US3884597A - Reciprocating pump - Google Patents

Reciprocating pump Download PDF

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Publication number
US3884597A
US3884597A US411410A US41141073A US3884597A US 3884597 A US3884597 A US 3884597A US 411410 A US411410 A US 411410A US 41141073 A US41141073 A US 41141073A US 3884597 A US3884597 A US 3884597A
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United States
Prior art keywords
chamber
plunger
diaphragm
reciprocating pump
valve
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
US411410A
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English (en)
Inventor
Kazuichi Ito
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Individual
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Individual
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Publication date
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Publication of US3884597A publication Critical patent/US3884597A/en
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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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • F04B11/0033—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a mechanical spring
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
    • 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/0009—Special features
    • F04B43/0081—Special features systems, control, safety measures
    • F04B43/009—Special features systems, control, safety measures leakage control; pump systems with two flexible members; between the actuating element and the pumped fluid
    • 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
    • F04B49/24—Bypassing
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/125—Reciprocating valves
    • F04B53/126—Ball valves
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/164—Stoffing boxes

Definitions

  • ABSTRACT A reciprocating pump comprising a pump casing having a cylinder chamber and a plunger driving chamber, a diaphragm being provided in the plunger driving chamber and defining a space with a partition separating the chambers.
  • a hollow elastic damping body is mounted in the space between the diaphragm and the partition and the hollow body communicates with the ambient atmosphere.
  • the present invention relates to a reciprocating pump incorporating a plunger and a diaphragm or bellows.
  • a reciprocating pump in accordance with this principle has the advantages of both the plunger type and the diaphragm type of reciprocating pumps while obviating the disadvantages thereof.
  • the above described reciprocating pump incorporating a plunger and a diaphragm has uniformity in pumping volume and gives a high discharge pressure (these being advantages of the plunger type reciprocating pump) and it also has resistance to leakage (which is one of the advantages of the diaphragm type reciprocating pump).
  • the above described reciprocating pump obviates a disadvantage of the plunger type reciprocating pump, namely the construction wherein the gland packing is exposed to the atomsphere. Therefore, the danger that any liquid might leak through the gland packing into the plunger drive means is obviated.
  • the above described reciprocating pump incorporating a plunger and a diaphragm also has the disadvantage that the volume of the small chamber formed on the plunger side between the diaphragm and an insidewall of the pump casing, changes drastically in accordance with the reciprocating motion of the plunger and the diaphragm.
  • the volume of the chamber is minimum, the inside pressure of the chamber will be maximum, and when the volume of the chamber is maximum, the inside pressure of the chamber will be minimum.
  • This repeated changing of the inside pressure of the chamber causes fatigue of the diaphragm, and when the fatigue exceeds a predetermined limit, the diaphragm will burst. Also such repeated changing of the volume of air or inside pressure of the chamber wastes power for work having no connection with transporting the liquid.
  • a primary object of the present invention is to provide a construction obviating the above disadvantage of a reciprocating pump incorporating a plunger and a diaphragm.
  • Another object of this invention is to provide, in a reciprocating pump incorporating a plunger and a diaphragm, a safety valve to allow liquid to escape from the cylinder chamber to a liquid inlet, when the inside pressure of the cylinder chamber exceeds a certain level.
  • Still another object of this invention is to provide, in a reciprocating pump incorporating a plunger and a diaphragm, a small chamber between the crosshead of the pump and an adjacent diaphragm for supplying lubricating oil to the means for driving the plunger of the pump.
  • the reciprocating pump according to the present invention comprises:
  • a pump casing including a partition defining on one side thereof a cylinder chamber having an inlet port with an inlet valve and an outlet port with an outlet valve, and on the other side thereof a second chamber;
  • a drive means mounted in said second chamber for driving said plunger in reciprocation
  • a diaphragm including a central portion secured between said plunger and said crosshead, and with a peripheral portion secured to said casing, said diaphragm defining a closed space with said partition;
  • a hollow elastic damping body disposed in said closed space between said diaphragm and said partition, said hollow elastic body extending through said casing and having an inner space which communicates with the ambient atmosphere.
  • said plunger can have a valve chamber with a check valve therein, said check valve being opened to communicate with said cylinder chamber and said valve chamber only when the pressure inside said cylinder chamber increases to a limit value, said valve chamber being in constant communication with the inlet port.
  • the crosshead can be formed as a piston-like body which is reciprocatably slidable in said pump casing and the crosshead can have at least two passages communicating between said second chamber and a further chamber formed between said crosshead and said diaphragm.
  • Each of said at least two passages has a check valve, and at least one of said check valves allows liquid to flow in one direction while at least one other allows liquid to flow only in the reverse direction.
  • FIGURE is a sectional view of an embodiment of the reciprocating pump according to the present invention.
  • the pump of the invention comprises a pump casing A including a cylinder chamber A, and a second chamber A for accommodating a plunger driving means, the chambers being divided by a partition A.
  • a hollow annular plunger 1 is slidably supported within cylinder chamber A in closely fitted relation.
  • the center portion of a diaphragm 2 is fixed to the base end of the plunger 1, and the peripheral portion of the diaphragm is secured in the outer shell of the pump casing A.
  • a second diaphragm 3 is provided.
  • the second diaphragm 3 has the same construction as the first diaphragm 2 and is fixed on a short stem 4 connected to the plunger 1.
  • the diaphragm 3 is secured in the outer shell of the pump casing A. It is preferred that the diaphragm 3 be parallel to the diaphragm 2.
  • One end of a crosshead 5 is connected to the short stem 4, and the other end of the crosshead 5 is pivotally connected to a slide bar 6 through a pin 7.
  • the slide bar 6 is pivotably connected at its base end to a crank 9 which is eccentrically fixed on a crank-shaft 8, one end of which extends outside the chamber A
  • the cylinder chamber A of the pump casing A has an inlet port H with an inlet check valve and an outlet port 13 with an outlet check valve 12.
  • a passage 14 extends between a location near the partition A in the cylinder chamber A, and a location upstream of the inlet check valve 10 of the inlet port 11.
  • a safety check valve 15 is provided at the end of the plunger 1, and a passage 16 in plunger 1 serves for connecting the safety check valve 15 and the passage 14.
  • the safety check valve 15 is spring-biassed and usually shut, but it opens when the pressure inside of the cylinder chamber A, increases to an unusually high value.
  • Numerals l7 and 18 designate gland packings for preventing leakage of transported liquid, and numeral 19 is a lantern ring.
  • a gland packing 20 is urged against the surface of the gland packing 18 on the side opposed to the lantern ring 19.
  • the pressure of packing 20 on packing 18 can be adjusted by tightening or loosening an adjustment screw 21.
  • the gland packing 20 has a ring-shaped portion 20a at one end abutting against the gland packing l8, and a disc portion 20b at the other end for receiving the pressure transmitted by the adjustment screw 21.
  • the ring-shaped portion 200 and the disc portion 20b are connected integrally by means of a plurality of flexible legs 200.
  • the crosshead 5 is provided with lubricating oil passages 22 and 23 with check valves 24 and 25 respectively.
  • the oil passes through the check valves 24 and 25 in opposite directions.
  • a hollow elastic body T is mounted for damping purposes, this being one of the most important elements of the present invention.
  • a part of the hollow elastic body T passes through and extends out of the pump casing A, and the inside space of the hollow elastic body T communicates with the atmosphere.
  • the portion of the hollow elastic body T in casing A is sealed by any suitable sealing means such as O-ring 27, and the space 26 is thereby sealed from the ambient atmosphere.
  • a space 28 is formed between the diaphragm 3 and the crosshead 5 and this space can be operated as a pump chamber of a diaphragm pump for circulating lubricating oil L.
  • One of the diaphragms 2 and 3 can be omitted, but considering durability and safety the use of two diaphragms is prevered.
  • the diaphragm 2 prevents any leakage of the liquid into the chamber A Since the volume of the closed space 26 changes periodically by the reciprocating movement of the plunger l and diaphragm 2, the inside pressure of the closed space 26 also varies in accordance with the change in volume of the space.
  • the hollow elastic damping body T (which is of ring-shape or other shape) and communicates with the atmosphere is mounted in the closed space 26 and when the inside pressure of the closed space 26 increases, the value of the hollow elastic body T decreases in accordance with the increased inside pressure of the space 26, and the air occupying the inside of the hollow elastic body T is exhausted into the atmosphere.
  • the volume of the closed space 26 increases in accordance with the leftward movement of the plunger 1 and the diaphragm 2, and therefore the inside pressure of the closed space 26 decreases, the volume of the hollow elastic body T increases by means of the air sucked into the body.
  • the magnitude of the change in volume and pressure of the interior space 26 is greatly reduced, and therefore, the durability of the diaphragm 2 is greatly increased. Since the portion of the hollow elastic body T extending in the casing wall is sealed by the O-ring 27, there is no fear that any liquid which has passed through the gland packing will leak outside to the pump casing.
  • the'case without the safety valve 15 will be considered. If the liquid flow stops suddenly as the result of an accident downstream of the outlet port 13, after starting rightward movement of the plunger 1, the outlet check valve 12 may not open. In such case, the inside pressure of the cylinder chamber A will increase abnormally, and the plunger driving means will be subjected to an over-load which may cause some type of damage such as overheating of the motor coils.
  • the safety valve 15 since the safety valve 15 is provided in the plunger 1, when the inside pressure of the cylinder chamber A, exceeds an allowable limit, the safety valve opens and the liquid in the cylinder chamber A, returns to the inlet port 11 through the passage 16 in the plunger 1, the lantern ring 19 and the passage 14, and therefore any type of damage can be prevented.
  • lantern ring 19 provides for constant communication between passages 14 and 16.
  • the space 28 can be used as a diaphragm pump for circulating the lubricating oil in the plunger driving means A
  • one of the diaphragms 2 and 3 can be omitted, but considering the possibility of damage to a single diaphragm, the use of two diaphragms, is preferred.
  • two diaphragms are used, if one of the two diaphragms is damaged, the function of the pump is not affected.
  • a reciprocating pump comprising:
  • a pump casing including a partition defining on one side thereof a cylinder chamber having an inlet port with an inlet valve and an outlet port with an outlet valve, and on the other side thereof a second chamber; plunger slidably supported in said casing;
  • a drive means mounted in said second chamber for driving said plunger in reciprocation
  • a diaphragm including a central portion secured between said plunger and said crosshead, and with a peripheral portion secured to said casing, said diaphragm defining a closed space with said partition;
  • a hollow elastic damping body disposed in said closed space between said diaphragm and said partition, said hollow elastic body extending through said casing and having an inner space which communicates with the ambient atmosphere.
  • a reciprocating pump according to claim 1, wherein said diaphragm defines a second space with said crosshead, said crosshead having at least two passages for connecting the second space with said second chamber, a check valve for each of said at least two passages, at least one of said check valves allowing liquid to flow only from said second space to said second chamber and at least one other check valve allowing liquid to flow in reverse direction from said second chamber to said second space.
  • a reciprocating pump according to claim 1, comprising sealing means between said elastic damping body and said casing.
  • a reciprocating pump according to claim 1 comprising a second diaphragm between the first diaphragm and said cross-head, the two diaphragms being parallel to one another.
  • a reciprocating pump according to claim 1, wherein said plunger has a valve chamber therein communicating with said inlet port through a fluid passage, said valve chamber including a check valve which is normally closed, but which is opened and thereby causes said cylinder chamber to communicate with said inlet port through said valve chamber and fluid passage when the pressure inside said cylinder chamber increases to a predetermined excessive value.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US411410A 1973-06-04 1973-10-31 Reciprocating pump Expired - Lifetime US3884597A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP48061833A JPS527562B2 (zh) 1973-06-04 1973-06-04

Publications (1)

Publication Number Publication Date
US3884597A true US3884597A (en) 1975-05-20

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ID=13182481

Family Applications (1)

Application Number Title Priority Date Filing Date
US411410A Expired - Lifetime US3884597A (en) 1973-06-04 1973-10-31 Reciprocating pump

Country Status (6)

Country Link
US (1) US3884597A (zh)
JP (1) JPS527562B2 (zh)
DE (1) DE2355191C3 (zh)
FR (1) FR2232225A5 (zh)
GB (1) GB1412024A (zh)
IT (1) IT994387B (zh)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3951569A (en) * 1975-05-02 1976-04-20 General Motors Corporation Air conditioning compressor
US5358389A (en) * 1992-09-10 1994-10-25 Electrolux Research & Innovation Aktiebolag Two-stage compression vacuum pump having valved piston and power limiting valve
US5525045A (en) * 1993-06-11 1996-06-11 Samsung Electronics Co., Ltd. Reciprocating compressor
AU684283B2 (en) * 1994-04-11 1997-12-11 Giovanni Cefis A submerged pump with coaxial opposing modular pistons, operated by double eccentric cams or similar
US20050265862A1 (en) * 2004-06-01 2005-12-01 Shinya Yamamoto Pump
US20070297926A1 (en) * 2006-06-21 2007-12-27 Mingxian Wang Multistep diaphragm pump
CN101603515B (zh) * 2009-07-02 2011-06-01 四川杰特机器有限公司 进口压力平衡式增压注水泵
CN108757367A (zh) * 2018-07-24 2018-11-06 潍坊胜利石化机械有限公司 往复式增压泵
CN111794929A (zh) * 2020-08-12 2020-10-20 宁波合力机泵股份有限公司 液力平衡往复泵
US11396868B2 (en) * 2020-03-09 2022-07-26 Schaeffler Technologies AG & Co. KG Linear actuator pumping system

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS53139204A (en) * 1977-05-12 1978-12-05 Shikutani Kk Horizontal type plunger pump
JPS5471701U (zh) * 1978-09-22 1979-05-22
JPS5571031A (en) * 1978-11-24 1980-05-28 Hitachi Ltd Semiconductor device
DE3210821C2 (de) * 1982-03-24 1986-01-09 Grünbeck Wasseraufbereitung GmbH, 8884 Höchstädt Dosierpumpe
DE3444978A1 (de) * 1984-12-10 1986-06-12 Berthold H. Dr. 5630 Remscheid Daimler Vorrichtung zur speicherung bzw. uebertragung von energie
JPH0615414B2 (ja) * 1985-08-13 1994-03-02 松下電器産業株式会社 レンズ成形方法
JPH0617240B2 (ja) * 1985-11-26 1994-03-09 松下電器産業株式会社 ガラスレンズの成形方法
DE3901071A1 (de) * 1989-01-16 1990-08-02 Uraca Pumpen Kolbenpumpe
EP1382851A1 (de) 2002-07-19 2004-01-21 CRENSO GmbH Creative Energy Solutions Pumpe für Flüssigkeiten und Dichtungsanordnung mit Pumpe für eine zirkulierende Sperrflüssigkeit
US8337175B2 (en) 2009-12-22 2012-12-25 Smith & Nephew, Inc. Disposable pumping system and coupler
CN111156155B (zh) * 2019-12-29 2021-11-12 陕西航天动力高科技股份有限公司 一种防止隔膜泵油液浪费的密封结构

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2795668A (en) * 1955-03-03 1957-06-11 Paul Asmussen Actuating means for electric light bulbs
US3118389A (en) * 1964-01-21 Contaminant barrier for reciprocating pumps
US3299828A (en) * 1964-12-16 1967-01-24 Lox Equip Reciprocating cryogenic pump
US3415198A (en) * 1966-08-16 1968-12-10 George J. Lappo Pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3118389A (en) * 1964-01-21 Contaminant barrier for reciprocating pumps
US2795668A (en) * 1955-03-03 1957-06-11 Paul Asmussen Actuating means for electric light bulbs
US3299828A (en) * 1964-12-16 1967-01-24 Lox Equip Reciprocating cryogenic pump
US3415198A (en) * 1966-08-16 1968-12-10 George J. Lappo Pump

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3951569A (en) * 1975-05-02 1976-04-20 General Motors Corporation Air conditioning compressor
US5358389A (en) * 1992-09-10 1994-10-25 Electrolux Research & Innovation Aktiebolag Two-stage compression vacuum pump having valved piston and power limiting valve
US5525045A (en) * 1993-06-11 1996-06-11 Samsung Electronics Co., Ltd. Reciprocating compressor
AU684283B2 (en) * 1994-04-11 1997-12-11 Giovanni Cefis A submerged pump with coaxial opposing modular pistons, operated by double eccentric cams or similar
US20050265862A1 (en) * 2004-06-01 2005-12-01 Shinya Yamamoto Pump
US20070297926A1 (en) * 2006-06-21 2007-12-27 Mingxian Wang Multistep diaphragm pump
CN101603515B (zh) * 2009-07-02 2011-06-01 四川杰特机器有限公司 进口压力平衡式增压注水泵
CN108757367A (zh) * 2018-07-24 2018-11-06 潍坊胜利石化机械有限公司 往复式增压泵
US11396868B2 (en) * 2020-03-09 2022-07-26 Schaeffler Technologies AG & Co. KG Linear actuator pumping system
CN111794929A (zh) * 2020-08-12 2020-10-20 宁波合力机泵股份有限公司 液力平衡往复泵

Also Published As

Publication number Publication date
DE2355191C3 (de) 1978-03-23
IT994387B (it) 1975-10-20
JPS509804A (zh) 1975-01-31
DE2355191A1 (de) 1974-12-12
DE2355191B2 (de) 1977-07-28
FR2232225A5 (zh) 1974-12-27
GB1412024A (en) 1975-10-29
JPS527562B2 (zh) 1977-03-03

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