High-efficiency high-power small-tooth-difference speed increasing or reducing power transmission device

Abstract

A high-efficiency high-power small-tooth-difference speed increasing or reducing power transmission device comprises an inner gear ring (1) in a circumferential floating state, two end faces of the inner gear ring (1) are fixedly connected with center plates (3) respectively, hollow shaft sleeves (4) are arranged in the centers of the center plates respectively, and first bearings (7) arranged on inner rings of the hollow shaft sleeves support mandrels at the two ends of an eccentric wheel (5) respectively. A second bearing (8) is arranged on the outer ring of the hollow shaft sleeve, the outer ring of the second bearing is fixedly connected to the static part, the end face of one hollow shaft sleeve is fixedly connected with an output / input shaft (10), and the end face of the other hollow shaft sleeve freely passes through a mandrel at one end of the eccentric wheel; the inner gear ring is meshed with more than one outer gear (2), and the center part of each outer gear is respectively supported on a rotating arm bearing (6). The gear can be widely applied to universal automobile transmission, train coupling transmission and airplane and ship transmission, and the tooth form of a meshing pair can be an involute, a cycloid or a circular arc tooth form.

Description

Technical Field

[0001] The invention relates to a gear transmission technology, in particular to a small-tooth-difference planetary gear transmission technology, specifically to a high-efficiency, high-power, small-tooth-difference speed-increasing or speed-reducing power transmission device. Background Art

[0002] As is known to all, small-tooth-difference planetary reducers (plane centric gear units - a common name abroad) have many advantages such as small size, light weight, low noise, low meshing linear speed, and extremely low contact stress. Together with cycloidal pinwheel reducers, they occupy the main market of small and medium-sized power and high speed ratio. Although there are many structural forms, they all have a common disadvantage that the transmission efficiency is not ideal (including cycloidal pinwheel type). The SCC series small-tooth-difference planetary reducers and SCC developed by the inventors II The series of planetary reducers with small tooth difference and our utility model patent ZL88211046.2 rolling pin sleeve output mechanism are used, but their efficiency is still not ideal, especially in high-power and extra-high-power transmission devices. Efficiency is a very sensitive issue. For example, 1% efficiency of a 10000kW speed increaser and reducer means 100kW of energy consumption or income; most of the 1000-2000kW wind power speed increasers produced in large quantities in my country today use 2-stage external gear meshing gear trains, which have high processing accuracy and large tooth contact stress (up to 80-100kg / mm 2 Or higher), while the contact stress of the corresponding small-tooth difference gear train is only 8-10KG / mm 2 The speed is about 1000 kW or lower, and the noise is generally below 70dB, but its rotation efficiency has not reached the kilowatt level, and the corresponding NGW gear train noise is about 80dB. High-speed and low-speed diesel engines or gas turbines are often used as prime movers, and the speed reducer ratio is between 4 and 8. When high-speed diesel engines or gas turbines are used as prime movers (n = 3000-6000r.pm), the weight of the ship's prime mover mechanism can be greatly reduced, and the speed ratio of the corresponding speed reducer may increase to 30 or higher. Relatively speaking, if an external meshing transmission structure is used, it is very large. Summary of the invention

[0003] The purpose of the present invention is to design a high-efficiency, high-power, small-tooth-difference power transmission device for increasing or decreasing power, in view of the problems of large volume and low efficiency of existing small-tooth-difference power transmission devices for increasing or decreasing power.

[0004] The technical solution of the present invention is:

[0005] A high-efficiency, high-power, small-tooth-difference power transmission device for increasing or decreasing the speed, which consists of an inner gear ring 1 in a circumferentially floating state, with a web 3 fixed to each of its two end faces, a hollow sleeve 4 is arranged at the center of each web 3, a first bearing 7 is arranged on the inner ring of the hollow sleeve 4 to support the two end spindles of the eccentric wheel 5, a second bearing 8 is arranged on the outer ring of the hollow sleeve 4, and the outer ring of the second bearing 8 is fixed to a stationary part, one end face of the hollow sleeve 4 is fixed to the output / input shaft 10, and the end face of the other hollow sleeve 4 is freely passed by one end spindle of the eccentric wheel 5; the inner gear ring 1 is meshed with more than one outer gear 2, and the core of each outer gear is supported on a rotating arm On the bearing 6, when multiple external gears 2 are used, the circumferential angles of the eccentric wheels axially arranged on the eccentric wheel 5 are equal, forming a small-tooth difference speed-up and speed-down power transmission device; when the web 3 is made into a hole-free structure to form a non-stationary housing power transmission device and no output / input shaft 10, the inner gear ring 1 forms a radial output transmission device, which is characterized in that: the swing arm bearing 6 is a kind of NGW-type tooth meshing pair used to replace the traditional pin-type output mechanism or any other form of output mechanism, which can not only withstand the rolling bearing effect, but also transmit torque between its inner and outer rings. The overall structure can be greatly simplified, the total transmission efficiency can reach more than 95%, and the single machine power can reach tens of thousands of kilowatts. The efficiency of the traditional pin-type small-tooth difference reducer and cycloid pinwheel reducer is only between 65% and 80%.

[0006] The first bearing 7 and the second bearing 8 may be in the same plane or not.

[0007] The tooth shape of the meshing pair is one of involute, cycloid or circular arc teeth.

[0008] The swing arm bearing 6 is composed of an inner ring 11 , an outer ring 13 and a roller planetary gear 12 . The roller planetary gear 12 is located between the inner ring 11 and the outer ring 13 and supports the inner ring 11 and the outer ring 13 .

[0009] Beneficial effects of the present invention:

[0010] 1. The sum of the reaction force of the swing arm bearing and the reaction force of the high-speed shaft end support of the present invention is reduced from 6 times the meshing force of the traditional pin-type output mechanism to 1.5 times the meshing force, that is, F∑≤1.5Ft, the meshing power consumption is only about 1%, the total transmission efficiency can reach more than 95%, and the single-stage speed ratio can reach more than 100. Therefore, the present invention can enter the ranks of high-power, extra-high-power, large-speed ratio and high-efficiency speed increase and reduction machines.

[0011] 2. The noise is 8-10dB lower than that of external meshing under the same processing accuracy.

[0012] 3. The contact stress is only about 1 / 10 of that of external tooth meshing, which can completely eliminate the damage caused by excessive contact stress on the tooth surface. According to the wear control Hang Book Table 4, when the contact stress is 2070N / m, the life is 102527 cycles. It can be seen that the contact stress is reduced by 1 times and the life can be increased by 100 times. Therefore, the tooth surface life of the present invention is increased by 1000 times compared with external tooth meshing.

[0013] 4. The structure is simple, which simplifies the overall structure. Moreover, since the bending stress of the tooth is the main stress, it has strong bearing capacity, small volume and low cost.

[0014] 5. The swing arm bearing 6 of the present invention is a kind of output mechanism that can replace the traditional pin shaft type or any other form of output mechanism. It can not only bear the rolling effect, but also transmit torque between the inner and outer rings. The NGW tooth meshing pair without a planetary carrier can greatly simplify the overall structure. Due to the elimination of the planetary carrier, the number of star gears can reach more than 8, which greatly reduces the contact application! The total transmission efficiency can reach more than 95%, the single machine power can reach tens of thousands of kilowatts, and the contact stress of the external meshing shaft system can reach 80-100kg / mm 2 , and the contact stress of this small-tooth difference gear train is only 8-10kg / mm 2 The noise is generally below 70dB. It can be widely used in general automobile transmission, train wheel transmission, aircraft and ship transmission. The tooth shape of the meshing pair can be involute, cycloid or circular arc tooth shape. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 is a schematic diagram of the double external gear meshing pair structure of the present invention,

[0016] Figure 2 It is a schematic diagram of the meshing structure of three external gears of the present invention.

[0017] Figure 3 It is a schematic diagram of the single external tooth meshing pair structure of the present invention.

[0018] Figure 4 It is a schematic structural diagram of the planet-less NGW tooth-shaped meshing auxiliary swing arm bearing 6 of the present invention.

[0019] In the figure:

[0020] 1. Internal gear ring;

[0021] 2. External gear;

[0022] 3. End plate;

[0023] 4. Hollow sleeve;

[0024] 5. Eccentric wheel;

[0025] 6. Swing arm bearing;

[0026] 7. Bearings;

[0027] 8. Bearings;

[0028] 9. Counterweight;

[0029] 10. Input / output shaft;

[0030] 11. Inner circle;

[0031] 12. Roller type planetary gear;

[0032] 13. Outer circle. DETAILED DESCRIPTION

[0033] The present invention will be further described below in conjunction with the accompanying drawings and embodiments.

[0034] The structures, proportions, sizes, etc. illustrated in the drawings of this specification are only used to match the contents disclosed in the specification for people familiar with this technology to understand and read, and are not used to limit the limiting conditions for the implementation of the present invention, so they have no substantial technical significance. Any modification of the structure, change of the proportion relationship or adjustment of the size, without affecting the effects and purposes that can be achieved by the present invention, should still fall within the scope of the technical content disclosed by the present invention. At the same time, the terms such as "upper", "lower", "left", "right", "middle" and so on quoted in this specification are only for the convenience of description, and are not used to limit the scope of implementation. The change or adjustment of their relative relationship should also be regarded as the scope of implementation of the present invention without substantially changing the technical content.

[0035] Embodiment 1

[0036] like Figure 1 shown.

[0037] A high-efficiency, high-power, small-tooth-difference speed-up or speed-down power transmission device, which consists of an inner gear ring 1 in a circumferentially floating state, with a web 3 fixed to each of its two end faces, a hollow sleeve 4 is arranged at the center of each web 3, the inner ring of the hollow sleeve 4 is provided with a first bearing 7, and the outer ring is provided with a second bearing 8, the first bearing 7 supports the two end spindles of an eccentric wheel 5, the outer ring of the hollow sleeve 4 is provided with a second bearing 8, the outer ring of the second bearing 8 is fixed to a stationary part, the end face of one of the hollow sleeves 4 is fixed to an output / input shaft 10, and the end face of the other hollow sleeve 4 is freely passed by a spindle at one end of the eccentric wheel 5; the inner gear ring 1 is meshed with more than one outer gear 2, and the core of each outer gear is supported on a swing arm bearing 6. When multiple outer gears 2 are used ( Figure 1There are two external gears 2), and the eccentric wheels 5 are axially arranged with the same circumferential angle, forming a small-tooth difference speed-up and speed-down power transmission device; when the web 3 is made into a hole-free structure to form a stationary housing power transmission device without an output / input shaft 10, the inner gear ring 1 forms a radial output transmission device, and the swing arm bearing 6 is a kind of output mechanism that replaces the traditional pin-type output mechanism or any other form of output mechanism. It can withstand the rolling bearing effect, and the NGW-type tooth meshing pair without a planetary carrier that can transmit torque between its inner and outer rings can greatly simplify the overall structure, and the total transmission efficiency can reach more than 95%, and the power of a single machine can reach tens of thousands of kilowatts; while the efficiency of traditional pin-type small-tooth difference reducers and cycloidal pinwheel reducers is only between 65% and 80%. The structural form of the swing arm bearing 6 can be adopted Figure 4 In the structure shown, the swing arm bearing 6 is composed of an inner ring 11, an outer ring 13 and roller planetary gears 12. The roller planetary gears 12 are located between the inner ring 11 and the outer ring 13 and support the inner ring 11 and the outer ring 13. The number of roller planetary gears 12 can be 8 or more, thereby greatly reducing their contact application.

[0038] In specific implementation, the first bearing 7 and the second bearing 8 can be in the same plane or not. The tooth profile of each meshing pair can be one of involute, cycloid or circular arc teeth.

[0039] Embodiment 2

[0040] like Figure 2 shown.

[0041] The difference between this embodiment and the first embodiment is that the number of the external gears 2 is three, and the three external gears 2 are arranged at equal angles in the internal gear ring 1 so that the combined forces acting on the housing are in a force balance state.

[0042] Embodiment 3

[0043] like Figure 3 shown.

[0044] The difference between this embodiment and the first embodiment is that the number of the external gear 2 is one. In this case, a balancing weight 9 should be loaded on the simulated heart wheel shaft to prevent vibration during operation.

[0045] The strength and efficiency calculation example of the present invention when used in a general-purpose reducer is as follows:

[0046] AOriginal conditions:

[0047] a, transmission power N = 20kw, prime mover speed n = 1500r.pm, reduction ratio i = 30

[0048] b. Select tooth profile parameters:

[0049] ① Small tooth difference meshing pair: the number of teeth of the external gear is Z C=30, number of teeth of inner ring gear Z B =31, reduction ratio i1=30, center distance

[0050] a=0.84m,m1=7mm,a=0.84×7=5.88mm,tooth width B1=160mm

[0051] ②NGW toothed rolling bearing: Za=48, Zc=12, Z B =72, m=2, i=1.5, tooth width B2=160mm

[0052] B. Strength calculation:

[0053] A, output torque of internal gear with small tooth difference:

[0054] ①

[0055] ②Circumferential force

[0056] ③Basic bending stress of tooth profile:

[0057]

[0058] b, NGW type rolling bearing:

[0059] ①Torque

[0060] ②Circumferential force:

[0061] ③Basic bending stress of tooth profile:

[0062]

[0063] C, efficiency calculation:

[0064] a,NGW type rolling bearing:

[0065] ①Circumferential force F NGW =77.3kg

[0066] ②Circumferential speed: V NGW =π.dn / 60=3.14×2a×1500 / 60

[0067] =3.14×2×0.84×7×1500 / 60=923mm / sec=0.923m / sec

[0068] ③ Friction power consumption (NGW type gear bearing)

[0069] Assume the tooth profile is in full sliding state, and its friction coefficient μ = 0.1

[0070] Then the friction force P0 = μ.F NGW =0.1×77.3=7.73kg

[0071] Relative sliding speed of tooth profile: V CP =V NGW .ξ

[0072] =0.923×0.2=0.184m / sec

[0073] Friction work E = P0.Vep = 7.73 × 0.184 = 1.42 kgm / sec

[0074] Friction power consumption Wf = E / 102 = 1.42 / 102 = 0.013KW

[0075] efficiency

[0076] b. Calculation of efficiency of small tooth difference pair:

[0077] Output torque: M = M2.i = 13 × 30 = 390 Kgm

[0078] Tooth profile relative speed: V CP =V NGW .ξ=0.923×0.2=0.184m / sec

[0079] Power consumption: Pc.V CT =3714×0.1×0.184=8.23Kgm / sec

[0080] Power consumption

[0081] Total efficiency The working principle of the present invention is:

[0082] The NGW type planetary carrier-free tooth meshing pair swing arm bearing of the present invention has more space because the planetary carrier is eliminated, so the number of roller-type planetary gears can be more, such as 8 to 12, which is more beneficial to the torque. The meshing linear speed of the meshing pair with small tooth difference is low. Generally, its linear speed of small power is about 1m / sec, while the meshing linear speed of the meshing pair with the same power can reach 10 to 15m / sec. Therefore, the tooth surface meshing power consumption in the meshing pair with small tooth difference is only about 1%; while the meshing power consumption of the external meshing pair can reach about 3 to 5%. This is because the external meshing linear speed is much higher than that of the meshing pair with small tooth difference. Because of the involute tooth shape, during the meshing process, when the meshing point leaves the point on the pitch circle diameter, the relative motion between them is in a rolling and sliding mode (see Wearcontrol Hand for details). Book), for the meshing pair with small tooth difference, the main part of power consumption is the bearing, especially the pin-type output mechanism and its swing arm bearing. Take the SCC series 3# machine base as an example (see the Mechanical Design Volume P70-704 of Chemical Industry Press): the tangential meshing force of the external gear Tt = 304kg, the sum of the forces on the pin F∑ = 601kg, the radial force on the swing arm bearing FR = 893kg, and the support reaction force of the high-speed shaft R1 = 293kg. From the above, we know that the total support reaction force of the bearing (including the pin) F∑≈1 787kg is equivalent to about 6 times the meshing force F. According to the test and calculation, the support reaction force of each Ft on the bearing consumes 1.5-2% of the total power. The meshing of the inner gear ring 1 and the outer gear 2 of the present invention is equal in size and opposite in direction on the same straight line, and its support reaction force acts on the bearing 7, so the bearing 7 is a zero-load bearing. If there is only one end plate 3, the bearing 8 must be double-row, and the support reaction force there can reach more than 2 times Fn, so the efficiency is very low. Moreover, due to the uneven contact force of the cantilever meshing tooth surface, it is difficult to adapt to high power and multiple external tooth structures. The sum of the swing arm bearing reaction force and the support reaction force of the present invention is only 1.5Ft, so there is every reason to obtain a meshing pair with higher transmission efficiency than the NGW type and other external meshing pairs, plus the advantages of other types of meshing pairs that the small tooth difference itself cannot match, so the present invention can enter the transmission category of large and extra-large kilowatts and high-efficiency transmission power, such as: providing high-tech equipment for the main transmission system of giant offshore ships and wind power. Recently, the inventor of this invention has been hoping to develop a high-efficiency, high-performance, and high-power speed-increasing and speed-reducing transmission device in adjacent application projects and relevant social departments. We have been developing the SCC series of small-tooth-difference speed reducers for 40 years, and the first inventor of this invention has been engaged in mechanical design for 70 years (this invention is the fifth generation product of the inventor, and the third-fourth generation products have been abandoned due to many shortcomings although they have obtained domestic and foreign patents).

[0083] The above embodiments are only preferred implementation modes of the present invention. It should be pointed out that ordinary technicians in this technical field can make several improvements and equivalent substitutions without departing from the principles of the present invention. These technical solutions after improvements and equivalent substitutions to the claims of the present invention all fall within the protection scope of the present invention.

[0084] The parts not involved in the present invention are the same as the prior art or can be implemented by using the prior art.

Claims

1. A high-efficiency, high-power, small-tooth-difference speed-up or speed-down power transmission device, comprising an inner gear ring (1) in a circumferentially floating state, with a web (3) fixed to each of its two end faces, a hollow shaft sleeve (4) provided at the center of each of the web plates (3), a first bearing (7) provided on the inner ring of the hollow shaft sleeve (4) supporting the two end spindles of the eccentric wheel (5), a second bearing (8) provided on the outer ring of the hollow shaft sleeve (4), the outer ring of the second bearing (8) fixed to a stationary part, an end face of one of the hollow shaft sleeves (4) fixed to an input / output shaft (10), and the other end face of the hollow shaft sleeve (4) fixed to an input / output shaft (10). The end face of the spindle sleeve (4) is freely passed by the spindle of one end of the eccentric wheel (5); the inner gear ring (1) is meshed with more than one outer gear (2), and the core of each outer gear is supported on the swing arm bearing (6). When multiple outer gears (2) are used, the circumferential angles of the eccentric wheels axially arranged on the eccentric wheel (5) are equal, forming a small tooth difference speed increase (decrease) power transmission device; when the web (3) is made into a hole-free structure to form a stationary part housing power transmission device and has no output / input shaft (10), the inner gear ring (1) forms a radial output transmission device, which is characterized by: The swing arm bearing (6) is a kind of output mechanism used to replace the traditional pin shaft type or any other form of output mechanism. It can not only withstand the rolling bearing effect, but also has an NGW-type tooth meshing pair of an invisible star frame that can transmit torque between its inner and outer rings. It can greatly simplify the overall structure, the total transmission efficiency can reach more than 95%, and the single machine power can reach tens of thousands of kilowatts; while the efficiency of traditional pin shaft type small tooth difference reducer and cycloid pinwheel reducer is only between 65% and 80%.

2. The high-efficiency, high-power, small-tooth-difference speed-up or speed-down power transmission device according to claim 1 is characterized in that: The first bearing (7) and the second bearing (8) may be in the same plane or may not be in the same plane.

3. The high-efficiency, high-power, small-tooth-difference speed-up or speed-down power transmission device according to claim 1 is characterized in that: The tooth shape of the meshing pair is one of involute, cycloid or circular arc teeth.

4. The high-efficiency, high-power, small-tooth-difference speed-up or speed-down power transmission device according to claim 1 is characterized in that: The swing arm bearing (6) is composed of an inner ring (11), an outer ring (13) and a roller planetary gear (12). The roller planetary gear (12) is located between the inner ring (11) and the outer ring (13) and supports the inner ring (11) and the outer ring (13).

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