US3166988A

US3166988A - Vacuum power unit

Info

Publication number: US3166988A
Application number: US259905A
Authority: US
Inventors: William J Kohler
Original assignee: Individual
Current assignee: Individual
Priority date: 1963-02-20
Filing date: 1963-02-20
Publication date: 1965-01-26
Anticipated expiration: 1982-01-26

Description

Jan. 26, 1965 w. J. KOHLER 3,166,988

VACUUM POWER UNIT Filed Feb. 20, 1.963 3 Sheets-Sheet l INVENTOR EG- ZJ WLL/AM J KOHLEF? ATTORNEYS Jan. 26, 1965 w. J. KOHLER 3,166,988

VACUUM POWER UNIT Filed Feb. 20, 1963 5 Sheets-Sheet 2 39 25 43 37 v 3/ 49 48 29 7a 8 74 73 57 l 76\ V k I 7 l I: A I T I L63: 79 61 50 1 Q 7775 i 50 l A 1N VENTOR.

WLL/AM 1/? KOHLEF? AT TORNEYS Jan. 26, 1965 w. J. KOHLER 3,166,988

VACUUM POWER UNIT Filed Feb. 20, 1963 3 Sheets-Sheet 5 I NVENTOR.

WLL/AM 1f KOHLE}? Baa /%W4.%, Q

ATTORNEYS United States Patent 3,166,988 VACUUM PUWER UNlT Wiiliam J. Kohier, 1254 1st St. N, Fargo, N. i'lak. Fiied Feb. 2d, 1963, Ser. No. 259,9tl 1 Ciaim. Ci. 91-347) This invention relates to a new and very useful penumatically operated diaphragm actuating device for diaphragm-type pumps driven by an axially reciprocating drive shaft.

There are now commercially available small sized diaphragm-type pumps which are hand operated. These pumps are commonly used as portable installations for gas or fuel oil delivery, as from a small tank to a tractor in the field or in construction work, and as stationary installations for transferring aqueous or organic fluids from large storage receptacles to portable tanks. However, so far as is known to me there is now available no conven ient means for operating such diaphragm-type pumps from sources of constant non-atmospheric pneumatic pressure, especially vacuum sources such as are conventionally available from operating internal combustion engines.

Accordingly, it is an object of this invention to provide a vacuum power unit for coupling to a diaphragmtype pump to enable one to drive the pump from the vacuum intake of an internal combustion engine.

lit is another object of this invention to provide a combination of a diaphragm-type pneumatic motor and a reversing valve therefor enabling one to utilize a generally constant source of pneumatic pressure to operate a diaphragm-type vacuum pump.

It is another object of this invention to provide a combination of a diaphragm pump and a power driven diaphragm operating or actuating device therefor in which the diaphragm pump and the actuating device are connected together for common movements by means of a single push and guide rod.

It is another object of this invention to provide a reversing valve having a rotary valve element mounted for rotary reciprocation within a cylindrical chamber for use in a diaphragm actuating device.

Other and further objects of this invention will become apparent to those skilled in the art from a consideration of the following specification taken together with the drawings wherein one preferred embodiment of the in vention is shown and described.

Referring to the drawings wherein like characters indicate like parts throughout the several views:

FIG. 1 is a side elevational view of an embodiment of a pneumatically operated diaphragm actuating device of the invention in combination with a diaphragm-type vacuum pump, some parts thereof broken away;

FIG. 2 is a top plan view of the embodiment shown in FIG. 1;

FIG. 3 is a side elevational view of the reversing valve mechanism used in the embodiment of FIG 1 as viewed from top to bottom of FIG. 2;

FIG. 4 is a vertical sectional view taken along the line 4-4 of FIG. 3;

FIG. 5 is a vertical sectional view taken along the line s 5 of FIG. 3;

FIG. 6 is a bottom plan view of the reversing valve mechanism used in the embodiment of FIG. 1 with the cover plate removed, some parts thereof shown in section;

FIG. 7 is an enlarged detail sectional view taken along the line 77 of FIG. 2;

FIG. 8 is a view similar to FIG. 7 showing the valve element reciprocated to a reverse position;

FIG. 9 is a side elevational View of the reversing valve mechanism viewed from bottom to top in FIG. 2 and greases showing the position of the crank arm immediately after valve reversal; and

FIG. 10 is a side elevational View of the reversing valve mechanism viewed from bottom to top in FIG. 2 and showing the position of the crank arm immediately after the valve has assumed the position shown in FIG. 8.

Turning to the drawings, there is seen in FIG. 1 a pneumatically operated diaphragm actuating device of the invention, herein designated in its entirety by the numeral 11, in combination with a conventional diaphragm-type vacuum pump, herein designated in its entirety by the numeral 12.

As diaphragm-type vacuum pumps are commercially available and well-known to those skilled in the art, no detailed description thereof is given herein. However, it "will be appreciated that a diaphragm-type pump has at least onetpressure compartment in which flexible diaphragm means forms at least a portion of one wall thereof. This compartment is provided with fluid inlet and discharge ports communicating therewith and valve means are associated with such ports. The inner end of a pump drive shaft is functionally associated with such diaphragm and the outer end portion of such pump drive shaft is adapted to axially reciprocate. Thus, when such drive shaft outer end portion is axially reciprocated, the diaphragm is caused to flexand thereby pump fluid through the discharge ports from the compartment after the fluid has entered into the compartment from the inlet ports.

The diaphragm actuating device 11 is seen to consist of a combination of three major components, a diaphragm unit 13, a reversing valve mechanism 14, and a push and guide rod assembly 15.

The diaphragm unit 13 employs a pair of dish-

shaped plates

16 and 17 having their outer annular edges suitably connected together by bolt and nut connections 18. The

plates

16 and 17 confine between them, around and within their circumferential edges, a diaphragm or flexible membrane 19. The outer peripheral edges of diaphragm 19 are rigidly secured between the annular edges of the plates 16 and 17f The diaphragm 19 has a central portion securely held between a pair of plates 20.

The inner end of the rod assembly 15 is secured to the plates 20 by means of a threaded stud 22 which is secured to one of the plates 20 and is threaded into the inner end of the rod assembly 15. The rod assembly 15 is mounted for reciprocation axially on a bearing (not shown) suitably supported within a hub 21 formed integrally with dish-shaped plate 16.

The outer end portion of the rod assembly 15 is fitted with a fork 23. Fork 23 has a pair of axially aligned apertures, one defined in each opposite end. One such aperture is adapted to receive the outer end portion of the rod assembly 15 and the other such aperture is adapted to receive the outer end portion of the pump drive shaft 24. Conveniently, a set screw extends through the wall of each aperture in the fork 23 for fixing drive shaft 24 and rod assembly 15 in their respective associated apertures. Thus, fork 23 interconnects the outer end portions, respectively, of drive shaft 24 and rod assembly 15 for common axial reciprocatory movements. The fork 23 further has a pair of aligned, axially spaced, radial projections 25. The opposed inner walls of each projection 25 are generally normal to the side of the fork 23.

In order to cause a generally constant source of pneumatic pressure to exert force first on one side of the diaphragm 19 and then on the other side thereof so as to produce flexing motion and reciprocation of the rod assembly 15, there is employed a reversing valve assembly or mechanism 14. The mechanics of the reversing valve can take any particular form but the embodiment of this invention as shown in the drawings employs a ro- Patented Jan. 26, 1965 tary valve element 28 to control the application of pneumatic pressure to opposite sides of the diaphragm 19 within the casing of the diaphragm unit 13.

The rotary valve element 28 is mounted for rotary reciprocation within a cylindrical chamber 29 whereby to alternatively, separately connect each one of a pair of pneumatic suction or

pressure outlet ports

31 and 32 with, respectively, a pneumatic suction or pressure inlet port 33 and the other outlet port with either one of a pair of

exhaust channels

34 and 35.

The cylindrical chamber 29 is contained within a valve body 37 in which are formed outlet port 31, outlet port 32, and inlet port 33. These

ports

31, 32 and 33 are circumferentially positioned about the cylindrical walls of cylindrical chamber 29 in spaced relationship to one another. The rotary valve element 28 itself is cylindrically shaped and has a valve shaft 38 axially extending from the inner face thereof. The outer face of the valve element 28 has a shoulder 39 integrally formed along its outer perimeter (see FIG. 4). The shaft 38 is separately formed and fits into an appropriately formed bore in the inner face of the valve element 28. The valve element 28 is free to rotate independently of movements of the valve shaft 38. To effect this arrangement, the upper end of the valve shaft 38 (referring to FIG. 4) is circumferentially grooved at 42 adjacent such end so that when the valve shaft 38 is positioned in the aperture in the valve element 28, and a set screw 41 is turned in an appropriately threaded bore set at right angles to the aperture for the valve shaft 38, the tip of the set screw 41 rides in the groove 42 but does not interfere with the free rotation of the valve shaft 38 with respect to the rotary valve element 28. Those skilled in the art will appreciate that any arrangement can be used here so long as the shaft 38 is free to independently revolve with respect to the valve element 28.

Within the valve element 28 are defined

channels

43 and 44. Channel 43 diametrically extends through the valve element 28 while channel 44 radially extends into the side of cylindrical valve element 28 to join the channel 44 in the axial region of the valve element 28. The included angle between

channels

43 and 44 is less than 90, and in order to form a continuous passageway between the inlet port 33 and the outlet port 31, a suitable circumferentially extending groove or slot 45 is formed in the valve element 28 in the Wall of the channel 43 on the side thereof away from that adjacent the channel 44 so as to permit a continuous passage to be formed in the valve element 28 between the inlet port 33 and the outlet port 31 when the valve element 28 is appropriately positioned within the cylindrical chamber 29, as shown for example in FIG. 7. The valve element 28, as are the other parts of the reversing valve mechanism 14, is preferably and conveniently formed of metal so that, for example, the

channels

43 and 44 and slot 45 are appropriately formed as by drilling and milling operations, respectively.

A pair of axially extending circumferentially spaced

grooves

34 and 35 are cut or formed in the cylindrical wall of the valve element 28 to form the respective exhaust ports 34 and 35 (the

numbers

34 and 35 being used herein to refer synonymously to the exhaust channel or the groove representing the same). These ports or

grooves

34 and 35 extend to and through the shoulder 39. Groove 35 is so positioned that, when the channel 43 interconnects inlet port 33 with outlet port 32, the groove 35 is centrally positioned or diametrically extends across the mouth of outlet port 31 (FIG. 8). Similarly, the groove 34 is so positioned that, when the channel 44 and the channel 43 with groove slot 45 interconnect the inlet port 33 with the outlet port 31, the groove 34 is so positioned as to diametrically extend across the mouth of outlet port 32 (FIG. 7). With respect to the cylindricalside wall of valve element 28, it is convenient to form the slot 45,

channels

43 and 44, and

grooves

34 and 35 at spaced intervals of 45 with respect to one another.

Interconnecting inlet port 33 with a source of pneumatic air pressure (not shown) is a pipe 46 having a screw-type coupling element 47 which threadedly engages the walls of inlet port 33. Interconnecting outlet port 31 with chamber 51 of diaphragm unit 13 is a pipe 48 which is connected to outlet port 31 by threaded couplings 49 and to chamber 51 through dished plate 17 by means of a threaded coupling 50. interconnecting outlet port 32 with chamber 52 of diaphragm unit 13 is a pipe 53. Pipe 53 is connected to the outlet port 32 by means of a threaded coupling 54 and to the disc shaped plate 16 by means of threaded coupling 55.

The constant source of pneumatic pressure can either be a vacuum or compressed air or other gas; for example, a suitable source of vacuum pressure can be obtained from an internal combustion engine vacuum intake while a suitable source of compressed gas is a conventional cylinder of carbon dioxide preferably fitted with a conventional reduction valve.

It is also convenient to place the

outlet ports

31 and 32 and the inlet port 33 in the valve body 37 circum ferentially in the cylindrical chamber 29 at axially spaced intervals of about with respect to each other.

The valve body 37 not only defines the cylindrical chamber 29 but also an enclosed chamber 57. The housing of chamber 57 is composed of a generally tub-shaped recess (a casting or the like) and is designated by the numeral 58 and which is formed integrally with the portion of the valve body 37 forming the cylindrical chamber 29. The closure of chamber 57 is effected by means of a plate 53 which fits over the peripheral side edges of the housing 58. The plate 59 is secured to the rim edges of the housing 58 by means of machine bolts 65 which extends through suitable apertures in plate 59 into threaded bores formed in bosses 61, the bosses 61 being formed as thickenings in the side walls of housing 58 at regularly spaced intervals.

To position and mount the valve element 28 in cylindrical chamber 29, the valve element 28 is positioned in the chamber with its attached valve shaft 38 extending through the housing 58. Then a retaining washer 62 having an axially positioned bore slightly larger than the diameter of the shaft 38 is slipped over the shaft 38 against the under side of the valve element 28. Through apertures in the washer 62 extend a pair of threaded

stop rods

63 and 83 which are also screwed into suitably formed threaded bores in the bottom or base of the rotary valve element 28. In this way common rotary reciprocatory movements of the washer 62 and the rotary valve element 28 are provided. There is provided a circumferentially extending slot 64 (see FIG. 6) in the washer 62, the circumferential distance of this slot 64 being chosen to correspond to the desired number of degrees through which it is desired to have the valve element 28 move during rotary reciprocation (in the embodiment shown, about 45). There is also mounted on the inside wall of valve body 37 (within the enclosed chamber 57) a stop plug 65, as by press fitting the stop plug 65 into a suitably formed and positioned recess or bore in the valve body 37. Stop plug 65 rides in slot 64 as element 28 reciprocates.

Next, over the shaft 38 is slipped a spacer washer 66 followed by the open end of link 68, which is made fast to the shaft 38 as by means of suitable keying (not shown). Lastly, there is slipped over the shaft 38 a second spacer washer 69.

The shaft 38, itself, is journalled in a hub 78 formed in the plate 59, the hub 70 being equipped with appropriate bearings 71.

A toggle joint, herein designated in its entirety by the numeral 73, is employed in the diaphragm actuating device 11 as a valve actuating arm which is spring biased,

This toggle joint 73 is seen to consist of a link 68, the open end of which is fast on the shaft 38 as described, and a link 74 which will be described below. Link 74, as a unit, has its open end pivotally mounted in the enclosed chamber 47 in the floor of the housing 5% adjacent one of the side walls thereof.

The link 17%, itself, is telescopically extensible and retractable and is composed of a cylindrical portion 81 (whose outer end is adapted to receive washer 79 and machine screw fed), and a rod portion 82 which slidably engages the inside walls of cylindrical portion 551. To p-ivotally mount the link '74 to the floor of housing 58, there is provided a thickened region 78 adjacent the side of the housing 58 as shown, for example, in FIG. 4. In this wall portion F8 a suitable bore is provided and this bore is threaded. A round-head machine screw has a suitable washer 7* slipped over its shank and then the machine screw 8b is slipped through an appropriate aperture in the end of the link 74, together with washer 7L and the screw fit; is turned into the threaded recess in the second portion 78 to provide the desired pivotal connection for fink i l with the valve body 37. The head or exposed end of rod portion 82 is broadened out and flattened and then provided with an appropriate port for reception of the rivet 75. Thus, link 74" and link 68 are pivotaily joined together at their inner ends by rivet f5. Rivet 75' is held in place by a head portion 7e and a splitring connector 77. To yieldingly bias the rod portion 82 and the cylindrical portion 81 in a position of maximum extension, a coiled compression spring S7 is placed loosely and circumferentiaily about the link 74. Gne end of spring $37 is allowed to abut against the thickened portion 7S and the other end against enlarged head region of rod portion 82.

Threaded stop rod 63 is so positioned that when the toggle joint '73 is in the position generally shown in FIGS. 3 and 6, the rotary valve element 28 is pivotally reciprocated about the axis of shaft 3% so as to connect inlet port 33 with exhaust outlet port 32 through the appropriate above described channels in the rotary valve element 28. When in this position, observe that the stop plug 65 has moved in slot 64 to a position where, in effect, the rotary valve element 28 is fixed or locked in position. On the other hand, when the toggle joint 73 is moved to the posi- .tion shown generally by the dotted lines in FIG. 6, the link 68 contacts a second threaded stop rod 83 which reciprocally rotates the rotary valve element 28 to a position where the inlet port 33 is connected with the outlet port 31. In this position, the rotary valve element 28 is also looked in place by the stop plug 6d which has now moved along the slot 64 relative thereto so that the rotary valve element 28 is, in effect, locked into this second or alternative position. Observe that this arrangement provides a prompt and substantially immediate (for purposes of the diaphragm actuating device 11) change-over of connections between the inlet port and respective ones of the

outlet ports

31 and 32 with substantially no intermediate or transition period. Such an arrangement is desirable in order to utilize the maximum amount of power available from the flexing of the diaphragm 19 in response to the changes of the reversing valve mechanism 14.

Diaphragm-type pump 12, diaphragm unit 13, and reversing valve mechanism It maintain their desired relationship to each other through the use of four tubes $4. The size of the diaphragm unit 13 in the device if is such that these tubes 34 are generally in spaced parallel relationship to one another forming a general parallelogram configuration. The procedure is to extend a long bolt 3'5 through each tube $4 while the pump and the diaphragm unit are positioned at opposite ends of the long bolt. The tubes 34 then act as spacers so that when nuts 36 are added to the long bolts the desired fixed relationship between pump 12 and diaphragm unit 13 is maintained.

and 9).

' Positioned fast on the exposed end of shaft 38 is a crank. Thus, one end of a crank anm SS is mounted on the exposed end of shaft 38 as by the use of a conventional key or the like. The other end of the crank arm 88 is fitted with a crank pin 89 whose exposed end portion is formed into a bearing 90. Pressure exerted laterally against the crank pin 89 causes the shaft 88 to pivot and thereby move the toggle joint 73 from one position to its alternative position, as discussed above, thus causing the rotary valve element 23 to change pneumatic pressure from one side of diaphragm 19 to the other.

Since the bearing 90 of crank pin 89 is to be positioned for reciprocatory movements between the projections 25 of fork 23, there is provided on the valve body 37 a pair of bosses 92, each outwardly oppositely extending from long sides of the valve body 37. Each boss has a suitably formed aperture therein for positioning the vaive body 37 between a pair of tubes 84, the tubes passing through the aperture in each boss 92.

In assembling the device 11, the crank pin bearing 953 is positioned between the projections 25 of fork 23 by means of the bosses 92 in such a manner that when the diaphragm 19 is moved to the left (as seen in FIG. 1) until the crank arm has its crank pin 89 resting against the right projection 25; then the toggle joint "73 is generally in the position shown in FIG. 6.

Briefly, the operation of the diaphragm actuating device 11, when operated from a source of vacuum, is as follows: When the device 11 is duly coupled, as described, by means of the fork 23 to the drive shaft 24 of a diaphragm-type pump 12 and the source of vacuum is admitted to the pipe 46, as shown in FTGS. l and 9, suction is exerted through the pipe 48, since the valve is initially in the position shown generally in FIG. 7. This suction causes the rod 15 to recipronate to the right by pulling the diaphragm 19 to the right (see FIGS. 1 Air is introduced through exhaust port 34 to allow the diaphragm 19 to flex. When the diaphragm 19 moves through its neutral position, the left projection 25 (see FIGS. 1 and 9) engages bearing 90 of crank pin 8% and rotates the shaft 28 clockwise until the edge or side of link 68 abuts against stop pin 83. As diaphragm 19 reaches a position of maximum flex (to the right as seen in FIG. 1), the toggle joint 73 passes over center and causes valve element 28 to rotate to the position shown in FIG. 8. Rotation of valve 28 is limited by two

stops

63 or 83 and d5 so channel 43 will interconnect hose 46 with hose 53. Vacuum is applied to pipe 41 through channel 43 to pipe 53 causing diaphragm 19 to move to the left and the whole cycle is reversed.

The operation of the device with compressed air is the same as with vacuum except that the two hoses 48 and 5'3 must be reversed in their connections to the diaphragm unit 13.

My invention has been thoroughly tested and found to be completely satisfactory for the accomplishment of the above objects, and while I have shown and described a preferred embodiment, I wish it to be specifically understood that the same is capable of modification without depar-ture from the spirit and scope of the appended claim.

I claim:

A fluid operated motor having a reciprocating drive shaft, and further comprising:

(a) a diaphragm unit including a casing and a flexible diaphragm dividing said casing into two chambers,

(5) rod means journalled for axial reciprocation in said casing and operatively interconnecting said diaphragm with said drive shaft whereby said diaphragm and said drive shaft are adapted to reciprocate in unison,

(c) a reversing valve including a housing and a valve element mounted therein for limited rotary reciprocatory movements alternatively in opposite directions, said housing defining a chamber for said valve element, an inlet port, exhaust port means, and a pair of outlet ports, and with all of said ports and port means communicating with said chamber,

(d) said valve element being disposed within said housing whereby upon rotary reciprocation, said valve element is moved between a first position wherein one of said outlet ports is connected with said inlet port and the other is connected with said exhaust port means and a second position wherein the other of said outlet ports is connected with said inlet port and said one thereof is connected with said exhaust port means,

(6) said outlet ports each communicating with a different one of said diaphragm chambers for driving said diaphragm and said shaft upon the introduction of fluid alternately into said diaphragm chambers, and

(f) a valve actuating assembly including a connection operatively associated with said valve element imparting said reversing movements to said valve element responsive to axial reciprocatory movements of said rod means, said valve actuating assembly further comprises:

(1) a shaft extending from said valve element in an axial direction with respect to the axis of rotary reciprocation of said valve element,

(2) a crank arm secured to said shaft and having a crank pin operatively connected with said rod means whereby rotary reciprocatory movement 8 is imparted to said shaft upon reciprocation of said rod means,

(3) a toggle joint having a pair of pivotally connected link elements one of which is secured on said shaft and the other of which is telescopically extensible and retractable and is also pivotally connected to said valve housing, said toggle joint including means biasing said other link element toward an extended condition and also biasing said one link element to one or the other of two angularly spaced positions about said shaft and on opposite sides of a longitudinal alignment of said link elements, and

(4) means connecting said shaft to said valve element so as to impart said rotary reciprocation to said valve element between its first and second positions upon rotation of said shaft by said crank arm and upon the biasing of said one link element of said toggle joint into one or the other of its said angularly spaced positions.

References Cited by the Examiner UNITED STATES PATENTS 7/15 Meiluk 91-345 8/37 De Motte 91 347 6 /54 Hein 103452 LAURENCE V. EFNER, Primary Examiner.

WARREN E.. COLEMAN, Examiner.