Gear pump having conditional dry valve closure structure

A dry valve for a gear pump includes a piston having a valve head and a piston head mounted on the opposite ends of a piston rod. The piston is selectively movable between an opened position, wherein hydraulic fluid is permitted to flow from a reservoir to a pumping chamber of the gear pump, and a closed position, wherein such flow is obstructed. A source of pressurized air exerts a biasing force against the piston head to selectively move the piston. An outlet port of the gear pump is connected through a feedback passageway to the dry valve. The feedback passageway communicates with the side of a chamber in which the piston rod of the dry valve reciprocates between the opened and closed positions. When the dry valve is in the opened position, the pressurized fluid from the outlet port of the gear pump exerts a side-loading pressure against the piston rod, causing a frictional force to be generated between the piston rod and the piston rod chamber which resists relative movement.

BACKGROUND OF THE INVENTION 
The present invention relates in general to pumping mechanisms for 
supplying pressurized fluid to hydraulically actuated systems. In 
particular, the present invention relates to a gear pump having an inlet 
port shut-off valve, referred to as a dry valve, which is prevented from 
closing when the fluid pressure delivered from the outlet port of the gear 
pump to such a hydraulic system is greater than a predetermined maximum 
safe magnitude. The present invention also relates to an improved means 
for providing a flow of lubricating and cooling fluid through the gear 
pump when the dry valve is closed and, thus, the gear pump is operated in 
the dry mode. 
Gear pumps are well known in the art and typically include a pair of gears 
mounted upon respective shafts for rotation within a pump housing. The 
shafts are arranged such that the gears mesh within a pumping chamber 
disposed between an inlet port and an outlet port. One of the shafts is 
rotated by an external source of power so as to cause the two gears to 
rotate. In this manner, hydraulic fluid is drawn from a reservoir through 
the inlet port and is discharged at a relatively high pressure from the 
outlet port to the hydraulic system. 
One common use for gear pumps of this type is on a refuse packing vehicle. 
Such a vehicle is typically driven by an internal combustion engine and 
includes one or more movable packing mechanisms which are hydraulically 
actuated. A gear pump can be connected to and driven by the internal 
combustion engine to generate a flow of pressurized fluid to operate the 
packing mechanisms. Because of its size and reliability, the gear pump is 
well suited to perform this function. Typically, however, such packing 
mechanisms are used only intermittently, requiring no flow of pressurized 
fluid for long periods of time. The internal combustion engine, on the 
other hand, is usually continuously operated. Thus, for this and other 
uses, some means must be provided for selectively interrupting the flow of 
pressurized fluid from the gear pump to the hydraulic system. 
Several structures are known in the art for accomplishing this selective 
interruption. A first known structure includes a valve provided between 
the outlet port of a continuously driven gear pump and the packing 
mechanisms actuated thereby. The valve is selectively actuated to direct 
the flow of pressurized fluid from the outlet port of the gear pump either 
to the packing mechanisms or back to the reservoir. Thus, when the packing 
mechanisms are not to be utilized, the flow of pressurized fluid is 
diverted from the packing mechanisms and is returned to the reservoir. 
Unfortunately, this structure results in undesirable power losses, 
particularly at high engine speeds and, therefore, at high flow rates. 
A second known structure includes a power take-off unit or a clutch 
provided as a connection between the internal combustion engine and the 
gear pump. The power take-off unit or clutch selectively makes and breaks 
the driving connection between the internal combustion engine and the gear 
pump. When the packing mechanisms are not to be utilized, the power 
take-off or clutch is disengaged so as to disable the gear pump. As a 
result, the flow of pressurized fluid to the packing mechanisms is 
interrupted. These structures, however, increase the cost and complexity 
of the overall refuse packing system, as well as introduce additional 
components which are subject to failure. 
A third and more preferable structure for interrupting the flow of 
pressurized fluid from the gear pump to the packing mechanisms includes a 
dry valve. The dry valve is well known in the art and can simply be 
described as a shut-off valve disposed in the inlet port of the gear pump. 
When closed, the dry valve obstructs the flow of hydraulic fluid from the 
inlet port to the pumping chamber of the gear pump. Consequently, the flow 
of pressurized fluid to the packing mechanisms is interrupted, even though 
the gear pump is continued to be operated. When the gear pump is operated 
while the dry valve is closed, it is said to be operating in the dry mode. 
Typically, means are provided in the dry valve for permitting a relatively 
small amount of hydraulic fluid to flow into the pumping chamber even when 
the dry valve is closed. Such relatively small amount of fluid flow is 
necessary for lubricating and cooling the components of the gear pump 
while it is operated in the dry mode. 
Several problems associated with the use of a dry valve in a gear pump are 
related to such flow of lubricating and cooling fluid. In such prior art 
gear pumps, a bleed valve must be provided between the gear pump and the 
packing mechanisms to prevent the flow of lubricating and cooling fluid 
from inadvertently operating the packing mechanisms. The bleed valve 
causes the relatively small amount of lubricating and cooling fluid to be 
returned back to the reservoir after being circulated through the gear 
pump. The use of such a bleed valve results in the undesirable loss of a 
portion of the pressurized fluid when the dry valve is opened. Thus, it 
would be desirable to provide a gear pump which avoids this problem. 
A third problem associated with the use of a dry valve in a gear pump can 
occur if the dry valve is attempted to be closed while the pump is 
generating a flow of hydraulic fluid at a relatively high pressure. 
Closure of the dry valve during such relatively high pressure output can 
cause a highly unbalanced pressure condition to occur within the gear 
pump. Specifically, the pressure within the pumping chamber drops rapidly 
to a relatively low level when the dry valve is closed. However, the 
pressure at the outlet port remains relatively high for a short period of 
time following such closure. In most gear pumps, such outlet port pressure 
is fed back within the gear pump to urge a pair of opposed pressure plates 
into sealing engagement with the sides of the gears. During this period of 
high pressure unbalance, the pressure plates exert excessively large 
forces against the sides of the gears, resulting in premature wear and 
failure of the gear pump. Thus, it would be desirable to provide a means 
for preventing the closure of the dry valve while the gear pump is 
generating a flow of hydraulic fluid at a pressure which is greater than a 
predetermined maximum safe magnitude. 
SUMMARY OF THE INVENTION 
The present invention relates to an improved design for a gear pump having 
a dry valve. The dry valve includes a piston having a valve head and a 
piston head mounted on the opposite ends of a piston rod. The piston is 
selectively movable between an opened position, wherein the valve head is 
positioned to permit hydraulic fluid to flow from a reservoir to a pumping 
chamber of the gear pump, and a closed position, wherein the valve head is 
positioned to obstruct such flow. The piston is actuated for such movement 
by a source of pressurized air acting on the piston head. The source of 
pressurized air exerts a biasing force against the piston head to 
selectively move the piston in either direction. The outlet port of the 
gear pump is connected to a hydraulic system adapted to be driven by the 
flow of pressurized fluid. The outlet port is also connected through a 
feedback passageway formed in the gear pump back to the dry valve. The 
feedback passageway communicates with the side of a chamber in which the 
piston rod of the dry valve reciprocates between the opened and closed 
positions. When the dry valve is in the opened position, the pressurized 
fluid from the outlet port of the gear pump exerts a side-loading pressure 
against the piston rod of the dry valve. This side-loading pressure causes 
a frictional force to be generated between the piston rod and the piston 
rod chamber which resists relative movement. If the frictional force is 
greater than the biasing force, the source of pressurized air is unable to 
move the piston to the closed position. If the frictional force is less 
than the biasing force, the source of pressurized air is able to move the 
piston rod to the closed position. Thus, the dry valve may be moved from 
the opened position to the closed position only if the pressure of the 
fluid at the outlet port of the gear pump is less than a predetermined 
maximum safe magnitude. After the dry valve is moved to the closed 
position, a reduced diameter portion of the piston rod is disposed 
adjacent the feedback passageway. As a result, fluid is permitted to flow 
through the feedback passageway and the piston rod chamber to an external 
drain connected to the reservoir. This structure returns the lubricating 
and cooling fluid to the reservoir after circulating once through the gear 
pump. 
It is an object of the present invention to provide an improved gear pump 
having a dry valve for operating an intermittently actuated hydraulic 
system. 
It is another object of the present invention to provide such a gear pump 
which prevents the dry valve from being moved from an opened position to a 
closed position while the gear pump is generating a flow of fluid at a 
pressure which is greater than a predetermined maximum safe magnitude. 
It is a further object of the present invention to provide such a gear pump 
which permits a relatively small flow of lubricating and cooling fluid 
while the dry valve is closed and returns such fluid to the reservoir 
after circulating once through the gear pump, thus preventing damage to 
the pump when run for long periods in the dry mode. 
Other objects and advantages of the present invention will become apparent 
to those skilled in the art from the following detailed description of the 
preferred embodiment, when read in light of the accompanying drawings.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
Referring now to the drawings, there is illustrated a gear pump, indicated 
generally at 10, in accordance with the present invention. As best shown 
in FIG. 2, the gear pump 10 includes a pump housing 11 having an end plate 
12 secured thereto by a plurality of bolts 13. A plurality of dowels 15 
may be provided to support and align the end plate 12 relative to the pump 
housing 11. Within the gear pump 10, a pair of shafts 16 and 17 are 
journalled for rotation. The shafts 16 and 17 are disposed in parallel 
fashion adjacent one another. The ends of each of the shafts 16 and 17 are 
supported for rotation within the gear pump 10 by respective sleeve 
bearings 19. The first shaft 16 can be formed having a toothed end portion 
18. The toothed end portion 18 can be utilized in conjunction with a 
conventional sensor (not shown) to generate an electrical signal which is 
indicative of the rotational speed of the shaft 16. 
A first gear, illustrated schematically at 20, is mounted on the first 
shaft 16 for rotation therewith. Similarly, a second gear, illustrated 
schematically at 21, is mounted on the second shaft 17 for rotation 
therewith. The first and second gears 20 and 21 mesh together within a 
pumping chamber, indicated generally at 22, formed in the gear pump 10. 
One end of the second shaft 17 extends through the end plate 12 outwardly 
of the gear pump 10. A key 23 is provided on that end of the second shaft 
17. The key 23 permits the second shaft 17 to be connected to a source of 
power, such as a vehicle engine (not shown), for rotation. A pair of 
pressure plates 25 are disposed on opposite sides of the first and second 
gears 20 and 21. The pressure plates 25 are adapted to form a seal between 
the first and second gears 20 and 21 and the other components of the gear 
pump 10. An 0-ring 26 and a back-up ring 27 are provided adjacent each of 
the pressure plates 25, also for sealing purposes. 
As best shown in FIGS. 4 and 5, the gear pump 10 is provided with an inlet 
port 30 and an outlet port 31. The inlet port 30 communicates with a 
reservoir (see FIG. 6) containing a supply of hydraulic fluid at a 
relatively low pressure. The outlet port 31 communicates with a hydraulic 
system (see FIG. 6) adapted to be actuated by the flow of pressurized 
fluid from the gear pump 10. When operated, the gear pump 10 draws 
hydraulic fluid from the reservoir through the inlet port 30 and 
discharges such fluid at a relatively high pressure from the outlet port 
31 to the hydraulic system. As is well known in the art, the pumping 
operation of the gear pump 10 is achieved by rotating the second shaft 17 
and the second gear 21 in one direction (clockwise when viewing FIG. 3), 
thereby causing rotation of the first shaft 16 and the first gear 20 in 
the opposite direction (counterclockwise when viewing FIG. 3). The 
structure of the gear pump 10 described thus far is conventional in the 
art. 
A dry valve, indicated generally at 32, is provided between the inlet port 
30 and the pumping chamber 22. The dry valve 32 is mounted in a valve 
block 33 secured to the pump housing 11. The structure and operation of 
the dry valve 32 will be explained in detail below. Briefly, however, the 
dry valve 32 provides a means for selectively obstructing the flow of 
hydraulic fluid from the inlet port 30 to the pumping chamber 22. When the 
dry valve 32 is opened, such flow is not obstructed, and the gear pump 10 
is enabled to generate a flow of pressurized fluid through the outlet port 
to the hydraulic system as described above. This is referred to as the 
active mode of operation of the gear pump 10. When the dry valve 32 is 
closed, however, the gear pump 10 is prevented from providing the flow of 
pressurized fluid, even though the first and second shafts 16 and 17 and 
the first and second gears 20 and 21 mounted respectively thereon continue 
to be rotated. This is referred to as the dry mode of operation of the 
gear pump 10. 
A priority flow control valve, indicated generally at 35, is provided 
between the pumping chamber 22 and the outlet port 31. The priority flow 
control valve 35 is conventional in the art and forms no part of the 
present invention. The priority flow control valve 35 regulates the amount 
of pressurized fluid flowing through the outlet port 31 to the hydraulic 
system by diverting excess flow greater than the regulated flow into an 
excess flow passageway 36 formed in the gear pump 10. Thus, the priority 
flow control valve limits the amount of pressurized fluid flowing through 
the outlet port 31 to a predetermined regulated level. The excess flow 
passageway 36 communicates with the inlet port 30. Consequently, the 
excess flow of pressurized fluid is returned directly from the pumping 
chamber 22 to the inlet port 30. A feedback passageway 37 is also formed 
in the gear pump 10. The feedback passageway 37 extends between the outlet 
port 31 and the valve block 33. Pressurized fluid which is delivered from 
the outlet port 31 to the hydraulic system is, therefore, also provided 
through the feedback passageway 37 to the valve block 33. The function of 
the feedback passageway 37 will be described in detail below. 
Referring to FIGS. 4 and 5, the structures of the dry valve 32 and the 
valve block 33 are illustrated in detail. The dry valve 32 includes a 
piston, indicated generally at 38, having a valve head 40 and a piston 
head 41 connected to the opposite ends of a piston rod 42. The piston head 
41 is enclosed within a piston head chamber 43 formed in the valve block 
33, while the valve head 40 extends outwardly from the valve block 33 into 
the inlet port 30. The piston rod 42 is disposed within a piston rod 
chamber 44 formed in the valve block 33 and is axially moveable 
therethrough. The piston 38 is adapted to reciprocate between an opened 
position (illustrated in FIG. 4) and a closed position (illustrated in 
FIG. 5). In the opened position, the valve head 40 is positioned within 
the inlet port 30 so as not to obstruct the flow of hydraulic fluid 
therethrough to the pumping chamber 22. In the closed position, however, 
the valve head 40 is moved into engagement with a seat 45 formed at the 
junction between the inlet port 30 and the pumping chamber 22. When so 
seated, the valve head 40 obstructs the flow of hydraulic fluid into the 
pumping chamber 22. A small aperture 46 is formed through the valve head 
40 which permits a relatively small amount of hydraulic fluid to flow from 
the inlet port 30 into the pumping chamber 22, even when the piston 38 is 
in the closed position. This relatively small flow of hydraulic fluid 
through the aperture 46 is utilized for lubricating and cooling the 
components of the gear pum 10 when the piston 38 is in the closed 
position, as will be described in detail below. 
As mentioned above, the piston head 41 is disposed within the piston head 
chamber 43 formed in the valve block 33. First and second passageways 47 
and 48 are formed in the valve block 33 which communicate with the piston 
head chamber 43 on opposite sides of the piston head 41. The first and 
second passageways 47 and 48 communicate with a control means (see FIG. 6) 
for selectively supplying pressurized air through one of the passageways 
47 and 48 and for simultaneously venting the other of the passageways 47 
and 48 to the atmosphere. When pressurized air is supplied through the 
second passageway 48 while the first passageway 47 is vented, the piston 
38 is biased to move toward the opened position illustrated in FIG. 4. 
When pressurized air is supplied to the first passageway 47 and the second 
passageway 48 is vented, the piston 38 is biased to move toward the closed 
position illustrated in FIG. 5. One example of a satisfactory control 
means is discussed below in connection with FIG. 6. However, it will be 
appreciated that any similar means for generating a biasing force to move 
the piston 38 between its opened and closed positions is contemplated to 
be within the scope of the present invention. 
The piston rod 42 has a reduced diameter portion 50 formed therein between 
the valve head 40 and the piston head 41. As shown in FIGS. 4 and 5, the 
reduced diameter portion 50 is located on the piston rod 42 such that it 
is always disposed within the piston rod chamber 44, regardless of whether 
the piston 38 is in the opened or closed positions. When the piston 38 is 
in the closed position illustrated in FIG. 5, the reduced diameter portion 
50 is disposed adjacent both a third passageway 51 and a fourth passageway 
52 formed in the valve block 33. The third passageway 51 provides 
communication between the feedback passageway 37 and the piston rod 
chamber 44. The fourth passageway 52 provides communication between the 
piston rod chamber 44 and an annular groove 53 formed in an end face 55 of 
the valve block 33. The end face 55 sealingly abuts the outer surface of 
the pump housing 11 when the valve block 33 is secured thereto. Thus, the 
groove 53 defines an annular chamber between the valve block 33 and the 
pump housing 11. The groove chamber 53 communicates with a drain 
passageway, indicated by dotted lines at 56, formed in the pump housing 
11. The drain passageway 56 communicates with a drain port 57, also formed 
in the pump housing 11. The drain port 57 communicates directly with the 
reservoir (see FIG. 6) for returning the hydraulic fluid thereto. 
Referring now to FIG. 6, a schematic diagram of a hydraulic circuit 
including the gear pump 10 of the present invention is illustrated. As 
shown therein, a reservoir 60 is provided to supply hydraulic fluid to the 
inlet port 30 of the gear pump 10. The outlet port 31 of the gear pump 10 
communicates with a hydraulic system 61. The reservoir 60 also receives 
hydraulic fluid from the drain port 57 of the gear pump 10 and from the 
hydraulic system 61. A control means, indicated generally at 62, is 
provided to selectively generate a biasing force to move the piston 38 of 
the dry valve 32 between its opened and closed positions, as described 
above. In the illustrated embodiment, the control means 62 includes a 
two-position valve 63 which is actuated by means of a solenoid driver 65. 
The valve 63 is connected between the first and second passageways 47 and 
48, respectively, formed in the valve block 33 and a source of pressurized 
air 66. 
When the valve 63 is in the first position illustrated in FIG. 6, the 
source of pressurized air 66 communicates through the first passageway 47 
with the upper side (when viewing FIGS. 4 and 5) of the piston head 
chamber 43 formed in the valve block 33. Consequently, a pressure is 
exerted against the upper side of the piston head 41. At the same time, 
the lower side of the piston head chamber 43 is vented through the second 
passageway 48 and the valve 63 to the atmosphere. The resulting pressure 
differential causes a downwardly directed force to be generated against 
the piston head 41. Under normal circumstances, the piston 38 will be 
moved to (or remain in) the closed position illustrated in FIG. 5 in 
response to this downwardly directed biasing force. The solenoid 65 may be 
activated to move the valve 63 to a second position, wherein the first 
passageway 47 is vented to the atmosphere and the second passageway 48 
communicates with the source of pressurized air. The pressure differential 
across the piston head 41 is reversed, causing an upwardly directed force 
to be generated against the piston head 41. Under normal circumstances, 
the piston 38 will be moved to (or remain in) the opened position 
illustrated in FIG. 4 in response to this upwardly directed biasing force. 
To operate the gear pump 10, the second shaft 17 is connected to rotate 
continuously with the vehicle engine. As a result, the first and second 
gears 20 and 21 are also continuously rotated. Assuming that the dry valve 
32 initially is in the closed position illustrated in FIG. 5, the gear 
pump 10 will be operated in the dry mode. In such mode, the hydraulic 
fluid in the reservoir 60 is prevented from entering the pumping chamber 
22 by the valve head 40. However, the aperture 46 permits a relatively 
small amount of hydraulic fluid to flow through the valve head 40 into the 
pumping chamber 22. This small amount of hydraulic fluid lubricates and 
cools the gears 20 and 21 and related components of the gear pump 10 while 
it is operated in the dry mode. The priority flow control valve 35 permits 
the small amount of hydraulic fluid to flow therethrough into the outlet 
port 31. At that point, however, all of such fluid will be diverted into 
the feedback passageway 37. This occurs because the reduced diameter 
portion 50 of the piston rod 42 is positioned to provide a path from the 
feedback passageway 37 through the third passageway 51, the piston rod 
chamber 44, the fourth passageway 52, the groove chamber 53, the drain 
passageway 56, and the drain port 57 to the reservoir 60. The fluid flows 
through this path because it faces a path of higher resistance from the 
outlet port 31 to the hydraulic system 61. Thus, while the gear pump 10 is 
in the dry mode, no fluid is delivered to operate the hydraulic system 61. 
When it is desired to operate the hydraulic system 61, the solenoid 65 is 
activated to move the valve 63 from the first position illustrated in FIG. 
6 to the second position. As a result, a pressure differential is created 
across the piston head 41 urging it upwardly (when viewing FIGS. 4 and 5) 
as described above. In response thereto, the piston 38 is moved to the 
opened position illustrated in FIG. 4. When so moved, the valve head 40 is 
moved out of engagement with the seat 45 to permit hydraulic fluid to flow 
from the inlet port 30 into the pumping chamber 22. Pressurized fluid 
flows through the priority flow control valve 35 and the outlet port 31 to 
the hydraulic system 61. The pressurized fluid does not flow through the 
above-described path to the reservoir 60 because the reduced diameter 
portion 50 of the piston rod 42 is moved away from the third passageway 51 
and the fourth passageway 52 when the piston 38 is moved to the opened 
position. As a result, communication between the third passageway 51 and 
the fourth passageway 52 is prevented. However, the pressurized fluid from 
the outlet port 31 does exert a pressure against the side of the piston 
rod 42 which is disposed adjacent the third passageway 51. This 
side-loading pressure is utilized when it is desired to move the piston 38 
back to the closed position, as described below. However, so long as the 
piston 38 is in the opened position, pressurized fluid is supplied from 
the gear pump 10 to operate the hydraulic system 61. 
When it is desired to disable the hydraulic system 61 from operation, the 
solenoid 65 is activated to move the valve 63 back to the first position 
illustrated in FIG. 6. As a result, a pressure differential is again 
created across the piston head 41 urging it downwardly (when viewing FIGS. 
4 and 5) toward the closed position. This pressure differential can be 
translated into a biasing force which is directed axially downwardly 
relative to the piston 38. The magnitude of this biasing force is 
determined basically by the magnitude of the pressure differential and the 
area of the piston head 41 exposed to such pressure differential. 
At the same time, however, the piston 38 is subjected to a side-loading 
pressure because of the relatively high pressure fluid being provided from 
the outlet port 31 through the feedback passageway 37. The side-loading 
pressure can be translated into a frictional force generated between the 
piston rod 42 and the piston rod chamber 44. This frictional force resists 
axial movement of the piston rod 42 relative to the piston rod chamber 44. 
The magnitude of the frictional force is determined basically by the 
magnitude of the pressure of the hydraulic fluid from the outlet port 31, 
the area of the piston rod 42 exposed to such pressure, and the 
coefficient of friction between the piston rod 42 and the piston rod 
chamber 44. When the magnitude of the biasing force is greater than the 
magnitude of the frictional force, the piston 38 will be moved from the 
opened position to the closed position. When the magnitude of the biasing 
force is less than the magnitude of the frictional force, the piston 38 
will not be moved to the closed position. 
As previously mentioned, it is undesirable to close the dry valve 32 when 
the gear pump 10 is generating a flow of fluid through the outlet port 31 
at a pressure which is greater than a predetermine maximum safe magnitude. 
By appropriately selecting the size of the opening of the third passageway 
51 which opens into the piston rod chamber 44 or the maximum pressure the 
source of pressurized air is capable of exerting, the dry valve 32 can be 
held automatically in its opened position until the pressure of the fluid 
flowing from the outlet port 31 drops below the predetermined maximum safe 
magnitude. As soon as the pressure of the fluid flowing from the outlet 
port 31 does drop below the predetermined maximum safe magnitude, the dry 
valve 32 will be moved to the closed position. The closure of the dry 
valve 32 is automatically prevented until the fluid pressure at the outlet 
port 31 is less than the predetermined maximum safe magnitude. 
In accordance with the provisions of the patent statutes, the principle and 
mode of operation of the present invention have been explained and 
illustrated in its preferred embodiment. It must be understood, however, 
that the present invention may be practiced otherwise than as specifically 
explained and illustrated without departing from its spirit or scope.