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Publication numberUS3572981 A
Publication typeGrant
Publication dateMar 30, 1971
Filing dateJul 1, 1969
Priority dateJul 1, 1969
Also published asCA919013A1, DE2027183A1
Publication numberUS 3572981 A, US 3572981A, US-A-3572981, US3572981 A, US3572981A
InventorsKenneth L Hagemeyer, Vernon W Pearson
Original AssigneeGreenlee Bros & Co
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Hermetically sealed pump
US 3572981 A
Abstract  available in
Images(3)
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Claims  available in
Description  (OCR text may contain errors)

United States Patent Vernon W. Pearson;

Kenneth L. Hagemeyer, Rockford, Ill. 838,115

July 1, 1969 Mar. 30, 1971 Greenlee Bros & Company Rockford, lll.

Inventors Appl. No. Filed Patented Assignee HERMETlCALLY SEALED PUMP 1 Claim, 6 Drawing Figs.

US. Cl 417/415, 417/420 Int. Cl ..F04b 17/00, H02k 5/10 Field of Search; 103/87 (M), 171,40; 230/15 (MC),285, 58;4l7/415,

References Cited UNITED STATES PATENTS 1 l/l9l 1 Hamilton 103/40 7/1934 Maccabee 230/185X 12/1952 Ramclow 230/58 3/1963 Sudmeier 310/104 4/1963 Tomlinson 64/6 Primary Examiner-Robert M. Walker Attorney-James H. Bower ABSTRACT: A hermetically sealed pump having a pair of rotatable magnetic discs, separated by a nonmagnetic member; one magnetic disc being permanently affixed to a drive shaft of a motor, and the other magnetic disc being affixed to a fluid pumping means.

Patented March 30, 1971 3 Sheets-Sheet 1 WAX/60M ATTORNEYS Patented March 30, 1971 3,572,981

3 Sheets-Sheet 2 ATTORNEYS Patented March 30, 1971 3 Sheets-Sheet 5 IKNVENTORS Ai/VA i/V/ z. Amer/wins? A. T T o R N E Y s HERMIETICALIX SEALED PUMP BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to a hermetically sealed pump in which fluid is moved from one location to another by means of a pump being driven by a pair of permanent magnetic discs. The permanent magnetic disc connected to the displacement pump is driven by another permanent magnetic disc connected to the shaft of a motor. The magnetic discs are separated by a nonmagnetic and nonconducting element.

2. Description of the Prior Art I It is known to move or pump liquid in a system that requires the system to be hermetically sealed from external-environment. However, the apparatus and methods used heretofore have proved to be of low efficiency compared with applicants device which pumps liquids at a high efficiency, in a safe manner, and in a hermetically sealed environment.

SUMMARY OF THEINVENTION According to the present invention, the pump is hermetically sealed against the external environment. The movement of the fluid is caused by two permanent magnetic discs,

separated by a nonmagnetic and nonconducting seal; one magnetic disc being driven by a motor. The driven magnetic disc transmits rotary motion through the nonmagnetic seal to the other magnetic disc. The second driven magnetic disc is connected to a pump means which pumps the fluid through the unit.

BRIEF DESCRTPTION OF THE DRAWINGS FIG. 1 shows an elevational view of the pump assembly unit connected to a motor;

FilG. 2 shows an end view of the pump unit with parts being broken away, marrow the inlet and outlet parts of thepump;v

FIG. 3 shows' a cross-sectional view of the pump showing the novel drive means;

FiG. 4 shows a magnetic disc of the type used in the drive means;

FIG. 5 shows an elevational view of the pump housing; and

FIG. ti shows a perspective view of the piston drive oscillating ring.

DESCRIPTION OF THE INVENTION The hermetically sealed pump, generally indicated at 10, shown in FIG. i, is connected to the mounting adapter 13 of motor unit by means of threaded bolts 15. Fluid is adapted to enter pump If) by means of pump inlet line 17 and exit through line l9.

Referring more specifically to FIG. 3, the shaft 21 os motor i2 is threaded connected to an adapter 23. The adapter 23 is held thereto by means of a threaded set screw 25. The motor driven magnetic disc 27'is connected to the adapter 23 and attached to the reinforcing ring 29 by epoxy or other suitable means. This comprises the motor or driving side of the unit.

The pump or driven side of the unit comprises a pump shaft housing 33 mounted betweenthe motor mounting adapter 13 and the pump block 33. Seals 35 and 37 are interposed between each mounted housing and pump block to prevent leakage of fluid to the atmosphere. The pump shaft housing 31 is comprised of a recessed chamber39 and an axial bore d1. Within the bore M is a carbon, ceramic bushing or other suitable material d3 which provides rotational stability of eccentric shaft 47. The eccentric shaft adapter 45 is secured to the threaded end 51 of shaft 47 by means of a threaded set screw $3. A magnetic disc 57 is connected to the adapter 4-5 and attached to the reinforcing ring by epoxy or other suitable means. A nonmagnetic and nonconducting seal 59 is interposed between the two magnetic discs 27 and 57 respectively for purposes to be hereinafter disclosed.

As shown in FIG. the magnetic disc is of a permanent magnetic type with multiple poles about the respective face thereof. The laws of magnetism clearly define that similar polarity will repel each other and unlike polarity will attract each other; thus the polarity on opposing faces or a pair of magnetic discs, such as disclosed herein, will repel and attract each other in continuous and simultaneous fashion. It has been found that for purposes disclosed herein, a magnetic disc with four or more magnetic poles performs with the efficiency desired.

In the operation, as the magnetic disc 27 is rotated by means of motor 12, the other magnetic disc 57 is caused to rotate by means of the magnetic coupling between the two opposing faces of the magnetic discs. The seal 59, being of nonmagnetic quality allows the transfer of the rotating magnetic field, thereby causing substantially equal rotation of the driven magnetic disc 57. It is to be noted that when the maximum torque of a synchronous drive, such as disclosed here, is exceeded, the follower or driven magnetic disc falls out of step and stops. The load cannot be picked up again unless the driving member is stopped and the unit restarted. The proper adjustment of magnetic gap is determined by threaded adjustment of eccentric shaft and/or motor shaft. As the gap is increased, the torque is reduced thereby reducing the magnetic pull between the discs. The purpose of changing the gap is primarily for operating the pump at maximum operating capabilities and secondly to provide a much needed safety feature by eliminating the usual safety or relief valve found in ordinary hydraulic systems.

As shown in FIG. 3, the fluid is adapted to be pumped by a fluid displacement pump means. Referring more specifically to FIG. 2 and FIG. 5, the fluid is adapted to enter intake port 61, through intake recess 63 of pump block 33, to the internal inlet port 65 into bore 67 of inlet insert seat 69. Inlet disc 71 is seated on the insert seat 69 to allow fluid to enter at specified times and prevent the fluid to reverse flow at the junction. To adjust the amount of fluid entering, an adjusting screw 73 is threaded into bore 75 to a predetermined distance and then set screw 77 is taper threaded into slotted bore 79 of adjusting screw 73, thereby expanding the head of the adjusting screw '73 to hold it in this position after adjustment has been made. A pipe plug Si is threaded into the bore #83 of the pump block 33 for sealing the access holes after making adjustments of the adjusting screw 73. Thus, it is apparent that the amount of fluid flow can easily be varied by setting the adjusting screw 73.

Referring now to FIG. 2 and FIG. 3, the movement of the fluid is caused by reciprocation of the pump means, which comprises a piston '55 in bore 87 of plunger sleeve d9. Plunger sleeve 89 is in turn slidable in bore he of block 33 with a pipe plug 88 threadedly fastened thereto. Each piston 35 is con nected for reciprocating movement to a piston drive oscillating ring 91, by means of a pivot pin 93. A clevis bushing 95 surrounds each pivot pin 93. The piston drive oscillating ring is in turn connected to the eccentric cam portion 97 of eccentric shaft 47. An eccentric bushing 99 protects the bearing surface of the eccentric cam portion 9 7 to minimize wear between it and the oscillating ring 91. As shown in FIG. 3 the eccentric shaft 47 comprises the threaded end 5i adjacent the axial shaft, and an eccentric cam portion 97 between the shoulder abutment l0 and pilot bearing I03. Pilot bushing M5 in pilot bore I07 of block 33 prevents radial thrust of the eccentric shaft 47 when rotated. Any axial movement of the eccentric shaft 47 is retained by the thrust washer W9.

As shown in HO. 2, a pair of piston drive oscillating rings 95 are oscillated inrecessed bore Iii of pump block 33 causing pistons to move radially in a reciprocating manner as the eccentric shaft 47 is rotated by magnetic disc 57. This is accomplished by providing the piston drive oscillating ring 9i with a segment I15 extending perpendicular to, on one side of the ring 9i, and parallel to the bore of the ring i i. The bore surface T16 is to provide the piston return. The segment M5, which provides the piston advance, comprises two segmented portions M5 and M6 separated by a radially extended arccd recess 13. A bore lid extends through both segmented portions M5 and 1%, and parallel to the bore of ring 91, for reception of pin 93. Thus, as the eccentric shaft 47 is rotated by the magnetic disc 57, the eccentric cam portion 97 is eccentrically rotated, and the piston drive oscillating ring 91 is caused to be moved radially in an oscillatory motion thereby effecting radial reciprocation of the piston. The arced recess 113 allows oscillatory movement of ring 91 with respect to the pivot pin 93.

On the inlet side of the pump, with the movement of the piston 85 radially inward, a suction is formed causing the disc 71 to move upward against the end of adjusting screw 73, allowing fluid to flow from bore 67, port 65, and recess channel 63 to flow by disc 71 and enter channel 317 to bore 139 of exit insert seat ll21l. n the exhaust side of the pump, a disc 123 is seated on top of the exit insert seat 1211, with an adjusting screw 1125 threadedly seated for adjustment of fluid flow therethrough. Set screw 127 is threaded in taper threaded and slotted bore 129 of adjusting screw 125 to hold it in position once the fluid flow adjustment has been made. As on the inlet side of thepump, a pipe plug i131 is threaded into bore R33 of the pump block 33 for sealing the access holes after making adjustments on the adjusting screw 125.

with the movement of piston 85 radially outward, as viewed in PEG. 2, the inlet disc 71 moves against the inlet insert seat 6& and thus prevents fluid flow from entering bore 67, port 65 and recem channel 63; however, the exit disc 123 is pushed open by the pressure of fluid flow and thus allows the fluid to escape into exit channel 1135 to exit port 137, and thence out through line 19.

The high efficiency of this unit is attributed to the pumping unit being hermetically sealed from the driving means. Another important feature is that in a corrosive fluid mixture, such as ammonia and others, the bearing parts are able to withstand the corrosive action of the fluid; that is, bushing 43, washer Mt bushing 95, bushing 9'9, M195, 89 are made of carbon, or other suitable material. it is to be noted that the fluid is t allowed to enter all areas on the driven or pump side of the unit by means of allowing fluid to flow from recess channel 63 through slots 139 and 141 of pump block 33, through holes 143 of pump shaft housing 3R, as shown in FIG. 2 and FIG. 5.

it is to be further noted that the capabilities of this hermetically sealed pump unit encompass the use of food substances.

I claim: l. in a hermetically sealed pump, comprising: i. a motor means;

A. a first magnetic disc connected to the shaft of said motor means; II. a pumping means;

A. a second magnetic disc connected to a shaft of said pumping means; B. piston drive means connected to said excentric shaft,

said piston drive means comprises: 1. a pair of piston drive oscillating rings; 2. each of said piston drive oscillating rings comprises:

a. an annular ring portion, having an axial bore therethrough, to provide for the piston movement;

b. a piston advance segment connected on one side of said annular ring portion extending perpendicular thereto and parallel to the axis of said axial bore;

c. said segment having an arced recess extending outwardly radially from said axial bore and providing two segmented portions;

(1. a bore extending through said two segmented portions, adapted to receive a piston pin therethrough;

3. a piston connected to said segmented portions, by

means of said piston pin; C. inlet and outlet flow means; and ill. a nonconducting and nonmagnetic seal interposed between said first and said second magnetic discs.

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US1008816 *May 6, 1911Nov 14, 1911William L HamiltonPump.
US1965198 *Jul 7, 1933Jul 3, 1934Stewart Warner CorpCompressor lubricating system
US2622788 *Jan 19, 1946Dec 23, 1952Mills Ind IncRefrigeration compressor
US3080495 *May 13, 1958Mar 5, 1963Gustav H SudmeierCompressor apparatus
US3085407 *Mar 20, 1962Apr 16, 1963Sprague Engineering CorpCoupling means
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US5039061 *Jan 26, 1990Aug 13, 1991John H. Carter Co., Inc.Magnetically actuated linear valve operator and method
US5066200 *May 17, 1990Nov 19, 1991Ansimag, Inc.Double containment pumping system for pumping hazardous materials
US5158440 *Nov 8, 1991Oct 27, 1992Ingersoll-Rand CompanyIntegrated centrifugal pump and motor
US5253986 *May 12, 1992Oct 19, 1993Milton Roy CompanyImpeller-type pump system
US5564908 *Feb 14, 1994Oct 15, 1996Phillips Engineering CompanyFluid pump having magnetic drive
US6024542 *Oct 10, 1996Feb 15, 2000Phillips Engineering Co.Piston pump and method of reducing vapor lock
US6179568Dec 14, 1999Jan 30, 2001Phillips Engineering Co.Piston pump and method of reducing vapor lock
CN100545460CMar 29, 2006Sep 30, 2009日本电产三协株式会社Magnetic coupling pump unit
Classifications
U.S. Classification417/415, 417/420
International ClassificationF04B1/04, F04B15/04, F04B1/053, F04B49/22, F04B9/02
Cooperative ClassificationF04B49/225, F04B15/04, F04B9/02, F04B1/053, F04B1/0426
European ClassificationF04B49/22A, F04B1/053, F04B1/04K5, F04B15/04, F04B9/02