CN2660218Y - Double point gear speed reducer of ordinary gear train - Google Patents
Double point gear speed reducer of ordinary gear train Download PDFInfo
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- CN2660218Y CN2660218Y CN 200320126094 CN200320126094U CN2660218Y CN 2660218 Y CN2660218 Y CN 2660218Y CN 200320126094 CN200320126094 CN 200320126094 CN 200320126094 U CN200320126094 U CN 200320126094U CN 2660218 Y CN2660218 Y CN 2660218Y
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- gear
- meshed
- multipoint
- reducing device
- fixed shaft
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Abstract
The utility model relates to a multi-point meshing gear reducing device of ordinary gear chain, which is used to solve the problem of the traditional gear reducing device that the transmission capacity of the gear pair fails to be given a full play. The utility model consists of a shell and a gear pair, characterized in that a plurality of gears (2) are meshed with a center gear (1) so as to achieve the maximization of service life of large and small gears or transmission torque of the device. As a universal device, the utility model can be widely applied in a variety of industries. The utility model can fully gives a full play to the transmission torque capacity of the gear pair, especially the large and heavy reducing devices; and also substantially decreases the size and weight of the gear reducing device with same carrying capacity, thus greatly reducing the production cost.
Description
Affiliated technical field
The utility model relates to a kind of fixed shaft gear train multipoint meshed gear speed-reducing device.
Background technique
The fixed shaft gear train gear reducer is compared with other mechanical deceleration device, is a kind of mechanical deceleration device of multiple advantages such as to have bearing capacity big, and velocity ratio is constant, thereby has obtained to use widely.
But also there are some shortcomings in existing fixed shaft gear train gear reducer:
1. the ability of gear carrying is not brought into play fully.For example, the normal kind of drive that adopts a pair of gear to be meshed of traditional fixed shaft gear train gear reducer like this, has just been wasted and can have been arranged many chances that gear is meshed simultaneously; Again for example, in the relatively advanced flexible gearing of technology, though also adopted many kinds of drive that gear is meshed,, still wasted and can arrange more chances that gear is meshed simultaneously; Consequently, lost the transmission capacity of several times under many circumstances.
2. under the bigger situation of velocity ratio, be difficult to realize the equivalent life design of gear pair.In design, though small gear has been selected for use better material and carried out better heat treatment,, only cause the phenomenon of scrapping of whole gear pair owing to the inefficacy of small gear, turned a blind eye to by many people, caused a large amount of wastes of the wealth of society.
3. can arrange more chances that gear is meshed simultaneously owing to having wasted, cause under the situation of equal specified output torque, the size of speed reducer, weight are very big, and occupation space and manufacture cost are also corresponding to be increased substantially.
The purpose of this utility model is, design a kind of can overcome above-mentioned shortcoming have that volume is little, in light weight, the rational more novel fixed shaft gear train multipoint meshed gear speed-reducing device of price performance.
Summary of the invention
Basic design of the present utility model is: getting a certain gear is central gear, what be meshed with this central gear is realizing big small gear equivalent life and realizing that the moment of torsion that this device transmits increases substantially even the maximum a plurality of gears that turn to purpose, and reaches the purpose of this utility model with this.
As quantize expressing, can make the number of teeth of a plurality of gears that are meshed with its central gear and greater than 0.9 times of the number of teeth of its central gear.For the ease of realizing the equivalent life design of whole transmission, can also make the number of teeth of a plurality of gears that are meshed with its central gear and therein between 0.9 times and 1.1 times of the number of teeth of heart gear.
Realize the common transmission of multi-gear, can adopt the shunt kind of drive of single power source, also can adopt the associating driving mode of a plurality of power sources.When adopting the shunt kind of drive of single power source, because transmission way of the present utility model is more, what drive a plurality of gears of being meshed with its central gear is the parallel four-bar linkage of multiple spot transmission, can obtain better transmission effect.Certainly, drive a plurality of gears be meshed with its central gear be the parallel four-bar linkage of multiple spot transmission the time, do not repel the associating driving mode of a plurality of power sources yet.
When adopting a plurality of gear that parallel four-bar linkage drives with its central gear is meshed of multiple spot transmission, this transmission device can have the structure of multistage transmission.
Because the utility model has adopted the common transmission of multi-gear,, in the Transmitted chains that drives a plurality of gears that are meshed with its central gear, be provided with load-balancing device in order under the certain condition of accuracy of manufacturing, to improve transmission quality.
When drive a plurality of gears be meshed with its central gear be the parallel four-bar linkage of multiple spot transmission the time, aforesaid load-balancing device can also constitute by having the porose disc that all carries parallel four-bar linkage groove, the multiple spot transmission; Also can constitute by radial spring.
Certainly, rotating part and the parts of forming the parallel four-bar linkage of multiple spot transmission should be the pieces O.K.s that meets the balance code requirement, and at this moment, it is a preferable solution that equilibrium block is set on bent axle.
As a kind of gear reducer, the moment of torsion of its transmission must come balance by certain external force or moment of face.In the prior art, the most common way is to utilize stone bolt that casing is fixed; Better method then is to utilize the torsion bar device to come balance in addition.But prior art do not consider when being driven part and having power bigger, that size and Orientation is constant substantially, the problem of utilizing the additional force of the equilibrium of forces system generation of transmission device to be offset.Therefore, on the direction parallel with the cardinal principle of the substantially constant power suffered by the component of its driving, and trying hard to keep with this and to hold the position of big distance, be provided with monolateral or bilateral but asymmetric torque balance device, is an effective solution.
Description of drawings
11 pages of the utility model drawings attacheds, totally 18 width of cloth.Wherein: Fig. 1 is embodiment one a structure diagram; Fig. 2 is embodiment two a structure diagram; Fig. 3 is embodiment two a schematic diagram of mechanism; Fig. 4 is embodiment four a structure diagram; Fig. 5 is embodiment five a structure diagram; Fig. 6 is embodiment six a structure diagram; Fig. 7 is the sketch with a kind of porose disc that all carries function; Fig. 8 is embodiment seven a structure diagram; Fig. 9 is embodiment eight a structure diagram; Figure 10 is embodiment three a structure diagram; Figure 11 is embodiment nine a structure diagram; Figure 12, Figure 13, Figure 14, Figure 15 are respectively the structure diagrams of the different radial spring of several structures [27]; Figure 16 is the structure diagram of expressing the mounting point of equilibrium block [29]; Figure 17, Figure 18 are two kinds of deformation mechanisms that are used to represent the parallel four-bar linkage of multiple spot transmission.
Below embodiment and being described further in conjunction with the accompanying drawings just.
Embodiment one, as shown in Figure 1.Among the figure, [1] is casing, and [2] are central gears, and [3] be meshed with central gear [2], to realize big small gear equivalent life and to realize that the torque maximization of transmitting is a plurality of gears of purpose.In the drawings, the small gear number that specifically draws is 8.
Embodiment two, as shown in Figure 2.In Fig. 2, [4] are the gear drives shown in the embodiment one, in the present embodiment, drive the parallel four-bar linkage of the multiple spot transmission of being made up of crank [5], porose disc [6] and bent axle [7] of a plurality of gears be meshed with its central gear.Here, the offset of crank [5] and bent axle [7] equates.
Fig. 3 is embodiment two a schematic diagram of mechanism, and with the kinematic relation of the parallel four-bar linkage that further specifies the multiple spot transmission of being made up of crank [5], porose disc [6] and bent axle [7], it turns to by symbol [8] represents.Need special one carry be, the parallel four-bar linkage of multiple spot transmission can have various deformation, Figure 17, shown in Figure 180 be wherein two kinds.In Figure 17, only be that the position with bent axle [7] has moved on to the next door; And in Figure 18, then be that bent axle [7] is respectively in both sides, so that carry out two the driving, to avoid carrying out single phenomenon that causes the load inequality that drives when bent axle [7] is other to be put.Note that among Figure 17, Figure 18, the shape of porose disc changes to some extent, still, its effect and working principle do not change, and therefore, still are denoted by porose disc [6], as for crank [5], are to have continued to use original mark yet.
Embodiment three, as shown in figure 10.Among the figure, [24], [25] all are the gear drives shown in the embodiment two, and this is a kind of structural type of secondary transmission, certainly, can also make the form of multistage transmission.Why different their size is, and purpose is to realize the coupling of its power.
Embodiment four, as shown in Figure 4.Among the figure, [4] are the gear drives shown in the embodiment one, and [10] are a plurality of asynchronous motors, are used for each small gear of single driving.Because asynchronous motor has softer mechanical property and when the same load of the common driving of a plurality of asynchronous motors, has the effect of rotating speed advolution, be enough to have the device that all carries function and use as a kind of; Add and to use the electric control system of loading between each asynchronous motor of balance, just form a kind of more complete device that all carries function that has.In the diagram of present embodiment, asynchronous motor [10] directly links with small gear, and as required, they can also link by certain speed reducer and small gear etc.
Embodiment five, as shown in Figure 5.Among the figure, [4] are the gear drives shown in the embodiment one, and [12] are a plurality of oil hydraulic motors, are used for each small gear of single driving.When selecting variable hydraulic motor for use, itself just can constitute load-balancing device; When selecting constant displacement hydraulic motor for use, if they are parallel in the oil hydraulic circuit, they also have the function of automatic load sharing, and therefore, they also are a kind of devices that all carries function that has.In the diagram of present embodiment, oil hydraulic motor [12] directly links with small gear, and as required, they also can link by certain speed reducer and small gear etc.
Embodiment six, as shown in Figure 6.In this figure,, used partial enlarged drawing in order to see details clearly.Among the figure, [4] are the gear drives shown in the embodiment one, and [14] are the transmission shafts with bigger torsional deflection ability.It originally can be longer from axially directly adding of gear shaft, for fear of taking bigger space, thereby makes the form of the location overlap of this and small gear.It locates to link with small gear in [15], and its connecting mode can adopt flat key, also can adopt spline or expansion set connection etc.Certainly, when adopting expansion set to connect, need suitably change its concrete structure.Undoubtedly, this structure itself also is a kind of device that all carries function that has.What need draw attention to a bit is, this have the device that all carries function and also be applicable to embodiment's two described gear drives.
In addition, in embodiment two, because porose disc [6] is a larger-size part, therefore, the device that it all carries function for having of top narration and this part unite two into one possibility are provided.
Fig. 7 is the sketch with a kind of porose disc that all carries function, and the porose disc note of this form is made porose disc [26].Wherein, [16] be the hole that is used to drive crank, [17] be the bar that is shaped on hole [16], why this bar makes more special shape, and its purpose is, when the hole [16] that drives crank is subjected to the power of any direction, distortion by bar [17], make the center line place in hole [16] locate, on all directions, have essentially identical rigidity and have bigger elastic deformation amount, to realize the function of symmetrical load, compensation integration foozle.Therefore, itself also is to have a kind of device that all carries function.
Embodiment seven, as shown in Figure 8.In Fig. 8, [19] be one of gear drive shown in embodiment one, two, three, four, five or six, in the present embodiment, on the parallel direction of the cardinal principle of the direction of direction suffered and the constant substantially power [P] of size and keep that the position of big distance [a] is provided with monolateral torque balance device [20] by the component of its driving.The structure of this torque balance device can be used in the flexible gearing with the structure of base part, has also repeated no more at this.The purpose that Equilibrator is done monolateral setting in such position is, when be driven part turn to relative fixed the time, at equilibrant to the axis " O " of central gear when locating to simplify, can produce an additional power, at this moment, just can utilize this additional power to come balanced action load on this axis, that size and Orientation is constant substantially, for example, the weight that is driven part in flexible gearing is very big, turn to relative fixed and this transmission device to be directly installed on when being driven on the part.
Embodiment eight, as shown in Figure 9.In Fig. 9, [19] also be one of gear drive shown in embodiment one, two, three, four, five or six, in the present embodiment, on the parallel direction of the cardinal principle of the direction of direction suffered and the constant substantially power [P] of size and keep that the position of big distance [a] and [b] is provided with bilateral but the asymmetric Equilibrator of trimming moment [22] and [23] by the component of its driving.Please note, here the difference of only requiring moment is bigger, therefore, can use the balancing pole with rigidity to reach this purpose with different throw of eccentric, also can adopt the balancing pole of identical throw of eccentric and different-stiffness to reach this purpose, also can adopt the mode of its combination etc.The structure of this torque balance device can be used in the flexible gearing equally with the structure of base part, has also repeated no more at this.The purpose that so asymmetric Equilibrator is set still is, when be driven part turn to relative fixed the time, at two equilibrant to the axis " O " of central gear when locating to simplify, can produce an additional power, at this moment, also can utilize this additional power to come balanced action load on this axis, that size and Orientation is constant substantially, for example, the weight that is driven part in flexible gearing is very big, turn to relative fixed and this transmission device to be directly installed on when being driven on the part.
Embodiment nine, as shown in figure 11.In the present embodiment, the load-balancing device of use is radial spring [27], owing to radial spring has by radial deformation to come the compensation integration foozle, realize the function that each gear substantially all carries, thereby has unique effect.In the present embodiment, radial spring [27] is mounted on the porose disc [6].The concrete form of radial spring can be a lot, and shown in Figure 12 is that a kind of employing rubber is done elastomeric radial spring; Figure 13, Figure 14, shown in Figure 15 then be the radial spring that adopts elasticity preferred metal material elastomer-forming.
Equilibrium block [28] also is housed in the present embodiment, be used for speed of crankshaft higher but when not too high to the balance of porose disc [6]; After the rotating speed of bent axle further improves, should use bilateral equilibration piece [29] as shown in figure 16, to eliminate additional torque because of using the unilateral equilibration piece to bring.
Compared with prior art, advantage of the present utility model is:
1. can excavate the gear pair transmitting torque ability of power in other words more fully, the dimension and weight of the identical gear drive of bearing capacity is significantly reduced.
2. can receive reducing significantly and because the dual economy benefit and the social benefit of the corresponding reduction that reduces the manufacturing expense of bringing significantly of size owing to weight.
3. this apparatus structure is compact, and it is little to take up room.
4. owing to adopted the parallel four-bar linkage of multiple spot transmission, the Combination Design of the multipolarity of this device can be realized easily, more above-mentioned advantage can be given full play to.
5. owing to adopted monolateral or bilateral but asymmetric torque balance device, can offset partial load effectively, improve transmission quality.
Embodiment
Realize that optimum scheme of the present utility model is: start with from design work, the policy of working along both lines of adopt releasing the new series product and in the process of the overhauling reform of existing product existing product being substituted is carried out specialization production.
When adopting a plurality of gear that parallel four-bar linkage drives with its central gear is meshed of multiple spot transmission, following each point be should give attention: 1. there are the angle requirement in the gear teeth and the eccentric shaft on the crank of the gear that connects with crank; 2. shaftgear and the crank with the crank connection preferably is split into fabricated structure, otherwise, should be specifically noted that its assembly condition; 3. each rotational parts, particularly crank, bent axle (and combination) should carry out corresponding dynamic and static balance by design code; 4. bearing is advisable to select rolling bearing for use as far as possible, and notes carrying out rational Combination Design; 5. to the mounting hole of each gear and each hole on the porose disc, should propose clear and definite and reasonably position degree requirement; 6. note lubricated reliability etc.
Claims (11)
1. fixed shaft gear train multipoint meshed gear speed-reducing device, it comprises casing and gear pair, it is characterized in that what be meshed with its central gear [2] is to realize big small gear equivalent life and to increase substantially even the maximum a plurality of gears [3] that turn to purpose with the moment of torsion of realizing this device transmission.
2. fixed shaft gear train multipoint meshed gear speed-reducing device as claimed in claim 1 is characterized in that, what drive a plurality of gears be meshed with its central gear is the parallel four-bar linkage { [5], [6] and [7] } of multiple spot transmission.
3. fixed shaft gear train multipoint meshed gear speed-reducing device as claimed in claim 2 is characterized in that, it has the structural type { [24] and [25] } of multistage transmission.
4. fixed shaft gear train multipoint meshed gear speed-reducing device as claimed in claim 1 is characterized in that, is provided with load-balancing device [10], [12] or [14] in the Transmitted chains that drives a plurality of gears that are meshed with its central gear.
5. fixed shaft gear train multipoint meshed gear speed-reducing device as claimed in claim 2 is characterized in that, is provided with load-balancing device [14], [26] or [27] in the Transmitted chains that drives a plurality of gears that are meshed with its central gear.
6. fixed shaft gear train multipoint meshed gear speed-reducing device as claimed in claim 5 is characterized in that, described load-balancing device is porose disc [26].
7. fixed shaft gear train multipoint meshed gear speed-reducing device as claimed in claim 5 is characterized in that, described load-balancing device is radial spring [27].
8. as claim 1,2,3,4,5,6 or 7 described fixed shaft gear train multipoint meshed gear speed-reducing device, it is characterized in that, on the direction parallel with the cardinal principle of the constant substantially power suffered by the component of its driving, and try hard to keep with this and to hold the position of big distance, be provided with monolateral or bilateral but asymmetric torque balance device [20] or { [22] and [23] }.
9. as claim 1,2,3,4,5,6 or 7 described fixed shaft gear train multipoint meshed gear speed-reducing device, it is characterized in that the number of teeth of its a plurality of gears [3] and greater than 0.9 times of the gearwheel number of teeth.
10. fixed shaft gear train multipoint meshed gear speed-reducing device as claimed in claim 9 is characterized in that, the number of teeth of its a plurality of gears [3] and between 0.9 times to 1.1 times of the gearwheel number of teeth.
11. as claim 2,3,5,6 or 7 described multipoint meshed gear speed-reducing device, it is characterized in that, equilibrium block [28] or [29] be housed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200320126094 CN2660218Y (en) | 2003-11-22 | 2003-11-22 | Double point gear speed reducer of ordinary gear train |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200320126094 CN2660218Y (en) | 2003-11-22 | 2003-11-22 | Double point gear speed reducer of ordinary gear train |
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| Publication Number | Publication Date |
|---|---|
| CN2660218Y true CN2660218Y (en) | 2004-12-01 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200320126094 Expired - Lifetime CN2660218Y (en) | 2003-11-22 | 2003-11-22 | Double point gear speed reducer of ordinary gear train |
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| CN (1) | CN2660218Y (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100359211C (en) * | 2003-11-21 | 2008-01-02 | 山东省冶金设计院 | Multipoint meshing gear speed reducing device |
-
2003
- 2003-11-22 CN CN 200320126094 patent/CN2660218Y/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100359211C (en) * | 2003-11-21 | 2008-01-02 | 山东省冶金设计院 | Multipoint meshing gear speed reducing device |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Effective date of abandoning: 20080102 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |