EP1559912B1 - Assemblage de rotor de pompe à huile à engrenage interne - Google Patents

Assemblage de rotor de pompe à huile à engrenage interne Download PDF

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Publication number
EP1559912B1
EP1559912B1 EP03769987.3A EP03769987A EP1559912B1 EP 1559912 B1 EP1559912 B1 EP 1559912B1 EP 03769987 A EP03769987 A EP 03769987A EP 1559912 B1 EP1559912 B1 EP 1559912B1
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EP
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Prior art keywords
rotor
rolling
circle
clearance
ødo
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EP03769987.3A
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German (de)
English (en)
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EP1559912A4 (fr
EP1559912A1 (fr
Inventor
Katsuaki c/o Mitsubishi Materials Corp. Hosono
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Diamet Corp
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Diamet Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-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
    • F04C2/102—Rotary-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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels

Definitions

  • the present invention relates to an oil pump rotor assembly used in an internal gear type oil pump which draws and discharges fluid by volume change of cells formed between an inner rotor and an outer rotor.
  • an internal gear type oil pump includes an outer rotor having internal teeth, an inner rotor having external teeth which are engageable with the internal teeth, and a casing in which a suction port for drawing fluid and a discharge port for discharging fluid are formed.
  • the inner rotor is rotated so that the outer rotor is rotated while the external teeth engage the internal teeth, which produces changes in the volumes of cells formed between the inner rotor and the outer rotor, and thereby fluid is drawn and is discharged.
  • Each of the cells is independently delimited at a front portion and at a rear portion as viewed in the direction of rotation by the external teeth of the inner rotor and the internal teeth of the outer rotor.
  • the volume of each of the cells is minimized at a rotational position in which one of the tooth tips of the external teeth of the inner rotor positionally coincides with one of the tooth spaces of the internal teeth of the outer rotor, and, from this rotational position, the cell draws fluid as the volume thereof increases while moving over the suction port.
  • each of the cells is maximized at a rotational position in which one of the tooth spaces of the external teeth of the inner rotor positionally coincides with one of the tooth spaces of the internal teeth of the outer rotor, and, from this rotational position, the cell discharges fluid as the volume thereof decreases while moving over the discharge port.
  • the inner rotor is driven so as to rotate, and the outer rotor is rotated because tooth surfaces of the external teeth push tooth surfaces of the internal teeth.
  • the rotational force is transmitted in the direction substantially perpendicular to the tooth surfaces when the teeth are placed near a position at which the volume of the cell is minimized.
  • the rotational force is not transmitted in the direction substantially perpendicular to the tooth surfaces, and components of slip and friction are dominant.
  • the present invention was conceived in view of the above circumstances, and an object of the present invention is to provide an internal gear type oil pump rotor assembly which stably rotates without emitting excessive noise.
  • the present invention provides an oil pump rotor assembly including: an inner rotor having "n" external teeth ("n” is a natural number); and an outer rotor having (n+1) internal teeth which are engageable with the external teeth, wherein the oil pump rotor assembly is used in an oil pump which, during rotation of the inner and outer rotors, draws and discharges fluid by volume change of cells formed between the inner rotor and the outer rotor, wherein when a clearance, which is defined between the teeth of the inner and outer rotors that together form one of the cells 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 that together form one of the cells whose volume is increasing during rotation of the inner and outer rotors, is designated as "b”, and a clearance, which is defined between the teeth of the inner and outer rotors that together form one of the cells which has the maximum volume among the cells, is designated as "c”, the following ine
  • the clearance which is defined between the teeth of the inner and outer rotors that together form one of the cells, may gradually decrease as the cell rotationally moves from a position at which the volume of the cell is maximized to a position at which the volume of the cell is minimized.
  • the clearance between the rotors that together form the cell is minimized at an engagement region, and then the clearance is continuously increased, without decreasing, to a maximum size, backlash at a position at which the teeth engage each other is minimized, and a sufficient clearance is ensured at a rotational position at which the teeth do not contribute to engagement.
  • the external teeth engage the internal teeth at a position at which a slip component is minimized so as to transmit rotational force, and the external teeth and the internal teeth do not contribute to transmitting rotational force at a position at which a slip component is increased. Therefore, an internal gear type oil pump rotor assembly can be obtained which does not emit excessive noise while having low levels of friction and high mechanical efficiency.
  • the tooth surfaces of the inner and outer rotors may be respectively formed using cycloid curves which are formed by rolling respective rolling circles along respective base circles without slip.
  • the tooth surfaces of the inner rotor may be formed using a trochoid envelope curve which is formed by moving a trajectory circle, whose center is positioned on a trochoid curve, along the trochoid curve, and the tooth tips of the outer rotor may be formed using an arc having the same radius as that of the trajectory circle.
  • a cycloid type rotor assembly which is formed using cycloid curves and a trochoid type rotor assembly which is formed using trochoid curves, both of which have been conventionally used, can be made so as to emit less noise and to have lower levels of friction.
  • the tooth tip profile of the inner rotor which is formed by the first circumscribed-rolling circle Di with respect the tooth space profile of the outer rotor which is formed by the second circumscribed-rolling circle Do, and the tooth tip profile of the outer rotor which is formed by the second inscribed-rolling circle "do" with respect to the tooth space profile of the inner rotor which is formed by the first inscribed-rolling circle “di” are determined such that the following inequalities are satisfied: ⁇ Do > ⁇ Di ; and ⁇ di > ⁇ do , so that a large backlash, which is defined between the tooth surfaces of the rotors during engagement, is ensured.
  • the backlash is a gap formed between the tooth surface of the inner rotor, which is opposite to the tooth surface to which force is applied during engagement, and the tooth surface of the outer rotor.
  • the diameter of the base circle of the outer rotor is made greater than that in a conventional case so that the base circle of the inner rotor does not contact the base circle of the outer rotor at the engagement region at which the inner rotor engages the outer rotor, i.e., the following inequality is satisfied: n + 1 ⁇ ⁇ bi ⁇ n ⁇ ⁇ bo .
  • FIGS. 1 to 3 A first embodiment of the present invention will be explained below with reference to FIGS. 1 to 3 .
  • the internal gear type oil pump rotor assembly shown in FIGS. 1 and 2 is a cycloid type rotor assembly in which teeth of an outer rotor 10 and teeth of an inner rotor 20 are formed using respective cycloid curves, each of which is formed by rolling a rolling circle along a base circle.
  • the parameters of the rotors 10 and 20 are set as follows:
  • the inner rotor 20 is inscribed in the outer rotor 10 while the external teeth of the inner rotor 20 engage the internal teeth of the outer rotor 10 so as to form cells R between the teeth.
  • Each of the cells R rotationally moves while the volume thereof changes when the inner rotor 20 along with the outer rotor rotate in the direction indicated by the arrows in FIGS. 1 and 2 (in the counterclockwise direction).
  • Each of the cells R draws fluid through a suction port formed in a casing (not shown) during the process in which the volume of the cell R increases.
  • an inter-tooth clearance is defined as the region which closes one of the cells R in the circumferential direction, i.e., the region at which the gap between the teeth of the rotors 10 and 20 that together form the cell R is minimized.
  • an inter-tooth clearance which is defined between the teeth of the rotors 10 and 20 that together form one of the cells R which has the minimum volume (Vmin) among the cells
  • an inter-tooth clearance which is defined between the teeth of the rotors 10 and 20 that together form one of the cells R whose volume is increasing during rotation of the rotors 10 and 20, is designated as "b" ( FIG.
  • FIG 3 The comparison between the clearance between the outer rotor 10 and the inner rotor 20 in the internal gear type oil pump rotor assembly of the present embodiment and that between the rotors in a conventional rotor assembly is shown in FIG 3 .
  • the clearance in the conventional rotor assembly is maximized where the volume of the cell is minimized, gradually decreases as the cell rotates, and is minimized where the volume of the cell is maximized. Accordingly, in the conventional rotor assembly, the teeth of the rotors tend to contact each other even in zones beta and gamma in which the clearance is smaller than that in an engagement effect zone alpha ; therefore, due to friction, mechanical efficiency may be decreased, and excessive noise may be emitted.
  • the inter-tooth clearance between the rotors that together form the cell R gradually and continuously increases during the process in which the volume of the cell R increases from the minimum volume (Vmin) to the maximum volume (Vmax), as shown in FIG 3 .
  • the teeth of the outer rotor 10 and the teeth of the inner rotor 20 engage each other so as to transmit rotational force in the zone a shown in FIG. 1 .
  • the clearance continuously increases as shown in FIG. 3 , i.e., the clearance in the cell R positioned forward as viewed in the direction of rotation is always greater than that in the cell R positioned backward.
  • the clearance in the zone ⁇ in which the inner rotor 20 has further rotated is greater than that in the zone a, and the clearance increases further. Accordingly, the teeth of the rotors 10 and 20 tend not to contact each other in the zone P when compared with the engagement effect zone a.
  • the clearance "c” ( FIG. 2 ), which is the clearance when the volume of the cell R is maximized (Vmax), may affect the performance of the pump because the cell R is at a transition point from drawing to discharging, and the clearance "c" is substantially the same as that in the conventional rotor assembly; therefore, performance of the pump is not degraded.
  • the clearance "d" ( FIG 1 ) in the cell R which is forwarded from the cell R having the maximum volume (Vmax)
  • the teeth tend not to contact each other in the performance effect zone ⁇ when compared with the engagement effect zone a.
  • the clearance is made small in the engagement effect zone a in which the rotational force is efficiently transmitted, the clearance is made large in the performance effect zone ⁇ in which the rotational force cannot be efficiently transmitted, and the clearance is made to gradually increase between the zones a and ⁇ ; therefore, the rotational force is transmitted by the contact between the teeth mainly in the engagement effect zone a, and the teeth tend not to contact each other in other zones. As a result, excessive noise and degradation of mechanical efficiency can be prevented.
  • the value "a" be in the following range: 0.010 mm ⁇ a ⁇ 0.040 mm .
  • the oil pump rotor assembly may not rotate smoothly, and the function as a pump may be lost.
  • the value "a” is set to be greater than 0.040 mm, backlash may become large, and operation noise may not be reduced.
  • the value "c" be in the following range: 0.040 mm ⁇ a ⁇ 0.150 mm .
  • the inner rotor 110 and the outer rotor 120 are accommodated in a casing 150.
  • each of the cells C is delimited at a front portion and at a rear portion as viewed in the direction of rotation of the inner rotor 110 and outer rotor 120 by contact regions between the external teeth 111 of the inner rotor 110 and the internal teeth 121 of the outer rotor 120, and is also delimited at either side portions by the casing 150, so that an independent fluid conveying chamber is formed.
  • Each of the cells C moves while the inner rotor 110 and outer rotor 120 rotate, and the volume of each of the cells C cyclically increases and decreases so as to complete one cycle in a rotation.
  • the inner rotor 110 is mounted on a rotational axis so as to be rotatable about an axis Oi.
  • Each of the tooth profiles of the inner rotor 110 is formed such that the tooth tip profile thereof is formed using an epicycloid curve which is formed by rolling a first circumscribed-rolling circle Ai along a base circle Di of the inner rotor 110 without slip, and the tooth space profile thereof is formed using a hypocycloid curve which is formed by rolling a first inscribed-rolling circle Bi along the base circle Di without slip.
  • the outer rotor 120 is mounted so as to be rotatable, in the casing 150, about an axis Oo which is disposed so as to have an offset (the eccentricity distance is "e") from the axis Oi.
  • Each of the tooth profiles of the outer rotor 120 is formed such that the tooth space profile thereof is formed using an epicycloid curve which is formed by rolling a second circumscribed-rolling circle Ao along a base circle Do of the outer rotor 120 without slip, and the tooth tip profile thereof is formed using a hypocycloid curve which is formed by rolling a second inscribed-rolling circle Bo along the base circle Do without slip.
  • the outer rotor “ro” engages the inner rotor 110 according to the present embodiment with a clearance of "t” while being disposed with respect to the inner rotor 110 so as to have an offset (the eccentricity distance is “e”).
  • the clearance "t” is a gap formed between one of the tooth tips of the inner rotor 110 and one of the tooth tips of the outer rotor 120 at a position which is away from an engagement region by 180° along the direction of rotation when the inner rotor 110 and the outer rotor 120 are disposed such that one of the tooth tips of the inner rotor 110 directly contacts one of the tooth spaces of the outer rotor 120 in the engagement region.
  • ⁇ Do n + 1 ⁇ ⁇ Di / n + n + 1 ⁇ t / n + 2 .
  • FIG. 4 shows the oil pump rotor assembly in which the inner rotor 110 is formed so as to satisfy the above relationship (the diameter ⁇ Di of the base circle Di is 52.00 mm, the diameter ⁇ Ai of the first circumscribed-rolling circle Ai is 2.50 mm, the diameter ⁇ Bi of the first inscribed-rolling circle Bi is 2.70 mm, and the number of teeth Zi, i.e., "n" is 10), the outer rotor 120 is formed so as to satisfy the above relationship (the outer diameter thereof is 70 mm, the diameter ⁇ Do of the base circle Do is 57.31 mm, the diameter ⁇ Ao of the second circumscribed-rolling circle Ao is 2.51 mm, and the diameter ⁇ Bo of the second inscribed-rolling circle Bo is 2.70 mm), and the rotors are combined with the clearance "t" of 0.12 mm, and the eccentricity distance "e” of 2.6 mm.
  • the outer rotor 120 is formed so as to satisfy the above relationship (the outer diameter
  • a suction port having a curved shape (not shown) is formed in a region along which each of the cells C, which are formed between the rotors 110 and 120, moves while gradually increasing the volume thereof, and a discharge port having a curved shape (not shown) is formed in a region along which each of the cells C moves while gradually decreasing the volume thereof.
  • Each of the cells C draws fluid as the volume thereof increases when the cell C moves over the suction port after the volume of the cell C is minimized in the engagement process between the external teeth 111 and the internal teeth 121, and the cell C discharges fluid as the volume thereof decreases when the cell C moves over the discharge port after the volume of the cell C is maximized.
  • the clearance "t” is preferably set so as to satisfy the following inequalities: 0.03 ⁇ mm ⁇ t ⁇ 0.30 ⁇ mm .
  • the clearance "t” is set to be 0.12 mm, which is considered to be the most preferable.
  • the profile of the tooth tip of the outer rotor 120 and the profile of the tooth space of the inner rotor 110 have substantially the same shape with respect to each other, as shown in FIG. 5 .
  • the circumferential clearances t2 in the engagement phase can be decreased while ensuring the radial clearance t1 such that t/2 is 0.06 mm, which is the same as in conventional rotors; therefore, engagement impacts between the rotors 110 and 120 during rotation are decreased.
  • transmission of torque between the rotors 110 and 120 is performed with high efficiency without slip, and heat generation and noise due to sliding resistance can be reduced.
  • a clearance which is defined between the teeth of the inner and outer rotors 110 and 120 that together form one of the cells which has the minimum volume among the cells
  • a clearance which is defined between the teeth of the inner and outer rotors 110 and 120 that together form one of the cells whose volume is increasing during rotation of the inner and outer rotors 110 and 120
  • c clearance, which is defined between the teeth of the inner and outer rotors 110 and 120 that together form one of the cells which has the maximum volume among the cells
  • a clearance which is defined between the teeth of the inner and outer rotors 110 and 120 that together form one of the cells whose volume is decreasing during rotation of the inner and outer rotors 110 and 120, is designated as "d"
  • the following inequalities are satisfied: a ⁇ b ⁇ c , a ⁇ c , and a ⁇ d ⁇ c .
  • FIG 6 is a graph showing comparison between noise from a pump incorporating a conventional oil pump rotor assembly and noise from another pump incorporating the oil pump rotor assembly according to the present embodiment. According to the graph, noise from the oil pump incorporating the oil pump rotor assembly according to the present embodiment is less than that of the conventional oil pump rotor assembly, i.e., the oil pump rotor assembly of the present embodiment is quieter.
  • the inner rotor 210 and the outer rotor 220 are accommodated in a casing 250.
  • each of the cells C is delimited at a front portion and at a rear portion as viewed in the direction of rotation of the inner rotor 210 and outer rotor 220 by contact regions between the external teeth 211 of the inner rotor 210 and the internal teeth 221 of the outer rotor 220, and is also delimited at either side portions by the casing 250, so that an independent fluid conveying chamber is formed.
  • Each of the cells C moves while the inner rotor 210 and outer rotor 220 rotate, and the volume of each of the cells C cyclically increases and decreases so as to complete one cycle in a rotation.
  • the inner rotor 210 is mounted on a rotational axis so as to be rotatable about an axis Oi.
  • Each of the tooth profiles of the inner rotor 210 is formed such that the tooth tip profile thereof is formed using an epicycloid curve which is formed by rolling a first circumscribed-rolling circle Di along a base circle "bi" of the inner rotor 210 without slip, and the tooth space profile thereof is formed using a hypocycloid curve which is formed by rolling a first inscribed-rolling circle "di" along the base circle "bi” without slip.
  • the outer rotor 220 is mounted so as to be rotatable, in the casing 250, about an axis Oo which is disposed so as to have an offset (the eccentricity distance is "e") from the axis Oi.
  • Each of the tooth profiles of the outer rotor 220 is formed such that the tooth space profile thereof is formed using an epicycloid curve which is formed by rolling a second circumscribed-rolling circle Do along a base circle "bo" of the outer rotor 220 without slip, and the tooth tip profile thereof is formed using a hypocycloid curve which is formed by rolling a second inscribed-rolling circle “do" along the base circle “bo” without slip.
  • the tooth tip profile of the inner rotor which is formed by the first circumscribed-rolling circle Di with respect the tooth space profile of the outer rotor which is formed by the second circumscribed-rolling circle Do, and the tooth tip profile of the outer rotor which is formed by the second inscribed-rolling circle "do" with respect the tooth space profile of the inner rotor which is formed by the first inscribed-rolling circle "di” are determined such that the following inequalities are satisfied: ⁇ Do > ⁇ Di ; and ⁇ di > ⁇ do , so that a large backlash which is defined between the tooth surfaces of the rotors during engagement is ensured.
  • the backlash is a gap formed between the tooth surface of the inner rotor, which is opposite to the tooth surface to which force is applied during engagement, and the tooth surface of the outer rotor.
  • the diameter of the base circle "bo" of the outer rotor 220 is made greater than that in a conventional case so that the base circle "bi" of the inner rotor 210 does not contact the base circle "bo" of the outer rotor 220 at the engagement region at which the inner rotor 210 engages the outer rotor 220, i.e., the following inequality is satisfied: n + 1 ⁇ ⁇ bi ⁇ n ⁇ ⁇ bo .
  • the above-mentioned engagement region is a region at which the tooth tip of one of the internal teeth 221 of the outer rotor 220 directly faces one of the tooth spaces between the external teeth 211 of the inner rotor 210.
  • the inner rotor 210 and the outer rotor 220 are formed such that the following inequalities are satisfied: 0.005 mm ⁇ ⁇ ⁇ Do + ⁇ do - ⁇ ⁇ Di + ⁇ di ⁇ 0.070 mm ( hereinafter , ⁇ ⁇ Do + ⁇ do - ⁇ ⁇ Di + ⁇ di is (hereinafter, ( ⁇ Do+ ⁇ do)-( ⁇ Di+ ⁇ di) is simply designated as "A").
  • the inner rotor 210 (the diameter ⁇ bi of the base circle is 65.00 mm, the diameter ⁇ Di of the first circumscribed-rolling circle Di is 3.90 mm, the diameter ⁇ di of the first inscribed-rolling circle “di” is 2.60 mm, and the number of teeth "n” is 10), and the outer rotor 220 (the outer diameter thereof is 87.0 mm, the diameter ⁇ bo of the base circle “bo” is 71.599 mm, the diameter ⁇ Do of the second circumscribed-rolling circle Do is 3.9135 mm, and the diameter ⁇ do of the second inscribed-rolling circle “do” is 2.5955 mm), each of which is formed so as to satisfy the above-mentioned conditions, are combined with an eccentricity distance "e" of 3.25 mm to form the oil pump rotor assembly.
  • the width of the teeth of the rotors (the size in the direction of the rotational axis) is set to be 10 mm. Because the diameter ⁇ di of the first inscribed-rolling circle “di” is set to be 2.60 mm, the diameter ⁇ Do of the second circumscribed-rolling circle Do is set to be 3.9135 mm, and the diameter ⁇ do of the second inscribed-rolling circle “do” is set to be 2.5955 mm, "A" is 0.009 mm (refer to FIG. 8 ).
  • a suction port having a curved shape (not shown) is formed in a region along which each of the cells C, which are formed between the rotors 210 and 220, moves while gradually increasing the volume thereof, and a discharge port having a curved shape (not shown) is formed in a region along which each of the cells C moves while gradually decreasing the volume thereof.
  • Each of the cells C draws fluid as the volume thereof increases when the cell C moves over the suction port after the volume of the cell C is minimized in the engagement process between the external teeth 211 and the internal teeth 221, and the cell C discharges fluid as the volume thereof decreases when the cell C moves over the discharge port after the volume of the cell C is maximized.
  • "A” be set in the range from 0.005 mm to 0.070 mm, and in this embodiment, "A” is set to be 0.009 mm.
  • the tooth tip profile of the outer rotor 220 substantially coincides with the tooth space profile of the inner rotor 210.
  • the circumferential clearances "ts" along the base circle are made small while the tip clearance "tt” is maintained as in a conventional case; therefore, the impacts applied to the rotors 210 and 220 during rotation become small. Accordingly, impacts between the internal teeth 221 of the outer rotor 220 and external teeth 211 of the inner rotor 210 can be prevented even when driving torque for the oil pump rotor assembly changes while oil pressure in the oil pump rotor assembly is low; therefore, quietness of the oil pump rotor assembly can be ensured. Moreover, because the rotational force is transmitted in the direction substantially perpendicular to the tooth surfaces, torque is transmitted between the rotors 210 and 220 without slip and with high efficiency, heat generation and noise due to sliding friction can be reduced.
  • FIG 9 is a graph showing comparison between a backlash (shown by a broken line in FIG 9 ) of a conventional oil pump rotor assembly with respect to the rotational position of the inner rotor and a backlash (shown by a solid line in FIG 9 ) of the oil pump rotor assembly of the present embodiment with respect to the rotational position of the inner rotor.
  • the backlash in the engagement region, the backlash in the process in which the volume of the cell C increases, and the backlash in the process in which the volume of the cell C decreases, are smaller than those in the conventional oil pump rotor assembly, and the backlash at a position at which the volume of the cell C is maximized is substantially equal to that in the conventional oil pump rotor assembly. Accordingly, in the oil pump rotor assembly of the present embodiment, because the fluidtight performance of the cell C having the maximum volume can be ensured, and fluid conveying efficiency can be maintained substantially the same as in a conventional pump. In FIG.
  • FIG 10 is a graph showing comparison between noise from an oil pump incorporating a conventional oil pump rotor assembly and noise from the oil pump incorporating the oil pump rotor assembly of the present embodiment.
  • the oil pump rotor assembly of the present embodiment makes it possible to reduce noise when compared with the conventional oil pump rotor assembly, i.e., a quiet oil pump can be made, because the backlash in the engagement region, the backlash in the process in which the volume of the cell C increases, and the backlash in the process in which the volume of the cell C decreases, are smaller than those in the conventional oil pump rotor assembly as shown in FIG 9 .
  • the rotors that form the internal gear type oil pump rotor assembly are so-called cycloid rotors having teeth which are formed using cycloid curves; however, any rotors may be used which satisfy the above-mentioned clearance conditions, such as so-called trochoid rotors which includes an inner rotor having teeth which are formed using a trochoid envelope curve which is formed by moving a trajectory circle, whose center is positioned on a trochoid curve, along the trochoid curve, and an outer rotor that is engageable with the inner rotor.
  • trochoid rotors which includes an inner rotor having teeth which are formed using a trochoid envelope curve which is formed by moving a trajectory circle, whose center is positioned on a trochoid curve, along the trochoid curve, and an outer rotor that is engageable with the inner rotor.
  • the clearance between the rotors that together form the cell is minimized at an engagement region, and then the clearance is continuously increased, without decreasing, to a maximum size, backlash at a position at which the teeth engage each other is minimized, and a sufficient clearance is ensured at a rotational position at which the teeth do not contribute to engagement.
  • the external teeth engage the internal teeth at a position at which a slip component is minimized so as to transmit rotational force, and the external teeth and the internal teeth do not contribute to transmitting rotational force at a position at which a slip component is increased. Therefore, an internal gear type oil pump rotor assembly can be obtained which does not emit excessive noise while having low levels of friction and high mechanical efficiency.
  • a cycloid type rotor assembly which is formed using cycloid curves and a trochoid type rotor assembly which is formed using trochoid curves, both of which have been conventionally used can be made so as to emit less noise and to have lower level of friction; therefore, an internal gear type oil pump having high performance can be obtained.

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Claims (7)

  1. Ensemble rotor de pompe à huile comprenant :
    un rotor intérieur (20) ayant "n" dents externes ("n" est un entier naturel) ; et
    un rotor extérieur (10) ayant (n+1) dents internes pouvant s'engager avec les dents externes,
    dans lequel l'ensemble rotor de pompe à huile est utilisé dans une pompe à huile qui, pendant la rotation des rotors intérieur et extérieur, aspire et décharge un fluide par changement de volume des alvéoles formées entre le rotor intérieur et le rotor extérieur,
    dans lequel un jeu, qui est défini entre les dents des rotors intérieur et extérieur qui forment ensemble l'une des alvéoles qui a le volume minimal parmi les alvéoles, est nommé "a", un jeu, qui est défini entre les dents des rotors intérieur et extérieur qui forment ensemble l'une des alvéoles dont le volume augmente pendant la rotation des rotors intérieur et extérieur, est nommé "b", et un jeu, qui est défini entre les dents des rotors intérieur et extérieur qui forment ensemble l'une des alvéoles qui a le volume maximal parmi les alvéoles, est nommé "c", caractérisé en ce que les inégalités suivantes sont satisfaites : a ≤ b ≤ c , et a < c ,
    Figure imgb0100
    et
    dans lequel, lorsque le jeu "b" " de l'alvéole positionnée vers l'arrière, telle que vue dans la direction de rotation est en outre nommé "b1", et le jeu "b" dans l'alvéole positionnée vers l'avant, telle que vue dans la direction de rotation est en outre nommé "b2", l'inégalité suivante est satisfaite : b ⁢ 1 ≤ b ⁢ 2 ,
    Figure imgb0101
    dans lequel un jeu, qui est défini entre les dents des rotors intérieur et extérieur qui forment ensemble l'une des alvéoles, augmente progressivement et en continu à mesure que l'alvéole se déplace en rotation d'une position à laquelle le volume de l'alvéole est minimisé vers une position à laquelle le volume de l'alvéole est maximisé.
  2. Ensemble rotor de pompe à huile selon la revendication 1,
    dans lequel lorsqu'un jeu, qui est défini entre les dents des rotors intérieur et extérieur qui forment ensemble l'une des alvéoles dont le volume diminue pendant la rotation des rotors intérieur et extérieur, est nommé "d", les inégalités suivantes sont satisfaites : a ≤ b ≤ c , a < c , et a ≤ d ≤ c ,
    Figure imgb0102
    et
    dans lequel, lorsque le jeu "d" dans l'alvéole positionnée vers l'arrière, telle que vue dans la direction de rotation, est en outre nommé "d1", et le jeu "d" dans l'alvéole positionnée vers l'avant, telle que vue dans la direction de rotation, est en outre nommé "d2", l'inégalité suivante est satisfaite : d ⁢ 1 ≥ d ⁢ 2.
    Figure imgb0103
  3. Ensemble rotor de pompe à huile selon la revendication 1, dans lequel le jeu, qui est défini entre les dents des rotors intérieur et extérieur qui forment ensemble l'une des alvéoles, diminue progressivement à mesure que l'alvéole se déplace en rotation d'une position à laquelle le volume de l'alvéole est maximisé vers une position à laquelle le volume de l'alvéole est minimisé.
  4. Ensemble rotor de pompe à huile selon l'une des revendications 1 à 3, dans lequel les surfaces de dents des rotors intérieur et extérieur sont respectivement formées en utilisant des courbes cycloïdes qui sont formées en faisant rouler des cercles de roulement respectifs le long de cercles de base respectifs sans glissement.
  5. Ensemble rotor de pompe à huile selon l'une des revendications 1 à 3, dans lequel les surfaces de dents du rotor intérieur sont formées en utilisant une courbe enveloppe trochoïde qui est formée en déplaçant un cercle de trajectoire, dont le centre est positionné sur une courbe trochoïde, le long de la courbe trochoïde, et les pointes des dents du rotor extérieur sont formées en utilisant un arc ayant le même rayon que celui du cercle de trajectoire.
  6. Ensemble rotor de pompe à huile selon la revendication 1,
    dans lequel chacun des profils de dents du rotor intérieur est formé de sorte que son profil de pointe soit formé en utilisant une courbe épicycloïde qui est formée en faisant rouler un premier cercle de roulement circonscrit Ai le long d'un cercle de base Di sans glissement, et son profil d'espace de dent est formé en utilisant une courbe hypocycloïde qui est formée en faisant rouler un premier cercle de roulement inscrit Bi le long du cercle de base Di sans glissement, et chacun des profils de dents du rotor extérieur est formé de sorte que son profil de pointe soit formé en utilisant une courbe épicycloïde qui est formée en faisant rouler un deuxième cercle de roulement circonscrit Ao le long d'un cercle de base Do sans glissement, et son profil de pointe est formé en utilisant une courbe hypocycloïde qui est formée en faisant rouler un deuxième cercle de roulement inscrit Bo le long du cercle de base Do sans glissement, et
    dans lequel le rotor intérieur et le rotor extérieur sont formés de sorte que les équations suivantes sont satisfaites : ØBo = ØBi ;
    Figure imgb0104
     ØDo = ØDi ⋅ n + 1 / n + t ⋅ n + 1 / n + 2 ;
    Figure imgb0105
    et ØAo = ØAi + t / n + 2 ,
    Figure imgb0106
    où 0Di est le diamètre du cercle de base Di du rotor intérieur, øAi est le diamètre du premier cercle de roulement circonscrit Ao, 0Bi est le diamètre du premier cercle de roulement inscrit Bi, øDo est le diamètre du cercle de base Do du rotor extérieur, øAo est le diamètre du deuxième cercle de roulement circonscrit Ao, øBo est le diamètre du deuxième cercle de roulement inscrit Bo, et t (≠0) est un jeu entre la pointe de dent du rotor intérieur et la pointe de dent du rotor extérieur.
  7. Ensemble rotor de pompe à huile selon la revendication 1,
    dans lequel chacun des profils de dents du rotor intérieur est formé de sorte que son profil de pointe soit formé en utilisant une courbe épicycloïde qui est formée en faisant rouler un premier cercle de roulement circonscrit Di le long d'un cercle de base "bi" sans glissement, et son profil d'espace de dent est formé en utilisant une courbe hypocycloïde qui est formée en faisant rouler un premier cercle de roulement inscrit "di" le long du cercle de base "bi" sans glissement, et chacun des profils de dents du rotor extérieur est formé de sorte que son profil de pointe soit formé en utilisant une courbe épicycloïde qui est formée en faisant rouler un deuxième cercle de roulement circonscrit Do le long d'un cercle de base "bo" sans glissement, et son profil de pointe est formé en utilisant une courbe hypocycloïde qui est formé en faisant rouler un deuxième cercle de roulement inscrit "do" le long du cercle de base "bo" sans glissement, et
    dans lequel le rotor intérieur et le rotor extérieur sont formés de sorte que les équations et les inégalités suivantes soient satisfaites : Øbi = n + ØDi + Ødi ;
    Figure imgb0107
     Øbo = n + 1 + ØDo + Ødo ;
    Figure imgb0108
     lʹune de ØDi + Ødi = 2 ⁢ e et ØDo + Ødo = 2 ⁢ e ;
    Figure imgb0109
     ØDo > ØDi ;
    Figure imgb0110
     Ødi > Ødo ;
    Figure imgb0111
     ØDi + Ødi < ØDo + Ødo ,
    Figure imgb0112
    où 0bi est le diamètre du cercle de base "bi" du rotor intérieur, 0Di est le diamètre du premier cercle de roulement circonscrit Di, 0di est le diamètre du premier cercle de roulement inscrit "di", øbo est le diamètre du cercle de base "bo" du rotor extérieur, øDo est le diamètre du deuxième cercle de roulement circonscrit Do, ødo est le diamètre du deuxième cercle de roulement inscrit "do" et "e" est une distance d'excentricité entre les rotors intérieur et extérieur.
EP03769987.3A 2002-10-29 2003-10-29 Assemblage de rotor de pompe à huile à engrenage interne Expired - Lifetime EP1559912B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2002314070 2002-10-29
JP2002314070 2002-10-29
PCT/JP2003/013880 WO2004044430A1 (fr) 2002-10-29 2003-10-29 Rotor de pompe hydraulique a huile a engrenage interne

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EP1559912A1 EP1559912A1 (fr) 2005-08-03
EP1559912A4 EP1559912A4 (fr) 2010-12-08
EP1559912B1 true EP1559912B1 (fr) 2015-12-09

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JP (1) JPWO2004044430A1 (fr)
KR (1) KR20050067202A (fr)
CN (1) CN100451339C (fr)
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HU (1) HUE027489T2 (fr)
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KR100812754B1 (ko) * 2006-09-03 2008-03-12 에스앤티대우(주) 내접기어의 치형
WO2008106198A1 (fr) * 2007-02-28 2008-09-04 Borgwarner Inc. Procédé de lamination d'acier estampé pour produire des rotors interne et externe de gérotor pour des applications de pompe
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RU2008148909A (ru) * 2008-12-12 2010-06-20 Андрей Викторович Бродовский (RU) Роторно-поршневая машина объемного действия
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DE102011089609A1 (de) * 2011-12-22 2013-06-27 Robert Bosch Gmbh Innenzahnradpumpe

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Also Published As

Publication number Publication date
EP1559912A4 (fr) 2010-12-08
ES2561939T3 (es) 2016-03-01
KR20050067202A (ko) 2005-06-30
WO2004044430A1 (fr) 2004-05-27
CN100451339C (zh) 2009-01-14
CN1708647A (zh) 2005-12-14
HUE027489T2 (en) 2016-11-28
MY168173A (en) 2018-10-11
JPWO2004044430A1 (ja) 2006-03-16
US20060239848A1 (en) 2006-10-26
EP1559912A1 (fr) 2005-08-03

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