Fluid control system

This invention relates to a pneumatic cylinder and valve control system in which a block and two plates bolted to the block form one end of the cylinder. This block and plate combination, moreover, provides the housing for the valves and conduits that comprise the pneumatic control system for the operation of the cylinder. To produce greater force, moreover, two pistons mounted within the cylinder on the same line of action both are in fluid communication with the pneumatic control system.

This invention relates to fluid control systems and, more particularly, to 
a combination of valves for controlling the operation of a fluid power 
piston and cylinder, and the like. 
Valve systems for controlling the operation of various actuating 
mechanisms, of which the pneumatically or hydraulically activated piston 
and cylinder combination are typical, have been used for a number of 
years. Illustratively, door opening mechanisms for use in hospitals, 
convalescent facilities, nursing homes, retail merchandising stores and 
similar establishments use these valve systems to enable doors to swing 
open and then to close automatically with minimal exertion on the part of 
the person who wishes to pass through the doorway. This is particularly 
important when dealing with heavy fire doors or "primary" doors and with 
people who may be burdened with parcels, old or infirm. 
Basically, these door opening systems combine a conventional hydraulic 
retarding type door closing apparatus with a pneumatically activated 
piston and cylinder combination for pushing the door open. The initial 
impetus must be small for causing the door opening piston and cylinder to 
commence operation. The cylinder and piston must press the door to a 
full-open condition and keep the door in that condition for a sufficiently 
long period of time to permit passage through the doorway. Naturally, the 
door should not close on the person or material passing through the 
doorway, nor should the door remain open too long and allow heat to be 
lost to the atmosphere, insects to enter the building or similar 
undesirable results. 
Door opener timing, that is, the speed with which it will swing open and 
the length of time that the door will remain open, necessarily must vary 
according to the circumstances of a particular application. Consequently, 
to be commercially acceptable, a door opening device should have an 
adjustable timing feature that would provide an individual control for the 
door opening speed and the length of time during which the door will 
remain open. In this manner, one general commercial device can be used in 
any number of applications, the timing being trimmed to suit individual 
needs. 
There is, of course, a continuing requirement to improve products of this 
nature, to make them less expensive without sacrificing quality or 
reliability, and to enhance their appearance in order to make them more 
acceptable to architects and builders. It would be even more satisfying 
and useful if, in the course of this product improvement, the result is a 
device that enjoys superior reliability. 
In the past, one type of door opener piston and cylinder combination was 
mounted on a flat plate attached to the door in question. The valves 
regulating the door opener timing were secured to the plate and coupled to 
the pneumatic system by means of tubes that were individually cut and 
manually secured in place. Not only was this technique expensive, but it 
also presented a number of quality assurance problems with respect to 
joints, connections, and the like. Further in this regard, this assemblage 
of valves and cylinders, even when covered with an appealing housing, was 
quite bulky and therefore was not entirely satisfactory from an 
architectural viewpoint. 
These and other problems that have characterized the prior art are 
overcome, to a great extent, through the practice of the invention. 
Typically, the valves that control the door opener timing all are formed 
in an integral plate and block assembly that forms one part of the 
pneumatic cylinder. In this way, the valve system not only is much more 
compact but the cost of manual assembly and the quality assurance 
difficulties that were inherent in the prior art are overcome. Quality 
assurance, moreover, is significantly improved because the integral plate 
and block assembly sharply reduces the chance for leaking connections 
between valves. 
To provide the needed door opening force, the piston and cylinder to which 
the integral plate and block assembly is attached actually accommodate two 
pistons in one cylinder, both of these pistons being spaced longitudinally 
from each other and mounted in parallel with coincident lines of action. 
In this manner, with all other things being equal, one cylinder is able to 
provide just slightly less than twice as much force as a conventional 
cylinder and piston set. The effect of this improvement is to produce a 
slimmer, less bulky device that is much more attractive, and hence, is 
more acceptable to architects and builders. 
There are a number of further improvements that characterize the invention. 
Thus, the adjustment controls for the door opening speed and the time 
during which the door will remain in the fully open position protrude from 
the integral plate and block assembly in a direction that is perpendicular 
to the door surface on which the entire device is mounted. This feature of 
the invention makes access for timing adjustment and readjustment quite 
easy.

For a more complete understanding of the invention, attention is invited to 
FIG. 1. An initial impulse or brief pulse of compressed air or other 
suitable fluid is admitted to a conduit 10 from a wall button or the like 
(not shown in the drawing) that is activated through an application of a 
small opening pressure or signal to a door (also not shown in the 
drawing). The conduit 10 communicates with a parallel connected check 
valve 11 and choke 12. 
The check valve 11 and the choke 12 are both coupled through a conduit 13 
to a pneumatic pressure accumulator 14. A conduit 15 connects the pressure 
accumulator 14 to a pilot valve 16. As illustrated in the drawing, the 
pilot valve 16 regulates the operation of a control valve 17. In turn, the 
control valve 17 is connected in fluid communication with another parallel 
connected choke 20 and check valve 21 through a conduit 22. 
Particular note should be made of the flow orientations of the check valve 
11 and the check valve 21. Thus, air flows through the check valve 11 only 
toward the pilot valve 16 of control valve 17. System air, moreover, flows 
through the check valve 21 only toward the control valve 17. 
The choke 20 and the check valve 21 are both coupled to the interior of a 
pneumatic cylinder 23 through a conduit 24. 
A compressed air supply is connected to the system by means of a conduit 
25. Preferably, the air supply should not be less than 20 pounds per 
square inch (psi). The compressed air then is admitted to the system 
through a pressure regulating valve 26 and through a conduit 27 to the 
control valve 17. 
For a more detailed description of the logic valves that form this system, 
attention now is invited to FIG. 2 which shows, in accordance with a 
salient feature of the invention, an integral block 30 that forms one of 
the transverse ends of the pneumatic cylinder 23. A pair of parallel and 
overlaying plates 31, 32 are securely fastened to the block 30 by means of 
screws 33, or the like. The block 30 and the plates 31, 32 have recesses 
and cavities formed in their respective structures which, when properly 
joined together, form the housings for the valves, chokes, pressure 
accumulator and conduits described in connection with FIG. 1. 
Attention now is invited to FIG. 7, which shows the conduit 10 that admits 
an initial pulse of air under pressure to activate the system from a door 
valve, or the like (not shown in the drawing). As previously mentioned, 
the conduit 10 establishes fluid communication for this pulse with a 
parallel combination of the choke 12 and the check valve 11. 
In FIG. 7, it can be seen that a housing 36 for the choke 12 is formed by 
means of a bore in the plate 31 that penetrates the longitudinal exposed 
side of that plate. A threaded portion 37 of the bore mates with a 
corresponding threaded portion on a choke valve stem 40. The choke valve 
stem 40 has a shaft 41 that is sealably contained in and protrudes out of 
the longitudinal side of the plate 31 and terminates in a slotted head 42 
that can accommodate a screw driver or the like for valve adjustment as 
described subsequently in more complete detail. 
Continuing with the description of the choke valve stem 40, it should be 
noted that the end of the stem which is lodged within the choke housing 36 
terminates in the frustrum of a cone 43. The threading 37 permits the gap 
between the choke housing 36 and the conical termination 43 of the valve 
stem 40 to be selectively varied in area, thereby impeding or promoting 
the flow of the pulse from the conduit 13 to the door valve. 
The check valve 11 communicates with the conduit 10 by way of an enlarged 
chamber that surrounds a portion of the choke valve stem 40 that is 
adjacent to the conical termination 43 of the stem. A longitudinal bore in 
the plate 31 forms a check valve housing 44. A ball 45 that is seated in 
one end of a coil spring 46 is pressed against the valve seat in the check 
valve housing 44. The spring 46, in turn, bears against the surface of the 
integral block 30 that is adjacent to the plate 31. As noted above, the 
check valve 11 permits fluid communication for the initiating pulse of air 
to flow into the conduit 13. 
The conduit 13 is coupled to a pressure accumulator 14. 
The pressure accumulator communicates through the conduit 15, which is 
formed in the integral block 30, with the pilot valve 16 (FIG. 5). The 
pilot valve 16 has a housing 52 that is formed by means of bores 53, 54 
that are formed in the integral block 30 and the plate 31. A thin 
diaphragm 55 is clasped between the block 30 and the plate 31 at their 
common interface in order to establish a partition between the bores 53 
and 54 that form the housing for the pilot valve 16. Note that the 
diaphragm 55 has a peripheral corrugation 56 that imparts a certain degree 
of resiliency to the diaphragm. 
A pilot valve stem 57 is lodged within the bore 54. The valve stem 57 has a 
flat head 58 that abuts the diaphragm 55 and a shank 60 that is supported 
for longitudinal sliding motion in a reduced diameter portion of the bore 
54. In the end of the shank 60, a shallow longitudinal cavity 61 is used 
to form an exhaust valve seat. A spiral spring 62 that is concentric with 
the longitudinal axis of the shank 60 presses the flat head 58 of the stem 
against the diaphragm 55. 
The valve seat end of the shank 60 abuts a control valve stem 63 when 
conduit 15 and diaphragm 55 are pressurized. Further in this regard, the 
control valve stem 63 is sealably retained in a bore 64 formed in the 
plate 32 that provides the housing for the control valve 17. Not only does 
this control valve stem 63 have a flat head 65 that abuts the end of the 
shank 60 and supply seat 70, but the stem 63 also has a longitudinally 
oriented bore 66 that establishes fluid communication between the 
atmosphere external to the plate 31 and the conduit 22 through the annular 
cavity formed by the supply seat 70. A coil spring 67 is received on the 
shank of the control valve stem in order to press the flat head 65 of the 
control valve stem 63 against supply seat 70 and the end of the pilot 
valve stem 57. 
As shown in the drawing the end of the shank 60 of the pilot valve stem is 
spaced from the side of the central aperture in an annular supply seat 70 
that sealably abuts the plate 32 at the common interface between the 
plates 31 and 32. The central aperture in the seat 70, however, has a 
diameter that is somewhat smaller than the diameter of the flat head 65. 
In this manner, compressed air, or other suitable fluid, which is admitted 
to the control valve bore 64 by way of the conduit 27, is selectively 
permitted to flow past the flat head 65 of the control valve stem 63 and 
into the conduit 22, depending on the longitudinal position of the flat 
head with respect to the plug 70. 
As shown in FIG. 4, the conduit 22 establishes fluid communication with the 
choke 20 and the check valve 21. The choke 20 is similar in construction 
to the choke 12 described in FIG. 7. Thus, a choke valve stem 71 is 
engaged in a mating thread that is formed in the choke housing 72. As 
illustrated in FIG. 4, the choke housing is provided by means of a bore in 
the plate 31. The bore enters a lateral, or longitudinal side of the plate 
31 to allow a slotted head 73 to protrude in parallel with and in the same 
plane as the slotted head 42, as best shown in FIG. 3. Note particularly 
in this respect that the knobs 42, 73 protrude from the valve system on a 
side that is opposite to the plane of the door to which the entire device 
is to be mounted. These heads further are mounted in a plane that is 
perpendicular to the door surface that supports the device under 
consideration. 
As shown, the portion of the choke valve stem 71 that is lodged within the 
plate 31 terminates in the frustrum of a cone 74. This conical termination 
of the control valve stem 71 permits the gap between the choke housing and 
the conical surface 74 to be selectively varied in order to regulate the 
air flow between the conduit 22 and the conduit 24. 
The check valve 21, which is coupled in parallel with the choke 20 across 
the conduits 22 and 24, has a housing 75 that is provided by a small bore 
in the plate 31. A ball 76 that is seated on a coil spring 77 blocks air 
from flowing through the check valve 21 from the conduit 22 to the conduit 
24. 
FIG. 4 also shows the continuation of the conduit 24 that is provided by 
bore 80 in the integral block 30. The conduit 24 penetrates the transverse 
surface of the integral block 30 in order to establish a fluid passageway 
to the interior of the pneumatic cylinder 23. 
In FIG. 2, the pneumatic cylinder 23 is shown with a transversely mounted 
piston 80 that is secured to a longitudinally disposed piston rod 81. 
According to a salient feature of the invention, a longitudinal bore 82 is 
formed in the piston rod 81. Although it is out of the plane of the 
drawing in FIG. 2, the conduit 24 as it emerges from the transverse 
surface the integral block 30 is in registry not only with the abutting 
transverse surface of the piston 80 but also is in fluid communication 
with the longitudinal bore 82 in the piston rod 81. 
The piston 80 and the piston rod 81 affixed to the piston 80 are capable of 
longitudinal reciprocating movement within a chamber 83 in the pneumatic 
cylinder 23. This longitudinal movement produces a line of action or force 
that coincides with a longitudinal axis 84 of the cylinder 23. 
The longitudinal bore 82 terminates at the extreme end of the piston rod 81 
in fluid communication with a small transverse bore 85. 
A retaining ring 86 seated in a groove formed in the internal surface of 
the pneumatic cylinder 23 separates the chamber 83 from a chamber 87. 
Within the chamber 87 a transversely disposed partition 90 is braced 
against the retaining ring 86. A centrally disposed aperture in the 
partition 90 provides a journal for the end of the piston rod 81, which 
rod protrudes slightly beyond the partition 90 and into the chamber 87. 
The transverse end of the piston rod 81 abuts another piston rod 91 in 
order to provide a small longitudinal clearance between the partition 90 
and a piston 92. This clearance between the piston 92 and the partition 90 
is in fluid communication with the conduit 24 by way of the bores 82 and 
85. In these circumstances, and in accordance with an aspect of the 
invention, pneumatic fluid discharging from the conduit 24 in the integral 
block 30 acts upon both of the pistons 80 and 92, driving these pistons 
and their associated piston rods 81 and 91 to the observer's right as 
viewed in FIG. 2 of the drawing. Air is exhausted from the chamber 87 
through the bores 85 and 82 and the conduit 24. Air in the chamber 83, 
however, is discharged directly through the conduit 24 (not shown in FIG. 
2). 
To complete the structural description of the valve system, attention is 
invited to FIG. 6 which shows the regulator valve 26 and an air or 
pneumatic fluid filter 93. Air, or other suitable working fluid, enters 
the conduit 25 under pressure from a supply source (not shown). The 
conduit 25 is formed through a bore 94 in the plate 32, a bore 95 in the 
plate 31 and a bore 96 in the integral block 30. The bore 95, moreover, 
accommodates the filter 93. As shown, the filter 93 has a screen or 
cylindrical foraminous member 97 through which all air entering the 
conduit 25 must flow before it enters the regulator valve 26. 
The regulator valve 26 is accommodated in a housing that is formed by three 
axially aligned bores 100, 101 and 102 in the plates 32, 31 and the 
integral block 30, respectively. An adjusting screw 98 is threaded into 
the bore 100. A knob 103 on the screw 98 protrudes from the bore 100 
beyond the transverse end of the plate 32. The knob 103 permits adjustment 
to the compression that is applied to a coil spring 104 which is lodged 
within the bore 100. As illustrated, the spring 104 is positioned between 
the end of the adjusting screw 98 and a diaphragm follower spring seat 
105. 
A transversely disposed diaphragm 99 is clamped between the plates 31 and 
32 at their common interface. The diaphragm 99 extends across the bore 100 
and effectively separates the bore 100 from the bore 116. An annular 
corrugation also is formed in the diaphragm 99. This corrugation is 
interposed in the gap between the diaphragm follower 105 and the 
immediately adjacent surface of the bore 100. 
A further valve stem 106 is lodged within the bore 116. A flat head 107 
formed on one end of the valve stem 106 bears against the diaphragm 99 
under the force applied by a conical spring 110 that is received on the 
valve stem 106 between the flat head 107 and a shoulder that is formed in 
the bore 116. The bore 101 provides a bearing to guide the valve stem 106. 
A small cavity 111 formed in the terminal portion of the valve stem 106 
forms a seat at the interface between the valve stem 106 and the valve 
element 113. This terminal portion of the valve stem 106, moreover, passes 
through the central aperture of valve seat 112 that is sealably lodged in 
the bore 101 at the plane of common intersection between the plate 31 and 
the integral block 30. 
As seen in FIG. 6, the aperture in the valve seat 112 is spaced from the 
adjacent portion of the valve stem 106 to provide an air passageway 
through which communication is established through valve 17 (FIG. 5) with 
the interior of the pneumatic cylinder 23 (not shown in FIG. 6) by way of 
the conduits 27, 22, and 24. Within the bore 102 the further valve element 
113 is biased against the end of the valve stem 106 that accommodates the 
cavity 111 by means of a coil spring 114. The flat face of the valve 
element 113 that abuts the valve stem 106 has a slightly greater diameter 
than the diameter of the corresponding aperture in the valve seat 112. In 
this way, depending on the relative longitudinal position of the flat face 
on the valve element 113 vis-a-vis the seat 112, air pressure is regulated 
proportional to load provided by spring 104. 
Further with respect to the valve element 113, a longitudinal bore 115 
extends the entire length of the element 113 and is in alignment with the 
cavity 111 on the end of the valve stem 106. 
In operation, as best shown in FIG. 1, a brief pulse of compressed air is 
admitted to the conduit 10 through the activation of a valve (not shown) 
mounted on or adjacent to the jamb of the door (also not shown) to be 
opened automatically. Thus, a slight initial manual pressure on the door 
valve is sufficient to produce a pulse that will commence automatic 
operation. This initial compressed air pulse essentially bypasses the 
choke 12 and flows through the check valve 11 to the conduit 13 and the 
pressure accumulator 14. 
Proceeding from the pressure accumulator 14 by way of the conduit 15, the 
pulse activates the pilot valve 16. In activating the pilot valve 16, and 
as most clearly shown in FIG. 5, the pilot valve stem 57 shifts to the 
observer's left, as viewed in the drawing. This movement of the valve stem 
57, in turn, presses the control valve stem 63 also to the observer's 
left. 
By shifting the control valve stem 63 to the left, fluid communication is 
established through a path from the compressed air supply (not shown in 
the drawing) which, preferably provides the desired quantity of compressed 
air at not less than 20 psi, through the conduit 25 (FIG. 1), the filter 
93, the pressure regulator valve 26, the conduit 27, past the flat head 65 
(FIG. 5) of the control valve stem 63, through the conduit 22 (FIG. 1) and 
the choke 20 to both chambers 83 and 87 (FIG. 2) of the pneumatic cylinder 
23 by way of the conduit 24 (FIG. 4). 
In accordance with another feature of the invention, the regulator valve 
26, as shown in FIG. 1 is subject only to air flow in one direction, i.e. 
from the filter 93 toward the pneumatic cylinder 23. This relative 
position of the pressure regulator valve 26 in the system increases valve 
life and decreases wear on this delicate component. Consequently, the 
durability and cycle life of the entire system is improved significantly 
because of this important component relocation. 
Within the pressure regulator valve 26, as shown more clearly in FIG. 6, 
the application of a proper degree of compressive force on the coil spring 
104 by turning the knob 103 to insert or withdraw the control valve stem 
98 into or out of the bore 100 causes the valve stem 106 to reduce the 
supply pressure of the compressed air from the filter 93 to some 
predetermined value. Preferably, it has been found that a pressure range 
of 3 to 100 psi is adequate for most purposes. The pressure output from 
the pressure control valve 26 is generally determined by the force that is 
required of the pneumatic cylinder 23 (not shown in FIG. 6) to swing open 
the door in question. This force must be slightly greater than closing 
force applied not only by the weight of the door, but also by the door 
closer apparatus (also not shown in the drawing). 
Turning now to FIG. 4, it can be seen that the compressed air from the 
pressure regulator valve 26 (FIG. 6) flows through the conduit 22, past 
the choke setting that the conical frustrum 74 establishes with the 
adjacent portion of the choke housing 72 and into the conduit 24. 
Manipulation of the slotted head 73 adjusts the gap between the conical 
frustrum 74 and the choke housing 72 to provide a desired door opening 
speed, in accordance with the needs of a particular door opener 
application. 
Looking now at FIG. 2, compressed air from the conduit 24 (not shown in 
FIG. 2) is applied directly to the piston 80 and indirectly by way of the 
bores 82 and 85 to the piston 92. This influx of compressed air drives the 
pistons 80, 92 to the observer's right as viewed in the drawing. Both of 
the piston rods 81 and 91 move to the right, pressing the door in question 
open all of the way without any further expenditure of manual effort. 
After the door has been fully opened, a conventional door closing mechanism 
(not shown in the drawing) applies the usual force to press the door shut. 
In this instance, however, the door closing device must overcome the 
countervailing force applied by the pneumatic cylinder 23 (FIG. 2). 
Accordingly, the door closing force tends to expel the air from the 
chambers' 83, 87 by pressing the pistons 80, 92, respectively to the 
observer's left as viewed in the drawing. 
The compressed air thus is forced out of the chamber 87 by way of the bores 
85, 82 and the conduit 24 as, at the same time, compressed air is forced 
out of the chamber 83 directly through the conduit 24. As shown in FIG. 1, 
this discharging air effectively bypasses the choke 20 by flowing through 
the check valve 21 to the conduit 22. In this situation, the control valve 
17 has been reset to permit the discharging air to flow directly into the 
atmosphere by way of the conduit 22 (FIGS. 1 and 4) and the communicating 
bore 66 (FIG. 5) in the control valve stem 63. Thus, the door closes. 
Naturally, the length of time during which the door will remain open is 
regulated through the setting on the choke 12 (FIG. 1). The greater the 
interval of time that a suitable pressure is applied to the pilot valve 16 
through the pressure accumulator 14, the longer the control valve 17 will 
remain in a door open status and block the air in the pneumatic cylinder 
23 from discharging to the atmosphere. This timed leakage of the air from 
the pressure accumulator is controlled by the setting on the choke 12. 
Turning to FIG. 7, it can be seen that this predetermined leakage rate is 
set by establishing a suitable clearance between the conical frustrum 43 
on the end of the choke valve stem 40 and the adjacent portion of the 
choke housing 36. 
The slender parallel arrangement of the pistons and the compact, generally 
trouble free integral assemblage of valves as a part of the pneumatic 
cylinder structure produces a small unit that can be covered with a small, 
eye-appealing and architecturally acceptable fairing (not shown in the 
drawing). In this manner, the invention overcomes a number of difficulties 
that have beset prior art devices.