EP3870877A2 - Curvilinear circular-arc tooth gears for use in external gear pumps - Google Patents
Curvilinear circular-arc tooth gears for use in external gear pumpsInfo
- Publication number
- EP3870877A2 EP3870877A2 EP19875034.1A EP19875034A EP3870877A2 EP 3870877 A2 EP3870877 A2 EP 3870877A2 EP 19875034 A EP19875034 A EP 19875034A EP 3870877 A2 EP3870877 A2 EP 3870877A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- gear
- tooth
- profile
- ccat
- axial
- 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.)
- Withdrawn
Links
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
-
- 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
- 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
-
- 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
- F04C2230/00—Manufacture
- F04C2230/10—Manufacture by removing material
Definitions
- the present invention relates generally to gears, and more particularly to gears used in gear pumps.
- the basic function of an external gear pump as shown in FIG. 1 is to drive the flow of a fluid through the rotary action of two meshed gears.
- the gear teeth At one side of the meshing zone (termed the suction side), the gear teeth unmesh, creating a void that draws fluid into the tooth spaces of the gears. These fluid packets are then rotated around the gear into the discharge region; at this side the teeth mesh together, driving the fluid out of the inter-tooth spaces. This pushes the fluid out the discharge of the pump through whatever hydraulic load is connected to the pump.
- a gear pump will pressurize the fluid to whatever pressure is required to drive the flow rate created by the meshing gears (a mechanical analog to a current-limited power supply).
- the most common gear tooth profile used in gear pumps is an involute profile.
- the primary advantages of the involute profile is that it provides smooth, consistent contact between two gears during meshing, and that it is relatively cost-effective to machine involute gears using basic cutting and hobbing techniques.
- a curvilinear circular-arc-toothed (CCAT) gear for improving gear performance and reducing noise while avoiding axial loads common to helical gears includes: an annular gear body; and a set of gear teeth, with each tooth extending radially away from the gear body and extending axially along the gear body.
- the gear tooth has a cross-sectional profile transverse to the rotational axis of the gear body, the cross-sectional profile formed from a hybridization of two or more curves, the two or more curves defining a tooth tip, a tooth flank, and a tooth root.
- the gear tooth has an axial tooth profile defining a circumferential positioning of the gear tooth on the gear body relative to a respective axial positioning of the gear tooth on the gear body, the axial tooth profile being symmetric across the midplane of the gear to reduce axial loading on gears induced by gear meshing.
- the axial tooth profile is continuously differentiable
- the axial tooth profile has an initial helix angle at each end of the gear.
- the axial tooth profile is curvilinear.
- the axial tooth profile is a half-period sinusoid function.
- the gear tooth cross-sectional profile is configured such that the tip of one gear fully sweeps along the tooth root of the mating gear.
- the tooth tip and root profiles include a circular-arc.
- the tooth flank is a curve that allows smooth meshing of the gears.
- the tooth flank is involute, cycloidal, or circular arc.
- the tooth flank is an involute curve.
- the tooth tip is circular
- the tooth flank is involute
- the tooth root is circular
- the two or more curves of the hybrid tooth profile are combined such that the cross-sectional profile of the tooth is continuously differentiable.
- the gear teeth extend radially outward from the annular gear body.
- a curvilinear circular-arc- toothed (COAT) gear for improving gear performance and reducing noise while reducing axial loads common to helical gears includes: an annular gear body; and a gear tooth having a hybrid gear tooth profile comprising one or more curves configured to provide a sweep of the gear tooth space by a mating gear tooth while maintaining smooth contact during gear mesh, and wherein the gear tooth extends along an axial length of the gear body along an axial profile.
- the hybrid gear tooth profile has a tip that conforms to a tooth root of the mating gear to allow fully sweeping out the volume between gear teeth to improve efficiency and reduce noise.
- the hybrid gear tooth profile has a circular arc at a tooth tip, a circular arc at a tooth root, and the profile combines the two arcs with an involute curve between the circular arcs to allow a full sweep of the volume between gear teeth while maintaining a constant line of action of the mesh.
- a radius of a tooth tip arc is equal to or less than a radius of a tooth root arc.
- the hybrid profile is continuously differentiable.
- the axial profile is configured to cause gradual contact between teeth to reduce shock stress on the gear teeth and noise during meshing.
- the axial profile is configured to balance axial forces imparted on the gears from meshing to reduce net axial load on the gear.
- FIG. 1 schematically shows the function of conventional and exemplary gear pumps.
- FIG. 2 shows exemplary geometry of one half of a tooth profile. Curve end points are identified A through D. Top and bottom lines (A-B and C-D) denote circular curves, while the curved line between(B-C) denote the involute curve. Pitch, base, and root circles are denoted by the dot-dash lines and labeled as r p , r b , and r r respectively.
- FIG. 3 shows the origin of an exemplary involute curve y ⁇ x).
- the dashed line between points C and Co denotes the part of the involute curve that is not used in the actual tooth profile.
- FIG. 4 shows an exemplary post-splice tooth profile
- FIG. 5 shows a simplified block diagram of an exemplary process for building a CAD model of an exemplary gear.
- FIG. 6 shows a graphical depiction of the process of FIG. 5.
- FIG. 7 shows a top view of an exemplary gear.
- FIG. 8 shows a side view of an exemplary gear.
- FIG. 9 shows an isometric view of an exemplary gear.
- the required flow rate out of the pocket is set by the geometry of the meshing gears and the shaft speed of the pump; pp will rise to whatever is sufficient provide this flow rate. Therefore, to reduce the maximum value of p p during meshing process, the exit area of the pocket must be increased.
- the limitation of the relief groove is that, for spur gears, the tooth-to-tooth seal forms completely along the width of the gear at the moment of contact.
- exemplary gears offer all the benefits mentioned thus far, but without any of the drawbacks that come from helical gears.
- the gear should display the following characteristics:
- Exemplary tooth profiles hybridize the profiles of the involute curve for smooth force transfer with the void-clearing capability of a circular-arc tip.
- the gradual engagement of a helical gear may be made symmetrical to balance the axial loading.
- a primary drawback of a helical gear is the net axial loading placed on the gears during meshing. Again, this axial load is imparted on the gear during meshing, as there is an axial component to the force exchange due to the orientation of the tooth surface.
- One way to passively balance this axial load is to make the gears symmetric about the central plane of the gear. For a helical gear, this results in a herringbone gear.
- the axial load of one half of the gear is balanced against the other, resulting in no net axial load.
- Herringbone gears have been used in power transmission applications for over a century, though not at such small scales.
- An exemplary design process of the CCAT gear is as follows. First, the overall gear geometry is selected, including the root circle radius, maximum outer radius, gear height, and the number of teeth. Second, the axial profile is formulated. Third, the hybrid tooth profile is created to fit the needs of the specific application, including any geometric or performance constraints. Fourth, the gear is modeled in a CAD software package. Finally, the generated CAD file is used in conjunction with a CNC milling machine to fabricate the gear.
- the first step is to select the overall geometric parameters of the gear, such as root and outer radii, as well as height and the number of teeth. These parameters are sometimes dictated by external requirements, such as pump cavity dimensions, a desired pump flow rate, or a required torque capacity.
- the second step is to create the axial profile mathematically.
- the side profile curve may be defined parametrically in Cartesian coordinates. Due to the nature of the geometry in question, this may necessitate conversion from cylindrical to
- y r sm t (1 ) z e [q, w ]
- t is the parametric parameter
- w is the height of the cylinder.
- r is the root radius of the gear
- w is the width of the gear that was chosen in the first step.
- Equation (4) To express the profile in 3D Cartesian parametric form, Equation (4) is
- Equation set (1 ) substituted into Equation set (1 ) as the parametric parameter.
- the axial profile is defined by convention as the locus of points that is the reference point of the tooth profile as it is propagated along the axis of the gear.
- the reference point of the tooth profile is where the tooth profile contacts the root circle.
- this reference point is at the minimum of the circular dedendum profile (point D Figure 2). This makes 6 D the half-angle of the tooth profile, which can be compared to the number of chosen teeth as a design check to ensure that the selected number of teeth fit within the circle.
- the third step is to create the hybrid tooth profile.
- the process for defining the hybrid profile mathematically is to divide the curve into the constituent parts, define any required curve origins, and express each segment as a function of geometric parameters. These parameters may be freely variable, such as the base circle for involute curves, or may be dependent on external constraints or previous assumptions, such as the outer radius or the number of teeth. These expressions can then be used in curve fitting calculations to refine parameter selection.
- An exemplary hybrid tooth profile 200 consists of three sections, as shown in figure 2: the addendum circular arc 210, the involute flank curve 220, and the dedendum circular arc 230.
- the two circular arcs have their separate origins located on the pitch circle.
- the addendum arc origin, O1 is located at the 12 o’clock position and is where the azimuthal position, Q, is defined to be zero.
- the dedendum arc origin, O2 is defined to be at the angle which defines the end of the half tooth profile.
- the beginning and end points of the profile are labeled A and D, respectively, while the transition points between circular arcs and the involute curve are labeled B and C.
- the arc length of the tooth in radians is determined by the number of teeth, nt, which also defines the angular position of O2. .
- the addendum and dedendum curves are circular profiles, best expressed parametrically using a reference angle, g.
- the addendum curve can be written as
- flank curve may need to be transformed using a variable rotation matrix to define the flank curve origin on the base circle, shown in Figure 3.
- a variable rotation matrix to define the flank curve origin on the base circle, shown in Figure 3.
- the gear may be generated in a CAD software package, for example NX 10, in process 500.
- the root cylinder may be created at block 520, having a radius r r and height w.
- the bore for the shaft may be cut, along with the keyway, at block 530.
- the tooth side profile may be created as a 3D parametric curve at block 540.
- the tooth profile may then be created at block 550 using 67 data points calculated using the tooth profile parameters; these data points may be imported into NX and used to generate the profile.
- the circular arc sections may be created using the arc command, while the involute section may be created using a fit spline to the corresponding data points.
- the tooth profile is then closed with a circular arc of radius r r and then swept along the side profile, generating the first tooth 560.
- the component features of this tooth are then grouped and propagated in a circular arc to complete tooth formation at block 570. The process is illustrated visually in Figure 6.
- fabrication may be performed using a high-quality mill such as a Kitamura Mytrunnion 5-axis CNC mill.
- Mytrunnion has a positional repeatability of 0.00002 inches, which allows for component tolerances less than 0.0005 inches.
- the gear 700 includes an annular gear body 710.
- a set of gear teeth 720 extend radially away from the gear body 710 and extending axially along the gear body 710.
- the gear 700 is an exterior gear with the teeth 720 extending radially outward from the annular body 710.
- an inner gear is also possible with the gear teeth extending radially inwardly from the annular body.
- Each tooth 720 has a cross-sectional profile taken transverse to the rotational axis of the gear body 710. The cross-sectional profile is shaped as described above, and is formed from a hybridization of two or more curves.
- exemplary embodiments include a profile having circular tips 722 and roots 724 with involute flanks 726.
- the radius of the tooth tip arc is equal to or less than a radius of a tooth root arc.
- flank may be circular or cycloidal, rather than involute.
- the gear tooth cross-sectional profile may be configured such that the tip sweeps through the tooth root volume of the mating gear and such that the gear smoothly meshes with a complimentary gear.
- the two or more curves of the hybrid tooth profile are combined such that the cross- sectional profile of the tooth is continuously differentiable.
- each tooth 720 has an axial tooth profile defining a
- the axial tooth profile is also symmetric about an axial mid-plane of the gear to eliminate axial loading from gear meshing. Also as described above, the axial tooth profile may be
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Gears, Cams (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201862749498P | 2018-10-23 | 2018-10-23 | |
PCT/US2019/057628 WO2020086699A2 (en) | 2018-10-23 | 2019-10-23 | Curvilinear circular-arc tooth gears for use in external gear pumps |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3870877A2 true EP3870877A2 (en) | 2021-09-01 |
Family
ID=70280596
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19875034.1A Withdrawn EP3870877A2 (en) | 2018-10-23 | 2019-10-23 | Curvilinear circular-arc tooth gears for use in external gear pumps |
Country Status (3)
Country | Link |
---|---|
US (1) | US20200124047A1 (en) |
EP (1) | EP3870877A2 (en) |
WO (1) | WO2020086699A2 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN116451384B (en) * | 2023-06-15 | 2023-09-05 | 合肥皖液液压元件有限公司 | Gear forming method based on optimized reference rack tooth profile curve |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7040870B2 (en) * | 2003-12-30 | 2006-05-09 | The Goodyear Tire & Rubber Company | Gear pump with gears having curved teeth and method of feeding elastomeric material |
KR100863981B1 (en) * | 2007-04-03 | 2008-10-16 | 안재섭 | Double helical gear and gear pump using the same |
DE102010027300A1 (en) * | 2010-07-16 | 2012-01-19 | Neumayer Tekfor Holding Gmbh | Spur gear, production of a system for torque transmission and corresponding system |
DE202014007647U1 (en) * | 2014-07-15 | 2015-01-22 | Universität Stuttgart Körperschaft des öffentlichen Rechts | Gear pump with curved toothing |
IT201600076227A1 (en) * | 2016-07-20 | 2018-01-20 | Settima Meccanica S R L Soc A Socio Unico | Bi-helical gear wheel with variable helix angle and non-encapsulating tooth profile for gear hydraulic equipment |
-
2019
- 2019-09-30 US US16/587,144 patent/US20200124047A1/en not_active Abandoned
- 2019-10-23 WO PCT/US2019/057628 patent/WO2020086699A2/en unknown
- 2019-10-23 EP EP19875034.1A patent/EP3870877A2/en not_active Withdrawn
Also Published As
Publication number | Publication date |
---|---|
WO2020086699A3 (en) | 2020-06-11 |
WO2020086699A2 (en) | 2020-04-30 |
US20200124047A1 (en) | 2020-04-23 |
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