US3838630A

US3838630A - Double-acting positioning linear actuator

Info

Publication number: US3838630A
Application number: US00346653A
Authority: US
Inventors: J Kobelt
Original assignee: Individual
Current assignee: Individual
Priority date: 1973-03-30
Filing date: 1973-03-30
Publication date: 1974-10-01
Anticipated expiration: 1991-10-01

Abstract

This disclosure relates to an infinitely variable double-acting positioning linear actuator which responds proportionally to fluid pressure. The actuator includes a cylindrical housing having a fluid actuating chamber at each end defined by the housing and an axially movable piston means. A center positioning ring is secured axially substantially at the center of the housing. A pair of spring retainer means interface the piston means at each end of the housing and interact compressively with opposite sides of the center positioning ring. A mechanical coil compression spring interacts with the spring retainer means. The piston means are interconnected to the housing by diaphragm means. The spring retainer means are slidably mounted on a positioning actuator rod which interconnects the pistons and extends slidably outside each end of the housing.

Description

Oct. 1, 1974 DOUBLE-ACTING POSITIONING LINEAR ACTUATOR [76] Inventor: Jack R. Kobelt, 235 E. 5th Ave., Vancouver 10, British Columbia, Canada [22] Filed: Mar. 30, 1973 [21] Appl. No.: 346,653

[52] US. Cl 92/48, 92/99, 92/131 [51] Int. Cl. F01b 19/00 [58] Field of Search 92/48, 97, 99, 130, 131, 92/38 [56] References Cited UNITED STATES PATENTS 867,282 10/1907 MacFarren 92/131 X 1,835,919 12/1931 Waseige 92/48 X 2,381,259 8/1945 Coffey 92/48 X 2,529,393 11/1950 Hogue 92/131 X 2,627,750 2/1953 Titus 92/38 X 2,671,470 3/1954 Boteler 92/48 X 3,106,135 10/1963 McAfee, Jr. et al.. 92/131 X 3,683,753 8/1972 Johnson 92/48 Primary Examiner-lrwin C. Cohen Assistant Examinen-Abraham Hershkovitz 5 7] ABSTRACT This disclosure relates to an infinitely variable doubleacting positioning linear actuator which responds proportionally to fluid pressure. The actuator includes a cylindrical housing having a fluid actuating chamber at each end defined by the housing and an axially movable piston means. A center positioning ring is secured axially substantially at the center of the housing. A pair of spring retainer means interface the piston means at each end of the housing and interact compressively with opposite sides of the center positioning ring. A mechanical coil compression spring interacts with the spring retainer means. The piston means are interconnected to the housing by diaphragm means. The spring retainer means are slidably mounted on a positioning actuator rod which interconnects the pistons and extends slidably outside each end of the housing.

7 Claims, 5 Drawing Figures PATENTEUBBT H874 3.838.630.

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DOUBLE-ACTING POSITIONING LINEAR ACTUATOR DISCLOSURE This invention relates to novel improvements in devices which are known in the art to which they pertain as fluid operated linear actuators, or to devices such as hydraulic and pneumatic actuators which are of the general character of linear actuators. Specifically, my invention relates to linear actuators in which fluid acutation is opposed by spring means, thereby providing an infinitely variable pressure proportional linear positioning means. Still more specifically, my invention provides infinitely variable pressure-proportional linear positioning in two axially opposite directions.

In their simplestform, positioning linear actuators comprise a cylinder portion, a piston portion, a rod portion, and a spring means. Fluid power is employed to move the rod and piston portions with respect to the cylinder portion. Where movement of the piston is opposed by a spring means whose force is proportional to deflection, or piston movement, the linear position of the rod and piston will be proportional to the fluid pressure. My invention provides structure whereby a single mechanical spring is interposed between a pair of pistons secured to a rod such that fluid pressure may be applied to either piston to provide double-acting positioning. Further, rolling diaphragms are employed to seal actuation chambers formed between the cylinder portions and piston portions, thereby substantially eliminating hysteresis in low pressure fluid positioning linear actuators. Still further, my invention incorporates a rod which is slidably mounted in the outer end of each actuation chamber thereby providing piston guidance, substantially equal piston pressures, and a double-acting positioning linear actuator assembly which may operatively actuate a device at either or both ends of the assembly.

My invention is adapted for use in devices which require infinitely variable linear positioning in two axial directions. An example of such a device is a controllable pitch propeller requiring infinitely variable forward Accordingly, it is one object of my invention to provide a double-acting positioning linear actuator employing a single centering and position proportioning spring means. Another object of my invention is to provide a double-acting positioning linear actuator wherein diaphragm piston-cylinder interconnections substantially eliminate positioning hysteresis. Yet another object of my invention is to provide a doubleacting positioning linear actuator assembly whose pistons are secured to a single rod which equalizes piston area, guides the pistons and provides positioning at either one or both ends of the assembly. Still another object of my invention is to provide a double-acting positioning linear actuator having structure which results in economics of manufacture and simplicity of maintenance. These and further objects of my invention,

which reside in its, details of structure and operation, will be evident from a study of the following disclosure and accompanying drawings which illustrate my now preferred embodiment of the invention. This embodiment is merely exemplary and is not intended to detract from the full scope'of the invention as set out of the annexed claims. I

In the drawings, wherein like numerals refer to lik parts:

FIG. 1 is a side elevation showing the overall outer structure of my invention;

FIG. 2 is a sectional view of my invention taken substantially along line 2-2 in FIG. 1, and illustrates the inner structure of my invention;

FIG. 3 is an end view of my invention taken substantially along line 33 in FIG. 1;

FIG. 4 is a sectional view of my invention taken substantially along line 4-4 in FIG. 1;

FIG 5 is a sectional view of my invention taken substantially along line 5-5 in FIG. 1.

Turning now to the drawings, FIGS. 1 and 3 illustrate the exterior of my invention wherein a cylindrical housing means 21 comprises a first end-portion 22 and a second end-portion 23. Housing means 21 may be op eratively mounted on a frame or base (not shown) by means of foot members 24 having holes 25. Actuation rod means 26 is slidably mounted in the end-

portions

22 and 23 for axial movement, substantially parallel to the central axis of housing means 21 and rod means 26, in either

direction

27 or 28. An actuated device may be connected operatively to either one or both

ends

29 and 30 of rod means 26 by means of threaded holes 31.

With reference now to all of FIGS. 1 5, it will be seen that housing means 21 comprises spring chamber portion 31 axially interposed between

actuation chambers

32 and 33. Actuation rod means 26 comprises spring section 34 and

outer sections

35 and 36 inter connectedby screw thread 37. Pistons means 38 and 39 secured axially by the threaded interconnections respectively between rod portions 34 and 35, and rod portions 34 and 36. Piston means 38 and 39 include rolling diaphragm means 40 secured between piston cover plate 41 and piston body 42 by means of screws 43. Diaphragms 40 are secured to housing 21 by means of actuation chamber flanges 44, spring chamber flanges 45, and bolts 46. Piston cover plate 41 is sealed by sealing means 47 to prevent fluid flow from

chambers

32 and 33 into spring chamber 31. Sealing means 67 prevents fluid flow from

chambers

32 and 33 to the exterior of housing 21.

Spring chamber portion 31 comprises two

flanged sections

48 and 49 having central flanges 50. Secured between flanges 50 by bolts 51 is centering means 52 comprising

split ring segments

53 and 54 extending radially inward to a diameter indicated by inner cylindrical surface 55. Slidably mounted on rod means 26 are a pair of spring retainer means 56 and 57, comprising

cup portions

58 and 59, each on one side of centering means 52, and a plurality of centering members 60 and 61, respectively, spaced about the outer circumferences of

cups

58 and 59 and extending through centering means 52.

Cup portions

58 and 59 are adapted respectively for compressive axial contact between

surfaces

62 and 63 and

surfaces

64 and 65 of piston means 38 and 39. Centering members 60 and 61 are adapted respectively for compressive axial interaction between

sides

62 and 63 of centering means 52 and are adapted to mesh axially whereby to permit axial movement of one of retainer means 56 and 57 with respect to the other. A compressive spring means 66 is interposed between retainer means 56 and 57, such that the spring retainer means are forced respectively against

pistons

38 and 39. Spring means 66 comprises a precision mechanical coil spring through the coils of which rod portion 34 passes.

Operation of my invention may now be considered with reference to FIGS. 1 and 2.When fluid pressure in

chambers

32 and 33 is less than that required to overcome the force of spring means 66,

member portions

68 and 69 of members 60 and 61 respectively will be forced against

sides

70 and 71 of centering means 52. Fluid entering actuation chamber 33 through

inlet ports

72 and 73, such that the force of spring means 66 is overcome, will cause piston 39 to move in direction 28. Whereas member portions 68 hold retainer 56 and end 77 of spring 66 with respect to centering means 52 and housing 21, portions 69 will be carried in direction 28 by piston 39 into a position away from side 70 of centering means 52, just as shown in FIG. 2. The higher the subsequent pressure in chamber 33, proportionately further in direction 28 piston 39 and retainer 57 will move, until ultimately surface 74 of piston 38 bottoms out against surface 75 of chamber 32. Conversely, if the fluid from chamber 33 is now exhausted and fluid pressure applied to chamber 32, portions 69 will hold end 76 of spring 66 and retainer 56 will be carried with piston 38 in direction 27.

Hence, equal pressures in

chamber

32 and 33 will cause rod 26 to be centered, a higher pressure in chamber 32 than in chamber 33 will cause rod 26 to move in direction 27, and a higher pressure in chamber 33 than in chamber 32 will cause rod 26 to move in direc tion 28. The distance moved from the center position in either

direction

27 or 28 will be directly proportional to the fluid pressure differentialbetween chambers 32 and33. When the pressure in

chambers

32 and 33 are returned to zero or an equal pressure, such as atmospheric pressure, rod 26 will consistently return to a a center or neutral position.

It should be noted that whereas theoretically no change in volume occurs in spring chamber 31 during movement of rod 26, vent holes 78 permit fluid leakage for whatever reason into chamber 31, from either of

chambers

32 and 33, to escape (see FIG. 1).

It is believed that my invention of a double-acting positioning linear actuator will have been clearly understood from the foregoing detailed description of my now preferred and illustrated embodiment. Various modifications, changes, additions, and equivalents may be resorted to in view of these teachings by one skilled in this art without departing from the spirit of my invention. For instance, split centering ring 52 might readily comprise a plurality of members extending radially into chamber 31; conversely,

member portions

68 and 69 might readily extend through slots in the cylindrical surface of chamber 31 thereby eliminating the need for inward radial projections in chamber 31.

Member portions

68 and 69 might be removable, adjustable, or otherwise operatively secured to spring retainer means 56 and 57. Spring retainer means 56 and 57 might be telescopically inter-related, slots being provided operatively for

member portions

68 and 69. Spring means 66 might readily comprise a plurality of spring means spaced about rod portion 34. Therefore, whereas a choice between such variations, modifications, changes, additions, and equivalents falling within the true scope of my invention will depend largely upon the circumstances in which my invention is used, itis my express intention that no limitations be implied and that the hereto annexed claims be given the broadest interpretation to which the language fairly admits.

The embodiments of the invention in which an exclusive property or privilege is claimed are defined as follows:

1. A double-acting positioning linear actuator comprising a cylindrical housing having first and second end-portions, an actuation chamber in each of said end-portions, a spring chamber portion interposed axially between said actuation chambers, an actuating rod means slidably mounted in at least one of said endportions for axial movement substantially parallel to the central axis of said cylindrical housing, in each of said actuation chambers a piston means operatively secured to said actuating rod means, a centering means secured to said spring chamber portion, a pair of spring retainer means slidably mounted on said actuating rod means between said piston means, compressive spring means between said pair of spring retainer means, each of said pair of spring retainer means comprising a cup portion and a centering portion, said centering means comprising a ring extending radially into said spring chamber portion, said cup portion interacting compressively with said piston means in said one of said endportions, said centering portion extending through said ring and interacting with a portion of said ring facing said other of said end-portions to limit the extent of outward movement of said cup portion, whereby fluid pressure in one of said actuation chambers compresses said spring means and causes said piston means and said actuating rod means and one of said pair of spring retainer means to move axially with respect to said cylindrical housing means.

2. A double-acting positioning linear actuator as delined in claim 1, wherein at least one of said piston means is slidably mounted in said cylindrical housing means, seal means adapted substantially to prevent fluid flow axially between one of said actuation chambers and said spring chamber portion.

3. A double-acting positioning linear actuator as defined in claim 1, wherein at least one of said piston means is secured axially to said actuating rod means, there being a clearance between the outer cylindrical surface of said piston means and the inner cylindrical surface of said actuation chamber, rolling diaphragm means operatively connected to said piston means and said cylindrical housing means, said actuating rod means extending outside each end of said cylindrical housing means.

4. A double-acting positioning linear actuator as deflned in claim 3, wherein at least one of said actuation chambers has an assembly flange, said spring chamber portion comprising two flanged sections, said centering means comprising a ring operatively secured between interfacing flanges of said two flanged sections and extending radially into said spring chamber portion, said rolling diaphragm means operatively secured between one flange of one of said flanged sections and said assembly flange.

5. A double-acting positioning linear actuator as defined in claim 1, wherein each of said cup portions on one side of said centering means and said centering portion comprising a plurality of centering members extending axially to the other side of said centering means, said plurality of centering members of one of said sping retainer means meshing axially with said centering members of the other of said spring retainer means, each of said centering members in operative compressive relation with said centering means.

6. A double-acting positioning linear actuator as defined in claim 1, wherein said compressive spring means comprises a single mechanical coil spring, said actuating rod means passing through the coils of said mechanical coil spring.

7. A double-acting positioning linear actuator comprising a cylindrical housing means having first and second end-portions, an actuation chamber in each of said end-portions, a spring chamber portion interposed axially between said actuation chambers, an actuating rod means slidably mounted in each of said end-portions, in each of said actuation chambers a piston means operatively secured to said actuating rod means, a centering means secured to said spring chamber portion, slidably mounted on said actuating rod means between said piston means a pair of spring retainer means having a cup portion and a centering portion, said cup portion on one side of said centering means and said centering portion comprising a plurality of centering members extending axially to the other side of said centering means, said plurality of centering members of one of said spring retainer means meshing axially with said centering members of the other of said spring retainer means, each of said centering members in operative compressive relation with said centering means, a compressive spring means between said pair of spring retainer means, whereby fluid pressure in one of said actuation chambers causes said piston means and said actuating rod means and one of said pair of spring retainer means to move axially with respect to said cylindrical housing means.

Claims

1. A double-acting positioning linear actuator comprising a cylindrical housing having first and second end-portions, an actuation chamber in each of said end-portions, a spring chamber portion interposed axially between said actuation chambers, an actuating rod means slidably mounted in at least one of said endportions for axial movement substantially parallel to the central axis of said cylindrical housing, in each of said actuation chambers a piston means operatively secured to said actuating rod means, a centering means secured to said spring chamber portion, a pair of spring retainer means slidably mounted on said actuating rod means between said piston means, compressive spring means between said pair of spring retainer means, each of said pair of spring retainer means comprising a cup portion and a centering portion, said centering means comprising a ring extending radially into said spring chamber portion, said cup portion interacting compressively with said piston means in said one of said end-portions, said centering portion extending through said ring and interacting with a portion of said ring facing said other of said end-portions to limit the extent of outward movement of said cup portion, whereby fluid pressure in one of said actuation chambers compresses said spring means and causes said piston means and said actuating rod means and one of said pair of spring retainer means to move axially with respect to said cylindrical housing means.

2. A double-acting positioning linear actuator as defined in claim 1, wherein at least one of said piston means is slidably mounted in said cylindrical housing means, seal means adapted substantially to prevent fluid flow axially between one of said actuation chambers and said spring chamber portion.

4. A double-acting positioning linear actuator as defined in claim 3, wherein at least one of said actuation chambers has an assembly flange, said spring chamber portion comprising two flanged sections, said centering means comprising a ring operatively secured between interfacing flanges of said two flanged sections and extending radially into said spring chamber portion, said rolling diaphragm means operatively secured between one flange of one of said flanged sections and said assembly flange.