CN101769369A - Nonorthogonal cylindrical worm gear pair and nonorthogonal cylindrical worm gear limited slip differential - Google Patents
Nonorthogonal cylindrical worm gear pair and nonorthogonal cylindrical worm gear limited slip differential Download PDFInfo
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- CN101769369A CN101769369A CN201010120614A CN201010120614A CN101769369A CN 101769369 A CN101769369 A CN 101769369A CN 201010120614 A CN201010120614 A CN 201010120614A CN 201010120614 A CN201010120614 A CN 201010120614A CN 101769369 A CN101769369 A CN 101769369A
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- worm
- worm gear
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- cylindrical worm
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Abstract
The invention discloses a nonorthogonal cylindrical worm gear pair, a manufacturing method thereof and a nonorthogonal cylindrical worm gear limited slip differential consisting of the worm gear pair, which belong to the technical field of mechanical driving. The nonorthogonal cylindrical worm gear pair is characterized by comprising a cylindrical worm gear (1) and a worm wheel (2); a cylindrical worm gear axis (3) crosses with a worm wheel axis (4) in space, and sigma is the fixed included angle of the two axes, and is greater than 0 DEG but is smaller than 90 DEG; the distance between the two axes is the center distance a of engaging driving; and the nonorthogonal cylindrical worm gear pair consists of the cylindrical worm gear (1) and the worm wheel (3) which satisfy the space position relationship of the two axes and the installing distance R2 of the worm wheel, and drives in an engagement way. The nonorthogonal cylindrical worm gear pair is applied to the motion of the non-90 DEG space crossing axes and the power driving, and the nonorthogonal cylindrical worm gear limited slip differential is applied to the torque sensing self-locking type differential between axles or wheels of the vehicle.
Description
Technical field
The present invention relates to a kind of nonopiate cylindrical worm gear and manufacture method thereof and, belong to the mechanical transmissioning technology field by the nonopiate cylindrical worm limited-slip differential that this worm gear pair constitutes.
Technical background
Worm drive is used for transmitting motion and the power between the two vertical interlaced axis of space, the shape of pressing the worm indexing curved surface, and worm drive is divided three classes: cylindrical worm gearing transmission, toroid helicoids worm transmission and conical worm transmission.The reference surface of cylindrical worm is the cylndrical surface, the worm gear in the cylindrical worm gearing transmission generally is to surround worm screw, also have not surround worm screw, but worm screw does not surround worm gear.
According to the curved surface forming principle of the cylindrical worm flank of tooth, cylindrical worm is divided into Archimedes's cylindrical worm, normal direction straight profile cylindrical worm, involute cylindrical worm, milled helicoids worm and hollow flank worm etc.Adopt cutters such as rectilinear edge, flat-faced wheel, angle milling cutter or conical wheel, during the worm screw revolution, cutter is parallel to worm axis with knife rest by certain speed ratio and moves, and rectilinear edge is the helicoid of cylindrical worm at track curved surface, plane or the conical wheel envelope surface on worm screw on the worm screw.In order to obtain the cylindrical worm gear of line contact, to get the generating surface cylinder hobboing cutter identical and on gear hobbing machine, process worm gear with the cylindrical worm helicoid, the cylindrical worm gear that obtains belongs to line contact conjugate surface.
The characteristics of cylindrical worm gear be many to tooth mesh simultaneously, line contact, bearing capacity can realize hard flank of tooth transmission greater than the alternating axis cylindrical helical gear drive.
Summary of the invention
The nonopiate cylindrical worm limited-slip differential that the objective of the invention is to provide a kind of nonopiate cylindrical worm gear and manufacture method thereof and constitute by this worm gear pair; Nonopiate cylindrical worm gear is applied to the motion and the power transmission of the staggered axis in non-90 ° of spaces, and nonopiate cylindrical worm limited-slip differential is applied between axle for vehicle or moment of torsion induction differential gear with self-locking device between wheel.
As follows in order to reach the technological scheme that purpose of the present invention takes:
Nonopiate cylindrical worm gear comprises cylindrical worm 1, worm gear 2, cylindrical worm axis 3 is staggered with worm gear axis 4 spaces, two axial lines fixed angle ∑, 0＜∑＜90 °, the two axial lines distance is engagement driving centre distance a, by satisfying two axial lines spatial relation and worm gear mounting distance R
2And the cylindrical worm 1 of engagement driving and worm gear 2 constitute nonopiate cylindrical worm gear (as Fig. 1,2).
Nonopiate cylindrical worm gear manufacture method comprises: cylindrical worm 1 is made by the existing processing technique of routine, get generating surface cylinder hobboing cutter 8 on gear hobbing machine the machining worm wheel blank 9 identical with cylindrical worm 1 helicoid, cylinder cutter shaft line 10 and blank of worm gear axis 11 angles are ∑, 0＜∑＜90 ° in the course of working, and the two axial lines distance is for engagement driving centre distance a and satisfy worm gear mounting distance R
2, press the velocity ratio i of cylindrical worm 1 and worm gear 2
12Rolling cut is processed into worm gear 2 (as Fig. 3) with blank of worm gear 9, by worm gear 2 and the cylindrical worm 1 retainer shaft angle of cut ∑, centre distance a and the worm gear mounting distance R that process
2Engagement driving obtains nonopiate cylindrical worm gear.
Nonopiate cylindrical worm limited-slip differential comprises: differential casing 7 is provided with space staggered cylindrical worm axis 3 and worm gear axis 4, and the two axial lines angle is ∑, β
1＜∑＜90 ° and 90 °-β
1＜∑＜90 °, the two axial lines distance is engagement driving centre distance a, the helixangle of dextrorotation cylindrical worm 1
1Dextrorotation cylindrical worm 1 and different other geometric parameters with dextrorotation cylindrical worm 1 rotation direction and left-handed cylindrical worm 5 coaxial lines of identical in structure are connected and constitute a planet worm screw, the planet worm screw is rotated connection around cylindrical worm axis 3 on differential casing 7, dextrorotation worm gear 2 and left-handed worm gear 6 rotate with differential casing 7 coaxial lines 4 respectively and connect, have the dextrorotation worm gear 2 of same rotation axis 4 and left-handed worm gear 6 respectively with dextrorotation cylindrical worm 1 and left-handed cylindrical worm 5 engagement driving, form two groups have worm screw with speed, in the same way, the stable drive ratio i that rotates of coaxial line 3
12=i
56Nonopiate cylindrical worm gear, by differential casing 7 input power and by dextrorotation worm gear 2, left-handed worm gear 6 respectively outputting power constitute nonopiate cylindrical worm limited-slip differential (as Fig. 4).
In the above-mentioned nonopiate cylindrical worm gear, change a number z of cylindrical worm 1
1Or helixangle
1Velocity ratio i with nonopiate cylindrical worm gear
12=z
2/ z
1Or the crossed axis angle ∑, can change forward and reverse transmission efficiency of nonopiate cylindrical worm gear, mechanism's self-locking when transmission efficiency η=0.
In the above-mentioned nonopiate cylindrical worm gear manufacture method, cylindrical worm 1 can be Archimedes's cylindrical worm, normal direction straight profile cylindrical worm, involute cylindrical worm, milled helicoids worm and hollow flank worm etc., is that ∑, centre distance are a and worm gear mounting distance R by generating surface cylinder hobboing cutter 8 retainer shaft angle of cut on gear hobbing machine identical with cylindrical worm 1 helicoid
2, the worm gear 2 and cylindrical worm 1 engagement driving that process all can obtain nonopiate cylindrical worm gear.
In the above-mentioned nonopiate cylindrical worm limited-slip differential, change the crossed axis angle ∑, perhaps change a number z of dextrorotation cylindrical worm 1
1Or helixangle
1With velocity ratio i
12=z
2/ z
1, left-handed cylindrical worm 5 a number z
5=z
1Or helixangle
5=β
1With velocity ratio i
56=z
6/ z
5=i
12During also along with respective change, can change the transmission efficiency of train, and then change the theoretical locking coefficient K of nonopiate cylindrical worm limited-slip differential, so that satisfy vehicle the differential mechanism performance demands.
In the above-mentioned nonopiate cylindrical worm limited-slip differential, for improve bearing capacity and stability of rotation on differential casing 7 around worm gear axis 4 a uniform p planet worm screw, p=2,3,4,5,6, p=3 as shown in Figure 5.
In the above-mentioned nonopiate cylindrical worm limited-slip differential, in order to improve bearing capacity, dextrorotation cylindrical worm 1 of planet worm screw and left-handed cylindrical worm 5 are the hard flank of tooth, with the dextrorotation worm gear 2 and the left-handed worm gear 6 of its corresponding engagement driving also is the hard flank of tooth, constitute nonopiate cylindrical worm limited-slip differential by two pairs of nonopiate cylindrical worm gears of the hard flank of tooth, so that improve the tractive force and the driving power of vehicle.
Description of drawings
Fig. 1 is nonopiate cylindrical worm gear schematic diagram;
Fig. 2 overlooks schematic diagram for nonopiate cylindrical worm gear;
Fig. 3 is the worm gear process principle figure of nonopiate cylindrical worm gear;
Fig. 4 is nonopiate cylindrical worm limited-slip differential schematic diagram;
Fig. 5 is the planet worm screw configuration schematic diagram of nonopiate cylindrical worm limited-slip differential.
Specific embodiments
With reference to the accompanying drawings embodiments of the invention are described below.
Nonopiate cylindrical worm gear shown in Figure 1 is made of cylindrical worm 1, worm gear 2, cylindrical worm axis 3 is staggered with worm gear axis 4 spaces, two axial lines fixed angle ∑, 0＜∑＜90 °, the two axial lines distance is engagement driving centre distance a, by satisfying two axial lines spatial relation and worm gear mounting distance R
2The be meshing with each other cylindrical worm 1 of transmission and worm gear 2 constitutes nonopiate cylindrical worm gears (as Fig. 2); A number z of cylindrical worm 1
1, helixangle
1, the number of teeth z of worm gear 2
2, by changing a number z of cylindrical worm 1
1Or helixangle
1Velocity ratio i with nonopiate cylindrical worm gear
12=z
2/ z
1Or the crossed axis angle ∑, can change forward and reverse transmission efficiency of nonopiate cylindrical worm gear, mechanism's self-locking when transmission efficiency η=0.When cylindrical worm 1 is dextrorotation, get β
1＜∑, worm gear 2 is dextrorotation, and it is left-handed that cylindrical worm 1 can be designed as, with the worm gear 2 of its engagement also be left-handed.
The manufacture method of nonopiate cylindrical worm gear comprises: 1.. the manufacturing of cylindrical worm 1: cylindrical worm 1 is made by the existing processing technique of routine, and cylindrical worm 1 can be Archimedes's cylindrical worm, normal direction straight profile cylindrical worm, involute cylindrical worm, milled helicoids worm and hollow flank worm etc.; 2.. the manufacturing of worm gear 2: as shown in Figure 3, getting the generating surface cylinder hobboing cutter 8 identical with cylindrical worm 1 helicoid is installed on the hob head, blank of worm gear 9 is installed on the gear hobbing machine Work turning table, regulating the hob head inclination angle is 90 °-∑, promptly satisfy cylinder hobboing cutter axis 10 and blank of worm gear axis 11 angles and be ∑, 0＜∑＜90 °, by mounting distance R
2Determine the axial position of blank of worm gear 9, adjust two axial lines centre distance O
1O
2Equal engagement driving centre distance a, press the velocity ratio i of cylindrical worm 1 and worm gear 2
12Calculate change gear and roll ratio, cylinder hobboing cutter 8 is processed into worm gear 2 with blank of worm gear 9 on gear hobbing machine, is that ∑, centre distance are a and worm gear mounting distance R by the worm gear 2 and the cylindrical worm 1 retainer shaft angle of cut that process
2Engagement driving obtains nonopiate cylindrical worm gear.When the hob head inclination angle is 0 ° in the course of working, promptly when cylinder hobboing cutter axis 10 and blank of worm gear axis 11 angle ∑=90 °, can obtain the normal cylindrical worm gear pair.
In the nonopiate cylindrical worm limited-slip differential schematic diagram shown in Figure 4, differential casing 7 is provided with space staggered cylindrical worm axis 3 and worm gear axis 4, and the two axial lines angle is ∑, β
1＜∑＜90 ° and 90 °-β
1＜∑＜90 °, the two axial lines distance is engagement driving centre distance a, the helixangle of dextrorotation cylindrical worm 1
1Dextrorotation cylindrical worm 1 and different other geometric parameters with dextrorotation cylindrical worm 1 rotation direction and left-handed cylindrical worm 5 coaxial lines of identical in structure are connected and constitute a planet worm screw, the planet worm screw is rotated connection around cylindrical worm axis 3 on differential casing 7, dextrorotation worm gear 2 and left-handed worm gear 6 rotate with differential casing 7 coaxial lines 4 respectively and connect, have the dextrorotation worm gear 2 of same rotation axis 4 and left-handed worm gear 6 respectively with dextrorotation cylindrical worm 1 and left-handed cylindrical worm 5 engagement driving, form two groups have worm screw with speed, in the same way, the stable drive ratio i that rotates of coaxial line 3
12=i
56Nonopiate cylindrical worm gear; ' central gear ' by dextrorotation worm gear 2,6 liang of coaxial line 4 independent rotation of left-handed worm gear is that ' tie-rod ' and relative differential casing 7 constitute the dual free dimension differential gear train around axis 3 rotations and with differential casing 7 around the planet worm screw of axis 4 revolution with the differential casing 7 that rotates around axis 4, and its rotation speed relation is n
7=(n
2+ n
6)/2, by differential casing 7 input power and by dextrorotation worm gear 2, left-handed worm gear 6 respectively outputting power constitute nonopiate cylindrical worm limited-slip differential.When the vehicle straight-line travelling, n
2=n
6=n
7, dextrorotation cylindrical worm 1 and dextrorotation worm gear 2, left-handed cylindrical worm 5 and left-handed worm gear 6 do not relatively rotate, and promptly the planet worm screw does not have rotation to have only revolution; Work as Ackermann steer angle, n
2=n
7+ Δ n, n
6=n
7-Δ n, turn left in Δ n＞0, and turn right in Δ n＜0, and Δ n ≠ 0 o'clock dextrorotation cylindrical worm 1 and dextrorotation worm gear 2, left-handed cylindrical worm 5 and left-handed worm gear 6 produce relative rotation, and the rotation of planet worm screw is revolved round the sun simultaneously; When a driving wheel skids, differential mechanism will limit this and take turns monolateral velocity jump.Change the crossed axis angle ∑, perhaps change a number z of dextrorotation cylindrical worm 1
1Or helixangle
1Number of teeth z with dextrorotation worm gear 2
2, left-handed cylindrical worm 5 a number z
5=z
1Or helixangle
5=β
1Number of teeth z with left-handed worm gear 6
6=z
2During also along with respective change, can change the transmission efficiency of train, and then change the theoretical locking coefficient K of nonopiate cylindrical worm limited-slip differential, so that satisfy vehicle the differential mechanism performance demands; Consider differential casing 7 stress balances, differential mechanism stability of rotation and for improve bearing capacity on differential casing 7 around axis 4 a uniform p planet worm screw, p=2,3,4,5,6, present embodiment p=3 (as Fig. 5); In order to improve bearing capacity, dextrorotation cylindrical worm 1 of planet worm screw and left-handed cylindrical worm 5 are the hard flank of tooth, with the dextrorotation worm gear 2 and the left-handed worm gear 6 of its corresponding engagement driving also is the hard flank of tooth, constitute nonopiate cylindrical worm limited-slip differential by two pairs of nonopiate cylindrical worm gears of the hard flank of tooth, so that improve the tractive force and the driving power of vehicle.
Claims (8)
1. nonopiate cylindrical worm gear comprises that cylindrical worm (1), worm gear (2) is characterized in that, cylindrical worm axis (3) is staggered with worm gear axis (4) space, two axial lines fixed angle ∑, 0＜∑＜90 °, the two axial lines distance is engagement driving centre distance a, mounting distance is R
2Worm gear (2) and cylindrical worm (1) satisfy two axial lines spatial relation engagement driving.
2. nonopiate cylindrical worm gear manufacture method comprises, cylindrical worm (1) is made by the existing processing technique of routine, it is characterized in that, get generating surface cylinder hobboing cutter (8) on gear hobbing machine the machining worm wheel blank (9) identical with cylindrical worm (1) helicoid, cylinder cutter shaft line (10) and blank of worm gear axis (11) angle are ∑, 0＜∑＜90 ° in the course of working, and the two axial lines distance is for engagement driving centre distance a and satisfy worm gear mounting distance R
2, press the velocity ratio i of cylindrical worm (1) and worm gear (2)
12Rolling cut is processed into worm gear (2) with blank of worm gear (9), realizes crossed axis angle ∑, centre distance a, worm gear mounting distance R by worm gear that processes (2) and cylindrical worm (1)
2Engagement driving.
3. nonopiate cylindrical worm limited-slip differential is characterized in that, differential casing (7) is provided with space staggered cylindrical worm axis (3) and worm gear axis (4), and the two axial lines angle is ∑, β
1＜∑＜90 ° and 90 °-β
1＜∑＜90 °, the two axial lines distance is engagement driving centre distance a, the helixangle of dextrorotation cylindrical worm (1)
1Dextrorotation cylindrical worm (1) constitutes a planet worm screw with being connected with different other geometric parameters of dextrorotation cylindrical worm (1) rotation direction and the left-handed cylindrical worm of identical in structure (5) coaxial line, the planet worm screw goes up around cylindrical worm axis (3) at differential casing (7) and rotates connection, dextrorotation worm gear (2) and left-handed worm gear (6) rotate with differential casing (7) coaxial line (4) respectively and connect, have the dextrorotation worm gear (2) of same rotation axis (4) and left-handed worm gear (6) respectively with dextrorotation cylindrical worm (1) and left-handed cylindrical worm (5) stable drive ratio i
12=i
56Engagement driving is by differential casing (7) input power and by dextrorotation worm gear (2), left-handed worm gear (6) difference outputting power.
4. nonopiate cylindrical worm gear according to claim 1 is characterized in that, changes a number z of cylindrical worm (1)
1Or helixangle
1Velocity ratio i with nonopiate cylindrical worm gear
12=z
2/ z
1Or the crossed axis angle ∑, can change forward and reverse transmission efficiency of nonopiate cylindrical worm gear.
5. nonopiate cylindrical worm gear manufacture method according to claim 2, cylindrical worm (1) can be Archimedes's cylindrical worm, normal direction straight profile cylindrical worm, involute cylindrical worm, milled helicoids worm and hollow flank worm, it is characterized in that, by generating surface cylinder hobboing cutter (8) on gear hobbing machine retainer shaft angle of cut ∑, centre distance a and the worm gear mounting distance R identical with cylindrical worm (1) helicoid
2, the worm gear that processes (2) all can be realized nonopiate engagement driving with cylindrical worm (1).
6. nonopiate cylindrical worm limited-slip differential according to claim 3 is characterized in that, changes the crossed axis angle ∑, perhaps changes a number z of dextrorotation cylindrical worm (1)
1Or helixangle
1With velocity ratio i
12=z
2/ z
1, left-handed cylindrical worm (5) a number z
5=z
1Or helixangle
5=β
1With velocity ratio i
56=z
6/ z
5=i
12During also along with respective change, can change the theoretical locking coefficient K of nonopiate cylindrical worm limited-slip differential.
7. nonopiate cylindrical worm limited-slip differential according to claim 3 is characterized in that, goes up around uniform p planet worm screw of worm gear axis (4), p=2,3,4,5,6 at differential casing (7).
8. nonopiate cylindrical worm limited-slip differential according to claim 3, it is characterized in that, dextrorotation cylindrical worm (1) and the left-handed cylindrical worm (5) of planet worm screw are the hard flank of tooth, also are the hard flank of tooth with the dextrorotation worm gear (2) and the left-handed worm gear (6) of its corresponding engagement driving.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010120614A CN101769369A (en) | 2010-03-08 | 2010-03-08 | Nonorthogonal cylindrical worm gear pair and nonorthogonal cylindrical worm gear limited slip differential |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010120614A CN101769369A (en) | 2010-03-08 | 2010-03-08 | Nonorthogonal cylindrical worm gear pair and nonorthogonal cylindrical worm gear limited slip differential |
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|---|---|
| CN101769369A true CN101769369A (en) | 2010-07-07 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010120614A Pending CN101769369A (en) | 2010-03-08 | 2010-03-08 | Nonorthogonal cylindrical worm gear pair and nonorthogonal cylindrical worm gear limited slip differential |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CZ304162B6 (en) * | 2012-07-23 | 2013-11-27 | Kutman@Tomás | Clearance-free worm and wheel gear with disk-type wheel |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06225497A (en) * | 1993-01-26 | 1994-08-12 | Sadayuki Amiya | Deceleration differential apparatus for electric |
| JPH0924855A (en) * | 1995-07-14 | 1997-01-28 | Nippon Seiko Kk | Reduction gear mechanism for motor-driven power steering |
| CN101033788A (en) * | 2006-03-08 | 2007-09-12 | 日本精工株式会社 | Worm reducer and electric power steering apparatus |
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2010
- 2010-03-08 CN CN201010120614A patent/CN101769369A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06225497A (en) * | 1993-01-26 | 1994-08-12 | Sadayuki Amiya | Deceleration differential apparatus for electric |
| JPH0924855A (en) * | 1995-07-14 | 1997-01-28 | Nippon Seiko Kk | Reduction gear mechanism for motor-driven power steering |
| CN101033788A (en) * | 2006-03-08 | 2007-09-12 | 日本精工株式会社 | Worm reducer and electric power steering apparatus |
Non-Patent Citations (3)
| Title |
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| 《机械工艺师》 19900331 董雪松 用小直径模数滚刀滚切蜗轮的方法 全文 2,5 , 2 * |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CZ304162B6 (en) * | 2012-07-23 | 2013-11-27 | Kutman@Tomás | Clearance-free worm and wheel gear with disk-type wheel |
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Application publication date: 20100707 |