US2049131A - Air compressor - Google Patents

Description

July 28, 1936. H. MORGAN 2,049,131

AIR COMPRESSOR INVENTOR.

July'28, 1936. H. MORGAN 2,049,131

AIR COMPRESSOR Filed Dec. 1'7, 1954 5 Sheets-Sheet 3 July 28, 1936. H. MORGAN 2,049,131

AIR COMPRESSOR Filed Dec. 17, 1934 5 Sheets-Sheet 4 H. MORGAN AIR COMPRESSOR July 28, 1936.

Filed Dec. 17, 1934 5 Sheets-Sheet 5 R O T N E V m Patented July 28, 1936 UNETEF STATES earner caries 12 Claims.

The invention refers to devices and systems for compressing air and gases, and has for its objects to raise the original pressure of the air or gas supply to a high point within the device in a com- -pact and economical manner to provide for a system of cycles that may provide for the use of the air compressed to operate machines, and many other objects that will become apparent as the invention is more fully set forth.

i The ordinary air compressor raises the pressure of air or gas directly in the first cylinder or compressor and then transmits it to a reservoir or service line. In this invention, the air or gas is raised in pressure by a series of travels through the same cylinders, each time being raised in pressure and progressively advanced, and other apparatus is used in the system to convert the energy developed in a series of cycles peculiar to its own system and methods which are hereinafter to be described.

In this application no regard has been made to i the effects of heat in the compression or expansion of air in the cylinders of the recompressors or other parts of the system, in order not to com- 5 plicate the operation of other phases of the invention described.

In the drawings, which illustrate by way of example an embodiment of this invention:

Figure 1 is a plan view of the apparatus in- 3Q volved in this invention.

Figure 2 is a sectional view in a longitudinal direction of one of the air recompressor cylinder units used in this apparatus.

Figure 3 is a sectional view along the line 33 of Figure 2.

Figure 4 is a sectional view along the line 44 of Figure 2.

Figure 5 is a longitudinal elevation of the motor unit used in the apparatus of this invention, along the line 55 of Figure 1.

Figure 6 is a side view of the rack and pinion portion along the line 66 of Figure 1.

Figure 7 is an end elevation of the recompressor cylinder along line I I-I I of Figure l.

Figure 8 is a diagrammatic view of the apparatus and method of operation.

Figure 9 is a sectional view of one of the air recompressor cylinder units, illustrating the application of the forces of air compression therein, in

the manner and method peculiar to itself and herein further described.

Similar reference characters refer to similar parts throughout the drawings.

In the device and system there are several distinct participating parts. These will be referred to as the compressor parts and the reservoir unit. The compressor units are made up of a series of four, in this embodiment, and marked IIBI, I02, I03 and I04. "They are similar in general and have similar reference characters 5 on their similar parts. The reservoir .unit is marked 30! The compressor units have main cylinder walls I, which have ports 2 for the admission of air at atmospheric pressure, and another series of ports 3 and 80 for high pressure air. The latter ports are connected with manifolds 4 that feed into the reservoir unit 3!.

The main cylinders of the compressor units are each provided with a valve sleeve 5 that has 15 ports 6 for low pressure and ports 6 for high pressure, while ports are provided in the head wall for back pressure relief. The valve sleeve moves or reciprocates in the main cylinder, closely fitting against the walls I and the ports are 20 provided in the forward end, the central portion and rear end portions as shown in the drawings, so that the functioning of the ports with respect to other cylinder ports may be in accordance with the working operation decided for the compressing cylinder system in the embodiment. The valve sleeve is provided with a bracket 1 which is connected with a gear rack 8, operated by a gear I! mounted on a shaft 9 that is operated from a motor in a manner to'be described. 30 Operating and moving within the valve sleeve are two so-called outer pistons, IE! and 20, which are arranged at the front and rear portions of the compressor, respectively, and holes IBI are provided in the head of cylinder ill for back pressure relief. These are compressing cylinders, and are connected together with rods l2, as indicated, which are slidable through a guiding spider l3, that guides them suitably. The spider 40 I3 is an integral part of the valve sleeve 5. The outer pistons are provided with ports I4, for lowpressure, which register with the lowpressure ports 6 in the valve sleeve 5, at proper intervals. They are also provided with high pressure ports 45 M0 which register with the high pressure ports in the valve sleeve, at proper intervals. Both sets of ports 6 and I4 periodically register with ports 2 in the main cylinder Wall. Likewise, high pressure ports 60 and I40 register with ports 3, 50 in the main cylinder wall I, at proper pre-determined intervals.

The outer piston I0 is provided with a large valve opening l5 centrally located at one end. This opening is closed by a plate'valve I6, mount- 55 ed on a hollow shaft 21, which is reciprocable, and also has another plate valve I8, which closes the central port IS, in outer piston 20.

The travel of the valves I6 and I8 is started by the movement of the valve sleeve 5, of which the spider I3 is an integral part and bears on one of the lugs 2I, on hollow shaft 21, as it slides along the rods I2, thereby seating the valve I6 or I8 in the end of outer piston I0 or 20, respectively, as the stroke of the outer pistons, I0 and 20, inner pistons, 26 and 36, begins. The spider continues to bear on the lug 2| through a proportion of the stroke of the pistons, which is twothirds, in this embodiment, and, as the pistons continue to the end of the stroke, the stress of compression retaining the valve I6 or I8 in its seat, the valve sleeve 5, and consequently, the spider I3 come to rest, but the other lug 2I, on hollow shaft 27, reaches a bearing position on the spider I3, in preparation for the return stroke of the valve sleeve.

An inner piston 26. disposed at one end of the cylinder and inside of the outer piston I0 reciprocates within the latter. This inner piston is also connected with another inner piston 36, operating within the outer piston 20, by the piston rod I1 which also is guided and supported by 21 and 22 as indicated in the drawings. The piston .rod I I is operated by a rack 28, through gears 29. This gear travels on a rack I28, operated by rack 28 at predetermined periods.

The cylinder is supported on a base 30 which is arranged to also support the motor. The

reservoir unit SM is provided with valve 3I, to

control the air to and from the latter and service pipe 32.

The main shaft 50 operates a bevel pinion gear 59 which in turn operates the gears 61. The

,latter drive cam members 68 and cam rods 69 and segmental gears I0 on their supports .II and drive gears I2 which operate shaft 9.

The operation of the recornpressing system is as follows:

The motor is started up, at the same time the compressing cylinders are operated through the shaft 50, the gears 59 and 61, cam 68, rods 69, the segmental gears I0 and spur gears 72 and shaft 9 in sequence. When the shaft 9 rotates,

it operates, for instance, the valve sleeve 5 of compressor unit I04, while at the same time, the respective shaft 9 pulls out the shafts 22 and I! of compressor unit I03, causing the outer pistons I0 and 20, the inner pistons 26 and 36 totravel toward the front end. This action causes the atmospheric air to be drawn in through ports 2 in cylinder wall I of unit I03, thence through ports 6 in valve sleeve 5, thence through ports I4 into outer piston I0, because the ports have registered to permit it. The piston 26 in cylinder I 0, by its movement toward the front end, produces a vacuum that draws in this air. It reaches the end of its stroke during this time, the valve I6 is closed, the ports I4 are closed, as well as ports 2 and 6. At the same moment ports 3, 60 and I40 in piston I0 are opened, while all the ports in piston 20 are closed but the valve I8 is open. The ports and BI are always in open registry.. The next step that 'follows occurs, and the sleeve 5. starts its return travel, this causes the spider I3 to bear on the lug 2I movingthe hollow shaft 2'! and thereby causing the valves l6 and I8 attached to it to open and close respectively. The shafts I I and 22 then begin their return stroke and move inner pistons 26 and 36 and outer pistons I0 and 20 respectively. The ports 2, 6 and I4 of the outer piston section 20 come into registry, while all the ports at the opposite end or section where outer piston I0 is are closed. The air under atmospheric pressure is then drawn into piston 20. At the same time, inner piston 26 commences to expel air from outer piston I0 through the opening I5 into the central chamber of the cylinder and through the ports 86 and BI into manifold 4. Then pistons and sleeves continue traveling and eventually the ports 3, 60 and I40 of the piston section 20 come into alignment and communicate with the outlet 3.

' All compressing cylinders are double acting and each of the so-called outer pistons I0 and 20 functions alternately as a piston and loading chamber in the movement of its loading stroke, and as a, discharge chamber in the movement of its delivery stroke. c

When two cylinder chambers are made into one chamber by the unseating of a valve between the two, the compression contained therein bears with equal stress on each end. If this compression is raised in pressure during the operation, the equality of stress is still maintained effective at each end of the chamber at all times, irrespective of to what pressure the air may be compressed.

If one end of the compressing chamber is an eight inch diameter piston, in a cylinder of eight and a half inch outside diameter and the other end of the chamber is, through the open end of the Valve seat of the cylinder from which a valve has been unseated, the closed end of an eight and a half inch outside diameter cylinder (now operating as a piston) and joined to the first cylinder mentioned by means of connecting rods, then the equal bearing pressure of air in the chamber bears with appropriate force on the piston head of eight and a half inch diameter with valve seated, and on the piston end of lesser diameter.

This appropriate force bearing on the piston head of outer piston I0, for instance, with valve I6 seated, effective through hollow shaft 22, yoke 24, rack 23, and gear I23 is expressed at shaft 9 in the direction of compression, and the equal bearing force on piston 36 in cylinder 20 effective through piston rod II, yoke I25, gear 29 (which it contacts centrifugally) rack 28 and gear I24 is expressed at the same shaft 9 and opposed to the direction of compression.

The ratio of gears 29 and I24 and the relativity of this ratio to gear I 23 determines the status of the shaft 9 and may show a surplus of energy in the direction of compression in accord with these ratios, which surplus is opposed to .compression and frictional resistances, while effecting economies in the consumption of drive power, see Figure 9.

Similarly the same condition prevails when the piston head of loading chamber 20, with valve I8 in its seat, and the appropriate bearing force thereon, recedes before the advance of compression piston 26, through discharge chamber I0, with valve I6 unseated.

The movement of the sleeve unseating the Valve in the first compressor, effected from another compressor, and movements of the sleeves in four double acting compressors, accomplish, by similar movements in each compressor, a movement of the compressor next to follow, then throwing the entire series into the reverse action of these same double-acting compressors.

The operation of the compressing cylinders,

pistons and valves is timed to suit the work. The closure and opening of ports may be set to work to any predetermined sequence to suit the system, and will be self evident to those skilled in the art.

The motor 13 proceeds through its mechanical connections to rotate shaft 50 operating the cams 68 through the bevel gears 59 and 61. The cam rods 69, segmental gears I and drive gears 12 are then operating shafts 9 and their incidental compression valve controls. Following is the operation of compressor unit H, which is typical of the othersz-The shaft 9 of this unit, through its gear I l, rack gear 8, moves the valve sleeve in the direction of the arrow shown in the diagram in Figure 8. This sleeve begins to close high pressure ports 3 and 60 in outer piston ill, at the same time it begins to open low pressure ports 2 and B in outer piston 20. The spider l3 incidentally contacting the lug 2i on hollow shaft 21 seats valve l8 in outer cylinder 29, converting it to a piston, and unseats valve [6 in outer piston l0, converting it to a discharge chamber. In order to move the outer pistons 10 and 20, which are next moved in this unit, connections through hollow shaft 22, connected to yoke 24, connected to rack 23 are propelled by a pinion I23 which is attached on one of the shafts 9 belonging to another of the compressor units, which in this case is I02. On the last mentioned shaft 9 are located gears I24 which operate the racks 28 moving the gears 29 placed on yoke I25. This yoke propels the inner pistons 26 and 36 through the rod I1.

The movement of the outer pistons in relation to the cylinder walls and the inner pistons changes the positions of the ports as indicated in the drawings.

Due to the position of the outer and inner pistons in this compressor unit, air is drawn through the low pressure ports 2, 6 and [4 into outer piston 20, while the air in the piston lll is being expelled through the opening l5 by piston 26 into the central chamber, and thence out of pipe 80. A moment later, in the continuation of the stroke, the sleeve 5 moves its port openings so that the low pressure ports 2, 6 and M of outer piston 29 are cut off, and high pressure ports 3, 6i] and I40 of the same piston are opened. This allows the expelled air from the central chamher to pass into the last mentioned high pressure ports. The return stroke now begins, and the sleeve and pistons approach the position shown in unit I03 of Figure 8. The atmospheric air is then drawn in through ports 2, 6 and M of outer piston Ill through forward travel of inner piston 26, while the air in piston is expelled by piston 36 into the central chamber through the outlet 19.

The'travel continues Lmtil the unit approaches the position of the ports indicated in HM of Figure 8. In this view, the atmospheric ports v2, 6 and M of outer piston II] are closed, and the high pressure ports 3, 60 and MD are opened allowing the built-up-pressure air from the central chamber through manifold 4 inlet 3 to enter into chamber of outer piston II].

It is, of course, noted that the operations of the various compressing cylinder units are not in unison so far as the sleeve and pistons are concerned, but according to the timing as indicated in general in Figure 8 which illustrates the sequence diagrammatically.

The system is progressively arranged for the increase of pressure in the compressing cylinders and provides, by its arrangement, a balanced power, particularly on the valve plates l6 and I8, and central chamber and pistons l0 and 20. This permits an easy movement of the parts and prevents excessive frictional resistance as well as other disadvantages.

While'but one form of this invention is indicated in the drawings, it is not intended to limit this application for patent to this particular system, except insofar as limited by the prior art, as it is appreciated that other forms might be developed and used that would use the same principles and come within the scope of the appended claims.

Having thus described the invention what is claimed is:

1. In an air compressing machine, the combination of an air storage tank, a plurality of air compressors connected with the said storage tank, a plurality of driving shafts, relative to the said air compressors, a plurality of gears mounted on said shafts, said gears being meshed with respective geared racks joined to terminals of respective piston connecting rods that control, within the compressors, reciprocating movements of a plurality of outer pistons, joined together by rods, and a plurality of inner pistons, mechanically connected, reciprocating within the said outer pistons, when the said driving shafts are actuated by a motor reciprocally, through mechanical connections in sequence and cam travel control.

2. In an air compressing machine, the combination of an air storage tank, a plurality of air compressors connected with the said storage tank, a plurality of driving shafts, respective to the said air compressors, a plurality of gears mounted upon them, said gears being meshed with geared racks that control, from the terminals of respective piston connecting rods, reciprocating strokes of outer and inner pistons in the air compressors, by reciprocating rotations of the said driving shafts, and means for coordinating the said plurality of air compressors in a timing adjustment designed for the system, by extension of each of the said driving shafts, to the next compressor to operate, having a gear mounted thereon meshed with a geared rack adjoined to a valve sleeve in the last mentioned compressor, effecting, thereby, reciprocating movements of the said valve sleeve, in unison with the movements of the outer pistons in the first v mentioned, or preceding, compressor.

3. In a system of the class described, a doubleacting compressor, comprising the combination of an outer cylinder having ports in the wall thereof, a valve sleeve reciprocable in the said wall and having ports in the wall thereof to coincide with the first mentioned ports, and a spider rigidly aflixed within its central portion for alternately seating and unseating central valves in the ends of interchangeable compressing chambers during the reciprocation, thereby converting the interchangeable compressing chambers to alternately operate as an outer piston and loading chamber, and as a discharge chamber, respectively.

4. In a double-acting compressor of the class described, a valve sleeve reciprocable within an outer cylinder, having a plurality of orifices in the wall thereof for the admission of air at normal and high pressures, adapted to coincide with a plurality of orifices in the said outer cylinder wall during its reciprocation, a large central port in the wall thereof, maintained in constant open registry with a central port in'the said outer cylinder during its reciprocation, to permit the constant passage of air at high pressure therefrom,

and a spider rigidly afiixedwithin the valve sleeve, adapted to move in unison therewith and effect reciprocating strokes of a plurality of central valves mounted upon a sleeve passing through the centre thereof. v s

5. In a system of the class described, a doubleacting compressor, comprising, .in combination, a sleeve, pistons and travel controls, and mechanism operatedby the motor for effecting the reciprocal movements of the pistons, and ofa valve sleeve, which, by a centrally located spider, therein, seats and unseats central valves, alternately, in the ends of interchangeable compressing chambers, converting the-interchangeable compressing chambers to alternately operate, respectively, as outer piston, with a dynamic force of compression bearing thereon, and as discharge chamber, with a statical force of compression bearing on an inner piston,th'erein through the open end of the discharge chamber from which the central valve has been unseated. 6. In a double-acting compressor of the class described, in combination a quadruple piston arrangement, consisting of two outer pistons, or interchangeable compressing chambers, joined together 'by rods, having a pluralityof ports in the wall thereof and reciprocating within a valve sleeve, and two inner pistons, mechanically connecte-d, and reciprocating within the so-called outer pistons, in the ends of which are formed central ports, in which, and from which, are -a1- ternately seated, and unseated, central valves mounted upon a hollow shaft passing through the centre of a spider rigidly affixed in, and reciprocating in unison with, the said valve sleeve.

7. A compressor of the class described, comprising the combination of an outercylinder having ports in the wall thereof, a valve sleeve rec'iprocable in the said wall, and having ports in the wall thereof to coincide with the first mentioned ports, a plurality of outer pistons attached together by rods, reciprocable in the sleeve, and having ports therein to periodically register with the ports in the outer cylinder, a plurality of inner pistons attached together mechanically and reciprocable in the outer pistons and adapted to draw air through the outer piston ports and compress it therein, means for operating the valve sleeve and pistons, and, a support for-.the.

pressures, a plurality of outer: pistons operatingwithin the said cylinder, having ports therein to correspond, during operation, with the orifices in said cylinder wall, and joined together by rods, a

plurality of inner pistons, mechanically connects, ed, operating within the said-outer pistons, and

having walls arranged to close off the ports of said outer pistons during the operation, and central ports formed in thesaid outer pistons for opening and closing passages within the said outer pistons, and controlling the passage of compressedfair thereethrough, and means for operating the outer and inner pistons in the said cylinder.

9. In a system of the class described, a compressor unit, comprising in combination, a cylinder with walls provided with ports, a valve sleeve reciprocable. in said cylinder and having ports tov periodically align with the ports in the cylinder wall during its reciprocation, a plurality of outer pistons, joined together by rods, reciprocable in the said sleeve, and having ports to'periodically coincide with those in the sleeve, a plurality of inner pistons, attached together mechanically, adapted to move in said outer pistonsya plurality: of central valves, adapted to operate periodically in unison with the motion of the sleeve, and open and close the passages of compressed air throughthe said outer pistons, and means for operating the said sleeve, central valves, and outer and inner pistons that cause the respective forces of compressed air exerted on the outer and inner pistons to be exercised on a common shaft in opposition.

10. In a double-acting compressor of the class described, incombination a plurality of central valves, mounted upon a sleeve passing through the centre of a spider, and adapted to be alternately seated and unseate-d in central ports formed in the ends of interchangeable compressingv chambers, or outerpistons, by reciprocating movements of the spider bearing on abutments upon the said sleeve, in coordination with a timing adjustment to suit the system.

11. In a system of the class described, a common shaft actuated by a motor reciprocally, through mechanical connections in sequence, and cam travel control, and, by gears fixed upon the common shaft, and meshed with geared racks, efiecting the reciprocal strokes of outer and inner pistons in a compressor unit by the common shaft so rotated-which is eXtendedto another compressor unit, and, by a'gear fixed upon it, and meshed with a geared rack adjoined to a valve sleeve "in the last mentioned compressor unit, effecting a movement of the Valve sleeve, its high and'low pressure intake port controls, and .a centrally located spider, therein, incidentally seating and un'seating central valves in so-called outer pistons. i

12."In' a compressor of the type described, a centrally located spider rigidly afiixed within a valve sleeve and adapted to bear, alternately, on abutments placed 'upon the sleeve of central valves passing through the centre thereof, effecting the reciprocal movement of the central valves in coordination with a timing adjustment to suit the system, thereby opening and closing passages through outer pistons, and creating a balance of the dynamic and statical forces of compression within the compressor bearing;respectively, on the outer piston with centre valve seated, and on the inner piston, through the open end of the so-called outer piston from which the centre valve has been unseated, thereby making it possible to operate, from the motor, a series of such compressor units, with opposing forces balanced in each unit.

' HOWARD MORGAN.

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