EP2012014A1 - Pompe à engrenages internes avec des pas d'engrenage irréguliers - Google Patents

Pompe à engrenages internes avec des pas d'engrenage irréguliers Download PDF

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Publication number
EP2012014A1
EP2012014A1 EP08159552A EP08159552A EP2012014A1 EP 2012014 A1 EP2012014 A1 EP 2012014A1 EP 08159552 A EP08159552 A EP 08159552A EP 08159552 A EP08159552 A EP 08159552A EP 2012014 A1 EP2012014 A1 EP 2012014A1
Authority
EP
European Patent Office
Prior art keywords
teeth
tooth
inner rotor
internal
external
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP08159552A
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German (de)
English (en)
Inventor
Kenichi Fujiki
Takatoshi Watanabe
Masashi Sadatomi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Yamada Manufacturing Co Ltd
Original Assignee
Yamada Manufacturing Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2008148955A external-priority patent/JP2009036194A/ja
Application filed by Yamada Manufacturing Co Ltd filed Critical Yamada Manufacturing Co Ltd
Publication of EP2012014A1 publication Critical patent/EP2012014A1/fr
Withdrawn legal-status Critical Current

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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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • 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
    • F04C2/101—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 with a crescent-shaped filler element, located between the inner and outer intermeshing members

Definitions

  • the present invention relates to an internal gear pump which comprises a crescent disposed between an outer rotor and an inner rotor and which is provided with the inner rotor with a trochoidal tooth profile, the internal gear pump making it possible to reduce vibrations caused by pulsations generated during fluid discharge.
  • an internal gear pump comprising an outer rotor having internal teeth formed therein, an inner rotor disposed on the inner peripheral side of the outer rotor and having formed therein external teeth that mesh with the internal teeth, and a crescent disposed in a clearance between the outer rotor and the inner rotor, wherein pitch spacings of the external teeth of the inner rotor are formed as non-equal spacings, and pitch spacings of the internal teeth of the outer rotor correspond to the pitch spacings of the external teeth of the inner rotor.
  • the aforementioned problems are resolved by the invention of claim 2 that provides the internal gear pump of the above-described configuration, wherein a row of teeth with the number of teeth equal to the common divisor of the number of external teeth of the inner rotor and the number of internal teeth of the outer rotor is taken as a non-equal spacing pitch row, and identical non-equal spacing pitch rows are formed repeatedly.
  • the aforementioned problems are resolved by the invention of claim 3 that provides the internal gear pump of the above-described configuration, wherein the number of the non-equal spacing pitch rows is 3 or more.
  • the aforementioned problems are resolved by the invention of claim 4 that provides the internal gear pump of the above-described configuration, wherein the number of teeth of the inner rotor is 6 or more, and the number of teeth of the outer rotor is 9 or more.
  • the aforementioned problems are resolved by the invention of claim 5 that provides the internal gear pump of the above-described configuration, wherein the tooth thicknesses of the external teeth and internal teeth in the non-equal spacing pitch rows are set to differ.
  • the aforementioned problems are resolved by the invention of claim 6 that provides the internal gear pump of the above-described configuration, wherein the tooth profile of the inner rotor is a trochoidal tooth profile.
  • an internal gear pump comprising an outer rotor having internal teeth formed therein, an inner rotor disposed on the inner peripheral side of the outer rotor and having formed therein external teeth that mesh with the internal teeth, and a crescent disposed in a clearance between the outer rotor and the inner rotor, wherein tooth thickness dimensions of the external teeth of the inner rotor are formed to be non-uniform, and the tooth thicknesses of the internal teeth of the outer rotor correspond to the tooth thickness dimensions of the inner rotor.
  • the invention of claim 8 that provides the internal gear pump of the above-described configuration, wherein the number of external teeth of the inner rotor and the number of internal teeth of the outer rotor are multiples of a common divisor of the number of external teeth and the number of internal teeth, a plurality of unit external tooth rows having the number of teeth at least equal to the greatest common divisor and also having different tooth thicknesses are provided in the external teeth of the inner rotor, and a plurality of unit internal tooth rows in which the internal teeth corresponding to the unit external tooth row of the inner rotor are arranged consecutively are provided in the outer rotor.
  • the aforementioned problems are resolved by the invention of claim 9 that provides the internal gear pump of the above-described configuration, wherein the number of unit external tooth rows of the inner rotor is 3 or more.
  • the aforementioned problems are resolved by the invention of claim 10 that provides the internal gear pump of the above-described configuration, wherein the number of teeth of the inner rotor is 6 or more, and the number of teeth of the outer rotor is 9 or more.
  • the aforementioned problems are resolved by the invention of claim 11 that provides the internal gear pump of the above-described configuration, wherein the tooth profile of the inner rotor is a trochoidal tooth profile.
  • the aforementioned problems are resolved by the invention of claim 12 that provides the internal gear pump of the above-described configuration, wherein a pitch angle of the external teeth of the inner rotor is formed to be non-uniform, and a pitch angle of the internal teeth of the outer rotor corresponds to the pitch angle of the external teeth.
  • the aforementioned problems are resolved by the invention of claim 13 that provides the internal gear pump of the above-described configuration, wherein a pitch angle of the external teeth of the unit external tooth row of the inner rotor is formed to be non-uniform, and a pitch angle of the internal teeth of the unit internal tooth row of the outer row corresponds to the pitch angle of the external teeth of the unit external tooth row.
  • the pitch spacings of the external teeth of the inner rotor are made different from each other.
  • the size of cells that are formed by the inner rotor and outer rotor at the time of discharge differ from each other, the amount of discharge from the cells is irregular, and the peak value of discharge pulsations is reduced, whereby the audible noise level and vibrations can be decreased.
  • a row of teeth with the number of teeth equal to the common divisor of the number of external teeth of the inner rotor and the number of internal teeth of the outer rotor is taken as a non-equal spacing pitch row, and identical non-equal spacing pitch rows are formed repeatedly.
  • the irregular discharge state produced by non-equal (uneven) discharge amount is generated periodically and consecutively, and the peak value of discharge pulsations can be reduced even more significantly.
  • the period of pitch spacings is 3 or more. As a result, three or more different pitch spacings can be created consecutively, the period of pitch spacings can be made even more complex, and the irregularity of discharge pulsations can be further increased.
  • the number of teeth of the inner rotor is 6 or more, and the number of teeth of the outer rotor is 9 or more.
  • the common divisor of the numbers of teeth of the inner rotor and outer rotor can be made equal to or more than 3, and three or more different irregular discharge states can be realized.
  • the tooth thicknesses of the external teeth and internal teeth in the non-equal spacing pitch rows are set to differ.
  • irregular pulsations are produced due to non-equally spaced pitches and also irregular pulsations are produced from cells of different size due to a sequential difference in tooth thickness.
  • the tooth profile of the inner rotor is a trochoidal tooth profile. As a result, the discharge performance can be improved, while reducing the peak of pulsations.
  • tooth thickness dimensions of the external teeth of the inner rotor are formed to be non-uniform, and the tooth thicknesses of the internal teeth of the outer rotor correspond to the tooth thickness dimensions of the inner rotor.
  • the tooth thickness dimensions of the external teeth of the inner rotor differ from each other, and the volume (capacity) of spaces bounded by the adjacent external teeth and the crescent differ from each other.
  • the tooth thickness dimensions of the internal teeth also differ from each other, and the volume (capacity) of spaces bounded by the adjacent internal teeth and the crescent differ from each other.
  • the size of cells that are formed by the inner rotor and outer rotor at the time of discharge differ from each other, the amount of discharge from the cells is irregular, and the peak value of discharge pulsations is reduced, whereby the audible noise level and vibrations can be decreased.
  • the number of external teeth of the inner rotor and the number of internal teeth of the outer rotor are multiples of a common divisor of the number of external teeth and the number of internal teeth, a plurality of unit external tooth rows having the number of teeth at least equal to the greatest common divisor and also having different tooth thicknesses are provided in the external teeth of the inner rotor, and a plurality of unit internal tooth rows in which the internal teeth corresponding to the unit external tooth row of the inner rotor are arranged consecutively are provided in the outer rotor.
  • the number of unit external tooth rows of the inner rotor is 3 or more.
  • three or more external teeth with different tooth thickness dimensions can be arranged sequentially, the configuration of the unit external tooth row can be further complicated, and the irregularity of the discharge pulsations can be further increased.
  • the number of teeth of the inner rotor is 6 or more, and the number of teeth of the outer rotor is 9 or more.
  • the common divisor of the numbers of teeth of the inner rotor and outer rotor can be made equal to or more than 3, and three or more irregular different discharge states can be realized.
  • the tooth profile of the inner rotor is a trochoidal tooth profile. As a result, the discharge performance can be improved, while reducing the peak of pulsations.
  • a pitch angle of the external teeth of the inner rotor is formed to be non-uniform, and a pitch angle of the internal teeth of the outer rotor corresponds to the pitch angle of the external teeth.
  • a pitch angle of the external teeth of the unit external tooth row of the inner rotor is formed to be non-uniform, and a pitch angle of the internal teeth of the unit internal tooth row of the outer row corresponds to the pitch angle of the external teeth of the unit external tooth row.
  • the configuration of the first embodiment of the present invention mainly comprises an inner rotor 1, an outer rotor 2, a crescent 3, and a pump casing 4.
  • the pump casing 4 has formed therein a rotor chamber 41, a suction port 42, and a discharge port 43.
  • the suction port 42 and discharge port 43 are formed as flow channels communicating with the outside of the pump casing 4.
  • the pump casing 4 can be used together with a casing cover (this configuration is not shown in the figure).
  • the inner rotor 1 has a plurality of external teeth 11, 11, ... formed on the outer periphery thereof.
  • the external teeth 11 can be also formed with trochoidal tooth profiles (including tooth profiles of an almost trochoidal shape).
  • a tooth bottom portion 12 is formed between the external teeth 11, 11.
  • Different spacings, that is, pitch spacings Pa, are set between the adjacent external teeth 11, 11, and these different pitch spacings Pa will be described below.
  • the outer rotor 2 has a plurality of internal teeth 21, 21, ... formed on the inner periphery thereof, and tooth bottom portions 22 are formed between the internal teeth 21, 21, ....
  • the inner rotor 1 is disposed on he inner peripheral side of the outer rotor 2, and the external teeth 11, 11, ... of the inner rotor 1 mesh with the internal teeth 21, 21, ... of the outer rotor 2.
  • pitch spacings Pb of the internal teeth 21, 21, ... of the outer rotor 2 are formed correspondingly to the pitch spacings Pa of the external teeth 11, 11, ... of the inner rotor 1 so as to enable effective meshing with the external teeth 11, 11, ... of the inner rotor 1.
  • the external teeth 11 of the inner rotor 1 have a trochoidal tooth profile (including a tooth profile of an almost trochoidal shape)
  • the internal teeth 21 of the outer rotor 2 have a tooth profile enabling effective meshing with the external teeth 11 of the inner rotor 1.
  • a trochoidal tooth profile including a tooth profile of an almost trochoidal shape
  • the crescent 3 is inserted and disposed in a gap formed between the outer rotor 2 and inner rotor 1. This gap is called an almost crescent-like space formed between the inner peripheral side of the outer rotor 2 and the outer periphery of the inner rotor 1. As shown in FIG. 2C , the crescent 3 has an almost crescent-like or arcuate shape and is composed of an arcuate concave surface side 31 and an arcuate convex surface side 32.
  • Interior cells Sa are formed between the arcuate concave surface side 31 of the crescent 3 and the external teeth 11, 11, ... of the inner rotor 1 (see FIG. 1B ).
  • exterior cells Sb are formed between the arcuate convex surface side 32 of the crescent 3 and the internal teeth 21, 21, ... of the outer rotor 2 (see FIG. 1B ).
  • the interior cells Sa are voids formed in a portion bounded by the external teeth 11, 11 of the inner rotor 1 and the arcuate concave surface side 31 of the crescent 3
  • the exterior cells Sb are voids formed in a portion bounded by the internal teeth 21, 21, ... and the arcuate convex surface side 32 of the crescent 3.
  • the configuration of the external teeth 11, 11, ... of the inner rotor 1 and the internal teeth 21, 21, ... of the outer rotor 2 is determined by the following relationship.
  • the pitch spacings Pa, Pa, ... between he adjacent external teeth 11, 11 are formed to differ from each other.
  • the pitch spacings Pb between the internal teeth 21, 21, ... of the outer rotor 2 are formed correspondingly to the pitch spacings Pa between the external teeth 11, 11, ... of the inner rotor 1, so as to ensure the meshing of the external teeth 11, 11, ... and internal teeth 21, 21, ..., and these pitch spacings Pb, Pb, ... are also different from each other.
  • the size of the pitch spacing Pa is determined by the pitch angle of the adjacent external teeth 11, 11, and the size of the range of the tooth bottom portion 12 between the adjacent external teeth 11, 11 is determined thereby.
  • Regions 13 between the teeth that configure the interior cells Sa are set between the adjacent external teeth 11, 11 to center on the tooth bottom portions 12 positioned between the adjacent external teeth 11, 11 (see FIG. 1B and FIG. 2A ).
  • the regions 13 between the teeth are equal to the corresponding pitch spacings Pa. More specifically, as shown in FIG. 2A , where the pitch angles of three appropriate external teeth 11, 11, ... in the inner rotor 1 are denoted by ⁇ 1, ⁇ 1, ⁇ 1, the relationship between the pitch spacings Pa will be ⁇ 1 ⁇ ⁇ 1 ⁇ ⁇ 1.
  • the regions 13 between the teeth match the size of the pitch angles ⁇ 1, ⁇ 1, ⁇ 1, and are denoted by 13 ⁇ , 13 ⁇ , and 13 ⁇ (see FIG. 2A ).
  • the size of these regions satisfies the conditions 13 ⁇ ⁇ 13 ⁇ ⁇ 13 ⁇ .
  • the size of regions changes in the following order in the rotation direction of the inner rotor 1: small (13 ⁇ ), large (13 ⁇ ), and intermediate (13 ⁇ ).
  • the volumes of interior cells Sa, Sa, ... formed between the inner rotor 1 and the crescent 3 also differ from each other, and there are small and large volumes. Therefore, the amount of liquid transferred by the plurality of interior cells Sa varies among the interior cells Sa.
  • the pitch spacings Pb of the internal teeth 21, 21, ... of the outer rotor 2 are made to correspond to the pitch spacings Pa of the external teeth 11, 11, ... of the inner rotor 1 so as to ensure the meshing of the teeth.
  • the volumes of the interior cell Sa and exterior cell Sb formed by he crescent 3 in the inner rotor 1 and outer rotor 2 differ from each other, the discharged amount varies among the cells (interior cell Sa, exterior cell Sb), the peak value of discharge pulsations is reduced, and vibrations and noise level that can be heard are reduced.
  • the pitch spacings of the external teeth 11, 11, ... of the inner rotor 1 and the internal teeth 21, 21, ... of the outer rotor 2 are defined as follows. First, a tooth row with a number of teeth equal to a numerical value N that is a common divisor of the number Za of the external teeth 11, 11, ... of the inner rotor 1 and the number Zb of the internal teeth 21, 21, ... of the outer rotor 2 is taken as a non-equal spacing pitch row Pi in the inner rotor 1, and the identical non-equal spacing pitch rows Pi are formed repeatedly (see FIG. 2A ). Thus, a plurality of non-equal spacing pitch rows Pi are included in one inner rotor 1.
  • the teeth with different pitch spacing Pa are formed as a unit (group) by the N (common divisor) external teeth 11, 11, ....
  • the pitch spacings Pa vary depending on whether the pitch angle ( ⁇ , ⁇ , ⁇ ) is large, medium, or small, and the regions 13 between the teeth in the non-equal spacing pitch row Pi also vary. Further, it is preferred that the arrangement order of the size of a plurality regions 13, 13, ... between the teeth in the non-equal spacing pitch row Pi be non-regular (random).
  • the order of sizes of regions 13 between the teeth in a plurality of non-equal spacing pitch rows Pi in one inner rotor 1 is such that they all are formed with the same pattern.
  • the outer rotor 2 there is present a non-equal spacing pitch row Po in which N (common divisor) internal teeth 21, 21, ... are configured with different pitch spacings Pb, in the same manner as in the non-equal spacing pitch row Pi.
  • the number of teeth Za, number of teeth Zb, and numerical value N which is a common divisor, will be explained below as specific integer values.
  • the number of teeth Za of the inner rotor 1 is taken as 6, and the number of teeth Zb of the outer rotor 2 is taken as 9.
  • the common divisor (numerical value N) of the number of teeth Za and number of teeth Zb is "3". This value is not necessarily the greatest common divisor of the number of teeth Za and number of teeth Zb.
  • the non-equal spacing pitch row Pi is composed of three external teeth 11, 11, ... with a different pitch spacing Pa. The three regions 13, 13, ... between the teeth that are set by the three external teeth 11, 11, ...
  • the non-equal spacing pitch row Po of the outer rotor 2 is composed of three internal teeth 21, 21, ... with a different pitch spacing Pb.
  • the regions 23, 23, ... between the teeth that are formed by the three internal teeth 21, 21, ... are composed of three pitch angles and, as described above, denoted by ⁇ 2, ⁇ 2, ⁇ 2.
  • the order of sizes of a plurality of regions 23, 23, ... between the teeth in the non-equal spacing pitch row Po has a pattern identical to the order of sizes of the regions 13, 13, ... between the teeth in the non-equal spacing pitch row Pi of the inner rotor 1.
  • Two non-equal spacing pitch rows Pi are present in the inner rotor 1
  • three non-equal spacing pitch rows Po are present in the outer rotor 2 (see FIG. 2B ).
  • the non-equal spacing pitch row Pi and non-equal spacing pitch row Po have three (common divisor) external teeth 11, 11, ... and internal teeth 21, 21, ..., respectively.
  • the arrangement of the order of sizes of the regions 13 between the teeth and regions 23 between the teeth can be an appropriate irregular arrangement.
  • the order of sizes of the pitch angles ( ⁇ , ⁇ , ⁇ ) of the regions 13, 13, ... between the teeth in the rotation direction of the rotor can be small, medium, large, or large, medium, small.
  • the order of sizes of the regions 23, 23, ... in the non-equal spacing pitch row Po of the outer rotor 2 is identical to that of the non-equal spacing pitch row Pi.
  • the period of the size of volume of the interior cells Sa (exterior cells Sb) formed by regions 13 (23) between the teeth of different size varies non-monotonically rather than monotonically when the external teeth 11 (internal teeth 21) move with different pitch spacings Pa (Pb).
  • the non-monotonous changes as referred to herein mean that the regions 13 (23) between the teeth of different size move through a predetermined position with irregular periods because of the irregular pitch spacing Pa (Pb).
  • FIG. 3 to FIG. 5 show the operation states in which the interior cells Sa and exterior cells Sb that differ in volume due to the difference in pitch angle between the regions 13 ⁇ , 13 ⁇ , 13 ⁇ between the teeth or regions 23 ⁇ , 23 ⁇ , 23 ⁇ between the teeth are discharged successively into the discharge port 43 as the inner rotor 1 makes one revolution.
  • One of the external teeth 11 of the inner rotor 1 is marked with a black dot, and the external tooth 11 with a dot makes one revolution as shown in FIG. 3 to FIG. 5 .
  • the size of the shape that is, a tooth thickness dimension Wa, differs between the external teeth 11, 11, ... arranged with the irregular pitch spacing Pa in the non-equal spacing pitch row Pi. Because there is a difference in size between the external teeth 11, 11, ..., as described above, the volume of interior cells Sa also varies (see FIG. 2A ). Likewise, the size of the shape, that is, a tooth thickness dimension Wb, differs between the internal teeth 21, 21, ... of the outer rotor 2 that are arranged in the irregular pitch spacing Pb in the non-equal spacing pitch row Po, and because there is a difference in size between the internal teeth 21, 21, ..., as described above, the volume of exterior cells Sb also varies.
  • FIG. 6 illustrates a configuration in which the number of teeth Za of the inner rotor 1 is 6 and the number of teeth Zb of the outer rotor 2 is 12.
  • the value of the common divisor of the number of teeth Za and number of teeth Zb is 6, and the number of non-equal spacing pitch rows Po of the outer rotor 2 formed thereby is 2.
  • the value of the common divisor is equal to the number of teeth Za of the inner rotor 1.
  • FIG. 7A is a graph illustrating the discharge pulsations in accordance with the present invention.
  • FIG. 7B is a graph illustrating the discharge pulsations of the conventional configuration. The comparison of the two graphs shows that in accordance with the present invention the pulsations are dispersed, whereby the peak of discharge pulsations is reduced (see FIG. 7A ).
  • the tooth thickness dimension Wa of the tooth thickness of the external teeth 11, 11, ... of the inner rotor 1 is not uniform.
  • the pitch angles ⁇ a, ⁇ a, ... of the adjacent external teeth 11, 11 in a plurality of external teeth 11, 11, ... of the inner rotor 1 are all formed as equal angles (see FIG. 8B , FIG. 9A ).
  • the pitch spacing Pa of the external teeth 11, 11, ... is uniform.
  • the term "corresponds" as used herein means that the internal teeth 21, 21, ... of the outer rotor 2 can mesh with the external teeth 11, 11, ... of the inner rotor 1 in the internal gear pump and the inner rotor 1 and outer rotor 2 can rotate effectively (see FIG. 10 to FIG. 12 ).
  • the tooth thickness dimension Wa of the external tooth 11 of the inner rotor 1 is a dimension of the portion that crosses a reference pitch circle Ca (see FIG. 9A ).
  • the reference pitch circle Ca is a virtual circle that passes through the intermediate position between the tooth tip and tooth bottom of the external tooth 11, this circle having the center of the diameter of the inner rotor 1 as a center.
  • the shape of the tooth bottom portion 12 between the adjacent external teeth 11, 11 differs depending on the tooth thickness dimension Wa of the external teeth 11.
  • the volumes of the interior cells Sa, Sa, ... formed between the adjacent external teeth 11, 11 of the inner rotor 1 and the crescent 3 differ accordingly, and there are large volumes and small volumes. Therefore, the amount of liquid transferred by a plurality of the interior cells Sa varies from one interior cell Sa to another.
  • the outer rotor 2 also has a reference pitch circle Cb (see FIG. 9B ).
  • the number Za of external teeth 11, 11, ... of the inner rotor 1 and the number Zb of internal teeth 21, 21, ... of the outer rotor 2 are multiples of the common divisor of Za and Zb.
  • a tooth row is composed of the number of teeth at least equal to the greatest common divisor, and the external teeth 11 in this tooth row have different tooth thickness dimensions Wa.
  • This tooth row is called a unit external tooth row Li (see FIG. 9A ).
  • the unit external tooth row Li is composed of N external teeth 11, where the numerical value N is the (greatest) common divisor, and the unit external tooth rows Li are formed repeatedly.
  • one inner rotor 1 comprises a plurality of unit external tooth rows Li.
  • the numerical value N which is the greatest common divisor of the number of teeth Za of the inner rotor 1 and the number of teeth Zb of the outer rotor 2 is equal to the number of teeth Za of the inner rotor 1
  • only one unit external tooth row Li is contained in the inner rotor 1.
  • the number 6, which is the number of teeth Za of the inner rotor 1 is the greatest common divisor
  • the inner rotor 1 is composed only of one unit external tooth row Li.
  • the tooth thickness dimensions Wa of the external teeth 11, 11, ... are all different from each other.
  • the arrangement order of sizes of tooth thickness dimensions Wa, Wa, ... of a plurality of external teeth 11, 11, ... contained in the unit external tooth row Li is preferably irregular (random). However, the arrangement orders of sizes of the tooth thickness dimensions Wa in a plurality of unit external tooth rows Li in one inner rotor 1 are all formed according to the same pattern.
  • a unit internal tooth row Lo composed of a total of N (common divisor) internal teeth 21, 21, ... with different tooth thickness dimensions Wb is provided similarly to the above-described unit external tooth row Li (see FIG. 9B ).
  • the numerical value N which is the common divisor, will be explained below for the number of teeth Za of the inner rotor 1 and the number of teeth Zb of the outer rotor 2.
  • the number of teeth Za of the inner rotor 1 is taken as 6, and the number of teeth Zb of the outer rotor 2 is taken as 9 (see FIGS. 9A, 9B ).
  • the common divisor (numerical value N) of the number of teeth Za and the number of teeth Zb is "3". Depending on the numerical values of the number of teeth Za and the number of teeth Zb, this numerical value "3" is not necessarily the greatest common divisor.
  • the unit external tooth row Li is composed of three external teeth 11, 11, ... having mutually different tooth thickness dimensions Wa.
  • the tooth thickness dimension Wa1, tooth thickness dimension Wa2, and tooth thickness dimension Wa3 are used to indicate that the three external teeth 11, 11, ... of the unit external tooth row Li have different tooth thickness dimensions Wa.
  • the size relationship of the tooth thickness dimensions is such that the tooth thickness dimension Wa1 is the maximum dimension and the tooth thickness dimension Wa3 is the minimum dimension.
  • the size relationship of the tooth thickness dimensions is Wa1 > Wa2 > Wa3 (see FIG. 9A ).
  • the unit internal tooth row Lo of the outer rotor 2 is composed of three internal teeth 21, 21, ... having mutually different tooth thickness dimensions Wb.
  • the tooth thickness dimension Wb1, tooth thickness dimension Wb2, and tooth thickness dimension Wb3 are used to indicate that the internal teeth 21, 21, ... contained in the unit internal tooth row Lo also have different tooth thickness dimensions Wb.
  • the inner rotor 1 has two unit external tooth rows Li, Li
  • the outer rotor 2 has three unit internal tooth rows Lo, Lo, ... (see FIGS. 9A, 9B ).
  • the external tooth 11 with the tooth thickness dimension Wa1 meshes with the tooth bottom portion 22 located between the internal tooth 21 with the tooth thickness dimension Wb3 and the internal tooth 21 with the tooth thickness dimension Wb1, the external tooth 11 with the tooth thickness dimension Wa2 engages with tooth bottom portion 22 located between the internal tooth 21 with the tooth thickness dimension Wb1 and the internal tooth 21 with the tooth thickness dimension Wb2, the external tooth 11 with the tooth thickness dimension Wa3 meshes with the tooth bottom portion 22 located between the internal tooth 21 with the tooth thickness dimension Wb2 and the internal tooth 21 with the tooth thickness dimension Wb3, and such engagement state of the inner rotor 1 and outer rotor 2 is repeated (see FIG. 10 to FIG. 12 ).
  • the period of the size of volume of the interior cells Sa formed by the external teeth 11, 11, ... having mutually different tooth thickness dimensions Wa (Wa1, Wa2, Wa3) that are contained in the unit external tooth row Li of the inner rotor 1 and the crescent 3 varies non-monotonically rather than monotonically.
  • the discharge pulsations with a larger irregularity (randomness) can be realized.
  • the period of the size of volume of the interior cells Sb formed by the internal teeth 21, 21, ... having mutually different tooth thickness dimensions Wb (Wb1, Wb2, Wb3) that are contained in the unit internal tooth row Lo of the outer rotor 2 and the crescent 3 also varies non-monotonically rather than monotonically.
  • the discharge pulsations with a larger irregularity (randomness) can be realized, and the peak of discharge pulsations can be reduced.
  • FIG. 10 to FIG. 12 show how the volume of interior cells Sa, Sa, ... successively configured by the external teeth 11, 11, ... having mutually different tooth thickness dimensions (Wa1, Wa2, Wa3) of the unit external tooth row Li and the crescent 3 varies as the inner rotor 1 makes one revolution.
  • the figures also show the variation of the volume of exterior cells Sb, Sb, ... successively configured by the crescent 3 and the internal teeth 21, 21, ... having mutually different tooth thickness dimensions (Wb1, Wb2, Wb3) of the unit internal tooth row Lo of the outer rotor 2 that rotates together with the inner rotor 1.
  • the third embodiment of the present invention will be described below with reference to FIG. 13 to FIG. 16 .
  • the pitch angles ⁇ a of the external teeth 11, 11, ... of the inner rotor 1 differ from each other.
  • the tooth thickness dimensions Wa and pitch angles ⁇ a of the external teeth 11, 11, ... are not uniform and differ from each other.
  • the tooth thickness dimensions Wb of the external teeth 21, 21, ... of the outer rotor 2 correspond to the tooth thickness dimensions Wa of the external teeth 11 of the inner rotor 1.
  • the term "corresponds" as used herein means that the external teeth 11, 11, ... of the inner rotor 1 and the internal teeth 21, 21, ... of the outer rotor 2 mesh effectively in the internal gear pump in the same manner as in the first and second embodiments.
  • the definition of the tooth thickness dimension Wa of the external tooth 11 of the inner rotor 1 is identical to that given in the second embodiment.
  • the volumes of interior cells Sa, Sa, ... formed between the adjacent external teeth 11, 11 of the inner rotor 1 and the crescent 3 differ from each other and there are small and large volumes.
  • the volumes of exterior cells Sb, Sb, ... formed between the adjacent internal teeth 21, 21 of the outer rotor 2 and the crescent 3 also differ from each other. Therefore, the amount of liquid transferred by the plurality of interior cells Sa and exterior cells Sb varies among the interior cells Sa and exterior cells Sb.
  • the inner rotor 1 has unit external teeth rows Li and the outer rotor 2 has unit internal tooth rows Lo, and the unit external tooth rows Li and unit internal tooth rows Lo are configured similarly to the unit external tooth rows Li and unit internal tooth rows Lo in the second embodiment described above.
  • the arrangement order of sizes of tooth thickness dimensions Wa, Wa, ... of a plurality of external teeth 11, 11, ... contained in the unit external tooth row Li is preferably irregular (random).
  • the arrangement orders of sizes of the tooth thickness dimensions Wa in a plurality of unit external tooth rows Li in one inner rotor 1 are all formed according to the same pattern.
  • a unit internal tooth row Lo composed a total of N (common divisor) of internal teeth 21, 21, ... with different tooth thickness dimensions Wb is provided similarly to the above-described unit external tooth row Li.
  • the following specific integer values are taken for the number of teeth Za of the inner rotor 1 and the number of teeth Zb of the outer rotor 2.
  • the number of teeth Za of the inner rotor 1 is taken as 6 and the number of teeth Zb of the outer rotor 2 is taken as 9 (see FIGS. 13A, 13B ).
  • the tooth thickness dimension Wa1, tooth thickness dimension Wa2, and tooth thickness dimension Wa3 are used to indicate that the three external teeth 11, 11, ... contained in the unit external tooth row Li have different tooth thickness dimensions Wa.
  • the size relationship of the tooth thickness dimensions is Wa1 > Wa2 > Wa3 (see FIG. 13A ).
  • the pitch angles ⁇ a of the external teeth 11, 11, ... contained in the unit external tooth row Li are assumed to differ from each other. More specifically, the pitch angle of the external teeth 11, 11 with the tooth thickness dimension Wa1 and tooth thickness dimension Wa2 is taken as ⁇ a1, the pitch angle of the external teeth 11, 11 with the tooth thickness dimension Wa2 and tooth thickness dimension Wa3 is taken as ⁇ a2, and the pitch angle of the external teeth 11, 11 with the tooth thickness dimension Wa3 and tooth thickness dimension Wa1 is taken as ⁇ a3.
  • the pitch angle of the external teeth 11, 11 with the tooth thickness dimension Wa3 and tooth thickness dimension Wa1 is a pitch angle of the pitch angle of the external tooth 11 with the tooth thickness dimension Wa3 and the pitch angle of the external tooth 11 with the tooth thickness dimension Wa1 of the adjacent unit external rows Li, Li.
  • the unit internal tooth row Lo of the outer rotor 2 is also composed of three internal teeth 21, 21, ... having mutually different tooth thickness dimensions Wb, and the internal teeth 21, 21, ... contained in the unit internal tooth row Lo also have respectively different tooth thickness dimensions Wb1, Wb2, Wb3.
  • the inner rotor 1 has two unit external tooth rows Li, Li, and the outer rotor 2 has three unit internal tooth rows Lo, Lo, ... (see FIGS. 13A, 13B ).
  • the pitch angles ⁇ b of the internal teeth 21, 21, ... in the unit internal tooth row Lo of the outer rotor 2 also differ from each other correspondingly to the external teeth 11, 11, ... of the inner rotor 1. More specifically, as shown in FIG. 13B , the pitch angle ⁇ b1, pitch angle ⁇ b2, and pitch angle ⁇ b3 differ from each other.
  • the teeth contained in the unit external tooth row Li of the inner rotor 1 have mutually different tooth thickness dimensions Wa (Wa1, Wa2, Wa3) and the pitch angles ⁇ a ( ⁇ a1, ⁇ a2, ⁇ a3) of the external teeth 11, 11, ... also differ from each other.
  • Wa Wa1, Wa2, Wa3
  • ⁇ a ⁇ a1, ⁇ a2, ⁇ a3
  • the period of the size of volume of the interior cells Sa configured by the external teeth 11, 11, ... and crescent 3 varies non-monotonically rather than monotonically. Therefore, discharge pulsations with a larger irregularity (randomness) can be realized.
  • FIG. 14 to FIG. 16 show how the volume of interior cells Sa, Sa, ... successively configured by the external teeth 11, 11, ... having mutually different tooth thickness dimensions (Wa1, Wa2, Wa3) of the unit external tooth row Li and the crescent 3 varies as the inner rotor 1 makes one revolution in the third embodiment.
  • the figures also show the variation of the volume of exterior cells Sb, Sb, ... successively configured by the crescent 3 and the internal teeth 21, 21, ... having mutually different tooth thickness dimensions (Wb1, Wb2, Wb3) of the unit internal tooth row Lo of the outer rotor 2 that rotates together with the inner rotor 1.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP08159552A 2007-07-06 2008-07-02 Pompe à engrenages internes avec des pas d'engrenage irréguliers Withdrawn EP2012014A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2007178177 2007-07-06
JP2008148955A JP2009036194A (ja) 2007-07-06 2008-06-06 内接歯車ポンプ

Publications (1)

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EP2012014A1 true EP2012014A1 (fr) 2009-01-07

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EP08159552A Withdrawn EP2012014A1 (fr) 2007-07-06 2008-07-02 Pompe à engrenages internes avec des pas d'engrenage irréguliers

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Cited By (2)

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Publication number Priority date Publication date Assignee Title
WO2010132914A1 (fr) * 2009-05-20 2010-11-25 Miba Sinter Austria Gmbh Roue dentée
FR3033370A1 (fr) * 2015-03-02 2016-09-09 Peugeot Citroen Automobiles Sa Pompe a palettes

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012001462A1 (de) * 2012-01-25 2013-07-25 Robert Bosch Gmbh Innenzahnradpumpe

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DE3416400A1 (de) * 1984-05-03 1985-11-28 Schwäbische Hüttenwerke GmbH, 7080 Aalen Zahnradmaschine
DE3533743A1 (de) * 1985-09-21 1987-04-02 Opel Adam Ag Verzahnte maschinenelemente zur uebertragung von drehbewegungen
GB2247283A (en) * 1990-08-23 1992-02-26 Pierburg Gmbh Rotary positive displacement pumps
DE4331482A1 (de) * 1992-09-21 1994-03-24 Luk Lamellen & Kupplungsbau Ketten- oder Zahnriementrieb
GB2284021A (en) * 1993-11-11 1995-05-24 Luk Fahrzeug Hydraulik Hydraulic pump
US6164944A (en) * 1999-03-21 2000-12-26 Damilerchrysler Corporation Random error generation of tooth index to eliminate pump noise
WO2005019652A1 (fr) * 2003-08-18 2005-03-03 The Boc Group Plc Reduction des pulsations d'echappement dans des pompes seches
EP1600667A1 (fr) * 2004-05-25 2005-11-30 Ford Global Technologies, LLC, A subsidary of Ford Motor Company Roue dentée et Procédé d'optimisation du comportement vibratoire d'un moteur a combustion interne au moyen d'une roue dentée

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Publication number Priority date Publication date Assignee Title
DE3416400A1 (de) * 1984-05-03 1985-11-28 Schwäbische Hüttenwerke GmbH, 7080 Aalen Zahnradmaschine
DE3533743A1 (de) * 1985-09-21 1987-04-02 Opel Adam Ag Verzahnte maschinenelemente zur uebertragung von drehbewegungen
GB2247283A (en) * 1990-08-23 1992-02-26 Pierburg Gmbh Rotary positive displacement pumps
DE4331482A1 (de) * 1992-09-21 1994-03-24 Luk Lamellen & Kupplungsbau Ketten- oder Zahnriementrieb
GB2284021A (en) * 1993-11-11 1995-05-24 Luk Fahrzeug Hydraulik Hydraulic pump
JPH07253083A (ja) 1993-11-11 1995-10-03 Luk Fahrzeug Hydraulik Gmbh & Co Kg ハイドロリック式ポンプ
US6164944A (en) * 1999-03-21 2000-12-26 Damilerchrysler Corporation Random error generation of tooth index to eliminate pump noise
WO2005019652A1 (fr) * 2003-08-18 2005-03-03 The Boc Group Plc Reduction des pulsations d'echappement dans des pompes seches
EP1600667A1 (fr) * 2004-05-25 2005-11-30 Ford Global Technologies, LLC, A subsidary of Ford Motor Company Roue dentée et Procédé d'optimisation du comportement vibratoire d'un moteur a combustion interne au moyen d'une roue dentée

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010132914A1 (fr) * 2009-05-20 2010-11-25 Miba Sinter Austria Gmbh Roue dentée
US9291248B2 (en) 2009-05-20 2016-03-22 Miba Sinter Austria Gmbh Gear wheel
FR3033370A1 (fr) * 2015-03-02 2016-09-09 Peugeot Citroen Automobiles Sa Pompe a palettes
WO2016139400A3 (fr) * 2015-03-02 2016-10-27 Peugeot Citroen Automobiles Sa Pompe a palettes

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