This application relates to motor driven metering pumps, and specifically to an improved motor driven duplex liquid end metering pump.
Motor driven chemical metering pumps or proportional pumps are commonly utilized to pump various liquids. They have the ability to vary their volumetric liquid displacement during their normal operation. This is typically achieved with their ability to change their discharge stroke length and or motor speed to vary the strokes per minute during their operation. This changes their liquid volumetric displacement. There are commercially available pumps that change their flow delivery by changing their motor speed or stroke length only.
These motors typically have one or more displacers commonly of a plunger, diaphragm or tube design. Two displacer pumps are commonly termed as duplex metering pumps. Duplex metering pumps would typically have each of the two separate displacers held in its separate liquid end pump housings. A side view of a duplex metering pump would show the pump housings parallel aligned side to side, either horizontally or vertically. Each pump housing has its own pump gear box or transmissions housing or main pump housing that are rigidly connected side to side. Both would typically have four liquid process connections. That is one discharge and one suction on each separate liquid end pump housing.
Conventional duplex pump metering pumps typically have four check valve assemblies. These valves are external, but rigidly connected to each liquid end. This prior art design has the pumped liquid flowing through all four valves. This requires more complex piping to integrate the two suction and two discharge check valves.
It therefore, would be desirable to construct a duplex motor driven duplex metering pump having a compact design of a simplex pump configuration having one liquid end with one diaphragm that is mounted at one position to the main pump housing. It would be advantageous to integrate the check valves into a single duplex liquid end as opposed to being external to the liquid ends. This would allow for a duplex metering pump to be connected to a process with a single pipe connection at the suction and the discharge sides of the pump. These process connections would be incorporated into the body of the single duplex liquid end.
This allows the liquid pumped through the pump to flow through housing and not through the check valves. This is advantageous, because the valves can be smaller in size for a given flow capacity of the duplex metering pump. This is due to the check valve body does not have to be large enough to have liquid flow around the valve's internal geometry.
Typically these duplex motor driven metering pumps will have a transmission housing or a pump housing. Within the housing there will be some form of one or two eccentric members, such as a cam or other form of mechanics. These mechanics convert rotary motion to rectilinear reciprocating motion. Typically there is a gear set within the pump's transmission for motor speed reduction and torque multiplication. Gears require some form of lubrication and the state of art metering pumps use gear oil or grease, depending on its design. The pumps will have various shafts that are reciprocating and rotating and where they protrude through the transmission housing, wiping seals are used to contain the lubricant. It would desirable to have a metering pump that does not utilize gearing. Gears within the pump housing add expenses to the pump's manufacturing costs. During the normal operation of the prior art motor driven pumps with gearing, the required gear lubricant will be need to be changed. In addition to contain the lubricant in the pump housing for the current state of art metering pumps over time the seals around the pump's shafts need to be replaced.
It would be desirable to design a metering pump that does not require a lubricant or wiping seals. It would be desirable to have all reciprocating and rotating shafts within a pump design that are supported and aligned with self-lubricated bearings that do require external lubrication.
This class of pumps utilize current state of art motors including digital type of motors. They typically are so designed to utilize motor control technology that allows for the drive motor to vary its speed to change the pump's momentary liquid flow creation. There are manufactures with a commercially available pumps that utilizes a digitally driven synchronous motors. For example, U.S. Pat. No. 6,948,914 and U.S. Pat. No. 7,118,347 disclose a digital impulse control logic. This digital impulse controls the velocity of the pump's single diaphragm to create a desired liquid delivery velocity. Its digital control electronics utilizes an impulse modulation that turns its motor on and off for prescribed time intervals. It would be desirable to have a metering pump that utilizes a digital motor, but only requires standard available state of art speed control to operate for speed modulation.
There are various patents that utilize a stepper motor or motors. For example, U.S. Pat. No. 6,293,756 is a pump system with four plungers that is designed for the needs of High Performance Liquid Chromatography (HPLC) applications. The concept is to control a desired flow rate based on an input of a pressure variable to the pump's controller. The basic design concept is four independent plunger pumps driven by four independent stepper motors. In the patent description it describes each motor driving a wheel cam via a 4:1 gear reducer set. The liquid flow of each independent pump is combined to create a single liquid continuous flow rate. The controller independently controls each motor speed to get the desired combined liquid flow rate relative to pressure.
It would be advantageous to divide the work of the pump's momentary liquid displacement and replenish over multiple synchronized stepper motors or other types of synchronous motors. These motors are either connected to the pump's eccentric member via gearing or directly coupled without gearing depending on the design. The momentary liquid displacement is equally divided to two motors driving one displacer that is pumping the liquid at any given moment in the pump's operation. This is opposed to U.S. Pat. No. 6,293,756 that has a stepper motor connected to each of its single displacer, described as plungers.
Metering pumps of this class typically have defined batch flow rate delivery. Each displacer displaces a given batch volume of liquid for each of its displacement cycles. The current state of art metering pumps typically have the liquid being pumped going from zero velocity at the beginning of a batch to peak velocity and back to zero at the end of the batch. This causes negative pulsating pressures being acted upon by the pump's liquid flow rates. These pressure variations are transferred to the liquid up-stream and down-stream of the liquid end of the pump. These sudden changes in liquid velocity creates mass acceleration problems being transferred to the pumped liquid. This causes undesirable pressure variations that in turn creates what is commonly called water hammer or cavitation. This is due to the sudden stopping of the liquid on the suction and discharge side of the pump at an end of a batch cycle. This causes wide pressure variations to be established, including negative pressures at the suction and discharge sides of the pump.
These pumps requires check valves to operate. These check valves require sufficient substantially continuous differential pressure across them to operate properly. Widely varying differential pressure at the check valves cause its ball or other geometry in the check valves to not properly seat. That is that the sealing geometry can float or bounce if the proper differential pressure is not maintained across the pump's check valves. It would be advantageous to design a duplex metering pump that better sustains a more constant differential pressure across its check valves for better pump performance.
These wide pressure variations, as described above are typically mitigated by the installation of a back pressure valve on the discharge side of the pump. It helps assure that there is sufficient back pressure for the check valve on the pump to properly seat. It further mitigates the magnitude of the pressure variations on the discharge side of the pump. It does not always solve the problem. It would be desirable to have a duplex metering pump that mitigates this pulsating flow rate and wide pressure variations being imposed on the pumped liquid. That is the batch flow delivery remains, but the time between batches is sufficiently small to mitigate the wider pressure variations being created by a duplex metering pump.
In addition, when the liquid displacement velocity of one batch ends, the liquid velocity of the next beginning is substantially the same. The velocity of the liquid being pumped virtually never goes to zero across the liquid end of the pump. It would be advantageous to have a virtually continuous liquid flow across a duplex metering pump's liquid end. The liquid that is pumped across the pump's liquid end does not go to zero velocity which minimizes the wider pressure variations at the suction and discharge sides of the duplex metering pump. Each liquid batch stream is commingled one after the other with virtually equal velocities and no dwell. It would be desirable to not require a back pressure valve to be installed on the liquid discharge side of a duplex metering pump on many process applications.
These negative wide pressure variations and pulsating flow, as described above are typically also mitigated by the installation of a pulsation dampener. The dampener is installed in the discharge piping of the pump. The dampener allows the discharge piping to be quickly expanded volumetrically during a liquid discharge event by the pump. The pulsation dampener then reduces its volume to force the pumped liquid to the discharge side of the pump when the pump is between a liquid discharge events. The pulsation dampener reduces the magnitude of the pulsating flow rate delivery. It would be advantageous to design a duplex metering pump that does not typically require a pulsation dampener to create substantially low pulsating liquid flow delivery.
As described above conventional pumps require proper sustained differential pressure across them to allow their check valves to properly operate. A properly operating check valve requires a limited time period to adjust from opened to closed. During short time period, the suction side and the discharge liquids are comingled within the liquid in the cavity or cavities of the pump. Yet that time interval is sufficiently short for pump to operate properly. When this time period is sufficiently short, the pump will create repeatable accurate liquid flow rate creation. These check valves can have poor seating performance when this time interval becomes too long. This can happen when the pump is operating at very low operational speeds.
The typical state of art metering pumps at low liquid displacement velocities can have operating issues due to their check valves not seating properly. This is due to the time period being too long for the pump's displacers to change from at state of open to closed or closed to open. The check valve's sealing elements will have too long of a time period with the elements floating. This allows the differential pressure across the liquid end of the pump to be equalized over the time period. This effects the accuracy and the ability of the pump to operate. This in practical terms reduces the achievable low end liquid displacement by many state of art metering pumps.
It would be advantageous for the pump to have speed modulation at the low end of its pump capacities. This would quickly increase the liquid displacement velocity just before and after the cross over position for a change is the reciprocating direction of the displacers. Then return to a low displacer velocity as chosen for the application between the cross over reciprocating change in direction positions.
Metering pumps are positive displacement pumps and therefore it is of common industry practice to utilize a safety relief valve (“SRV”) to protect the pumping system from unsafe over pressurization. This SRV is typically installed inline in the discharge piping of the pumping system. The valve is typically so installed to allow for the liquid to be piped back to the suction side of the pump or back to the source of the liquid being pumped. That is this valve will open to allow the over pressurized pumped liquid to safely be relieved. This protects the pumping system from self-destruction. Typically this over pressure condition happens when you have a blocked or partially blocked discharge condition in the discharge piping. The state of art SRV is sized for the maximum liquid flow capacity for any given state of art metering pump. Typically the SRV's valve body size and capacity is determined by the manufactures recommended discharge pipe size specifications. These pipe sizes are sufficiently large to minimize the liquid velocities to in turn minimize liquid mass accelerations of the pumped liquid. A drawback of sizing the SRV based on discharge pipe size is that the SRV can get quite large and this adds costs to the overall pumping system.
As described metering pumps of this type cause liquid displacement by reciprocating a displacer and creating and collapsing a cavity or cavities. By creating a cavity, the liquid to be pumped is displaced into the created cavity and by collapsing the cavity the liquid is displaced out of the pump. The process is repeated and each occurrence is termed a stroke. A duplex pump would have two discharge and two suction events per stroke. It is measured in strokes per minute (“SPM”). It would be advantageous to have an integral safety equalization valve (SEV) or SRV that is integrated into the single duplex liquid end.
A drawback of locating the SRV in the discharge piping is that it is sized based on the pump's total capacity that is made up of the maximum sum of SPM. It would be advantageous for the SRV design capacity and physical size being based on the liquid volume of one stroke. It would therefore be advantageous to directly attach the SRV or SEV on the single liquid end. This would allow a much smaller SRV to accomplish the same over pressurization protection allow for a more advantageous discharge piping from a duplex metering pump. This is because the pumped liquid is not piped back to the suction side of the pump or to the source of the liquid, such as a tank.
The embodiments of the present invention address and overcome drawbacks of duplex metering pumps by providing a single duplex metering pump having a single liquid end with two oppositely phased diaphragms.
Embodiments of the present invention is a two motor driven duplex metering pump. That these two motors are synchronized concurrently to drive one displacer shown as a diaphragm displacing liquid at a given operational moment and one diaphragm in liquid replenish. This is achieved with drive gears or direct connect type without drive gears.
Embodiments of the invention is to incorporate the eccentric cam system from the invention U.S. Pat. No. 8,752,451 fixed cam assembly design with multiple congruent non-cardioid shaped cam profiles that are so designed to create continuous positive motion with constant or uniform velocity for its imparted reciprocating motion. This is virtually sustained over the complete 360° of cam angle. That is the drive motor operating at any given constant speed results in an advantageous virtual continuous uniform liquid displacement by the invention. The liquid velocity entering the liquid end is virtually equal to the liquid discharged from the invention. Other eccentric members of common art to create reciprocating motion can be utilized, but not shown or described.
Embodiments of the present invention is a design that it utilizes a stepper or other type of motor or motors with direct drive. That is there is no gear reduction utilized by the pump.
Embodiments of the invention is to have motor speed modulation control for diaphragm velocity management when the invention is at low liquid rate delivery. This assure that the momentary liquid velocity is sufficient to quickly activate the check valve's change in state to maintain proper differential pressure across the liquid end pump housing.
Embodiments of the invention is to have its four check valve assemblies integral within its single duplex liquid end or within a pump housing assembly closely rigidly connected to the duplex liquid end. This facilitates the integration of two fluid streams pumped by each independent diaphragm or displacer to be comingled within the single duplex liquid end. That is the liquid on the suction side of the pump is comingled independent of the discharge side of the invention and the same is true for the discharge side of the pump. To the discharge side of the invention within the single duplex liquid end, the two liquid streams for the two displacers are combined. During normal operation a virtual sustained back pressure is applied to the pumped liquid on the discharge of the invention. This is within the internal liquid discharge channels. That sustained back pressure would be applied to the check valve geometries within the check valve assemblies for efficient seating.
Embodiments of the present invention is for an integral is for over pressurization protection with an incorporated integral or close mounted safety relief pressure equalization valve SEV or SRPEV to protect the invention and the pumping system.
There has thus been outlined, rather broadly, the more important features of the invention in order that the detailed description thereof that follows may be better understood and in order that the present contribution to the art may be better appreciated.
Numerous objects, features and advantages of the present invention will be readily apparent to those of ordinary skill in the art upon a reading of the following detailed description of presently preferred, but nonetheless illustrative, embodiments of the present invention when taken in conjunction with the accompanying drawings. The invention is capable of other embodiments and of being practiced and carried out in various ways. Also, it is to be understood that the phraseology and terminology employed herein are for the purpose of descriptions and should not be regarded as limiting.
As such, those skilled in the art will appreciate that the conception, upon which this disclosure is based, may readily be utilized as a basis for the designing of other structures, methods and systems for carrying out the several purposes of the present invention. It is important, therefore, that the claims be regarded as including such equivalent constructions insofar as they do not depart from the spirit and scope of the present invention.
For a better understanding of the invention, its operating advantages and the specific objects attained by its uses, reference should be had to the accompanying drawings and descriptive matter in which there are illustrated preferred embodiments of the invention.
The following drawings illustrate by way of example and are included to provide further understanding of the invention for the purpose of illustrative discussion of the embodiments of the invention. No attempt is made to show structural details of the embodiments in more detail than is necessary for a fundamental understanding of the invention, the description taken with the drawings making apparent to those skilled in the art how the several forms of the invention may be embodied in practice. Identical reference numerals do not necessarily indicate an identical structure. Rather, the same reference numeral may be used to indicate a similar feature of a feature with similar functionality. In the drawings:
As a preliminary matter, it should be noted that in this document (including the claims) directional terms, such as “above”, “below”, “upper”, “lower”, etc., are used for convenience in referring to the accompanying drawings. Additionally, it is to be understood that the various embodiments of the invention described herein may be utilized in various orientations, such as inclined, inverted, horizontal, vertical, etc., without departing from the principles of the invention.
Prior art examples of a conventional simplex and duplex metering pump designs are shown in
a are a representative views for another design of a conventional duplex metering pump 68. This duplex metering pump 68 is a representative inline side-to-side pump design having at least two liquid ends 56. It would typically have one gear housing 66 per liquid end 56. As is consistent with other duplex metering pump designs, pump 68 has a liquid end pump housing 56 connected at pump mounting flanges 60 with attachment bolts 62. The pump 68 has its common motor 52, mounted to flange 54 and a single stroke adjustor knob 70 for each displacer. This pump design typically allows for additional pumps 68 to be added beyond two. There is a variety of ancillary components of common art not shown on these drawings to comprise a functional metering pump. Pumps 44 and 68 depict common designs for commercially available duplex metering pumps, but there is a wide variation of these two designs with similar layouts not shown.
This is the opposite to conventional duplex metering pumps which include two liquid ends 36 or 56 and two flange mounting positions 38 or 60 as shown in
Pump 76 utilizes four integral check valve assemblies 152, not shown in
a, and 13b illustrate a liquid end 208 that pump 76 can use in place of liquid end housing 92. Pump 76 could also utilize a split liquid end pump housings 142a and 142b of assembly 142 as depicted in
Referring to
As depicted, pump 76 further includes a direct coupled stepper motor 72 or other variable speed motor to drive the pump 76. This embodiment of the invention does not have a gear set within it, such as shown on
The liquid end housing 92 with plugs 84 is further detailed in
Referring to
An alternative design is to split the follower frame 132 into two halves that are held together with compression or tension springs depending on design, however, this embodiment is not illustrated in the figures. The springs would be utilized to hold the split cam follower frame 132 together as a complete assembly. Each of the cams 126 are congruent to each other with non-cardioid cam profiles. The cams 126 are rigidly connected to cam shaft 124 and properly phased to cause in unison virtual continuous positive uniform reciprocating motion. There are at least two cams 126 on a common cam shaft 124 or on multiple shafts, not shown, depending on design requirements.
The follower assembly 130 has an integral drive cross arm 106 as part of the cam follower frame 132 that in turn is mechanically connected to the two drive connecting shafts 108a and 108b. The drive connecting shafts 108a and 108b project through cross arms 106 and 118 and are partially supported and aligned by guide linear bearings 112 that are in liquid end housing holes 174 as best seen in
The stepper motor 72 is controlled for speed variation by controller 743. The pump 76 further includes an encoder 120 for electronic feedback to the controller 74 for the motor 72 speed control verification. In operation, when the motor 72 is rotating the direct connected cam shaft 124 rotates. This results in a 1:1 speed relationship between the motor 72 and cam shaft 124 and its integrated cams 126. The follower bearings 128 are in constant contact with cams 126. This causes a substantially constant, positive velocity ratio of 1:1 and rectilinear reciprocating motion being imparted to the cam follower 130, its integrated drive arm 106, shafts 108a and 108b and drive arm 118. This reciprocating motion would have a substantially uniform velocity of motion for any given motor rotational speed. The drive arm 106 is directly driving diaphragm 114a and 114b via its connecting shafts 110a and 110b.
Drive arm 106 drives the shafts 108a and 108b that are driving the arm 118 and its reciprocating motion is transferred to the first diaphragm shaft 110a and in turn to the first mated diaphragm 114a. All of these named components will operate in unison with a resultant common uniform displacement and replenish velocity for both diaphragms 114a and 114b. The 1:1 speed relationship of motor 72 through to both diaphragms 114a and 114b reciprocating is preserved during normal operation of the invention. Normal operation has each diaphragm sustained 180° out of phase. There are two cross over moments 214 as shown on
The resultant liquid flow rate creation by this embodiment of the invention is as shown and described by
To form a liquid end assembly 64 with two liquid ends split components 142a and 142b that are combined to create one single duplex liquid end housing assembly 142 as a component within the complete pump liquid housing assembly 64. Each liquid end 142a and 142b could be made up of multiple components, not shown. Other components, such as diaphragms 114a and 114b and their shafts 110a and 110b not detailed, to drive shafts 108a and 108b are combined with a single drive arm 144 with various other ancillary components, not detailed, to form the liquid end assembly 64. This complete liquid end assembly 64 with its liquid end components 142a and 142b and its mated components are an alternate design to the liquid end housing 92 or liquid end 208 and their mated components. This design concept is to show that the opposing diaphragms 114a and 114b can be mounted in a different opposing back to back orientation. Each of the two diaphragms 114a and 114b and their drive shafts 110a and 110b are rigidly connected to a common drive arm 144. The liquid end housings 142a and 142b are held together by bolts 86 and additional bolts not shown to create a complete liquid end pump housing assembly 64. Diaphragm 114a is attached to liquid end pump housing 142a and diaphragm 114b is attached to liquid end pump housing 142b. Each diaphragm 114a and 114b are held to their respective liquid end pump housing 142a and 142b by a diaphragm mounting ring, not shown. This design would also have its complete liquid end pump housing assembly 64 rigidly mounted to the pump transmission 78 with bolts 86 to its integrated mounting flange 2 position.
Drive arm 144 is rigidly attached to the two drive shafts 108a and 108b. The drive shafts 108a and 108b connected to diaphragms 114a and 114b by their shafts 108a and 108b. The mechanics and all the components required to accomplish these rigid connections between the diaphragm's shafts 108a and 108b and the drive arm 144 and drive shafts 108a and 108b are not shown. The drive shafts 108a and 108b and nuts 104 will be rigidly connected to the cam follower's drive arm 106 as shown on
Each independent cam follower assembly 130a and 130b has its cam follower bearings 128, follower frame 132a and 132b and an integrated common follower frame drive cross arm 106. Operationally the embodiment of pump 156 with two motors 72 is basically the same as pump 76 with a single motor as shown in
It is understood that there are many ways to achieve the same equalized and divided work of liquid displacement of pump 156 by the two cam assemblies 100. Also, it is understood that the use of other forms of mechanical, electro mechanical, or electrical feedback components may be used to keep the two drive shafts 108a and 108b synchronized.
All other components depicted are the same as shown on
Operationally the resultant liquid flow rate creation by pump 43 is as shown and described by
a and 10b illustrate a liquid end housing 92 as a single component, it is understood that liquid end housing 92 could be composed of more than one component to form an assembly to achieve the same.
To ensure there is adequate back pressure, it is common to install a back pressure valve into a pump. This mitigates cam system 20 having virtually zero dwell at the two moments of change in the direction of reciprocating motion being applied to the diaphragms 114a and 114b. This sustained back pressure within zone in the discharge channel area 168 assures that there is sufficient back pressure across the check valves 152 to assure proper seating on the valves when the pump is operating under normal conditions. The cartridge check valve assembly 152 would be rigidly seated in a portion of the channels 168 at areas 170. The cartridge check valves 152 could be of a different design, such as being shaped like a ball and be disposed along a seating area built into the liquid end housing 92, not shown. For example, a portion of the channel 168 within the liquid end 92 could be so designed to comprise a check valve body rather than utilizing the valve body 182 as shown on
As shown in
In addition the bolt holes 166 are to allow bolts 86 to pass through to be connect to mounting position 80 and holes 174 are for the linear bearings 112 to seat and support the drive shafts 108a and 108b. Area 172 is the opening that connects the cavity areas 162 to channels 168. The holes 176 are the threaded holes that allow the diaphragm mounting ring 116, not shown, to be rigidly attached to the liquid end housing 92 to secure the diaphragms 114a and 114b. The areas 160 are passage ways for alternate suction or discharge ports and would be sealed with plugs 84, not shown, if not utilized for fluid porting. They also allow for the creation of the passage way 168.
Operationally the SRV 202 changes the pressure setting by turning the adjustment bolt 194 to load the diaphragm 192 with sufficient spring force to stay on its seat during normal pump operation. If there is an unsafe pressure reached the diaphragm 192 overcome the spring 190 resistance. This will allow the diaphragm 192 to lift off its seating area allowing pressure to equalize in the channel 200. This will cause liquid flow equalization and comingling between the two diaphragms 14a and 114b and protect an over pressurization condition within the invention and the piping system. When the pump continues to operate, the liquid is shuttled between the two cavities 162 within the liquid end 92, 64 or 208. When the valve 202 is open, liquid is unable to be displaced from the pump. When the over pressure condition is equalized, the diaphragm 192 will re-seat and the liquid within the liquid end will be pumped.
Referring now to
a and 14b depict a diagrammatic example of the pump's liquid volumetric flow rate displacement. That is the preferred embodiment that utilizes multiple cams 126 that are congruent geometries as described and detailed in U.S. Pat. No. 8,752,451, the entirety of which is incorporated herein by reference. These cam profiles create uniform continuous positive reciprocating motion with non-cardioid cam profiles that impart continuous uniform positive reciprocating motion to be transferred to both diaphragms 114a and 114b over virtually 360° of cam angle. This creates substantially continuous liquid displacement by the pump over a significant range of motor speeds. That is the suction liquid and discharge liquid velocities are substantially equal across the duplex liquid end 92, 64 and 208 of the invention. Therefore the diaphragms 114a and 114b motion is sustained to a given direction until the crossover moment at position 214 and motion is reversed, which occurs every 180 degrees. There is virtually no or very minimal dwell time created by the profiles of cams 126. This is accomplished without spring return being applied to the cam follower.
The line 210 represents the sustained volumetric displacement as a uniform velocity virtually without acceleration and 212 represents acceleration of the volumetric displacement with virtually no velocity for the liquid to be displaced by the invention. In practical terms this velocity to acceleration relationship is not absolute due to characteristics of the pump's practical application of mechanics and the pumping system.
a are graphical depictions of the pump operating with low diaphragm velocity and resultant low liquid volumetric displacement.
The running cam angle change over time and resultant liquid displacement 216 is insufficient to properly operate the pump's check valve assemblies 152 or other external check valves. That is the free moving ball or other geometry in the pump's check valve assemblies is in a float position and will not sufficiently seat. That is there is too much time where the check valve will not seat properly.
To mitigate this inefficient check valve seating, the controller 74 would be monitoring this low velocity condition of the pump 76 or 156 or other embodiments of the invention. The controller 74 would change the motor 72 or motors 72 speed for a sudden rise in acceleration and velocity of the diaphragms 114a and 114b between points 224. The curves 220 illustrating the diaphragms 114a and 114b velocity change, as shown in
The liquid of the suction and discharge of the pump would be connected and be of one liquid stream across the liquid end of the pump when the ball or other element is floating. The sudden change in diaphragms 114a and 114b velocity, as shown, would increase the volumetric displacement by the invention over a shorter time period of cam angle change. Whereas,
A number of embodiments of the present invention have been described. Nevertheless, it will be understood that various modifications may be made without departing from the spirit and scope of the invention. Accordingly, other embodiments are within the scope of the following claims.
This application claims the benefit of U.S. Provisional Application No. 62/198,754, filed Jul. 30, 2015, and U.S. Provisional Application No. 62/183,202, filed on Jun. 23, 2015 the entirety of each is incorporated herein by reference.
Number | Date | Country | |
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62198754 | Jul 2015 | US | |
62183202 | Jun 2015 | US |