US2083797A - Hydraulic machine - Google Patents

Description

June 15, 1937. J. D. SCOVILLE HYDRAULIC MACHINE 9 Shets-Sheet 1 Filed Nov. 15, 1935 I2! I24 I20 June 15, 1937. scov 2,083,797

HYDRAULIC MACHINE Filed Nov. 15, 1935 9 sheets-sheet 2 TO on. TANK INVENTOR ATTORNEY June 15, 1937. J. D. SCOVlLLE HYDRAULIC MACHINE Filed NOV. 15, 1935 9 Sheets-Sheet 5 June 15, 1937. scov 2,083,797

HYDRAULIC MACHINE Filed Nov. 15, 1935 9 Sheets-Sheet 4 55 )2 I In v I i i 1 1 lNVENTOR J efD.\/c :or i11e s H ATTOREY J ne 5, 1937. .1. D. SCOVILLE HYDRAULIC MACHINE Filed Nov. 13, 1955 9 Sheets-Sheet 5 lllfllfllll Y E N R O T A INVEW TD 9; CO 4 BY j) J2? W'k lllllt liiII!IIIIWIIIIlilllrl!!!I IIIIIIIIIIIIIIIIIII I m w w u Illlllflli'llk June 15, 1937.

J. D. SCOVILLE HYDRAULIC MACHINE Filed NOV. 13, 1935 9 Sheets-Sheet 6 June 15, 1937. J. D. SCOVILLE 2,083,797

HYDRAULIC MACHINE Filed Nov. 13, 1935 9 Sheets-Sheet 7 m 0 N m awucnkoo June 15, 1937. J. D. SCOVILLE 2,083,797

HYDRAULIC MACHINE Filed Nov. 15, 1935 9 Sheets-Sheet 8 INVENTOR June 15, 1937. scow E 2,083,797

HYDRAULIC MACHINE Filed NOV. 13, 1935 9 Sheets-Sheet 9 INVENTOR Jo a, jlJaoaflle,

ATTORNEY Patented June 15, 1937 UNITED STATES HYDRAULIC MACHINE James D. Scovllle, York, Pa., assignor to S. Morgan Smith Company, York, Pa., a corporation of Pennsylvania Application November 13, 1935, Serial No. 49,457 2 Claims. (Cl. 253-143) This invention relates to improvements in hydraulic machines of the type wherein the blades of the runner are adjustable to vary their angle and the area, of the water opening through the runner to correspond with the angle and opening of the wicket gates which control the admission of water to the runner.

Heretofore, in hydraulic machines of this type, it has been customary to construct the mechanism so that when the wicket gates were operated by the governor in response to variations in the load, the adjustable blades of the runner would be correspondingly moved to thereby maintain a definite relationship between the angle or position of the wicket gates and the angle or position of the runner blades at all times.

For a given head, as the wicket gates are opened the runner blades must be opened, slowly in the lower gate range, rapidly from about 60% 2 to 90% gate range, and slowly at the end of the gate stroke. This relationship is determined by tests and is obtained in the hydraulic machines by means of a cam in the blade control valve, said cam being operatively connected to the shaft of the wicket gates so that motion of the gates causes the blade control valve to rise or fall, which in turn causes the runner blades to open or close to their correct position.

For a given head the above referred to cam has a definite shape. However, if the head at the plant increases, the relationship between the wicket gates and the runner blades must be changed to obtain the maximum efficiency. For a given gate opening the blade angle must be larger,

An object of the present invention is to provide an improved hydraulic machine of the above type in which means are provided by which the relative positions of the runner blades with respect to the wicket gates can be quickly adjusted to obtain the maximum efficiency of the hydraulic machine when the head at the plant changes.

Another object of the invention is to provide an improved hydraulic machine of the above type 45 in which means are provided for adjusting the cam of the runner blade operating mechanism control valve, so that the relative positions of the runner blades with respect to the wicket gates will be correspondingly adjusted to maintain such a relationship between the angle or position of the gates and the angle or position of the runner blades when the head at the plant changes that maximum efliciency will be obtained.

Another object of the invention is to provide an improved hydraulic machine of the character mentioned, which is simple in construction, and reliable and exact in function under all conditions of service.

The invention also comprises certain new and useful improvements in the construction, ar-

rangement and combination of the several parts of which it is composed, as will be hereinafter more fully described and claimed.

In the accompanying drawings:-

Figure 1 is a side elevation, partly in section,

of a hydraulic machine employing a runner of the adjustable blade type and embodying controlling means according to the present invention, the main part of the governor being omitted so as to show the control valve device;

Fig. 2 is a plan of a portion of the structure.

shown in Fig. 1, showingthe governor and control valve device;

Fig. 3 is an enlarged vertical section of the lower end of the runner and shaft, showing the construction of the parts within the hub of the runner; i

Fig. 4 is an enlarged vertical section of the servo motor associated with the runner blade operating mechanism;

Fig. 5 is an enlarged vertical section of the 011 head and associated parts on top of the generator;

Fig. 6 is an elevation, partly in section, of the control device as seen from the line 6-6 of Fig. 2;

Fig. '7 is a diagrammatic section of the control valve device, taken on the line 'l-I of Fig. 2;

Fig. 8 is a view similar to Fig. 6 showing the cam of the control valve device in an adjusted position;

Fig. 9 is an elevation of the adjustable blade runner, the blades being shown in the position assumed when the cam of the control valve device has been shifted from the position illustrated in Fig. 6 to the position shown in Fig. 8;

Fig. 10 is a horizontal section taken on the line ill-l 0 of Fig. 1 showing the wicket gates and their operating mechanism;

Fig. 11 is a detail plan of the adjustable rod connecting the cam of the control valve to the governor;

Fig. 12 is a side elevation of the structure shown in Fig. 11;

Fig. 13 is a sectiontaken on the line Iii-l3 of Fig. 11; and

Fig. 14 is an enlarged view of a portion of the rod shown in Fig. 11.

Referring to the drawings and especially to Figs. 1, 2 and 10, the hydraulic machine may be in the form of a hydraulic turbine ll adapted to operate an electrical generator l2, and included in the complete generating unit is a governor l3 adapted to automatically control the operation of the turbine l I, so that the turbine will operate at a substantially uniform speed, irrespective of the variations in the load.

The turbine H has a runner which is made with adjustable blades, the angular positions of which are adapted to be varied, together with the wicket gates, according to the load, so that the turbine will operate at its highest efficiency at all times.

In mechanisms falling within the scope of the present invention, the operating fluid is generally oil, and the oil is supplied from the usual pressure tank (not shown) which is installed in the power house as a part of the equipment. The oil pressure tank is connected with the governor 3 and also with the runner blade operating mechanism, means being provided for controling the oil in such a manner that when the governor operates in either direction to adjust the angles of the wicket gates, the runner blades will be caused to rotate in a similar direction so as to effect a corresponding adjustment in the angles or positions thereof. In this way the parts of the turbine will be simultaneously adjusted, so that all of the parts will at all times retain their correct relationship with each other, and the turbine will operate with maximum eiiiciency and smoothness and with minimum vibration.

For the purpose of controlling the actuation of the runner blade operating mechanism, a control valve device 5 is employed. This control valve is connected to the fluid pressure line and is adapted to be operated in the manner to be hereinafter described.

The turbine comprises a casing it which forms a peripheral water inlet in which are mounted an annular series of movable wicket gates l1 and stationary guide vanes l4.

Projecting from the lower end of the wicket gates H, are trunnions l8 which are journalled in the adjacent portion of the casing l6.

Stems |9 project upwardly from the wicket gates I1 and terminate a suitable distance thereabove, said stems being journalled in suitable bearings carried by the casing IS.

The wicket gates H are adapted to be rotated simultaneously into different angular positions to control the flow of water into the turbine in the usual manner, and for this purpose the upper ends of the stems l9 are provided with gate operating arms 2|) which are fixed to said stems and connected by links to a gate adjusting ring 2|, as shown in Fig. 10.

The gate adjusting ring 2| is connected by link means 22 to a shaft 23. Fixed to the upper end of the shaft 23 is an arm 24 which is connected by a link 25 in a well known manner to the controlling member (not shown) of the governor l3 (see Fig. 2).

As shown in Fig. 1 the lower portion of the turbine casing 5 forms an axially directed chamber 21 in which the runner 28 operates.

The hub of the runner 28 is fixed to the lower end of a hollow or tubular shaft 29 which is journalled in a suitable bearing 30 mounted in the turbine casing. The upper end of the runner shaft 29 is directly connected to the shaft 3| of the generator l2 (see also Fig. 4).

Any suitable type of setting may be used for the turbine installation, a concrete setting 32 being shown in the present instance. The portion of the setting below the turbine forms a draft tube 33 into which the water is discharged from the runner. The electrical generator l2 may rest on top of the setting as shown in Fig. 1.

Referring now to Fig. 3, the hub of the runner 28 is bolted or otherwise fixed to the lower end of the runner shaft 29.

A suitable number of blades 34 are rotatably supported in the hub of the runner 28 and pro- 'J'ect radially therefrom. In the present instance four blades are shown (see also Figs. 1 and The inner end of each blade 34 is formed with a trunnion 35 which is journalled in bearings 36 and 31 supported in the hub. The construction is such that the blades are rotatable into differ ent angular relationships with the axis of the runner.

Means are provided for simultaneously rotating all of the blades 34 and for maintaining them in equal angular relationship, such means comprising preferably an, arm 38 rigidly fixed on the trunnion 35 of each blade, and links 39 which pivotally connect the arms on the different blades to a cross head 40. The cross head 40 is guided to reciprocate in a direction axially of the runner by guide pins 4|, which are mounted in the hub of the runner in the manner shown in Fig. 3. It will be understood that the relative positions of the blades 34 govern the area of the water passages or openings between the blades, and that when the blades are rotated, the area of the water passages is increased or decreased depending upon the direction in which the blades are moved.

As shown in Figs. 1, 3 and 9, a cap 42 is bolted or otherwise removably secured to the lower end of the hub of the runner 28. Since the hub of the runner is otherwise enclosed and the hub is hollow, the cap 42 provides a closed chamber or reservoir for containing a supply of grease for lubricating the various working parts of the mechanism contained within the hub :f the runner.

The cross head 40 is bolted or otherwise fixed to the lower end of an operating rod 43 which extends upwardly through the hollow runner shaft 29.

As shown in Fig. 4 the upper end of the operating rod 43 is fixed to the piston 44 of a servo motor 45 which is mounted in the runner shaft 29 adjacent to the point where the runner shaft is joined to the generator shaft 3|.

The servo motor piston 44 is contained in a cylinder which may be formed as an enlargement of the runner shaft 29, the upper portion of said cylinder being closed by the lower portion of the generator shaft 3|, as shown in Fig. 4.

The upper portion of the operating rod 43 passes through a bushing 46 mounted in the runner shaft 29, and this bushing besides forming a bearing for the operating rod 43, provides means for closing the chamber 41 on the lower side of the piston 44.

The servo motor piston 44 is double acting, and in order to supply oil to both sides thereof for the purpose of operating the same in either direction, two tubes or pipes 48 and 49 are employed. The pipes 48 and 49 are mounted within the hollow generator shaft 3| and rotate therewith, said pipes extending from the servo motor upwardly through the shaft 3| to a head 50 which is mounted on top of the generator |2 (see Figs. 1 and 5). If so desired the pipe 49 can be concentrically disposed within the pipe 48.

The lower end of the pipe 49 is in communication with the chamber 41 on the lower side of the servo motor piston 44 and the lower end of the pipe 48 is in communication with chamber 5| on the upper side of said piston.

The lower end of the pipe 49 is fixed to a cap 52 carried by the servo motor piston 44, and therefore thepipe 49 will be moved rectilinearly in the generator shaft 3| when the servo motor operates. A chamber 53 is provided within the cap 52, said chamber being connected to the piston chamber 41 by means of passages or ports 54 formed in the piston 94, so that oil supplied through the pipe 99 will flow into the chamber 01.

The lower end of the pipe 48 terminates above the cap 52, so as to hem communication with the chamber H of the servo motor. The lower end of the pipe 08 may be secured to the lower end of the generator shaft 3 I, by means of a member 59 having a peripheral flange which is bolted or otherwise secured to the adjacent portion of the generator shaft 9!. The member 55 provides means for closing the lower end of the hollow generator shaft 9| and thereby cut off communication from the chamber bl to the space within said shaft exteriorlyof the pipes 09 and 09.

Referring now to Fig. 5, the head 50 is formed with a plurality of superposed cavities 56, 91, 50 and 59, the cavities 5i and 59 constituting chambers for containing oil, and the cavities 50 and 59 forming housings for the mechanism.

The upper end of the pipe 48 terminates within the chamber 58 so that said chamber is at all times in communication with the servo motor chamber 5 I. For the purpose of securing the upper end of the pipe 99 in position, a member 59 is employed. This member has a peripheral flange which is bolted or otherwise secured to the adjacent portion of the body of the head 50. In order to prevent leakage of oil from the chamber 50 into the cavity 59, a packing gland GI is fitted to the member 60 and surrounds the pipe 00.

The pipe 09 projects upwardly through the chambers 58 and 51, and terminates in the cavity 56. For the purpose of guiding the pipe 09, a bearing 62 is fitted in the wall separating the chambers 51 and 50. Since the bearing 62 snugly fits around the pipe 99, leakage of oil between the chambers 51 and 58 is reduced to a minimum.

The top of the chamber 51 is closed by means of a cap plate 63 which is detachably secured to the head 50 by means of bolts or other suitable fastening means. A packing gland is secured to the cap plate 63 and surrounds the upper portion of the pipe 49 so as to seal the top of the chamber 51.

A plurality of openings 95 are formed in the portion of the pipe 09 which is located within the chamber 51, so that oil can flow from said chamber into the pipe and from thence downwardly to the chamber 51.

At a convenient point in the cavity 59, the pipe 08 has fixed thereto a sealing ring 56. This sealing ring is associated witha pan 6'? carried by the upper portion of the generator I2 in such a manner that any oil seeping through the packing gland BI will be prevented from passing down the exterior of the pipe 98 to the upper end of the generator shaft 3 I. In order to prevent oil from accumulating in the pan 01, the bottom of the pan is perforated, as at 00 (Fig. near the outer edge thereof, so that the oil will pass to the outside of the upper end of the generator shaft 3|.

The upper end of the pipe 99 is closed by a plug 69. The plug projects upwardly into the cavity 56. The upper portion of the plug 09 is hollowed out to form a recess I0.

Mounted on a shaft I3 which is transversely disposed in the upper portion of the head 50, is a lever I2, and depending from said lever is an arm II which extends into the recess I0 in the plug 69. A ball I4 is interposed between the end of the arm II and a bearing block I5 in the bottom of the recess.I0. The construction and arrangement of these parts is such that vertical movement of the pipe 49 in either direction is transmitted through the arm II and lever H .to

by a vertically movable the shaft 13, with the result that the shaft will be rotated in either direction. It will also be understood that due to the provision of the ball Id, a universal joint is formed between the pipe 49 and arm II, so that the pipe- 09 will be free to rotate with respect to the non-rotating arm II, during the operation of the turbine.

Referring now to Figs. 6, 7 and 8, the control valve device I5 comprises a casing formed with a cylinder 96. Contained in the cylinder 80 is a valve 81. As shown, the cylinder and valve may be vertically disposed, and the valve has a stem 08 which projects upwardly through the top of the casing of the valve device IE.

A plurality of ports M, 92, 90, 94 and 95 are provided for connecting the cylinder 80 with a plurality of chambers 96, 91, 99, 99 and I00 respectively. The valve 91 is formed with a pair of spaced apart and connected heads 89 and 90. The ports 92 and 94 are spaced apart a suitable distance, so that the heads 99 and 90 will lap said parts when the valve 81 is in one position, as will be hereinafterdescribed, and all of the ports are so disposed relatively to each other, that when the valve 81 is in certain other positions said ports will be connected in the manner to be hereinafter described.

Chamber 91! is connected by a pipe IOI, with the chamber 58 in the head 50, and apipe I02 connects chambers 99 and 51 (see Figs. 5 and 7). The chamber 99 is connected to the oil pressure conduit E03, by a pipe I04, which is fitted with a manually operated valve I05. (See Figs. 2 and 7.)

Chambers 90 and I00 are connected by a pipe I09 to the return conduit I01 which connects the governor I3 with the sump tank (not shown) of the oil pressure system (see Figs. 2 and '7) For the purpose of operating the valve 81, a cam I00 is provided. This cam comprises an elongated body which is mounted for horizontal movement in a slot I9I formed in a saddle I09. The saddle I09 is bolted or otherwise attached to the side of the casing of the control valve device I5, as shown in Figs; 6 and '7.

One end of the cam I00 is connected by a link or rod IIO, to an arm III fixed to and projecting from the gate operating shaft 23, so that rotation of the shaft 23 resulting from the opera.- tion of the governor I3, results in the cam being moved rectilinearly in the saddle I09 (see Fig. 2).

As shown in Figs. 6 and ,8, the upper surface of the cam I08 is formed with a cam face H2 which is adapted to engage a roller H3, carried plunger I. The plunger is mounted in a bore I32 formed in the saddle I09.

The upper end of the plunger I is formed with a threaded portion I25 which passes thrmgh an opening I21 formed in a bracket I28. Above the bracket I20, the threaded portion I26 has nuts I29 and a washer I30 mounted thereon so as to provide means for manually raising the plunger Ill, should it be so desired.

The bottom of the plunger II is formed with an enlarged portion II5, which constitutes a weight for maintaining the roller H3 in contact with the cam face.

A pair of bars I II, which are arranged in parallel relation on oppositesides of the valve stem 88 and plunger I, have one end pivotally connected, as at H8, to the plunger III, their intermediate portion pivoted to the valve stem 00, as indicated at I I9, and their other end connected by a link I20, to one arm of a bell crank lever I2I, the link I20 being connected to the bars II 1 by means of a pivot pin I24 (see also Fig. 1). The bars II1 constitute a floating lever, the purpose of which will be hereinafter described.

The bell crank lever I2I is supported by a bracket I22 mounted on the base of the apparatus, as shown in Figs. 1 and 2. The other arm of the lever I2I is connected by a rod I23 to an arm I25 fixed to the shaft 13.

It will be understood that when the parts are operatively assembled and the chambers 5| and 41 are charged with oil under pressure, the weight of the parts connecting the floating lever Ill and the arm I25 will pull the lever 12 downwardly, thereby maintaining the free end of the arm H in engagement with the ball 14, so that any movement of the pipe 49 will be transmitted through the levers and links hereinbefore described to the floating lever II1.

As shown in Figs. 2, 11, 12, 13 and 14, the link or rod H is so made that its length can be changed, so that the position of cam III with respect to saddle I06 of control valve device I can be shifted or adjusted for the purpose to be hereinafter described.

The link or rod-IIII is formed with an elongated portion I40, one end of which is formed with an eye I through which is inserted a pivot pin I 42 carried by a bracket on the outer end of the cam I08. The opposite end of portion I40 is formed with left hand threads I43.

The opposite end of the link or rod H0 is preferably made in the form of a yoke I44 having two arms which straddle the end portion of arm III of the governor shaft 23, said yoke being pivotally connected to said arm by means of a pin I45, as shown in Fig. 2.

The yoke I44 is formed with an internally threaded portion having right hand threads I46 (see Fig. 13). Engaging the threads I46.is an end of a threaded rod I41 which is mounted in the yoke I44 and projects outwardly therefrom.

For the purpose of connecting portion I40 of rod III) with the yoke I44, use is made of an elongated nut I48, the threaded bore of which is formed with right hand threads for engaging the threaded portion I43 of portion I40 and left hand threads for engaging the rod I41. Nut I48 is formed with a plurality of openings I46 so that the nut can be turned by means of a suitable tool (not shown) having prongs adapted to be inserted in said openings.

In order that the parts of the link or rod IIO may be locked in an adjusted position, lock nuts I50, I5I and I52 are provided, nut I50 being mounted on the threaded portion I43 of rod I40 and being adapted to engage the adjacent end wall of nut I46, nut I 5I being mounted on rod I41 for engagement with the adjacent end wall of nut I46, and nut I52 being mounted on rod I41 for engagement with the end of yoke I44. Threaded rod I41 is held in position in the yoke I44 by means of a set screw I53.

The above described construction of the link or red I I0 constitutes a turnbuckle arrangement by means of which the length of the link or rod IIO can be adjusted to suit varying conditions, and in order that an operator or power house attendant can readily observe the adjustment of the link or rod IIO, suitable indicating means are provided. Such indicating means may comprise, as shown in Figs. 11 and 12, an indicator arm I54 having one end fixed to the yoke I44 and its opposite or free end made in the form of a pointer I55, and a series of notches I56, I51 and I56 formed on the rod I40 and adapted to cooperate with said pointer. Any number of notches may be employed. In the instant case, three notches are shown, and the intermediate notch I56 is so formed on the rod I40 that when the pointer I55 is disposed adjacent thereto the link or rod IIO will have such length that the cam I06 will be positioned in the control valve device I5 at the correct position for the normal head for which the apparatus is designed. Notch I51 may be for a lower, and notch I56 for a higher head, as will be hereinafter described.

In operation, when the governor I3 operates to swing the wicket gates I1 toward open or closed position to vary the gate opening to conform with variations in the load on the turbine, the rotation of the shaft 23 in either direction will effect a corresponding movement of the valve 61 of the control valve device I5, since said valve is connected to the governor through the floating lever II1, plunger II4, cam I08, link H0, and arm III, and the servo motor 45 will be supplied with fluid under pressure so as to operate the runner blade operating mechanism toward open or closed position.

In Figs. 1 and 10, the runner blades 34 are shown approximately one-half opened and the governor and wicket gates are shown correspondingly positioned. With the runner blades 34 opened approximately one-half, the cam I06 of the control valve device I5 is so positioned that the roller II3 engages the cam face I I2 at a point approximately equi-distant from the highest and lowest points thereof, so that the plunger II4 is maintained correspondingly positioned within the frame provided by the saddle I08 (see also Figs. 6 and 7).

When the governor I3 and control valve device I5 are inactive, the valve 61 is so positioned in the cylinder 86, that the valve'heads 89 and 60 lap the ports 92 and 94, respectively. With the valve 81 in this position, communication is cut off between the cylinder 66 and the chambers 91 and 39, respectively, and oil under pressure is retained or bottled up in chambers 51 and 56, pipes 48 and 49, and chambers SI and 41, respectively, so that the servo motor piston 44 remains in a position corresponding to the position of the runner blades 34. The parts will remain so positioned until the governor I3 operates, in response to a variation in load, to shift the wicket gates I1.

As shown by the arrow in Fig. 2, the governor I3 moves toward the left to close the wicket gates and toward the right to open said gates.

The cam I 06 is connected to the gate shaft 23 in such a manner that movement of the governor I3 in one direction, causes the cam to move in the opposite direction. That is to say, when the governor moves toward the left (Fig. 2), the cam I06 is moved toward the right (Fig. 6) and vice versa, when the governor moves toward the right, the cam I06 moves toward the left.

Should the load on the turbine decrease, the governor I3 will act to move the wicket gates I1 toward closed position, so as to decrease the quantity of the driving fluid supplied to operate the runner 26.

The movement of the governor toward the left causes a corresponding movement of the cam I06 toward the right, with the result that the plunger II4 moves downwardly. The downward movement of the plunger II 4 is effective through the floating lever I I1, and said lever is swung downwardly on the fulcrum provided by the pivot pin I24, and this action causes a downward movement of 'the valve Bl, so that the valve heads 89 and 99 uncover the ports 92 and 99, respectively.

When the valve Bl moves downwardly and port 92 is uncovered, chamber 91 is connected to chamber 99, through port 92, chamber i133, and port 9i, and fluid under pressure is vented from the servo motor chamber St to the return conduit on, through pipe 99, chamber 98, pipe l0l, chamber 9l, port 92, chamber 833, port 9|, chamber stand pipe nus.

Simultaneously with the venting of fluid under pressure fromthe chamberfi i ,iluid under pressure is supplied to the chamber 91 of the servo motor 99, from the supply pipe 993, through pipe E06, chamber 98, port 93, valve chamber I 39, port 99, chamber 99, pipe I92, chamber 51 and pipe #39.

The fluid under pressure thus supplied to the chamber 97 acts on the underside of the servo motor piston 99 and forces said piston upwardly. This upward movement of the piston 99 is transmitted by the rod 93 to the cross head 90, and said cross head acting through the links 39 and arms 39, will simultaneously rotate the runner blades about their trunnions as axes, toward closed position.

Since the shaft I9 is connected to the servo motor piston 94 by means of the lever 12, arm H, and the pipe 39, said shaft will be rotated in a clockwise direction as soon as the servo motor piston M commences to move upwardly to effect a change in the angle or position of the runner blades.

The rotation of the shaft 73 is transmitted by the arm I25, rod I23, bell crank Hi and link H20, to the left hand end of the floating lever I I! (Fig. 7), and said lever will accordingly be swung upwardly about the fulcrum provided by the pivot pin H8. In this action of the floating lever ill, the valve 97 will be raised slightly, thereby moving the valve Bl toward lap position. However,

the upward movement of the valve 91 is counteracted by the continued downward movement of the plunger I I4, so that while the left end of the lever ill is gradually raised, the right end of said lever will be gradually lowered. In this way the valve 81 will be maintained in the position in which the ports 92 and 94 are respectively uncovered by the valve heads 99 and 90 an amount sufficient to establish communication in the above described manner to both sides of the servo motor piston 59.

The movement of the right end of the floating lever H1 is definitely limited by the governor l3, but the opposite or left end of said lever will continue to move as long as the ports 92 and 99 are not lapped by the heads 89 and 90, respectively, of the valve 81. lherefore, the left end of the floating lever Ill will continue its upward motion until the ports 92 and 94 are lapped, thereby cutting off the communication through which fluid under pressure is supplied to operate the servo motor 45.

The action of the governor l3 will continue until the wicket gates have been closed an amount suflicient to cause an overload on the turbine, whereupon the governor reverses and moves the wicket gates toward open position, thereby gradually relieving the load on the turbine.

Since the rotation of the runner blades as effected by the servo motor 45, is not simultaneous with the action of the governor i3, but closely follows the same, the upward movement of the plunger H4 resulting from the reversed action of the governor, taken in connection with the movement of the servo motor piston 44, will,

through the action of the floating lever H1, cause the valve 81 to move to the position in which the ports 92 and94 are lapped. In this way the communication through which fluid under pressure is supplied to operate the servo motor piston 64 is cut off and the operation of the servo motor is interrupted. The runner blades will then have been brought to an angle or position corresponding with the adjusted position into which the wicket gates have been brought by the governor 59. v

The parts will then remain so positioned relative to each other until the wicket gates are again operated, whereupon a runner blade adjusting operation similar to that Just described will again take place to automatically move the runner blades into proper position with respect to the position assumed by the wicket gates.

However, when the load is increased, the governor 53 will move in the direction opposite to that shown by the arrow in Fig. 2 and the operation of the other parts will be reversed to that heretofore described. In this connection it will be noted that the valve 91 moves upwardly in the cylinder 86, so that when the port 99 is uncovered, chambers 99 and "ill will be connected, and chambers Bl and 98 will be connected. Fluid under pressure will then be vented from the servo motor piston chamber 91 and fluid under pressure will be supplied to the servo motor piston chamber 5i, so that the piston 94 will be moved downwardly.

The extreme positions of the floating lever H! are shown by broken lines in Fig. "I. When the runner blade adjusting mechanism is inactive and the runner blades are approximately onehalf opened, the floating lever Ill will be in an approximately horizontal position, as shown. When the runner blades are closed, the floating lever ill will be in the position shown by the broken lines indicated at A (Fig. '7), and when the runner blades are opened wide, the floating lever will be in the position shown by the broken lines indicated at B (Fig. '7).

As above described, under a predetermined head the adjustable runner blades of a hydraulic turbine are opened or closed to conform with the opening or closing of the wicket gates by the usual governor to maintain the speed of the turbine constant under increases or decreases in the load, so that the runner blades may always occupy an angle or position which corresponds with a definite position of the wicket gates as determined by the output of the turbine.

However, if the head at the plant increases or decreases, the relationship between the relative positions of the wicket gates H and the runner blades 34 should be changed to obtain the maximum efliciency.

For instance, if the head increases, for a given gate opening, the blade angle must be larger.

Heretofore, when the head at plant changed this has been taken care of by removing cam I98 and installing in place thereof another cam having a different cam surface for engaging roller H3. But this method has proven unsatisfactory on many occasions, due to the fact that cams were not available to suit the change in head. That is to say, when the operating head was half way between the points for which the cams were designed, there was an unavoidable loss in efficiency when one cam was substituted for another.

Therefore, in order to provide means whereby the relative position of the cam I08 can be readily shifted in accordance with variations in the operating head at a plant, it is proposed to shift the position of the cam in the control valve device by lengthening or shortening the link or rod H which connects the cam with the governor arm I I I.

In Fig. 6' the broken line indicating cam surface H2 is in the same position as the full line of said cam surface shown in Fig. 8, and the broken line indicating cam surface H2 in Fig. 8 is the same as the full line of the cam surface shown in Fig. 6. This shifting of the position of cam I00 may be easily effected by unscrewing lock nuts I50 and lil and then rotating nut I48 to shorten the link H0.

Thus, assuming that the normal head at a plant is 35 feet (see Fig. 11), and the head increases to 40 feet, the above described method of shortening the link H0 can be quickly effected and when the indicator I55 registers with the notch I58 (40 foot mark on rod), the operator will have correctly shortened the link H0 to take care of the change in head at the plant.

When the link H0 is thus shortened and cam I08 moved toward the left (Figs. 6 and 8), plunger II4 will, through. the engagement of roller H3 with the cam surface H2, be moved upwardly in the bore I32 of the saddle I09.

The upward movement of the plunger H4 will effect an upward swinging movement of the floating lever III on the fulcrum provided by the pivot pin I24, and this action causes an upward movement of the valve 81, so that the valve heads 09 and uncover the ports 92 and 94, respectively.

When the valve 0! moves upwardly and ports 92 and 94 are uncovered, chamber 91 is connected to chamber 98, and chamber 99 is connected to chamber I00. Fluid under pressure will then be vented from the servo motor piston chamber 41, through ports 54, chamber 53, pipe 49, ports 65, chamber 51, pipe I02, chambers 99 and I00 to pipe I06, and fluid under pressure will be supplied toservo motor piston chamber 5|, from pipe I04, through chambers 98 and 91, pipe IOI, chamber 50, and pipe 48, so that the piston 44 will be moved downwardly. This downward movement of servo motor piston 44 is transmitted by the rod 43 to the cross head 40, and saidcross head acting through the links 39 and arms 30, will simultaneously rotate the runner blades 34 about their trunnions as axes, so that the runner blades are shifted from the dotted line position shown in Fig. 9, which dotted line position it will be noted corresponds to the full line position, Fig. 1, in which the runner blades have a position corresponding to the onehalf opened position of the wicket gates (see also Fig. 10) toward the full line position, Fig. 9.

As the governor I3 is inactive during this adjustment in position of the runner blades, no change in position will be imparted to the wicket gates I1, as will be understood.

Since shaft 13 is connected to the servo motor piston 44 by means of the lever I2, arm II, and pipe 49, said shaft will be rotated in a counterclockwise direction as soon as the servo motor piston 44 commences to move downwardly. This rotationof shaft 13 is transmitted by arm I25, rod I23, bell crank I2I and link I20, to the left hand end of the floating lever II'I (Fig. 7) and said lever will accordingly be swung downwardly about the fulcrum provided by the pivot pin H8. In this action of the floating lever H1, the valve 01 will be lowered until ports 92 and 94 are lapped, thereby cutting oil. the communication through which fluid under pressure is supplied to operate the servo motor 45. The runner blades will then have been moved to the full line position shown in Fig. 9, from the position indicated by the broken lines, which full line position corresponds with the adjusted position of cam III.

In this way the relative positions of the runner blades with respect to the wicket gates can be altered to suit variations in head, so that when the head on the turbine changes, the turbine will operate at the maximum emciency.

It will be understood that when the head on the plant decreases the cam I00 can be shifted in the opposite direction, which action will effect a corresponding adjustment of the runner blades in the opposite direction so that under variations in head in either direction the adjusted positions of the runner blades with respect to the wicket gates can be altered so that under all conditions the turbine will operate at the maximum efficiency.

While one illustrative embodiment of the invention has been described in detail. it is not my intention to limit its scope to that embodiment or otherwise than by the terms of the appended claims.

Having thus described my invention what I claim is:--

1. In a turbine, a runner having blades and means for adjusting the blades into different angular positions, gates and means for adjusting the gates into different angular positions, a governor, mechanism operated by the governor for controlling the operation of the gate adjusting means, means separate from said mechanism operated by the "governor for controlling the runner blade adjusting means, means for adjusting said controlling means, a rod connecting the governor with said controlling means, and means for changing the length of said rod whereby the adjustment of said controlling means is changed in accordance with variations in head on the runner.

2. The combination with a runner having blades adjustable into different angular positions, and gates adjustable into different angular positions and controlling the flow of the driving fluid to the runner, of a governor for adjusting the angular positions of the gates, fluid pressure operating means for adjusting the positions of the runner blades, means for maintaining the relative positions of the runner blades in synchronization with the gates, comprising a valve device for controlling the supply of fluid under pressure to said runner blade adjusting means, a cam for actuating said control valve device, a rod connecting said cam with said governor whereby operation of said governor simultaneously effects operation of said cam so that the runner blades will be adjusted in accordance with changes in position imparted to the gates by the governor, and means for changing the length of said rod whereby the position of said cam with respect to said valve device is changed in accordance'with variations in head on the runner so that the relative positions of the runner blades with respect to the wicket gates are changed in order that the runner will operate at the maximum efliciency.

JAMES D. SCOVILLE.

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