US3400913A - Vibrator - Google Patents

Description

Sept. 10, 1968 c. c. MATSON VI BHATOR 2 Sheets-Sheet 1 Filed Oct. 21, 1966 FIG. 2

FIG. 4

FIG. I

FIG. 3

l V1.5 \"l OR. CARL G. MATSON Sept. 10, 1968 c. e MATSON VIBRATOR 2 Sheets-Sheet 2 Filed Oct. 21, 1966 FIG..?

United States Patent 3,400,913 VIBRATOlR Carl G. Matson, 401 E. Central Blvd, Kewanee, Ill. 61443 Filed Oct. 21, 1966, Ser. No. 588,387 10 Claims. (Cl. 259-1) ABSTRACT OF THE DISCLOSURE A vibrator comprising a casing-enclosed member having alternately pressurized and depressurized pistons reacting on the casing wall to give the member a gyrating and oscillating motion and wherein the radial cooperative walls of the member and easing are in confronting relationship and have ports serving a valve means.

This invention relates to a vibrator useful in the fields of material handling; for example, in the loading, unloading and conveyor-transporting of fluent material, in the shaking of hoppers, in the agitation of materials such as concrete and the like, all of which uses and allied uses are known to those versed in the art.

,A principal object of the invention is to provide a novel vibrator featuring simplicity, direct fluid pressure drive, a novel porting system, high efiiciency, balanced pressure, extremely favorable rolling contact area and readily adaptable to varying conditions. Another principal object is to provide a casing-enclosed member having fluid-pressurizable and -exhausti'ble piston means reacting on the casing wall and ported by valve means that gives the member a continuous motion that partakes of oscillation and gyration as it rapidly changes its eccentric relation to the casing. A still further feature is to provide the member and easing with slidably engageable confronting surfaces in which pressure and exhaust ports are provided and which ports are interchanged to pressurize and exhaust the driving pistons, thus avoiding complicated separate valving components.

The novel design features a casing-enclosed member in which the several cylinders and their respective alternately pressurized and exhausted ports are :angularly olfset so that each port and its piston are out of direct radial alinement, thereby compelling a component of force that tends to move the member within the casing in other than a simple diametrical path. Still further objects and features reside in utilizing in one form of the invention, a plurality of axially spaced apart rows of cylinders and pistons and pressurizing and exhausting these rows in sets, thereby avoiding extremely long passages that are inherently difiicult to bore, especially in small units; in the provision of a unit that has a pressure inlet at one end and an exhaust at the other so as to avoid reversals in the path of fluid travel; and in utilizing the source of fluid pressure to augment the seal between the confronting valve surface portions.

The foregoing and other important objects and significant features, inherent in and encompassed by the invention, will become apparent as preferred embodiments are disclosed, by way of examples, in the ensuing description and accompanying drawings, wherein FIGURE 1 is a diametrical sectional view of one form of vibrator;

FIGURE 2 is a section on the line 2-2 of FIGURE 1 but having omitted portions superimposed in broken lines;

FIGURE 3 is a section on the line 3-3 of FIGURE 1;

FIGURE 4 is a section on the line 4-4 of FIGURE 1, with the internal member in a position different from its position in FIGURE 2 and again with other illustrative matter superimposed;

FIGURE 5 is a longitudinal section of an elongated 3,400,913 Patented Sept. 10, 1968 ice vibrator of the so-called immersion type, with intermediate portions broken away, illustrating the use of plural rows of cylinder-piston means;

FIGURE 6 is a section on the line 6-6 of FIGURE 5;

FIGURE 7 is a longitudinal section of a vibrator in which the inlet and exhaust passages are respectively at opposite ends of the unit;

FIGURE 8 is an enlarged fragmentary section illustrating an alternate type of piston means.

FIGURES 1-4 AND 8 The vibrator includes a casing 10 having annular wall means 12 and radial Wall means including axially spaced part radial walls 14 and 16 that define a chamber 18-here cylindricaL-in which a movable member 20 is loosely enclosed. The annular wall means 12 may have a hardened steel liner 22 that affords a cylindrical track 24. This liner is not essential to the basic invention but it does add to the life of the unit and enables the casing to be made up of low- cost castings 26 and 28 that may be secured together by a snap ring 30. The annular wall means will be herein-after referred to simply as such and as including the track 24, irrespective of whether the track is formed on the liner 22 or directly on the wall means 12. The center of the track is designated at A.

This track (or annular wall means) has an inside diameter greater than the comparable dimension of the member 20 which, although shown here as circular, need not be of that particular shape. However, the circular shape makes the member easy to manufacture and balance and it, like the castings 26 and 28, may be of any suitable low-cost material having bores 32-here radial-fitted with hardened cylindrical tubular inserts 34 that respectively provide cylinders 36, each of which carries a piston 38, in this case in the form of a ball; although, this is not a limiting characteristic, for, as shown in FIGURE 8, each piston may be of cylindrical form as seen at 39, having a crowned track-engaging portion 41.

In the case of FIGURES 1-4, the member 20 is shown as having four cylinders 36 and pistons 38 uniformly angularly spaced about the member center B. A member with but two cylinder-piston units would be operative but would be difiicult to start. Three such units would overcome the starting problem. Four pistons smooth out the operational characteristics and insure self starting but do not establish either a bottom or a top limit on the number of pistons that could be employed.

The cylinders 36 are here shown as being formed respectively on radii of the member 20, but here again this is a preferred construction. These cylinders open to the track 24 and the pistons engage this track.

It will be observed that, because of the dimensional relationship between the member 20 and the track 24, the member center B is eccentric to the casing center A, but this is an ever-changing condition because the eccentricity of the member continually varies as to location and amount, as will be brought out below. It will also be observed that the member 20 has no mechanical connection or journal with the casing, nor does it have any torque-transmitting input or output as in the case of a radial-piston or motor pump. The member 20 is confined axially between the radial wall means 14-16 but is free to shift in unlimited directions transverse to the axis of the track 24, the amount or magnitude of which is restricted only by the excess of the diametrical dimension of the track over that of the member. In a preferred construction, and regarding the member 20 as being circular-by way of example only-the member diameter will be on the order of of that of the track 24.

One radial side of the member 26 and the confronting radial face of the proximate radial wall means 14 ar provided respectively with confronting, slidably engaged radial valve surface portions or land areas 40 and 42, the latter of which has formed therein a circular center port 44 on the casing axis A and a concentric annular or circular larger port or groove 46. Both of these ports face toward the proximate valve surface portion 4t) of the member 29, and the port 44 is connectible by a casing passage 48 to any suitable source of fluid under pressure, such as compressed air, oil etc. The annular port 46 is led by a casing passage 50 to exhaust. In the embodiment under discussion both ports 44 and 46 and passages 48 and 50 are at the same side of the casing.

The opposite radial side of the member 2t) is engaged by a seal ring 52, preloaded by a spring 54; and a passage 56 centrally through the member 29 communicates the center pressure port 44 with a recess 58 in the radial wall 16 in which the ring 52. and spring 54 are carried, so that fluid pressure behind the ring augments the spring 54- in sealing complementary surfaces against pressure leaks.

The ports 44 and 46, together with member ports about to be described, provide valve means for porting fluid pressure to and from the cylinders to pressurize and exhaust the cylinders 36 to cause the pistons 38 to react against the track 24 for imparting vibratory motion to the member 20. The member ports are of course equal in number (here four) to the pistons 38 and are designated by the numeral 60, and these open at the member valve surface portion 40 and are equally angularly spaced (here at 90) about the member center B, lying on a circle about that center. Each port 60 is essentially the outer end of a bore that extends inwardly to communicate via a cross passage 62 with a cylinder 36 radially inwardly of the respective piston 38. The manner of drilling the member 20 to provide the port-to-passage-to-cylinder connections will be apparent from the drawings.

It will also be apparent that the four ports 6t) are so related to the center and annular ports 46 and 48 that the following relationship obtains: regardless of the position of eccentricity of the member 2% in the chamber 18, at least one member port 60 will communicate with the center port 44 (inlet) and at least one other member port will communicate with the annular port 46 (exhaust). Thus, at least one piston 33 will be pressurized while another will be exhausted. (At this point it should be observed that the pressure and exhaust passages 48 and 59 could be interchanged and the same operational results would follow.)

One other characteristic should be noted before proceeding with the description of the operation of the unit: Each member port 60 is out of direct radial alinement with its cylinder 36 and is angularly offsethere by 90- from its cylinder 36, each passage 62 being drilled at an angle to a radius of the member 20. The 90 lead can of course be varied within rather wide limits and is provided so that the force components shifting the member 20 give it a rolling movement as well as a shifting movement, causing the member to oscillate or gyrate.

For example, and looking now at FIGURE 2, it will be seen that the lowermost port at (at six oclock) is in partial register with the pressure port 44 (the diameter of which is such that its circular outline passes substantially through the centerline of that port 60 but does not at this time intersect the other ports 60); and this port 60 communicates not with the lowermost cylinder 36 but to the cylinder 36 at three oclock. In other words, this port 60 leads its cylinder by an angular amount, here 90. Similarly, each of the other ports 60 leads its cylinder 36 by 90. Hence, fluid pressure at this stage is transmitted to the piston 38 at three oclock and pressure is exhausted from the cylinder 36 at nine oclock because its port 60 is at twelve oclock and in partial register with the annular exhaust port 46.

Now, with the three oclock piston 38 extended, the member 20 will move not ony to the left but will tend to roll clock-wise. The tendency of the member to roll will of course be affected by the fluid pressure medium em ployed, because oil, for example, has a lower co-efiicient of friction than air, for example, between the pistons 38 and the track 24. The amount of roll could of course also be affected by the mass of the member 26 and the position of the axes of the casing and member relative to the horizontal. But in a theoretically perfect situation in which the above factors are ignored, the motion of the member 20 will include several gyrations or oscillations per each complete revolution thereof. By way of example, in the particular example employed here, the member will turn only one-tenth of a revolution each time it changes position. As the member moves, each port 60 travels through what may be described as a crescent C as respects the pressure port 44 and a diametrically opposite crescent D as respects the exhaust port 46 (FIGURE 4). Hence, as one pressurized port 60 is leaving its pressure crescent C, the next port 60 is moving into the pressure crescent. Compare, in FIGURE 4, the uppermost port 60 (in but moving out of the crescent C) with the port 60 90 counterclockwise therefrom (ready to move into the crescent C). The same is true of the exhaust relationship. Compare the lowermost port 60 in FIGURE 4 (in but leaving the exhaust crescent D) and the next trailing or counterclockwise port 60 (about to enter the exhaust crescent). Thus the pistons are sequentially pressurized and exhauted to continue the oscillating or gyrating movement of the member 20 and the forces developed thereby are transmitted to the casing as vibrational forces useful for the purposes earlier described. The valve porting and other factors are preferably such that the member 20 does not actually strike the track 24.

FIGURES 5 AND 6 The vibrator here represents an immersion type; i.e., one that is immersed in the material to be agitated, as in the case of concrete. An elongated casing 10a confines an elongated member a by annular wall means 12a and opposite radial walls 14a and 16a that define a chamber 18a. Because of the length of the unit, several sets or rows of pistons may be employed. By way of example, FIG- URE 5 shows two sets respectively adjacent to the opposite ends or radial faces of the member 20a, each set comprising pistons 38a in cylinders 36a that lead via passages 62a to adjacent ports 60a that open at a radial valve surface portion 40a in confronting relation to a complementary radial portion 42a on the radial casing wall 1611. This radial wall has a center port 44a and an annular concentric port 46a that bear the same relationship to the member ports 60a as that between the similar ports 44-46-60 previously described. There is this difference, however: In FIGURE 5, the port 46a is open to the chamber 18a, as is a duplicate annular port 4611 at the opposite end of the unit so that the two ports 46a are interconnected via the chamber, but the land area between each port 44a and its companion prevents loss of pressure. There is also a duplicate center port 44a at the remote end of the unit and the two ports 44a are interconnected by an axial passage 56a through the member 20a. The casing has inlet and exhaust passages 48a and 50a (which could of course be reversed) and these are connected by two coaxial hose lines 47 and 49 to typical pressure and exhaust media remote from the vibrator.

The left end of the unit as seen in FIGURE 5 has a recess 58a which contains a ring 52a and a spring 54a like and for the same purpose as those described before, but in this case the open center of the ring provides the adjacent center port 44a and the radial face of the ring and the confronting radial face portion of the member 20a com bine to provide complementary lands or valve surface portions 40a and 42a that functionally duplicate those at the right end of the unit and which function in the control of the duplicate set of adjacent member ports 60a. The basic reason for the duplication of the porting system at both ends of the unit is to avoid the need for drilling several passages lengthwise through the member 20a, and hence the sets of pistons 38a at the ends of the member 20a have their own respective and identical porting systems. It is necesary only to have the central through passage 56a, and the bores that open as the ports 60a and that intersect the cylinder passage 62a may terminate as shown at 51. Thus, both ports 44a are pressurized at the same time and both ports 46a are likewise simultaneously connected to exhaust. The porting arrangement at each end is exactly like that described for FIGURES 1-4 and 8. The through pressure passage 56a causes the ring 52a to function exactly like the ring 52.

FIGURE 7 This form of vibrator has a casing 10b including annular wall means 12b and opposite radial end walls 14b and 16b that define a chamber 18b within which a movable member 20b is enclosed. Like the member 20 previously described, the member 20b has piston and cylinder means and a porting system. The cylinders--here again four in number by way of illustrationare shown at 36b and each contains a piston 38b and leads via a passage 62b to a through passage 53, there being four such passages in the member 20b, each opening at its opposite ends as member ports 60b. The basic distinction in this unit over that of FIGURES 1-4 is that here the center port 44b is provided at one end of the casing and the annular port 46b is at the opposite end. Again using the previous example of inlet and exhaust, the port 44b is connected to a casing inlet passage 48b and the port 46b is connected to a casing exhaust passage 50b. In other words, the exhaust port 46 of FIGURES 1-4 is moved to the end of the unit opposite that of the port 44. And this is why the passages 53 are necessary to duplicate the ports 60b at both radial ends or faces of the member 20b. Cooperative valve surface portions or lands between the member and casing faces will be readily apparent at 40b, 42b. Thus as fluid under pressure is supplied at port 44b and thence along a passage 53 (uppermost in FIGURE 7, for example) to a cylinder passage 62b, it must pressurize the associated piston 38b because this pressure cannot escape at the left end of the passage 53 in question, since it is blocked by the end wall land or valve surface portion 42b. However, the lowermost passage 53 in FIGURE 7, although closed at its right end to inlet pressure, is open at its left end to the exhaust port 46b. This straight-through flow system has the advantage of eliminating the need for the fluid to travel in circuitous paths, and particularly avoids fluid reversal. Other than that, the FIGURE 7 unit has the same characteristics as those described for the other units.

Summary In the interests of clarity, various expressions of geometric nature have been employed; viz., annular, radial, diameter etc., but it should be understood that these terms are not intended to be limited to their connotation with respects to circles, cylinder-s, etc., because the invention is deemed to have wide scope and application and other than purely circular shapes may be developed in the exploitation of the invention. Likewise, the invention is not intended to be restricted to the exemplary embodiments disclosed nor as having only the features and objects enumerated, for a large area of variation in structure and mode of operation and attainment of objects and features will occur to those versed in the art, all without departure from the spirit and scope of the invention.

What is claimed is:

1. A vibrator comprising a casing and a movable member enclosed thereby for vibratory movement therein, said casing having annular Wall means and radial wall means defining a chamber of greater diameter than the comparable dimension of the member so that the member is movable among several positions eccentric to the casing axis,

said radial wall means and said member having complementary slidably engaged radial valve surface portions, said member having a plurality of cylinders spaced apart angularly about its central axis and opening to the annular wall means, pistons in the cylinders and engaging the annular wall and passages leading respectively from the cylinders substantially radially inwardly of the pistons and terminating respectively in a plurality of ports spaced apart angularly on a circle about the central axis of the member and opening at said valve surface portions, said radial wall means having a central port and a coaxial larger annular port opening at said valve surface portions, said radial wall means ports having such respective diameters that in any eccentric position of the member at least one member port communicates with the central port and at least another member port simultaneously communicates with the annular port, and said casing having fluid pressure inlet and exhaust passages connected respectively to the radial Wall means ports for pressurizing and exhausting the cylinders to cause the pistons to react on the annular wall means for shifting the member within the casing.

2. The invention defined in claim 1, in which the valve surface portions are located at one radial side of the member and the member has through passage means separate from the cylinder passages and extending to the opposite radial side of the member and always in communication with the inlet passage for pressurizing said opposite radial side so as to augment the sealing relation of the valve surface portions to each other.

3. The invention defined in claim 1, in which the member has at least three cylinders, pistons, passages and ports and the ports are angularly offset respectively from direct radial alinement with their cylinders.

4. The invention defined in claim 1, in which the member ports extend through the member from one radial side thereof to the other so as to provide duplicate member ports at said other side, the radial Wall means and said other member side have cooperative valve surface portions, and the central port is located in the radial wall means at one radial side of the member for cooperation with the first-mentioned member ports and the annular port is located in the radial wall means at said other radial side of the member for cooperation with said duplicate member ports.

5. The invention defined in claim 1, in which the aforesaid member ports, passages, valve surface portions and radial wall means ports are located at one radial side of the member, duplicate member ports, valve surface portions and radial Wall means ports are provided at the opposite radial side of the member, said member has a duplicate set of cylinders and pistons proximate to the opposite radial side and said duplicate cylinders are connected respectively to said duplicate member ports by member passages separate from those aforesaid, and said duplicate radial wall means ports are connected respectively to the casing passages.

6. The invention defined in claim 5, in which the con nection of the duplicate central port to one casing passage is effected by a through passage in the member in communication with the first-mentioned central port.

7. The invention defined in claim 5, in which the connection of the duplicate annular port to one casing passage is effected by inter-communicating the two annular ports via the space between the member and the annular wall means.

8. The invention defined in claim 5, in which the connection of the duplicate central port to one casing passage is effected by a through passage in the member in communication with the first-mentioned center port and the connection of the duplicate annular port to the other casing passage is effected by inter-communicating the two annular ports via the space between the member and the annular wall means.

9. The invention defined in claim 1, in which the valve surface portions, member ports and radial wall means ports are located at one side of the casing, and the casing passages open outwardly at said casing side.

10. A vibrator comprising a casing and a movable member enclosed thereby for vibratory movement therein, said casing having annular wall means and radial wall means defining a chamber of greater diameter than the comparable dimension of the member so that the member is movable among several positions eccentric to the casing axis, said member having a plurality of cylinders spaced apart angularly about its center and opening to the annular wall means, pistons in the cylinders and engaging the annular wall, said casing having pressure fluid inlet and outlet passages, said member having a plurality of passages connected respectively to the cylinders, and valve means comprising cooperative portions of at least one radial side of the member and a confronting portion of the radial wall means for sequentially porting pressure fluid to and from each of the member passages to cause the pistons to sequentially react on the annular wall means to impart substantially continuous motion to the member.

References Cited UNITED STATES PATENTS WALTER A. SCHEEL, Primary Examiner.

I. M. BELL, Assistant Examiner.

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