US2470670A - Rotary expansible chamber pump - Google Patents

Description

May 17, 1949. A. H. WINKLER ET'AL 2,470,670

ROTARY EXPANSIBLE CHAMBER PUIIP Filed July 28, 1944 3 Sheets-Sheet 1 lNVE/WURS /J 4 ATTORNEY y 17, 9 A. H. WINKLER ETAL 2,470,670

ROTARY BXPANSIBLE CHAIBER PUIP Filed Jun} 28. 1944 a Shoots-Shoot 3 g/lf luvzumzs ALBERT hi MAI/n5? HEM/L 0. MRTH Arwms Patented May 17, 1949 UNITED STATES PATENT OFFICE 2,479,670 ROTARY EXPANSIBLE CHAMBER PUMP Albert II. Winkler and Emil 0. Wirth, South Bend, Ind., assignors to Bendix Aviation Corporation, South Bend, Ind-,1. corporation of Delaware Application July as, 1944, Serial No. 547,056

4 Claims. (email-154) This invention relates generally to pumps and more particularly to air pumps generally known as superchargers.

While the invention is shown and described as combustion engines have been heretofore pro-" posed, such superchargers being ordinarily of either the positive. type or the centrifugal type, both of which have inherent objectionable characteristics. The centrifugal type generally delivers large volumes and pressures at its rated speed and is more compact and lighter than the positive type, but will not deliver suilicient pressure at speeds below its rated speed. n the other hand in a positive type of supercharger the pressure curve characteristic is usually low at low speeds due to leakage. Moreover, mechanical limitations make this type impractical for operation at very high speeds, hence it is larger and heavier than the centrifugal type designed for specific deliveryconditions.

In internal combustion engines for motor vehicles, it is generally not necessary or desirable to continuously supercharge the engine because the amount of power normally developed by the engine will sufllce under ordinary operating conditions although in some installations for such vehicles the supercharging pump or blower is continuously driven by the engine and power which would otherwise be available for useful work is needlessly consumed. In order to avoid the needless consumption of power by the supercharger when supercharging of the engine is not necessary, it has been proposed to drive the supercharger through a variable speed coupling or transmission so that at such times as supercharging is not necessary, the supercharger may be operably disconnected from its source of power, 1. e. the engine. However, such coupling or transmission arrangements are relatively complicated and require complicated speed controls.

It is therefore, an object of the present invention to overcome the foregoing undesirable features of previous devices.

Another object of the invention is to provide a device of this character wherein said device is connected with the engine at all times but in which the discharge of fluid may be varied or adjusted as desired from zero to maximum, and

when adjusted so as to provide no discharge, but little power will be required to operate it.

As far as we are aware present variable displacement superchargers approach zero clearance volume at one given displacement per revolution setting so that at all other settings there is not a complete clearance or exhaustion of said chamber and a certain amount of compressed air is carried over and lost to use when the pumping member begins its intake stroke. Thus the pump efflciency is substantially lower.

It is therefore another object ofthe present invention to provide a variable displacement pump wherein the pumping member will, in the course of its cycle, approach zero clearance volume before opening the breathing compartment to the inlet port at all the various displacement settings so that there is substantially a complete clearance or exhaustion of said chamber at the end of each discharge cycle and there is substantially no carryover of fluid, compressed or otherwise. Thus the overall operating emciency of the device is extremely high.

It is a further object of the invention to provide a device of this character wherein under various operating conditions the adiabatic type of coinression is secured.

Other features of the invention reside in the provision of pumping members pivoted on a rotatable support or rotor within the pump casing or stator, the pumping members being actuated so as to draw fluid in and discharge it from the stator. The pumping members are connected to an anchor which rotates at the same speed as the rotor, the axis of said anchor being shiftable relative to the axis of said rotor and the distance the axis of the anchor is spaced from the axis of the support determines the extent of the movement or stroke of the pumping members. When the axis of the anchor is coincident with the axis of the rotor, the pumping members have substantially no effective stroke and the further the axis of the anchor is moved from the rotor axis the greater will be the strike of the pumping members.

The characteristics and advantages of the invention are further sufiiciently referred to in connection with the following detailed description of the accompanying drawings, which represent a preferred embodiment thereof. After considering these examples, skilled persons will understand that many variations may be made therein without departing from the principles disclosed; and we contemplate the employment of any structures, arrangements, or modes of operation that are properly appended claims. a

In the drawings:

Figure 1 is a vertical schematic section taken on line I -I of Figure 3 with the device adjusted for zero discharge;

Figure 2 is a similar view with the device adjusted for substantially maximum output;

Figure 3 is a section taken on line 3--3 of Fi ure 1;

Figure 4 is a view of the rear of the device; and

Figure 5 is a diagrammatic view showing the gear arrangement.

Referring to the drawings, the invention is illustrated as including a stator or casing, indicated generally at I0, having an inlet I2 and an outlet I4. If desired an air filter, not shown, may be attached to the inlet. The outlet is provided with a flange I6 for attachment to the inlet of a carburetor, indicated generally at I8, or to any other device to be provided with fluid under pump pressure. While the device is shown as being attached to the carburetor inlet it is to be understood that it may be interor posed between the carburetor and the intake manifold of the engine or otherwise, or if the pump is to be used for other purposes it may be connected with the fluid line in any manner which will produce the desired results. The casing or stator includes oppositely disposed arcuate portions 20 forming cylindrical wall portions of a chamber 22 within which is a rotatable disc or rotor 24. The rotor 24 is provided with an annular flange 26 extending outwardly thereof with respect to the chamber 22'. The flange 26 is mounted on bearings 28 supported by an annular flange 30 integral with, and extending laterally of, a plate 32 which is secured by screws 34 to an annular extension 36 of the casing or stator I0. The extension 36 and plate 32- provides an enclosure which is divided by the flange 30 into chambers 38 and 40. The rotor 24 is provided with a large central opening 42 about which is a flange 44 which extends into the chamber 40 and to the free end of which a ring gear 46 is secured by screws 48. The ring gear 461s provided with external teeth which mesh with a gear 50 rotatable on a reduced end portion 52 of a shaft 54 in chamber 40, said shaft 54 being fixed to a portion 56 of the plate 32 by means of a nut 58 on a threaded reduced diameter portion 60 of said shaft 54. Bearings 62 may be provided between the gear 50 and the portion 52 for reducing the friction between these parts and the bearings may be secured in position by any suitable means such as a nut 64 at one end of portion 52 and a Washer 53 at the other end of said portion bearing against the adjacent shoulder of shaft 54. If desired, a sleever 55 may be provided between the bearings to space same apart. A member is pivoted on the shaft 54 and ,the free end of said member I0 is adapted to rotatably support a shaft I2. said shaft being rotatable in bearings I4 received in a bore I6 of said member 10. The bearings 14 are spaced apart by a sleeve I8 which may be press fitted into the bore 16 or otherwise secured therein. Any suitable means may be provided for preventing longitudinal displacement of the shaft 12. As shown, said means comprises a nut 80 on a reduced threaded end portion 82 of shaft 12, there being a washer 84 interposed between said nut. and a shoulder of shaft 12 against within the scope of the 4 which said washer abuts. The opposite end of the shaft I2 is enlarged as at 86 thus providing a bearing retaining shoulder adjacent the inner bearing I4. A gear is secured by a pin 82 to an enlarged portion 86 of shaft 12 and is meshed with the gear 60, the gear 80 bein of substantially the same size as gear 46 and is provided with the same number of teeth so that both gears will rotate at the same speed, the purpose of this arrangement being hereinafter described.

An enlarged end portion 84 of shaft 12 extends through the opening 42 in the rotor 24 and into the chamber 22 of the stator. as best shown in Figure 3. The portion 84 of the shaft is provided with a threaded, reduced, diameter portion 96 on which is disposed an anchor plate or disc 88 held in position by a nut I00 screwed onto the reduced diameter portion 96 there bein a shoulder on the portion 94 of the shaft 12 against which the plate 98 is held by the nut I00. A plurality of connecting rods I02 are pivotally connected at I04 to the anchor plate 98 and extend tangentially of said plate, the outer ends of said rods I02 being pivotally connected at I06 to respective pumping members I08. The pumping members I08 are arcuate in shape and the respective pumping members are pivoted adjacent one end, as indicated at IIO, to the rotor 24. The curvature of the outer faces of members I08 is the same as that of the periphery of the rotor 24 and said members are circumferentially spaced apart, there being contoured partitions H2 secured to the rotor 24 and spaced circumferentially apart relative to said rotor and extending longitudinally in the chamber 22. The pivoted ends of the pumping members I08 include a curved portion adapted to closely fit into similarly curved notches I I4 of the partitions I I2. The faces II6 of the partitions adjacent the free ends of the members I08 are curved on an arc parallel to the are described by the said free ends of the members I08, said faces II6 being closely adjacent to the free ends of said members I08. It is to be understood, of course, that the various parts of the device are fitted closely enough to effect proper functioning without undue losses.

The device is adapted to be operated by means of a shaft I20 rotatable on bearings I22 in a bearing support I24 formed integral with plate 32 and extending into chamber 38. The shaft I20 carries a pulley I26 which is secured thereto by any suitable means, there being a belt I28 which provides an operating connection between the pulley I26 and flange 26, the shaft I20 being attached to any suitable rotating part of the engine or to any other suitable source of power, and rotation of the flange 26 effects rotation of the rotor and anchor plate 88, due to the arrangement of gears 46, 50 and 80. It is to be understood, of course, that other means for driving the device may be employed. For example, the gear 50 may be fixed to shaft 54 which may be rotatable and connected to a source 01' power.

Adjustment of the output of the device is infinitely variable between a minimum and a maximum value depending upon the relationship between the axis of the plate or disc 98 relativoj to the axis of the rotor. When said plate or disc and rotor are in coaxial relationship, as shown in Figure 1, the stroke of the pumping members is substantially zero and there is substantially no pumping of fluid by the device. However, when the axis of the plate or disc is offset the maximum amount permitted by struc- I tural limitations of the device the maxim stroke of the pumping members is obtained and results in maximum output. as will be more fully described hereinafter.

The adjustment between minimum to maximum stroke and output is infinitely variable and is effected, in the arrangement as shown, by a lever III secured to the member I! by means of screws I32. If desired, means for retaining the lever III in various positions of adjustment may be provided. which means may comprise a friction device indicated generally at I which includes a body portion Ill having a reduced diameter portion Ill received through an opening in the lever Ill and secured therein by a nut Ill. The end of the body I adjacent the plate 32 is spaced from said plate and is provided with an axial opening in which a plunger M is slidably received. The outer end of the Plunger is adapted to frictionally engage an arcuate boss I42, integral with the plate 32, and said plunger is provided with a head I against which a spring I reacts to urge the plunger against said boss I. The end of the spring opposite the head I42 reacts against the adjacent end of an adjustment screw I whereby the tension'of said spring may be varied.

Should it be desired to control the device from a remote point, lever I" may be connected with suitable manual or automatic control means, which connection may include a rod I49, and the means I" for retaining the lever. III in adjusted positions may or may not be used, depending upon the installation.

Referring now to Figure 1 wherein the device is shown as. adjusted for minimum, or zero stroke and output, gears I. and II are arranged coaxially. As the motor 24 and disc 80 rotate at the same speed and on a common axis, no pumping movement is imparted to the pumping members I", the outer surfaces of which are substantially concentric with the periphery of the rotor.

In Figure 2 the device is shown as being adiusted for maximum output, the axis of gear ll being offset relative to the axis of gear 48. Now, as the rotor 24 and the disc to rotate (the direction of rotationbeing indicated by arrows III) the respective pumping members III will be progressively swung inwardly on their intake stroke as they approach the inlet l2 and as the pumping chambers, indicated generally at I I2, coinmunicate with said inlet fluid will be drawn into said chambers; The respective pumping members reach their maximum inward movement as the respective chambers I52 pass out of communication with said inlet [2 so that said chambers are fully fllled with fluid. After the pumping members reach the end of their intake movement they begin to move outwardly for discharging fluid from the respective chambers I52 when the latter communicate with the outlet I4 and said pumping members and reach their outward limit of movement as the free ends thereof rotate past the outlet It. When the pumping members move outwardly air may be compressed in the chambers in at least until said chambers come into communication with the outlet M and it is to be noted that when the pumping members are at their outward limit of movement their outer surfaces are concentric with the periphery of the rotor.

While but two positions of stroke adjustment of the pumping members are shown the axis of the gear it may be swung to an infinite number of intermediate positions between the minimum and maximum positions for varying the output of the pump and it is to be noted that, regardless of the position of the axis of gear ll relative to the axis of the rotor, the outer surfaces of the pumping members, when at their outward limit of movement, are always substantially concentric with the periphery of the rotor. Thus there is a complete exhaustion of the respective pumping chambers at the end of each discharge stroke of the respective pumping members and therefore there is no carryover of air in said chambers and therefore no loss of emciency of the device from this source.

In Figure 5 the arrangement of the gears It, SI and It is shown diagrammatically. The axes A and B respectively of the gears 48 and 50 are spaced apart substantially the same distance as the axes B and C respectively of the gears II and 00 and the axis 0 of gear so is adapted to swing on an arc A--C the radius of which is equal to the combined radii of gears 50 and 80.

It is thought that the invention and many of its attendant advantages will be readily under- I central opening therein; means for mounting said rotor for rotation within the casing; a gear secured to the rotor and having a common axis therewith; inwardly extending circumferentially spaced partitions on the rotor; pumping members disposed between the partitions; means pivoting the respective pumping members adjacent one end thereof, the pivoted ends of said members being disposed adjacent respective partitions and the free ends of said members being adapted to swing on their respective axes through an are substantially parallel with one face of the respective partitions, the .pumping members and partitions being adapted to define pumping chambers; a shaft. extending into the casing through the opening in the rotor; a member in the casing secured to said shaft; means connecting the member with the respective pumping members; a gear secured to said shaft; means for rotating the gears at the same speed; and infinitely variable adjusting means for varying the position of the shaft from coaxial association relative to the rotor to an offset position relative to the axis of said rotor; the mechanism being so constructed and arranged that the pumping members may be moved inwardly in respect to the center of the rotor when adjacent the inlet and outwardly when adjacent the outlet.

2. In a rotary pump, a casing defining an annular chamber provided with intake and discharge ports, a rotor mounted in said chamber and having a series of annularly spaced partitions and movable pumping members coacting with said partitions, a shaft extending axially of the rotor, means connecting said shaft with said members, means for driving the rotor, and means 15 providing a driving connection between the rotorwav '1 and said shaft including a first gear connected to said rotor, a second gear connected to said shaft and being of the same eirective diameter as said first gear, a third gear meshing with said first and second gears, means mounting said third gear at a fixed radius with respect to said shaft, and

means for adjusting said shaft from a coaxial position with respect to said rotor to an oflset position relative to the axis of the rotor to thereby adjust the effective pumping stroke of said members.

3. In a rotary pump, a casing defining an annular rotor chamber provided with intake and discharge ports, a rotor mounted in said chamber and provided with a series of annularly spaced partitions and oscillatable pumping members coacting with said partitions, a shaft extending axially of the rotor, a means secured on said shaft and provided with a series of arms pivotaily connecting said means to said members, means for driving said rotor, and means providing a driving connection between said rotor and shaft including a first gear secured to said rotor, a second gear secured to said shaft and being of substantially. the same eflective diameter as said first gear, a third gear in mesh with said first and second gears, means mounting said third gear at a fixed radial position with respect to said shaft,

and means for adjusting said shaft and second gear arcuately about said third gear tothereby adjustv the position of the shaft from a coaxial minimum-capacity pumping position with respect to the said rotor to an offset maximum-capacity putlziping position with respect to the axis of said ro r.

4. The invention defined in claim 3 wherein said adjusting means includes a lever connected to said shaft and means are provided for frictionally maintaining said lever in a predetermined adjusted position.

ALBERT H. WINKLER. EMJL 0. WIRTH.

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

UNITED STATES PATENTS Number Name Date 1,516,053 Morgan Nov. 18, 1924 1,652,317 Morgan Dec. 13, 1927 2,362,541 De Lancey Nov. 14, 19-14 FOREIGN PATENTS Number Country Date 427,988 France June 10, 1911

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