US2169807A

US2169807A - Compressor

Info

Publication number: US2169807A
Application number: US193986A
Authority: US
Inventors: George R Lyon
Original assignee: Individual
Current assignee: Individual
Priority date: 1938-03-04
Filing date: 1938-03-04
Publication date: 1939-08-15
Anticipated expiration: 1956-08-15

Description

C'. R. LYON coMPREssoR Filed Marfl 4; *1938 Fig. 23 v Aug. 15, 1939.4

om? @'v f INVENTOR MAI@ ATTORNEY Aug. l15. 1939. G. RqLYN f 2,169,801-

- coMlREssR l Filed March 4.1958 z'sneets-sheet 2 INVEN TOR ATTORNEY Patented Aug. 1s, 1939 zusam compassion George, n. man, Highland Para, nach.

Application March ,4, 1938, Serial No. '193,986

.. i 5 claims. (ci zat-reo) This invention relates to an improvementl in pumps and more especially, pumps for pumping liquids and compressing gases in which two pistons operate in a single cylinder.

. 1 One of the objects of this'v "invention is the provision of a pump functioning without valves in which-'opposed pistons operating in va single cylinder control the supply andl distribution of the iluid handled.

l A secondobject of this invention'is the provision of a pump of the type set forth in the preceding paragraph ln which the opposed pistons are actuated by rods from cranks which op'- l erate at the same speed and have dillerent V throws'. v

It is another object `of the present invention to regulate the speeds and paths oi travel of the opposed pistons in relation toeach other and in coordination with respect to the inlet and outlet ports,v whereby the optimum displacement is achieved and the two pistons are prevented from interfering with one another.

A further object of this invention i's the provision of a pump of the type set forth in the pre- :5 ceding paragraphs, which, because of its simplicity of design, is capable ofv a wide rang of uses yin the pump and compression iield.

Additional objects and advantages of this invention .will be more apparent as the description ,0, proceeds, wherein, 4

Figure 1 is a horizontal sectional view of a pump takenalong the line I-l of Figure 2.

Figure 2 is a sectional elevational view taken along line 2 2 of Figure 1.

5 Figure 3 ls a diagram showing one complete cycle of the operation of the pump.

Figure 4 is a sectional plan view of a modication of the pump shown in Figures 1 and 2.

Figure 5 is a sectional side elevational view of 0 the modified structure taken cn lines 5 5 ,of

Figure 4.

Figure 6 is a curve showing a characteristic cycle of the piston-functioning of the modication shown by Figures 4 and4 5 With reference to Figures 1 to 3, there is shown a cylinder I0 having therein an inlet port II and a discharge port I2. Located within this cylinder are opposed pistons I3 and It connected to cranks I5 and I6 by rods Il and I8. Crank II is pro- 3 vided with means for receiving suitable motivating power and this motion istransmitted to crank I5 by means of side cranks I9, 20, 2l, and 22, `which are connected by

links

23 and 24, hereinafter more fully described.

i With special reference to Figure 3, the operation ol' the pump is as follows: In this ligure, four sets of numerals from 0 to 35 have been set out.v Those numerals below X-X represent the different positions of piston I6 and the set above line X-X represent the different positions of 5l piston I3. Thus, by comparison of similar numerals, the relative location of the pistons and the relative location of the' cranks may be accurately determined and compared, throughout the cycle. The adjoining faces of the pistons are 1I)y in essential contact when the movements of the pistons are in the direction from the discharge port I2 towards thelnlet port II, as shown by O--O in Figure 3. At this point piston I3 covers and closes the discharge port l2.' With continued ld movement of the pistons toward the inlet port I l, the velocity of the piston It accelerates more rapidly than that of piston i3 because` of the relative position of the crank centers 25 and 26 in their rotative paths and because of the dii- 20 `ference between the lengths of the cranks I5 and I5. Thus, depressed pressure of partial vacuum is created between the pistons. With continued movement, separation of the pistons increases and at the passage ci piston i4 over the inlet 25 i port II,as as l0, (below X-Xlof Figure 3, the uidfrom the inlet connection will be caused to flow into the space between the pistons. 'I'he pistons 'continue to separate with the inlet port vII `open, piston i3 then reaching the end of its 80 stroke and reversing its direction as at Il (above X-X) of Figure 3, followed by the same action on the part kof piston It as at I5 (below X-X) of Figure 3. The rate of separation of the pistons then gradually decreases until they 'momentarily 35 attain equal velocity at the point at which piston I8 completely closes inlet port Il in its return stroke, as at point 2l) (below X-X) of Figure 3. The space between the pistons then decreases as bothtravel towardthe discharge portl l2, com- 40 pressing the contents of the cylinder.

With continued movement of piston I3, the discharge port is opened, as at point 22 (abov y X-X) of Figure 3. As piston I3 reverses at the end of its travel beyond the discharge port, piston Il' continues to approach that port which it partially covers and then reverses, as at point 35 (below X-X) of Figure 3. Piston I3 overtakes piston VI4 just as the velocities become equalized momentarily, which is at the point where piston I3 covers the discharge port and thus completely ejects the contents of the space between the pistons and completes 'the cycle.

With additional reference to Figures 1, 2, and 3, more in detail, it will be seen that cylinder at the end of cylinder I0.

I0 has an inner wall 21 and an outer wall 28 and located between are chambers 28 for circulation of lal suitable cooling medium. The cylinder is also provided with annular spaces 38 and 3|, therein communicating .with the interior of the cylinder by means ofinlet and discharge ports Il and I2. Although not shown, it is to be 4understood that suitable connections extend ing from the source of supply and point of delivery will be provided at the exterior openings of inlet and discharge annular spaces 30 and 3|. Secured to the piston I4 by means of .wrist pin 34 is the forward portion of rod I8. The rearward portion of rod I8 is connected to crank IB b'y bearing cap 32. Rod I1 has its forward portion connected to piston I3 through the medium of wrist pin 33 and the rearward portion of this rod is connected to crankV I5'by bearing cap 35.v

Cranks |5 and I6 have their ends 52. 53, 54, and 55 seated in

bearings

62, 63,54, and 85, formed It will be noticed that crank I 8 has a greater depth than crank I5 and as herein shownthe diameter of circle of travel of crank I8 is approximately one third' greaterthan th circle of travel of crank I5. This is done to impart a greater throw to piston I4 than to piston I3 and makes the path of travel of piston I4 also approximately one third farther than the path of travel of piston I3. AIn addition to the difference of the diameter of the path of. travel between cranks I5 and I6, there is an additional difference 1 in that crank I6 is also provided with a gear wheel 38 which is connected to suitable motivating power. i

At the end 5210i crank I8 there is provided a side crank 40 and at the end of 53 of crank I5, is provided a side crank 4 I. 'I'hese two side cranks are connected to each other by link 23. The

opposite ends

54 and 55 of cranks I5 and I6 are also provided with

side cranks

42 and 43 which in turn are connected by link 24. 'I'hese side cranks are positioned so that those on one side will be ninety degrees in advance of those on the opposite side,

-thus causing delivery of uniform turning effort from crank shaft I6 to crank shaft I5, and rotation of the two crank shafts is positively synchronized. It will, of course be understood in 'this connection that I do not desire to-limit myself to the particular driving means, to wit, side,

- cranks and links hereinl disclosed. Obviously,

other commercially known means for. synchronizing rotation of crank shafts are usable without departing from the scope of my invention.

If desired, the lubrication of my pump may be accomplished by several well known means of lubrication, for example, pressure lubrication by oil lines through the moving parts, with connections to external source of oil supply and outlets into the various bearings.

, With reference to the modified structure shown in Figures 4 to 6, it will be seen that cylinder |0a is provided with an inlet port IIa anda discharge port I2a las well as pistons I3a and I4a. Piston |40, is connected to crank ISa by rod l8a and piston I3a is connected to rocker-shaftv by rod I'Ia.

Portions

45 and 48 of crank shaft I 8a are seated in bearings 62a and 63a and rocker -shaft 44 has

portions

41 and 48 seated in 63a and .64a.

motivating power.u Motion is imparted to rocker shaft 44 by means of side crank 48 on crank shaft Ilia through link 50 to rocker arm 5I on rocker shaft 44, thereby causing rocker shaft 44 to operate with a reciprocating action.

The operation of this modified structure is essentially the same as that of Figures 1 to 3, ex-

v cept that by means of this construction it is posvof .the arcs through which both crank arms of the rocker shaft travel, thus retarding or accelerating th'e 'motion bf' the piston driven from the rocker shaft withrelation to the motion of the crankdriven piston during the various functions of the cycle.

Thus, when the device is used as a compressor,

piston' I3a may be caused to follow closely the motion of piston |4a during the first part of the cyclefthus minimizing vacuum effect prior to opening of the inlet port, and retarding the motion of piston I3a on the return stroke following closure of the inlet port, thereby permitting compression of the contents of the inter-piston space to 0r near the desired delivery pressure before opening of the discharge port.

Figure 6 is a representation of typical variations of inter-piston space during one complete cycle of operation ina machine of the modified construction (Figures 4 and 5), in'which, however, the coordination of piston movements with relation to the inlet and discharge ports is similar to that characteristic of the two-crank construction (Figures 1 and 2). In the diagram (Figure 6) the vertical scale` indicates the face-to-face separation of the twoI pistons in percentage of ual separation of the pistons to point II where the long-stroke piston uncovers the inlet port; continued separation to point 2|, where the longstroke piston covers and closes the inlet port; relative approach of the pistons to point 24, where the short-stroke piston uncovers and opens the discharge port; and continued reduction of interpiston space during the remainder of the cycle, in which the material between the pistons is ejected through the discharge port, this action being completed at point 36, when the shortstroke piston covers and closes the discharge port, with the pistons again in virtual contact, moving in the same direction at momentarily uniform velocity. v

This feature of complete delivery of the contents of the cylinder is a distinct improvement in the art of gas compression and vacuum pumping of mechanical accuracy.

What I claim as my invention is:

.1. A pump having a cylinder provided with inlet and outlet ports, two opposed pistons reciprocably mounted in the cylinder and controlling said ports,.m'ea.ns for driving said pistons to -eifect differential movement of the pistons in a manner to increase the space therebetween when the fluid, and discharge the same through the outlet port, and said means comprising cranks having diierent throws and respectively operatively connected to the pistons and means for driving the cranks at the same speed.

2. A lpump having a cylinderprovided with in. let and outlet ports, two opposed pistons recipro- 'cably mounted in the cylinder and controlling to increase the space therebetween when the inlet port is open to draw iiuid into the cylinder between the pistons and` to eiect movement of the pistons at different rates in a manner to compress the fluid, and discharge the same through the outlet port, and said means comprising cranks having different throws and different angular advances and respectively operatively connected to the pistons, and means for driving the cranks at the same speed.

3. A pump `having a cylinder provided with inlet and outlet ports, opposed pistons reciprocably mounted in the cylinder for controlling said ports, means for reciprocating the opposed pistons in the cylinder in a manner that the pistons cooperate with one another to draw fluid into the cylinder therebetween during the interval the intake port is open and to compress the iluid and open the' outlet port, said means comprising a pair of cranks having diierent throws with the throw of one crank in advance of the throw of the other and means respectively operatively connecting the cranlm to the pistons.

4. A pump having a cylinder provided with inlet and outlet ports, opposed pistonsreciprocably mounted in the cylinder for controlling said ports, means for reciprocating the opposed pistonsin the cylinder in a manner that the pistons cooperate with one another to draw fluid into the cylinder therebetween during the interval the intake port is open and to compress the fluid and open. the outlet port, said means comprising a pair of cranks driven at the same speed and having different throws, the throw of one crank being in advance of the throw of the other and means respectively operatively connecting the cranks to the pistons.

5. A pump having a cylinder provided with inlet and outlet ports, opposed pistons reciprocably mounted in the cylinder for controlling said ports, means for reciprocatingl the opposed pistonsvin the cylinder in a manner that the pistons cooperate with one anotherto draw fluid into the cylinder 'therebetween during the interval the intake port is open and to compress the fluid and open .the outlet port,- said .means comprising a pair of cranks driven at the same speed and con-` GEORGE n. LYON.