Systems and methods for a tangent drive high pressure pump

Systems and methods are described for a reciprocating mechanism. The system includes at least one axially translating y-axis component configured to reciprocate substantially along a y-axis with a reciprocating motion of a piston assembly relative to a base. The system also includes at least one x-axis component slidingly coupled via at least one bearing assembly to and translating with the at least one y-axis component along the y-axis. The at least one x-axis component is configured to reciprocate substantially perpendicularly to the y-axis relative to the at least one y-axis component, and includes an orbital output component and an orbital linking component disposed substantially concentric with the orbital output component. The system also includes a stationary output component rotatably attached to the base in a direction that is substantially perpendicular to both the x-axis and y-axis, and a stationary linking component rotatably attached to the base in a direction that is substantially concentric with the stationary output component.

TECHNICAL FIELD

This application relates generally to reciprocating engines, pumps, and compressors. In particular, this application relates to power delivery devices for reciprocating engines, pumps, and compressors, and to related systems and methods.

BACKGROUND

A reciprocating engine generally uses a crankshaft—connecting rod mechanism to convert the linear reciprocating motion of one or more pistons translating within cylinders into the rotational motion of the crankshaft and vice versa. This type of mechanism is herein referred to as a power delivery device. For example, the internal combustion engine (IC engine) is the most common type of reciprocating engine. Reciprocating engines are generally used to convert the chemical energy released during the combustion of various fuels (such as gasoline) or thermal energy (such as energy derived from steam) into kinetic energy (e.g., mechanical rotating motion), which can be more readily usable to move things (e.g., propel objects). The crankshaft of a reciprocating engine is typically the engine element that is connected to output devices used to move various devices or vehicles, such as automobiles, generators, trucks, airplanes, welders, ships, bulldozers, motorcycles, boats, etc.

One challenge with power delivery devices generally has been to maximize the amount of usable power that is able to be transitioned through the device. This is true for reciprocating engines (e.g., internal combustion engines) along with other types of engines, pumps and compressors. Traditional power delivery devices are not necessarily capable of optimal power delivery due to constraints that are often a result of the way the power delivery device itself is constructed. Especially where industries in which power delivery devices are used become increasingly focused on minimizing energy losses where possible, there is a need for more efficient power delivery devices, including those from which power can be more effectively transitioned through the device as compared to traditional, previously-available devices.

SUMMARY

The technology, in one aspect, features a system including a reciprocating mechanism. The system includes at least one axially translating y-axis component configured to reciprocate substantially along a y-axis with a reciprocating motion of a piston assembly relative to a base to which the piston assembly is slidingly attached via at least one bearing assembly. The system further includes at least one x-axis component slidingly coupled via at least one bearing assembly to and translating with the at least one y-axis component along the y-axis. The at least one x-axis component includes an orbital output component and an orbital linking component disposed substantially concentric with the orbital output component.

The system further includes a stationary output component rotatably attached to the base in a direction that is substantially perpendicular to both the x-axis and y-axis. The stationary output component is configured to engage with the orbital output component via a first integral interconnecting output link. The system further includes a stationary linking component rotatably attached to the base in a direction that is substantially concentric with the stationary output component. The stationary linking component configured to engage with the orbital linking component of the at least one x-axis component via the first integral interconnecting link.

The technology can further include any of the following features.

In some embodiments, the at least one x-axis component is configured to reciprocate substantially perpendicularly to the y-axis relative to the at least one y-axis component. In some embodiments, the x-axis component is slidingly attached to a bearing shaft via plain bushing bearings. For example, in some embodiments, the plain bushing bearings include at least one plain bushing bearing assembly fixed to the at least one x-axis component and slidingly attached to the at least one y-axis component via a shaft on which the plain bushing bearing slides. In other embodiments, the plain bushing bearings include at least one plain bushing bearing assembly fixed to the at least one y-axis component and slidingly attached to the at least one x-axis component via a shaft on which the plain busing bearing slides.

In some embodiments, the shaft is a hardened polished steel shaft. In some embodiments, the piston assembly includes a piston and a piston rod. For example, in some embodiments, the piston rod is slidingly attached to the base via a plain busing bearing. In some embodiments, the piston rod is a hardened polished steel shaft.

In some embodiments, one or more y-axis components are slidingly coupled to the x-axis component. For example, in some embodiments each y-axis component is attached to and reciprocating with a corresponding piston assembly.

In some embodiments, each of the bearing assemblies includes a plain bushing bearing. For example, in some embodiments, the plain bushing bearings is made of at least one of Babbitt soft metal; or engineered industrial plastics, available from many manufacturers, such as: Dupont's Bearing Grade SP-21 VESPEL® or Bearing Grade 4540 TORLON®, or Bearing Grade PEEK®; or a recirculating ball type linear bushing.

In some embodiments, the bearing assemblies include at least one recirculating ball bushing assembly. In some embodiments, each of the bearing assemblies includes a plain busing bearing including a commercial plastic bearing material.

The technology, in another aspect, features a reciprocating engine. The reciprocating engine includes at least one axially translating y-axis component configured to reciprocate substantially along a y-axis with a reciprocating motion of a piston assembly relative to a base to which the piston assembly is slidingly attached via at least one bearing assembly. The reciprocating engine further includes at least one x-axis component slidingly coupled via at least one bearing assembly to and translating with the at least one y-axis component along the y-axis. The at least one x-axis component includes an orbital output component and an orbital linking component disposed substantially concentric with the orbital output component. In some embodiments, the at least one x-axis component is configured to reciprocate substantially perpendicularly to the y-axis relative to the at least one y-axis component.

The reciprocating engine further includes a stationary output component rotatably attached to the base in a direction that is substantially perpendicular to both the x-axis and y-axis. The stationary output component configured to engage with the orbital output component via a first integral interconnecting output link. The reciprocating engine further includes a stationary linking component rotatably attached to the base in a direction that is substantially concentric with the stationary output component. The stationary linking component configured to engage with the orbital linking component of the at least one x-axis component via the first integral interconnecting link.

The technology, in another aspect, features a reciprocating compressor. The reciprocating compressor includes at least one axially translating y-axis component configured to reciprocate substantially along a y-axis with a reciprocating motion of a piston assembly relative to a base to which the piston assembly is slidingly attached via at least one bearing assembly. The reciprocating compressor further includes at least one x-axis component slidingly coupled via at least one bearing assembly to and translating with the at least one y-axis component along the y-axis. The at least one x-axis component includes an orbital output component and an orbital linking component disposed substantially concentric with the orbital output component. In some embodiments, the at least one x-axis component is configured to reciprocate substantially perpendicularly to the y-axis relative to the at least one y-axis component.

The reciprocating compressor further includes a stationary output component rotatably attached to the base in a direction that is substantially perpendicular to both the x-axis and y-axis. The stationary output component configured to engage with the orbital output component via a first integral interconnecting output link. The reciprocating compressor further includes a stationary linking component rotatably attached to the base in a direction that is substantially concentric with the stationary output component. The stationary linking component configured to engage with the orbital linking component of the at least one x-axis component via the first integral interconnecting link.

The technology, in another aspect, features a reciprocating pump. The reciprocating pump includes at least one axially translating y-axis component configured to reciprocate substantially along a y-axis with a reciprocating motion of a piston assembly relative to a base to which the piston assembly is slidingly attached via at least one bearing assembly. The reciprocating pump further includes at least one x-axis component slidingly coupled via at least one bearing assembly to and translating with the at least one y-axis component along the y-axis. The at least one x-axis component includes an orbital output component and an orbital linking component disposed substantially concentric with the orbital output component. In some embodiments, the at least one x-axis component is configured to reciprocate substantially perpendicularly to the y-axis relative to the at least one y-axis component.

The reciprocating pump further includes a stationary output component rotatably attached to the base in a direction that is substantially perpendicular to both the x-axis and y-axis. The stationary output component configured to engage with the orbital output component via a first integral interconnecting output link. The reciprocating pump further includes a stationary linking component rotatably attached to the base in a direction that is substantially concentric with the stationary output component. The stationary linking component configured to engage with the orbital linking component of the at least one x-axis component via the first integral interconnecting link.

DETAILED DESCRIPTION

The technology features a novel tangent drive mechanism that has several inventive features over that which is already known. For example, the technology described herein includes improvements over the tangent drive mechanisms described in U.S. Pat. Nos. 9,958,041, 10,436,296, 10,801,590, and 10,851,877. In addition, the technology described herein includes improvements over similar existing drive mechanisms such as the Scotch Yoke, Stiller-Smith, and the Double-Slider mechanism described in U.S. Pat. Nos. 10,138,807 and 9,316,249. The tangent drive mechanism described herein has been developed for various applications, including engines, pumps, and compressors. All of the above prior art mechanisms have the beneficial attribute of generating, as does the tangent drive mechanism of the current invention, pure sinusoidal piston movement. This sinusoidal piston movement has several thermodynamic advantages over the piston motion generated by the slider-crank arrangement of traditional crankshaft-connecting rod mechanisms. These thermodynamic advantages have been disclosed in several engineering publications including SAE International publication no. 870615 (Thermodynamic Implications of the Stiller-Smith Mechanism). The prior art mechanisms, however, generate this movement with inventive yet intricate designs that are overly complicated and inefficient.

For example, the tangent drive invention of U.S. Pat. Nos. 9,316,249, 10,138,807, 10,801,590, and 10,851,877 describe a typical embodiment which uses hypocycloid gearing to generate the sinusoidal reciprocating movement of a piston. The geared embodiment is expensive to produce and has the disadvantage of higher frictional losses due to the gearing. Also, the prior art tangent drive mechanism requires multiple linear bearings for each axis of movement, this is true for either a geared or non-geared embodiment of U.S. Pat. No. 10,851,877. Each bearing is a source of additional frictional losses. As described herein, by slidingly connecting an embodiment piston rod assembly directly to an embodiment base the tangent drive mechanism is simplified by then allowing the piston and piston rod assembly to function as the y-axis component.

As a further example, the Scotch Yoke mechanism requires the direct engagement and sliding of the rotating crankshaft journal on a linear slide groove perpendicularly attached to either a piston rod or rod slide. The required material strength, the required tolerances, the rapid wear of parts, and frictional losses of this mechanism are very high. This unconventional use of the crankshaft journal has kept this mechanism out of mainstream use in reciprocating engines, pumps, and compressors for more than one hundred years. As a further example, the Stiller-Smith mechanism uses a complicated, many-component linkage mechanism to generate the sinusoidal piston movement. This mechanism has high frictional losses, many-parts reliability issues, dynamic balancing issues, and is expensive to produce. This mechanism was used in academic research laboratories to study the benefits of sinusoidal piston movement but was never moved to a practical producible mechanism. As still a further example, the Double Slider mechanism requires a fixed L-Bracket relationship between moving axis and multiple Dove Tail slides to control the linear slide movement. The restrictive nature of the mechanisms L-Bracket design limits application and cost effectiveness. The sliding components yield high frictional losses, difficult dynamic balancing problems and costly manufacture.

In one embodiment, the tangent drive mechanism of the current invention includes at least one y-axis component comprising at least one piston assembly which is directly and slidingly attached to the base of an engine, pump, or compressor via at least one linear plain bushing bearing assembly, or the like. The y-axis component then being constrained to reciprocate in the y-direction only by combination of the piston guides (seals or rings) and the at least one linear plain bushing bearing fixed to the base and slidingly attached to the piston rod of the piston assembly. The y-axis component then includes a piston assembly, including a piston rod, a guiding and/or constraining linear plain bushing bearing attached to the base and slidingly attached to the piston rod, and a slidingly attached x-axis component assembly which is constrained to translate with and move substantially perpendicular to the y-axis component. By applying the y-axis component directional constraint to the piston, piston rod and base, the overall mechanism is greatly simplified. Allowing, for example, multiple pistons at various angles from each other on a single crank throw. Constraining each piston assembly at its corresponding angle via corresponding y-axis component (piston and piston rod) assemblies slidingly attached to the base at the corresponding angle.

The x-axis component assembly is slidingly attached via at least one linear plain bushing bearing assembly to the y-axis component assembly, and in the preferred embodiment encompasses a hardened steel shaft that is affixed to either the y-axis component or the x-axis component, and the at least one linear plain bushing bearing which is slidingly attached to the shaft and interfaces with either the y-axis or x-axis component. The x-axis component assembly also being rotatably attached via a plain journal bearing to, and being driven by or driving, a crank throw. In some embodiments, a single x-axis component, on a single crank throw, can have multiple y-axis components slidingly attached to it at various angles from each other. The angles being set by the y-axis components placement in the base. In some embodiments, multiple x-axis components, on a single crank throw, can be slidingly attached to multiple y-axis components at various angles from each other. The angles again being set by the y-axis components placement in the base. In some embodiments, active oiling of the bearings will be accomplished through drilled oil passages in the crankshaft, plain bearings, x-axis component assemblies, y-axis component assemblies and machine base assemblies. In some embodiments, the use of balancing weights and/or additional y-axis (or y-plate) assemblies with the preferred connection through a bicycle crank link is necessary for overall dynamic mechanism balancing.

The need for mitigating bearing frictional losses, the need for very long bearing life, and the need to keep the mechanism workable for both single and double acting machines are some of the considerations that led to the tangent drive mechanism described herein, particularly on the sliding connection of the x-axis to y-axis components. Plain bearings are bearings that essentially operate on a thin film of oil, which under ideal conditions eliminates almost all friction between two moving surfaces. The use of plain bushing bearings may also require strong forced oiling of the interface between the rotating or moving surfaces.

In one embodiment, the bushing bearings are made from either a plain soft metal (such as Babbitt) or an industrial bearing grade plastic such as SP-21 VESPEL® and may be strongly oiled. A relatively high oil pressure may be required because of the reciprocating nature of the machines and the fact that during operation the x-axis component (or x-plate) assembly stops and reverses direction every 180 degrees of crankshaft rotation. This motion causes the oiling requirement to behave both hydrodynamically and hydrostatically. To ensure that the high dynamic operating oil pressure does not deplete the oil gap of oil during direction reversals, check valves, in some cases may be required. Because the x-plate is attached to the output crank link or shaft a strong oil flow can typically be supplied through the shaft. Depending upon which plate the bushing bearing is attached to (either the x-plate or y-plate) accommodating the oil passages may be more involved. In some embodiments, the bushing bearing assembly is fixed on the x-axis component (x-plate) assembly where one simple drilled passage is required.

In some embodiments, bushing bearing materials of the highest quality are used, in addition to the use of oiled Babbitt, the use of tough industrial plastics will make the simple design one of long life. VESPEL®, TORLON® and Peek® are three petrochemical plastics from three separate manufactures that are preferred materials for the plain bushing bearings of the current tangent drive invention. There are many specific grades and types of each of the above manufacture plastics. The bearing bushings of the current invention is the ideal application for these plastic materials in that they are specifically made and marketed for applications that exhibit the behavior of intermittent, or stop and go, bearing movement realized by the reciprocating (back and forth) movement of both the x-axis and y-axis components of the tangent drive. For example, SP-21 VESPEL® is a plastic grade that can be run with no lubrication and perform as well or better with the same friction coefficient as oiled Babbitt in bushing bearing application.

FIGS.1-3show a perspective, front and side view of the tangent drive mechanism applied to a two-cylinder engine, pump, or compressor apparatus. The engine, pump, or compressor represented by apparatus5ofFIGS.1-3shows the apparatus crankcase10and cylinder block11as outlined only for clarity. All other parts not essential to the instant invention are also not shown.FIG.4shows a section view through one of the pistons of apparatus5showing the main components of the invention.FIG.5shows the x-axis component andFIG.6shows a section through the x-axis component.FIG.7shows the piston rod bushing bearing assembly andFIG.8shows a section through the piston rod bushing bearing assembly.FIG.9shows the crankshaft assembly.FIG.10shows the current invention configured as a triplex plunger pump.

Crankshaft20includes input/output links21a,21b,21c,21d, input/output power shaft22, main bearing journals23aand23b, and x-axis component bearing journals24aand24b. When operated as a pump or compressor, the power input shaft22drives the crankshaft in a circular motion. The power input shaft can be driven by an electric motor or IC engine (not shown). The links are integral parts of the monolithic crankshaft, which is made up of several input/output links and bearing journals. The crankshaft has oil lubricant passages drilled throughout to deliver oil under pressure to the bearings located on the journals. In the two-cylinder apparatus, as shown, there are main bearing journals23aand23b, and x-axis component bearing journals24aand24b. These bearing journals are designed to accommodate plain lubricated bearings or ball or roller bearings.

In the preferred embodiment, the x-axis component bearings are plain journal bearings and rely on a hydrodynamic oil film to reduce friction and protect the journal from metal to metal contact during rotation of the crankshaft20. The main bearings journals23aand23bare located along the input shaft axis22a. These main bearing journals can accommodate plain journal bearings with the same operating characteristics as the x-axis component bearings, or they can be lubricated ball or roller bearings. In the apparatus5, as shown inFIGS.1-3, tapered roller bearings25aand25bare used. Tapered roller bearings are sometimes used in crankshaft applications to accommodate the possibility of thrust forces along the crankshaft. The two cylinder apparatus, as shown inFIGS.1-4, has a crankshaft20that consists of two crank throws26aand26b. Each throw is made up of two links and a bearing journal. In order to dynamically balance the rotation of the crankshaft and connected assemblies, the two crank throws are typically positioned 180° apart.

As shown inFIG.1, the piston cylinders11aand11bare positioned side by side in block11(or base). That is, when looking at the cylinder block from direction z the centerline of the two cylinders have a zero angle between them. in cylinder block11(or base). This configuration is common for many engines, compressors, and pumps. An equally popular configuration in gas compression is a configuration where the two cylinders11aand11bare positioned 180° apart in cylinder block11(or base) when looking from the z direction. In gas compression the compressor can be configured to work in either a single acting or a double acting way, where the piston is compressing gas in both directions of the piston stroke. Also, in gas compression, the compressor can be configured to be a single stage compressor or a double (or more) stage compressor, where the first compression feeds the second compression and so on. The tangent drive mechanism works essentially the same for all of these gas compressor configurations.

In some embodiments, other crankshaft balancing features are employed such as extra weighing on various features of the crankshaft20. As a main feature of the current invention much of the need for additional balancing techniques are essentially no longer necessary. This is due to the near elimination of the unbalanced x-axis forces caused by the motion of the crankshaft connecting-rod mechanism which is no longer present. The tangent drive mechanism essentially eliminates those unbalanced x-axis forces which have been replaced by only weak sliding frictional forces all while producing pure sinusoidal motion. For example, reciprocating gas compressors typically use a crankshaft/connecting rod/crosshead arrangement which generates large x-axis forces on the crosshead perpendicular to both the crankshaft axis of rotation and the y-axis (axis of the piston movement). This force is transmitted through the compressor and is a strong source of vibration. The tangent drive mechanism replaces the connecting rod and crosshead with a sliding x-axis component movement with only weak sliding frictional forces developed, essentially eliminating the need for additional balancing techniques.

Attached to the x-axis bearing journals24aand24bare the x-axis component assemblies27aand27brespectively. In some embodiments, the two assemblies27aand27bare identical. The x-axis component assembly27ais shown separately inFIGS.5and6. The x-axis component assemblies27aand27bare interfacing components that transfer power to and from the crankshaft20and their counterpart y-axis components40aand40b. The x-axis component is the key linking element in the tangent drive mechanism. It contains the linking bearing elements that make the smooth low friction sinusoidal movement possible and distinguish it over other similar sinusoidal movement mechanisms.

The x-axis component assemblies27aand27bare each comprised of a body28, a journal bearing cap29a, journal bearing cap bolts29band29c, plain journal bearings30aand30band two plain bushing bearings31aand31b. These two bushing bearings allow for the low friction movement of the x-axis linking element and distinguish this tangent drive mechanism from all other similar mechanisms. The use of two bushing bearings adds to the stability of the movement. In some embodiments, the x-axis body28and the journal bearing cap29aare made of high strength steel, high strength aluminum or titanium. The plain bushing bearings31aand31bare designed to freely slide on the bushing bearing shafts41aand41b, which are fixedly attached to y-axis components40aand40b, respectively. In some embodiments, plain bushing bearings31aand31bare made of either a soft metal Babbitt material, which can be either cast in place or fitted in place as a pressed or heat shrunk part or locked in place by some means such as glue or separate screws. In other embodiments, the plain bushing bearings31aand31bcan be made of an industrial plastic such as SP-21 VESPEL® and pressed or heat shrunk in place or locked in place by glue, dowel pins, or separate screws. Heat shrinking is a manufacturing technique that uses thermal expansion to fix assembled parts together and is commonly used.

Lubricating the bushing bearings is important for long life and reduced friction. As shown inFIG.4, the lubrication holes42a, the lubrication channel42b, and lubrication grooves42callow for lubrication of the bushing bearings. High pressure oil is supplied to the bearings via oil feed passages drilled in the crankshaft20. In some embodiments, oil pressures can range from 20 psig to 150 psig. In some embodiments, oil is pumped into the crankshaft20by an external pump, not shown. As an alternative to plain bushing bearings, the use of commercial ball bushings is also possible. In some embodiments, bushing bearing shafts41aand41bare identical and are made of high strength hardened steel, and are highly polished to give it a very smooth surface for the forced sliding of the lubricated bushing bearings31aand31b. A typical hardened shaft would have a Rockwell Hardness of HRC50 to HRC60. As discussed in many engineering texts and journals, surface hardness is a most important parameter. If a shaft surface is too soft (under 30 HRC for example) a plain bushing can damage the shaft, causing premature bearing failure, and requiring shaft replacement.

Shaft41is tightly fitted to y-axis component40and has snap rings43fixed on each end to retain the shaft in place. As an alternative, bushing bearing shaft41can be pressed or heat shrunk into position on y-axis component40. Shaft41is very heavily loaded during operation of the invention, whether the application is an engine, pump or compressor. During operation there is typically a strong and variable load or force applied perpendicularly to its axis as the x-axis component slides back and forth along the shafts' length. The load (force) magnitude is very similar to that of the wrist pin in engine applications. In some embodiments, because of its somewhat long typical length {6″ to 9″) and being supported by its ends only, the material tensile and shear strength need to be very high and are critical engineering considerations. Typically, the high strength steels used in manufacture of engine wrist pins will be the material of choice for the bushing bearing shafts41aand41b. In some embodiments, alloy steels such as 1018, 4130, 4340, H13 and Maraging Steel C300 can be used.

Y-axis components40aand40bare fixed to the lower ends of the piston rods50aand50brespectively thus becoming part of a piston or piston rod assembly. The y-axis components40aand40bcan be threaded on to piston rods50aand50band locked into place by lock nuts51aand51bor, as an alternative, y-axis components40aand40bcan be pressed or heat shrunk on to piston rods50aand50brespectively. In some embodiments, the piston rods are made of high strength hardened steel and highly polished to yield a very smooth surface for the forced sliding of the lubricated plain bushing bearings61aand61b. In some embodiments, a hardened piston rod would have a Rockwell Hardness of HRC50 to HRC60. The use of two bushing bearings on the y-axis piston rod slide adds stability and smooth operation to the overall mechanism and is a key design feature. Plain bushing bearings61aand61bare pressed or otherwise fixed into housings60aand60b.

FIGS.7and8show bearing housing assembly60b. In some embodiments, housings60aand60bare typically made of steel or stainless steel and are fixed to the apparatus base. Fixing the y-axis movement to the piston rod movement is a key feature of the current invention. By fixing the y-axis components40aand40bto the piston assemblies and then the piston assemblies (piston rods) to the apparatus base, we remove important design constraints. Removing constraints such as the y-axis mounting and the y-axis movement that would dictate the required space and the exact placement of the pistons and cylinders. This invention feature essentially eliminates alignment, tolerancing and space issues. For example, by fixing the spatial relationship of the piston to the cylinder bore by the y-axis bushing bearings only the piston cylinder alignment and tolerancing is greatly improved.

In some embodiments, plain bushing bearings61aand61bare made of either a soft metal Babbitt material, which can be either cast in place or fitted in place as a pressed part or locked in place by some means such as glue or separate screws. The plain bushing bearings61aand61bcan be made of an industrial bearing grade plastic such as SP-21 VESPEL® and pressed in place or locked in place by glue or separate screws. Lubricating the bushing bearings is important for long life and reduced friction. Shown inFIGS.7and8are the lubrication holes72a, the lubrication channel72b, lubrication grooves72c. High pressure oil is supplied to the bearings via oil feed passages drilled in the crankshaft. Typical oil pressures can range from 20 psig to 150 psig. Oil is typically pumped into the crankshaft by an external pump, not shown. As an alternative to plain single material bushing bearings the use of commercial linear ball bushings such as THOMSON TYPE SUPER METRIC ball bushing is also possible.

Pistons80aand80bare attached to the top end of piston rods50aand50brespectively. In some embodiments, pistons80aand80bcan be threaded on to piston rods50aand50band locked into place by lock nuts51cand51dor, as an alternative, pistons80aand80bcan be pressed or heat shrunk on to piston rods50aand50brespectively. In operation as a pump or compressor, the inventions' power input is applied to input shaft22of crankshaft20and drives the crankshaft in a circular orbit around crankshaft axis22a. A clockwise rotation is shown in the figure as a, +rotation, a counter-clockwise rotation would have a, −rotation.

FIG.10shows the invention configured as a liquid or volatile gas triplex plunger pump. Where three plunger pump pistons are driven by the input power shaft. The crank throws driving each piston are positioned 120° apart around the crankshaft. This design is made possible by the unique feature of the invention where the y-axis movement is fixed to the piston rod movement relative to the pump base. This allows the x-axis component, which is slidingly fixed to the y-axis piston assembly the ability to move perpendicularly to the y-axis for any number of y-axis piston assemblies. The simplicity of the design allows for more piston throws to be positioned at different angles around the crankshaft. For example, 6 piston crank throws could be positioned around the crankshaft at 60°; or 5 piston throws at 72°; or 4 or 8 piston throws positioned at 45°.

Variations, modifications, and other implementations of what is described herein will occur to those of ordinary skill in the art without departing from the spirit and the scope of the invention. Accordingly, the invention is not to be limited only to the preceding illustrative descriptions.