EP0173778A1 - Improvements relating to pumps - Google Patents

Improvements relating to pumps Download PDF

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Publication number
EP0173778A1
EP0173778A1 EP84306071A EP84306071A EP0173778A1 EP 0173778 A1 EP0173778 A1 EP 0173778A1 EP 84306071 A EP84306071 A EP 84306071A EP 84306071 A EP84306071 A EP 84306071A EP 0173778 A1 EP0173778 A1 EP 0173778A1
Authority
EP
European Patent Office
Prior art keywords
pump
lobe
lobes
angle
clearance
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.)
Granted
Application number
EP84306071A
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German (de)
French (fr)
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EP0173778B1 (en
Inventor
Ian Trevor Bristow
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.)
HOBOURN ENGINEERING LIMITED
Original Assignee
HOBOURN ENGINEERING Ltd
Hobourn Eaton Ltd
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 HOBOURN ENGINEERING Ltd, Hobourn Eaton Ltd filed Critical HOBOURN ENGINEERING Ltd
Priority to EP19840306071 priority Critical patent/EP0173778B1/en
Priority to DE8484306071T priority patent/DE3481536D1/en
Publication of EP0173778A1 publication Critical patent/EP0173778A1/en
Application granted granted Critical
Publication of EP0173778B1 publication Critical patent/EP0173778B1/en
Expired 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels

Definitions

  • This invention relates to pumps and is more particularly concerned with pumps of the kind variously known as rotor pumps, Eaton pumps or N(N+1) pumps.
  • a pump comprising an internally lobed annular pump member, and an externally lobed inner pump member disposed within the outer member and arranged to rotate in mesh with the outer member about an axis which is eccentric with respect to that of the outer member, the profile of each lobe of the inner member having two flank portions interconnected by a crown portion, wherein the profiles of the two flanks of each lobe of the inner member define between them at each value of radius from the centre of the inner member an included angle which angle reaches a minimum value of 20° or less and wherein, at the position of full mesh of a lobe of the inner rotor between two lobes of the outer member, the clearance (measured radially from the centre of the inner rotor) between the crown portion of the lobe of the inner member and the co-operating portions of the outer member is greater than a working clearance, a working clearance being provided at two selected locations which are disposed at opposite circumferential ends respectively of the crown portions and which are at a common radius relative to said
  • FIGs 1, 2 and 3 respectively illustrate three forms of pump according to the invention.
  • the pumps illustrated are of the well-known N, N+1 type comprising in one example, an inner rotor mounted on a drive shaft and having N external lobes, and an outer rotor surrounding the inner rotor formed with N+1 internal lobes with which the external lobes of the inner rotor mesh.
  • the outer rotor is mounted in an external casing for rotation about an axis disposed eccentrically with respect to the axis of the drive shaft and is driven by the inner rotor.
  • This general type of pump is described in more detail in UK Patent Specification No. 596379.
  • the form of the lobes may be such as to approximate rather to that of teeth, but for convenience, the term lobes is used herein to include such forms.
  • FIG. 1 of the drawing there is illustrated a form of pump with a lobe 10 of the inner rotor fully engaged in the space between two adjoining lobes 11, 12 of the outer rotor.
  • the rotors are initially in this instance conventionally designed by shaping the outer lobes 11, 12 as arcs of circles interconnected by a cylindrical surface which is centred on the axis of the outer member, and then using the shape of the outer lobes to define the required shape of the inner lobe.
  • the lobe 10 is required to form a seal with the outer lobes 11 and 12 and at the same time to limit the depth of mesh of the inner and outer rotors, and this militates against employing small included angles in the flank regions of the inner member, because the smaller the included angle, the larger the possible extent of relative movement of the members in the radial direction for a given circumferential clearance.
  • the angle 0 commonly has a minimum value of 30 0 or more, but it is advantageous to use smaller included angles on the flanks of the inner rotor for the purpose of improved efficiency of operation.
  • the two convergent flank curves 13, 14 of the lobe 10 define at each radial section an included angle 8 and this angle decreases progressively to a minimum value of 12 0 and then increases sharply with increasing radius in the region indicated at 15 near the maximum radius of the inner rotor.
  • the profile of the outer member is modified in two respects. Firstly the profile is modified to form a radial clearance well in excess of the working clearance is left in the crown or tip regions 16 of the lobe 10 to provide a relatively large volume about the tip region of the lobe and thereby to reduce the noise level of the pump in operation.
  • the profile of the outer rotor is modified at opposite circumferential ends of the crown region to form two locations 18, 19 respectively at which the radial clearance between lobe 10 and lobes 11 and 12 is a working minimum so that the maximum relative radial movement of the two members is determined by the clearance at these two locations and is such as to provide a correct seal between the members at the diametrically opposite side of the two members.
  • the peripheral extent of the two locations 18, 19 can be selected as desired but between these two locations the clearance between the two members is in excess of a working clearance.
  • the included angle at the locations 18, 19 is 90°.
  • flanks 13, 14 of the inner member of 20° or less are employed (e.g. the flanks may be parallel to each other over part of their length and provides improved volumetric efficiency and improved driving efficiency while retaining the advantages of the large clearance in the tip region of the lobe 10.
  • the working clearance is set at two locations at opposite circumferential ends of the tip region respectively.
  • FIG. 2 shows an application of the invention to a pump in which each lobe 22 of the inner rotor is asymmetrical about a radial line through the tip of the lobe.
  • the outer rotor has lobes 23, 24 and the rotary drive is transmitted between the flank 25 of lobe 22 and the co-operating flank 26 of lobe 23.
  • the shape of the flank 26 is modified to provide a location 28 at which the clearance between the two rotors (measured in a direction parallel to a radial line through the mid-point between location 28 and the corresponding point 30 on the other flank 29) has a value such as to constitute a working clearance.
  • the engagement of location 28 and point 30 with the respective co-operating locations on the lobes 23, 24 produces a wedge-like action which serves to provide an effective limit on the depth of mesh of lobe 22 between the lobes 23, 24.
  • the clearance between the crown or tip region of lobe 22 and the co-operating portions of the outer rotor is substantially in excess of the normal working clearance.
  • FIG. 3 there is illustrated a way in which the invention can be applied to a pump of the N(N+1) type in which the lobes 30 of the inner rotor are waisted, the lobes 31a, 31b of the outer rotor being of appropriately modified profile.
  • the full lines 33, 34 show the modified profile of the outer rotor employed as a result of the application of the present invention, and the chain lines 35 indicate the modified portions of the profile.
  • the profile of the co-operating surface portions of the outer rotor is modified to reduce the clearance between the members (measured in directions parallel to the radial centre line of the lobe 30) to a value which is the lowest over the whole periphery of the lobe and which determines the maximum radial depth of mesh of lobe 30 between lobes 31a and 31b. Over the whole of the crown region between locations 36 and 37 the radial clearance between the rotors is well in excess of a working clearance.
  • the seal at the diametrically opposite side of the member will be formed by each of two lobes flanking opposite sides of the diameter engaging co-operating lobes of the outer rotor by portions which are offset from the axis of symmetry of the lobes, and it is therefore desirable to ensure that the portions of the inner lobes which form these seals are out of contact with the outer rotor at the point of full mesh, so as to avoid unnecessary wear on these portions.
  • the working clearance is set at two shoulder locations at opposite ends respectively of the tip region.
  • the modification of the profile of the outer rotor at the locations where the clearance is a minimum as described in the foregoing may be such as to form a step-like formation at such locations.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

A pump of the N, N+1 type has inner and outer lobed rotors designed to provide at the position of deepest mesh a clearance greater than a working clearance over the whole of the tip region to the lobe (10) of the inner rotor, a working clearance being defined at opposite circumferential sides of the said tip region at positions (18, 19) where tangents to the profile at a selected radial section (21) form a first included angle of 20° or more, e.g. 54°. The flanks (13, 14) of the lobe (10) define at each radial section an included angle which reduces to 20° or less, but in any event less than said first included angle.

Description

  • This invention relates to pumps and is more particularly concerned with pumps of the kind variously known as rotor pumps, Eaton pumps or N(N+1) pumps.
  • According to this invention there is provided a pump comprising an internally lobed annular pump member, and an externally lobed inner pump member disposed within the outer member and arranged to rotate in mesh with the outer member about an axis which is eccentric with respect to that of the outer member, the profile of each lobe of the inner member having two flank portions interconnected by a crown portion, wherein the profiles of the two flanks of each lobe of the inner member define between them at each value of radius from the centre of the inner member an included angle which angle reaches a minimum value of 20° or less and wherein, at the position of full mesh of a lobe of the inner rotor between two lobes of the outer member, the clearance (measured radially from the centre of the inner rotor) between the crown portion of the lobe of the inner member and the co-operating portions of the outer member is greater than a working clearance, a working clearance being provided at two selected locations which are disposed at opposite circumferential ends respectively of the crown portions and which are at a common radius relative to said centre, said locations being where tangents thereto are convergent in a radially outward direction at an angle of 200 or more to each other but greater than the first said included angle.
  • Some embodiments of the invention will now be described with reference to the accompanying diagrammatic drawings each of which shows the radially outer portions of co-operating lobes of a pump. In the drawings:
  • Figures 1, 2 and 3 respectively illustrate three forms of pump according to the invention.
  • The pumps illustrated are of the well-known N, N+1 type comprising in one example, an inner rotor mounted on a drive shaft and having N external lobes, and an outer rotor surrounding the inner rotor formed with N+1 internal lobes with which the external lobes of the inner rotor mesh. The outer rotor is mounted in an external casing for rotation about an axis disposed eccentrically with respect to the axis of the drive shaft and is driven by the inner rotor. This general type of pump is described in more detail in UK Patent Specification No. 596379. In some constructions the form of the lobes may be such as to approximate rather to that of teeth, but for convenience, the term lobes is used herein to include such forms.
  • Referring now to Figure 1 of the drawing there is illustrated a form of pump with a lobe 10 of the inner rotor fully engaged in the space between two adjoining lobes 11, 12 of the outer rotor.
  • The rotors are initially in this instance conventionally designed by shaping the outer lobes 11, 12 as arcs of circles interconnected by a cylindrical surface which is centred on the axis of the outer member, and then using the shape of the outer lobes to define the required shape of the inner lobe. The lobe 10 is required to form a seal with the outer lobes 11 and 12 and at the same time to limit the depth of mesh of the inner and outer rotors, and this militates against employing small included angles in the flank regions of the inner member, because the smaller the included angle, the larger the possible extent of relative movement of the members in the radial direction for a given circumferential clearance. In known pumps the angle 0 commonly has a minimum value of 300 or more, but it is advantageous to use smaller included angles on the flanks of the inner rotor for the purpose of improved efficiency of operation.
  • In applying the present invention, the two convergent flank curves 13, 14 of the lobe 10 define at each radial section an included angle 8 and this angle decreases progressively to a minimum value of 120 and then increases sharply with increasing radius in the region indicated at 15 near the maximum radius of the inner rotor. Also, the profile of the outer member is modified in two respects. Firstly the profile is modified to form a radial clearance well in excess of the working clearance is left in the crown or tip regions 16 of the lobe 10 to provide a relatively large volume about the tip region of the lobe and thereby to reduce the noise level of the pump in operation. Secondly, at a radial section of the inner member where the included angle is in excess of 20°, the profile of the outer rotor is modified at opposite circumferential ends of the crown region to form two locations 18, 19 respectively at which the radial clearance between lobe 10 and lobes 11 and 12 is a working minimum so that the maximum relative radial movement of the two members is determined by the clearance at these two locations and is such as to provide a correct seal between the members at the diametrically opposite side of the two members. The peripheral extent of the two locations 18, 19 can be selected as desired but between these two locations the clearance between the two members is in excess of a working clearance.
  • In one form of the pump the included angle at the locations 18, 19 is 90°.
  • In constructions according to the invention a minimum value of the included angle 8 in the flank regions 13, 14 of the inner member of 20° or less is employed (e.g. the flanks may be parallel to each other over part of their length and provides improved volumetric efficiency and improved driving efficiency while retaining the advantages of the large clearance in the tip region of the lobe 10.
  • In effect the working clearance is set at two locations at opposite circumferential ends of the tip region respectively.
  • Figure 2 shows an application of the invention to a pump in which each lobe 22 of the inner rotor is asymmetrical about a radial line through the tip of the lobe. In this case the outer rotor has lobes 23, 24 and the rotary drive is transmitted between the flank 25 of lobe 22 and the co-operating flank 26 of lobe 23. At a radial section 21 at which the included angle 8 reaches a value 20° or more (540 in this instance), the shape of the flank 26 is modified to provide a location 28 at which the clearance between the two rotors (measured in a direction parallel to a radial line through the mid-point between location 28 and the corresponding point 30 on the other flank 29) has a value such as to constitute a working clearance. The engagement of location 28 and point 30 with the respective co-operating locations on the lobes 23, 24 produces a wedge-like action which serves to provide an effective limit on the depth of mesh of lobe 22 between the lobes 23, 24. As before, the clearance between the crown or tip region of lobe 22 and the co-operating portions of the outer rotor is substantially in excess of the normal working clearance.
  • Referring now to Figure 3, there is illustrated a way in which the invention can be applied to a pump of the N(N+1) type in which the lobes 30 of the inner rotor are waisted, the lobes 31a, 31b of the outer rotor being of appropriately modified profile. The full lines 33, 34 show the modified profile of the outer rotor employed as a result of the application of the present invention, and the chain lines 35 indicate the modified portions of the profile. At locations 36, 37 on a radial section 38 on the inner rotor, where the included angle 6 has a value of 20° or more, the profile of the co-operating surface portions of the outer rotor is modified to reduce the clearance between the members (measured in directions parallel to the radial centre line of the lobe 30) to a value which is the lowest over the whole periphery of the lobe and which determines the maximum radial depth of mesh of lobe 30 between lobes 31a and 31b. Over the whole of the crown region between locations 36 and 37 the radial clearance between the rotors is well in excess of a working clearance.
  • It will be understood that where the inner rotor has an odd number of lobes, the seal at the diametrically opposite side of the member will be formed by each of two lobes flanking opposite sides of the diameter engaging co-operating lobes of the outer rotor by portions which are offset from the axis of symmetry of the lobes, and it is therefore desirable to ensure that the portions of the inner lobes which form these seals are out of contact with the outer rotor at the point of full mesh, so as to avoid unnecessary wear on these portions.
  • Thus, a large clearance is provided over the whole of the tip region, and the working clearance is set at two shoulder locations at opposite ends respectively of the tip region. In some cases, the modification of the profile of the outer rotor at the locations where the clearance is a minimum as described in the foregoing may be such as to form a step-like formation at such locations.

Claims (7)

1. A pump comprising an internally lobed annular pump member, and an externally lobed inner pump member disposed within the outer member and arranged to rotate in mesh with the outer member about an axis which is eccentric with respect to that of the outer member, the profile of each lobe of the inner member having two flank portions interconnected by a crown portion, wherein the profiles of the two flanks of each lobe of the inner member define between them at each value of radius from the centre of the inner member an inckuded angle which angle reaches a minimum value of 20° or less and wherein, at the position of full mesh of a lobe of the inner rotor between two lobes of the outer member, the clearance (measured radially from the centre of the inner rotor) between the crown portion of the lobe of the inner member and the co-operating portions of the outer member is greater than a working clearance, a working clearance being provided at two selected locations which are disposed at opposite circumferential ends respectively of the crown portions and which are at a common radius relative to said centre, said locations being where tangents thereto are convergent in a radially outward direction at an angle of 20° or more to each other but greater than the first said included angle.
2. A pump as claimed in claim 1, wherein said tangents converge at an angle in excess of 30°.
3. A pump as claimed in claim 1, wherein said tangents converge at an angle in excess of 40°.
4. A pump as claimed in claim 1, wherein said tangents converge at an angle in excess of 50°.
6. A pump as claimed in any one of the preceding claims, wherein said working clearances at said two locations are achieved by modifying the profiles of the flanks of the lobes of the outer member.
7. A pump as claimed in any one of the preceding claims, wherein the lobes of the inner member are waisted radially inward of said common radius.
8. A pump as claimed in any one of the preceding claims, wherein the crown portion of each of the lobes of the inner member is asymmetric about a radial line extending through the tip of the lobe.
EP19840306071 1984-09-05 1984-09-05 Improvements relating to pumps Expired EP0173778B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP19840306071 EP0173778B1 (en) 1984-09-05 1984-09-05 Improvements relating to pumps
DE8484306071T DE3481536D1 (en) 1984-09-05 1984-09-05 PUMP.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19840306071 EP0173778B1 (en) 1984-09-05 1984-09-05 Improvements relating to pumps

Publications (2)

Publication Number Publication Date
EP0173778A1 true EP0173778A1 (en) 1986-03-12
EP0173778B1 EP0173778B1 (en) 1990-03-07

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EP19840306071 Expired EP0173778B1 (en) 1984-09-05 1984-09-05 Improvements relating to pumps

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DE (1) DE3481536D1 (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4813853A (en) * 1986-07-19 1989-03-21 Barmag Ag Internal gear pump
FR2712638A1 (en) * 1993-11-18 1995-05-24 Barmag Luk Automobiltech Internal gear pump with discharge projections.
WO2002035097A1 (en) * 2000-10-25 2002-05-02 Eckerle Industrie-Elektronik Gmbh Internal geared wheel pump without a filler piece
EP1340912A1 (en) * 2002-03-01 2003-09-03 Hermann Härle Internal gear machine with teeth clearance
DE102012022787A1 (en) * 2012-11-22 2014-05-22 Volkswagen Aktiengesellschaft Internally controlled gear pump used in pressurized control system, has axial grooves that extend axially over entire length of inner rotor, where ratio of radius of outer tooth root surface and radius of groove is of specific value

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1251504A (en) * 1960-02-04 1961-01-20 Borg Warner Gear with new tooth profile, in particular for pumps or gear motors with internal and external teeth
GB2085969A (en) * 1980-10-17 1982-05-06 Hobourn Eaton Ltd Rotary positive-displacement pumps
EP0072636A2 (en) * 1981-08-15 1983-02-23 Concentric Pumps Limited N/N +1 lobed rotary fluid pumps

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1251504A (en) * 1960-02-04 1961-01-20 Borg Warner Gear with new tooth profile, in particular for pumps or gear motors with internal and external teeth
GB2085969A (en) * 1980-10-17 1982-05-06 Hobourn Eaton Ltd Rotary positive-displacement pumps
EP0072636A2 (en) * 1981-08-15 1983-02-23 Concentric Pumps Limited N/N +1 lobed rotary fluid pumps

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4813853A (en) * 1986-07-19 1989-03-21 Barmag Ag Internal gear pump
FR2712638A1 (en) * 1993-11-18 1995-05-24 Barmag Luk Automobiltech Internal gear pump with discharge projections.
DE4440782C5 (en) * 1993-11-18 2006-05-24 Luk Automobiltechnik Gmbh & Co. Kg Internal gear pump with displacement projections
WO2002035097A1 (en) * 2000-10-25 2002-05-02 Eckerle Industrie-Elektronik Gmbh Internal geared wheel pump without a filler piece
US6893239B2 (en) 2000-10-25 2005-05-17 Eckerle Industrie-Elektronik Gmbh Internal geared wheel pump having asymmetric tooth tips
EP1340912A1 (en) * 2002-03-01 2003-09-03 Hermann Härle Internal gear machine with teeth clearance
US6893238B2 (en) 2002-03-01 2005-05-17 Siegfried A. Eisenmann Ring gear machine clearance
DE102012022787A1 (en) * 2012-11-22 2014-05-22 Volkswagen Aktiengesellschaft Internally controlled gear pump used in pressurized control system, has axial grooves that extend axially over entire length of inner rotor, where ratio of radius of outer tooth root surface and radius of groove is of specific value

Also Published As

Publication number Publication date
DE3481536D1 (en) 1990-04-12
EP0173778B1 (en) 1990-03-07

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