Subsurface safety valve actuation pressure amplifier

A hydraulic pressure booster is disclosed which, when used in conjunction with a control system for a subsurface safety valve, allows the use of lower pressure ratings on the wellhead equipment, yet at the same time provides sufficient hydraulic pressure to actuate a subsurface safety valve at depths that could exceed 4,000 feet. A preferred embodiment compensates for any fluid loss through the seals to ensure effective operation. The hydraulic pressure booster comprises an amplifier to receive fluid pressure from a fluid pressure source and magnify the pressure. A conduit system facilitates connection of the pressure source to the amplifier and the magnified pressure from the amplifier to the subsurface safety valve. The system is simple and self-regulating and can be alternatively installed as an integral portion of the subsurface safety valve or immediately adjacent the subsurface safety valve or immediately below the wellhead.

FIELD OF THE INVENTION 
The field of this invention relates to subsurface safety valves which are 
controlled from the surface and a control pressure amplifier which 
facilitates use of wellheads having lower pressure ratings for subsurface 
safety valves mounted at significant depths. 
BACKGROUND OF THE INVENTION 
In some locations, the use of subsurface safety valves is mandated. 
Historically, this has been in locations such as in the Gulf of Mexico 
where wells were drilled on the Outer Continental Shelf to fairly shallow 
depths. The subsurface safety valves used in those applications required 
control lines which went to the surfaces with the subsurface safety valve 
generally deployed at depths of about 1,000 ft. The subsurface safety 
valve was maintained in a closed position by a return spring which was 
sized to keep a sleeve in the position required for the valve to be closed 
against the hydrostatic forces in the control line, as well as any 
pressures in the wellbore surrounding the subsurface safety valve. 
As wells began to be drilled more deeply and subsurface safety valves had 
to be placed further and further below the surface, the force necessary 
for the return spring to resist these forces became far greater with 
increasing depth. Thus, one approach that was used previously was simply 
to increase the pressure rating of the control components, including the 
wellhead, so that they would be suitable for the pressures expected. Other 
techniques involved use of pressurized chambers to offset the effect of 
hydrostatic forces or equalization techniques to neutralize the effects of 
such hydrostatic forces. U.S. Pat. No. 4,660,646 illustrates the use of 
pressurized chambers to offset the return spring forces. U.S. Pat. No. 
5,415,237 illustrates the use of valving arrangements to obtain the 
requisite pressure balance on the sliding sleeve so as to minimize the 
forces required to actuate the sleeve against a much smaller return 
spring. 
These techniques were fairly complex, involving numerous moving parts and 
seals. While they accomplish the purpose of allowing wellheads of a lower 
pressure rating to be used, even in applications involving significant 
depths such as 10,000 ft., their cost was high and the numerous components 
used made maintenance and upkeep an issue. Accordingly, the apparatus and 
method of the present invention have been developed to allow a simple way 
to be able to use low-pressure wellheads, even in applications of fairly 
deep subsurface safety valves in the order of deeper than 10,000 ft., 
where the pressure rating on the wellhead can be fairly minimal, such as 
5,000 PSI, yet the subsurface safety valve can operate effectively. The 
device can be installed at or near the surface or adjacent the wellhead to 
make access and maintenance considerably easier. The simple design 
dictates that the device is low cost and easy to install. By virtue of 
fairly minor changes in the configuration of the device, any given degree 
of amplification that would be needed for current applications and those 
likely to occur in the future can be achieved. 
SUMMARY OF THE INVENTION 
A hydraulic pressure booster is disclosed which, when used in conjunction 
with a control system for a subsurface safety valve, allows the use of 
lower pressure ratings on the wellhead equipment, yet at the same time 
provides sufficient hydraulic pressure to actuate a subsurface safety 
valve at depths that could exceed 4,000 feet. A preferred embodiment 
compensates for any fluid loss through the seals to ensure effective 
operation. The system is simple and self-regulating and can be 
alternatively installed as an integral portion of the subsurface safety 
valve or immediately adjacent the subsurface safety valve or immediately 
below the wellhead.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
FIG. 1 illustrates a wellbore 10 which has a packer 12 through which 
extends a production tubing string 14. The tubing string 14 extends to the 
surface wellhead 16. The wellhead 16 is connected to piping for further 
processing and transmission of the hydrocarbons produced. Within the 
tubing string 14 is a subsurface safety valve (SSV) 18, which is 
preferably of the flapper type and is well-known in the art. One such 
embodiment of this type of valve is illustrated in the previously 
mentioned U.S. Pat. No. 4,660,646. The SSV 18 can conceivably be mounted 
thousands of feet below the surface 20. In order to actuate the SSV 18 
into the open position, pressure must be applied from the surface through 
control line 22. Those skilled in the art can appreciate that, if the SSV 
18 is 10,000 ft below the surface, a column of fluid within the control 
line 22, which is 10,000 ft high, acts upon the sliding sleeve whose 
movement is used to hold the flapper open. In order to make the SSV 18 
failsafe closed, a return spring is customarily used which, in older 
designs, has had to be stiff enough to resist at least the hydrostatic 
column of fluid in the control line, such as 22. Accordingly, in order to 
overcome the force of the spring acting on the sliding sleeve within the 
SSV 18 from the surface, a pressure greater than the hydrostatic force at 
the SSV 18 had to be applied at the surface. The reason for this was that 
the spring resisted all the hydrostatic forces and, therefore, its force 
had to be overcome from the surface to get movement within the SSV 18 to 
get it to stay open. Since this spring was stiff, moving it required a 
large force. Thus, in prior designs the need to apply such high pressures 
from the surface required that the wellhead 16 be rated for the 
anticipated pressures in the control system and a comfortable margin of 
safety. 
As shown in FIG. 1 the present invention employs an amplifier, 
schematically illustrated as 24 in FIG. 1. The amplifier 24 is connected 
to the control line 22 and into a fluid pressure inlet 26, which is 
connected to a low-pressure hydraulic fluid source 28. A vent 30 is also 
provided. While the amplifier 24 is shown adjacent to wellhead 16, it can 
be installed downhole anywhere along the tubing string 14 or can be made 
integral with the SSV 18. However, access becomes much better if it is 
mounted adjacent the wellhead 16. 
Reference to FIG. 2 illustrates how the preferred embodiment operates. As 
shown in FIG. 2, inlet 26 is connected to valve 32. Valve 32 is connected 
to line 34, as well as to chamber 36. Piston 38 is disposed within housing 
40. Seal 42 seals around piston 38, thus defining variable volume cavity 
36. Seal 44 helps to define variable volume cavity 46. The cross-sectional 
area of cavity 46 is smaller than the cross-sectional area of cavity 36. 
Line 34 runs into cavity 46. The piston 38 has a line 48 extending from 
its lower face 50 to valve 52, which is mounted adjacent the upper face 
54. Spring 56 is disposed in chamber 58. Seals 42 and 44 help define 
chamber 58 which varies in volume as piston 38 moves. Chamber 58 has a 
valve 60, which functions as a breather, as will be explained below. 
Outlet 62 is connected to the control line 22. 
The components now having all been described, the operation of the 
particular embodiment illustrated in FIG. 2 will be explained. The purpose 
of the 3-way valve 32, which can direct pressure from the hydraulic fluid 
source 28 alternatively into chamber 36 or line 34, is to ensure that the 
piston 38 has stroked upwardly sufficiently so that when it is pushed 
downwardly toward outlet 62, a sufficient amount of fluid will be 
displaced to ensure that the SSV 18 fully opens. If there is any 
compressible fluid in chamber 46, it is displaced to chamber 36 through 
valve 52. In other words, valve 32 is programmed to align itself with 
passage 34 until pressure is built up to a predetermined amount. By 
pressurizing chamber 46, any compressible fluids which may have gotten in 
there through leakage around seal 44, are displaced through line 48 
through valve 52, which, in essence, acts as a check valve, allowing flow 
in line 48 only in the direction toward upper face 54 but not in the 
reverse direction. Thus, if there's any entrapped compressible fluid in 
chamber 46, it is pushed out through line 48 into chamber 36 through valve 
52. 
The pressure is then further built up on valve 32, which causes it to be 
shifted to a position aligning the inlet 26 to chamber 36 while at the 
same time blocking off line 34. Pressure is then applied in chamber 36 
which acts on upper face 54. Piston 38 moves downwardly, compressing 
spring 56 and displacing fluid out of chamber 46 into outlet 62. The 
amplification is the area ratios of surface 54 to surface 50. On order to 
allow the piston 38 to move downwardly, valve 60 allows fluid to be 
displaced out of chamber 58. Subsequently, in order to allow the SSV 18 to 
close, the pressure is reduced at the fluid pressure source 28, which 
allows the valve 32 to once again shift positions so that the pressure in 
chamber 36 is reduced. This can be done by venting chamber 36 through 
valve 32 into the control system at the surface 20, or more directly by 
simply allowing chambers 36 and 46 to equalize through line 34 or through 
valve 52. Once that happens, spring 56 is of sufficient strength to move 
piston 38 upwardly as valve 60 allows fluid to enter chamber 58 to 
facilitate movement of piston 38. Spring 56 only needs to resist friction 
on piston 38 since at this time piston 38 is nearly in hydraulic balance. 
Yet another way that chambers 36 and 46 can be equalized is by merely 
reducing the pressure in chamber 36 which allows flow through line 48 and 
valve 52 to equalize the chambers 36 and 46. Valve 60 acts as a breather, 
sometimes allowing fluid to escape out of housing 40 when the piston 38 is 
shifted toward outlet 62 while allowing fluid to enter chamber 58 as the 
piston 38 is returned by spring 56. Valve 60 can be connected to the 
annulus or to another location, such as the surfaces if desired. 
It should be noted that the design is equally workable with the elimination 
of valves 32 and 52 and the replacement of valve 60 with a vent hole. In 
this embodiment, line 34 is eliminated. Instead, the pressure is applied 
directly at inlet 26 into chamber 36 to displace the piston 38. The piston 
38 is enabled to move because instead of having valve 60 there is an open 
vent in its place which allows fluid to be moved into and out of chamber 
58. The amplification is obtained when the piston 38 moves under pressure 
in chamber 36. Again, the amplification ratio is the ratio of the area of 
upper face 54 to lower face 50. One disadvantage of the elimination of 
valves 32 and 52 and the substitution of an opening for valve 60 is that, 
to the extent there has been any leakage around seal 44, a mechanism would 
not exist to remove compressible fluids from below the piston 38. If too 
much compressible fluid accumulated in chamber 46, stroking of the piston 
38 may not result in sufficient actuation of SSV 18 to put it in the open 
position. This situation could occur over an extended period of time if 
any leakage occurs around seal 44. 
Those skilled in the art can now see that when the amplifier 24 is used in 
conjunction with a control system for an SSV 18, the requisite hydraulic 
pressure can be obtained at the SSV 18 to open it while at the same time 
using a significantly lower pressure source 28 and a wellhead 16 rated at 
lower pressures. For example, if the SSV 18 is at 10,000 ft below the 
surface, a 5,000 psi-rated wellhead can still be used in conjunction with 
the amplifier 24. 
The design of the amplifier 24 as shown in FIG. 2 is simple and reliable, 
allowing this objective to be easily accomplished. 
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.