US2331878A

US2331878A - Vane pump

Info

Publication number: US2331878A
Application number: US275643A
Authority: US
Inventors: Jesse S Wentworth
Original assignee: WENTWORTH AND HULL
Current assignee: WENTWORTH AND HULL
Priority date: 1939-05-25
Filing date: 1939-05-25
Publication date: 1943-10-19
Anticipated expiration: 1960-10-19

Description

Oct 19,1943. J. s. WENTWORTH VANE PUMP Filed May 25, 1939 5 Sheers-Sheet l v INVENTOR. Jesse S. WENTWORTH,

r I ATTORNEY Oct. 19, 1943. .1. s. WENTWORTH VANE PUMP Filed May 25, 1939 5 Sheets-Sheet 2 INI'ENTOR. JESSE S. WENTWORTH,

ATTORNEY 1943. .1. s. WENTWORTH 2,331,878

VANE PUMP Filed May 25, 1959 5 Sheets-Sheet 3 INVENTOR. JESSE S. WENTWORTH ATTORNEY v 9 1943- J. s. WENTWORTH I 2,331,873

,VANEPUMP 7 Filed May 25 1959 5 Sheets-Sheet 4 5 52.1 I 3.1211. 147 I INVENTOR.

JEssE S. WENTWORTH,

Egg? mg?? Patented Qct. re, 1943 VANE PUMP Jesse S. Wentworth, Cincinnati, @hio, assignor to Wentworth and Hull, a mutual cat-partnership composed oi Jesse S. Wentworth and Bertram G. "Hull, Cincinnati, (Ohio a Application May 25.1w, Serial No. was

8 Claims. (6i. 230-439) I y This invention relates ,to improvements inpumps, such as are used in connection with me chanical or electrical refrigerators,,for delivering fluid or gas under pressure, and for similar purposes. I

One of the principal objects of this invention is the provision of such a pump, which is ,com-

pactin size and relatively inexpensive to manu-.

facture, yet highly eficienttin operation.

Another object of this invention. is the provi sion of a pump in which the friction between- 1 moving parts is reduced to a minimum, thereby reducing wear between the parts and materially 1 extending the lifeof suchpumps. A further object of this invention is the prosubstantially without packing, and in which'the parts are so related to one another as to prearound the pump shaft. I

A still further object of this invention is. the provision of a pump to-be used as a compressor vent leakage and losses, despite .no packing in connection with mechanical andeleetrical re- 'frigerators, and in which solid particles and glob:

ules of oil are removedfrom the gas before the compressed' gas is injectedinto the compressed gas line.

A still further object of this invention is to arrange thepump and its driving means with respect to.one another, whereby only the heighth of one of these members is required to take in both the pumpand itsdriving means.

A stillfurther and'specific object {of this-inq vention is the provision of'apump as above re-' ferred'to, in which the friction is reduced to aminimum, in that only an oscillatory, sliding- '15 Vision of a'pump as' above-described, which is pump is'started, and the pressure then raised to a maximum after the pump is running.

Other objects and advantages of the present j I invention should be readily apparent by refer- .ence to the following specification, considered in conjunction with the accompanying drawings forming a part thereof, and it to be understood that any modifications may be made in the exact structural details there shown and described,

within the scope of the appended claims and without departing from or exceeding the spirit of the invention.

' In the drawings:

Fig. 1 is a vertical, sectional view through a combined pump and motor, assembled in its -pre ferred form.

5 Fig.- 2 is anelevation aliview of: the pump of Fi .1, as seen, from 'thebottom thereof.

Fig. 3 is' a horizontal, sectional view,.take'n on line .of Fig. .1.

Fig. 4 a, horizontal, sectional View, taken on i 3 line sg-s of Fig.1..

v 'Fig. 5 'is' airagmentary, horizontal, sectional view, taken in-a.plane below Fig.4 and showing the parts in a second position of adjustment.

, -Fig. 6 is;a fragmentarm seotional view,'showv Fig. 1.

,Fig. :7 is an" enlarged, horizontal, sectional view,

ing partsin elevation, and taken on line 6+6 of contact between the rotor and its housing-is had,

instead of a constantly running -'e ngagement..

Itis also an object of this. invention to pro;

errors in manufacture, and alsoto take up pos-- siblewear between the parts.

A still further object of this invention is the .vide an adjusting means; for adjusting the throw: i of the eccentricto take care of possible 'small- .lower end :uti lized in this Fig. 8 is a vertical, sectional view through the,

of Fig. 1 and taken1on;line 8'8 of F 1 Fi 9'is:a perspective view of thepump Wing lustrated on an enlarged scale over-that shown n the other views.

Figaro is a v'erticalfsectionalviewthrough pump and its" drivemotor, illustrating amodification therein.

Fig. .11 is a. transverse, .sectionaliview,taken .pr'ovisiono'i a pump of the class above. referred to, wherein the'eccentric throw of the pump rotor may be varied'o'r adjusted to increase and de- I crease pressure thereof on'the housing, and wherein-this decrease is employed to=reduce the starting torque necessary ininitially starting .the pump,-' I

It is also an objectofl'this invention to provide a pump-whereinthe pressure between the pump; rotorand its housing is reduced to zero before the I Fig. 121s a fragmentary. horizontal, sectional v Fig. 13 is a=fragmentary,. sectional view, taken.

'Fig. 14 is an frag'mentaryy vertical sectional vi'ew,- tak'en, on line Ni l-4 of'Fig. I3. 'Fig.- 15, is a verticah sectional 'VlCW, similar to Figsullzandlm-throiigh a pump'and its drive motor, illustrating further modifications in the construction and operation thereof.

Fig: 16 is aihorizontal, .sectional view, taken v.online ifi lfiof Fig. 15. 3 I v f application,- said wing being ,il-'

Fig. 1'1 is a fragmentary, horizontal, sectionalview, taken on line |1| 1 of Fig. 15.

Fig. 18 is a view, similar to Fig. 16, taken in a plane below that of Fig. 16, on line |8|8 of Fig. 15.

Fig. 19 is a vertical, sectional view, on an enlarged scale, of the pump mechanism of Fig. 10, and showing certain modifications therein whereby the throw of the pump impeller may be adjusted.

Fig. 20 is a transverse, sectional view of a portion of the disclosure in Fig. 19, taken on line 2|12|l of Fig. 19.

Fig. 21 is a view similar to that shown in Fig. 20, with the parts in an adjusted position to one side of that shown in Fig. 2-1.

Fig.22 is a view similar to that shown in Fig. 21, with the parts in the opposite position of adjustment.

Fig. 23 is a bottom plan view of the pump mechanism of Fig. 19, taken on line 23-23 of Fig. 19, showing the means for obtaining the adjustments of Figs. 20, 21 and 22.

Fig. 24 is a view very similar to that of Fig. 23, showing the means for automatically effecting the adjustments of Figs. 20, 21 and 22.

Fig. 25 is a wiring diagram showing the connection of the motor fields and solenoid employed in effecting the automatic adjustment of the parts.

Throughout the several views of. the drawings, similar reference characters are employed to denote the same or similar parts.

As was noted above, this invention pertains to a pump for use in connection with mechanical or electrical refrigerators, and similar purposes,

where it is desired to compress gases or fluids or to transfer liquids or fluids under pressure. It is also one of the chief purposes of this invention to supply such a pump or compressor unit in which the parts are intimately associated with one another and enclosed in substantially a single housing, whereby the manufacturing costs may be materially reduced and required accommodating space likewise reduced to a minimum.

Specifically referring to the drawings, and particularly to Figs. 1 to 9 inclusive, which illustrates the preferred embodiment of this invention, it will be noted that use is made of an upper housing 25 and a lower housing 26. These housings are substantially cup shaped and have, respectively at their adjacent ends, radial flanges 21 and 28, through which pass looking or clamp screws or bolts 29. If desired, a" gasket (not shown) may be inserted between said flanges for making the interior of the housings air and gas tight to the exterior. In addition, each of the

housings

25 and 25 have projecting from their outer surfaces,

fins

30 and 3| for radiating heat generated and developed within the housings.

The upper housing 25 is counter bored to provide a shoulder or seat 32; against which the motor field laminations 33 abut, and the seat 32 forms a shoulder which, along with the inner overhanging portion 34 of radial flange 28, affords means for clamping 'the motor field laminations in position. Associated with said laminations, as is usual practice, is the motor field coil 35. Secured to the upper housing 25, and passing through the wall thereof, is a sealed-in plug or connector 36, through which the external elec-' tric source or wires 93 is connected with the motor field coil 35.

Centrally of the motor field laminations 33 are the armature laminations shown here as secured over the pump assembly, and indicated in general by the reference numeral 31. In other words, the motor armature has built within its center the pump or compressor, whereby the rotation of the motor armature operates the pump. The pump assembly 38 comprises a central pump cylinder 39 in the form of a ring or sleeve, having secured to its upper end a plate 48, and to its lower end a second plate 4|. The plates 40 and 4| respectively have projecting outwardly thereof bearings or

trunnions

42 and 43, respec tively received in inwardly projecting bearing

bosses

44 and 45, formed integral with the

housings

25 and 26, and projecting toward one another. The plates 48 and 4|, and their

respective sleeves

42 and 43, are each provided with a bore in axial alignment, and which bores are concentric with the inner housing sleeve 39 when in assembled position. The securing of end plates 40 and 4| to sleeve 39 provides, interiorly of said sleeve, a chamber 46 in which is disposed the pump rotor 41, which is in the form of a sleeve, centrally bored and having an external diameter less than the internal diameter of the cylinder sleeve 39.

Disposed in the bores of

closure plate sleeves

42 and 43 are the ends ofa shaft 48, which has its such that the rotor 41 has at all times tangential line contact with the inner surface of the cylinder ring 39 or chamber 46, as seen clearly in Figs. 4 and 5. It will be noted that there is no positive connection between the shaft 48 and rotor 41, since, in fact, and as will later appear, the shaft 48 is always held stationary, and the rotor is loose thereon.

In order to hold the shaft 48 stationary, the upper end thereof, see Fig. 6, is formed to provide a pair of flats 50 which are received in an aperture, having the cross section of the end of the shaft, and formed in a lever or wrench 5|. This wrench, see Fig. l, is located within a cavity 52, formed within the bearing boss 44 and in the main lies above the upper surface of closure plate sleeve 42. Referring again to Fig. 6,

the wrench or lever 5| has, at its other end, an

aperture 53, through which passes a clamp screw 55, threaded into the base of the cavity 52 and therefore into the stationary bearing lug 44. From the description just given, it will be noted that the wrench or lever 5| holds the shaft 48 against'rotation. It will also be noted that the pump cylinder 39, and end closure plates 40 and 4| are rotated around the shaft 48, particularly around the eccentric portion 49 thereof, as is also the rotor member 41.

In order to rotate the rotor member 41, it is connected with the pump cylinder 39 by a pump wing or vane 58, shown most clearly in Fig. 9, and shown in two operative positions in Figs. 4 and 5. As will be seen, the wing 58 has a hinge connection with both the cylinder member 39 and the rotor member 41, and for this reason the wing or vane 58 is provided at opposite ends with ,hinge portions or

knuckles

59 and 60, respecing with the cavityEZ.

- and 26. wise in communication with the cavity ,52; throughvertical and radial bores or ports 86 crosses the chamber 36, dividing same into a pair communicated with a groove 65 formed'circumferentially and exteriorly in the eccentric portion. of the shaft at a point near the upper end thereof. Extending from the groove 66 into the shaft is a port 6? which communicates with a vertical port or bore -8-8 in said shaft, which has its lower end closed and upper end communicat- Likewise, the intake or suction chamber 36" has extending from it, through the pump member, a port 69 which communicates with'a groove i8 formed circumferentially and exteriorly of-the eccentric portion of the shaftat a point near the lower end thereof. This groovejfl communicates through a port ll with a verticalport or bore 12 in the lower end dial flange 90, stopping short of the bearing boss 6G to provide a passage way 9!.

It should be noted that the interior of the housing 25, above the motor la'minations, forms a pressure chamber, while the space below the said laminations forms alubricating oil chamber with these chambers in substantial unrestricted communication by way of the bores 89 and the necessary clearance between the rotor laminations and field lamiriations' It should also be noted that oil for lubricating the bearing sur-' faces of the running parts is fed into the supply port and carried to these surfaces by the gases and fluids being circulated. For this purpose,

use is made of a small pipe 92, connecting the .oil chamber, or lower end of the housing, with the supply-port id.

The operation of the pump is as, follows:

The electric power is supplied I through the" lead wires 93, through the plug 36, to the motor field ,coil'for energizing same and causing the rotation of the motor armature 37. Since this armature has secured thereto the pump mechaof the shaft, -and which bore or port '72 has its upper end closed and its lower end communicating with a cavity 13, located below the shaft 48 and within the closure plate sleeve 43. It will be noted that this pump shaft is, to all intents and suitable or desirable construction. As shownin the drawings, the check valve 15 is conical shaped, having extending therefrom a stem 76 shaft 38.

nism, thepump is rotated therewith about the the pumriqnechanism to revolvearound its eccentricportion 39. The rotation of the pump mechanism around the eccentric, portion Moi the shaft, causes. the pump rotor M to roll its .outer periphery on the inner periphery of the pump cylinder 39 in much the same manner that a small planetary gear would roll within an internal gear.

Since, however, the pump rotor and cylinder ring are connected with one another by the wing or vane 58 against independent rotation,

these members rotate as a unit, with a slight slippage therebetween. V

As will readily be appreciated, this slight relative movement causes the wing or vane 58 to move from the position illustrated in Fig. 5 to the position illustrated in Fig. 4, and then back again to the position of Fig. 5 during each rotation oi the pump mechanism, and therefore of the modisposed for guiding purposes in a spider J'H located within the cavity 13 and below the shaft 48.

Between the valve 75, and surrounding the valve stem 16, and the spider Ti is a spring 18, which abuts on one end'with the spider I1 and on theother end with the'valve 15 for atall times urging the check valve to a closed position.'

Between the cavity 52- and the vertical discharge or compression port 68 is a check valve ,1 9, similar in all respects to thecheck valve [5, andlikewise' spring loaded. The stem of check ivalve l9 is mounted-for guiding purposes, in a the plate 80 is aring"83, having formed therethrough radial bores 84, whereby communication between the cavity 8| may be had through bores or ports 85formed vangularly througlr the bear.

ing boss 4,4,.with the interior of the housings 25 The. interiorofthe housings is likeformed in the bearing boss 44.

- On the upper surface of the motor rotor laminations 3'! are a pair of

baflies

81 and 88, respectively circular and disposed at diametrically optor rotor. This causes an increase in the suction chamber 46" and a corresponding reduction of the discharge or compression chamber 46', thereby creating a suction or vacuum in the chamber 46", which unseats check valve I5,

- drawing gas or fluid throughthe' port Hand ejecting same from the chamber 66', thereby unseating the check valve- 19 and filling the cavity 52. The compressed gases and fluids in the cavity 52 pass down throughfvertical and radial ports 86, and are discharged against the bafile 81. This baffle 81 causesthe gas or fluid to slide thereover and have the oil suspended therein removed whereupon the gas or fluid engages the baffle 88-90. In striking the-baflies 81 and 8890,

practically all of the oil supplied to the gas and fluid by way of pipe 92 is centrifugally removed therefrom, thereby completely removing any suspended oil or moisture from the gas or fluid, and

providing substantially oil free compressed gas which flows from the baflies through the pasposite points of vertical bores or apertures 89 formed through the rotor laminations. baffle 88 is provided at its upper endwith a ra- The.

This oil or, fluid collects on the inner surfaces of the baffle Ala-90 and flows downwardly wardly through bafile outlet 9| into-the pressure chamber, where it flows through the angular ports and ring ports 84 into thecavity 8!. The gas and fluid escapes from the cavity 8| Theshaft Q8, being stationary, causes ed with the supply port 14, andthis vacuum is likewise in the said port I4. With the motor and pump quiescent, this vacuum will tend to suck the oil from within the housing 26 into the gas or fluid supply tank, and gravity fiow of the oil to the lowest point may drain all the oil into the supply tank. In order to prevent this, a check valve is placed in the port I4 at the most convenient or desirable point, which is shown in the drawings as at the end of this port. This check valve, indicated in general by the reference character I29, may take any desirable or acceptable form, and that shown in the drawings comprises a nipple 95, threaded into the end of the port I4, which has a passage therethrough and at the same time forms a seat for one end of a spring 96 which bears on its other end'against a ball valve 91. The ball valve 91 is held to a seat at the inner end of a port 90, formed through a coupling 99, which is in turn threaded onto the nipple 95.

It will be readily appreciated that the cessation of suction in the suction chamber 46" will allow both the check valve I5 and ball check 91 to seat, thereby stopping any return flow in the suction system of the line, and any lubricant or oil that is in the housing 26 will flow by gravity into the port 14 between these check valves and will not be drawn into the supply tank.

With this construction, also, when the motor is again. started, and thereby the pump, the first flow through the system is lubricating oil, which floods all of the rotating parts, and by supplying bearings or their bushings with suitable oil feeding grooves, the lubricating oil is distributed throughout the running bearing surfaces, and since the oil is almost immediately supplied to these bearings upon the starting up of the motor and the pump, the bearings are without lubricant at substantially no time during their rotation.

As is usual practice, and in order to hold the temperature of the pump or motor to a minimum at all times, both the upper and

lower housings

25 and 26, as above indicated, are respectfully provided with radiating fins 30 and 3I substantially throughout their exterior surfaces.

In the mechanism just described, the pump and its prime mover are built one within the other, while in the modified construction disclosed in Figs. to 14 inclusive, the pump and motor structures are built independently of one another, and subsequently secured to one another, but including the same principles of construction and operation. Specifically referring to the construction disclosed in Figs. 10 to 14 inclusive, use is there made of a housing 25', in which is mounted the motor field laminations 33 shown as disposed between the shoulder 32 within the housing 25' and the upper end of a pair of pins I02 which upstand from a plate I03 partly disposed within the housing 25'. The

' motor rotor laminations 31, instead of being secured to the pump cylinder, are secured in the usual manner to a motor shaft I04 which has its upper end joumaled in a bearing boss I05. The lower end of the shaft I04 is journaled in a bearing boss I06 integral with the plate I03, and this hearing being shown in the drawings as including a bearing bushing I01 carried by the boss I05 and receiving the lower end I08 of the shaft I04.

An outer pump housing casting 26 is utilized and has at its upper end the radial flange 28 which engages a radial flange 21 at the lower end of the motor housing 25', and these flanges are secured to one another by the connecting screws or bolts 29, and between them the usual gasket for sealing this joint. The said connecting screws or bolts provide the clamping pressure for holding the field laminations 33 in compressed superimposed position between the upper ends of the pins I02 and the housing shoulder 32, since the plate I03 is secured as by clamp bolts I09 to the casting 26'.

Secured to the undersurface of the plate I03, as by bolts or screws H0, is a sleeve III carrying at its other end a bearing plate II2. Within the sleeve III.is the pump cylinder sleeve 39 which carries at its opposite ends closure plates 40 and 4|, from which respectively project the trunnions or bearing sleeves 42 and 43'. The sleeve 42', in addition to forming interiorly thereof the bearing for the pump shaft 48, forms additionally a clutch or connection with the motor drive shaft I04. This clutch is clearly shown in Fig. 12 and has several. clutch teeth II3 projecting therefrom intermeshing with similar complementary clutch teeth II4 formed on the lower end of the motor drive shaft I04.

Within the pump cylinder 39 is the pump rotor 41, connected with the pump cylinder by the double hinge wing or vane 58, and which operates in the same manner as that above described, and is rotated through the drive of the pump cylinder about the eccentric portion 49 of the shaft 48. The internal construction of the shaft 49, in Fig. 10, is substantially identical with that disclosed in Fig. 1, except that the ends of the shaft are provided with counter bores in order that the intake and exhaust valves respectively I5 and I6 may be positioned much nearer to the intake and supply ports respectively 69 and 55, so as to reduce any possible re-expansion in the gas during the cycle of the pump. The discharge port 69 in thepump shaft 48 connects with abore II5 formed through the center of the plate trunnion and bearing sleeve 42', and motor shaft I04 connected with a cavity IIS formed within the housing bearing lug I05. This cavity II6 has its upper end defined by an imperforate plate II'I held to its seat within the cavity by a cap H8 and lugs II9 projecting therefrom. The cavity H6 communicates with the interior of the housing 25' by way of ports I20 with the baiiles 81 and 88-430 in the path of flow therethrough. The interior of the housing 25' communicates by wayof angular ports I2I with a chamber or cavity I22 formed between the above mentioned irnperforate plate In and closure cap H8, and this cavity I22 communicates with the discharge or pressure port 94 and a pipe or conduit (not shown) connected therewith. a

The interior of the housing 25' communicates with the interior of the housing 25' by way of vertical ports I23 formed through; the plate I03,

- the motor rotor 31.

and which ports deliver the separated lubricating oil into the housing 26' for injection into the system inthe same manner as above described.

The shaft 48, in Fig. 10, similar to said shaft in Fig. 1, is held stationary by a lever or wrench I24 connected therewith in the same manner as the lever or wrench key I and locked in position by a screw or bolt I25 passing into the bearing plate H2. The lower bored end of the shaft -48 projects beyond the lever or wrench I24 into a coupling I26 which has connected therewith one end of a tube I21 lying below the bearing plate H2, and which tube takes the place of the supply port I4, and is connected with the supply tank (not shown). A small bleed hole I28 is formed through one wall of the tube to provide for the injection of the oil into the system. The tube I2! is projected, at a suitable point, through the wall of the housing 26' and has connected therewith the oil check valve I29, which may be of any suitable or desirable construction, such as above described.

In order to prevent the shifting of the motor field laminations 33, a construction similar to that illustrated in Figs. 13 and 14 may be employed, wherein a pin I32 is arranged half within the inner wall of the housing 25 and half Within the field laminations 33. In order that this pin I32 may be removed, in the event it is desired to take out the field laminations, it is provided with a finger hold or shoulder I33.

The operation of the combined motor and pump structure in Figs. to 14 inclusive is substantially identical with that above described in connection with the structure in Figs. 1 to 9 inclusive. In other words, rotation of motor armature 37 carries with it the motor shaft I04, which, through its clutch connection II3II4 with the pump cylinder 39, rotates this housing.

The rotation of the pump housing 39, through the.

double hinge vane 58, rotates the pump rotor, thereby effecting a pumping and compressing action through the pump.

The path of flow is from the supply tank (not shown), oil check valve mechanism I29, pipe or ciiuduit I21, port in the lower end of the shaft 48, check valve 75, radial ports 69 into the chamber 46'. her, when converted into the compression cham ber 46', through the radial port 65, vertical port 68 in the upper end of shaft 48, past the check valve I6, port H5 in the closure plate trunnion and bearing sleeve 42 and motor shaft I04, cavity IIG, vertical ports I20, interior of housing 25', angular ports I2I, cavity I22 and exhaust port 94 and conduit and storage tank (not shown) connected with the port 94. The flow of fiuid from the supply tank to the pump supply chamber 46" carries with it lubricating oil drawn through bleed hole I28 in the pipe or conduit I21. The fiow of the compressed gas or fluid from cavity II6 to the cavity II! is by way of

baffles

87 and 88--90 for removing the lubricating oil therein as above described, and for directing the lubricating oil through the vertical bores 89 in This separated lubricating oil fiows by way of ports I23 to the interior of the housing 26 and is collected therein, as well as in the inverted cup shaped lower housing closure plate I30 secured to the open end of the lower housing by means of bolts or screws I3I.

In connection with the construction just described and illustrated in Figs. 10 to 14 inclusive, it should be noted that the use of the clutch I I3-I I4 between the motor shaft I04 and driven The pressure flow is from this champump member 39 is advantageous in compensating for slight inaccuracies in the manufacture of the several parts, should they not be in absolute axial alignment and slightly out of line. It should also be noted that the mounting of the closure plate bearing on the

trunnion sleeves

42 and 43 is in the same manner as above described, so that the shaft 48 may be angularly adjusted to compensate for wear and slight inaccuracies in the alignment of the parts.

In the modifications above described, the pump cylinder ring was driven by the prime mover, which, through its connection by the double hinge vane, effected the rotation or drive of the pump rotor. It has been found that substantially the same results can be obtained by driving the shaft and holding the cylinder ring stationary and allowing the pump rotor to roll within the cylinder ring and this rolling effected by the eccentricity of the shaft.

This latter construction is illustrated in Figs.

15 to 18 inclusive, wherein use is made of the same motor drive as disclosed in Fig. 10, and for a description of which reference to the above may be had. As shown in Fig. 15, the pump shaft 48" is provided at its upper end, see Fig. 17, with clutch teeth I34 which intermesh with the clutch teeth H4 at the lower end of the motor shaft I04. The eccentric portion 49" of the shaft 48 is encircled by the pump rotor member 535 disposed within the pump cylinder sleeve I36. The pump housing sleeve I36 is connected with the rotor member by the double hinged vane 58 in the same manner as above described, but this pump cylinder sleeve I36 is secured against rotation by screws or bolts I31 passing through the plate I03 into the upper end of the sleeve I36.

The sleeve I36 is encased in a casting or lower housing member I38, and which housing member has formed at its lower end a. supply port I39 communicating with a vertical bore or port I40 in the lower end of the shaft 48". At the outer end of the port I39 is the oil ball check valve I29.-

The upper end of theshaft 48" is provided with a vertical port I4I, which communicates with the port II5 formed centrally of the motor shaft I04. The pump shaft ports I40 and I 4| are respectively in communication with the chambers in the pump cavity by way of ports I42 and I43, respectively, through the shaft 48" and adapted to be connected respectively with ports I44 and I45 formed through the pump port I43 has connected therewith the open end of a groove I46 formed through a portion of the periphery of the eccentric portion 49" of the shaft, and which groove terminates in a shoulder I41. The port I42 likewise has connected therewith the open end of a groove I48 terminating at its other end in a shoulder I49. From this it will be seen that there is a blank space between the ends or shoulders of these grooves and their ports which out off any flow through the pump rotor ports I44 and I45 during a portion of each rotation of the pump drive shaft.

By this construction, the compression in the pump pressure chamber 46' is built up to the pressure in the pressure receiving tank before any additional compressed-gasis forced thereinto, and a suction is created in the chamber 46" equal to the suction in the supply tank before the said supply tank is connected therewith. By this construction, a return surge from the pressure and supply tanks is prevented and at the same time the extraneous check valves are eliminated.

In Figs. 19 to 23 inclusive, there is illustrated means for adjusting the throw of the pump rotor, which may be employed for compensating for slight inaccuracies in machining the parts in order to have the proper tangential line contact between the said pump rotor and its housing, and may also be employed for taking up wear between these parts. It will be understood that this adjusting mechanism is applicable to any type of pump wherein a vane is employed for effecting the pumping operation, but for convenience in illustration, use is made in the drawings of the pump mechanism shown in Fig. 10, and enlarged for clear illustration. Accordingly, the pump rotor sleeve 41 has its bore slightly enlarged to accommodate a sleeve I60 which is mounted about the eccentric portion I6I of the pump shaft I62. The pump shaft I62 has projecting from its ends the trunnion portions I63 and I64 which are formed around the axis of the pump drive shaft, of which the clutch I I4 is the only thing shown in Fig. 19. This axis is indicated by the point I65 in Figs.

20, 21 and 22. The shaft eccentric I6I is generated about an axis offset with respect to the axis for the shaft as a whole, and is indicated in Figs. 20, 21 and 22 by the reference character I66. The interior or bore .of the sleeve I60 is likewise generated about the axis I66 of the shaft eccentric, while the exterior or outer surface of said sleeve is generated about an axis offset with respect to both the shaft axis I65 and the shaft eccentric axis I66, and is indicated by a point by the reference character I61,

Extending through the lower end of the shaft I62 and the trunnion I64 is a bore receiving an oscillatable rod I68. from its upper end a headed screw or shifter I89 which passes through a slot I10 in the shaft eccentric I6I and is received in an aperture I1I formed in the sleeve. Secured to the lower end of the rod I68 is a wrench or lever I12 having at its free end an elongated arcuate aperture I13 through which passes a clamp screw or bolt I14. The rod I68 below the screw I69 is hollow to receive a tube I15 which forms the supply port for the pump and is connected with the head I28 and supply conduit I21, and at its upper end forms the valve seat for the check valve 16, all

as disclosed in Fig. 10, and as above described.

The parts as illustrated in Figs. 19 and show them in normal position; that is, in pump operating position and with the pump rotor 41 having tangential line contact with the pump housing sleeve 39. In order that proper communication may be had between the pump chambers and the discharge port 68 at the top of the shaft and with the supply port at the bottom of the shaft, the eccentric sleeve I60 is provided with exterior circumferential grooves I16 and I11, respectively communicating with-one or more bores I18 and I19 formed through the sleeve and in turn communicating with the grooves in the shaft eccentric which communicate with a bore leading to the shaft supply and discharge ports. Should, for some reason, the tangential line contact between the pump rotor and pump housing be too great as with the parts as illustrated for example in Fig. 20, it is only necessary to release the clamp The rod I68 has projecting bolt I14 and shift the lever I12 forwardly as seen in Fig. 19 or in a counter clockwisedirection as seen in Fig. 23, for thereby rotating or oscillating the rod I68 and through its screw or shifter I69 to shift the eccentric sleeve I60 in a clockwise direction as seen in Figs. 20 and 21 and thereby break or relieve the pressure at the point of tangential line contact; As will be seen in Fig. 21, the parts are so illustrated that with the adjustment just described, a clearance, indicated by the reference character I in Fig. 21, may be obtained. Should now, with parts as illustrated in Figs. 19 and 20, the proper tangential line contact not be established and a clearance exist. it is only necessary to oppositely operate the lever I12 for shifting the eccentric sleeve I60 toward the position illustrated in Fig. 2-2, which shows, by a dot and dash line, a portion of the inner wall of the pump cylinder sleeve 39 as being taken or cut away by the pump rotor member 41. In either position of adjustment, the lever I12 is then secured in position by the clamp screw or bolt I14. It will be appreciated that the shaft I62 is held against lateral or rotative movement by the lever I24.

From the foregoing, it will be noted that the throw of the pump rotor may be adjusted to vary the pressure at the tangential line contact and to take up wear on these parts without interfering in any wise with the operation of the pump.

In some instances, it may be desirable toautomatically adjust the position of the rotor, as for example to relieve the pump of any contact of the rotor and its housing when starting the pump and subsequently to effect this contact. In order to do this, a mechanism is illustrated in Figs. 24 and 25. As there shown, the clamping screw I14 is dispensed with and the lever I12 has secured to it the inner ends I82 and I83 respec tively of springs I84 and I85. The other end of the spring I84 is secured to a permanent anchor I86, while the other end of the spring I85 is connected with the movable core I81 of a solenoid I88. The spring I84 is utilized to shift the eccentric sleeve I60 and thereby the pump rotor 41 to the position illustrated in Fig. 21, while the solenoid is employed to shift these parts from this position to the desired pumping contact position which may be anywhere between the position shown in Fig. 21 and that shown in Fig. 22 and passing through the position shown in Fig. 20. The spring I85 being employed to cushion the contact and to form a yielding connection and avoid excessive pressure at the line or point of tangential line contact, due to the pull of the solenoid.

In Fig. 25, there is diagrammatically illustrated an electric motor armature I89 having associated therewith the starting and running field coils I90 and I9I. The starting coils I90 have their opposite ends connected with the power lines I92 and I93, with a cut-out switch I94 connected therein and which switch is normally yieldingly closed as illustrated. The running coils I9I have their opposite ends likewise connected with the power lines I92 and I93, having imposed in the circuit the coil of the switch opening solenoid I95. The closing of the running coils circuit and likewise energization of the switch solenoid I95 completes a circuit through said switch, which includes the solenoid I88 for adjusting the position of the pump rotor.

The operation of this mechanism is as follows:

When the pump is stationary, the spring I84 actuates the lever I 12 to a position for relieving all pressure between the pump rotor and its cylthereby shifting the pump rotor into contact with the housing.

With this construction, a motor may be employed having a, relatively low starting torque, which, when in operation, does the same amount of work and just as efficiently as the high-starting torque motor as heretofore employed.

From the foregoing, it will be seen that there has been provided a pump or compressor mechanism in which the friction has been reduced to a minimum, since the only moving parts of the pump slide or oscillate on one another for a short distance, which is the difierence in the diameters of these parts, instead of having continuous sliding and rotating surfaces throughout the peripheries, as is the case with the usual type of pump constructions. It will further be noted that this result is obtained whether the pump cylinder or the normal pump rotor member is the driven member of the unit. By this construction also, the-parts may be so arranged and assembled as to take up the smallest amount of space. It will further be appreciated that with the construction above the throw of the pump rotor is fully adjustable to take care of possible small errors in machining and to take up possible wear between the pump housing and pump rotor.

What is claimed is:

her, a double hinge pump wing vbetweenfsaid pump .cylinder member and rotor member-clividing the pump chamber into a suction chamber and a ,compression chamber, a prime mover for effecting relative movement between the pump cylinder member and rotor member, and conduits respectively connected with the pump suction and compression chambers for respectively supplying a medium'to be compressed and carry-. ing off the compressed medium.

3. In a pump mechanism of the class described the combination of a pair of housing members adapted to be connected with each other for completely inclosing the pump mechanism and each having a bearing inalignment with each other, a pump cylinder member having at, its

1. In a pump mechanism of the class described I the combination of a pairof housing members adapted to be connected with each other for completely inclosing the pump mechanism and each having a bearing in alignment with each other, a pump. cylinder member having at it's opposite ends journals, journaled in the housing members bearings, a pump rotor member within said cylinder member, a shaft having its ends journaled in the pump cylindermember journals and having intermediate its ends an eccentric portion, said eccentric portion forming a journal for and being encircled by the rotor member and the eccentricity of said portion being such as to cause the rotor member to bear against and have line contact with the inner peripheral wall of 'the pump cylinder member, a pump wing simultaneously hingedly connecting with the pump cylinder member and rotor, and means for driving one of said pump members.

2. In a pump mechanism of the class described the combination of a pair of housing members adapted to be connected with, each other for completelyinclosing the pump mechanism and each having a bearing in alignment with each other, a pump cylinder member having at its opposite ends journals, journaled in the housing members bearings, a pumprotor member within said cylinder member, a shaft having its ends journaled in the pump cylinder member jour 'nals and having intermediate its ends an eccentric portion, said eccentric portion forming a journal for and being encircled by the rotor member and the eccentricity of said portion being such as to cause the rotor member to bear against and have line contact with the inner peripheral wall of the pump cylinder member thereby forming around the rotor a pump chamopposite ends journals, journaled in the housing members bearings, a pump rotor member within said cylinder member, a shaft having its ends journaled in the pump cylinder member journals and having intermediate its ends an eccentric portion, said eccentric portion forming a journal for and being encircled by the rotor member and the eccentricity of said portion being such as to cause the rotor member to bear against and have line contact with the inner peripheral wall 'of the pump cylinder member thereby forming around .the rotor a pump chamber, a double hinge pump wing between said pump cylinder member and .rotor member dividing the pump chamber into a suction chamber and a compression chamber, a prime mover for efiecting relative movement between the pump cylinder member and rotor member, conduits respectively connected with the pump suction and compression chambers for respectively supplying a medium to be compressed and carrying off the compressed medium, means for supplying lubricating -oil to the pump supply conduit for mixture with the medium to be compressed, and means for removing the lubricating 'oil from the compressed medium after it has passed through the pump compression chamber.

4. In a mechanism of the class described the combination of a pair of housing support membersadapted to be connected to each other to form an hermetically sealed housing, said housing members each having a bearing boss in axial alignment with each other and respectively bored to provide bearings, a motor field carried by one of the housing members interiorly thereof, a motor armature centrally of the field, a pump cylinder sleeve, end plates carried by the pump cylinder sleeve and respectively provided with bored journals, journaled in the housing bearing bosses, said pump cylinder sleeve and end plates forming the' means on which is mounted the motor armature laminations,'a shaft centrally of the pump cylinder sleeve and journaled in the bores of the end plates journals, an eccentric on the shaft within the pump cylinder sleeve between the end plates, a pump rotor journaled on the eccentric whose eccentricity is such as to cause the pump rotor member to bear against and have line contact with the inner peripheral wall of the-cylinder sleeve to form around the rotor a pump chamber, a pump vane between the pump cylinder sleeve and pump rotor adapted to drive the rotor by the sleeve around the shaft eccentric and said pane being adapted to divide the pump combination of a pair of housing support members adapted to be connected to each other to form and hermetically. sealed housing, said housing members each having a bearing boss in axial alignment with each other and respectively bored to provide bearings, a motor field carried by one of the housing members interiorly thereof, a motor armature centrally of the field, a pump cylinder sleeve, end plates carried. by the pump cylinder sleeve and respectively provided with bored journals, journaled in the housing bearing bosses, said pump cylinder sleeve and end plates forming the means on which is mounted the motor armature laminations, a shaft centrally of the pump cylinder sleeve and journaled in the bores of the end plates journals, an eccentric on the shaft within'the pump cylinder sleeve between the end plates, a pump rotor journaled on the eccentric whose eccentricity is such as to cause the pump rotor member to bear against and have line contact with the inner peripheral wall of the cylinder sleeve to form around the rotor a pump chamber, a pump vane between the pump cylinder sleeve and pump rotor adapted to drive the rotor by the sleeve around the shaft eccentric and said vane being adapted to divide the pump chamber into a suction chamber and a compres-' sion chamber, means providing a source of supply of a medium to be compressed to the suction chamber and storage for the compressed medium from the compression chamber, said shaft being centrally bored from opposite ends to provide a supply port and a discharge port respectively for the supply and compression chambers, and one way check valves between the last mentioned ports and the source of supply and storage.

6. In a mechanism of the class described the combinatipn of a pair of housing support members adapted'to be connected to each other to form an hermetically sealed housing, said housing members each having a bearing boss in axial alignment with each other and respectively bored to provide bearings, a motor field carried by one of the housing members interiorly thereof, a motor armature centrally of the field, a pump cylinder sleeve, end plates carried by the pump cylinder sleeve and respectively provided with bored journals, journaled in the housing'bearing,

bosses, said pump cylinder sleeve and end plates forming the means on which is mounted the motor armature laminations, a shaft centrally of the pump cylinder sleeve and journaled in the bores of the end-plates journals, an eccentric on the shaft within the pump cylinder sleeve between the end plates, a pump rotor journaled on the eccentric whose eccentricity is such as to cause the pump rotor member to bear against and have line contact with the inner peripheral wall of the cylinder sleeve to form around the rotor a pump chamber, a pump vane between the pump cylinder sleeve and pump rotor adapted to drive the rotor by the sleeve around the shaft eccentric and said vane being adapted to divide the pump chamber into a suction chamber and a compression chamber, mea'ns providing a source of supply of a medium to be compressed to the suction chamber and storage for the compressed medium from the compression chamber, lubricant storage means within the inclosing housing, and means for supply said lubricant to the medium as it passes between the supply source and pump suction chamber.

combination of a pair of housing support members adapted to be connected to each other to form an hermetically sealed housing, said housing members each having a. bearing boss in axial alignment with each other and respectively bored to provided bearings, a motor field carried by one of the housing members interiorly thereof, a motor armature centrally of the field, a pump cylinder sleeve, end plates carried by the pump cylinder sleeve and respectively provided with bored journals, journaled in the housing bearing bosses, said pump cylinder sleeve and end plates forming the means on which is mounted the motor armature laminations, a shaft centrally of the pump cylinder sleeve and journaled in the bores of the end plates journals, an eccentric on the shaft within the pump cylinder sleeve between the end plates, a pump rotor journaled on the eccentric whose eccentricity is such as to cause the pump rotor member to bear against and have line contact with the inner peripheral wall of the cylinder sleeve to form around the rotor a pump chamber, a pump vane between the pump cylinder sleeve and pump rotor adapted to drive the rotor by the sleeve around the shaft eccentrio and said vane being adapted to divide the pump chamber into a suction chamber and a compression chamber, means providing a source of supply of a medium to be compressed to the suction chamber and storage for the compressed medium from the compression chamber, lubricant storage means within the inclosing hous- -ing, means for supplying said lubricant to the medium as it passes between the supply source .sleeve member, a pump rotor member, a shaft mounted concentrically with respect to the pump cylinder sleeve member and having an eccentric portion within the pump cylinder sleeve on which is journaled the pump rotor and the eccentricity being such as to eccentrically arrange the pump rotor with respect to the pump cylinder sleeve so as to have tangential line contact between the pump cylinder sleeve member and rotor member, .said pump members being 'so mounted for rotation as to have one of them driven around the axis of the shaft, an electric motor connected with said one driven member to effect its drive and rotation, means for changing the eccentric throw of the shaft and thereby changing the eccentric arrangement of the pump cylinder sleeve member and pump rotor member including a sleeve journaledon the shaft eccentric, said shaft eccentric sleeve having an outer surface developed about an axis eccentric to the axes of the shaft and its eccentric, an arm for revolving the shaft eccentric sleeve around the shaft eccentric to add or subtract its eccentricity to that of the shaft eccentric and thereby change the throw of the shaft eccentric, spring means for actuating the arm to subtract the sleeve eccentricity from the shaft eccentricity, and electro-magnetic means operable with the pump member driving electric motor for adding the sleeve eccentricity to the shaft eccentricity.

JESSE s. WENTWOR'IH.