US1423559A - Fluid-pump mechanism - Google Patents

Description

F. C. GUERRLICH.

FLUID PUMP MECHANISM.

APPLICATION FILED DEC. 1, 1919.

1,42 3,559. Patented July 25, 1922.

6 SHEETS-SHEET 1.

INVENTOR ATTORNEY F. C. GUERRLICH.

FLUID PUMP MECHANISM. APPLICATION FILED DEC. 1. 1919.

Patented July 25, 1922.

6 SHEETSSHEET 2.

F. C. GUERRLICH.

FLUID PUMP MECHANISM.

APPLICATION FILED DEC. 1, i919.

Patented July. 25, 1922.

6 SHEETS-SHEET 3.

7 nw/avro/e F6 [izmrrlm/a, V

it? ATTORNEY F. C. GUERRLICH.

FLUID PUMP MECHANISM.

. APPLICATION FILED DEC. 1, I919. 1,423,55. Patented y 25, 1922.

6 SHEETS-SHEET 4.

INVENTOR By F6 fiuem lzbli A TTO Y6 F. C. GUERRLlCH.

FLUID PUMP MECHANISM.

APPLICATION FILED 0'50. 1. 1919.

1,423,559, Patented July 25, 1922.

6 SHEETS-SHEET 5.

6'3 IN vk/v TO I? F. C. GUERRLICH.

FLUIDPUMP MECHANISM.

APPLICATION FILED DEC. 1. 1919.

Patented July 25, 1922.

6 SHEETS-SHEET 6- FREDERICK cnennns sensation, on STAMFORD, oonnne'rroor.

FLUID-Elfin? MECHANISM.

Specification of Letters Patent.

Patented July 25, 1922.

Application field December 1,1912%. Serial No. 341,680.

To o7? ufmmc't may conccwt:

Be it known that I, Fnnnnnion C. men, at Stamford, county of llairfield, State of Connecticut, have invented a certain new Gnnnnand useful Improvement in Fluid-Pump liflechanism, of which the following is, a full, clear, and exact description.

My invention relates to improvcmentsin fluid pumps by which I mean pumps adapted for pumping air and other fluids, and has for its object to provide a pump of very high volumetric eflicienoy for a small size and weight. it further has for its object to pro vide a convertible pump which is adapted to be actuated as a motor by stored air or gas, or by a fluid from. another pump.

One feature of my invention consists in a plurality of pairs of oppositely located cylinders, having pistons therein and a common piston rod therefor. Another feature of my invention consists in the use of a crank shaft and eccentrics thereon for actuating said' piston rods. Another feature of my invention. consists in actuating said pump" by a shaft which revolves in one direction and causes the pump cylinders to revolve in the OQJOSltG direction Ai'iotlier feature .of my invention consists in providing novel means for causing said air under pressure to drive the pump mechanism a motor. Another feature of my invention consists of a cam and connecting mechanism for controlling certain valves at the pump when acting to store air. Another feature consists in providing novel means for controlling said valves of said pump mechanism to cause the nnnp mechanism to act as a motor. other :iioature of my invention. consists of a novel automatic controlling valve for stepping the storage action of the pump when the pressure in the storage tank has reached a predetermined point.

The following is a description of an embodiment of my invention, reference being h ad to the accompanying drawings, in which,

Fig. 1 is a side elevation of a pump embodying my invention;

Fig. 2 is a section of: the same on vertical plane passing through the axis of its shaft;

Fig. 3 is a vertical section of the pump on the line 3-3, Fig, 2;

Fig. l is an end elevation of the pump, certain parts outside the casingbeing broken away;

a citizen ofthe United States, residing n lg. o is a eitical section on the line oo G is a detail of a valve operating V 14 p big. l is a further detail showing certain valve controlling parts in an actuated position;

F 1g. 8 1s a side elevation of the controlling canrseparated from the pump;

F 1g. 9 shows an automatic controlling; valve for my pump, the same being in fully closed position;

F 1g. 19 shows the same in its normally open position. while B g. 11 shows the same opened'itor supplying the 3.11 to-run the pump. as motor, and I I h i2 is a section of a pump cylinder on the line 12-12, F 1g. 2.

Referring more particularly to the drawings, ll and 2 2 are two pairs of; cylinders located. at right angles to one another upon a casing 23. l-.4; and 5-5 are two pairs of pistons for said cylinders, one pair of pistons being connectedby a riaid piston rod 6. while the other pair of pistons is connected by a rigid piston rod 7 Thesepiston rods pass through suitable stufling bones, as shown at S, and have elongated cross-sections, the major axes being parallel to a vertical plane so as to resist the strains which are also parallel to said plane.

Each piston rod is provided with a hoop or band forming an opening and constituting an eccentric strap. lVithin these opennns eccentrics 9 and 10, which are rigidly connected together, as shown in Fig. 2, being preferably formed from a single These eccentrics are revolvablv mounted upon a crank-pin 11. of a cranlishaft 12. journaled at one end in a bearing carried by a stationary support 13 and at the other in a stationary support 14:. The eccentrics 9 and 10 and the shaft '12 bear a peculiar relation to one another as follows: The centers of the. disks 9 and 10 andv axis of the crank-pin 11 are in line with one another, the aXis of the crank-pin being half way between the other two centers and the distance between the axis of the crank-pin and either of said other centers is equalto the distance between the axis of the crank pin and the axis of the shaft 12. When the partsare-so proportioned, the revolution of the shaft 12 will cause the piston rods and pistons to reciprocate within their cylinders and conversely, when pressure is applied to the cylinders successively, the pistons will cause the shaft 12 to rotate. By using the crank-shaft and eccentrics above described, located and proportioned as above specified, I am enabled to dispense with the ordinary connecting rod commonly employed in pumps and to reduce the dimensions ofthe pump relatively to the throw of its piston I am also enabled to obtain for each piston a throw equal to twice the length of the crank plus twice the eccentricity or crank-arm of its eccentric, whereas the maximum throw with an ordinary crank and connecting rod is equal simply to twice the length of the crank.

The pump cylinders are provided with the ordinary inlet and outlet ports and the ordinary inlet valves 15-15 and outlet valves 1616, the same being poppet valves controlled by springs 17 and 18 in the ordinary manner. The inlet valves in the pump shown are connected with the external air, while the outlet valves discharge into chambers 19. From the chambers 19 lead pipes 20 which discharge into a manifold 21, rotatably mounted upon the shaft 12, from which it is collected by a sleeved pipe 22 and conducted to the point at which it is to be used.

The cylinders 11 and 2-2 with their inlet and outlet valves are all double-acting cylinders and the capacity of the pump is accordingly increased. In order to further increase the capacity of the pump at a given speed of its shaft 12, I construct the pump in such a way that as the shaft 12 is revolved in one direction the pump cylinders and the casing to which they are connected revolve in the other direction. These rates of revolution under some conditions may be such as desired, but the result is that for a given rate of revolution of the shaft the pistons make as many reciprocations relatively to their cylinders as though the speed of the shaft were its own. speed plus the speed of the cylinders. In the present embodiment the speed. of the cylinders is equal and opposite to that of the shaft for reasons Which. will appear.

In order to secure this double revolution action, I provide a spider 23, which is keyed by the key 24 to the support 13 so as to be fixed relatively thereto. I mount on this spider at intervals adjacent to its periphery shafts 25 011 which are revolvably mounted gears 26-2. rigidly connected. together. I mount upon the shaft 12 a gear 28 keyed so as to revolve therewith, the same meshing with the gears 26, and mount upon the easing of the pump a gear 29 with. which the gears 27 engage. The pump casing is journaled at one end upon the spider 23, as shown at 30, and at the other end is car- 'fore referred. to.

preserve this gear ratio in an apparatus used merely for ordinary pumping purposes, but in the present embodiment it should be prescut on account of the valve control hereinafter described.

The pump, as described, is intended to supply air through the pipe 22 for an internal combustion engine such, for instance, as the engine of an aeroplane. Since it is,

in that connection, desirable to use the pump as a starter for such an engine, and also to be able to use it to fill a storage tank with air under pressure for starting purposes, I provide each cylinder with an additional or supplemental valve 3.1 held to its seat by a spring 32, which spring is of suilicient tension to hold the valve closed against the ordinary pump pressures. These valves discharge into a suplemental discharge system 33, which, through a pipe 34t, discharges into a chamber 35 of the manifold hereto This manifold revolves within the collector tains a chamber 37, into which air delivered by the pipe 20 discharges, and from which it passesthrough suitable ports to the pipe 22. The collector also contains a chamber 38, which collects air from the section 35 of 105 the manifold and discharges it througl'i a pipe 89'and an intermediate automatic controller to the tank 40. The automatic controller just referred to consists of a valve casing 4-1, having a rod. 42 passing there- 170 through, which rod carries a 'alve 4-3 and a piston 44, engaging a suitable seat and cylinder. the same being normally held in downward posit-ion so that the valve 43 is opened by a sprin a. washer 4-6. The spring 4:5 is in a vented chamber 41-5. he valve stem 41-2 is provided with a head 47 against which the nose 4L8 of a lever 4-9, pivoted at 50 and actuated by a link 51, is adapted to engage so as to 120 depress the valve stem 42 when desired. The upper end of the valve stem 42 is connected to the arm 52 of two bell-crank levers pivoted at 53. Each bell-crank lever is provided with a slot which surrounds pin 54 1 5 mounted upon a projection from the inner surface of a stationary cam member 55 carried and guided by rods 56 (Fig. 4:) carried by the part 1 1-. This cam member is for controlling certain valves when the pump is op- 130 sleeve 36, which con- 45., which bears against erated to fill the storage tank and also for controlling them when the flow of the fluid to the machine is reversed so as to run it as a motor.

It is necessary, on account of the high pressure, that the valves 31 should be opened to permit the air to pass and the valves 16 should be positively closed so as to not permit the air to pass through them at that time. In order to secure this action, I provide for each valve 31 a lever 57 pivotedto the casing at 58 and having its nose 59 hearing against the cam 55. The load arm of each lever 57 acts upon a rod 60 carried by the pump casing, which in turn acts upon a lever 61 so that when the arm 57 is moved toward the left the lever 61 causes the valve 31 to be lifted from its seat. The arm 57 also acts upon a rod 62 normally held in retracted position at its spring 63, and causes the rod 62 to engage the valve stem of the valve 16 when the valve 31 is lifted so as to hold the valve 16 firmly to its seat. The cam 55 determines when the lever 57 shall be actuated so as to cause these opening and holding actions upon the valves 31 and 16. In order to actuate the levers 57, the cam 55 is provided with twelve surfaces, divided into groups of three, and adapted to act upon the four levers 57 according to how the cam 55 is positioned. In the first position, the normal pumping position, the noses 59 of the levers 57 bear against a plain circumferential. surface, indicated by the letters 0;m -0, a, Fig.- 8. In the second position of the cam 55 the noses 59 bear against alternately rising and falling surfaces, the rising surfaces being indicated by the letters bc 5 -0*. With the cam 55 in this second position the apparatus acts to pump air to the storage tank 40. In the third position, motor position, the noses also bear against surfaces which rise and fall, the rising surfaces being The surfaces bb are so disposed relatively to the surfaces c0 of the same set that one pair of them is offset relatively to the other by The surfaces b 5 are also displaced from c 0 by 90. The several rises ?)Z) are arranged so as to be 45 ahead of the risers 5 -4) so that when the valve 16 of one cylinder is about to be held closed by one of the Z) series, the valve 16 of the next cylinder (clockwise of the shaft) will have been re leased for half a period, the valve 16 of the third cylinder will be about to be released and'the valve 16 of the fourth cylinder will have been held closed for half a period. The result is that when the pump is running normally as a pump the valves 31 remain on their seats and the inlet and outlet valves of the pump operate in ordinary fashion. When the cam 55 is shifted so that the surfaces Z)c b c come into play, they cause the valves 31 to be opened and the valves 16 to beheld to their seats during the inward discharge strokes of the pistons so as to force air into the tank 40, and when the cam is shifted so that. the surfaces 0b o b* come into play the valves 31 are opened and the valves 16 are held to their seats during the movements of the pi tons in the outward strokes, the pumpthen acting as a motor under the influence of the compressed air within the storage tank.

The automatic controller acts follows: After air from the valves 31. has passed through the pipe 39 and the automatic controller into the tank 4&0 and charged the tank to the desired degree of pressure, the pressure on the piston M closes the valve 13 so as toshut oil the tank 10. At the same time the rod 12 actuated by the piston 14 acts through the levers 52 to shift the cam mem ber 55 so that the noses of the levers 57 rest on the plain portions aa -a -w* of the cam, thus throwing the pump out of action so far as supplying air to the tank 1-0 is concerned. If the pressure inthe tank 10 becomes reduced below a predetermined point for any reason. the spring depresses the piston 4A and valve 13 so as to open the passage to the tank 40 and. at the same time moves the cam 55 through the bell-crank lever 52 so as to bring the noses of the levers 57 in line with the surfaces Z2c b c of the cam 55, whereuponthe charging of the tank eO is resumed. If it is desired to draw air from the tank 41:0 and operate the pumping mechanism thereby as a motor. the lever 51 is moved toward. the right until the nose 48 of the lever 1-9, engaging the head 17, depresses the stem 42 so to open the valve 43 and also move the cam 55 to the left a sufficient distance to cause the portions cb c b to come in line with the noses 59 of the lever 57. This acts to supply air to the inner side of the cylinders 11, 22 in such order that the pumping mechanism is thereby driven as a motor, the valves 16 being held closed whenever the corresponding valves 31 are open. In this way means are provided for automatically starting and stopping the charging of the tank 10 and for connecting the tank 420 with the pump mechanism so as to drive it a motor. The valve 4-3 in Figs. 2 and 9 is shown as closed. In Fig. 10 it is shown as open, the lever 52 having been shifted by the spring 45 so as to cause the pump to supply air under pressure to the tank 10. In Fig. 11 the valve stem 12 is shown to be still furtherdepressed by the action of the lever 4:59, the position being such that the tank 10 will be connected to the pump pistons and the cam 55 will be in such a position as to control the valves 31 and 16 tuate the valves 31 to cause the pump mechanism to supply air to the tank 40, the valves 31 being open and the valves 16 being closed during the inward strokes of the pistons.

When the valve 43 is once closed it is held to its seat by the pressure upon the piston 44 and also any unbalanced pressure due to the" air in the tank 40. The larger the piston 44 the more strongly the valve 43 is held to its seat under all conditions. In order that the valve 43 may be held to its seat after the pressure on the piston 44 has been reduced considerably below tank pressure, on account of leakage in connections 39, I make the valve 43 larger than the piston 44. Thus if the piston 44 is sufiiciently large to overcome the spring 45 at a predetermined charging pressure and the valve 43 is one and onehalf times as large as the piston 44, the pressure on the valve 48 tending to hold it closed will keep it closed until the pressure in the tank has fallen to below two-thirds of the pressure which was required to close it through the action of the piston 44 against the spring 45, i. e., if the closing pressure I is 50 pounds and the pressure in the piping is lost, the valve 48 will remain closed so long as the tank pressure is above two-thirds of the closing pressure, the tank pressure on it being when first closed 25 pounds above that required to overcome spring 45. It would remain closed until enough air leaked from the tank to reduce its pressure to below 381} pounds.

While in the embodiment shown there are two pairs of cylinders and two pairs of pietons, this is for the purpose of showing the simplest form of embodiment. In embodying my invention a plurality of pairs of cylinders and a. corresponding number of pistons is necessary, diametrically opposite pistons being connected by rigid piston rods and the general rule is that the cylinders should be spaced around an axis so that the angle between any two adjacent cylinders shall be equal to 360 divided. by the total number of cylinders and the connection be tween the piston rods and the crank-pin of the crank-shaft whether connected by eccen trics or other form of connector should be such that the connector is pivotally connected to each piston rod and revolvably mounted upon the crank-pin, the distance between each pivotal connection and the center of the crank-pin being equal to the distance between the axes of the shaft and crank-pin, and the angle between lines passing through the center of any two adjacent pivotalconnections and the center of the crank-pin being twice the angle between any two adjacent cylinders. Thus, in the embodiment shown, there are two pairs of cylinders, m aking four cylinders in all, and adjacent cylinders are displaced from one another by anvided by the total number of cylinders, pistons in said c linders oiston rods rigidl connecting the pistons of each pair of cylinders, a crank-shaft having a. crank-pin, and

a connector rotatably mounted upon said crank-pin and having pivotal connections with said rigid piston rodsythe angle be tween lines oining the axis of the crank-pin and any two adjacent pivotal connections being equal to twice the angle between two adjacent cylinders.

2; Ina pump mechanism, the combination of a plurality of pairs of cylinders spaced at angles to one another equal to 360 divided. by the total number of cylinders, pistons in said cylinders, piston rods rigidly connecting the pistons of each pair of cylinders, a crank-shaft having crank-pin, and a connector comprising a plurality of rigidly connected eccentrics, equal in number to said piston rods, rotatably mounted on the crankpin of said shaft and embraced by said rigid piston rods respectively, the centers of said eccentrics being displaced relatively to the axis of said crank by twice the angle be tween two adjacent cylinders and symmetrically arranged relatively to said crank, the distances between the centers of said eccentrics and said crank-pin being equal to the distance between the axis of said crank-pin and the axis of said shaft.

3. In a'pump mechanism, the combination of a plurality of pairs of cylinders spaced at angles to one another equal to 360 divided by the total number ot cylinders pistons in said cylinders, piston rods rigidly connc i=ting the pistons oi? each pair of cylinders, a crank-shaft having am'ank-pin, a plurality ot rigidly connected eccentrics equal in number tosaid piston rods and rotatably mounted on the crank-pin of said shaft and embraced by said rigid piston rods respectively, the centers of said eccentrics being displaced relatively to the axis of said crank by twice the angle between two adjacent cylinders and symmetrically arranged relatively to said crank, the distance between the centers of said eccentrics and said crank-pin being equal to the distance between the axis of: said crank-pin and the axis 01 said shaft, a

gear rigidly mounted on said shaft, a gear rigidly connected "to said cylinders, two gears rigidly connected together and engaging respectively with the gears connected to said cylinders and shaft, and a fixed carrier for said connected gears, said cylinders and shaft being revolvable in opposite directions, and the ratio ofthe rigidly con nected gears being equal to the ratio of their respective movable gears.

d. In a pump mechanism, the combination of a plurality of pairs of cylinders spaced at angles to on another equal to 360 divided by the total. number of cylinders, pistons in said cylinders, piston rods rigidly connecting the pistons of each pair of eylinders, a crankshaft having a crank-pin, a plurality of rigidly connected eccentrics equal in number to said piston rods and rotatably mounted on the crank-pin of said shaft and embraced by said rigid piston rods respectively, the centers of said eccentrics being displaced relatively to the axis of said crank by twice the angle between two adjacent cylinders and symmetrically arranged relatively to said CIELDK, the distance between the centers of said eccentrics and said crank-pin being equal to the distance between the axis of said cranlepin and the axis of said shaft, regular inlet and outlet ports for said cylinders, supplemental outlet ports for said. cylinders, an air chamber connected to said supplemental outlet ports, and means for holding said regular outlet ports closed and opening said supplemental outlet ports successively to actuate said pump,

5. In a pump mechanism, the combination of a plurality of pairs of cylinders spaced at angles to one another equal to 360 divided by the total number of cylinders, pistons in said cylinders, piston rods rigidly connecting the pistons of each pair of cylinders, a crank-shaft having a. crank-pin, a plurality of rigidly connected eccentrics equal in number to said piston rods and rotatably mounted on the crank-pin of said shaft and embraced by said rigid piston rods respectively, the centers of said eccentrics being displaced relatively to the axis of said crank by twice the angle between two adjacent cylinders and symmetrically arranged relatively to said crank, the distance between the centers of said eccentrics and said crank-pin being equal to the distance between the axis of said crank-pin and the axis of said shaft, regular inlet and outlet ports for said cylinders, supplemental outlet ports for said cylinders, an air chamber connected to said supplemental outlet ports, means for holding said regular outlet ports closed and opening said supplemental outlet ports successively to actuate said pump, and means for throwing said holding means in. and out of action.

6. In a pump mechanism, the combination of a plurality of pairs of cylinders spaced at angles to one another equal to 360 divided by the total number of cylinders, pistons in said cylinders, piston rods rigidly connecting the pistons of each pair of cylinders a crank-shaft having a crank-pin, a plurality of rigidly connected. eccentrics equal in nuniher to said piston rods and rotatably mount ed on the crank-pin of said shaft and embraced by said rigid piston rods respectively, the centers of said eccentrics being displaced relatively to the axis of said crank by twice the angle between two adjacent cylinders and symmetrically arranged relatively to said crank, the distance between the centers of said eccentrics and said crank-pin being equal to the distance between the axis of said crankpin and the axis of said shaft, regular inlet and outlet ports for said cylinders, supplemental outlet ports for said cylinders, an air chamber connected to said supplemental outlet ports, means for holding said regular outlet ports closed and opening said supplemental outlet ports successively to actuate said pump to charge Said air chamber, and means for automatically closing the connection between said supple mental outlet ports and said chamber when the pressure in said chamber reaches a predetern'iined point.

7. In a pump mechanism, the combination of a plurality of pairs of cylinders spaced at angles to one another equal to 860 divided by the total number of cylinders, pistons in said cylinders piston rods rigidly connecting the pistons of each pair of cylinders, a crank-shaft having a crank pin, a plurality of rigidly connected eccentrics equal in number to said piston rods and rotatably mounted on the crank-pin of said shaft and embraced by said rigid piston rods respectively, the centers of said eccentries being displaced relatively to the axis of said crank by twice the angle between two adjacent cylinders and symmetrically arranged relatively to said crank, the distance between the centers of said eccentrics and said crank-pin being equal to the distance between the axis of said crank-pin and the axis of said shaft, regular inlet and outlet ports for said cylinders, supplemental outlet ports for said cylinders, an air chamber connected to said supplemental outlet ports, means for holding said regular outlet ports closed and opening said supple mental outlet ports successively to actuate said pump, means for automatically closing the connection between said supplemental outlet ports and said chamber when the pressure in said chamber reaches a predetermined point, and means for opening said connection when desired and throwing said holding means into action.

8. In a pump mechanism, the combination of a plurality of pairs of cylinders spaced at angles to one another equal to 360 divided by the total number of cylinders, pistons in said cylinders, piston rods rigidly connecting the pistons of each pair of cylinders, a crank-shaft having a crankpin, a plurality of rigidly connected eccentrics equal in number to said piston rods and rotatably mounted on the crank-pin of said shaft and embraced by said rigid piston rods respectively, the centers of said eccentrics being displaced relatively to the axis of said crank by twice the angle between two adjacent cylinders and symmetrically arranged relatively to said crank, the distance between the centers of said eccentrics and said crank-pin being equal to the distance between the axis of said crank-pin and the axis of said shaft, a gear rigidly mounted on said shaft, a gear rigidly connected to said cylinders, two gears rigidly connected together and engaging respectively with the gears connected to said cylinders and shaft, a fixed carrier for said connected gears, said cylinders and shaft being revolvable in opposite (lirec tions, the ratio of the rigidly connected gears being equal to the ratio of their re spective movable gears, a manifold fixed relatively to said cylinders and connected with said regular outlet ports and concentrio with the axis of said shaft, and a stationary receiver continuously connected to said manifold.

9. In a pump mechanism, the combination of two pairs of pump cylinders at right angles to one another, piston rods rigidly connecting the pistons of each pair, a crankshaft, and a connector pivotally connected to said piston rods and said crank-shaft, the pivotal connection to said crank-shaft being in line with the pivotal connections to said piston rods and spaced therefrom by a distance equal to the crank arm of said crankshaft.

10. In a pump mechanism, the combination of two pairs of pump cylinders arranged at right angles, pistons therefor, rigid piston rods connecting the pistons of each pair of cylinders, a crank-shaft rotatable relatively thereto, two rigidly connected eccentrics rotatably mounted on the crank-pin of said shaft and embraced by said rigid piston rods respectively, the axis of said crank-pin being in line with the plane passing through two axes of said connected eccentrics and equally spaced from the axes of said eccentrics, said distance being equal,

to the distance between the axes of said crank-pin and its shaft, and inlet and outlet ports for said cylinders.

FREDERICK CHARLES GUERRLICH.

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