CN101021147B - Sucker rod connection with improved fatigue resistance - Google Patents
Sucker rod connection with improved fatigue resistance Download PDFInfo
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- CN101021147B CN101021147B CN 200710000844 CN200710000844A CN101021147B CN 101021147 B CN101021147 B CN 101021147B CN 200710000844 CN200710000844 CN 200710000844 CN 200710000844 A CN200710000844 A CN 200710000844A CN 101021147 B CN101021147 B CN 101021147B
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Abstract
Sucker rod connections are provided, preferably for rods with 5/8'' to 1 1/8'' diameter, with improved fatigue resistance, formed by applying diametrical interferenc e to prevent disengagement, reducing axial interference between the pin shoulder of a mal e member and the box shoulder of a female member. The connection may comprise a tapered threaded connection and trapezoidal threads, where contact among threads is flank-to- flank, load and stab, the crest of the thread being a little larger than the root of the thread. Each rod may have from about 4 to 10 threads per inch, preferably about 6 and 10 threads per inch (25.4 mm), the thread flank angle ranges from about 2.degree. to 10.degree., preferably about 3.degree. with a line perpendicular to the connection axis, and the connection taper is from about 1/15 to 1/30 relative to diameters of the connection. The flank-to-flank contact improves fatigue performance and the width and angle of the threads are determined considerin g a very low plastic thread deformation. Furthermore, the tensile stresses and plastic deformations that appear upon loading the rod connection are reduced and their distribution is more homogeneous than in the case of a cylindrical connection with no diametrical interference, where release engagement depends solely on axial interference.
Description
Technical field
Embodiments of the invention relate to a kind of pumping rod connecting device, more particularly, relate to a kind of pumping rod connecting device with improved antifatigue and preparation method thereof.
Background technology
The bar that sucker rod is normally made by steel or other materials is to be used for forming the mechanical component between surface and downhole (downhole) element of being positioned at of insert pump.Sucker rod is grown up approximately 25 to 30 feet (about 7 to 9 meters) usually, has threaded so that the downhole element easily advances and withdraws from the end of stock.Sucker rod can with is connected that a screw thread box connects or other are threaded the connecting thread pin.Usually the diameter of sucker rod be 5/8 " (5/8 inch), 3/4 ", 7/8 ", 1 " and 1-1/8 ".
Diameter is 22.22 millimeters (1/8 inches), grade D, and the bar of API-11B produces the failure problems especially severe.Most of faults of pole occur in the last connecting portion (screw thread) of threaded.In the prior art, for example diameter is 22.22 millimeters (1/8 inches), grade D, and the bar of API-11B, the screw thread of bar is columniform, the diameter of pin screw thread is slightly more small than the diameter of described box.As Figure 1A and shown in Figure 3, when linking together, only have the load side (load flanks) of pin to contact with box.Therefore in other words, because there is no radial interference (interference), be necessary when they contacts, introduce in connecting between the shoulder of the shoulder of box and pin high be out of shape in case anti-avulsion from.This distortion produces larger axial tension and produce compression in box in pin.Due to assembling, the pulling force in pin is added to again the external tension (fatigue) of circulation, and is displaying when bar is pumped in well.As a result, thus the screw thread place that this tension force often surpasses that power that steel can bear in the end connects shank is ruptured.
Summary of the invention
For solving the problem of bar fatigue, some embodiments of the present invention relate to the connection of sucker rod, and target is to strengthen the fault-resistant ability that causes due to fatigue.
One embodiment of the present of invention relate to a kind of linkage of sucker rod, preferably include the threaded pin of end tool of the rod that is connected to the screw thread box, wherein improve antifatigue by using radial interference, it prevents from breaking away from and reduces substantially with the axial interference in formerly design.More particularly, the embodiment of the present invention relates to a kind of linkage, and it comprises tapered thread connection, trapezoidal thread and side being threaded to side, load and clinching.Further embodiment comprises that its Surface Vertical is in the axle of pin near the shoulder of the rear end screw thread of pin.Described box can have another shoulder that close screw thread begins, and its Surface Vertical is in the axis of described box.In the time assembling, two surfaces are in contact with one another with accurate control radial interference.
In one embodiment, the connection of a taper or taper thread, trapezoidal thread, side are combined side screw thread contact, load and clinching.Preferably, described linkage per inch approximately comprises 4 to 10 screw threads, it is characterized in that, the angle of the flank of each screw thread roughly becomes 2 degree to the scope of 10 degree with respect to the vertical line that connects axis, preferably, is approximately 3 degree.The tapering that is threaded is roughly from 1/15 to 1/30 of the diameter of described connection.
End in assembling also can comprise shoulder, and is similar with front case but not identical.The minimizing that like this, can obtain by the mode of radial interference axial interference prevents from breaking away from.The reason that can obtain this radial interference is that the trapezoidal entity part of a screw thread enters the part of the trapezoidal sky of another screw thread, obtains the wedge shape effect.In other words, the top of screw thread is greater than the root of screw thread.
As mentioned below, tired parameter D is calculated by following formula:
Wherein:
S
ai: the alternating component of main stress bar
S
mi: the average weight of main stress bar
T: minimum tensile strength
Calculate alternating component and average weight according to maximum value and the minimum value of duty cycle.
Preferably, coefficient D higher than or equal 1 to guarantee extremely long fatigue life.
In research formerly, (API recommends to carry out 11BR according to the API-11BR standard, " Recommended Practice for Care and Handling of Sucker Rods ", in October, 1989, this whole introducing for your guidance), after shoulder contact, the circumferential displacement of the external diameter of the shoulder of pin be 7.14 millimeters (9/32 "); Such shift value means 0.14mm (the axial interference of .0055 ").(external diameter of the shoulder of 1.626 "), girth are 129.75 millimeters (5.108 ") for 41.3 millimeters of pins; Therefore screw thread axial distance (thread lead) is 2.54 millimeters, and (.100 "), the circumferential displacement of 7.14 millimeters (.281 ") produces the axial interference of 0.14 millimeter (.0055 ").
Therefore, the purpose of some embodiment described herein is to provide to be had radial interference the sucker rod of (diametricalinterference) connects, and it can reduce axial interference.
Another purpose of some embodiment described herein is to connect by tapered thread to provide described connection, has trapezoidal thread, side to side, load and clinching and the contact between them.
Another purpose of some embodiment described herein is to reduce axial interference by radial interference.
Another purpose of some embodiment described herein is by the side, side, load and clinching and the contact between them to be improved anti-fatigue ability.
The other purpose of some embodiment described herein is the width of thread and the angle that low thread distortion and design correspondingly are provided.
The other purpose of some embodiment described herein is to reduce tensile stress and distortion when connecting when loading, and reduces plastic strain, and is more even compared with the distribution of those tension force of cylindrical thread connected mode and distortion like this.
Description of drawings
Fig. 1 shows the taper connection according to one embodiment of the present invention.
Figure 1A is presented at cylindricality traditional between sucker rod and screw thread box and connects.
Figure 1B shows the taper connection of using trapezoidal thread according to one embodiment of the present invention.
Fig. 1 C shows the pitch line position with respect to trapezoidal thread in Figure 1B, and making the cavity side of this screw thread is identical with solid side.
Fig. 2 A and 2B show the improved Goodman chart of D grade pumping rod, both for detection of the maximum stress of fatigue limit, minimum stress and the permission of stress.Three load cycles are from-1.8 to 7.2kg/mm
2(2.56 to 10.2ksi (KSI)), 1.8 to 20.7kg/mm
2(2.56 to 29.4ksi) and 13.5 to 27kg/mm
2(19.2ksi is to 38.4ksi).The 3rd load cycle of here using refers to connect in three load cycle pointed that.
Fig. 3 is presented at each main stress bar of the yield stress that connects with respect to tradition in assembling process.
Fig. 4 A is presented at the plasticity tension force in assembling process, and Fig. 4 B is presented at the plasticity tension force under the 3rd load cycle maximum load that connects for traditional cylinder.For two kinds of situations, plasticity tension force is at (A) with (C).
Fig. 5 is presented at the chart that five zoness of different are used for the fatigue ratio D of traditional rod connection.
Fig. 6 is presented in assembling process and is used for cylinder in tension force and is connected on screw thread contact force corresponding to maximum fatigue and cyclic.
Fig. 7 is presented in a connection of embodiment of the present invention under the 0.20mm radial interference, in assembling process corresponding to three right angle main stress bares of yield stress; Wherein the main stress bar for numerical value i equals 1,2 or 3.Relative main stress bar N ° of i=main stress bar i/ yield stress.(also with reference to Figure 11)
Fig. 8 A is connected the plasticity tension force under the 0.20mm radial interference in the connection of an embodiment of the invention with 8B, in assembling process and under maximum load, show plasticity tension force (A).
Fig. 9 shows the chart of fatigue ratio D in the connection of one embodiment of the present invention, under five kinds of zoness of different and 0.20mm radial interference, has shown regional C.
Figure 10 is presented in the connection of one embodiment of the present invention, and under the 0.20mm radial interference, the chart of contact force on screw thread in assembling process and in the assembling process of maximum load, has the top line of the expression axial force limit (5000kg).
Figure 11 is presented in the connection of one embodiment of the present invention, under the 0.10mm radial interference, in assembling process with respect to three main stress bares of yield stress.
Figure 12 A is connected the plasticity tension force in the connection of one embodiment of the present invention with 12B, the 0.10mm radial interference and have shown in the maximum load of plasticity tension force (A).
Figure 13 shows the fatigue ratio D chart of one embodiment of the present invention, the plasticity tension force (C) shown in having under five zones of different 0.10mm radial interference.
Figure 14 is presented at the chart of contact force on the screw thread of connection of one embodiment of the present invention, under the 0.10mm interference, in assembling process and have in the assembling process of maximum load, has the top line of the expression axial force limit (5000kg).
The specific embodiment
The present invention is about sucker rod, illustrates hereinafter especially for the embodiment of the connection of this sucker rod.
As shown in Figure 1, being threaded between sucker rod and screw thread box comprises box thread end 20 according to one embodiment of present invention, and perhaps box, and male thread end 40 is perhaps sold, and both are mutually corresponding, usually, and cone-shaped inner surface 22,42.Preferably, cone-shaped inner surface 22,42nd, about 1/15 to 1/30 of the diameter of pin or box.These cone-shaped inner surfaces 22,42 comprise screw thread.As shown in Figure 1B, screw thread 100 have internal diameter wherein the external surface of each screw thread and pin or box engage, and external diameter wherein each screw thread arrive its top.Like this, each screw thread has the groove 102 that is adjacent.
Box thread end 20 and male thread end 40 are adjacent to shoulder 30 when coupling together fully, as shown in Figure 1.
The connection that the present invention proposes, what be connected with radial interference is that tapered thread connects, the axial shrink value that does not need original known thread to connect is so high.Analyze two axial shrink values (0.10 and 0.05 millimeter), on the basis of obtaining a result according to the limited component models that is used for connecting, adopted less value.
The character of D grade material is existing in API 11B to be determined.According to von Mises stress criterion and isotropic hardening, desirable material is elastoplast, have the polyteny hardened material of relevant plasticity.Steel are embodiment, and this material has the linear deformation in its elastic limit.Along with the generation of permanent deformation, plastic deformation occurs on elastic limit.
The cardinal principle situation of five embodiment of following form display analysis.Comprise that from one tapered thread connects, trapezoidal thread and side are to the side, (for example contacting of load and clinching, the contacts side surfaces of shown screw thread 100 in Figure 1B), but the effect of difference choice variable, for example in the axial interference of shoulder, radial interference, width and the flank angle of screw thread are all analyzed.
In the embodiment of each above-mentioned five analysis, the pitch diameter of thread of selling by measurement, the pitch diameter of thread of box, thus and both diameters are subtracted each other the measured place radial interference.Like this, the pitch diameter of thread on the meaning pin of radial interference is larger than the pitch diameter of thread of box.
But the groove of screw thread also may interference.In other words, the outside diameter of thread of pin can be larger than the screw thread interior diameter of box.
Each width of thread of above five embodiment is in threaded line place's measurement of each screw thread 100, as shown in the label Y of Fig. 1 C.Measure flank angle γ (gamma) in lateral side wire with between perpendicular to the line of connecting axle, as shown in Figure 1B.
Following table shows different situations.
| The axial screw thread of per inch (screw thread/25.4 millimeter) | Angle of the flank (load and clinching) | Axially interference | Radial interference | |
| Embodiment 1 | 8 | 7° | 0.10mm | 0.20mm |
| Embodiment 2 | 8 | 7° | 0.05mm | 0.20 |
| Embodiment | ||||
| 3 | 8 | 7° | 0.05mm | 0.05 |
| Embodiment | ||||
| 4 | 6 | 3° | 0.05mm | 0.20mm |
| Embodiment 5 | 6 | 3° | 0.05mm | 0.10mm |
Yield stress: 59.77kg/mm2=85KSI (initial stress of D grade yield stress or plastic strain)
Five embodiment interpretations of result
The icon that should be noted that Fig. 6 shows the power on the screw thread be applied to pin, and No. 1 pitch of thread from shoulder farthest.
Embodiment 1
Design more undesirable both ways: (the plastic screw thread) of structure and fatigue (larger negative value coefficient).In the higher place of major principal stress, coefficient D shows poorer performance.Such stress is the result of axial interference.
Embodiment 2
We improve stress distribution in the reduction of axially interference at hypothesis, and therefore, fatigue ratio D is confirmed.But, the problem of screw thread plasticizing or screw thread fatigue is still arranged.
From structure and tired related angle, although the result that the present embodiment obtains is pretty good, radial interference is considered very little, because it is near producer's the grade of tolerance, and 0.05 millimeter of general every part (perpart).Like this, the radial interference of 0.05 millimeter means, in practical operation, this radial interference is can be the same with 0.10 millimeter large or can be the same little with 0.00 millimeter.
With tired relevant, the result that obtains is pretty good from structure.Remember linkage producer's tolerance, repeatedly analyze with 0.20 millimeter radial interference, this numeral is considered to the radial interference value of nominal.
Embodiment 5
Analyzed a less radial interference value in the present embodiment.Obtained result is good concerning two radial interference values.The scope of determining and producer's tolerance are consistent.
Fig. 1 (A and B) and Fig. 2 (A and B) be existing the description hereinbefore.Fig. 3 to 14 shows the comparative result of two designs, and clear proof taper connection is for the advantage of cylindrical connection.As in Fig. 3 to 14 description used, " equipment " or " assembling " moment of torsion is the needed moment of torsion of axial interference of obtaining specified quantitative, after being applied to shoulder 30 and contact, as shown in Figure 1.Numeral has shown and is tightening the process intermediate principal stress, equal plastic strain and the final power on the pin screw thread, and calculate the fatigue ratio that is considered to crucial in some zone.Remember the relation of producer's tolerance value, test need to be considered two radial interference when carrying out, and in embodiment A, one lower (0.10 millimeter) in higher one (0.20 millimeter) and Embodiment B, all produce similar effect.Fig. 3,7 and 11 show the disappearance along with the high stress areas between the last screw thread that is connected at shoulder with pin, the main stress bar value is also reducing.Because reduce axial interference, thereby improve the fatigue performance that connects.
About plastic strain, it is unimportant that Fig. 8 A, 8B, 12A, 12B are presented in taper connection plasticity.For the radial interference of 0.20 millimeter in Fig. 8 A and 8B, only have plastic strain, for the radial interference of 0.10 millimeter in Figure 12 A and 12B, almost there is no plasticity.In Fig. 4, the plasticity of seeing in cylindrical connection is more remarkable, and the last threaded portion that impact is connected with pin is also the most incidental place of fatigue.
It is better that fatigue ratio D shows in taper connection, and (referring to Fig. 5,9 and 13), this coefficient must be than 1 great fatigue lives to guarantee to connect greatly,
At last, be understandable that due to less axial interference, the power on the pin screw thread that (Figure 10 with are connected) is added in the cylindrical connection of final force rate on the pin screw thread in taper connection is less.
Although foregoing description shows, describes and points out the novel feature that the present invention is the most basic, but be understandable that, technical field those skilled in the art still can utilize the present invention with different omission of the present invention, variation alternative, the details form in the scope that does not break away from the present invention's enlightenment.Therefore, the scope of the present invention's enlightenment should be not limited to aforementioned discussion, and should be limited by attached claim.
Claims (20)
1. pumping rod connecting device comprises:
Be positioned at the taper male element of end of the rod of sucker rod, comprise that several have the outer trapezoidal screw thread of crest and pitch diameter of external thread, and
The female element of taper, comprise several have tooth at the bottom of and the inner trapezoidal thread of thread pitch diameter, wherein said male element can be housed in to be threaded in described female element;
Wherein, the screw thread of described male element and the screw thread of described female element are that the side is to contacts side surfaces, each screw thread has two sides, at the bottom of the tooth of described externally threaded crest greater than described internal thread, and set up radial interference between described male element and female element, prevent the disengaging between described male element and female element and fully reduce axial interference
Wherein by the described central diameter of the described internal thread of the described externally threaded described central diameter of described male element and described female element is subtracted each other, described radial interference provides positive difference.
2. linkage according to claim 1, is characterized in that, described male element has shoulder and its Surface Vertical in the longitudinal axis of described male element, and described shoulder is positioned at the screw tip near described screw thread augmenting portion.
3. linkage according to claim 2, is characterized in that, described female element has shoulder in its front, perpendicular to the longitudinal axis of described female element.
4. linkage according to claim 3, is characterized in that, when the assembly and connection device, described two shoulders contact and be provided at accurate radial interference between described male element and female element screw thread.
5. linkage according to claim 1, is characterized in that, each described male element and female element comprise 4 to 10 screw threads on per inch.
6. linkage according to claim 1, is characterized in that, each described male element and female element comprise 6 to 10 screw threads on per inch.
7. linkage according to claim 1, is characterized in that, the screw thread of described male element and female element has angle of the flank, and load and clinching are with respect to have 2 to 10 degree perpendicular to the vertical line that connects axis.
8. linkage according to claim 1, is characterized in that, the screw thread of described male element and female element has angle of the flank, and load and clinching are with respect to have about 3 degree perpendicular to the vertical line that connects axis.
9. linkage according to claim 1, is characterized in that, the tapering of described male element and female element with respect to male element and female element diameter separately in 1/15 to 1/30 scope.
10. pumping rod connecting device comprises:
Pin with screw tip part of taper; With
Box with screwed hole of taper, the end portion of wherein said pin is fixed by radial interference;
Wherein, at the bottom of the screw thread of described pin and box is respectively outer trapezoidal screw thread with crest and pitch diameter of external thread and has tooth and the inner trapezoidal thread of thread pitch diameter, at the bottom of the tooth of described externally threaded crest greater than described internal thread, the screw thread of described pin and the screw thread of described box are that the side contacts with clinching side, load and contacts, the wedge shape effect is provided, wherein by the described central diameter of described externally threaded described central diameter and described internal thread is subtracted each other, described radial interference provides positive difference
The trapezoidal entity part of one of them screw thread enters the part of the trapezoidal sky of another screw thread, obtains the wedge shape effect.
11. linkage according to claim 10 is characterized in that, comprises 4 to 10 screw threads on described each pin and box per inch.
12. linkage according to claim 10 is characterized in that, approximately comprises 6 screw threads on described each pin and box per inch.
13. linkage according to claim 10 is characterized in that, described pin is connected screw thread to be had angle of the flank and has the angles of 2 to 10 degree with respect to the vertical line that connects axis with box.
14. linkage according to claim 10 is characterized in that, the screw thread of described pin and box has clinching side and load flanks, has the angle of about 3 degree with respect to the vertical line of pin and box axis.
15. linkage according to claim 10 is characterized in that, the tapering of the perforate of described pin end portion and box with respect to separately diameter in 1/15 to 1/30 scope.
16. the pumping rod connecting device with axial interference of improved antifatigue and minimizing comprises:
The pin with tapered distal end part that comprises several trapezoidal threads; With
Box with screwed hole of taper, the end portion of wherein said pin is fixed by radial interference;
Wherein having at the bottom of tooth of the outer trapezoidal screw thread with crest and pitch diameter of external thread of (i) described pin and box is side contacting the side with the inner trapezoidal thread of thread pitch diameter, the load contact contacts with clinching, at the bottom of the tooth of described externally threaded crest greater than described internal thread; (ii) comprise four to ten screw threads on each described pin and box per inch; (iii) screw thread of described pin and box has angle of the flank, and load and clinching have respectively the angle of 2 to 10 degree with respect to the vertical line perpendicular to pin and box axis; (iv) tapering of the perforate of described pin and box with respect to the diameter of end portion and perforate in 1/15 to 1/30 amplitude range; (v) surperficial shoulder is positioned on pin and is positioned at the front of described box perpendicular to the axis of described box perpendicular to described pin axis and near rear end screw thread and another surperficial shoulder, wherein by the described central diameter of described externally threaded described central diameter and described internal thread is subtracted each other, described radial interference provides positive difference
The trapezoidal entity part of one of them screw thread enters the part of the trapezoidal sky of another screw thread, obtains the wedge shape effect.
17. linkage according to claim 16 is characterized in that, comprises six screw threads on each described pin and box per inch
18. linkage according to claim 16 is characterized in that, the screw thread of described pin and box has angle of the flank, and load and clinching have the angle of about 3 degree with respect to the vertical line of linkage axis.
19. the method for a connecting with pumping rod comprises:
The sucker rod that has with the tapered thread end portion of the outer trapezoidal screw thread that possesses crest and pitch diameter of external thread is provided;
Provide and have with at the bottom of possessing tooth and the box of the tapered thread perforate of the inner trapezoidal thread of thread pitch diameter;
At the bottom of the tooth of described externally threaded crest greater than described internal thread, wherein by the described central diameter of described externally threaded described central diameter and described internal thread is subtracted each other, set up the radial interference of the difference that provides positive between described external screw thread and described internal thread,
To be screwed into the perforate of described box with the tapered thread end portion, and it is characterized in that, the screw tip part radially is connected with described threaded hole,
The trapezoidal entity part of one of them screw thread enters the part of the trapezoidal sky of another screw thread, obtains the wedge shape effect.
20. the method for connecting with pumping rod according to claim 19 is characterized in that, the end portion of described screw thread comprises trapezoidal thread.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US77352306P | 2006-02-15 | 2006-02-15 | |
| US60/773,523 | 2006-02-15 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101021147A CN101021147A (en) | 2007-08-22 |
| CN101021147B true CN101021147B (en) | 2013-06-26 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200710000844 Expired - Fee Related CN101021147B (en) | 2006-02-15 | 2007-01-12 | Sucker rod connection with improved fatigue resistance |
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| CN (1) | CN101021147B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10077858B2 (en) | 2015-06-18 | 2018-09-18 | Vetco Gray, LLC | Anti-rotation key for threaded connectors |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2211173A (en) * | 1938-06-06 | 1940-08-13 | Ernest J Shaffer | Pipe coupling |
| US4917409A (en) * | 1983-04-29 | 1990-04-17 | Hydril Company | Tubular connection |
| US6050610A (en) * | 1997-05-20 | 2000-04-18 | Hydril Company | Stress reduction groove for tubular connection |
| CN2413015Y (en) * | 1999-12-17 | 2001-01-03 | 侯毅 | Coupling for round thread connecting oil field casing and tubing |
| CN2731065Y (en) * | 2004-05-21 | 2005-10-05 | 中国石油天然气集团公司 | Air sealed threaded sleeve joint |
-
2007
- 2007-01-12 CN CN 200710000844 patent/CN101021147B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2211173A (en) * | 1938-06-06 | 1940-08-13 | Ernest J Shaffer | Pipe coupling |
| US4917409A (en) * | 1983-04-29 | 1990-04-17 | Hydril Company | Tubular connection |
| US6050610A (en) * | 1997-05-20 | 2000-04-18 | Hydril Company | Stress reduction groove for tubular connection |
| CN2413015Y (en) * | 1999-12-17 | 2001-01-03 | 侯毅 | Coupling for round thread connecting oil field casing and tubing |
| CN2731065Y (en) * | 2004-05-21 | 2005-10-05 | 中国石油天然气集团公司 | Air sealed threaded sleeve joint |
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| Publication number | Publication date |
|---|---|
| CN101021147A (en) | 2007-08-22 |
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Granted publication date: 20130626 Termination date: 20210112 |