Note: Descriptions are shown in the official language in which they were submitted.
Nader's reciprocating mono or double acting linear pump in which the natural
incompressibility of liquids is the used technology to pump liquids.
This invention relates to the construction of a Reciprocating mono or double
acting linear
pump using the natural incompressibility of liquids and the volume of a piston
that moves
alternatively inside the liquid of a compressing chamber full of liquid
regardless of the size
and the form of said compressing chamber and said piston but a tight seal must
be provided
between said piston and its opening inside the wall of said compressing
chamber to prevent
liquid to leak to the exterior of said compressing chamber.
The prior art includes in addition pumps using conventional hydraulic
cylinders and pistons or
other means. The manufacturing of Said pumps of the prior art has a limit in
the size and in
the flow while they are very expensive and never easy to be built.
The subject of this invention is a Reciprocating mono or double acting linear
pump using the
natural incompressibility of liquids and the volume of a solid corps called
piston that moves
alternatively inside the liquid of a compressing chamber full of said liquid.
Said Reciprocating mono or double acting linear pump includes compression
chambers that
replace said conventional hydraulic cylinders in the prior art, while said
compression
chambers can have any size and any shape without any limitation. The natural
incompressibility of liquids is the main functioning technology of this
invention that pushes
part of said liquid out of any chamber with the introduction of said solid
corps (Piston) inside
its present liquid. The main issue of the introduction of the piston inside
the liquid is to have
only a variation in the volume of said liquid inside said compressing chamber
that favors the
liquid pumping because of the natural incompressibility of liquids, and the
volume of the
pumped liquid is equal to the volume of the introduced part of said piston.
Thus, in real life, the displaced volume of liquid will be pushed to exit said
compressing
chamber through one way valves then through canalisation pipes that take said
liquid to where
we need it to go.
The present invention is practical, easy to be built and costs a little
fraction of the cost of a
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similar pump of the prior art.
Finally, and Because of the simplicity of the construction of this pump the
subject of the
present invention, that permits the use of any solid material available like
cement, plastic,
carbon fiber, metals or the like to build it, the developed countries will
have the pumping
mean that favors effectively and at a very low cost in addition the irrigation
of their fields.
Said pump will use any available energy to operate like electrical,
mechanical, hydraulic
energy in addition to human or animal energy or else.
The embodiment of this invention includes the following:
1- A compression chamber having any shape or any size including inlet and
outlet one
way valves
2- A solid corps called piston of any shape or any size, but said piston
has to have a form
that permits it to move freely and in an alternative motion while allowing
liquid to
enter and exit said compression chamber. The applied alternative movement
allows
said piston to enter and exit said compression chamber through an opening in
the wall
of said chamber made specifically to house it, while the use of an appropriate
seal is
needed to seal tightly between said opening and said piston while admitting
liquid to
the compression chamber and then while expelling said liquid to flow through
one
way valves to reach the proper canalisation pipes of said pump.
3- Inlet and outlet one way valves for every compressing chamber are needed
for the
good functioning of said pump.
4- This pump can be reciprocating mono acting linear and will be built with
one
compressing chamber, or reciprocating double acting linear that will be built
with two
compressing chambers,
5- One or multiple pistons can be used with any compression chamber while
respecting a
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tight seal between every piston and its opening.
6- Said compression chambers of every pump are affixed on a solid base.
7- For a double acting linear pump, two compression chambers will be
mounted on the
same solid base, and a double acting linear piston that permits liquid inlet
to one
compression chamber and liquid outlet from the other compression chamber with
any
movement being to the right or to the left. The size of every compression
chamber can
vary from each other of the same double acting linear pump that help to mount
practical pumps inside wells without problems that helps effectively to
configure said
double acting linear pump in a very restrained compartment.
8- For a reciprocating mono acting linear pump, one compression chamber
will be
mounted on a solid base, and a reciprocating mono acting linear piston that
permits
liquid inlet while moving to one side of the compressing chamber accordingly
to the
way said reciprocating mono acting linear pump is mad with, and liquid outlet
while
moving alternatively to the other side in the same compression chamber. The
size of
the compression chamber can vary from one pump to the other accordingly to the
need
of the user. This reciprocating mono acting linear pump can be huge or small,
but it is
recommended to use it to provide small flows because of the cheap cost of its
manufacturing. While the double acting linear ones are recommended to be used
in
bigger projects.
9- In the following text, the description will be made Claire to describe
the reciprocating
mono or double acting linear pumps in order to not confuse the reader. Said
reciprocating mono acting linear pump is simple to build. So, every
reciprocating
double acting linear pump is made out of two reciprocating mono acting linear
pumps
but combined in one on the same base, and only one power system runs the
combination of the two reciprocating mono acting linear pumps.
10- A brace is affixed between said pistons of the two compression chambers
of the same
reciprocating double acting linear pump. Said brace permits to apply at the
same time
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an alternative movement to said pistons, while one piston compresses the
present
liquid in the first compressing chamber, and the other one admits liquid into
the other
compressing chamber.
11- A solid frame that allows the use of any power system being hydraulic
mechanical or
else that is needed for the good functioning of said reciprocating mono or
double
acting linear pump.
12- Said pistons that move alternatively inside said liquid of every
compressing chamber
of said reciprocating mono or double acting linear pump, can be hollow from
the
inside, because we only need the volume that is introduced in the liquid in
order to
expel an equal volume of liquid from said compression chambers to the part of
said
piston that is introduced into said liquid of said compressing chamber, or
when pulled
out to admit an equal volume of liquid to the part of said piston that is
pulled out of
said liquid of the same compressing chamber.
13- The compression chambers can be built in a proper way to sustain low or
high
pressures accordingly to low and high heads.
14- A Hydraulic system is needed to operate said reciprocating mono or
double acting
linear pump including: a hydraulic oil tank, a hydraulic oil pump, a pressure
control
valve, a hydraulic directional oil control valve that alternates the movement
of said
piston (s) by sending the hydraulic oil under pressure in one direction or the
other to
regular hydraulic cylinder (s) and piston (s), hydraulic oil pipes that are
needed to flow
hydraulic oil in and out from said regular hydraulic cylinder (s), a nitrogen
shock
absorber that diminishes the effect of the alternative movement of the oil
under
pressure during the functioning of said pump, and oil pipes for the return of
the
hydraulic oil during the functioning of said hydraulic system.
15- In addition, among all other sources of power systems that can be used
to operate the
present subject of the present invention, a simple Cable-Polis mechanical
system that
will be operated by any turning wheel and the use of a connecting rod and
swivels in
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order to apply a back and forth movement to said above mentioned Cable-Polis
mechanical system that in turn said Cable-Polis mechanical system will operate
the
pistons in there compressing chambers of said pump through the use of a brace
that is
affixed on said pistons. The above mentioned Cable-polis mechanical system can
be
used too without the cables and polis if we can connect the connecting rod
directly to
the brace of said piston (s).
16- Moreover, a screw jack device operating system of my Canadian patent no
2473077
can be used instead of the abovementioned operating devices in order to render
said
pump a very useful device specifically when said pump is used to pump crude
oil
from oil wells located at very deep depth, where the torque needed to operate
the
screw of the screw jack, can be smaller than the torque needed to operate the
pumps
of the existing prior art that are used actually in the oil exploration
fields, in order to
overcome the force created by the hydrostatic pressure that exerts by the
column of
water or crude oil on the surface of all the pistons that are pumping water or
crude oil
accordingly to the following formula: (The total force to overcome expressed
in
Newton (Time)(x) the pitch of the screw of the screw jack expressed in meters)
(Divided by)(/) (2 x pi 3.1416). My patent no CA 2473077 discloses the
embodiment
and the functioning of a reciprocating double acting linear air compressor
that can be
operated by the screw of a screw jack device. This screw jack device can be
used as
power supply system for the present subject of my present invention without
any
modifications. Said screw, communicates a linear and reciprocating movement to
all
pistons of said reciprocating double acting linear pump the subject of the
present
invention through cables and polls systems in addition. Said reciprocating
double
acting linear cable oil pump, uses less energy for the same pumped quantity of
oil
comparing with the conventional linear cable oil pumps of the prior art that
are not
double acting and actually are used in the oil exploration domain. In said
cable pump
of the prior art, the time needed for the pistons to go back to the pumping
position of
the next cycle, is not productive, while it is productive in this
reciprocating double
acting linear cable oil pump the subject of the present invention.
17- Examples of said double acting linear pumps are used to pump
underground water
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from water wells of different sizes. And, because of the limited space in some
water
wells, the used pumps can be built in a way to fit any water well without any
complications, while the bottom part of the same double acting linear pump can
have a
different size than the upper part in order to have the proper pumping system.
The principal technology of the functioning of the reciprocating mono or
double acting linear
pump the subject of the present invention will be as follow:
First of all, I would like to explain how the natural incompressibility works
in this
reciprocating mono or double acting linear pump before disclosing the real
functioning of said
pump.
If we just take a container completely full of liquid being water or else and
we introduce into
that liquid a solid corps, right away we notice that part of that liquid goes
out of said
container, and the volume of the overflowing liquid is equal to the volume of
the immerged
part of said solid corps.
So, the present reciprocating mono or double acting linear pump the subject of
the present
invention functions exactly according to the abovementioned simple technology
of the natural
incompressibility of liquids where the following will describe the functioning
of an example
of a double acting linear pump.
1- How said reciprocating mono acting linear Pump works:
When said piston of said reciprocating mono acting linear Pump is at the end
of its run inside
its compressing chamber that means that the end of the last outlet cycle of
the actual pump is
reached. At this position the outlet one way valve is open and it is at the
verge of closing
when said piston will restart it is run to the other direction by exiting said
compressing
chamber that enlarges the volume inside that chamber and liquid will reflow
into said
chamber by suction where the one way inlet valve opens that means that a new
inlet cycle is
starting that favors the automatic closing of said outlet one way valve. The
admission of
liquid into said compression chamber is done only as explained in the above by
suction, and
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the pumping when said piston starts entering said compressing chamber is done
only by the
incompressibility of the present liquid inside said compressing chamber that
forces the liquid
to exit said compressing chamber through said outlet one way valve then to the
canalisation
pipe that takes the exiting liquid to where we want to go.
2- How said reciprocating double acting linear Pump works:
First of all, I have to mention that Said reciprocating double acting linear
pump is made out of
two reciprocating mono acting linear pumps.
Thus, before starting an example of a reciprocating double acting pump a
subject of the
present invention, all of the components of said example have to be in place
and affixed on a
solid base ready to run.
a. The outlet one way valves have to be hooked to the needed canalisation
pipes that take
the pumped water to where we need it to go. The inlet one way vales have to be
hooked to a source of water being by gravity or else.
b. The compressing chambers have to be full of water without any trace of
air.
c. The chosen power system that commands in a linear and alternative motion
said solid
corps that are called pistons to enter and exit their respective compressing
chambers, is
in place and hooked to the brace that is used to communicate at the same time
the
alternative movement of the power system that is powering said pistons of said
pump.
d. Because said reciprocating double acting linear pump is made out of two
reciprocating
mono linear pumps but operated with one double acting piston of just one
operating
system, that means when an outlet cycle is in one compressing chamber it will
be
faced with an inlet cycle in the other compressing chamber all the time, and
the
contrary happens for the second cycle where when the inlet cycle of the first
compressing chamber starts, a new outlet cycle starts in the second chamber.
So,
e. When the first piston that is at the end of its outlet cycle inside its
compressing
chamber that means that it is about to start exiting from its compressing
chamber, then
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an inlet cycle starts for this compressing chamber and water starts entering
that
compressing chamber by suction from its inlet one way valve.
f. Thus, with the move of the first piston to exiting its own
compressing chamber for a
new inlet cycle, the second piston will be forced to enter its own compressing
chamber
while an outlet cycle starts for its own compressing chamber, and water starts
exiting
that compressing chamber from its outlet one way valve by an equal volume to
the
volume of the entered part of said second piston and that because of the
natural
incompressibility of the liquid.
g. The proper seal that is located between every piston and its own opening
prevents
liquid from leaking without reason to the outside of said compressing chamber,
and it
has to be maintained all the time in good working conditions while it can be
made out
from an appropriate rubber or other materials.
h. For a good functioning of said pump, the speed of said pistons to entering
and exiting
their own compressing chambers has to be well calculated in a way that allows
liquid
to entering and exiting from said compressing chambers without any
restrictions.
Depending on site specifications and the output required, various components,
configurations
and dimensions for the embodiment may be combined to achieve the desired
results,
And to those skilled in the art to which the invention relates, may changes in
construction and
widely differing embodiments and applications of the invention will suggest
themselves
without departing from the scope of the invention as defined in the appended
claims. The
disclosures and the descriptions herein are purely illustrative and are not
intended to be in any
sense limiting.
For a better understanding of this invention and to facilitate its
examination, it is represented
in the following 27 Figures.
Brief description of the drawings:
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Figure 1 a front view of a reciprocating double acting linear pump for low
heads, having one
single piston and showing compression cycle to the left and admission cycle to
the right.
Figure 2 a front view of a reciprocating double acting linear pump for low
heads, having
multiple pistons and showing compression cycle to the left and admission cycle
to the right.
Figure 3 a top view of a reciprocating double acting linear pump for low
heads, having one
single piston and showing compression cycle to the left and admission cycle to
the right.
Figure 4 a top view of a reciprocating double acting linear pump for low
heads, having
multiple pistons and showing compression cycle to the left and admission cycle
to the right.
Figure 5 a front view of a reciprocating double acting linear pump for low
heads, having one
single piston and showing compression cycle to the left and admission cycle to
the right. It is
mounted on a solid frame and operated hydraulically.
Figure 6 a front view of a reciprocating double acting linear pump for low
heads, having
multiple pistons and showing compression cycle to the left and admission cycle
to the right. It
is mounted on a solid frame and operated hydraulically.
Figure 7 a top view of a reciprocating double acting linear pump for low
heads, having one
single piston and showing compression cycle to the left and admission cycle to
the right. It is
mounted on a solid frame and operated hydraulically.
Figure 8 a top view of a reciprocating double acting linear pump for low
heads, having
multiple pistons and showing compression cycle to the left and admission cycle
to the right. It
is mounted on a solid frame and operated hydraulically.
Figure 9 a front cross sectional view along line E-E of Fig. 3 of a
reciprocating double acting
linear pump for low heads having one single piston.
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Figure 10 a front cross sectional view along line F-F of Fig. 4 of a
reciprocating double
acting linear pump for low heads having multiple pistons.
Figure 11 a front view of a reciprocating double acting linear pump for high
heads, having
one single piston and showing compression cycle to the left and admission
cycle to the right.
It is mounted on a solid frame and operated hydraulically.
Figure 12 a front view of a reciprocating double acting linear pump for high
heads, having
multiple pistons and showing compression cycle to the left and admission cycle
to the right. It
is mounted on a solid frame and operated hydraulically.
Figure 13 a top view of a reciprocating double acting linear pump for high
heads, having one
single piston and showing compression cycle to the left and admission cycle to
the right. It is
mounted on a solid frame and operated hydraulically.
Figure 14 a top view of a reciprocating double acting linear pump for high
heads, having
multiple pistons and showing compression cycle to the left and admission cycle
to the right. It
is mounted on a solid frame and operated hydraulically.
Figure 15 a front cross sectional view along line G-G of Fig. 13 of a
reciprocating double
acting linear pump for high heads having one single piston.
Figure 16 a front cross sectional view along line F-F of Fig. 4 of a
reciprocating double
acting linear pump for high heads having multiple pistons.
Figure 17 a left cross sectional view along line A-A of Fig. 9 of a
reciprocating double acting
linear pump for low heads having one single piston.
Figure 18 a left cross sectional view along line B-B of Fig. 10 of a
reciprocating double
acting linear pump for low heads having multiple pistons.
Figure 19 a left cross sectional view along line C-C of Fig. 15 of a
reciprocating double
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acting linear pump for high heads having one single piston.
Figure 20 a left cross sectional view along line D-D of Fig. 16 of a
reciprocating double
acting linear pump for HIGH heads having multiple pistons.
Figure 21 a top view of a reciprocating double acting linear pump for low
heads, mounted
with its hydraulic operating system and having one single piston and showing
compression
cycle to the left and admission cycle to the right.
Figure 22 a top view of a reciprocating double acting linear pump for low
heads, mounted
with its hydraulic operating system and having one single cylinder and showing
compression
cycle to the right and admission cycle to the left.
Figure 23 a top view of a reciprocating double acting linear pump for low
heads, mounted
with its reciprocal cable-polis operating system and having one single piston
and showing
compression cycle to the left and admission cycle to the right.
Figure 24 a cross sectional view of a reciprocating double acting linear pump
mounted with
its reciprocal cable-polis operating system, it is used to pump underground
water from water
well.
Figure 25 a cross sectional view of a reciprocating double acting linear pump
mounted with
its screw jack device operating system of my Canadian patent no 2473077, it is
used to pump
underground water from water well and crude oil from oil well regardless of
the depth.
Figure 26 a front cross sectional view of a reciprocating mono acting linear
pump showing
the end of its inlet cycle and mounted with its screw jack device operating
system of my
Canadian patent no 2473077.
Figure 27 a front cross sectional view of a reciprocating mono acting linear
pump showing
the end of its outlet cycle and mounted with its screw jack device operating
system of my
Canadian patent no 2473077.
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When considered with the description herein, the characteristics of the
invention are apparent
from the accompanying drawings, which exemplify an embodiment of the invention
for
purposes of illustration only, and in which -
Figure 1 a front view of a reciprocating double acting linear pump for low
heads, having one
single piston and showing compression cycle to the left and admission cycle to
the right,
including the compression chambers 1 and 1A, the pistons 2 and 2A, the brace 3
which is
used to operate and alternate the movement of the pistons 2 and 2A, air
bleeding means 1B
and IC That helps to empty any trace of air from the compressing chambers 1
and 1A, the
outlet one way valves 5 and 5A that are used to send the liquid to the
canalization pipes 9 and
9A, the inlet one way valves 4 and 4A that allow liquid to enter the
compression chambers 1
and 1A during liquid inlet cycle, the solid base 7 with the brackets 6 and 6A
that affix the
compression chambers 1 and IA to said base 7.
Figure 2 a front view of a reciprocating double acting linear pump for low
heads, having
multiple pistons and showing compression cycle to the left and admission cycle
to the right,
including the compression chambers 1 and 1A, the multiple pistons 8 and 8A,
air bleeding
means 1B and IC That helps to empty any trace of air from the compressing
chambers 1 and
1A, the brace 3 which is used to operate and alternate the movement of the
multi pistons 8 and
8A, the outlet one way valves 5 and 5A that are used to send the liquid to the
canalization
pipes 9 and 9A, the inlet one way valves 4 and 4A that allow liquid to enter
the compression
chambers 1 and IA during liquid inlet cycle, the solid base 7 with the
brackets 6 and 6A that
affix the compression chambers 1 and lA to said solid base 7.
Figure 3 a top view of a reciprocating double acting linear pump for low
heads, having one
single piston and showing compression cycle to the left and admission cycle to
the right,
including the compression chambers 1 and 1A, the pistons 2 and 2A, air
bleeding means 1B
and 1C That helps to empty any trace of air from the compressing chambers 1
and 1A, the
brace 3 which is used to operate and alternate the movement of the pistons 2
and 2A, the
outlet one way valves 5 and 5A that are used to send the liquid to the
canalization pipes 9 and
9A.
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Figure 4 a top view of a reciprocating double acting linear pump for low
heads, having
multiple pistons and showing compression cycle to the left and admission cycle
to the right,
including the compression chambers 1 and 1A, the multi pistons 8 and 8A, air
bleeding means
1B and 1C That helps to empty any trace of air from the compressing chambers 1
and 1A, the
brace 3 which is used to operate and alternate the movement of the pistons 8
and 8A, the
outlet one way valves 5 and 5A that are used to send the liquid to the
canalization pipes 9 and
9A.
Figure 5 a front view of a reciprocating double acting linear pump for low
heads, having one
single piston and showing compression cycle to the left and admission cycle to
the right. It is
mounted on a solid frame and operated hydraulically, including a reciprocating
double acting
pump affixed to a solid frame 7, hydraulic cylinders 10 and 10A with their
pistons 11 and
11A that are used to alternate the movement of the brace 3 that in turn
alternates the
movement of pistons 2 and 2A, air bleeding means 1B and 1C That helps to empty
any trace
of air from the compressing chambers 1 and 1A, the affixing points 13 of the
cylinder 10 to
the bracket 12, the affixing points 13A of the piston 11 to the brace 3, the
affixing points 13C
of the cylinder 10A to the bracket 12A, the affixing points 13B of the piston
11A to the brace
3,
Figure 6 a front view of a reciprocating double acting linear pump for low
heads, having
multiple pistons and showing compression cycle to the left and admission cycle
to the right. It
is mounted on a solid frame and operated hydraulically, including a
reciprocating double
acting pump affixed to a solid frame 7, hydraulic cylinders 10 and 10A with
their pistons 11
and 1 IA that are used to alternate the movement of the brace 3 that in turn
alternates the
movement of pistons 8 and 8A, air bleeding means 1B and 1C That helps to empty
any trace
of air from the compressing chambers 1 and IA, the affixing points 13 of the
cylinder 10 to
the bracket 12, the affixing points 13A of the piston 11 to the brace 3, the
affixing points 13C
of the cylinder 10A to the bracket 12A, the affixing points 13B of the piston
11A to the brace
3.
Figure 7 a top view of a reciprocating double acting linear pump for low
heads, having one
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single piston and showing compression cycle to the left and admission cycle to
the right. It is
mounted on a solid frame and operated hydraulically, including a solid frame
7, cylinders 10
and 10A with their pistons 11 and 11A and the hydraulic cylinders 10B and 10C
and their
pistons 11B and 11C that are used to alternate the movement of the brace 3
that in turn
alternates the movement of pistons 2 and 2A, air bleeding means 1B and 1C That
helps to
empty any trace of air from the compressing chambers 1 and 1A, the affixing
points 13 of the
cylinder 10 to the bracket 12, the affixing points 13A of the piston 11 to the
brace 3, the
affixing points 13C of the cylinder 10A to the bracket 12A, the affixing
points 13B of the
piston 11A to the brace 3, the affixing points 13D of the cylinder 10B to the
bracket 12, the
affixing points 13E of the piston 11B to the brace 3, the affixing points 13G
of the cylinder
10C to the bracket 12A, the affixing points 13F of the piston 11C to the brace
3. Here I have
to mention that cylinders 10, 10A, 10B and 10C, receive hydraulic oil under
pressure from the
operating hydraulic oil control valve at the same time either to move the
pistons 11, 11A, 11B
and 11C to the right or to the left. Thus, because the brace 3 is affixed from
one side to the
pistons 2 and 2A or to the pistons 8 and 8A and from the other side to the
abovementioned
hydraulic pistons 11, 11A, 11B, 11C and 11D, then said pistons 2 and 2A or
said pistons 8
and 8A move accordingly to the same direction of said above mentioned
hydraulic pistons of
the operating hydraulic system 11, 11A, 11B and 11C, during the functioning of
said pimp.
Figure 8 a top view of a reciprocating double acting linear pump for low
heads, having
multiple pistons and showing compression cycle to the left and admission cycle
to the right. It
is mounted on a solid frame and operated hydraulically, including a solid
frame 7, cylinders
and 10A with their pistons 11 and 11A and the hydraulic cylinders 10B and 10C
and their
pistons 11B and 11C that are used to alternate the movement of the brace 3
that in turn
alternates the movement of pistons 8 and 8A, air bleeding means 1B and 1C That
helps to
empty any trace of air from the compressing chambers 1 and 1A, the affixing
points 13 of the
cylinder 10 to the bracket 12, the affixing points 13A of the piston 11 to the
brace 3, the
affixing points 13C of the cylinder 10A to the bracket 12A, the affixing
points 13B of the
piston 11A to the brace 3, the affixing points 13D of the cylinder 10B to the
bracket 12, the
affixing points 13E of the piston 11B to the brace 3, the affixing points 13G
of the cylinder
10C to the bracket 12A, the affixing points 13F of the piston 11C to the brace
3. Here I have
to mention that cylinders 10, 10A, 10B and 10C, receive hydraulic oil under
pressure from the
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CA 2969325 2017-06-05
operating hydraulic oil control valve at the same time either to move the
pistons 11, I1A, 11B
and 11C to the right or to the left. Thus, because the brace 3 is affixed from
one side to the
pistons 2 and 2A or to the pistons 8 and 8A and from the other side to the
abovementioned
hydraulic pistons 11, 11A, 11B, 11C and I ID, then said pistons 2 and 2A or
said pistons 8
and 8A move accordingly to the same direction of said above mentioned
hydraulic pistons of
the operating hydraulic system 11, 11A, 11B and 11C, during the functioning of
said pimp.
Figure 9 a front cross sectional view along line E-E of Fig. 3 of a
reciprocating double acting
linear pump for low heads having one single piston, including the compression
chambers 1
and 1A, the pistons 2 and 2A, the seal 46 that seals between the pistons 2 and
2A and their
openings in the compression chambers 1 and 1A, the brace 3 which is used to
operate and
alternate the movement of the pistons 2 and 2A, the outlet one way valves 5
and 5A that are
used to send the liquid to the canalization pipes 9 and 9A, the inlet one way
valves 4 and 4A
that allow liquid to enter the compression chambers 1 and IA during liquid
inlet cycle, air
bleeding means 1B and 1C That helps to empty any trace of air from the
compressing
chambers 1 and 1A, the solid base 7 with the brackets 6 and 6A that affix the
compression
chambers 1 and lA to the base 7.
Figure 10 a front cross sectional view along line F-F of Fig. 4 of a
reciprocating double
acting linear pump for low heads having multiple pistons, including the
compression
chambers 1 and 1A, the multi pistons 8 and 8A, the brace 3 which is used to
operate and
alternate the movement of the multi pistons 8 and 8A, the seal 47 that seals
between the multi
pistons 8 and 8A and their openings in the compression chambers 1 and 1A, the
outlet one
way valves 5 and 5A that are used to send the liquid to the canalization pipes
9 and 9A, the
inlet one way valves 4 and 4A that allow liquid to enter the compression
chambers 1 and IA
during liquid inlet cycle, air bleeding means 1B and 1C That helps to empty
any trace of air
from the compressing chambers 1 and 1A, the solid base 7 with the brackets 6
and 6A that
affix the compression chambers 1 and IA to the base 7.
Figure 11 a front view of a reciprocating double acting linear pump for high
heads, having
one single piston and showing compression cycle to the left and admission
cycle to the right.
It is mounted on a solid frame and operated hydraulically, including a
reciprocating double
CA 2969325 2017-06-05
acting pump affixed to a solid frame 7, the brackets 6 and 6A that affix the
compression
chambers 1 and 1A to the base 7, hydraulic cylinders 10 and 10A with their
pistons 11 and
11A that are used to alternate the movement of the brace 3 that in turn
alternates the
movement of pistons 2 and 2A, the affixing points 13 of the cylinder 10 to the
bracket 12, the
affixing points 13A of the piston 11 to the brace 3, the affixing points 13C
of the cylinder 10A
to the bracket 12A, the affixing points 13B of the piston 11A to the brace 3.
Figure 12 a front view of a reciprocating double acting linear pump for high
heads, having
multiple cylinders and showing compression cycle to the left and admission
cycle to the right.
It is mounted on a solid frame and operated hydraulically, including a
reciprocating double
acting pump affixed to a solid frame 7, the brackets 6 and 6A that affix the
compression
chambers 1 and 1A to the base 7, hydraulic cylinders 10 and 10A with their
pistons 11 and
11A that are used to alternate the movement of the brace 3 that in turn
alternates the
movement of pistons 8 and 8A, the affixing points 13 of the cylinder 10 to the
bracket 12, the
affixing points 13A of the piston 11 to the brace 3, the affixing points 13C
of the cylinder 10A
to the bracket 12A, the affixing points 13B of the piston 11A to the brace 3.
Figure 13 a top view of a reciprocating double acting linear pump for high
heads, having one
single piston and showing compression cycle to the left and admission cycle to
the right. It is
mounted on a solid frame and operated hydraulically, including a solid frame
7, cylinders 10
and 10A with their pistons 11 and 11A and the hydraulic cylinders 10B and 10C
and their
pistons 11B and 11C that are used to alternate the movement of the brace 3
that in turn
alternates the movement of pistons 2 and 2A, the affixing points 13 of the
cylinder 10 to the
brace 12, the affixing points 13A of the piston 11 to the brace 3, the
affixing points 13C of the
cylinder 10A to the bracket 12A, the affixing points 1313 of the piston 11A to
the brace 3, the
affixing points 13D of the cylinder 1013 to the bracket 12, the affixing
points 13E of the piston
11B to the brace 3, the affixing points 13G of the cylinder 10C to the bracket
12A, the
affixing points 13F of the piston 11C to the brace 3. Here I have to mention
that cylinders 10,
10A. 10B and 10C, receive hydraulic oil under pressure from the operating
hydraulic oil
control valve at the same time either to move the pistons 11, 11A, 11B and 11C
to the right or
to the left. Thus, because the brace 3 is affixed from one side to the pistons
2 and 2A or to the
pistons 8 and 8A and from the other side to the abovementioned hydraulic
pistons 11, 11A,
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11B, 11C and 11D, then said pistons 2 and 2A or said pistons 8 and 8A move
accordingly to
the same direction of said above mentioned hydraulic pistons of the operating
hydraulic
system 11, 11A, 1113 and 11C, during the functioning of said pimp.
Figure 14 a top view of a reciprocating double acting linear pump for high
heads, having
multiple pistons and showing compression cycle to the left and admission cycle
to the right. It
is mounted on a solid frame and operated hydraulically, including a solid
frame 7, cylinders
and 10A with their pistons 11 and I lA and the hydraulic cylinders I OB and
10C and their
pistons 11B and 11C that are used to alternate the movement of the bracket 3
that in turn
alternates the movement of pistons 8 and 8A, the affixing points 13 of the
cylinder 10 to the
bracket 12, the affixing points I3A of the piston 11 to the brace 3, the
affixing points 13C of
the cylinder 10A to the bracket 12A, the affixing points 13B of the piston 11A
to the brace 3,
the affixing points 13D of the cylinder 10B to the bracket 12, the affixing
points 13E of the
piston 11B to the brace 3, the affixing points 13G of the cylinder 10C to the
bracket 12A, the
affixing points 13F of the piston 11C to the brace 3. Here I have to mention
that cylinders 10,
10A, 10B and 10C, receive hydraulic oil under pressure from the operating
hydraulic oil
control valve at the same time either to move the pistons 11, 11A, 11B and 11C
to the right or
to the left. Thus, because the brace 3 is affixed from one side to the pistons
2 and 2A or to the
pistons 8 and 8A and from the other side to the abovementioned hydraulic
pistons 11, 11A,
11B, 11C and 11D, then said pistons 2 and 2A or said pistons 8 and 8A move
accordingly to
the same direction of said above mentioned hydraulic pistons of the operating
hydraulic
system 11, 11A, 11B and 11C, during the functioning of said pimp.
Figure 15 a front cross sectional view along line G-G of Fig. 13 of a
reciprocating double
acting linear pump for high heads having one single cylinder, including the
compression
chambers I and 1A, the pistons 2 and 2A, the seal 46 that seals between the
pistons 2 and 2A
and their openings in the compression chambers 1 and 1A, the brace 3 which is
used to
operate and alternate the movement of the pistons 2 and 2A, the outlet one way
valves 5 and
5A that are used to send the liquid to the canalization pipes 9 and 9A, the
inlet one way valves
4 and 4A that allow liquid to enter the compression chambers 1 and 1 A during
liquid inlet
cycle, the solid base 7 with the brackets 6 and 6A that affix the compression
chambers 1 and
IA to the base 7.
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Figure 16 a front cross sectional view along line F-F of Fig. 4 of a
reciprocating double
acting linear pump for high heads having multiple cylinders, including the
compression
chambers 1 and 1A, the multi pistons 8 and 8A, the brace 3 which is used to
operate and
alternate the movement of the multi pistons 8 and 8A, the seal 47 that seals
between the multi
pistons 8 and 8A and their openings in the compression chambers 1 and 1A, the
outlet one
way valves 5 and 5A that are used to send the liquid to the canalization pipes
9 and 9A, the
inlet one way valves 4 and 4A that allow liquid to enter the compression
chambers 1 and lA
during liquid inlet cycle, the solid base 7 with the brackets 6 and 6A that
affix the
compression chambers 1 and IA to the base 7.
Figure 17 a left cross sectional view along line A-A of Fig. 9 of a
reciprocating double acting
linear pump for low heads having one single piston, including the compressing
chamber IA
and the piston 2.
Figure 18 a left cross sectional view along line B-B of Fig. 10 of a
reciprocating double
acting linear pump for low heads having multiple cylinders, including the
compressing
chamber lA and the multi pistons 8A.
Figure 19 a left cross sectional view along line C-C of Fig. 15 of a
reciprocating double
acting linear pump for high heads having one single piston, including the
compressing
chamber 1A, the piston 2, the outlet one way valve 5A that are used to send
the liquid to the
canalization pipes 9A, the inlet one way valve 4A that allow liquid to enter
the compression
chambers IA during liquid inlet cycle.
Figure 20 a left cross sectional view along line D-D of Fig. 16 of a
reciprocating double
acting linear pump for high heads having multiple pistons, including the
compressing
chamber 1A, the multi pistons 8, the outlet one way valve 5A that are used to
send the liquid
to the canalization pipe 9A, the inlet one way valve 4A that allow liquid to
enter the
compression chambers lA during liquid inlet cycle.
Figure 21 a top view of a reciprocating double acting linear pump for low
heads, mounted
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with its hydraulic operating system and having one single piston and showing
compression
cycle to the left and admission cycle to the right, including a solid frame 7,
cylinders 10 and
10A with their pistons 11 and 11A and the hydraulic cylinders 10B and 10C and
their pistons
11B and 11C that are used to alternate the movement of the brace 3 that in
turn alternates the
movement of pistons 2 and 2A, the affixing points 13 of the cylinder 10 to the
bracket 12, the
affixing points 13A of the piston 11 to the brace 3, the affixing points 13C
of the cylinder 10A
to the bracket 12A, the affixing points 13B of the piston 11 A to the brace 3,
the affixing
points 13D of the cylinder 10B to the bracket 12, the affixing points 13E of
the piston 118 to
the brace 3, the affixing points 13G of the cylinder 10C to the bracket 12A,
the affixing points
13F of the piston 1 IC to the brace 3, the compression chambers 1 and 1A, air
bleeding means
1B and IC That help to purge any trace of air from the compressing chambers 1
and 1A, the
pistons 2 and 2A, the brace 3, the outlet one way valves 5 and 5A that are
used to send the
liquid to the canalization pipes 9 and 9A, hydraulic oil tank 14, hydraulic
oil pump 15, oil
pressure control valve 16, nitrogen shock absorber 16A, hydraulic oil
directional control valve
17, hydraulic oil pipes 18- 18A- 18B- 18C- 18D and 18E that send hydraulic oil
under
pressure to push the pistons 1 and lA toward the right side, oil pipes 19- 19A-
19B- 19C- 19D
and 19E that send hydraulic oil under pressure to push the pistons 1 and 1A
toward the left
side, hydraulic oil return pipe 20.
Figure 22 a top view of a reciprocating double acting linear pump for low
heads, mounted
with its hydraulic operating system and having one single piston and showing
compression
cycle to the right and admission cycle to the left, including a solid frame 7,
cylinders 10 and
10A with their pistons 11 and 11A and the hydraulic cylinders 10B and 10C and
their pistons
118 and 11C that are used to alternate the movement of the brace 3 that in
turn alternates the
movement of pistons 2 and 2A, the affixing points 13 of the cylinder 10 to the
bracket 12, the
affixing points 13A of the piston 11 to the brace 3, the affixing points 13C
of the cylinder 10A
to the bracket 12A, the affixing points 13B of the piston 11A to the brace 3,
the affixing
points 13D of the cylinder 10B to the bracket 12, the affixing points 13E of
the piston 118 to
the brace 3, the affixing points 13G of the cylinder 10C to the bracket 12A,
the affixing points
13F of the piston 11C to the brace 3, the compression chambers 1 and 1A, air
bleeding means
1B and IC That help to purge any trace of air from the compressing chambers 1
and 1A, the
pistons 2 and 2A, the brace 3, the outlet one way valves 5 and 5A that are
used to send the
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liquid to the canalization pipes 9 and 9A, hydraulic oil tank 14, hydraulic
oil pump 15, oil
pressure control valve 16, nitrogen shock absorber 16A, hydraulic oil
directional control valve
17, hydraulic oil pipes 18- 18A- 18B- 18C- 18D and 18E that send hydraulic oil
under
pressure to push the pistons 1 and lA toward the right side, oil pipes 19- 19A-
19B- 19C- 19D
and 19E that send hydraulic oil under pressure to push the pistons 1 and 1A
toward the left
side, hydraulic oil return pipe 20.
Figure 23 a top view of a reciprocating double acting linear pump for low
heads, mounted
with its reciprocal cable-polis operating system and having one single piston
and showing
compression cycle to the left and admission cycle to the right, including a
reciprocating
double acting pump affixed to a solid frame 7, cable-polis operating system
having cable 39
and 40 that are used to alternate the movement of the brace 3 through the
system of polis 42-
43- 44- 45, turning wheel 35 of any mechanical, electrical, or any other
system, a connecting
rod 37 that communicates the power and the rotational movement of the turning
wheel 35 into
back and forth movement to the cables 39 and 40, a swivel 38 that connects the
cable 39 and
40 to the connecting rod 37, a swivel 36 that connects the wheel 35 to the
connecting rod 37,
this configuration transforms the turning movement of the wheel 35 into an
alternative
movement to the cable-polis system that operate the pistons 2 and 2A of said
reciprocal
double acting pump
Figure 24 a cross sectional view of a reciprocating double acting linear pump
mounted with
its reciprocal cable-polis operating system, it is used to pump underground
water from water
well. Including a water well 21, a reciprocating double acting linear pump
with its
compressing chambers 1 and 1A, pistons 2 and 2A, a rod 31 for piston 2 and a
rod 32 for
piston 2A, an operating cable 25 of rod 31 and piston 2 through an attachment
33, an
operating cable 26 of rod 32 and piston 2A through an attachment 34, a frame
29 that supports
poly 30 through it the cable 26 operates the piston 2A through the rod 32, an
outside frame 28
that supports poly 27 through it the cable 25 operates the piston 2 through
the rod 31, a
hydraulic cylinder 22 operates the cables 25 and 26 through its piston 23 and
an attachment
24, a solid frame 7 that holds said linear double acting pump together, outlet
one way valves 5
and 5A that are used to send water or else to appropriate canalization pipes 9
and 9A then to
9B, inlet one way valves 4 and 4A that allow water or else to enter the
compression chambers
CA 2969325 2017-06-05
1 and 1A during liquid inlet cycle.
Figure 25 a cross sectional view of a reciprocating double acting linear pump
operated with a
screw jack operating system as described in my Canadian patent no 2473077, it
is used to
pump underground water from water wells or crude oil from oil wells regardless
of the depth
of these wells. Including an oil well 21, a reciprocating double acting linear
pump with its
compressing chambers 1 and IA, pistons 2 and 2A, a rod 31 for piston 2 and a
rod 32 for
piston 2A, an operating cable 25 of rod 31 and piston 2 through an attachment
33, an
operating cable 26 of rod 32 and piston 2A through an attachment 34, a frame
29 that supports
poly 30 through it the cable 26 operates the piston 2A through the rod 32, an
outside frame 28
that supports poly 27 through it the cable 25 operates the piston 2 through
the rod 31, screw
jack device 35 of my Canadian patent 2473077 that operates the cables 25 and
26 through its
screw jack 36 and an attachment 24 that affixes the screw jack 36 to said
cables 25 and 26, a
solid frame 7 that holds said linear double acting pump together, outlet one
way valves 5 and
5A that are used to send water or oil to appropriate canalization pipes 9 and
9A then to
canalization pipe 9B, inlet one way valves 4 and 4A that allow water or oil to
enter the
compression chambers 1 and IA during liquid inlet cycle. Said screw jack
device 35 is very
useful device specifically when said pump is used to pump crude oil from oil
wells located at
very deep depth where the torque needed to operate the screw 36 of the screw
jack 35, in
order to overcome the force created by the hydrostatic pressure that exerts by
the column of
water or crude oil on the surface of all the pistons that are pumping water or
crude oil at the
same time, is relatively very small accordingly to the following formula:
(The total force to overcome expressed in Newton (Time)(x) the pitch of the
screw of the
screw jack expressed in meters) (Divided by)(/) (2 x pi 3.1416).
Figure 26 a front cross sectional view of a reciprocating mono acting linear
pump showing
the end of its inlet cycle and mounted with its screw jack device operating
system of my
Canadian patent no 2473077, including the compression chambers 1, the piston
2A, the seal
46 that seals between the pistons 2A and its openings in the compression
chambers 1, the
outlet one way valves 5 that is used to send the pumped liquid to the
canalization pipes is
closed, the inlet one way valves 4 that allows liquid to enter the compression
chambers 1
during liquid inlet cycle is open, air bleeding mean 1B That helps to empty
any trace of air
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from the compressing chambers 1, the solid base 7 on which the compression
chambers 1 and
the screw jack operating system 35 are mounted.
Figure 27 a front cross sectional view of a reciprocating mono acting linear
pump showing
the end of its outlet cycle and mounted with its screw jack device operating
system of my
patent no 2473077, including the compression chambers 1, the piston 2A, the
seal 46 that
seals between the pistons 2A and its opening in the compression chambers 1,
the outlet one
way valves 5 that is used to send the liquid to the canalization pipes is
open, the inlet one way
valves 4 that allow liquid to enter the compression chambers 1 during liquid
inlet cycle is
closed, air bleeding mean 1B That helps to empties any trace of air from the
compressing
chambers 1, the solid base 7 on which the compression chambers 1 and the screw
jack
operating system 35 are mounted.
It should be understood, of course, that this pump can be built from various
materials and in
different dimensions according to the quantity of fluid required. The drawings
do not show
every step in the construction of the present invention, but they set out the
overall result
clearly.
Operation of the invention.
The pumping of liquid in this reciprocating double acting pump the subject of
the
present invention is done accordingly to the following:
A- Reciprocating double acting linear pump for low heads, having one or
multiple piston
and powered with a hydraulic system like in Fig. 21 and Fig. 22.
a. All of the components of this example have to be in place before starting
it. The
combination of the compressing chambers 1 and IA coupled to their respective
single pistons 2 and 2A like in Fig. 9 or their multiple pistons 8 and 8A like
in Fig.
10, have to be affixed on the solid base 7 through the brackets 6 and 6A.
22
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b. The brace 3 has to be affixed between piston 2 and 2A like in Fig. 9 or
between
the multiple pistons 8 and 8A like in Fig.10, in a way that permits to every
piston
or pistons of every side to enter the corresponding compressing chamber
freely.
c. The outlet valve 5 and the inlet valve 4 have to be installed on the
compressing
chamber 1, and the outlet valve 5A and the inlet valve 4A have to be installed
on
the compressing chamber 1A.
d. The bracket 12 has to be affixed in place on the base 7 in a way that
permits to
install on it the hydraulic cylinders 10 and 10B of the operating hydraulic
system
through their affixing means 13 and 13D.
e. The bracket 12A has to be affixed in place on the base 7 in a way
that permits to
install on it the hydraulic cylinders 10A and 10C of the operating hydraulic
system
through their affixing means 13C and 13G.
f. The piston 11 of the cylinder 10 has to be affixed on the brace 3 through
the
affixing mean 13A. The piston 11A of the cylinder 10A has to be affixed on the
brace 3 through the affixing mean 13B. The piston 11B of the cylinder 10B has
to
be affixed on the brace 3 through the affixing mean 13E. The piston 11C of the
piston 10C has to be affixed on the brace 3 through the affixing mean 13F.
g. The hydraulic control system has to be in place and it includes; the
hydraulic oil
tank 14, the hydraulic oil pump 15, the pressure control valve 16, the
Nitrogen
shock absorber 16A, the hydraulic oil directional valve 17, the hydraulic oil
pipes
18- 18A- 18B- 18C- 18D and 18E that communicate hydraulic oil under pressure
coming from the hydraulic oil directional valve 17 at the same time (Fig. 22)
in
order to push into chamber JA piston 2 and to push out chamber 1 piston 2A. Or
to
push into chamber IA the multi piston 8 and to push out chamber 1 the multi
pistons 8A when they are installed like in Fig. 6, the hydraulic oil pipes 19-
19A-
19B- 19C- 19D and 19E that communicate hydraulic oil under pressure coming
from the hydraulic oil directional valve 17 at the same time (Fig. 21) in
order to
23
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push out from chamber 1A piston 2 and to push into chamber 1 piston 2A. Or to
push out chamber IA the multi piston 8 and to push into chamber 1 the multi
pistons 8A when they are installed like in Fig. 6.
h. Once all of the components of the abovementioned example are in place, the
Reciprocating double acting pump is ready to run.
i. Now water is supplied to the pump by hooking the abovementioned one way
inlet
valves 4 and 4A to a source of water being by gravity or else.
j. As the hydraulic system from the compressing chambers 1 and IA to
the source of
water has no air what so ever because we had purge any existing air through
the air
purge means 1B and 1C of chamber 1 and IA Fig. 10. Any movement of any
piston inside the present liquid in said chambers 1 and 1A, being to exiting
the
chamber, that enlarges the volume of the chamber, or to entering the chamber,
that
diminishes the volume of that chamber. So, as illustrated in Fig. 21, the
piston 2A
is at the end of its run to the left in chamber 1 that means that an equal
volume of
water to the volume of the introduced part of piston 2A had already exited
chamber 1 through the one way outlet valve 5 while the inlet one way valve 4
is
closed, as a must, piston 2A is in this position to the left inside chamber 1
while
the inlet one way valve 4A is open and the outlet one way valve 5A is closed,
the
piston 2 had been forced to be out of the liquid of chamber 1A, that means
that an
equal volume of water to the volume of the exited part of piston 2 had already
entered chamber lA through the one way inlet valve 4A. Thus, at this point
when
piston 2 stars its run to the right, it means that piston 2A will be forced to
start his
run to the right too. So, piston 2 will start pushing water out from chamber
lA
because the volume inside chamber 1A starts to be smaller, the exiting flow
goes
through the one way outlet valve 5A that communicates with pipes 9, 9A and 913
to send the liquid under pressure to one common place as shown in Fig. 24 and
Fig. 25, automatically the inlet one way valve 4A closes by the pressure that
exists
inside said chamber 1A, while piston 2A will start sucking water into chamber
1
through the one way inlet valve 4 by suction while the outlet one way valve 5
closes automatically because it communicates with pipes 9, 9A and 9B that are
24
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connected together to send the liquid under pressure to the same common place
as
shown in Fig. 24 and Fig. 25. When said piston 2 will reach the end of its run
to
the right, an equal volume of water to the volume of the entered part of
piston 2
had already exited chamber IA through the one way outlet valve SA, and piston
2A will have reached the end of its run to the right, that means that an equal
volume of water to the volume of the exited part of piston 2A had already
entered
chamber 1 through the one way inlet valve 4. Then, at this point another cycle
will
start to the left, and at this point when piston 2A stars its run to the left,
it means
piston 2 will be forced to start his run to the left too. So, piston 2A will
start
pushing water out of chamber 1 through the one way outlet valve 5 because the
volume inside chamber 1 starts to be smaller while the inlet one way valve 4
closes
automatically, and piston 2 will start sucking water into chamber 1A through
the
one way inlet valve 4A while the outlet one way valve 5A closes automatically,
and that because the volume inside chamber IA starts to be bigger. When the
piston 2A will reach the end of its run to the left, an equal volume of water
to the
volume of the entered part of piston 2A had already exited chamber 1 through
the
one way outlet valve 5, and piston 2 will have reached the end of its run to
the left,
that means that an equal volume of water to the volume of the entered part of
piston 2 had already entered chamber lA through the one way inlet valve 4A.
k. Now and after the explanation of the cycles of said pump, it is time to
explain how
the coupled hydraulic system had behaved to reach what we had explained in the
above mentioned text.
1. The hydraulic oil pump 15 is running and compressing oil that is sucked
from the
oil tank 14 at a desired pressure that is suitable to run said pump 15 to
overcome
the effect of the pressure of the water head where we intend to pump the
water.
The desired pressure is regulated by the pressure control valve 16, then
through the
hydraulic oil directional control valve 17, the compressed hydraulic oil will
be sent
through the oil pipes 19, 19A, 1913, 19C, 19D and 19E to reach the position
that is
illustrated in Fig. 21 where water had exited chamber 1 and water had entered
chamber 1A. At this cycle, low pressure hydraulic oil had return from the
other
CA 2969325 2017-06-05
sides of pistons 11, 11A, 11B and 11C through the hydraulic oil return pipe 20
to
the oil tank 20.
m. At the end of the cycle of Fig. 21, another cycle will start as illustrated
in Fig. 22.
n. Then through the hydraulic oil directional control valve 17 the compressed
hydraulic oil will be sent through the oil pipes 18, 18A, 18B, 18C, 18D and
18E to
reach the position that is illustrated in Fig. 22 where water had exited
chamber IA
and water had entered chamber 1. At this cycle, low pressure hydraulic oil had
return from the other sides of pistons 11, 11A, 11B and 11C through the
hydraulic
oil return pipe 20 to the oil tank 14.
o. During the functioning of said pump and with the change of direction of the
hydraulic oil under pressure by the hydraulic oil directional control valve
17, the
produced shock will be absorbed by the Nitrogen shock absorber 16A that
prevents possible damages to the hydraulic system.
B-
Reciprocating double acting linear pump for low heads, having one or multiple
pistons and powered by a cable-polls system.
This example has the same Reciprocating double acting linear pump for low
heads as
described in the above mentioned subsections a, b, c, d, e, f, g, h, i and j
of section A, but said
reciprocating double acting pump is powered with a mechanical cable-polls
system as
described in Fig 23. In addition the following have to be in place before
starting this example.
a. As illustrated In Fig. 23 the cable-polis operating system that has to be
in place
before starting said pump, the cables 39 and 40 and the polls 42- 43- 44- 45
will
receive the rotational movement of the turning wheel 35 of any mechanical,
electrical, or any other system as linear and alternative movement through the
connecting rod 37 and the swivel 36 that connects the wheel 35 to the
connecting
rod 37, and the swivel 38 that connects the connecting rod 37 to the cable 39
and
40. this configuration will communicate a linear and alternative movement to
the
brace 3 that in turn will operate said pump exactly as described in the above
26
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mentioned subsections a, b, c, d, e, f, g, h, i and j, of section (A). of said
reciprocal double acting pump.
b. This pump functions exactly the way the pump in Fig. 21 and Fig. 22 did
without
any exception. But, the operating system is different where:
c. The turning wheel 35 will communicate its rotational movement to the
connecting
rod 37 through the swivel 36 to be transformed as linear and alternative
movement. Then In turn the connecting rod 37 will communicate this linear and
alternative movement to the cables 39 and 40 through the swivel 38. Thus, At
this
point the cables 39 and 40 will operate the pistons 2 and 2A inside chambers 1
and IA exactly with the way it was done for the first example (A) in
subsections
a, b, c, d, e, f, g, h, i and j with the hydraulic operating system.
d. In addition this system can be used where needed without the cables and the
polis
while the turning wheel will communicate directly its torque to said pistons
with
the use of a connecting rod and swivels.
C- Reciprocating double acting linear pump for water or oil wells and powered
with a
cable-polis system like illustrated in Fig. 24.
This example has the same Reciprocating double acting linear pump as described
in the above
mentioned subsections a, b, c, d, e, f, g, h, i and j, of section (A) with
only exception where
the brace 3 is replaced by the rod 31 that communicates the alternative and
linear movement
to piston 2 from one side and from the other side the rod 32 communicates the
alternative and
linear movement to the piston 2A. But a mechanical cable- polis system
operated by a
hydraulic system is used to operate this pump as illustrated in Fig 24.
a- In addition the following have to be in place before starting this example
b- As illustrated In Fig. 24 the cable-polis operating system has to be in
place
before starting said pump, the polis 27 has to be affixed on the outside frame
28,
27
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and the poly 30 has to be affixed on the frame 29 that is affixed on the
bottom
part of the pump itself. Then the cables 25 and 26 will be put in place in a
way
that cable 25 will be connected to the rod 31 of piston 2, through the
connection
33, and the cable 26 will be connected to the rod 32 of piston 2A through the
connection 34. And finally as illustrated in Fig 24, a regular hydraulic
cylinder
22 will provide an alternative and linear movement to the cables 25 and 26
through the piston23 and the connection 24, and in turn, the cables 25 and 26
will provide the needed alternative and linear movement to the pistons 2 and
2A
of the compression chambers I and IA of this pump that is needed to pump
water or oil from any water or oil wells,
c- Once all of the components of the abovementioned example are in place, and
the
Reciprocating double acting pump is installed inside the well 21 and it is
ready
to run. Now this pump is affixed and submerged in the water of the water well
21 where water can enter by gravity through the one way valves 4 and 4A to
chamber 1 and IA during water admission cycles.
d- Then, this pump will function exactly the same way the pump in Fig. 21 and
Fig.
22 did without any exception and as detailed in subsections a, b, c, d, e, f,
g, h, i
and j of section (A). But, the operating system is different where the
hydraulic
piston 23 of the hydraulic cylinder 22 exerts an alternative movement on the
cables 25 and 26 in order to operate the pistons 2 and 2A inside the chambers
1
and lA through the poly 27 of the frame 28, and the poly 30 of the frame 29
and
the rods 31 and 32.
D- Reciprocating double acting linear pump operated with a screw jack
operating
system as described in my Canadian patent no 2473077, this pump is used to
pump
underground water from water wells or crude oil from oil wells regardless of
the
depth of these wells.
This example has the same Reciprocating double acting linear pump too as
described in the
above mentioned subsections a, b, c, d, e, f, g, h, i and j, of section (A)
with only exception like
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in section (C) where the brace 3 is replaced by the rod 31 that communicates
the alternative
and linear movement to piston 2 from one side and from the other side the rod
32
communicates the alternative and linear movement to the piston 2A. But a screw
jack
operating system as described in my Canadian patent no 2473077, is used to
operate this pump
as illustrated in Fig 25.
a- In addition the following have to be in place before starting this example.
b- As illustrated In Fig. 25 this example has all of the components of example
(C),
but the hydraulic piston 22, that communicated the alternative and linear
movement to the pistons 2 and 2A, is replaced by a screw jack operating system
as described in my Canadian patent no 2473077
c- Once all of the components of the abovementioned example are in place, this
pump will run exactly the way the pump of example (C) did in the above
mentioned description for Fig 24 but with the screw 36 of the screw jack
device
35 of my Canadian patent no 2473077.
d- Said screw jack device 35 is a very useful device specifically when said
pump is
used to pump crude oil from oil wells located at very deep depth where we need
a powerful device to operate this pump with the use of smaller torque in order
to
overcome the force created by the hydrostatic pressure that is created by the
column of water or crude oil on the surface of all the pistons that are
pumping
water or crude oil.
e- The following formula shows how a little torque can operate this pump:
(The total force to overcome expressed in Newton (Time)(x) the pitch of the
screw of
the screw jack expressed in meters) (Divided by)(/) (2 x pi 3.1416).
f- And the following is an example of a study of the torque needed to operate
the
screw of the screw jack of the reciprocating double acting pump the subject of
the present invention.
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g- If the discharge pressure is about 70kg/cm2 (Head of about 700m above the
used
pump), and the total surface of the pistons is 1000 cm2, and the pitch of the
screw of the screw jack is 0.008 m, and the run between the beginning and the
end of the discharge cycle is: 1 m.
h- Hence, the total force to overcome from the beginning to the end of the
discharge is:
i- (7 kgs/cm) x 1000 cm2 x ION = 35,000 N.
j- Then the torque needed for every screw pitch is:
k- (35,000 N x 0,008 m) / (2 x 3.1416) = 45 mN.
1- So, the abovementioned result explains how small the needed torque for the
screw jack to operate that means that this double acting pump is the solution
for
the future pumps that can replace especially the actually used oil pumps in
the oil
domain.
The advantage of using the reciprocating mono or double acting pump the
subject of the
present invention, is that this pump is very effective for the irrigation, and
especially when it
is used to pump oil from oil wells specifically from the very deep ones, where
conventional
cable pumps are used actually and wasting a lot of energy, because the time
needed for the
pistons to go back to the pumping position in conventional cable pumps of the
prior art is not
productive, while it is productive in these cable pumps the subject of the
present invention
that helps to conserve a tremendous amount of energy.
It should be understood of course, that the foregoing disclosure relates to
only a preferred
embodiment of the invention. This disclosure is intended to cover all changes,
and
modifications of the example of the invention herein chosen for the purposes
of the
disclosure, which do not constitute departures from the spirit and scope of
the invention.
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