US2000271A - Variable delivery pump or motor - Google Patents

Description

May 7, 1935. E .K BENEDEK 2,000,271

VARIABLE DELIVERY PUMP 0R MOTOR i my May 7, 1935.. E. K. 4BENEDl-:K

VARIABLE DELIVERY PUMP on MOTOR FiledApril 25. 1932 4 Sheets-Sheet 2 J a, 39 s I J9 -Ja .fr/ a" 6*- 1 *I EITe/zede/E 53% v w, M@ 91 W76* May 7, 193s. E, k. BENEDEK 2,000,271

VARIABLE DELIVERY PUMP OR MOTOR Filed April 25, 1952 4 Sheets-Sheet :5I

May 7, 1935 E. K. BENEDEK 2,000,271

VARIABLE DELIVERY PUMP 0R MOTOR 'f Filed April 25, 1952 v 4 sheets-sheet 4 l y v/ l. v 69 l Emme/wm,

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`Patented May 7, 1'935 PATENT OFFICE 2,000,271 y VARIABLE DELIVERY PUMP on Moron Elek K. Benedek, Mount Gilead, Ohio, assignor to The Hydraulic Press Manufacturing Company, Mount Gilead, Ohio Application April 25, 1932, Serial No. 607,409

6 Claims.

This invention relates generally to rotary, multiple, radial piston pumps or motors of the type disclosed inmy copending application for patent Serial No. 564,404, filed September 22, 1931; and

primarily has for its object to provide certain structural improvements in and arrangements of the mechanisms employed in pumps or motors of the character stated, enabling the building of pumps or motors which are more compact, morev quiet and efficient in operation, more sturdy, and more readily assembled and disassembled than any like mechanisms of which I am at present aware.

In general terms, the invention comprises a l5 casing containing two rotors one Within the other,

the outer one being adjustable eccentrically relatively to the inner. one; cylinder and piston assemblies positively connecting these rotors for driving one from the other; means for systematically delivering pressure uid to and from said cylinders; a rigid unitary secondary rotor .or eccentric comprising a pair of complementary plates and segmental reaction blocks, the blocks being clamped tween the plates and positively positioned; balanced arrangement of bearings for said rotors; a construction, mounting and operation of cross head enabling automatic high pressure lubricant lm maintenance-and the method of forming and maintaining such a lm, a shifting ring construction adapted to damp vibration; the provision of primary load transmitting means and reaction surfaces always concentric to the axis of rotation of the secondary rotor; the cooperating pads or slides carried by theshifter ring and casing, respectively, and so disposed that any load imposed on the eccentric will be transmitted through the shifter ring to the casing; and other features and constructions which will appear from the following detailed description.

In order to more clearly disclose the construction, operation and use of the invention, ref- I erence should be had to the accompanying drawings forming part of the present application.

4 In the drawings:-

Figure 1 is a central horizontal section of a form of pump embodying my invention;

Figure 2 is a side elevation of a ring from which a plurality of perfectly aligning guide blocks have been formed by the making of equidistantly spaced radial cuts; r

Figure 3 is a vertical cross section taken through the plane of the pumping units of the pump .shown in Figure 1;

Figure 4 is a cross section taken on the line 4 4 on Figure 2;

Figure 5 is a central longitudinal section of a single guide block formed' as shown in Figure 2;

'Figure 6 is a detail cross section taken on the 5 line 6-6 on Figure 5;

Figure '7 is a View similar to Figure 1 illustrating a slightly modified form of the invention;

Figure 8`is a detail transverse section taken through the plane of the pumping units of the l0 cylinder barrel and eccentric shown in Figure 7, three of the piston and cross head units and two of the guide blocks being shown removed;

Figure 9 is a detail cross section taken on the line 9 9 of Figure '7; l5

Figure 10 is a detail sectional View illustrating an alternative form of piston and cross head unit;

Figure ll is a detail sectional view of the unit shown in FigureY 9, the section being taken in a plane normal to the plane of the section in Fig- 20 ure 9;

Figure l2 is a partial central horizontal section of a pump embodying a modified form of the invention;

Figure 13 is a detail cross section taken on the 25 line 12-12 on Figure 12; and

Figure 14 is a somewhat diagrammatic detail section illustrating the manner in which the cross head block is capable of shifting slightly during` operation. 30

In the practical development of my improved l pump, I provide a casing comprising a cylindrical shell or ring 5 which is equipped with a supporting base 6, upper and lower slide guide pads 1, and diametrically oppositely disposed hubs 8 35 apertured as shown to accommodate the usual eccentric or secondary rotor shifting rods. The usual drain port 9 may also be provided.

The casing shell is closed at its ends. by end casing plates I0 and II provided with centering 40 shoulders I2 and secured as at- I3 to the respective ends of the casing ring.

Each end. plate is provided with a recess I4 for receiving a ball race I5, and the plate I0 is equipped with a hub extension I6 in which the 45' enlarged head I'I of the valve pintle I8 is secured by employment of a key or other suitable equipment. The hub I6 includes the usual combined intake and exhaust ports I9 and 2l), each of which communicates with pintle cut-outs 2I, which cut- 50 outs in turn communicate with upper and lower pairsof combined inlet and outlet bores respectively designated 22 and 23. y

The portion of the pintle which projects into the pump chamber formed by the casing ring 5 55 and the end plates IU rand I I is provided with upnot by the rotor.

per and lower valve cut-outs respectively designated 24 and 25 through which the inlet and exhaust bore pairs 22 and l23 may communicate suitably with the cylinder bores formed in the cylinder barrel or primary rotor, to be referred to in detail hereinafter. The portion of the pintle remaining after the forming of and between the cut-outs 24 and 25 provides a pintle bridge 26 which serves a purpose well understood in the art. On reference to Fig. 1 it will be noticed that the primary rotor and connected drive shaft 28 are journaled in the end plates II] and II, and that the valve is coaxial with it but mounted independently of it. The valve is also mounted in the same end plate I0. It will be clear that the entire load imposed will be carried by the valve and This independent mounting with the valve sustaining the load, permits perfect hydraulic balance of the primary rotor and greatly reduces vibration and wear. It provides a simple, efficient, compact and durable construction free from serious friction and resulting overheating and freezing between valve and rotor. The casing end plate II is'provided with a bearing 21 for receiving the drive shaft section 28 which extends from the pump casing and to which power may be applied in any suitable manner. The portion of the drive shaft section pro.- jecting into the pump casing terminates in an abutment head 29, and the cylinder barrel or primary rotor 30 is axially bored to receive the extended end -of the drive shaft section which carries said abutment head. The rotor 39 is also counterbored as at 3I to` fit rotatably the portion of the pintle which projects into the pump casing, and in this manner an abutment shoulder 32 is formed against which the abutment head 29 is securely clamped by employment of a threaded clamp ring 33, as shown in Figure l of the drawings. The drive shaft section and the rotor 30 are also key connectedas at 34 for driving purposes.

The cylinder barrel or primary rotor 30 is in the nature of a long rigid hollow cylindrical body and is reduced at its ends to receive ball race rings 35 which cooperate with the previously described rings I5 and with ball bea-rings 36 interposed between said rings in the forming of anti-friction bearings for said rotor. In a plane disposed centrally between the bearing rings 35 and likewise disposed centrally between the casing plates I0 and II, the rotor 30 is provided with a plurality, ve being shown,` of equidistantly spaced radial cylinder bores l31 which communicate through ports 38 with the pintle cutouts 24 and 25.

A rigid single-piece shifter ring 39 is provided and is equipped with guide pads 40 for engaging the guide pads 1 of the casing, and suitable provision generally designated 4I for connection with ordinary shifter rods or other suitable mechanical shifting equipment not shown. The ring is annularly recessed at its ends as at 42 to receive shoulder rings 43 which may be secured in position by set screws or other equipment as indicated at 44. Each shoulder ring includes a keeper flange 45 and serves as a mounting for a ball race 46.

Ihe eccentric or secondary rotor surrounds the primary rotor, and in my improved pump construction comprises two plate-like half units in the nature of parallel opposed flat rings or fianges 41. These halves or flanges are equipped with opposed annular recesses 48 which are concentric to the axis of rotation of the secondary rotor.

The secondary rotor halves also include laterally extending flanges 49 likewise concentric with relation to the axis of rotation of the secondary rotor, and on which are mounted race rings 50 which, with the rings 46 previously described and interposed ball bearings 5I, provide anti-friction bearings for the secondary rotor within the shifter ring 39. It will be observed that the secondary rotor is centered on the plane of the primary rotor bores 31, and that the antifriction bearings for the secondary rotor are disposed equidistantly at each side of that central plane and within the anti-friction bearings for the primary rotor 30 previously described.

Between the eccentric or secondary rotor halves individual guide blocks 52 are' mounted, there being one guide block for each primary rotor cylinder bore, and the guide blocks are provided with arcuate ribs 53 which t the annular recesses 48 of the secondary rotor halves, tangentially disposed grooveways 54 forming reaction faces 55, and inwardly directed openings for permitting freedom of movement. of the pistons 56 reciprocable in the bores 31 of the primary rotorand which are connected with the secondary rotor by engagement of the integral plate cross heads 51 with which they are equipped in the grooveways 54 of the guide blocks.

As is well understood in this art, when the primary and secondary rotors are positioned as shown in Figure 3 of the drawings, with their axes of rotation coinciding, and power being applied through the drive shaft section 28, no reciprocation will be imparted to the pistons and cross heads. When the eccentric or secondary rotor is shifted so that its axis of rotation lies to one side or the other of the axis of the pintle, which is the axis of rotation of the primary rotor, the pistons 56 will be caused to reciprocate radially in their bores 31, and the plate-like cross heads 51 will reciprocate tangentially in the guide block grooveways 54, such piston reciprocation being occasioned by the relative movement of which the rotors partake because of their off center relation. 'I'he'degree of reciprocation will of course vary as the degree of separation of the axes of rotation of the respective rotors varies.

It will be observed that, by reason of the provision of the secondary rotor grooveways 48 and the guide, block ribs 53, both being in concentric relation with the axis of rotation of the secondary rotor, said ribs and grooves or recesses will afford primary reaction surfaces always concentric with the axis of rotation. of the secondary rotor. In order absolutely to assure this concentric relation of the ribs of all of the guide blocks, I prefer to include in the manufacture of these blocks the turning of a laterally shouldered ring somewhat as is disclosed in Figure 2 of the drawings, thus assuring perfectly coordinated reaction ribs and grooveways. After the ring has been thus formed'it may be severed by radial saw cuts as indicated in the said Figure 2 and thereafter provided with the additional grooveways and recesses which characterize the guide blocks.

The guide blocks are clamped between the secondary rotor plates or halves 41 by use of clamp screws or bolts 58 which pass through said flanges or halves 41 as illustrated in Figure l4 of the drawings. The screws 58 thus secure the secondary rotor halves and the guide blocks 52 together as a rigid rotor unit.

In the form of the disclosure in Figures 1 to form a'ball head 13 adaptedl to iit a semithrough 6, the guide blocks abut or directly engage the clamp screws 58 as indicated at 59, and thus the screws serve not only to clamp the guide blocks between the secondary rotor half flanges, but also positively to secure them against end play.

It will be observed by reference to Figure 1 of the drawings that the spaced relation of the secondary rotor half flanges 41 provides an annular space within which the guide blocks 52 are mounted and in which lubricant will be impounded constantly to engage and provide lm bearing for the reciprocating cross heads 51. In order to assure this impounding of lubricant, a retaining shell 60 surrounds the rotor flanges 41 and the guide blocks 52 clamped therebetween and V is secured as at 6I to said flanges.

lio

In Figures 7 and B of the drawings I have illustrated a slightly modied form of the invention, in which the general structural arrangement hereinbefore described is embodied and in which modified secondary rotor and cross head equipments are included. The previously described features will be remembered and need not be described again in detail. In this form of the invention secondary rotor half flanges 41 are clamped against interveningV equidistantly spaced spacer blocks 62 by screws63 which pass through said anges and the spacer blocks as indicated .in Figures 7 and 8. The guide blocks are similar to those previously described in that they include the cross head guide grooves 65 and arcuate ribs 66 for fitting the concentric recesses 48 of the rotor halves, but in this form of the invention said guide blocks terminate at their ends short of the spacer blocks, providing a clearance therebetween. as indicated in Figure 8. The pistons 56 are equipped with two-part cross heads, namely, a part`68 formed integrally with the piston bo'dy 56l and a part 68 freely slidable thereon, the engaging faces of the parts 68 and 59 being curved on an arc struck from the pintle axis. 'I'he reaction surface of the slidable element 69, like the reaction surface of the guide block it opposes, is perfectly at.

By reason of the provision of the clearance 61 at the ends of the guide blocks, the pump parts may be assembled and the guide blocks permitted to self-align, the clearances being suflicient to permit whatever slight movement/is necessary :for this purpose, after which the/guide' blocks may be positively secured by'employment of set screws 12 or other suitable equipment as indicated in Figures '7 and 8.

Naturally, a moving clearance is provided between the reaction face 1| of the cross head and the reaction face of the guide block which it opposes, and, during operation of the pump and the resultant tangential reciprocation of the cross heads, the part 69 'of each cross head will slide back and forth slightly yin the direction of reciprocation and on the curved surface 10, thu's causing the reaction face 1| of the cross head to tilt alternately with respect to the piston body 56 or the opposed flat reaction face of the guide block, and thus provide an alternating wedge shaped clearance between the reaction surfaces highly advantageous in providing a high pressure lubricant film bearing for the cross head, see Figures 8 and 14.

In Figures 10 and l1, I have disclosed an altert native piston and cross head construction in which the piston body proper is designated 56" and is equipped with an extended portion shaped spherical recess or socket 14 extending well up into the body ofthe cross head 15 and secured in the cross head by employment of a sectional threaded ring or other suitable equipment. Like the reaction face of the guide block which it vis designed to, oppose, the reaction face of the cross head 15 is perfectly flat, and it will be observed by reference to Figure 11 of4 the drawings that the cross head is longer at one end than at the other so as to unbalance the cross head and cause it to tilt during operation by reason ofthe action of centrifugal force, thus providing a wedge shaped clearance between the guide block and cross head reaction surfaces. 'Ihis equipment serves the purpose of building up a high pressure wedge shaped lm of lubricant between the otherwise contacting reaction surfaces. High pressure of they lubricant is attained and main- 'tained by centrifugal action ofthe high speed rotation of the'pumps and motors. The dynamical force of the cross heads is due to the rapid reciprocation tangentially. With the'high speed rotation'there is corresponding reciprocation but multiplied in proportion to the number of pistons. Consequently, as the cross heads, in their reciprocations, are driven against and through the centrifugally compressed lubricant, the movable member will be tipped away from the relatively stationary member to provide a wedge shaped opening between the two for a distance approximately that of the area of contact between the two. the direction of travel of the cross head, as will be understood. Consequently, lubricant, under high pressure instantly, forcefully fills the space. On the reverse movement of the reciprocation identically the same method applies, with the wedge openings 'forming at the opposite side of the cross head'. This method and the construc tion applying it completely eliminate all antifriction bearings and greatly reduce the size of parts at these points. It also entirely eliminates all oil duct and other similar lubricant supplying means. It is substantially infallible and continuous in operation and requires no attention or repairs.

Inthe form of the Ainvention disclosed in Figures 12 and 13 of the d1;aWings,.I have shown an additional modification of the invention, in which are employed two-part cross heads of the type disclosed in Figures 7 and 8 in combination with guide blocks of the clamp screw abutting type disclosed in Figures l and 3. In the disclosure of this modification of the invention, the pistons are designated 56"', the cross head parts 68 and 69'. the guide blocks 52', the tangential groove- Ways of the guide blocks 54', the screws by which the secondary rotor halves and the guide blocks are secured 58', the secondary rotor flange 41, and the concentric rib-receiving recesses or grooves therein 48". Since the individual parts cooperate in the exact manner hereinbefore described, the advantages of the specific elements mentioned in this new combination will be ob- The opening forms with the wide endv in vious, and it is thought to be urmecessary to recapitulate the detailed advantages of these parts.

From the foregoing description, taken in connection with the accompanying drawings, it is -able relatively during rotation, and radial piston and cylinder assemblies connecting the rotors and including crosshe'ads, said secondary rotor comprising half members having opposed grooves concentric with the axis of rotation of the secondary rotor, clamping means for clamping the halves together, and guide blocks clamped between the rotor halves and tangentially grooved to slidably receive the crossheads and having arcuate primary reaction shoulders engaging in the rotor half grooves, said clamping means comprising clamp screws positioned equidistantly about the secondary rotor axis one between each adjacent pair of blocks, and said blocks directly engaging said screws and being positively held against displacement by such engagement.

2. A pump or motor comprising a casing, ak

primary rotor within said casing, a secondary rotor within said casing, said secondary rotorcomprising complementary grooved plates, piston crosshead guide blocks arranged between said plates, clamping means disposed between said guide blocks, said blocks being clamped end to end against said clamping means, whereby the assembly of said blocks and said clamping means constitutes a complete continuous circle, pistonand-cylinder assemblies, crosshead means on said assemblies and engaging said guide blocks, and eccentric shifting 'means engaging and actuating said secondary rotor to predetermined positions. y

3. A pump or motor comprising a casing, a primary rotor within said casing, a secondary rotor within said casing, said secondary rotor comprising complementary grooved plates, piston crosshead guide blocks arranged between said plates, clamping means disposed between said .guide'blocks said blocks. being clamped end to end against said clamping means, whereby the assemblyof said blocks and said clamping means constitutes a complete continuous circle, pistonand-cylinder assemblies, and crosshead means on said assemblies and engaging said guide blocks.

4. In a pump ormotor, primary and secondary rotors rotatable about individual axes and movable relatively during rotation, piston-and-cylin der assemblies arranged therebetween', a plurality of segmental piston-actuating blocks engaging said assemblies, and means securing said blocks to said secondary rotor, said securing means extending between and abutting the ends of said blocks, whereby the assembly of said blocks and said securing means constitutes a complete continuous circle.

5. In a pump or motor, primary and secondary rotors rotatable about individual axes and movable relatively during rotation, piston-and-cylinder assemblies arranged therebetween, a plurality of segmental piston-actuating blocks engaging said assemblies, and means securing said blocksv to said secondary rotor, said securing means extending between and abutting the ends of said blocks, whereby the assembly of said blocks and said securing means constitutes a complete continuous circle, each block having a cut-away portion tangential to said circle and adapted for engagement by said assemblies.

6. In a pump or motor, 'primary and secondary rotors rotatable about individual axes, and piston-and-cylinder assemblies connecting the -rotors and including crosshead means, said secondary rotor comprising half members, clamping means for clamping the halves together, and guide blocks clamped between the rotor halves and adapted to be engaged by said crosshead means, said clamping means comprising clamp members positioned one between each adjacent pair of blocks, and said blocks directly engaging said members and being positively held against displacement by such engagement.

ELEK K. BENEDEK.

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