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Publication numberUS2322739 A
Publication typeGrant
Publication dateJun 22, 1943
Filing dateNov 14, 1939
Priority dateNov 14, 1939
Publication numberUS 2322739 A, US 2322739A, US-A-2322739, US2322739 A, US2322739A
InventorsHarry H Vanderzee
Original AssigneeSullivan Machinery Co
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Hydraulically operated apparatus
US 2322739 A
Abstract  available in
Images(3)
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Claims  available in
Description  (OCR text may contain errors)

June 22, 1943. H. H. VANDERZEE 2,322,739

HYDRAULICALLY OPERATED APPARATUS I Filed Nov. 14, 1959 s Sheets-Sheet 1 v June 22, 1943. VANDERZEE 2,322,739

HYDRAULICALLY OPERATED APPARATUS Filed Nov. 14, 1959 3 Sheets-Sheet 2 [Elam or: any/5. Vail/2166.

vJune 22, 1943. I H, VANDERZEE 2,322,739

HYDRAULICALLY OPERATED APPARATUS Filed Nov 14; 19:59 5 Sheets-Sheet a lzzyjar 16 175916. .1729. 12' W 36 7 1;

Patented June .22, 1 943 UNITED s'rik rus PATENT OFFICE I nmnaumcmjfii ntzrnp nrraua'rus I 7 Harry B. Vanderlec, Michigan City, Ind.,

ass

or to Sullivan Machinery Company, a om. tion of Massachusetts I v 15 Claims.

This invention relates to hydraulic pump systems, and more particularly to improvements in the controlling means for a rotary drilling apparatus of the type embodying hydraulically operated feeding means and hydraulic operating means forthe drill chuck. y

In drilling apparatus of the rotary core type, the drill bit is usually fed by hydraulic pressure toward and from the work. Inthe normal drilling operation, the drill bit is fed toward the work rather slowly and; as drilling progresses and the weight of the drill rods increases, apoint is finally reached when no hydraulic feeding force is necessary. and beyond this point the weight of the drill rods, in excess of thepressure required to feed the drill bit to the work, must be removed from the bit, or an excessive feeding pressure on the bit will? result. Ordinarily. when the weight of the drill rods becomesexcessive, the excess weight is removed from the -bit by hydraulic pressure. In other words. the. feeding pressure applied to the drillbit is determined by the weight of thedrill rods. 'The hydraulic pressure in the hydraulic system must, be suflicient for lifting the weight of the drill rod line for a hole of a given depth. .It is accordingly evident that the feeding pressure on the drill bit must be relatlvely high during starting of the drill hole, and as the length of the rod line increases; the feeding pressure must be reduced, and when the ing apparatus wherein the volume of liquid supplied, to the system may be varied in accordance with .the demand. Yet another object is to provide a dual capacity pump arrangement embodying a pump unit of small capacity and a pump unit of large capacity, the pump of small capacity normally maintaining the required; pressure in the fluid system when a small volume is required, and the pump of large capacity supplying a substantially greater volume of of the small capacity pump eliminating the excessive generation of heat in the fluid system which would occur if the large pump had to force;

vention will, however, hereinafter more fully ap- I pea In the accompanying drawings there is shown for purposes of illustration one form which the invention may assume in practice.

In these drawings: Fig. 1 is a vertical sectional view, withparts in elevation, illustrating a portion of a drilling apparatus with which the inventionis associated.

weight of the rod line becomes excessive, the

hydraulic pressure in the feeding'means must be suflicient to remove the excessive rod line weight from the drill bit. Also it is desirable to obtain a rapid feeding movement of the'drill chuck 1 when the latter is moved to a new rod line gripping position after the feed has moved its distance of travel. Also under certain conditions, it is required that the rod line be raised and lowered while being rotated, and here again a relatively rapid rate of chuck advance is necessary for the sake of efliciency.

An object of this invention improved hydraulic pump system having improved controlling means' Another object is to provide an improved multiple pump system embodied in the hydraulic feeding means of a rotary core drill whereby the drill bit is fed and 'controlled in an improved manner. A further'object is to provide improved hydraulic operating means for the drill'ch uck associated with the is to provide an fluid system for. thefeeding means whereby the chuck may be controlled in an improved manner. Yet another object is to provide animproved multiplepum'p system for a rotary drill- 'Fig'. 2 is'an enlarged fragmentary side elevational view of a portion of the drilling apparatus shown in Fig. 1.

Fig. 3 is an enlarged horizontal sectional view taken substantially on line 3-3 of Fig. 1.

Fig. 4 is an enlarged detail sectional view show ing a portion of one of the fluid supply connection s.

Fig. 5 is an enlarged side elevational view of one of the control valve mechanisms.

1 Fig. 6 is a cross sectional view taken on line 6-6 of Fig. 5.

Fig. 7 is a view similar to Fig. 6, showing the control valve in a different position.

Fig. 8 is a cross sectional view taken on line 's-a'or Fig. 5.

Fig. 9 is a view'sim-ilar control valve in a difierentposition.

Fig. 10 is an enlarged side elevational view of the by-pass valve mechanism.

Fig. 11 is a cross sectional view taken on line l|--'-il of'Fig. 10. Fig. 12 is a view similar to Fig. by-pass valve in a different position. I

Fig. 13is a cross sectional view taken on line 13-43 of Fig. '10.

Fig. 14 is a. view similar toFig. 13, showing the by-pass valve in a different position.

fluid to the system when rapid operation is desired, as for I rapid drilling in soft formations, the utilization to Fig. 8, showing the 11, showing the s Fig. 15 is an enlarged side elevational view of Fig. 1'7 is a view similar to Fig. 16, showing the feed control valve in a different position.

Figs. 18 and 19 are diagrammatic views illustrating the hydraulic fluid system.

In this illustrative embodiment of the invention the improved hydraulic fluid system is shown embodied in a rotary drilling apparatus of the heavy duty, oil well drill type generally similar to that disclosed in the patent to H. C. Johansen, No. 2,114,305, patented April 19, 1938, although it will be evident that various features of the invention may be incorporated in drilling apparatus of various other types.

The rotary drilling apparatus illustrated herein comprises a vertical frame structure I mounted on a suitable base 2 and supporting a transverse upper frame 3. Secured within heads 4 mounted within the upper portion of the frame structure are vertical hydraulic feed cylinders 5, 5 arranged in parallel relation at the opposite sides of the frame structure and containing reciprocable feed pistons 6 having piston rods 1 extending downwardly through stuffing boxes 8 arranged within the cylinder heads 4. Formed along the opposite sides of the frame sections I beneath the feed cylinders are vertical guideways 9 having mounted therein, for vertical reciprocatory movement, sliding guide shoes II. The lower portions of these sliding guide shoes are secured, as by screws. II, to a transverse frame I2, the frame I2, together with the sliding guide shoes, forming a sliding crosshead structure vertically reciprocable along the guideways with respect to the frame structure I. .As illustrated, the lower ends of the piston rods I are secured at I3 within the transverse crosshead frame I2, so that when hydraulic pressure is supplied to the feed cylinders the feed pistons are reciprocated therein, moving vertically therewith the sliding crosshead structure. Journaled in ball bearings I4, within the transverse crossi head frame I2, is a rotary drive sleeve I5 having a central opening I6 through which a drill rod ll of the drilling apparatus is adapted to extend.

Keyed to the drive sleeve I5 and arranged be-' tween the ball bearings I4 is a spur gear I8 meshing with and driven by a spur gear I9 (see Fig. 3) likewise joumaled within the transverse crosshead. The gear I9. is keyed to a vertical drive shaft 2I, the latter having telescopic relation with a driving element arranged within the transverse upper frame 3, in the manner fully described in the above mentioned Johansen patent, so that irrespective of the position of the sliding crosshead structure along its guideways the drive sleeve may be rotated.

Carried by the drive sleeve I5 is a hydraulically operated chuck mechanism comprising vertical cylinders 22 carried by the transverse crosshead frame I2 andcontaining vertically reciprocable pistons 23 having their piston rods 24 extending upwardly through stufllng boxes 25 carried by the transverse crosshead frame I2. The upper ends of the piston rode 24 are secured at 26 to a transverse frame 21, the latter supporting a ball bearing in which is joumaled the cylindrical hub 29. of a rotatable chuck casing 30. Guided within guideways 3I formed within a cylindric enlargement 32 of the drive sleeve I5 are chuck jaws 33 adapted to grip the drill rod.

Mounted in the chuck casing are blocks 4, co n I hected by pivoted links a to the chuck-Jaws so that when hydraulic pressure is supplied to the lower ends of the cylinders 22 the pistons 23 are moved upwardly, moving therewith the chuck casing, and, through the toggle links, moving the chuck jaws into gripping relation with the drill rod, thereby connecting the drill rod to the drive sleeve for rotation therewith.

Now referring to the means for supplying liquid under pressure to the chuck jaw operating cylinders 22, it will be noted that vertical pipes 31 are secured within the lower portion of the frame portion I, and these pipes extend upwardly through stumng boxes 33 carried within members 39 which constitute the securing elements for securing the lower ends of the piston rods I to the sliding crosshead frame I2. The pipes 31 extend upwardly within the bores 43 in the piston rods I, these piston rod bores being of slightly larger diameter than the diameter of the pipes, so that the liquid flowing through the pipes is discharged through the upper ends of the pipes into the piston rod bores. The piston rod bores communicate at their lower ends through ports 4| with annular chambers 42 formed in the sliding crosshead frame I2. As shown most clearly in Fig. 3, the annular chamber 42, at the right hand side of the transverse frame I2, is connected through a pipe 43 and branch pipes 44 to the upper ends of the bores of the cylinders 22 at the upper sides of the pistons 23, while the annular chamber". at the left handside of the frame I2, is connected through a pipe 45 and branch pipes 46 to the lower ends of the bores of the cylinders 22 at the lower sides of the pistons 23. When hydraulic pressure is supplied to the right hand supply pipe 31, shown'in Fig. 1, liquid under pressure flows to the right hand annular chamber 42 and thence through the pipes 43 and 44 to the upper ends of the cylinders 22, the pressure acting on the upper surface of the pistons 23 to move the latter downwardly into the position shown in Fig. 1, thereby to release the chuck jaws from the drill rod. When.hydraulic pressure is supplied to the left hand supply pipe 31, liquid under pressure flows to the left hand chamber 42 and thence through the pipes 45 and 48 to the lower ends of the cylinders 22, the pressure acting on the lower surfaces of the pistons 23 to move the latter upwardly to connect the chuck jaws with the drill rod. It is accordingly evidentthat irrespective of the adjusted position of the sliding crosshead structure within its vertical guideways relativeto the frame structure I, hydraulic pressure maybe supplied to the hydraulic chuck operating cylinders 22 through the supply pipes 31 telescopically arranged within the tubular feed piston rods I, As the structure of the drilling apparatus is fully described in the above mentioned Johansen patent, further description thereof is herein unnecessary.

Now referring to the improved hydraulic fluid system, it will be noted that a liquid pump 5| is provided, this pump being of the dual capacity type and preferably having a small capacity side and a large capacity side. This pump may consist of two distinct pumping units coupled'together,

one pump unit preferably having a substantially larger capacity than the other. The feature, hereinafter more fully explained, of the provision of means enabling supply from two sources in parallel when needed, but with power consumption and heat production minimized, is a feature of basic importance. The pump It herein comprises a large capacity unit 5| and a small capacity unit 52, these pump units being driven by essence a motor It. The intake sides oi the pump units 56. A branch conduit 66 leads from the conduit.

56 also to the valve mechanism 56 v(see Fig. The valve mechanisms illustrated and now tobe described are to be understood as but illustrative Y of the means which can be utilized to accomplish the desired functions.

The valve mechanism 59, as shown'in Figs. 5 to 9'in'clusive, comprises a valve casing 6| having a bore 62 containing a rotary control valve 63, the

latter having a suitable manual operating handle. The conduits 58 and 60 communicate with the valve bore at longitudinally spaced points, while communicating with the valve bore at points diametrically oppositetrom the conduits 58 and 66, respectively, are conduits 64 and 65. The valve is cut away at the opposite sides of a diametric plane to provide passages 66 and 61. Communicating at diametrically opposite points with the valve bore, midway between the conduits 58 and 64, are conduits 68 and 69 respectively leading, through the connections described with respect to Fig. 1, to the upper and lower ends of the chuck operating cylinders 22. The com duit 64 is connected to a return conduit 10, in turn communicating with a liquid discharge conduit ll leading back to the tank 51. Traversing the valve body is a passage 12 adapted to connect the conduits 60 and 65. When the valve 63 is in the position shown in Fig. 7, the supply conduit 56 and the exhaust conduit 64 are cut oi! from the conduits 68 and 66 leading to the chuck operating cylinders 22, and, as shown in Fig. 9, the conduit 60 is connected by the passage 12 in the valve with the conduit 65, so that liquid under pressure is conducted through the conduit 65 to a by-pass valve mechanism generally designated 13. When the valve 63 is in the position shown in Fig. 6, the supply conduit 56 is connected to the lower ends of the chuck operating cylinders 22 through the conduit 69, while the upper ends of the chuck operating cylinders are connected to exhaust through the conduit 64. When the position of, the valve 63 is reversed, the upper ends of the chuck operating cylinders are connected to the liquid supply while the lower ends of the cylinders are connected to exhaust. Whenever bypassing occurs through the passage I2 in the valve, thesupply of 1mm to the chuck operating cylinders 22 is always out on.

The by-pass valve mechanism 13 comprises, as shown in Figs. to 14 inclusive, a casing 14 having a bore 15 containing a rotary valve 16, the latter having a suitable manual operating handle. The conduit 65 communicates with the '55 either with the conduit II 'or the conduit 16. Also traversing the valve body is a passage 63 having a narrow bleeding or metering slot 86 for connecting the conduit "to the exhaust conduit 86 whereby the lay-passing of fluid past the valve 16, may be closely regulated. A conduit 85 connects the discharge side of the small pump unit 52 with the conduit 11. The conduit 11 leads to a valve mechanism, generall designated 66, for controlling the flow of liquid under pressure to the feed cylinders. I

The feed control valve mechanism 86 as shown in Figs. 15, iii-and 17 comprises a casing 81 having a bore 68 containing a rotary valve 69, the latter having a suitable manual operating handle.

The conduit 1'! communicates with the valve bore, and communicating with the valve bore, at a diametrically opposite point, is a conduit 90, the latter being connected to the return conduit H leading back to the tank. Also communicating with the valve bore in the same transverse plane with and located midway between the conduits .11 and 90 are conduits 9| and 82 leading respectively to the upper and lower ends of the feed valve bore, as shown in Fig. 11. and a conduit 11 communicates with the valve bore at a diametrically opposite point. Communicating with the valve bore at a point in the same plane with and I TI, and the conduit 18 has a branch conduit 8.0

communicating with thevalve bore in the same cylinders 5. The valve body is traversed by passages '93 and 94, and in the difierent positions of the valve the passage 93 is adapted to connect the conduit 92 with either the supply conduit T1 or the exhaust conduit 90, and the passage 94 is adapted to connect the conduit 9| either with the conduit 11 or'9ll, so that when liquid under pressure is supplied to one of the conduits 9|, 92 the other conduit is always connected to exhaust. Communicating withthe passage 93 is a bleeding or metering slot 95 whereby the flow of liquid under pressure from the bottoms of the feed cylinders may be closely regulated, thereby to enable regulation of the rate of forward feed. When the valve 89 is in the position shown in Fig.. 1'7, the supply of liquid under pressure through the conduits 9| and 92 to the .opposite ends of the feed cylinders is completely out oif, but the connection 92 from beneath the feed pistons has a .restricted connecticn through the slot 95, the passage 93 and alateral enlargement of the mouth of the passage with which .the exhaust conduit 90 connects, with the exhaust conduit 90, sothat during drilling under the weight of the red line the rate of feed can be controlled by finely regulating the escape of liquid from beneath the fluid pistons.

The supply conduits 58 and respectively leading from the discharge sides of the large arid small pump units are connected through relief valves 96 and 91 with a conduit 88 leading to the discharge conduit H so that when the pressure in the supply conduits becomes excessive the relief valves open automatically to relieve the pressure in the system. The relief valves 96 and 91 may be set at any appropriate pressures suitable to the particular'conditions encountered, but preferably the relief valve 91 for the large pump unit is set at a relatively lower pressure. than the pressure setting 'o'fgther'elief valve 96 for the small pump unit. This difference in pressure settings of the relief valves is desirable since at times, in'a drilling apparatus of the character disclosed herein, a relatively'high pressure must be available to effect certain auxiliary drill operating functions. However, such differences in the pressure settings of the relief valves do not come into effect in the structure embodying the present transverse planes as the conduit 19 (Fig. 13).

The valve 16 has a passage 8| provided with a widened mouth 82 for connecting the conduit invention, and, therefore, the pressure settings are of no particular. importance herein. In this instance, the feedingpressure is-determined by the position of the by-pass valve means and not by the'relief valve settings. of course, when both pump units are discharging to the feed cylinders 5; 5, the maximum pressure available is the setting pressure of the relief valve 81 for the large pump unit, as both pump units may by-pass through this relief valve.

From the foregoing it will be evident that the liquid discharged from the large pump unit 5| may be conducted, under the control of the valve 63, to the operating cylinder 22 of the chuck so that the full volume may be utilized to apply or release the chuck jaws. When the supply of liquid under pressureto the chuck operating cylinders 22 is cut oil, as shown in Fig. 7, the liquid flowing in the conduit 58 is lay-passed through conduit Gil, passage 12 in the valve and conduit I! to the by-pass valve mechanism 13. When the valve 16 is in the position shown in Fig. 12, the liquid is by-passed through conduit 18 to the return conduit'leading back to the tank. When the by-pass valve 16 is in the position shown in Fig. 11, liquid under pressure may flow from conduit 65 through the passage ii in the valve to the conduit Tl leading to the feed control valve mechanism 06. Liquid under pressure is continuously supplied from one (herein the small) pump unit through conduit 85 to the conduit I1, and when the valves 63 and 16 are in the positions shown in Figs. 9 and 11 pressure is supplied from the large pump unit to the conduit ll, so that the total available supply of pressure fluid is that delivered by the pump units combined. When the feed control valve 89 is in the position shown in Fig. 16, liquid under pressure may flow from conduit 11 through the valve passage $4 to the conduit 9i leading to the tops of the feed cylinders 5, and the bottoms of the feed cylinders are at that time connected to exhaust through conduit 92, passage $3 in the valve and conduit 90 leading to the liquid return conduit Ii. When the valve 89 is rotated to a position so that passage 93 connects conduits I1 and 82, and passage 94 connects conduits 90 and ll, pressure fluid is supplied to the bottoms of feed cylinders 5 and vented from the tops of feed.

cylinders 5. When the liquid supply from the large pump unit is connected to the return conduit, liquid under pressure may continue to be supplied from the small pump unit through conduit 85 to the feed cylinders. The large volume discharge from both pump units is utilized when a rapid rate of feed is desired, while the small volume discharge from the small pump unit is used in slow feed during normal drilling; and during the slow feedin operation the discharge side of the large pump unit is connected back to the tank through the return valve mechanism.

The presence of the small capacity pump eliminates the excessive generation of heat from the fluid system which occurs when a large volume of liquid is forced through a loaded by-pass valve for any substantial length of time. When the valve 16 is in the position shown in Figs. 12 and 14 the discharges from both the large and small pump units are conducted through the return conduit III back to the tank. When the valve I6 is in the position shown in Figs. 11 and 13, liquid under pressure may be. conducted through conduits 58, 65 and 11 to the feed control valve 86, so that the feed pistons may be fed upwardly or downwardly as desired under the control of the valve 88 at a relatively rapid rate. When the valve I6 is in'its by-passing position shown in Figs. 12 and 14,the wide mouth 82 of the passage 8| permits a limited amount of adjustment of the valve, thereby to permit bleeding of the output from the small pump unit by means of the metering slot 84 to whatever pressure is required. The rate and direction of feed may then be determined by the position '0! the feed control valve 89. When the weight of the drill rods is in excess to the pressure required to feed the drill bit to the work both pump units may be by-passed, and the rate of feed is at that time regulated by metering the flow of liquid from the lower ends of the feed cylinders beneath the feed pistons by means of the metering slot in the four-way valve as heretofore explained. Further, when varying or cavernous formations are encountered by the drill bit, the "under feed" method of feeding the drill bit may be employed. and at that time the small pump unit may supply liquid under pressure to the upper ends of the feed cylinders above the feed pistons, and the rate of feed may be controlled, as by regulating the amount of liquid by-passed.

As a result of this invention, it -will be noted that an improved controlling means is provided in the hydraulic fluid system of a rotary drilling apparatus whereby the feeding means may be controlled in an improved manner. It will further be evident that by the provision of the improved controlling means for the hydraulic feeding means, the feeding pressure on the drill bit may be controlled through a relatively wide range. hydraulic controlling means for the drill chuck is associated with the fluid system for the feeding means whereby the chuck may be controlled in an improved manner. It will also be evident that by the provision of the improved multiple pump system the volume of the liquid supplied to the system may be varied in accordance with the demand. Other uses and advantages of the invention will be clearly apparent to those skilled in the art.

While there is in this app cation specifical y described one form which the invention may assume in practice, it will be understood that this form of the same-is shown for purposes of illustration and that the invention may be modified and embodied in various other forms without departing from its spirit or the scope of the appended claims.

What I claim as new and desire to Letters Patent is:

secure by 1. In a hydraulically operated apparatus, hy-

draulically operable means for selectivel gripping and releasing a tool, hydraulically operable means for selectively feeding and retracting a tool when it is gripped by said first mentioned hydraulically operable means. a relatively large capacity pumping unit, a relatively small capacity pumping unit. a valve means for selectively rendering one of said pumping units operable to supply fluid to said first mentioned hydrauli- It will also be noted that an improved 2. In dhydraulically operated apparatus, hydraulically operable means for selectively gripping and releasing a tool, hydraulically operable means for selectively feeding and retracting a tool when it is gripped by said first mentioned hydraulically operable means, a' relatively large capacity pumping unit, a relatively small capacity pumping unit, valve means for selectively rendering said first mentioned pumping unit operable to supply fluid to said first mentioned hydraulically operable means to efi'ect gripping of a tool or to trap fluid in said first mentioned hydraulically operable means to maintain tool gripping while rendering the discharge of said first men'- tloned pumping unit available for other purposes, means for selectively rendering one or both of said pumping units operable to supply fluid to said second mentioned hydraulically operable means, a return line, and means operable to connect the discharge from one or both of said pumping units freely to said return line when the same are not supplying fluid to said second men'- tioned hydraulically operable means.

3. In a hydraulically operated apparatus, hydraulically operable means for selectively grip; ping and releasing a tool, hydraulically operable means for selectively feeding and retracting a tool when it is gripped by said first mentioned hydraulically operable means, a relatively large ca pacity pumping unit, a relatively small capacity pumping unit, valve means for selectively rendering one of said pumping units operable to supply fluid to said first mentioned hydraulically operable means to effect gripping of a tool or to trap fluid in said first mentioned hydraulically operable means to maintain tool gripping while rendering the discharge of said pumping unit available for other purposes, means for selectively rendering the second or both of said pumplng units operable to supply fluid to said second mentioned hydraulically operable means, a return line, and means operable to connect the discharge from one or' both of said pumping units freely to said return line when the same are not supplying fluid to said second mentioned hydraulically operable means.

4. In a hydraulically operated apparatus, hydraulically operable means for selectively gripping and releasing a tool, hydraulically operable means for selectively feeding and retracting a tool when it is gripped by said first mentioned hydraulically operable means, a relatively large capacity pumping unit, a relatively small capacity pumping unit, valve means for selectively rendering said first mentioned pumping unit operable to supply fluid to said first mentioned hydraulically operable means to efiect gripping of a tool or to trap fluid in said first mentioned hydraulically operable means to maintain tool gripping while rendering the discharge of sa d first mentioned pumping unit available for other purposes, means for selectively rendering the second or both of said pumping units operable to supply fluid to said second mentioned hydraulically operablemeans, a return line, and mean operable to connect the discharge from one or both of said pumping units freely to said return line when the same are not supplying fluid to said second mentioned hydraulically operable means.

5. In a hydraulically operated apparatus, hydraulically operable means for selectively gripping and releasing a tool, hydraulically operable means for selectively feeding and retracting a tool when it is gripped by said firstmentioned hydraulically operable means, a relatively large capacity pumping unit, a relatively small capacity pumping unit, valve means for selectively render- 7 ing one of said pumping units operable to supply fluid to said first mentioned hydraulically oper-' able means .to eflect gripping. o! a tool or to trap fluid in said first mentioned hydraulically operable means to maintain tool gripping whilerendering the discharge of said pumping unit avail- .able for other purposes, means for selectively rendering one or both of said pumping units operable to supply fluid to said second mentioned hydraulically operable means, a return line, and means operable to connect the discharge from one or both of said pumping units freely to said return line when the same are not supplying fluidto said second mentioned hydraulically operable means, said latter means embodying metering slot means whereby the discharge from one of said pumping units may be closely regulated.

6. In a hydraulically operated apparatus, hy-

hydraulically operable means to eifect gripping of a tool or to trap fluid in said first mentioned hydraulically operable means to maintain tool gripping while rendering, the discharge of said first mentioned. pumping unit availablefor other purposes, means for selectively rendering one or both of said pumping unit operableto supply fluid to said second mentioned hydraulically operable means, a return line, and means operable to connect the. discharge from one or both of said pumping units freely to said return line'when the same are not supplying fluid to said second mentioned hydraulically operable means, said latter means embodying metering slot means whereby the discharge from the small pumping unit may be closely regulated.v

7. In combination, a hydraulically operable device including an element subjectable to working pressure on its opposite sides, a pump of small capacity, a pump of larger capacity, a valve casing providing a bore having a connection with said pump of larger capacity, and at opposite sides of said first mentioned connection connections to the opposite sides'of said element or said hydraulically operable device, said valve casing bore also having a second connection with said larger capacity pump, means providing a connection for said bore with said smaller capacity pump, and a valve movable in said casing and having means formed thereon toward one end thereof for connecting said first connection a selectively with the opposite sides of said element of said hydraulically operable device and means formed adjacent the other end thereof for establishing or interrupting communication between said second. connection and said means providing a connection with said smaller capacity operated means and to said mechanism return line to said pumps, and controlling means for fluid flow relative to them from said pumps including means providing three valve receiving bores, three valves movable in said bores respectively, one in each of said bores, fluid supply conduits leading from said pumps, one fluid supply conduit having passages leading to two of said bores and another having communication with the third of said bores, passage means for connecting said last'mentioned bore with one of the others, the valve in the third mentioned bore being movable therein to control said mechanism and the connection of the third mentioned bore with the one of the others to which said passage means leads from said third mentioned bore, the valve in the bore to which said last mentioned passage means leads controlling communication'between that bore and said third mentioned bore and communication between each of said supp y conduits and the return line to said pumps, and the valve in the other of said bores controlling said hydraulically operated means.

9. In combination, a hydraulically operable device including an element subjectable to working pressure on its opposite sides, a pump of small capacity, a pump of larger capacity, a valve casing providing a bore having a connection with said pump of larger capacity, and at opposite sides of said first mentioned connection connections to the opposite sides of said element of said hydraulically operable device, said valve casing bore also having a second connection with said larger capacitypump, means providing a connection for said bore with said smaller capacity pump, and a valve movable in said casing and having means formed thereon toward one end thereof for connecting said flrst connection selectively with the opposite sides of said element viding valve-receiving bores, valves movably arranged in said bores respectively, a passage connecting the pump of large discharge capacity with one of said bores, a second passage connecting the pump of small discharge capacity with the other bore, a third passage connecting said boreswhereby the liquid flowing from the large capacity pump from said one of said bores flows throughsaid third passage to said other bore, the liquid flowing past the valve in said one of said bores to said third passage, and a fourth passage communicating with said second passage, and said valve in said other bore controlling the flow of liquid from said third passage to said fourth passage. 1

11. In a hydraulically operated apparatus, a pump having a small discharge capacity, a pump having a larger discharge capacity, means providing valve receiving bores, valves movably arthrough said third passage to said other bore, the liquid flowing past the valve in said one of said bores to said third passage, a fourth passage communicating with said second passage, and

said valve in said other bore controlling the flow I of liquid from said third passage to said fourth passage, and the liquid from the smaller discharge capacity pump flowing directly from the second passage to said fourth passage independently of control of the valve in said other bore.

12. In a hydraulically operated apparatus, a pump having a small discharge capacity, a pump having a larger discharge capacity,-means providing valve receiving bores, valves movably arranged in said bores respectively, a passage connecting the pump of large discharge capacity with one of said bores, a second passage connecting the pump of small discharge capacity with the other bore, a third passage connecting said bores whereby the liquid flowing from the large capacity pump from said one of said bores flows through said third passage to said other bore, the liquid flowing past the valve in said one of said bores to said third passage, a fourth passage communicating with said second passage,

1 and said valve in said other bore controlling the flow of liquid from said third passage to said fourth passage, and the liquid from the smaller discharge capacity pump flowing directly from the second passage to said fourth passage independently of control of the valve in said other bore, and a discharge line communicating with said other bore and the valve in said other bore controlling the connection of said second passage with said discharge line.

13. In a hydraulically operated apparatus, a pump having a small discharge capacity, a pump having a larger discharge capacity, means providing valve receiving bores, valves movably arranged in said bores respectively, a passage connecting the pump of large discharge capacity ranged in said bores respectively, a passage conwith one of said bores, a second passage connecting the pump of small discharge capacity with the other bore, a third passage connecting said bores whereby the liquid flowing from the large capacity pump from said one of said bores flows through said third passage to said other bore, the liquid flowing past the valve in said one of said bores to said third passage, a fourth passage communicating with said second passage, and

said valve in said other bore controlling the flow of liquid from said third passage to said fourth passage, and the liquid from the smaller discharge capacity pump flowing directly from the second passage to said fourth passage independently of control of the valve in said other bore, and a discharge line communicating with said other bore and the valve in said other bore controlling the connection of said second .passage with saiddischarge line, said valve in said other bore also controlling the connection of said third passage with said discharge line.

14. In a hydraulically operated apparatus, a pump of small discharge capacity, a pump of large discharge capacity, means providing valvereceiving bores, valves arranged in said bores respectively, a passage connecting the pump of large discharge capacity with one of said bores, a second passage connecting the-pinnp of small discharge capacity with said other bore, a third passage connecting said bores whereby the liquid valve in said other bore controlling the connection or said third passage with said second passage and with said discharg line, and a fourth passage communicating with said one bore and controlled by the valve in said one bore.

15. In a hydraulically operated apparatus, a pump of small discharge capacity, a pump of large discharge capacity, means providing valvereceiving bores, valves arranged in said bores respectively, a passage connecting the pump of large discharge capacity with one of said bores, a second passage connecting the pump of small discharge capacity with said other bore, a third passage connecting said bores whereby the liquid valve in said other bor controlling the connection of said third passage with said second passage and with said discharge line, and a fourth passage communicating with said one bore and controlled by the valve in said one bore, said 10 valve in said other bore also controlling the connection of said second passage with said discharge line.

HARRY H. VANDERZEE.

CERTIFICATE OF CORRECTION Patent No. 2,522,759. June 22, 1945.

HARRY H. VANDERZEE.

It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows: Page 2, first column, line 68, for rode read -rods page 14., second column, line 60,

before "valve" strike out "a"; and that the said Letters Patent should be read with this correction therein that the same may conform to the record of the case in the Patent Office. I

Signed and sealed this 25rd day of November, A. D. 19143.

. Henry 'Van Arsdale, (Seal) Acting Commissioner of Patents.

Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US2536304 *Jan 12, 1946Jan 2, 1951Signal Oil & Gas CoSpinning head
US2672015 *Jul 10, 1947Mar 16, 1954Frank AdamsHydraulic brake booster
US2739790 *Sep 29, 1948Mar 27, 1956Joy Mfg CoRotary oil well drilling apparatus
US2912131 *Oct 1, 1957Nov 10, 1959Demag Baggerfabrik GmbhHydraulically operated machines
US2934804 *Mar 17, 1955May 3, 1960De Long CorpReleasable gripper for jack assemblies
US2969702 *May 19, 1955Jan 31, 1961O & M Machine Company IncApparatus for running thread-jointed oil well strings into and out of oil wells
US7228913 *Jun 18, 2004Jun 12, 2007Varco I/P, Inc.Tubular clamp apparatus for top drives and methods of use
Classifications
U.S. Classification60/471, 24/463, 60/486, 91/519, 60/421, 173/149, 92/14
International ClassificationE21B3/02, E21B3/00, F15B11/00
Cooperative ClassificationF15B11/00, E21B3/02, F15B2211/30525, F15B2211/50518, F15B2211/324, F15B2211/20584, F15B2211/45, F15B2211/31594
European ClassificationE21B3/02, F15B11/00