CN100387868C - Pump-type stepless speed variator with gears and roller bearing - Google Patents
Pump-type stepless speed variator with gears and roller bearing Download PDFInfo
- Publication number
- CN100387868C CN100387868C CNB011288736A CN01128873A CN100387868C CN 100387868 C CN100387868 C CN 100387868C CN B011288736 A CNB011288736 A CN B011288736A CN 01128873 A CN01128873 A CN 01128873A CN 100387868 C CN100387868 C CN 100387868C
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- gear
- roller
- transmission
- pump
- speed
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Abstract
The present invention provides a bearing pump type structure with a preload, which is formed by a gear roller of a jumping gear, an internal gear, a central gear and an isolating drive frame. Various stepless speed variators, differential gears, constant pumps or variable pumps, and torque fixed couplers or torque variable couplers can be formed from the bearing pump type structure independently or through series connection or parallel connection. Because of good sealing performance, no pocketed oil, large power, high efficiency, large speed range, good high and low speed characteristics, self controlled deceleration and torque increase and other excellent economic and technical norms, besides being used for various kinds of hydraulic mechanical drive, the present invention can particularly and sufficiently meet various drive requirements of the speed change and the differential speed of automobiles, and meanwhile, the present invention can directly provide the work applying requirements of other additional controlled variable power.
Description
Technical field
The invention belongs to mechanical fluid power transmission field.
Technical background
In transmission field, gear transmission is with a long history, and technology maturation greatly to mining machinery, is all covered by gear transmission to instrument, instrument for a short time.However, its narrow limitation also is conspicuous.With regard to gear graduation, a pair of gear pair that differs in size produces a gear-stage velocity ratio, when requiring speed ratio intensive, just needs a large amount of gears; With regard to gear pump, shortcoming such as structure characteristics such as its gear shaft unbalance loading, pocketed oil, leakage of oil make its transmitted power little, and efficient is low, and discharge amount is little and limited purposes.All adopt gear graduation with regard to most of automobiles at present, but can not fully satisfy the requirement of vehicle transmission, not adopt the torque converter and the planetary transmission that involve great expense to form Hydromechanical transmission to satisfy the requirement of transmission gear shift so the automobile of some high-grade cars and specific (special) requirements is stinted.
At present, though the balanced planetary gear pump that Chinese patent is announced can be made the stepless speed variator of variable displacement motor, also improved some intrinsic shortcoming of gear pump.But still exist as gear pump pocketed oil, leakage of oil and speed characteristics problem, also just be restricted in the size of power transmission and the selection of speed range.
Summary of the invention
Purpose of the present invention utilizes that gear pump structure is simple, compact, the economic dispatch advantage, changes its drive characteristics, when keeping original advantage, intrinsic shortcoming is converted into advantage constitutes a kind of novel stepless speed variator.
Technological scheme of the present invention as shown in Figure 1, it is by plural gear roller 3, internal gear 1, in the structural fluid loop of central gear 2 and isolation gear frame 4, by the flow of convection cell and the pump formula structure of pressure controlling enforcement speed regulating control and the regulator control system formation jumping tooth engagement Gear Planet Transmission that commutation constituted, gear roller 3, internal gear 1, the gear teeth of central gear 2 each gear select identical jumping tooth to form in pairs, and engagement is the gear pair of intermittent drive, the gear pair of the intermittent drive that three kinds of gears are formed combines with the gearing of isolating gear frame 4 and forms the gear roller bearing and form and jump tooth and mesh Gear Planet Transmission, have the function of roller bearing and planetary pinion transmission concurrently, and fluid force is arranged, pump, the pump formula structure of motor combination.
The wherein bearing type rolling transmission that contacts with interference with the root circle of internal gear 1 and central gear 2 respectively of the top circle of the gear roller 3 in the gear roller bearing structure, each surface of contact of isolating gear frame 4, with the fluid height nip that the gear teeth meshing position of each gear in the Gear Planet Transmission forms, make the cooperation of surface of contact at facewidth two ends of gear roller 3 and tooth top and the cooperation in the aperture of isolation gear frame 4 should guarantee the relative transmission pump formula structure formed of the gap of pressure bearing and seal again.
Z
1＝Z
2+Z
3；
Z
1/i
2＝Z
1′；
Z
2/i
2＝Z
2′；
Z
3/i
2＝Z
3′；
ε
max＜i
2＜i
1·ε
min
i
2Be respectively Z
1, Z
2, Z
3Approximate number
i
1Be respectively Z
1', Z
2', Z
3' prime number
Z′/i
1＝a
1……Z
1″；
Z/i
1＝a
2……Z
2″；
Z
1″+Z
2″＝i
2
Above-listed various in:
Z
1, Z
2, Z
3Be respectively the design number of teeth of the master gear of internal gear 1, central gear 2, gear roller 3.
Z
1', Z
2', Z
3' be respectively Z
1, Z
2, Z
3Number of actual teeth behind the jumping tooth.i
2For gear roller 3 reduces teeth groove, internal gear 1 and central gear 2 reduce the jumping tooth circular pitch of the number of actual teeth behind the tooth and the multiple of design number of teeth circular pitch, promptly jump the number of teeth.
i
1Number of packages for gear roller 3
ε
Max, ε
MinFor gear roller 3 respectively with internal gear 1, the maximum value and the minimum value of the contact ratio of the design number of teeth in engagement driving of central gear 2.
Z
1", Z
2" be respectively Z
1'/i
1, Z
2'/i
1The aliquant surplus number of teeth.
The condition of above-listed various establishment is roller gear 3 circumference five equilibrium in the hole that isolates gear frame 4, and the circumference five equilibrium obtains also having guaranteed the radial mechanical balance of total the simplification except making design and processes.
Z
3' be preferably odd number, each gear roller 3 is increased with the quantity that internal gear 1 and central gear 2 mesh simultaneously.
The transmission implication of the jumping tooth Gear Planet Transmission of above-listed various expression is:
1, i
2＞ε
MaxRepresent that each gear is that the rolling transmission of bearing type and the engagement driving of gear pair all are intermittent drive.
2, no matter straight-tooth or helical teeth, each gear roller 3 have only a tooth engagement at most during with internal gear 1 and central gear 2 transmissions.
3, at i
1In the engagement driving of individual gear roller 3, have at least a gear roller 3 to mesh simultaneously with internal gear 1 and central gear 2 respectively.
4, each gear roller 3 have at least a tooth with internal gear 1 or central gear 2 engagement driving.
5, any time in transmission, when arbitrary gear roller 3 meshed simultaneously with internal gear 1 and central gear 2 respectively, the radially line at two contact pointss and roller gear 3 centers in line.
As mentioned above, be not difficult to find out that the rolling transmission and the engagement driving of interruption use interval gear frame 4 synchronous with each gear roller 3 revolution, the Gear Planet Transmission of being formed is as the Z of end jumping tooth
1, Z
2, Z
3, be same continuous Gear Planet Transmission.The fluid of the height nip of the pump formula structure that this transmission constituted connects regulation and control by each pump discharge orifice 5 with control system, and with the extending end of central gear 2 as input shaft, with internal gear 1 and the extending end of isolating 4 arbitrary of gear frames as output, select different Transmission Parts, the rotation speed change that obtains different range forms stepless change.
The present invention has adopted the rolling transmission of interruption and the pump formula structure of the continuous Gear Planet Transmission composition that jumping tooth engagement driving is constituted, fluid is radially intercepted by the rolling transmission of interference at each height nip of jumping wheel tooth engagement formation, its sealing not only can be made liquid pump, also can make air pump; i
2＞ε
MaxNot only spur gear can not have pocketed oil, and helical teeth too; The radially offset loading force that does not only add in the transmission, simultaneously transmission shaft can also bear bigger radially with axial working load, after adding the jumping tooth, stay between bigger transverse tooth thickness modified spatial, the bearing strength of the whole gear teeth can be doubled and redoubled, this all is that the gear pump of common tooth can not be accomplished, this structure can be independent, series connection, compose in parallel stepless speed variator miscellaneous, and slewing range is big, high low-speed characteristic is good, and the automatic control reduction of speed increases the superior technical-economic index of turning round with other, remove and be used for all kinds of machineries, outside the hydraulic transmission, particularly can fully satisfy the speed change of all kinds of automobiles, the differential requirement, even can form the drive line of whole automobile, finish many bridges and drive, and the requirement of other additional controlled variable power of automobile directly is provided.
Description of drawings
Fig. 1 is the pump-type stepless speed variator with gears and roller bearing principle schematic.
Fig. 2 is an auto continuously variable transmission axial section schematic representation.
1, internal gear; 2, central gear; 3, gear roller; 4, isolate gear frame; 5, pump discharge orifice; 6, internal gear; 7, central gear; 8, gear roller; 9, isolate gear frame; 10, key; 11, transmission joint ring; 12, off-load ring.
Embodiment
Use the essentially identical pump-type stepless speed variator with gears and roller bearing of two covers to be connected into one and can be suitable for the stepless change that vehicle transmission requires.
As shown in Figure 2, wherein one overlaps internal gear 1, central gear 2, gear roller 3, isolate gear frame 4 as input system, power is by the outrigger shaft input of central gear 2, another set of internal gear 6, central gear 7, gear roller 8, isolate gear frame 9 as output system, power is by the outrigger shaft output of central gear 7, end tooth by transmission joint ring 11 two ends and input are that the isolation gear frame 9 corresponding end teeth of internal gear 1 and output system connect run-in synchronism, the internal gear 6 that to export system with key 10 is fixing, each pump discharge orifice 5 of input system and output system respectively with control system connects enforcement with the high pressure oil of two systems with low pressure oil by connecting pipe to be regulated and control, and constitutes complete speed variator system.
In the system, isolate gear frame 4 and 9 and revolved round the sun synchronously in branches such as the position circumference precision location of each gear roller 3 and 8 respectively.Isolate gear frame 4 with 9 respectively cooperate surface of contact should keep rotating flexibly the time assurance pressure oil pressure bearing and seal.As stepless speed variator, can with two cover systems separately central gear 2 and 7 and gear roller 3 and the 8 height nips that produced of engagement by isolating gear frame 4 and 9 endoporus increase, top circle with respect to two central gears 2 and 7 is reserved passage, with the inner UNICOM of oil circuit of each height nip to reduce transmission loss.
The paired external diameter of the off-load ring of making 12 root circle that equals the top circle of gear roller 3 and 8 and central gear 2 and 7 respectively two ends of two kinds of gears of originally packing into respectively, pack into the hole and the roller gear axle interference fit of off-load ring 12 of each gear roller, bigger gap is left with axle in pack into the hole of two central gear off-load rings 12, the outside diameter control fitted position of paired off-load ring produces the interference contact and applies preload, in transmission, can guarantee the contact pressure of the root circle of the top circle of gear roller 3 and 8 and internal gear 1 and 6 all the time, when intercepting the radially leakage of oil of height nip, utilized the sliding force of non-pure rolling in the rolling transmission, balance gear roller pressure that the hole wall of isolating gear frame is produced in transmission, adopt internal gear 1 that off-load ring 12 can be bigger with technology difficulty and 6 and the manufacturing tolerances increase of the root circle of central gear 2 and 7, improved manufacturability.
In the said system, the Z of internal gear 1,6
1=60, the Z of central gear 2,7
2=30, the Z of gear roller 3,8
3=15.Jump number of teeth i
2=3, the number of packages i of gear roller 3,8 each cover
1It is listed various that foregoing jumping tooth Gear Planet Transmission is satisfied in the collocation of=3, two each autoregressive parameter of cover system respectively.
When the speed changer, oil path control system can according to the following transmission principle of pump formula structure with to be equipped with.
When center gear 2 and 7 was just changeing in the same way, slewing range can be selective between n=0 → 3n, and the high low pressure oil circuit connects constant.N-input speed in the formula/minute, n
1-output speed/minute.
Work as n
1Input system is controlled at the high pressure oil outlet of output system with the zone of high pressure UNICOM of output system during＜3n/5.Work as n
1During=3n/5, input system equates with the volume-variation of the zone of high pressure of output system.At n
1In the slewing range of≤3n/5, the oil pressure transmission of input system is half fluid power, half pump formula, and output system is half fluid power, half motor type.
Work as n
1During＞3n/5, the high-pressure outlet of input system is controlled.At this moment, input system is controlled hydraudynamic drive, driving output shaft, and output system is the regulation and control pump of a zero load.
When the output shaft counter-rotating is rolling-back of car, the coupling direction when output system is just being changeed with the high low pressure oil circuit of importing system, the high pressure oil outlet of output system is controlled, and the system of input at this moment is a pump, and output system is the controlled variable motor.
When just changeing, the zone of high pressure of input system and the low pressure area of output system, pressure increase and decrease direction is identical, show it is that speed governing changes, pressure increase and decrease direction is opposite, show that descending quickens, the opposite information start-up control system that utilizes that two corresponding sensors relatively obtain is the direction throttling to output, and the braking descending quickens.Same principle, braking reversing descending quickens.
In car running process, when load surpasses rated load,, the controlling element auto-control reduction of speed that is arranged on the zone of high pressure of input system turns round but increasing.If the rotating speed torque characteristics of known engine is also monitored its rotating speed simultaneously and is arranged at that to import be that the pressure transducer of zone of high pressure combines, can realize that automatic reduction of speed in the whole speed range of automobile increases and turn round and automatic speed changing, make the output of motor and load balance mate energy-conservation.
When this speed changer is used as the automobile variable speed transmission, whole transmission oil circuit sealing, can keep the shortest oil circuit transmission, power loss is dropped to minimum, when oil circuit was open, stepless speed variator can become controlled variable displacement pump, the variable power source suitable with engine power directly is provided, realize the lifting of automobile, container upset, additional functions such as brake.
Claims (2)
1. one kind with plural gear roller (3), internal gear (1), in the structural fluid loop of central gear (2) and isolation gear frame (4), flow by convection cell and pressure controlling are implemented the pump-type stepless speed variator with gears and roller bearing that speed regulating control and regulator control system that commutation constituted are formed, gear roller (3) in the jumping tooth engagement Gear Planet Transmission that it is characterized in that forming, internal gear (1), it is the gear pair of intermittent drive that the gear teeth of each gear of central gear (2) select the identical jumping number of teeth to form paired the engagement, and the gear pair of the intermittent drive of three kinds of gear compositions combines with the gearing of isolating gear frame (4) and forms the pump formula structure that gear roller bearing formation jumping tooth meshes continuous Gear Planet Transmission.
2. pump-type stepless speed variator with gears and roller bearing according to claim 1, the top circle that it is characterized in that the gear roller (3) in the gear roller bearing structure respectively with the root circle of internal gear (1) and central gear (2) with the transmission of interference touch scrolling, each surface of contact of isolating gear frame (4), the fluid height that the gear teeth meshing position of each gear in the Gear Planet Transmission is formed, low pressure area makes the cooperation of surface of contact at facewidth two ends of gear roller (3) and tooth top and the cooperation in the aperture of isolation gear frame (4) should guarantee the pump formula structure of forming in the gap of not only relative transmission but also pressure bearing and seal.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB011288736A CN100387868C (en) | 2001-09-19 | 2001-09-19 | Pump-type stepless speed variator with gears and roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB011288736A CN100387868C (en) | 2001-09-19 | 2001-09-19 | Pump-type stepless speed variator with gears and roller bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1338579A CN1338579A (en) | 2002-03-06 |
| CN100387868C true CN100387868C (en) | 2008-05-14 |
Family
ID=4668686
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB011288736A Expired - Fee Related CN100387868C (en) | 2001-09-19 | 2001-09-19 | Pump-type stepless speed variator with gears and roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100387868C (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3283783B1 (en) * | 2015-04-12 | 2020-09-30 | Concept&design Ltd. | A hydrostatic transmission and method of operation |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2349075A1 (en) * | 1976-04-20 | 1977-11-18 | Libourel Rene | Automatic vehicle transmission system - generates torque proportional to drive speed of motor and has satellite pinions and crown wheel held by means of hydraulic pressure |
| CN85108936A (en) * | 1985-12-06 | 1987-09-02 | 方祖彭 | Hydraulic stepless speed change fewer differential teeth planetary decelerator series |
| CN2077933U (en) * | 1990-04-24 | 1991-05-29 | 李玉涛 | Controllable hydraulic twister |
| JPH07317884A (en) * | 1994-05-25 | 1995-12-08 | Nippon Seiko Kk | Rotation support device for planetary gear |
| JPH08247245A (en) * | 1995-03-07 | 1996-09-24 | Koyo Seiko Co Ltd | Continuously variable transmission |
-
2001
- 2001-09-19 CN CNB011288736A patent/CN100387868C/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2349075A1 (en) * | 1976-04-20 | 1977-11-18 | Libourel Rene | Automatic vehicle transmission system - generates torque proportional to drive speed of motor and has satellite pinions and crown wheel held by means of hydraulic pressure |
| CN85108936A (en) * | 1985-12-06 | 1987-09-02 | 方祖彭 | Hydraulic stepless speed change fewer differential teeth planetary decelerator series |
| CN2077933U (en) * | 1990-04-24 | 1991-05-29 | 李玉涛 | Controllable hydraulic twister |
| JPH07317884A (en) * | 1994-05-25 | 1995-12-08 | Nippon Seiko Kk | Rotation support device for planetary gear |
| JPH08247245A (en) * | 1995-03-07 | 1996-09-24 | Koyo Seiko Co Ltd | Continuously variable transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1338579A (en) | 2002-03-06 |
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| PB01 | Publication | ||
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| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080514 Termination date: 20110919 |