Two stroke steam-to-vacuum engine

Abstract

A two stroke steam-to-vacuum engine comprises a plurality of cylinders (500, 502) each cylinder having a piston (504, 510), a piston rod (506, 512), and a steam chamber (508, 514), the piston rods connected for synchronous movement such that each piston is reciprocally moveable between an expanded position and a collapsed position. Admission of steam at 3-5 p.s.i. above atmospheric pressure into the steam chambers (508, 514) is controlled by steam valves (522, 524) and exposure of the steam chambers to a vacuum is controlled by vacuum valves (548, 550). Steam is supplied to the steam chambers (24, 38) through a boiler 520, a solar power source, or an alternative fuel of choice. An auxiliary vacuum tank (572) may be isolated from a primary vacuum tank (554) to replenish the vacuum in a condensate collector tank (560) after removal of condensate. Auxiliary vacuum pumps (614, 616), driven by power from cylinders (500, 502), replenish the vacuum in the auxiliary vacuum tank (572) leaving the main vacuum pump (570) to support the primary vacuum tank (554).

Description

BACKGROUND OF THE INVENTION

This invention relates to steam engines and particularly to steam engines in which steam at atmospheric to slightly above atmospheric pressure in the steam chamber of a cylinder is exposed to a vacuum causing a power stroke. In particular, this invention is directed to steam-to-vacuum engines having two or more cylinders having linked pistons, each cylinder of which has a steam chamber which may be exposed to steam at or slightly above atmospheric pressure, which steam exits the cylinder creating a vacuum in that cylinder which permits ambient air pressure to push one of the linked pistons through a power stroke.

The development of modern steam power began with the Savery pump patented by Thomas Savery in 1698, which was used to remove water from mines. It worked by heating water to vaporize it, filling a tank with steam, then creating a vacuum by cutting off the tank from the steam source and then injecting cold water into the tank to condense the steam. The resulting vacuum was used to draw water up from a mine.

Thomas Newcomen (1663-1729) improved on the Savery pump by combining a steam cylinder and piston with a pivoting beam. The beam is heavier on the side opposite the steam cylinder so that gravity pulls that side down. As the heavy side descends, the piston in the steam cylinder rises. Power is created by filling the cylinder with steam at about atmospheric pressure and then spraying water into the cylinder to condense the steam. The resulting vacuum allows atmospheric pressure to push the piston down causing the side of the beam above the cylinder to pivot down and further causing the heavy side of the beam to ascend, filling a pump below the ascending side with water. At the bottom of the power stroke, a valve opens to restore steam to the cylinder, allowing the heavy side of the beam to be pulled back down by gravity to activate the pump. Thus, the Newcomen engine was driven by atmospheric pressure pushing on a piston to fill a vacuum using steam at about atmospheric pressure. Newcomen's engines were inefficient primarily because the steam cylinder was repeatedly heated and cooled, wasting energy to heat the cylinder.

James Watt (1736-1819) made a pioneering breakthrough in 1765 with his discovery that a great efficiency could be achieved by using a separate condenser. Like Newcomen's atmospheric engine, Watt's engine also operates on the principle of atmospheric pressure pushing a piston down. However, valves permit the steam to be sucked into the separated condenser for cooling of the steam and creation of the vacuum. Separating the condenser allows the steam piston and cylinder to remain hot at all times resulting in a substantial increase in efficiency over Newcomen's engine.

Subsequent improvements to steam engine technology focused primarily on high pressure steam and new mechanical designs, leaving production of power using atmospheric pressure vacuum engines relegated to the sidelines.

SUMMARY OF THE INVENTION

A steam-to-vacuum engine according to the invention comprises a first cylinder and a second cylinder. The first cylinder has a first piston defining a first steam chamber in the cylinder. The first piston is reciprocally moveable in the first cylinder delimiting the boundary of the first steam chamber. A first piston rod is attached to the first piston. The second cylinder has a second piston and a second steam chamber. The second piston is likewise reciprocally moveable in the second cylinder delimiting the boundary of the second steam chamber. A second piston rod is attached to the second piston. The cylinders are in fixed spaced relation and the piston rods are linearly connected together by a coupler such that the first and second pistons move simultaneously in fixed reciprocating relation. In another aspect of the invention, the piston rods of more than two cylinders are connected together by a crankshaft and connecting rods or other appropriate mechanical connection means for synchronous movement.

A source of steam, e.g., a boiler, a solar collector, or a fuel of choice, produces steam at slightly above atmospheric pressure and is in communication with the first and second cylinders. Preferably, steam is produced at 3-5 p.s.i. above ambient for optimal function. Entry of steam into each cylinder is controlled by a plurality of steam valves. Similarly, exposure of each cylinder to a vacuum is controlled by a plurality of vacuum valves.

The piston in each cylinder is moveable between an expanded position and a collapsed position. When the piston is in the expanded position, the steam chamber is expanded to its maximum volume. When the piston is in the collapsed position, the steam chamber is collapsed to it smallest volume. At the beginning of movement in either cylinder of the piston from the collapsed position to the expanded position, a vacuum valve seals off the steam chamber from the vacuum and a steam valve exposes the steam chamber to the steam source. The steam chamber therefore fills with steam at near atmospheric pressure behind the sliding piston during the expansion defining a steam intake stroke. As the first cylinder moves through the steam intake stroke, the piston in the second cylinder moves from the expanded position to the collapsed position defining a power stroke. At the beginning of the power stroke a steam valve seals off the second cylinder's steam chamber from the steam source and a vacuum valve exposes the steam chamber to the vacuum. Immediately upon exposure of the steam in the steam chamber to the vacuum, the steam rushes out of the steam chamber to the vacuum, leaving a vacuum in the steam chamber in order that atmospheric pressure can drive the piston through the power stroke. Therefore, by coupling the pistons for simultaneous movement, moving one cylinder through the power stroke drives the other cylinder through the steam intake stroke. Accordingly, as the linked pistons reciprocate, one piston in one cylinder is always producing a power stroke, while an intake of steam occurs in the other cylinder, resulting in a two stroke atmospheric steam engine. In an alternate embodiment including more than two connected pistons, a power stroke by each one of the pistons drives movement through a power stroke—steam intake stroke cycle by the pistons in all the other cylinders.

In one embodiment of the invention, each cylinder has an air chamber defined by the cylinder walls, a distal wall of the cylinder and the piston. The distal wall is provided with an air valve for controlling entry of air into the air chamber, and with one or a plurality of check valves for controlling the discharge of air from the air chamber, for refined control of the reciprocating movement of the pistons. For example, delaying the inflow of air into a cylinder in which the piston is entering into a power stroke will slow movement of the piston through the power stroke. Alternately, air outflow from the cylinder experiencing the steam intake stroke may be blocked or restricted to slow the progress of the power stroke in the other cylinder.

A steam-to-vacuum engine as described has the significant advantages of producing continuous dual power strokes by linking the pistons, and being able to produce substantial amounts of energy only using steam at near atmospheric pressure. The invention uses steam at relatively low pressure such that steam at required pressures is easily obtained from a wide variety of heat sources including a standard array of solar heating devices, other naturally occurring heat sources, heat from radioactive waste derived from the nuclear fission process, and other fuels of choice. After installation, using a non-polluting fuel, power produced by the invention is essentially free and environmentally clean.

BRIEF DESCRIPTION OF THE ILLUSTRATED EMBODIMENTS

FIG. 1 is a schematic representation of a steam-to-vacuum engine according to the invention.

FIG. 1A is an enlarged schematic representation of the controllers and switches of the steam-to-vacuum engine shown in FIG. 1.

FIG. 2 is a schematic representation of the valve operations of the steam and vacuum valves of the steam-to-vacuum engine depicted in FIG. 1.

FIG. 3 is a schematic representation of an alternate embodiment of a steam-to-vacuum engine according to the invention.

FIG. 3A is an enlarged schematic representation of the controllers and switches of the steam-to-vacuum engine depicted in FIG. 3.

FIG. 4 is a schematic representation of the cylinders of a steam-to-vacuum engine according to the invention showing the coupler attached to a pivot bar.

FIG. 5 is a schematic representation of the cylinders of a steam-to-vacuum engine according to the invention showing the coupler attached to a wheel.

FIG. 6 is a schematic representation of two cylinders of an alternate embodiment of a steam-to-vacuum engine according to the invention linked to a crank assembly.

FIG. 7 is a schematic view of three cylinders of an alternate embodiment of a steam-to-vacuum engine according to the invention linked to a crank assembly.

FIG. 8 is a schematic view of two cylinders of an alternate embodiment of a steam-to-vacuum engine according to the invention linked to a slide assembly.

FIG. 9 is a schematic representation of two cylinders of an alternate embodiment of a steam-to-vacuum engine according to the invention showing the steam and vacuum valves relocated to the outer ends of the cylinders and showing air valves installed on the inner ends of each cylinder.

FIG. 10 is a schematic representation of two cylinders of an alternate embodiment of a steam-to-vacuum engine according to the invention linked to a crank assembly.

FIG. 11 is a schematic representation of two cylinders of an alternate embodiment of a steam-to-vacuum engine according to the invention linked to a crank assembly.

FIG. 12 is a schematic representation of two cylinders of alternate embodiment of a steam-to-vacuum engine showing air valves on the outer ends of the cylinders and showing the invention linked to a wheel.

FIG. 13 is a schematic representation of two cylinders of an alternate embodiment of a steam-to-vacuum engine showing vacuum pumps operated by the engine for replenishing the vacuum.

FIG. 14 is a schematic representation of another embodiment of a steam-to-vacuum engine according to the invention including a condensate collector tank and small vacuum pumps.

DETAILED DESCRIPTION OF THE ILLUSTRATED EMBODIMENTS

With reference initially to FIG. 1 of the illustrations, a steam-to-vacuum engine, indicated generally at 10, comprises a first cylinder 12 on the left and a second cylinder 14 on the right. The first cylinder 12 has a first piston 16 and a first piston rod 18. The first piston 16 is moveable between an expanded position B and a collapsed position A defining the moveable boundary of a first steam chamber 24 in the first cylinder 12. The second cylinder 14 similarly has a second piston 30 and a second piston rod 32. The second piston 30 is moveable between an expanded position B′ and a collapsed position A′ defining the moveable boundary of a second steam chamber 38 in the second cylinder 14.

In the illustrated embodiment, a coupler 40 connects the first and second piston rods 18, 32 such that the first and second pistons 16, 30 are linked in linear relation for simultaneously movement. It will be readily appreciated that there are numerous options available in the art for joining the pistons rods including, for example, forming the pistons rods as one part, forming the piston rods and pistons as one part, and welding the piston rods together.

A steam reservoir 42 is connected to the first and second steam chambers 24, 38 through a plurality of steam valves considered in greater detail below. Water for producing steam is heated by the solar power source 44 shown in FIG. 1, such as an array of solar collectors. Steam at atmospheric pressure will successfully operate the engine, but experimentation has shown that steam at 3-5 psi over ambient will provide for optimum operation. A condenser 46 and vacuum tank 48 are similarly connected to the first and second steam chambers 24, 38 through a plurality of vacuum valves also considered in greater detail below. In the illustrated embodiment steam expansion chambers 50, 51 are provided intermediate the condenser 46 and each cylinder 12,14 to provide an enlarged vacuum space adjacent to the steam chambers 24, 38 for facilitating the immediate expansion of steam from the steam chambers 24, 38 en route to the vacuum tank 48. A controlled vacuum of 15-20″ Hg in the vacuum tank will ensure an instantaneous rush of steam from the cylinder to vacuum producing a vacuum in the cylinder so that air pressure on the piston will make a vigorous power stroke.

In addition to solar collectors, steam at required pressures may also be obtained from geothermal sources and utilizing heat generated by nuclear waste, methane, or natural gas. Nuclear waste is typically stored in canisters having an ambient temperature of 300° F. By using heat exchangers, indefinite amounts of steam can be generated with good radiation control.

Considering first cylinder 12, when the first piston 16 is in the expanded position B, the steam chamber 24 is expanded to its maximum volume. Conversely when the first piston 16 is in the collapsed position A, the steam chamber 24 has its smallest volume. Similarly, when the second piston 30 of the second cylinder 14 is in the expanded position B′, the second steam chamber has its maximum volume. When the second piston is in the collapsed position A′, the second steam chamber 38 has its smallest volume. Entry of steam into the first steam chamber 24 is controlled by first steam valve 52 which, when open, admits steam from the steam reservoir 42. Entry of steam into the second steam chamber 38 is controlled by a second steam valve 54 when admits steam from the steam reservoir 42 when the valve is opened. When a first vacuum valve 56 is opened, the first steam chamber 24 is exposed to the steam expansion chamber 50, condenser 46, and finally, the vacuum tank 48. When a second vacuum valve 58 is opened, the second steam chamber 38 is exposed to the other steam expansion chamber 51, the condenser 46, and the vacuum tank 48.

With continuing reference to FIG. 1, a first switch X is electrically connected to the steam valves 52, 54 and to the vacuum valves 56, 58. When activated, the first switch closes the first vacuum valve 56 and the second steam valve 54, and opens the first steam valve 52 and the second vacuum valve 58. Hence, when the first switch X is activated, the first steam chamber 24 is placed in open communication with the steam reservoir 42 for admission of steam, and the second steam chamber 38 is put in communication with vacuum tank 48. Accordingly, any steam in the second steam chamber 38 will rush out to the steam expansion chamber 51 and on to the condenser 46 and vacuum tank 48, creating a vacuum in the second steam chamber 38. Ambient air therefore will drive the second piston 30 towards the collapsed position A′ which simultaneously moves the first piston 16 towards the expanded position B. It will be readily appreciated that the second piston 30 will not be able to complete the power stroke unless the first piston 16 is free to move from the collapsed position A to the expanded position B. Accordingly, closing the second steam valve 54 prevents steam from interfering with the vacuum in the second steam chamber 38, and closing the first vacuum valve 56 prevents steam in the first steam chamber 24 from going to vacuum.

A second switch Y is also electrically connected to the steam valves 52, 54 and to the vacuum valves 56, 58. When activated, the second switch Y closes the first steam valve 52 and the second vacuum valve 58, and opens the second steam valve 54 and the first vacuum valve 56. Hence, when the second switch Y is activated, the second steam chamber 38 is in open communication with the steam reservoir 42 for admission of steam, and the first steam chamber 24 is in communication with vacuum tank 48. In this state, any steam in the first steam chamber 24 will rush out through the steam expansion chamber 50 and on to the condenser 46 and vacuum tank 48, creating a vacuum in the first steam chamber 24, air pressure then driving the first piston 16 towards the collapsed position A and simultaneously moving the second piston 30 towards the expanded position B′. Obviously, the first piston 16 will not be able to complete the power stroke unless the second piston 30 is free to move from the collapsed position A′ to the expanded position B′. Closing the first steam valve 52 to prevent steam from interfering with the vacuum in the first steam chamber 24, and closing the second vacuum valve 58 to prevent steam in the second steam chamber 38 from going to vacuum, allows steam at atmospheric pressure to flow into the second steam chamber 38 thereby equalizing the pressure inside the steam chamber 38 with respect to outside air pressure and permitting the first cylinder 12 to perform work.

With reference now to FIG. 2, the relationship between valves, 52, 54, 56, 58, switches X, Y, and pistons 16, 30 is graphically illustrated. The initial status, indicated at the leftmost broken line B-A′, shows the mechanical condition of the valves and pistons immediately before that shown in FIG. 1. Broken line B-A′ indicates the exact point at which the first piston 16 is at the expanded position B and at which the second piston 30 is at the collapsed position A′. At that point, the first vacuum valve 56, the first steam valve 52, the second vacuum valve 58, and the second steam valve 54 are all closed. Within a very short increment of time, due to the immediately preceding activation of switch Y, the first vacuum valve 56 and the second steam valve 54 open. It will be appreciated that a delay may be built into the circuit to coordinate when the first vacuum valve 56 and the second steam valve 54 open relative to each other as suggested by the dotted line just to the left of the line indicating that the first vacuum valve 56 is open, and by the dotted line just to the right of the line indicating that the second steam valve 58 is open. As generally shown in FIG. 1, the first vacuum valve 56 will open a very short time before the second steam valve 58 is open. The timing will vary according to the mechanical nuances of different embodiments of the invention. It also will be obvious to one skilled in the art that the first steam chamber 24 must be primed with steam before commencing the first cycle of the engine, absent which there will be no steam to collapse to vacuum in the steam chamber when the first vacuum valve 56 opens. When the first vacuum valve 56 opens, the first piston 16 moves through a power stroke until just before broken line A-B′. During the power stroke the first steam valve 52 and second vacuum valve 58 are both closed.

Moving from left to right in FIG. 2, the second vertical broken line A-B′ indicates the point at which the first piston 16 is at the collapsed position A and at which the second piston 30 is at the expanded position B′. Immediately preceding that point, activation of switch X closes the second steam valve 54 and the first vacuum valve 56, terminating conditions for the first cylinder 12 to engage in a power stroke. As indicated by the dotted lines, a delay can be built in to the connections between switch X, on the one hand, and the second steam valve 54 and the first vacuum valve 56, on the other, to determine when the latter close relative to each other. Very quickly after the pistons reach the positions indicated by broken line A-B′, switch X opens the first steam valve 52 and the second vacuum valve 58. Accordingly, a vacuum occurs in the second steam chamber 38 permitting ambient air to drive the second piston 30 through a power stroke.

Immediately before the pistons reach the positions indicated by (the second) broken line B-A′, switch Y is activated, returning all valves to the closed position for beginning the cycle again. The timing of how close to the piston positions indicated by broken line B-A′ (and broken line A-B′) that the valves should be opened and closed is a matter of choice to be determined by the size and efficiency of a particular engine embodying the invention. Through a further delay in the circuit, activated switch Y opens the first vacuum valve 56 and the second steam valve 54 to repeat the power stroke in the first cylinder 12.

Referring to FIGS. 1 and 1A, a first controller 60 and a second controller 62 are pivotally linked together by horizontal bar 64 for simultaneous pivoting movement between a first position 66 indicated by the solid lines in FIG. 1A and a second position 68 indicated by the dashed lines in FIG. 1A. Intermediate first controller 60 and second controller 62, coupler 40 reciprocates in tandem with pistons 16, 30. As the coupler moves left, it engages the first controller 60, pivoting both controllers 60, 62 to the first position 66 and causing the second controller 62 to activate switch Y. Activation of switch Y, as explained above, drives the first cylinder 12 through a power stroke causing the pistons 16, 30 and, in turn, the coupler 40, to move from left to right. Towards the end of this movement, coupler 40 engages the second controller 62, pivoting both controllers 60, 62 to the second position 68 thereby causing the first controller 60 to engage and activate switch X as shown in FIG. 3A. This, of course, induces a power stroke in the second cylinder 14 which moves the coupler 40 back towards the first controller 60.

Applicant has determined that an operating prototype of a steam-to-vacuum engine according to the invention including cylinders having a 6″ diameter and a 13″ stroke average 120 strokes per minute. The Newcomen engine at its most rapid operation averaged 15 strokes per minute. It will be easily appreciated that the power output of a Newcomen engine having a 5 foot diameter cylinder and an 8 foot stroke will be exceeded by multiple cylinders of a two stroke steam-to-vacuum engine according to the invention.

FIG. 3 shows an alternate embodiment of a steam-to-vacuum engine according to the invention comprising a first cylinder 100 and a second cylinder 102. The first cylinder 100 has a first piston 104 and a first piston rod 106 connected to the first piston 104. The first piston 104 is moveable between a collapsed position A and an expanded position B defining the boundary of a first steam chamber 108. The second cylinder 102 has a second piston 110 and a second piston rod 112 connected to the second piston 110. The second piston is moveable between a collapsed position A′ and an expanded position B′ defining the boundary of a second steam chamber 114. The first and second piston rods 106,112 are connected by a coupler 116.

A boiler 120 provides steam for a steam reservoir 122. The steam reservoir 122 is connected to the first steam chamber 108 and the second steam chamber 114, respectively, by a first steam valve 124 and a second steam valve 126. A first expansion chamber 128 is in controlled communication with the first steam chamber 108 via a first vacuum valve 130. A second expansion chamber 132 is in controlled communication with the second steam chamber 114 via a second vacuum valve 134. The expansion chambers 128,132 are connected to a condenser 136. Cooling fluids flow into the condenser 136 at entry point 138, and flow out at exit point 140. A cooling fluid entry valve controls inflow of the cooling fluid into the condenser 136. Similarly, a cooling fluid exit valve controls the outflow of cooling fluid from the condenser.

A cooling fluid entry valve 142 controls entry of the cooling fluid into the condenser 136. Similarly, a cooling fluid exit valve 144 controls the outflow of cooling fluid from the condenser 136.

The condenser 136 is connected to a primary vacuum 146, exposure to which is controlled by a third vacuum valve 148. The primary vacuum 146 is in communication with a vacuum pump 150 controlled by a first vacuum pump valve 152. The condenser 136 is also connected to an auxiliary vacuum 154, exposure to which is controlled by a fourth vacuum valve 156. The auxiliary vacuum 154 is also connected to the vacuum pump 150, and communication between the auxiliary vacuum 154 and the vacuum pump 150 is controlled by second vacuum pump valve 158.

The primary vacuum 146 and auxiliary vacuum 154 are each connected to a condensate removal pump 160, access to which is controlled by first and second condensate removal valves 162,164, respectively. The condensate removal pump 160 is connected to a drain pan 166 for collection and, if desired, reuse of condensate.

In operation, steam exiting from one or the other of steam chambers 108, 114 flows first to one or the other of the expansion chambers 128, 132. The expansion chambers provide an expanded void more nearly proximate the steam chambers in order to facilitate the immediate rushing out of steam from the steam chambers 108, 114 by reducing pressure when the first and second vacuum valves 130, 134 are opened.

After passing through the expansion chambers 128, 132, steam flows through the condenser 136. There heat in the steam is transferred to and carried away by the cooling fluid circulating through the condenser, facilitating condensation of the steam to liquid condensate.

After passing through the condenser 136, the condensate will continue flowing through to the primary vacuum 146. Necessarily, the vacuum will require periodic replenishment which is accomplished by activating the vacuum pump 150. Condensate in the primary vacuum 146 drains by gravity out of the primary vacuum 146, is periodically pumped out of the system by the condensate removal pump 160, and is ultimately drawn off to the drain pan 166. The auxiliary vacuum 154 can be used to increase the volume of the operative vacuum that is available or be held ready for use in case of failure of the primary vacuum. Alternatively, it can be used to augment the primary vacuum. As with the primary vacuum 146, any condensate which accumulates in the auxiliary vacuum 154 drains by gravity out of the auxiliary vacuum 154, is pumped out of the system by the condensate removal pump 160, and is drawn off to the drain pan 166.

FIG. 4 shows an alternate embodiment of a steam-to-vacuum engine comprising a first cylinder 180 and a second cylinder 182. The first cylinder 180 has a first piston 184 and a first piston rod 186. The second cylinder 182 has a second piston 188 and a second piston rod 190 connected by a coupler 192. The pistons 184, 188 define first and second steam chambers 194, 196 in the first and second cylinders 180, 182, respectively. Steam is admitted to the first steam chamber 194 through a first steam valve 198, and to the second steam chamber 196 by a second steam value 200. The first steam chamber 194 is in communication with a vacuum controlled by first vacuum valve 202. The second steam chamber 196 is in communication with a vacuum through a second vacuum valve 204.

The coupler 192 is pivotally coupled to the lower end 206 of a pivot bar 208. The top of the pivot bar is pivotally attached about a dog and slat system 210 to a stationary beam 212. The pivot bar 208 is disposed intermediate opposing pickup knobs 214 which are, in turn, attached to a mechanism (not illustrated) for performing work. As the linked piston rods 186, 190 reciprocate the lower end 206 of the pivot bar 208 will likewise reciprocate pivoting the pivot bar relation to the beam. Accordingly, the pickup knobs 214 will be driven through a reciprocating action. Since the pickup knobs are interposed between the coupler 192 and beam 212, the force produced by the engine will be applied to the pivot points on a leveraged ratio.

FIG. 5 illustrates a fourth embodiment of the invention except that a base end 220 of a horizontal bar 222 is pivotally attached to the pivot bar 208. A distal end 224 of the horizontal bar is pivotally attached to the periphery of a wheel 226. As the coupler 192 engages in reciprocating motion, the base end 220 of the horizontal bar 224 reciprocates, forcing the distal end 224 of horizontal bar 224 to trace a circular path in the direction of the arrow.

FIG. 6 illustrates a fifth embodiment of the invention comprising two like oriented, parallel, spaced cylinders 230, 232 having first and second pistons 234, 236 and first and second piston rods 238, 240. In this embodiment, a connecting rod 240 is pivotally attached to the distal end 242 of each piston rod. The distal ends 244 of the extension members are rotatably attached to crank handles 246, 248. The two braces are in fixed and oppositely faced relation and are mutually rotatable in an axis perpendicular to the plane of motion of the piston rods. It will be readily understood that the power stroke of one piston will drive the other piston through a steam intake stroke as described above. The rotation of the fixed braces is therefore translated to an associated wheel 250 for performing work.

FIG. 7 shows a sixth embodiment of the invention very similar to that shown in FIG. 6 except that a third cylinder 252, piston 254, and piston rod 256 have been added. A third crank handle 258 is attached to the third piston 254 via the piston rod 256 and connecting rod 240. In this embodiment, the first piston 234 is in the collapsed position causing the first crank handle 246 to be in an innermost position (0°) along its rotation. The second piston has moved most of the way through a steam intake cycle towards the expanded position causing the second crank handle 248 to be positioned approximately 120° through a complete rotation and most of the way towards its outermost position (180°). The third piston 254 is beginning its movement through a power stroke and is still positioned near to, but is moving away from, the expanded position such that the third crank handle 258 has rotated an addition 120° relative to the second crank handle 248, or 240° relative to the first crank handle 246. This relative orientation of the three pistons and handles has the advantage that one cylinder of the three will always be moving through a power stroke driving the pistons in the other cylinders through the power stroke—steam intake stroke cycle, resulting in increased and more smoothly delivered power. It will be appreciated by those of skill in the art that the embodiments illustrated in FIGS. 6 and 7 are representative of embodiments of a two stroke steam-to-vacuum comprising a plurality of cylinders in which the pistons are connected for synchronous movement and that further embodiments of the invention including more than three cylinders are intended to be encompassed by the invention.

FIG. 8 shows a seventh embodiment of the invention comprising two opposing cylinders 270, 272 having pistons 274, 276 and piston rods 278, 280 joined by a coupler 282. The coupler in this embodiment is attached to a lateral axle on each end of which are provided dual side blocks 286 for guided sliding reciprocating movement along slide bars 288.

FIG. 9 illustrates an eighth embodiment of the invention comprising a first and second cylinder 300, 302, first and second pistons 304, 306, first and second piston rods 308, 310 joined by a coupler 312, the pistons defining the boundaries of first and second steam chambers 314, 318. In this embodiment, the steam and vacuum valves are connected to the steam chambers on the outer, rather than inner, ends of the respective cylinders. Thus, entry of steam into the first steam chamber 314 is controlled by a first steam valve 320 and entry of steam into the second steam chamber 318 is controlled by a second steam valve 322. Communication of the first steam chamber 314 with the vacuum is controlled by a first vacuum valve 324 and exposure of the second steam chamber 318 to the vacuum is controlled by a second vacuum valve 325.

As discussed above, air must be admitted into the air chambers 314, 318 to push pistons 304, 306 through a power stroke. Conversely, air must be freely released from the air chamber of a cylinder during a steam intake stroke to allow air to push the piston of the other cylinder through a power stroke. Generally, the full power stroke will be delayed until the air valves are opened. Air inflow tubing 326 on the inner ends of the first and second cylinders provides air to first and second air chambers 328, 330 on the rear sides of the pistons 304, 306. Inflow of air into the first air chamber 328 is controlled by a first air valve 332. Similarly, air inflow into the second air chamber 318 is controlled by a second air valve 334. A first check valve 336 is provided on the inner side of the first cylinder 300 in communication with the first air chamber 328. The first check valve 336 permits air to flow out from the first air chamber 328, but prevents admission of air into the air chamber at any pressure. Similarly, a second check valve 338 is provided on the inside end of the second cylinder 302 permitting outflow of air from the second air chamber 318, but prevent inflow of air into the air chamber. Air valves 332, 334 and check valves 336, 338 can be used to control the rate of movement of the pistons 304, 306. For example, restricting the flow of air into air chamber 328 as piston 304 is ready to move through a power stroke will slow or delay the power stroke. Alternately, blocking outflow of air from air chamber 330 by failing to open check valve 338 would create increased pressure in air chamber 330 that would delay the progress of piston 304 through a power stroke. Those of skill in the art will recognize that there are myriad ways to use air valves 332, 334 and check valves 336, 338 to control the rate of the reciprocating movement of pistons 304, 306. Relays may easily be associated with each valve to delay or advance the opening of that valve. Electronic control of any of the valves allows the invention to be controlled by a computer. It will be readily appreciated that a plurality of air valves and check valves can be attached to each cylinder according to the needs of particular situations or for enhanced control.

FIG. 10 shows a ninth embodiment of the invention wherein the first and second cylinders 350, 352 are arranged in parallel alignment. A transverse arbor 354 is attached to the distal ends of the first and second piston rods 356, 358. A gudgeon is 360 attached to the arbor 354 and a slide block 362 fixed to the gudgeon is mounted over two guide bars 366 for guided reciprocating motion. A connecting rod 364 is pivotally attached to the distal end of the gudgeon 360 about an axis perpendicular to the piston rods 356, 358. In regular operation of the device, as the piston rods 356, 358 engage in reciprocal movement, the arbor 354, gudgeon 360 and slide block 362 will move along the guide bars 366 for controlled positioning of the connecting rod 364. A distal end of the extension shaft 364 is pivotally attached to a crank handle 368, rotation of which turns a crank shaft 370 and, in turn, a wheel or gear 372 attached to the crank shaft 370 in order to perform work.

The first cylinder 350 shown in FIG. 10 is provided with access to steam and exposure to the vacuum via ports 374 on the left side of the cylinder. Accordingly, the position of the first piston 376 as shown in the expanded position is such that the steam chamber 378 is poised for a power stroke. Conversely, access to steam and exposure to the vacuum of the second cylinder 352 is provided via ports 380 on its right side. Accordingly, the second piston 382 is shown in the collapsed position at the end of a power stroke. Therefore, as the pistons 376, 382 move in parallel alignment, the extension shaft 364 engages in reciprocal motion which is translated to rotation of the crank handle 368. In regular operation, when the second cylinder 352 has completed a power stroke moving the pistons 376, 382 to the positions shown in FIG. 10, the extension shaft 364 will have rotated the crank handle 368 to the position shown in FIG. 10. After the first cylinder 350 has moved through a power stroke, driving the pistons 376, 382 to the positions shown in FIG. 11, the extension shaft 364 will have rotated the crank handle 368 to the position shown in FIG. 11.

FIG. 12 shows an eleventh embodiment of the invention wherein the first and second cylinders 390, 392 arranged in parallel relation and the steam valves 394, 396 and vacuum valves 398, 400 are connected to the air chambers on the inner ends of the cylinders. Air valves 402, 404 are provided on the outer ends of the cylinders 390, 392 for controlling admission of air into the air chambers of the cylinders as indicated by the arrows. Check valves 406, 408 are provided on the outer ends of the cylinders 390, 392 for controlling the escape of air from the cylinders. Check valves 406, 408 prevent air from entering the cylinders through the check valves, but allow air to escape from the cylinders as indicated by the immediately adjacent arrows. As discussed above, air valves 402, 404 and check valves 406, 408 can be used to control the rate of the reciprocating movement of pistons 410, 412 in the cylinders 390, 392. A vertical arm 414 extends upwardly from coupler 416, an upper part of the arm 414 pivotally joined to a link arm 418. A distal end 420 of the link arm 418 is pivotally attached to the periphery of a rotating wheel 422 such that reciprocal motion of the pistons 410, 412 is translated to rotational movement of the wheel 422.

FIG. 13 shows a twelfth embodiment of the invention wherein first and second cylinders 430, 432 are in parallel relation. A vertical arm 434 is attached to and extends upwardly from coupler 436. The upper end 438 of the vertical arm 434 is attached to a horizontal piston rod 440. At each end of the piston rod 440, pistons 442, 444 engage in reciprocal movement within vacuum pumps 446, 448 in tandem with pistons 450, 452 of the first and second cylinders 430, 432. Vacuum pumps 446, 448 are in communication with vacuum 450 such that reciprocal movement of the pistons 450, 452 will drive the piston rod 440 to operate the vacuum pumps 446, 448 to replenish the vacuum 450 automatically during operation of the engine.

FIG. 14 shows a thirteenth embodiment of a steam-to-vacuum engine according to the invention, comprising a first cylinder 500 and a second cylinder 502. The first cylinder 500 has a first piston 504 and a first piston rod 506 connected to the first piston 504. The first piston 504 is movable between a collapsed position A and an expanded position B, indicated by the dotted lines, defining the boundary of a first steam chamber 508. The second cylinder 502 has a second piston 510 and a second piston rod 512 connected to the second piston 510. The second piston is movable between a collapsed position A′, indicated by the dotted lines, and an expanded position B′ defining the boundary of a second steam chamber 514. The first and second piston rods 506, 512 are connected by a coupler 516.

A boiler 520 for providing steam is connected to the first steam chamber 508 through a first steam valve 522, and is connected to the second steam chamber 514 through a second steam valve 524. A first air valve 526 controls admission of air into first air chamber 528. Similarly, a second air valve 530 controls admission of air into second air chamber 532. Check valves 534 and 536 allow expulsion of air from air chamber 528 during a steam intake stroke in the first cylinder 500; check valves 538 and 540 allow expulsion of air from the second air chamber 532 during a steam intake stroke in the second cylinder 502. Check valves 534, 536, 538, 540 prevent air from returning to the air chambers 528, 532 except via air valves 526, 530.

The first steam chamber 508 is in controlled communication with vertical heat exchangers 544 and horizontal heat exchanger 546 through first vacuum valve 548. The second steam chamber 514 is in controlled communication with the vertical heat exchangers 544 and horizontal heat exchanger 546 through a second vacuum valve 550. Vertical heat exchangers 544 are disposed as nearly adjacent to steam chambers 508, 514 as practicable to facilitate the rush of steam out of the steam chambers at the beginning of each power stroke. Cooling fluid runs through the vertical heat exchangers 544 in the direction indicated by the arrows through cooling fluid pipe 552 to cool the environment inside the vertical heat exchangers. The vertical heat exchangers 544 are in direct communication with the horizontal heat exchanger 546, which, in turn, is in controlled communication with vacuum tank 554 through vacuum control valve 556. A condensate drain pipe 558 depends from the vertical heat exchangers 544 and extends downwardly to a condensate collector tank 560 for drainage by gravity of condensate collecting in the vertical heat exchangers 544 and steam chambers 508, 514 to the condensate collector tank 560. Condensate descending through the condensate drain pipe 558 is prevented from flowing into the horizontal heat exchanger 546 by an inverted U-shaped portion 562 of connector pipe 564. The inverted U-shaped portion is connected to the condensate drain pipe 558 by horizontal leg 566 such that steam is free to flow through pipe 564 to horizontal heat exchanger 546, but condensate is prevented from flowing into horizontal heat exchanger 546 by the inverted U-shaped portion 562, even if it has entered intervening leg 566.

Vacuum pump 570 is in communication with vacuum tank 554 and auxiliary vacuum tank 572. Vacuum pump valve 574 permits isolation of vacuum pump 570. Vacuum control valve 576 controls communication between vacuum pump 570 and vacuum tank 554. Vacuum control valve 632 controls communication between vacuum pump 570 and auxiliary vacuum tank 572. Vacuum control valve 580 controls communication directly between vacuum tank 554 and auxiliary vacuum tank 572. Vacuum tank condensate valve 582 controls communication between vacuum tank 554 and condensate collector tank 560. Condensate drain pipe control valve 584 controls communication through the condensate drain pipe 558 between vertical heat exchangers 544 and steam chambers 508, 514 and condensate collector tank 560.

Water is injected into vacuum tank 554 through injector 586 to assist in cooling vacuum tank 554. Residual condensate collecting in vacuum tank 554 drains by gravity through vacuum tank condensate pipe 588 via vacuum tank condensate valve 582 to condensate collector tank 560. Similarly, condensate drains from vertical heat exchangers 544 by gravity through condensate drain pipe 558 into condensate collector tank 560.

There are two methods, according to the invention, for removing condensate from the condensate collector tank 560. According to a first method, a volume 590 is sealed from communication with vacuum tanks 554, 572 by closing collector control valve 592. The volume 590 is then exposed to a holding chamber 594 by opening an expeller valve 596. The volume is then collapsed by moving piston 598 disposed in condensate collector tank 590 using piston rod 600. Collapsing volume 590 moves condensate collected therein into holding chamber 594. Holding chamber 594 is then sealed from the volume 590 in the condensate collector tank 560 by closing expeller valve 596. Water is expelled from the holding chamber 594 by opening air valve 602. It will be appreciated that water may be allowed to drain from the holding chamber 594 by gravity. Alternatively, it could be removed from the holding chamber by a pump. The holding chamber is then sealed from ambient air by closing the air valve 602, after which the holding chamber is exposed again to the volume 590 in the condensate collector tank 560 allowing air present in the holding chamber 594 to be admitted into volume 590. Volume 590 is then exposed to the vacuum by opening collector control valve 592, whereupon the vacuum is reestablished in the volume 590 of the condensate collector tank 560.

According to a second method for removal of condensate from the condensate collector tank 560, air is used to push the piston to collapse the volume 590. This method commences with first sealing a first volume 590 against communication with the vacuum by closing first collector control valve 592, then exposing first volume 590 to first holding chamber 594 by opening first expeller valve 596. A second volume 604 is then sealed against communication with the vacuum by closing second collector control valve 606. The second volume 604 is then exposed to ambient air by opening second expeller valve 608 and second air valve 610. Since second volume 604 is exposed to ambient air while first volume 590 is still under vacuum, the air pressure in the second volume expands the second volume 604, and simultaneously collapses first volume 590. Condensate in first volume 590 is thereby moved into first holding chamber 594. Condensate is removed from first holding chamber 594 in similar fashion as in the first method described above by sealing first holding chamber 594 from first volume 590 by closing first expeller valve 596, exposing holding chamber 594 to ambient air by opening first air valve 602, expelling the condensate from first holding chamber 594, and sealing first holding chamber 594 from ambient air by closing the first air valve 602. The second volume 604 is next sealed from ambient air by closing second expeller valve 608 and second air valve 610 capturing air in newly expanded second volume 604. First holding chamber 594 is then exposed to first volume 590 by opening first expeller valve 596, admitting air from holding chamber 594 into now collapsed first volume 590. Finally, the first volume 590 is exposed to vacuum by opening first collector control valve 592, and the second volume is exposed to the vacuum by opening the second collector control valve 606, whereby a vacuum is restored in both the first and second volumes 590, 604 of the condensate collector tank 560. It will be appreciated that this method can be reversed to remove condensate collected in second volume 604 by moving it into second holding chamber 605 for expulsion. Condensate removed from the condensate collector tank 560, according to either of the above methods, drains off to drain pans 612.

With continuing reference to FIG. 14, first and second auxiliary vacuum pumps 614, 616 each have an interior volume that is substantially smaller than the combined volumes of cylinders 500, 502. The first vacuum pump cylinder 614 includes a longitudinally movable vacuum pump piston 618. Similarly, the second auxiliary vacuum pump 616 includes a longitudinally movable second vacuum pump piston 620. A first vacuum pump piston rod 622 is connected to the first vacuum pump piston 618. A second vacuum pump piston rod 624 is connected to the second vacuum pump piston 620. Vacuum pump piston rods 622, 624 are connected by auxiliary connector 626, which is, in turn, rigidly connected to coupler 516 via power takeoff 628. Hence, movement of pistons 504, 510 drive movement of vacuum pump pistons 618, 620. Check valves 634 allow air to be pumped from the vacuum lines into the auxiliary vacuum pumps 614, 616, but prevent air from inadvertently entering the system. Check valves 635 allow air to be pumped out of the vacuum pumps but prevent air from entering the vacuum pumps. Valve 579 permits elective isolation of auxiliary vacuum pumps 614, 616 as needed, e.g., for maintenance.

The auxiliary vacuum pumps 614, 616 provide an alternative vacuum source driven by the power strokes in cylinders 500, 502. In a preferred mode of operation, the vacuum is delivered via auxiliary vacuum line 630 to auxiliary vacuum tank 572 by closing valve 632 to isolate the auxiliary vacuum tank 572 from the vacuum pump 570, closing valve 580 to isolate the auxiliary vacuum tank 572 from the vacuum tank 554 and closing vacuum tank condensate valve 582 and condensate drain pipe control valve 584 to isolate cylinders 500, 502, vertical heat exchangers 544, horizontal heat exchanger 546 and vacuum tank 554 from auxiliary vacuum tank 572, condensate collector tank 560 and auxiliary vacuum pumps 614, 616, while maintaining communication between vacuum tank 554 and vacuum pump 570. Thus, after condensate is removed from the condensate collector tank 560, according to one of the methods described above, air released into the engine will travel to the auxiliary vacuum tank, where the vacuum will be restored by the action of the auxiliary vacuum pumps 614, 616, without interfering with the vacuum in the vacuum tank 554 enabling the pistons 504, 510 to continue to operate without negative effect resulting from intrusion of air into the steam chambers 508, 514.

The embodiment illustrated in FIG. 14 has the significant advantage that an auxiliary vacuum system comprising the auxiliary vacuum tank 572 and auxiliary vacuum pumps 614, 616 can work independently to restore the vacuum in the condensate collector tank after condensate has been drained from the system. Accordingly, the vacuum tank 554 will continue to supply a vacuum to the horizontal heat exchanger 546, pistons 500, 502 and vertical heat exchangers 544. When air is introduced into the engine system as a result of draining condensate out of the condensate collector tank 560, the auxiliary vacuum tank alone can be used to restore the vacuum to the condensate collector tank.

There have thus been described certain preferred embodiments of a steam-to-vacuum engine. While preferred embodiments have been described and disclosed, it will be recognized by those with skill in the art that modifications are within the true spirit and scope of the invention. The appended claims are intended to cover all such modifications.

Claims

1. A two stroke steam-to-vacuum engine comprising: a plurality of cylinders, each cylinder having a steam chamber and a piston bounding said steam chamber, said piston moveable between an expanded position and a collapsed position, a power stroke defined by movement of said piston from said expanded position to said collapsed position, a steam intake stroke defined by movement of said piston from said collapsed position to said expanded position, a vacuum, a first plurality of valves controlling exposure of said steam chamber to said vacuum during said power stroke, a second plurality of valves controlling admission of steam into said steam chamber during said steam intake stroke, said plurality of pistons connected for synchronous movement, and said power stroke in one of said plurality of cylinders driving movement of said pistons in the other of said plurality of cylinders.

2. The two stroke steam-to-vacuum engine of claim 1 further comprising: at least one vertical heat exchanger in controlled communication with said steam chamber of each of said plurality of cylinders, said at least one vertical heat exchanger in communication with said vacuum.

3. The two stroke steam-to-vacuum engine of claim 2 wherein: said vertical heat exchanger having a horizontal width and a vertical dimension greater than said width.

4. The two stroke steam-to-vacuum engine of claim 3 wherein: at least one vertical heat exchanger is in proximate disposition to each of said plurality of cylinders.

5. The two stroke steam-to-vacuum engine of claim 3 further comprising: at least one cooling pipe for circulating cooling fluid, said at least one cooling pipe disposed in said at least one vertical heat exchanger.

6. The two stroke steam-to-vacuum engine of claim 3 further comprising: a horizontal heat exchanger having a first port for communication with said at least one vertical heat exchanger and with said plurality of cylinders and a second port for communication with said vacuum.

7. The two stroke steam-to-vacuum engine of claim 2 wherein: said at least one vertical heat exchanger comprises a plurality of vertical heat exchangers.

8. The two stroke steam-to-vacuum engine of claim 1 further comprising: a condensate collector tank in controlled communication with said plurality of cylinders.

9. The two stroke steam-to-vacuum engine of claim 2 further comprising: a condensate collector tank in communication with said at least one vertical heat exchanger, said condensate collector tank disposed below said vertical heat exchanger.

10. The two stroke steam-to-vacuum engine of claim 9 further comprising: a condensate drain pipe depending from said at least one vertical heat exchanger and extending to said condensate collector tank, and a vacuum connector pipe having a horizontal leg and an inverted U-shaped section, said horizontal leg having a first end connected to said condensate drain pipe and a second end connected to said U-shaped section, said U-shaped section in communication with said vacuum.

11. The two stroke steam-to-vacuum engine of claim 10 further comprising: said vacuum comprising a vacuum tank, and a horizontal heat exchanger in communication with said vacuum tank, said U-shaped section of said vacuum connector pipe connected to said horizontal heat exchanger.

12. The two stroke steam-to-vacuum engine of claim 9 further comprising: said condensate collector tank having a first side, a second side, an interior surface and a piston, said piston moveable longitudinally between a first position adjacent said first side and a second position adjacent said second side, movement of said piston between said first and second positions sweeping said interior surface for removal of condensate.

13. The two stroke steam-to-vacuum engine of claim 12 further comprising: said piston bounding a first volume adjacent said first side and a second volume adjacent said second side, a first collector control valve controlling communication between said first volume and said at least one vertical heat exchanger, a second collector control valve controlling communication between said second volume and said at least one vertical heat exchanger, a first expeller valve in communication with said first volume of said condensate collector tank, a first air valve in communication with said first expeller valve, said first air valve controlling exposure of said first expeller valve to ambient air, a second expeller valve in communication with said second volume of said condensate collector tank, a second air valve in communication with said second expeller valve, said second air valve controlling exposure of said second expeller valve to ambient air.

14. The two stroke steam-to-vacuum engine of claim 1 further comprising: said vacuum comprising a vacuum tank, said vacuum tank having and interior and a injector for introducing water into said interior.

15. The two stroke steam-to-vacuum engine of claim 1 further comprising: each of said plurality of cylinders having an interior volume, an auxiliary vacuum tank, at least one auxiliary vacuum pump, said auxiliary vacuum pump having a vacuum pump cylinder and a vacuum pump piston, said vacuum pump cylinder having an interior volume substantially smaller than the combined interior volume of all of said plurality of cylinders, said vacuum pump piston movable longitudinally in said vacuum pump cylinder between a first position and a second position, said vacuum pump piston connected to said plurality of pistons for synchronous movement, and a check valve in communication with said at least one auxiliary vacuum pump and with said auxiliary vacuum tank, said check valve preventing exposure of said auxiliary vacuum tank to air from said at least one auxiliary vacuum pump.

16. The two stroke steam-to-vacuum engine of claim 15 further comprising: a condensate collector tank in controlled communication with said plurality of cylinders, said auxiliary vacuum tank in communication with said condensate collector tank.

17. The two stroke steam-to-vacuum engine of claim 1 further comprising: a vacuum pump, a vacuum tank in communication with said plurality of cylinders and with said vacuum pump, a condensate collector tank in communication with said plurality of cylinders and with said vacuum tank, an auxiliary vacuum tank in communication with said vacuum pump, with said vacuum tank, and with said condensate collector tank, at least one auxiliary vacuum pump driven by movement of said pistons, said at least one auxiliary vacuum pump in communication with said auxiliary vacuum tank, and a third plurality of valves for isolating said vacuum tank from said auxiliary vacuum tank and from said condensate collector tank.

18. A two stroke steam-to-vacuum engine comprising: a plurality of cylinders, each of said plurality of cylinders having an interior volume, each cylinder having a steam chamber and a piston bounding said steam chamber, said piston moveable between an expanded position and a collapsed position, a power stroke defined by movement of said piston from said expanded position to said collapsed position, a steam intake stroke defined by movement of said piston from said collapsed position to said expanded position, a primary vacuum tank, a first plurality of valves controlling exposure of said steam chamber to said primary vacuum tank during said power stroke, a second plurality of valves controlling admission of steam into said steam chamber during said steam intake stroke, said plurality of pistons connected for synchronous movement, said power stroke in one of said plurality of cylinders driving movement of said pistons in the other of said plurality of cylinders, a condensate collector tank in communication with and disposed below said plurality of cylinders, an auxiliary vacuum tank, at least one auxiliary vacuum pump, said auxiliary vacuum pump having an auxiliary vacuum pump cylinder and an auxiliary vacuum pump piston, said vacuum pump cylinder having an interior volume substantially smaller than the combined interior volume of all of said plurality of cylinders, said auxiliary vacuum pump piston movable longitudinally in said vacuum pump cylinder between a first position and a second position, said auxiliary vacuum pump piston connected to said plurality of pistons for synchronous movement, and a check valve in communication with said at least one auxiliary vacuum pump and with said auxiliary vacuum tank, said check valve preventing exposure of said auxiliary vacuum tank to air from said at least one auxiliary vacuum pump.

19. The two stroke steam-to-vacuum engine of claim 18 further comprising: said plurality of cylinders including a first cylinder having a first piston and a second cylinder having a second piston, a first piston rod attached to said first piston, a second piston rod attached to said second piston, and a coupler connecting said first and second pistons in linear relation.

20. The two stroke steam-to-vacuum engine of claim 19 further comprising: said at least one auxiliary vacuum pump including a first auxiliary vacuum pump and a second auxiliary pump, said first auxiliary vacuum pump including a first auxiliary vacuum pump cylinder, a first auxiliary vacuum pump piston and a first auxiliary vacuum pump piston rod connected to said first auxiliary vacuum pump piston, said second auxiliary vacuum pump including a second auxiliary vacuum pump cylinder, a second auxiliary vacuum pump piston and a second auxiliary vacuum pump piston rod connected to said second auxiliary vacuum pump piston, said first and second auxiliary vacuum pump pistons connected in linear relation and connected to said coupler.

21. A method for removing condensate from a two stroke steam-to-vacuum engine, the steam-to-vacuum engine of the type having a plurality of cylinders, each cylinder having a steam chamber and a piston bounding said steam chamber, the piston moveable between an expanded position and a collapsed position, a power stroke defined by movement of the piston from the expanded position to the collapsed position, a steam intake stroke defined by movement of the piston from the collapsed position to the expanded position, a vacuum, a first plurality of valves controlling exposure of the steam chamber to the vacuum during the power stroke, a second plurality of valves controlling admission of steam into the steam chamber during the steam intake stroke, the plurality of pistons connected for synchronous movement, and the power stroke in one of the plurality of cylinders driving movement of the pistons in the other of said plurality of cylinders, the method comprising: sealing a volume in a condensate collector tank against communication with the vacuum, exposing said volume to a holding chamber, collapsing said volume, moving condensate in said volume into said holding chamber, sealing said holding chamber from said volume, exposing said holding chamber to ambient air, expelling condensate from said holding chamber, sealing said holding chamber from ambient air, exposing said holding chamber to said volume, and exposing said volume to the vacuum.

22. A method for removing condensate from a two stroke steam-to-vacuum engine, the steam-to-vacuum engine of the type having a plurality of cylinders, each cylinder having a steam chamber and a piston bounding said steam chamber, the piston moveable between an expanded position and a collapsed position, a power stroke defined by movement of the piston from the expanded position to the collapsed position, a steam intake stroke defined by movement of the piston from the collapsed position to the expanded position, a vacuum, a first plurality of valves controlling exposure of the steam chamber to the vacuum during the power stroke, a second plurality of valves controlling admission of steam into the steam chamber during the steam intake stroke, the plurality of pistons connected for synchronous movement, and the power stroke in one of the plurality of cylinders driving movement of the pistons in the other of said plurality of cylinders, the method comprising: sealing a first volume in a condensate collector tank against communication with the vacuum, said first volume bounded by an interior surface of said condensate collector tank and a piston, exposing said first volume to a holding chamber, sealing a second volume in said condensate collector tank against communication with the vacuum, said second volume bounded by said interior surface and said piston, exposing said second volume to ambient air, expanding said second volume and simultaneously collapsing said first volume, moving condensate in said first volume into said holding chamber, sealing said holding chamber from said first volume, exposing said holding chamber to ambient air, expelling said condensate from said holding chamber; sealing said holding chamber from ambient air, sealing said second volume from ambient air, exposing said holding chamber to said first volume, exposing said first volume to the vacuum, and exposing said second volume to the vacuum.