US2681011A

US2681011A - Pump, compressor, and the like

Info

Publication number: US2681011A
Application number: US242925A
Authority: US
Inventors: Porte Eugene Frederic
Original assignee: Individual
Current assignee: Individual
Priority date: 1950-10-25
Filing date: 1951-08-21
Publication date: 1954-06-15
Anticipated expiration: 1971-06-15

Description

June 15, 1954 Filed Aug. 21 1951 E. F. FORTE PUMP, COMPRESSOR, AND THE LIKE 2 Sheets-Sheet 1 Eugn 1 In vex? far 6 Fndnc Parie June 15, 1954 l E. F. PORTE PUMP, COMPRESSOR, AND THE LIKE 2 Sheets-Sheet. 2

Filed Aug. 21 1951 FIG. 2

Patented June 15, 1954 UNITED STATES TENT OFFICE Claims priority, application France October 25, 1950 1 Claim.

The invention is for improvements in or relating to pumps, compressors and like rotative volumetric machines operating with a continuous circulation of fluid, that is to say, in which there is practically no pulsation.

The rotative machine according to the inven tion, which may be employed as a liquid pump, a compressor, a vacuum pump or a meter or for any other purpose, is characterised by the fact that it comprises in combination with a closed casing comprising admission and delivery ducts, and bearings or bearing surfaces for the rotative parts, the following elements:

(a) A rotor substantially in the form of a cylindrical drum subdivided into two compartments by a partition perpendicular to its axis and connected to a shaft mounted in bearings in the casing, the said rotor having on its periphery two radial blades secured in separate compartments and disposed at an angle of 180 with respect to one another;

(b) Two coaxial bosses of substantially cylindrical form, each situated in a separate compartment of the rotor and tangentiahy thereto along a common generatrix, the said bosses being so mounted as to be capable of turning about their geometrical axis, which is fixed in relation to the casing, and having on their periphery a slide- Way for engaging the corresponding blade, means being provided to ensure free orientation of the slideway and fluid-tightness between the rotor and each boss on either side of the corresponding blade;

A set of ports for affording, through the rim of the rotor, the admission and escape of the fluid into and from the chambers formed between the rotor and the bosses and to the rear and in front, respectively, of each blade with respect to' the direction of rotation of the rotor; and

(d) Finally, means for ensuring fluid-tightness between the fluid intake and delivery ducts.

The invention also concerns a volumetric pump having the aforesaid features and other advan tageous features arising out of a simple construction comprising a small number of parts, most of which are moulded and machined to afiord the necessary fluid-tightness between the various fixed and movable elements by means of an accurate fit between the surfaces in contact. Only two plastic packings, disposed on the shaft of the rotor in the immediate vicinity of the bearings of the said shaft, are employed.

One embodiment of the invention will now be described with reference to the drawings, this embodiment being referred to only by way of example.

In the drawings:

Figure 1 is a section taken through the axis of rotation of a pump according to the invention, along the line I-I of Figure 2,

Figure 2 is a section perpendicular to the axis of rotation, taken along the line l1-II of Figure 1.

The pump 2! comprises a rotor 22 having the form of a cylindrical drum sub-divided into two symmetrical parts by a partition 23 perpendicular to the axis thereof. A driving shaft 2 is keyed by means of a threaded portion co-aoting with a screwthread 25 in the partition 23 against which a collar 26 bears in a recess of similar form.

The closed casing of the pump 21 comprises two lateral parts 2'? and a centre part 28, the said parts bein bolted together as at 2t and 3E].

The shaft Ed is journalled in hearing in the casing, its free end being carried in a thrust bearing 3| comp-rising a ring of rollers 32 while the opposite side which extends through the casing is supported by a bearing 33 comprising a ring of balls 34. The

bearings

31 and 33 are secured by screws 35 to the parts 21 of the casing. 36 are packing rings disposed around the shaft 2% in recesses formed in the casing on the inner side of the bearings 3| and 33.

The parts 2'! of the casing comprise two cylindrical bearing surfaces 31 eccentric in relation to the orifice for the passage of the shaft 2 5. 38 are anti-friction bearing rings mounted on the said bearing surfaces 31. 39 are two cylindrical bosses bored along their axes to enable them to turn about the rings 38 without clearance.

The bosses 39 are fitted with precision against the partition 23 and at their radial periphery they are tangential to the inner cylindrical wall of the rotor 22 along a generatrix. Thus, there are formed on either side of the partition 23 two annular chambers, the cross-section of which has the form of a crescent, the points of which adjoin one another (see Figure 2).

The bosses 39 are maintained laterally on the outer side by an annular packing 40 which is in turn held in position by a threaded ring 45 screwed in a corresponding thread in the rotor 22. The rotor 22 is capable of turning freely between two neighbouring lateral faces of the parts 27 of the casing, the said neighbouring faces having formed therein two toroidal recesses 42 communicating through suitable cavities with a liquid admission duct 43 (Figure 2) The rotor 22 is provided internally with two radial blades 44 disposed on either side of the partition 23 and mounted at with respect to one another. The said blades 44 are connected to the rotor by any suitable means. They are shown as being fitted in grooves in the rotor 22, in the partition 23 thereof and in the packing ring 48.

A pin 45 slides on each of the blades 44 and each pin is arranged to rock freely in a cylindrical recess in the boss 39, the. said recess being coaxial with and, along a generatrix, tangent to the said boss. By virtue of this arrangement, the rotation of the rotor 22 produces the rotation of the bosses 39, the pin 45 sliding against the blade 44 while rocking freely in its recess in relation to the boss 39. The blade 44 is therefore surrounded or enclosed on its four sides.

48 is an annular centre chamber formed between the part 28 of the casing and the outer surface of the rotor. The chamber 46 communicates with the delivery duct 41 of the pump. On one side of each blade 44, rotor 22 is provided with an orifice 48 communicating with the corresponding admission chamber 42 and an orifice 39 communicating with the delivery chamber 45.

Two valves 58 are pivotally mounted in the chamber 56 on a pin i parallel to the shaft 24. The inner surface of these valves bears tightly against the outer surface of the rotor 22 under the action of springs 52. 54 are two metal packing rings consisting of two parts held between the part 28 and the parts 27 of the casing and lodged in two corresponding grooves in the rotor 22, thus preventing any leakage between the chamber 66 and the chambers 42.

Finally, a safety valve 53 is provided between the delivery duct 4! and the admission duct 43 for protection against excess pressure.

During operation, the pump turns in the direction indicated by the arrows. In Figure 2, the upper blade is shown at the commencement of its movement, and assuming a pressure head of liquid in the admission duct the space between the rotor 22 and the boss 39 connected to the said blade is filled with liquid through the corresponding orifice 58. The delivery orifice E9 is closed by the valve 59. The blade, in advancing, forces the liquid before it without delivering it until the orifice l8 situated behind the blade has passed beyond the line of contact between the rotor 22 and the boss 39. At this point, the liquid situated in front of the blade is retained in a closed space, whence it can escape only through the discharge orifice 49. The blade delivers liquid until the point at which it returns into its starting position. During this same revolution of the blade, the liquid has been drawn behind it through the orifice 4B and the same cycle recommences at each revolution. The operation of the blade 54, which is situated at an angle of 180 with respect to the first blade in its compartment (separated from the first compartment by the partition 23) is the same, but its delivery is at a maximum when the delivery of the first blade is a minimum. A continuou and practically constant delivery, i. e. without any appreciable pulsation, is thus obtained in the delivery duct. The pump described may in fact be rotated at high speed and the shaft 24 of the pump may be directly coupled with the shaft of an electric motor. A high-output motor-driven pump occupying a small amount of space is thus obtained, which is capable of delivery at high pressure. This result is essentially due to the fact that the blades are enclosed on their four sides, whereby all leakage is avoided between the compressed fluid and the fluid drawn in.

In order to facilitate the explanation of the operation, it has been assumed that on the inlet side of the pump there is a positive pressure head, but experiment has shown that a negative pressure of 720 mm. of mercury can be readily obtained on the suction side and a positive pressure higher than '7 kg. can be obtained on the delivery side,

It will be obvious that various modifications, improvements or additions may be made to the embodiment described. In particular, a rotative machine according to the invention could be provided for use as a compressor for gaseous fluid, with two compression stages, more especially by so arranging the partition of the rotor as to form two compartments of clearly different volume, the larger for the low pressure and the smaller receiving the compressed fluid at low pressure and compressing it to the final pressure, preferably after cooling. Naturally it would then be necessary to provide fixed fluid circulation ducts.

What I claim is:

A rotary machine with continuous circulation of fluid comprising, in combination, a casing, a cylindrical drum disposed in said casing, a partition perpendicular to the axis of said drum dividing said drum into two compartments having two lateral walls, a first blade in one of said compartments and a second blade in the other of said compartments, said blades being disposed at an angle of in relation to one another, admission orifices and discharge orifices in said drum on each side of said blades, an inner cylindrical body in each compartment tangential to the drum and having acavity therein, a cylindrical pin disposed in the cavity of each cylindrical body and tangential thereto, said pin being formed with a guide-way for receiving the inner edge of a blade, 2. drive shaft coaxial with the drum and secured to said partition, bearings in said casing supporting said drive shaft, a bearing coaxial with the cylindrical body for supporting said body around said drive shaft and permitting free rotation thereof, circular admission and discharge channels formed in said casing around said drum, said admission orifices and said discharge orifices communicating with said admission and discharge channels, respectively, check valves pivoted in said casing adapted to close the discharge orifices, resilient means holding said check valves against said drum, and packing means between said drum and said casing separating the admission and discharge channels.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 1,941,651 Behlmer Jan. 2, 1934 1,965,388 on; July 3, 1934 FOREIGN PATENTS Number Country Date 27,091 Netherlands Jan. 15, 1932