US3680442A

US3680442A - Gas pressure driven vibratory cylinder construction

Info

Publication number: US3680442A
Application number: US87187A
Authority: US
Inventors: Donald C Kanning
Original assignee: Individual
Current assignee: Individual
Priority date: 1970-11-05
Filing date: 1970-11-05
Publication date: 1972-08-01
Anticipated expiration: 1989-08-01

Abstract

A freely reciprocating piston is movable between opposite cylinder end chambers with pressurized gas introduced alternately into the end chambers and exhausted from each chamber during at least a portion of the period that it is not being so introduced into that chamber so as to oppositely drive the piston continuously reciprocally. A single exhaust port in the cylinder side wall is located adjacent a first of the cylinder end chambers directly open to that end chamber during part of the piston movement and overlapped by the piston disrupting such direct opening during the remainder of piston movement. A single gas inlet port at the cylinder side wall is spaced between the cylinder end chambers communicating through a first gas channel formed through the piston with the first cylinder end chamber during a part of the time the piston overlaps the exhaust port and communicating through a piston second gas channel with a second of the cylinder end chambers during a part of the time the exhaust port is directly open to the first cylinder end chamber.

Description

United States Patent Kanning [is] 3,680,442 [4 1 Aug. 1,1972

[54] GAS PRESSURE DRIVEN VIBRATORY CYLINDER CONSTRUCTION [72] lnyentorz- Donald .C. Kanning, Long Beach,

Calif.

[73] Assignee: Ben C. Klingenmlth, Compton,

Calif.

[22] Filed: Nov. 5, 1970 [21] Appl.No.: 87,187

[52] U.S.Cl. ..91/234 [51] lnt.Cl. ..F01l 21/02 [58] Field of Search ..91/234 56] References Cited UNITED STATES PATENTS.

2,763,060 9/1956 Swanson ..91/234 2,797,664 7/1957 Swanson ..91/234 FOREIGN PATENTS OR APPLICATIONS 1,138,621 1/1957 France ..91/234 Primary Examiner-Paul E. Maslousky Attorney-Mahoney, Hornbaker & Schick 7 cylinder end chamber.

A freely reciprocating piston is movable between opposite cylinder end chambers with pressurized gas introduced alternately into the end chambers and exhausted from each chamber during at least a portion of the period that it is not being so introduced into that chamber so as to oppositely drive the piston continuously reciprocally. A single exhaust port in the cylinder side wall is located adjacent a fust of the cylinder end chambers directly open to that end chamber during part of the piston movement and overlapped by the piston disrupting such direct opening during the remainder of piston movement. A single gas inlet port at the cylinder side wall is spaced between the cylinder end chambers communicating through a first gas channel formed through the piston with the first cylinder end chamber during a part of the time the piston overlaps the exhaust port and communicating through a piston second gas channel with a second of the cylinder end chambers during a part of the time the exhaust port is directly open to the first 13 Claims, 10 Drawing Figures PATENTEDMIQ H912 3.680.442

SHEET 1 0F 2 FIG.I. 42 46 4o F/G.2. 42\ 46 FIG.3. 2 46 3 40 F165. x

INVENTOR DONALD C. KANNl/VG MAHONEY, HORNBAKER AND SCH/CK ATTORNEYS PATENTEDMIG H972 3.680.442

SHEET 2 OF 2 FIG. 6.

FIG. Z

58\ 54 FIG. 8.

58 54 82 72 56 78 52 80 FIG. 9.

58\54 82 72 56 78 52 80 FIG. I0.

INVENTOR.

54 82 56 78 52 DONALD CKANNING MAHONEY, HORNBAKER AND SCH/CK ATTORNEYS GAS PRESSURE DRIVEN VIBRATORY CYLINDER CONSTRUCTION BACKGROUND OF THE INVENTION This invention relates to an improved gas pressure driven vibratory cylinder construction and more particularly, to such a vibratory cylinder of simplified form operating in an improved manner. According to the principles of the present invention, only a single exhaust port is required for exhausting gas from the opposite cylinder end chambers during the operation thereof, thereby, not only simplifying the original manufacture of the cylinder, but also greatly simplifying the normal exterior controls connected to the exhaust port such as exterior valving for cylinder amplitude control and variation, and exterior muffling for reducing the noise created by the vibratory cylinder operation.

Also, according to certain of the principles of the present invention, the vibratory cylinder construction may include a unique gas inlet port and piston gas channel relationship such that when the operation of the cylinder is ceased and the piston thereof stops endwise midway of the cylinder, a relatively common occurrence in vibratory cylinders of the character involved, the gas inlet port is always partially open, through a particular of the piston gas channels, to one of the cylinder end chambers so that the cylinder will once again resume normal operation when restarted despite the piston midpoint positioning. Still in addition, and with even further refinement and expansion of the foregoing principle providing a unique relationship between all of the cylinder inlet and exhaust ports and the piston gas channels, the vibratory cylinder of the present invention may be provided with at least one of the cylinder gas inlet and exhaust ports always in gas flow communication with one of the cylinder end chambers despite the particular endwise positioning of the piston within the cylinder. This latter refinement assures that the vibratory cylinder will always properly commence operation upon inlet gas being admitted to the cylinder gas inlet port and the piston can never assume a position in which such immediate operational starting will not take place.

Various forms of gas pressure driven, free piston, vibratory cylinders of the general character herein involved have been produced, the prime use thereof being for supplying vibrational motion to various mechanisms where such is required or desired. For instance, in modern mass production manufacturing lines, there are many occasions where component parts are separately manufactured and then must be transported in various sequential orders to subassembly and final assembly equipment. In some cases, if proper conveying equipment can be provided, the component parts may be automatically conveyed as produced one at a time to the various assembly equipment and used by the assembly equipment one at a time upon such arrival. In other cases, the components parts may be manufactured and transported en masse in lots to the various assembly equipment, there placed into various forms of specialized conveying equipment to be properly positioned or aligned and directly fed into the assembly equipment in proper positionable form, an example of the former being generally in-line or straight-line conveying equipment and an example of the latter being bowl feeding equipment.

In either case, although various forms of endless belt conveyors have been previously used, it has become quite common to use vibratory equipment for producing the motions required and for progressively moving the various components, for instance, along a particu;

lar path of travel or from a mass quantity supply into consecutive positioning and into some form of assembly machine. It is this latter vibratory equipment with which the vibratory cylinders of the present invention may be involved for producing the vibratory motion required for the proper transportation and positioning. Furthermore, in this more refined use of vibratory cylinders, selectively variable frequency of vibration and selectively variable amplitude of vibration are required of the vibratory cylinders to produce the results desired.

To my knowledge, all prior constructions of gas pressure driven, free piston, vibratory cylinders have been similarly formed including a normally centrally located gas inlet port at the cylinder side walls and opposite gas outlet ports at opposite end portions of the cylinder side walls and adjacent the opposite cylinder end chambers. Various forms of gas channels have been formed directly through the piston providing gas flow communication between the cylinder inlet port and the opposite cylinder end chambers during various movement of the piston. The overall resulting arrangement is that the inlet gas entering through the cylinder inlet port is alternately directed by the piston gas channels to the opposite cylinder end chambers, the inlet gas being directed into one cylinder end chamber while the cylinder exhaust port at the opposite cylinder end chamber is opened to exhaust gas therefrom, thereby producing reciprocating movement of the piston on a continuous basis merely through piston movements to produce the vibrations of the vibratory cylinder.

One of the more troublesome problems encountered with such vibratory cylinders is that, due to the particular positioning of the cylinder gas inlet and exhaust ports in combination with the piston gas channels, it is possible to position the pistons within the cylinders so that at the start of feeding of the inlet gas into the cylinder, initial piston movement will not be produced, but rather the piston will remain stationary within the cylinder and operation thereof will be frustrated. In such cases with these prior vibratory cylinder constructions, in order to accomplish normal operation, it is necessary to apply sharp impacts to the cylinder sufficient to urge the piston in one direction or another until an unbalanced condition is obtained and the cylinder will operate normally. This can result in damage to the particular vibratory cylinder and the equipment upon which it is installed, and furthermore, there are many occasions where the vibratory cylinders must be installed at locations not accessible for applying such impacts so that such condition can become completely prohibitive as to vibratory cylinder use.

Still further with the use of gas pressure driven, free piston, vibratory cylinders, it is obvious that an increase in inlet gas pressure to the cylinder will increase the speed of movement or, in this case, the frequency of the piston movement and a decrease in inlet gas pressure will decrease the same, thereby directly varying the frequency of vibration of the vibratory cylinder construction. More important to the principles of the present invention, it is further obvious that a variable control of exhaust gas flow from the vibratory cylinders will necessarily control the amplitude of movement of the pistons within the cylinders, a restriction of exhaust gas flow decreasing the piston amplitude and an increase in exhaust gas flow increasing the amplitude. With the combined frequency and amplitude control in use of vibratory cylinders, desired vibratory effects on various conveying equipment may be produced in order to properly convey at the desired speeds and in the desired manners the production materials involved.

With the prior vibratory cylinder constructions having the two exhaust ports at opposite ends of the cylinder, if proper exhaust gas control is to be accomplished for the amplitude control, it is necessary to either join the cylinder exhaust ports or separately control the same by the use of various tubing and valving. At the same time, it is usually desirable to provide some means for muffling the exhaust gas flow, again requiring mechanism to be attached to the vibratory cylinders immediately exterior thereof. Obviously, if the cylinder exhaust ports can be reduced to one in number for each such cylinder, rather than the two presently involved, this exteriorly connected mechanism can not only be reduced in size and complication, but the cost thereof will be reduced accordingly.

OBJECTS AND SUMMARY OF THE INVENTION It is, therefore, an object of this invention to provide an improved gas pressure driven vibratory cylinder construction wherein by providing a unique combination of cylinder inlet and exhaust gas porting, piston gas channeling and piston movement, it is possible to provide a fully operational vibratory cylinder which has merely a single cylinder gas inlet port and, more important, merely a single cylinder gas exhaust port. In one form of the invention, a single purpose piston inlet gas channel directs the inlet gas from the cylinder inlet port to a first cylinder end chamber, the gas being exhausted from this first cylinder end chamber immediately into the single cylinder exhaust port, and a dual purpose piston gas channel directs inlet gas from the cylinder inlet port to the second cylinder end chamber and from this second cylinder end chamber into the single cylinder exhaust port depending on the piston position. In another form of the invention, the first cylinder end chamber receives inlet gas and exhausts directly to the cylinder exhaust port in the same manner, but the dual purpose piston gas channel for the second cylinder end chamber is replaced by two particularly positioned piston gas channels, one acting as a gas inlet channel from the cylinder gas inlet to the second end chamber and the other acting as a gas exhaust channel from the second end chamber to the cylinder exhaust port.

Thus, not only are the original manufacturing operations for producing the vibratory cylinders reduced in number due to the elimination of one of the previously required cylinder exhaust gas ports, but only a single control for cylinder amplitude control is required due to there now only being a single gas exhaust port. This results in greatly simplified exterior mechanisms for the vibratory cylinders occupying less space and reducing the cost for provision of the same. Also, where exhaust gas muffling is desired to reduce the noise thereof, only a single exterior muffling mechanism is required for each vibratory cylinder, again reducing required space and cost.

It is also an object of this invention to provide an improved gas pressure driven vibratory cylinder construction with which, if the piston stops within the cylinder at a dead center endwise positioning when cylinder operation is interrupted, the relative positioning between the cylinder gas inlet port and one of the piston gas channels is such that the cylinder functioning may be resumed without difficulties, thereby eliminating a relatively commonly encountered problem with the prior vibratory cylinder constructions. According to certain of the principles of the present invention, with the piston endwise midway of the cylinder, the cylinder gas inlet port is always in communication with one of the cylinder end chambers through one of the piston gas channels. Thus, when inlet gas flow is applied to the cylinder gas inlet port, movement of the piston within the cylinder will always be commenced and the automatic operation thereof will necessarily follow.

With an even further refinement of the vibratory cylinder construction of the present invention, the cylinder gas inlet and exhaust ports, along with the piston gas channels may be positioned relative to each other such that regardless of the position of the piston endwise within the cylinder, there will always be a communication from at least one of the cylinder end chambers and at least one of the cylinder inlet and exhaust ports. This results in the fact that it is virtually impossible to position the piston stationary at any location within the cylinder where functional operation of the cylinder cannot be immediately commenced merely by applying a pressurizedv gas supply to the cylinder inlet port. The vibratory cylinder of the present invention is, therefore, fully operational under virtually every piston positioning which has not been true with the prior constructions as hereinbefore discussed.

Other objects and advantages of the invention will be apparent from the following specification and the accompanying drawings which are for the purpose of illustration only.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a vertical sectional view of a first embodiment of the vibratory cylinder principles of the present invention illustrating the cylinder with the piston thereof at a midway endwise position to clearly show certain of the inventive features of the vibratory cylinder construction of the present invention;

FIGS. 2, 3, 4 and 5 are similar views to FIG. 1, but showing progressive positions of the piston within the cylinder during normal operation thereof;

FIG. 6 is a view similar to FIG. 1, but of a second embodiment of the principles of the present invention; and

FIGS. 7, 8, 9 and 10 are views similar to FIG. 6 showing progressive positions of the piston within the cylinder during normal operation thereof.

DESCRIPTION OF THE BEST EMBODIMENTS CONTEMPLATED Referring to FIGS. 1 through 5 of the drawings, a first embodiment of the improved gas pressure driven vibratory cylinder construction of the present invention is shown and includes a cylinder generally indicated at 20 having a single gas inlet port 22 and a single gas exhaust port 24 formed through a side wall 26 thereof. A piston generally indicated at 28 is endwise reciprocal within the cylinder and defines a first cylinder end chamber between a first piston end 32 and a first cylinder end wall 34, and defines a second cylinder end chamber 36 between a second piston end 38 and a second cylinder end wall 40. This first embodiment of the improved vibratory cylinder construction of the present invention, as well as the second embodiment to be hereinafter described, are formed of usual materials and by usual manufacturing processes appropriate to the uses to which the cylinders are subjected.

The cylinder exhaust port 24 is spaced from the first cylinder end wall 34 a distance relative to the length of the piston 28 so that when the piston moves to the right as shown, expanding the first cylinder end chamber 30 and reducing the second cylinder end chamber 36, the exhaust port is ultimately uncovered or opened by such piston movement approximately one-half way directly to the first cylinder end chamber. At the same time, the exhaust port 24 is located such that when the piston 28 moves inthe opposite direction or to the left as shown, the piston ultimately completely overlaps and completely interrupts the communication between said exhaust port and the first cylinder end chamber 30. The cylinder inlet port 22 is spaced from the cylinder exhaust port 24 and a greater distance from the first cylinder end wall 34, the inlet port always being overlapped by the piston 28 although in a particular relative location as will be hereinafter described.

A piston first gas channel 42 is formed angularly through the piston 28 between an annular groove 44 circumscribing the piston and opening outwardly against the cylinder side wall 26, and the first piston end 32, thereby providing communication between the cylinder side wall 26 completely around the extent thereof and the first cylinder end chamber 30. A similar piston second gas channel 46 is formed angularly through the piston 28 between a similar piston circumscribing groove 48 and the second piston end 38 so as to provide communication between the cylinder side wall 26 and the second cylinder end chamber 36. Obviously, the piston first and

second gas channels

42 and 46 and their

grooves

44 and 48 are particularly positioned within the piston 28 and relative to the cylinder inlet and

exhaust ports

22 and 24, and it will be noted that the groove 44 for the piston first gas channel 42 is spaced toward the second cylinder end chamber 36 while the groove 48 for the piston second gas channel 46 is spaced toward the first cylinder end chamber 30.

The relative positioning of the piston first and

second gas channels

42 and 46, as well as the positioning of the cylinder inlet and

exhaust ports

22 and 24 will be clearly understood from a description of the normal operation of the cylinder 20 which is clearly illustrated in FIGS. 2 through 5. Beginning with FIG. 2, the piston 28 at this particular stage of operation is in the process of moving toward the right as shown expanding the first cylinder end chamber 30 and decreasing the second cylinder end chamber 36. The piston first gas channel 42 and its groove 44 have just been cut off from communication with the pressurized inlet gas, preferably air, entering through the cylinder inlet port 22, the piston second gas channel 46 and its groove 48 have just been cut off from communication with the cylinder exhaust port 24 and are just commencing communication with the cylinder inlet port 22, and the first cylinder end chamber 30 is just beginning to open into direct communication with the cylinder exhaust port 24. Thus, gas pressure still remains in the first cylinder end chamber 30 urging the piston 28 to the right, while gas pressure is just initially beginning to build in the second cylinder end chamber 36.

As shown in FIG. 3, the piston 28 has progressed to the right to approximately the maximum or turning point with the piston second gas channel 46 well open in communication with the inlet port 22 building pressure in the second cylinder end chamber 36 beginning to force the piston 28 in reverse direction to the left. The piston first gas channel 42 is well cut off from communication with the inlet port 22, but the movement of the piston 28 has open direct communication from the first cylinder end chamber 30 and the exhaust port 24 virtually removing all pressure from the first cylinder end chamber.

As shown in FIG. 4, the piston 28 has fully reversed direction in its reciprocal movement and has moved to the left nearly midway of the cylinder 20 just cutting off communication between the inlet port 22 and the piston second gas channel 46, but not yet establishing communication between the piston first gas channel 42 and the inlet port. The piston 28 is nearly completely overlapping the exhaust port 24 and is just ready to cut off the direct opening communication between the first cylinder end chamber 30 and the exhaust port. Thus, with the piston second gas channel 46 not yet having reached the location of the exhaust port 24, the contained pressure within the second cylinder end chamber 36 continues to force the piston 28 to the left and pressure has not yet begun to build in the first cylinder end chamber 30.

Completing the illustration of operation of the first embodiment cylinder 20, as shown in FIG. 5, the piston 28 has reached its extent of movement to the left, has reversed and is beginning to move to the right as a result of the pressurized gas from the inlet port 22 through the piston first gas channel 42 entering the first cylinder end chamber 30 and the second cylinder end chamber 36 exhausting through the piston second gas channel 46 into the exhaust port 24. The piston 28 is, therefore, approaching the position of FIG. 2 completing one reciprocal cycle.

Thus, the cylinder 20 is fully operational despite the fact that there is only a single cylinder exhaust port 24. In operation, and as is clear from the foregoing description, the piston first gas channel 42 acts as a single purpose gas inlet channel, while the piston second gas channel 46 is a dual purpose channel acting part of the time as a gas inlet channel and part of the time as a gas exhaust channel.

As hereinbefore described and as illustrated in FIG. 1, one of the frequently encountered problems with the prior similar vibratory cylinder constructions is that when the pistons thereof stop at dead center, as they occasionally do, the cylinder operation will not automatically start when pressurized inlet gas is applied thereto and according to certain of the principles of the present invention, such problem has been eliminated. It will be noted from FIG. 1 that when the piston 28 is exactly endwise midway of the cylinder 20, the groove 44 of the piston first gas channel 42 is slightly open to the inlet port 22. For this reason, when initial gas pressure is applied to the inlet port 22, pressure immediately begins to build in the first cylinder end chamber 30 urging the piston 28 to the right so that initial motion will always be started.

Furthermore, according to additional refinements of the present invention as included in this first embodiment vibratory cylinder construction shown in FIGS. 1 through 5, the particular positioning relationship between the various inlet and

exhaust ports

22 and 24 and the piston first and

second gas channels

42 and 46 is such that, regardless of the position that the piston 28 stops within the cylinder 20 at termination of the cylinder operation, there will always be at least one of the inlet and

exhaust ports

22 and 24 open to at least one of the first and second

cylinder end chambers

30 and 36. Thus, any time that pressurized gas is again applied to the inlet port 22, motion of the piston 28 within the cylinder 20 will always be immediately resumed.

In the midpoint positioning of the piston 28 within the cylinder 20, the first cylinder end chamber 30 is open to the inlet port 22 through the piston first gas channel 42 as hereinbefore pointed out so that application of pressurized gas to the inlet port will begin movement of the piston to the right. In the FIG. 2 position of the piston 28, the second cylinder end chamber 36 is open to the inlet port 22 through the piston second gas channel 46 and the first cylinder end chamber 30 is directly open to the exhaust port 24, again assuring start of motion of the piston, in this case, to the left.

The FIG. 3 positioning of the piston 28 is similar to that of FIG. 2 with slightly greater openings, thereby assuring a start of piston motion to the left. Likewise, the position of the piston 28 in FIG. 5 is merely slightly advanced to the left from that in FIG. 1. In FIG. 5, the inlet port 22 is open to the first cylinder end chamber 30 through the piston first gas channel 42, and the exhaust port 24 is open to the second cylinder end chamber 36 through the piston second gas channel 46 beginning the motion of the piston 28 to the right as in FIG. 1.

In the FIG. 4 position of the piston 28, the exhaust port 24 is open directly to the first cylinder end chamber 30 but the piston is positioned such that the inlet port 22 is closed by the piston exactly between the

grooves

44 and 48 to the piston first and

second gas channels

42 and 46, respectively. When pressurized gas is applied to the inlet port 22, however, the natural minute clearances between the piston 28 and the cylinder 20 will permit gas leakage substantially equally into the first and second

cylinder end chambers

30 and 36 through their respective piston first and

second gas channels

42 and 46. Since the exhaust port 24 is open directly to the first cylinder end chamber 30, the pressurized gas entering this first cylinder end chamber will begin to exhaust through the exhaust port while pressure will begin to rise in the second cylinder end chamber through lack of communication into the exhaust port, thereby again assuring initial motion of the piston 28 to the left.

The second embodiment of the vibratory cylinder construction of the present invention illustrated in FIGS. 6 through is similar in many respects to the first embodiment construction just described and includes a cylinder generally indicated at 50 having inlet and

exhaust ports

52 and 54 formed through a side wall 56. A piston generally indicated at 58 is endwise reciprocal between a first cylinder end chamber 60 defined by a first piston end 62 and a first cylinder end wall 64, and a second cylinder end chamber 66 defined by a second piston end 68 and a second cylinder end wall 70. The basic difference between the first and second embodiment cylinder construction is in the formation of the piston gas channels and the particular relationship thereof with the inlet and

exhaust ports

52 and 54.

Returning briefly to the first embodiment of the vibratory cylinder construction of the present invention as shown in FIGS. 1 through 5, the piston first gas channel 42 communicating to the first cylinder end chamber 30 is a single purpose inlet gas channel, since the first cylinder end chamber 30 can communicate directly to the exhaust port 24 for exhausting gas therefrom upon particular positioning of the piston 28. Still in this first embodiment, the piston second gas channel 46 acts as a dual purpose gas channel for the second cylinder end chamber 36, admitting or communicating pressurized gas from the inlet port 22 in certain positions of the piston 28 and exhausting or communicating exhaust gas from the second cylinder end chamber 36 to the exhaust port 24 in certain positions of the piston 28. In this second embodiment of the vibratory cylinder construction of the present invention as shown in FIGS. 6 through 10, three piston gas channels are used, each serving as a single purpose gas channel.

Again referring to FIGS. 6 through 10, a piston first gas channel 72 with its annular groove 74 is a single purpose inlet gas channel for communicating between the inlet port 52 and the first cylinder end chamber 60, the first cylinder end chamber again exhausting directly to the exhaust port 54. A piston second gas channel 76 with its annular groove 78 is also a single purpose inlet channel serving to communicate between the inlet port 52 and the second cylinder end chamber 66. Finally, the piston third gas channel 80 with its annular groove 82 is a single purpose exhaust channel serving to communicate between the second cylinder end chamber 66 and the exhaust port 54.

Particularly referring to the sequential positioning illustrations of FIGS. 7 through 10, in FIG. 7, gas pressure has been built in the second cylinder end chamber 66 forcing the piston 58 in its endwise motion to the left, gas pressure having been previously exhausted from the first cylinder end chamber 60 directly into and through the exhaust port 54, although such communication at this point having been closed. In view of continued motion of the piston 58 to the left being desired, the piston third gas channel 80 has not yet reached the exhaust port 54 so that exhausting of gas from the second cylinder end chamber 66 has not yet commenced. The inlet port 52, however, is just beginning to open to and communicate with the piston first gas channel 72 so that pressurized gas is just beginning to be admitted to the first cylinder end chamber 60.

The piston 58 continues to the left from the position of FIG. 7 to the position of FIG. 8 wherein the piston motion is beginning to reverse toward the right by pressurized gas from the inlet port 52 through the piston first gas channel 72 into the first cylinder end chamber 60, while the exhaust port 54 remains closed thereto. The second cylinder end chamber 66 is being exhausted through the piston third gas channel 80 into the exhaust port 54, while the piston second gas channel 76 remains closed to the inlet port 52.

In FIG. 9, the piston 58 is moving to the right as a result of the gas pressure within the first cylinder end chamber 60 even though the inlet port 52 has been closed from communication therewith. The second cylinder end chamber 66 has been exhausted and both of the piston second and

third gas channels

76 and 80 remain closed thereto.

Finally in the position of the piston 58 in FIG. 10, the piston has reached the extent of its motion to the right for the particular inlet gas pressure being used and has just reversed so as to move toward the left and toward the position of FIG. 7. In this FIG. 10 position, the inlet gas is being admitted to the second cylinder end chamber 66 from the inlet port 52 through the piston second gas channel 76, while the gas is being exhausted I from the first cylinder end chamber 60 directly into and through the exhaust port 54. The piston third gas channel 80 is displaced from and therefore sealed off from the exhaust port 54. Such piston motion will continue to the left into the position of FIG. 7 completing one cycle of reciprocation and starting the next.

As shown in FIG. 6, this second embodiment vibratory cylinder construction similarly includes the sophistication of positioning of the piston second gas channel 76 relative to the inlet port 52 such that, when the piston 58 is stopped at its exact endwise midpoint location, motion of the piston will always be started upon reapplication of pressurized gas to the inlet port. As shown, in the endwise midpoint positioning of the piston 58 within the cylinder 50, the piston second gas channel 76 constituting the inlet gas channel to the second cylinder end chamber 66 is open to the inlet port 52. Pressurized gas applied to the inlet port 52 will, therefore, always enter the second cylinder end chamber 66 beginning motion of the piston 58 toward the left to start operation of the vibratory cylinder con struction.

According to the principles of the present invention, therefore, an improved gas pressure driven vibratory cylinder construction is provided wherein only a single exhaust port is required for exhausting gas from the opposite cylinder end chambers during operation thereof so as to not only simplify the original manufacture of the particular cylinder construction, but to also greatly simplify the normal exterior controls connected to the cylinder exhaust port such as exterior valving for cylinder amplitude control and variation, and exterior muffling for reducing the noise created by the vibratory cylinder operation. In the first embodiment construction shown in FIGS. 1 through 5, the single exhaust port 24 can communicate directly with the first cylinder end chamber 30 in certain positions of the piston 28, while at the same time, this single exhaust port 24 can also communicate through the piston second gas channel 46 with the second cylinder end chamber 36 in certain positions of the piston 28. In the embodiment shown in FIGS. 6 through 10, the exhaust port 54 can again communicate directly with the first cylinder end chamber 60 in certain positions of the piston 58, and can also communicate through the piston third gas channel 80 with the second cylinder end chamber 66 in certain positions of the piston 58. Thus in both embodiments of the present invention, the

vibratory cylinder

20 or 50 is perfectly operable with a

single exhaust port

24 or 54.

Further according to certain of the principles of the present invention, the vibratory cylinder construction may be formed with a unique gas inlet port and piston gas channel relationship such that when the operation of the cylinder is ceased and the piston thereof stops endwise midway of the cylinder, the gas inlet port is always partially open to one of the cylinder end chambers so that the cylinder will once again resume normal operation when restarted, despite the piston midpoint positioning. In the embodiment shown in FIGS. 1 through 5, the gas inlet port 22 is always open through the piston first gas channel 42 to the first cylinder end chamber 30 when the piston 28 is exactly midway endwise of the cylinder 20, assuring that the piston will immediately begin movement to the right when pressurized gas is applied to the inlet port. In the embodiment shown in FIGS. 6 through 10, the inlet port 52 is always in communication with the second cylinder end chamber 66 through the piston second gas channel 76 when the piston 58 is at its exact midpoint position assuring that the piston 58 will always begin movement to the left when pressurized gas is applied to the inlet port 52.

Still further according to even additional sophistication according to certain of the principles of the present invention, the vibratory cylinder construction of the present invention may be provided with at least one of the cylinder gas inlet and exhaust ports always in gas flow communication with one of the cylinder end chambers despite the particular endwise positioning of the piston within the cylinder, that is, endwise midway or in any other relative positioning. As hereinbefore described, in the first embodiment construction of FIGS. 1 through 5, one of the inlet and exhaust ports 22 and'24 is always in communication for gas flow from one of the first and second

cylinder end chambers

60 and 66, thereby assuring that the vibratory cylinder will always properly commence operation upon inlet gas being admitted to the inlet port 22 and the piston 28 can never assume a position in which such immediate operational starting will not take place.

I claim:

1. In a gas pressure driven vibratory cylinder of the type having a free reciptocatory piston with said piston having opposite piston ends defining opposite cylinder end chambers against opposite cylinder end walls wherein, through piston endwise movements in said cylinder, pressurized gas is introduced from a cylinder side wall alternately into said opposite cylinder end chambers and is exhausted from each of said chambers during at least a portion of the period that it is free of being so introduced into that chamber to oppositely drive said piston continuously reciprocally in said cylinder; the improvements comprising in combination therewith: a gas exhaust port opening into said cylinder from said cylinder sidewall spaced from one of said cylinder end walls, said exhaust port being located at least partially directly open into a first of said cylinder end chambers at said one cylinder end wall during movement of said piston directly approaching and leaving a maximum distance from said one cylinder end wall, said exhaust port being obstructed by said piston from communication into said first cylinder end chamber during a remainder of said piston movement; a gas inlet port opening into said cylinder from said cylinder side wall spaced a greater distance from said one cylinder end wall than said exhaust port and spaced along said cylinder side wall from said exhaust port; gas channel means formed in said piston, said gas channel means communicating between said inlet port and said first cylinder end chamber during at least a part of said piston obstruction from communication of said exhaust port into said first cylinder end chamber, said gas channel means communicating between said exhaust port and a second of said cylinder end chambers during at least a part of said piston obstruction from communication of said exhaust port into said first cylinder end chamber, said gas channel means communicating between said inlet port and said second cylinder end chamber during at least a part of said exhaust port direct opening into said first cylinder end chamber.

2. A vibratory cylinder as defined in claim 1 in which said gas channel means includes at least one separate gas channel communicating from said cylinder side wall through said piston into each of said cylinder end chambers.

3. A vibratory cylinder as defined in claim 1 in which said gas channel means includes a single gas channel communicating from said cylinder side wall through said piston into said first cylinder end chamber constituting solely a gas inlet channel, a single gas channel communicating from said cylinder side wall through said piston into said second cylinder end chamber constituting a dual gas inlet and exhaust channel directing inlet gas from said inlet port into said second cylinder end chamber during a portion of piston movement and directing exhaust gas from said second cylinder end chamber into said exhaust port during a portion of piston movement.

4. A vibratory cylinder as defined in claim 1 in which said gas channel means is located relative to said inlet port always communicating between said inlet port and one of said cylinder end chambers when said piston is endwise positioned exactly midway of said cylinder.

5. A vibratory cylinder as defined in claim 1 in which said gas channel means, said inlet port and said exhaust port are located relative to each other with their always being at least one of said inlet and exhaust ports in open communication with one of said cylinder end chambers regardless of endwise positioning of said piston in said cylinder.

6. A vibratory cylinder as defined in claim 1 in which said gas channel means is located relative to said inlet port always communicating between said inlet port and one of said cylinder end chambers when said piston is endwise positioned exactly midway of said cylinder; and in which said gas channel means, said inlet port and said exhaust port are located relative to each other with their always being at leastone of said inlet and exhaust ports in open communication with one of said cylinder end chambers regardless of endwise positioning of said piston in said cylinder.

7. A vibratory cylinder as defined in claim 1 in which said gas channel means includes a first gas channel communicating from said cylinder side wall through said piston into said first cylinder end chamber constituting solely a gas inlet channel, a second gas channel communicating from said cylinder side wall through said piston into said second cylinder end chamber constituting a dual gas'inlet and gas exhaust channel directing inlet gas from said inlet port into said second cylinder end chamber during a part of piston movement and directing exhaust gas from said second cylinder end chamber into said exhaust port during a part of piston movement, said first gas channel being located relative to said inlet port always communicating between said inlet port and said first cylinder end chamber when said piston is endwise positioned exactly midway of said cylinder.

8. A vibratory cylinder as defined in claim 1 in which said gas, channel means includes a first gas channel communicating from said cylinder side wall through said piston into said first cylinder end chamber constituting solely a gas inlet channel directing inlet gas from said inlet port into said first cylinder end chamber during a part of piston movement, a second gas channel communicating from said cylinder side wall through said piston into said second cylinder end chamber constituting a dual inlet gas and exhaust gas channel directing inlet gas from said inlet port into said second cylinder end chamber during a part of piston move ment and directing exhaust gas from said second cylinder end chamber into said exhaust port during a part of piston movement, said first and second gas channels, said inlet port and said exhaust port being located relative to each other with their always being at least one of said inlet and exhaust ports in open communication with one of said cylinder end chambers regardless of endwise positioning of said piston in said cylinder.

9. In a gas pressure driven vibratory cylinder of the type'having a free reciptrocatory piston with said piston having opposite piston ends defining opposite cylinder end chambers against opposite cylinder end walls, wherein, through piston endwise movement in said cylinder, pressurized gas is introduced from a cylinder side wall alternately into said opposite cylinder end chambers and is exhausted from each of said chambers during at least a portion of the period that it is free of being so introduced into the chamber to oppositely drive said piston continuously reciprocally in said cylinder; the improvements comprising in combination therewith: a gas exhaust port opening into said cylinder from said cylinder side wall at a location at least partially directly open into a first of said cylinder end chambers during movement of said piston directly approaching and leaving a maximum endwise movement into a second of said cylinder end chambers, said piston overlapping said exhaust port obstructing communication between said exhaust port and said first cylinder end chamber during a remainder of said piston movement; a gas inlet port opening into said cylinder from said cylinder side wall at a location spaced at all times during said piston movement from said first cylinder 6 end chamber; a first gas channel formed in said piston communicating between said cylinder side wall and said first cylinder end chamber, said first gas channel being located communicating into said inlet port during at least a part of said piston exhaust port obstruction and being free of communication into said inlet port during at least a part of said exhaust port direct opening into said first cylinder end chamber; a second gas channel formed in said piston communicating between said cylinder side wall and said second cylinder end chamber, said second gas channel being located communicating into said exhaust port during at least a part of said piston exhaust port obstruction and communicating into said inlet port during at least a part of said exhaust port direct opening into said first cylinder end chamber.

10. A vibratory cylinder is defined in claim 9 in which said inlet port is located relative to said first and second gas channels always communicating from said inlet port through one of said gas channels into one of said cylinder end chambers when said piston is endwise positioned exactly midway of said cylinder.

11. A vibratory cylinder as defined in claim 9 in which said inlet port and said first gas channel are located relative to each other always in communication therebetween into said first cylinder end chamber when said piston is endwise positioned exactly midway of said cylinder.

12. A vibratory cylinder as defined in claim 9 in which said first and second gas channels, said inlet port and said exhaust port are located relative to each other with their always being at least one of said inlet and exhaust ports in open communication with one of said cylinder end chambers regardless of endwise positioning of said piston in said cylinder.

13. A vibratory cylinder as defined in claim 9 in which said inlet port and said first and second gas channels are located relative to each other always communicating between said inlet port and one of said cylinder end chambers when said piston is endwise positioned exactly midway of said cylinder; and in which said first and second gas channels, said inlet port and said exhaust port are located relative to each other with their always being at least one of said inlet and exhaust ports in open communication with one of said cylinder end chambers regardless of endwise positioning of said piston in said cylinder.

Claims

6. A vibratory cylinder as defined in claim 1 in which said gas channel means is located relative to said inlet port always communicating between said inlet port and one of said cylinder end chambers when said piston is endwise positioned exactly midway of said cylinder; and in which said gas channel means, said inlet port and said exhaust port are located relative to each other with their always being at least one of said inlet and exhaust ports in open communication with one of said cylinder end chambers regardless of endwise positioning of said piston in said cylinder.

7. A vibratory cylinder as defined in claim 1 in which said gas channel means includes a first gas channel communicating from said cylinder side wall through said piston into said first cylinder end chamber constituting solely a gas inlet channel, a second gas channel communicating from said cylinder side wall through said piston into said second cylinder end chamber constituting a dual gas inlet and gas exhaust channel directing inlet gas from said inlet port into said second cylinder end chamber during a part of piston movement and directing exhaust gas from said second cylinder end chamber into said exhaust port during a part of piston movement, said first gas channel being located relative to said inlet port always communicating between said inlet port and said first cylinder end chamber when said piston is endwise positioned exactly midway of said cylinder.

8. A vibratory cylinder as defined in claim 1 in which said gas channel means includes a first gas channel communicating from said cylinder side wall through said piston into said first cylinder end chamber constituting solely a gas inlet channel directing inlet gas from said inlet port into said first cylinder end chamber during a part of piston movement, a second gas channel communicating from said cylinder side wall through said piston into said second cylinder end Chamber constituting a dual inlet gas and exhaust gas channel directing inlet gas from said inlet port into said second cylinder end chamber during a part of piston movement and directing exhaust gas from said second cylinder end chamber into said exhaust port during a part of piston movement, said first and second gas channels, said inlet port and said exhaust port being located relative to each other with their always being at least one of said inlet and exhaust ports in open communication with one of said cylinder end chambers regardless of endwise positioning of said piston in said cylinder.

9. In a gas pressure driven vibratory cylinder of the type having a free reciptrocatory piston with said piston having opposite piston ends defining opposite cylinder end chambers against opposite cylinder end walls, wherein, through piston endwise movement in said cylinder, pressurized gas is introduced from a cylinder side wall alternately into said opposite cylinder end chambers and is exhausted from each of said chambers during at least a portion of the period that it is free of being so introduced into the chamber to oppositely drive said piston continuously reciprocally in said cylinder; the improvements comprising in combination therewith: a gas exhaust port opening into said cylinder from said cylinder side wall at a location at least partially directly open into a first of said cylinder end chambers during movement of said piston directly approaching and leaving a maximum endwise movement into a second of said cylinder end chambers, said piston overlapping said exhaust port obstructing communication between said exhaust port and said first cylinder end chamber during a remainder of said piston movement; a gas inlet port opening into said cylinder from said cylinder side wall at a location spaced at all times during said piston movement from said first cylinder end chamber; a first gas channel formed in said piston communicating between said cylinder side wall and said first cylinder end chamber, said first gas channel being located communicating into said inlet port during at least a part of said piston exhaust port obstruction and being free of communication into said inlet port during at least a part of said exhaust port direct opening into said first cylinder end chamber; a second gas channel formed in said piston communicating between said cylinder side wall and said second cylinder end chamber, said second gas channel being located communicating into said exhaust port during at least a part of said piston exhaust port obstruction and communicating into said inlet port during at least a part of said exhaust port direct opening into said first cylinder end chamber.