KR20020005609A - Variable stroke motor and valve - Google Patents

Abstract

The fluid valve shaft 16 is provided to the variable stroke motor 10. The valve shaft 16 has a cylinder 14, a first fluid inlet 18 into the cylinder 14, a first fluid outlet 20 from the cylinder 14, and a into the cylinder 14. A second fluid inlet 22, and a second fluid outlet 24 from the cylinder 14. Within the cylinder 14 is provided a valve shaft 16 provided with slots 26, 28, 90 and 92. When the valve shaft 16 rotates to the first position, the fluid communication between the first fluid inlet 18 and the first fluid outlet 20 is interrupted, and the second fluid inlet 22 and the second fluid inlet are blocked. The fluid communication between the fluid outlets 24 is opened. When the valve shaft 16 rotates to the second position, the communication portion between the first fluid inlet 18 and the first fluid outlet 20 is opened, and the second fluid inlet 22 and the second fluid are open. The communication between the outlets 24 is cut off. The device is preferably hooked with a drive cylinder 48 in fluid communication between the first fluid outlet 20 and the second fluid inlet 22. A piston 52 is provided in the drive cylinder 48. The fluid supply is operably coupled to the first fluid inlet 18 and means 42 are provided to rotate the valve shaft 16 at a constant speed. As the pressure of the fluid increases, the stroke of the piston 52 increases, resulting in a longer piston stroke, and the speed of the rotary valve shaft 16 is constant.

Description

Variable stroke motors and valves {VARIABLE STROKE MOTOR AND VALVE}

In conventional internal combustion piston-type apparatus, it is known to inject liquid hydrocarbons into the piston assembly, form a vacuum strong enough to pull the pistons outwards to vaporize the hydrocarbons, and then compress the hydrocarbons before combustion. . Since combustion of hydrocarbons typically generates waste and consumes most of the oxidant in the piston assembly, the operation of removing the waste and introducing fresh oxidant into the piston assembly must be carried out before further combustion of the hydrocarbon.

One disadvantage associated with internal combustion engines is the pollution caused by such engines (engines). In addition, since fuel is typically not completely burned in an internal combustion engine, waste deposits accumulate in the piston, which reduces engine efficiency or requires regular maintenance of the engine.

Another disadvantage associated with internal combustion engines relates to the speed range in which conventional internal combustion engines operate. Since the internal combustion engine is operated based on a predetermined stroke distance, the combustion force (explosion force) should be sufficient to move the piston at least by the predetermined stroke distance. However, the force does not have to be too large or the parts of the internal combustion engine will be damaged. You can manipulate the "force" of the stroke, but usually the stroke of the internal combustion engine cannot be changed. Thus, vehicles powered by an internal combustion engine usually require clutches and gears to step up or down the rotational energy generated by the internal combustion engine.

The difficulties faced by the prior art mentioned above can be substantially eliminated by the present invention. The present invention provides a variable stroke motor with a constant speed rotary valve, to reduce the disadvantages associated with conventional combustion engines and to increase efficiency.

The present invention relates generally to valves and their associated piston actuated motors, and more particularly to variable stroke motors and valves that rotate at a constant speed.

1 is a side cross-sectional view showing a valve assembly and a piston assembly of the present invention.

FIG. 2 is a perspective view of the valve assembly and piston assembly of FIG. 1. FIG.

3 is an exploded view of the valve assembly and piston assembly of FIG. 2;

4 is a top view of the valve and piston assembly of FIG.

According to the present invention, a fluid valve system includes a hollow cylinder, a first fluid inlet in fluid communication with the hollow cylinder, a first fluid outlet in fluid communication with the hollow cylinder, and a fluid communication with the hollow cylinder. A valve housing having a second fluid inlet and a first fluid outlet in fluid communication with the hollow cylinder; A first position located in the hollow cylinder and substantially sealing the fluid communication portion between the first fluid inlet and the first fluid outlet and a first position substantially sealing the fluid communication between the second fluid inlet and the second fluid outlet; A shaft rotatable between two positions, and means coupled to the shaft to rotate the shaft between the first position and the second position; The shaft has a first slot and a second slot; A first slot on the shaft is oriented in such a way as to open a fluid communication between the first fluid inlet and the second fluid outlet when the shaft is in the second position; When in position, it is oriented in a manner that opens the fluid communication between the first fluid inlet and the first fluid outlet.

Referring to the accompanying drawings, the variable stroke motor is denoted by reference numeral 10 as a whole in FIG. As shown in FIG. 3, the variable stroke motor includes a valve housing 12. In a preferred embodiment, the valve housing 12 is made of aluminum and has a hollow cylinder 14 for receiving the valve shaft 16. The valve housing 12 is configured to form a first fluid inlet 18 in fluid communication with the hollow cylinder 14 and a first fluid outlet 20 in fluid communication with the hollow cylinder 14. As shown in FIG. 1, the valve housing 12 is also formed with a second fluid inlet 22 and a second fluid outlet 24.

As shown in FIG. 3, the valve shaft 16 has a first slot 26 and a second slot 26. The valve shaft 16 also has a first ring seat 30, a second ring seat 32, and a third ring seat 34. The first ring seating portion 30, the second ring seating portion 32, and the third ring seating portion 34, 3 for preventing fluid from flowing out between the valve shaft 16 and the hollow cylinder 14. Tefron rings 36, 38, 40 are provided.

As shown in FIG. 2, a shaft rotor 42 is fixed to the valve housing 12, which is operably fixed to a key 44 extending from the valve shaft 16 shown in FIG. 3. . The shaft rotor 42 may be a small electric motor or other similar rotating device known in the art.

As shown in FIG. 3, the first slot 26 and the second slot 28 of the valve shaft 16 are disposed opposite the valve shaft 16. Thus, as shown in FIG. 1, when the valve shaft 16 is located in the hollow cylinder 14 of the valve housing 12, the second slot 28 is connected to the second fluid inlet 22 and the second. Open fluid communication between the fluid outlets 24. As shown in FIG. 1, when the second slot 28 opens the fluid communication portion between the second fluid inlet 22 and the second fluid outlet 24, the first slot 26 is a valve housing ( 12) completely covered (see FIGS. 1 and 3). Thus, the portion of the valve shaft 16 opposite the first slot 26 blocks the fluid communication between the first fluid inlet 18 and the first fluid outlet 20.

Similarly, when the shaft rotor 42 rotates the valve shaft 16 by 180 degrees, the first slot 26 connects the fluid communication between the first fluid inlet 18 and the first fluid outlet 20. While open, the portion of the valve shaft 16 opposite the second slot 28 blocks the fluid communication between the second fluid inlet 22 and the second fluid outlet 28. In a preferred embodiment, the slots 26 and 28, the inlets 18 and 22 and the outlets 20 and 24 are provided with fluid communication between the first fluid inlet 18 and the first fluid outlet 20. It is sized so that the fluid communication between the second fluid inlet 22 and the second fluid outlet 24 when closed is closed. Similarly, when the fluid communication portion between the second fluid inlet portion and the second fluid outlet portion 24 is opened, the fluid communication portion between the first fluid inlet portion 18 and the first fluid outlet portion 20 is closed.

As shown in FIG. 1, a drive housing 46, which forms a drive cylinder 48, is fixed to the valve housing 12. In a preferred embodiment, the drive housing 46 consists of a seamless tubing made of stainless steel. Preferably, the drive housing 46 is fixed to the drive box 50, which preferably consists of aluminum. The piston 52 is provided in the drive cylinder 48. The piston 52 is preferably composed of an aluminum cap 54 and an aluminum base 56. Since the piston 52 is wobble-type, the piston 52 has a plastic seal ring 58, which seal seals between the seal ring 58 and the drive housing 46. While retaining, the piston 52 can be pivoted two degrees from a position perpendicular to the central axis of the drive cylinder 48.

The piston rod 60, which preferably consists of hardened metal, is fixed to the piston 52 by means of a set screw 62 (FIG. 1). As shown in FIG. 3, the piston rod 60 is provided with an eyelet 62 and fits inside the yoke 64 of the swing arm 66. Inside the eyelet 62 is provided a needle roller bearing 68 or similar bearing well known in the art to reduce friction. The needle roller bearing 68 is located inside the eyelet 62, and the eyelet 62 is located inside the yoke 64, and a dowel pin 70 formed by heat treatment is a first eyelet of the yoke 64. 72, penetrating through the needle roller bearing 68 and the second eyelet 74 of the yoke 64. The dowel pin is preferably composed of steel heat treated to withstand the large pressures caused by the action of the piston rod 60. Swing arm 66 is preferably constructed of heat-treated steel and is provided with large holes 76 to accommodate a pair of drive sprags 78. The drive sprag 78 transfers rotational energy from the swing arm 66 to the drive shaft 80 when in the drive stroke and the drive shaft 80 is " free wheel " freewheel ”so that the drive shaft 80 is not rotated in the opposite direction and is connected to the drive shaft 80. As shown in FIG. 2, drive shaft 80 extends through drive box 50 to power a vehicle or any other driveable device.

The first fluid inlet 18, operably connected to the fluid communication section, is a fluid pressure generator 82 (FIG. 2). In the preferred embodiment, the pressure generator 82 is a steam generator, but of course the pressure generator 82 can be any similar device. The fluid pressure generator 82 is connected to the first fluid inlet 18 via a delivery hose 84 (FIGS. 2 and 3). In a preferred embodiment, the second fluid outlet 24 is also connected to the fluid pressure generator 82 by a replenishment delivery hose 86.

As shown in FIG. 2, the variable stroke motor 10 is also provided with a supplemental valve and piston assembly 88. The supplemental valve and piston assembly 88 is substantially the same as the assembly described above. However, as shown in FIG. 3, the valve shaft 16 has a third slot 90 and a fourth slot opposite to the first slot 26 and the second slot 28 on the valve shaft 16. 92). The position of these slots 26, 28, 90, 92 drives the piston 52 as described above when the replenishment valve and piston assembly 88 recovers, and when the replenishment valve and piston assembly 88 drives. Let's do it. This complementary operation of the pistons 52, 94 causes the drive shaft 80 to be driven substantially continuously by one of the two pistons 52, 94.

As shown in FIG. 4, the recovery springs 96, 98 return the swing arm 66 and swing arm 100 of the supplemental valve and piston assembly 88 to the starting position described above. As each swing arm 66, 100 makes selective movement to the starting position, the swing arms 66, 100 also move their corresponding pistons 52, 94 to the starting position. Recovery springs 96 and 98 are secured to drive box 50 around drive shaft 80. Each recovery spring 96, 98 is provided with recovery arms 102, 104 and securing fingers 106, 108. First, after the recovery springs 96, 98 are secured to the drive box 50, the fingers 106, 108 are positioned inside the holes 110, 112 provided in the swing arms 66, 100. As shown in FIG. 4, the drive shaft 80 is connected to the inner periphery of the pair of drive sprags 114 and then to the swing arm 100 around its outer periphery. The drive sprag 114 is oriented like the swing arm 100 driven by the piston 94, and the drive sprag 114 transmits the rotational movement of the swing arm 100 to the drive shaft 80. During the recovery stroke, the drive sprags 114 allow the recovery spring 96 to return the swing arm 100 to its starting position without transferring a large amount of rotational energy to the drive shaft 80. "do.

An anti-backlash sprag 116 secures the drive shaft 80 between the swing arms 66, 100, thereby rotating between the swing arms 66, 100 and the drive shaft 80. To further reduce the transfer of energy. As shown in FIG. 4, the anti-reverse sprag 116 is fixed to the drive box 50 inside the drive shaft opening 118 provided in the drive box 50 between the swing arms 66, 100. do.

The anti-reverse sprag 116 is fixed to the drive box 50 by welding or other similar fastening means. The anti-reverse sprag 116 is similar in configuration to the drive sprag 114 but is connected to the drive shaft 80 in the direction of operation opposite to the drive sprag 114. Thus, when the swing arm 100 is in the drive stroke, the drive sprags 114 transmit rotational energy of the swing arm 100 to the drive shaft 80. During this drive stroke, the anti-reverse sprag 116 is free to rotate the drive shaft 80 while being in the orientation of the "free wheel". After swing arm 100 has completed its drive stroke once, recovery spring 96 returns swing arm 100 to its starting position. As the recovery spring 96 rotates the swing arm 100, the drive sprags 114 limit the rotational energy transmitted from the swing arm 100 to the drive shaft 80 and drag on the recovery spring 96. Is oriented with a "free wheel" to decrease).

The anti-reversal spring 116 provides for preventing any further rotation in the direction in which the drive shaft 80 restores the swing arm 100. If the friction between the drive sprag 114 and the drive shaft 80 is large enough to transfer some rotational energy from the drive sprag 114 to the drive shaft 80 during the recovery stroke of the swing arm 100. In this case, the anti-reverse sprag 116 prevents rotation of the drive shaft 80. Since the anti-reverse sprag 116 is welded to the drive box 50, the anti-reverse sprag 116 may be applied to the drive box 50 at any “backward” rotational energy of the drive shaft 80. And prevents rotation of the drive shaft 80 in the direction of swing arm 100 recovery.

The anti-reverse sprag 116 also prevents the reverse rotation of the drive shaft 80 until one of the swing arms 66, 100 begins to rotate the drive shaft 80 during the drive stroke. In this way, the anti-reverse sprag 116 ensures that the drive shaft 80 rotates in only one direction.

To operate the variable stroke motor 10 of the present invention, the shaft rotor 42 is actuated to rotate the valve shaft inside the hollow cylinder 14. The fluid pressure generator 82 is then activated to supply pressurized fluid, such as steam, to the first fluid inlet 18 and the auxiliary valve and piston assembly 88. When fluid is supplied to the first fluid inlet 18 at low pressure, a small amount of fluid is opened as the first slot 58 opens fluid communication between the first fluid inlet 18 and the first fluid outlet 20. Fluid enters the drive cylinder 58. This inflow of fluid into the drive cylinder 48 forces the piston 52 to be spaced apart from the valve housing 12. As the swing arm 66 rotates, the eyelet 62 of the piston rod pivots slightly as the swing arm 66 reciprocates. This pivoting movement of the piston rod 60 causes the entire piston 52 to be slightly inclined relative to the drive cylinder 48. To reduce this inclination, the piston 52 is arranged such that the piston 52 is somewhat inclined at both the start position and the end position of the piston. This reduces the inclination of the piston 52 when the piston is located at the center of the full stroke. The swing arm 66 and the piston rod 60 are preferably configured to have a length sufficient to position the piston in the starting position, the piston 52 being two degrees from the top with respect to the central axis of the drive cylinder 48. Incline

To check the inclination of the piston 52, it is desirable to inspect the full stroke of the piston 52 when fluid is applied to the first fluid inlet 18 at the full stroke. As fluid begins to be injected into the drive cylinder 48, the piston 52 is moved away from the valve housing 12 toward the swing arm 66, thereby causing the swing arm 66 to pressurize and rotate. As the swing arm 66 rotates, the piston rod 60 pivots inside the yoke 64 of the swing arm 66. The piston 52 rotates continuously until it is perpendicular to the center axis of the drive cylinder 48. This occurs when the piston 52 is one quarter of the path through the full stroke of the piston 52.

As the fluid flows further into the drive cylinder 48, the piston 52 is continuously spaced apart from the drive shaft 80 until the piston 52 reaches the intermediate path through the full stroke as shown in FIG. 1. Pivot the movement. At this point, the piston 52 is inclined two degrees from perpendicular to the axis of the drive cylinder 48 but is located in the direction opposite to the two degree orientation of the starting point. When the drive cylinder 48 is continuously filled with fluid, the swing arm 66 further rotates until the piston 52 reaches three quarters of the path through the full stroke. At this point, the piston 52 has rotated sufficiently to be perpendicular to the center axis of the drive cylinder 48 again. When the drive cylinder 48 is continuously filled with fluid, the swing arm 66 rotates continuously and the piston 52 moves in a 2 degree position perpendicular to the center axis of the drive cylinder 48. This two degree inclination is equal to the position of two degrees from the vertical orientation of the piston 52 at the start of the previous stroke. Under the pressure of the full fluid, this full stroke occurs whenever fluid communication is opened between the first fluid inlet 18 and the first fluid outlet (FIG. 3).

Thus, the piston 52 is oriented perpendicular to the central axis of the drive cylinder 48 in the starting position, and instead of pivoting the piston 52 at a large angle as the swing arm 66 rotates through the cycle, The piston 52 is oriented to start at an angle of 2 degrees from vertical. In this way, the piston 52 starts at a position of 2 degrees from the vertical and cycles through the vertical position, at the position of vertical and 2 degrees in the opposite direction, at another position in the vertical, and finally at the position of 2 degrees in the same direction as the starting position. do. In this way, the total amount of deviation from the vertical position is kept to the minimum throughout the entire stroke.

The variable stroke motor 10 can fully cycle through the above-described full stroke, but this full stroke is realized only under full fluid pressure. When only a small amount of pressure is applied to the first fluid inlet 18, the piston 52 moves through a shorter stroke cycle. As the pressure of the fluid provided by the fluid pressure generator 82 increases, the drive cylinder 48 through the first fluid outlet 20 from the first fluid inlet 18 by each rotation of the valve shaft 16. A larger amount of fluid passes through it. This larger amount of fluid enters the drive cylinder 48, so that the faster the piston moves, the longer the stroke. Swing arm 66 translates this longer stroke into a greater rotation of drive shaft 80. Since the shaft rotor 42 rotates the valve shaft 16 at a constant speed, each cycle consumes the same amount of time regardless of whether the fluid pressure is applied. Thus, greater rotation of the drive shaft 80 at the same amount of time translates to greater speed of the drive shaft 80.

For each rotation of the valve shaft 16, a second slot 28 provided on the valve shaft 16 opens the fluid communication between the first fluid inlet 22 and the second fluid outlet 24 ( 1). During this period, the swing arm 66 presses the piston rod 60 into the piston 52 by the force of the recovery spring 96 to push the fluid out of the drive cylinder 48. Thereafter, the fluid is returned to the fluid pressure generator 82 via the auxiliary transfer hose 86, whereby the fluid can be pressurized back through the motor 10 and recycled (FIG. 2). When the piston 52 is driven, the auxiliary valve and piston assembly 88 operate reciprocally to drive the drive shaft 80 when the piston 52 is in the recovery stroke. As noted above, anti-backlash sprag 116 prevents swing arms 66 and 98 from transmitting rotational energy to drive shaft 80 during the recovery stroke.

Since the valve shaft 16 rotates at a constant speed, the piston 52 strokes a longer distance by varying the amount of fluid pressure entering the first fluid inlet 18, thereby allowing a greater distance for the same period. Let drive shaft 80 drive. The fluid pressure generator 82 is provided with a heat control controller 120, such as a propane valve, to change the pressure of the fluid by varying the amount of heat transferred to the fluid pressure generator 82. Thus, the variable stroke motor 10 can directly convert a greater amount of thermal energy into faster rotation of the drive shaft 80.

The foregoing description and drawings are merely for describing the present invention, and the present invention is not limited to the above description and drawings except as limited by the claims, and the person skilled in the art having the disclosure of the present specification Modifications and variations may be made without departing from the spirit of the invention. For example, any number of auxiliary valve and piston assemblies may be coupled to the drive shaft 80, and a wide variety of dimensions are available for slots in the valve shaft and for fluid inlets and fluid outlets of the valve housing. Do.

Claims (20)

A fluid valve system, (Iii) hollow cylinder, (Ii) a first fluid inlet in fluid communication with the hollow cylinder, (Iii) a first fluid outlet in fluid communication with the hollow cylinder, (Iii) a second fluid inlet in fluid communication with the hollow cylinder, (Iii) a valve housing containing a second fluid outlet portion in fluid communication with the hollow cylinder; A shaft disposed within the hollow cylinder, the shaft having a first position substantially sealing a fluid communication portion between the first fluid inlet and the first fluid outlet, and the second fluid inlet and the second fluid A shaft rotatable between a second position that substantially seals the fluid communication between the outlets, and Means coupled to the shaft for rotating the shaft between the first and second positions, The shaft is provided with a first slot and a second slot, The first slot is oriented in the shaft in such a way as to open a fluid communication between the first fluid inlet and the second fluid outlet when the shaft is in the second position, And the second slot is oriented in the shaft in such a way as to open a fluid communication between the first fluid inlet and the first fluid outlet when the shaft is in the second position. The fluid valve system of claim 1 further comprising means for supplying fluid to the first fluid inlet. 3. The fluid valve system of claim 2 further comprising means for varying the pressure at which the fluid is supplied to the first fluid inlet. 2. The fluid valve system of claim 1, further comprising a drive housing defining a drive cylinder in fluid communication with the first fluid outlet and the second fluid inlet. 5. The fluid valve system of claim 4 further comprising a piston disposed within the drive cylinder. 6. The piston of claim 5 wherein said piston is provided to maintain a substantial fluid tight seal between said piston and said drive housing when said piston rotates at least two degrees from a position perpendicular to a continuous axis through said drive cylinder. The fluid valve system further comprising means. 7. The piston of claim 6 wherein the piston comprises a piston cap secured to a piston rod, (a) a swinging arm fixed to the piston rod to pivot; (b) the drive shaft, and and (c) a sprag operatively fixed between the swing arm and the drive shaft. 8. The fluid valve system of claim 7 further comprising a reversing sprag operably secured to the drive shaft. 10. The fluid valve system of claim 8, further comprising means for biasing the piston to push fluid out of the drive cylinder. 10. The fluid valve system of claim 9, wherein the biasing means is a spring. The method of claim 1, (Iii) secondary hollow cylinder, (Ii) a first auxiliary fluid inlet in fluid communication with the auxiliary hollow cylinder, (Iii) a first auxiliary fluid outlet in fluid communication with the auxiliary hollow cylinder, (Iii) a second auxiliary fluid inlet in fluid communication with the auxiliary hollow cylinder, (Iii) an auxiliary valve housing containing a second auxiliary fluid outlet in fluid communication with the auxiliary hollow cylinder; The shaft is disposed within the secondary hollow cylinder, The first position of the shaft substantially seals the fluid communication between the second auxiliary fluid inlet and the first auxiliary fluid outlet, The second position of the shaft substantially seals a fluid communication between the first auxiliary fluid inlet and the second auxiliary fluid outlet, The shaft is provided with a third slot and a fourth slot, The third slot is oriented in the shaft in such a way as to open a fluid communication between the first auxiliary fluid inlet and the first auxiliary fluid outlet when the shaft is in the first position, And the fourth slot is oriented in the shaft in a manner that opens the fluid communication between the second auxiliary inlet shelf and the second auxiliary output when the shaft is in the second position. 12. The fluid valve system of claim 11, further comprising means for supplying fluid to the first fluid inlet and the first auxiliary fluid outlet. 13. The fluid valve system of claim 12, further comprising means for varying the pressure at which the fluid is supplied to the first fluid inlet and the first auxiliary fluid inlet. The method of claim 11, (a) a drive housing defining a drive cylinder in fluid communication with the first fluid outlet and the second fluid inlet; and (b) an auxiliary drive housing defining an auxiliary drive cylinder in fluid communication with the first auxiliary fluid outlet and the second auxiliary fluid inlet. The method of claim 14, (a) a piston disposed in the drive cylinder, and (b) a fluid valve system further comprising an auxiliary piston disposed within said auxiliary drive cylinder. The method of claim 15, (a) means supplied to the piston to maintain a substantially fluid tight seal between the piston and the drive housing when the piston rotates at least two degrees from a position perpendicular to the axis of the drive cylinder, and (b) when the auxiliary piston is rotated at least two degrees from a position perpendicular to the axis of the auxiliary drive cylinder, it is supplied to the auxiliary piston to maintain a substantially fluid tight seal between the auxiliary piston and the auxiliary drive housing; A fluid valve system further comprising auxiliary means. 17. The method of claim 16, wherein the piston includes a piston cap fixed to the piston rod, and the auxiliary piston includes an auxiliary piston cap fixed to the auxiliary piston rod, a swing arm fixed to the piston rod to pivot; (b) an auxiliary swing arm fixed to pivot with the auxiliary piston rod, (c) the drive shaft, (d) a sprag secured between the swing arm and the drive shaft, and (e) a fluid valve system further comprising an auxiliary sprag secured between the auxiliary swing arm and the drive shaft. 18. The fluid valve system of claim 17 further comprising a reversing sprag secured to the drive shaft. The method of claim 18, (a) means for biasing the piston to force fluid from the drive housing, and (b) auxiliary means for biasing the auxiliary piston to apply force to the fluid from the auxiliary drive cylinder. 20. The fluid valve system of claim 19, wherein the biasing means is a spring and the auxiliary biasing means is an auxiliary spring.