US20140037473A1 - Pumping assembly for feeding oil under pressure to a user - Google Patents
Pumping assembly for feeding oil under pressure to a user Download PDFInfo
- Publication number
- US20140037473A1 US20140037473A1 US13/981,678 US201213981678A US2014037473A1 US 20140037473 A1 US20140037473 A1 US 20140037473A1 US 201213981678 A US201213981678 A US 201213981678A US 2014037473 A1 US2014037473 A1 US 2014037473A1
- Authority
- US
- United States
- Prior art keywords
- pumping assembly
- lateral surface
- teeth
- assembly according
- toothed
- 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.)
- Abandoned
Links
- 238000005086 pumping Methods 0.000 title claims abstract description 24
- 230000008878 coupling Effects 0.000 claims 3
- 238000010168 coupling process Methods 0.000 claims 3
- 238000005859 coupling reaction Methods 0.000 claims 3
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
Images
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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
-
- 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
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0007—Radial sealings for working fluid
- F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
-
- 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
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0023—Axial sealings for working fluid
- F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
-
- 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
- F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- 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
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
-
- 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
- F04C2210/00—Fluid
- F04C2210/14—Lubricant
-
- 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
- F04C2210/00—Fluid
- F04C2210/40—Properties
- F04C2210/44—Viscosity
Definitions
- the present invention relates to a pumping assembly for feeding oil under pressure to a user.
- the present invention relates to a pumping assembly of the type comprising a gear pump and an electric motor for actuating the gear pump itself.
- the gear pump comprises a pair of gears coupled to each other, each of which comprises a gear wheel with external teeth formed at an intermediate portion of a support shaft assembled so as to rotate around a rotation axis parallel to the rotation axis of the other gear wheel.
- the two gears are mounted in a pump body comprising a sleeve, which extends around the gear wheels, has a length substantially equal to the length of the gear wheels, and is closed axially by two side elements, which are mounted in contact with the end faces of the sleeve perpendicular to the rotation axes of the gears, are engaged in a rotary manner by said support shafts, and define, together with the sleeve itself, a containing chamber of the gear wheels.
- the containing chamber is limited internally by a pair of substantially cylindrical lateral surfaces, each of which extends around a respective gear wheel, is substantially coaxial with a respective rotation axis, and presents a concavity facing the other lateral surface.
- the torque delivered by the electric motor for actuating the gear pump depends on the outlet pressure of the oil from the gear pump, on the forces of mechanical friction generated between the gears, and on the forces of viscous friction generated in the oil advanced by the gears themselves.
- the forces of viscous friction are transmitted between layers of oil adjacent to each other and are proportional, for fluids such as oil, to the viscosity and to the shear rate of the oil in a direction perpendicular to said lateral surfaces.
- the shear rate and, therefore, the viscous friction forces present the maximum values in correspondence of the clearance present between the gears, that is to say the mobile elements of the gear pump, and the pump body, namely the fixed element of the gear pump itself.
- the oil viscosity increases with a decrease of the operating temperature of the pumping assembly and that the shear rate is relatively high since the gear wheels are substantially fluid-tight radially with the relative lateral surfaces and axially with the side elements so as to fluid-tight separate an oil inlet in the containing chamber from an outlet of the oil under pressure from the containing chamber itself.
- the known pumping assemblies of the type described above have several drawbacks, mainly due to the fact that the electric motor must be dimensioned to deliver a relatively high drive torque and is therefore relatively complex and expensive.
- the purpose of the present invention is to provide a pumping assembly for feeding oil under pressure to a user that is free from the drawbacks described above and which is of simple and inexpensive implementation.
- a pumping assembly for feeding oil under pressure to a user as claimed in the appended claims.
- FIG. 1 is a schematic perspective view of a preferred embodiment of the pumping assembly of the present invention
- FIGS. 2 and 3 are two schematic perspective views of a detail of the pumping assembly of FIG. 1 ;
- FIG. 4 is a schematic cross section, with parts removed and parts enlarged for clarity, of the detail of FIGS. 2 and 3 .
- a pumping unit which is adapted to draw oil from a containing tank (not shown) at atmospheric pressure and to feed oil under pressure to a user (not shown), for example, a user of the automotive sector, and comprises a gear pump 2 , in this case a pump with external gears, substantially immersed in said containing tank (not shown) and an electric motor 3 for actuating the pump 2 itself.
- the pump 2 is provided with a pair of gears 4 coupled to each other, each of which comprises a support shaft 5 presenting a longitudinal axis 6 parallel to axis 6 of the other gear 4 , and an externally toothed gear wheel 7 , which is formed at an intermediate portion of the shaft 5 , and has a plurality of teeth 8 equally spaced about axis 6 .
- the gear wheels 4 are mounted in a pump body 9 comprising a sleeve 10 , which extends around the gear wheels 7 , presenting a length, measured parallel to axes 6 , substantially equal to the length of gear wheel 7 , also measured parallel to the axes 6 , and is limited internally by a shaped lateral wall 11 .
- the wall 11 defines two lateral surfaces 12 , each of which has, in this case, a substantially cylindrical shape with concavity facing the other surface 12 , extends around a respective gear wheel 7 , and presents a longitudinal axis 13 , which is parallel to the relative axis 6 , is distinguished from relative axis 6 , and is arranged at a distance from the axis 13 of the other surface 12 less than the sum of the radii of curvature of the two surfaces 12 .
- each surface 12 is wound in a spiral around the relative gear wheel 7 from one of its ends 14 substantially tangent to the gear wheel 7 itself so that the radial distance Dr between the surface 12 and the relative teeth 8 increases progressively in the direction of rotation of the relative gear 4 .
- each surface 12 is wound around teeth 8 of the respective gear wheel 7 according to a profile different from that described and illustrated in FIG. 4 , and presents, for example, downstream of the end 14 , a constant radial distance Dr from teeth 8 themselves.
- the sleeve 10 is closed axially by two substantially flat closing plates 15 , which are mounted on opposite sides of the sleeve 10 perpendicularly to axes 6 , are engaged in a rotary manner by the shafts 5 , each being limited axially by a respective flat lateral surface 16 facing the sleeve 10 , and are locked against the end faces of the sleeve 10 to define, together with the sleeve 10 itself, a containing chamber 17 of the gear wheels 7 .
- the chamber 17 comprises an area 18 of low pressure hydraulically connected with said containing tank (not shown) of the oil through a suction conduit 19 formed radially through the sleeve 10 , and an area 20 of high pressure, which is separated in a substantially fluid-tight manner from the area 18 , and is hydraulically connected with said user (not shown) by a delivery conduit 21 formed in part through the sleeve 10 and in part through one of the plates 15 parallel to axes 6 .
- Each plate 15 has an elongated cavity 22 , which opens towards the outside in correspondence with the relative surface 16 , presents a substantially ⁇ shape, and comprises two sections connected to each other, each of which presents a substantially circular shape, is facing axially to the teeth 8 of a relative gear wheel 7 , extends around relative axis 6 substantially at the area 20 of high pressure, and is limited by a bottom wall 24 arranged at a substantially constant axial distance Da from the teeth 8 of the relative gear wheel 7 .
- each section 23 may present a profile and an axial distance from the teeth 8 of the relative gear wheel 7 different from those described and illustrated in FIGS. 2 and 3 ;
- each plate 15 is eliminated and replaced with two cavities separated from each other and each facing the teeth 8 of the relative gear wheel 7 .
- the operation of the pump 2 requires, therefore, a relatively low driving torque even at relatively low operating temperatures and allows the use of relatively simple and inexpensive electric motors 3 .
- the external gear pump 2 is eliminated and replaced with an internal gear pump comprising a pump body, inside which are housed an internally toothed crown wheel and an externally toothed gear wheel, which presents an outer diameter smaller than the inner diameter of the crown wheel, is mounted inside of the crown wheel, and is coupled with the crown wheel itself.
- the internal gear pump further comprises at least one filling body, which is mounted inside the pump body between the crown wheel and the gear wheel, and is limited by two lateral surfaces, which are radially facing the teeth of the crown wheel and, respectively, to the teeth of the gear wheel, and present respective ends substantially tangent to the crown wheel and, respectively, to the gear wheel.
- the two lateral surfaces are wrapped helically from their ends around the crown wheel and, respectively, to the gear wheel so that the radial distance Dr between the lateral surfaces and the relative teeth increases in the direction of rotation of the crown wheel and, respectively, of the gear wheel.
- the pump body of the internal gear pump can be closed axially by two closing plates similar to the plates 15 .
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
A pumping assembly for feeding oil under pressure to a user is defined by a gear pump, which is actuated by an electric motor, and has a pair of gears, which are coupled to each other within a pump body, and are each provided with a respective plurality of teeth facing radially to a respective lateral surface of the pump body and axially to two recesses formed on two side elements of the pump body itself; the radial distance of the teeth from the respective lateral surface increasing in the direction of rotation of the gears around their own rotation axes.
Description
- The present invention relates to a pumping assembly for feeding oil under pressure to a user.
- In particular, the present invention relates to a pumping assembly of the type comprising a gear pump and an electric motor for actuating the gear pump itself.
- Generally, the gear pump comprises a pair of gears coupled to each other, each of which comprises a gear wheel with external teeth formed at an intermediate portion of a support shaft assembled so as to rotate around a rotation axis parallel to the rotation axis of the other gear wheel.
- The two gears are mounted in a pump body comprising a sleeve, which extends around the gear wheels, has a length substantially equal to the length of the gear wheels, and is closed axially by two side elements, which are mounted in contact with the end faces of the sleeve perpendicular to the rotation axes of the gears, are engaged in a rotary manner by said support shafts, and define, together with the sleeve itself, a containing chamber of the gear wheels.
- The containing chamber is limited internally by a pair of substantially cylindrical lateral surfaces, each of which extends around a respective gear wheel, is substantially coaxial with a respective rotation axis, and presents a concavity facing the other lateral surface.
- The torque delivered by the electric motor for actuating the gear pump depends on the outlet pressure of the oil from the gear pump, on the forces of mechanical friction generated between the gears, and on the forces of viscous friction generated in the oil advanced by the gears themselves.
- The forces of viscous friction are transmitted between layers of oil adjacent to each other and are proportional, for fluids such as oil, to the viscosity and to the shear rate of the oil in a direction perpendicular to said lateral surfaces.
- The shear rate and, therefore, the viscous friction forces present the maximum values in correspondence of the clearance present between the gears, that is to say the mobile elements of the gear pump, and the pump body, namely the fixed element of the gear pump itself.
- In this regard it should be specified that the oil viscosity increases with a decrease of the operating temperature of the pumping assembly and that the shear rate is relatively high since the gear wheels are substantially fluid-tight radially with the relative lateral surfaces and axially with the side elements so as to fluid-tight separate an oil inlet in the containing chamber from an outlet of the oil under pressure from the containing chamber itself.
- Since, for relatively low operating temperatures, the viscosity of the oil and, therefore, the frictional force of a viscous type are relatively high, the known pumping assemblies of the type described above have several drawbacks, mainly due to the fact that the electric motor must be dimensioned to deliver a relatively high drive torque and is therefore relatively complex and expensive.
- The purpose of the present invention is to provide a pumping assembly for feeding oil under pressure to a user that is free from the drawbacks described above and which is of simple and inexpensive implementation.
- According to the present invention a pumping assembly is provided for feeding oil under pressure to a user as claimed in the appended claims.
- The present invention will now be described with reference to the attached drawings, which illustrate a non limitative example of an embodiment, in which:
-
FIG. 1 is a schematic perspective view of a preferred embodiment of the pumping assembly of the present invention; -
FIGS. 2 and 3 are two schematic perspective views of a detail of the pumping assembly ofFIG. 1 ; and -
FIG. 4 is a schematic cross section, with parts removed and parts enlarged for clarity, of the detail ofFIGS. 2 and 3 . - With reference to
FIG. 1 , with 1 is indicated as a whole, a pumping unit, which is adapted to draw oil from a containing tank (not shown) at atmospheric pressure and to feed oil under pressure to a user (not shown), for example, a user of the automotive sector, and comprises agear pump 2, in this case a pump with external gears, substantially immersed in said containing tank (not shown) and anelectric motor 3 for actuating thepump 2 itself. - As shown in
FIGS. 2 , 3, and 4, thepump 2 is provided with a pair ofgears 4 coupled to each other, each of which comprises asupport shaft 5 presenting alongitudinal axis 6 parallel toaxis 6 of theother gear 4, and an externallytoothed gear wheel 7, which is formed at an intermediate portion of theshaft 5, and has a plurality ofteeth 8 equally spaced aboutaxis 6. - The
gear wheels 4 are mounted in apump body 9 comprising asleeve 10, which extends around thegear wheels 7, presenting a length, measured parallel toaxes 6, substantially equal to the length ofgear wheel 7, also measured parallel to theaxes 6, and is limited internally by a shapedlateral wall 11. - The
wall 11 defines twolateral surfaces 12, each of which has, in this case, a substantially cylindrical shape with concavity facing theother surface 12, extends around arespective gear wheel 7, and presents alongitudinal axis 13, which is parallel to therelative axis 6, is distinguished fromrelative axis 6, and is arranged at a distance from theaxis 13 of theother surface 12 less than the sum of the radii of curvature of the twosurfaces 12. - As a result of the eccentricity between each
axis 6 and therelative axis 13, eachsurface 12 is wound in a spiral around therelative gear wheel 7 from one of itsends 14 substantially tangent to thegear wheel 7 itself so that the radial distance Dr between thesurface 12 and therelative teeth 8 increases progressively in the direction of rotation of therelative gear 4. - Obviously, according to a variant not shown, each
surface 12 is wound aroundteeth 8 of therespective gear wheel 7 according to a profile different from that described and illustrated inFIG. 4 , and presents, for example, downstream of theend 14, a constant radial distance Dr fromteeth 8 themselves. - The
sleeve 10 is closed axially by two substantiallyflat closing plates 15, which are mounted on opposite sides of thesleeve 10 perpendicularly toaxes 6, are engaged in a rotary manner by theshafts 5, each being limited axially by a respective flatlateral surface 16 facing thesleeve 10, and are locked against the end faces of thesleeve 10 to define, together with thesleeve 10 itself, a containing chamber 17 of thegear wheels 7. - Since the
gear wheels 7 are substantially fluid-tight coupled with theends 14 of thesurfaces 12 and with thesurfaces 16 ofplates 15, the chamber 17 comprises anarea 18 of low pressure hydraulically connected with said containing tank (not shown) of the oil through asuction conduit 19 formed radially through thesleeve 10, and anarea 20 of high pressure, which is separated in a substantially fluid-tight manner from thearea 18, and is hydraulically connected with said user (not shown) by adelivery conduit 21 formed in part through thesleeve 10 and in part through one of theplates 15 parallel toaxes 6. - Each
plate 15 has anelongated cavity 22, which opens towards the outside in correspondence with therelative surface 16, presents a substantially ω shape, and comprises two sections connected to each other, each of which presents a substantially circular shape, is facing axially to theteeth 8 of arelative gear wheel 7, extends aroundrelative axis 6 substantially at thearea 20 of high pressure, and is limited by abottom wall 24 arranged at a substantially constant axial distance Da from theteeth 8 of therelative gear wheel 7. - According to some variations not shown:
- the
wall 24 of eachsections 23 may present a profile and an axial distance from theteeth 8 of therelative gear wheel 7 different from those described and illustrated inFIGS. 2 and 3 ; and - the
cavity 22 of eachplate 15 is eliminated and replaced with two cavities separated from each other and each facing theteeth 8 of therelative gear wheel 7. - The presence of a free radial space between the
teeth 8 of eachgear wheel 7 and therelative surface 12 and of a free axial space between theteeth 8 of eachgear wheel 7 and the twocavities 22 allow to reduce the shear rates present between thegear wheels 7, i.e. the mobile elements of thepump 2, and thesleeve 10 and theplates 15, i.e. the fixed elements of thepump 2 itself. - The reduction of shear rates results in the reduction of the frictional forces of a viscous type, which are, consequently, relatively small even at relatively low operating temperatures, i.e. at operating temperatures to which the oil viscosity is relatively high.
- The operation of the
pump 2 requires, therefore, a relatively low driving torque even at relatively low operating temperatures and allows the use of relatively simple and inexpensiveelectric motors 3. - According to a variant not shown, the
external gear pump 2 is eliminated and replaced with an internal gear pump comprising a pump body, inside which are housed an internally toothed crown wheel and an externally toothed gear wheel, which presents an outer diameter smaller than the inner diameter of the crown wheel, is mounted inside of the crown wheel, and is coupled with the crown wheel itself. - The internal gear pump further comprises at least one filling body, which is mounted inside the pump body between the crown wheel and the gear wheel, and is limited by two lateral surfaces, which are radially facing the teeth of the crown wheel and, respectively, to the teeth of the gear wheel, and present respective ends substantially tangent to the crown wheel and, respectively, to the gear wheel.
- The two lateral surfaces are wrapped helically from their ends around the crown wheel and, respectively, to the gear wheel so that the radial distance Dr between the lateral surfaces and the relative teeth increases in the direction of rotation of the crown wheel and, respectively, of the gear wheel.
- Obviously, the pump body of the internal gear pump can be closed axially by two closing plates similar to the
plates 15.
Claims (12)
1. Pumping assembly for feeding oil under pressure to a user, the pumping assembly comprising a gear pump, and an electric motor for actuating the gear pump; the gear pump comprising, in turn, two toothed members, which are coupled to each other, are assembled so as to rotate around respective rotation axes parallel to each other, and present respective teeth; and a pump body defining a containing chamber, which houses in its inside the two toothed members, presents, for each toothed member, a respective first lateral surface extending around, and at a given radial distance (Dr) from, the teeth of the respective toothed member, and is, furthermore, axially limited by two side elements parallel to each other and perpendicular to said rotation axes; the radial distance (Dr) increasing in the direction of rotation of the toothed members around respective rotation axes, and each side element being limited by a second lateral surface perpendicular to said rotation axes and facing the toothed members; wherein each side element presents, for each toothed member, a respective recess, which is formed on the relative second lateral surface, is facing the teeth of the respective toothed member, and is limited by a bottom wall arranged at a given axial distance from the teeth of the respective toothed member.
2. Pumping assembly according to claim 1 , wherein the axial distance is constant in the direction of rotation of the toothed members around respective rotation axes.
3. Pumping assembly according to claim 1 , wherein the axial distance increases in the direction of rotation of the toothed members around respective rotation axes.
4. Pumping assembly according to claim 1 , wherein the two recesses are connected to each other, so as to define a cavity.
5. Pumping assembly according to claim 1 , wherein the two recesses are separated from each other.
6. Pumping assembly according to claim 1 , wherein each said first lateral surface presents a coupling end coupled in fluid-tight manner to the teeth of the relative toothed member and wherein each said second lateral surface is coupled in fluid-tight manner with the teeth (8) of the toothed members.
7. Pumping assembly according to claim 6 , wherein the pump body presents an oil inlet to the containing chamber and an outlet of the oil under pressure from the containing chamber itself; the radial distance being substantially null in correspondence to each said coupling end and each said second lateral surface being arranged substantially in contact with the teeth of the toothed members so as to separate in a fluid-tight manner said inlet and said outlet from each other.
8. Pumping assembly according to claim 7 , wherein each recess extends around the respective rotation axis downstream of said inlet the direction of rotation of the respective toothed member.
9. Pumping assembly according to claim 1 , wherein each said first lateral surface presents a cylindrical shape, and is wound in a spiral around the respective toothed member.
10. Pumping assembly according to claim 9 , wherein each said first lateral surface presents a longitudinal axis parallel to, and distinct from, said rotation axis of the relative toothed member.
11. Pumping assembly according to claim 9 , wherein the pump body presents an oil inlet to the containing chamber and an outlet of the oil under pressure out of the containing chamber itself; each said first lateral surface presenting a coupling end substantially tangent to the teeth of the respective toothed member so as to separate in a fluid-tight manner said inlet and said outlet from each other.
12. Pumping assembly according to claim 1 , wherein each toothed member is an externally toothed gear wheel, each said first lateral surface presenting a substantially cylindrical shape, a given radius of curvature, and a longitudinal axis arranged at a distance from the longitudinal axis of the other said first lateral surface less than the sum of the radii of curvature of the two said first lateral surfaces.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ITBO2011A000025 | 2011-01-25 | ||
ITBO2011A000025A IT1403528B1 (en) | 2011-01-25 | 2011-01-25 | PUMPING GROUP TO SUPPLY OIL IN PRESSURE TO A USER |
PCT/IB2012/050350 WO2012101588A2 (en) | 2011-01-25 | 2012-01-25 | Pumping unit for feeding oil under pressure to a user |
Publications (1)
Publication Number | Publication Date |
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US20140037473A1 true US20140037473A1 (en) | 2014-02-06 |
Family
ID=43975262
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/981,678 Abandoned US20140037473A1 (en) | 2011-01-25 | 2012-01-25 | Pumping assembly for feeding oil under pressure to a user |
Country Status (5)
Country | Link |
---|---|
US (1) | US20140037473A1 (en) |
EP (1) | EP2668371A2 (en) |
CN (1) | CN103443401A (en) |
IT (1) | IT1403528B1 (en) |
WO (1) | WO2012101588A2 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20180190934A1 (en) * | 2016-12-29 | 2018-07-05 | Lg Display Co., Ltd. | Display Device Having an Auxiliary Electrode |
CN112283106A (en) * | 2019-07-24 | 2021-01-29 | 株式会社丰田自动织机 | Electric roots pump |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITUB20159736A1 (en) * | 2015-12-21 | 2017-06-21 | Bosch Gmbh Robert | PUMPING GROUP FOR FUEL SUPPLEMENTATION, PREFERABLY GASOIL, TO AN INTERNAL COMBUSTION ENGINE |
DE102016102433B3 (en) * | 2016-02-11 | 2017-05-11 | Steyr Motors Gmbh | Gear pump |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2103102A (en) * | 1936-05-09 | 1937-12-21 | Petroleum Heat & Power Co | Heat exchanger |
US6902382B2 (en) * | 2003-09-11 | 2005-06-07 | Matthew Peter Christensen | Gear motor start up control |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB556701A (en) * | 1941-07-05 | 1943-10-18 | Du Pont | Improvements in and relating to gear pumps |
GB550621A (en) * | 1941-07-14 | 1943-01-18 | Du Pont | Improvements in and relating to gear pumps |
US2697987A (en) * | 1951-05-30 | 1954-12-28 | Barclay Cecil Maddison | Gear type pump |
DE1293599B (en) * | 1958-01-14 | 1969-04-24 | Borg Warner | Gear pump |
DE1528949A1 (en) * | 1963-07-19 | 1969-09-11 | Bosch Gmbh Robert | Pump with adjustable throttle built into the suction line |
US3286643A (en) * | 1963-10-14 | 1966-11-22 | Dowty Technical Dev Ltd | Gear pumps and motors |
FR1457377A (en) * | 1965-07-03 | 1966-01-24 | Hydraulic gear pump allowing the use of the discharge pressure normally applied to the teeth of the pinions to obtain a balancing torque of the bearings | |
KR20040099555A (en) * | 2003-05-19 | 2004-12-02 | 현대자동차주식회사 | housing structure for oil pump |
DE102006045932A1 (en) * | 2006-09-28 | 2008-04-03 | Robert Bosch Gmbh | Gear pump with reduced pressure pulsations on the delivery side |
CN101216031A (en) * | 2007-12-26 | 2008-07-09 | 王丽 | Heavy pressure gear oil pump |
-
2011
- 2011-01-25 IT ITBO2011A000025A patent/IT1403528B1/en active
-
2012
- 2012-01-25 CN CN2012800064939A patent/CN103443401A/en active Pending
- 2012-01-25 WO PCT/IB2012/050350 patent/WO2012101588A2/en active Application Filing
- 2012-01-25 EP EP12707908.5A patent/EP2668371A2/en not_active Withdrawn
- 2012-01-25 US US13/981,678 patent/US20140037473A1/en not_active Abandoned
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2103102A (en) * | 1936-05-09 | 1937-12-21 | Petroleum Heat & Power Co | Heat exchanger |
US6902382B2 (en) * | 2003-09-11 | 2005-06-07 | Matthew Peter Christensen | Gear motor start up control |
Non-Patent Citations (3)
Title |
---|
English Machine Translation of DE 1293599 B (translated on March 21, 2015). * |
English Machine Translation of FR 1457377 A (translated on March 21, 2015). * |
English Machine Translation of FR1457377 (translated on 11/11/2015) * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20180190934A1 (en) * | 2016-12-29 | 2018-07-05 | Lg Display Co., Ltd. | Display Device Having an Auxiliary Electrode |
CN112283106A (en) * | 2019-07-24 | 2021-01-29 | 株式会社丰田自动织机 | Electric roots pump |
Also Published As
Publication number | Publication date |
---|---|
IT1403528B1 (en) | 2013-10-31 |
WO2012101588A2 (en) | 2012-08-02 |
WO2012101588A8 (en) | 2012-12-13 |
EP2668371A2 (en) | 2013-12-04 |
WO2012101588A3 (en) | 2013-03-14 |
CN103443401A (en) | 2013-12-11 |
ITBO20110025A1 (en) | 2012-07-26 |
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Legal Events
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AS | Assignment |
Owner name: TRW AUTOMOTIVE ITALIA S.R.L., ITALY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:GAMBETTI, DAVIDE;ZAMBARDI, ROBERTO;BERTAGNA, BRUNO;REEL/FRAME:031416/0644 Effective date: 20131003 |
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |