CN1862032A - Dual cycloid hydraulic motor - Google Patents
Dual cycloid hydraulic motor Download PDFInfo
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- CN1862032A CN1862032A CN 200510025723 CN200510025723A CN1862032A CN 1862032 A CN1862032 A CN 1862032A CN 200510025723 CN200510025723 CN 200510025723 CN 200510025723 A CN200510025723 A CN 200510025723A CN 1862032 A CN1862032 A CN 1862032A
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Abstract
A double-cycloid hydraulic motor comprises a output shaft, front and back end caps, a distributing valve, a motor base, internal and external rotors and several pin teeth. The output shaft is connected with the internal rotor each other. The pin teeth disposed between the external and internal rotors are engaged with the external and internal rotors at the same time. Between the internal and external rotors and the pin teeth are formed several independent enclosed tooth cavities, which are in communication with the distributing valve separately and then in communication with the fuel inlet and outlet through the distributing valve.
Description
Technical field
The present invention relates to a kind of hydraulic transmission, specifically a kind of oil hydraulic motor.
Technical background
Figure 1 shows that existing planetary rotor gerotor motor, it mainly is made up of output shaft, pintle, housing, spline coupling, cycloid rotor, stator, front cover and rear end cover.Pintle is output shaft, and the cycloid rotor profile of tooth is a curtate epicycloid, and the stator profile of tooth is a circular arc.Has Z
1The cycloid rotor of individual tooth is an outer tooth pinion, and has Z
2The stator of individual tooth is that ring gear is meshed, and forms Z
2Individual enclosed volume.These enclosed volumes by pintle with connect into and out of hydraulic fluid port, pintle plays a part switch valve, is controlling into and out of being switched on or switched off of hydraulic fluid port and each enclosed volume, it makes above-mentioned Z
2In the individual enclosed volume nearly half is communicated with pressure oil, and remaining communicates with the low pressure oil return.
When pressure oil enters Z by pintle
2During/2 enclosed volumes, rotor (small gear) is under the pressure oil effect, by the direction rotation that hyperbaric chamber between cog volume is increased.Because stator is fixed, so rotor is around self axes O
1When doing the low speed rotation, rotor center O
1Also around stator center O
2Do the high-speed reverse revolution.During revolution, its high pressure, oil-discharging cavity constantly change, but all the time with line of centers O
1O
2For the boundary is divided into two chambeies.The between cog volume of one side increases, and is hyperbaric chamber; The between cog volume of opposite side dwindles, and is oil-discharging cavity.Public affairs are goed around, tooth of rotation, and each between cog volume is finished once, the oil return circulation, and revolution is i=(Z with the speed ratio of rotation
1): 1.Spline coupling passes to output shaft with the spinning motion of rotor, can drag operation mechanism's rotation.Because output shaft itself is exactly a pintle, the continuous flow of pintle, hyperbaric chamber are just with line of centers O
1O
2Rotation and rotation synchronously and then makes rotor and output shaft rotate continuously.
The discharge capacity of planetary rotor gerotor motor is Z
2Epicyclodial wheel tooth root circle doubly and the ring-shaped cylinder volume between the top circle.Advantages such as this motor has simple in structure, and volume is little, and is in light weight, and speed range is wide, and moment is big to the ratio of weight, and price is low, uses reliably, and low-speed stability is good.Defectives such as but also exist discharge capacity little, output torque is little, and mechanical efficiency is low, and the life-span is short.
Summary of the invention
Technical problem to be solved by this invention is to improve the combination property of oil hydraulic motor, increase the discharge capacity of oil hydraulic motor, increase output torque, reduce the volume of oil hydraulic motor, reduce the fretting wear of the inside and outside rotor flank of tooth, provide the oil hydraulic motor of a kind of mechanical efficiency height, long service life, to overcome the above-mentioned defective that prior art exists.
The technological scheme of technical solution problem of the present invention is as follows:
A kind of dual cycloid hydraulic motor comprises output shaft, front and rear cover, flow-distributing valve, support and internal rotor, and described support is provided with filler opening and oil outlet, and flow-distributing valve and internal rotor interconnect by link, it is characterized in that, also comprises external rotor and a plurality of pin tooth; Described internal rotor is eccentric to be provided with, and described output shaft and internal rotor interconnect; Described pin tooth is arranged between external rotor and the internal rotor, described external rotor is meshed with the pin tooth, the pin tooth is meshed with internal rotor again simultaneously, form a plurality of tooth cavities that independently seal between described internal rotor, external rotor and the pin tooth, described tooth cavity communicates with flow-distributing valve respectively, is communicated with oil inlet and outlet on the support through flow-distributing valve; Described pin tooth is the cam pin tooth, and described pin tooth is located with the hole, eccentric rotation, and the positioning hole central distribution of described pin tooth is on the cylinder of central shaft at the rotating center with external rotor.
A kind of dual cycloid hydraulic motor, comprise output shaft, front and rear cover, flow-distributing valve, support and internal rotor, described support is provided with filler opening and oil outlet, described internal rotor is epicycloid rotor or disk, flow-distributing valve and internal rotor interconnect by link, it is characterized in that, also comprise external rotor and a plurality of pin tooth; Described external rotor is hypocycloid rotor or disk, and described internal rotor is eccentric to be provided with, and described output shaft and external rotor are mutually permanently connected; Described pin tooth is arranged between external rotor and the internal rotor, described external rotor is meshed with the pin tooth, the pin tooth is meshed with internal rotor again simultaneously, form a plurality of tooth cavities that independently seal between described internal rotor, external rotor and the pin tooth, described tooth cavity communicates with flow-distributing valve respectively, is communicated with oil inlet and outlet on the support through flow-distributing valve; Described pin tooth is the cam pin tooth, and described pin tooth is located with the hole, eccentric rotation, and the positioning hole central distribution of described pin tooth is on the cylinder of central shaft at the rotating center with external rotor.
Described internal rotor is the curtate epicycloid gear, and described external rotor is hypocycloid rotor or disk, the throw of eccentric of described pin tooth be internal rotor throw of eccentric 1/2.The throw of eccentric of internal rotor is the throw of eccentric between internal rotor and the external rotor.
Described internal rotor is a disk, and described external rotor is the hypocycloid rotor, and the throw of eccentric of described pin tooth equates with the throw of eccentric of internal rotor.
Described external rotor is the curtate hypocycloid gear ring.
Described flow-distributing valve is a pintle, shown in pintle and output shaft be a whole body structure, output shaft is positioned at base inner and is divided into pintle.
Working principle of the present invention a: throw of eccentric is arranged between the inside and outside rotor center, have Z
1The internal rotor of individual tooth is with Z
2Individual pin tooth is meshed, these pin teeth simultaneously again with have Z
3The external rotor engagement of individual tooth forms Z
2Individual enclosed volume.These enclosed volumes by flow-distributing valve with connect into and out of hydraulic fluid port, flow-distributing valve plays a part switch valve, is controlling into and out of being switched on or switched off of hydraulic fluid port and each enclosed volume, it makes above-mentioned Z
2In the individual enclosed volume nearly half is communicated with pressure oil, and remaining communicates with the low pressure oil return.When pressure oil enters Z by pintle
2During/2 enclosed volumes, internal rotor is under the pressure oil effect, by the direction rotation that hyperbaric chamber between cog volume is increased.Internal rotor is around self axes O
1When doing the low speed rotation, rotor center O
1Also around the external rotor center O
2Do the high-speed reverse revolution.During revolution, its high pressure, the continuous conversion of oil-discharging cavity, but all the time with line of centers O
1O
2For the boundary is divided into two chambeies.The between cog volume of one side increases, and is hyperbaric chamber; The between cog volume of opposite side dwindles, and is oil-discharging cavity.Public affairs are goed around, tooth of rotation, and each between cog volume is finished once, the oil return circulation, and revolution is i=(Z with the speed ratio of rotation
1): 1.By shaft coupling the spinning motion of rotor is passed to output shaft, can drag operation mechanism's rotation.If output shaft itself is exactly a pintle, the continuous flow of pintle, hyperbaric chamber are just with line of centers O in addition
1O
2Rotation and rotation synchronously and then makes rotor and output shaft rotate continuously.
By above disclosed technological scheme as can be known, the present invention's beneficial effect compared with prior art is as follows:
1) oil drain quantity is big, and output torque is big: the discharge capacity of double cycloid motor adds the Z of the ring-shaped cylinder volume sum between hypocycloid wheel root circle and the top circle for the ring-shaped cylinder volume between epicyclodial wheel tooth root circle and the top circle
2Doubly.When internal rotor was epicyclodial wheel, in the process of engagement, inside and outside two cycloid wheel meshed with the pin tooth simultaneously, and therefore, the discharge capacity of this motor is existing more than 2 times of planetary rotor gerotor motor discharge capacity, so can obtain bigger output torque.
2) flowed fluctuation is little: each tooth cavity be high-voltage oil cavity be again oil-discharging cavity, it is high-voltage oil cavity that a plurality of tooth cavities are wherein arranged, other has a plurality of tooth cavities is oil-discharging cavity, advances, oil extraction carries out simultaneously.Rotation along with line of centers, each tooth cavity is progressive continuously by being pressed into the process that oil (or oil extraction) changes oil extraction (or oil suction) over to, and whenever there is a tooth cavity to change oil extraction (or oil suction) over to by being pressed into oil (or oil extraction), just have another tooth cavity and changed over to by oil extraction (or oil suction) and be pressed into oil (or oil extraction), whole process all hockets continuously.
3) little, the long service life of mechanical efficiency loss: the pin tooth also rotates, and makes it and inside and outside rotor contact surface be bordering on pure rolling, and it is little to rub, wear and tear; In addition each tooth cavity be pumping cavity be again oil-discharging cavity, after oil is pressed into, be discharged from again on the spot, no handling process has also reduced the mechanical efficiency loss.
4) in addition because flowed fluctuation is little, eliminated the influence of flowed fluctuation to the oil liquid pressure stationarity, helped reducing oil liquid pressure and impact, reduced noise, output torque is steady; Because discharge capacity is big, also can reduce the volume of motor.
5) easy to maintenance, easy to process: as when wearing and tearing take place the rotor flank of tooth, only need to change the pin tooth, and more exchanging rotor both can; Curtate hypocycloid external rotor gear ring is than the easier processing of circle-arc tooth external rotor gear ring of cycloid formula rotor pump.
Motor to sum up of the present invention has advantages such as volume is little, in light weight, and speed range is wide, and moment is big to the ratio of weight, and price is low, uses reliably, and low-speed stability is good.Belong to middling speed by its performance, in, the high pulling torque scope.
Description of drawings
Fig. 1 is existing hydraulic motor structure schematic representation;
Fig. 2 is an A-A sectional schematic diagram among Fig. 1;
Fig. 3 is dual cycloid hydraulic motor cross-sectional configuration schematic representation of the present invention;
Fig. 4 is a B-B sectional schematic diagram among Fig. 3;
Fig. 5 is another example structure schematic representation of dual cycloid hydraulic motor of the present invention;
Fig. 6 is a C-C sectional schematic diagram among Fig. 5.
Embodiment
Further specify the present invention below in conjunction with accompanying drawing.
Referring to Fig. 3, Fig. 4, Fig. 5 and Fig. 6, a kind of dual cycloid hydraulic motor of the present invention, comprise output shaft 1, front cover 2, rear end cover 9, flow-distributing valve 10, support 3 and internal rotor 8, described support 3 is provided with filler opening 301 and oil outlet 302, flow-distributing valve 10 interconnects by link 4 with internal rotor 8, also comprises external rotor 6 and a plurality of pin tooth 7; Described internal rotor 8 eccentric settings; Described pin tooth 7 is arranged between external rotor 6 and the internal rotor 8, described external rotor 6 is meshed with pin tooth 7, pin tooth 7 is meshed with internal rotor 8 again simultaneously, form a plurality of tooth cavities 11 that independently seal between described internal rotor 8, external rotor 6 and the pin tooth 7, described tooth cavity 11 communicates with flow-distributing valve 10 respectively, is communicated with oil inlet and outlet 301,302 on the support through flow-distributing valve 10; Described pin tooth 7 is the cam pin tooth, and described pin tooth 7 is located with the hole, eccentric rotation, and the positioning hole central distribution of described pin tooth 7 is on the cylinder of central shaft at the rotating center with external rotor 6.Described output shaft 1 promptly can interconnect by link with internal rotor 8; Can also be mutually permanently connected with external rotor 6,
Embodiment 1:
As shown in Figure 3, Figure 4, a kind of dual cycloid hydraulic motor.This motor mainly is made up of output shaft 1, pintle 10, front cover 2, support 3, spline coupling 4, housing 5, external rotor 6, pin tooth 7, internal rotor 8, rear end cover 9 or the like component.Internal rotor 8 is curtate epicycloid wheel or disk; Pin tooth 7 is the cam pin tooth, with the location, hole, and eccentric rotary, the positioning hole central distribution of pin tooth 7 is on the cylinder of central shaft at the rotating center with external rotor 6; External rotor 6 is the curtate hypocycloid gear ring, and internal rotor 8 is with respect to external rotor 6 eccentric settings.When internal rotor was disk, the throw of eccentric of described pin tooth equated with the throw of eccentric of internal rotor; When internal rotor is the curtate epicycloid gear, the throw of eccentric of described pin tooth be internal rotor 8 throw of eccentric 1/2.Internal rotor 8, pin tooth 7, external rotor 6 formed a plurality of tooth cavities 11 that independently seal, the tooth cavity 11 of these sealings be hyperbaric chamber be again oil-discharging cavity.Described pintle 10 is an integral shaft structure with output shaft 1, and the part that output shaft 1 is positioned at support 3 is a pintle 10, and described output shaft 1 interconnects by the spline coupling 4 that is connected the pintle place with internal rotor 8.During work, when pressure oil enters Z by pintle 10
2During/2 enclosed volumes, internal rotor 8 is under the pressure oil effect, by the direction rotation that hyperbaric chamber between cog volume is increased.Internal rotor 8 is around self axes O
1When doing the low speed rotation, internal rotor 8 center O
1Also around external rotor 6 center O
2Do the high-speed reverse revolution.During revolution, its high pressure, the continuous conversion of oil-discharging cavity, but all the time with line of centers O
1O
2For the boundary is divided into two chambeies.The between cog volume of one side increases, and is hyperbaric chamber; The between cog volume of opposite side dwindles, and is oil-discharging cavity.Public affairs are goed around, tooth of rotation, and each between cog volume is finished once, the oil return circulation, and revolution is i=(Z with the speed ratio of rotation
1): 1.Spline coupling 4 passes to output shaft 1 with the spinning motion of internal rotor among the figure, can drag operation mechanism's rotation.Because output shaft itself is exactly a pintle, the continuous flow of pintle, hyperbaric chamber are just with line of centers O
1O
2Rotation and rotation synchronously and then makes internal rotor 8 and output shaft 1 rotate continuously.
Embodiment 2:
As Fig. 5, shown in Figure 6, a kind of dual cycloid hydraulic motor, this oil hydraulic motor mainly are made up of component such as output shaft 1, front cover 2, flow-distributing valve 10, preceding support 3, spline coupling 4, casing 5, hypocycloid external rotor 6, pin tooth 7, epicycloid internal rotor 8, back support 12, rear end covers 9.External rotor 6 is the curtate hypocycloid wheel, and internal rotor 8 is curtate epicycloid wheel or disk, and pin tooth 7 is the cam pin tooth.Output shaft 1 connects firmly with hypocycloid external rotor 6; The pin tooth is located with the hole, eccentric rotary, and the positioning hole central distribution of pin tooth 7 is on the circumference in the center of circle at the rotating center with external rotor; Internal rotor 8 is with respect to external rotor 6 eccentric settings.When internal rotor was disk, the throw of eccentric of described pin tooth equated with the throw of eccentric of internal rotor; When internal rotor is the curtate epicycloid gear, the throw of eccentric of described pin tooth be internal rotor throw of eccentric 1/2.Flow-distributing valve 10 is pintle or thrust plate, and described output shaft 1 and pintle 10 are separately positioned on the both sides of internal rotor 8, and described flow-distributing valve 10 is connected by spline coupling 4 with internal rotor 8.Internal rotor 8, pin tooth 7, external rotor 6 formed a plurality of tooth cavities 11 that independently seal, the tooth cavity 11 of these sealings be pumping cavity be again oil-discharging cavity.
During work, when pressure oil enters Z by flow-distributing valve 10
2During/2 enclosed volumes, external rotor 6 rotates by the direction that hyperbaric chamber between cog volume is increased under the pressure oil effect.Simultaneously, internal rotor 8 is around self axes O
1When doing the low speed rotation, internal rotor 8 center O
1Also around external rotor 6 center O
2Do the high-speed reverse revolution.During revolution, its high pressure, the continuous conversion of oil-discharging cavity, but all the time with line of centers O
1O
2For the boundary is divided into two chambeies.The between cog volume of one side increases, and is hyperbaric chamber; The between cog volume of opposite side dwindles, and is oil-discharging cavity.Public affairs are goed around, tooth of rotation, and each between cog volume is finished once, the oil return circulation, and revolution is i=Z with the speed ratio that external rotor rotates
3: 1.External rotor and output shaft connect firmly exports away rotation, can drag operation mechanism's rotation.Spline coupling 4 passes to flow-distributing valve 10 with the spinning motion of internal rotor among the figure, drives the continuous flow of flow-distributing valve, and hyperbaric chamber is just with line of centers O
1O
2Rotation and rotation synchronously and then makes external rotor 6 and output shaft 1 rotate continuously.
Claims (10)
1. dual cycloid hydraulic motor, comprise output shaft, front and rear cover, flow-distributing valve, support and internal rotor, described support is provided with filler opening and oil outlet, and flow-distributing valve and internal rotor interconnect by link, it is characterized in that, also comprise external rotor and a plurality of pin tooth;
Described internal rotor is eccentric to be provided with, and described output shaft and internal rotor interconnect;
Described pin tooth is arranged between external rotor and the internal rotor, described external rotor is meshed with the pin tooth, the pin tooth is meshed with internal rotor again simultaneously, form a plurality of tooth cavities that independently seal between described internal rotor, external rotor and the pin tooth, described tooth cavity communicates with flow-distributing valve respectively, is communicated with oil inlet and outlet on the support through flow-distributing valve;
Described pin tooth is the cam pin tooth, and described pin tooth is located with the hole, eccentric rotation, and the positioning hole central distribution of described pin tooth is on the cylinder of central shaft at the rotating center with external rotor.
2. dual cycloid hydraulic motor, comprise output shaft, front and rear cover, flow-distributing valve, support and internal rotor, described support is provided with filler opening and oil outlet, described internal rotor is epicycloid rotor or disk, flow-distributing valve and internal rotor interconnect by link, it is characterized in that, also comprise external rotor and a plurality of pin tooth;
Described external rotor is hypocycloid rotor or disk, and described internal rotor is eccentric to be provided with, and described output shaft and external rotor are mutually permanently connected;
Described pin tooth is arranged between external rotor and the internal rotor, described external rotor is meshed with the pin tooth, the pin tooth is meshed with internal rotor again simultaneously, form a plurality of tooth cavities that independently seal between described internal rotor, external rotor and the pin tooth, described tooth cavity communicates with flow-distributing valve respectively, is communicated with oil inlet and outlet on the support through flow-distributing valve;
Described pin tooth is the cam pin tooth, and described pin tooth is located with the hole, eccentric rotation, and the positioning hole central distribution of described pin tooth is on the cylinder of central shaft at the rotating center with external rotor.
3. dual cycloid hydraulic motor according to claim 1 is characterized in that, described internal rotor is the curtate epicycloid gear, and described external rotor is hypocycloid rotor or disk, the throw of eccentric of described pin tooth be internal rotor throw of eccentric 1/2.
4. dual cycloid hydraulic motor according to claim 1 is characterized in that, described internal rotor is a disk, and described external rotor is the hypocycloid rotor, and the throw of eccentric of described pin tooth equates with the throw of eccentric of internal rotor.
5. dual cycloid hydraulic motor according to claim 2 is characterized in that, described internal rotor is the curtate epicycloid gear, and described external rotor is hypocycloid rotor or disk, the throw of eccentric of described pin tooth be internal rotor throw of eccentric 1/2.
6. dual cycloid hydraulic motor according to claim 2 is characterized in that, described internal rotor is a disk, and described external rotor is the hypocycloid rotor, and the throw of eccentric of described pin tooth equates with the throw of eccentric of internal rotor.
7. according to claim 1,3 or 4 described dual cycloid hydraulic motors, it is characterized in that described flow-distributing valve is a pintle, shown in pintle and output shaft be a whole body structure, output shaft is positioned at base inner and is divided into pintle.
8. according to claim 2,5 or 6 described dual cycloid hydraulic motors, it is characterized in that described flow-distributing valve is a pintle, described output shaft and pintle are separately positioned on the both sides of internal rotor, and described pintle is connected by spline coupling with internal rotor.
9. dual cycloid hydraulic motor according to claim 7 is characterized in that, also comprises housing, and described internal rotor, external rotor and pin tooth are arranged within the housing, being fixed on the support of the eccentric rotation of described pin tooth.
10. dual cycloid hydraulic motor according to claim 8 is characterized in that, also comprises housing, and described internal rotor, external rotor and pin tooth are arranged within the housing, being fixed on the support of the eccentric rotation of described pin tooth.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200510025723 CN1862032A (en) | 2005-05-10 | 2005-05-10 | Dual cycloid hydraulic motor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200510025723 CN1862032A (en) | 2005-05-10 | 2005-05-10 | Dual cycloid hydraulic motor |
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| Publication Number | Publication Date |
|---|---|
| CN1862032A true CN1862032A (en) | 2006-11-15 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200510025723 Pending CN1862032A (en) | 2005-05-10 | 2005-05-10 | Dual cycloid hydraulic motor |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100520059C (en) * | 2007-08-23 | 2009-07-29 | 镇江大力液压马达有限责任公司 | High pressure and large torque cycloid hydraulic motor and special hob cutter |
| CN112879602A (en) * | 2021-03-23 | 2021-06-01 | 同济大学 | Axial flow distribution pulse switch valve |
-
2005
- 2005-05-10 CN CN 200510025723 patent/CN1862032A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100520059C (en) * | 2007-08-23 | 2009-07-29 | 镇江大力液压马达有限责任公司 | High pressure and large torque cycloid hydraulic motor and special hob cutter |
| CN112879602A (en) * | 2021-03-23 | 2021-06-01 | 同济大学 | Axial flow distribution pulse switch valve |
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