US1819285A - High speed compressor - Google Patents

Description

Aug. 18, 1931. w. FOURNESS 1 8 HIGH SPEED COMPRESSOR Filed Feb. 20, 19218 2 Sheets-Sheet 1 MAE fro Aug. 18, 1931. I w. FOURNESS ,3

HIGH SPEED COMPRESSOR Filed Feb. 20, 1928 V 2 Sheets-Sheet 2 (i/free 7 5 urn ass TToBn E 3 Patented Aug. 18, 1931 UNrrs SATES PATENT orrlcs WILFRED FOURNESS. OF OAKLAND. CALIFORNIA, ASSIGNOR TO THE FOURNESS DEVELOPMENT CORPORATION, OF NEJV YORK, N. Y., A CORPORATION OF NEW YORK HIGH SPEED COMPRESSOR Application filed February 20, 1928. Serial No. 255,759.

This invention relates to compressors, and particularly to high speed compressors of the reciprocatory piston type, adapted to compress a gas such as used in refrigerating systems.

' t is one of the objects of my invention to increase the efficiency of such compressors, and especially by so simplifying the moving parts that there is little loss by friction.

m It is another object of my invention to make it possible to control the various port openings in proper sequence both for intake and discharge by only a single moving valve that is driven by the same source of power as the compressing mechanism, whereby high speed operation at high efiiciency can be secured.

Spring pressed poppet valves controlling the discharge from the cylinder to a reserm voir where the compressed fluid is stored are now quite well known. The spring pressure can indeed be made so great that the fluid in the cylinders must be compressed to substantially the same value as the pressure in the reservoir before the valve opens. In

this way, the compressor works against full pressure only at the eiztreme end of its stroke, with an attendant saving in energy.

While such poppet valve arrangements are 3c ,v adapted for low speed operation, at high. speeds of say two thousand reciprocations or more per minute, the inertia effects of the valve parts hinder'its correct action. With. the aid of my invention, the same beneficial 35. effects as with poppet valves are obtained in high speed compressors by the aid of mechanically driven valves. Thus the compressor efiiciency is greatly improved; and in addition to the saving in energy, it is pos- 40. sible to utilize smaller mechanisms or fewer cylinders for the same output as with compressors of the prior art.

It is still another object of my invention to provide an effective liquid seal against leakage from the cylinder past the valve openings.

My invention possesses many other advantages, and has other objects which may be made more easily apparent from a consideration of one. embodiment of my invention.

For this purpose I have shown a form in the drawings accompanying and forming part of the present specification. I shall now proceed to describe this form in detail, which illustrates the general principles of my invention; but it is to be understood that this detailed description is not to be taken in a limiting sense, since the scope of my invention is best defined by the appended claims.

Referring to the drawings:

Figure 1 is a longitudinal sectional view of a high speed compressor embodying my invention;

Fig. 2 is a diagram for explaining the op- 65. eration of the valves and the pistons in the compressor shown in Fig. 1; y

Fig. 3 is a sectional view of a part of the compressor shown in Fig. 1, indicating a different phase in the movement of the valves .and pistons;

Fig. 4 is a diagram similar to Fig. 2, for explaining the position of the valves and pistons in Fig. 3; and

Fig. 5 is a detail section, taken along 75. plane 55 of Fig. 4.

In Fig- 1,. Ishow an assembly structure similar in many respects to that described and claimed in my prior application, Serial Number 61,372, filed October 8, 1925, and so entitled Compressors. It includes in general, a housing 11, upon one wall 12 of which is supported a hollow member 11 that has incorporated therein, a plurality of cylinders, and through which passes the shaft s5 13 that actuates the valves and pistons all as hereinafter described.

This housing 11 is arranged to serve as a reservoir or container for the compressed fluid which can be drawn off as desired through an outlet 1%. The inlet for the compressor is formed by passageway 15 in wall 12. This wall supports the member 11 which is closed at its opposite end by the flange or cover 16. The passageway 15 is continued around wall 12 so that it can be placed in communication with all the cylinder intake ports.

Thus in the present instance, the left hand end of shaft 13 is accommodated in bearing 10c 17 formed in the end of cover 16. This cover clamps tightly to member 11 to form a fluid tight compartment, in which the cylinders 22, 23 open at their inner ends. These cylinders in the present instances are diametrically displaced and there are only two of them.

Each cylinder bore 22, 23 extends inwardly radially of shaft 13, in which bores are slidable the pistons 24, 25. The rotation of shaft 13 causes the pistons to reciprocate, as by the aid of an eccentric 26 disposed in a block 27. This block and the pistons 24, 25 are dovetailed together to permit sliding between them, as indicated at 28; and it is evident that as the eccentric 26 revolves, the block 27 is constra' .ied by the pistons to move radially of the shaft 13. All this being explained in my prior application, requires no further detailing.

The cylinder bores 22, 23 have each a valve opening or bore 29 or 30 in which a valve piston 31 or 32 operates. These pistons are operated by mechanism similar to that used in connection with the main pistons 24:, 25, and includes the eccentric 33 and block 34-. The manner in which the valve stems 31 and 32 control the inlet and outlet ports forms an important part of my invention.

At the inner end or" each bore 22 and 23 there is a port 35 or 36 which serves both as an intake and as a discharge port. Port 35 communicates with the valve bore 29, and port 36 with valve bore 30. These valve bores at their outer ends connect to conduits 37 and 38 which conduct the discharged fluid into housing 11. These bores also communicate respectively with openings 39,

40 that lead to the intake passageway 15. The valves 31 and 32 are so arranged that as they are reciprocated in bores 29 and 30, they establish communication alternatively with the intake 15 through the apertures 39 40, and with the discharge conduits 37, 38.

Thus when valve 31 for example is drawn in radially to such an extent that its outer edge uncovers port 35, cylinder 22 is then in communication with the dischar e conduit 37 by way of bore 29 and port 30. The intake aperture 39 is covered by the valve 31 during this period. Now as valve 31 moves radially outward, it first covers port 35, hen its inner edge uncovers port 39, and finally port 35, so that these two ports are in communication through bore 29. The valves each have a reduced stem portion, such as 41 around which the fluid can pass when the valve 31 has passed opening 39 while movin outwardly. A guiding portion 42 is used to'assist in keeping the valve 31 alined.

It is to be noted particularly that valves 31, 32 move in the same direction to provide a change from intake to discharge connection of the cylinders 22, 23. For example, in Fig. 3 the valve 32 permits intake aperture 40 to be in communication with the cylinder port 36. An inward radial movement of this valve first covers port 36; then it covers aperture 40, and finally uncovers port 36 again and establishes communication from this port to the discharge conduit 38. Upon a reversal of the valve motion, the reverse actions take place: first port 36 is covered; then aperture 40 is uncovered, and finally port 36 is uncovered to reestablish connection between the intake aperture 40 and cylinder 23.

This port and valve action has been carefully analyzed as a preparatory to a detailed explanation of the phases of the compression cycle. As will be apparent hereinafter, this cycle is such that the compression the valve rapidly moves to intake position,-

so that there is little motion of the pistons before the pressure in the intake aperture 15 is effective to assist the piston in its suction stroke. In other words, there is little wasted energy in creating a suction in the cylinders before the intake is secured.

This not only increases the efliciency, but

also assists in maintainingthe mechanism smoothly operative, as no great or sudden pressure variations are produced in the cylinders.

To secure these beneficial results, the eccentrics 26, 33 or their equivalents are so arranged that the change from discharge condition to intake condition is accomplished quickly. Thus as shown in the diagram of Fig. 2, the piston eccentric 26 is in such position that piston 24 is ready to begin its suction stroke. 180 of movement, this piston moves downwardly, or out of cylinder 22. The valve eccentric 33 is in such angular position (about 135 behind eccentric 26) that the outward radial movement for the next 90 of the valve 31 is at the fastest rate, and theintake opening 39 will be rapidly uncovered. The cylinder 22 will then be connected to the intake aperture 39 soon after it begins the suction stroke.

In fact, this intake condition is illustrated for cylinder 23 in Figs. 3 and 4. In Fig. 3, it is seen that valve 32 has moved outwardly sufficiently to uncover port 36; this movement occurred in the 90 of move- During the next ment of eccentric 33 from position 43 to position 44. From this point, the next 45 of movement of eccentric 33 will continue to move valve 32 outwardly, but at a much slower rate. The condition after another 45 movement (that is 180 from the position of piston 24 in Fig. 1) can be explained from Fig. 1 in connection with cylinder 23. In this position, compression is ready to begin, piston 25 beginning its compression stroke, and valve 32 just closing the port 36 so as to permit the fluid in the cylinder to be compressed. Further rotation finally brings the piston 24 into the position of Fig. 3, in which the valve 31 is just about to uncover port 35 to discharge, and piston 24 has compressed the fluid to about that desired at the discharge. Further rotation of the eccentrics causes the fluid to discharge, and ultimately the cycle is ended,

the eccentrics being then in the position of Fig. 2.

By an inspection of Figs. 1 and 2, it will be noted that the length of valves 31 and 32 is so proportioned that the cylinder port 35 or 36 is covered just as soon as the piston 24 or 25 begins its suction stroke; and the port is again covered just as soon as the piston begins its compression stroke. It is thus evident that the valve functions to connect the cylinder to intake or dis charge depending upon which side of the cylinder port it happens to be.

The disclosure of the valve actions is now complete. There is no further explanation necessary, except to mention that piston rings such as 45 can be provided in the pistons and valves to maintain the passages fluid tight even at high pressure.

The outlet conduits 37 and 38 are so arranged that a liquid seal is provided for the valves therethrough, the discharge taking place through oil or other sealing liquid. For this purpose, an oil container 46 is provided, into the bottom on which lead the two outlet conduits. These conduits have bell mouths 47, so that the oil 48 in the container 46 will readily flow into the conduits when the valves are drawn inwardly. Sufflcient oil is provided to take care of the variations in the valve positions; and the conduits 37, 38 remain full with oil except when the compressed fluid passes through them. When the compressor delivers compressed fluid into housing 11, the fluid is forced through the oil seal, and after the discharge, the oil returns toseal the valve.

I preferably provide a pressure oiling system for all the parts, as by providing a conduit 50 that connects the end of journal bearing 17 with a body of oil 17 in the bottom of the casing 11. The pressure in this casing forces oil into hollow member 11 through oil passages 51, 52, 53 that connect with the bearing surfaces of the varia checkvalver '55 that permits egress of the gas into casing 11. 1

I (11311112 I I 1. In a compressor, a cylmderand piston,

means for causing reciprocatory movement between the cylinder and piston, and asliding valve operated by said means, said cylinder having a port opening in apassageway over which opening the valve'is arranged to slide, saidpassageway also communicating with a-discharge opening and an intake opening, said openings being so an ranged that. movement ofthe valve in onedirection serves successively to place the cylinder port in communication with one of said apertures while interrupting communication with the other, andthen on continued movement, communication with said one aperture is interrupted and communication with the other is established.

2. The combinationas set 'forth in claim 1, in which the valve and its actuating means are so constructed that the communication with-the'discharge aperture occurs at a point when the compression in the cylinder is sub-- stanti'ally' that desired to be obtained, and the communicationwith the intake aperture occurs at a' point near the beginning of the suction stroke.

3. The combination asset forth in claim 1, in which the cycle of ope-rationsof the valve actuation isabout 135 behind that of the piston and cylinder actuation.

4. In a compressonn cylinder and piston, means for causing reciprocatory movement between the cylinder and piston, and a sliding valve structure including a passage in which a piston valve works, said passage connecting with a port leading to the cylinder, and also communicating at one end with a discharge aperture, as well as with an intake aperture spaced from the discharge aperture, said piston valve covering the cylinder port during a part of its movement, and uncovering at another part of its movement both said port and the intake aperture while it blocks communication to the discharge aperture, and during another part of its movement, uncovering said port and covering the intake aperture, while it leaves said passage clear between the port and the discharge aperture.

5. The combination as set forth in claim 4, in which the valve mechanism is so constructed that the discharge from the port takes place only after considerable movement of the piston in the cylinder, and the of fluid to and from said compression creatintake aperture is opened near the end of, the compression stroke.

6. The combination as set forth in claim 4, in which the piston valve reciprocates in the passage and has its cycle about behind that of the main piston. V

7. In a compressor, a pair of relatively moving parts for creating compression, a valve mechanism for controlling the passage ing device, said mechanism operating to permit discharge of the compressed fluid through an aperture, and means providing a liquid seal for said aperture.

8. In a compressor, a pair of relatively moving parts for creating compression, a valve mechanism for controlling the passage of'fluid to and from said compression creating device, said mechanism operating to permit discharge of the compressed fluid through an aperture, and means providing a liquid seal for said aperture, comprising a liquid container, and a conduit having a distended opening in the bottom of said con-V tainer and connecting it with said aperture.

9. In a compressor, a pair of relatively moving parts. for creating compression, a valve mechanism for controlling the passage of fluid to and from said compression creating device, said mechanism operating to permit discharge of the compressed fluid through an aperture, and means providing a liquid seal for said aperture, comprising a liquid container and a conduit connecting into the bottom of-the container and in communication with said aperture, said conduit having an open end in the container that is conical, having its larger side forming the opening in the conduit.

1 testimony whereof I'have hereunto set my hand.

' WILFRED FOURNESS.

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