US3280747A - Distributor pump - Google Patents

Description

Oct. 25, 1966 ERICA s. MULLER-MEYER 3,230,747

DISTRIBUTOR PUMP Filed June 14, 1965 5 Sheets-Shet 1 O 1966 ERICA s. MULLER-MEYER 3,280,747

DISTRIBUTOR PUMP 3 Sheets-Sheet 2 Filed June 14, 1965 Oct. 25, 1966 ERICA s. MULLER-MEYER 3,230,747

. DISTRIBUTOR PUMP Filed June 14. 1965 5 Sheets-Sheet 5 United States Patent 3,280,747 DISTRIBUTOR PUMP Erica S. Muller-Meyer, Lugano, Switzerland, assignor to Louis Sarrazin, Nice, France Filed June 14, 1965, Ser. No. 463,512 Claims priority, application Switzerland, June 16, 1964, 7,818/ 64 6 Claims. (Cl. 103-2) The invention concerns a distributor pump, in particular for lubricating oil, with a pump casing having several outlets and a piston guided in a distributing member, the distributor being driven progressively by a rotary shaft fitted with a ratchet freewheel, the delivery strokes being forced upon the piston by a cam ring and the filling strokes by the cam-type heads of adjustable screws.

Distributor pumps of this type are already known. Com-pared to distributor pumps whose distributing member is driven uniformly, progressive drive has the advantage that with equal time of rotation, or equal delivery interval respectively, a multiplication of the piston speed and so a considerable increase of suction and discharge preformance is achieved.

The drawback of known pumps of this type was that step-by-step advance was not synchronized with the filling and delivery strokes of the piston. The consequence was that frequently an advance step of the ratchet wheel came to an end in the middle of a delivery stroke of the piston and that the discharge stroke was only completed after termination of the next advance step. This resulted in leakage losses at the piston and therefore unequa-l delivery quantities, which is undersirable.

The purpose of the invention is to eliminate these drawbacks.

The invention is characterized in that the number of teeth of the vfreewheel ratchet [forms an integral ratio with respect to the number of outlets in the pump casing with the object of adapting the advance steps of the ratchet freew'heel to the overlapping additions of the inlet and outlet ducts in such a way that each delivery stroke of the piston occurs during a single advance step of the ratchet freewheel.

In the accompanying drawing, one form of execution of the mechanical lubricating pump according to the invention is illustrated by way of example, where:

FIG. 1 shows an axial section through the lubricating p p;

FIG. 2 partly a view from above and on the upper left side a section on line 11-11 in FIG. 1;

FIG. 3 an axial section of the upper part of the pump on line III-III in FIG. 2, but with the distributor turned clockwise through about 20";

FIG. 4 a section of the lower part of the pump on line IVIV in FIG. 1, but with the driving shaft turned anticlockwise through 90;

FIG. 5 the same section as FIG. 4, but with the driving shaft turned anticlockwise through further 180";

FIG. 6 a diagram where, with reference to each other, are graphically represented, in the lower part the piston movement at A, /2, and full stroke, in the middle part the overlapping conditions of the control ducts, and in the upper part the intermittent movement imposed upon the distributor by the ratchet freewheel.

According to the drawing, in the upper pump casing or body 1 a ring 2 is fixed in which the distributor 3 can turn. At the upper part of the distributor '3 a slot 4 is provided in which a pin '5 is fitted transversely on which a tilting lever 6 can freely turn. In an axial bore of the distributor the piston 7 can move in which a slot 8 is provided with a fixed pin 9. A member 10 which can rock freely in the slots 4 and 8, and resting with its middle part of the piston 7 and sliding with its ends under 3,280,747 Patented Oct. 25, 1966 "ice a ring 11 fixed on the casing 1, serves as a means for producing the delivery stroke of the piston 7.

The ring is provided with an even number of cams arranged at equal distances. Above this ring 11 and separated from it by a slotted spacer 13, a ring '15 provided with set screws 16 is fixed. These set screws are used for adjusting the suction strokes of the piston. In order to render impossible the jamming of the outer arm of tle'ver 6 behind the set screws its freedom of upward movement is limited to the useful amount by a wire spring 17 surrounding the rotor in a circular groove. The shafts of the set screws 16 are provided with a slot 18 (FIG. 3) in which a wire spring 19 is inserted pressing with its outer legs against the female thread provided for the screw in ring 15, and according to the pretension of spring 19 opposes the rotation of the screw by tractive stress, thus precluding any unvoluntary displacement of the set screw.

In order to :facilitate the setting of the screw to a predetermined output the threaded bores in ring 15 are provided with an uneven number of grooves parallel to the axis with which the outer legs of the spring engage alternately, the result being double the number of engaging positions per screw revolution. The members 11, 14 and 15 are confined in the upper casing by means of a threaded ring 21, whereby the pins 22 and 23 ensure correct position of parts 11 and 15 with respect to the alternately grouped suction and discharge ducts.

The suction ducts 24 in the distributor seat 2 are directly connected to the oil tank by vertical bores 25, the annular channel 26 and the screwed connection 27 for a suction pipe. Seven of the eight discharge ducts 28 are attached to screwed connections 29, whilst the eighth which is situated above the suction duct 27 communicates with the internal space of the pump through a slot 30. The oil discharged on this point is used for self-lubrication of the pump mechanism. A single port at the outer end of a radial channel 31 in the tapered distributor sweeps over the suction and discharge ducts 24 and 28 and alternately connects them with the working chamber 32 of the pump. The bottom of said chamber is formed by a plug 33 fastened within the central through-hole of the distributor.

At its lower part the distributor ends in a shaft 3 turning within a downward extension of the upper casing. This extention comprises a frame-like part 1 forming a window 34 (FIGS. 4 and 5) for the mounting of a driving and reduction gear and ends in a tenon 1" which finds its target in an axial bore of the lower casing 35. A lateral flange of the lower casing serves as bearing for the driving shaft 36 whose free end is provided with a slot for accommodating a rotary driver. In axial direction the driving shaft is fixed by a stud bolt 38 engaging in a circular groove provided on the shaft. An excentric pivot 39 at the pump end of the latter by means of a vertically movable piston 40, initiates a horizontal reciprocal motion in a U-type rocker 41 which turns about the lower part 3' of the rotor. Between the parallel parts of rocker 41, a pin 42 fixes a ratchet wheel 43 to the distributor shaft and, swiveling on a pin 44, a pawl 45 is arrested and released by a preloaded annular coil spring 46 provided to slip with adequate friction on the lower part of ratchet wheel 43 and engaged with a loop 46' in a transverse slot in the lower part of pawl 45. A second coil spring 47 engages with an eye 47 in the radial slot 48 of ring 15 and from there closely encircles the rotor almost completely anticlockwise in a shallow annular groove. The oil discharges for internal lubrication into the upper casing by duct 30 rises to the horizontal shoulder of the rotor underneath ring 15, then through two symmetrically arranged vertical ducts 49 in the rotor, drains into the ring space 50 underneath the tapered part of the distributor and from here, through duct 51 in the bottom of the upper casing falls into the lower casing. Through cross holes 52 it enters the lower end of the rotor and from there it enters the hollow lower end of the rotor and from there, through an axial bore of the screw-plug 53 provided with an extension taking a transparent plastic tube, flows back into the tank. The method of working of the lubricating pump is a follows: Independent of its sense of rotation, by means of eccenter 39 and piston 40, driving shaft 34 imparts positively to rocker 41 a synchronous reciprocal movement. Out of the full cycle of this sinusoidal oscillation approximately one forth is transmitted to the rotor as follows. After completed rotor advance which according to the layout of the ratchet is always produced clockwise (see corresponding position in FIG. 4), the rotor stops while, by the reverse movelent of the rocker which now begins, the pawl 44 is swung anticlockwise around the rotor axis. Hereby the pawl is disengaged by the loop 46 of the still stationary coil spring 46 whose two arms encircle the shaft of the ratchet wheel 43. But as soon as the pawl finger bears against the crosspiece 41 of the rocker which serves as a stop, the spring is shifted on the ratchet wheel shaft for the rest of the swing by overcoming its frictional resistance. After the end of this phase of movement, rocker 41 begins its clockwise rotation. Hereby in the first instance the spring loop 46 engages the pawl 45 with the still motionless ratchet wheel and only after the gear has been interlocked the complete rocker and the rotor are jointly shifted for a tooth pitch into the end position shown in FIG. 4. This ratchet free-wheel known in similar execution is supplemented and improved by an additional freewheel gear which releases clockwise and blocks anticlockwise rotation of the distributor, thus ensuring that the latter neither by excessive friction of coil spring 46 on the ratchet wheel shaft nor by an increase of friction between the movable members of the ratchet gear, due to impurities or minor manufacturing discrepancies, can be put into an oscillating movement. In the example of execution this locking mechanism is formed by an annular coil spring 47, retained with an eye 47 in a radial slot of ring 15 and from there encircles the upper part of the rotor counterclockwise. It thus opposes the undesired movement of the rotor in this direction considerably by jamming, whilst clockwise it is expanded and exerts only an insignificant friction on to the rotor which in .this direction, in the locked position of the ratchet gear, is positively driven by the driving shaft. The same result could be achieved by an adequately arranged helical spring.

In its rotation, the distributor 3 carries along with it in the slot 4 the lever 6 and the member 10. The latter slides with its ends under the cam track of ring 11 fixed to the casing. Whenever member resting on the middle part of piston 7 is pressed downwards by two diametrically opposite cams, it effects the descent of the piston. During this downward movement duct 31 connects the chamber 32 underneath the piston with a discharge duct 28. After the end of the descent of the piston and the expulsion of the oil, the tilting lever 6 in positive coaction with the piston, comes in touch with a set screw 16 and, rocking around pin 5, with its other arm and by means of pin 9 lifts the piston whereby the latter effects a filling stroke. Whilst the piston rises the chamber underneath enlarges in volume and, through duct 31 in the distributor, communicates with one of the suction ducts 24 and consequently, through a vertical duct 25, with the circular channel 26 (FIG. 3) and the suction connection 27 (FIG. 1). When the set screws are brought into their highest position (at left in FIG. 1) lever 6 does not anymore get in contact with that screw and the piston and member 10 stay in their lowest position, so that neither filling nor ejection takes place. In order to obtain the delivery of a predetermined quantity, it is sufficient to set the respective screw to the desired height. The set screw are secured against unintentional displacement by means of the springs 19.

In order to take full advantages of the intermittant rotor drive, the advance steps should be adapted to the number of the discharge openings in such a way that the same optimal conditions are provided for all openings. For this reason in the example of construction the ratchet wheel which is provided with 24 teeth is fixed to the rotor by means of pin 42 in such a way that each discharge stroke is accomplished in one course and the suction stroke is performed in two sections during two advance steps following one another with an interval (see diagram in FIG. 6). In order to make sure that each delivery stroke occurs during a single advance step, the number of teeth of the ratchet wheel must be in an integral ratio to the number of outlets in the upper casing. In the described example there are 24 teeth and 8 outlets.

What I claim is:

1. A distributor pump, in particular for lubricating oil, comprising a pump body having a plurality of outlets therein and a rotary distributing member having control ports progressively driven by a rotary shaft, a piston guided in said rotary distributing member, a ratchet freewheel gearing provided on said shaft, a cam ring acting upon the said piston to effect the delivery strokes of the latter, cam-type heads of adjustable screws acting also on said piston to individually effect the filling strokes for each of said control ports, the number of teeth of the said ratchet wheel being an integral ratio of the number of outlets in the said pump body in order to adapt the advance steps of the ratchet free-wheel to the overlapping conditions of the said control ports sweeping over the inlet and outlet ducts in such a manner that each delivery stroke of the piston is accomplished during a single advance step of the ratchet free-wheel.

2. A distributor pump, in particular for lubricating oil, comprising a pump body having a plurality of outlets therein and a rotary distributing member having control ports progressively driven by a rotary shaft, a piston guided in said rotary distributing member, a ratchet freewheel gearing provided on said shaft, a cam ring acting upon the said piston to effect the delivery strokes of the latter, cam-type heads of adjustable screws acting also on said piston to individually effect the filling strokes for each of said control ports, the number of teeth of the said ratchet wheel being an integral ratio of the number of outlets in said pump body in order to adapt the advance steps of the ratchet free-wheel to the overlapping conditions of the said control ports sweeping over the inlet and outlet ducts in such a manner that each delivery stroke of the piston is accomplished during a single advance step of the ratchet free-Wheel, the suction stroke of the piston being performed during two consecutive advance steps of the ratchet free-Wheel.

3. A distributor pump, in particular for lubricating oil, comprising a pump body having a plurality of outlets therein and a rotary distributing member having control ports progressively driven by a rotary shaft, a piston guided in said rotary distributing member, a ratchet freewheel gearing provided on said shaft, a cam n'ng acting upon the said piston to elfect the delivery strokes of the latter, cam-type heads of adjustable screws acting also on said piston to individually effect the filling strokes for each of said control ports, the number of teeth of the said ratchet wheel being an integral ratio of the number of outlets in said pump body in order to adapt the advance steps of the ratchet free-wheel to the overlapping conditions of the said control ports sweeping over the inlet and outlet ducts in such a manner that each delivery stroke of the piston is accomplished during a single advance step of the ratchet free-wheel, the suction stroke of the piston being performed during two consecutive advance steps of the ratchet freewheel, the said ratchet gearing being designed to impart to the rotary distributing member during one complete revolution three times as many advance steps as there are outlets.

4. A distributor pump, in particular for lubricating oil, comprising a pump body having a plurality of outlets therein and a rotary distributing member having control ports progressively driven by a rotary shaft, a piston guided in said rotary distributing member, a ratchet freewheel mechanism connected to said shaft and blocking the rotary distributing member in the counter-direction of the advance steps, a cam ring acting upon the said piston to effect the delivery strokes of the latter, camtype heads of adjustable screws acting also on said piston to individually effect the filling strokes for each of said control ports, the number of teeth of the said ratchet wheel being an integral ratio of the number of outlets in the said pump body in order to adapt the advance steps of the ratchet free-wheel to the overlapping conditions of the said control ports sweeping over the inlet and outlet ducts in such a manner that each delivery stroke of the piston is accomplished during a single advance step of the ratchet free-wheel.

5. A distributor pump, in particular for lubricating oil, comprising a pump body having a plurality of outlets therein and a rotary distributing member having control ports progressively driven by a rotary shaft, a piston guided in said rotary distributing member, a ratchet free- Wheel mechanism connected to said shaft and blocking the rotary distributing member in the counter-direction of the advance steps, a cam ring acting upon the said piston to effect the delivery strokes of the latter, cam-type heads of adjustable screws acting also on said piston to individually effect the filling strokes for each of said control ports, the number of teeth of the said ratchet wheel being an integral ratio of the number of outlets in the said pump body in order to adapt the advance steps of the ratchet free-wheel to the overlapping conditions of the said control ports sweeping over the inlet and outlet ducts in such a manner that each delivery stroke of the piston is accomplished during a single advance step of the ratchet free-wheel, the said free-wheel locking mechanism comprising a leaf spring or a helical spring closely encircling a cylindrical part of the rotary distributing member and engaging with one end in a slot of a ring fixed to the pump body.

6. A distributor pump, in particular for lubricating oil, comprising a pump body having a plurality of outlets therein and a rotary distributing member having control ports progressively driven by a rotary shaft, a piston guided in said rotary distributing member, a ratchet freewheel gearing provided on said shaft, a cam ring acting upon the said piston to effect the delivery strokes of the latter, cam-type heads of adjustable screws acting also on said piston to individually effect the filling strokes for each of said control ports, the number of teeth of the said ratchet Wheel being an integral ratio of the number of outlets in the said pump body in order to adapt the advance steps of the ratchet free-wheel to the overlapping conditions of the said control ports sweeping over the inlet and outlet ducts in such a manner that each delivery stroke of the piston is accomplished during a single advance step of the ratchet free-wheel, an axial slot of the cam-type set screws governing the filling strokes and a prestressed wire spring being provided, which presses with its legs against the female thread of the screw, this latter thread being provided with an uneven number of axial grooves.

References Cited by the Examiner UNITED STATES PATENTS 1,781,948 11/1930 Davis 184-27 2,481,856 9/1949 Medhaug 103-2 2,546,585 3/ 1951 Caldwell 1032 3,046, 894 7/ 1962 Machen 1033 8 MARK NEWMAN, Primary Examiner. W. J. KRAUSS, Assistant Examiner.

Claims (1)

1. A DISTRIBUTOR PUMP, IN PARTICULAR FOR LUBRICATING OIL COMPRISING A PUMP BODY HAVING A PLURALITY OF OUTLETS THEREIN AND A ROTARY DISTRIBUTING MEMBER HAVING CONTROL PORTS PROGRESSIVELY DRIVEN BY A ROTARY SHAFT, A PISTON GUIDED IN SAID ROTARY DISTRIBUTING MEMBER, A RATCHET FREEWHEEL GEARING PROVIDED ON SAID SHAFT, A CAM RING ACTING UPON THE SAID PISTON TO EFFECT THE DELIVERY STROKES OF THE LATTER, CAM-TYPE HEADS OF ADJUSTABLE SCREWS ACTING ALSO ON SAID PISTON TO INDIVIDUALLY EFFECT THE FILLING STROKES FOR EACH OF SAID CONTROL PORTS, THE NUMBER OF TEETH OF THE SAID RATCHET WHEEL BEING AN INTEGRAL RATIO OF THE NUMBER OF OUTLETS IN THE SAID PUMP BODY IN ORDER TO ADAPT THE ADVANCE STEPS OF THE RATCHET FREE-WHEEL TO THE OVERLAPPING CONDITIONS OF THE SAID CONTROL PORTS SWEEPING OVER THE INLET AND OUTLET DUCTS IN SUCH A MANNER THAT EACH DELIVERY STROKE OF THE PISTON IS ACCOMPLISHED DURING A SINGLE ADVANCE STEP OF THE RATCHET FREE-WHEEL.

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