US1736507A - Compressor-operating means - Google Patents

Description

Nov. 19, 1929.

E. F. PETERSON 1,736,507

COMPRESSOR OPERATING MEANS 3 Sheets-Shet o O N O 7 Filed July 6, 1926 Nov. 19, 1929. E. F. PETERSON 1,736,507

COMPRESSOR OPERATING MEANS Filed July 6, 1926 I 3 Sheets-Sheet 2 F E I w Y 7 gwuento'o Edwin-1 PETEPEEITL Nov. 19, 1929. E. F. PETERSON 3 COMPRESSOR OPERATING MEANS Filed July 6, 1926 5 Sheets-Sheet 3 v F i lm.

Patented Nov. 19, 1929 EDWIN F. PETERSON, OF MENQMINEE, 'MICH IGAN' COM-PRESSOR-OPEE- KTING MEANS Application filed July 6, 1926. Serial No. 120,796.

The present invention relates to compres sors, primarily intended for use 'as an air compressor.

The primary object of the invention is to provide an improved type of air compressor operating under a novel principle whereby a constant and uniform delivery of air under compression will be delivered by the compressor. 1 I I Q A further object of the invention is to pro-- vide a compressor embodying a plurality of cylinder-s and co-operating pistons which act successively for compressing of the air, thus resulting in no lost motion during operation of the compressor.

A further object of the invention is to pro-- vide an improved type of air compressor'embodying a plurality of pairs of axially aligned cylinders with one of the pairs of cylinders serving as a low pressure cylinder and its'companion cylinder serving as a high pressure cylinder, and the plurality of pairs of cylinders co-acting with one another for serving as ashockabsorbing medium for the companion pairs of cylinders.

A still further object of the invention is to provide an air compressor embodying a novel actuating means for the cylinders whereby the compressor is devoid of any cranks or wrist :pinsl A still furtherobject of the invention resides in the provision of improved means whereby the opposed pistons ot' the compressor are caused toreciprocate in a straight I path when a rectilinear motion is :i'nnaa'rted to the pistons.

A still further object of the invention is to providela multiple cylinder, multiple stage, constant, :no lost motion air compressor which is of extremely simple and durabl construction, and which compressor will operate with comparatively little vibration, and which will also be practically noiseless in its operation.

Other objects and advantages of the invention will be apparent during thecourse of the "following detailed description, taken in connection with the accompanying drawings forming a part of this specification and in which drawings:

Figure 1 is a side elevation of the improved compressor and showing one o-f-the-side-cover plates removed. i

Figure 2 is a horizontal section taken substantiallyon line2 2 of Figure 1. v

Figure 3 is a vertical transverse section on line 3-3 of Figure 2 and looking in the direction of the arrows. 1

Figure 4 is a vertical transverse section taken substantially on line i -d oi Figure 2 in the directionot the arrows, and showing the manner in which the pistons are retained in a straight path during their reciprocato'ry motions.

Figure 5 isa sectional view taken substantially on line 55 of Figure 4; and looking in the direction of the arrows.

Figure 6 is a detail view of the drive cam for imparting a :reciprocatory motion to the pistons.

Fi ure :7 is an end View of the discharge end of the compressor.

Figure 8 is an end view of the intake end oi the compressor.

Figure 9 is a detailed sectional view on line 99 of Figure 10,, and showing the contruction of the cross heads connecting the opposed piston-s.

Figure 10 is a sectional View on line 1 0 m of Figure 9., and showing the manner in which the opposed pistons are connected with the cross head.

Figure 11 isa view partly in elevation and part in section, and showing a slightly modig tied for-m 0t cross head.

Figure 12 shows a still further modified form of the cross head.

Figure 13 is .a fragmentary perspective view of one end of the minor or roller guides for the cross heads. Referring to the drawings in detail, and wherein similar reference characters de'si g nate corresponding parts throughout the several views, 15 designates a suitable base plate upon which the compressor is intended toFbe mounted.

Mounted transversely upon the upper face or" the base plate 15, is a pair of supporting plates 16 and 15 which are preferably square in outline, and which preferably have right angular flanges 17 formed along their lower edges and through which suitable bolts 18 may pass for anchoring of the plates in spaced parallel confronting relation. Each of the plates 16 and 16 is provided with symmetrically arranged aligning circular shaped openings 19 which are arranged concentric to the axis of the plates.

Mounted in surface contact with the inner face of each of the supporting plates 16 and 16', are square bearing plates 20 and 20 re spectively, and which plates as will be observed in Figures 3 and 4, are arranged in angular relation to the supporting plates with their marginal edges intersecting the supporting plate openings 19. These bearing plates 20 are preferably secured to their respective supporting plates by means of headed bolts 21 which pass inwardly thru the supporting plates with their shanks threaded into the corner portions of the bearing plates. The intermediate portion of each marginal edge of each of the bearing plates 20 and 20, is provided with semi-circular shaped depressions 22 which align with the openings 19 of the respective supporting plates to which the bearing plates are attached. These semi-circular shaped depressions 22 serve as a further anchoring means for the supporting plates, in a manner to be subsequently explained.

Revolubly mounted axially of the supporting plates as by a suitable bearing 23 and an end thrust bearing 24 carried by the plates 16 and 16 respectively, is a drive shaft 25 which may be driven from any suitable source of power. The bearings 23 and 24 are preferably of the roller type as illustrated in Figure 3, meta suitable stuffing box 26 is preferably provided for the drive shaft 25 where it extends thru the bearing 23. The end thrust bearing 24 is preferably in the form of a cap bolted to the outer face of the supporting plate 16.

A drive cam 28 is mounted upon the drive shaft 25 between the bearing plates 20 and 20, and is secured to the drive shaft for rotation therewith as by means of suitable keys 29. Provided in the peripheral face of the cylindrical shaped drive cam 28, is an endless cam groove 30 having its opposite terminals disposed at diametrically opposite sides of the drive cam. Thrust bearing washers 31 are provided at each end of the drive cam 28, and which washers are intended for hearing relation against the confronting faces of the bearing plates 20 and 20 for preventing longitudinal shifting'of the drive cam when being rotated by the drive shaft 25. This cylindrical shaped drive cam 28 is preferably of a diameter such that when the cam is mounted between the bearing plates, the circumferential face of the cam will be spaced but a slight distance inwardly from the axial center of the aligning openings 19, Thisconstruction is clearly illustrated in Figure 4 of the drawings.

Carried by the supporting plate 16, and extending longitudinally of the base plate 15, is a group of four low pressure cylinders 32 having annular flanges 33 provided adjacenttheir inner ends for abutting with the outer face of the supporting plate when the cylinders are in assembled relation to the plates. Extending inwardly from the annu lar flanges 33 of each cylinder, are tubular skirt portions 34 of a diameter to snugly fit within the openings 19 with the inner ends of the skirt portion disposed flush with the inner face of the bearing plate 20. Suitable bolts 35 extend through the flanges 33 and are threaded into the supportingplate 16 for rigid mounting of the low pressure cylinders in parallel relation upon the supporting plate. open ends of the low pressure cylinders 32, and all of which are of similar construction, open inwardly of the supporting plate 16. Closing the outer end of each of the cylinders 32, are cylinder heads 36 provided with horizontally aligned ports 37 Directly connected with the outer port of each of the cylinder heads 36, is an automatically operable valve 38, and each of which connect with transfer ducts 39 which extend longitudinally of the compressor to each side of the supporting plates 16 and 16. Connecting each upper and lower set of the low pressure cylinders 32, and communicating with the inner ports 37 of the cylinder heads, is a double acting check valve 40 provided with a screened intake 41. This double acting check valve 40, as will be observed in Figure 2, acts for automatically checking egress of air from the low pressure cylinders during their compression strokes. By observing Figure 8, it will be seen that by so connecting the upper and lower sets of low pressure cylinders 32 by means of the double acting check valve 40, permits of a suitable space being provided between the cylinders through which the drive shaft 25 may extend for connection to a suitable source of power for imparting a rotary movement to the shaft.

Arranged in axial alignment with each of the low pressure cylinders 32, and carried by the supporting plate 16, are high pres sure cylinders 42 of an internal diameter and area less than that of their opposed low pressure cylinders. These high pressure cylinders 42 are also provided with annular flanges 43 adapted tobear against the outer face of the supporting plate 16, and skirt portions 44 which extend through the supporting plate openings 19 with their ends flush with the inner face of the bearing plate 20'. Bolts 45 extend through the flanges 43 for rigidly mounting of the cylinders in parallel relation upon the supporting plate 16. Closing the outer end of each of the high Thus it will be seen that the inner,

pressure cylinders 42, is a cylinder head '46 providedat its outer side with a horizontally opening port 47 and provided at its end face withan exhaust portion 47 An automatically operable check valve 48 is connected at the outer side of each of the heads 46, at the ports 47, and respectively connect with the discharge end of the respective transfer ducts 39. Thus it will be seen that each of the high pressure cylinders 42 are connected withtheir companion low pressure cylinders 32 by means of an independent transfer duct 39. Connected with each of the terminally opening,- exhaust ports 47 of each of the cylinder heads 46, is a check valve 49, and all of which open into a collector 50 which connects all of the high pressure cylinders 42 with a common outlet pipe 51 leading to a pressure tank or for use in any preferred manner. By observing Figure 7, it will be seen that the collector 50 embodies a pair of vertically disposed pipes 52 connecting the top-and bottom cylinders, and which pipes 52 are connected at their intermediate portions by a horizontally disposed pipe section 53-which leads to the common outlet pipe 51.

Reciprocally mounted in each of the aligning companion pairs ofcylinders 32 and 42, areopposed pistons 55 and 56, adapted for movement in the cylinders 32 and 42 respectively. As will readily be observedin Figure 5, the piston 55 is of greater diameter than that of'the piston 56, and that thepistons are provided with a desired number of piston rings for causing the pistons to fit snugly within their respective cylinders. Connected with eachof the pistons 55 and 56, and extending in axial alignment toward one another, are piston or connecting rods 57 connected at their inner ends by means of a crosshead 58. Thiscross head 58 embodies a substantially rectangularly shaped connecting block 59 having threaded openings 60 provided in axial alignment at each end thereof for threaded reception of the threaded innerends of the piston rods 57. Lock nuts 61 threaded upon the inner end of the piston rods 57, are adapted to be turned into binding engagement with the end faces of the connecting blocks for preventing possible disconnection of the rods from the connect ing block. Fitted about the outer andside faces of the connecting block 59, is a substantially U-shaped guide bearing 62 having its side arms 63 provided with longitudinally extending guide grooves 64. Extending transversely through the connecting block 59 and guide bearing 62, is a carrier pin 65 having a bearing portion 66 provided at the inncrsideof the connecting block for rotatable mounting. of a tubular shaped cam roller 67. This bearing portion 66.pr0vides a shoulder atthe inner end-ofthe carrier pin for engagingthe inner face of the connecting block, and that portionofthe carrier pin directly outwardly ofthe outer face of the guide hearing 62, is: threaded as at 68 for receiving suitable jam nuts 69 which, when turned into binding engagement with the guide bearing, secure the carrier pin against rotation wit in thecross head, and also rigidly connect the guide bearing 62 with the connecting block 59, Provided on the carrier pin 65 outwardly of the threaded portion 68, is a second or outer bearing portion 7 O for rotatablev mounting of atubular shaped guide roller 71. The outer terminal end of the carrier pin may-be threaded for receiving suitable lock nuts 7 2 for securing the roller 71 against movement oil the carrier pin.

Extending longitudinally of the base plate 15, and between the supporting plates 16 and 16, are main or cross head guides 75 having their opposite ends rigidly secured to the edges of the respective bearing plates 20 and 20 as by suitable fastening elements such as cap screws76. These guides 75, and two of which are disposed at each edge of the bearing plates, serve as guides for the cross heads 58 for causing the pistons 55 and 56 to move in straight paths within their respective cylinders. As will be observed in Figure 4, the inner edges of the companion guides 75 receive the longitudinally extending guide grooves 64 provided in the side arms of the guide bearings 62. By observing Figure 3, it will be seen that the transversecenters of the main guides 75 intersect the axis of the aligned cylinders 32 and 42. It may here be well to state that these guides 75 by reason of being anchored at their ends to the bearing plates 20 and 20,serve as a tie for rigidly retaining the supporting plates 16 and 16 in proper parallel spaced apart relation.

When the cross heads 58 are mounted be tween the guides 7 5, their respective cam rollers 67 will be disposed in the cam groove 30 of the drive cam 28, with their carrier pins 65 extending in directions radially of the drive cam and toward each corner of the square supporting plates 16 and 16.

Rig-idly mounted at the inner face of each of the supporting plates 16 and 16, and at each corner portion of the plates, are L-shaped brackets 78 having oil'set portions 79 extend ing in parallel relation with the side edges of the'bearing plates 20 and 20. These brackets 78 are eachadapted to support longitudinally extending spaced roller guides 80 which are preferably secured to the inner faces of the ofiiset portions 79 as by suitable bolts 81. These roller guides 80 are provided with fiat confronting faces 82 between which the guide roller 71 moves during reciprocation of the cross head 58. By observing Figure 4, it will be seen that these guide rollers 71 and coacting guides 80 serve to prevent binding of the cross heads 58 upon the guides 75 and thus permit of free and easy movement ofthe cross heads along their guides.

' spectively, are or ried by the side and top edges of the supporting plates 16 and 16 for enclosing the structures between the supporting plates, and providing a housing for receiving a lubricant in liquid form for lubricating of the moving parts operating between the supporting plates. A suitable filler opening 87 may be provided in the top cover plate for the placing of the lubricant within the housing formed by the cover plates, and a 1 suitable drain opening 88 may be provided in the base plate for draining of the lubricant when desirable. This inclosing of the movable portions between the supporting plates will not only provide an effective 1 method of lubrication, but will also tend to cause the compressor to operate with but comparatively little noise.

By so providing the arcuate shaped recesses in the edges of the bearing plates 20 and 21, and allowing the skirt portions of the cylinders to extend into the recesses, will permit of the bearing plates being more rigidly held against possible rotary movement and which movement would cause the main guides 75 to move out of proper aligning relation with the cylinders.

\Vith reference to the form of cross-head as shown in Figure 11, the bearing portion 66 disposed at the inner side of the connecting block 59, as well as the threaded portion 68 and the bearing portion disposed at the outer side of the connecting block, are shown as forming an integral structure, with the cam roller 67 held in position by a cap screw In the form of cross head as illustrated in Figure 12, the guide roller 71 has been dispensed with, and when using this type of cross head the roller guides 80 are not necessary.

By referring to Figure 2, and wherein the pistons are shown in position in the lowermost pairs of cylinders. and when the drive cam is moving in the direction of the arrow, the connected pistons will be moving in a di rection of the arrows as illustrated at the respective cylinders. The companion pairs of cylinders have been marked A, B, C, and D. Upon movement of the piston within the cylinder B and in a direction of the arrow, air will be drawn through the screened intake e1 opening the check va ve leading to the head 36 of the low pressure cylinder B and at which time the check valve 38 ofthe low pressure cylinder B is closed. At the same time, the piston of the high pressure cylinder B is moving toward. the cylinder head 46 and compressing its charge through the exhaust port 47 and into the collector 50. The check valve 48 is closed during the compression stroke of the high pressure piston 56, thus entrapping compressed air from the low pressure cylinder B in the transfer duct 39. Upon return movement of the connected pistons 55 and 56, the intake check valve will automatically close and allow the compressed air in the low pressure cylinder to be forced through the transfer duct 39, opening both of the check valves 38 and 48, and enter the high pressure cylinder during the suction or intake stroke of the high pressure piston. During the last mentioned operation, the check valved?) automatically closes. Each of the cylinders A, B, C and D, operates in a like manner and in successive order, thus causing a constant and uniform delivery of air under pressure to the common outlet pipe 51.

The pitch of the endless cam groove 80 may be varied for providing a desired stroke of the connected pistons 55 and 56.

From the foregoing description it will be apparent that a compressor embodying novel features construction has been provided whereby the connected pistons are retained in a true straight path of movement within their respective cylinders, and which pistons successively operate for providing an efficient multiple stage compressor having no lostmo tion, and producing a uniform and constant delivery of air to a common outlet pipe. It will also be apparent that a novel arrangement of parts has been incorporated in the compressor whereby the movable portions of the compressor act in an eiiicient manner in an extremely compact form.

Various changes may be made to the speciiic form and arrangement of parts herein shown and described, without departing from the spirit of the invention or the scope of the following claims.

I claim:

1. In motion transmitting mechanism for converting continuous rotary motion into rectilinear reciprocatingmotion, the combination with a pair of spaced apart supporting plates, of a drive shaft revolubly mounted in the plates and provided with a cam groove disposed between the plates, companion sets of elements reciprocally movable in a path parallel with the axis of rotation of the drive shaft, rods connecting companion sets of reciprocatory elements and extending parallel with the drive shaft, cross heads rigidly carried by said rods between the plates and having guide and cam rollers mounted upon their outer and inner faces respectively, guides connected between the supporting plates and providing tracks for the cross heads, said cam roller of the cross heads to engage in the cam groove of the drive shaft and be held against displacement by said cross head guides, and

further guides carried by the supporting plates outwardly of said cross head guides for receiving the guide roller mounted at the outer face of said cross heads.

2. In motion transmitting mechanism for converting continuous rotary motion into rectilinear reciprocating motion, the combination with a pair of spaced apart supporting plates, of a drive shaft revolubly mounted in the plate and provided with a cam groove disposed between the plates, a rod reciprocally movable in a path parallel with the axis of rotation of the drive shaft, a cross head rigidly carried by the rod between the plates, guides for the cross head, a carrier pin for the cross head extending in a direction radially of the drive shaft and projecting from the inner and outer faces of the cross head, a roller mounted on the carrier pin at the inner side of the cross head for engaging in the cam groove of the drive shaft, a roller mounted upon the carrier pin at the outer side of the cross head, and guides for said last mentioned roller.

3. In motion transmitting mechanism for converting continuous rotary motion into rectilinear reciprocating motion, the combination with a pair of parallel spaced apart square supporting plates, of a drive shaft revolubly mounted in the plates and provided with a cam groove disposed between the plates, companion sets of reciprocally movable elements movable in a path parallel with the axis of rotation of said drive shaft, rods connecting each companion set of reciprocally movable elements and extending longitudinally of the drive shaft between the plates, means carried by each rod and engageable in said cam groove for imparting reciprocatory motion to the rods, bearing plates rigidly car ried by the inner face of each supporting plate in angular relation to the supporting plates, main guides carried by and connected at their ends to the edges ofthe bearing plates, and roller guides carried by the supporting plates outwardly of said main guides, said main and roller guides to co-act with said cam engaging means for guiding the companion sets of reciprocally movable elements and their respective connecting rods in a straight path of movement.

EDWIN F. PETERSON.

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