KR20050067202A - Internally meshed oil hydraulic-pump rotor - Google Patents

Abstract

An oil hydraulic-pump rotor assembly where an inner rotor (20) having n (n: natural number) number of outer teeth and an outer rotor (10) having (n + 1) number of inner teeth mesh and fluid is sucked and discharged by variation in volume of cells (R) formed between tooth flanks of the rotors. The oil hydraulic- pump rotor assembly is constructed such that the relationships a <= b <= c and a < c are satisfied, where a is the magnitude of the clearance between tooth flanks of both rotors (20, 10), in one of the cells (R) that has a minimum volume, b is the magnitude of the clearance between tooth flanks of both rotors (20, 10), in one of the cells (R) the volume of which cell is increasing, and c is the magnitude of the clearance between tooth flanks of both rotors (20, 10), in one of the cells (R) that has a maximum volume.

Description

Internal oil pump rotor {INTERNALLY MESHED OIL HYDRAULIC-PUMP ROTOR}

The present invention relates to an oil pump rotor assembly for use in an internal oil pump for sucking and discharging fluid in accordance with a volume change of a cell formed between an outer rotor and an inner rotor.

Conventionally, in an internal type oil pump having an outer rotor having an inner tooth, an inner rotor having an outer tooth engaged with the inner tooth, and a casing having a suction port through which the fluid is sucked in and a discharge port through which the fluid is discharged, By rotating the rotor, the outer tooth engages with the inner tooth to rotate the outer rotor, and a plurality of cells formed between both rotors rotate to move in and out of the fluid as the volume changes.

The cells are separately partitioned by the outer teeth of the inner rotor and the inner teeth of the outer rotor, respectively, in the front side and the rear side of the rotational direction thereof. Each cell has a minimum volume at the position where the tooth line of the outer tooth of the inner rotor and the inner tooth of the outer rotor become the same rotational angle. Inhale. The volume is maximized at the position where the jig of the outer tooth of the inner rotor and the jig of the inner rotor of the outer rotor have the same rotation angle, and discharge the fluid by reducing the volume when rotating along the discharge port.

In this internal oil pump, the inner rotor is driven to rotate, and the tooth surface of the external tooth presses the tooth surface of the internal tooth to rotate the external rotor. Considering the engagement of both rotors that transmit the rotational force, in the vicinity of the rotational position where the cell volume is minimum, the direction of force transmission is substantially perpendicular to the tooth surface, and the rotational position where the cell volume is maximum In the vicinity, since the vicinity of the tooth line apex of both rotors comes into contact with each other, the frictional force is generated because the sliding component is not perpendicular to the tooth surface but the slipping component is large.

Therefore, when the tooth surfaces of both rotors come in contact with each other in such a slip-producing part, there is a problem that the sliding surfaces rub against each other without increasing the transmission of the rotational force, thereby increasing the sliding friction, resulting in the occurrence of noise and deterioration in mechanical efficiency.

In response to this problem, a rotor in which a skin is formed on the tooth surface in order to avoid contact without transmitting rotational force is also proposed (see, for example, Japanese Patent Laid-Open No. 9-166091).

However, in such an internal oil pump rotor assembly, a clearance is generally formed between the teeth of both rotors forming the cell. The main purpose of this is to prevent teeth from coming into contact with each other depending on the shape of the rotor and the accuracy of attachment, and to prevent the occurrence of noise, etc., and to maximize the uniformity of the teeth of the external rotor and to flatten the curve forming the tooth surface. It is implemented by various means, such as these.

However, simply forming a clearance by means such as maximizing tooth flattening, flattening, or forming the escape portion of the conventional tooth causes the backlash to become larger than necessary, and the rotor is shaken during rotational driving. There is a problem that it is difficult to avoid the occurrence of noise.

BRIEF DESCRIPTION OF THE DRAWINGS It is a top view which shows the internal type oil pump rotor assembly which concerns on 1st Embodiment of this invention, and shows interdental clearance a, b, d.

Fig. 2 is a plan view showing the internal oil pump rotor assembly according to the first embodiment of the present invention, and shows interdental clearance c.

Fig. 3 is a diagram comparing the internal oil pump rotor assembly according to the present invention shown in Fig. 1 with the conventional rotor assembly with respect to the relationship between the rotation angle of the internal rotor and the clearance between teeth.

4 is a plan view showing a second embodiment of the oil pump rotor assembly according to the present invention, in which the inner rotor and the outer rotor are provided.

While φBo = φBi

φDo = φDi · (n + 1) / n + t · (n + 1) / (n + 2)

It is a top view which shows the oil pump rotor assembly which satisfy | fills the relationship of (phi) Ao = (phi) Ai + t / (n + 2), and the value of clearance (t) was set to t = 0.12mm.

FIG. 5 is an enlarged view of a V portion showing the engagement portion of the oil pump rotor assembly shown in FIG. 4. FIG.

FIG. 6 is a graph showing a comparison between noise by an oil pump using the oil pump rotor assembly shown in FIG. 4 and noise by a conventional oil pump.

It is a top view which shows 3rd embodiment of the oil pump rotor assembly which concerns on this invention.

FIG. 8 is an enlarged view of a portion showing the engagement portion of the oil pump shown in FIG. 7. FIG.

It is a graph which shows the comparison of the backlash of the oil pump using the oil pump rotor assembly shown in FIG. 7 with the backlash of the conventional oil pump.

FIG. 10 is a graph showing a comparison between noise by an oil pump using the oil pump rotor assembly shown in FIG. 7 and noise by a conventional oil pump. FIG.

Disclosure of the Invention

The present invention has been made in view of the above problems, and an object thereof is to realize an internal oil pump rotor assembly capable of stably rotating and suppressing noise.

In order to solve the above problem, the present invention provides a volume of a plurality of cells formed between an inner rotor having n (n is a natural number) outer teeth and an outer rotor having (n + 1) inner teeth and formed between the teeth. An oil pump rotor assembly that constitutes an internal oil pump that sucks and discharges fluid during rotation of an internal and external rotor according to a change, wherein the clearance between teeth of both rotors in a cell with minimum volume is increased by a B is the magnitude of the interdental clearance of both rotors in the cell in the process of forming a, c is the magnitude of the interdental clearance of both rotors in the cell where the volume becomes the largest, and a <b <c and a <c Furthermore, the clearance (b) satisfies b1 ≤ b2, with b1 being the magnitude of the clearance in the rear cell in the rotational direction and b2 being the magnitude of the clearance in the front cell in the rotational direction. One provides a pump rotor assembly.

In the oil pump rotor assembly, d is the magnitude of the interdental clearance of both rotors in the cell in the process of decreasing volume, d,

a ≤ b ≤ c, a <c, and a ≤ d ≤ c, and the clearance d is defined as the magnitude of the clearance in the rear cell in the rotational direction of d1 and the clearance in the front cell in the rotational direction. Let size be d2

You may comprise so that d1≥d2 may be satisfied.

The present invention also relates to an internal rotor having n (n is a natural number) external teeth and an external rotor having (n + 1) internal teeth, wherein the fluid is internally changed according to the volume change of a plurality of cells formed between the tooth surfaces. An oil pump rotor assembly constituting an internal oil pump that sucks and discharges during rotation of an external rotor, wherein the clearance between teeth of both rotors forming a cell in the process of expanding volume from minimum to maximum is increased as the cell moves. An oil pump rotor assembly is provided that is gradually increased.

In the oil pump rotor assembly, the inter-gear clearance of both rotors forming a cell in the process of decreasing in volume from maximum to minimum may be configured to gradually decrease with rotational movement of the cell.

According to these inventions, since the clearance between both rotors forming the cell becomes the minimum in the engaging portion, then it does not shrink and continuously increases and becomes the maximum, so that the clearance in the engaging portion is small and does not contribute to the engagement. Clearance at is secured. In addition, the rotational force is transmitted by the outer tooth engaging the inner tooth at the portion where the slip component is the smallest, and the engagement of the outer tooth and the inner tooth is difficult to occur at the portion where the slip component is increased. Therefore, the noise and friction (friction) are small, and the internal oil pump rotor assembly with a high mechanical efficiency can be obtained.

In addition, in the process of decreasing the volume of the cell, the clearance between both rotors gradually decreases and is not increased but becomes minimum, so that the clearance at the portion that does not contribute to the engagement over the entire circumference can be sufficiently secured. In this part, the backlash can be made small, and it becomes possible to obtain an internal oil pump rotor assembly with low noise and friction.

In the oil pump rotor assembly, the teeth of the outer rotor and the inner rotor may each be formed using a cycloid curve first generated by the trajectory of a rolling circle rolling without slipping on the base circle.

In the oil pump rotor assembly, the tooth surface of the inner rotor is formed by using a trocoid envelope that is first generated by an envelope when a ruled circle having a center on the trocoid curve is moved along this trocoid curve, and the tooth line of the outer rotor is formed. You may form using the arc curve of the same diameter as a locus circle.

According to these inventions, the cycloid rotor formed using the conventionally used cycloid curve and the trocoid rotor formed using the trocoid curve can be made low noise and low friction.

In the oil pump rotor assembly, when the teeth of both rotors are formed using the cycloid curve, the teeth of the inner rotor are first rolled up by the first outer rolling circle Ai, which does not slide outside the base circle Di. The outer cloud cycloid curve generated by the tooth line, and the inner cloud cycloid curve first generated by the first inner cloud circle Bi, which does not slide inscribed to the base circle Di, is formed as the tooth jig, The tooth of the outer rotor is a tooth of the jig, and the inner rolling cycloid curve first generated by the second outer rolling circle Ao that rolls without being circumscribed to the base circle Do is slipped inward to the base circle Do. Tooth teeth of the inner cloud cycloid curve first generated by the second rolling cloud source (Bo) And the diameter of the base circle Di of the inner rotor is φDi, the diameter of the first outer cloud source Ai is φAi, and the diameter of the first inner cloud source Bi is φBi, the base circle of the outer rotor. (Do) the diameter φDo, the diameter of the second outer cloud source (Ao) φAo, the diameter of the second inner cloud source (Bo) φBo, the size of the gap between the tooth of the inner rotor and the tooth of the outer rotor t When (≠ 0),

While φBo = φBi,

φDo = φDi · (n + 1) / n + t · (n + 1) / (n + 2)

The inner rotor and the outer rotor may be constituted by satisfying φ Ao = φ Ai + t / (n + 2).

In this case, in order to determine the tooth shape of the inner rotor and the outer rotor, first, since the rolling distances of the outer and inner cloud sources of the inner rotor and the outer rotor must end in one circumference,

φDi = n (φAi + φBi)

It is necessary to satisfy each equation of φDo = (n + 1) · (φAo + φBo).

Moreover, in this aspect, in order to reduce clearance in the main direction of the jig | tool of an inner rotor and the tooth line of an outer rotor, the diameter of the inner rolling source of an inner rotor and an outer rotor is made the same.

φBo ＝ φBi

The base of the outer rotor is larger than that of the conventional oil pump rotor assembly,

φDo = φDi · (n + 1) / n + (n + 1) · t / (n + 2)

To finish the rolling distance of the outer and inner cloud sources, adjust the outer cloud sources of the outer rotor,

φAo = φAi + t / (n + 2)

According to this oil pump rotor assembly, the clearance in the radial direction between the outer teeth of the inner rotor and the inner teeth of the outer rotor is secured, and the clearance between the teeth of each rotor in the circumferential direction between teeth is smaller than before, so that both rotors are noisy. This small, high-quiet oil pump can be realized.

In addition, as another type of oil pump rotor assembly, the inner rotor has a toothed tooth shape in which the inner rotor cycloid curve first generated by the first outer rolling circle Di, which rolls out without slipping outside the base circle bi, is rolled. And the inner cloud cycloid curve first generated by the first inner cloud source di which rolls inscribed to the base circle bi without sliding, is formed as a jagged tooth, and the outer rotor is formed on the base circle bo. To the second internal cloud source (do) which rolls without slipping by inscribed to the base circle (bo) by making the external cloud cycloid curve first generated by the second external cloud source (Do) that does not slip outside and rolls to the base circle (bo) The inner cloud cycloid curve first generated by the tooth line is formed, and the base circle (bi) of the inner rotor Diameter φbi, diameter of first outer cloud source Di, φDi, diameter of first inner cloud source di, φdi, diameter of base circle bo of outer rotor φbo, second outer cloud source (Do When the diameter of) is φDo, the diameter of the second inner rolling circle (do) is φdo, and the eccentricity of the inner rotor and the outer rotor is e,

The relationship between φbi = n · (φDi + φdi), φbo = (n + 1) · (φDo + φdo) is established,

Moreover, φDi + φdi = 2e or φDo + φdo = 2e,

Moreover, you may comprise an internal rotor and an external rotor so that φDo> φDi, φdi> φdo, and (φDi + φdi) <(φDo + φdo) hold.

In this case, in order to determine the tooth shape of the inner rotor and the outer rotor, first, since the rolling distances of the outer and inner cloud sources of the inner rotor and the outer rotor must end in one circumference,

φbi = n · (φDi + φdi) and φbo = (n + 1) · (φDo + φdo) must be satisfied.

Moreover, the shape of the tooth line of the inner rotor formed by the first outer cloud source Di to the shape of the jig of the outer rotor formed by the second outer cloud source Do, and the first inner cloud source di In order to ensure a large backlash formed between the teeth of both rotors during the engagement, the shape of the teeth of the outer rotor formed by the second inner cloud source do with respect to the shape of the jig of the inner rotor formed by

φDo> φDi and φdi> φdo must be satisfied. Here, the backlash is a gap generated between the tooth surface of the outer rotor and the tooth surface opposite to the tooth surface to which the load of the inner rotor is applied during the engagement process.

In addition, since the inner rotor and the outer rotor are engaged,

One of φDi + φdi = 2e and φDo + φdo = 2e must be satisfied.

Further, in the present invention, the inner rotor and the outer rotor are engaged with each other in order to rotate the inner rotor satisfactorily inside the outer rotor, to secure the chip clearance, to optimize the size of the backlash, and to reduce the engagement resistance. In order to prevent the base circle of the inner rotor and the base circle of the outer rotor from contacting each other, the diameter of the base circle of the outer rotor is made larger than before. In other words,

(n + 1) .phibi <n.phibo is satisfied.

Thus, (φDi + φdi) <(φDo + φdo) is induced.

According to this configuration, while the chip clearance between the inner tooth of the inner rotor and the inner tooth of the outer rotor is secured, the circumferential clearance of the base circle between tooth surfaces of each rotor is smaller than before, so that both rotors are less rattling and quieter. It is possible to realize an excellent oil pump. In particular, even if the oil pressure generated in the oil pump rotor assembly is minute and the torque for driving the oil pump rotor assembly is fluctuated, the occurrence of collision between the outer inner tooth and the inner outer tooth can be avoided, so that the oil pump rotor assembly can be avoided. Quietness can be surely realized.

Best Mode for Carrying Out the Invention

EMBODIMENT OF THE INVENTION Hereinafter, 1st Embodiment of this invention is described with reference to FIGS.

In the internal oil pump rotor assembly of the present embodiment shown in Figs. 1 and 2, the cycloid curve generated for the first time by the trajectory of the rolling source in which the tooth surfaces of the outer rotor 10 and the inner rotor 20 roll without slipping on the base circle, respectively. As a cycloidal rotor formed by using, each parameter of both rotors 10 and 20 is set as follows.

Diameter of the base circle Do of the outer rotor 10: φ57.31 [mm]

Diameter of the outer rolling circle Ao of the outer rotor 10: φ2.51 [mm]

Diameter of the inner rolling circle Bo of the outer rotor 10: φ2.70 [mm]

Dimensions of the outer rotor 10 (Zo): 11 [pieces]

Diameter of the base circle Di of the inner rotor 20: φ52.00 [mm]

Diameter of the outer rolling circle Ai of the inner rotor 20: φ2.50 [mm]

Diameter of the inner rolling circle Bi of the inner rotor 20: φ2.76 [mm]

Dimensions of the inner rotor 20 (Zi): 10 [pcs]

Eccentricity (e): 2.60 [mm]

The outer rotor 10 and the inner rotor 20 are internally in contact with the inner tooth and the outer tooth to form a cell R between the surfaces. This cell R is rotated while the volume changes by the rotation of the outer rotor 10 together with the inner rotor 20 rotating in the arrow direction (counterclockwise direction) of FIGS. 1 and 2.

The volume of the cell R becomes the minimum (Vmin) when θ = 0 ° when the rotation angle position θ of the inner rotor 20 is 0 ° and the upper part is 180 °. ), it is gradually enlarged by the rotation of the inner rotor 20 until it becomes the maximum (Vmax) at θ = 198 ° (FIG. 2). The cell R sucks fluid from the suction port formed in the casing (not shown) during this volume expansion process.

Here, the part which closes arbitrary cell R to the circumferential direction, ie, the narrowest part of the interdental gap of both rotors 10 and 20 which form the arbitrary cell R, is inserted into the cell R. This is called interdental clearance.

Among these clearances, the magnitude of the interdental clearance of both rotors 10 and 20 in the cell R (Vmin) with the smallest volume is a, and the rotor 10 in the cell R in the process of expanding the volume. , 20) the interdental clearance of b (FIG. 1) and the interdental clearance of both rotors 10 and 20 in the cell (R; Vmax) where the volume becomes the largest, c (FIG. 2) , The magnitude of the clearance in each cell (R),

a <b <c and a <c.

Further, if the size of the interdental clearance of both rotors 10 and 20 in the cell R in the process of decreasing volume is d,

a <d <c.

3 shows a comparison between the clearance magnitude between the outer rotor 10 and the inner rotor 20 in the internal oil pump rotor assembly of the present embodiment, and the magnitude of the clearance between both rotors in the conventional rotor.

The clearance in the conventional rotor is maximum at the portion where the cell volume is minimum, and gradually decreases with the rotational movement of the cell, and is minimized at the portion where the cell volume is maximum. For this reason, in the conventional rotor, tooth surfaces of both rotors are more likely to contact each other even in the range β or the range γ with a smaller clearance than the engagement effect portion α, so that the mechanical efficiency and friction due to friction may occur.

On the other hand, in this embodiment, as shown in this figure, the inter-gear clearance of both rotors which form the cell R continues to increase gradually in the process of the volume expanding from the minimum (Vmin) to the maximum (Vmax). That is, with respect to the clearance b in the range of 0 <θ <198 °, the clearance size in the rear cell R in the rotational direction is b1 and the magnitude of the clearance in the front cell R in the rotational direction is b2. B1 ≤ b2 is always established.

When the inner rotor 20 rotates from the rotation angle position θ = 0 °, the outer rotor 10 and the inner rotor 20 are engaged with the teeth in the range α shown in FIG. 1 to transmit the rotational force. Also in this range (alpha; engagement influence part), the magnitude | size of clearance increases only as shown in FIG. 3, and does not become smaller than the back side of a rotation direction.

In addition, the clearance in the range (beta) in which the internal rotor 20 has rotated is larger than the range (α), and continues to increase with rotation. Therefore, between the rotors 10 and 20 in this range (beta), compared with the engagement influence part (alpha), it is difficult to contact a cross section between them.

In addition, the clearance in the range (γ: performance influence part) in which the inner rotor 20 is rotated is larger than the range (β), and becomes larger by the front side in the rotational direction, and the rotation angle θ = 198 ° of the inner rotor 20. Is the maximum at. Therefore, between the rotors 10 and 20 in this range (gamma), it is becoming difficult to contact cross sections with each other compared with the range (beta).

And since the clearance c (FIG. 2) when the volume of the cell R reaches the maximum Vmax isolates the suction side and the discharge side of the cell R, the performance is affected, but the same size as before. For this reason, performance does not fall from the conventional point at this point.

After the volume of the cell R reaches the maximum Vmax, the clearance d at the front side in the rotational direction gradually decreases further with the rotation of the inner rotor 20, again at θ = 396 °. Minimum. That is, with respect to the clearance d in the range of 198 <θ <396 °, the magnitude of the clearance in the rear cell R in the rotational direction is d1 and the magnitude of the clearance in the front cell R in the rotational direction is determined. When d2 is set, d1 ≥ d2 is always established.

Therefore, similarly to the side where the volume of the cell R decreases, it is difficult for the cross section to contact the performance-affecting portion γ side more than the engagement- affecting portion α side.

As explained above, in the internal oil pump rotor assembly of this embodiment, the clearance in the engagement influence part (alpha) which transmits rotational force with high efficiency is small, and the clearance in the performance influence part ((gamma)) which cannot transmit rotational force with high efficiency is Since the clearance is increased so as to gradually increase the clearance therebetween, the transmission of the rotational force in contact with the teeth is made in the engagement effect portion (α), and the other surfaces become difficult to contact the teeth, resulting in noise generation and efficiency. The degradation can be avoided.

In addition, when the clearance is increased from a to c, it is more preferable that a <b, b1 <b2, b <c, but a = b, b1 = b2 if a <c is not reduced. Or the part which b = c may generate | occur | produce.

Similarly, it is more preferable that c> d, d1> d2, d> a when the magnitude of the clearance decreases from c to a, but c = d, d1 if it is not increased and c> a. The part where = d2 or d = a may generate | occur | produce.

In the oil pump rotor assembly and the oil pump rotor assembly having the same dimensional specification as in the present embodiment having the above-described dimensional specification, the value of a is preferably in the following range.

0.010 ≤ a ≤ 0.040 [mm]

When a is set smaller than 0.010 mm, the rotation of the oil pump rotor assembly is not smoothly performed, and the function as a pump is impaired. On the contrary, when a is set larger than 0.040 mm, the backlash is large, and the effect of noise reduction is not obtained.

Moreover, it is preferable that the value of said c exists in the following ranges.

0.040 ≤ c ≤ 0.150 [mm]

When c is set smaller than 0.040 mm, the engagement in the engagement position (near 0 ° in FIG. 1) becomes impossible, and when it is set larger than 0.150 mm, the amount of oil leaking from the interdental gap increases, and the pump discharge performance This is significantly worse.

Next, a second embodiment of the present invention will be described with reference to FIGS. 4 to 6. The oil pump rotor assembly shown in FIG. 4 has an internal rotor 110 in which n (n is a natural number, n = 10) outer teeth in this embodiment, and meshes with each outer tooth (n + 1; in the present embodiment). In the present invention, an inner rotor 120 having n + 1 = 11 inner teeth formed therein is provided, and the inner rotor 110 and the outer rotor 120 are housed inside the casing 150.

A plurality of cells C are formed between the inner surfaces of the inner rotor 110 and the outer rotor 120 along the rotational directions of the two rotors 110 and 120. Each cell C is individually contacted by the outer tooth 111 of the inner rotor 110 and the inner tooth 121 of the outer rotor 120 at the front side and the rear side in the rotational directions of both rotors 110 and 120, respectively. It is partitioned, and both sides are partitioned off by the casing 150, thereby forming an independent fluid conveyance chamber. And the cell C rotates with the rotation of both rotors 110 and 120, and repeats increase and decrease of a volume by making one rotation one cycle.

The inner rotor 110 is attached to the rotating shaft and is rotatably supported about the center of the shaft Oi, and is the first outer rolling circle Ai that rolls without sliding externally to the base circle Di of the inner rotor 110. The first external cloud cycloid curve created by the first internal cloud circle Bi, which is rolled without being slipped inscribed to the base circle Di, is used as the tooth shape of the tooth line. It is formed.

The outer rotor 120 is arranged with the shaft center Oo eccentrically (eccentricity e) relative to the shaft center Oi of the inner rotor 110, and rotates inside the casing 150 about the shaft center Oo. The external cloud cycloid curve generated by the second external cloud source Ao, which is supported by the second external cloud source Ao, which is supported by the outer rotor 120 and rolls without sliding outside the base circle Do of the outer rotor 120, is the tooth of the jig. The internal cloud cycloid curve first generated by the second internal cloud source Bo that rolls without sliding inscribed to Do) is formed as a tooth tooth.

ΦDi is the diameter of the base circle Di of the inner rotor 110, φAi is the diameter of the first outer cloud source Ai, φBi is the diameter of the first inner cloud source Bi, the base circle of the outer rotor 120 When the diameter of (Do) is φDo, the diameter of the second outer cloud source (Ao) is φAo, and the diameter of the second internal cloud source (Bo) is φBo, there is a gap between the inner rotor (110) and the outer rotor (120). The following relation holds. In addition, a dimension unit shall be mm (millimeter) here.

First, with respect to the inner rotor 110, the rolling distance of the first outer cloud source Ai and the first inner cloud source Bi must end in one week. That is, in that the integer multiples of the rolling distances of the rolling distances of the first outer cloud source Ai and the first inner cloud source Bi must be equal to the circumference of the base circle Di. ,

π · φDi = n · π · (φAi + φBi), that is, φDi = n · (φAi + φ Bi) ... (Ia)

Similarly, with respect to the outer rotor 120, an integer multiple of the rolling distance of each rolling distance of the second outer cloud source Ao and the second inner cloud source Bo (times of the dimension) is equal to the circumference of the base circle Do. In that it must be the same,

π · φDo = (n + 1) · π · (φAo + φBo), that is, φDo = (n + 1) · (φAo + φBo) ... (Ib)

Next, with respect to the outer rotor 120, a conventional outer rotor ro (second outer cloud source (ao; diameter phi ao), second inner cloud source (bo; diameter φ bo), base circle (do; diameter φ do Based on)), the conditions which determine the tooth shape of the external rotor 120 of this embodiment are demonstrated.

In addition, the outer rotor ro is eccentric with respect to the inner rotor 110 of the present embodiment (arc amount e), and is engaged with a clearance t. The clearance t is a rotational direction from this engagement position when the inner rotor 110 and the outer rotor 120 are disposed so that one tooth line of the inner rotor 110 comes into close contact with one jig of the outer rotor 120. It is the size of the gap formed between one tooth line of the inner rotor 110 and one tooth line of the outer rotor 120 at a position 180 degrees apart.

Here, the following relationship holds.

φdo = φDi · (n + 1) / n ... (II)

φdo = (n + 1) · (φao + φbo) ... (III)

φao = φAi + t / 2 ... (IIIa)

φbo = φBi-t / 2 ... (IIIb)

In addition, with respect to the inner rotor 110 meshed with the outer rotor ro, a general relational expression

φai + φbi = φAi + φBi = 2e ... (1)

φDi = φdo-2e ... (2) is satisfied.

In this embodiment, in order to reduce the clearance t2 of the circumferential direction between the tooth line of the outer rotor 120 and the jig of the inner rotor 110 in the engagement position, and to ensure the clearance t1 of the radial direction. ,

φBo = φbi = φBi ... (Ⅳ)

Moreover, from this Formula (IV) and Formula (1),

φai = φAi ... (3)

In this way, if the internal cloud source of the outer rotor 120 is set,

The clearance (t) with t = (φDo-φBo + φAo)-(φDi + φAi + φAi) is represented by the formulas (1) to (3) and (IV),

t = (φDo-φdo) + (φAo-φai) ... (V).

From the above formulas (Ib), (III), (IV), (V),

Since t = (φAo-φai) · (n + 2) ... (VI),

? Ao =? ai + t / (n + 2).

Here, the diameter phi Do of the base circle Do is first determined. From (Ib), (III)

φDo-φdo = (n + 1) · (φAo + φBo)-(n + 1) · (φao + φbo), and also by (IIIa), (IIIb), (IV)

φDo-φdo = (n + 1) · (φAo-φai) ... (Ⅶ), (VI) from (VI)

Since φDo-φdo = (n + 1) · t / (n + 2), φDo is also defined from (II).

φDo = (n + 1), φDi / n + (n + 1), t / (n + 2) ... (A)

Next, from (Ib)

Since φAo = φDo / (n + 1)-φBo, by (A)

φAo = φDi / n + t / (n + 2)-φBo, and also from (Ia), (IV)

φAo = φAi + t / (n + 2) ... (B)

In summary, the external rotor 120 is

φBo = φbi = φBi ... (Ⅳ)

φDo = (n + 1), φDi / n + (n + 1), t / (n + 2) ... (A)

It is comprised satisfying (phi) Ao = (phi) Ai + t / (n + 2) ... (B).

In Fig. 4, the inner rotor 110 configured to satisfy the above relationship (Di is 52.00 mm for Di, 52.00 mm for the first outer cloud source, φAi = 2.50 mm for the first outer cloud source Ai, and 1st inner cloud source Bi is φBi = 2.70 mm, dimension (n) = 10) and outer rotor 120 (outer diameter φ70 mm, base circle Do is φDo = 57.31 mm, second outer cloud source Ao is φAo = 2.51 mm, first 2 The internal cloud source Bo represents φBo = 2.70 mm) and the oil pump rotor assembly in which clearance (t) = 0.12 mm and eccentricity (e) = 2.6 mm are combined.

In the casing 150, an arc-shaped suction port (not shown) is formed along the cell C in the process of increasing the volume among the cells C formed between the tooth surfaces of both rotors 110 and 120. In addition, an arc-shaped discharge port (not shown) is formed along the cell C in the volume reduction process.

After the volume C is minimized in the middle of the engagement process of the outer tooth 111 and the inner tooth 121, the cell C enlarges the volume to suck the fluid when moving along the suction port, and after the volume reaches the maximum, In addition, when moving along the discharge port, the volume is reduced to discharge the fluid.

In addition, if the clearance t is too small, pressure pulsation occurs in the fluid compressed from the cell C in the volume reduction process, cavitation noise is generated, and the operation sound of the pump is increased. The rotor does not rotate smoothly.

On the other hand, if the clearance t is too large, the pressure pulsation of the fluid does not occur, the operation noise is reduced, and the backlash is increased, so that the sliding resistance between the tooth surfaces is reduced, thereby improving the mechanical efficiency, while the individual cells C ), The liquid tightness in () is impaired, deteriorating pump performance, in particular volumetric efficiency. In addition, since the transmission of the drive torque in the correct engagement position is not performed and the loss of rotation becomes large, the mechanical efficiency also decreases.

Therefore, it is preferable to make clearance t into the range which satisfy | fills 0.03mm <= t <= 0.30mm, It is made into the most preferable 0.12mm in this embodiment.

By the way, in the oil pump rotor assembly comprised as mentioned above, by satisfying the relationship of said Formula (IV), (A), (B), as shown in FIG. 5, the tooth shape of the tooth line of the outer rotor 120 is an internal rotor. It is almost the same as the teeth of the jig of 110. As a result, as shown in FIG. 5, since the clearance t1 in the radial direction at the engaged position is smaller than the conventional t / 2 = 0.06 mm, the clearance t2 in the circumferential direction becomes small, and therefore, the amount at the time of rotation is positive. The impact that the rotors 110 and 120 receive from each other is small. In addition, since the pressure direction at the time of engagement becomes perpendicular to the tooth surface, torque transmission between both rotors 110 and 120 is not slippery and high efficiency, and heat generation and noise due to sliding resistance are reduced.

In addition, also in this embodiment, the magnitude | size of the clearance between the tooth surfaces of both rotors 110 and 120 in the cell C with the minimum volume is a (clearance a, b, c, etc. are not shown), The magnitude of the clearance between the teeth of the both rotors 110 and 120 in the cell C in the process of being enlarged is b, and the teeth between the teeth of the both rotors 110 and 120 in the cell C having the maximum volume. When the magnitude of the clearance is c, a ≤ b ≤ c, a <c, and the clearance b further includes the magnitude of the clearance in the rear cell in the rotational direction b1 and the clearance in the front cell in the rotational direction. The magnitude | size is b2 and b1 <= b2 is satisfied. Further, assuming that the magnitude of the clearance between the teeth of both rotors 110 and 120 in the cell C in the process of decreasing volume is d, a ≦ b ≦ c, a <c, and a ≦ d ≦ c Further, the clearance d satisfies d1? D2 when the magnitude of the clearance in the rear cell in the rotational direction is d1 and the magnitude of the clearance in the front cell in the rotational direction is d2.

6, the graph which compares the noise which generate | occur | produces when the conventional oil pump rotor assembly is used, and the noise which arises when the oil pump rotor assembly which concerns on this embodiment is used is shown. From this graph, it can be seen that the oil pump using the oil pump rotor assembly according to the present embodiment has a lower noise and higher quietness than before.

Next, a third embodiment of the present invention will be described with reference to FIGS. 7 to 10.

The oil pump rotor assembly shown in FIG. 7 has an internal rotor 210 having n (n is a natural number, n = 10) outer teeth in this embodiment, and n + 1 meshing with each outer tooth (in this embodiment, 11) external rotors 220 having inner teeth formed therein, and these inner rotors 210 and outer rotors 220 are housed inside the casing 250.

A plurality of cells C are formed between the teeth of the inner rotor 210 and the outer rotor 220 along the rotational directions of both rotors 210 and 220. Each cell C is individually contacted by the outer tooth 211 of the inner rotor 210 and the inner tooth 221 of the outer rotor 220 at the front side and the rear side in the rotational directions of both rotors 210 and 220, respectively. It is partitioned, and both sides are partitioned off by the casing 250, thereby forming the independent fluid conveyance chamber. The cell C rotates in accordance with the rotation of both rotors 210 and 220, and repeats the increase and decrease of the volume with one rotation as one cycle.

The inner rotor 210 is attached to the rotating shaft and is rotatably supported about the center of the shaft Oi, and is the first outer cloud source Di that rolls without sliding externally to the base circle bi of the inner rotor 210. The first external cloud cycloid curve generated by the tooth curve, and the first internal cloud cycloid curve generated by the first internal cloud source (di) which does not slide inscribed to the base circle (bi). It is formed.

The outer rotor 220 is arranged with the shaft center Oo eccentrically (eccentricity e) relative to the shaft center Oi of the inner rotor 210, and rotates inside the casing 250 about the shaft center Oo. The external cloud cycloid curve firstly supported by the second external cloud source Do, which is supported by the second external cloud source Do, which is rolled on the outside of the base circle bo of the outer rotor 220 without slipping, is formed as a tooth of the jig, and the base circle ( The inner cloud cycloid curve first generated by the second inner cloud source do that does not slide inwardly in a sliding direction is formed as a tooth tooth.

Φbi is the diameter of the base circle bi of the inner rotor 210, φDi is the diameter of the first outer cloud source Di, φdi is the diameter of the first inner cloud source di, and the base circle of the outer rotor 220 is When the diameter of bo is φbo, the diameter of the second external cloud source Do is φDo, and the diameter of the second internal cloud source do is φdo, there is a gap between the inner rotor 210 and the outer rotor 220. The following relation holds. In addition, a dimension unit shall be mm (millimeter) here.

First, with respect to the inner rotor 210, the rolling distances of the first outer cloud source Di and the first inner cloud source di must end one week. That is, in that the integer multiple of the rolling distance of the rolling distance of the first outer cloud source Di and the first inner cloud source di must be equal to the circumference of the base circle bi,

π · φbi = n · π · (φDi + φdi), that is, φbi = n · (φDi + φdi) ... (Ia)

Similarly, with respect to the outer rotor 220, the rolling distances of the second outer cloud source Do and the second inner cloud source do must be equal to the circumference of the base circle bo.

π · φbo = (n + 1) · π · (φDo + φdo) That is, φbo = (n + 1) · (φDo + φdo) ... (Ib)

Moreover, the shape of the tooth line of the inner rotor formed by the first outer cloud source Di to the shape of the jig of the outer rotor formed by the second outer cloud source Do, and the first inner cloud source di In order to ensure a large backlash formed between the teeth of both rotors during the engagement, the shape of the teeth of the outer rotor formed by the second inner cloud source do with respect to the shape of the jig of the inner rotor formed by

φDo> φDi and φdi> φdo must be satisfied. Here, the backlash is a gap generated between the tooth surface of the outer rotor and the tooth surface opposite to the tooth surface to which the load of the inner rotor is applied during the engagement process.

In addition, since the inner rotor and the outer rotor are engaged,

One of φDi + φdi = 2e and φDo + φdo = 2e must be satisfied.

In addition, in the present invention, the inner rotor 210 is rotated satisfactorily inside the outer rotor 220, while the chip clearance is secured, the backlash is optimized, and the inner rotor is reduced in order to reduce the engagement resistance. The base circle of the outer rotor 220 such that the base circle bi of the inner rotor 210 and the base circle bo of the outer rotor 220 do not come into contact with each other in the engaged position of the 210 and the outer rotor 220. The diameter of bo is enlarged. In other words,

(n + 1) .phibi <n.phibo is satisfied.

From this formula and formulas (Ia) and (Ib), (φDi + φdi) <(φDo + φdo) is obtained. In addition, the above-mentioned engagement position means the position when the tooth line of the outer side tooth 221 and the jig | tool of the inner side tooth 211 were opposite.

only,

The inner rotor 210 and the outer rotor 220 are configured to satisfy 0.005 mm ≤ (φDo + φdo)-(φDi + φdi) ≤ 0.070 mm (mm: millimeter) ... (Ic) (hereinafter, ( φDo + φdo)-(φDi + φdi) is simply called A).

In the present embodiment, the inner rotor 210 configured to satisfy the above relationship (the base source bi is φbi = 65.00 mm, the first external cloud source Di is φDi = 3.90 mm, the first internal cloud source) (di) φdi = 2.60 mm, dimension n = 10) and outer rotor 220 (outer diameter φ87.0 mm, base circle bo φbo = 71.599 mm, second outer cloud circle Do is φDo = 3.9135 mm and the 2nd internal cloud source do (phi) = 2.5955mm are combined by the eccentricity (e) = 3.25 mm, and comprise the oil pump rotor assembly. In addition, in this embodiment, the tooth width (size of a rotating shaft direction) of both rotors is set to 10 mm. Further, the first external cloud source Di is φDi = 3.90 mm, the first internal cloud source di is φdi = 2.60 mm, the second external cloud source Do is φDo = 3.9135 mm, and the second internal cloud source ( do) is phido = 2.5955mm, and A = 0.009mm by this (refer FIG. 8).

In the casing 250, an arc-shaped suction port (not shown) is formed along the cell C in the process of increasing volume among the cells C formed between the tooth surfaces of both rotors 210 and 220. In addition, an arc-shaped discharge port (not shown) is formed along the cell C in the volume reduction process.

After the volume C is minimized in the middle of the engagement process of the outer tooth 211 and the inner tooth 221, the cell C enlarges the volume to suck the fluid when moving along the suction port, and after the volume reaches the maximum, In addition, when moving along the discharge port, the volume is reduced to discharge the fluid.

In addition, if A is too small, the chip clearance and the backlash cannot be optimized, and the engagement noise between the inner tooth 211 and the outer tooth 221 cannot be reduced.

On the other hand, if A is too large, the difference between the length of teeth (the size of teeth in the normal direction of the base circle) of the inner tooth 211 and the outer inner teeth 221, or the difference of the thickness (the size of teeth in the circumferential direction of the base circle) Optimalization can not be achieved, and a part where backlash disappears may occur during rotation of the inner and outer rotors 210 and 220. In this case, it is impossible to realize good rotation of both rotors, resulting in deterioration of mechanical efficiency and generation of noise due to collision between the external teeth 211 and the internal teeth 221.

Therefore, it is preferable to make A into the range which satisfy | fills 0.005 mm <= A <0.070mm, and it is set as 0.009 mm which is the most preferable in this embodiment.

In the oil pump rotor assembly configured as described above, the teeth of the teeth of the outer rotor 220 become substantially the same as the teeth of the teeth of the inner rotor 210. Accordingly, as shown in Fig. 8, since the chip clearance tt is secured in the same manner as in the prior art, since the circumferential clearance ts of the base circle becomes small, both rotors 210 and 220 receive each other at the time of rotation. The impact is small. Therefore, in particular, even if the hydraulic pressure generated in the oil pump rotor assembly is minute and the torque for driving the oil pump rotor assembly is varied, the occurrence of collision between the outer inner tooth 221 and the inner outer tooth 211 can be avoided. As a result, the quietness of the oil pump rotor assembly can be surely realized. In addition, since the pressure direction at the time of engagement becomes perpendicular to the tooth surface, torque transmission between both rotors 210 and 220 is not slippery and high efficiency, and heat generation and noise due to sliding resistance are reduced.

9, backlash (broken line in FIG. 9) for every rotation angle position of the internal rotor in the conventional oil pump rotor assembly, and every rotation angle position of the internal rotor in the oil pump rotor assembly according to the present embodiment. The graph which compares backlash (solid line in FIG. 9) is shown. From this graph, the oil pump rotor assembly according to the present embodiment can make the backlash smaller than before in the process of increasing and decreasing the engagement position and the volume of the cell C, and the volume of the cell C. It can be seen that the backlash equivalent to the conventional one can be obtained at this maximum position. Therefore, in the latter case, it can be seen that the liquid-tightness of the cell C when the volume becomes maximum can be ensured, and the conveyance efficiency can be maintained in the same manner as before. In addition, in FIG. 9, the rotation angle of the internal rotor described only backlash from 0 ° to 198 ° is the same as the change of backlash from 198 ° to 0 ° shown in FIG. 9 from 198 ° to 396 °. (Symmetry) The description is omitted for the purpose of symmetry.

10, the graph which compares the noise which generate | occur | produces when the conventional oil pump rotor assembly is used, and the noise which arises when the oil pump rotor assembly which concerns on this embodiment is used is shown. From this graph, the oil pump rotor assembly according to the present embodiment has a smaller backlash in the process of increasing and decreasing the engagement position and the volume of the cell C, as shown in FIG. It can be seen that the noise can be reduced and the quietness can be improved.

In addition, each structural member shown in the above embodiment, its various shapes, a combination, etc. can be variously changed based on a design request in the range which does not deviate from the meaning of this invention as an example.

For example, for both rotors constituting the internal oil pump rotor assembly, in the above embodiment, both rotors were so-called cycloid rotors having a tooth surface shape formed using a cycloid curve, but a trajectory center having a center on the trocoid curve was used as this trocoid. Any tooth shape as long as it satisfies the above-described clearance conditions, such as an inner rotor having a tooth shape formed by using an envelope in the case of moving along a curve, and a so-called trocoid rotor composed of an outer rotor engaged with the inner rotor. It may be a rotor having a.

As described above, according to the internal oil pump rotor assembly according to the present invention, since the clearance between both rotors forming the cell becomes the minimum at the engaging portion, it continues to increase and become the maximum, so that the backlash at the engaging portion is increased. Is small and clearance in the part which does not contribute to the engagement is secured.

In addition, according to another internal oil pump rotor assembly according to the present invention, since the clearance between both rotors forming the cell is maximized, it is continuously reduced and minimized at the engaging portion, so that the backlash at the engaging portion is small. In this case, clearance is secured at the part which does not contribute to the engagement.

Therefore, the outer tooth engages the inner tooth at the portion with the smallest sliding component, and the rotational force is transmitted, and the engagement between the outer tooth and the inner tooth is less likely to occur at the portion with the large sliding component, so that the noise and friction (friction) are small, resulting in high mechanical efficiency. A good internal oil pump can be realized.

According to another internal oil pump rotor assembly according to the present invention, the cycloid rotor formed by using the conventionally used cycloid curve and the trocoid rotor formed by using the trocoid curve can be made quieter and lower friction, resulting in higher performance. It is possible to realize an internal oil pump.

Claims (8)

The inner rotor having n (n is a natural number) outer teeth and the outer rotor having (n + 1) inner teeth mesh with each other and the fluid is rotated during the rotation of the inner and outer rotors according to the volume change of a plurality of cells formed between the tooth surfaces. An oil pump rotor assembly constituting an oil pump for sucking and discharging oil, In the cell where the volume is the minimum, the size of the interdental clearance of both rotors is a, and the size of the interdental clearance of both rotors in the cell in the process of expanding the volume is b. Let c be the magnitude of the interplanar clearance of both rotors, a ≤ b ≤ c, a <c, and further, the clearance b is defined as b1 for the clearance in the rear cell in the rotational direction and b2 for the clearance in the front cell in the rotational direction, An oil pump rotor assembly characterized by satisfying b1 ≤ b2. An oil pump rotor assembly according to claim 1, D is the magnitude of interdental clearance of both rotors in the cell in the process of volume reduction, a ≤ b ≤ c, a <c, and a ≤ d ≤ c, and further, the clearance d represents the magnitude of the clearance in the rear cell in the rotational direction d1 and the clearance in the front cell in the rotational direction Let d be the size of d2, An oil pump rotor assembly characterized by satisfying d1 ≥ d2. The inner rotor having n (n is a natural number) outer teeth and the outer rotor having (n + 1) inner teeth mesh with each other and the fluid is rotated during the rotation of the inner and outer rotors according to the volume change of a plurality of cells formed between the tooth surfaces. An oil pump rotor assembly constituting an oil pump for sucking and discharging oil, Oil tooth rotor assembly, characterized in that the inter-gear clearance of both rotors forming the cell in the process of volume expansion from minimum to maximum gradually increases with the rotational movement of the cell. The oil pump rotor assembly according to claim 3, wherein the inter-gear clearance of both rotors forming the cell in the process of decreasing in volume from maximum to minimum is gradually reduced with rotational movement of the cell. Rotor assembly. An oil pump rotor assembly according to any one of claims 1 to 4, And the tooth surfaces of the outer rotor and the inner rotor are each formed using a cycloid curve first generated by the trajectory of the rolling circle rolling without slipping on the base circle. An oil pump rotor assembly according to any one of claims 1 to 4, The tooth surface of the inner rotor is formed by using a trocoid envelope first generated by the envelope when the ruler circle having a center on the trocoid curve is moved along the trocoid curve, and the tooth of the outer rotor is the same as the trajectory circle. An oil pump rotor assembly, characterized in that formed using an arc of diameter. An oil pump rotor assembly according to claim 1 or 3, The teeth of the inner rotor are toothed teeth of the outer cloud cycloid curve which is first generated by the rolling first outer rolling circle Ai, which does not slip around the base circle Di, and slides inward to the base circle Di. The second external cloud source, which is formed by the internal cloud cycloid curve first generated by the first internal cloud source Bi, which is rolled freely as a tooth shape, and the tooth of the external rotor is rolled without sliding around the base circle Do. The outer cloud cycloid curve generated by (Ao) is the tooth of the jig, and the inner cloud cycloid curve first generated by the second inner cloud circle (Bo) which rolls inscribed to the base circle (Do) does not slip. It is formed as a tooth shape, ΦDi is the diameter of the base circle Di of the inner rotor, φAi is the diameter of the first outer cloud source Ai, φBi is the diameter of the first inner cloud source Bi, the diameter of the base circle Do of the outer rotor φDo, the diameter of the second outer cloud source Ao is φAo, the diameter of the second inner cloud source Bo is φBo, and the size of the gap between the tooth line of the inner rotor and the tooth line of the outer rotor is t (≠ 0). time, While φBo = φBi, φDo = φDi · (n + 1) / n + t · (n + 1) / (n + 2) An oil pump rotor assembly comprising an inner rotor and an outer rotor satisfying φAo = φAi + t / (n + 2). An oil pump rotor assembly according to claim 1 or 3, The inner rotor is toothed with an external cloud cycloid curve generated by the first external cloud source Di, which rolls without sliding externally to the base circle bi, and slips inwardly on the base circle bi. The inner cloud cycloid curve first generated by the first rolling cloud source (di), which is rolled free, The outer rotor is toothed with the outer cloud cycloid curve generated by the second outer cloud source Do that does not slide outside the base circle bo and rolls, and slides inward to the base circle bo. It is formed by the tooth cloud of the internal cloud cycloid curve first generated by the second internal cloud source (do) rolling without The diameter of the base circle bi of the inner rotor is φbi, the diameter of the first outer cloud source Di is φDi, the diameter of the first inner cloud source di is φdi, and the diameter of the base circle bo of the outer rotor is When φbo, the diameter of the second outer cloud source (Do) is φDo, the diameter of the second inner cloud source (do) is φdo, and the eccentricity of the inner rotor and the outer rotor is e, The relationship between φbi = n · (φDi + φdi), φbo = (n + 1) · (φDo + φdo) is established, Moreover, φDi + φdi = 2e or φDo + φdo = 2e, An oil pump rotor assembly comprising an inner rotor and an outer rotor satisfying φDo> φDi, φdi> φdo, and (φDi + φdi) <(φDo + φdo).