US3870282A

US3870282A - Noiseless air-actuated turbine-type vibrator

Info

Publication number: US3870282A
Application number: US355681A
Authority: US
Inventors: Theodore S Wadensten
Original assignee: Individual
Current assignee: Individual
Priority date: 1973-04-30
Filing date: 1973-04-30
Publication date: 1975-03-11
Anticipated expiration: 1992-03-11
Also published as: CA1000137A; DE2416398A1; GB1449208A; DE2416398C2

Abstract

This invention pertains to an air-actuated vibrator of the turbine-type in which the rotor and enclosing chamber is so contoured as to provide within the normal operating range a noise level which is below 85 db (Hertz). Preferably this noise level is about 72 db or less which is much below the tolerant level established as acceptable. The rotor is the only moving part in this vibrator and has its periphery formed with small transverse serrations such as gear-tooth, saw-tooth or similar profiles. The tooth profile is of such small size that the driven rotor which is peripherally driven by pressurized air within a normal supply range produces noise levels which are sufficiently low so that the operation of the vibrator is considered to be virtually silent.

Description

[ Mar. 11, 1975 ABSTRACT NOISELESS AIR-ACTUATED TURBINE-TYPE VIBRATOR [76] Inventor:

g ir g 'X 3 i l 8 This invention pertains to an air-actuated vibrator of en 898 the turbine-type in which the rotor and enclosin chamber is so contoured as to g provide within the normal operating range a noise level which is below 85 db (Hertz). Preferably this noise level is about 72 db or less which is much below the tolerant level established as acceptable. The rotor is the only moving part in this vibrator and has its periphery formed with small transverse serrations such as gear-tooth, saw-tooth or similar profiles. The tooth profile is of such small size that the driven rotor which is peripherally driven by pressurized air within a normal supply range produces noise levels which are sufficiently low so that the operation of the vibrator is considered to be virtually Sllent.

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sum 3 r 4 MODEL I00 I I60 I90 250 PSI dB. RPM dB. RPM dB RPM CIB RPM dB RPM 30 55 6000 58 I500 6|.5 I800 63 I500 H0 70 H800 63.5 9900 64 6000 72.5 6I00 72 6000 PATENTED 1 I975 3,870,282 sum a ar 4 TOOTH SHAPE 4OF.S.I. 5ORSJ. SOPSJ. 70RSJ. 80P5J. 9095.1. ON WHEEL I dB RPM dB RPM dB RPM dB RPM dB RPM dB RPM 48PITCH 78TEETH 56.5 3600 5Z5 4800 525 6000 58 6800 60 6900 63 7200 KNURLED 73 55 3800 55.5 4400 525 5400 58-5 6200 59.5 6600 63 7000 SAWTOOTH 32P'TCH 50TEETH55 6000 56 8500 5a 8700 58.5 8900 so 9000 as 10500 32PITCH SOTEETH 55 6800 55.5 7200 56.5 7200 57 7800 58.5 7800 59 B000 dB SAWTOOTH 32F RPM X I000 NOISELESS AIR-ACTUATED TURBINE-TYPE VIBRATOR BACKGROUND OF THE INVENTION 1. Field of the Invention In accordance with the classification of art as established by the U.S. Patent Office this invention is found in the general class entitled, Agitating (class 259) and the subclass therein entitled, miscellaneous (subclass l) which has been further identified in this subclass as 1 R and Digest 43." The method of making a vibration apparatus as in the embodiment shown is found in the general class entitled, Metal Working (Class 29) and the subclass therein of impellers" (subclass 156.8).

2. Description of the Prior Art Air turbines are not new and making the rotor with an eccentric weight is also well known as seen in U.S. Pat. No. 3,074,151 to Kroeckel as issued on Jan. 22, 1963. Another patent using the same general concept includes U.S. Pat. No. 2,875,988 to Wysong as issued on Mar. 3, 1959. Other air driven vibrators also generally used include ball-type vibrators as seen in U.S. Patents to Peterson, No. 2,793,009 as issued on May 21, 1957 and No. 2,917,290 as issued on Dec. 15, 1959. In the above apparatus-as well as others known to the applicant the noise levels exceed the tolerance levels for continuous duty operation (i.e., 85 db) as established by the Federal Occupational Safety and Health Act of 1970.

The turbine-type pneumatic vibrator of this invention as reduced to practice and extensively tested and used in commercial installations has operated substantially continuously for weeks at noise levels below the established 85 db and many units of smaller size have operated at levels of 60 to 70 db. This, of course, falls well within the safety limits of the federal standard. In sharp contrast to this quiet vibrator is the ball-and-race vibrator now and for the past several years in extensive use. This ball-and-race vibrator is shown and described in U.S. Pat. No. 2,793,009 as issued on May 21, 1957 and U.S. Pat. No. 2,917,290 as issued on Dec. 15, 1959 both to Peterson. The noise level usually found in the installations of these ball-and-race vibrators is often in excess of 100 db. This noise level for periods of eight or more hours, of course, is unacceptable.

In the present invention the size of the rotor, the number and depth of teeth used therewith and the normal operating range of air pressure used to drive the vibrator are closely related factors. The air turbine vibrator of this invention uses a close limit control of these factors to successfully meet or exceed the requirements for a quiet operation of the vibration apparatus.

SUMMARY OF THE INVENTION The present invention may be summarized at least in part with reference to its objects.

It is an object of this invention to provide, and it does provide, an air-actuated turbine-type vibrator in which the eccentrically weighted rotor has its periphery formed with a regular pattern and spacing of small tooth forms. These tooth forms of a determined size and configuration commensurate with the size of the rotor.

It is a further object of this invention to provide, and it does provide, an air-actuated turbine-type vibrator in which the air inlet is of a size which is proportioned as to the diameter of the rotor. The outlet is also proportioned as to the diameter of the rotor. The ratio of the inlet to the outlet diameter of the smaller diameter vibrators is about 40 percent of the outlet diameter whereas in the large diameter rotors the ratio of the inlet to the outlet is about 50 percent.

The air-actuated turbine-type vibrator of this invention as reduced to practice ranges from a rotor diameter of 1% inches to a diameter of5 inches and the number of teeth carried by the rotor ranges from 50 to I00 teeth. The groove depth of the teeth on the various diameter rotors ranges from one thirty-second to onequarter of an inch depending upon the diameter of the wheel. The air turbine of this invention includes a standard circumferential chamber in which the inlet and the outlet are disposed on diametrically opposite sides. In the various size units the inlet and outlet diameters vary. The threaded portion of the inlet terminates at about one-eighth to five-sixteenths of an inch depending on size of the unit. The unthreaded portion creates a venturi action prior to the inlet entering the peripheral path of the turbine Wheel. The inlet of the silent turbine is of a smaller diameter than is the outlet. The turbine has an eccentric weighted rotor and the eccentric weight is selected as to the amount of vibratory force to be exerted. The teeth are formed on the periphery and are generally parallel to the axis of the rotor and in many instances are gear-like in form. The number-of teeth on the rotor is carefully calculated and in actual tests provide the lowest db noise level achievement while providing a high rpm. output. The air-actuated turbine-type vibrator is contemplated to operate at air pressure ranging from 30 to 110 p.s.i.

In addition to the above summary the following disclosure is detailed to insure adequacy and aid in understanding of the invention. This disclosure, however, is not intended to prejudice that purpose of a patent which is to cover each new inventive concept therein no matter how it may later be disguised by variations in form or additions of further improvements. For this reason there has been chosen a specific embodiment of the noiseless, air-actuated turbine-type vibrator as adapted for use with inlet air pressure of 30 to l 10 p.s.i. and showing a preferred means for the construction of the turbine chamber and the tooth profile formed on the periphery of the rotor.

This specific embodiment has been chosen for the purposes of illustration and description as shown in the accompanying drawings wherein:

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 represents an exploded isometric view showing in general the constructional relationship of the various components which provide the air turbine vibrator of this invention;

FIG. 2 represents a partly sectional and partly diagrammatic side view of the housing as used for the air turbine and showing in particular the relationship of the inlet and the outlet of a preferred housing arrangement of the air turbine;

FIG.-3 represents a chart showing the noise level changes provided by various inlet diameters of the smaller diameter vibrator. This chart shows the resulting decibel level and the r.p.m.s derived from either 60 p.s.i. or p.s.i. inlet pressures. The inlet size diameter holes shown are used with a h-inch outlet diameter hole;

FIG. 4 represents a chart in accordance with table FIG. 3 and showing the relationship of the noise level in dbs where the inlet hole diameter is varied while the outlet hole remains the same and with the same wheel operating at two different inlet pressures, one at 60 p.s.i. and the other at 90 p.s.i.;

FIG. 5 represents a chart showing in graph form the relative db levels and the increase or decrease in r.p.m.s resulting from changes in inlet diameter to a fixed outlet diameter, the information derived from chart FIG. 3;

FIG. 6 represents a tabulation or chart showing the derived r.p.m.s of the rotors of five different models. The inlet pressures increasing from 30 to 110 p.s.i. The noise and r.p.m.s are noted for each of the five models;

FIG. 7 represents a graph showing in graph form the chart information of FIG. 6;

FIG. 8 represents a chart in which a rotor of 1% inches in diameter and made with four different surface forms is compared as to r.p.m.s and the noise level where the inlet pressures vary from 40 to 90 p.s.i., and

FIG. 9 represents a graph of the chart of FIG. 8 and demonstrates that when about 90 percent of the absolute maximum r.p.m.s is reached that the least little increase in speed causes a high rise in the noise level.

In the following description and in the claims various details will be identified by specific means for convenience; these names, however, are intended to be generic in their application. Corresponding reference characters refer to like members throughout the figures showing the construction of the turbine-type vibrator and in the charts and graphs used therewith.

The drawings and charts accompanying, and forming part of, this specification discloses certain details of construction for the purpose of explanation of the invention, but it should be understood that structural details may be modified in various respects without departure from the concept and principles of the invention and that the turbine-type vibrator may be incorporated in other structural forms than shown.

DESCRIPTION OF THE PREFERRED EMBODIMENT Referring now in particular to the drawings there is shown in FIG. 1 an isometric exploded view of the preferred construction of the air turbine vibrator of this invention. This vibrator includes a housing generally designated as 10 and having a base adapted for mounting onto a flat surface. This base includes

leg portions

12 and 14 and above and between these portions is provided a chamber portion 16 which is circular in configuration and of a determined depth. This chamber has formed outwardly and on the near side an outer larger circular recess 18 adapted to receive and retain a disclike end 20, which has mounted to it an axle 22. This axle includes an unthreaded portion 23 and at its left or distal end the axle is threaded at 24 to receive and be retained by a nut 25. A back wall 26 fixedly mounted in a recess in the housing closes off the rear portion of the chamber area 16. This back wall is formed with a hole 28 providing a passage therethrough for the axle member 22.

Adapted for mounting on the axle 22 is a rotor generally designated as 30. This rotor includes a ball bearing 32 which provides the antifriction bearing portion around which the rotor is driven. Around this ball bearing 32 is a rotor portion 34 which has formed on the outer periphery thereof teeth 36 whose size and spacing is essential in the quiet operation of the turbine. Between the bearing 32 and the outer tooth portion 36 there is mounted in the rotor portion 34 heavier elements in the form of dowels or rods and generally identified as 38. These heavier elements may be of steel, sintered heavy metal, lead or the like. These rods are mounted as by a press fit or by threaded retention into previously prepared holes in the rotor which is generally a die casting or aluminum. It is to be noted that the rotor need not be limited to metal as plastic may also be used. Since the air being fed into the turbine often carries impurities with it in the form of rust, scale or dust the use of a plastic for the rotor may or may not be feasible depending upon the environment in which it is used. However, it is to be contemplated that the scope of this invention includes the use of plastics and the like for both the rotor and the housing.

Referring now to FIG. 2 there is depicted the preferred housing construction for guiding pressurized air to and from the chamber portion 16. An inlet 40 has a threaded portion for mounting a threaded nipple therein. This thread is of a selected size and a like thread is provided in outlet 42. From chamber 16 the outlet has a drilled hole 43 which has a diameter which is generally one-quarter of an inch or more. The inlet 40 has the smooth reduced diameter 44 leading from the threaded portion to chamber 16 sized so as to provide a jet force with this reduced diameter concentrating the incoming air as an impinging force on the teeth of the rotor. This short length 44 is about one-eighth to five-sixteenths of an inch in length depending on the size of rotor and chamber. The diameter of section 44 is sized between about one-tenth to one-quarter inch according to various charts to be hereinafter described.

Assembly of the Vibrating Turbine of this Invention The chamber 16 is of a determined size which, as reduced to practice, is substantially the diameter of the rotor and may be from 1% inches to 5 inches. The weights 38 placed in the rotor portion 34 may be light, medium or heavy depending upon the effective vibratory force exerted at the desired operating conditions of the unit. The ball bearing 32 is assembled in the rotor 34 as a press fit in a bore formed therein. This assembly 30 is then pressed on a snug fit on the smooth shank portion 23 of shaft 22 after which the disc end 20 and the shaft mounted rotor are then pushed into bore 16 of the housing 10. The periphery of the tooth portion 36 provides a clearance of a few thousandths of an inch to one-sixteenth of an inch between the outer periphery of the teeth and the inner surface of bore 16. The threaded end portion 24 of axle 22 is passed through the hole 28 and with nut 25 end 20 is drawn into recess 18 and when the nut has been tightened the unit is assembled.

The effectiveness of this vibrator as far as operating at or below a safe noise level results from a careful forming of the teeth portion 36 in the manner of straight-sided or slightly crowned tooth form. The relationship of this toothform and the pressurized air fed through the inlet portion 44 of the inlet is selected so that the vibrator will operate at maximum r.p.m.s with a noise level below 85 dbs and preferably in the range of 65 to dbs which is less than the established level permitted where continuous presence of workmen in or around these vibrators may occur without damage to their hearing.

As reduced to practice, and as seen in the following charts and graphs the effective r.p.m.s of the rotor while maintaining the low level of noise is dependent on tooth size, inlet size and outlet size.

Chart of FIG. 3

In chart 3, the model 130 noted in later charts has a rotor which is 1% inches in diameter. The inlet hole identified as 44 is shown with varying sizes while a onequarter inch diameter outlet hole is used for all these tests. A fixed number of teeth, as for example 50, and formed as a 32 diametral pitch gear is provided on this rotor. Inlet air at 60 and 90 p.s.i. is fed in through the inlet whose hole diameter 44 is varied from 0.059 to 0.226 inch in diameter. As noted in this chart the preferred inlet diameter with the lowest sound level is found at 0.116 inch hole diameter. This diameter results in a 61 db noise level at 7,200 r.p.m. and with an increase of pressure from 60 p.s.i. to 90 p.s.i. the db level goes up to 63 db at 2 foot on an A-scale. The rotor speed of 7,800 r.p.m. at this diameter is substantially close to the maximum. Because of the effective r.p.m.s and the noise levels achieved the inlet hole standard for this 1% diameter unit is one hundred ten-thousandths of an inch. An effective inlet may vary from one hundred-one to one hundred thirty-six-thousandths of an inch in diameter. The inlet selected which has one hundred ten-thousandths inch diameter has a noise level of 62 db at 7,600 r.p.m. and 60 pounds inlet pressure and 62% noise level db at 8,000 r. p.m. and 90 pounds.

Chart of FIG. 3 and Graphs of FIGS. 4 and 5 Referring next to the chart of FIG. 3 and the graphs of FIGS. 4 and 5 there is depicted the importance of the inlet size ofportion 44 to the fixed outlet size 43. Measurement of a vibrator was made of a rotor having 1% inches in diameter and having 50 teeth corresponding generally, if not exactly, to a 32 diametral pitch gear form. The inlet hole diameter varies from a minimum of fifty-nine-thousandths of an inch in diameter to a maximum of two hundred twenty-six-thousandths of an inch in diameter. The outlet diameter is fixed at onequarter inch diameter. As seen in the chart and the graphs the speed in r.p.m.s increases from a low of 3,600 r.p.m.s at both extremes of inlet diameter to the maximum r.p.m.s developed at one hundred tenthousandths of an inch in diameter. The noise level at this standard size is about 62 dbs at both 60 and 90 p.s.i. inlet pressure and at the same time the r.p.m.s are also at or near their maximum at this diameter inlet.

FIG. 5 represents a graph of the noise level changes resulting from the change in inlet openings as noted in the chart of FIG. 3. The minimum noise levels are recorded when the inlet diameters are at one hundred tenand one hundred sixteen-thousandths inch in diameter. It is to be noted that where the inlet diameter approaches the size of the outlet that the r.p.m.s drop drastically while the noise level increases a great deal. When the inlet diameter exceeds the outlet diameter the unit stalls.

Chart of FIG. 6 and Graph of FIG. 7

Referring next to the chart of FIG. 6 and the graph of FIG. 7 there is shown information and the relationship pertaining to the performance at various inlet pressures of five of the models which have their rotors provided with teeth in size and number designed to operate at optimum efficiency as to r.p.m.s of the rotor and the noise levels. Model No. 100, for example, has a rotor with 57 teeth with a tooth form of 48 diametral pitch. Line A" on the graph of FIG. 7 applies to the noise level versus the r.p.m.s of both Model and Model 130. This line is nearly a straight line. The line 8" re lates to the performanceofthe Model the line C" to Model and the line D" to Model 250.

As below noted the rotor diameter and tooth size gets progressively larger as the rotor size increases. As noted in both FIGS. 6 and 7 the lower decibel noise levels are desirable and'are achieved and in none of the models is the government standard maximum of 85 db approached or exceeded.

The models above noted and other in the series have preferred inlet and outlet sizes to produce r.p.m.s which are nearly at the peak available while the noise level is at or near the minimum. As noted below the preferred inlet and outlet sizes and the tooth profile for the several sizes are:

Standard Vibrator Design It is important to note that the inlet size relates to both rotor diameter and tooth size until the rotors using 24 diametral pitch gear tooth sizes is reached. Even at the largest rotor sizes the ratio of the inlet to the outlet is about 50 percent. The careful relationship of tooth size and inlet and outlet size as established for use in these successful vibrators operate at noise levels below 75 db at l and 2 feet.

Chart of FIG. 8 and Graph of FIG. 9

Having determined an effective design for a rotor of 1% inches in diameter the efficiency of the tooth shape used on the rotor was analyzed. Rotors with very fine teeth, with a knurled surface, with a saw-tooth form and with a standard gear-like tooth form were tested. In the chart of FIG. 8, all rotors were 1% inches in diameter. A rotor having a very fine gear-tooth form was provided with a 48 diametral pitch gear-tooth form and had 78 teeth. The noise level in dbs was just slightly higher than the 32 pitch model (selected as standard) seen in the fourth line. The 32 diametral pitch rotor is formed with 50 teeth and the r.p.m.s at 40 p.s.i. inlet pressure is 6,800. At 90 p.s.i. inlet pressure the noise level in dbs is at a very satisfactory 59 while rotating at 8,000 r.p.m.

In line three of FIG. 8 a saw-tooth formcorresponding somewhat to the tooth form seen in conventional turbines was provided on the turbine rotor and was made with 32 pitch and 50 teeth. Although the r.p.m. efficiency increased so also did the noise level in dbs and at 90 p.s.i. inlet pressure this level moved above 65 dbs. In line two, a rotor having its periphery formed with a coarse knurl with about 73 knurls formed on the periphery had such a low r.p.m. output that it was rejected as unacceptable even though the noise level was marginally acceptable.

It is acknowledged that the r.p.m.s of the 32 diametral pitch rotor could be greatly increased by forming the teeth as a saw-tooth, however, the saw-tooth rotor having a 32 pitch and 50 teeth disposed upon the periphery at 40 p.s.i. derived r.p.m.s were slightly less than the standard rotor while the noise level was exactly the same as the vibrator having the standard recommended rotor. With an increase in p.s.i. to 50 the r.p.m.s drastically jumped and the noise level moved to 56 db. With 60 p.s.i. often and commonly used in vibrating systems, the noise level moved to 58 db and the r.p.m.s increased to 8,700. At 70 p.s.i. the noise level increased to 58% dbs which is well within the acceptable noise limit and at 70 p.s.i. the r.p.m.s go up to 8,900. With the inlet pressure increased to 80 p.s.i. the noise moved to about 60 db and the r.p.m.s increased to 9,000. At an inlet pressure of 90 p.s.i. the noise level moved to 66 db which is above the noise level of the 32 pitch rotor ofline four and at the same time the r.p.m.s moved up to 10,500.

Note that as seen on the chart of FIG. 8 and as represented on the graph of FIG. 9 that with 100 p.s.i. inlet pressure and the resulting increased r.p.m.s cause the saw-tooth form and the 48 pitch wheel to operate at noise levels in excess of 60 db. Since most air pressure supply systems have 100 or more p.s.i. pressure available this must be considered when one is furnishing a quiet vibrator.

As of filing this application the noise level acceptable for 8 hour exposure is 85 db. This level is likely to be reduced in the near future to 75 or 80 db. Assuming when the input diameter is from 30 to 55 percent of the output diameter the number of teeth usable on a given rotor is shown in the chart below. These teeth enable the vibrator to operate at less than the 85 db limit.

Rotor Diameter Teeth 1% to 1% inches 40 to 80 1% to 2% inches 45 to 80 2% to 3% inches 45 to 85 3% to 5 inches 60 to l teeth Within these ranges the noise level is below 85 db. An appreciably lower noise level than this maximum is found when using the standard vibrator design above noted. The teeth configurations to maintain these low levels must be relatively alike and evenly spaced.

Terms apply to the position in which the turbine-type vibrator may be constructed or used.

While a particular embodiment of this vibrator has been shown and described it is to be understood the invention is not limited thereto since modifications may be made within the scope of the accompanying claims and protection is sought to the broadest extent the prior art allows.

What is claimed is:

1. A relatively silent, compressed gas-actuated, turbine-type vibrator having a rotor of not less than 1% inches and not more than 5% inches diameter and within a speed range of 6,000 to 10,000 rpms having a noise level not greater than decibels hz., the vibrator including: (a) a substantially closed housing having a cylindrical chamber therein; (b) a dynamically unbalanced rotor freely rotatable in the cylindrical bore of the chamber, the diameter and length of the rotor being established so that not less than one thirty-second of an inch clearance is provided between the rotor and ends and bore of the chamber, the rotor having a plurality of tooth-like configurations formed on its outer periphery, the tooth-like configuration further having a depth which corresponds to a distance not exceeding 7 percent and not less than 1% percent of the diameter of the rotor; (c) an air outlet formed in the housing and extending from the rotor chamber to the outside of the housing, and (d) an air inlet formed in the housing and extending from the outside of the housing to the rotor chamber, the air inlet arranged to direct the incoming pressurized air tangentially against the teeth of the mounted rotor and with the tooth like configurations so formed that in a plane normal to the axis of the rotor the face of the tooth like configuration against which the incoming air impinges defines an angle of intersection with the theoretical radial line of said rotor, said defined angle being as little as 0 and as great as 30 as measured from said point of intersection and inclined in such a direction that the circumferential thickness of the tooth like configurations tends to decrease as the radial distance from the axis increases and with the tooth-like configuration so formed that in a plane normal to the axis of the rotor the face of the tooth-like configuration against which the incoming air impinges defining an angle of intersection with a theoretical radial line of said rotor, said defined angle being as little as zero and as great as 30 as measured from said point of intersection and inclined in such a direction that the circumferential thickness of the tooth-like configurations tend to decrease as the radial distance from the axis increases, the cross-sectional area of the inlet being 30 to 55 percent of the area of the outlet diameter.

2. A turbine-type vibrator as in claim 1 in which the rotor is provided with gear-like teeth ranging in size from 48 to 24 diametral pitch on rotors whose outer diameters range from 1% inches to 5 inches.

3. A turbine-type vibrator as in claim 1 in which the length of the controlling inlet size is between oneeighth and five-sixteenths inch and the diameter of the inlet is between one-tenth and one-quarter inch.

4. A turbine-type vibrator as in claim 1 in which at least one end of the chamber is closed by a disc and an axle on which the rotor is mounted is secured thereto, the disc adapted to snugly engage mating positioning means formed at the opening and in which the other chamber end wall has an aperture sized to receive and retain the axle which is passed therethrough and by a fastening means the axle and attached disc is tightly drawn into a closing condition of the chamber.

5. A turbine-type vibrator as in claim 4 in which the rotor is carried on a ball bearing mounted on the axle which is nonrotating when assembled for use.

6. A turbine-type vibrator as in claim 1 in which rotors of 1%. inches in diameter to and including 3 /2 inches in diameter have not less than 40 teeth and more than 80 teeth, and rotors of 3% inches in diameter to and including 5 inches in diameter have not less than 60 teeth and more than 120 teeth.

7. A turbine-type vibrator as in claim 1 in which the teeth on the rotor are arranged to lay in a plane passing through the axis of the rotor.

8. A turbine-type vibrator as in claim 1 in which the outlet and the inlet from and to the rotor chamber are each connected to a pipe tap opening formed in the housing.

9. A turbine-type vibrator as in claim 1 in which the housing is provided with a pair ofleg portions providing means for securing the assembled vibrator to a device to be vibrated.

10. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 1% inches diameter has an inlet diameter of one hundred nine-thousandths inch and an outlet diameter of one-quarter inch.

11. A turbine-type vibrator as in claim in which the rotor of 1% inches diameter has its tooth profile as 48 diametral pitch or coarser.

12. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 1% inches diameter has an inlet diameter of one hundred sixteen-thousandths and an outlet diameter of one-quarter inch.

13. A turbine-type vibrator as in claim 12 in which the rotor of 1% inches diameter has its tooth profile as 32 diametral pitch or coarser.

14. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 1% inches diameter has an inlet diameter of one hundred sixteen-thousandths and an outlet diameter of one-quarter inch.

15. A turbine-type vibrator as in claim 14 in which the rotor of 178 inches diameter has its tooth profile as 32 diametral pitch or coarser.

16. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 2 inches diameter has an inlet diameter of one hundred sixteen-thousandths and an outlet diameter of five-sixteenths inch.

17. A turbine-type vibrator as in claim 1 in which the rotor of 2 inches diameter has its tooth profile as 32 diametral pitch or coarser.

18. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 2% inches diameter has an inlet diameter of one hundred sixteen-thousandths and an outlet diameter of five-sixteenths inch.

19. A turbine-type vibrator as in claim 18 in which the rotor of 2%. inches diameter has its tooth profile as 32 diametral pitch or coarser.

20. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 2% inches diameter has an inlet diameter of one hundred twenty-five-thousandths and an outlet diameter of three hundred ninety-sixthousandths inch.

21. A turbine-type vibrator as in claim 20 in which the rotor of 2% inches diameter has its tooth profile as 24 diametral pitch or coarser.

22. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 3 /2 inches diameter has an inlet diameter of one hundred fifty-six-thousandths and an outlet diameter of three hundred ninety-six thousandths inch.

23. A turbine-type vibrator as in claim 22 in which the rotor of 3 /2 inches diameter has its tooth profile as 24 diametral pitch or coarser.

24. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 5 inches diameter has an inlet diameter of two hundred twenty-thousandths and an outlet diameter of twenty-seven sixty-fourths inch.

25. A turbine-type vibrator as in claim 24 in which the rotor of 5 inches has its tooth profile as 24 diametral pitch or coarser.

P0405) UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent 3,870,282 Dated March 11th, 1975 Inventor( Theodore Wadensten It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shovm below:

Change inventor's address to read P,O, Box 8, Stilson Road, Wyoming, Rhode Island 02898 A change of address was filed with the Final Form.

Signed and sealed this 6th day of May 1975.

(SEAL) Attest:

C. MARSHALL DANN RUTH C. MASON Commissioner of Patents Attesting Officer and Trademarks

Claims

1. A relatively silent, compressed gas-actuated, turbine-type vibrator having a rotor of not less than 1 1/4 inches and not more than 5 1/2 inches diameter and within a speed range of 6, 000 to 10,000 rpms having a noise level not greater than 85 decibels hz., the vibrator including: (a) a substantially closed housing having a cylindrical chamber therein; (b) a dynamically unbalanced rotor freely rotatable in the cylindrical bore of the chamber, the diameter and length of the rotor being established so that not less than one thirty-second of an inch clearance is provided between the rotor and ends and bore of the chamber, the rotor having a plurality of tooth-like configurations formed on its outer periphery, the tooth-like configuration further having a depth which corresponds to a distance not exceeding 7 percent and not less than 1 1/2 percent of the diameter of the rotor; (c) an air outlet formed in the housing and extending from the rotor chamber to the outside of the housing, and (d) an air inlet formed in the housing and extending from the outside of the housing to the rotor chamber, the air inlet arranged to direct the incoming pressurized air tangentially against the teeth of the mounted rotor and with the tooth like configurations so formed that in a plane normal to the axis of the rotor the face of the tooth like configuration against which the incoming air impinges defines an angle of intersection with the theoretical radial line of said rotor, said defined angle being as little as 0* and as great as 30* as measured from said point of intersection and inclined in such a direction that the circumferential thickness of the tooth like configurations tends to decrease as the radial dIstance from the axis increases and with the tooth-like configuration so formed that in a plane normal to the axis of the rotor the face of the tooth-like configuration against which the incoming air impinges defining an angle of intersection with a theoretical radial line of said rotor, said defined angle being as little as zero and as great as 30* as measured from said point of intersection and inclined in such a direction that the circumferential thickness of the tooth-like configurations tend to decrease as the radial distance from the axis increases, the cross-sectional area of the inlet being 30 to 55 percent of the area of the outlet diameter.

1. A relatively silent, compressed gas-actuated, turbine-type vibrator having a rotor of not less than 1 1/4 inches and not more than 5 1/2 inches diameter and within a speed range of 6,000 to 10,000 rpms having a noise level not greater than 85 decibels hz., the vibrator including: (a) a substantially closed housing having a cylindrical chamber therein; (b) a dynamically unbalanced rotor freely rotatable in the cylindrical bore of the chamber, the diameter and length of the rotor being established so that not less than one thirty-second of an inch clearance is provided between the rotor and ends and bore of the chamber, the rotor having a plurality of tooth-like configurations formed on its outer periphery, the tooth-like configuration further having a depth which corresponds to a distance not exceeding 7 percent and not less than 1 1/2 percent of the diameter of the rotor; (c) an air outlet formed in the housing and extending from the rotor chamber to the outside of the housing, and (d) an air inlet formed in the housing and extending from the outside of the housing to the rotor chamber, the air inlet arranged to direct the incoming pressurized air tangentially against the teeth of the mounted rotor and with the tooth like configurations so formed that in a plane normal to the axis of the rotor the face of the tooth like configuration against which the incoming air impinges defines an angle of intersection with the theoretical radial line of said rotor, said defined angle being as little as 0* and as great as 30* as measured from said point of intersection and inclined in such a direction that the circumferential thickness of the tooth like configurations tends to decrease as the radial dIstance from the axis increases and with the tooth-like configuration so formed that in a plane normal to the axis of the rotor the face of the tooth-like configuration against which the incoming air impinges defining an angle of intersection with a theoretical radial line of said rotor, said defined angle being as little as zero and as great as 30* as measured from said point of intersection and inclined in such a direction that the circumferential thickness of the toothlike configurations tend to decrease as the radial distance from the axis increases, the cross-sectional area of the inlet being 30 to 55 percent of the area of the outlet diameter.

2. A turbine-type vibrator as in claim 1 in which the rotor is provided with gear-like teeth ranging in size from 48 to 24 diametral pitch on rotors whose outer diameters range from 1 3/8 inches to 5 inches.

3. A turbine-type vibrator as in claim 1 in which the length of the controlling inlet size is between one-eighth and five-sixteenths inch and the diameter of the inlet is between one-tenth and one-quarter inch.

6. A turbine-type vibrator as in claim 1 in which rotors of 1 1/4 inches in diameter to and including 3 1/2 inches in diameter have not less than 40 teeth and more than 80 teeth, and rotors of 3 3/4 inches in diameter to and including 5 inches in diameter have not less than 60 teeth and more than 120 teeth.

9. A turbine-type vibrator as in claim 1 in which the housing is provided with a pair of leg portions providing means for securing the assembled vibrator to a device to be vibrated.

10. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 1 3/8 inches diameter has an inlet diameter of one hundred nine-thousandths inch and an outlet diameter of one-quarter inch.

11. A turbine-type vibrator as in claim 10 in which the rotor of 1 3/8 inches diameter has its tooth profile as 48 diametral pitch or coarser.

12. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 1 5/8 inches diameter has an inlet diameter of one hundred sixteen-thousandths and an outlet diameter of one-quarter inch.

13. A turbine-type vibrator as in claim 12 in which the rotor of 1 5/8 inches diameter has its tooth profile as 32 diametral pitch or coarser.

14. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 1 7/8 inches diameter has an inlet diameter of one hundred sixteen-thousandths and an outlet diameter of one-quarter inch.

15. A turbine-type vibrator as in claim 14 in which the rotor of 1 7/8 inches diameter has its tooth profile as 32 diametral pitch or coarser.

18. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 2 1/2 inches diameter has an inlet diameter of one hundred sixteen-thousandths and an outlet diameter of five-sixteenths inch.

19. A turbine-type vibrator as in claim 18 in which the rotor of 2 1/2 inches diameter has its tooth profile as 32 diametral pitch or coarser.

20. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 2 3/4 inches diameter has an inlet diameter of one hundred twenty-five-thousandths and an outlet diameter of three hundred ninety-six-thousandths inch.

21. A turbine-type vibrator as in claim 20 in which the rotor of 2 3/4 inches diameter has its tooth profile as 24 diametral pitch or coarser.

22. A turbine-type vibrator as in claim 1 in which a vibrator having a rotor of 3 1/2 inches diameter has an inlet diameter of one hundred fifty-six-thousandths and an outlet diameter of three hundred ninety-six thousandths inch.

23. A turbine-type vibrator as in claim 22 in which the rotor of 3 1/2 inches diameter has its tooth profile as 24 diametral pitch or coarser.