US3658452A - Gear pump or motor - Google Patents

Gear pump or motor Download PDF

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Publication number
US3658452A
US3658452A US24215A US3658452DA US3658452A US 3658452 A US3658452 A US 3658452A US 24215 A US24215 A US 24215A US 3658452D A US3658452D A US 3658452DA US 3658452 A US3658452 A US 3658452A
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US
United States
Prior art keywords
gear
pressure
piston
drive
shaft
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
US24215A
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English (en)
Inventor
Yasuo Kita
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.)
Shimadzu Corp
Shimadzu Seisakusho Ltd
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Shimadzu Corp
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Filing date
Publication date
Application filed by Shimadzu Corp filed Critical Shimadzu Corp
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Publication of US3658452A publication Critical patent/US3658452A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump

Definitions

  • the primary object of the invention is to provide new and improved gear pumps or motors including a pair of intermeshing single-helical pump gears in which the above mentioned disadvantages with known gear pumps or motors can be avoided.
  • Another object of the invention is to provide new and improved gear pumps or motors including a pair of single helical pump gears in which the thrusts acting on the intermeshing helical gears due' to various factors are all conveniently balanced though the utilization of the liquid pressure of the higher pressure side of the pumps or motors.
  • a further object of the invention is to provide improved means for applying liquid pressure from the higher pressure side of gear pumps or motors to the one end of the gear shafts thereof in such a manner that different total pressures are applied to the one end of the gear shafts according to the different total thrusts acting on those gear shafts.
  • the thrusts acting on the intermeshing helical gears are balanced with a liquid pressure.
  • the source for such liquid pressure for balancing the thrusts acting on the gears may be the higher pressure side of the gear pump or motor.
  • the liquid pressure is applied to the one end of each of the gear shafts.
  • the one end of each of the gear shafts is engaged with a piston axially slidable in a cylinder which is formed in the casing.
  • Each of the cylinder is communicated with the higher pressure side of the pump or motor so as to apply the liquid pressure to the pistons in the respective cylinders.
  • the liquid pressure receiving areas at the one ends of the gear shafts are so dimensioned as to balance the respective thrusts of different magnitudes.
  • the liquid pressure receiving area at the one end of the drive gear shaft is approximately three times the liquid pressure receiving area at the one end of the driven gear shaft.
  • FIG. I is a central vertical longitudinal sectional view of a typical form of the gear pump embodying the present invention.
  • FIG. 2 is an enlarged view of the portion indicated by the lines of 2-2 of FIG. 1.
  • FIG. 1 the present'invention is illustrated in connection with a gear pump, but it should be understood that the invention may be utilized in connection with a gear motor.
  • the pump includes a pair of intermeshing helical gears 11 and 12 mounted within a cylindrical casing 13.
  • the casing 13 comprises a cylindrical side wall body 14 and end closures l5, 16 at opposite ends of the body 14.
  • one end closure 15 is referred to as the front head while the other end closure 16 is referred to as the end cover plate.
  • the cylindrical body 14 is clamped between the front head 15 and the end cover plate 16 by .four bolts (not shown) which extends through the inside of the cylindrical body 14 from the cover plate 16 to the front head 15. Though not shown in the drawings, the ends of bolts may terminate at the front head 15 and be screw-secured thereto.
  • the front head 15 is recessed to contain a roller-bearing 19 and a suitable oil-seal assembly 20.
  • a drive shaft 21 extends through the oil-seal assembly 20 and the roller-bearing 19 and into the inside chamber of the casing 13 to engage and drive the drive gear 11.
  • the gear 11 is keyed in a conventional manner to the shaft 21.
  • the drive shaft 21 is supported on the opposite sides of the gear 11 by a pair of needle bearings 26 and 27 which are in turn received within bores 28 and 29 recessed in the front head 15 and the end cover plate 16, respectively.
  • a driven shaft 25 is supported on the opposite sides of the driven gear 12 by a pair of needle bearings 30 and 31 which are in turn received within bores 32 and 33 recessed in the front head 15 and the end cover plate 16, respectively.
  • the intermeshed helical gears 11 and 12 are supported between a pair of side sealing plates 34 and 35.
  • the side sealing plates 34 and 35 are at their inner ends in sliding contact and in sealing relationship with the end faces of the intermeshing gears 11 and 12 and abut at their outer ends the end wall 36 of the front head 15 and the end wall 37 of the end cover plate 16 via seat plates 38 and 39.
  • the seat plates 38 and 39 are always in contact with the end wall 36 of the front head 15 and the end wall 37 of the end cover plate 16, respectively.
  • the reference numerals 40 and 41 indicates sealing means which are inserted between the side sealing plate 34 and the seat plate 38, and, between the side sealing plate 35 and the seat plate 39, respectively.
  • the contact pressure for securing the sealing engagement between each of the side sealing plates 34, 35 and the intermeshing gears 11, 12 is given by liquid pressure applied to the outer end of each of the side sealing plates 34, 35.
  • liquid pressure from the higher pressure side of the pump is introduced to the gaps, which may exist between the side sealing plates 34, 35 and their respective facing seat plates 38, 39, from their peripheries.
  • Sealing means 40 and 41 define the liquid pressure receiving areas of the side sealing plates 34 and 35, respectively.
  • the liquid pressure receiving area at the outer end of the side sealing plate 34 is larger than that at the outer end of the side sealing plate 35 since the thrust force of the liquid introduced between the intermeshing gear teeth is larger at the side of the plate 34 than at the side of the plate 35.
  • This system for urging the side sealing plates to the intermeshing gears through the utilization of the liquid pressure of the higher pressure side of the pump is known as Balanced Pressure Loading. No further explanation would therefore be necessary.
  • the arrows A and B denote the thrusts which act on the helical gear 11 and 12, respectively.
  • the thrust A which act on the drive gear 11 is represented by the sum of a thrust Fa due to the intermeshing torque Tand a thrust Fp exerted by the liquid on the side sealing plates 34 and 35.
  • the discharge volume D of the pump per revolution is expressed by the following formula:
  • Fa Ft-tan is bhp tan 0 wherein 0 is the helical angle of the gears 11 and 12.
  • the above mentioned thrusts A and B acting on the gears 11 and 12 are balanced with the liquid pressure from the higher pressure side of the pump which is applied to the one end of the respective gear shafts 21 and 25.
  • the gear shafts 21 and 25 are engaged at their respective one ends with pistons 51, 52 via pressure receiving plate 53, 54.
  • the pistons 51 and 52 are slidable in axial directions within the respective cylinders 55, 56 recessed in the end cover plate 16.
  • the cylinders 55 and 56 are communicated with pressure chambers 57, 58 which are in turn communicated with the higher pressure side of the pump through passages 59, 60 and common port 61. This construction is more clearly illustrated in FIG. 2.
  • the drive shaft 21 with the drive gear 11 is formed at its end face 62 with a shallow recess 63 at which the pressure receiving plate 53 is attached and carried.
  • the pressure receiving plate 53 is in turn in contact with the piston 51 which is slidably carried in a cylinder 55 which is recessed in the end cover plate 16.
  • the reference numeral 64 indicates an O-ring attached to the piston 51.
  • the cylinder 55 is opened to a pressure chamber 57 to which a liquid pressure is supplied through the passage 59 and the port 61 from the higher pressure side (not shown) of the pump.
  • the piston 51 has a central small opening 65 which communicates the cavity formed between the surface of the pressure receiving plate 53 and the piston 51 with the pressure chamber 57.
  • the piston 51, the cylinder 55 and the pressure chamber 57 are all elongated in the direction of an extension of the central axis of the shaft 21.
  • the pressure receiving plate 54, the piston 52, the cylinder 56 and the pressure chamber 58 are arranged with respect to the driven shaft 25 is in the same manner as those for the drive shaft 21.
  • the gist of the invention resides in directly or indirectly constituting the end of the gear shaft as a pressure receiving surface, the presence of a balancing piston and pressure receiving surface is not absolutely necessary. It is also possible to directly admit pressurized liquid to the gear shaft end surface by providing a seal mechanism of superior performance in the bearing part. In this case, the gear shaft end surface itself constitutes a pressure receiving surface. Concerning all modified embodiments constituting other pressure surfaces including these modified forms, the invention will comprehend them.
  • the arrangement is not necessarily limited to the one shown in the drawing.
  • the piston area ratio for example, it is not absolutely necessary to make it 3:1 and such area may be formed depending upon the unbalanced force acting on the corresponding shaft.
  • the static pressure bearing mechanism has been constructed with pressure receiving plates interposed, such pressure receiving plates are not absolutely necessary and the balancing pistons may be disposed directly opposed to the shaft ends and it is possible to effect simpler engagement in lieu of the static pressure receiving mechanism.
  • the arrangement of the side seating plates of the bearing mechanism for the gear shafts, etc. is not limited to the one shown in the drawing.
  • the liquid handled by the gear mechanism for feeding of liquid will not be limited to oil.
  • toothform of the gears of the gear pump embodying the present invention the case described above is one in which a continuous curve toothform is used, but the invention can also be embodied in a gear pump using an involute toothform or the like which is in wide use, and the technical scope of the invention is in no sense limited with regard to these toothforms.
  • a gear pump or motor including a drive shaft, a driven shaft, a pair of intermeshing drive and driven helical gears fixedly mounted on the drive and driven shaft respectively, which drive and driven gears react an axial force on the drive and driven shaft, a casing housing the gears, the improvement comprising pressure chambers formed in said casing in alignment with and spaced from the end of each of the gear shafts toward which the axial force is directed, means outside the casing for providing communication between each pressure chamber and the higher pressure side of the pump or motor so as to have a liquid pressure supplied from the higher pressure side of the pump or motor to each pressure chamber, axially movable means located in each pressure chamber for engaging the end of the gear shaft adjacent the pressure chamber and sealing the pressure chamber, whereby the thrust from the end of the gear shaft and the liquid pressure in the pressure chamber bear against the opposite ends of the axially movable means to balance the thrust on the ends of the drive and driven shafts.
  • a gear pump or motor according to claim 2 further comprising a pressure-receiving plate interposed between each shaft end and each piston.
  • liquid pressure receiving area of the piston engaging with the drive gear shaft is approximately three times the liquid pressure receiving area of the piston engaging with the driven gear shaft.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US24215A 1969-11-18 1970-03-31 Gear pump or motor Expired - Lifetime US3658452A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP9238269 1969-11-18

Publications (1)

Publication Number Publication Date
US3658452A true US3658452A (en) 1972-04-25

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Family Applications (1)

Application Number Title Priority Date Filing Date
US24215A Expired - Lifetime US3658452A (en) 1969-11-18 1970-03-31 Gear pump or motor

Country Status (3)

Country Link
US (1) US3658452A (de)
DE (1) DE2016097C3 (de)
GB (1) GB1310289A (de)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3796526A (en) * 1972-02-22 1974-03-12 Lennox Ind Inc Screw compressor
US3932073A (en) * 1973-07-05 1976-01-13 Svenska Rotor Maskiner Aktiebolag Screw rotor machine with spring and fluid biased balancing pistons
US4017223A (en) * 1975-03-24 1977-04-12 Houdaille Industries, Inc. Axial thrust adjustment for dual screw-type pump
US5102295A (en) * 1990-04-03 1992-04-07 General Electric Company Thrust force-compensating apparatus with improved hydraulic pressure-responsive balance mechanism
EP1921319A3 (de) * 2000-03-08 2008-06-25 Mario Antonio Morselli Verdrängungsrotationspumpe mit Spiralrotoren
FR2987406A1 (fr) * 2012-02-27 2013-08-30 Pomtava Sa Pompe de dosage de peinture
US8979518B2 (en) 2009-03-12 2015-03-17 Robert Bosch Gmbh Hydraulic toothed wheel machine
US9366250B1 (en) * 2013-06-27 2016-06-14 Sumitomo Precision Products Co., Ltd. Hydraulic device
US9567999B2 (en) * 2013-05-30 2017-02-14 Marzocchi Pompe S.P.A. Gear pump or hydraulic gear motor with helical toothing provided with hydraulic system for axial thrust balance
CN107076140A (zh) * 2014-09-30 2017-08-18 大金工业株式会社 齿轮泵或齿轮马达
US20180230999A1 (en) * 2015-08-06 2018-08-16 Jurop S.P.A. Volumetric lobe compressor for equipment collecting waste material
CN110617213A (zh) * 2019-10-24 2019-12-27 山东大学 轴端动静压浮动支承的螺旋齿双圆弧齿形液压齿轮泵

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009012854A1 (de) * 2009-03-12 2010-09-16 Robert Bosch Gmbh Hydraulische Zahnradmaschine

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US681581A (en) * 1901-01-21 1901-08-27 John Richards High-pressure rotary pump.
US742231A (en) * 1901-10-07 1903-10-27 Auguste Camille Edmond Rateau Centrifugal pump.
US1620261A (en) * 1924-06-11 1927-03-08 Laval Steam Turbine Co Rotary gear pump
US1677980A (en) * 1925-08-05 1928-07-24 Montelius Carl Oscar Josef Rotary pump, motor, meter, or the like
US2095168A (en) * 1935-03-14 1937-10-05 Burghauser Franz Axial pump
US2206079A (en) * 1936-07-28 1940-07-02 Francis W Davis Pump
GB661329A (en) * 1948-06-24 1951-11-21 Guinard Paul Andre Balanced screw pumps
US2590561A (en) * 1947-12-10 1952-03-25 Montelius Carl Oscar Josef Screw pump
US2748714A (en) * 1952-10-17 1956-06-05 Fred W Henry Thrust bearing
US3481532A (en) * 1967-12-20 1969-12-02 Ingersoll Rand Co Compressor

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US681581A (en) * 1901-01-21 1901-08-27 John Richards High-pressure rotary pump.
US742231A (en) * 1901-10-07 1903-10-27 Auguste Camille Edmond Rateau Centrifugal pump.
US1620261A (en) * 1924-06-11 1927-03-08 Laval Steam Turbine Co Rotary gear pump
US1677980A (en) * 1925-08-05 1928-07-24 Montelius Carl Oscar Josef Rotary pump, motor, meter, or the like
US2095168A (en) * 1935-03-14 1937-10-05 Burghauser Franz Axial pump
US2206079A (en) * 1936-07-28 1940-07-02 Francis W Davis Pump
US2590561A (en) * 1947-12-10 1952-03-25 Montelius Carl Oscar Josef Screw pump
GB661329A (en) * 1948-06-24 1951-11-21 Guinard Paul Andre Balanced screw pumps
US2748714A (en) * 1952-10-17 1956-06-05 Fred W Henry Thrust bearing
US3481532A (en) * 1967-12-20 1969-12-02 Ingersoll Rand Co Compressor

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3796526A (en) * 1972-02-22 1974-03-12 Lennox Ind Inc Screw compressor
US3932073A (en) * 1973-07-05 1976-01-13 Svenska Rotor Maskiner Aktiebolag Screw rotor machine with spring and fluid biased balancing pistons
US4017223A (en) * 1975-03-24 1977-04-12 Houdaille Industries, Inc. Axial thrust adjustment for dual screw-type pump
US5102295A (en) * 1990-04-03 1992-04-07 General Electric Company Thrust force-compensating apparatus with improved hydraulic pressure-responsive balance mechanism
EP1921319A3 (de) * 2000-03-08 2008-06-25 Mario Antonio Morselli Verdrängungsrotationspumpe mit Spiralrotoren
US8979518B2 (en) 2009-03-12 2015-03-17 Robert Bosch Gmbh Hydraulic toothed wheel machine
FR2987406A1 (fr) * 2012-02-27 2013-08-30 Pomtava Sa Pompe de dosage de peinture
WO2013127651A1 (fr) * 2012-02-27 2013-09-06 Pomtava Sa Pompe de dosage de peinture
US9567999B2 (en) * 2013-05-30 2017-02-14 Marzocchi Pompe S.P.A. Gear pump or hydraulic gear motor with helical toothing provided with hydraulic system for axial thrust balance
US9366250B1 (en) * 2013-06-27 2016-06-14 Sumitomo Precision Products Co., Ltd. Hydraulic device
CN107076140A (zh) * 2014-09-30 2017-08-18 大金工业株式会社 齿轮泵或齿轮马达
CN107076140B (zh) * 2014-09-30 2018-02-27 大金工业株式会社 齿轮泵或齿轮马达
US20180230999A1 (en) * 2015-08-06 2018-08-16 Jurop S.P.A. Volumetric lobe compressor for equipment collecting waste material
US10871160B2 (en) * 2015-08-06 2020-12-22 Jurop S.P.A. Volumetric lobe compressor for equipment collecting waste material
CN110617213A (zh) * 2019-10-24 2019-12-27 山东大学 轴端动静压浮动支承的螺旋齿双圆弧齿形液压齿轮泵
CN110617213B (zh) * 2019-10-24 2021-06-04 山东大学 轴端动静压浮动支承的螺旋齿双圆弧齿形液压齿轮泵

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Publication number Publication date
DE2016097A1 (de) 1971-06-03
GB1310289A (en) 1973-03-14
DE2016097C3 (de) 1975-03-27
DE2016097B2 (de) 1974-08-08

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