Substantially Constant Time Delay Fishing Jar

Abstract

A fishing jar for removing stuck objects from a well bore wherein an upward strain on the running string compresses hydraulic fluid in a compression chamber to the amount of the upward jar or impact load desired to be applied to the fish stuck in the well including a movable piston means having a substantially constant flow regulator by-pass means therein to pass or transfer the compressed hydraulic fluid from one end to the other end of the piston means in the compression chamber. The piston means also includes seal means which define cross sectional areas adjacent each end of the piston means that are of different sizes and are responsive to the compressed hydraulic fluid to move it through the constant flow regulator by-pass means in the piston means, and thereby move the piston means in the compression chamber at substantially a constant rate to contact and open a valve which substantially instantaneously releases the compressed hydraulic fluid through a by-pass passage means so that a jar or impact is applied to the fish. The cross sectional areas formed by the seal means are of a predetermined size relative to each other, to thereby control the pressure differential of the compressed hydraulic fluid acting through the substantially constant flow regulator by-pass means, and to maintain such pressure differential within a predetermined range regardless of the load applied to the fish, within the design limits of the jar. Regardless of the hydraulic pressure in the compression chamber due to the jar load to be applied to the fish, the constant flow regulator by-pass means conducts substantially the same compressed fluid volume across the piston means at substantially the same rate so long as the pressure differential is within the predetermined range. Thus, the time delay to actuate the jar is relatively short and constant and is independent of downhole temperatures and pressures, or jarring loads, within the design limits of the tool.

Description

SUMMARY OF THE INVENTION

Various types of fishing jars are employed for removing some tool or tubular member or other object from a well bore in the earth. The object stuck in the well bore is commonly referred to as a "fish" and fishing jars are run at the lower end of a string of drill pipe or tubing which ordinarily is referred to as the fishing, running or working string and the fishing tool is engaged with the lower end thereof. The fishing tool may be a spear, or overshot or similar device adapted to engage the fish so that the fish may be jarred loose by the jar and thereafter retrived from the well bore.

Jars are employed for the purpose of applying hammer blows to aid in releasing the stuck fish while the fishing string is under tension. Jars of the hydraulic type, in general, are quite well known and comprise telescoping members. When telescoped a pressure chamber containing a quantity of hydraulic fluid resists elongation of the jar. However, when an upward strain or tension is applied to the running string, the hydraulic fluid is compressed and bleeds through a restricted flow passage thus permitting a gradual telescoping of the tool until a large by-pass is opened and the induced pressure on the hydraulic fluid is instantaneously released. Since the fishing string is no longer resisted by the compressed fluid, the jar telescopes rapidly until such telescoping is stopped by engagement of a hammer and anvil that form part of the fishing tool which applies a jar to the fish.

Fishing jars presently employed can deliver various amounts of upward impacts or jarring loads to the fish; however, with all fishing jars presently known to applicant, the time delay from the time of placing a tension on the fishing string to compress the hydraulic fluid until the time that the fluid is by-passed or released so that an upward impact or jar may be applied by the fishing tool to the fish will vary considerably depending on the load to be applied.

When multiple hammer blows are to be successively applied to the fish, the operation of jars may be time consuming since the by-passing or bleeding of the hydraulic fluid through a restricted passage causes a time delay depending upon the magnitude of the tension which is applied to the fishing string, and the magnitude of tension of the fishing string determines the jarring load to be applied to the fish. Thus, if the jarring load is low, say for example 15,000 pounds, a comparatively long period of time is required for the flow of hydraulic fluid through the restricted passage. Where higher jarring forces say for example, 60,000 pounds are employed, the oil flows more rapidly through the restricted passage due to the higher tension applied to the fishing string and resulting greater pressure differential across the restriction.

Generally speaking, then, such prior art hydraulic jars employ tripping mechanisms which are load sensitive, and the time delay from starting the jarring stroke varies inversely with the jarring load.

Some jars presently available are adjustable to vary the release time, although such adjustment is generally good only for a small range of jarring forces. For example, if it is desired, by way of example only, to jar at 20,000 pounds, the prior art devices are adjusted to effect such jar in a predetermined time range and if it is then desirable to jar at 60,000 pounds, the jar may trip prematurely before the 60,000 pound jar is applied to the jarring tool.

Thus, if the operator desires to initially apply a low jar, say 20,000 pounds, it is generally necessary to withdraw the running string and jar from the well bore and readjust the jar at the earth's surface where a higher jar, such as 60,000 pounds, is desired. The running string must then be again lowered into the well bore, all of which involves time and expense.

On the other hand, if the jar is initially adjusted for a higher jarring force, say 60,000 pounds, much time is consumed if it is then desired to jar at a lower force.

Other jars have no adjustment.

Still another disadvantage of hydraulic jars with which applicant is presently familiar is that generally the metering stroke may vary from 2 inches to 7 inches and the substantial volume of liquid is metered at a very high pressure. It can be appreciated that hydraulic jars of present construction which require metering a hydraulic volume through a piston, or by-pass, under high differential pressure causes substantial heat build up. This in turn causes seal failures and where the jar is employed over an extended period of time, the excessive heating of the hydraulic fluid reduces its viscosity and causes premature tripping of the jar before the desired load is placed on the fishing string at the earth's surface.

From the foregoing, it can be appreciated that with hydraulic jars presently employed, the tripping mechanism is sensitive or responds to the load to be applied, and the smaller the load the slower the tripping mechanism is in functioning.

The present invention overcomes the above and other problems presently encountered in hydraulic fishing jars.

One object of the present invention is to provide a hydraulic jar wherein the tripping or actuating mechanism is not responsive or dependent upon the amount of load.

One object of the present invention is to provide a hydraulic jar wherein the tripping or actuating mechanism is not responsive or dependent upon the amount of load and which is constructed and arranged to actuate or trip at a relatively constant, short time regardless of the jarring load.

An object of the present invention is to provide a hydraulic fishing jar which does not depend upon metering the hydraulic fluid under high differential pressures, thus sustaining negligible heat buildup.

Yet a further object of the present invention is to provide a hydraulic fishing jar which has a constant time delay regardless of the load applied to the fishing jar within the range of the design limitations of the particular size jar.

Still another object of the present invention is to provide a constant time delay fishing jar wherein the upward impact applied by the jar to the fish occurs approximately ten to twenty seconds after the operator starts the jarring stroke, regardless of the load to be applied to the fish by the jar, regardless of downhole temperatures and pressures and within the design limits of the jar.

Yet a further object of the present invention is to provide a fishing jar for removing stuck objects from a well bore in which hydraulic fluid within a compression chamber is compressed by the jar load desired to be applied to the fish without requiring any initial setting or adjustment by an operator at the earth's surface, or any adjustment of the hydraulic jar once it is in operation.

Yet a further object of the present invention is to provide a fishing jar for removing stuck objects from a well bore in which hydraulic fluid within a compression chamber is compressed by the jar load desired to be applied to the fish without requiring any initial setting or adjustment by an operator at the earth's surface, or any adjustment of the hydraulic jar once it is in operation and wherein such jar includes spaced cross sectional areas in the chamber of a different size which are responsive to the compressed hydraulic fluid for passing the compressed hydraulic fluid through a constant flow regulator by-pass means in a piston to effect movement of the piston to open a valve and release the compressed hydraulic fluid through a by-pass so that a jar may be applied to the fish.

Yet a further object of the present invention is to provide a fishing jar for removing stuck objects from a well bore in which hydraulic fluid within a compression chamber is compressed by a piston to the jar load desired to be applied to the fish without requiring any initial setting by an operator at the earth's surface, or any adjustment of the hydraulic jar once it is in operation and wherein such jar includes spaced cross sectional areas in the chamber of a different size which are responsive to the compressed hydraulic fluid for passing the compressed hydraulic fluid through a constant flow regulator by-pass means in a piston to effect movement of the piston to open a valve and release the compressed hydraulic fluid through a by-pass so that a jar may be applied to the fish, said spaced cross sectional areas being a predetermined relationship for controlling the compressed hydraulic fluid pressure differential in the chamber acting through the constant flow regulator means to move the piston at a constant rate with a minimum of pressure differential in the compression chamber acting through the constant flow regulator means and with a minimum metering stroke of the jar from a minimum jar load to a maximum jar load for which the fishing jar is designed.

Yet a further object of the present invention is to provide a hydraulic fishing jar which eliminates the substantial time delays presently encountered with hydraulic jars.

Still another object of the present invention is to provide a hydraulic jar of relatively simple design wherein a minimum stroke is required to compress hydraulic fluid in the hydraulic compression chamber to a desired load and thereafter meter such compressed fluid across a relatively small pressure differential as compared with prior art hydraulic jars with the time for compression to any desired load and tripping to apply an impact requiring a minimum and relatively constant amount of time such as ten to twenty seconds.

Still another object of the present invention is to provide a hydraulic jar of relatively simple construction which should be normally substantially foolproof to apply any desired load to a fish with the time delay at any load being substantially the same as at any other load.

Other objects and advantages of the present invention will become apparent from the following description and drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIGS. 1A through 1C together constitute generally a longitudinal partial quarter section of a jarring tool of the preferred form of the present invention installed in a fishing string and illustrates the position of the components when the tool is in a collapsed or telescoped relation;

FIGS. 2A through 2C together constitute a fragmentary, generally longitudinal quarter section through portions of the jarring tool illustrated in FIGS. 1A through 1C, FIGS. 2A through 2C illustrating the components when the tool is extended and at the moment that an upward impact is delivered to the fish; and

FIG. 3 is a fragmentary sectional view showing a check valve means mounted in the piston means.

DESCRIPTION OF THE PREFERRED EMBODIMENT

The hydraulic fishing jar of the present invention is referred to in FIG. 1A generally by the numeral 5. It comprises an elongated tubular inner mandrel or body 6 and an outer tubular elongated body or housing 7. The inner body 6 at its upper end is provided with a threaded box 8 of well known configuration which is adapted to receive the externally threaded pin 9 at the lower end of the upwardly extended section of drill pipe or drill collar or other tubular member 10 consituting a portion of the running or fishing string on which the jar 5 is run into the well bore, and by which the jarring tool is operated to provide a jarring action for a fishing tool which may be designated F connected to the threaded end 13 on the lower end of the outer housing or body 7 as more clearly seen in FIG. 1C.

The inner housing or body 6 is provided adjacent its upper end with a plurality of elongated circumferentially spaced grooves 15 having longitudinally extending projections 16 extending between the grooves which elongated, circumferentially spaced grooves 15 are adapted to receive the circumferentially spaced projections 18 formed on the annular member 20 adjacent the upper end of the outer body or housing 7. The circumferentially spaced projections 18 are provided with elongated recesses therebetween illustrated at 22 for receiving the elongated circumferentially spaced projections 16 on the inner body 6.

This arrangement provides a splined configuration for enabling th inner body 6 and outer body 7 to telescope longitudinally relative to each other while inhibiting relative rotation therebetween.

It can be appreciated that the grooves 15 and projections 16 will be of any suitable or longitudinal extent to accommodate the desired telescoping movement of the inner body 6 and outer body 7 for compression of the hydraulic fluid in the compression chamber and for release thereof to enable an upward blow to be delivered to the fish in a manner as will be described in greater detail.

An annular member 26 is secured on the body 6 below the spline arrangement hereinbefore described by means of the threads 24 formed on the inner body 6 and threads 25 formed on the annular member 26. Also if desired such member may be further secured in place by the threaded pin 28 extending through the member 26 and into a suitably threaded opening 29 in the inner body 6.

The upper annular end 26a of the member 26 forms the hammer for delivering an upward impact when the inner body 6 is released relative to the outer body 7 as will be described.

The inner body 6 comprises a plurality of longitudinally tubular portions secured together including the portion 6a and to which is secured the tubular, longitudinally extending portion 6b by suitable means such as the cooperating threads on 6a and 6b referred to at 6c.

A suitable seal 31 is interposed between unthreaded portions of the cylindrical surfaces of 6a and 6b for sealing therebetween. Threadedly secured to the lower end of the tubular section 6b is the tubular section 6d which forms the lower end of the inner tubular body or housing 6. Suitable cooperating threads referred to generally at 6e formed on the tubular inner body portion 6d and tubular inner body portion 6e enable them to be threadedly connected together and suitable seal means as shown at 32 are provided between the unthreaded portions of the cylindrical surfaces of the members 6b and 6d for sealing therebetween.

The outer tubular body or housing 7 includes the uppermost tubular portion 7a on which are formed the circumferentially spaced projections 18 with the recesses 22 therebetween as previously described. The lower annular end 30a on member 20 forms an anvil against which hammer 26a strikes to deliver a jar as will be described. The upper outer body portion 7a threadedly connected to the next adjacent outer tubular body portion 7b by suitable cooperating threads referred to generally at 7c formed on the lower end of 7a and at the upper end of 7b as shown in FIG. 1A of the drawing. The portion 7b includes the upwardly extending annular projection 7d which is threadedly engaged with the annular member 7e by means of the threads referred to generally at 7f formed on the extension 7d and the annular member 7e as shown in FIG. 1A. It will be noted that the annular member 7e surrounds and slidably engages the inner tubular body 6 and more particularly the tubular body portion 6b as shown in FIGS. 1A and 2A of the drawings.

Suitable seal means comprising the annular seal rings 35 and 36 are positioned on the shoulder 38 of the member 7b adjacent the cylindrical surface 39 of the member 6b and are retained in position by the annular member 7e and retainer 40. The seal means 35 and 36 provide means which define the upper end of a hydraulic fluid chamber referred to generally at 45 in the drawings. Such chamber extends longitudinally from the seal means 35, 36 between the inner body 6 and outer body 7 to the seal means 42 and 43 carried in the annular floating piston 44 at the lower end of the jar 5 in the annular space between the inner body 6 and the outer body 7 as shown in FIG. 1C. Suitable openings O are provided for filling chamber 45 and bleeding air therefrom as such filling occurs. The plugs P may then be threadedly engaged in the openings O, with a suitable seal ring S thereon to prevent loss of fluid.

The outer tubular body portion 7b is connected to the outer tubular body portion 7g by suitable means such as the cooperating threads formed on the lower end of the outer body portion 7b and the upper end of the outer body portion 7g, which cooperating threads are referred to generally by the numeral 7h. Suitable seal means 46 are provided between the unthreaded cylindrical surfaces of the members 7b and 7g to inhibit leakage therebetween. The outer tubular body portion 7g is connected at its lower end to the outer tubular body portion 7i by suitable means such as the cooperating threads adjacent the lower end of the outer tubular body portion 7g and the upper end of the outer tubular body portion 7i, such threads being referred to generally by the numeral 7j. Suitable seal means as shown at 48 are provided between the unthreaded cylindrical surfaces of the outer tubular body portions 7g and 7i to inhibit leakage therebetween.

As previously noted the threaded end 13 of the outer tubular body 7i provided for connecting with the fishing tool F of a suitable type.

Power piston means are referred to generally at 55 and include the annular element 55' and the annular enlargement 57 on body portion 6g, which cooperate to provide a valve arrangement in the power piston 55 as will be described. The annular element 55' is between the outer body 7 and inner body portion 6g and is spaced radially from the outer surface of 6g to form a flow passage 6g" therebetween as shown in FIG. 1C when the element 55' is spaced from enlargement 57. The element 55' is supported on the annular shoulder 56 formed in outer body portion 7g. Suitable seal means 55a' seal between element 55' and the inner cylindrical wall of housing 7. The annular element 55' of power piston 55 is retained in position on the shoulder 56 when the jar of the present invention is in the collapsed position shown in FIGS. 1A-1C by means of the spring 58 extending longitudinally of the chamber 45. The spring at its upper end abuts an annular shoulder on the lower end of piston means referred to generally by the numeral 60, which piston means also is slidably mounted within the chamber 45 as shown in FIGS. 1B and 2B.

The piston means 60 includes piston valve means 65, substantially constant flow by-pass means referred to generally at 61 and the passage means 62 for by-passing fluid across the piston means 60 in a manner as will be described. The piston means 60 also includes one-way acting check valve means 61d as shown in FIG. 3 which is carried in passage means 62a in annular piston means 60 at a position circumferentially spaced relative to constant flow by-pass means 61. The check valve means 61d functions as will be described to flow fluid from compression chamber 101 to 100 beneath piston means 60.

The annular piston valve means referred to at 65 is provided with an annular surface 66 for sealably engaging with the upper end 68 of the piston means 60 as illustrated in FIG. 1C of the drawings. The piston valve means 65 includes a plurality of circumferentially spaced flow ports 67 formed in the annular projection 67a which when the piston valve means 65 is seated on the end 68 of piston means 60 extends beyond the end 68 of piston means 60 and between such piston means and body portion 6b. This prevents communication of ports 67 with chamber portion 101. The piston valve means 65 is urged towards seated position on the upper end 68 of the piston means 60 by means of the resilient means 69 which abuts the shoulder 70 on the outer housing body portion 7b at one end, with its other end resting on the end 65a of the valve means 65. The annular valve means 65 is slidably arranged on the inner body 6 and more specifically the inner body portion 6b as shown in FIG. 1B and is provided with seal means 71 for slidably and sealably engaging with the outer cylindrical surface of the member 6b.

A valve member 80 is carried in chamber 45 beneath the annular piston means 60 and in spaced relation thereto.

The lower most inner body portion 6d abuts an annular upwardly extending annular skirt 6g which skirt thus is part of inner body 6 and extends longitudinally of, and surrounds the lower most inner body portion 6b as shown in FIGS. 1B and 1C of the drawings.

The upper end 6h of the extension 6g terminates in spaced relation to the annular shoulder 81 formed on the valve member 80 as shown in FIG. 1B and the valve member 80 is slidable relative to the upwardly extending body portion 6g as shown in FIGS. 1B and 1C. Suitable seal means as shown at 81a are provided between the cylindrical surface of 6g and the valve member 80 so that the valve member 80 is thus sealably and slidably carried by the inner body 6.

The upper end 83 of the valve member 80 seats against the lower end 84 of the annular skirt means 85 which is secured by any suitable means such as threads 86 or the like to the tubular portion 6d of the inner body 6 and thus forms a part of the inner body 6.

When the components of the jar of the present invention are in the relative position as shown in FIGS. 1A through 1C, it will be noted that the resilient means 88 supported on the shoulder 89 of the annular skirt 6g engages the annular shoulder 90 on valve member 80 to urge the valve member 80 upwardly into sealing contact with the lower end 84 of the annular skirt means 85 and to maintain 57 in spaced relation to element 55' when the inner and outer bodies of the tool are collapsed relative to each other.

It will be further noted that by-pass flow passage means 61a extends from immediately above the end 85a of the means 85 and extends longitudinally therebeneath as well as beneath the annular skirt 6g carried on inner body portion 6d so as to communicate with the lower end of the chamber 45 through the port means 91 formed in skirt 6g beneath power piston 55 as shown in FIG. 1C.

Suitable seal ring means 96 are provided between the annular piston means 60 and the outer body 7 and additional seal ring means 97 are provided between the piston means 60 and inner body 6. It will be noted that the seal 96 sealably and slidably engages the inner cylindrical surface of the outer body portion 7g while the seal 97 engages the outer cylindrical surface of the means 85 secured to and forming part of the inner body 6.

By way of example only the constant flow regulating means referred to generally at 61 includes a substantially constant flow regulating valve 61c of well known configuration which will transfer compressed hydraulic fluid from the hydraulic compression chamber 100 to the hydraulic compression chamber 101 at substantially a constant flow rate so long as the pressure differential of the hydraulic fluid between compression chamber 100 and compression chamber 101 is within a predetermined range. By way of example only, when the pressure differential between chambers 100 and 101 is greater than approximately 50 p.s.i. differential, but less than approximately 3,000 p.s.i. differential, the flow rate from chamber 100 to chamber 101 is constant at 0.3 gallons per minute. Since such flow regulator is of well known construction and may be obtained commercially, it is not deemed necessary to give a detailed description as it is well known to those skilled in the art.

It can be appreciated that a constant flow regulating valve responsive to a different range of pressure differentials and a different constant flow rate may be employed, and the foregoing is given by way of illustration only.

In order to maintain the proper hydraulic pressure differential between compression chamber 100 and compression chamber 101, seal means are provided in the chamber 45 between the piston valve means 65 and said inner body 6 and between said piston means 60 and the outer body 7g and between the piston means 60 and means 85 to provide cross sectional areas respectively adjacent each end of the piston means in the compression chamber 100 and compression chamber 101 which are responsive to the compressed hydraulic fluid for passing the compressed hydraulic fluid through said constant flow by-pass means 61 at substantially a constant rate and with a minimum pressure differential for any load applied to the jar.

More particularly, the seal means 71 in the annular piston valve means 65 which engages inner body portion 6b and the seal means 96 between the piston means 60 and outer housing portion 7g define one effective cross sectional area adjacent one end of the piston means 60 responsive to compressed hydraulic fluid within the compression chamber 101 and which is illustrated at A1, in FIG. 1B. Similarly, seal means 96 between the piston means 60 and outer housing portion 7g and seal means 97 between the piston means 60 and the means 85 define an effective cross sectional area illustrated at A2 adjacent the other end of the piston means 60 responsive to compressed hydraulic fluid in compression chamber 100. The jar is designed and constructed so that cross sectional area A1 defined by the seals 71 and 96 is larger than the cross sectional area A2 defined by the seals 96 and 97.

When hydraulic fluid is compressed in the chamber between the inner body 6 and outer body 7, the forces acting on the piston means 60 will tend to balance, and the hydraulic pressure in the compression chamber 100 beneath the piston 60 is greater than that in compression chamber 101 above the piston means 60 by the ratio of A1 divided by A2. Thus, when a load is applied to the hydraulic column in chamber 45 by the inner tubular member and power piston 55 to compress the hydraulic fluid, fluid will be displaced from the compression chamber 100 to the compression chamber 101 through the constant flow regulator means 61 carried by the piston 60.

As fluid is displaced from beneath the piston means 60 to the top of the piston means 60, the piston means 60 will travel downwardly at a fixed rate of travel in the compression chamber portion 100.

When piston means 60 engages valve member 80 and moves it off the seat 84, compressed hydraulic fluid from chamber 100 is discharged through by-pass flow passage 61a to chamber portion 45a beneath power piston 55. Release of the compressed hydraulic fluid permits the inner mandrel 6 to move upwardly until the end 85a of means 85 engages the lower end 65b of valve means 65 and moves it away from piston means 60, so that compressed fluid from chamber 101 is conducted to by-pass 61a. The inner body 6 continues its upward movement so that hammer 26a strikes an upward blow on anvil 30a.

Description of Operation

While it is believed that the operation of the present invention is apparent by the reason of the foregoing, to further amplify and describe, attention is now directed to FIGS. 2A through 2C of the drawings.

In such views, the components of the jar 5 of the present invention are shown in their relative position at the time that an upward jarring blow is delivered by the jar to a fish engaged by fishing tool F.

In order to deliver an upward jarring blow to a fish in a well bore, the fishing tool F is first engaged with the stuck fish when the operating string is lowered into the well bore.

Thereafter an upward strain is taken on the fishing or operating string at the earth's surface in a desired amount. For example, in a tool of the present design of 4 1/4 inches outer diameter of the outer tubular body 7, the maximum load or jar that may be applied to a fish is 55,000 pounds due to the physical limitations and strength of the materials involved. However, any desired load up to this amount may be applied by the present invention without any adjustment at the earth's surface or in the well bore. There is a relatively constant time delay from the time that the desired load is applied by the fishing string until the jar is released to deliver an impact to the fish whether the jarring load applied is 15,000 or 55,000 pounds and the relatively constant time delay is independent of downhole temperatures and pressures.

As an upward strain or pull is applied at the earth's surface to the fishing string 10 illustrated in FIG. 1A of the drawings, this is transmitted through the inner body 6 and its body portions previously described. The outer body 7 will remain stationary since it is connected by its respective outer body portions to the fishing tool F which in turn is secured to the fish to which the upward jarring impacts are to be delivered.

Upward movement of the inner body 6 including body portions 6a, 6b, 6d, and 6g moves the shoulder 6g' on enlargement 57 into sealing engagement with the lower end 55a of annular element 55'. When 57 and 55' are thus sealingly engaged, passage 6g" is closed off and the power piston means formed by 57 and 55' compresses the hydraulic fluid in compression chambers 100 and 101, since chamber 45 referred to as 45a beneath power piston 55 is isolated from the compression chamber, including compression chambers 100 and 101 on each end of piston means 60. Thus, the desired jarring load is transmitted to the hydraulic fluid within such compression chamber defined by chambers 100 and 101 to compress it.

If it is desired to apply a jarring load of 20,000 pounds to the stuck fish, then the operating string will be pulled at the earth's surface to compress the hydraulic fluid by power piston means 55 in jar 5 until the weight indicator at the earth's surface indicates that such load is present in the compressed hydraulic fluid, of course, such weight indicator indicating the 20,000 pounds load plus the weight of the working string in the well bore.

When the 20,000 pound load is properly indicated on the weight indicator, the driller at the earth's surface may set his brake and due to the difference in the cross sectional area between A1 on one side of the piston means 60 and A2 on the other side of the piston means 60, there will be a greater hydraulic pressure per unit area beneath the piston means 60 in compression chamber 100 than above piston means 60 in compression chamber 101 so that hydraulic fluid flows through the constant flow regulator means 61 in piston means 60 to the compression chamber 101 above the piston from chamber 100.

The flow of hydraulic fluid across piston means 60 is at substantially a constant rate due to the constant flow regulator by-pass means 61 and the piston means 60, by reason of the hydraulic fluid flow to the top side thereof, moves downwardly and spring 58 yields as the piston means 60 moves relative to power piston means 55. The movement of piston means 60 is at substantially a constant rate until its lower end 60a tags the top 83 of the valve member 80. At the time that the piston means 60 contacts the top 83 of the valve means 80 there will still be a pressure differential between compression chamber 101 and compression chamber 100 and compressed hydraulic fluid will continue to flow from compression chamber 100 to compression chamber 101. However, since the effective cross sectional area A1 in pressure chamber 101 is larger than the effective cross sectional area A2 in pressure chamber 100 the additional fluid flow from hydraulic compression chamber 100 through constant flow regulator means 61 to compression chamber 101 causes piston means 60 to move further downwardly and move the top 83 of valve means 80 away from the lower end 84 of means 85. When this occurs, by-pass flow passage 61a is communicated with compression chamber 100 by means of the annular spaced port means 60b immediately adjacent the lower end 60a of piston means 60 and dumps the compressed fluid in chamber 100.

This permits the inner body 6 along with power piston 55 to move upwardly substantially instantaneously relative to the outer housing 7 since the compressed hydraulic fluid from compression chamber 100 is dumped by the by-pass flow passage 61a and ports 91 in 6g to the chamber portion 45a beneath the power piston 55. The upward movement of inner body portion 6 along with power piston 55 at the time that by-pass flow passage 61a communicates with compression chamber 100 moves the upper end 6h of 6g from the position shown in FIG. 1B to the position shown in FIG. 2B so that end 6h engages shoulder 81 of valve member 80. The upward movement of inner body 6 also moves means 85 from the position shown in FIG. 1B to the position shown in FIG. 2B so as to contact the upper end 85a of the means 85 on inner body 6 with the lower end 65b of the piston valve means 65 and thereby unseat it from engagement with the upper end 68 of piston means 60.

It should be noted that as piston means 60 moves in the compression chamber, valve means 65 remains in sealing engagement with the upper end 68 of piston means 60 until means 85 engages its end 65b and unseats it.

When this occurs, compressed hydraulic fluid from compression chamber 101 flows to by-pass means 61 through annular spaced port means 67 in valve means 65 as shown in FIG. 2B.

As previously noted, once communication is established between compression chamber 100 and fluid by-pass flow passage 61a, the upward relative movement of inner body 6 relative to outer housing or body 7 is relatively sudden and the inner body 6 continues its rapid, upward movement so that hammer 26a strikes a blow against anvil 30a.

To further illustrate the operation of the present invention on a 4 1/4 inch O.D. tool, the cross sectional area at A2 may preferably be 4.643 square inches and the cross sectional area of A1 may preferably be 5.409 square inches. When a load of 20,000 pounds is applied by the operating string 10 as described in the above example, the pressure in compression chamber 100 will therefore be approximately 4,310 pounds per square inch and the pressure in compression chamber 101 piston means 60 will be approximately 3,700 pounds per square inch, thus yielding a pressure differential of only 610 pounds per square inch between cross sectional area A2 and cross sectional area A1.

By way of further example, if a load of 50,000 pounds is desired to be applied to the fish, then the inner body is again tensioned upwardly until the weight indicator at the earth's surface indicates that such load plus the weight of the fishing string is applying a 50,000 pound load in the hydraulic compression chambers 100 and 101.

Under these conditions the effective cross sectional area A2 in compression chamber 101 has a pressure of approximately 11,200 pounds per square inch applied thereto and the pressure in compression chamber 101 acting on the effective cross sectional area A1 is approximately 9,250 pounds so that the pressure differential is approximately only 1,950 pounds per square inch even though the jarring load is 50,000 pounds.

It should be noted that valve member 80 is constructed and arranged so that it is biased towards closed position against the end of means 85 as shown in the drawings, but as long as the difference in cross sectional areas A1 and A2 is substantially greater than the biased area of valve member 80, the piston means 60 will overcome the spring force 88 and bias of the valve member 80 to open it as described.

It can be appreciated that floating piston 44 is a pressure compensating piston to equalize the pressure in chamber 45 with the pressure in the fishing string since the underside of the piston 44 is exposed to the pressure present in the running or fishing string 10.

In addition to a substantially less pressure differential during the metering cycle in the present hydraulic jar as compared with prior device which normally meter at the full differential of the jarring load, substantially less travel of the inner body 6 relative to outer body 7 occurs during the metering cycle, that is during the period that hydraulic fluid is conducted from compression chamber 100 through constant flow regulator by-pass means 61 to compression chamber 101.

Piston means 60 travels downwardly during the metering cycle when fluid is displaced upwardly through the constant flow by-pass means 61 as described previously. Since cross sectional area A1 in compression chamber 101 is larger than the cross sectional area A2 in compression chamber 100, the volume in compression chamber 101 opened up by the downward movement of piston means 60 will be larger than that displaced below the piston means 60 as it moves downwardly. To compensate for this the inner body 6 will move upwardly relative to outer housing 7 to make up for this difference in volume and the amount it will move up equals the stroke of the piston means 60 relative to inner body 6 times the difference between the cross sectional areas A1 and A2 divided by the cross sectional area A1.

As mentioned previously on a 4 1/4 inch O.D. tool, the cross sectional area A1 in the example is 5.409 square inches and the cross sectional area A2 in the example is 4.643 square inches and the stroke of the piston means is 4 inches. Therefore the total metering stroke of the present hydraulic jar is 5.409 minus 4.643 divided by 5.409 times 4 which equals 0.567 inches. Thus the metering stroke of the device of the present invention is relatively small compared with prior art devices.

The amount of heat generated in a hydraulic jar is proportional to the load applied times the metering stroke of the jar. Thus, it can be appreciated that the amount of heat generated by the hydraulic jar of the present invention would be 0.567 divided by 7, or approximately 1/12 that of the conventional hydraulic jars at the same load, assuming that such conventional hydraulic jar has a stroke of 7 inches during the metering cycle of the compressed hydraulic fluid.

After the tool has been actuated, the inner and outer bodies may be collapsed or moved to the position shown in FIG. 1A-1C. As this occurs, enlargement 57 moves away from element 55' and passage 6g" along with check valve means 61d and passage 61a enable hydraulic communication in the chamber to be accomplished so that the tool components may be quickly and easily repositioned so that another jar may be applied. The one-way check valve means 61d communicates, or passes fluid across piston means 60 from the top thereof to the bottom thereof.

From the foregoing it is also seen that enlargement 57 and element 55' not only cooperate to form the power piston means 55, but also cooperate to form a valve arrangement in the power piston means 55 for closing off flow therearound or for opening for flow across the power piston means 55.

The construction and arrangement of the present invention overcomes the objections of prior art hydraulic jars which meter hydraulic fluid at the full pressure induced by the tensile load on the jar, whether it is 20,000 pounds, 50,000 pounds or any other load, and thus overcomes the problems of heat build up, seal failures, and premature tripping which often occur with conventional hydraulic jars presently known to applicant.

Also, the travel of the inner body 6 during the metering stroke is substantially less, as above noted, than that possible with hydraulic jars of present conventional design known to applicant.

Thus, the hydraulic jar of the present invention need only be assembled and filled with hydraulic fluid in chamber 45 and connected in fishing string S for lowering into the well bore. After the fish is engaged by the fishing tool F, any desired load may be applied to the jar, within its design limits, and approximately ten to twenty seconds after tension is initiated in the operating string as described herein, the jar will actuate and deliver an impact, the elapsed time being independent of the magnitude of the load and independent of well temperatures and pressures.

The present invention can be repeatedly employed and the jarring load may be varied, that is, increased or decreased as desired, while the jar remains in the well bore.

All of the foregoing is accomplished without any operator adjustment of the jar; nor is any presetting of the jar required before it goes into the well bore, nor is any adjustment required once the jar is in operation.

Also, as noted previously, since the tripping mechanism is not load sensitive, and since the invention incorporates a constant time delay design, the jar of the present invention will trip ar actuate approximately ten to twenty seconds after the operator begins the jarring stroke, regardless of the jarring load, within the design limits of the tool.

The foregoing disclosure and description of the invention are illustrative and explanatory thereof, and various changes in the size, shape, and materials as well as in the details of the illustrated construction may be made without departing from the spirit of the invention.

Claims

What is claimed is:

1. In a hydraulic fishing jar adapted to be run into a well on a fishing string and connected to a fish in the well bore:

a. inner and outer telescopically interengaged bodies;

b. means defining between said bodies a hydraulic fluid chamber;

c. power piston means in the chamber operable upon tensioning the fishing string for telescopic movement of said bodies to compress and apply a predetermined force to the hydraulic fluid in the chamber;

d. therebeing by-pass flow passage means in one of said bodies;

e. a valve member in the chamber for normally closing off one end of the by-pass flow passage means from the compressed fluid in the chamber and shiftable to open so that compressed hydraulic fluid is released to the by-pass flow passage means;

f. piston means including substantially constant flow by-pass means to transfer the compressed hydraulic fluid in the chamber across said piston means and thereby move it in the fluid chamber at substantially a constant rate to engage and move said valve member to open the by-pass flow passage means at one end to the compressed hydraulic fluid;

g. said piston means including valve means normally closing off the other end of the by-pass flow passage means and shiftable to open so that hydraulic fluid is released from the chamber above said piston means;

h. means on one of said bodies to move said piston valve means and open the other end of the by-pass flow passage means when said valve member is moved to open one end of the by-pass flow passage means to the compressed hydraulic fluid; and

i. hammer and anvil means on said bodies movable into engagement when said valve member and piston valve means open the by-pass passage means to the chamber across said piston means.

2. The invention of claim 1 wherein said piston means includes seal means sealably and slidably engaged in the chamber to provide cross sectional areas of different size on said piston means responsive to the compressed hydraulic fluid in the chamber for transfer thereof across said piston means.

3. The invention of claim 2 wherein said cross sectional areas are of a predetermined relationship for controlling the compressed hydraulic fluid pressure differential across said piston means in the chamber acting to move said piston means.

4. The invention of claim 2 wherein said piston means is an annular member having top and bottom ends and wherein the cross sectional area defined by said seal means adjacent said bottom piston end is smaller than the cross sectional area defined by said seal means adjacent said top piston end.

5. The invention of claim 1 including annular seat means formed on said piston valve means and said piston means for seating said piston valve means on said piston means.

6. The invention of claim 1 including resilient means normally urging said piston valve means into sealing engagement with said piston means until said means on one of said bodies engages said piston valve means.

7. The invention of claim 1 wherein said means on one of said bodies at one end thereof forms seat means for said valve member.

8. The invention of claim 7 including resilient means normally urging said valve member into sealing engagement with said seat means until said piston means moves said valve member off said seat means.

9. The invention of claim 1 including resilient means in the chamber urging said piston means away from said valve member and yieldable as said piston means moves to engage said valve member.

10. The invention of claim 9 wherein said resilient means urging said piston means away from said valve member also engages said power piston and is yieldable upon movement of said piston means relative to said power piston.

11. The invention of claim 1 wherein said means defining the hydraulic fluid chamber comprises upper and lower seal means between said bodies, one of said seal means being a floating piston for compensating for the pressure of fluid in the well.

12. The invention of claim 1 wherein said valve member is slidably and sealably carried by said inner body.

13. The invention of claim 1 wherein said piston valve means is slidably and sealably carried by said inner body.

14. The invention of claim 1 wherein said piston means is slidably and sealably carried in said chamber.

15. The invention of claim 1 wherein said by-pass flow passage means is formed in said inner body;

16. The invention of claim 2 wherein one of said cross sectional areas is defined by seal means between said piston valve means and inner body and seal means between said piston means and outer body, and the other of said cross sectional areas is defined by seal means between said piston means and outer body and seal means between said piston means and inner body.

17. The invention of claim 2 wherein said cross sectional areas are of a predetermined relationship for maintaining the compressed hydraulic fluid pressure differential across said piston means within a predetermined range.

18. The invention of claim 1 wherein said substantially constant flow by-pass means, includes substantially constant flow regulator means whereby the compressed hydraulic fluid moves therethrough at substantially a constant rate within the predetermined pressure differential range.

19. In a hydraulic fishing jar adapted to be run into a well on a fishing string and connected to a fish in the well bore:

a. inner and outer telescopic bodies;

b. means including longitudinally spaced seals defining between said bodies a hydraulic fluid chamber;

c. power piston means including an annular piston carried by one of said bodies and shiftable longitudinally in said chamber by the other of said bodies upon tensioning the fishing string for telescopic movement of said bodies to compress and apply a predetermined force to the hydraulic fluid in the chamber;

d. therebeing by-pass flow passage means in one of said bodies;

e. a valve member in the chamber for normally closing off one end of the by-pass flow passage means from the compressed fluid in the chamber and shiftable to open so that compressed hydraulic fluid is released to the by-pass flow passage means;

f. piston means including substantially constant flow by-pass means to transfer the compressed hydraulic fluid in the chamber across said piston means and thereby move it in the fluid chamber at substantially a constant rate to engage and move said valve member to open the by-pass flow passage means at one end to the compressed hydraulic fluid;

g. said piston means including valve means normally closing off the other end of by-pass flow passage means and shiftable to open so that hydraulic fluid is released from the chamber above said piston means;

h. means on said inner body to move said piston valve means and open the other end of the by-pass flow passage means when said valve member is moved to open one end of the by-pass flow passage means to the compressed hydraulic fluid; and

i. hammer and anvil means on said bodies movable into engagement when said valve member and piston valve means open the by-pass passage means to the chamber across said piston means.

20. The invention of claim 19 wherein said piston means includes seal means sealably and slidably engaged in the chamber to provide cross sectional areas of different size on said piston means responsive to the compressed hydraulic fluid in the chamber for transfer thereof across said piston means.

21. The invention of claim 20 wherein said cross sectional areas are of a predetermined relationship for controlling the compressed hydraulic fluid pressure differential across said piston means in the chamber acting to move said piston means.

22. The invention of claim 21 wherein said piston means is an annular member having top and bottom ends and wherein the cross sectional area defined by said seal means adjacent said bottom piston end is smaller in size than the cross sectional area defined by said seal means adjacent said top piston end.

23. The invention of claim 19 including annular seat means formed on said piston valve means and said piston means for seating said piston valve means on said piston means.

24. The invention of claim 19 including resilient means normally urging said piston valve means into sealing engagement with said piston means until said means on said inner body engages said valve means.

25. The invention of claim 19 wherein said means on said inner body at one end thereof forms seat means for said valve member.

26. The invention of claim 25 including resilient means normally urging said valve member into sealing engagement with said seat means until said piston means moves said valve member off said seat means.

27. The invention of claim 19 including resilient means in the chamber urging said piston means away from said valve member and yieldable as said piston means moves to engage said valve member.

28. The invention of claim 20 wherein said valve member is slidably and sealably carried by said inner body.

29. The invention of claim 27 wherein said resilient means urging said piston means away from said valve member also engages said power piston and is yieldable upon movement of said piston means relative to said power piston.

30. The invention of claim 19 wherein said piston valve means is slidably and sealably carried by said inner body.

31. The invention of claim 19 wherein said piston means is slidably and sealably carried in said chamber.

32. The invention of claim 19 wherein the by-pass flow passage means is formed in said inner body.

33. The invention of claim 20 wherein one of said cross sectional areas is defined by seal means between said piston valve means and inner body and seal means between said piston means and outer body, and the other of said cross sectional areas is defined by seal means between said piston means and outer body and seal means between said piston means and inner body.

34. The invention of claim 20 wherein said cross sectional areas are of a predetermined relationship for maintaining the compressed hydraulic fluid pressure differential across said piston means within a predetermined range.

35. The invention of claim 19 wherein said substantially constant flow by-pass means, includes substantially constant flow regulator means whereby the compressed hydraulic fluid moves therethrough at substantially a constant rate within the predetermined pressure differential range.

36. In a well bore fishing string hydraulic fishing jar having inner and outer telescopically interengaged bodies with a hydraulic fluid chamber therebetween and power piston means in the chamber to compress and apply a predetermined force to the hydraulic fluid in the chamber upon tensioning the fishing string for telscopic movement of the bodies, the improvement comprising:

a. therebeing by-pass flow passage means in one of the bodies;

b. a valve member in the chamber for normally closing off one end of the by-pass flow passage means from the compressed fluid in the chamber and shiftable to open so that compressed hydraulic fluid is released to the by-pass flow passage means;

c. piston means including substantially constant flow by-pass means to transfer the compressed hydraulic fluid in the chamber across said piston means and thereby move it in the fluid chamber at substantially a constant rate to engage and move said valve member to open the by-pass flow passage means at one end to the compressed hydraulic fluid;

d. said piston means including valve means in the chamber normally closing off the other end of the by-pass flow passage means and shiftable to open so that hydraulic fluid is released from the chamber above said piston means; and

e. hammer and anvil means on said bodies movable into engagement when said valve member and piston valve means open the by-pass passage means to the chamber across said piston means.

37. The invention of claim 36 wherein said piston means includes seal means sealably and slidably engaged in the chamber to provide cross sectional areas of different size on said piston means responsive to the compressed hydraulic fluid in the chamber for transfer thereof across said piston means.

38. The invention of claim 37 wherein one of said cross sectional areas is defined by seal means between said piston valve means and inner body and seal means between said piston means and outer body, and the other of said cross sectional areas is defined by seal means between said piston means and outer body and seal means between said piston means and inner body.

39. The invention of claim 37 wherein said cross sectional areas are of a predetermined relationship for maintaining the compressed hydraulic fluid pressure differential across said piston means within a predetermined range.

40. The invention of claim 36 wherein said substantially constant flow by-pass means, includes substantially constant flow regulator means whereby the compressed hydraulic fluid moves therethrough at substantially a constant rate within the predetermined pressure differential range.

41. The invention of claim 1 wherein said power piston means includes a valve arrangement normally open to communicate the chamber on one side of said power piston with said piston means in the chamber on the other side of said power piston, but which valve arrangement closes upon tensioning the fishing string to compress the hydraulic fluid in the chamber.

42. The invention of claim 1 including check valve means in said piston means for communicating fluid across said piston means.

43. The invention of claim 19 wherein said power piston means includes a valve arrangement normally open to communicate the chamber on one side of said power piston with said piston means in the chamber on the other side of said power piston, but which valve arrangement closes upon tensioning the fishing string to compress the hydraulic fluid in the chamber.

44. The invention of claim 19 including check valve means in said piston means for communicating fluid across said piston means.

45. The invention of claim 36 wherein said power piston means includes a valve arrangement normally open to communicate the chamber on one side of said power piston with said piston means in the chamber on the other side of said power piston, but which valve arrangement closes upon tensioning the fishing string to compress the hydraulic fluid in the chamber.

46. The invention of claim 36 including check valve means in said piston means for communicating fluid across said piston means.