US20050169776A1

US20050169776A1 - Hydraulic gravity ram pump

Info

Publication number: US20050169776A1
Application number: US10/765,979
Authority: US
Inventors: Richard McNichol
Original assignee: Individual
Current assignee: Individual
Priority date: 2004-01-29
Filing date: 2004-01-29
Publication date: 2005-08-04
Also published as: ATE451551T1; HK1098186A1; CA2554856A1; EP1714031A4; CA2554856C; RU2006130682A; AU2011201523B2; EP1714031B1; AU2005207990B2; JP2007519849A; US8932030B2; US7967578B2; US20070172364A1; EP1714031A1; US20110255997A1; RU2362050C2; MXPA06008420A; US20150125315A1; AU2011201523A1; WO2005073555A1

Abstract

A piston type pumping apparatus comprises a vertically oriented cylinder having a top and a bottom with a first passageway for liquid in the cylinder adjacent to the top thereof. There is a second passageway for liquid in the cylinder adjacent to the bottom thereof A piston is reciprocatingly mounted within the cylinder. A hollow piston rod is connected to the piston and extends slidably and sealingly through the bottom of the cylinder. There is a reload chamber below the cylinder, the piston rod extending slidably and sealingly into the reload chamber and having a third passageway for liquid communicating with the reload chamber. The piston rod has a smaller cross-sectional area within the reload chamber than the piston, whereby liquid in the cylinder acting downwardly on the piston exerts a greater force on the piston than liquid in the reload chamber acting against the piston rod. There is a first one-way valve located in the third passageway which permits liquid to flow from the reload chamber into the piston rod and prevents liquid from flowing from the piston rod into the reload chamber. A fourth passageway for liquid extends from the reload chamber to a source of liquid to be pumped. A second one-way valve in the fourth passageway permits liquid to flow from the source of liquid into the reload chamber and prevents liquid from flowing from the reload chamber towards the source of liquid. There is means for storing pressurized liquid connected to the second passageway for storing pressurized liquid displaced below the piston, as the piston moves downwardly, and to assist in raising the piston and, accordingly, liquid contained within the piston rod, to pump liquid upwardly and through the first passageway.

Description

BACKGROUND OF THE INVENTION

This invention relates to pumps, and in particular to piston type pumps for pumping liquids to significantly higher elevations and pumps having energy recovery means.
Pumping liquids against substantial hydraulic heads is a problem encountered in pumping out mines, deep wells, and similar applications such as pumping water back up, over a hydro dam during low energy usage periods, for subsequent recovery during high energy usage periods, and for use in run-of-the-river hydro power applications utilizing the potential energy of water in a standing column.
A number of earlier patents attempt to provide devices which utilize a piston type pump where energy is recovered from a column of liquid acting downwardly on the piston, as the piston moves downwardly, in order to assist in subsequently raising the piston together with a volume of liquid to be pumped upwardly. An example of such an earlier patent is U.S. Pat. No. 6,193,476 to Sweeney. However such earlier devices have not been efficient enough to justify their commercial usage. For example, in the Sweeney patent, the efficiency of the apparatus is significantly reduced due to the fact that the upper piston 38 has the same cross-sectional area as lower piston 43. Thus the pressure of liquid acting upwardly on the lower piston 43 inhibits downward movement of the upper piston 38 under the weight of the liquid in the cylinder above.
It is an object to the invention to provide an improved pumping apparatus capable of pumping liquids against significant hydraulic heads, such as encountered in deep wells or in pumping out mines, without requiring pumps with high output heads.
It is a further object of the invention to provide an improved piston type pumping apparatus with provision for energy recovery, having significantly improved efficiency compared with prior art devices of the general type as well as the ability to use the potential energy of a standing column.
It is still further object of the invention to provide an improved piston type pumping apparatus which is simple and rugged in construction, and efficient to operate and install.

SUMMARY OF THE INVENTION

According to the invention there is provided a piston type pumping apparatus, comprising a vertically oriented cylinder having a top and a bottom with a first passageway for liquid in the cylinder adjacent to the top thereof. There is a second passageway for liquid in the cylinder adjacent to the bottom thereof. A piston is reciprocatingly mounted within the cylinder. The piston has an area against which pressure acts in the direction of movement of the piston. A hollow piston rod is connected to the piston and extends slidably and sealingly through an aperture in the bottom of the cylinder. There is a reload chamber below the cylinder, the piston rod extending slidably and sealingly into the reload chamber and having a third passageway for liquid communicating with the reload chamber. The piston rod has a smaller area within the reload chamber upon which pressurized fluid in the reload chamber acts in a direction of movement of the piston and piston rod, compared to the area of the piston, whereby liquid in the cylinder acting downwardly on the piston exerts a greater force on the piston than liquid in the reload chamber acting against the piston rod. There is a first one-way valve located in the third passageway which permits liquid to flow from the reload chamber into the piston rod and prevents liquid from flowing from the piston rod into the reload chamber. A fourth passageway for liquid extends from the reload chamber to a source of liquid to be pumped. A second one-way valve in the fourth passageway permits liquid to flow from the source of liquid into the reload chamber and prevents liquid from flowing from the reload chamber towards the source of liquid. There is means for storing pressurized liquid connected to the second passageway for storing pressurized liquid displaced from below the piston, as the piston moves downwardly, and to assist in raising the piston and, accordingly, liquid contained within the piston rod, to pump liquid upwardly and through the first passageway.
For example, the means for storing may include a pressurized body of liquid.
There may be a pump connected to the body of liquid for pumping liquid into the cylinder below the piston to raise the piston.
In one example the pump is a piston pump. The body of liquid may be a vertical column of liquid.
In another example, the pump may be a rotary pump and the means for storing may include a receiver for pressurized liquid connected to the pump.
The invention offers significant advantages compared with conventional pumps for deep wells, pumping out mines and other applications for pumping liquids up relatively high hydraulic heads, such as energy recovery at hydro dams. It allows the use of a pump which requires far less energy input to pump liquids up significant vertical distances because it converts the potential energy of the standing column into kinetic energy. At the same time, it overcomes disadvantages associated with prior art pumps of the general type by increasing its efficiency significantly by comparison. Thus the invention is attractive for commercial applications where prior art devices have not proven to be viable.

BRIEF DESCRIPTION OF THE DRAWINGS

In the drawings:
FIG. 1 is a simplified elevational view, partly in section, of a pumping apparatus according to an embodiment of the invention;
FIG. 2 is a simplified elevational view, partly in section, of the upper fragment of an alternative embodiment employing a centrifugal pump;
FIG. 3 is a graph of the efficiency of the pressure head concept of the pump;
FIG. 4 is a sectional view of the embodiment of FIG. 1 showing the Force Balance in the pump;
FIGS. 5 a and 5 b are simplified sectional views showing Pressure Head Concept of a pump and the Power Cylinder Concept of the pump.

DETAILED DESCRIPTIONS OF THE PREFERRED EMBODIMENTS

Referring to the drawings, and first to FIG. 1, this shows a piston type pumping apparatus 20 according to an embodiment of the invention. The apparatus is intended to pump liquids, typically water, up relatively great vertical distances, such as from the bottom of a mine to the surface as exemplified by the distance between points 22 and 24. The system includes a vertically oriented first transfer cylinder 26 having a top 28, adjacent point 24, and a bottom 30. There is a first passageway 32 for liquid adjacent the top where liquid is discharged from the cylinder. There is a second passageway 34 near the bottom of the cylinder which allows liquid to enter or exit the cylinder.
A transfer piston 40 is reciprocatingly mounted within the cylinder and is connected to a vertically oriented, hollow piston rod 42 which extends slidably and sealingly through aperture 44 in the bottom of the cylinder. The piston 40 has an area 29 at the top thereof against which pressurized fluid in the cylinder acts. The passageway 32 is above or adjacent to the uppermost position of the piston and the passageway 34 is below its lowermost position. It should be understood that FIG. 1 is a simplified drawing of the invention and seals and other conventional elements which would be apparent to someone skilled in the art are omitted. These components would be similar to those disclosed in U.S. Pat. No. 6,913,476 which is incorporated herein by reference.
There is a first one-way valve 41 at the bottom of the piston rod 42 which includes a valve member 43 and a valve seat 45 which extends about a third passageway 47 in bottom 49 of the piston rod. This one-way valve allows liquid to flow into the piston rod, but prevents a reverse flow out the bottom of the piston rod.
There is a reload chamber 46 below the cylinder 26 which is sealed, apart from aperture 48 at top 50 thereof, which slidably and sealingly receives piston rod 42, and fourth passageway 52 at bottom 54 thereof. The piston rod acts as a piston within the reload chamber. There could be a piston member on the end of the rod within the reload chamber and the term “piston rod” includes this possibility. A second one-way valve 56 is located at the passageway 52 and includes a valve member in the form of ball 58 and a valve seat 60 adjacent to the bottom of the reload chamber. There is an annular stop 62 which limits upward movement of the ball. This one-way valve allows liquid to flow from a source chamber 70 into the reload chamber 46, but prevents liquid from flowing from the reload chamber towards the chamber 70. Chamber 70 contains liquid to be pumped out of passageway 32 at top of the cylinder.
The piston 40 has a diameter D1 which is substantially greater than diameter D2 of the piston rod and, accordingly, the piston rod, acting as a piston in the reload chamber, has a significantly smaller area upon which pressurized liquid acts, in the direction of movement of the piston rod and piston 40, within the reload chamber 46 compared to the cross-sectional area of the piston 40 and the interior of cylinder 26. For example, in one embodiment the piston is 3″ in diameter, while the piston rod 42 is 1″ in diameter. Therefore liquid in the cylinder at a given pressure exerts a much greater force on the piston and piston rod compared to the force exerted upwardly on the piston rod and piston by a similar pressure of liquid in reload chamber 70.
There is means 80 for storing pressurized liquid 82 connected to the second passageway 34. This means 80 stores pressurized liquid recovered from chamber 90 in the cylinder 26 below the piston 40. In this particular embodiment the means includes a column of liquid 92 extending from passageway 34 to a point 94 at the top of the column. The column in this example is formed by an annular jacket 96 extending about the cylinder 26 and a conduit 98 extending to discharge end 100 of a second, power cylinder 102. The column can be pressurized by a remotely located power cylinder or by using a body of liquid (water), located at a higher elevation, as a pressure head.
The cylinder 102 has a piston 104 reciprocatingly mounted therein. The liquid 82 occupies chamber 106 on side 108 of the piston which faces discharge end 100 of the cylinder. Chamber 110 on the opposite side of the piston is vented to atmosphere through passageway 112. There is a piston rod 114 connected to the piston 104 to drive the piston towards the discharge end and thereby discharge liquid 82 from the cylinder.
In operation, the cylinder 26 is filled with liquid, typically water, above the piston 40. Likewise chamber 90 is filled with water along with the jacket 96 and chamber 106 of the second cylinder 102. Similarly piston rod 42 is filled with water or other liquid along with the reload chamber 46 and the source chamber 70. The piston is in the lowermost position as shown in FIG. 1. This is required to prime the pump.
The piston rod 114 is then moved to the left, from the point of view of FIG. 1, typically by a motor or engine with a crank mechanism or a pneumatic or hydraulic device, although this could be done in other ways. This displaces liquid 82 from the cylinder 102 downwardly through the column 92, through the second passageway 34 into the chamber 90 where it acts upwardly against the bottom of piston 40 and pushes the piston upwards in the cylinder 26.
The piston rod 42 is pushed upwardly along with the piston and thereby reduces pressure in reload chamber 46, since the volume occupied by the piston rod in the reload chamber is reduced as the piston rod moves upwardly. One-way valve 41 prevents liquid from flowing from the piston rod into the reload chamber, but the reduced pressure within the reload chamber causes ball 58 to rise off of its seat 60, such that liquid flows from chamber 70 into the reload chamber.
When piston 104 of the cylinder 102 approaches the end of its travel adjacent discharge end 100, and piston 40 approaches its uppermost position towards top 28 of the cylinder 26, liquid is discharged from the passageway 32. When the piston 104 has reached its limit adjacent discharge end 100, pressure against piston rod 114 is released. The weight of liquid occupying cylinder 26 above the piston 40 acts downwardly on the piston and forces the piston towards its lowermost position shown in FIG. 1. This forces liquid out of chamber 90 and into the chamber 106 of cylinder 102, moving the piston 104 to the right, from the point of view of FIG. 1, so it returns to the original position shown.
At the same time, the piston rod 42 is forced downwardly into the reload chamber 46. This increases pressure in the reload chamber and keeps the ball 58 against valve seat 60 to prevent liquid from flowing back into the source chamber 70 through the passageway 52. The liquid in the reload chamber is thus forced upwardly into the piston rod 42 by raising valve member 43 off of valve seat 45. In this way, a portion of the liquid in reload chamber 46, which had flowed into the reload chamber from the source chamber as the piston was previously raised, moves from the reload chamber into the piston rod and refills the cylinder 26 above the piston 40 as the piston moves downwardly towards its lowermost position shown in FIG. 1.
The piston 104 in the cylinder 102 is then pushed again to the left, from the point of view of FIG. 1, and again raises the piston 40. A volume of liquid equal to the volume of liquid which moved into the piston rod 42 from the reload chamber 46, as the piston 40 previously moved downwards, is then discharged from passageway 32 as the piston 40 approaches its uppermost position and piston 102 approaches its position closest to the discharge end 100 of cylinder 102.
The cycles are then continued and, as may be readily understood, each time the piston 40 moves down and back up, it pumps a volume of liquid from the reload chamber 46, and ultimately from source chamber 70, equal to the difference in volume occupied by the piston rod 44 within the reload chamber 46, when the piston 40 is in the lowermost position as shown in FIG. 1, less the volume it occupies within the reload chamber (if any) when the piston 40 has reached its uppermost position. The travel of the piston 40 is adjusted so that the piston rod remains within the aperture 48 at the uppermost limit of travel of the piston 40 and piston rod.
The pump apparatus described above is capable of pumping liquid from point 22 to point 32 as described above. Thus the apparatus is capable of pumping liquid against a significant hydraulic head, such as experienced in pumping water from the bottom of a mine, without requiring a pump with a high hydraulic head output. This is because liquid in column 92 acts upwardly against the bottom of the piston 40 and assists the movement of the piston 104 towards the left, from the point of view of FIG. 1. When the piston 40 is moved downwardly by the weight of liquid in cylinder 26 above the piston, it moves the liquid in chamber 90 upwardly, increasing its hydraulic head and building up its potential energy. Thus a large portion of the energy lost as the piston 40 moved downwardly is recovered in potential energy represented by the liquid in column 92 extending to cylinder 102.
Thus it may be seen that the cylinder 102 should be placed as high as possible for the maximum recovery of the energy. It should be understood that the position of cylinder 102 could be different than shown in FIG. 1. It could be, for example, oriented vertically. The terms “left” and “right” used above in relation to the cylinder, piston and piston rod are to assist in understanding the invention and are not intended to cover all possible orientations of the invention.
FIG. 2 shows a pumping apparatus 20.1 which is generally similar to the apparatus shown in FIG. 1 with like parts having like numbers with the addition of “0.1”. It is herein described only with respect to the differences between the two embodiments. Only the upper portion of the apparatus is shown, the reload chamber and source chamber being omitted because they are identical to the first embodiment. In this example passageway 34.1 is fitted with a one-way valve 120 which permits liquid to flow from chamber 90.1 into conduit 122, but prevents liquid from flowing in the opposite direction. The conduit 122 is connected to a receiver 124 which may be similar in structure to a hydraulic accumulator, for example, and is capable of storing pressurized hydraulic fluid. When the piston 40.1 is moved downwardly by the liquid in cylinder 26.1, it is forced into the receiver 124.
There is a hydraulic conduit 126 which connects the receiver to a centrifugal pump 128 which is connected to passageway 130 in the cylinder 26.1 below the piston 40.1 via a conduit 132. After the piston reaches its bottommost position, as shown in FIG. 2, pump 128 is started to pump liquid from the receiver 124 into the chamber 90.1 to lift the piston 40.1. The fact that the liquid in the receiver 124 was pressurized during the previous downward movement of piston 40.1 reduces the work required from pump 128 to assist in raising the piston. Thus this apparatus operates in a manner analogous to the embodiment of FIG. 1, but uses the receiver to store pressurized hydraulic fluid instead of utilizing a physical, vertical hydraulic head as in the previous embodiment. Furthermore a centrifugal pump 128 is employed instead of the piston pump comprising cylinder 102 and piston 104 of the previous embodiment. Otherwise this apparatus operates in a similar manner.

ANALYSIS OF PRESSURES AND FORCE BALANCE

Referring to FIGS. 1 through 5:

- A₁is the area of the top 29 of the transfer piston 40 which is the area of the transfer cylinder 26
- A₂is the area of the bottom of the piston rod 42
- A₁-A₂is the area of the transfer piston in contact with the power fluid
- S is the stroke length
- P₁is the pressure of the standing column
- P₂is the pressure of the working fluid during the power stroke
- P₃is the available head of the fluid to be pumped
- P₄is the pressure in the transfer chamber
- P₅is the pressure of the power fluid during the recovery stroke
- P_cis the pressure created in the power cylinder 102 located at the same level as the standing column discharge 32
- W is the weight of the piston
- R is the resistance created by the seals
- d is the density of water (0.036 lbs/in3)
- A_cis the area of the Power Cylinder
- S_cis the stroke of the Power Cylinder
- H is the height of the standing column of water
- d is the density of water

During the recovery stroke the transfer piston moves down, with valve member 43 open and valve 56 closed.
Downward Forces F _d =P ₁ A ₁ +W
Upward Forces F _u =P ₂(A ₁ −A ₂)+P ₄ A ₂ +R
Net force F=F _d −F _u =P ₁ A ₁ +W−P ₂(A ₁ −A ₂)−P ₄ A ₂ −R
If we assume:

- P₁=45 psig, approximately 100 feet of water, and A₁=8 in²,
  P ₁ A ₁=45×8=360 lbs
a piston weight of 2 lbs (approximately 8 in³of steel)
a seal resistance 20 lbs
P₄=P₁and therefore P₄A₂=P₁A₂
F=P ₁ A ₁ −P ₁ A ₂ −P ₅(A ₁ −A ₂)−R
F=P ₁(A ₁ −A ₂)−P ₅(A ₁ −A ₂)−R=(P ₁ −P ₅)(A ₁ −A ₂)−R
For this to be a net downward force, P₅must be less than P₁. The area that P₁operates on is (A₁−A₂).

During the power stroke the transfer piston moves up and valve member 43 closed.
Downward forces F _d =P ₁ A ₁ +W+R
Upward forces F _u =P ₂(A ₁ −A ₂)+P ₄ A ₂
Net force=F=F _u −F _d =P ₂(A ₁ −A ₂)+P ₄ A ₂ −P ₁ A ₁ −W−R

- P₄=P₃. If we assume P_3<<P ₁or P₂, we can ignore P₄A₂.
- As for the recovery stroke we can ignore W.
  F=P ₂(A₁ −A ₂)−P ₁ A ₁ −R

Efficiency

- Work in during the recovery stroke
- P₅=P₁−P_cwhere P_cis the pressure created in the power cylinder located at the same level as the standing column discharge.
- Work done at the power cylinder W_i=P_cA_cS_c,
- A_cS_cis the volume of power fluid moved per stroke=(A₁−A₂)S W_i=P_c(A₁−A₂)S,
- For an example, P_c=14 psig, A₁=8 in² _{1 A}2=4 in² ₁and S=12 in W₁=14(8−4)12=672 in lbs (56 ft lbs) plus R×S20×12=240 in lbs. A₂/A₁=0.5
- Work in during the Power Stroke
- P₂=P₁+P_c. In order to create an acceleration of “a” times g (32.2 ft/sec²) in the standing column, the net force must be “a” times the weight of the standing column. F=P₂(A₁−A₂)−P₁A₁−R=aHA₁d=aP₁A₁
  (P ₁ +P _c)(A ₁ −A ₂)−P ₁ A ₁ −R=aP ₁ A ₁
  P ₁ A ₁ −P ₁ A ₂ +P _c A ₁ −P _c A ₂ −P ₁ A ₁ −R=aP ₁ A ₁. The bold terms cancel.
  P _c(A ₁ −A ₂)=aP ₁ A ₁ +P ₁ A ₂ +R
  $P_{c} = \frac{P_{1} ({aA}_{1} + A_{2})}{(A_{1} - A_{2})} + \frac{R}{(A_{1} - A_{2})}$
- For a head of 100 feet, P₁=43.3 psig, and a=1 g, R=20 lbs. $P_{c} = \frac{43.3 (1 \times 8 + 4)}{4} + \frac{20}{4} = 130 + 5 = 135 psig$
- Work In at the power cylinder
  W _i =P _c(A ₁ −A ₂)S=135×4×12=6480 in lbs
- Work Output
- The amount of water lifted is SA₂d=12×4×0.036=1.73 lbs it is raised 1200 inches
  W ₀=1/73×1200=2070 in lbs=173 ft lbs
- Efficiency based on A₂/A₁ratio of 0.5
  E=W ₀ /W ₁=2070/(6480+672+240)=28.0%
- By examining the above formula for P_cone can see how changing the acceleration and the ratio of A₂/A₁affects the pressure necessary to drive the pump. For example:
- A₂/A₁=0.8 or in the example A₂would now=6.4 sq. in. and a=0.25 g $\begin{matrix} P_{c} = \frac{P_{1} ({aA}_{1} + A_{2})}{(A_{1} - A_{2})} + \frac{R}{(A_{1} - A_{2})} \\ P_{c} = \frac{43.3 (.25 \times 8 + 6.4)}{1.6} + \frac{20}{1.6} = 227 + 12.5 = 239.5 psig \end{matrix}$
  or using a lower A₂/A₁ratio−say 0.25, now A₂=2 and leaving acceleration at 0.25 g $P_{c} = \frac{P_{1} ({aA}_{1} + A_{2})}{(A_{1} - A_{2})} + \frac{R}{(A_{1} - A_{2})}$ $P_{c} = \frac{43.3 (.25 \times 8 + 2)}{6} + \frac{20}{6} = 28 + 3.33 = 31.33 psig$
  We are now moving a volume of water up 100 feet in our example by adding 31.33 psi (72.37 ft.) of head to the power column.

DYNAMIC ANALYSIS OF THE ORIGINAL CONCEPT

Recovery Stroke

- Continuing with the same example the net force on the Standing Column 26 is:
  F=P _c(A ₁ −A ₂)−R=14(8−4)−20=36 lbs
- The mass of the Standing Column is
  1200×8×0.036=346 lbs.
- The acceleration is
  36/346=0.10 g=3.22 ft/sec²
- The time required to complete the stroke $D = \frac{{at}^{2}}{2} : D = S in feet = 1 foot;$
  t=(2S/a)^0.5=(2/3.22)^0.5=0.79 seconds

Power Stroke

- The acceleration was defined as 1 g or 32.2 ft/sec².
  t=(2/32.2)^0.5=0.25 seconds.
- The complete stroke will take 0.79+0.25=1.03 seconds

The above analysis of pressures and force can be manipulated using different ratios of A₂/A1, P₂/P₁and acceleration “a”.

Attached as FIG. 3 is a performance curve for the pressure head concept showing the efficiency against the ratio A₂/A₁Also included as Table 1 are the calculations from which FIG. 3 is drawn showing the absolute numeric variations as parameters are changed.

TABLE 1


Efficiency vs A2/A1

A2/A1=

P2/P1	0.4	0.5	0.6	0.7	0.8	0.82

1.5	0.0%	0.0%	0.0%	0.0%	0.0%	0.0%
1.8	0.0%	0.0%	0.0%	0.0%	0.0%	0.0%
2.0	41.4%	0.0%	0.0%	0.0%	0.0%	0.0%
2.5	31.6%	45.7%	0.0%	0.0%	0.0%	0.0%
3.0	25.5%	37.2%	53.3%	0.0%	0.0%	0.0%
4.0	18.5%	27.1%	39.3%	59.1%	0.0%	0.0%
5.0	14.5%	21.3%	31.2%	47.1%	0.0%	0.0%
7.5	9.4%	13.9%	20.5%	31.3%	53.7%	61.1%
10	6.9%	10.3%	15.3%	23.5%	40.2%	45.8%
Optimum	26.6%	315.%	36.0%	40.7%	46.3%	47.5%
P5/P1, req	0.39	0.31	0.185	0.05	0.05	0.05
Rec Acc ft/sec2	8.04	8.01	8.04	7.21	4.21	3.61
P2/P1 opt	2.9	3.48	4.35	5.79	8.69	9.65

For the pressure head concept, the curves demonstrate that a pump could approach an efficiency of up to 61% if used in applications where a very high pressure head is available and the power water can be discharged at a very low level, both compared to the height of the standing column. Efficient pump designs have a high A₂/A₁ratio indicating that the volume of water discharged from the standing column is greater than the volume of water used on the power side of the transfer piston. This feature indicates that the pump may be attractive in lifting water from a well or de-watering a mine as long as there is a convenient source of suitable power water; i.e. compatible with the water to be lifted and having a very high head. As previously discussed, a pressure head pump could be attractive in some run-of-the-river hydro applications if a suitable source of power water is convenient.
For the power cylinder concept, the curves indicate that the higher the A₂/A₁ratio the more efficient the pump, and the lower the accelerations the more efficient the pump.
Efficient pressure head concept pumps move a greater volume of process water per stroke than the volume of power water required. This again is a direct result of the high ratios of A₂/A₁This means that the power water could be released to join the process water and still allow effective pumping to occur. Conversely, pumps with low ratios of A₂/A₁but with a large amount of power water and a lower head can move smaller amounts of process water up greater heights. They will expend more power water than the process water they move. This process is similar to the classic hydraulic ram principle where a large amount of fluid at a low pressure head is used to transfer a small amount of fluid up a higher elevation.
A different embodiment of the pump utilizes a bladder similar to a pressure tank in a water system or a packer similar to a drill hole packer that houses the water in the power cylinder that is pressurized by air or hydraulic pressure and then the pressure lowered and again repressurized. This allows the use of the pump without expending the power fluid.

ANALYSIS

FIG. 5 shows the two main embodiments of the pump. FIG. 5A describes the pressure head concept showing how the liquid, generally water, stored at a higher elevation 83 supplies excess pressure for the power stroke 85 and reduced pressure 87 when point 89 is used for the power fluid release. FIG. 5B shows the power cylinder concept where the excess pressure is generated by the power cylinder 102 and the recovery stroke is augmented by the creation of a vacuum when piston 104 is withdrawn from the column of power fluid.
Performance Curves
Pressure Head Concept
Referring to Table 1, the valves were manipulated to calculate the efficiency of various pressure head arrangements. The manipulation required:

setting various ratios of A₂/A₁from 0.4 to 0.82 then, for each of the ratios,
calculating the recovery stroke performance for various ratios of P₅/P₁(the height of the power water release compared to the standing column height),
“optimising” P₅/P₁to obtain a recovery stroke acceleration of 8 ft/sec², if possible,
using the “optimised” results from the recovery stroke calculations as input for the power stroke calculations,
calculating the power stroke performance for various ratios of P₂/P₁(the height of the power water source compared to the standing column height),
“optimising” P₂/P₁was to obtain a power stroke acceleration of 8 ft/sec²,
transferring the calculated efficiencies to another spreadsheet along with the “optimised” P₅/P₁and P₂/P₁ratios and the recovery stroke acceleration,
using the calculated efficiencies to plot a graph of efficiency vs A₂/A₁for the most significant ratios of P₂/P₁.

The results indicated that high ratios of A₂/A₁result in higher efficiency and low acceleration. The results also indicate that a low ratio of P₅/P₁is required to create reasonable recovery stroke acceleration.
Referring to Table 1, performance data for the ratio A₂/A₁=0.82 is shown which indicates that an efficiency of 61% could be achieved if a power stroke acceleration of 8 ft.sec 2 (0.25 g) is considered acceptable. The recovery stroke acceleration will be around 4 ft/sec2 with this design.
What is not immediately apparent is that when the A₂/A₁ratio is high, the amount of power water released per stroke is much less than the amount of process water lifted per stroke. The amount of process water lifted per stroke is A₂S and the amount of power water released per stroke is (A₂−A₁)S.
When A₂/A₁=0.8:

- (A₂−A₁)=A₁−0.8A₁=0.2A₁
- and the amount of power water released per stroke is
  (A ₂ −A ₁)S=0.2 A ₁ S
- and A₂=0.8A₁:
- therefore the amount of process water lifted is
- A₂S=0.8 A₁S
- or four times the amount of power water released.
  This means that the power water could be released into the process water and the pump will still pump a net of (0.8−0.2)A₁S=0.6A₁S per stroke.
  Power Cylinder Concept

Values were manipulated to calculate the efficiency for various power cylinder arrangements. The manipulation required is:

setting various ratios of A₂/A₁; from 0.4 to 0.82, then, for each of the ratios,
setting the pressure in the power cylinder (P_c) during the recovery stroke,
calculating the recovery stroke performance for various ratios of H_p/H₁(the height of the pump compared to the height of the standing column),
“optimising” H_p/H₁to obtain a recovery stroke acceleration of 8 ft/sec², if possible,
using the “optimised” results from the recovery stroke calculations as input for the power stroke calculations,
calculating the power stroke performance for various ratios of P₂/P₁,
“optimising” P₂/P₁to obtain a power stroke acceleration of 8 ft /sec²,
transferring the calculated efficiencies to another spreadsheet along with the “optimised” H_p/H₁and P₂/P₁ratios and the recovery stroke acceleration,
using the calculated efficiencies to plot a graph of efficiency vs A₂/A₁for the most significant ratios of P₂/P₁,

The results indicate that high ratios of A₂/A₁result in higher efficiency and lower ratios allow moving fluid to higher heads but using more process water or a larger power column if contained in a bladder or packer.

Attractive Applications

For the concept pump to be reasonably efficient, the ratio A₂/A₁must be high. For this sort of pump to have a reasonable recovery stroke acceleration the power water in a pressure head style pump must be released very low relative to the height of the standing column. For this sort of pump to have a reasonable power stroke acceleration the power column must be very tall relative to the standing column. These features indicate that the pump would be attractive in applications where there is a source of power water at an elevation much higher than the standing column height. It must also be possible to release the power water at a very low elevation relative to the height of the power column in a pressure head style pump.

the previously discussed run-of-the-river hydro booster application could fit these requirements, Analysis shows that this application allows the recovery of more than 55% of the energy of a high elevation tributary if it is channeled to a pressure head style pump placed at the bottom. The pump lifts almost five times as much water as is used to power the pump if the water is lifted 1/10^thof the height of the power head. The water is then recycled through the turbine at the bottom.
using the pump to de-water a mine could also be attractive,
raising water from a well could be attractive.
raising water to a reservoir or to a higher elevation (pressure) could also be attractive

Claims

1. A piston type pumping apparatus, comprising:

a vertically oriented cylinder having a top and a bottom;

a first passageway for liquid in the cylinder adjacent to the top thereof;

a second passageway for liquid in the cylinder adjacent to the bottom thereof;

a piston reciprocatingly mounted within the cylinder and having an area against which pressurized fluid acts in the direction of movement of the piston;

a hollow piston rod connected to the piston and extending slidably and sealingly through an aperture in the bottom of the cylinder;

a reload chamber below the cylinder, the piston rod extending slidably and sealingly into the reload chamber and having a third passageway for liquid communicating with the reload chamber, the piston rod having a smaller area within the reload chamber upon which pressurized fluid in the reload chamber acts in a direction of movement of the piston and piston rod compared to said area of the piston, whereby liquid in the cylinder acting downwardly on the piston exerts a greater force on the piston than liquid in the reload chamber acting against the piston rod;

a first one-way valve located in the third passageway which permits liquid to flow from the reload chamber into the piston rod and prevents liquid from flowing from the piston rod into the reload chamber;

a fourth passageway for liquid extending from the reload chamber to a source of liquid to be pumped;

a second one-way valve in the fourth passageway which permits liquid to flow from the source of liquid into the reload chamber and prevents liquid from flowing from the reload chamber towards the source of liquid; and

means for storing pressurized liquid connected to the second passageway for storing pressurized liquid displaced below the piston, as the piston moves downwardly, and to assist in raising the piston and, accordingly, liquid contained within the piston rod, to pump liquid upwardly and through the first passageway.

2. The apparatus of claim 1 wherein the means for storing pressurized liquid includes a body of liquid.

3. The apparatus of claim 2, including a pump connected to the body of liquid for pumping liquid into the cylinder below the piston to raise the piston.

4. The apparatus of claim 3, wherein the pump is a piston type pump.

5. The apparatus as claimed in claim 4, wherein the pump is above the second passageway.

6. The apparatus of claim 3, wherein the pump is a centrifugal pump.

7. The apparatus of claim 6, including a sixth passageway for liquid adjacent to the bottom of the cylinder, a first conduit connecting the sixth passageway to the pump and a second conduit connecting the second passageway to the body of liquid.

8. The apparatus of claim 7, wherein the body of liquid is a receiver.

9. The apparatus of claim 8, including a pressure release valve adjacent to the second passageway in the second conduit.