US2690765A - Hydraulic operating apparatus - Google Patents

Description

Oct. 5, 1954 F. J. KRUMMEL HYDRAULIC OPERATING APPARATUS 5 Sheets-Sheet 1 Filed July 14, 1951 INVENTOR. Frederic-1S" J fiammel. BY 1J5 ma'o'mvz'y Filed July 14, 1951 F. J. KRUMMEL HYDRAULIC OPERATING APPARATUS 5 Sheets-Sheet 2 7 INVENTOR. fiede cbli J hi' cmzmel.

His gwbmv Get 5, 1954 J KRUMMEL 2,690,765

HYDRAULIC OPERATING APPARATUS Filed July 14, 1951 5 Sheets-Sheet 3 INVENTOR. fiwdemlc Jifi'ummel.

Oct. 5, 1954 F. J. KRUMMEL HYDRAULIC OPERATING APPARATUS 5 Sheets-Sheet 4 Filed July 14, 1951 INVENTOR. fiedepc'dz J b muzzmel.

Willi/III!!! my ,0, l Em II 15 ATTORNEY Oct. 5, 1954 F. J. KRUMMEL HYDRAULIC OPERATING APPARATUS v .h 6 a f 8 8 INV TOR. figdepicz j mmeZ.

Patented Oct. 5, 1954 UNITED STATES ATENT OFFICE HYDRAULIC OPERATING APPARATUS Application July 14, 1951, Serial No. 236,830

6 Claims.

This invention relates to hydraulic operating apparatus and more particularly to hydraulic operators for valves and the like.

An object of this invention is to control the operated element either from adjacent the element or from a remote location.

Another object of the invention is to apply the component parts of the hydraulic actuator directly to the valve or other operated element.

Another object of the invention is to permit the operated element to be actuated selectively at a rapid rate where excessive force is not required or at a slower rate to reduce the operating efiort.

Another object of the invention is to facilitate the changeover from one operating rate to another.

Another object of the invention is to prevent excessive pressure from building up in the actuator.

Another object of the invention is to arrest high velocity in the fluid connections and prevent damage to the operated element.

The foregoing and other objects and advantages are achieved by the hydraulic pump assembly having a cylinder attached to the operated element, such as a conventional valve. The reciprocable stem of the valve is provided with a piston operable in the cylinder under pressure of fluid transferred from a reservoir by operation of a pump. The reservoir is formed by an annular space between the hydraulic cylinder and an outer cylinder. The pump may be attached directly to the operated element adjacent the cylinder or may be located remotely therefrom and connected by suitable fluid lines.

The pump comprises a dual piston arrangement for increasing the speed at which the operated element is moved from one position to another, such as a valve opening operation. Ad- ,iustment of a selector device permits only one piston to be operated so that the valve is initially opened with minimum efiort. Thereafter, the selector device is readjusted to bring both pistons into operation so that the remaining opening movement is effected at a more rapid rate.

A directional control valve forms part of the pump assembly in a compact arrangement. The control valve ay be ositioned to direct the fluid under pressure from the pump to one end or the other of the cylinder for operating the piston in both directions. Suitable check valve means are incorporated in the fluid connections to control the operating speed of the operated element. Moreover, sufiioient fluid is retained in the reservoir to substantially equal the displacement difference on opposite sides ofthe piston, due to the valve stem, as visually indicated to the operator.

In the drawings,

Fig. 1 is a front elevation, artly in section, of the hydraulic operating device applied to the operated element;

Fig. 2 is a side elevation of the pump and control valve assembly shown in Fig. 1, but separated from the operated element;

Fig. 3 is a cross-section taken on the line III-4H of Fig. 2;

Fig. 4 is a section taken on the line IV-IV of Fig. 2;

Fig. 5 is a section taken on the line V--V of Fig. 4;

Fig. 6 is a partial section taken on the line VI-VI of Fig. 3;

Fig. 7 is a section taken on the line VII-VII of Fig. 3;

Fig. 8 is a partial section taken on the line VIlI--VIII of Fig. 1;

Fig. 9 is similar partial section taken on the line IX-IX of Fig. 1;

Fig. 10 is a partial section of the hydraulic operating device showing a modified form;

Fig. 11 is a schematic view of the hydraulic operating device illustrating the relationship of the fluid passageways, and

Fig. 12 is a section taken on the line XIIXII of Fig. 4.

Referring more particularly to the drawings, the hydraulic actuator of this invention is shown in Fig. l as applied to a conventional rising stem valve, a portion of which is shown as comprising a yoke element 19 having a support cap 2 formed integrally therewith and through which a reciprocable member or valve stem I4 is adapted to project. A recessed stufiing box IE is provided in the cap l2 for the stem M. Since conventional valves of this nature may take many forms, further description is deemed unnecessary.

Hydraulic cylinder An hydraulic cylinder I6 is supported at one end on the cap support l2 which is suitably recessed as at is for its reception. An outer cylinder 20 is also mounted on the support i2 and is of larger diameter than the cylinder it to provide a reservoir 22 in cooperation therewith. As in the case of the hydraulic cylinder It, the end of the outer cylinder 2c is received within a recess 24 formed in the support [2. Both recesses l8 and 24 may be provided with a suitable packing to prevent leakage from the reser voir '22 and the cylinder l6.

The opposite ends of the cylinders l6 and 2B are mounted within recesses 26 and 28, respectively, formed in a head member 30. Suitable packing may also be employed in the recesses 26, 28 to prevent leakage from this end of the reservoir 22. The head member 30 and the cylinders I6 and 2B are secured rigidly in position on the support l2 by through-bolts 32 which extend longitudinally from the cap member 30 to the support I2 through the reservoir 22.

The reservoir 22 is adapted to contain a quantity of hydraulic fluid, such as oil. The level of this fluid in the reservoir 22 is visible through one or the other of a pair of spaced sight gages 34, 36 which are secured in the wall of the outer cylinder 20 in appropriate locations An additional sight gage 38 is also secured in the wall of the outer cylinder 20 adjacent support 12 to indicate substantially complete lack of fluid in the reservoir 22. As indicated by the broken lines in Fig. 1, the level of the fluid in the reservoir 22 is visible in the lower sight gage 36 under one condition of operation of the hydraulic operating device as will hereinafter be apparent. Under other conditions of operation the fluid level will be visible in the upper sight gage 34 as will also be apparent hereinafter.

A main piston M1 is secured to the projecting end of the valve stem l4 within the hydraulic cylinder it. In this instance, the piston 40 and the stem M are in threaded engagement and a securing pin 42 is employed between these parts to prevent relative rotation. The support I2 is provided, as shown in Fig. 8, with a transverse passage 44 extending from the outer wall thereof to the recess l5 and communicating with a point within the cylinder It on one side of the piston 40. The head 36 is also provided with a transverse passage 46 extending from the outer wall thereof to the central portion and terminating in a restricted orifice 48 extending substantially perpendicular to the passage 46 and communicating with a point within the cylinder 16 on the opposite side of the piston 40. The passage 46 also communicates with a point within the cylinder l6 adjacent the orifice 48 by the provision of an opening 50 having a suitable check valve 52 positioned therein and adapted to close under excess pressure developed within the cylinder [6. Upon such closure of the check valve 52 communication between the passage 45 and the cylinder IS on the adjacent side of the piston 40 is eifected by means of the restricted orifice 48 only.

The passage 46 in the head 3!! communicates with a branch passage 54 which extends perpendicularly thereto and overlies the reservoir 22. The branch passage 54 communicates with one end of a tubular member 56 which extends longitudinally through the reservoir 22 to the support I2. The opposite end of the tubular member 56 communicates with a branch passage 58 which extends transversely to the outer wall of the support 12. The arrangement thus provides a pair of passages 44 and 58 communicating with points Within the cylinder E6 on either side of the piston 40. The reservoir 22 has an outlet formed by a tubular member 51 which projects for a short distance into the reservoir 22 from the support l2 and communicates with an outlet passage 59 extending transversely to the exterior of the support l2.

Manual pump The pump and control valve assembly of this invention is jointly contained within a casing 60 which is secured by bolts 62 to the wall of the support 12 overlying the passages 44, and 59. The casing 89 is bored transversely in two places to provide a pair of substantially parallel pump chambers 64. Suitable sealing disks 65 are pro vided at each end of the chambers 64 which have individual pump pistons 65 mounted for reciprocation in the respective chambers. Such movement of the pump pistons 6% is eflfected by the provision of rack teeth 58 thereon which operatively engage with a pair of pinions 7t, 7! respectively. Pinion T9 is in axial alignment with pinion ii and has a hollow stem '52 journaled in the casing 69 and projecting therefrom. A cruciform handle socket Z4 is secured to the projecting end of the stem 12 for the reception of an operating handle '86 in any one of the four socket arms. Preferably, a locking lug 18 projects from one of the arms of the socket 14 for cooperation with an apertured projection 19 on the casing Gil to receive a padlock or other device for locking the parts in any desired position of operation.

The handle 3'6 is adapted to be oscillated through an are set by the toothed portion of the pinions 1G, 7! which are consequently rotated in an arcuate path. Provision is made in this invention for rotating both pinions i H simultaneously or for retaining the pinion 1! stationary while the pinion rotates. Under the latter condition of operation, only th one pump piston 66 associated with the pinion IE will be reciprocated, as will be apparent, thus reducing the effort required on the operating handle 76. To this end, driving means for the pinions '58, H are provided and take the form of a sleeve 15 which is slidable axiall of the pinions iii, 7.! which are suitably bored for its reception. The sleeve 15 carries a pair of longitudinally aligned key elements ll which in one position of the sleeve :5 operatively engage with suitable keyways H9 formed in each of the pinions Ell, H and adapted to register longitudinally one with the other. However, the key elements I? are positioned sufficiently close together on the sleeve 15 that both may be contained within the one pinion H as will appear hereinafter.

The sleeve 15 is mounted on a selector rod 8! which is slidable at one end in the hollow stem 12 and in an apertured projection 33 on the easing Bil at the opposite end. The selector rod 8! is suitably anchored at either end thereof to the sleeve 75 to prevent relative movement. Since the sleeve 15 is shorter in length than the combined pinions 18, l I, it will be apparent that the key elements Tl can be located by slidable movement of the selector rod 8! either in the position shown in Fig. 3 for cooperation with the keyways ITS in both pinions or for cooperation with the single keyway l'lE in the pinion i! only. In the latter event, pinion Til only will be rotated by operation of the handle '56 since the sleeve '55 and key elements I! will be ineffective as a driving means in this position of adjustment.

The casing 60 contains a plurality of fluid passageways for conveying fluid from the reservoir 22 to the pump chambers 64 as will now be described. Reference may be had to Fig. 11 for the purpose of tracing the fluid passageways pertinent to this description, but it will be understood that this illustration is schematic only and reference should be had to the remaining figures of the drawing for a proper understanding of the preferred construction.

A pump inlet passage extends through the casing 63 substantially parallel with the axis of the pump chambers 55 and communicates. therewith adjacent the sealing means 65 at either end thereof by means of branch passages I81, 82 at one end of the pump chambers 64 and by means of branch passages 33, 84. at the opposite end thereof. Return of fluid from the chambers 6d through the branch passages I3I, 84 to the inlet passage 86 is prevented by the provision of a plurality, in this instance four, check valves 85 positioned one at each junction of these respective passages. The pump inlet passage 330 communicates intermediate its ends with an angular branch passage 88 which in turn, communicates with the outlet passage 59. It is apparent, therefore, that fluid from the reservoir 22 can be introduced to both ends of the pump chambers 84 from the single outlet passage 59.

A second transverse passage 90 extends through the casing 66 substantially parallel with the axis of the pump chambers 64 and spaced from the transverse passage 80. The opposite ends of the transverse passage 90 terminate in two pairs of angular branch passages 9|, 92 and 93, 9'4. The passages s2 and a l are axially aligned with the branch passages 82 and 84 respectively and communicate therewith. Return of fluid to the pump chambers 64 from the passage 90 is prevented by the provision of a plurality of check valves 96 positioned one at each intersection of the passage 96 and the branch passages 9I93 respectively.

Control valve As shown in Fig. 3 the control valve of this invention comprises a valve chamber 98 formed in the casing 8c transversely of and in spaced relation to the pump chambers 6-4. The valve chamber as has a bottom wall I60 extending substantially parallel with a portion of angular passage 88 and providing a seat for a disk valve member 502 having a. reduced stem I 84 spaced from the wall of the chamber 98. An operating stem Ills projects from the reduced stem Hi4 through the wall of the casing 60: and is provided with a handle H38 by means of which the valve member I82 may be rotated between controlling positions on its seat I00. As indicated in Fig. 2, such rotation occurs through an arc of approximately 180 and the legends Open and Shut on the casing 60 have reference to the position of the operated element, such as the main valve stem Isl shown in Fig. 1.. As will hereinafter be fully apparent, the valve handle I08 may also occupy an intermediate position in which communication is prevented between the reservoir 22 and the hydraulic cylinder I6 under certa n alternative modes of operation of the operated element.

The valve chamber 98 is positioned in the casing 58 with reference to the transverse passage 90 so that the chamber 98 intersects the passage 98 intermediate its ends and provides access for fluid into the space in the chamber 33 defined by the reduced st portion lot. A transverse port H0 is formed in the reduced stem portion I04 and communicates with an eccentric recess IIZ formed in the valve member I02 adjacent the valve seat The recess I12 communicates at all times with a connecting passage I'M which connects the valve seat Hill with the passage 88. The recess E 52 also communicates with either one of a pair of laterally disposed passages H6, IIS formed in the casing E9 on either side of the passage El i for communication with the valve seat Hill. The passage I I6 is axially aligned with the passage 44 in the support I2. The valve member I02 is provided with an oifset port I20 which extends therethrough from the valve seat I09 to the stem IM substantially parallel with the wall thereof and is adapted to connect the transverse passage with either one of the lateral passages I I5, IIB as will hereinafter be apparent.

Th valve member I02 is axially apertured between the recess H2 and the port H0 for the reception of a relief valve means in the form of a ball valve member I22 biased by a spring I26 against the wall of the port III; and being yieldable to permit the escape of fluid thereby under excess pressure and through the passages I I4, '88 and 59 to the reservoir 22.

The valve member m2 is biased toward the valve seat I69 by a coil spring I24 mounted on the reduced stem portion HM and operative between the valve member !02 and an anti-friction bearing I25 (Fig. 3) in which is journaled a portion of the operating stern Hi6 within the valve chamber 98.

Operation In the operation of the apparatus, fluid is drawn from the reservoir 22 by reciprocation of the pump pistons 66 when operated by the handle 18 through the mechanism described. In a manual closing cycle of the operated element, such the valve stem it, the selector rod BI is positioned to place the sleeve 75 and the key elements IT in position to cause the pinions 79, II to actuate both pistons 66 simultaneously. Under such conditions the parts are in the positions shown in Fig. 3 and the handle it may be oscillated to cause the pistons 56 to reciprocate in their respective chambers 5 3 to intake fluid from the reservoir 22. Since the control valve member I02 will have been placed in Close position to connect the recess II2 with the passages IM and I It, as shown in Fig. 11, then fluid expelled from the pump chambers 56 is transmitted under high pressure through the passages 92, 94 as the case may be and passage 93 into the control valve chamber 98. Such fluid will then pass through the valve port I 20, passage IIS and passage 58 in the support 52 to flow through the tubular member 56, passage te l and passage 46 and enter the hydraulic cylinder it above the piston 40 by way of the check valve 55 and restricted orifice 48. The fluid will exert sufficient force upon the piston iii to move the valve stem M in a direction to close the conventional valve being operated. During this cycle, fluid beneath the actuating piston 40 is forced from the space in the hydraulic cylinder it through passage 45, passage 1 IE, recess H2, passage H4, passage Bil, check valves 86, to the passages 82, at, It! and 83 for the pump chambers 6 3.

It should be observed that sufficient fluid is drawn from the reservoir 22 to equalize the displacement diiierence between the fluid volume above the piston 49 and the volume beneath the piston 46 due and equal to the displacement volume of the operating stem It causing the fluid level in the reservoir 22 to be lowered from a level visible in the upper sight gage 35 to a level visible in the lower sight gage 3 6.

In the event that the final closing of the operated element requires excessive manual effort, then the selector rod 8I is repositioned to place the sleeve 75 and key elements l? in a position where motion of the pinion 76 cannot be transmitted to the pinion H. Consequently, during oscillation of the handle 76 only the pinion I6 and its related piston 66 are actuated with reduced effort to intake and expel fluid through the described passages by way of the control valve means I02. Thus, while a similar and sufllcient downward force is exerted upon the main piston 40, less manual effort is required than that necessary where both pump pistons 66 move simultaneously.

In moving the operating stem I4 in the opposite direction, that is during a main valve opening cycle, it is probable that undesirable manual effort would initially be required if both pump pistons 56 were actuated simultaneously. Consequently, the selector rod 8! is preferably positioned to place the sleeve I in position to register both key elements T! with the keyway I9 in the single pinion II. Consequently, oscillation of the handle I6 as described will cause rotation of the pinion '10 only and actuation of its single related pump piston 66.

In this opening cycle, the control valve handle I08 is rotated approximately 180 to oppositely align the control valve port I28 with the passage H5. Hence, the recess II2 connects the passage H4 with passage IIB under these conditions. Thus, fluid under pressure created by the pump piston 56 will flow through the passages IIS and 44 into the hydraulic cylinder I3 beneath the piston 49 to react with sufficient force to open the operated element connected to the operating stem I4. The return of fluid from above the piston 40 will be clear from the foregoing description of the closing operation as will the return of fluid to the reservoir 22 to equalize the displacement difference due and equal to the stem I4. The fluid level rises from the lower sight gage 36 to become visible in the upper sight gage 34.

In this opening cycle, the check valve 50 will close in the event the operating speed becomes greater than desirable. Thus, fluid can flow from the cylinder It only through the restricted orifice 48 and an automatic check is provided for arresting high velocity in the opening direction.

During the opening cycle, the operated element such as a conventional valve frequently requires less actuating force after the initial opening is effected. Thus, after an initial opening movement utilizing a single pump piston 66, the selector rod 8i can be repositioned to place the key elements 1'! in the position shown in Fig. 3 wherein both pinions 13 and 'II are actuated. Since in such event both pistons 66 will be actuated simultaneously when the handle I6 is operated as described, the remaining amount of movement of the operating stem I4 is eifected at an increased speed.

In instances where a source of fluid pressure is available and power operation of the valve in addition to manual operation is desirable, a modified form of apparatus may be utilized. Reference may be had to Fig. '7 wherein a pair of pipe connections I30, I32 is provided in the casing 5!! for communication with the passages H6 and H8 respectively. As shown in broken lines, a pair of fluid conveying lines is connected to the pipe connections I30, I32 and to a multi-way valve which in turn is connected to a power driven pump. Prior to such power operation, the control valve member I62 is placed in the intermediate position between Open and Close as described. to isolate the reservoir 22 and the pump chambers I34 from the available source of fluid pressure. As indicated in Fig. 11, the pipe connections I30, I32 bypass the control valve member I02 and the recess II2 does not register with either passage II6 or H8 in this position.

When the multi-way valve is placed in appropriate position, fluid under pressure is permitted to flow into the pipe connection I30 and passage H6 in the casing 60 to the passage 44 to enter the hydraulic cylinder It below the piston 40 and operate the valve stem I4 in a direction to open the conventional valve being operated. During this cycle, fluid above the actuating piston 40 is forced from the space in the hydraulic cylinder I6, passage 53 and passage II8 to the pipe connection I32 and multi-way valve to any suitable reservoir at the available source of fluid pressure.

Closure of the conventional valve being operated through the valve stem I4 is effected upon reversal of the port alignment of the multi-way valve whereupon fluid enters the pipe connection I32, passage H8 and passage 58 to enter the hydraulic cylinder I5 above the piston 40 by way of the check valve 50 and restricted orifice 58. Since the closing operation of the conventional valve has been described in connection with the operation of the manual pump, further description is deemed unnecessary.

A further modified form of device is shown in Fig. 10 wherein a main piston I34 is provided with a cylindrical extension I36 which is cooperable with the wall of a hollow projection I38 formed on the support I40. The passage 44 in this embodiment is formed in the support I48 and communicates by way of a restricted opening I42 with the interior of the projection I38 beneath the extension I36. Since a slight clearance exists between the extension I36 and the wall of the projection I38, fluid in the cylinder I6 beneath the piston I34 will create a dashpot effect and serve to cushion the conventional valve being operated by the valve stem I4 during its final closing movement.

It will be apparent that the pump and control valve assembly of this invention could be located at a remote point from the operated device and connected to the support by suitable pipes to transmit fluid pressure to the hydraulic actuator. These and other changes could be made in the arrangement of parts and in the details of construction within the scope of the appended claims.

I claim:

1. Pumping means comprising in combination, a casing providing a pair of cylinders, a pair of pistons reciprocably mounted in said cylinders respectively, each end of each piston forming with the adjacent walls of its associated cylinder a pressure generating chamber, means defining a pair of racks each operatively associated with one of said pistons respectively, pinion means rotatable in said casing and engageable with said racks for reciprocating said pistons, manually operable actuating means, a driving element between said actuating means and said pinion means for transmitting torque therebetween, said element having a first position wherein said actuating means is operatively connected to both of said pistons and a second position wherein said actuating means is operatively connected to a selected one of said pistons, manually operable means for moving said element between said positions, and means for passing fluid under pressure from said chambers upon reciprocation of said pistons.

2. Pumping means as claimed in claim 1 where in said pinion means includes a pair of pinions meshing respectively with said racks, said driving element being connected to both of said pinions in said first position and to a selected one of said pinions in said second position.

3. Hydraulic operating means for a fluid motor comprising a casing having at least one pump chamber therein, pumping means in said chamber, manually operable means for actuating said pumping means, a first passage in said casing communicating with said chamber and adapted to be connected to one source of fluid under pressure, a valve chamber in said casing, second and third passages in said casing communicating with said valve chamber and adapted to be connected to the fluid motor, a fourth passage in said casing for conveying fluid discharged by said pumping means to said valve chamber, control valve means in said valve chamber having a first position wherein said fourth passage communicates with said second passage, a second position wherein said fourth passage communicates with the said third passage, and a third position wherein communication between said fourth passage and said second and third passages is prevented, means for moving said control valve between said positions, and a pair of auxiliary passages in said casing communicating with said second and third passages respectively and adapted to be connected to a second source of fluid under pressure.

4. Pumping means comprising in combination, a casing providing a pair of cylinders, a pair of pistons reciprocably mounted in said cylinders respectively, each end of each piston forming with the adjacent walls of its associated cylinder a pressure generating chamber, means for passing fluid under pressure from said chambers upon reciprocation of said pistons, means defining a pair of racks each operatively associated with one of said pistons respectively, a pair of axiall aligned pinions in said casing and engageable respectively with said racks, and driving means engageable with said pinions for reciprocating said pistons, said driving means including an element slidable axially relative to said pinions and having a first position wherein said driving means is operatively connected to both of said pinions and a second positionwherein said driving means is operatively connected to a selected one of said pinions.

5. Pumping means as claimed in claim 4 wherein said axially aligned pinions have hollow walls for reception of said slidable element therein, and interengaging means on said hollow walls and said element operable in said first position of said element on both of said pinions and being disengaged from said selected one of said pinions in said second position.

6. Pumping means comprising in combination, a casing having a pair of substantially parallel cylinders therein, a pair of pistons reciprocably mounted in said cylinders respectively, each end of each piston forming with the adjacent walls of its associated cylinder a pressure generating chamber, means for passing fluid under pressure from said chamber upon reciprocation of said pistons, said pistons each having a rack formed on the side wall thereof, a pair of axially aligned hollow pinions extending transversely of said pistons and meshing respectively with said racks, a hollow stem on one of said pinions and extending exteriorly of said casing, manual operating means carried by said stem for rotating said one pinion, a slidable element extending through said stem and said pinions and accessible exteriorly of said casing, and interengaging means on said pinions and said slidable element operative in one position of the latter for connecting both pinions to said operating means and in another position for connecting said one pinion only to said operating means.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 99,403 Cardwell Feb. 1, 1870 162,256 Starks Apr. 20, 1 17 4 Hull Apr, 4, 1876 1,463,310 Davis July 31, 1923 1,589,389 Headstream June 22, 1926 1,616,841 Beebe Feb. 8, 1927 1,680,536 Gensmer Aug. 14, 1928 1,794,356 Baker Mar. 3, 1931 2,311,443 Keeler Feb. 16, 1943 2,352,390 Kirkland June 27, 1944 2,440,060 Page Apr, 20, 1948

Images