US2420426A - Compressor - Google Patents

Description

May 13, 1947.

H. W. HARRER COMPRESSOR Filed April 30, 1945 7 Sheets-Sheet 1 INKENTOR.

May 13, 1947. H. w. HARRER COMPRESSOR Filed April 30, 1945 7 Sheets-Sheet 2 INVEN TOR.

May 13, 1947. H. w. HAIQRER COMPRESSOR Filed April 30, 1945 7Sheets-Sheet 3 May 13, 1947.

H. w. HARRER COMPRESSOR Filed April 30, 1945 7 Sheets-Sheet 4 IN V EN TOR.

May 13, 1947. H. w. HARRER COMPRESSOR Filed April 30, 1945 7 Sheets-Sheet 5 IN V EN TOR.

May 13, 1947. H. w. HARRER COMPRESSOR Filed April 30, 1945 7 Sheets-Sheet 6 IN V EN TOR.

HITOF/VEVS'.

May 13, 1947. H. w. HARRER COMPRESSOR Filed April 30, 1945 '7 Sheets-Sheet 7 III iliiiib liilii;

IN VEN TOR.

Patented May 13, 1947 UNITED STATES PATENT OFFICE- COWRESSOR Herbert W. Harrer, New Washington, Ohio Application April 30, 1945, Serial No. 590,980

7 Claims.

The device forming the subject matter of this application is a compressor for fluids, preferably a1r.

One object of the invention is to provide a compressor having oppositely disposed power cylinders, the pistons whereof are connected in a novel way to the pistons of first stage compression cylinders and to the pistons of second stage compression cylinders.

Another object of the invention is to provide novel means whereby the exhaust from the internal combustion or power cylinders may be made efiective to heat air which is delivered into the said cylinders.

A further object of the invention is to supply novel means whereby air which is compressed on the back stroke of the first stage cylinders will be made effective to scavenge the products of combustion from the power cylinders.

Another object of the invention is to supply a novel impact wheel which is actuated by the escaping exhaust from the power cylinders, to carry certain parts of the machine over dead centers.

Other and further objects of the invention will be made manifest as the description proceeds.

A mechanic who abides by what is claimed may make changes in the precise structure shown, without departing from the spirit of the invention.

In the drawings:

Figure 1 shows in top plan, a compressor constructed in accordance with the invention;

Figure 2 is a side elevation;

Figure 3 is a vertical longitudinal section show ing approximately one-half of the compressor;

Figure 4 is a vertical longitudinal section showing the cooperating half of the compressor;

Figure 5 is a horizontal section taken through the casing approximately on the line 55 of Figure 3, the cylinders directly thereunder being shown in section;

Figure 6 is a vertical transverse section taken approximately on the line 6-6 of Figure 3;

Figure 7 is a vertical transverse section taken approximately on the line 'I'! of Figure 4;

Figure 8 is a horizontal sectional view showing certain of the cylinders'and attendant parts;

Figure 9 is a section on the line 9-9 of Figure 5, parts being omitted.

In carrying out the invention, there is provided a casing or support C, including an intermediate member embodying a shell I, having end Walls 2. The casing C comprises tapered end members 3 assembled with opposite ends of the shell I. There is a transverse partition 3 in each end member 3, and each end wall 2 likewise forms a partition. The casing C has detachable access plates 5, located as preferred.

Power cylinders 6 are secured to the end walls 2 and project into the intermediate member l-2 of the casing, the cylinders being open at their inner ends. The cylinders 6 are supplied with transverse exhaust ports 1 and with transverse scavenging ports 8. The scavenging ports 8 are located nearer to the open ends of the cylinders 8 than are the exhaust ports 1.

Power pistons 9 are mounted for reciprocation in the power cylinders 6 and are carried by rods it, secured to a first cross head I00.

First stage compression cylinders H are provided and are disposed in parallel relation, these cylinders extending between the partitions 2 and 4. Pistons l2 are mounted for reciprocation in the cylinders II and are carried by rods [4, which are secured to the cross head I65. Air is admitted to the spaces between the partitions 2 and 4 in any suitable way, for instance, through ports P in the end members 3. Air is admitted to the cylinders I I, ahead of the pistons l2, through outwardly closing check valves l5 (Figs. 3 and 8) carried by the cylinders, and located adjacent to the partitions t. For a purpose to be described hereinafter, air is admitted behind the pistons l2 through similar check valves 46, located in the cylinders, and shown in Fig. 8.

Second stage compression cylinders I! are secured to the partitions 4, within the casing parts 3, in axial alignment with the power cylinders 6. The heads of the first stage cylinders H, the partitions and the heads of the second stage cylinders I? have ducts l8, by which air can pass from the first stage cylinders to the second stage cylinders, check Valves I9 being located in the ducts and closing toward the first stage cylinders. The second stage cylinders I! are provided with outwardly opening check valve mechanisms 29 (Fig. 3) located near the partitions 4. From the check valve mechanisms 20, conduits 2| lead to a storage tank or the like (not shown).

In their outer ends, the cylinders I! are vented as shown at 22, to facilitate reciprocation of pistons 23 in the cylinders, the pistons being carried by rods 24, secured to the intermediate portions of second cross heads 25. Rods 26 external to the cylinders l! and 6, are secured terminally to the cross heads 25 and IE0, and reciprocate in the partitions 2 and 4, and in flanges 21 on the cylinders II, II and 6.

Oil, water or some other liquid is maintained at a predetermined level in the intermediate member of the casing C. The lowermost of the rods 26 (Figure 3) carries agitators 28, which operate on the liquid in the casing flinging it about, as said rods 26 reciprocate, a cooling and lubrication of the working parts thus being effected. If water is used for cooling, lubrication of the cylinders will have to be done by a system of mechanical lubricators not shown.

Housings 29 are fixed in the intermediate memher |-2 of the casing 0. Exhaust headers 30 (Figures 3 and 9) are in communication with the exhaust ports 1 of the power cylinders 6, and communicate with the housings 29. The housing 29 communicate, as shown at 3| in Figures 1 and 3, with receivers 32 mounted on the intermediate portion of the casing C, and having ex-" haust outlets 33. Within receiver 32 is located an air tank 34.

Shafts 35 (Figures 3 and 4) are journaled in the intermediate portion ofthe casing C and carry, within the housings 29, impact wheels 36, responsive to the exhaust passing through the housings. The impact wheels 36 comprise a small number of grouped blades 31. The blades may be altered in number but, in any event, they extend through a, limited are only, leaving a solid portion which is adapted to cover the exhaust ports, during the period of rotation.

Eccentrics 38' and 39 are secured to the shafts 35, externally of the housings 29. The eccentrics 38 and 39 carry wrist pins 40 whereunto are pivoted pitmans 4|, pivotally mounted on pins 42 mounted in the cross head I00.

The eccentrics 39 cooperate with the plungers 43 of fuel pumps 44, mounted on the walls 2 of the casing C. The sources of fuel supply for the pumps 44 are marked by the numeral 45; Conduits 46 lead from the pumps 44 to the power cylinders 6. By adjusting the length of the fuel pump stroke, the amount of fuel delivered is determined and metered.

The eccentrics 38 cooperate with the plungers 41 of air starting valves 43, mounted on the partitions 2. The tanks 34 are adapted to contain air under pressure, which is heated by'the exhaust which passes through the receivers 32. Conduits 49 lead from the tanks 34 to the air starting valves 48, and in the conduits 49 are interposed cut-off valves 59, under the control of an operator. Conduits lead from the air starting valves 48 to the power cylinders 6. The starting air works on the power piston that is expanding and at full stroke is shut off and then automatically changed to the other power pistons. This is timed and actuated by the eccentrics 38 and air starting valves 48. When motion of the unit has been attained by its own power the valve 59 is secured. During this starting and warming up period, the compression cylinders H and I! are vented to cause easier motion.

Air cylinders 52, shown in Figures 9 and 3, are

secured to the power cylinders Band are disposed transversely thereof, the scavenging ports 8 of the cylinders 6 being in communication with the air cylinders 52 shown in Figures 8 and 9. The cylinders 52 extend through theshell of the casing C, and include heads 53, wherein breather ports 54 are formed, the breather ports being in communication with the atmosphere external to the casin C, Pistons 55 are slidably mounted in the air cylinders 52 and are advanced by compression spring 56, interposed between pistons 55 and heads 53.

Transverse manifolds 51 (Figure 8) are mounted in the first stage compression cylinders H, in

close relation to the end walls 2 of the shell I, the" manifolds being open at their ends. The manifolds 51 have a branch 59 in communication with the cylinders 52. A check valve 61 is interposed in each branch 59, the check valve opening toward the cylinders 52. g

The pitmans 4| constitute means for imparting rotation to the eccentrics-38fand 39. The air starting valves 4'8 are operated by the eccentrics 38 on the shafts 35, since the plungers 41 of air starting valves 48 engage the eccentrics. The air in the tanks 34 is heated and expanded, since the exhaust produced when the power pistons are actuated by internal combustion, enters the receivers 32 by way of the connections 3| and leaves by way of the outlets 33. This air which is preheated, is more powerful than air of room temperature, and is discharged into the main supply tank for use. .The air comes in the tank only to be expanded by the exhaust heat, giving it more-power just before using.

The plungers 43 of the metering fuel pumps 44 cooperate with the eccentrics 39 on the shafts 35. The pumps 44 are put into operation, the pumps receiving fuel from the conduits 45, and passing the fuel by way of the conduits 46 to the power cylinders 6, through an injection valve into the highly compressed air in the cylinders, causing immediate" combustion and expansion on the Diesel principle which is automatic due to high cylinder pressure and the heat of the compressed air. However, an ignition system can be used.

The pistons |2 of Figs. 3 and 9, moving to the right, draw in air through the check valves l5, the air being supplied through the ports P or their equivalent. When the pistons |2 of Fig. 3 move to the left, under the influence of the pistons 9 of Figs. 3 and 4, air is forced past the check valves l9 into the cylinders I1. When the piston 23 of Fig. 3 moves to the right, along with the cross head I90, air is forced outwardly past the check valve 20 and through the outlet 2| to the place of storage for use.

Operation Referring to Figure 3, the reciprocating cross head Hi0- imparts rotation to the eccentrics 38' and 39 by way of the pitmans 4|, and to the shafts 35'. The shafts 35 rotate impact wheels 36.

As the piston 9 moves to the right in Figure 3, to make a power stroke, the piston uncovers the exhaust ports 1-. The exhaust passes through the headers 30 and enters-the housings 29. From the housings 29, the exhaust products pass through the connections 3| into the receivers 33, to heat the air tanks 34, the exhaust finding an exit through the outlets 33. With this movement of the piston 9 shown in Figure 3, the piston 9 at the opposite side of the cross heads I00, moves in its cylinder to cover the exhaust ports 1 of its cylinder, and move to compress a charge in its cylinder.

Referring to Figure 5, it will be seeri that the impact wheels 36 do not have a full set of blades 31, circumferentially considered. The centers of mass of the impact wheels 36 do not coincide with the axes of rotation of the shafts 35. Consequently, the impact wheels 36 act as aneccentric weight which aids in carrying the crank pins 40 over dead centers. These impact wheels act to direct the exhaust gases into the receivers 32 heating the air in the tanks 34 for distribution into the power cylinders.

Passing to Figure 8, when the pistons |2 make a compression stroke, air is drawn into the cylinders through the check valves I6. When the pistons l2 make a return stroke, air in the cylinders H is forced through the manifolds 5 1 and the branch 59, past the check valve 6|, into the cylinders 52. At that time, the pistons 9 have closed the scavenging ports 8, and the pistons 55 are forced to retire, under air pressure, compressing the springs 56. As' the piston 9 moves to the right in Figure 3, it uncovers the ports 8 in the cylinder 6, and the spring 56 advances the piston 55, air in the cylinder 52 is forced through the ports 8 into the cylinder 6, to clear it of burned gases, and the product leaves by way of the exhaust ports 1, leaving the cylinder 6 full of clean cool air.

The operation has been dealt with hereinbefore step by step, but by way of summary, the power pistons 9 of Figures 3 and 4 actuate the stagecompression pistons I2 and 23, and compressed air leaves the cylinders I! by way of the outlet conduits 2|. The cylinders 6 are scavenged by the mechanism shown in Figures 8 and 9. The eccentrics 38 and 39 cooperate, respectively, with the valves and pumps 48 and 44, and the valves and pumps, respectively, supply the cylinders 6 with air and with combustive fuel.

The manifolds 51, the branch 59, and the cylinders 52 constitute a conducting means leading from the spaces behind the compression pistons l2 to the scavenging ports 8.

What is claimed is:

1. In a compressor, an internal combustion power cylinder having a scavenging port, a power piston slidable in the power cylinder, a compression cylinder, a compression piston slidable in the compression cylinder, the compression cylinder having a check valve inlet and a check valve outlet located ahead of the compression piston, and having a check valve inlet disposed behind the compression piston, means for connectin the pistons for movement together, and a third cylinder communicating with the scavenging port, a conduit connection between the third cylinder and the space behind the compression piston, a check valve interposed in the conduit, a piston slidable in the third cylinder and retiring under pressure derived from the conduit connection, and yieldable means for advancing the last specified piston after it has retired, the power piston constituting a closure for the scavenging port during the retirement of the last specified piston.

2. In a compressor, a power cylinder having an exhaust port, a power piston slidable in the power cylinder, a compression cylinder, a compression piston slidable in the compression cylinder, means for connecting the pistons for movement together, said means including a cross head, a housing having an exhaust outlet, means for conducting exhaust from the exhaust port to the housing, an exhaust-actuated impact wheel supported for rotation in the housing, a valve, a conduit leading from the valve to the power cylinder, means for actuating the valve, said means comprising a rotary member connected to the impact wheel, and an operative connection between the cross head and the rotary member and including a wrist pin on the rotary member, the impact wheel comprising a segmental group of rotating blades, arranged throughout only a portion of the radius of the wheel, overbalancing the wheel, whereby the wheel is rotated, passing the wrist pin over dead centers.

3. A compressor constructed as set forth in claim 2, and wherein the valve is an air starting valve, and means for supplying air thereto for starting or setting the unit in motion by the pres-.

sure of the air from the starting tank through connections to said tank.

4. A compressor constructed as set forth in claim 2, and wherein the valve is a metering fuel pump, and means for supplying fuel thereto.

5. In a compressor, a power cylinder having an exhaust port, a power piston slidable in the power cylinder, a compression cylinder, a compression air starting valve to the power cylinder, means.

for supplying air to the air starting valve, a fuel pump, a conduit leading from the fuel pump to the power cylinder, means for supplying fuel to the fuel pump, an impact wheel in the housing and actuated by exhaust moving through the housing, eccentrics connected to the impact wheel to rotate therewith and constituting actuators for the pump, and valve and an operative connection between the cross head and the eccentrics, said connection including a wrist pin on one of the eccentrics, the impact wheel comprising a segmental group of blades constituting means for passing the wrist pin over dead centers.

6. In a compressor, a support, an internal combustion power cylinder carried by the support and having an exhaust port, a power piston slidable in the power cylinder, a compression cylinder carried by the support, a compression piston slidable in the compression cylinder, 3, connection between the pistons, a receiver having an outlet, means for conducting exhaust from the exhaust port to the receiver, an air tank in the receiver, means for conducting heated air from the tank to the power cylinder operating the piston therein, and means for supplying the power cylinder with fuel.

7. A compressor comprising oppositely disposed power cylinders, a first cross head located between the power cylinders, power pistons slidable in the power cylinders and connected to the first cross head, second stage compression cylinders located in a common longitudinal axis with the power cylinders and having outlets, second stage pistons slidable in the second stage cylinders, second cross heads located at the outer ends of the second stage cylinders and connected to the second stage pistons, connections between the first and second cross heads, a pair of first stage compression cylinders located between each power cylinder and the corresponding second stage cylinder and located at opposite sides of said axis, first stage pistons slidable in the first stage cylinders and connected to the first cross head, means for admitting fluid to the first stage cylinders, and check valve connections between each of the first stage cylinders and the corresponding second stage cylinder.

HERBERT W. HARRER.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 2,077,802 Martin Apr. 20, 1937 2,382,598 Andresen Aug. 14, 1945 2,038,442 Pescara Apr. 21, 1936 2,230,760 Pescara Feb. 4, 1941 2,241,957 Pescara May 13, 1941 FOREIGN PATENTS Number Country Date 698,563 France Nov. 24, 1931 Addition to Patent 39,764 770,023 France June 18, 1934 772,901 France Aug. 20, 1934

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