US3158035A

US3158035A - Multi-bank radial type machine

Info

Publication number: US3158035A
Application number: US55041A
Authority: US
Inventors: Biginelli Oreste Flavi Alfredo
Original assignee: Individual
Current assignee: Individual
Priority date: 1959-11-26
Filing date: 1960-09-09
Publication date: 1964-11-24
Anticipated expiration: 1981-11-24
Also published as: FR1241097A; BE594822A; GB969627A

Description

Nov. 24, 1964 o. F. A BI'GlNELLl MULTI-BANK RADIAL TYPE MACHINE Filed Sept 9, 1960 2 Sheets-Sheet 1 l P2 P3 P4 PI P3 R2 35 F F FF 50 54 33 1F F 50 1 h LJ F F u b b b 0 R2 0] b b b c 39 FIG. 6

Nov. 24, 1964 o. F. A. BIGINELLI MULTI-BANK RADIAL TYPE MACHINE 2 Sheets-Sheet 2 Filed Sept. 9, 1960 United States Patent 3,153,935 MUL'il-EANK FiAl'llAL TYPE MACHEQE Ureste Fiavio Alfredo Biglnelli, 22 Rare do Marechal Foch, @ierrnonhFerrand, France Filed Sept. 9, 196i), Ser. No. 55,041 priority, application France, Nov. 26, 195$,

8ll,342, Patent 1,241,097 2 Claims. (Cl. 74-459) Piston machines are already known, in which the pistons are actuated by an eccentric mounted on the shaft, the rotation movement of this shaft causing the rise and fall of the pistons by rotation of the eccentric.

In the case where the machine drives, the thrust of the pistons caused by the driving fiuid effects the rotation of the shaft by acting on the eccentric.

in these known machines such as pumps, the shaft is generally formed as a crankshaft, and comprises a cylindrical part off-centered in relation to the rotation axis. Roller bearings are mounted on this off-centered part. Their external cages control the clearance in the radial direction of the pistons of the pump.

in pumps of this type with a considerable delivery, We are obliged to arrange the cylinders and pistons radially in several planes parallel banks perpendicular to the axis of the shaft. The single eccentric device then has the disadvantage that the pistons on one side of the shaft, at the moment of the compression stage, have a component action of the same radial direction on the shaft, the pistons on the other side are at the intake stage and have a zero component action on the shaft. Thus, the bearings receive the whole of the load due to half the pistons.

The present invention has more particularly the object of effecting an improved arrangement of the pistons and shaft of a multi-cylinder bank, radial type piston machine, the pistons of the various cylinder banks being placed in opposition so that the reaction forces of the pistons and shaft divide up into two groups of equal power, but opposed.

The invention enables the reduction, to a great extent, of the reaction support of the shaft by these bearings, and hence, to ensure longer and more efficient service of the bearings, particularly in the case of intensive use.

The invention possesses the advantage of being adaptable to any radial type of multiple bank piston machine. The invention especially relates to a machine in which a simple and etlicient means of effecting the arrangement comprises roller bearings or ball bearings with an off-centered bore slipping on to the shaft with which they are rotatively integral, this arrangement affording an easy and speedy assembly of the. machine.

Another advantage of the invention is the rotational integralization of the bearings and shaft ensured by longitudinal fiutings or grooves of the shaft cooperating with complementary fiutings provided in the oil-centered internal rin of the bearings, enabling each bearing playing the part of eccentric to be fitted with any kind of orientation, without causing any difficulty in fitting. The grooves extend axially along a portion of a drive shaft and the bearin s having an inner bore with projections extending radially inwardly for driving the bearings from the shaft. Moreover, the bearings can be slipped on or off the shaft at one end as described hereinafter.

The arrangement and the radial type multi-cylinder bank piston machine or" the invention are shown, by way of example, in the particular application to a pump in the attached drawings, in which:

FIGURE 1 is a diagram showing the arrangement of the forces acting on the shaft and the reactions of support of the shaft in its bearings in the case of a single-eccentric pump.

3,15%,h35 Patented Nov. 24, 1964 FIGURES 2 and 3 show the arrangement of the forces acting on the shaft and the reactions of support of the shaft in its bearings according to two examples of application of the invention.

FIGURE 4 shows, in axial section, a pump in which the invention is incorporated.

FIGURE 5 shows a sectional elevation of the shaft and the arrangement of pistons around the eccentric.

FIGURE 6 shows an embodiment of the piston md its drive on the eccentric.

In the known single-eccentric pumps, we have stated that the bearings receive the whole of the load due to half of the pistons in their cylinders. In this case, the shaft St) is subected in the hypothesis of pistons of four cylinder banks to forces F separated by a distance [2 corresponding to the distance between the cylinder banks P P P P The reactions of support of the shaft 56 on the

bearings

33 and 34 are repsectively shown by the arrows R and R the distance between the bearing 33 and the force F of pistons of the first cylinder bank is denoted by a; the distance between the bearing 34 and the force F of pistons of the last cylinder bank is denoted by C. The total distance between the

bearings

33 and 34 is denoted by L.

In these conditions, the computation of the reactions on the bearings gives:

We see that the reactions on the bearings are very considerable.

To obviate this disadvantage, according to the invention, an individual eccentric is used for each cylinder bank for putting the pistons of one cylinder bank, for example, successively in opposition to the pistons of the other cylinder bank.

In these conditions, FIGURE 2 shows the arrangement of the forces acting on the shaft 5t? and the reactions of support of the shaft in its

bearings

33 and 34.

The forces F acting on the shaft 50 of these the pistonsof cylinders P and P are in opposition with the forces F acting on the shaft 50 due to the pistons of cylinder banks P and P 1 In these conditions, the computations of the reactions R' and R on the

bearings

33 and 34 give:

By considering that the value of the distance between the centers 0 and c is generally greater than that of the distance b, we see that the reactions R have values at the most equal to of the reactions R and R (the case of FIGURE 1).

It is also easy to see that the device according to diagram 1 involves a greater force exerted on the shaft to deflect it than in the device according to diagram 2.

Obviously, we can modify the arrangement of FIG. 2 without going outside of the scope of the invention for this purpose, by opposing the forces in pairs acting on the shaft into a multi-eccentric crankshaft reveals a fitting.

ditliculty if it is required to retain the simple device of roller bearings as intermediary for the transmission of the eccentric movement to the pistons.

The machine according to the invention eliminates the above-mentioned difiiculty by effecting an arrangement of the shaft and removable roller bearings controlling the pistons which enables various orientations of the eccentrics to be obtained from one cylinder bank to another, by means of a possible and easy fitting.

The principle of this device is as follows:

The shaft 54) of the machine does not comprise any eccentric, but a cylindrical part with longitudinal fiutings. The various roller bearings corresponding to each cylinder bank are fitted on to this part of the shaft. These bearings have an internal ring whose bore is off-centered and machined into complementary shapes for engaging the flutings on the shaft. The internal ring is thus keyed on to the shaft and in the rotation movement of the shaft acts as an eccentric. Each bearing can thus be fitted with any kind of orientation of the eccentric, without any fitting difiiculty arising therefrom.

In the machine, such as the pump shown in FIGURE 4, the pistons are arranged in four cylinder banks marked P P P P in accordance with the structure of FIGURE 2.

In each cylinder banks, eight cylinders and thin pistons are arranged radially around the shaft 50 spaced 45 from each other.

The pump is formed by a special cast-iron body 1 of general cylindrical shape with horizontal axis mounted on a stand 2, to which it is attached by bolts 3. The body is bored successively along its axis at 4 for receiving the side plate 5 supporting the bearing on the drive side, at 6 for housing eccentrics fitted on the shaft 50 and at 7 for receiving the roller bearing on the opposite side to the drive. A screw plug 8 closes the end of the bore and is provided for facilitating disassembly. Two

circular channels

9 and 10 are respectively reserved in the body at each end of the cylinder. The channel 9 acts as intake collector. The inlet nozzle 11 connected with the supply tank emerges in this collector. The channel 10 acts as delivery collector. The outlet nozzle 12 emerges in this collector. The four cylinder banks P P P P normal to the axis, are each formed by eight radial borings, such as 13, at angular intervals of 45 This radial arrangement coincides in the cylinder banks P P on the one hand, and in the cylinder banks P R, on the other.

For smoother running of the machine the pairs of cylinder banks can be staggered for n being the number of cylinders, i.e., for 2230 in the case of FIGURE 4 with eight cylinders and pistons in each of the cylinder banks P P and P P4 FIGURE 4 exactly shows an upper half-section staggered by 2230 in relation to the lower half-section. In each of the bores 13 cylindrical pistons such as 14 can slide radially thrust towards the axis of the pump by a spring 15, bearing, on the outer side, on a hollow plug 16 fitted with a ball air cock 17. FIGURE 6 shows, as an alternative, a piston 18 provided with a swivel head 19.

Each radial bore or cylinder 13 of the bank P is connected with the corresponding radial bore of the bank P by an aperture 20 drilled in the body normal to said bores of cylinders. This also applies to the radial bores of the cylinder banks P and P All these drillings emerge in the suction channel 9 and on this side are all fitted with suction valves 21. On the opposite side, these drillings emerge in the delivery channel 10 through a smaller diameter hole 22, which is provided with a delivery valve 23 at its end. Screw

plugs

24 and 25 respectively afford access to the suction and delivery valves.

The driving shaft 50 comprises a cylindrical part 26 for coupling with the motor and a smaller diameter part 27 having longitudinal flutings. On this part of the shaft 4.- (FIGURE 5) four roller bearings are slipped whose internal rings 23 are eccentrically bored and machined in this bore in the shape complementary to the flutings of the shaft 27. By this means these internal rings are keyed on to the shaft and communicate an eccentric movement to the external cages 29. The internal rings are successively fitted on in such manner that the eccentricity direction is in opposition alternately at from each other. They are kept in position on the shaft by looking, on one side, between the shoulder due to the difference in diameter of the

parts

26 and 27 of the shaft, and on the other, a ring 39 secured by the screw 31 and small plate 32.

The shaft 50 is carried by two tapered

roller bearings

33 and 34 mounted in opposition while forming plummetblocks. The bearing 33 is mounted in the bore 7 of the body. The other bearing 34 is mounted in a side plate 5 housed in the bore 4 of the body and comprising fixing members (screw 36) for adjustment (screw 37) and fluidtightness (ring 38).

The shaft unit 50 and eccentric bearings together are so fitted that a bearing is arranged in alignment with the pistons of each of the cylinder banks P P P and P4.

The machine thus made enables, in addition to the other advantages afforded by the invention, an easy and speedy assembly and disassembly of the control members formed by the shaft 50 and its bearings.

What I claim is:

1. In a machine having a plurality of cylinders and pistons reciprocable therein, said cylinders being arranged in separate planes, each plane having a plurality of cylinders arranged angularly disposed therein, the improvement which comprises means for reciprocably actuating said pistons and for balancing the reaction forces of said pistons, the last mentioned means comprising a driven shaft rotatably mounted, said shaft having a plurality of substantially linear, elongated, axially extending grooves disposed substantially parallel and angularly spaced in a circumferential direction thereon and terminating at one end of said shaft, a plurality of removable bearings having outer peripheral surfaces for reciprocably driving said pistons, said bearings having an inner bore having projections for complementary fitting into said grooves for rotatably driving said bearings with said shaft, said bearings being mountable on said shaft over said end of said shaft and slipped off therefrom, disposed in operation axially on said shaft with one bearing in each of said planes, said planes being disposed axially along said shaft, each passing through a respective bearing, said cylinders being further arranged and said bearings having their bores eccentric each in a direction for displacing the pistons radially in alternate ones of said planes in opposite directions to cause the reaction forces of one of said planes to compensate by opposite reaction forces generated in a next adjacent plane.

2. In a machine having a plurality of cylinders and pistons reciprocably therein, said cylinders being arranged in separate planes, each plane having a plurality of cylinders arranged angularly disposed therein, the improvement which comprises means for reciprocably actuating said pistons and for balancing the reaction forces of said pistons, the last mentioned means comprising a driven shaft rotatably mounted, said shaft havin a plurality of substantially linear, elongated, axially extending grooves disposed substantially parallel and angularly spaced in a circumferential direction thereon and terminating at one end of said shaft, a plurality of removable bearings having outer peripheral surfaces for reciprocably driving said pistons, said bearings having an inner bore having projections for complementary fitting into said grooves for rotatably driving said bearings with said shaft, said bearings being mountable on said shaft over said end of said shaft and slipped off therefrom, disposed in operation axially on said shaft with one bearing in each of said planes, said planes being disposed axially along said shaft, each passing through a respective bearing, said the pistons radially in one of two groups in opposite directions to cause the reaction forces of one of said groups of pistons to compensate by opposite reaction forces generated in the other of said groups of pistons.

References Cited by the Examiner UNITED STATES PATENTS 1,216,378 2/17 Thomas. 2,010,378 8/35 Sassen 10.3-174 2,050,578 8/36 Morreau 74-55 6 Warner.

Huber 74-50 Orshansky 103-174 Whittingharn 103-174 Irving 74-55 Widmer 74-49 Benedek 103-174 Navarro 103-174 Lane 103-174 Palmer 74-49 BROUGHTON G. DURHAM, Primary Examiner.

DON A. WAITE, Examiner.

Claims

1. IN A MACHINE HAVING A PLURALITY OF CYLINDERS AND PISTONS RECIPROCABLE THEREIN, SAID CYLINDERS BEING ARRANGED IN SEPERATE PLANES, EACH PLANE HAVING A PLURALITY OF CYLINDERS ARRANGED ANGULARLY DISPOSED THEREIN, THE IMPROVEMENT WHICH COMPRISES MEANS FOR RECIPROCABLY ACTUATING SAID PISTONS AND FOR BALANCING THE REACTION FORCES OF SAID PISTONS, THE LAST MENTIONED MEANS COMPRISING A DRIVEN SHAFT ROTATABLY MOUNTED, SAID SHAFT HAVING A PLURALITY OF SUBSTANTIALLY LINEAR, ELONGATED, AXIALLY EXTENDING GROOVES DISPOSED SUBSTANTIALLY PARALLEL AND ANGULARLY SPACED IN A CIRCUMFERENTIAL DIRECTION THEREON AND TERMINATING AT ONE END OF SAID SHAFT, A PLURALITY OF REMOVABLE BEARINGS HAVING OUTER PERIPHERAL SURFACES FOR RECIPROCABLY DRIVING SAID PISTONS, SAID BEARINGS HAVING AN INNER BORE HAVING PROJECTIONS FOR COMPLEMENTARY FITTING INTO SAID GROOVES FOR ROTATABLY DRIVING SAID BEARINGS WITH SAID SHAFT, SAID BEARINGS BEING MOUNTABLE ON SAID SHAFT OVER SAID END OF SAID SHAFT AND SLIPPED OFF THEREFROM, DISPOSED IN OPERATION AXIALLY ON SAID SHAFT WITH ONE BEARING IN EACH OF SAID PLANES, SAID PLANES BEING DISPOSED AXIALLY ALONG SAID SHAFT, EACH PASSING THROUGH A RESPECTIVE BEARING, SAID CYLINDERS BEING FURTHER ARRANGED AND SAID BEARINGS HAVING THEIR BORES ECCENTRIC EACH IN A DIRECTION FOR DISPLACING THE PISTONS RADIALLY IN ALTERNATE ONES OF SAID PLANES IN OPPOSITE DIRECTIONS TO CAUSE THE REACTION FORCES OF ONE OF SAID PLANES TO COMPENSATE BY OPPOSITE REACTION FORCES GENERATED IN A NEXT ADJACENT PLANE.