IDLER GEAR FOR A GENERATOR

• US 20100327684A1
• Filed: 06/30/2009
• Published: 12/30/2010
• Est. Priority Date: 06/30/2009
• Status: Active Grant

• Current Assignee: Hamilton Sundstrand Corporation (Rtx Corporation)
• Original Assignee: Hamilton Sundstrand Corporation (Rtx Corporation)
• Inventors: Grosskopf, Andrew P., Brust, Eric A.
• Granted Patent: US 7,926,381 B2
• Time in Patent Office: Days
• US Class Current: 310/83
• CPC Class Codes: F16H 1/20 involving more than two intermeshing members
• CPC Class Codes: F16H 2055/0893 for parallel shaft arrangement of toothed members
• CPC Class Codes: F16H 55/0806 Involute profile
• CPC Class Codes: H02K 2213/03 Machines characterised by numerical values, ranges, mathematical expressions or similar information
• CPC Class Codes: H02K 7/00 Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
• CPC Class Codes: H02K 7/116 with gears
• CPC Class Codes: Y10T 29/49009 Dynamoelectric machine
• CPC Class Codes: Y10T 74/19972 form

Abstract

A gear set for a generator includes a first gear having a first set of involute teeth and a second gear having a second set of involute teeth circumferentially located about a center axis of rotation. Each set of involute teeth includes respective roll angles, ε_A-D. For a diametrically smaller one of the first gear and the second gear the roll angle ε_A is 1.51°-3.51°, the roll angle ε_B is 7.64°-9.64°, the roll angle ε_C is 26.03°-28.03°, and the roll angle ε_D is 32.16°-34.16°, and for a diametrically larger one of the first gear and the second gear the roll angle ε_A is 15.02°-17.02°, the roll angle ε_B is 16.7°-18.7°, the roll angle ε_C is 21.73°-23.73°, and the roll angle ε_D is 23.41°-25.41°.

Claims

1. A gear set for a generator, comprising:

a first gear having a first set of involute teeth circumferentially located about a center axis of rotation; and

a second gear axially spaced from the first gear and coupled with the first gear such that the first gear and the second gear co-rotate, the second gear having a second set of involute teeth circumferentially located about the center axis of rotation, each tooth of the first set of involute teeth and the second set of involute teeth including an involute surface that extends between a tooth tip and a tooth base, each involute surface including at least reference points A-D thereon with reference point A near the base, reference point D near the tip, reference point B between reference points A and D, and reference point C between reference points B and D, the reference points A-D having respective roll angles, ε

_A-D, between a corresponding first line that is perpendicular to the involute surface at the given reference point A-D and a second line that is tangent at a reference point that lies on a terminal end of the involute surface at the tooth base to a reference base circle having a center origin at the center axis, for a diametrically smaller one of the first gear and the second gear the roll angle ε

_A is 1.51°

-3.51°

, the roll angle ε

_B is 7.64°

-9.64°

, the roll angle ε

_C is 26.03°

-28.03°

, and the roll angle ε

_D is 32.16°

-34.16°

, and for a diametrically larger one of the first gear and the second gear the roll angle ε

_A is 15.02°

-17.02°

, the roll angle ε

_B is 16.7°

-18.7°

, the roll angle ε

_C is 21.73°

-23.73°

, and the roll angle ε

_D is 23.41°

-25.41°

.

2. The gear set as recited in claim 1, wherein the roll angle ε

_A is 2.01°

-3.01°

, the roll angle ε

_B is 8.14°

-9.14°

, the roll angle ε

_C is 26.53°

-27.53°

, and the roll angle ε

_D is 32.66°

-33.66°

for the diametrically smaller one of the first gear and the second gear.

3. The gear set as recited in claim 1, wherein the roll angle ε

_A is 2.51°

, the roll angle ε

_B is 8.64°

, the roll angle ε

_C is 27.03°

, and the roll angle ε

_D is 33.16°

for the diametrically smaller one of the first gear and the second gear.

4. The gear set as recited in claim 1, wherein the roll angle ε

_A is 15.52°

-16.52°

, the roll angle ε

_B is 17.2°

-18.2°

, the roll angle ε

_C is 22.23°

-23.23°

, and the roll angle ε

_D is 23.91°

-24.91°

for the diametrically larger one of the first gear and the second gear.

5. The gear set as recited in claim 1, wherein the roll angle ε

_A is 16.02°

, the roll angle ε

_B is 17.7°

, the roll angle ε

_C is 22.73°

, and the roll angle ε

_D is 24.41°

for the diametrically larger one of the first gear and the second gear.

6. The gear set as recited in claim 1, wherein a first ratio of the roll angle ε

_A of the first set of involute teeth to the roll angle ε

_A of the second set of involute teeth is 0.08-0.24, a second ratio of the roll angle ε

_B of the first set of involute teeth to the roll angle ε

_B of the second set of involute teeth is 0.4-0.58, a third ratio of the roll angle ε

_C of the first set of involute teeth to the roll angle ε

_C of the second set of involute teeth is 1.09-1.29, and a fourth ratio of the roll angle ε

_D of the first set of involute teeth to the roll angle ε

_D of the second set of involute teeth is 1.26-1.46

7. The gear set as recited in claim 6, wherein the first ratio is 0.12-0.2, the second ratio is 0.44-0.54, the third ratio is 1.14-1.24, and the fourth ratio is 1.31-1.41.

8. The gear set as recited in claim 6, wherein the first ratio is 0.16, the second ratio is 0.49, the third ratio is 1.191, and the fourth ratio is 1.36.

9. The gear set as recited in claim 1, further comprising a common shaft that couples the first gear and the second gear together.

10. The gear set as recited in claim 9, wherein the common shaft includes a shoulder having an axial face.

11. The gear set as recited in claim 10, including a first axial distance between the axial face of the shoulder and an axial face of the first set of involute teeth and a second axial distance between the axial face of the shoulder and an axial face of the second set of involute teeth, and a ratio of the first axial distance to the second axial distance is 0.1-0.2.

12. The gear set as recited in claim 11, wherein the ratio of the first axial distance to the second axial distance is 0.14-0.15.

13. The gear set as recited in claim 10, including a first axial distance between the axial face of the shoulder and an axial face of the first set of involute teeth that is 0.117-0.127 inches and a second axial distance between the axial face of the shoulder and an axial face of the second set of involute teeth that is 0.853-0.863.

14. The gear set as recited in claim 10, wherein the common shaft further comprises another shoulder, and the first gear and the second gear are each located axially between the shoulders.

15. A generator comprising:

a stator;

a rotor shaft that is rotatable;

a rotor mounted on the rotor shaft to be driven within the stator and having a plurality of magnetic members circumferentially spaced around the rotor shaft;

a gear train including a rotor gear mounted on the rotor shaft, a gear set engaged with the rotor gear, and a pump gear operative to be driven by the rotor gear through the gear set;

a pump operatively coupled to the rotor shaft through the pump gear of the gear train, and

the gear set including a first gear intermeshed with the pump gear and a second gear intermeshed with the rotor gear, the first gear having a first set of involute teeth circumferentially located about a center axis of rotation, the second gear is axially spaced from the first gear and coupled with the first gear such that the first gear and the second gear co-rotate, the second gear having a second set of involute teeth circumferentially located about the center axis of rotation, each tooth of the first set of involute teeth and the second set of involute teeth including an involute surface that extends between a tooth tip and a tooth base, each involute surface including at least reference points A-D thereon with reference point A near the base, reference point D near the tip, reference point B between reference points A and D, and reference point C between reference points B and D, the reference points A-D having respective roll angles, ε

_A-D, between a corresponding first line that is perpendicular to the involute surface at the given reference point A-D and a second line that is tangent at a reference point that lies on a terminal end of the involute surface at the tooth base to a reference base circle having a center origin at the center axis, for a diametrically smaller one of the first gear and the second gear the roll angle ε

_A is 1.51°

-3.51°

, the roll angle ε

_B is 7.64°

-9.64°

, the roll angle ε

_C is 26.03°

-28.03°

, and the roll angle ε

_D is 32.16°

-34.16°

, and for a diametrically larger one of the first gear and the second gear the roll angle ε

_A is 15.02°

-17.02°

, the roll angle ε

_B is 16.7°

-18.7°

, the roll angle ε

_C is 21.73°

-23.73°

, and the roll angle ε

_D is 23.41°

-25.41°

.

16. The generator as recited in claim 15, wherein and a first ratio of the roll angle ε

_A of the first set of involute teeth to the roll angle ε

_A of the second set of involute teeth is 0.08-0.24, a second ratio of the roll angle ε

_B of the first set of involute teeth to the roll angle ε

_B of the second set of involute teeth is 0.4-0.58, a third ratio of the roll angle ε

_C of the first set of involute teeth to the roll angle ε

_C of the second set of involute teeth is 1.09-1.29, and a fourth ratio of the roll angle ε

_D of the first set of involute teeth to the roll angle ε

_D of the second set of involute teeth is 1.26-1.46.

17. The generator as recited in claim 15, further comprising a common shaft that couples the first gear and the second gear together, the common shaft including a shoulder having an axial face and a first axial distance between the axial face of the shoulder and an axial face of the first set of involute teeth and a second axial distance between the axial face of the shoulder and an axial face of the second set of involute teeth, and a ratio of the first axial distance to the second axial distance is 0.1-0.2.

18. A method for installing a gear train in a generator, comprising:

disassembling at least a portion of a generator that includes a stator, a rotor shaft that is rotatable, a rotor mounted on the rotor shaft to be driven within the stator and having a plurality of magnetic members circumferentially spaced around the rotor shaft, a gear train including a rotor gear mounted on the rotor shaft, a first gear set engaged with the rotor gear, and a pump gear operative to be driven by the rotor gear through the gear set, and a pump operatively coupled to the rotor shaft through the pump gear of the gear train; and

inserting a second gear set into the generator in place of the first gear set, the second gear set including a first gear intermeshed with the pump gear and a second gear intermeshed with the rotor gear, the first gear having a first set of involute teeth circumferentially located about a center axis of rotation, the second gear is axially spaced from the first gear and coupled with the first gear such that the first gear and the second gear co-rotate, the second gear having a second set of involute teeth circumferentially located about the center axis of rotation, each tooth of the first set of involute teeth and the second set of involute teeth including an involute surface that extends between a tooth tip and a tooth base, each involute surface including at least reference points A-D thereon with reference point A near the base, reference point D near the tip, reference point B between reference points A and D, and reference point C between reference points B and D, the reference points A-D having respective roll angles, ε

_A-D, between a corresponding first line that is perpendicular to the involute surface at the given reference point A-D and a second line that is tangent at a reference point that lies on a terminal end of the involute surface at the tooth base to a reference base circle having a center origin at the center axis, and for a diametrically smaller one of the first gear and the second gear the roll angle ε

_A is 1.51°

-3.51°

, the roll angle ε

_B is 7.64°

-9.64°

, the roll angle ε

_C is 26.03°

-28.03°

, and the roll angle ε

_D is 32.16°

-34.16°

, and for a diametrically larger one of the first gear and the second gear the roll angle ε

_A is 15.02°

-17.02°

, the roll angle ε

_B is 16.7°

-18.7°

, the roll angle ε

_C is 21.73°

-23.73°

, and the roll angle ε

_D is 23.41°

-25.41°

.