US3572981A - Hermetically sealed pump - Google Patents

Hermetically sealed pump Download PDF

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Publication number
US3572981A
US3572981A US838115A US3572981DA US3572981A US 3572981 A US3572981 A US 3572981A US 838115 A US838115 A US 838115A US 3572981D A US3572981D A US 3572981DA US 3572981 A US3572981 A US 3572981A
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US
United States
Prior art keywords
piston
bore
pump
axial bore
segmented portions
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US838115A
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English (en)
Inventor
Vernon W Pearson
Kenneth L Hagemeyer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Greenlee Brothers and Co
Original Assignee
Greenlee Brothers and Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Greenlee Brothers and Co filed Critical Greenlee Brothers and Co
Application granted granted Critical
Publication of US3572981A publication Critical patent/US3572981A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/04—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being hot or corrosive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical

Definitions

  • 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.
  • the pump is hermetically sealed against the external environment.
  • the movement of the fluid is caused by two permanent magnetic discs,
  • 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.
  • 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
  • FIG. ti shows a perspective view of the piston drive oscillating ring.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the fluid is adapted to be pumped by a fluid displacement pump means.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • this hermetically sealed pump unit encompass the use of food substances.
  • said piston drive means comprises: 1. a pair of piston drive oscillating rings; 2. each of said piston drive oscillating rings comprises:
  • annular ring portion having an axial bore therethrough, to provide for the piston movement
  • 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;
  • said segment having an arced recess extending outwardly radially from said axial bore and providing two segmented portions;

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US838115A 1969-07-01 1969-07-01 Hermetically sealed pump Expired - Lifetime US3572981A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US83811569A 1969-07-01 1969-07-01

Publications (1)

Publication Number Publication Date
US3572981A true US3572981A (en) 1971-03-30

Family

ID=25276302

Family Applications (1)

Application Number Title Priority Date Filing Date
US838115A Expired - Lifetime US3572981A (en) 1969-07-01 1969-07-01 Hermetically sealed pump

Country Status (4)

Country Link
US (1) US3572981A (enExample)
CA (1) CA919013A (enExample)
DE (1) DE2027183A1 (enExample)
FR (1) FR2056165A5 (enExample)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD282546S (en) 1982-02-26 1986-02-11 Tokyo Shibaura Denki Kabushiki Kaisha Rotary compressor
US5039061A (en) * 1990-01-26 1991-08-13 John H. Carter Co., Inc. Magnetically actuated linear valve operator and method
US5066200A (en) * 1990-05-17 1991-11-19 Ansimag, Inc. Double containment pumping system for pumping hazardous materials
US5158440A (en) * 1990-10-04 1992-10-27 Ingersoll-Rand Company Integrated centrifugal pump and motor
US5253986A (en) * 1992-05-12 1993-10-19 Milton Roy Company Impeller-type pump system
US5564908A (en) * 1994-02-14 1996-10-15 Phillips Engineering Company Fluid pump having magnetic drive
US6024542A (en) * 1994-02-14 2000-02-15 Phillips Engineering Co. Piston pump and method of reducing vapor lock
USD450328S1 (en) 1999-10-29 2001-11-13 Sanden Corporation Refrigerant compressor for a vehicle air conditioner
US20050061846A1 (en) * 2003-08-14 2005-03-24 Martin Automatic, Inc. Magnetic roller
CN100545460C (zh) * 2005-03-29 2009-09-30 日本电产三协株式会社 磁耦合泵装置
US20140077646A1 (en) * 2012-09-18 2014-03-20 Honeywell International Inc. Shaft coupling apparatus, rotary fluid damper, and deployable device with magnetic coupling mechanism
US20140117824A1 (en) * 2011-06-14 2014-05-01 Makoto Hayami Constant-temperature device provided with rotating specimen table

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2635828B1 (fr) * 1988-08-23 1994-03-11 Commissariat A Energie Atomique Machine volumetrique de type pompe ou compresseur etanche aux produits pompes
FR2635830B1 (fr) * 1988-08-23 1993-10-22 Commissariat A Energie Atomique Machine volumetrique de type pompe ou compresseur depourvue de lubrification
DE29923340U1 (de) * 1999-08-26 2001-04-26 Becker, Peter, Dipl.-Ing., 59423 Unna Berührungsloses gas- und druckdichtes Antriebsmitnahmesystem

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1008816A (en) * 1911-05-06 1911-11-14 William L Hamilton Pump.
US1965198A (en) * 1933-07-07 1934-07-03 Stewart Warner Corp Compressor lubricating system
US2622788A (en) * 1946-01-19 1952-12-23 Mills Ind Inc Refrigeration compressor
US3080495A (en) * 1958-05-13 1963-03-05 Gustav H Sudmeier Compressor apparatus
US3085407A (en) * 1962-03-20 1963-04-16 Sprague Engineering Corp Coupling means

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1008816A (en) * 1911-05-06 1911-11-14 William L Hamilton Pump.
US1965198A (en) * 1933-07-07 1934-07-03 Stewart Warner Corp Compressor lubricating system
US2622788A (en) * 1946-01-19 1952-12-23 Mills Ind Inc Refrigeration compressor
US3080495A (en) * 1958-05-13 1963-03-05 Gustav H Sudmeier Compressor apparatus
US3085407A (en) * 1962-03-20 1963-04-16 Sprague Engineering Corp Coupling means

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD282546S (en) 1982-02-26 1986-02-11 Tokyo Shibaura Denki Kabushiki Kaisha Rotary compressor
US5039061A (en) * 1990-01-26 1991-08-13 John H. Carter Co., Inc. Magnetically actuated linear valve operator and method
US5066200A (en) * 1990-05-17 1991-11-19 Ansimag, Inc. Double containment pumping system for pumping hazardous materials
US5158440A (en) * 1990-10-04 1992-10-27 Ingersoll-Rand Company Integrated centrifugal pump and motor
US5253986A (en) * 1992-05-12 1993-10-19 Milton Roy Company Impeller-type pump system
US6024542A (en) * 1994-02-14 2000-02-15 Phillips Engineering Co. Piston pump and method of reducing vapor lock
US5564908A (en) * 1994-02-14 1996-10-15 Phillips Engineering Company Fluid pump having magnetic drive
US6179568B1 (en) 1994-02-14 2001-01-30 Phillips Engineering Co. Piston pump and method of reducing vapor lock
USD450328S1 (en) 1999-10-29 2001-11-13 Sanden Corporation Refrigerant compressor for a vehicle air conditioner
US20050061846A1 (en) * 2003-08-14 2005-03-24 Martin Automatic, Inc. Magnetic roller
CN100545460C (zh) * 2005-03-29 2009-09-30 日本电产三协株式会社 磁耦合泵装置
US20140117824A1 (en) * 2011-06-14 2014-05-01 Makoto Hayami Constant-temperature device provided with rotating specimen table
US9364082B2 (en) * 2011-06-14 2016-06-14 Rorze Corporation Constant-temperature device provided with rotating specimen table
US20140077646A1 (en) * 2012-09-18 2014-03-20 Honeywell International Inc. Shaft coupling apparatus, rotary fluid damper, and deployable device with magnetic coupling mechanism
US9362812B2 (en) * 2012-09-18 2016-06-07 Honeywell International Inc. Shaft coupling apparatus, rotary fluid damper, and deployable device with magnetic coupling mechanism

Also Published As

Publication number Publication date
DE2027183A1 (de) 1971-01-21
FR2056165A5 (enExample) 1971-05-14
CA919013A (en) 1973-01-16

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