CN103111377A - Differential mechanism of spiral discharge centrifugal machine - Google Patents

Abstract

The invention belongs to the technical field of centrifugal machines, and particularly relates to a differential mechanism of a spiral discharge centrifugal machine. The differential mechanism of the spiral discharge centrifugal machine solves the technical problems that a differential mechanism in the prior art is not reasonable enough, difference adjustment is inconvenient and the like. The differential mechanism of the spiral discharge centrifugal machine comprises a shell body connected with a centrifugal machine revolving drum. An involute planetary gear differential mechanism connected with a centrifugal machine spiral body is arranged inside the shell body. The differential mechanism of the spiral discharge centrifugal machine is characterized in that a slip regulating mechanism is further arranged inside the shell body, an output end of the slip regulating mechanism is connected with the involute planetary gear differential mechanism, and when the slip regulating mechanism drives the involute planetary gear differential mechanism to work, slip between the centrifugal machine spiral body and the centrifugal machine revolving drum can be directly adjusted according to rotating speed of an input end of the slip regulating mechanism. Compared with the prior art, the differential mechanism of the spiral discharge centrifugal machine has the advantages that differential speed adjustment is convenient, and a control system is simple and easy to operate.

Description

The differential mechanism of helical-conveyer centrifugal

Technical field

The invention belongs to the Centrifuge Techniques field, relate to differential mechanism, relate in particular to a kind of differential mechanism of helical-conveyer centrifugal.

Background technology

In helical-conveyer centrifugal (hereinafter to be referred as centrifuge), the isolated sediment of centrifugal sedimentation is along vertically moving on the rotary drum inner surface, be by the relative rotary drum leading of spiral or hysteresis rotatablely move realize.In order to guarantee that rotary drum and spiral turn round in the same way with different angular speed, and obtain best slip value, therefore, centrifuge all needs a transmission device between from the motor to the working machine, and this transmission device is exactly differential mechanism.

Differential mechanism is parts the most complicated and very important in centrifuge, and its Performance and quality is often determining ability to work and the reliability of whole machine.The differential mechanism type has mechanical type, fluid pressure type etc., and mechanical type mainly contains: cycloidal pin teeth planetary differential, harmonic gear differential mechanism and involute planet gear differential mechanism.The involute planet gear differential mechanism is most widely used driving type in modern centrifuge.It has 2K-H, 3K and three kinds of structural shapes of K-H-V.Most widely used in centrifuge is twin-stage 2K-H type (claiming again twin-stage NGW type).Although it is high that this differential mechanism has bearing capacity, volume is little, and is lightweight, compact conformation, and efficient also exists poor rotational speed regulation inconvenient, the shortcoming that requirements for automatic control is high up to the series of advantages such as 0.99.

Fig. 1 is existing differential mechanism, wherein, the housing of differential mechanism 2 and the 5th ring gear b1, the 6th ring gear b2 is connected mutually, and be connected with rotary drum 3, second level tie-rod H2 is connected with spiral 4, and first order sun gear a1 is connected with auxiliary motor 1, regulate the auxiliary motor rotating speed, can regulate the slip between rotary drum 3 and spiral 4.

One, gearratio is calculated as follows: $i_{a1\mathrm{<figure-callout\; id="1b"\; label="H"\; filenames="HSA00000853911500021.png"\; state="\{\{state\}\}">H</figure-callout>}1}^b=(1+\frac{\mathrm{Zb}1}{\mathrm{Za}1})(1+\frac{\mathrm{<figure-callout\; id="2"\; label="Zb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Zb</figure-callout>}2}{\mathrm{Za}2})---\left(1\right)$

Following formula represents: when the 5th ring gear b1 (or the 6th ring gear b2) driving link a1 gearratio to output H2 fixedly the time;

Wherein: Za1, Za2 are respectively the numbers of teeth of first order sun gear a1 and second level sun gear a2, and Zb1, Zb2 are respectively the numbers of teeth of the 5th ring gear b1, the 6th ring gear b2;

Two, differing from rotating speed is calculated as follows:

$\mathrm{\&Delta;n}=\frac{\mathrm{nb}-\mathrm{na}1}{i_{a1H2}^b}---\left(2\right)$

In formula: the poor rotating speed (r/min) of Δ n;

Nb rotary drum 3 rotating speeds (r/min);

Na1 first order sun gear a1 rotating speed (r/min);

Differential mechanism the 5th ring gear b1 (or the 6th ring gear b2) is the gearratio of first order sun gear a1 to second level tie-rod H2 fixedly the time;

By formula (2) formula as can be known: the size of poor rotating speed is directly proportional to the difference of rotary drum rotating speed and one-level sun gear rotating speed, and the gearratio of differential mechanism is inversely proportional to.That is to say: regulate poor rotating speed and need to regulate simultaneously rotary drum rotating speed and one-level sun gear rotating speed;

The size of centrifuge operation time difference rotating speed and stable, directly the moisture content of solid phase and the solid content of discharge liquid phase are discharged in impact, affect machine traveling comfort and output, it is an important indicator weighing centrifuge performance quality, fairly obvious, there is the problem of poor rotational speed regulation inconvenience and control system complexity in above-mentioned this driving type.

In addition, the limitation of using at centrifuge in order to further illustrate twin-stage 2K-H differential mechanism, the below describes the calculating of gearratio and poor rotating speed:

One, gearratio is referring to accompanying drawing 1: calculate with the transformation mechanism method:

To a1, b1, g1, H1 has: $\frac{\mathrm{na}1-\mathrm{nH}1}{\mathrm{nb}1-\mathrm{nH}1}=-\frac{\mathrm{Zb}1}{\mathrm{Za}1},$ $\mathrm{nH}1=\frac{\mathrm{nb}1\mathrm{Zb}1+\mathrm{na}1\mathrm{Za}1}{\mathrm{Za}1+\mathrm{Zb}1};$

To a2, b2, g2, H2 has: $\frac{\mathrm{na}2-\mathrm{<figure-callout\; id="2"\; label="nH"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">nH</figure-callout>}2}{\mathrm{nb}2-\mathrm{<figure-callout\; id="2"\; label="nH"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">nH</figure-callout>}2}=-\frac{\mathrm{<figure-callout\; id="2"\; label="Zb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Zb</figure-callout>}2}{\mathrm{Za}2},$ $\mathrm{<figure-callout\; id="2"\; label="nH"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">nH</figure-callout>}2=\frac{\mathrm{<figure-callout\; id="2"\; label="nb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">nb</figure-callout>}2\mathrm{<figure-callout\; id="2"\; label="Zb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Zb</figure-callout>}2+\mathrm{na}2\mathrm{Za}2}{\mathrm{Za}2+\mathrm{<figure-callout\; id="2"\; label="Zb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Zb</figure-callout>}2};$

Due to nb1=nb2, make nb1=nb2=nb, nH1=na2,

Have: $\mathrm{<figure-callout\; id="2"\; label="nH"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">nH</figure-callout>}2=\frac{\mathrm{Zb}1\mathrm{<figure-callout\; id="2"\; label="Zb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Zb</figure-callout>}2+\mathrm{Za}1\mathrm{<figure-callout\; id="2"\; label="Zb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Zb</figure-callout>}2+\mathrm{Zb}1\mathrm{Za}2}{(\mathrm{Za}1+\mathrm{Zb}1)(\mathrm{Za}2+\mathrm{Zb}2)}\mathrm{nb}+\frac{\mathrm{Za}1\mathrm{Za}2}{(\mathrm{Za}1+\mathrm{Zb}1)(\mathrm{Za}2+\mathrm{Zb}2)}\mathrm{na}1;$

Make nb=0, can get gearratio: $i_{a1H2}^b=\frac{\mathrm{na}1}{\mathrm{<figure-callout\; id="2"\; label="nH"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">nH</figure-callout>}2}=\frac{(\mathrm{Za}1+\mathrm{Zb}1)(\mathrm{Za}2+\mathrm{Zb}2)}{\mathrm{Za}1\mathrm{Za}2},$

Can obtain formula (1) after arrangement;

In formula: g1 is the fifth line star-wheel, g2 is the 6th planetary gear, H1 is first order tie-rod, nH1 is the rotating speed of first order tie-rod H1, and nH2 is the rotating speed of second level tie-rod H2, and na1 is first order sun gear a1 rotating speed, na2 is second level sun gear a2 rotating speed, nb1 is the rotating speed of the 5th ring gear b1, and nb2 is the rotating speed of the 6th ring gear b2, and g1 and g2 are planetary gear.

Two, differ from rotating speed:

Define according to poor rotating speed: Δ n=nb-nH2,

Therefore: $\mathrm{\&Delta;n}=\mathrm{nb}-(\frac{\mathrm{Zb}1\mathrm{<figure-callout\; id="2"\; label="Zb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Zb</figure-callout>}2+\mathrm{Za}1\mathrm{<figure-callout\; id="2"\; label="Zb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Zb</figure-callout>}2+\mathrm{Zb}1\mathrm{Za}2}{(\mathrm{Za}1+\mathrm{Zb}1)(\mathrm{Za}2+\mathrm{Zb}2)}\mathrm{nb}+\frac{1}{i_{a1H2}^{\mathrm{<figure-callout\; id="2"\; label="b"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">b</figure-callout>}2}}\mathrm{na}1);$ Can obtain formula (2) after arrangement, in sum, existing differential mechanism obviously exists the problems such as the inconvenient and requirements for automatic control of poor rotational speed regulation is very high, difficult being applied.

Summary of the invention

The objective of the invention is for the problems referred to above, provide a kind of poor rotational speed regulation convenient, control system simply and the differential mechanism of the helical-conveyer centrifugal of easily controlling.

for achieving the above object, the present invention has adopted following technical proposal: the differential mechanism of this helical-conveyer centrifugal comprises the housing that is connected with bowl, be provided with the involute planet gear box of tricks that is connected with the centrifuge conveyor screw in housing, it is characterized in that, also be provided with the slip governor motion in described housing, the output of described slip governor motion is connected with described involute planet gear box of tricks and the directly slip between centrifuge conveyor screw according to the rotational speed regulation of slip governor motion input and bowl when the slip governor motion drives the work of involute planet gear box of tricks.

Obviously, differential mechanism of the present invention not only can be controlled the numerical value of poor rotating speed more accurately, and control system simply and easily controls, and has reduced the higher requirement of automatic control; Secondly, the vibrations of current peak and machine in the time of can also reducing to greatest extent the centrifuge startup.Be in particular in: when centrifuge starts, at first start the centrifuge conveyor screw, thereby can get rid of so the large situation of the contingent Vibration on Start-up that causes due to residuals skewness when last time, the residuals that may stay in service avoided bowl to start; Simultaneously, when closing centrifuge, at first the bowl rotating speed is reduced, then continued residuals is discharged outside machine by the centrifuge conveyor screw.

in the differential mechanism of above-mentioned helical-conveyer centrifugal, described slip governor motion comprises input central gear and the output shaft that is arranged in housing, input central gear outer race have the fixedly central gear of setting coaxial with it and fixedly the central gear outer end be fixedly installed by external location structure outside housing, described output shaft is connected with the involute planet gear box of tricks, described input central gear is arranged with at least two planetary gear slip adjusting parts that difference is coupled outward, described planetary gear slip adjusting part is connected with fixing central gear respectively, be fixed with the first ring gear that is connected with each planetary gear slip adjusting part respectively on described housing, be fixed with the second ring gear that is connected with each planetary gear slip adjusting part respectively on described output shaft.The input central gear is connected with buncher, and bowl is connected with drive motors, is used for input speed and regulates poor rotating speed, can control accurately the numerical value of poor rotating speed by planetary gear slip adjusting part.

In the differential mechanism of above-mentioned helical-conveyer centrifugal, described planetary gear slip adjusting part comprise respectively with the first row star-wheel of fixedly central gear and the first ring gear engagement, respectively with the second planetary gear of input central gear and the engagement of the second ring gear, described the first row star-wheel and the second planetary gear are set up in parallel and a planet axis is passed the first row star-wheel and the second planetary gear, be provided with clutch shaft bearing between planet axis and the first row star-wheel, be provided with the second bearing between planet axis and the second planetary gear.The non-deformability of meshed transmission gear structure is strong, stable drive, the stability when having improved complete machine work.Secondly, the clutch shaft bearing here and the second bearing can be needle bearings, can be also sliding bearings.

In the differential mechanism of above-mentioned helical-conveyer centrifugal, described planet axis is separately fixed on planet carrier, described planet carrier comprises the first toroidal frame that is fixed on planet axis one end and the second toroidal frame that is fixed on the other end, middle part every planet axis is respectively equipped with bulge loop, form the clutch shaft bearing installing zone between described the first toroidal frame and bulge loop, described clutch shaft bearing is located in the clutch shaft bearing installing zone, form the second bearing installing zone between described the second toroidal frame and bulge loop, described the second bearing is located in the second bearing installing zone.Can prevent the first row star-wheel and the second relative planet axis axial float of planetary gear, in addition, the harmony when planet carrier has improved transmission.

In the differential mechanism of above-mentioned helical-conveyer centrifugal, be provided with the flying height for planetary gear slip adjusting part axial float between described output shaft and planetary gear slip adjusting part, be provided be used to the unsteady adjustment structure of regulating described flying height on output shaft and/or planetary gear slip adjusting part.This confession planetary gear slip adjusting part does not have radial support and axial location, in the situation that discontinuity equalization can be done axial float, thereby reaches the purpose of all carrying.

In the differential mechanism of above-mentioned helical-conveyer centrifugal, described unsteady adjustment structure comprises the adjustable ring that is fixed on output shaft.Adjustable ring is fixed on output shaft by removable structure, and removable structure can be the some screws that are located on adjustable ring, is provided with the some and described screw screw of corresponding setting one by one on output shaft, and installing/dismounting is simple and convenient.

In the differential mechanism of above-mentioned helical-conveyer centrifugal, described housing and fixedly be provided with two the 3rd bearings between central gear is provided with axle sleeve between described the 3rd bearing, is provided with the 4th bearing between described fixedly central gear and input central gear; One end of described input central gear inserts in the end of output shaft, and is provided with the 5th bearing between input central gear and output shaft.Be used for keeping the fixedly center of central gear, guarantee dynamical stability output.

in the differential mechanism of above-mentioned helical-conveyer centrifugal, described involute planet gear box of tricks comprises the one-level sun gear that is arranged on output shaft, be connected with primary planet pinion slip adjusting part on described one-level sun gear, described primary planet pinion slip adjusting part is connected with the 3rd gear ring on being fixed on housing, described primary planet pinion slip adjusting part is connected with secondary solar gear, be connected with secondary planetary gear slip adjusting part on described secondary solar gear, described secondary planetary gear slip adjusting part is connected with the 4th gear ring on being fixed on housing, described secondary planetary gear slip adjusting part is connected with the centrifuge conveyor screw.

In the present invention, primary planet pinion slip adjusting part comprise at least two respectively with the third line star-wheel of the 3rd gear ring and one-level sun gear engagement, described the third line star-wheel is connected with secondary solar gear by the secondary tie-rod, secondary planetary gear slip adjusting part comprise at least one respectively with the fourth line star-wheel of the 4th gear ring and secondary solar gear engagement, described fourth line star-wheel is connected with the centrifuge conveyor screw by three grades of tie-rods.

In the differential mechanism of above-mentioned helical-conveyer centrifugal, the speed discrepancy of described centrifuge conveyor screw and bowl adopts following formula to calculate:

$\mathrm{\&Delta;n}=\frac{\mathrm{na}2}{\frac{\mathrm{<figure-callout\; id="2"\; label="Zb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Zb</figure-callout>}2}{\mathrm{Za}2}(1+\frac{\mathrm{<figure-callout\; id="3"\; label="Zb"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Zb</figure-callout>}3}{\mathrm{Za}3})(1+\frac{\mathrm{Zb}4}{\mathrm{Za}4})}$

In formula: Δ n is poor rotating speed, unit: r/min;

Na2 is input sun gear a2 rotating speed, unit: r/min;

Za2, za3 and za4 are respectively the numbers of teeth of input sun gear a2, one-level sun gear a3 and secondary solar gear a4; Zb2, zb3 and zb4 are respectively the numbers of teeth of the second ring gear b2, the 3rd gear ring b3 and the 4th gear ring b4.

Obviously, this computing formula and formula of the prior art (2) are compared, can see that differential mechanism of the present invention is just can directly regulate poor rotating speed by the buncher that is connected with the input central gear, greatly simplify differential control system, be easy to control.

In the differential mechanism of above-mentioned helical-conveyer centrifugal, described location structure comprises and is connected in the fixedly connecting rod of central gear one end, is provided with elastomeric joint on connecting rod, also is provided with the through hole that passes for described input central gear on described connecting rod.Connecting rod and fixedly the syndeton of central gear be some securing members that are located on connecting rod, the other end of securing member is fixed on fixedly in central gear; In addition, elastomeric joint is connected by the support of pin and centrifuge, guarantees the fixedly stability of central gear.

Compared with prior art, the advantage of the differential mechanism of this helical-conveyer centrifugal is: 1, design is more reasonable, and structure is simpler.2, not only can control more accurately the numerical value of poor rotating speed, the vibrations of current peak and machine in the time of can also reducing to greatest extent the centrifuge startup, in addition, control system of the present invention simply and is easily controlled, and has reduced the requirement of automatic control.3, the input central gear is connected with buncher, is used for input speed and regulates poor rotating speed, can control accurately the numerical value of poor rotating speed by planetary gear slip adjusting part.4, the non-deformability of meshed transmission gear structure is strong, stable drive, the stability when having improved complete machine work.5, this confession planetary gear slip adjusting part does not have radial support and axial location, in the situation that discontinuity equalization can be done axial float, thereby reaches the purpose of all carrying.

Description of drawings

Fig. 1 is the structural representation of prior art.

Fig. 2 is structural representation provided by the invention.

Fig. 3 is cross-sectional view provided by the invention.

in Fig. 2-Fig. 3, bowl 1a, centrifuge conveyor screw 1b, housing 2, involute planet gear box of tricks 3, primary planet pinion slip adjusting part 31, secondary planetary gear slip adjusting part 32, slip governor motion 4, output shaft 41, adjustable ring 41a, planetary gear slip adjusting part 42, clutch shaft bearing 42a, the second bearing 42b, planet carrier 43, the first toroidal frame 43a, the second toroidal frame 43b, clutch shaft bearing installing zone 44, the second bearing installing zone 45, connecting rod 46, through hole 46a, elastomeric joint 47, outer becket 47a, interior becket 47b, rubber layer 47c, the 3rd bearing 51, the 4th bearing 52, the 5th bearing 53, axle sleeve 54, buncher 6, drive motors 7, fixing central gear a1, input central gear a2, one-level sun gear a3, secondary solar gear a4, the first ring gear b1, the second ring gear b2, the 3rd gear ring b3, the 4th gear ring b4, the first row star-wheel g1, the second planetary gear g2, the third line star-wheel g3, fourth line star-wheel g4, planet axis H1, bulge loop H1a, secondary tie-rod H2, three grades of tie-rod H3.

The specific embodiment

The present invention will be further described in detail below in conjunction with the drawings and specific embodiments.

as shown in Fig. 2-3, the differential mechanism of this helical-conveyer centrifugal comprises the housing 2 that is connected with bowl 1a, bowl 1a is connected with drive motors 7, be provided with the involute planet gear box of tricks 3 that is connected with centrifuge conveyor screw 1b in housing 2, for the convenient difference rotating speed of regulating, also be provided with slip governor motion 4 in housing 2, the output of described slip governor motion 4 is connected with described involute planet gear box of tricks 3 and can be directly according to the rotational speed regulation described centrifuge conveyor screw 1b of slip governor motion 4 inputs and the slip between bowl 1a when slip governor motion 4 drives 3 work of involute planet gear box of tricks.Obviously, the slip governor motion 4 of this enforcement is connected with buncher 6, and slip governor motion 4 can directly be regulated poor rotating speed, has greatly simplified differential control system, has the following advantages at least: being to be easy to control on the one hand, is easy to adjust on the other hand.

the slip governor motion 4 of this enforcement comprises input central gear a2 and the output shaft 41 that is arranged in housing 2, input central gear a2 outer race have the fixedly central gear a1 of setting coaxial with it and fixedly central gear a1 outer end be fixedly installed by external location structure outside housing 2, described output shaft 41 is connected with involute planet gear box of tricks 3, prioritization scheme, the location structure here comprises and is connected in the fixedly connecting rod 46 of central gear a1 one end, be provided with elastomeric joint 47 on connecting rod 46, also be provided with the through hole 46a that passes for described input central gear a2 on described connecting rod 46, elastomeric joint 47 is connected by the support of pin and centrifuge, and the structure of this elastomeric joint 47 is: wear the outer becket 47a that is fixed on connecting rod 46, be provided with outside interior becket 47b in becket 47a, be filled with rubber layer 47c between outer becket 47a and interior becket 47b.Secondly, for the fixing center of central gear, the output of assurance dynamical stability, at housing 2 with fixedly be provided with two the 3rd bearings 51 between central gear a1, be provided with axle sleeve 54 between described the 3rd bearing 51, be provided with the 4th bearing 52 between described fixedly central gear a1 and input central gear a2; The end of described input central gear a2 inserts in the end of output shaft 41, and is provided with the 5th bearing 53 between input central gear a2 and output shaft 41.

For can be in the situation that discontinuity equalization can be done axial float, thereby reach the purpose of all carrying, be provided with the flying height for planetary gear slip adjusting part 42 axial floats between output shaft 41 and planetary gear slip adjusting part 42, be provided be used to the unsteady adjustment structure of regulating described flying height on output shaft 41 and/or planetary gear slip adjusting part 42; Concrete, unsteady adjustment structure comprises the adjustable ring 41a that is fixed on output shaft 41.Adjustable ring 41a is fixed by screws on output shaft 41, and dismounting and installation are all more for convenience.

In addition, be arranged with at least two planetary gear slip adjusting parts 42 that difference is coupled outside input central gear a2 of the present invention, described planetary gear slip adjusting part 42 is connected with fixing central gear a1 respectively, be fixed with the first ring gear b1 that is connected with each planetary gear slip adjusting part 42 respectively on described housing 2, be fixed with the second ring gear b2 that is connected with each planetary gear slip adjusting part 42 respectively on described output shaft 41.Concrete, the planetary gear slip adjusting part 42 here comprise respectively with the first row star-wheel g1 of fixedly central gear a1 and the first ring gear b1 engagement, respectively with the second planetary gear g2 of input central gear a2 and the second ring gear b2 engagement, described the first row star-wheel g1 and the second planetary gear g2 are set up in parallel and a planet axis H1 passes the first row star-wheel g1 and the second planetary gear g2, be provided with clutch shaft bearing 42a between planet axis H1 and the first row star-wheel g1, be provided with the second bearing 42b between planet axis H1 and the second planetary gear g2.

in order to prevent the first row star-wheel g1 and the second planetary gear g2 axial float, and can fix described clutch shaft bearing 42a and the second bearing 42b, described planet axis H1 is separately fixed on planet carrier 43, and this planet carrier 43 comprises the first toroidal frame 43a that is fixed on planet axis H1 one end and the second toroidal frame 43b that is fixed on the other end, be respectively equipped with bulge loop H1a at the middle part of every planet axis H1, form clutch shaft bearing installing zone 44 between described the first toroidal frame 43a and bulge loop H1a, described clutch shaft bearing 42a is located in clutch shaft bearing installing zone 44, form the second bearing installing zone 45 between described the second toroidal frame 43b and bulge loop H1a, described the second bearing 42b is located in the second bearing installing zone 45.

as Fig. 2, shown in 3, the involute planet gear box of tricks 3 of this enforcement comprises the one-level sun gear a3 that is arranged on output shaft 41, be connected with primary planet pinion slip adjusting part 31 on described one-level sun gear a3, described primary planet pinion slip adjusting part 31 is connected with the 3rd gear ring b3 on being fixed on housing 2, described primary planet pinion slip adjusting part 31 is connected with secondary solar gear a4, be connected with secondary planetary gear slip adjusting part 32 on described secondary solar gear a4, described secondary planetary gear slip adjusting part 32 is connected with the 4th gear ring b4 on being fixed on housing 2, described secondary planetary gear slip adjusting part 32 is connected with centrifuge conveyor screw 1b.Further, primary planet pinion slip adjusting part 31 comprise at least two respectively with the third line star-wheel g3 of the 3rd gear ring b3 and one-level sun gear a3 engagement, described the third line star-wheel g3 is connected with secondary solar gear a4 by secondary tie-rod H2, secondary planetary gear slip adjusting part 32 comprise at least one respectively with the fourth line star-wheel g4 of the 4th gear ring b4 and secondary solar gear a4 engagement, described fourth line star-wheel g4 is connected with centrifuge conveyor screw 1b by three grades of tie-rod H3.

The speed discrepancy of centrifuge conveyor screw 1b of the present invention and bowl 1a adopts following formula to calculate:

$\mathrm{\&Delta;n}=\frac{\mathrm{na}2}{\frac{\mathrm{<figure-callout\; id="2"\; label="Zb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Zb</figure-callout>}2}{\mathrm{Za}2}(1+\frac{\mathrm{<figure-callout\; id="3"\; label="Zb"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Zb</figure-callout>}3}{\mathrm{Za}3})(1+\frac{\mathrm{Zb}4}{\mathrm{Za}4})}$

In formula: Δ n is poor rotating speed, unit: r/min;

Na2 is input sun gear a2 rotating speed, unit: r/min;

Za2, za3 and za4 are respectively the numbers of teeth of input sun gear a2, one-level sun gear a3 and secondary solar gear a4; Zb2, zb3 and zb4 are respectively the numbers of teeth of the second ring gear b2, the 3rd gear ring b3 and the 4th gear ring b4.This computing formula and formula (2) are compared, find that obviously differential control system of the present invention is easy to control, easy to adjust.

This computing formula is by the following derivation of equation out:

Gearratio is calculated as follows:

$i_{a2H3}^b=\frac{\mathrm{<figure-callout\; id="2"\; label="Zb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Zb</figure-callout>}2}{\mathrm{Za}2}(1+\frac{\mathrm{<figure-callout\; id="3"\; label="Zb"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Zb</figure-callout>}3}{\mathrm{Za}3})(1+\frac{\mathrm{Zb}4}{\mathrm{Za}4})---\left(3\right)$

Poor rotating speed is calculated as follows:

$\mathrm{\&Delta;n}=\frac{\mathrm{na}2}{i_{a2H3}^b}---\left(4\right)$

Formula (4) just equals the computing formula of the present embodiment;

The below uses transformation mechanism method calculating book differential mechanism output speeds at different levels: the size that proves poor rotating speed is only relevant with the rotation speed n a2 of input sun gear a2, and the rotation speed n b of bowl 1a is irrelevant:

For fixing central gear a1, the first row star-wheel g1, the first ring gear b1, planet axis H1 mechanism has:

$\frac{\mathrm{nb}1-\mathrm{nH}1}{\mathrm{na}1-\mathrm{nH}1}=\frac{-\mathrm{Za}1}{\mathrm{Zb}1};$

In formula: nH1 is planet axis H1 rotating speed; Za1 is the fixing number of teeth of central gear a1; Zb1 is the number of teeth of the first ring gear b1; Nb1 is the first ring gear b1 rotating speed; Na1 is fixing central gear a1 rotating speed.

Due to the fixing rotation speed n a1=0 of central gear a1

$\mathrm{nH}1=\frac{\mathrm{nb}1\mathrm{Zb}1}{\mathrm{Za}1+\mathrm{Zb}1}---(5-1)$

For a2, g2, b2, H1 mechanism has:

$\frac{\mathrm{nb}2-\mathrm{nH}1}{\mathrm{na}2-\mathrm{nH}1}=\frac{-\mathrm{<figure-callout\; id="2"\; label="Za"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Za</figure-callout>}2}{\mathrm{<figure-callout\; id="2"\; label="Zb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Zb</figure-callout>}2}$

Have $\mathrm{<figure-callout\; id="2"\; label="nb"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">nb</figure-callout>}2=\frac{(\mathrm{<figure-callout\; id="2"\; label="Za"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Za</figure-callout>}2+\mathrm{Zb}2)\mathrm{nH}1-\mathrm{na}2\mathrm{<figure-callout\; id="2"\; label="Za"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Za</figure-callout>}2}{\mathrm{Zb}2}---(5-2)$

In formula: nb2 is the second ring gear b2 rotating speed; Na2 is input central gear a2 rotating speed;

For a3, g3, b3, H2 mechanism has:

$\frac{\mathrm{nb}3-\mathrm{<figure-callout\; id="2"\; label="nH"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">nH</figure-callout>}2}{\mathrm{na}3-\mathrm{<figure-callout\; id="2"\; label="nH"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">nH</figure-callout>}2}=\frac{-\mathrm{<figure-callout\; id="3"\; label="Za"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Za</figure-callout>}3}{\mathrm{<figure-callout\; id="3"\; label="Zb"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Zb</figure-callout>}3}$

Have $\mathrm{<figure-callout\; id="2"\; label="nH"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">nH</figure-callout>}2=\frac{\mathrm{na}3\mathrm{<figure-callout\; id="3"\; label="Za"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Za</figure-callout>}3+\mathrm{<figure-callout\; id="3"\; label="nb"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">nb</figure-callout>}3\mathrm{<figure-callout\; id="3"\; label="Zb"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Zb</figure-callout>}3}{\mathrm{<figure-callout\; id="3"\; label="Za"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Za</figure-callout>}3+\mathrm{Zb}3}---(5-3)$

In formula: nb3 is that the 3rd ring gear b3 rotation speed n a3 is one-level sun gear a3 rotating speed; NH2 is secondary tie-rod H2 rotating speed;

For a4, g4, b4, H3 mechanism has:

$\frac{\mathrm{nb}4-\mathrm{<figure-callout\; id="3"\; label="nH"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">nH</figure-callout>}3}{\mathrm{na}4-\mathrm{<figure-callout\; id="3"\; label="nH"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">nH</figure-callout>}3}=\frac{-\mathrm{Za}4}{\mathrm{Zb}4}$

Have $\mathrm{<figure-callout\; id="3"\; label="nH"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">nH</figure-callout>}3=\frac{\mathrm{na}4\mathrm{Za}4+\mathrm{nb}4\mathrm{Zb}4}{\mathrm{Za}4+\mathrm{Zb}4}---(5-4)$

In formula: nb4 is the 4th ring gear b4 rotating speed; Na4 is secondary solar gear a4 rotating speed; NH3 is three grades of tie-rod H3 rotating speeds;

Due to nb1=nb3=nb4, make nb=nb1=nb3=nb4, and nb2=na3, nH2=na4, and Za1+Zb1=Za2+Zb2, Zb1=Zb2,

Unite the formula of finding the solution (5-1), (5-2), (5-3), (5-4):

$\mathrm{<figure-callout\; id="3"\; label="nH"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">nH</figure-callout>}3=\mathrm{nb}-\mathrm{na}2*\frac{\mathrm{<figure-callout\; id="2"\; label="Za"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Za</figure-callout>}2\mathrm{<figure-callout\; id="3"\; label="Za"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Za</figure-callout>}3\mathrm{Za}4}{\mathrm{Zb}2(\mathrm{<figure-callout\; id="3"\; label="Za"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Za</figure-callout>}3+\mathrm{Zb}3)(\mathrm{Za}4+\mathrm{Zb}4)}$

Definition by poor rotating speed:

Δn＝nb-nH3

Therefore have

$\mathrm{\&Delta;n}=\mathrm{na}2*\frac{\mathrm{<figure-callout\; id="2"\; label="Za"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Za</figure-callout>}2\mathrm{<figure-callout\; id="3"\; label="Za"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Za</figure-callout>}3\mathrm{Za}4}{\mathrm{Zb}2(\mathrm{<figure-callout\; id="3"\; label="Za"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Za</figure-callout>}3+\mathrm{Zb}3)(\mathrm{Za}4+\mathrm{Zb}4)}$

Or $\mathrm{\&Delta;n}=\frac{\mathrm{na}2}{i_{a2H3}^b}$

Here $i_{a2H3}^b=\frac{\mathrm{Zb}2(\mathrm{<figure-callout\; id="3"\; label="Za"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Za</figure-callout>}3+\mathrm{Zb}3)(\mathrm{Za}4+\mathrm{Zb}4)}{\mathrm{<figure-callout\; id="2"\; label="Za"\; filenames="HSA00000853911500011.png"\; state="\{\{state\}\}">Za</figure-callout>}2\mathrm{<figure-callout\; id="3"\; label="Za"\; filenames="HSA00000853911500011.png,HSA00000853911500021.png"\; state="\{\{state\}\}">Za</figure-callout>}3\mathrm{Za}4}$

Obtain formula (4) after simplification.

The size of the poor rotating speed of above explanation is only relevant with the rotation speed n a2 of input central gear a2, and bowl 1a rotation speed n b is irrelevant.

In addition, Material selection of the present invention is:

Fixedly central gear a1, the first row star-wheel g1, the second planetary gear g2, input central gear a2, output shaft 41 use 38CrMoAl nitrated steels are made, modified HB260～280 of arriving, the ionic nitriding of tooth section, nitrogenize bed thickness 0.15～0.2, hardness HV900～950;

Planet axis H1 makes with high-carbon-chromium bearing steel GCr15, spheroidizing HB170～207; Quenching HRC55～60;

The first ring gear b1, the second ring gear b2 make with 40Cr, modified HB250～280;

Planet carrier 43, axle sleeve 54 45 steel makings, HB220～250;

Clutch shaft bearing 42a, the second bearing 42b, the 3rd bearing 51, the 4th bearing 52 and the 5th bearing 53 all adopt the SKF bearing.

Check slag dumping condition of the present invention:

Be not difficult to judge with the method for drawing arrow: during the centrifuge operation, bowl 1a, centrifuge spiral 1b are consistent with input central gear a2 three's rotation direction, in Fig. 2, when centrifuge spiral 1b is right-hand screw, turn to when counterclockwise, centrifuge spiral 1b rotating speed lags behind bowl 1a rotation speed n b, therefore satisfies centrifuge slag dumping condition.

The course of work of the present embodiment is described below: during the centrifuge operation, the first ring gear b1 is with the rotating speed identical with bowl 1a rotation speed n b and identical direction High Rotation Speed, because fixing central gear a1 fixes, the first row star-wheel g1 will produce rotation and revolution, because planet axis H1 links together the first row star-wheel g1 and the first row star-wheel g2, and it is from the speed-regulating signal acting in conjunction that input central gear a2 inputs, and makes the second ring gear b2 produce output speed, thereby regulates slip.

Obviously, differential mechanism of the present invention not only can be controlled the numerical value of poor rotating speed more accurately, the vibrations of current peak and machine in the time of can also reducing to greatest extent the centrifuge startup, in addition, control system of the present invention simply and is easily controlled, and has reduced the requirement of automatic control.Be in particular in: when centrifuge starts, at first start centrifuge conveyor screw 1b, thereby can get rid of so the large situation of the contingent Vibration on Start-up that causes due to residuals skewness when last time, the residuals that may stay in service avoided bowl 1a to start; Simultaneously, when closing centrifuge, at first bowl 1a rotation speed n b is reduced, is then continued residuals is discharged outside machine by centrifuge conveyor screw 1b.

Specific embodiment described herein is only to the explanation for example of the present invention's spirit.Those skilled in the art can make various modifications or replenish or adopt similar mode to substitute described specific embodiment, but can't depart from spirit of the present invention or surmount the defined scope of appended claims.

although this paper has more used bowl 1a, centrifuge conveyor screw 1b, housing 2, involute planet gear box of tricks 3, primary planet pinion slip adjusting part 31, secondary planetary gear slip adjusting part 32, slip governor motion 4, output shaft 41, adjustable ring 41a, planetary gear slip adjusting part 42, clutch shaft bearing 42a, the second bearing 42b, planet carrier 43, the first toroidal frame 43a, the second toroidal frame 43b, clutch shaft bearing installing zone 44, the second bearing installing zone 45, connecting rod 46, through hole 46a, elastomeric joint 47, outer becket 47a, interior becket 47b, rubber layer 47c, the 3rd bearing 51, the 4th bearing 52, the 5th bearing 53, axle sleeve 54, buncher 6, drive motors 7, fixing central gear a1, input central gear a2, one-level sun gear a3, secondary solar gear a4, the first ring gear b1, the second ring gear b2, the 3rd gear ring b3, the 4th gear ring b4, the first row star-wheel g1, the second planetary gear g2, the third line star-wheel g3, fourth line star-wheel g4, planet axis H1, bulge loop H1a, secondary tie-rod H2, three grades of terms such as tie-rod H3, but do not get rid of the possibility of using other term.Using these terms is only in order to describe more easily and explain essence of the present invention; They are construed to any additional restriction is all contrary with spirit of the present invention.

Claims (10)

1. the differential mechanism of a helical-conveyer centrifugal, comprise the housing (2) that is connected with bowl (1a), be provided with the involute planet gear box of tricks (3) that is connected with centrifuge conveyor screw (1b) in housing (2), it is characterized in that, also be provided with slip governor motion (4) in described housing (2), the output of described slip governor motion (4) is connected with described involute planet gear box of tricks (3) and can be directly according to the described centrifuge conveyor screw of rotational speed regulation (1b) of slip governor motion (4) input and the slip between bowl (1a) when slip governor motion (4) drives involute planet gear box of tricks (3) work.

2. the differential mechanism of helical-conveyer centrifugal according to claim 1, it is characterized in that, described slip governor motion (4) comprises input central gear (a2) and the output shaft (41) that is arranged in housing (2), input central gear (a2) outer race have the fixedly central gear (a1) of setting coaxial with it and fixedly central gear (a1) outer end be fixedly installed by external location structure outside housing (2), described output shaft (41) is connected with involute planet gear box of tricks (3), be arranged with at least two planetary gear slip adjusting parts (42) that difference is coupled outside described input central gear (a2), described planetary gear slip adjusting part (42) is connected with fixing central gear (a1) respectively, be fixed with the first ring gear (b1) that is connected with each planetary gear slip adjusting part (42) respectively on described housing (2), be fixed with the second ring gear (b2) that is connected with each planetary gear slip adjusting part (42) respectively on described output shaft (41).

3. the differential mechanism of helical-conveyer centrifugal according to claim 2, it is characterized in that, described planetary gear slip adjusting part (42) comprises respectively and the fixing the first row star-wheel (g1) of central gear (a1) and the first ring gear (b1) engagement, respectively with the second planetary gear (g2) of inputting the engagement of central gear (a2) and the second ring gear (b2), described the first row star-wheel (g1) and the second planetary gear (g2) are set up in parallel and a planet axis (H1) is passed the first row star-wheel (g1) and the second planetary gear (g2), be provided with clutch shaft bearing (42a) between planet axis (H1) and the first row star-wheel (g1), be provided with the second bearing (42b) between planet axis (H1) and the second planetary gear (g2).

4. the differential mechanism of helical-conveyer centrifugal according to claim 3, it is characterized in that, described planet axis (H1) is separately fixed on planet carrier (43), described planet carrier (43) comprises the first toroidal frame (43a) that is fixed on planet axis (H1) end and the second toroidal frame (43b) that is fixed on the other end, be respectively equipped with bulge loop (H1a) at the middle part of every planet axis (H1), form clutch shaft bearing installing zone (44) between described the first toroidal frame (43a) and bulge loop (H1a), described clutch shaft bearing (42a) is located in clutch shaft bearing installing zone (44), form the second bearing installing zone (45) between described the second toroidal frame (43b) and bulge loop (H1a), described the second bearing (42b) is located in the second bearing installing zone (45).

5. the differential mechanism of according to claim 2 or 3 or 4 described helical-conveyer centrifugals, it is characterized in that, be provided with the flying height for planetary gear slip adjusting part (42) axial float between described output shaft (41) and planetary gear slip adjusting part (42), be provided be used to the unsteady adjustment structure of regulating described flying height on output shaft (41) and/or planetary gear slip adjusting part (42).

6. the differential mechanism of helical-conveyer centrifugal according to claim 5, is characterized in that, described unsteady adjustment structure comprises the adjustable ring (41a) that is fixed on output shaft (41).

7. the differential mechanism of helical-conveyer centrifugal according to claim 5, it is characterized in that, described housing (2) and fixedly be provided with two the 3rd bearings (51) between central gear (a1), be provided with axle sleeve (54) between described the 3rd rolling bearing (51), be provided with the 4th bearing (52) between described fixedly central gear (a1) and input central gear (a2); One end of described input central gear (a2) inserts in the end of output shaft (41), and is provided with the 5th bearing (53) between input central gear (a2) and output shaft (41).

8. the differential mechanism of helical-conveyer centrifugal according to claim 5, it is characterized in that, described involute planet gear box of tricks (3) comprises the one-level sun gear (a3) that is arranged on output shaft (41), be connected with primary planet pinion slip adjusting part (31) on described one-level sun gear (a3), described primary planet pinion slip adjusting part (31) is connected with the 3rd gear ring (b3) on being fixed on housing (2), described primary planet pinion slip adjusting part (31) is connected with secondary solar gear (a4), be connected with secondary planetary gear slip adjusting part (32) on described secondary solar gear (a4), described secondary planetary gear slip adjusting part (32) is connected with the 4th gear ring (b4) on being fixed on housing (2), described secondary planetary gear slip adjusting part (32) is connected with centrifuge conveyor screw (1b).

9. the differential mechanism of helical-conveyer centrifugal according to claim 8, is characterized in that, described centrifuge conveyor screw (1b) adopts following formula to calculate with the speed discrepancy of bowl (1a):

$\mathrm{\&Delta;n}=\frac{\mathrm{na}2}{\frac{\mathrm{Zb}2}{\mathrm{Za}2}(1+\frac{\mathrm{Zb}3}{\mathrm{Za}3})(1+\frac{\mathrm{Zb}4}{\mathrm{Za}4})}$

In formula: Δ n is poor rotating speed, unit: r/min;

Na2 is input sun gear a2 rotating speed, unit: r/min;

Za2, za3 and za4 are respectively the numbers of teeth of input sun gear (a2), one-level sun gear (a3) and secondary solar gear (a4); Zb2, zb3 and zb4 are respectively the numbers of teeth of the second ring gear (b2), the 3rd gear ring (b3) and the 4th gear ring (b4).

10. the differential mechanism of helical-conveyer centrifugal according to claim 2, it is characterized in that, described location structure comprises and is connected in the fixedly connecting rod (46) of central gear (a1) end, be provided with elastomeric joint (47) on connecting rod (46), also be provided with the through hole (46a) that passes for described input central gear (a2) on described connecting rod (46).

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