US1954002A - Fluid compressor - Google Patents

Description

April 10, 1934. c. M TURSKY l FLUID COMPRESSOR Filed June f5, 1935 April 10, 1934. c. M. TURSKY FLUID ACOMPRESSOR Filed June 5, 1953 3 Sheets-Sheet 2 April 10, 1934. c, M. TURSKY FLUID COMPRESSOR 5 sheets-sheet s Filed June 5, 1933 Patented Apr. 10, 1934 UNITED STATES PATENT OFFICE Thisinvention relates to apparatus of the generalcharacter claimed in my application Serial No. 655,880 filed February 9, 1933, wherein a pair of axially alined pistons are reciprocated in respective cylinders in a rotor in which the cylinders are held stationary; such reciprocation being effected by a stationary crank. However, my present invention involves a substantial reversal of that arrangement in that the pistons are held in stationary position in the rotor, whereas the cylinders are reciprocated with respect thereto by such crank. Moreover, in said copending application, the intake of fluid to the pistons is controlled by valves which are carried by the reciprocatory pistons but relatively movable therein, whereas, in the present invention, the flow of fluid to and from the cylinders is controlled by oscillation of a single body in which the two cylinders are formed, which body has fluid passages in its -surface for registry with vports in the rotor through which the fluid flows to and from the cylinders.

- Adjunctive advantageous features of my present invention include the provision of a single inclosing casing for both the compressor and the electric motor by which it is driven; a fan within that casing carried by the rotor for creating a forced draft through the casing to both supply the compressor with air for compression and to cool it; and the compressed uid is further cooled by being forced to traverse thin return bend conduits carried at the perimeter of the rotor and subjected to the air draft of the fan.

My invention includes various other novel features of yconstruction and arrangement hereinafter more definitely specified.

In said drawings, Fig. I is a" longitudinal verv tical sectional view of a convenient embodiment of my invention.

Fig. II is a longitudinal sectional view of the rotor indicated in Fig. I, but taken in a substantially horizontal plane.

Fig. III is an elevation of the annular band which is carried at the perimeter of the rotor, as shown in Fig. I, and provided with the return bend conduits for cooling the compressed fluid.

Fig. IV is a fragmentary' transverse sectional vView of 4saidbandand the adjacent port of the rotor with a portion of the outer casing which is concentric therewith.

Fig. Vis a transverse sectional view of the rotor taken on the line V, V, in Fig. 1I.

Fig. VI is an elevation of the left hand end of the compressor shown in Fig. I.

In said figures, the compressor is conveniently provided with the outerl casing formedl of the,

cylindrical tube 1 having opposite end plates 2 and 3 connected therewith by tap bolts 5 and 6, said plates 2 and 3 having feet 7 and 8 with holes for fastening means by which the compressor may be secured in stationary position.

Said plates 2 and 3 have axially alined bearings 10 and 11 and said bearing 10 holds the stationary axial shaft 12 which is secured therein conveniently by the nut 13 engaging the screw thread 14 on said shaft exterior to said bear- 65 ing 10.

As indicated in Fig. VI, said bearing 10 has suction and discharge ports 15 and 16 respectively at opposite sides thereof with which respective conduits 17 and 18 may be connected exterior to 70 said casing, to direct the iiow of uid to and from the latter. Said ports 15 and 16 are respectively in communication with the passageways 20 and 21 which are formed in coaxial relation with said stationary shaft 12 conveniently as indicated in Fig. I. Said passageways 20 and 21 are respectively provided with ports 22 and 23 extending transversely through the wall of said shaft 12 to the exterior thereof, as indicated in Fig. I.

The rotor 25 has the tubular shaft 26 journaled on said stationary shaft 12, as indicated in Fig. I, and has the shaft 27 at its opposite end in coaxial relation with said shaft 26 and journaled in the casing bearing 11, as shown in Fig. I.

As shown in Figs. II and V, said rotor 25 has a pair of axially spaced and alined pistons 29 and 30 xed at their outer ends at the perimeter of said rotor, conveniently by annular flanges 31 and 32 which are push tted in corresponding seats in said rotor from which they may, however, be withdrawn for repairs by screw devices then temporarily engaged with sockets 34 and 35 in said pistons. The cylinder 37, shown in Figs. I, II, and V, has recesses 38 and 39 at its opposite ends in coaxial relation, `fitted to said pistons 29 and 30, and has the crank bearing 40 intermediate of said recesses for thel crank 41 by which said cylinder is caused to reciprocate and oscillate upon. its axis in said rotor as a consequence of the rotation of the latter.

Said crank 41- has at its outer end the ball member 42 fitted in the ballsocket bearing 43` which is held stationary by the nut 45 on the 47 and 48 in said rotor, by oscillation of said cylinder; whereby rotation of said rotor effects reciprocation and oscillation of said cylinder 37 and controls the passage of fluid toand from said recesses 38 and 39 at the inner ends of said pistons 29 and 30.

Said fluid inlet passageway 20 in said stationary shaft 12 is in communication with said fluid inlet passageways 47 in the rotor, through the annular chamber 52, surrounding said shaft 12 within the rotor shaft 26, and the drilled holes 53, 54, and

55 in the rotor. Similarly, the fluid outlet passageway 21 in the stationary shaft 12 is in communication with the fluid outlet passageways 48 in said rotor 25 through the annular chamber 57 surrounding said shaft 12 and the drilled holes 58, 59, 60, and 61, shown at the lower part of Fig. I. Said holes 60 and 61 are connected by the return bend conduits 62. There are six of said conduits 62 arranged in a circular series at the perimeter of the rotor, as indicated in Figs. III and IV, and but two of the drilled openings 61, as indicated in Fig. V. However, said return bend conduits 62 are connected around the circumference of said rotor 25 by channels 64 extending spirally in the circumference of said rotor, as indicated in Fig. III. As indicated in Figs. I and IV, I find it convenient to mount said return bend conduits 62 in the annular band 65 which fits the circumference of said rotor 25 and is held upon the latter by the annular flanges 66 and 67 of the bearing members respectively carry- I ing the shafts 26 and 27 and which are rigidly connected with said rotor by cap screws 68 indicated in Figs. I and V. The effect of the arrangement above described is Lsuch that the compressed iluid discharged from the cylinder recesses 38 and 39 by the reciprocation of the cylinder is forced through the passageways 48 and drilled holes 61 and caused to traverse the entire circumference of the rotor through the channels 64 and return bend conduits 62 so as to be cooled by exchange of heat with the atmosphere around said rotor through the side walls of said return bends 62. Such cooling effect is enhanced by the disposition of said return bends 62 obliquely with respect to the axis of the rotor 25, as shown in Fig. III, so that they serve as fan blades to force the circulation of air through the compressor casing. Moreover, such circulation is augmented by providing said rotor 25 with the fan comprising the blades 70, shown in Fig. I, With the effect of minimizing the temperature of the compressor and the fluid compressed thereby.

Although said rotor 25 and its appurtenances may be rotated by any convenient means; I find it convenient to provide the rotor shaft 26 with the armature 71 in cooperative relation with the stationary field 72 which is conveniently-fixed in the casing 1, by bolts 74 and nuts 75 indicated in Fig. I. Said field 72 is conveniently energized by the electric coils 76 which are operatively connected with a source of current exterior to said casing by way of the cable 77 shown in Fig. I.

As indicated in Fig. I, I prefer to interpose the bronze bushing 78 between said stationary shaft 12 and the rotor shaft 26, said bushing being held stationary in the shaft 26 by the nut 79 and bearing axially upon the steel thrust washer 80 in said bearing 10. In order to compensate for wear and prevent endwise movement and consequent noise of said rotor, I also prefer to interpose the bronze bushing.81 between said stationary shaft 12 and said rotor shaft 26 with the spring 82 constantly stressing said bushing 81 toward the annular flange 46 on said shaft 12. Said spring extends in the sealing chamber 52 surrounding the joint between said shaft 12 and the rotary compressor shaft 26 and has at its opposite ends abutment washers 83 and abutment rings 84. Said rings 84 are ground to fit the contiguous surfaces of the bushings 78 and 81 and hold elastic packing material 84', whereby said joint is normally rendered airtight to prevent direct communication between said air inlet port 15 and air outlet port 16 around said stationary shaft l2. However, said chamber 52 serves as a by-pass from the outlet passageway 58 to the inlet passageway 53 for any compressed fluid which may leak past said seal, and thus accumulation of detrimental fluid pressures is prevented.

Moreover, I find it convenient'to lubricate said shafts and bushings by forming the oil chamber 85 in the bearing 10 on said casing which is maintained charged with oil 86 through the oil inlet 87 and to encircle said bushing 78 with the loose ring 88 which dips into said oil and causes it to flow through the oil inlets 89 in said bushing 78 to lubricate the surface of the latter which is in contact with said stationary shaft l2. The oil thus supplied to the surface of said stationary shaft l2 finds its way between said rings 84 and bushings 78 and 81 and into the annular grooves 90 in the bronze bushing 81 and thence through the oil hole 91, shown in Fig. I, to. the surface of the ball 42 which is gyrated in the stationary socket bearing 43, by the rotation of the rotor 25. The drilled hole 92 extending axially through said crank 41 is in communication with said oil hole 91 and with the oil chamber 93 in said rotor 25, as shown in Fig. I, and effects the delivery of oil to the surface of the cylinder 37 which oscillates and reciprocates in said rotor 25. The axial opening 94 in said rotor is merely an air vent for said chamber 93 to permit reciprocation of said crank 41 transversely to the axis of said cylinder 37, incident to the oscillation of the latter, without compressing the air in said chamber 93.

I also find it convenient to provide said bearing 11 with the oil chamber 95 charged with oil 96 through the oil inlet 97 and to encircle the bushing 98 with the loose ring 99 which dips into said oil and causes it to flow through the oil inlet 100 in said bushing 98 to lubricate the surface of the latter which is in contact with the rotor shaft 27.

In order to eliminate dust from the atmospheric air or other fluid which may b e compressed in the structure above described, I prefer to provide the compressor casing with screens 101 and 102 covering the openings in the opposite ends of said casings. Said screens are preferably made of wire cloth of a mesh much finer than indicated in the drawings. l

Said compressor operates as follows: The stationary field 72 being energized through the cable 77 shown in Fig. I, the armature 71 is rotated, carrying with it the tubular shaft 26 and rotor 25 with the effect of reciprocating the cylinder 37 with respect to the pistons 29 and 30 which are fixed in said rotor 25, as shown in Fig. 1I. Such reciprocation draws air alternately into the piston chambers which are recesses 38 and 39 in said cylinder 37, through the inlet conduit 17 and suction port v15 indicated in Fig. VI, passageway 20 and inlet port 22, shown at thel left hand end of Fig. I, and through the intake chamber 52, and drilled holes 53, 54, and 55 shown in the upper part of Fig. I. Such reciprocation also alternately expels the compressed air from said piston chambers through the drilled holes 61, return bend conduits 62, drilled holes 60, 59, and 58, shown at the lower portion of Fig. I, into the annular chamber 57 shown in Fig. I, and thence out through the port 23 and axial passageway 21 in the shaft 12 to the discharge port 16 indicated at the left hand end of Fig. VI, which port is in communication with the discharge conduit 18 shown at the left hand side of Fig. VI. As above noted, said return bends 62 and the fan blade 70 carried by said rotor 25 forcibly circulate the atmospheric air through the compressor casing screens 101 and 102 with the effect of cooling the armature coil 'l1 and field coil 72 and the return bends 62 so that the heat of compression of the air in said piston chambers is dissipated through said return bends 62 as the compressed air is on its Way to said discharge port 16.

However, I do not desire to limit myself tol the precise details of construction and arrangement herein set forth, as it is obvious that various modiiications may be made therein without departing from the essential features of my invention, as defined in the appended claims.

I claim: f

1. In a fluid compressor, the combination with a rotor; of a pair of axially spaced and alined pistons fixed at their outer ends at the perimeter of said rotor; a cylinder having recesses at its respectively opposite ends, in coaxial relation, fitted to said pistons and having a crank bearing intermediate of said recesses; said cylinder being mounted to reciprocate and oscillate upon its axis in said rotor; a crank fitted to said bearing and having at its outer end a ball member; a bearing fitted to said ball member having means to hold said bearing stationary; fluid inlet and outlet passageways in said rotor; fluid ports in said cylinder respectively in communication with the recesses therein and adapted to be alternately registered with said inlet and outlet passageways by oscillation of said cylinder; whereby,rotationof said rotor effects reciprocation and oscillation of said cylinder and controls the passage of fluid to and from said recesses at the inner ends of said pistons.

2. A structure as in claim 1, including a circular series of return bend conduits at the perimeter of said rotor in communication with the fluid passageways in said rotor; whereby rotation of said rotor is effective to cool the fluid during its traverse of said return bends by exchange of heat through the walls of said conduits to the atmosphere surrounding said rotor.

3. A structure as in claim 1, including a circular series of return bend conduits at the perimeter of said rotor in communication with the fluid passagewaysf in said rotor; each of said conduits being similarly inclined to the axis of said rotor to form fan blades; whereby rotation of said rotor forces the air to traverse the outer surface of said conduits and is effective to cool the uid during its traverse of said return bends by exchange of heat through the walls of said conduits to the atmosphere surrounding said rotor. l

4. In a fluid compressor, the combination with an outer casing having openings at each end for circulation of air therethrough and bearings at its opposite ends which are axially alined; of a shaft having means for holding it stationary in one of said bearings; a rotor having a tubular shaft at one end journaled on said stationary shaft, and having a shaft at its opposite end, in coaxial relation therewith, journaled in the other of said casing bearings; a pair of axially spaced and alined pistons extending in diametrical relation with said rotor and fixed at their outer ends at the perimeter of said rotor; a cylinder having recesses at its respectively opposite ends, in coaxial relation, iitted to said pistons and having a crank bearing intermediate of said recesses; said cylinder being mounted to reciprocate and oscillate upon said pistons; a crank fitted to said cylinder bearing and having at its outer end a ball member; a ball socket bearing fitted to said ball member; means for holding said socket bearing stationary on said stationary shaft; fluid inlet and outlet passageways in said rotor; fluid ports in said cylinder respectively in communication with the recesses therein and adapted to be alternately registered with said inlet and outlet passageways by oscillation of said cylinder; whereby, rotation of said rotor effects reciprocation -and oscillation of said cylinder and controls the passage of iluid to and from said recesses at the inner ends of said pistons.

5. A structure as in claim 4, having ud suction and discharge ports in said casing bearing which supports said stationary shaft, and having fluid passageways in said stationary shaft in coaxial relation in respective communication with said ports and with the passageways in said rotor.

6. A structure as in claim 4, including a cirof said rotor in communication with the fluid passageways in said rotor; each of said conduits being inclined to the axis of said rotor to form a fan blade; whereby rotation of said rotor forces the air in said casing to traverse the outer surface of said conduits and is effective to cool the fluid during its traverse of said return bends by exchange of heat through the walls of said conduits to the atmosphere surrounding said rotor.

CHARLES M. TURSKY.

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