CN100451339C - Internally meshed oil hydraulic-pump rotor - Google Patents

Internally meshed oil hydraulic-pump rotor Download PDF

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Publication number
CN100451339C
CN100451339C CNB2003801020479A CN200380102047A CN100451339C CN 100451339 C CN100451339 C CN 100451339C CN B2003801020479 A CNB2003801020479 A CN B2003801020479A CN 200380102047 A CN200380102047 A CN 200380102047A CN 100451339 C CN100451339 C CN 100451339C
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CN
China
Prior art keywords
tooth
rotor
gap
circle
external
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CNB2003801020479A
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Chinese (zh)
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CN1708647A (en
Inventor
细野克明
Original Assignee
三菱综合材料Pmg株式会社
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Priority to JP2002314070 priority Critical
Priority to JP314070/2002 priority
Application filed by 三菱综合材料Pmg株式会社 filed Critical 三菱综合材料Pmg株式会社
Publication of CN1708647A publication Critical patent/CN1708647A/en
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Publication of CN100451339C publication Critical patent/CN100451339C/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084Toothed wheels

Abstract

An oil pump rotor assembly includes an inner rotor ( 20 ) having 'n' external teeth ('n' is a natural number), and an outer rotor ( 10 ) having (n+1) internal teeth which draws and discharges fluid by volume change of cells (R) formed between the inner and outer rotors ( 20, 10 ). The oil pump rotor assembly is configured such that a clearance, which is defined between the teeth of the inner and outer rotors ( 20, 10 ) that together form one of the cells (R) which has the minimum volume among the cells, is designated as 'a', a clearance, which is defined between the teeth of the inner and outer rotors ( 20, 10 ) that together form one of the cells (R) whose volume is increasing during rotation of the inner and outer rotors ( 20, 10 ), is designated as 'b', and a clearance, which is defined between the teeth of the inner and outer rotors ( 20, 10 ) that together form one of the cells (R) which has the maximum volume among the cells, is designated as 'c', the following inequalities are satisfied: a<=b<=c, and a<=c.

Description

The internally meshed type oil hydraulic-pump rotor

Technical field

The present invention relates to sucking employed oil hydraulic-pump rotor assembly in the internally meshed type oil pump of discharging fluid according to the volume-variation that is formed at the cell between external rotor and the internal rotor.

Background technique

In the past, in the internally meshed type oil pump, by making the internal rotor rotation, external tooth and internal tooth engagement also make the external rotor rotation, the a plurality of cells that are formed between two rotors produce volume-variation while rotating to move, suck the discharge fluid thus, described internally meshed type oil pump has: the housing with discharge port of the external rotor of internal tooth, the internal rotor with the external tooth that meshes with this internal tooth, the inhalation port that is formed with the suction fluid and discharge fluid.

Cell is separated by the external tooth of internal rotor and the internal tooth of external rotor respectively individually at its sense of rotation front side and rear side.Tooth top at the external tooth of internal rotor becomes on the position of identical angle of swing with the teeth groove of the internal tooth of external rotor, and the volume of each cell becomes minimum, sucks fluid thereby volume is enlarged in move along the inhalation port rotation.In addition, become on the position of identical angle of swing with the teeth groove of the internal rotor of external rotor at the teeth groove of the external tooth of internal rotor, the volume of cell becomes maximum, thereby when making volume reduce to discharge fluid along discharging the port rotation in moving.

In this internally meshed type oil pump, constitute, internal rotor is rotated driving, thereby the flank of tooth of the flank of tooth of external tooth pushing internal tooth makes the external rotor rotation thus.If investigate the engagement of two rotors that transmit rotating force, then can find: near the rotational position of cell volume minimum, the direction of transfer of power and flank of tooth approximate vertical, but near the rotational position of cell volume maximum, contact with each other near the tooth top of two rotors, so the direction of transfer of power is not vertical with the flank of tooth, the slip composition is bigger, thereby can produce friction.

Therefore, when the flank of tooth of two rotors each other producing like this on the part of sliding in the contact, can not help the transmission of rotating force, sliding friction increases thereby the flank of tooth rubs each other, can cause the generation of noise and the problems such as reduction of mechanical efficiency.

At this problem, propose to have the scheme of following rotor: it is formed with yielding portion on the flank of tooth, avoid producing the contact of not transmitting rotating force.(for example, opening flat 9-166091 communique) with reference to the spy.

But, general in such internally meshed type oil hydraulic-pump rotor assembly, between the flank of tooth of two rotors that form cell, be provided with the gap.Its main purpose is in order to prevent owing to the shape of two rotors or installation precision cause thereby collision can not be rotated between the tooth top the problem and the generation of noise etc., and this be by the profile of tooth of external rotor even finishing, the whole bag of tricks such as curve planarization that form the flank of tooth are realized.

But if just with in the past even finishing of profile of tooth or methods such as planarization, formation yielding portion the gap only is set, then backlash can reach more than the necessary degree, thereby the problem of the noise that the vibration of rotor when being difficult to avoid drive because of rotation causes is arranged.

Summary of the invention

The present invention makes in view of the above problems, and its purpose is to realize stably rotating to drive and the internally meshed type oil hydraulic-pump rotor assembly of inhibition noise.

In order to address the above problem, the invention provides a kind of oil hydraulic-pump rotor assembly that constitutes oil pump, described oil pump is the internal rotor and the external rotor engagement with (n+1) individual internal tooth with the individual external tooth of n (n is a natural number), come in the rotary course of inner and outer rotors, to suck the internally meshed type oil pump of discharging fluid by the volume-variation that is formed at a plurality of cells between its flank of tooth, it is characterized in that, if the gap length that volume becomes between the two rotor flank of tooth at minimum cell place is a, if the gap length between the two rotor flank of tooth at the cell place in the volume expansion process is b, if the gap length that volume becomes between the two rotor flank of tooth at maximum cell place is c, then a≤b≤c and a<c, and then, for gap b, if establishing the size in gap at the cell place of sense of rotation rear side is b1, if the size in the gap at the cell place of sense of rotation front side is b2, then satisfy the relation of b1≤b2.

In above-mentioned oil hydraulic-pump rotor assembly, can constitute, if establishing the size in the gap between the two rotor flank of tooth that volume reduces the cell place among the process is d, a≤b≤c and a<c and a≤d≤c then, and then, for gap d, be d1 if establish the size in gap at the cell place of sense of rotation rear side, if the size in the gap at the cell place of sense of rotation front side is d2, then satisfy the relation of d1 〉=d2.

The present invention also provides a kind of oil hydraulic-pump rotor assembly that constitutes oil pump, described oil pump be have the internal rotor of the individual external tooth of n (n is a natural number) and have (n+1) individual internal tooth external rotor engagement, come in the rotary course of inner and outer rotors, to suck the internally meshed type oil pump of discharging fluid by the volume-variation that is formed at a plurality of cells between its flank of tooth, it is characterized in that, form volume and expand rotation that gap between the two rotor flank of tooth of the cell the maximum process is accompanied by cell to from minimum and move and increase gradually.

In above-mentioned oil hydraulic-pump rotor assembly, can constitute, form volume and narrow down to rotation that gap between the two rotor flank of tooth of the cell the minimum process is accompanied by cell from maximum and move and dwindle gradually.

According to these inventions, form gap between two rotors of cell after mate becomes minimum, do not continue to increase with dwindling and reach maximum, so the backlash on mate is less, and can guarantee meshing the gap on the inoperative part.In addition, in the part of slip composition minimum, external tooth and internal tooth engagement are also transmitted rotating force, and in the bigger part of slip composition, external tooth and internal tooth are difficult to produce engagement, so can realize noise and the internally meshed type oil hydraulic-pump rotor assembly that friction is little and mechanical efficiency is high.

And then, in the process that cell volume reduces, gap between two rotors reduces gradually, and be not arrive minimum with increasing, so can in complete all scopes, guarantee fully to meshing the gap on the inoperative part, and on mate, make backlash less, thereby can obtain noise and the little internally meshed type oil hydraulic-pump rotor assembly of friction.

In above-mentioned oil hydraulic-pump rotor assembly, the flank of tooth of external rotor and internal rotor can use respectively by the cycloid that track generated of the rolling circle that fricton-tightly rolls on basic circle and form.

In above-mentioned oil hydraulic-pump rotor assembly, the flank of tooth of internal rotor can use the trochoid envelope and form, described trochoid envelope is by generating at the envelope of the locus circle that has the center on the trochoid when this trochoid moves, and the tooth top of external rotor can use the circular curve with the locus circle same diameter to form.

According to these inventions, can make in the past to be adopted, use the cycloid rotor that cycloid forms and use trochoid rotor that trochoid the forms low frictionization of low noise more.

In above-mentioned oil hydraulic-pump rotor assembly, using cycloid to form under the situation of profile of tooth of two rotors, also can constitute, the profile of tooth of internal rotor forms, with the epicycloid that generated by the 1st outer rolling circle Ai circumscribed with basic circle Di and that fricton-tightly roll profile of tooth as tooth top, with by with basic circle Di inscribe and fricton-tightly roll the 1st in the hypocycloid that generated of rolling circle Bi as the profile of tooth of teeth groove; The profile of tooth of external rotor forms, with the epicycloid that generated by the 2nd outer rolling circle Ao circumscribed with basic circle Do and that fricton-tightly roll profile of tooth as teeth groove, with by with basic circle Do inscribe and fricton-tightly roll the 2nd in the hypocycloid that generated of rolling circle Bo as the profile of tooth of tooth top, when the diameter of the basic circle Di that establishes internal rotor is φ Di, if the diameter of the 1st outer rolling circle Ai is φ Ai, if the diameter of rolling circle Bi is φ Bi in the 1st, if the diameter of the basic circle Do of external rotor is φ Do, if the diameter of the 2nd outer rolling circle Ao is φ Ao, if the diameter of rolling circle Bo is φ Bo in the 2nd, if the gap length of the tooth top of the tooth top of internal rotor and external rotor is in the t (≠ 0), internal rotor and external rotor satisfy following relation:

φ Bo=φ Bi, and

φDo=φDi·(n+1)/n+t·(n+1)/(n+2)

φAo=φAi+t/(n+2)。

In this case, in order to determine the profile of tooth of internal rotor and external rotor, at first, the rolling distance of the outer rolling of internal rotor and external rotor circle and interior rolling circle must be closed with a week, so must satisfy following various:

φDi=n·(φAi+φBi)

φDo=(n+1)·(φAo+φBo)

And then, in this mode,, make internal rotor identical with the interior rolling diameter of a circle of external rotor for the teeth groove that reduces internal rotor and the tooth top gap in a circumferential direction of external rotor.

ΦBo=φBi

The situation of the basic circle ratio oil hydraulic-pump rotor assembly in the past of external rotor is big,

φDo=φDi·(n+1)/n+(n+1)·t/(n+2)

For make outer rolling circle and in the rolling distance closure of rolling circle, and the outer rolling circle of external rotor is adjusted, make

φAo=φAi+t/(n+2)

According to this oil hydraulic-pump rotor assembly, guaranteed the internal tooth gap diametrically of the external tooth and the external rotor of internal rotor, and make between the flank of tooth of each rotor that gap in a circumferential direction is littler than in the past, so rocking of two rotors diminishes, can realize quietness oil pump preferably.

And then, oil hydraulic-pump rotor assembly as other modes, aforementioned internal rotor forms, with the epicycloid that generated by the 1st outer rolling circle Di circumscribed with its basic circle bi and that fricton-tightly roll profile of tooth as tooth top, with by with basic circle bi inscribe and fricton-tightly roll the 1st in the hypocycloid that generated of rolling circle di as the profile of tooth of teeth groove, aforementioned external rotor forms, with the epicycloid that generated by the 2nd outer rolling circle Do circumscribed with its basic circle bo and that fricton-tightly roll profile of tooth as teeth groove, with by with basic circle bo inscribe and fricton-tightly roll the 2nd in the hypocycloid that generated of rolling circle do as the profile of tooth of tooth top, when the diameter of the basic circle bi that establishes internal rotor is φ bi, if the diameter of the 1st outer rolling circle Di is φ Di, if the diameter of rolling circle di is φ di in the 1st, if the diameter of the basic circle bo of external rotor is φ bo, if the diameter of the 2nd outer rolling circle Do is φ Do, if the diameter of rolling circle do is φ do in the 2nd, if the offset of internal rotor and external rotor is in the e, internal rotor and external rotor constitute, φ bi=n (φ Di+ φ di), the relation of φ bo=(n+1) (φ Do+ φ do) is set up, and φ Di+ φ di=2e or φ Do+ φ do=2e establishment, in addition, φ Do>φ Di, φ di>φ do, (φ Di+ φ di)<(φ Do+ φ do) also sets up.

In this case, determine the profile of tooth of internal rotor and external rotor, at first, the rolling distance of the outer rolling of internal rotor and external rotor circle and interior rolling circle must be closed with a week, so must satisfy following various:

φ bi=n (φ Di+ φ di) and φ bo=(n+1) (φ Do+ φ do)

In addition, bigger in the process of engagement in order to ensure the backlash between the flank of tooth of being located at two rotors, with respect to the tooth top shape of the internal rotor slot form of the external rotor that forms by the 2nd outer rolling circle Do, that forms by the 1st outer rolling circle Di, and must satisfy following condition with respect to the tooth top shape of the external rotor slot form of the internal rotor that forms by rolling circle di in the 1st, that form by the 2nd interior rolling circle do:

φ Do>φ Di and φ di>φ do.Here, in the process of the engagement effect of referring to of said backlash have internal rotor load the flank of tooth opposition side the flank of tooth, and the flank of tooth of external rotor between the gap that produced.

In addition, because internal rotor and external rotor engagement, so

Must satisfy some among φ Di+ φ di=2e and the φ Do+ φ do=2e.

And then, in the present invention, for internal rotor being rotated well in the inboard of external rotor and guaranteeing tip clearance and reach appropriate backlash size, to reduce to mesh resistance, make the diameter of basic circle of external rotor bigger than in the past, so that on the engaging position of internal rotor and external rotor, the basic circle of internal rotor can not contact with the basic circle of external rotor.

Promptly satisfy (n+1) φ bi<n φ bo.

According to this formula, can derive (φ Di+ φ di)<(φ Do+ φ do).

Constitute according to this, can guarantee the tip clearance of the internal tooth of the external tooth of internal rotor and external rotor, and the gap on the basic circle circumferencial direction is littler than in the past between the flank of tooth of each rotor, so rocking of two rotors diminishes, can realize the oil pump that quietness is good.Particularly the hydraulic pressure that produces in the oil hydraulic-pump rotor assembly is small, even change has taken place in the torque that this oil hydraulic-pump rotor assembly is driven, also can avoid the generation of collision of the external tooth of the internal tooth of external rotor side and internal rotor side, so can realize the quietness of oil hydraulic-pump rotor assembly reliably.

Description of drawings

Fig. 1 is the plan view of the internally meshed type oil hydraulic-pump rotor assembly of expression the 1st mode of execution of the present invention, gap a, b, d between the expression flank of tooth.

Fig. 2 is the plan view of the internally meshed type oil hydraulic-pump rotor assembly of expression the 1st mode of execution of the present invention, gap c between the expression flank of tooth.

Fig. 3 is with regard to the angle of rotation of internal rotor and the relation between the gap between the flank of tooth, the figure that internally meshed type oil hydraulic-pump rotor assembly of the present invention shown in Figure 1 and in the past rotor assembly are compared.

Fig. 4 is the plan view of the 2nd mode of execution of expression oil hydraulic-pump rotor assembly of the present invention, is that expression internal rotor and external rotor satisfy following relation:

φ Bo=φ Bi, and

φDo=φDi·(n+1)/n+t·(n+1)/(n+2)

φAo=φAi+t/(n+2)

And then the value of clearance t is set at t=0.12mm and the plan view of the oil hydraulic-pump rotor assembly that constitutes.

Fig. 5 is the V portion enlarged view of the mate of expression oil hydraulic-pump rotor assembly shown in Figure 4.

Fig. 6 is the chart that compares to the noise that oil pump produced that has used oil hydraulic-pump rotor assembly shown in Figure 4, with in the past the noise that oil pump produced.

Fig. 7 is the plan view of the 3rd mode of execution of expression oil hydraulic-pump rotor assembly of the present invention.

Fig. 8 is the VIII portion enlarged view of the mate of expression oil pump shown in Figure 7.

Fig. 9 is the chart that compares to the backlash of the oil pump that has used oil hydraulic-pump rotor assembly shown in Figure 7, with the backlash of in the past oil pump.

Figure 10 is the chart that compares to the noise that oil pump produced that has used oil hydraulic-pump rotor assembly shown in Figure 7, with in the past the noise that oil pump produced.

Embodiment

Below, referring to figs. 1 through Fig. 3 the 1st mode of execution of the present invention is described.

The internally meshed type oil hydraulic-pump rotor assembly of Fig. 1, present embodiment shown in Figure 2 is a cycloid rotor, the flank of tooth of its external rotor 10 and internal rotor 20 is to use the cycloid that track generated by the rolling circle that fricton-tightly rolls on basic circle to form the following setting of each parameter of two rotors 10,20 respectively.

The diameter of the basic circle Do of external rotor 10: φ 57.31[mm]

The diameter of the outer rolling circle Ao of external rotor 10: φ 2.51[mm]

The diameter of the interior rolling circle Bo of external rotor 10: φ 2.70[mm]

The tooth number Z o:11[of external rotor 10]

The diameter of the basic circle Di of internal rotor 20: φ 52.00[mm]

The diameter of the outer rolling circle Ai of internal rotor 20: φ 2.50[mm]

The diameter of the interior rolling circle Bi of internal rotor 20: φ 2.76[mm]

The tooth number Z i:10[of internal rotor 20]

Eccentric amount e: φ 2.60[mm]

External rotor 10 and internal rotor 20 interior engagements, the external tooth engagement of the internal tooth of external rotor 10 and internal rotor 20 is formed with cell R between the flank of tooth.External rotor 10 is with internal rotor 20 rotations along the rotation of the direction of arrow (being rotated counterclockwise) of Fig. 1, Fig. 2, while this cell R produces volume-variation and rotates mobile thus.

Rotary angle position θ for internal rotor 20, if the below of figure is 0 °, the top of figure is 180 °, then the volume of cell R in θ=0 ° be minimum (Vmin) (Fig. 1), and enlarge gradually along with the rotation of internal rotor 20, in θ=198 °, reach maximum (Vmax) (Fig. 2).Cell R sucks fluid from the inhalation port of being located at housing (not shown) in the process that this volume enlarges.

Here, the part of along the circumferential direction certain cell R closure being got up, in other words, form the least part in the gap between the flank of tooth of two rotors 10,20 of certain cell R, be called the gap between the flank of tooth at this cell R place.

If among this gap, the size that volume becomes the gap between the flank of tooth of two rotors 10,20 that minimum cell R (Vmin) locates is made as a, the size in the gap between the flank of tooth of two rotors 10,20 at the cell R place among the volume expansion process is made as b (Fig. 1), the size that volume becomes the gap between the flank of tooth of two rotors 10,20 that maximum cell R (Vmax) locates is made as c (Fig. 2), and then the size in the gap at each cell R place is

A≤b≤c and a<c.

And then, be made as d (Fig. 1) if establish the size in the gap between the flank of tooth of two rotors 10,20 that volume reduces the cell R place among the process, then

a≤d≤c。

Size to two gap between rotor in the size in external rotor 10 in the internally meshed type oil hydraulic-pump rotor assembly of present embodiment and the gap between the internal rotor 20 and the rotor in the past in Fig. 3 compares.

Gap in the rotor in the past becomes minimum part for maximum in cell volume, and the rotation that is accompanied by cell is moved and dwindled gradually, and becomes minimum at the cell volume the best part.Therefore, according to rotor in the past, even influence among little range beta of the α of portion or the scope γ than engagement in the gap, the flank of tooth of two rotors is also contact easily each other, thereby causes the reduction of mechanical efficiency and the generation of noise because of friction sometimes.

On the other hand, as shown in the drawing according to present embodiment, to expand to the process of maximum (Vmax) from minimum (Vmin) at volume, the gap between the flank of tooth of two rotors of formation cell R continues to increase gradually.That is, if the size in the gap at the cell R place of sense of rotation rear side is made as b1, the size in the gap at the cell R place of sense of rotation front side is made as b2, then for the gap b in ° scope of 0<θ<198, b1≤b2 sets up all the time.

When internal rotor 20 ° began to rotate from rotary angle position θ=0, external rotor 10 was engaged with each other and transmits rotating force with internal rotor 20 flank of tooth in scope α shown in Figure 1.Even in this scope α (engagement influences portion), the size in gap also increases as shown in Figure 3, and it is littler than sense of rotation rear side can not become always.

And then the gap in the range beta of internal rotor 20 rotations is bigger than the gap in the scope α, and is accompanied by rotation and the continuation increase.Therefore, influence the α of portion with engagement and compare, the flank of tooth between two rotors 10,20 in this range beta more is difficult to contact each other.

And then the gap in the scope γ (performance impact portion) of internal rotor 20 rotation is also bigger than the gap in the range beta, and leans on the sense of rotation front side big more more, becomes maximum during in angle of swing θ=198 of internal rotor 20 °.Therefore, compare with range beta, the flank of tooth between two rotors 10,20 in this scope γ more is difficult to contact each other.

In addition, cell R become in the volume maximum (Vmax) gap c (Fig. 2) thus can with the suction side of cell R with discharge side and separate performance is impacted, but owing to be and identical in the past size, so performance can't be than reduce in the past in this.

And after the volume of cell R became maximum (Vmax), the sense of rotation more gap d of front side (Fig. 1) was accompanied by the rotation of internal rotor 20 and reduces gradually, and became minimum during in θ=396 ° once more.That is, if the size in the gap at the cell R place of sense of rotation rear side is made as d1, the size in the gap at the cell R place of sense of rotation front side is made as d2, then for the gap d in ° scope of 198<θ<396, d1 〉=d2 sets up all the time.

Therefore, also same even reduce side with volume increase side at the volume of cell R, influence the α of portion one side with engagement and compare, in the γ of performance impact portion one side, the flank of tooth more is difficult to contact each other.

As described above, internally meshed type oil hydraulic-pump rotor assembly according to present embodiment, constitute, gap in the engagement of transmitting rotating force efficiently influences the α of portion is less, gap in can not transmitting the γ of performance impact portion of rotating force efficiently is bigger, between it, the gap slowly increases, therefore, the flank of tooth contacts with each other and the rotating force that carries out is delivered in engagement and influences and carry out in the α of portion, in other parts, the flank of tooth then is difficult to contact each other, thereby can avoid the generation of noise and the reduction of efficient.

In addition, when the size in gap increases to c from a, preferably, a<b, b1<b2, b<c, but only otherwise satisfy a<c gets final product with dwindling, also can produce the part of a=b, b1=b2, b=c.

Similarly, when the size in gap is reduced to a from c, preferably, c>d, d1>d2, d>a, but only otherwise increasing ground c>a gets final product, also can produce the part of c=d, d1=d2, d=a.

At the oil hydraulic-pump rotor assembly of the present embodiment with above-mentioned dimensional parameters and have in the oil hydraulic-pump rotor assembly of equal therewith dimensional parameters, the value of above-mentioned a preferably is within the following ranges.

0.010≤a≤0.040【mm】

When a sets than 0.010mm under the little situation, the rotation of oil hydraulic-pump rotor assembly can not carried out smoothly, can hinder the function as pump.Conversely, when a sets than 0.040mm under the big situation, it is big that backlash becomes, the effect of the noise that can not be reduced.

In addition, the value of above-mentioned c preferably is within the following ranges.

0.040≤c≤0.150【mm】

When c sets than 0.040mm under the little situation, can not near (0 ° among Fig. 1) engagement in the engaging position, when c sets than 0.150mm under the big situation, it is many that the oil mass of exposing from the gap between the flank of tooth becomes, and the discharging performance of pump can significantly worsen.

Below, with regard to the 2nd mode of execution of the present invention, describe with reference to Fig. 4 to Fig. 6.Oil hydraulic-pump rotor assembly shown in Figure 4 has: (n is a natural number to be formed with n, n=10 in the present embodiment) internal rotor 110 of individual external tooth, be formed with (n+1) of each external tooth engagement (in the present embodiment, n+1=11) external rotor 120 of individual internal tooth, these internal rotors 110 and external rotor 120 are accommodated in the inside of housing 150.

Between the flank of tooth of internal rotor 110, external rotor 120, be formed with a plurality of cell C along the sense of rotation of two rotors 110,120.Sense of rotation front side and rear side at two rotors 110,120, the external tooth 111 of internal rotor 110 contacts respectively with the internal tooth 121 of external rotor 120, each cell C is separated individually thus, and bi-side have formed the independent fluid conveying chamber thus by housing 150 separations.Cell C be accompanied by the rotation of two rotors 110,120 and rotate mobile, one to transfer increase that one-period carries out volume repeatedly to, to reduce.

Internal rotor 110 is installed on the running shaft and can is that the center is supported rotatably with axle core Oi, form the epicycloid that will be generated by the 1st outer rolling circle Ai circumscribed with the basic circle Di of internal rotor 110 and that fricton-tightly roll profile of tooth as tooth top, and will by with basic circle Di inscribe and fricton-tightly roll the 1st in the rolling circle Bi hypocycloid that be generated as the profile of tooth of teeth groove.

External rotor 120 makes the axle core Oi off-centre (offset: e) dispose of a core Oo with respect to internal rotor 110, and can be that the center is supported rotatably in the inside of housing 150 with axle core Oo, form the epicycloid that will be generated by the 2nd outer rolling circle Ao circumscribed with the basic circle Do of external rotor 120 and that fricton-tightly roll profile of tooth as teeth groove, and will by with basic circle Do inscribe and fricton-tightly roll the 2nd in the rolling circle Bo hypocycloid that be generated as the profile of tooth of tooth top.

When the diameter with the basic circle Di of internal rotor 110 is made as φ Di, the diameter of the 1st outer rolling circle Ai is made as φ Ai, the diameter of the 1st interior rolling circle Bi is made as φ Bi, the diameter of the basic circle Do of external rotor 120 is made as φ Do, if the diameter of the 2nd outer rolling circle Ao is φ Ao, if the diameter of rolling circle Bo is made as in the φ Bo in the 2nd, between internal rotor 110 and external rotor 120, following relation is set up.Wherein, dimensional units is mm (millimeter).

At first, the rolling distance for rolling circle Bi in internal rotor 110, the 1 outer rollings circle Ai and the 1st must be closed with a week.That is, in the 1st outer rolling circle Ai and the 1st each rolling distance of rolling circle Bi and integral multiple (number of teeth doubly) must equal the girth of basic circle Di, so,

π φ Di=n π (φ Ai+ φ Bi), that is,

φDi=n·(φAi+φBi) ...(Ia)

Similarly, for each rolling distance of rolling circle Bo in external rotor 120, the 2 outer rollings circles Ao and the 2nd and integral multiple (number of teeth doubly) must equal the girth of basic circle Do, so,

π φ Do=(n+1) π (φ Ao+ φ Bo), that is,

φDo=(n+1)·(φAo+φBo) ...(Ib)

Below, about external rotor 120, based in the past external rotor ro (rolling circle bo (diameter phi bo), basic circle do (diameter phi do) in the 2nd outer rolling circle ao (diameter phi ao), the 2nd), the condition of the profile of tooth of the external rotor 120 that determines present embodiment is described.

In addition, external rotor ro disposes with respect to internal rotor 110 off-centre of present embodiment (eccentric amount e), has the engagement of clearance t ground.Clearance t refers to, when the mode of being close to a teeth groove of tooth top of internal rotor 110 and external rotor 120 disposes internal rotor 110 in external rotor 120, leaving to sense of rotation from this engaging position on 180 ° the position, be formed at the size in the gap between the tooth top of tooth top of internal rotor 110 and external rotor 120.

Wherein, following relation is set up.

φdo=φDi·(n+1)/n ...(II)

φdo=(n+1)·(φao+φbo) ...(III)

φao=φAi+t/2 ...(IIIa)

φbo=φBi-t/2 ...(IIIb)

In addition, for the internal rotor 110 of external rotor ro engagement, satisfy following general relation:

φai+φbi=φAi+φBi=2e ...(1)

φDi=φdo-2e ...(2)

In the present embodiment, in order to reduce between the teeth groove of tooth top on the engaging position, external rotor 120 and internal rotor 110 clearance t 2 in a circumferential direction, and guarantee clearance t 1 radially,

φB0=φbi=φBi ...(IV)

And, obtain from this formula (IV) and formula (1)

φai=φAi ...(3)

If set the interior rolling circle of external rotor 120 like this, then

The clearance t of t=(φ Do-φ Bo+ φ Ao)-(φ Di+ φ Ai+ φ Ai) from formula (1)~(3) and formula (IV) obtain

t=(φDo-φdo)+(φAo-φai) ...(V)

Can get according to above-mentioned formula (Ib), (III), (IV), (V)

t=(φAo-φai)·(n+2) ...(VI)

So obtain

φAo=φai+t/(n+2)

Here, at first obtain the diameter phi Do of basic circle Do.Can get according to (Ib), (III),

φ Do-φ do=(n+1) (φ Ao+ φ Bo)-(n+1) (φ ao+ φ bo), and then, obtain according to (IIIa), (IIIb), (IV)

φDo-φdo=(n+1)·(φAo-φai) ...(VII)

According to (VI), (VII) become

φ Do-φ do=(n+1) t (n+2), and then according to (II), φ Do becomes

φDo=(n+1)·φDi/n+(n+1)·t/(n+2) ...(A)

Then, according to (Ib),

φ Ao=φ Do/ (n+1)-φ Bo, so, can get according to (A)

φ Ao=φ Di/n+t/ (n+2)-φ Bo, and then can get according to (Ia), (IV)

φAo=φAi+t/(n+2) ...(B)

Concluding above-mentioned form can get, and external rotor 120 satisfies following condition:

φBo=φbi=φBi ...(IV)

φDo=(n+1)·φDi/n+(n+1)·t/(n+2) ...(A)

φAo=φAi+t/(n+2) ...(B)

In Fig. 4, show the internal rotor 110 (basic circle Di is that φ Di=52.00mm, the 1st outer rolling circle Ai are that rolling circle Bi is that φ Bi=2.70mm, the number of teeth are n=10 in the φ Ai=2.50mm, the 1st) and external rotor 120 (external diameter is that φ 70mm, basic circle Do are that φ Do=57.31mm, the 2nd outer rolling circle Ao are that rolling circle Bo is φ Bo=2.70mm in the φ Ao=2.51mm, the 2nd) the oil hydraulic-pump rotor assembly that combination gets under the condition of clearance t=0.12mm, eccentric amount e=2.6mm that satisfy above-mentioned relation ground and constitute.

On housing 150, cell C in the volume increase process among the cell C that is formed between the flank of tooth of two rotors 110,120 is formed with circular-arc inhalation port (not shown), and the cell C that reduces in the process along volume is formed with circular-arc discharge port (not shown).

Cell C is after volume becomes minimum in the way of external tooth 111 and the process of internal tooth 121 engagements, thereby in moving, make volume enlarge the suction fluid along inhalation port, volume becomes after the maximum, thereby makes volume reduce to discharge fluid in moving along the discharge port.

In addition, if clearance t is too small, then reduces the fluid that the cell C the process extrudes from volume and can produce pressure pulsation, thereby produce the cavitation erosion noise, the operation sound change of tune of pump is big, and because the pressure pulsation meeting causes the rotation of two rotors not carry out smoothly.

On the other hand, if clearance t is excessive, then can not produce the pressure pulsation of fluid, operating sound reduces, and, thereby the slip resistance that can reduce between the flank of tooth because backlash increases improves mechanical efficiency, but its reverse side, the close property of liquid at each cell C place is impaired, can cause particularly volumetric efficiency deterioration of pump performance.And, can not carry out the transmission of the driving torque under the correct engagement position, it is big that the loss of rotation becomes, so also can cause mechanical efficiency to reduce.

Therefore, preferably, clearance t is in satisfies in the scope of 0.03mm≤t≤0.30mm, be most preferably 0.12mm in the present embodiment.

In addition, in above-mentioned such oil hydraulic-pump rotor assembly that constitutes, by satisfying the relation of above-mentioned formula (IV), (A), (B), as shown in Figure 5, the profile of tooth of the teeth groove of the profile of tooth of the tooth top of external rotor 120 and internal rotor 110 is roughly the same.Thus, as shown in Figure 5, the clearance t that the footpath on the engaging position makes progress guarantee for identical in the past t/2=0.06mm, the clearance t 2 on circumferencial direction under such state diminishes, thus the rotation in, 110, the 120 mutual impacts of bearing of two rotors diminish.And, because the pressure direction in when engagement meets at right angles with respect to the flank of tooth, thus the transmission of torque between two rotors 110,120 can fricton-tightly efficiently carry out, thereby reduced heating and the noise that causes because of slip resistance.

In addition, in the present embodiment, if volume is become two rotors 110 at minimum cell C place, the size in the gap between 120 the flank of tooth is made as a (gap a, b, c etc. are not shown), two rotors 110 at the cell C place among the volume expansion process, the size in the gap between 120 the flank of tooth is made as b, volume becomes two rotors 110 at maximum cell C place, the size in the gap between 120 the flank of tooth is made as c, then a≤b≤c and a<c, and then, aforementioned gap b is b1 with the size in the gap at the cell place of sense of rotation rear side, size with the gap at the cell place of sense of rotation front side is b2, satisfies the relation of b1≤b2.In addition, if establishing the size in the gap between the flank of tooth of two rotors 110,120 that volume reduces the cell C place among the process is d, a≤b≤c and a<c and a≤d≤c then, and then, aforementioned gap d is d1 with the size in the gap at the cell place of sense of rotation rear side, size with the gap at the cell place of sense of rotation front side is d2, satisfies the relation of d1 〉=d2.

In Fig. 6, show to the noise that produced under the situation of using oil hydraulic-pump rotor assembly in the past, with the situation of the oil hydraulic-pump rotor assembly that uses present embodiment under the chart that compares of the noise that produced.From this chart as can be known, used the oil pump noise compared with the past of oil hydraulic-pump rotor assembly of present embodiment littler, quietness is better.

Below, with regard to the 3rd mode of execution of the present invention, describe with reference to Fig. 7 to Figure 10.

Oil hydraulic-pump rotor assembly shown in Figure 7 has: (n is a natural number to be formed with n, n=10 in the present embodiment) internal rotor 210 of individual external tooth, be formed with the external rotor 220 with the individual internal tooth of (n+1) (being 11 in the present embodiment) of each external tooth engagement, these internal rotors 210 and external rotor 220 are accommodated in the inside of housing 250.

Between the flank of tooth of internal rotor 210, external rotor 220, be formed with a plurality of cell C along the sense of rotation of two rotors 210,220.Sense of rotation front side and rear side at two rotors 210,220, the external tooth 211 of internal rotor 210 contacts respectively with the internal tooth 221 of external rotor 220, each cell C is separated individually thus, and bi-side have formed the independent fluid conveying chamber thus by housing 250 separations.Cell C be accompanied by the rotation of two rotors 210,220 and rotate mobile, one to transfer increase that one-period carries out volume repeatedly to, to reduce.

Internal rotor 210 is installed on the running shaft and can is that the center is supported rotatably with axle core Oi, the epicycloid that will be generated by the 1st outer rolling circle Di circumscribed with the basic circle bi of internal rotor 210 and that fricton-tightly roll is as the profile of tooth of tooth top, and will by with basic circle bi inscribe and fricton-tightly roll the 1st in the rolling circle di hypocycloid that be generated as the profile of tooth of teeth groove.

External rotor 220 makes the axle core Oi off-centre (offset: e) dispose of a core Oo with respect to internal rotor 210, and can be that the center is supported rotatably in the inside of housing 250 with axle core Oo, form the epicycloid that will be generated by the 2nd outer rolling circle Do circumscribed with the basic circle bo of external rotor 220 and that fricton-tightly roll profile of tooth as teeth groove, and will by with basic circle bo inscribe and fricton-tightly roll the 2nd in the rolling circle do hypocycloid that be generated as the profile of tooth of tooth top.

When the diameter with the basic circle bi of internal rotor 210 is made as φ bi, the diameter of the 1st outer rolling circle Di is made as φ Di, the diameter of the 1st interior rolling circle di is made as φ di, the diameter of the basic circle bo of external rotor 220 is made as φ bo, if the diameter of the 2nd outer rolling circle Do is φ Do, if in the diameter of rolling circle do was φ do in the 2nd, between internal rotor 210 and external rotor 220, following relation was set up.Wherein, dimensional units is mm (millimeter).

At first, the rolling distance for rolling circle di in internal rotor 210, the 1 outer rollings circle Di and the 1st must be closed with a week.That is, in the 1st outer rolling circle Di and the 1st rolling distance of rolling circle di and integral multiple (number of teeth doubly) must equal the girth of basic circle bi, so,

π φ bi=n π (φ Di+ φ di), that is,

φbi=n·(φDi+φdi) ...(Ia)

Similarly, must equal the girth of basic circle bo for the rolling distance of rolling circle do in external rotor 220, the 2 outer rollings circles Do and the 2nd, so,

π φ bo=(n+1) π (φ Do+ φ do), that is,

φbo=(n+1)·(φDo+φdo) ...(Ib)

In addition, bigger in the process of engagement in order to ensure the backlash between the flank of tooth of being located at two rotors, with respect to the tooth top shape of the internal rotor slot form of the external rotor that forms by the 2nd outer rolling circle Do, that forms by the 1st outer rolling circle Di, and must satisfy following condition with respect to the tooth top shape of the external rotor slot form of the internal rotor that forms by rolling circle di in the 1st, that form by the 2nd interior rolling circle do:

φ Do>φ Di and φ di>φ do.Here, in the process of the engagement effect of referring to of said backlash have internal rotor load the flank of tooth opposition side the flank of tooth, and the flank of tooth of external rotor between the gap that produced.

In addition, because internal rotor and external rotor engagement, so

Must satisfy any among φ Di+ φ di=2e and the φ Do+ φ do=2e.

And then, in the present invention, for internal rotor 210 being rotated well in the inboard of external rotor 220 and guaranteeing tip clearance and reach appropriate backlash size, to reduce to mesh resistance, make the diameter of basic circle bo of external rotor 220 bigger, so that on the engaging position of internal rotor 210 and external rotor 220, the basic circle bi of internal rotor 210 can not contact with the basic circle bo of external rotor 220.

Promptly satisfy (n+1) φ bi<n φ bo.

According to this formula and formula (Ia), (Ib), can obtain (φ Di+ φ di)<(φ Do+ φ do).In addition, aforementioned engaging position refers to, as shown in Figure 8, the teeth groove of the tooth top of the internal tooth 221 of external rotor side and the external tooth 211 of internal rotor side over against the position.

In addition, internal rotor 210 constitutes satisfied with external rotor 220

0.005mm≤(φ Do+ φ do)-(φ Di+ φ di)≤0.070mm (mm: millimeter) ... (Ic)

(below, abbreviate (φ Do+ φ do)-(φ Di+ φ di) as A).

In addition, in the present embodiment, satisfy internal rotor 210 (basic circle bi is that φ bi=65.00mm, the 1st outer rolling circle Di are that rolling circle di is that φ di=2.60mm, the number of teeth are n=10 in the φ Di=3.90mm, the 1st) and external rotor 220 (external diameter is that φ 87.0mm, basic circle bo are that φ bo=71.599mm, the 2nd outer rolling circle Do are that rolling circle do is φ do=2.5955mm in the φ Do=3.9135mm, the 2nd) combination under the condition of eccentric amount e=3.25mm that above-mentioned relation ground constitutes and constitute the oil hydraulic-pump rotor assembly.In addition, in the present embodiment, the facewidth of two rotors (rotating axial size) is set at 10mm.And the 1st outer rolling circle Di is that rolling circle di is that φ di=2.60mm, the 2nd outer rolling circle Do are that rolling circle do is φ do=2.5955mm in the φ Do=3.9135mm, the 2nd in the φ Di=3.90mm, the 1st, thus, and A=0.009mm (with reference to Fig. 8).

On housing 250, cell C in the volume increase process among the cell C that is formed between the flank of tooth of two rotors 210,220 is formed with circular-arc inhalation port (not shown), and the cell C that reduces in the process along volume is formed with circular-arc discharge port (not shown).

Cell C is after volume becomes minimum in the way of external tooth 211 and the process of internal tooth 221 engagements, thereby in moving, make volume enlarge the suction fluid along inhalation port, after volume becomes maximum, thereby in moving, make volume reduce to discharge fluid along the discharge port.

In addition,, then can not realize suitableization of tip clearance and backlash size, thereby can not reduce the external tooth 211 of internal rotor side and the gearing noise of the internal tooth 221 of external rotor side if gap A is too small.

On the other hand, if gap A is excessive, then can not realize the external tooth 211 of internal rotor side and suitableization of the difference of the poor and thickness (size of tooth on the circumferencial direction of basic circle) of the tooth depth (tooth is in the size on the Normal direction of basic circle) of the internal tooth 221 of external rotor side, in the rotary course of internal rotor, external rotor 210,220, produce the part that does not have backlash sometimes.In this case, the good rotation of two rotors can not be realized, the reduction of mechanical efficiency can be caused and the generation of the noise that causes because of the collision of external tooth 211 and internal tooth 221.

Therefore, preferably, gap A is in the scope that satisfies 0.005mm≤A≤0.070mm, is most preferably 0.009mm in the present embodiment.

In above-mentioned such oil hydraulic-pump rotor assembly that constitutes, the profile of tooth of the teeth groove of the profile of tooth of the tooth top of external rotor 220 and internal rotor 210 is roughly the same.Thus, as shown in Figure 8, tip clearance tt guarantees that for identical in the past, the clearance t s on basic circle circumferencial direction under such state diminishes, so in rotation, 210, the 220 mutual impacts of bearing of two rotors diminish.Therefore, particularly the hydraulic pressure that produces in the oil hydraulic-pump rotor assembly is small, even change has taken place in the torque that this oil hydraulic-pump rotor assembly is driven, also can avoid the internal tooth 221 of external rotor side and the generation of the collision of the external tooth 211 of internal rotor side, so can realize the quietness of oil hydraulic-pump rotor assembly reliably.And, because the pressure direction in when engagement meets at right angles with respect to the flank of tooth, thus the transmission of torque between two rotors 210,220 can fricton-tightly efficiently carry out, thereby reduced heating and the noise that causes because of slip resistance.

Illustrated among Fig. 9 to the backlash on each rotary angle position of each internal rotor in the oil hydraulic-pump rotor assembly in the past (dotted line among Fig. 9), with the oil hydraulic-pump rotor assembly of present embodiment in each rotary angle position of internal rotor on the chart that compares of backlash (solid line among Fig. 9).From this this chart as can be seen, the oil hydraulic-pump rotor assembly of present embodiment the volume of aforementioned engaging position and cell C increase and the process that reduces among, the backlash that can make compared with the past is littler, and becomes on the maximum position at the volume of cell C, can guarantee backlash same.Therefore, in the latter case, can guarantee that volume becomes the close property of liquid of the cell C in the maximum, transfer efficiency can maintain on the level same.In addition, the angle of rotation of only having put down in writing internal rotor in Fig. 9 is from 0 ° to 198 ° backlash, and this is because in 198 ° to 396 ° scope, and changing with backlash in 198 ° to 0 ° the scope shown in Figure 9 is same (symmetry), so omitted record.

In Figure 10, show to the noise that produced under the situation of using oil hydraulic-pump rotor assembly in the past, with the situation of the oil hydraulic-pump rotor assembly that uses present embodiment under the chart that compares of the noise that produced.From this chart as can be seen, the oil hydraulic-pump rotor assembly of present embodiment as shown in Figure 9, the volume of engaging position and cell C increase and the process that reduces among, the backlash that makes compared with the past is littler, so noise is littler than in the past, thereby can improve quietness.

In addition, for each component parts shown in the above mode of execution, its different shape and combination etc. only are examples, can carry out all changes based on designing requirement in the scope that does not break away from purport of the present invention.

For example, for two rotors that constitute internally meshed type oil hydraulic-pump rotor assembly, in the above-described embodiment, adopted two rotors to have the so-called cycloid rotor of the tooth surface shape that forms by cycloid, but also can be the so-called trochoid rotor that constitutes by following internal rotor and external rotor, described internal rotor has the tooth surface shape that forms at the envelope of locus circle when this trochoid moves that is centered close on the trochoid by making, described external rotor and the engagement of this internal rotor, get final product so long as satisfy the rotor of the condition in above-mentioned gap, the rotor with any tooth surface shape all can.

Industrial applicibility

As described above, according to internally meshed type oil Pump rotor assembly of the present invention, form Gap between two rotors of cell continue to increase and becomes after mate becomes minimum So the backlash on mate is littler, thereby can guarantee meshing inoperative greatly, Gap on the part.

In addition, the internally meshed type oil Pump rotor assembly according to other modes of the present invention forms little Gap between two rotors of chamber becomes after the maximum, continues to reduce and becomes at mate Little, so the backlash on the mate is littler, thereby can guarantee meshing inoperative section Gap on the branch.

Therefore, in the part of slip composition minimum, external tooth and internal tooth engagement are also transmitted revolving force, In the bigger part of slip composition, external tooth and internal tooth be difficult to the engagement, so can realize noise and Internally meshed type oil pump little and that mechanical efficiency is high rubs.

Internally meshed type oil Pump rotor assembly according to other modes of the present invention can make in the past institute The trochoid rotor that the cycloid rotor that adopts, use cycloid formation and use trochoid form more Add the low frictionization of low noise, thereby can realize the internally meshed type oil pump that performance is higher.

Claims (5)

1. oil hydraulic-pump rotor assembly, it is the oil hydraulic-pump rotor assembly that constitutes oil pump, described oil pump be have the internal rotor of a natural number n external tooth and have n+1 internal tooth external rotor engagement, come in the rotary course of inner and outer rotors, to suck the oil pump of discharging fluid by the volume-variation that is formed at a plurality of cells between its flank of tooth
It is characterized in that, if the gap length that volume becomes between the two rotor flank of tooth at minimum aforementioned cell place is a, if the gap length between the two rotor flank of tooth at the aforementioned cell place in the volume expansion process is b, if the gap length that volume becomes between the two rotor flank of tooth at maximum aforementioned cell place is c, then a≤b≤c and a<c, and then, for aforementioned gap b, if establishing the size in gap at the cell place of sense of rotation rear side is b1, if the size in the gap at the cell place of sense of rotation front side is b2, then satisfy the relation of b1≤b2.
2. oil hydraulic-pump rotor assembly as claimed in claim 1, if establishing the size in the gap between the two rotor flank of tooth that volume reduces the aforementioned cell place among the process is d, a≤b≤c and a<c and a≤d≤c then, and then, for aforementioned gap d, if establishing the size in gap at the cell place of sense of rotation rear side is d1, the size in gap of establishing the cell place of sense of rotation front side is d2, then satisfies the relation of d1 〉=d2.
3. oil hydraulic-pump rotor assembly as claimed in claim 1 or 2, the flank of tooth of aforementioned external rotor and internal rotor are to use the cycloid that track generated by the rolling circle that fricton-tightly rolls on basic circle to form respectively.
4. oil hydraulic-pump rotor assembly as claimed in claim 1 or 2, the flank of tooth of aforementioned internal rotor is to use the trochoid envelope to form, described trochoid envelope is by generating at the envelope of the locus circle that has the center on the trochoid when this trochoid moves, and the tooth top of aforementioned external rotor is to use the circular curve with aforementioned locus circle same diameter to form.
5. oil hydraulic-pump rotor assembly as claimed in claim 1, aforementioned internal rotor forms, with the epicycloid that generated by the 1st outer rolling circle Di circumscribed with its basic circle bi and that fricton-tightly roll profile of tooth as tooth top, with by with basic circle bi inscribe and fricton-tightly roll the 1st in the hypocycloid that generated of rolling circle di as the profile of tooth of teeth groove
Aforementioned external rotor forms, with the epicycloid that generated by the 2nd outer rolling circle Do circumscribed with its basic circle bo and that fricton-tightly roll profile of tooth as teeth groove, with by with basic circle bo inscribe and fricton-tightly roll the 2nd in the hypocycloid that generated of rolling circle do as the profile of tooth of tooth top
When the diameter of the basic circle bi that establishes internal rotor is φ bi, if the diameter of the 1st outer rolling circle Di is φ Di, if the diameter of rolling circle di is φ di in the 1st, if the diameter of the basic circle bo of external rotor is φ bo, if the diameter of the 2nd outer rolling circle Do is φ Do, if the diameter of rolling circle do is φ do in the 2nd, if the offset of internal rotor and external rotor is in the e, internal rotor and external rotor are in φ bi=n (φ Di+ φ di), under the relation of φ bo=(n+1) (φ Do+ φ do), and satisfy φ Di+ φ di=2e or φ Do+ φ do=2e, also satisfy φ Do>φ Di, φ di>φ do, (φ Di+ φ di)<(φ Do+ φ do).
CNB2003801020479A 2002-10-29 2003-10-29 Internally meshed oil hydraulic-pump rotor CN100451339C (en)

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CN1708647A (en) 2005-12-14
WO2004044430A1 (en) 2004-05-27
MY168173A (en) 2018-10-11
US20060239848A1 (en) 2006-10-26
HUE027489T2 (en) 2016-11-28
EP1559912B1 (en) 2015-12-09
EP1559912A1 (en) 2005-08-03
JPWO2004044430A1 (en) 2006-03-16
KR20050067202A (en) 2005-06-30
ES2561939T3 (en) 2016-03-01

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