Abstract:
A hydraulic jar for use in a well and a method of operating same in which an outer housing assembly extends around an inner mandrel assembly in a coaxial relation thereto to define two fluid chambers separated by a piston. The housing assembly is movable relative to the mandrel assembly to force the fluid from one of the chambers to the other. The fluid flow rate is varied between a relative low flow rate and a relative high flow rate in response to the relative position of the housing assembly causing corresponding movement at the latter assembly. A high impact load is transferred to a member connected to the jar in response to a movement at the relatively high flow rate. The jar can be used to create a high impact load in both an upward direction and a downward direction.

Description:
This is a continuation of co-pending application Ser. No. 269,996 filed on Nov. 14, 1988, now abandoned. 
    
    
     BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     This invention relates to a jar for providing high impact loading in a well and a method of operating same, and, more particularly, to such a jar and method in which the loading can be in both an upward and downward direction. 
     In various downhole operations in wells for producing hydrocarbon fluids, high impact loading is often necessary to retrieve or set tools for servicing the wells. Both mechanical and hydraulic jars have evolved which are lowered into the wellbore in a well tool string including an accelerator and a stem, which together function to produce a high impact load. In the case of an up jar, the load is directed upwardly to retrieve tools, remove obstructions and the like. In the case of a down jar the load is directed downwardly to set tools, plugs, flow control devices, and the like. 
     The need for efficient jars becomes more acute in wells that deviate from the traditional vertical orientation, since the angular disposition of at least a portion of the well increases the friction in the well and dissipates some of the vertical thrust needed to activate the jars. Further, the advent of coil, or reeled, tubing, which requires a jar that passes fluid used to service the well, places additional design limitations on the up and down jars, especially from a size standpoint. 
     In view of these structural and functional demands, a separate jar has to be designed and used for the up operation and a separate jar for the down operation, thus adding to the overall cost of the well service tools. The jars disclosed in U.S. Pat. Nos. 2,828,822 and 2,851,110, issued to C.B. Greer on Apr. 1, 1958, and Sep. 9, 1958, respect are exemplary of hydraulic jars that can only operate in an upward direction. Thus an entirely different jar would have to be designed for use in a downward direction. 
     SUMMARY OF THE INVENTION 
     It is therefore an object of the present invention to provide a hydraulic jar which is compact in size and efficient in operation. 
     It is a further object of the present invention to provide a jar of the above type and a method of operating same in which the jar can be used for both upward and downward impact loading. 
     It is a further object of the present invention to provide a jar and method of the above type which is adapted for use with coil tubing. 
     It is a further object of the present invention to provide a jar and method of the above type which can be used in deviated wells. 
     Additional objects and advantages of the present invention will be apparent to those skilled in the art from studying the following detailed description in conjunction with the accompanying drawings in which the preferred embodiment of the invention is shown. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIGS. 1A, 1B and 1C are longitudinal views, in section and elevation, of the hydraulic jar of the present invention set for use as a down jar in its actuated or retracted position, with FIGS. 1B and 1C being downward continuations of FIG. 1A; 
     FIGS. 2, 3, 4 and 5 are cross sectional views taken along the lines 2--2, 3--3, 4--4 and 5--5, respectively, of FIG. 1B; 
     FIGS. 6A, 6B and 6C are views similar to FIGS. 1A, 1B and 1C, respectively, but depicting the jar of FIGS. 1A, 1B and 1C in its cocked or extended position; 
     FIGS. 7A, 7B and 7C are views similar to FIGS. 1A, 1B and 1C but depicting the jar cf FIGS. 1A, 1B and 1C set for use as an up jar in its cocked or retracted position; 
     FIGS. 8A and 8B are views similar to FIGS, 7A and and 7B, respectively, but showing the jar of FIGS. 7A, 7B and 7C in its actuated or extended position; and 
     FIG. 9 is a cross-sectional view taken along the line 9--9 of FIG. 1B. 
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENT 
     Referring to FIGS. 1A, 1B and 1C of the drawings, the reference numeral 10 refers, in general, to the jar of the present invention adapted to operate as a &#34;down jar&#34;, i.e. to provide high impact loading in a downward direction as viewed in the drawings. The jar 10 is shown in its collapsed position after completion of its impact stroke and includes an outer cylindrical housing assembly 12 formed by an intermediate housing member 14 connected between an upper housing member 16 and a lower cap member 18. Internal threading is provided on the two end portions of the intermediate housing member 14 which threadably engage cooperating external threading provided on the upper housing member 16 and the cap member 18, respectively. 
     The upper end of the upper housing member 16 is adapted for connection to a corresponding end of a section of coil tubing or wireline (not shown). When the jar 10 is placed in the well to be serviced, the coil tubing extends above the surface of the ground and is utilized to push or pull the jar 10 and pass fluid to the jar for passage through the jar for use in servicing the well. The connection between the coil tubing and the upper housing member 16 and the actuation of the coil tubing are well known in the art, and are disclosed in U.S. Pat. No. 4,515,220 and U.S. Pat. No. 4,655,291, issued to Phillip S. Sizer et al. and Don C. Cox, respectively, on May 7, 1985, and Apr. 7, 1987, respectively, and assigned to the same assignee as the present application. In view of this, and due to the fact that these techniques do not form a part of the present invention, they will not be shown nor further described. 
     A set screw 20a extends through aligned threaded radial bores extending through the intermediate housing member 14 and the upper housing member 16, respectively; and a set screw 20b extends through aligned threaded bores extending through the intermediate housing member 14 and the cap member 18, respectively, to secure the members against rotational movement. A pair of seal rings 22a and 22b extend in grooves formed in the upper housing member 16 and the cap member 18, respectively, and engage corresponding inner surfaces of the intermediate housing member 14. 
     A fluid inlet 24 is provided through the cap member 18 for the purpose of introducing fluid into the housing assembly 12 for reasons to be described. The inlet 24 is formed by a threaded bore which receives a plug 26 for closing same. 
     As shown in FIG. 2, four machined grooves 14a, 14b, 14c and 14d are formed in the inner wall of the intermediate housing member 14 and are spaced apart at 90 degree intervals, with groove 14a also shown in FIG. 1B. 
     An inner cylindrical mandrel assembly, shown in general by the reference numeral 30, extends within the housing assembly 12 in a coaxial relationship thereto. The assembly 30 consists of an intermediate mandrel member 32 connected between an upper mandrel member 34 and a lower member, or sub, 36. The lower end portion of the upper mandrel member 34 is externally threaded and engages a threaded counterbore formed in the upper end portion of the intermediate mandrel member 32. Internal threading is provided on the upper end portion of the sub 36 which threadedly engages corresponding external threading on the lower end portion of the intermediate mandrel member 32. A set screw 38 extends through aligned threaded radial bores in the sub 36 and in the intermediate mandrel member 32 to secure the members against rotational movement. The lower end portion of the sub 36 is adapted for connection to a well bore tool, or the like, in a conventional manner. 
     A pair of seal rings 40a and 40b extend within grooves formed in the upper housing member 16 and the cap member 18, respectively, and engage the outer surfaces of the upper mandrel member 34 and the intermediate mandrel member 32, respectively. The rings 40a and 40b function to seal against the escape of fluid from the chambers defined by the housing assembly 12 and the mandrel assembly 30, while permitting relative movement between the two assemblies, as will be described. A seal ring 42 extends in a groove formed in the upper mandrel member 34 and engages the inner surface of the intermediate mandrel member 32 to provide a seal between the two members, and a seal ring 44 extends in a groove in the lower sub 36 and engages the corresponding external surface of the intermediate mandrel member 32. 
     An annular shoulder 32a is formed on the outer surface of the intermediate mandrel member 32 near its upper end and, as shown in FIG. 3, has two diametrically opposed grooves 32b and 32c milled therein. An annular shoulder 34a extends from the outer surface of the upper mandrel member 34 near its lower end and, as shown in FIG. 4, has two diametrically opposed grooves 34b and 34c milled therein. The function of the shoulders 32a and 34a and their corresponding grooves will be described in detail later. 
     A seat ring 50 extends around the outer surface of the intermediate mandrel member 32 near its upper end and abuts against the upper end of the shoulder 32a. A seal ring 52 is disposed in a groove formed in the upper surface of the intermediate mandrel member 32 and engages the inner wall of the seat ring 50, and a retaining ring 54 is disposed in another groove formed in the upper surface of the intermediate mandrel member 32 and projects slightly from the later groove to retain the seat ring 50 in the abutting position relative to the end of the shoulder 32a as shown. 
     A cylindrical piston 56 extends around the outer surface of the intermediate mandrel member 32 just above the seat ring 50. The inner diameter of the piston 56 is slightly greater than the corresponding outer surface of the intermediate mandrel member 32 to enable the piston 56 to slide in an axial direction in a chamber 58 defined by the members 32 and 14, the upper end of the seat ring 50 and the lower end of the shoulder 34a. The diameter of the piston 56 is slightly greater than that of the seat ring 50 and that of the shoulder 34a so that the outer annular portions of the respective ends of the piston are exposed for reasons that will be described. 
     A pair of piston rings 60 and 62 extend in grooves formed in the outer surface of the piston 56 and their outer diameters conform to the inner diameter of the intermediate housing member 14. As shown in FIG. 9, an annular cut, or groove, is formed in the outer surface of each piston ring 60 and 62, as shown by the reference numeral 62a in connection with the ring 62, which forms an end gap. The flow of fluid is thus metered through these end gaps and the annular space between the cylindrical piston 56 and the intermediate housing member 14. As shown in FIG. 5, four grooves 56a, 56b, 56c and 56d are provided in the inner wall of the piston 56 and are spaced at 90 degree intervals to permit fluid flow therethrough. 
     In the position of the housing assembly 12 relative to the mandrel assembly 30 as shown in FIG. 1A-1C, the grooves 14a (and therefore grooves 14b, 14c and 14d which are not shown in FIGS. 1A, 1B and 1C) extend immediately adjacent the piston 56 in registry with the piston chamber 58. 
     A fluid chamber is defined by the housing assembly 12 and the mandrel assembly 30 and consists of two sections 64a and 64b. The chamber section 64a communicates with an annular flow passage 66 defined between the inner surface of the cap member 18 and a corresponding outer surface of the intermediate mandrel member 32 which passage receives fluid from the inlet 24. The piston 56, in effect, divides the chamber into the two sections 64a and 64b extending to the respective ends of the piston and communicating through the piston chamber 58. The fluid thus flows from the inlet 24, through the passage 66 and into the chamber section 64a from which it flows into and through the piston chamber 58 and to the chamber section 64b. The piston 56 forms a flow restriction to the passage of fluid through the chamber 58 and functions to control the fluid flow between the chamber sections as will be described. 
     In operation, and assuming the jar 10 is in the wellbore in the collapsed position of FIG. 1A-1C after having being actuated, and assuming that an additional actuation stroke is desired, the housing assembly 12 is cocked by pulling it upwardly, relative to the mandrel assembly 30. This is done by securing the sub 36 and pulling upwardly at a constant force via the coil tubing or wireline, attached to the upper end of the housing member 16. As the housing assembly 12 moves upwardly relative to the mandrel assembly 30, the upper end of the cap member 18 approaches the lower end of the shoulder 32a and thus decreases the volume of the chamber 64a. This forces the fluid to flow at a relatively high rate from the chamber section 64a into the chamber 5 and around the shoulder 32a, the seat ring 50, and the piston 56, largely via the added flow paths provided by the grooves 14a-14d. This flow continues into the chamber section 64b via the grooves 14a-14d, the annular space between the outer surface of the shoulder 34a and the inner wall of the intermediate housing member 14, and the grooves 34b and 34c of the shoulder 34a. The fluid is accommodated in the chamber section 64b due to the fact that the latter chamber continuously increases in volume with movement of the housing assembly 12 upwardly due to the lower end of the upper housing member 16 moving away from the upper end of the shoulder 34a. Since the diameters of the intermediate mandrel member 32 and the upper mandrel member 34 are the same, the sum of the volumes of the chambers 64a and 64b remain constant through the stroking process. 
     During this flow of fluid from the chamber section 64a into the chamber 58 and the chamber section 64b, the force of the fluid acting on the exposed outer annular portion of the lower end of the piston 56 and the frictional forces of the fluid between the non-grooved inner surface of the intermediate housing member 14 and the outer surfaces of the piston rings 60 and 62, forces the piston to slide upwardly until it contacts the lower end of the shoulder 34a. However, this does not disrupt the relatively high flow rate described above since, upon release of the piston 56 from its contact with the seat ring 50, the grooves 56a-56d are exposed thus permitting flow therethrough, which flow continues through these grooves and through the grooves 34b and 34c of the shoulder 34a when the piston contacts the shoulder. This movement and flow continue until the upper end of the cap member 18 contacts the lower end of the shoulder 32a and the jar 10 is in its expanded, or cocked, position as shown in FIGS. 6A, 6B and 6C. In this position the great majority of the fluid is in the chamber section 64b. 
     When it is desired to actuate the jar 10 from the cocked position of FIGS. 6A, 6B and 6C and produce the desired high impact loading, a constant downward pushing force is exerted on the housing assembly 12 by the coil tubing or wireline connected to the upper end of the housing member 16. This causes the housing assembly 12 to move downwardly relative to the mandrel assembly 30 and force the fluid from the chamber section 64b, which continuously decreases in volume with said movement, through the chamber 58 and into the chamber section 64a, which continuously increases in volume. The initial movement is relatively slow since the grooves of 14a-14d of the intermediate housing member 14 are not in registry with the chamber 58 (but rather are located above the chamber 58). Thus, the piston 56 restricts flow through the chamber 58 to meter the flow at a relatively low rate through the end gaps of the piston rings 60 and 62, and the annular flow passage defined between the piston and the corresponding inner wall surface of the intermediate housing member 14. The fluid, by virtue of being metered at a low rate, creates a frictional resistance to downward movement of the housing assembly 12. 
     During this movement, the force of the fluid acting on the exposed annular upper end portion of the piston 56, and the frictional forces of the fluid between the inner surface of the intermediate housing member 14 and the outer surface of the piston rings 60 and 62, forces the piston away from contact with the shoulder 34a and causes downward slideable movement of the piston toward the seat ring 50. During this brief time, additional flow is provided through the grooves 56a-56d of the piston until the lower end of the piston abuts against the upper end of the seat ring 50 but this additional flow is inconsequential due to the very brief time involved. When the piston 56 reaches the seat ring 50, the latter ring blocks communication between the grooves 56a-56d of the piston and the grooves 32b and 32c of the shoulder 32a. As a result, the flow from the chamber section 64b, through the piston chamber 58 and into the chamber section 64a continues at a metered, relatively low rate through the end gaps of the piston rings 60 and 62 and the annular flow passage between the piston 56 and the corresponding inner surface of the intermediate housing member 14. 
     With the chamber section 64a gradually increasing in volume and the chamber section 64b gradually decreasing in volume, this relative slow movement continues until the grooves 14a-14d of the intermediate housing member 14 align with the piston 56. At this position, the area of the flow passage dramatically increases, thus eliminating the frictional resistance of the fluid and causing a downward movement of the housing assembly 12 relative to the mandrel assembly 30 at a relatively high rate. This continues until the lower end of the cap member 18 strikes the upper end of the sub 36 causing a high impact. The resulting force is transmitted by the sub 36 to the tool, plug, or the like to which the lower end of the sub is attached causing the desired high impact loading. This completes the full cycle of operation which can be repeated if desired. 
     FIGS. 7A-7C, 8A and 8B depict the down jar 10 of FIGS. 1A-1C, 2-5, and 6A-6C, converted to an up jar, i.e., to provide high impact loading in an upwardly direction. More particularly, the seat ring 50 is moved upwardly to a position where its upper end abuts the lower end of the shoulder 34a of the upper mandrel member 34. It is noted that in FIG. 7B the seat ring 50 is provided with a groove in its inner wall which receives the seal ring 52 while in FIG. 1B the seal ring 52 is provided in a groove formed in the outer surface of the intermediate mandrel member 32. Although this latter arrangement is preferred from an assembly standpoint to prevent damage to the ring 52 during assembly, it is understood that either arrangement is within the scope of the invention. 
     Also in the arrangement of FIGS. 7A-7C, 8A and 8B, the intermediate housing member 14 has been rotated 180 degrees about a horizontal axis as viewed in the drawings so that the location of its ends are reversed. Thus the grooves 14a-14d are located below the piston chamber 58 when the lower end of the cap member 18 is in abutment with the upper end of the sub 36 as shown in FIG. 7C. In the latter position, the jar 10 is depicted in its collapsed position which corresponds to the collapsed position of the jar in FIG. 1A-1C, but in the case of FIG. 7A-7C this position is its cocked position. 
     When it is desired to actuate the jar 10 from its cocked position of FIG. 7A-7C, a constant upward pulling force is exerted on the housing assembly 12 by the coil tubing or wireline connected to the upper end of the housing member 16. This causes the housing assembly 12 to move upwardly relative to the mandrel assembly 30 which is held in place by the weight of the tool, or the like, to which it is attached. This forces the fluid from the chamber section movement, through the chamber 58 and into the chamber section 64b, which continuously increases in volume. This initial movement is relatively slow since the grooves 14a-14d of the intermediate housing member 14 extend below the chamber 58, resulting in a metered flow at a relatively low rate through the flow passage defined between the end gaps of the piston rings 60 and 62 and the annular flow passage between the piston 56 and the inner wall of the intermediate housing member 14. The fluid thus creates a frictional resistance to movement of the housing assembly 12. 
     During this movement, the force of the fluid acting on the exposed annular upper end of the piston 56 and the frictional forces of the fluid between the inner wall surface of the intermediate housing member and the piston rings 60 and 62 forces the piston away from contact with the shoulder 32a and causes upward slideable movement of the piston toward the seat ring 50. Thus, additional flow is provided through the grooves 56a-56d of the piston until the upper end of the piston abuts against the lower end of the seat ring 50, but this additional flow is inconsequential due to the very brief time involved. When the piston 56 reaches the seat ring 50, the latter ring blocks communication between the grooves 56a-56d and the grooves 34b and 34c of the shoulder 34a. As a result, the flow from the chamber section 64a through the piston chamber 58 and into the chamber section 64b continues at a metered, relatively low, rate resulting in relative slow movement of the housing assembly 12. 
     This relative slow movement continues until the grooves 14a-14d of the intermediate housing member 14 align with the piston 56 at which time the area of the flow passage dramatically increases. The frictional resistance of the fluid is thus eliminated causing a high velocity upward movement of the housing assembly 12 relative to the mandrel assembly 30 which is aided by the tensile forces stored in the coil tubing or wireline. 
     This relatively high-velocity movement continues until the upper end of the cap member 18 strikes the lower end of the shoulder 32a as shown in FIG. 8A and 8B causing a relative high impact. The resultant force is transmitted by the sub 36 to the tool, or the like, to which the lower end of the sub is attached causing the desired high impact loading and resultant dislodging of the tool. 
     The jar 10 can be recocked by pushing the housing assembly downwardly 12 relative to the mandrel assembly 30, which movement is at a relatively high velocity due to the alignment of the grooves 14a-14d with the piston 56 as described in connection with the upward movement of the housing assembly described in connection with FIG. 1A-1C. As previously described, once the piston 56 traverses the by-pass grooves 14a-14d, fluid can flow through the piston grooves 56a-56d and the slots 32b and 32c until the housing assembly reaches the cocked position of FIG. 7A-7C, and the above operation can be repeated as desired. 
     It is understood that in both the downloading and uploading operations described above, an accelerator and stem can be used in conjunction with the jar of the present invention to further increase the impact loading. 
     The previous description is illustrative of only some of the embodiments of the invention. Those skilled in the art will readily see other variations of the hydraulic jar of the present invention. Changes and modifications may be made without departing from the scope of the invention which is defined by the following claims.