CN203146748U - Double-speed ratio gyration reducer - Google Patents
Double-speed ratio gyration reducer Download PDFInfo
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- CN203146748U CN203146748U CN 201220699254 CN201220699254U CN203146748U CN 203146748 U CN203146748 U CN 203146748U CN 201220699254 CN201220699254 CN 201220699254 CN 201220699254 U CN201220699254 U CN 201220699254U CN 203146748 U CN203146748 U CN 203146748U
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Abstract
The utility model relates to a double-speed ratio gyration reducer used for a device with various working conditions. The reduction gears comprises a first planetary gear transmission unit, a second planetary gear transmission unit, and a hydraulic clutch system, wherein the first planetary gear transmission unit comprises a sun gear, a ring-shaped gear, at least three planetary gears, and a planet carrier all connected with a driving shaft; and the second planetary gear transmission unit comprises a sun gear, a fixed ring-shaped gear, at least three planetary gears, and a planet carrier all connected with the first planetary gear transmission unit. The reducer is characterized in that the hydraulic clutch system selectively allows the ring-shaped gear of the first planetary gear transmission unit to be fixed or rotate freely relative to the drive shaft.
Description
Technical field
The utility model relates to the double speed of equipment that a kind of double speed than rotary reducer, especially has multiple working state than rotary reducer, thereby this double speed comprises planetary gear transmission unit and the hydraulic clutch system that planetary gear transmission unit is carried out hydraulic control change reduction speed ratio/velocity ratio than rotary reducer.
Background technique
Such as revolving in the drilling equipment that digs brill, when drill bit during from underground extracting, thereby drill bit still constantly rotation the mud on the drill bit is thrown away, in order to carry out more deep drilling operation next time.Can expect, in order to get rid of the mud on the drill bit more, need drill bit with high as far as possible rotating speed rotation.But when drill bit pierces when underground, in order to obtain big as far as possible moment of torsion to overcome the resistance of subsurface rock, earth etc., drill bit need be with relatively low rotating speed rotation.
That is to say, in order to realize probing work more efficiently, this revolve dig brill drill bit need moment of torsion must be different when extracting drill bit changing over to different rotating speed rotations, moment of torsion at different operating mode (operating mode when for example, piercing and the operating mode when extracting).
But, prior art such as revolving in the drilling equipment that digs brill, drill bit only links to each other with the rotary reducer that a reduction speed ratio can be provided.Therefore, if change the rotating speed of drill bit, can only change the rotating speed that drives oil hydraulic motor.And well-known, the rotating speed that changes oil hydraulic motor by direct change electric current is not that efficient is high, and can cause the difficulty of oil hydraulic motor design aspect yet.
Therefore, hope further improves to revolve in a kind of lower-cost mode digs brill, thereby when piercing or extract drill bit, drill bit can be with different rotating speed rotations, namely piercing drill bit low speed rotation (high moment of torsion) when underground, and drill bit high speed (low moment of torsion) throws away mud when extracting drill bit, revolves the working efficiency of digging brill with further raising.
The model utility content
In order to pierce when extracting with different rotating speed rotations such as the drill bit that revolves the drilling equipment that digs brill, throw away mud as much as possible in order to improve the rotating speed of drill bit when extracting, and thereby in order to improve the working efficiency of drilling equipment, the utility model proposes a kind of being applicable to such as the double speed that revolves in the drilling equipment that digs brill and compare rotary reducer.This double speed than rotary reducer under the control of hydraulic clutch system can so that drill bit respectively with two different rotating speeds rotations, thereby can when extracting, efficiently throw away the mud that carries from underground, improved the working efficiency of drilling equipment.
According to an aspect of the present utility model, provide a kind of double speed be used to the equipment with multiple working state to compare rotary reducer, it is characterized in that, described double speed comprises first planetary gear transmission unit, second planetary gear transmission unit and the hydraulic clutch system that acts on described first planetary gear transmission unit than rotary reducer
Described first planetary gear transmission unit comprise the sun gear that links to each other with the live axle of described equipment, and the planetary pinion between described sun gear and ring gear, installed of the coaxial mounted ring gear of described sun gear, at least three and install at described planetary pinion and can be around the planet carrier of the coaxial rotation of described sun gear
Described second planetary gear transmission unit comprise the sun gear that links to each other with the planet carrier of described first planetary gear transmission unit, with respect to the co-axially fixed ring gear of this sun gear, at least three the planetary pinion of installing between this sun gear and the ring gear and install at described planetary pinion and can be around the planet carrier of the coaxial rotation of described sun gear
Described hydraulic clutch system has the structure that can make optionally that the ring gear of described first planetary gear transmission unit is fixed with respect to described live axle or rotated freely with respect to described live axle.
Preferably, described double speed comprises housing than rotary reducer, second hydraulic lock assembly that described hydraulic clutch system is included in first hydraulic lock assembly that acts between the ring gear of described housing and described first planetary gear transmission unit and acts between the ring gear of described first planetary gear transmission unit and live axle.
Preferably, described housing is provided with for the oil hole that injects hydraulic oil, described hydraulic clutch system is according to the pressure height of the hydraulic oil that injects, and controls the described first hydraulic clutch locking device respectively or the described second hydraulic clutch locking device correspondingly is in disengaged condition or closed state.
Preferably, when the described first hydraulic clutch locking device was in disengaged condition and the described second hydraulic clutch locking device and is in closed state, the ring gear of described first planetary gear transmission unit maintained static with respect to described live axle.
Preferably, when the described first hydraulic clutch locking device was in closed state and the described second hydraulic clutch locking device and is in disengaged condition, the ring gear of described first planetary gear transmission unit maintained static with respect to described housing.
Preferably, described hydraulic clutch system comprises and acts on the first piston on the described first hydraulic clutch locking device and act on second piston on the described second hydraulic clutch locking device.
Preferably, described hydraulic clutch system also comprises first spring and second spring, described first spring action is on described first piston, so that described first piston is away from the described first hydraulic clutch locking device, described second spring action is on described second piston, so that described second piston contacts the described second hydraulic clutch device.
Preferably, when enough the hydraulic oil of big pressure injected, described first piston and described second piston can move along opposite direction.
Preferably, the described first and second hydraulic clutch locking devices are the polydisc plate clutch.
Preferably, described equipment with multiple working state is to revolve to dig brill.
According to another aspect of the present utility model, a kind of drilling equipment also is provided, for example revolve and dig brill, it comprises that above-mentioned double speed compares rotary reducer.
Adopt the technical solution of the utility model, revolving the drilling rod that digs brill can freely switch at a high speed and between the low speed, thereby can drill efficiently in the mode of the slow-speed of revolution, high pulling torque piercing when underground drilling rod, and when extracting, drilling rod can rotate at a high speed, thereby as much as possible mud is thrown away, be convenient to the operation that pierces next time.With this, improved and revolved the working efficiency of digging brill.
Description of drawings
Can more fully understand aforementioned and other aspect of the present utility model from detailed description described later and in conjunction with following accompanying drawing.In the accompanying drawings:
Fig. 1 shows according to the longitudinal sectional view of double speed of the present utility model than rotary reducer, and wherein this double speed is in first (output at a high speed) serviceability than rotary reducer;
Fig. 2 shows as shown in Figure 1 double speed than the partial enlarged drawing of rotary reducer;
Fig. 3 shows the similar partial enlarged drawing with Fig. 2, but double speed is in second (low speed output) serviceability than rotary reducer; And
Fig. 4 has schematically shown another embodiment according to clutch locking device of the present utility model.
Embodiment
Preferred implementation of the present utility model is described with reference to the accompanying drawings.In each accompanying drawing, identical parts are represented by identical reference character.
Fig. 1 shows according to the longitudinal sectional view of double speed of the present utility model than rotary reducer.This double speed than rotary reducer such as arranging between the driving oil hydraulic motor that revolves the drilling equipment that digs brill and the drilling rod (it links to each other with drill bit).Drive hydraulic motor output shaft and link to each other with the input end of this double speed than rotary reducer, and this double speed can for example link to each other with drilling rod via spline than the output shaft of rotary reducer and drives this drilling rod.According to the utility model, this double speed is connected with hydraulic clutch system operability than rotary reducer, thereby can with two different reduction speed ratio power be passed to drill bit from oil hydraulic motor respectively.
Double speed of the present utility model comprises housing 1, live axle 12, hydraulic clutch system, the first planetary gear transmission unit I and the second planetary gear transmission unit II than rotary reducer.Live axle 12 is used for receiving the input torque from oil hydraulic motor rotating shaft (not shown), so that via the planetary gear transmission unit outputting power.Housing 1 is used for installing live axle 12, the first planetary gear transmission unit I and the second planetary gear transmission unit II.The hydraulic clutch system is used for the first planetary gear transmission unit I is controlled, make the two work simultaneously or only the second planetary gear transmission unit II work so that whole double speed switches between two gears than the velocity ratio of rotary reducer.Here said " working " refers to first or second planetary gear transmission unit and has the input-output speed discrepancy.Below specify double speed than the each part mentioned above of rotary reducer.
At first, it is to be noted if do not mention especially that double speed of the present utility model is rotational symmetric structure than the each several part of rotary reducer.
The first planetary gear transmission unit I installs in housing 1 via bearing 21.The first planetary gear transmission unit I mainly comprise the gear sleeve 14 that is provided with annular tooth, sun gear 12a, with annular tooth and at least three planetary pinions 13 that sun gear 12a meshes simultaneously and the planet carrier of installing with respect to described planetary pinion 13 15 of gear sleeve 14.
In embodiment of the present utility model, sun gear 12a is integrally formed on the end of the live axle 12 that passes gear sleeve 14 coaxial settings.What can expect is that sun gear 12a also can be used as independent parts and for example is installed on this end of live axle 12 via keyway arrangements.Described at least three planetary pinions 13 also are used for supporting sun gear 12a, are used for supporting driving shaft 12 at Fig. 1 particularly except being used for transferring power.
In the first planetary gear transmission unit I, sun gear 12a is as the input end that receives from live axle 12 power, and planet carrier 15 is as output terminal.If gear sleeve 14 fixed words, when live axle 12 rotations, under the effect of sun gear 12a, planetary pinion 13 is done planetary motion around live axle 12 between the annular internal tooth of gear sleeve 14 and sun gear 12a, thereby drives planet carrier 15 around the central axis rotation of live axle 12.
The second planetary gear transmission unit II comprises ring gear 2, at least three planetary pinions 17, planet carrier 18 and sun gears 16.Ring gear 2 is permanently connected with respect to housing 1.Be fixedly attached to planet carrier 15, thereby planet carrier 15 can drive sun gear 16 rotations sun gear 16 and live axle 12 coaxial lines.Planetary pinion 17 is arranged between ring gear 2 and the sun gear 16, thereby can mesh simultaneously with the internal tooth of ring gear 2 and the external tooth of sun gear 16.
In the second planetary gear transmission unit II, sun gear 16 is as the input end that receives from planet carrier 15 power, and planet carrier 18 is as output terminal.Particularly, that end 18b that the axis longitudinally of planet carrier 18 is opposite with mounting column 18a can be used in and links to each other such as the drilling rod that revolves the drilling equipment that digs brill.When sun gear 16 under the drive of planetary pinion 15 during around the rotation of the central axis of live axle 12, planetary pinion 17 is done planetary motion around the central axis of live axle 12 between ring gear 2 and sun gear 18, rotate thereby drive planet carrier 18.
Below only put down in writing a kind of exemplary embodiment that adopts the concrete structure of planetary gear transmission unit I and II at double speed of the present utility model than rotary reducer.But, as long as should be understood that any other concrete planetary gear transmission unit can be realized specification as above and function as described below all can adopt in than rotary reducer at double speed of the present utility model.
Further referring to Fig. 2.End cap 3 is fixed on an end of housing 1, and for example, this end cap is fixed on the right-hand member of housing 1.In housing 1, respectively piston 6 and piston 7 can be installed slidably.End cap 3 has the end face 3a that extends in the housing 1.
As shown in Figure 2, piston 6 has the first acting surface 6a, the second acting surface 6b, the 3rd acting surface 6c and the 4th acting surface 6d.Piston 7 has the first acting surface 7a, the second acting surface 7b and the 3rd acting surface 7c.Piston 6 and 7 is formed with being stepped shape, thereby piston 7 can be set in the piston 6 slidably, and the 4th acting surface 6d of piston 6 is relative with the 3rd acting surface 7c of piston 7, and the second acting surface 6b of piston 6 is relative with the second acting surface 7b of piston 7.
Between piston 6 and 7, be provided with back-up ring 5.Particularly, this back-up ring 5 is between the 3rd acting surface 7c of the 4th acting surface 6d of piston 6 and piston 7.Be provided with oil hole 4 at housing 1, be used for injecting the hydraulic oil of different pressures.
In state as illustrated in fig. 1 and 2, opposite two end faces of back-up ring 5 are close to the 4th acting surface 6d of piston 6 and the 3rd acting surface 7c of piston 7.
This back-up ring 5 radially is provided with the through hole (not shown) with 4 pairs of normal incidences of this oil hole.When hydraulic oil is injected into via oil hole 4, can enter into (as shown in Figure 1) by piston 6,7 and the hydraulic pressure room formed of back-up ring 5 by described through hole.
As shown in Figure 1, position suitable in housing 1 is provided with mounting hole, is used for mounting spring 9 therein.These spring 9 one ends abut against housing 1, and the other end is for the 3rd acting surface 6c that is pushing piston 6, so that along the direction pushing tow piston 6 away from the first planetary gear transmission unit I.
In piston 7, also be provided with mounting hole, be used for mounting spring 10 therein.These spring 10 1 ends abut against piston 7, and the other end abuts against the end face 3a of end cap 3, so that along the direction pushing tow piston 7 towards the first planetary gear transmission unit I.
As illustrated in fig. 1 and 2, on an end 12b opposite with sun gear 12a of live axle 12, sleeve 8 can be slidably mounted on this live axle 12.The end 12b of live axle 12 is provided with keyway, in order to be connected and transferring power with unshowned oil hydraulic motor rotating shaft.Live axle 12 passes the center hole of piston 7.Periphery at live axle 12 is provided with circumferential recess 8b, in this circumferential recess 8b back-up ring 25 is installed.As shown in Figure 2, the center hole of piston 7 is provided with one the 4th acting surface 7d.The 4th acting surface 7d is used for contacting with back-up ring 25, so that when piston 7 moves along the direction away from the first planetary gear transmission unit I, can drive back-up ring 25 also thereby drive sleeve 8 correspondingly mobile.
On that end opposite with circumferential recess 8b of sleeve 8, be extended with peripheral flange radially outwardly.The end face towards the first planetary gear transmission unit I of this peripheral flange is labeled as 8a.
Between the peripheral flange with this end face 8a and circumferential recess 8b, back-up ring 26 can be slidably mounted on the outer surface of sleeve 8.This back-up ring 26 is fixedlyed connected with the gear sleeve 14 of the first planetary gear transmission unit I.For example, in an illustrated embodiment, be formed with circumferential recess at the internal surface of gear sleeve 14, this back-up ring 26 is inlaid in this circumferential recess.
As illustrated in fig. 1 and 2, between the peripheral flange of sleeve 8 and back-up ring 26, spring 11 is installed.Spring 11 applies tension force, makes sleeve 8 always be subjected to the elastic force effect towards sun gear 12a direction.
The first clutch locking device 19 is installed between the gear sleeve 14 of housing 1 and the first planetary gear transmission unit I, and the second clutch locking device 20 is installed between gear sleeve 14 and live axle 12.In embodiment of the present utility model, the polydisc plate clutch that described clutch locking device can be known in the art so hereinafter only schematically illustrates at this.
The first clutch locking device 19 mainly is made up of external friction disc and the inside friction disc of a plurality of mutual superposition, wherein the external friction disc is fixed on the housing 1 by the mode of profile of tooth engagement known in the art, and inside friction disc is fixed on the outer surface of gear sleeve 14 similarly.
In the time spent of doing that is not subjected to axial force, be not in contact with one another between the interior and external friction disc, this moment, gear sleeve 14 can rotate freely with respect to housing 1.This state is called the disengaged condition of the first clutch locking device 19.
In case the first clutch locking device 19 is subjected to the effect of enough axial forces, then in the external friction disc between the enough frictional force of generation make gear sleeve 14 maintain static with respect to housing 1.This state is called the closed state of the first clutch locking device 19.
The second clutch locking device 20 mainly is made up of external friction disc and the inside friction disc of a plurality of mutual superposition equally, wherein the external friction disc is fixed on the respective inner surfaces of gear sleeve 14 by the mode of profile of tooth engagement known in the art, and inside friction disc is fixed on the outer surface of live axle 12 similarly.
In the time spent of doing that is not subjected to the spring axial force, be not in contact with one another between the interior and external friction disc, this moment, gear sleeve 14 can rotate freely with respect to live axle 12.This state is called the disengaged condition of the second clutch locking device 20.
In case the second clutch locking device 20 is subjected to the effect of enough axial forces, then in the external friction disc between the enough frictional force of generation make gear sleeve 14 maintain static with respect to live axle 12.This state is called the closed state of the second clutch locking device 20.
Hydraulic clutch of the present utility model system comprises first clutch system, second clutch system and the hydraulic pressure cavity volume that is used for receiving hydraulic oil between described two hydraulic clutch systems substantially, wherein said first clutch system comprises above-mentioned piston 6, the first clutch locking device 19 and spring 9, described second clutch system comprises above-mentioned piston 7, sleeve 8 and spring 10 and 11, and described hydraulic pressure cavity volume is formed by means of back-up ring 5 by piston 6 and 7.
As illustrated in fig. 1 and 2, double speed is in first (at a high speed) serviceability than rotary reducer.In first serviceability, spring 9,10 and 11 elastic force are enough big, so that acting directly on the second clutch locking device 20, the end face 8a of sleeve 8 make this second clutch locking device 20 be in closed state, thereby gear sleeve 14 can't move with respect to live axle 12, and the first acting surface 6a of piston 6 makes this first clutch locking device 19 be in disengaged condition away from the first clutch locking device 19, thereby gear sleeve 14 can rotate freely with respect to housing 1.In this serviceability, do not have or hydraulic oil that pressure is very low acts between the 3rd acting surface 7c of the 4th acting surface 6d of piston 6 and piston 7 via oil hole 4 and the radial direction through hole by back-up ring 5.Therefore, the thrust that produces of hydraulic oil is not enough to promote piston 6 and 7 or make them be moved into the state that changes the above-mentioned first and second clutch locking devices.
Under this first serviceability, the gear sleeve 14 of the first planetary gear transmission unit I keeps motionless with respect to live axle 12, the planetary pinion 13 of this first planetary gear transmission unit I also keeps motionless with respect to live axle 12 like this, so planet carrier 15 keeps motionless with respect to live axle 12 equally.In the case, the rotating speed of live axle 12 is the output speed of planet carrier 15.That is to say, the input end of the second planetary gear transmission unit II directly receives the rotating speed input from live axle 12, and this moment, double speed of the present utility model only depended on the number of teeth setting of ring gear 2, planetary pinion 17 and the sun gear 18 of the second planetary gear transmission unit II than the reduction speed ratio of rotary reducer.
When expectation double speed of the present utility model adopts higher reduction speed ratio than rotary reducer, that is to say that when double speed forwarded second (low speed) serviceability to than rotary reducer, high-pressure and hydraulic oil injected from oil hole 4.
As shown in Figure 3, this double speed is in second serviceability than rotary reducer.The hydraulic fluid pressure that injects is enough high, and the active force that makes piston 6 and 7 overcome spring 9 and 10 and 11 respectively moves along opposite direction.For example, piston 6 moves along the direction towards the first planetary gear transmission unit I, and piston 7 moves along the direction away from the first planetary gear transmission unit I.Finally, under sufficiently high pressure effect, the first acting surface 6a of piston 6 applies enough big axial pressure at the first clutch locking device 19, makes this first clutch locking device 19 be in its closed state; Simultaneously, the end face 8a of sleeve 8 leaves the second clutch locking device 20, makes this second clutch locking device 20 be in its disengaged condition.
Therefore, when double speed is in second serviceability than rotary reducer, the gear sleeve 14 of the first planetary gear transmission unit I keeps motionless with respect to housing 1, and the sun gear 12a on the live axle 12 drives planetary pinion 13 and does planetary motion, thereby planet carrier 15 is correspondingly with the reduction speed ratio output speed of this first planetary gear transmission unit I.Like this, whole double speed depends on the number of teeth setting of the first planetary gear transmission unit I and the second planetary gear transmission unit II than the reduction speed ratio of rotary reducer in second serviceability, thereby under this second serviceability, the rotating speed of the drilling rod that links to each other than rotary reducer with double speed is further reduced and is obtained the output of high pulling torque.
When double speed need turn back to first serviceability than rotary reducer, the pressure that only needs to reduce the hydraulic oil that injects got final product.Between first serviceability and second serviceability, switch more reliably than rotary reducer in order to ensure double speed of the present utility model, preferably when handover operation, make earlier and shut down such as revolving the drilling equipment that digs brill.
Below only schematically illustrate an embodiment of the present utility model, should be understood that double speed of the present utility model is not limited to foregoing than rotary reducer.
For example, for the first clutch locking device 19, can adopt as shown in Figure 4 form as an alternative.This first clutch locking device 19 comprises respectively and is fixed on first friction piece 27 on the housing 1 and is fixed on second friction piece 28 on the gear sleeve 14.These two tapers that friction piece is set to cooperate each other.Be provided with axial opposed tank at these two friction pieces 27 and 28.Described tank is used for holding spring 30.Spring 30 applies tension force makes friction piece 27 and 28 be tending towards separately.Friction piece 27 and friction piece 28 rubbing surface between the two when being subjected to the first acting surface 6a pushing tow of piston 6 is in contact with one another.As mentioned above, when enough big hydraulic oil was provided to make that enough big masterpiece is used on the friction piece 28, the frictional force between the friction piece 27 and 28 was enough to make gear sleeve 14 motionless with respect to housing 1 maintenance.Similarly, when needs gear sleeve 14 can rotate freely with respect to housing 1, get final product thereby only need the reduction hydraulic fluid pressure to make the acting surface 6a that wins leave this first clutch locking device 19.Similarly, the second clutch locking device 20 also can adopt above-mentioned similar structure.
In addition, as an alternative, in order to improve the reliability that piston 7 drives sleeve 8, back-up ring 25 can directly be substituted by the back-up ring 25 with internal thread, simultaneously the corresponding end at sleeve 8 is provided with outside thread, and this back-up ring is screwed on the sleeve 8, with this when piston 7 moves along the direction away from the first planetary gear transmission unit I, the 4th acting surface 7d can be applied to bigger active force on the back-up ring 25, with drive spool 8 more reliably away from the second clutch locking device 20.
By adopting double speed of the present utility model to compare rotary reducer in the drilling equipment that digs brill such as revolving, drilling rod can freely switch at a high speed and between the low speed, thereby can drill efficiently in the mode of the slow-speed of revolution, high pulling torque piercing when underground drilling rod, and when extracting, drilling rod can rotate at a high speed, thereby as much as possible mud is thrown away, be convenient to the operation that pierces next time.With this, improved the working efficiency of whole drilling equipment.Should be understood that, except described in this manual such as revolve in the drilling equipment that digs brill adopt, double speed of the present utility model also can be like any demand class and have in the equipment of multiple working state and adopt than rotary reducer.
Although describe specific implementations of the present utility model here in detail, they only provide for the purpose of explaining, and should not think that they are construed as limiting scope of the present utility model.Under the prerequisite that does not break away from the utility model spirit and scope, various replacements, change and transformation can be come out by conception.
Claims (10)
1. the double speed for the equipment with multiple working state compares rotary reducer, it is characterized in that, described double speed comprises first planetary gear transmission unit, second planetary gear transmission unit and the hydraulic clutch system that acts on described first planetary gear transmission unit than rotary reducer
Described first planetary gear transmission unit comprise the sun gear that links to each other with the live axle of described equipment, and the planetary pinion between described sun gear and ring gear, installed of the coaxial mounted ring gear of described sun gear, at least three and install at described planetary pinion and can be around the planet carrier of the coaxial rotation of described sun gear
Described second planetary gear transmission unit comprise the sun gear that links to each other with the planet carrier of described first planetary gear transmission unit, with respect to the co-axially fixed ring gear of this sun gear, at least three the planetary pinion of installing between this sun gear and the ring gear and install at described planetary pinion and can be around the planet carrier of the coaxial rotation of described sun gear
Described hydraulic clutch system has the structure that can make optionally that the ring gear of described first planetary gear transmission unit is fixed with respect to described live axle or rotated freely with respect to described live axle.
2. double speed according to claim 1 compares rotary reducer, it is characterized in that, described double speed comprises housing than rotary reducer, second hydraulic lock assembly that described hydraulic clutch system is included in first hydraulic lock assembly that acts between the ring gear of described housing and described first planetary gear transmission unit and acts between the ring gear of described first planetary gear transmission unit and live axle.
3. double speed according to claim 2 compares rotary reducer, it is characterized in that, described housing is provided with for the oil hole that injects hydraulic oil, and described hydraulic clutch system has according to the pressure height of the hydraulic oil that injects and controls the structure that described first hydraulic lock assembly or described second hydraulic lock assembly correspondingly are in disengaged condition or closed state respectively.
4. double speed according to claim 3 compares rotary reducer, it is characterized in that, when described first hydraulic lock assembly was in disengaged condition and described second hydraulic lock assembly and is in closed state, the ring gear of described first planetary gear transmission unit maintained static with respect to described live axle.
5. double speed according to claim 3 compares rotary reducer, it is characterized in that, when described first hydraulic lock assembly was in closed state and described second hydraulic lock assembly and is in disengaged condition, the ring gear of described first planetary gear transmission unit maintained static with respect to described housing.
According to the arbitrary described double speed of claim 2 to 5 than rotary reducer, it is characterized in that described hydraulic clutch system comprises and acts on the first piston on described first hydraulic lock assembly and act on second piston on described second hydraulic lock assembly.
7. double speed according to claim 6 compares rotary reducer, it is characterized in that, described hydraulic clutch system also comprises first spring and second spring, described first spring is so that described first piston acts on the described first piston away from the mode of described first hydraulic lock assembly, and described second spring is so that the mode that described second piston contacts described second hydraulic lock assembly acts on described second piston.
8. double speed according to claim 7 is characterized in that than rotary reducer, and when enough the hydraulic oil of big pressure injected, described first piston and described second piston moved along opposite direction.
According to the arbitrary described double speed of claim 2 to 5 than rotary reducer, it is characterized in that described first and second hydraulic lock assemblies are the polydisc plate clutch.
According to the arbitrary described double speed of claim 2 to 5 than rotary reducer, it is characterized in that described equipment with multiple working state is to revolve to dig brill.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220699254 CN203146748U (en) | 2012-12-17 | 2012-12-17 | Double-speed ratio gyration reducer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220699254 CN203146748U (en) | 2012-12-17 | 2012-12-17 | Double-speed ratio gyration reducer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203146748U true CN203146748U (en) | 2013-08-21 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220699254 Expired - Lifetime CN203146748U (en) | 2012-12-17 | 2012-12-17 | Double-speed ratio gyration reducer |
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| CN (1) | CN203146748U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103883686A (en) * | 2014-03-11 | 2014-06-25 | 徐州科源液压股份有限公司 | Double-speed ratio walking speed reducer |
| WO2014094595A1 (en) * | 2012-12-17 | 2014-06-26 | 博世力士乐（北京）液压有限公司 | Double-speed ratio gyration reducer |
| CN103994187A (en) * | 2014-04-29 | 2014-08-20 | 北京航天发射技术研究所 | Electric drive two-gear double-stage hub reduction gear |
| CN106122385A (en) * | 2016-08-18 | 2016-11-16 | 张家港保税区永大机械有限公司 | A kind of twist bit |
-
2012
- 2012-12-17 CN CN 201220699254 patent/CN203146748U/en not_active Expired - Lifetime
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014094595A1 (en) * | 2012-12-17 | 2014-06-26 | 博世力士乐（北京）液压有限公司 | Double-speed ratio gyration reducer |
| CN103883686A (en) * | 2014-03-11 | 2014-06-25 | 徐州科源液压股份有限公司 | Double-speed ratio walking speed reducer |
| CN103883686B (en) * | 2014-03-11 | 2016-04-20 | 徐州科源液压股份有限公司 | Dual-speed-ratio driving speed reducer |
| CN103994187A (en) * | 2014-04-29 | 2014-08-20 | 北京航天发射技术研究所 | Electric drive two-gear double-stage hub reduction gear |
| CN103994187B (en) * | 2014-04-29 | 2017-10-31 | 北京航天发射技术研究所 | Electric drive two keeps off two-stage hub reduction gear |
| CN106122385A (en) * | 2016-08-18 | 2016-11-16 | 张家港保税区永大机械有限公司 | A kind of twist bit |
| CN106122385B (en) * | 2016-08-18 | 2018-07-24 | 张家港保税区永大机械有限公司 | A kind of twist bit |
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