US20160363141A1

US20160363141A1 - Balanced rotary helical Actuator

Info

Publication number: US20160363141A1
Application number: US15/249,345
Authority: US
Inventors: Jianchao Shu
Original assignee: Individual
Current assignee: Individual
Priority date: 2010-10-01
Filing date: 2016-08-26
Publication date: 2016-12-15
Also published as: US20120079901A1; US9464643B2

Abstract

This invention relates to a novel helical dual-center engagement converting mechanism and its applications in fluid-powered actuation system, more particularly to a highly reliable, simple, powerful and balanced and less expensive helical rotary actuator. This actuator comprises a self-balanced linear/rotary dual-center engagement converter, compact porting systems and easy manufacturing modules and various bodies and shaft interface with other components. This actuator also provides a rotary position control and backlash eliminating mechanism to meet various requirements with lighter weight, smaller size and higher accuracy of position and can be interfaced with different machines, such as subsea valves, earthmoving equipment, construction equipment, lifting equipment, landing gears, militarily equipment and medical devices, robotic and artificial leg and arm joints.

Description

CROSS-REFERENCE TO RELATED APPLICATION

This is a division of application Ser. No. US 2012/0079901 A1 filed on Sep. 15, 2011 by Jianchao Shu, now pending to be allowed.

FEDERALLY SPONSORED RESEARCH

No

SEQUENCE LISTING OR PROGRAM

No

BACKGROUND

This invention relates to a novel helical dual-center engagement converting mechanism and its applications in fluid-powered actuation system, more particularly to a highly reliable, simple, powerful and balanced and less expensive helical rotary actuator. This actuator comprises a self-balanced linear/rotary dual-center engagement converter, compact porting systems, easy manufacturing modules, various body configuration and shaft interfaces with other components. This actuator also provides a rotary position control and backlash eliminating mechanism to meet high precision requirements with lighter weight, smaller size and higher accuracy of position and can be interfaced with different machines, such as subsea valves, earthmoving equipment, construction equipment, lifting equipment, landing gears, militarily equipment and robotic and medical devices, artificial arm and leg joints.
Conventional fluid-powered helical actuators have been used in many industries for years, it is based on an old helical linear/rotary converter mechanism and includes a cylindrically shaped housing and two moving parts: a shaft and an annular piston. Helical spline teeth machined on the shaft engage a matching complement of splines on an inside diameter of the piston, an outside diameter of the piston carries a second set of helical splines that engages a ring gear integral with the housing. While conventional linear pistons with pivot joint, the rack and pinion and vane actuators still have majority market share over the helical rotary actuators, the reason is that conventional fluid-powered helical rotary actuators have many unsolved problems and disadvantages; (1) low efficiency, about 60%-70% efficiency for helical rotary actuator is in comparison with that of 90 to 98% for the rack and pinion or vane actuators, so it prevents the actuator from low pressure applications, there are fewer helical pneumatic actuators in the market in comparison with rack and pinion and vane actuators, it not only wastes lot of materials and energy but also can not be used for limited space or restrict weight applications (2) high unbalanced thrust, the unbalanced thrust is still an unsolved problem, it requires more internal parts to balance the thrust, so length of actuator becomes very longer, size of the actuator becomes bigger even there are some balanced helical actuators in the prior art, none of the trials has been commercial success (3) backlashes, due to cumulative clearances of two sets of helical teeth engagements, it increases the impact on the teeth and reduces the accuracy of moving position, life of actuator, some efforts were made in the prior art, but none of trials has been commercial success (4) high stress concentration on cylindrical bodies with helical teeth either by pinging, welding or integrating, it has been struggled for years to seek the solution, under high pressure 3000-5000 psi, the root of helical teeth on cylindrical body generates high stress concentration, this structural problem not only reduces the load capacity and increase the actuator size and weights, but also it can cause sudden break down based on Paris law and is considered to be unreliable and unsafe for critical operations where linear piston with pivot joint devices which have the same rotation function still play a key role in earthmoving equipment and landing gears (5) restrict installation position, most helical actuators are designed for either vertical or horizontal position, they are not suitable for any position between them, due to lack of proper structure and bearing (6) lack of position control, due to lack of control of rotary position and fail to close or open function, it prevents the actuator from critical applications such as military equipment, robotic devices and valve control (7) lack of interface function, most of the actuator bodies are cylindrical shape, such a shape is difficult for three dimensional joint (8) low reliability, according to Failure Modes and Effects Analysis (FMEA), a piston with internal and external helical teeth has the highest severity, with lack of redundancy, the conventional helical actuator never can compete with linear piston with pivot joint in critical applications like landing gears (9) structural inferiority (a) most cylindrical body cannot sustain high structural bending load and compression load, it prevent it from those applications like rotation with high bending or compression (b) material incomparability, since material requirement of mechanical property for body is very different from that of teeth, for the body, it requires high strength, ductile, while for the teeth, high hardness and wearing resistance are the key requirements, since the helical teethes are a part of the body, so most designs are to put the body strength first and to scarify teeth design, as a result the teeth with soft surface will be damaged first or wore out fast even with hydraulic fluid (10) difficult and expensive manufacturing, it is difficult and expensive to make helical teeth, specially internal helical teeth or internal splines on the body as an integral part, it not only makes the manufacturing process more difficult if not impossible, it is impossible to replace the teeth alone, since there is no modulization design in the actuator, conventional actuator manufacturing require large inventory for each size actuator (11) inlet and outlet ports are far away and not standardized, so it is difficult to connect the ports, especially in case of counterbalanced valve is required, additional tube and adapter is needed, it not only increase cost but also reduce reliability, any addition joint adapter and tube can cause leak.
In order to overcome the disadvantages or solve the problems of the conventional fluid-powered helical rotary actuators, many efforts have been made in the prior arts. There are four approaches to improve the conventional helical actuators in the prior arts, but those approaches work against each other within a limited scope.
The first approach is to improve the conversion mechanism. U.S. Pat. No. 3,255,806 to Kenneth H. Meyer (1966), U.S. Pat. No. 4,089,229 to James Leonard Geraci (1978) show a approach is to use a number of keys and keyway to prevent the piston sleeve from rotation under linear force, this conversion mechanism did work, but there were two drawbacks, one is to waste large internal body space due to the keyway, the other is to cause high stress concentration on the body, under 3000 -5000 psi pressure, such stress condition is unsafe and prohibited, likewise other actuators are provided with splined design to prevent the piston from rotation for valve actuations, in addition, it is expensive to make, so many other solutions came out like U.S. Pat. No. 1,056,616 to C. E Wright (1913), U.S. Pat. No.6,793,194 B1 to Joseph Grinberg (2004) the approach is to use two bars to prevent piston sleeve from rotation, the drawback is to waste a large interior housing space and it is restricted to smaller actuator applications, finally current widely acceptable helical actuator is shown in U.S. Pat. No. 3,393,610 to R. O. Aarvold (1966) disclosed a device with a pair helical gearing means between a housing and a shaft in an opposite direction, but it did not prevent the piston rotation, rather it is used as medium to generate a reaction torque between the housing and the shaft and in turn to rotate the shaft, the drawback is to waste internal space and more energy to rotate the piston and increase backlash and cost, a desirable design for this conversion mechanism is that only rotary part should be a rotary shaft, not a body or a piston, moreover the additional rotation will wear bearings and o rings faster and more than under a linear movement only, in addition the arrangement greatly restricts an engaged diameter of the piston, as a result, the output torque is greatly reduced, again, high stress concentration on the body still exists, even it become more difficulty to manufacture with internal and external teeth in a piston.
The second approach is to balance thrust force and ease consequences of the unbalanced forces on helical actuators, U.S. Pat. No. 3,255,806 to Kenneth H. Meyer (1966) shows an actuator with two actuator assembled in an opposite teeth and direction, the design become more difficulty for machining the keyways on the longer body, other effort made is shown on U.S. Pat. No. 4,745,847 to Julian D. Voss (1988) discloses a new design with four parts; a shaft, a housing, a linear piston, a rotation piston, it causes more leak paths and make the actuators more complicated and less reliable, finally U.S. Pat. No. 3,393,610 to R. O. Aarvold (1966) shows two sets of helical teeth in an opposite direction on a piston, it balances the thrust force on the piston but not on the shaft or housing, this arrangement causes a constant tension on the piston during linear/rotary converting, so the piston is subject to torsion well as tension while the load is still applied to shaft and housing, as a result the size of piston is increased while the housing and shaft are underused, so far there is no successful full balance design in the market.
The third approach is to simplify the manufacturing process, there is few development in the field, the most internal helical teeth are as an integral part of a housing or shaft, few welding process or pining process have been tried, but for the current pressure vessel safety standards, those practices under 3000-5000 psi pressure are considered to be unsafe, so stronger, heaver body or shaft with a integral helical teeth are only the solution for now, there is no improvement in the filed
The fourth approach is to ease the backlash and improve performances of the actuator, a typical example is shown in U.S. Pat. No. 2,791,128 to Howard M. Geyer (1957) and U.S. Pat. No.4,858,486 to Paul P. Meyer (1989), a complex mechanical adjustable devices are introduced, but in most applications, such a design is considered to be impractical or too costly due to inherent disadvantage of clearance of two set of helical teeth., the fundamental adjustment mechanism is still unchanged.
So the fluid-powered actuation industry has long sought means of improving the performance of fluid-powered actuation system, eliminating the unbalanced thrust increate efficiency, increate integrity of the body strength, and increasing reliability and accuracy rotary position with less cost.
In conclusion, insofar as I am aware, no fluid-powered actuation system formerly developed provides higher system performances with a modularization structure, less parts, highly efficient, versatile, reliable, easy manufacturing at low cost.

SUMMARY

This invention provides a simple, highly reliable, modular, compact, efficient and balanced rotary actuator. This actuator comprises a novel and improved helical linear/rotary converting modules, compact porting systems and shaft/body interface modules and is much simpler for manufacturing and assembly. It is constructed as converting modules and shaft/body modules, which are easily connected to various components. It also provides rotary position controllers for 90, 180 or 360 degrees with no backlash and lighter weight, smaller space and higher accuracy of position and can be used for a combination device of a hinge and rotary actuator or a rotary actuator either under high axial load or gravity load between vertical and horizontal positions, or for quick cycle, high vibration, quick opening or closing applications and other critical applications to replace linear pistons with pivot joint devices or landing gears for aircraft or artificial or robotic leg and arm joints
The helical linear/rotary converting module can be constructed as a body, a converting unit and a shaft, the converting unit can be constructed as one piston having a two-center linear engagement means and a helical rotary engagement means with the body and the shaft, the two-center linear engagement means is constructed as a pair of a centric and eccentric section which are engaged with a centric bore and eccentric bore between the converting piston and the body or shaft, the helical rotary engagement means is constructed with a pair of helical converting means which includes spline teeth engagement, spline groove/pin and teeth engagement with balls between the converting piston and the body or the converting piston and the shaft, the converting unit can be constructed as two pistons have two pairs of the linear engagement means and rotary engagement means located and moved in an opposite direction. The body can be constructed as one piece a body or two piece split bodies, while shaft can be constructed as one pieces part with helical rotary converting means or two-center linear converting means or multiple pieces parts. The actuator includes various shapes of bodies for different applications.
The actuator can be constructed with various shape of bodies, the spherical shape of the body is constructed for supporting high axial load both on the shaft or body or installed between vertical and horizontal positions and sustain high bending and compression loads or with robotic and artificial arm and leg joints, other shape of body is provided with one end closed and other end opened for operating rotary valve, finally a split body is constructed to receive large engaged diameter of piston with smaller end shaft or large spring to generate return force.
The actuator can be constructed with position control devices. One of the feature is to combine a vane actuator and helical actuator as one unit, it not only eliminate backlash but increase output torque and improve the accuracy of rotary position, other is to provide two hard adjustable hard stop in both ends of rotation of 90, 180, 270 or 360 degree. In the manufacturing of the actuator, this invention provides other joint method to separate helical teeth from shaft or body, so the helical teeth can be manufactured replaced easily at low cost.
Accordingly, besides objects and advantages of the present invention described in the above patent, several objects and advantages of the present invention are:

(a) To provide a highly efficient linear/rotary converting mechanism with less energy, maxim output torque and fewer components.
(b) To provide a linear/rotary converting mechanism with less stress concentration, so the mechanism can be more reliable, compact and still robust for critical applications
(c) To provide a fluid-powered actuation system with highly optimal division of functions among the modular members in a balanced manner, so such a system allows a user to have higher integrity of a system with fewer components and reduce a system space, leakage and manufacturing and replacement cost
(d) To provide a directly coupling means for an actuator and other components so as to eliminate adapters, reduce the space for their connection.
(e) To provide a fully balanced means for an actuator, so the actuator is constructed with more powerful and reliable mechanism with less weight, parts and cost.
(f) To provide a fluid-powered actuation system with actuator, which has less displaced fluid volumes on both sides of pistons, so the energy loss can be reduced to a minimum level
(g) To provide an internal porting means for a fluid-powered actuation system, the system is not subject to external tube corrosion and breakdown and has quick response time and can be either connected through a shaft or body.
(h) To provide a fluid-powered actuator with high holding torque, so it is not susceptible to vibration and more stable and can be used in applications of high vibration, quick cycle.
(i) To provide a fluid-powered actuation system with gravity balance mechanism, so the actuator can be used between vertical and horizontal positions.
(j) To provide a fluid-powered actuation system without backlash, so the system becomes more stable and accurate at pre-setting position
(k) To provide a fluid-powered actuation system with highly reliable, inherently redundant, intrinsically safe control functions, so the system can be used for critical applications such as military operation, medical emergence care/device and aircraft landing gears
(l) To provide a produced-friendly, fluid-powered actuation modules with simple, flexible structures, easy manufacturing and process and various size and material selection, the modules require simple manufacturing process and flexible construction methods for different applications, so a manufacturer for the system can easily implement rapid product development and outsourcing at lower cost
(m) To provide a linear-rotary converting device with compact, adaptable rotary shaft and body. Therefore, the devices can use as a combination of a hinge joint and rotary actuator for robotic or artificial arm and leg joints.

Still further objects and advantages will become apparent from study of the following description and the accompanying drawings.

DRAWINGS

Drawing Figures

FIG. 10 is an exploded, quarter cut view of a helical rotary actuator embodiment of the helical linear/rotary converting mechanism of FIG. 8.

FIG. 11 is a front view of the helical rotary actuator of FIG. 10.

FIG. 12 is a cross sectional view of the helical rotary actuator of FIG. 11. Along line B-B.

FIG. 13 is a cross sectional view of the helical rotary actuator of FIG. 11. Along line C-C.

FIG. 14 is a detail view of the helical rotary actuator of FIG. 13. Along cycle of F.

FIG. 15 is an exploded, quarter cut view of an alternative embodiment of helical rotary actuator of FIG. 10.

FIG. 16 is a front view of the helical rotary actuator of FIG. 15.

FIG. 17 is a cross sectional view of the helical rotary actuator of FIG. 16 along line E-E.

FIG. 18 is a cross view of the helical rotary actuator of FIG. 16. along line D-D.

FIG. 19 is an isometric view of the helical rotary actuator of FIG. 16.

FIG. 20 is an exploded, quarter cut view of an alternative embodiment of helical rotary actuator of FIG. 10.

FIG. 21 is a detail view of the helical rotary actuator of FIG. 20. along cycle of A

FIG. 22 is a front view of a subassembly of FIG. 20.

FIG. 23 is a side view of the subassembly of FIG. 22.

FIG. 24 is a cross sectional view of the subassembly of FIG. 22 along line F-F.

FIG. 25 is a cross sectional view of the subassembly of FIG. 22 along line G-G.

FIG. 26 is an exploded, quarter cut view of an alternative embodiment of helical rotary actuator of FIG. 10.

FIG. 27 is a front view of the helical rotary actuator of FIG. 26.

FIG. 28 is a cross sectional view of the helical rotary actuator of FIG. 27 along line I-I.

FIG. 29 is a cross sectional view of the helical rotary actuator of FIG. 27 along line H-H.

FIG. 30 is an exploded, quarter cut view of an alternative embodiment of helical rotary actuator of FIG. 10.

FIG. 31 is a front view of the helical rotary actuator of FIG. 30.

FIG. 32 is a cross sectional view of the helical rotary actuator of FIG. 31 along line K-K.

FIG. 33 is a cross sectional view of the helical rotary actuator of FIG. 30 along line J-J.

FIG. 34 is an exploded view of an alternative embodiment of helical rotary actuator of FIG. 30.

FIG. 35 is a front view of the helical rotary actuator of FIG. 34.

FIG. 36 is a cross sectional view of the helical rotary actuator of FIG. 35 along line L-L.

REFERENCE NUMBER IN DRAWING

10 Single Helical Converter a,b,c,d,e,f,h
11 body a,b,c,d
12 Converting piston, a,b,c,d
13 Shaft, a,b,c,d,e,f,g,h
14 Centric section, a,b,c,d
15 Eccentric section, a,b,c,d
16 Centric bore, a,b,c,d
17 Eccentric bore a,b,c,d
18 Helical internal teeth, a,b,d
19 helical external teeth a,b,d
18 Helical groove, c
19 Helical groove pin, c,
20 Double Helical converter a,b,f
21 Body, a,b,f
22,22′ Converting piston a,b,f
23 Shaft, a,b,f
24 Centric section a,b,f
25,25′ Eccentric section a,b,f
26,26′ Centric bore a,b,f
27,27′ Eccentric bore a,b,f
28,28′ Helical internal teeth a,b,f
29 29′ Helical external teeth a,b,f
1 Support ring e,f,g,h
4 Centric section, e,f,g,h
5 Eccentric section, e,f,g,h
6 Centric bore e,f,g,h
9 Retaining ring g
2 Helical teeth ring, e,f,g,h
3 Shaft e,f,g,h
7 Eccentric bore, e,f,g,h
8 Set of Balls
100 Helical Actuator, a,b,c,d,e,g
A port, 1,2,3,4,5,6,7
B Port, 1,2,3,4,5,6,7
101′,101 Body,
102′,102 Centric bore,
103′,103 Eccentric bore
104′,104 body end
105 Horizontal Passageway
106 Spherical external surface
107 Cylindrical External surface
108′,108 Groove
109′,109 End Vertical surface
110′,110 End Horizontal surface
111 End Spherical surface
112 Out-vertical surface
113 Horizontal surface
117 Inter-vertical surface
120 Center chamber
121′,121 Side chamber,
122′,122 Helical internal teeth right
123′,123 Helical internal teeth left
124 Spherical external surface
125 Thread hold
126 Bolt hole
127 hole
128 hole
129 O ring groove
140 Shaft
141′,141 External helical teeth,
142
143 Centric section
144 Eccentric section
145′,145 end
146 keyway
147 center hole
148′,148 Side hole
160 O ring
161 Oring
162 Oring
163 Oring
164 Oring
165 Spherical bearing
166 bolt
190 Spherical supporter
191 Shell plate
192 Recess surface
193 Thread hole
130″,130 Converting piston
131′,131 Groove
132′,132 Centric section
133′,133 Eccentric section
134′,134 Internal helical teeth
135′,135 External helical teeth
136′,136 Piston inward surface
137′,137 Piston outward surface
138′,138 Link hole
139′,139 bore
150 Spherical Cover
151 Spherical internal surface
152 Out-Vertical surface
153 Horizontal surface
154 Spherical external surface
155 End Vertical surface
156 Shaft hole
157 Inter-Vertical surface
158 Flat cover
159 O ring groove
170 Vane cover
171 Vane
172 Piston land
173 Inward port
174 Outward port
175 vane Key
176 Middle ring
177 hole
178 Inside surface
179 Outside surface
197 Link port
198 recess
180 Conical step
181 Conical surface
182 Conical surface
183 Vane chamber
184 Vane chamber
185′, 185 Slot
186 plug
187 setscrew
188 Flat screw
189 spring
195 Vane land
196 groove

Description

FIGS. 10-14 illustrate a fluid powered helical rotary actuator 100 a based on helical linear/rotary converting mechanism 20 a constructed in accordance with the present invention. The actuator 100 a comprises a body 101 a having an eccentric bore 103 a, two centric bores 102 a,102 a′ and pistons 130 a,130 a′, a shaft 140 a is movably disposed in pistons 130 a,130 a′, body 101 a is covered by a spherical cover 150 a and a flat cover 158 a and has standard ports A1, B1 which includes port size and distance between port A1, B1 and respectively connected to a pressurized fluid and a sink fluid (not shown), the actuator 100 a is provided for rotary movements.
Pistons 130 a,130 a′ are axially opposed and respectively have sections 132 a, 133 a movably engaged with bores 102 a, 103 a and sections 132 a′, 133 a′ movably engaged with bores 102 a′,103 a in an opposite direction. Pistons 130 a,130 a′ also include internal helical teeth 134 a,134 a′ in inner surfaces to operatively engage with sections 141 a,141 a′ of the shaft 140 a, a center chamber 120 a is provided between inward surfaces 136 a, 136 a′ and bore 103 a and is connected to port B1 and to grooves 131 a,131 a′ through gaps between teeth 134 a and 141 a, teeth 134 a′and 141 a′ and link holes 138 a,138 a′, while side chambers 121 a,121 a′ are defined respectively by cover 150 a, an outward surface 137 a and bore 102 a and by cover 158 a, an outward surface 137 a′ and bore 102 a′ and connected to port Al through a passageway 105 and grooves 108 a,108 a′.
Cover 150 a is mounted on a left side of shaft 140 a and has a first vertical surface 152 a, spherical surface 151 a, a second vertical surface 157 a and a horizontal surface 153 a with an o ring groove 159 a, body 101 a has a first vertical surface 112 a, a spherical surface 111 a, a second vertical surface 117 a with an o ring groove 129 a and horizontal surface 110 a, a spherical bearing 165 a is placed between surfaces 151 a and 111 a for providing a bearing and a seal, while o- rings 160 a and 161 a are respectively placed in groove 129 a and groove 159 a for providing a vertical seal and a horizontal seal between cover 150 a and body 101 a.
Referring to FIGS. 15-19, a fluid powered helical rotary actuator 100 b based on fluid powered helical rotary actuator 100 a comprises a spherical body 101 b, pistons 130 b,130 b′, a shaft 140 b is movably disposed in pistons 130 b,130 b′, body 101 b is covered by two spherical covers 150 b, 150 b′ and has standard ports A2, B2 which includes port size and distance between port A2, B2 and respectively connected to a pressurized fluid and a sink fluid (not shown), there are other optional ports A3, B3 respectively connected to a pressurized fluid and a sink fluid (not shown), the actuator 100 b is provided for rotary movements.
A center chamber 120 b is connected to port B2 through hole 147 b, while side chambers 121 b, 124 b′ are connected to port A2 through holes 148 b,148 b′ and grooves 108 b,108 b′. Covers 150 b,150 b′ are mounted respectively on a left side and a right side of shaft 140 b, a holder 190 b has a cylindrical bar extended to shell 191 b with a spherical recess 192 b to receive actuator 100 b for securing a pre-set position, holes 193 b and thread holes 125 b are provided for bolting between actuator 100 b and holder 190 b.
Referring to FIG. 20-25, a fluid powered helical rotary actuator 100 c based on fluid powered helical rotary actuator 100 a comprises a body 101 c, pistons 130 c,130 c′, two vanes 171 c and two vane covers 170 c, a shaft 140 c is movably disposed in pistons 130 c,130 c′, vanes 171 c and vane covers 170 c, body 101 c is covered by two covers 158 c, 158 c′ and has standard ports A4, B4 which includes size port and distance between ports A4, B4 respectively connected to a pressurized fluid and a sink fluid (not shown). the actuator 100 c is provided for rotary movements.
Pistons 130 c,130 c′ are axially opposed, movably disposed in body 101 c since the left piston 130 c is as the same as the right piston 130 c′, only the left side piston is described here, two vane chambers 183 c and 184 c are defined by piston 130 c, vane cover 170 c, vane 171 c, a vane land 195 c of vane 171 c and a piston land 172 c of piston 130 c, a center chamber 120 c is connected to vane chamber 183 c through gaps between shaft 140 c and piston 130 c, radial hole 138 c and axial hole 173 c and a slot 185 c′, while a side chamber 121 c is connected to chamber 184 c through hole 174 c, slot 185 c, vane 171 c is coupled with shaft 140 c by keyway 146 c and key 175 c.
Referring to FIG. 26-29, a fluid powered helical rotary actuator 100 d based on fluid powered helical rotary actuator 20 a comprises a body 101 d having a left closed end except a shaft hole 127 d and a right end with a centric bore 102 d to receive a middle ring 176 d, pistons 130 d,130 d′, a shaft 140 d is movably disposed in pistons 130 d,130 d′ and middle ring 176 d, body 101 d is covered by cover 158 d and has standard ports A5, B5 which includes port size and distance between ports A5 and B5 respectively connected to a pressurized fluid and a sink fluid (not shown), the actuator 100 d is provided for rotary movements.
Middle ring 176 d is axially placed between pistons 130 d,130 d′ and has a centric outside surface 179 d and an eccentric inside surface 178 d. Pistons 130 d,130 d′ have respectively centric sections 132 d,132 d′ engaged with bore 102 d and eccentric sections 133 d,133 d′ engaged with eccentric surface 178 d. Pistons 130 d,130 d′ also include internal helical teeth 134 d,134 d′ in inner surfaces to operatively engage with external helical teeth 141 d,141 d′ of the shaft 140 d. Middle ring 176 d also includes three radial holes 177 d,177 d′ and is secured by two screws 187 d through holes 177 d, conical tips of two screws 187 d are engaged with conical surfaces of 182 d,182 d′ for controlling inward positions of pistons 103 d ,103 d′, two screws 188 d are threaded through cover 158 d for controlling outward positions of piston of 130 d, hole 176 d′ is linked between port B5 and inside surface 178 d .
Referring to FIG. 30-33, a fluid powered helical rotary actuator 100 e based on fluid powered helical rotary actuator 100 a comprises a pair of split bodies 101 e,101 e′ to receive a middle ring 176 e and pistons 130 e,130 e′, bodies 101 e,101 e′ respectively have centric bores 102 e,102 e′ and eccentric bores 103 e,103 e′, pistons 130 e,130 e′ are axially opposed and respectively have sections 132 e,133 e engaged with bores 102 e,103 e and sections 132 e′,133 e′ engaged with bores 102 e′, 103 e′, a shaft 140 e is movably disposed in pistons 130 e,130 e′ and middle ring 176 e, split bodies 101 e,101 e′ are secured by four of bolts 166 e and sealed by o-ring 164 e, bodies 101 e,101 e′ have standard ports A6, B6 which includes size port and distance between port A6, B6 respectively connected to a pressurized fluid and a sink fluid (not shown), the actuator 100 e is provided for rotary movements.
Pistons 130 e,130 e′ are axially opposed, movably disposed in bodies 101 e,101 e′, a center chamber 120 e is connected to port B6, while side chamber 121 e,121 e′ are connected to port A6 through a passageway 105 e and grooves 108 e,108 e′, body 101 e has two holes 128 e, two screws 187 e are respectively threaded through holes 128 e and engaged with conical surfaces 181 e,181 e′ defined by ring 176 e and piston 130 e for controlling an inward position of pistons of 130 e,130 e′, screws 188 e are threaded through cover 158 e for controlling outward positions of piston 130 e and are secured by plugs 186 e.
Referring to FIG. 34-36, a fluid powered helical rotary actuator 100 g based on fluid powered helical rotary actuator 100 e comprises a pair of split bodies 101 g,101 g′, spring set 189 g, pistons 130 g,130 g′, a shaft 140 g is movably disposed in pistons 130 g,130 g′ and a spring set 189 g, split bodies 101 g,101 g′ are secured by four of bolts 166 g and sealed by o-ring 164 g, the pair of split bodies 101 g,101 g′ has standard ports A7, B7 which includes size of port and distance between ports A7,B7 respectively connected to a pressurized fluid and a sink fluid (not shown), the actuator 100 g is provided for rotary movements.
Bodies 101 g,101 g′ respectively have centric bores 102 g,102 g′ and eccentric bores 103 g,103 g′, pistons 130 g,130 g′ are axially opposed and have respectively sections 132 g,133 g and sections 132 g′,133 g′ engaged with bores 102 g, 103 g and bores 102 g′ and 103 g′, the spring set 189 g is placed between pistons 130 g and 130 g′ for spring return.

Operations

For the mechanisms 10 a, assume that piston 12 a is inserted into body 11 a by engaging between sections 14 a,15 a, and bores 16 a,17 a with a clearance fit, then shaft 13 a is inserted into piston 12 a by engaging between helical teeth 19 a and helical teeth 18 s with a clearance fit, piston 12 a tends to rotate under axial force, but since there is an offset between bores 16 a,17, the offset only allows piston 12 a to move linearly but prevents piston 12 a from rotation, as a result, the helical teeth 18 a on piston 12 a forces helical teeth 19 a as well as the shaft 13 a to rotate, in case of mechanisms 10 c, 10 d, only difference is the helical converting means.
For the mechanisms 10 b, assume that piston 12 b is inserted into body 11 b by engaging between helical teeth 19 b and helical teeth 18 b with a clearance fit then shaft 13 b is inserted into piston 12 b by engaging between sections 14 b,15 b, and bores 16 b,17 b with a clearance fit, piston 12 b rotates under axial forces, since there is an offset between bores 16 b, 17 b, as a result, the offset force shaft 130 b to rotate along with the piston 12 b.
For mechanisms 20 a, assume that shaft 23 a is inserted into body 21 a, then piston 22 a is inserted into ring 21 a from the left side by engaging between sections 24 a, 25 a, and bores 26 a,27 a with a clearance fit and between helical left teeth 29 a and left helical teeth 28 a, then piston 22 a′ is inserted into body 21 a from the right side by engaging between sections 24 a′, 25 a′ and bores 26 a′,27 a with a clearance fit and between right helical teeth 29 a′ and right helical teeth 28 a′, two equal but opposite forces are applied inwardly and outwardly to piston 22 a and 22 a′, piston 22 a tends to rotate under axial forces, but since there is an offset between bores 26 a,27 a, the offset only allow piston 22 a to move linearly but prevents piston 22 a from rotation, as a result, the helical teeth 28 a on piston 22 a forces helical teeth 29 a as well as the shaft 23 a to rotate clockwise, while piston 22 a′ tends to rotate under axial forces, but since there is an offset between bores 26 a′,27 a′, the offset allows piston 22 a′ to move linearly but prevents piston 22 a′ from rotation, as a result, the helical teeth 28 a′ on piston 22 a′ forces helical teeth 29 a′ as well as shaft 23 a rotate the clockwise due to opposite direction between teethes of 29 a,28 a and 29 a′,28 a′, so the axial forces balances on shaft 23 a.
For the mechanisms 20 b, the balance mechanism is the same as the mechanism 20 a, while the operation is the same as mechanism 10 b
For actuator 100 a, assume that shaft 140 a is inserted into body 101 a, then piston 130 a is inserted into body 101 a from the left side by engaging between sections 132 a,133 a, and bores 102 a,103 a with a clearance fit and between helical teeth 134 a and helical teeth 141 a, then piston 130 a′ is inserted into body 101 a from the right side by engaging between sections 132 a′,133 a′ and bores 102 a′,103 a with a clearance fit and between helical teeth 134 a′ and helical teeth 141 a′.
Port A1 and port B1 are respectively connected to a pressurized fluid source/a fluid sink (not shown), there is no movement of the piston 130 a,130 a′ or that of shaft 140 a. When a pressurized flow fluid is allowed to enter to chamber 121 a,121 a′ through port A1, then spilt into two flows into passageways 105 a, then into grooves 108 a,108 a′, the flow fluids provide sufficient pressure against pistons 130 a, 103 a′ from outward surfaces 137 a,137 a′, while fluids in chambers 120 a through B1 connected to the fluid sink have a lower pressure, so pressure differentials generate two equal but opposite forces against pistons 130 a,130 a′ inwardly and cause inward movements of two pistons 130 a,130 a′ in a synchronized manner, so shaft 140 a is balanced in the axial direction, because of offset engagement between body 101 a and piston 130 a,130 a′, piston 130 a,130 a′ are only allowed to move linearly, as a result, the helical teeth 134 a on piston 130 a and teeth 134 a′ in piston 130 a′ force helical teeth 141 a, 141 a′ as well as the shaft 140 a to rotate clockwise. On the contrary, when the connections of ports Al and port B1 with the fluid source/the fluid sink are switched, the conditions of flow fluids are reversed, shaft 140 a is rotated anti-clockwise.
For the actuator 100 a installed in between vertical and horizontal positions, the gravity force or an external axial force is applied to cover 150 a and shaft 140 a, in turn cover 150 a will distribute the load into bearing 165 a and body 101 a evenly due to the spherical surface engagement, then shaft 140 a distribute the torsion evenly to two pistons 130 a,130 a′ due to the balanced arrangement of pistons 1301 a,130 a′.
For actuator 100 b, it can be used as a combination of a hinge and an actuator, actuator 100 b can installed in any position and sustain great bending as well as axial force due to spherical shape of body and cover which can cancel out most of non axial force, it also can be easily used for connecting other dimensional rotary device.
For actuator 100 c, when a backlash is not allowed, actuator 100 c can be used, by nature a vane actuator has no backlash, actuator 100 c based on 100 a can be modified by adding two the same vane actuators on both ends of pistons 130 c,103 c′. Ports A4, B4 are respectively connected to a pressurized fluid source/a fluid sink (not shown), there is no movement of the pistons 130 c,130 c′, or that of shaft 140 c. When a pressurized flow fluid is allowed to enter to chamber 121 c,121 c′ through port A4, then spilt into two flows into passageways 105 c, then through hole 174 c, slot 185 c into vane chamber 184 c, the flow fluids provide sufficient pressure against land 195 c which is keyed with shaft 140 c by key 175 c and keyway 146 c, while low pressure fluids in vane chambers 183 c enters chamber 120 c through holes 173 c,138 c and engagement gaps between shaft 140 c and piston 130 c, in turn, chamber 120 c is connected to the fluid sink, so pressure differentials forces lands 195 c as well as shaft 140 c to rotate clockwise. On the contrary, when the connections of ports A4 and port B4 with the fluid source/the fluid sink are switched, the conditions of flow fluids are reversed, shaft 140 c is rotated anti-clockwise.
For actuator 100 d which can be used when precision rotary position is required, piston 130 d,130 d are placed in center of body 101 d, two screws 187 d are threaded in holes 128 d,177 d with conical tips engaged with both conical surfaces 182 d,182 d′, by rotating the screw 182 d,182 d′, inward movement of pistons 130 d,130 d′ are controlled to a preset position, on the outward sides, two flat tip screws 188 d are threaded through cover 158 d, by rotating the screw 188 d,188 d′, outward movement of pistons 130 d,130 d′ are controlled for a pre-set position of shaft 140 d.
For actuator 100 e, assume that ring 176 e is pressed into piston 130 e, then two pistons 130 e,130 e′ are placed from both ends of shaft 140 e, then two bodies 101 e,101 e′ are placed from both ends of shaft 140 e by aligning up between hole 128 e, conical surfaces 181 d,182 d and secured by bolts 166 e. Port A6 and port B6 are respectively connected to a pressurized fluid source/a fluid sink (not shown), there is no movement of the piston 130 e,130 e′ or that of shaft 140 e. When a pressurized flow fluid is allowed to enter to chamber 121 e,121 e′ through port A6, then spilt into two flows into passageways 105 e, then into grooves 108 e,108 e′, the flow fluids provide sufficient pressure against pistons 130 e, 130 e′, while fluids in chambers 120 e through port B6 connected to the fluid sink have a lower pressure, so pressure differentials move pistons 130 e,130 e′ inwardly in a synchronized manner then make shaft 140 e to rotate clockwise. On the contrary, when the connections of ports A6 and port B6 with the fluid source/the fluid sink are switched, the conditions of flow fluids are reversed, shaft 140 e is rotated anti-clockwise.
For actuator 100 g which can be used for single acting application, top and bottom is interchangeable for fail closed and fail open of valve control without changing any part, assume that one set of springs 189 g is placed into shaft 140 g, then two pistons 130 g,130 g′ are placed from both ends of shaft 140 g, then two bodies 101 g,101 g′ are placed from both ends of shaft 140 g and secured by bolts 166 g. Port Aland port Blare respectively connected to a pressurized fluid source/a fluid sink (not shown), there is no movement of the piston 130 g,130 g′ or that of shaft 140 e. When a pressurized flow fluid is allowed to enter to chamber 121 g,121 g′ through port A7, then split into two flows into passageways 105 g, then into grooves 108 g,108 g′, the flow fluids provide sufficient pressure against pistons 130 g,130 g′, while fluids in chambers 120 g through port B7 connected to the fluid sink have a lower pressure, so pressure differentials move pistons 130 g,130 g′ inwardly in a synchronized manner then make shaft 140 g to rotate clockwise and compress springs 189 g. On the contrary, when the connections of ports A7 loses pressure, the pressure differentials disappears, the compressed springs force pistons 130 g,130 g′ to move outward and make shaft 140 g rotated anti-clockwise.

Advantages

From the description above, a number of advantage of some embodiments of my helical rotary actuator become evident:

(1) high efficiency, with double effective areas of pistons, balance design, this embodiment increase the efficiency of helical rotary actuator from about 60%-70% to 85-95, with less materials and weights, smaller size, it opens the door to the low pressure pneumatic actuators market against rack and pinion and vane actuators
(2) a balanced thrust, the thrust is fully balanced on the shaft without any bearing under both inward and outward pressures, so under no time, the piston bears any external axial load, both the body and shaft take external side or axial loads evenly, so the piston can generates more torque than any helical actuator and last longer, the other benefit is vibration proof, due to left and right pistons work in an opposite direction, any axial movement will not change rotation position of shaft as long as there is no the relative position change between the left and right positions.
(3) no backlashes, first the dual center engagement does not add any axial clearance, second the left helical teeth and right helical teeth works against each other and cancel out any clearance in the axial direction, finally the piston with the vane actuator completely eliminate any backlashes structurally
(4) No high stress concentration on the body, with the dual center engagement, the body no longer has high stress concentration on the wall without the teeth or shape spline, it greatly reduce the wall thickness of the body and increase safety of the body and meet the pressure vessel standards for critical applications
(5)free installation position, with spherical joint between body and cover, balanced thrust, the invention provides an actuator which can be installed between any position between vertical and horizontal positions.
(6) precision position control, with conical and flat surfaces engagements devices, both inward and outward positions are fully controlled, now this actuator can be used for a critical applications such as military equipment, robotic devices and valve control
(7) versatile interface functions, most of the actuator bodies are cylindrical shape, such a shape is difficult for three dimensional joint
(8) high reliability, without high stress concentration on the body, high tension on the piston and balanced thrust on the shaft, this actuator has highest safety design over all existing helical rotary actuators, in addition, the dual independent pistons, porting systems provide redundant functions, if a left piston fails, the right piston still functions independently, it can be used for airplane landing gears or linear piston with pivot joint in the construction machines or lift equipment.
(9) optimized structural design (a) spherical body can sustain high structural bending and compression loads, it can be used for stand-along or combine with additional actuator for 2 D or 3 D position control (b) material comparability with design, now material for body can be different from that of teeth rings for design or application purpose, so teeth ring can be heat treated or hardened, while body can be ductile with anti wearing coating in ID wearing resistance, so it sustains high pressure on body and high compression and wearing on ID surface and does not scarify any design requirement and greatly increase the life of the product.
(10) Easy and low cost manufacturing, the dual-center mechanism with two pair of simple cyclical bore/sections engagements greatly reduce manufacturing and assembly cost and time at least by 50%, an axial distance adjustment becomes much easy, most of all, helical teeth ring can be replaced without replacing the body or shaft, with middle ring with eccentric surfaces, even the offset machining becomes simpler, moreover, teeth ring can be pre-made, only left is ID or OD,
(11) Standard input and out port, the novel internal port system makes standardized the port size and distance between inlet port and outlet port possible, it reduces adaptor and tube, but also increases the reliability of the connection, the ports can be directly connected with counterbalanced valve, two way to four way solenoid valve without tube or adaptors.

Conclusion, Ramifications and Scope

The dual-center engagement mechanism in helical rotary actuator completely changes the rotary/linear converting concept and provides breakthrough performances and advantages over all existing rotary actuators (1) simplicity, two simple cylindrical engagement with an offset, but magically much better than the conventional helical actuators either have complicated dual internal and external helical teeth on piston or external spline and internal helical on the piston, more effective areas for axial forces than that of conventional helical actuators, the double center engagement can be arranged as example of mechanism 20 a, A left offset+A center+A right offset, so the left offset can be balanced the right left offset within the body under axial forces, or A centric+An offset+A centric, such a arrangement can reduce machining, or simple a centric bore with middle ring with a centric OD and an eccentric ID like mechanism 100 d (2) robust, there is no detrimental features on the body, two cylindrical engagement convert the torsion from the piston to compression, such a compression structure greatly increase the body ability for holding the torque than any other methods on the conventional helical actuators while no space waste for keyway or helical or spline teeth or seals, in case of high cycle operation, there is no one location standing high impact force on the body unlike the conventional helical actuator, the impact force can enlarged the small fraction on teeth on the body and cause body buster. (3) compact, since there is no external helical teeth, the internal teeth diameter on piston can be made bigger with the size of the conventional helical piston, since there is no keyway or spline teeth, the seal groove can be on any place on the piston, it reduce at 50% length of the conventional helical actuator requires. (4) synergy, without the dual-center engagement mechanism, no full thrust balance can succeed, as the readers look back the history of helical actuator, as it evolves, no truly balance structure has been succeed, the reason is that the conventional helical actuator without an axial balance mechanism is already too longer at least twice as longer than that of the dual-center engagement mechanism actuator, if other half is added, it will be at four time longer than the dual-center engagement mechanism actuator, it is away beyond design scope in term of strength, stability and concentricity, and it is difficult to make, with dual-center engagement mechanism, fully balance helical actuator is about the same as the conventional one piston helical actuator
Each of embodiments of the present invention provides each advantage, each unique solution and each special modular structure to solve each problem existing for very long time, there are three interface elements, body where to hold, shaft where to rotate, fluid port where to get energy for operation, with all existing problem in mind (1) mechanism 100 a is used as a hinge with rotary actuator in many lift equipment and deal with installation issue between vertical and horizontal positions, it provide a novel sandwich three seals, vertical o ring and horizontal o ring and conical or spherical bearing, which made out soft metals like bronze, or engineering plastics like peek to provide a seal between the cover and the body and, a bearing function to shift the load from the cover and shaft to the body to the body, the triple seals secure a sound sealing function in any rotation position between vertical and horizontal positions, when it is installed in vertical position, or a horizontal position or between the vertical seal or horizontal seal with no or a bit effect of gravity for seal due to spherical or conical engagement between the cover and body, while spherical bearing play a key to swift gravity load to the body as well for hard seal (2) mechanism 100 b dealt with adaptability issue, it is used for providing 360 degree rotation, it is breakthrough in term of usage, it can sustain very high compression load or bending load, three of them combine can provide any three dimension position due to the spherical joint between cover and body, it can be used as robotic arm joint to replace linear piston with a pivot joint device or artificial arm or leg joint with a linear piston arm or leg, it can be used as a self motored hydraulic wheel for at 360 degree rotation (3) mechanism 100 c dealt with backlash issue, the backlash causes loss of control of position, damage of output shaft or other piston or body and weakens joint between actuator and other connected part and is a nightmare for control engineers, with a conventional helical actuator, it is impossible to eliminate the backlash, or loss motion, because two sets of clearance between the body and piston, piston and shaft are caused by one piece of the piston, but with this embodiment, the two teeth engagements are separated by two pistons, there is no cumulative clearance, moreover actuator 100 c solves the problem by adding two vane actuator on both sides, by nature, vane actuator has no backlash, the helical actuator provide a converting, rigid torque, the torque is not susceptible to an inlet pressure frustrations, while the vane actuator provides a soft direct torque without converting or delay, when the actuator start to rotate the shaft, a combination soft and rigid torques provides a smooth, backlash free rotation movement, by changing size of hole 174 c vane torque can be either reduced or increased, moreover the vane actuator can be used as a damper when actuator acts too fast, this combination of vane actuation and two pistons arrangement solution surpass all previous efforts (4) mechanism 100 d is used for applications like rotary valve actuation, it is required a body bottom connection with a valve for precision position, inward position control is provided with a pair of conical tips of screws, outward position are controlled by two flat tip screws, since the piston is not rotated unlike conventional helical actuator (5) mechanism 100 e is used for lager torque output with limited axial space and precision position, with split bodies, the diameter of helical teeth can be made much larger without wasting lot material, since they are symmetric, it reduce the casting or forging mould cost, other application is used for spring return, it saves lot of money by reducing haft the spring sets in comparison with the conventional helical actuator with spring return devices, specially in subsea rotary valve applications, light weight, easy installation, versatility are the key requirements for a diver to install a valve system, the other advantage is top and button of connection can be interchanged for fail closed or fail open applications without changing any part.
Although the description above contains many specifications, these should not be construed as limiting the scope of the invention but as merely providing illustration of some of the presently preferred embodiments of this invention.
Thus, the scope of the invention should be determined by the appended claims and their legal equivalents, rather than by the examples given.

Claims

I claim:

1. An actuation module comprising;

(a) A body assembly having a body;

(b) A shaft assembly having a shaft;

(c) A conversion-transmission assembly having one of a plurality of configurations including;

(c1) Said conversion-transmission assembly positioned between said shaft assembly and said body assembly having a helical movement converting mechanism and a movable piston, said helical movement converting mechanism including a helical engagement for providing conversions between reciprocal movements and rotary movements and a reactionary engagement for generating reactionary torques, said helical movement converting mechanism is defined by one of a plurality of arrangements inducing said helical engagement between said piston and said shaft, and said reactionary engagement between said piston and said body, said body has a front cylindrical bore defined by a fixed, centric axis and a back cylindrical bore defined by a fixed eccentric axis, parallel to said fixed centric axis, said piston has two mated cylindrical sections engaged respectively with said front centric bore and said back eccentric bore of said body for providing said reactionary engagement, said helical movement converting mechanism is defined by one of a plurality of structures including a helix spline/helix spline structure and a helix spline/non-helix spline structure, said shaft has helical splines, said piston has mated helical splines engaged with said helical splines of said shaft for providing said helical engagement, whereby said body, said piston and said shaft having a conversion means for providing conversions between reciprocal movements of said piston and rotatory movements of said shaft, and a non-friction reaction means for generating reactionary compression forces with said axises against said shaft;

(c2) Said conversion-transmission assembly positioned between said shaft assembly and said body assembly having helical movement converting mechanisms, a right movable piston and a left movable piston, said helical movement converting mechanism including a helical engagement for providing conversions between reciprocal movements and rotary movements and a reactionary engagement for generating reactionary torques, said helical movement mechanism is defined by one of a plurality of arrangements inducing said helical engagement between said pistons and said shaft, and said reactionary engagement between said pistons and said body, said body has a right, cylindrical bore and at least one middle cylindrical bore respectively defined by a fixed centric axis, a fixed eccentric axis parallel to said fixed centric axis and a left cylindrical bore and said middle cylindrical bore respectively defined by said fixed centric axis and said fixed eccentric axis, said right piston has two mated cylindrical sections engaged respectively with said right bore and said middle bore of said body for providing said reactionary engagement, said left piston has two mated cylindrical sections engaged respectively with said left bore and said middle bore of said body for providing said reactionary engagement, said helical movement converting mechanism is defined by one of a plurality of structures including a helix spline/helix spline structure, and a helix spline/non-helix spline structure, said shaft has right helical splines and left helical splines, said right piston has mated right helical splines engaged with said right helical splines of said shaft for providing said helical engagement, said left piston has mated left helical splines engaged with said left helical splines of said shaft for providing said helical engagement, whereby said body, said pistons and said shaft having a conversion means for providing conversions between reciprocal movements of said pistons and rotatory movements of said shaft, and a non-friction reaction means for generating reactionary compression forces with said axises against said shaft and a balance means for balancing side loads on said left helical splines of said shaft engaged with said right piston with side forces on said left helical splines on said shaft engaged with said right piston;

(d) A porting system including one of a plurality of arrangements having;

(d1) said body porting including a port 1 and a port 2 and a right groove of said right bore and a left groove of said left bore on said body, said port 1 is expanding respectively to said right groove on said right bore and said left groove on said right bore of said body, said right groove connecting to a right chamber with an outward surface of said right piston, said left groove connecting to a left chamber with an outward surface of said left piston, said port 2 is through a wall of said body into a middle chamber with an inward surface of said left piston and an inward surface of said right piston;

(d2) said shaft porting including an axial port 3 and an axial port 4 on said shaft, said body having a right groove of said right bore and a left groove of said left bore, said port 3 is respectively expending to a right radial hole to connect to said right groove into a right chamber with an outward surface of said right piston and a left radial hole to connect to said left groove into a left chamber with an outward surface of said left piston, said port 4 of said shaft is expanding through a middle hole into a middle chamber with an inward surface of said left piston and an inward surface of said right piston;

(d3) said hybrid porting including a body porting and a shaft porting, said body porting including a port 1 and a port 2 and a right groove of said right bore and a left groove of said left bore on said body, said port 1 is expanding respectively to said right groove and said left groove, said right groove connecting to a right chamber with an outward surface of said right piston, said left groove connecting to a left chamber with an outward surface of said left piston, said port 2 is through a wall of said body into a middle chamber with an inward surface of said left piston and an inward surface of said right piston, said shaft porting including an axial port 3 and an axial port 4 on said shaft, said port 3 of said shaft is respectively expending to a right radial hole to connect to said right groove into said right chamber with said inward surface of said right piston and to a left radial hole to connect to said left groove into said left chamber with said outward surface of said left piston, said port 4 of said shaft is expanding through a middle hole into said middle chamber with said inward surface of said left piston and said inward surface of said right piston.

2. The actuation module of claim 1, said body assembly further including at least one cover assembly, said cover assembly has a cover, at least one bearing, at least one vertical O-ring and at least one horizontal O-ring, said bearing having an extremal surface and an internal surface respectively defined by one of a plurality of profiles including a spherical profile and a conical prolife, said body having an edge on said right bore, said edge is defined by a mated external surface engaged with said conical internal surface of said bearing, said cover is defined by an internal mated surface engaged with said external conical surface of said bearing, a vertical O-ring groove and a horizontal O-ring groove are respectively defined between said edge and said cover, said vertical O-ring is disposed in said vertical groove, said horizontal O-ring is placed in said horizontal groove, whereby said cover assembly, and said body having a sealing means for providing seals between said body and said cover at any installed position, and a bearing means for supporting loads at any installed position.

3. The actuation module of claim 1, wherein said piston is structured with one of a plurality of materials including a magnetic material, aluminum bronze, ductile iron, said bearing is structured with one of a plurality of materials including a magnetic material, aluminum, nylon, copper.

4. The actuation module of claim 1, wherein said piston is structured with one of a plurality of materials including a magnetic material, aluminum bronze, ductile iron, said bearing is structured with one of a plurality of materials including a magnetic material, aluminum, nylon, copper.

5. The actuation module of claim 1, said body assembly further including a position control assembly having a left screw threaded into a left side of said body assembly for controlling outward positions of said left piston, a right screw threaded into a right side of said body assembly for controlling outward positions of said right piston, at least one middle screw threaded in said body having a conical end to control inward positions of said left piston and inward positions of said right piston.

6. The actuation module of claim 1, said body assembly further including a right set spring against said right piston and a left set spring against said left piston, whereby said body, said pistons and said shaft, said spring sets having a spring means for eliminating backlash between said pistons and said shaft, preventing hard hits between said shaft and said pistons at stop positions, respectively returning presetting positions of said pistons, controlling return speed without counter balance valves.

7. The actuation module of claim 1, said body assembly further at least one vane assembly, said vane assembly having a vane having a land, vane cover and key, said vane cover having a link port, said land having an outward slot and an inward slot, said shaft has a keyway, said vane is disposed between a left side of said body and said left piston and covered by said vane cover, a first chamber and a second chamber are defined by said piston and said vane cover and said vane land, said first chamber is connected to said link port, a second chamber is connected to said center chamber through said inward slot and said axial port and said radial port and gaps between said shaft and said left piston, said vane is coupled with said shaft by said key and said keyway of said shaft for driving said shaft.

8. An actuation module comprising;

(a) At least one body assembly having a body;

(b) At least one shaft assembly having a shaft;

(c) A least one conversion-transmission assembly having one of configurations including;

(c1) A conversion-transmission assembly positioned between said shaft assembly and said body assembly having a helical movement converting mechanism and a movable piston, said helical movement converting mechanism including a helical engagement for providing conversions between reciprocal movements and rotary movements and a reactionary engagement for generating reactionary torques, said helical movement converting mechanism is defined by one of a plurality of arrangements inducing said helical engagement between said piston and said shaft, and said reactionary engagement between said piston and said body, said body has a front cylindrical bore defined by a fixed, centric axis and a back cylindrical bore defined by a fixed eccentric axis, parallel to said fixed centric axis, said piston has two mated cylindrical sections engaged respectively with said front centric bore and said back eccentric bore of said body for providing said reactionary engagement, said helical movement converting mechanism is defined by one of a plurality of structures including a helix spline/helix spline structure and a helix spline/non-helix spline structure, said shaft has helical splines, said piston has mated helical splines engaged with said helical splines of said shaft for providing said helical engagement, whereby said body, said piston and said shaft having a conversion means for providing conversions between reciprocal movements of said piston and rotatory movements of said shaft, and a non-friction reaction means for generating reactionary compression forces with said axises against said shaft;

(c2) Said conversion-transmission assembly positioned between said shaft assembly and said body assembly having helical movement converting mechanisms, a right movable piston and a left movable piston, said helical movement converting mechanism including a helical engagement for providing conversions between reciprocal movements and rotary movements and a reactionary engagement for generating reactionary torques, said helical movement mechanism is defined by one of a plurality of arrangements inducing said helical engagement between said pistons and said shaft, and said reactionary engagement between said pistons and said body, said body has a right, cylindrical bore and at least one middle cylindrical bore respectively defined by a fixed centric axis, a fixed eccentric axis parallel to said fixed centric axis and a left cylindrical bore and said middle cylindrical bore respectively defined by said fixed centric axis and said fixed eccentric axis, said right piston has two mated cylindrical sections engaged respectively with said right bore and said middle bore of said body for providing said reactionary engagement, said left piston has two mated cylindrical sections engaged respectively with said left bore and said middle bore of said body for providing said reactionary engagement, said helical movement converting mechanism is defined by one of a plurality of structures including a helix spline/helix spline structure, and a helix spline/non-helix spline structure, said shaft has right helical splines and left helical splines, said right piston has mated right helical splines engaged with said right helical splines of said shaft for providing said helical engagement, said left piston has mated left helical splines engaged with said left helical splines of said shaft for providing said helical engagement, whereby said body, said pistons and said shaft having a conversion means for providing conversions between reciprocal movements of said pistons and rotatory movements of said shaft, and a non-friction reaction means for generating reactionary compression forces with said axises against said shaft and a balance means for balancing side loads on said left helical splines of said shaft engaged with said right piston, with side forces on said left helical splines on said shaft engaged with said right piston.

9. The actuation module of claim 9, wherein said module having a porting system having one of a plurality of arrangements including (a) a body porting (b) a shaft porting (c) a hybrid porting;

(a) Said body porting including a port 1 and a port 2 and a right groove of said right bore and a left groove of said left bore on said body, said port 1 is on an external surface of said body expanding respectively to said right groove on said right bore and said left groove on said right bore of said body, said right groove connecting to a right chamber with an outward surface of said right piston, said left groove connecting to a left chamber with an outward surface of said left piston, said port 2 is through a wall of said body into a middle chamber with an inward surface of said left piston and an inward surface of said right piston;

(b) Said shaft porting including an axial port 3 and an axial port 4 on said shaft, said body having a right groove of said right bore and a left groove of said left bore, said port 3 is expending to a right radial hole to connect to said right groove into a right chamber with an outward surface of said right piston and a left radial hole to connect to said left groove into a left chamber with an outward surface of said left piston, said port 4 of said shaft is expanding to a middle hole into a middle chamber with an inward surface of said left piston and an inward surface of said right piston;

(c) Said hybrid porting including a body porting and a shaft porting, said body porting including a port 1 and a port 2 and a right groove of said right bore and a left groove of said left bore on said body, said port 1 is on an external surface of said body expanding respectively to said right groove and said left groove on said right bore of said body, said right groove connecting to a right chamber with an outward surface of said right piston, said left groove connecting to a left chamber with an outward surface of said left piston, said port 2 is through a wall of said body into a middle chamber with an inward surface of said left piston and an inward surface of said right piston, said shaft porting having an axial port 3 and an axial port 4, said port 3 of said shaft is expending to a right radial hole to connect to said right groove into said right chamber with said inward surface of said right piston and a left radial hole to connect to said left groove into said left chamber with said outward surface of said left piston, said port 4 of said shaft is expanding to a middle hole into said middle chamber with said inward surface of said left piston and said inward surface of said right piston.

10. The actuation module of claim 9, where said body assembly including at least one cover assembly, said cover assembly has a cover, at least one bearing, at least one vertical O-ring and at least one horizontal O-ring, said bearing is defined by one of a plurality of profiles including a spherical profile and a conical prolife, said body having an edge on said right bore, said edge is defined by a mated external surface engaged with said conical bearing, said cover is defined by an internal mated surface engaged with said conical bearing, a vertical O-ring groove and a horizontal O-ring groove are respectively defined between said edge and said cover, said vertical O-ring and is disposed in said vertical groove, said horizontal O-ring is placed in said horizontal groove, whereby said cover assembly, said shaft and said body having a sealing means for providing seals between said body and said cover at any installed position under loads, and a bearing means for supporting loads at any installed position.

11. An actuation module comprising;

(a) A body assembly having a body;

(b) A shaft assembly having a shaft;

(c) A conversion-transmission assembly positioned between said shaft assembly and said body assembly having helical movement converting mechanisms, a right movable piston and a left movable piston, said helical movement converting mechanism including a helical engagement for providing conversions between reciprocal movements and rotary movements and a reactionary engagement for generating reactionary torques, said helical movement mechanism is defined by one of a plurality of arrangements inducing said helical engagement between said pistons and said shaft, and said reactionary engagement between said pistons and said body, said body has a right, cylindrical bore and at least one middle cylindrical bore respectively defined by a fixed centric axis, a fixed eccentric axis parallel to said fixed centric axis and a left cylindrical bore and said middle cylindrical bore respectively defined by said fixed centric axis and said fixed eccentric axis, said right piston has two mated cylindrical sections engaged respectively with said right bore and said middle bore of said body for providing said reactionary engagement, said left piston has two mated cylindrical sections engaged respectively with said left bore and said middle bore of said body for providing said reactionary engagement, said helical movement converting mechanism is defined by one of a plurality of structures including a helix spline/helix spline structure, and a helix spline/non-helix spline structure, said shaft has right helical splines and left helical splines, said right piston has mated right helical splines engaged with said right helical splines of said shaft for providing said helical engagement, said left piston has mated left helical splines engaged with said left helical splines of said shaft for providing said helical engagement, whereby said body, said pistons and said shaft having a conversion means for providing conversions between reciprocal movements of said pistons and rotatory movements of said shaft, and a non-friction reaction means for generating reactionary compression forces with said axises against said shaft and a balance means for balancing side loads on said left helical splines of said shaft engaged with said right piston, with side forces on said left helical splines on said shaft engaged with said right piston.

(d) A porting system including a port 1 and a port 2 and a right groove of said right bore and a left groove of said left bore on said body, said port 1 is expanding respectively to said right groove on said right bore and said left groove on said right bore of said body, said right groove connecting to a right chamber with an outward surface of said right piston, said left groove connecting to a left chamber with an outward surface of said left piston, said port 2 is through a wall of said body into a middle chamber with an inward surface of said left piston and an inward surface of said right piston;

(e) A spring assembly including a right set spring against said right piston and a left set spring against said left piston, whereby said body, said pistons and said shaft assembly, said spring assembly having a spring means for eliminating backlash between said pistons and said shaft, preventing hard hits between said shaft and said pistons at stop positions, respectively returning presetting positions of said pistons, controlling return speed without counter balance valves.

(f) A position control assembly having a left screw threaded into a left side of said body assembly for controlling outward positions of said left piston, a right screw threaded into a right side of said body assembly for controlling outward positions of said right piston, at least one middle screw threaded in said body having a conical end to control inward positions of said left piston and inward positions of said right piston.