port a at the upper end of cylinderA for the downstroke of the piston G. In the position shown in Figs. 5 and 6 both valves are fully open, the piston G having moved a short distance on its upstroke and the piston G having started upon its downstroke as the valve 0 is shifted.

lVith the valve movement shown the pump may readily be run with the pistons on the respective sides, operating the valves on the opposite side at the same point in the stroke that is, with each piston operating the valve on the opposite side with lost motion between the piston and the valve during the first part of the stroke, as usual in double-cylinder pumps of various formsand the valve movement shown provides also for this operation of the pump in case, through accident, piston G fails to actuate the valve 0' at the beginning of the stroke. Thus if the spring and the abutment 25 be removed from the connection between the piston G and the valve 0 it is obvious that the valve 0 will be operated by piston G through the valve movement in the same manner as described in connection with the operation of valve 0 by the piston G. The piston G will then shift the valve 0 as the piston G reaches the end of its stroke in either direction, and the piston G will similarly shift the valve 0 as it approaches the end of its stroke in either direction, and the point in the stroke of pistons G G at which the valves 0 c are operated may readily be arranged by the construction or adjustment of the parts, so as to secure the operation desired when the pump is operated with no spring 23 applied in connection with the valve 0', as above described. It is obvious also that if the spring fail to act so as to secure the shifting of the valve 0' at the beginning of the stroke of the piston G the piston G will shift the valve 0 at the end of its stroke by the end of the slot 1 coming in contact with the end of the piston 19, as described above in connection with the operation of the valve 0, and the admission of steam to the piston G will certainly be controlled by the piston G to assure such a movement of the piston G as to maintain the pump in operation even though the spring 23 fail to act.

The connections between the piston G and the valve 0 for operating the latter at or near the beginning of the stroke of piston G may be widely varied, and many simple and efficient forms of such connections may be devised. I have shown in Figs. 1010 23 certain modified constructions employing some of the preferred forms of such connections, and these will now be described.

In Figs. 10 to 15 I have shown a construction in which the lost-motion connections are between the crank-arm 15 and link h, the latter being connected directly to a crank-arm 17 on valve-stem 19, so that the link h actuates the valve c positively through valvestem 1?). The lost-motion connections between the crank-arm 15 and the link h are as follows: The crank-arm 15 has a circular disk portion 29 at its end and carries a screwbolt 30, upon which is mounted next the face of the portion 25) a friction-disk upon the opposite side of which is a pressure-disk 31, by which the requisite pressure upon the triotion-disk 7c is secured by coil-spring 32 upon the screw-bolt 30, this pressure being adjustable by nut 33 outside the spring. Frictionpieces 2, of any suitable material, are preferably interposed between the adjacent faces of the friction-disk 7c and the disks 29 31. The friction-disk 7c is provided with an arm 34, to which the link 71 is pivotally connected by stud 35. The crank-arm 15 also carries arms 36 37, projecting into line with the arm 34 and on opposite sides of the latter, so as to come in contact with the arm 34: and positively move the link 72., connected to the latter, near the end of the movement of the crank -arm 15 in either direction, in case the arm 34 is not previously moved by friction upon the disk k,as hereinafter explained. The crank-arm 17 is provided with the arm 26 on the opposite side of the valve-stem 19 from the link 7z,and abutments 27 28 are used in connection therewith,as in the construction previously described. The disks 29 31 do not rotate upon the bolt 30, but the disk k is free to rotate thereon. For operating the valve 0 at or near the end of the stroke of piston G the usual lost-motion connection 70 is used between the link 71. and the crank 17 on valve-stem 19 of this valve. The general operation of this pump is the same as that of the pump described in connection with Figs. 1 to 9, the valves being operated as follows: As the piston G approaches the. end of its stroke in either direction it operates the valve 0 through link It and lost-motion connection 70, as usual in such constructions. As the piston G commences its stroke in either direction the crank-arm 15 is moved in one direction or the other and carries with it the friction-disk k by the friction between the disk 70 and the disks 29 31, and this movevalve. \Vhen the valve 0 is fullyshifted,how-

ever, the arm 26 comes in contact with one or the other of the abutments 27 28, so as to stop the upward or downward movement of the friction-disk is with the arm 15,and the disk 76 then slips upon the disks 29 31 and rotates on the bolt 30, so as to permit the movement of the arm 15, and the continued movement of the crank-arm 15 by the piston C then results simply in the rotation of the frictiondisk 7c during the rest of the stroke of piston G without operating the valve 0'. It is obvious that a similar friction-disk device may be applied between the link it and the valve or elsewhere between the piston-rod g and the valve instead of between the crank-arm l and link h.

In case the friction between disks 29 31 and the friction-disk 7c fails to move the latter with the crank-arm 15, so as to thus shiftthe valve at the beginning of the stroke of piston G, the valve will be positively shifted later in the stroke of the piston Gby the engagement of one of the arms 36 37, carried by the crank-arm 15,.with the arm 34, and by releasing the friction upon the crank-disk 7.1 the valve 0 may be operated regularly by these arms 36 37 and the pump thus run with the valves on the two sides operated similarly, as described above in connection with the pump shown in Figs. 1 to 9.

In Figs. 10 and 11 I have shown the parts in a position nearly the sameas shown in Figs. 1 to 4, but with the valve 0 just about to be operated by the piston G through piston-rod g and the connections to disk 70 at the beginning of the downstroke of the piston G of cylinder A. In Fig. 12 I have shown the parts in their position when the piston G of cylinder A is just about to operate the valve 0 through piston-rod g as the piston G commences its upstroke.

In Figs. 16 to 21 I have illustrated a construction employing a roller device for operating the valve 0, which will be found very positive and efficient in action. In these figures I have shown only the valve movement for valve 0 of cylinder A, which is to be operated at or near the commencement of the stroke of the piston G, as the valve movement for valve 0 of cylinder A may be the common lost-motionconuect-ion shownin Fig. 11 or of any other common or suitable construction. In this construction the crankarm is a sleeve splined upon or otherwise secured to the rock-shaft 13 and is provided with a circular bearing-face 3 and having a hub 38, upon which is mounted to rotate freely a plate Z, extending on opposite sides of the shaft 13, and to one end of which is pivotally connected link h by pin 39. Upon the shank of the pin 39 and upon a bolt 40, also carried by the plate Z on the opposite side of the crank 15, are mounted upon one side of the plate circular bearingblocks 4, between which and the bearing-face 3 of the crank 15 are mounted rollers 5, which are supported by springs 6, secured to the bearing-blocks 4, so as to prevent these rollers 5 from dropping out, and by the yielding of the springs 6 permit some play of the rollers 5 vertically between the bearing-surfaces 3 4 while holding them up to the position necessary to secure the locking of the crank and plate Z when required. The plate Z is preferably provided with a flange 41, extending entirely about the upper side of the plate and inclosing the parts, and the plate is held in place upon the hub 38 by a collar 42, secured to the shaft 13. Upon the opposite side of the crank 15 from the plate Z is mounted in fixed position upon the frame a bracket-plate 43, which carries two stationary abutments or stops 7 in the path of and above the rollers 5. The crank 15 is provided upon its under side with an arm 44, which plays between lugs 46 on the under side of the plate Z, so that the arm 44 will engage one or the other of these lugs 45 46 near the end of the movement of the crank 15 and move the plate Z in one direction or the other if it has not previously been moved by the rollers 5, as hereinafter described. The link 7b is connected directly to the crank 17 of valve-stem 19, as in the constructions previously described, but the arm 26 and abutments 27 28 are not used. The operation of this construction in connection with the operation of valve 0 of cylinder A is as follows, the parts being shown in Figs. 16 and 17in their position just as the piston G through piston-rod g is operating the valve 0 at the beginning of the upstroke of the piston G and in Figs. 18 to 21 just as the piston G through piston-rod g is operating the valve 0 at the commencement of the downstroke of piston G: As the shaft 13 is rocked by the piston G through piston-rod g and lever 11 the crank-disk 15 is rotated in one direction or the other, so that the movement of its bearing-surface 3 in engagement with the roller 5 on one side tends to raise the roller and, aided by the spring 6 on the bearing-block 4, locks the roller between the bearing-surfaces 3 4. so as to move the plate Z, with the crank 17 on valve-stem 19, in one direction or the other, according to the direction in which the crank 15 and plate Z rock, and thus shift the valve 0. This movement continues until the side of the plate Z that is moving upward with the roller 5 locked between the bearing-surfaces 3 4 reaches a position in which the roller 5 engages the stop 7 above it, when the further movement of the roller 5, with the plate Z, is prevented, so that the roller is loosened from between the bearing-surfaces 3 4 and the crank 15 completes its movement without moving the plate Z, the bearing-surface 3 moving past the roller 5. Upon the movement of the crank 15 in the opposite direction on the next stroke of the piston G the operation is reversed, the plate Z then being rocked in the opposite direction by the bearing-surfaces 3 4 and roller 5 on the opposite side of the shaft 13. As shown in Figs. 18 to 21, the roller 5 on the left-hand side of the shaft 13 is locked in position to raise the left arm of the plate Z and depress the right arm, with the crank h, as the crank 15 rocks to the right in these figures. In case this valve movement fails to act to shift the valve at or near the commencement of the stroke of piston G through the roller 5, the valve 0 will be shifted later in the stroke by piston G by the engagement of the arm 44 with one of the lugs 45 46 on the plate Z, and by removing the rollers 5 the valve 0" may be operated regularly by the arm 44, engaging the lugs 45 46, the valves on both sides then being operated similarly, as previously described in connection with the other constructions.

\Vhile I prefer to use connections between the pistons and the valves, by which the valves are operated without the interposition of fluidpressure, the result desired may be secured with one or both of the valves actuated by fluid-pressure controlled by the piston on the opposite side.

In Figs. 22 and .3 I have shown a simple construction that will be found eflicient, in which the valve 0 of cylinder A is operated by a common lost-motion connection in between the link 7L and the crank-arm 17 on valve-stem 19 of valve 0, so as to actuate the valve 0 at or near the end of the stroke of piston G, as above described, while the valve 0' of cylinder A 'is operated by fluid-pressure controlled by the piston G, so as to be shifted at or near the commencement of the stroke of the piston G. For this purpose the valvestem 19 of valve 0 of cylinder A is provided with a crank-arm 47, which is actuated by piston-rod 48 of piston 49, moving in a small cylinder 50, shown as menu ted on cylinder A, and which is connected at opposite ends by pipes 51 52 with the cylinderA at opposite ends, or, as shown, with the lower end of cylinder A by pipe 51 and with the valve-chamber on the induction-port Ct at the upper end of the cylinder A, this connection being made either in the cylinder or valve-chamber, as desired, provided that it be at such point that when or shortly after steam is admitted to one or the other end of the cylinder A by the shifting of the valve 0 the steam will also be admitted to one or the other of the pipes 51 52, so as to move the piston 49 in the proper direction to shift valve 0' for the stroke of pis ton G in the opposite direction. The other end of the piston-rod 48 preferably carries a piston moving in a dash-pot 53, so as to secure the desired smoothness and regularity of action of the valve 0 as operated by the piston 49. The valve-stem 19 is shown as having also the crank-arm 17, which is connected to the piston g through lost-motion connections m, link h, crank-arm 15, rockshaft13, and lever 11, so that the valve 0 will be shifted by the piston G later in the stroke if the valve and its stem 48 have not been shifted by the piston 49 at or near the commencement of the stroke of piston G, as described hereinafter. The operation of this construction is as follows, the parts being shown in Fig. 22 in their positions when the piston G has just completed its downstroke and shifted the valve of cylinder A, so that the piston G has just commenced its downstroke and is about to shift the valve of cylinder A, and the parts being shown in Fig. 23 in their opposite positions, with the piston G at the end of its upstroke and the piston G just commencingits upstroke. As shown in Fig. 22, the lost motion in connection m between the link 7b and the crank 17 of valve 0 has been taken up, so as to shift this valve, and steam having thus been admitted to the upper end of cylinder A, so as to start the piston G on its downstroke, steam passes also through the pipe 52 onto the right side of the piston 49, so as to move the latter tothe leftin cylinder 50, as indicated by the arrow, thus shifting the valve 0 through piston-rod 48 and crankarm 47 on valve-stem 19, so as to position the valve 0 for the upstroke of the piston G, this movement of the valve-stem 19 and valve 0 being permitted by the upward movement of the link 71/ as the piston G moves downward. In shifting the valve 0 at ornear the commencement of the upstroke of the piston G, as shown in Fig. 23, the movement is the same except that the steam is admitted tothe op posite side of the piston 49 through pipe 51, and the piston-rod 48, crank 47, valve-stem 19, and the valve 0 are moved in the opposite direction, this movement being permitted as the link 7t moves downward from the position shown in Fig. 23 on the upstroke of the piston G. If the fluid-pressure connections to the valve c fail to operate so as to shift the valve 0, the valve will be shifted later in the stroke of the piston when the lost motion in connection m between the link It and crank 17 is taken up, and by disconnecting the fluid-pressure connections the valve 0 may be operated regnlarlyby crank-arm 17 and its connections to piston G, the valves on both sides thus being operated similarly as in the case of the constructions above described.

It will be understood that the invention is not to be limited to pumps of the general construction orhaving valves of the form or movement illustrated or to the form or arrangement of any of the devices shown for securing the desired operation of the valves, as many modifications may be made in the constructions shown and other devices substituted for those illustrated without departing from the invention.

WVhat I claim is 1. The combination with two engine-cylinders with pistons movable independently of each other and their valves controlling the admission and exhaust of the motor fluid, of means for shifting the valve of one cylinder for a stroke in one direction at the end of the stroke of the piston of the other cylinder and the valve of the other cylinder for a stroke in the opposite direction at the commencement of the stroke of the piston of the first-mentioned cylinder, substantially as described.

2. The combination with two engine-cylinders with pistons movable independently of each other and their valves controlling the admission and exhaust of the motor fluid, of means controlled by the pistons for shifting the valve of one cylinder for a stroke in one direction at the end of the stroke of the piston of the other cylinder and the valve of the other cylinder for a stroke in the opposite direction at the commencement of the stroke of the piston of the first-mentioned cylinder, substantially as described.

The combination with two engine-cylinders and their valves controlling-the admission and exhaust of the motor fluid, of means for controlling the valve of one cylinder by the piston of the other cylinder to secure the shifting of said valve for a stroke in one direction at the end of the stroke of said piston and for controlling the valve of the other cylinder by the piston of the first-mentioned cylinder to secure the shifting of said valve for a stroke in the opposite direction at the commencement 0f the stroke of said piston, substantially as described.

4. The combination with two engine-cylinders and their valves controlling the admission and exhaust of the motorfluid, of means for shifting the valve of one cylinder by .the piston of the other cylinder for a stroke in one direction at the end of the stroke of said piston and for shifting the valve of the other cylinder by the piston of the first-mentioned cylinder for a stroke in the opposite direction at the commencement of the stroke of said piston, substantially as described.

5. The combination with two engine-cylinders and their valves controlling the admission and exhaust of the motor fluid, of lostmotion actuating connections between the valves of each cylinder and the piston of the other cylinder, one of said connections being arranged to actuate the valve for a stroke in one direction at the end of the piston-stroke and the other of said connections to actuate the valve for a stroke in the opposite direction at the beginning of the piston-stroke, substantially as described.

. 6. The combination with two engine-cylinders and their valves controlling the admission and exhaust of the motor fluid, of lostmotion actuating connections between the valves of each cylinder and the piston of the other cylinder, one of said connections being arranged to actuate the valve for a stroke in one direction at the end of the piston-stroke and the other of said connections to actuate the valve for a stroke in the opposite direction at the beginning of the piston-stroke, and means for positively actuating the said last-mentioned valve later in the stroke in case of failure to actuate it at the beginning of the piston stroke, substantially as described.

7. The combination with two vertical single-acting pump-plungers and their motorcylinders, pistons movable independently of each other and valves controlling the admission and exhaust of the motor fluid, of valve movements controlled by the pistons for securing the movement of the pistons in opposite directions with one of the pistons reversed for a stroke in one direction at the end of the stroke of the other piston and the other piston reversed for a stroke in the opposite direction at the commencement of the stroke of the first-mentioned piston, substantially as described.

S. The combination with two vertical single-acting pump-plungers and their motor cylinders, pistons movable independently of each other and valves controlling the admission and exhaust of the motor fluid, of valve movements actuated by the pistons for securing the movement of the pistons in opposite directions with one of the pistons reversed for a stroke in one direction at the end of the stroke of the other piston and the other piston reversed for a stroke in the opposite direction at the commencement of the stroke of the first-mentioned piston, substantially as described.

9. The combination with two vertical single-acting pump-plungers and their motorcylinders, pistons and valves controlling the admission and exhaust of the motor fluid, of valve movements for each cylinder actuated by the piston of the other cylinder for securing the movement of the pistons in opposite directions with one of the pistons reversed for a stroke in one direction at the end of the stroke of the other piston and the other piston reversed for a stroke in the opposite direction at the commencement of the stroke of the first-mentioned piston, substantially as described.

10. The combination with two engine-cylinders and pistons therein movable independently of each other, of valve mechanism controlling the admission and exhaust of the motor fluid, and connections between said valve mechanism and the pistons for controlling the valves of each cylinder by the piston of the other cylinder for the movement of the pistons in opposite directions during their entire strokes, substantially as described.

11. The combination with an engine-valve, of a reciprocating member and yielding or friction connections between said member and the valve for actuating the valve during the first part of the movement of the member in either direction and releasing said member from the Valve after the latter is moved to permit said member to complete its movement, substantially as described.

12. The combination with an engine-valve, of a reciprocating member and yielding or friction connections between said member and the valve for actuating the valve during the first part of the movement of the mem her in either direction and releasing said member from the valve after the latter is moved to permit said member to complete its movement, and means carried by said member for positively actuating said valve later in its movement in case the valve is not moved by the yielding or friction connections, substantially as described.

13. The combination with the valve-stem l9 and crank 17 thereon, of crank '2; pivoted on crank 1'7, bar 21 connected to crank tand having a limited movement permitting the crank 7; to swing on crank 17 in either direction for a certain distance and then locking means for stopping the valve when shifted, 1c

the cranks together, and means for actuatl substantially as described.

ing crank 'i, substantially as described. In testimony whereof I have hereunto set 14:. The combination with the valve-stem my hand in the presence of two subscribing 19 and crank 17 thereon, of crank 2" pivoted Witnesses.

on crank 17, bar 21 connected to crank i, CHARLES C. WVORTHINGTON. spring 23 acting on said bar to oppose the 'Witnesses: swinging of crank t" toward the center on LOUIS R. ALBERGER,

crank 17, means for actuatin crank i and l BOWEN W. PIERSON.

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