Liquid spring accumulator with self-charging means

A liquid spring accumulator includes a housing having inlet and outlet ports connected to a source of liquid under pressure. The housing contains a high pressure chamber and a cylindrical chamber containing a spring-loaded piston. A rod attached to the piston is movable therewith into the high pressure chamber. A passageway through the axis of the piston and rod provides communication between the inlet port and the high pressure chamber and includes a valve seat. A check valve member in the passageway includes a shaft holding the movable member off its seat during initial flow of hydraulic liquid into cylinder, permitting flow to fill the high pressure chamber. As the liquid pressure increases, the initial movement of the piston permits the check valve to close, and still further increases in pressure cause the piston to force the rod into the high pressure chamber, substantially increasing its hydraulic pressure.

This invention relates to a liquid spring accumulator with self-charging 
means. 
A liquid spring accumulator includes a high strength housing having inlet 
and return ports communicating with a source of liquid under high pressure 
and incorporating a high pressure chamber and a cylindrical chamber 
containing a piston communicating on one side with said source of liquid 
under high pressure and on its other side with the return side of said 
source and with a resilient member which urges the piston toward said 
inlet port. A rod of substantially smaller area than said piston and 
attached thereto communicates with the high pressure chamber such that 
when said piston is exposed to said high pressure liquid, the piston 
forces the rod into the volume of liquid in the high pressure chamber to 
effect a substantial pressure increase in said high pressure chamber. 
Accumulators of various types have been commonly used in pneumatic and 
hydraulic control actuation systems to suppress pressure surges or to 
supply energy during peaks of demand when the fluid pressure requirements 
may be greater than the pressure source can deliver. Probably the greatest 
number of accumulators in use are pneumatic rather than liquid, and such 
pneumatic accumulators tend to be somewhat lighter in weight than liquid 
accumulators. With increasing operating pressures and increased 
requirements for reliability, it has begun to appear that, as compared 
with a pneumatic accumulator, a liquid spring accumulator has several 
advantages with relatively little sacrifice in weight and space 
requirements. The primary benefits are related to elimination of the gas 
charge, i.e., no system degradation because of gas leakage and no service 
required. As compared with gas or pneumatic-type accumulators, reliability 
is enhanced because: 
(1) there are no high pressure gas lines that require continual servicing 
with special maintenance equipment, 
(2) there is no depletion of the gas charge externally, which requires 
extra fluid reservoir volume to compensate, and 
(3) there is no depletion of the gas charge internally, which results in 
low spring rate unstable operation. 
Since the regular hydraulic actuating liquid is used in the spring 
accumulator, any leakage goes directly into the system return chamber at 
return pressure and so no special fluids are required. 
An additional advantage of the liquid spring accumulator as compared with a 
gas accumulator is that it is inherently much less vulnerable to battle 
damage or structural damage because of the thick walls required. Further, 
if the liquid spring accumulator is damaged severely, the energy entrapped 
in the high pressure chamber is released with much less potential damage 
to the surrounding structure. 
Because of the very high liquid pressures created in liquid spring 
accumulators, special care must be taken with seals to avoid premature 
failure. In earlier efforts to design such accumulators, applicant 
succeeded in producing an operative accumulator which developed a liquid 
spring pressure of approximately 5000 Kg/cm.sup.2, but seal failures were 
experienced after approximately 60 cycles. The seal problems have been 
successfully surmounted, and the liquid spring accumulator now appears to 
offer increased reliability with a reduction in overall space 
requirements. For specific applications these advantages more than offset 
a possible weight penalty. A self-charging liquid spring accumulator is 
defined as one which uses system hydraulic fluid compressability as the 
energy storage spring. Pressure generated for energy storage is achieved 
by an area stepdown reduction from the system piston to the liquid spring 
pressure chamber rod; thus, ultra high pressure is developed in this 
chamber from the feeding of normal system pressure. The self-charging 
feature is incorporated by means of a check valve which opens when system 
pressure and return pressure are approximately equal and provides 
communication between system pressure and the liquid spring fluid chamber 
to fill the chamber. When system pressure is applied, the first pressure 
buildup will overcome the system piston return spring; then piston 
movement will close the check valve. Further pressure buildup transmits 
load to the closed liquid spring volume through the area ratio of the 
system piston to the liquid spring rod.

Referring now to the schematic of FIG. 1, a pump 10 of any suitable design 
is shown supplying hydraulic liquid under pressure through a control valve 
12 via a line 14 to a hydraulic actuator 16. Actuator 16 consists of a 
conventional hydraulic cylinder with a piston therein movable to effect 
movement of a control surface or other member. Control valve 12 also has a 
connection to the return side of the pump through conduit 18. In the 
position of the control valve 12 shown no fluid is supplied to or from the 
actuator 16 which is therefore locked in position. Were the valve 12 to be 
moved downwardly, the high pressure would be supplied to the upper end of 
hydraulic cylinder 16 and the lower end would be connected to the return 
line. My liquid spring accumulator 20 is shown connected through lines 22 
and 24 to the return and high pressure lines from pump 10 respectively. A 
control valve 26 is shown connected to lines 22 and 24 whose function is 
to provide assurance that the liquid spring accumulator 20 can be 
depressurized when desired. Valve 26 can be operated either manually or 
through a solenoid or suitable control means. The liquid spring 
accumulator 20 consists of a housing 28 having heavy walls and including a 
cylindrical chamber 30 containing a spring 32. This spring urges a piston 
34 in an upward direction against the force of hydraulic pressure supplied 
from line 24 through an inlet port 36 to the upper side of piston 34. 
Attached to piston 34 is a rod 38 which extends downwardly through a 
channel in the housing 28, thereby communicating with a high fluid 
pressure chamber 40. A movable check valve member 42 is located in an 
elongated axial passage 44 extending through the center of piston 34 and 
rod 38. Member 42 includes an elongated shaft 46 which, as shown, makes 
contact with the upper end of housing 28, and because of this contact the 
valve member 42 is prevented from seating on its seat in passage 44. A 
light spring 50 urges check valve member 42 toward its seat. The high 
pressure chamber 40 is connected to return line 22 through a conduit 52 
containing a bleed valve 54, shown manually operated but which could be 
operated through other means. Through the use of this bleed valve it is 
possible between operating cycles for maintenance personnel to directly 
connect chamber 40 with the return side of pump 10 thereby effectively 
removing air from this chamber to assure that it is filled with hydraulic 
liquid. 
In the position shown in FIG. 1, high pressure from pump 10 is connected 
through line 24 and inlet port 36 to the upper side of piston 34. Since 
piston 34 is in its uppermost position, the shaft 46 attached to check 
valve member 42 is in contact with the end of the chamber and valve member 
42 is held open. This permits high pressure fluid to be communicated 
through passageway 44 to the high pressure chamber 40 and permitting this 
high pressure chamber to be filled with fluid. FIG. 1a shows a subsequent 
position of piston 34 which, under pressure, has begun to move in a 
downward direction. As it does so, it carries the check valve member 42 
along, and this member now seats under the influence of spring 50 because 
the rod 46 is no longer in contact with the end of the cylindrical 
chamber. 
The pressure on the upper side of piston 34 will continue to build up to 
system pressure as supplied by the pump which might, for example, be 570 
Kg/cm.sup.2, and the effect of building to this pressure level is shown in 
FIG. 1b wherein it will be seen that the piston 34 is moved downwardly a 
substantial distance in cylindrical chamber 30 compressing spring 32 and 
forcing the rod 38 deeply into the high pressure chamber 40. Since the 
increase in pressure in chamber 40 acts through the center of rod 38 to 
even more firmly seat the check valve member 42, the pressure in chamber 
40 is trapped and will be increased as its displacement is reduced from 
further intrusion of the rod 38 into chamber 40. Since the hydraulic fluid 
in this chamber is liquid and only somewhat compressible, the pressure 
will rise very considerably to a value which is controlled by the relative 
area ratios between the area of piston 34 and that of rod 38. In one 
accumulator with which applicant has been working, the maximum pressure in 
the high pressure chamber reached 5700 Kg/cm.sup.2 with 570 Kg/cm.sup.2 in 
cylinder 30. From the foregoing it is believed that the reader will 
understand the operation of my liquid spring accumulator as installed in a 
hydraulic circuit for an actuator or similar control device. The valve 26 
shown connected in line 24 leading to the accumulator 20 is not always 
necessary but provides a means for reducing pressure in the accumulator 
when desired. 
Structural details of my liquid spring accumulator will become somewhat 
more clearly defined from examination of the sectional drawing, FIG. 2. In 
this drawing an external housing is shown at numeral 60 including a 
spherical section 62 having heavy walls for resisting very high liquid 
pressures. A very high pressure spherical chamber 64 is enclosed within 
the walls of section 62. Housing 60 also encloses a cylindrical chamber 66 
which is closed at one end by means of an end cap member 68 including a 
boss 70 containing an inlet passage 72 which is adapted to be threadedly 
engaged with a conduit such as conduit 24 (see FIG. 1) connected to the 
high pressure source. Movable within the cylinder 66 is a piston 74 to 
which is attached a rod 76. A spring 78 urges piston 74 toward the end cap 
member 68. Part of the wall of section 62 which is directed toward the 
inside housing 60 includes a cylindrical opening 80 for receiving and 
supporting the end of rod 76. A portion of the cylindrical passageway 80 
is of expanded diameter as shown at numeral 82 and this opening combined 
with a member 84, which surrounds and partially supports the rod 76, 
together define an annular groove which receives a seal consisting of a 
rubber O-ring 85 covered by an annular seal 86 of polytetrafluoroethylene 
material and a plurality of metal and plastic backup rings 88. An 
additional expanded diameter collar 90 constituting an extension of 
section 62 which supports the rod 76 is threadedly engaged with a member 
92 which, as it is turned into the inside of collar 90, compresses the 
seal members such that they provide a proper seal between section 62 and 
the end of the rod 76. This must be an unusally good seal because of the 
extremely high pressures within chamber 64. 
Communicating with chamber 64 is a small passageway 94 which is normally 
closed by means of a bleed valve member 96 threadedly engaged with housing 
60 and which communicates with another small passageway 98 leading to the 
interior of cylindrical chamber 66. Bleed valve member 96 provides a means 
of permitting the contents of chamber 64 to be exhausted through 
passageways 94 and 98, the interior of cylindrical chamber 66, and out of 
a port 100 which leads to the return line 22 (see FIG. 1). 
It will be observed that piston 74 includes a stepped groove arrangement 
102 at its periphery which contains a seal including an O-ring member 104 
and a plurality of metal and plastic backup rings 106. Radially inwardly 
from the O-ring 104 is a small sealing ring 112 which senses system 
pressure tending to drive the O-ring radially outward. This ring 112 is 
placed adjacent another small ring 116, and each of these rings is 
adjacent a small annulus 114 which communicates pressure forcing ring 112 
outwardly. Ring 116 serves to prevent ring 112 from blocking ports (not 
shown) communicating the annulus 114 with the sealing ring 104. An 
essentially identical sealing arrangement is used in both the end cap 68 
and the piston 74. The end cap 68 is secured in the housing 60 by means of 
a shear ring 118 which is secured against a shoulder in the end cap 68 and 
within a groove in the housing 60 to prevent internal pressure acting on 
the inside of the end cap 68 from forcing this end cap out of the housing 
60. 
A small plate 120 is secured to the end cap 68 by means of a series of 
bolts 122 which feed through some heavy washers 124 and which are 
threadedly engaged with the end cap 68. Since end plate 120 extends over 
the ends of the housing 60, the arrangement described will prevent end cap 
68 from moving inwardly as a result of any unusual low pressures in the 
interior of cylindrical chamber 66 or from external forces. 
A small diameter passageway 126 is drilled through the central axis of 
piston 74 and rod 76, and this passageway contains a shaft 128 fastened to 
a check valve member 130. At the inside end of passageway 126 nearest the 
high pressure chamber 64 this passage is expanded to include a valve seat 
area 132 which is circular and formed at right angles to the axis of the 
shaft 128. The check valve member 130 has a flat circular face opposing 
seat 132 and includes a plurality of annular rings 134 which make contact 
against seat 132. A light spring 136 tends to urge check valve member 130 
against the seat 132. To assure proper alignment of the check valve member 
130 with the seat 132, shaft 128 is secured in annular support members 138 
and 140 which freely permit the passage of liquid therethrough. 
The liquid spring accumulator of FIG. 2, although slightly different in 
configuration from that described above, operates in almost exactly the 
same manner. Hydraulic oil supplied under initial pressure to inlet port 
72 will pass through a plurality of passages 142 to the adjacent surface 
of piston 74 and will also flow through the passageway 126 and past check 
valve member 130 into chamber 64. Check valve 130 is held open because the 
shaft 128 is in direct contact with the end cap member 68. Further 
increases in fluid pressure applied to the upper end of piston 74 will 
cause the piston to move downwardly against the force of spring 78, 
carrying the shaft 128 away from its contact with end cap 68 and 
permitting the check valve member 130 to close against seat 132. With a 
further buildup of pressure, piston 74 and rod 76 will continue to move 
downwardly, forcing rod 76 into chamber 64 where a comparatively small 
displacement of the rod will result in rapid increases in the fluid 
pressure. This pressure will increase until a stability is reached wherein 
the system pressure operating on the area of piston 74 equals the pressure 
in housing 64 acting on the smaller area of rod 76. With an area ratio 
between the piston and rod of approximately 10 to 1, the resulting liquid 
pressure in housing 64 will approach a value 10 times that of the system 
pressure. This pressure is then available in the system to supply energy 
during peaks of demand as required or to absorb pressure surges. 
When the hydraulic system is shut down, it is considered desirable to 
remove the pressure from the high pressure chamber. This can be done 
automatically by reducing system pressure to return pressure and allowing 
spring 78 to drive the piston 74 to the right and to force open check 
valve 132 or through operation of the bleed valve 96 which can be manually 
turned to provide communication between passages 94 and 98 to thereby 
permit the pressure in chamber 64 to be exhausted through the conduits 94 
and 98, chamber 66, return port 100 and return pressure line 22. It is 
considered advantageous to remove the pressure from the accumulator at the 
end of each duty cycle and refill and repressurize at the beginning of the 
next cycle, primarily because some leakage is practically inevitable with 
the pressures encountered, and retaining the accumulator in a pressurized 
condition between cycles will result in initiating subsequent cycles with 
lower pressures because of such leakage.