Metal seal well packer

A well packer has a metal seal which seals between the packer mandrel and the casing. The metal seal includes a seal sleeve located on the exterior of the mandrel. The sleeve has an inner wall and an outer wall radially separated by a channel. The inner channel is initially separated from the exterior of the mandrel by a clearance. An energizing ring is sizably mounted to the mandrel for axial movement relative to the mandrel. Initially, the energizing ring will be located at the entrance of the channel. An actuating device moves the energizing ring into the channel, wedging the walls of the seal sleeve apart. The inner wall seals against the mandrel. The outer wall seals against the casing.

BACKGROUND OF THE INVENTION 
1. Field of the Invention 
This invention relates in general to oil and gas well downhole production 
equipment, and in particular to a packer that has a metal seal for sealing 
against the casing. 
2. Description of the Prior Art 
An oil well packer is a device that is set downhole to separate a zone 
below from a zone above. The packer has a seal element which seals against 
casing. The packer will be connected to production tubing, sealing the 
annulus surrounding the tubing. 
There are many varieties of packers. Packers generally include set of slips 
which grip the casing and a packer element which seals against the casing. 
Normally, the packer element is an elastomer. However, some wells have 
temperatures of 450 degrees F., and at these temperatures, elastomers are 
not suitable. Metal seal packer elements are known. Metal seals are longer 
lasting and will withstand higher temperatures and pressures than 
elastomers. However, it is difficult to form a high pressure seal against 
the casing bore with a metal seal. The casing has an interior surface that 
is not machined for sealing. The bore may have scratches, pits and other 
irregularities that are not conducive to a high pressure metal seal. Some 
wells require that the packer be able to seal 20,000 psi. 
Additionally, slight axial movement between the casing and the packer may 
occur after installation, such as during hydraulic fracturing operations. 
The pumping action creates pressure pulses of 60 to 120 cycles per minute. 
This relative movement is detrimental to metal seals. 
SUMMARY OF THE INVENTION 
A metal seal packer element is provided in this invention. The packer has a 
tubular mandrel which secures to a string of tubing. A metal seal sleeve 
is carried on the exterior of the mandrel. The seal sleeve has inner and 
outer walls which are radially separated by a channel. Also, the inner 
wall is radially separated from the exterior of the mandrel by a 
clearance. An energizing ring slidably mounts to the mandrel for axial 
movement. While in the running-in position, the energizing ring is located 
at the entrance of the channel of the setting sleeve. The energizing ring 
has a greater radial thickness than the initial width of the channel. An 
actuating means will move the energizing ring axially relative to the seal 
sleeve, so that it enters the channel and wedges the inner and outer walls 
apart from each other. This causes the inner wall to seal against the 
exterior of the mandrel and the outer wall to seal against the interior of 
the casing. 
In the preferred embodiment, the mandrel has a set of wickers on its 
exterior. The inner wall of the seal sleeve embeds within the wickers when 
set. Also, preferably, the outer wall of the seal sleeve has a plurality 
of bands which protrude from the outer surface. These bands provide 
recesses between them. An inlay of soft metal is located in the recesses. 
The bands deform when the outer wall is pressed into sealing engagement 
with the casing hanger.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
Referring first to FIG. 2, the sealing portion of the packer is shown in 
enlarged detail. The packer has a mandrel 11 which extends along the 
longitudinal axis. Mandrel 11 is a tubular member which is lowered within 
the casing 13 of the well. Mandrel 11 has a bore 15. A seal sleeve 19 
having an outer diameter slightly less than the inner diameter 17 of 
casing 13, is carried on the exterior of mandrel 11. Seal sleeve 19 is 
secured to mandrel 11 by a set of threads 21. The upper end of seal sleeve 
19 makes up against a downward facing make-up shoulder 23 formed on 
mandrel 11. During assembly, seal sleeve 19 is tightened to a selected 
preload against make-up shoulder 23, so as to assure that there will be no 
axial movement of seal sleeve 19 relative to mandrel 11 during the setting 
action. 
Seal sleeve 19 has a cylindrical inner wall 25 that extends downward and 
has an inner diameter that is slightly greater than the outer diameter of 
mandrel 11 at that point. A set of wickers 29 are formed on the exterior 
of mandrel 11 and surrounded by seal sleeve inner wall 25. Wickers 29 are 
parallel circumferentially extending parallel grooves, not threads. 
Wickers 29 are preferably triangular in cross-section and have a pitch of 
about 1/8th inch. An initial clearance exists between wickers 29 and inner 
wall 25 during the running-in position which is shown in FIG. 2. 
Seal sleeve 19 has an outer wall 31 that is cylindrical and spaced radially 
outward from inner wall 25. In the embodiment shown, outer wall 31 does 
not extend downward as far as inner wall 25, terminating about one-half 
the length of inner wall 25. An annular channel 33 exists between inner 
wall 25 and outer wall 31. 
A plurality of bands 35 protrude from the exterior of outer wall 31. Bands 
35 are parallel, circumferential, metal ribs integrally formed with the 
body of outer wall 31. The outer diameter of bands 35 is slightly less 
than the inner diameter 17 of casing 13 during running-in. Seal sleeve 19, 
and thus bands 35, has a lesser hardness or yield strength than casing 13, 
preferably about one-half. The yield strength for casing 13 for high 
pressure, high temperature wells is typically in excess of 100,000 psi, 
and preferably about 125,000 psi. Similarly, mandrel 11, and thus wickers 
29, has a greater hardness or yield strength than inner wall 25, 
preferably about twice. 
Bands 35 have recesses between them which are partially filled with an 
inlay 37 of soft metal such as a lead/tin alloy. Inlay 37 has to have the 
ability to withstand well temperatures up to 450 degrees F., but be 
capable of soldering or flame spraying. Inlay 37 has a lesser hardness or 
yield strength than the hardness of bands 35, preferably about one-fourth. 
Inlay does not completely fill the recesses between the bands 35, rather a 
V-shaped groove is formed within the outer surface of each inlay 37. The 
amount of inlay 37 is selected so that when bands 35 deform, decreasing 
the volume of the recesses, inlay 37 will substantially fill the decreased 
volume and will not significantly extrude out past bands 35. Inlay 37 
lubricates the seal during the setting action and also during slight 
relative movement due to cyclic movement that occurs after setting. 
An energizing ring 39 is located below seal sleeve 19 for performing the 
setting action. Energizing ring 39 has a tapered upper nose that locates 
within a tapered section at the entrance of channel 33. The radial 
thickness of energizing ring 39 is greater than the radial dimension of 
channel 33 so that it will wedge inner and outer walls 25, 31 apart when 
forced into channel 33. A plurality of saw-toothed shaped grooves 40 are 
located on the inner diameter of energizing ring 39. When energizing ring 
39 is forced into channel 33, grooves 40 grip the outer diameter of inner 
wall 25 to anchor energizing ring 39 in the set position. Displacement 
passage 41 allows for the displacement of fluid from channel 33 when 
energizing ring 39 moves into channel 33. During the setting action, an 
actuating means which will be described subsequently moves energizing ring 
39 upward into channel 33. This movement wedges inner and outer walls 25, 
31 radially apart. Inner wall 25 embeds permanently into wickers 29, 
forming a metal-to-metal seal. Bands 35 deflect and permanently deform 
against inner diameter 17 of casing 13, forming a metal-to-metal seal. 
After installation, such as during hydraulic fracturing operations, some 
axial movement between seal sleeve 19 and casing 17 might occur. Inlay 37 
provides lubrication and helps maintain sealing against inner diameter 17 
of casing 13. 
The remaining portions of the packer do not form a part of the invention 
being claimed, but are shown to illustrate one means for actuating seal 
sleeve 19. Mandrel 11 is secured at its upper end to a string of tubing 43 
that extends to the surface. In the embodiment shown, mandrel 11 has a set 
of upper ramps 45 which support a set of upper slips 47. An upper coil 
spring 49 when released will provide energy to force slips 47 upward on 
ramps 45 to grip casing 13 (FIG. 2). An upper spring housing 51 surrounds 
upper spring 49. 
Referring to FIG. 1B, a lower spring 53 is carried below upper spring 49. 
Lower spring 53 is also a coil spring, however it operates downward to 
actuate a set of lower slips 54 (FIG. 1C). Lower slips 54 are carried on 
lower ramps 56. Lower spring 53 (FIG. 1B) is surrounded by a lower spring 
housing 55. 
Slips 47, 54 are shown in the running-in position. Springs 49, 53 are 
restrained from moving slips 47, 54 to the setting position. In the 
embodiment shown, the means to release springs 49, 53 comprises an 
explosive bolt 57. Explosive bolt 57 is connected to a detonator and coil 
assembly 58. To set the packer, an electrical coil (not shown) is lowered 
through the tubing by a wireline onto a locator shoulder 59 adjacent coil 
assembly 58. When supplied with current, electrical power is induced into 
coil assembly 58, which ignites a detonator to part bolt 57. This releases 
coil springs 49, 53 to move slips 47, 54 to a setting position gripping 
casing 13 (FIG. 2). Slips 47, 54 prevent relative movement between mandrel 
11 and casing 13 once set. 
Referring to FIG. 1D, after slips 47, 54 have been set, seal sleeve 19 will 
be set. In this embodiment, this is handled by an actuating sleeve 63, 
which is secured to the lower end of energizing ring 39. Actuating ring 63 
is driven by a number of pistons 65. Pistons 65 are rigidly secured to the 
exterior of mandrel 11. A movable cylinder 66 surrounds each piston 65. 
Each cylinder 66 is secured rigidly by screws to each other, with the 
upper one being rigidly secured to actuating sleeve 63. A pressure chamber 
67 is formed within each cylinder 66 above each piston 65. A communication 
passage 69 is located within mandrel 11 for communicating mandrel bore 15 
with pressure chambers 67. The lower end 70 (FIG. 1E) of communication 
passage 69 is open to mandrel bore 15. High pressure fluids, up to 10,000 
psi, are pumped down the tubing and supplied to the bore 15 of mandrel 11. 
Passages (not shown) lead from each pressure chamber 67 to communication 
passage 69. A shear screw 71 holds cylinders 66 in an initial lower 
running-in position. From the application of high pressure to bore 15, 
shear screw 71 will shear because of the high pressure in pressure 
chambers 67. This forces cylinders 66 upward, and along with them 
actuating sleeve 63 and energizing ring 39. This sets seal sleeve 19. 
Then, the pressure may be relieved as the wedging of energizing ring 39 
into channel 33 (FIG. 2) is permanent. 
The invention has significant advantages. The metal seal will effectively 
seal against casing. It withstands high temperatures and high pressures. 
It has a long life and is capable of accommodating slight movement due to 
cyclic loading. 
While the invention is shown in only one of its form, it should be apparent 
to those skilled in the art that it is not so limited but is susceptible 
to various changes without departing from the scope of the invention.