US2212497A - Rotary pump or motor - Google Patents

Description

1940- v T. w. EDIXHOVEN 2,212,497

ROTARY PUMP 0R MOTOR Filed Oct. 21, 1938 2 Sheets-Sheet 2 won Hum Theodorus WL'alir/zoveu Patented Aug. 27, 1940 UNITED STATES PATENT oFF -cE 3 Claims.

This invention pertains to rotary pumps or motors such as disclosed in my British Patents 'No. 227,342, dated January 15, 1925, and No. 249,940

. of April 6, 1926. Pumps of the general type therein shown comprising a cover and a rotat ing piston working in a conical guide rotatably mounted in a hemispherical casing are well known to the art. Hersey, Patent No. 24,872 dated July 26, 1859, and Rider, Patent No. 45,636 dated December 2'7, 1864, disclose early pumps of this type.

Inherent defects and insufliciencie's have long been present in this type of pump due to frictional wear, leakage and other causes and it is the primary object of .the present invention to eliminate many of-the defects present heretofore in pumps of this type. T

It is another object of this invention to produce a pump of this, type with a greatly increased output whereby a relatively small pump may do the work which formerly required a much larger installation.

Another object of this invention is to improve the piston and cover of the pump to attain the above mentioned ends.

Another object of the present invention is. tb;

improve the structure of the suction and deliver ports of the pump to eliminate objectionable pump noise andto increase the pump output.

.Another object of the invention is to make the head free expanding to eliminate misaiigh ment of the pump when used to deliver hot fluids.

Other and further objects of the invention will become apparent as this specification proceeds.

Referring to the drawings: Fig. 1 is a vertical section of the shaft assembly;

pump and 40 plate illustrating the preferred method of mounting the piston on the plate and the plate to the shaft;

- Fig. 3 is a top plan of the improved pump showing the improved form of the suction and delivery ports of the pump; I

Fig. 4 is a vertical section view of the hemispherical head; and

Fig. 5 is an end plan of the hemispherical head showing the suction and delivery recesses wit the piston and sphere-conical guide member in position.

Referring to Fig. 1, l indicates a suitable base for the pump carrying suction and delivery ports 2 and 3 at its upper extremity. As indicated Fig. 2 is a plan of the improved piston aiiii in Fig. 3 suction and delivery ports 2 and l are suitably streamlined to reduce friction and pump noise. Mounted at one extremity of base I is support 4 carrying suitable bearings 5 in which rotates drive shaft 6 of the pump. Suitably 5 mounted at one extremity of shaft 6 is cover 1. Cover 1 may be of any suitable metal and is preferably cylindrically shaped and afllxed to shaft 8 in any suitable manner. As illustrated cover I iaafllxed to shaft 6 by suitable keys 8 and ex- 10 tends approximately one-half of the length of said shaft within said base., Base i is suitably recessed to receive cover I and carries suitable bearing 9 to provide a fluid-tight joint with cover I at its periphery. The center portion of cover I is preferably hemispherically recessed to receive spherical tightening boss iii of piston Ii. Tight ening boss III is preferably slotted as indicated to receive tongue l2 .of shaft 6 andis suitably flattened at one of its axes. It is preferably of a go radius equal to approximately the width of piston Ii. Piston II is set into projections 2i and 'on cover I (see Fig. 2) which carry set screws 22 and 23 registering with spherical boss I. to provide a fluid-tight adjustable joint between ,pis 25 ton Ii and cover 1. Piston ii is so mounted on cover I as to oscillate. 1 Piston ii is preferably semicircular.v in shape and of any suitable material. It is designed to make a fluid-tight joint with the interior wall of head l3. Head i3 is hemispherically recessed and the radius of piston II is equal tothe radius of this hemispherical recess. Head i3 is preferably hemispherical in shape and is suitably affixed to base i as by bolt l4 and projection 26. Base l is suitably recessed as indicated to receive head l3. Clamping screw l9 bears against head l3 whereby it may be adjusted on base I. Clamping screw I6 is carried by a suitable semicircular; bracket, which is preferably pivotally mounted at opposite sides of base I about head l3. A 'ertical section of a portion of this bracket is ilustrated in Fig. 1 of the drawings. It willbe noted that head I: is not rigidly afllxed to base 5 I. It is preferably aiilxed to be free expanding to eliminate danger of misalignment should the pump be utilized to deliver hot fluids.

Guide member I 5 is suitably rotatably mounted in head i3 as by stud l6. Guide member I! is 50 preferably sphero-conical in shape and of any suitable size and material. It is designed to make a. fluid-tight connection with the interior wall of head i3 and cover Guide I5 is preferably disposed at about a angle to shaft 5 head I3 and shaft 6.

6 and is suitably slotted to receive piston II. The interior extremity of guide I5 is suitably truncated to provide a fluid-tight joint with spherical tightening boss I0.

Suitable suction and delivery recesses I1 and I8 are provided in head I3 as indicated in Fig. 5. Suction and delivery recesses I1 and I8 are preferably disposed on opposite sides of guide I5 and are separated from each other by said guide. They are preferably sphere-triangular in shape and register with suction and delivery ducts 2 and 3 in base I.

Basel carries suitable thrust ring I9 for cover I and is provided with suitable packing glands 20 and gland clamp 2I which may be adjusted to prevent seepage of fluid about shaft 6.

In Fig. 2, 6 represents the drive shaft for the pump to which is suitably aflixed cover I as by keys 8. Tongue I2 of shaft 6 registers with a suitable slot in spherical tightening boss I of piston II. As illustrated screws 22 and 23 are mounted through suitable projections 24 and 25 of cover I into tightening boss III to provide a fluid-tight joint between piston II and cover I. Tightening boss I0 is shown suitably flattened at one of its axes to form fluid-tight joints with studs 24 and 25 of cover I. By adjustment of screws 22 and 23 piston Il may be tightened on cover 'I. Piston II is preferably so mounted on cover I as to oscillate on screws 22 and 23 as an axis.

In Fig. 3, I represents the pump base carrying A suitable streamlined configuration of suction port 2 and delivery port 3 is shown. With such a streamlining of the ports little obstruction is opposed to the passage of fluid through the pump with a resulting diminution of noise and Wear and with a corresponding increase in output.

Figs. 4 and 5 show respectively a side section and an end View of head I3. Fig. 4 shows suitable suction or delivery recess I I and auxiliary recess 21 designed to accommodate cylindrical stud I 6 of guide I5.

In Fig. 5, I3 represents the pump head containing suction recess I1 and delivery recess I8, positioned on opposite sides uf guide I 5 and separated thereby. These recesses are preferably spherotriangular in shape and preferably extend on each side of guide I5 from points near the vertical axis of head I3 to points approximately at its horizontal axis, as shown. Also illustrated is semicircular piston II shown in neutral position.

The improved pump functions as follows:

On rotation being imparted to shaft 6, from any suitable source of power, cover I and piston II commence to rotate. This rotation causes opening of suction recess I1 and closes delivery recess I8 from suction recess I'I. As the degree of rotation is increased piston II slides in guide I5 and takes on not only a rotative movement but also a sweeping movement. As rotation increases the suction area in the hemispherical recess'in head I3 enlarges more and more due to the slide of piston II in guide I5 until at point of 270 rotation piston II clears the delivery recess I8 and the fluid load of the hemispherical chamber is forced out through delivery port 3 in the last 90 of rotation. The cycle is then recommenced.

It must be borne in mind that at all times sphero-conical guide I5 makes fluid-tight connections with the interior wall of head I3 and with cover I. Guide I5, moreover, is so recessed at its apex asto form a fluid-tight connection with tightening boss I0. Furthermore, piston II, at all times bears in fluid-tight relation against the interior wall of head I3. As all these connections are fluid-tight the full pumping eflect is obtained by the ability of piston II to slide in guide I5'and the sweep generated by the combined rotation of piston II and its slide.

The higher efliciency of the improved pump is due in no small degree to the configuration of tightening boss I0 aind screws 22 and 23, which pass through studs 24 and 25 of cover I. In prior pumps of this type no allowance was made for wear with the result that the connections between piston and cover soon became worn, leakage started and the pump shortly went out of operation. With the present tightening boss, screw and stud arrangement, as soon as wear ocurs leakage can be forestalled by a proper adjustment of the tightening screws. Moreover, by utilization of the enlarged tightening boss a greater peripheral sweep is imparted to the fluid in the chamber greatly increasing the power of the pump. V

Another feature of the pump lies in the improved cover 1, as illustrated in Figs. 1 and 2. In former pumps of this type the covers comprised comparatively thin metal discs keyed or otherwise affixed at one end of the shaft and rotatable in shallow circular recesses in the base. Great difliculty was experienced with the old type of cover. After comparatively short use it became worn and misaligned due to vibration and shaft whip. This wear and misalignment resulted in leakage past the cover, in freezing of the pump and in general low performance of the installation. Moreover, due to the misalignment, pump fluid leaked into the shaft bearings and caused gumming and clogging of the bearings. Due to the vibration of the cover it was almost impossible to assure a fluid-tight joint between the conicai guide and the cover and between the piston and head of-the pump. As a result of this leakage the pump became practically unusable.

The present cover eliminates most of these faults. As will be seen in Figs. 1 and 2 the improved cover is cylindrical in form and extends about the shaft approximately one-half of its length in the pump base. The outer extremity of the cover is formed into a cylindrical extended shoulder I which bears against bearing 9 applied to the internal wall of the enlarged base recess. The cylindrical body of the cover I -is extended substantially along shaft 6 as shown and is suitably afiixed thereto as by keys 8. The extremity of cover 1 bears against thrust bearing I9 applied about the end of the enlarged base recess.

The improved bearing surface provided by shoulder I and by the cylindrical extension of the cover eflectively eliminates vibration of the cover. Thus leakage between the cover and base are eliminated and a fluid-tight joint between the various elements is insured. Moreover, with the free expanding and clamping head construction the pressure of the elements against the cover can be regulated and through this regulation the highest pump performance maybe procured.

Thus, with the new cover construction vibration, leakage and misalignment of the elements of the pump are eliminated and a performance is procured which was impossible with former pumps of this type. 1

With this cover it is not necessary to groove the face of the cover along one diameter to provide a recess for the base of the piston. The elimination of this recess and the provision of studs 24 and 25 adjacent the enlarged tightening boss I of the piston gives a completely stable combination of the elements and eliminates one of the main prior sources of leakage.

Hot fluids may be delivered by this pump with high efficiency due to the manner in which head I3 is aflixed to base I. In former pumps of this type the head was rigidly aflixed to the base at two or more points and the pump was not free expanding. As a result the pump was susceptible to misalignment and freezing due to the unequal expansion of its'parts if a hot fluid were passed through it. In the present pump head i3 is expansibly aflixed to base I by bolt l4, projection 26 and screw l6. As head l3 and base I are thus slidably linked together any expansion occurring within the pump body will be compensated for.

The streamlined configuration of suction and delivery ports 2 and 3 is another factor which contributes to the improved performance of this pump. By constructing these ports as shown in Fig. 3, the fluid entering and leaving the pump follows a smooth curve without striking obstructions. In this way vibration and pump noise are eliminated and output is greatly increased.

The pump is highly efficient. A pump made under these specifications with a cover three inches in diameter, driven at 400 R. P. M. by a l H. P. motor will deliver over three and one-half tons of fluid per hour. The same pump has flfteen feet of free suction and is capable of raising the fluid to a height of forty feet when valves are used.

Due to the improved enlarged tightening boss, friction and wear on the piston are greatly decreased due to the added bracing eifect imparted to the boss by the sphere-conical guide.

This pump is capable of pumping the more viscous fluids, molasses, honey, etc., and is extremely flexible. Regardless of the viscosity of the fluid delivered its output remains generally constant. For this reason a comparatively small unit can do work which formerly required a large and expensively powered installation.

This invention is susceptible of many adaptations andembodiments. If desired, it can be used as a source of motive power.

Nothing in this specification is intended to limit the scope of the invention; attention being had to the appended claims for this purpose.

What is claimed is:

1. In a rotary pump, a base, a shaft rotatably mounted in said base, a cylindrical shouldered, cover mounted about one end of said shaft and rotatable with said shaft in said base, the shouldered portion of said cover bearing in fluidtight relationship against suitable bearing means in said'base, tightening studs carried .by said cover, a hemispherical head mounted to be free expanding on said base, a sphere-conical slotted guide rotatably mounted in said head and bearing in fluid-tight relationship against said head and said cover, semi-triangular suction and delivery recesses in said head on opposite sides of said guide and separated thereby, said recesses being disposed in said head substantially from its vertical axis to its horizontal axis, a semi-circular piston mounted to oscillate on said cover bearing in fluid-tight relationship against said head and siidably mounted in the slot in said guide, said piston having a radially inner bearing base comprising a spherical tightening boss flattened at the extremities of one axis running at right angles to said shaft, said flattened portions of said boss bearing against the tightening studs on said cover and screw adjustable therebetween in said cover, and streamlined suction and delivery ports in said base arran ed to pass fluid through said pump in a smoo h curve and registering with said suction and de-- livery recesses.

2. In a rotary pump, a base, a shaft rotatably mounted in said base, a cylindrical cover mounted over one end of said shaft extending a substantial distance along said shaft and rotatable in said base, a pair of tightening studs carried by the inner face of said cover, a hemispherical head mounted for free expension on said base, a sphero-conical slotted guide rotatably mounted in said head at an angle of about 45 to said shaft and bearing in fluid-tight relationship against said head and said cover, sphero-triangular suction and discharge recesses in said head on opposite sides of said guide and separated thereby, said suction and discharge recesses extending about said guide substantially from the vertical axis of said head to its horizontal axis, streamlined suction and delivery ports in said base registering with said suction and delivery recesses and designed to pass fluid through said pump without obstruction, a semicircular piston mounted to oscillate on said cover bearing in fluid-tight relationship against said head and said cover and slidably mounted in the slot in said guide, said piston having a radially inner bearing base comprising a spherical tightening boss fitted between the tightening studs upon the face of said cover and screw-adjustable therebetween, said boss bearing in fluid-tight relationship against said guide.

3. A rotary pump comprising a base, a shaft rotatable in said base, a cylindrical shouldered cover aflixed about said shaft for rotation therewith, the shouldered portion thereof bearing against suitable bearing surfaces within said base and rotatable in said base, a substantially hemispherical head adjustably afllxed to said base, a hemispherical working chamber within said head, fluid inlet and outlet ports registering with said chamber, a slotted sphere-conical guide rotatably mounted in said head at an angle of about to said shaft separating said fluid inlet and outlet ports, a semicircular piston mounted to oscillate on said cover, bearingin fluid-tight relationship against the wall of said chamber and slidably mounted in the slot in said guide, and a spherical boss adjustably mounted in said cover and of a radius approximately equal to the radial width of said piston and comprising a bearing surface upon which said piston os-

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