EP3187734A1 - Schraubenrotor - Google Patents

Schraubenrotor Download PDF

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Publication number
EP3187734A1
EP3187734A1 EP15837048.6A EP15837048A EP3187734A1 EP 3187734 A1 EP3187734 A1 EP 3187734A1 EP 15837048 A EP15837048 A EP 15837048A EP 3187734 A1 EP3187734 A1 EP 3187734A1
Authority
EP
European Patent Office
Prior art keywords
lobe
main
gate
rotor
leading
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Withdrawn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
EP15837048.6A
Other languages
English (en)
French (fr)
Inventor
Masazumi Hayashi
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.)
IHI Corp
Original Assignee
IHI Corp
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Filing date
Publication date
Application filed by IHI Corp filed Critical IHI Corp
Publication of EP3187734A1 publication Critical patent/EP3187734A1/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels

Definitions

  • Embodiments described herein relate to a screw rotor used in a screw compressor.
  • a screw compressor includes two screw rotors provided with helical grooves (interlobes) in the outer peripheries thereof, and a casing that contains the two screw rotors.
  • the two rotors mesh with each other and rotate in synchronization.
  • the screw compressor is a device that rotates the rotors to thereby narrow the space between the casing and the rotors to compress a fluid confined between the casing and the rotors.
  • FIG. 1A to FIG. 1C are explanatory diagrams of conventional screw rotors.
  • FIG. 1A, FIG. 1B and FIG. 1C illustrate the process sequence of fluid compression.
  • each of the two rotors includes a plurality of lobes or interlobes. Respective rotors have shapes twisted around rotating axes at twist angles matching with each other.
  • main rotor 1 the rotor having a plurality of lobes 1a
  • gate rotor 2 the rotor having a plurality of interlobes 2a
  • fluid confining spaces 4 defined by the lobes 1a of the main rotor 1, the interlobes 2a of the gate rotor 2, and a casing 3 are indicated by the hatched areas.
  • the cross-sectional shape of the confining space 4 changes in the order of FIG. 1A, FIG. 1B and FIG. 1C .
  • the confining space 4 is squeezed in the axial direction when the sectional area formed between the main rotor 1 and the gate rotor 2 eventually becomes a minimum.
  • the confining space 4 moves in the axial direction as the main rotor 1 and the gate rotor 2 rotate. As a result, a fluid is compressed as the confining space 4 is gradually narrowed.
  • FIG. 2B is an explanatory diagram of a leakage path.
  • the lobe tip of the main rotor 1 leaves the casing 3. Thereafter, a clearance (hereinafter referred to as "blow hole") appears among the main rotor 1, the gate rotor 2 and the casing 3 in a rotation phase until a lobe tip arc C2 of the gate rotor 2 (a gate leading-side lobe tip arc 24b, which is discussed later) comes in contact with a trailing lobe face of the main rotor 1.
  • the blow hole leads to the occurrence of a leakage 5 of the compressed fluid, thus resulting in lower efficiency of the compressor.
  • an object of the present disclosure is to provide a screw rotor capable of reducing a clearance (a blow hole) among a main rotor, a gate rotor and a casing to thereby reduce the leakage amount of a compressed fluid, thus permitting higher efficiency of a compressor.
  • a screw rotor including a main rotor and a gate rotor each having a plurality of lobes or interlobes, and the main rotor and the gate rotor being meshed with each other and rotatable about a rotating axis of each thereof in an operating space formed by a casing, wherein
  • This arrangement minimizes an area of a blow hole so that deterioration in the efficiency of a compressor can be suppressed as much as possible.
  • the screw rotor described above at the specific rotation phase of the rotor, the three points of the main trailing-side lobe tip point B1, the gate leading-side lobe tip point D2', and the intersection point Q between the surface of the casing facing the main rotor and the surface of the casing facing the gate rotor coincide each other.
  • a main trailing lobe face is formed by the epicycloid curve traced by the gate leading-side lobe tip point D2' in accordance with rotation phase advancement from the specific rotation phase
  • a gate leading lobe face is formed by the epicycloid curve traced by the main trailing-side lobe tip point B1 in accordance with rotation phase advancement from the specific rotation phase.
  • FIG. 3A, FIG. 3B and FIG. 5 are explanatory diagrams of the screw rotors in accordance with the present disclosure, illustrating a section perpendicular to the rotating axes of the screw rotors.
  • FIG. 3A and FIG. 3B are the explanatory diagrams illustrating ideal lobe shapes
  • FIG. 5 is the explanatory diagram illustrating practical lobe shapes.
  • a screw compressor in accordance with the present disclosure includes a main rotor 10 and a gate rotor 20 meshed with the main rotor 10, the respective rotors being configured to be rotatable about parallel axes in an operating space formed (e.g., airtightly) by a casing 3.
  • the two rotors each include a plurality of lobes or interlobes, and are formed in shapes twisted around the rotating axes at twist angles matching with each other.
  • the rotational centers i.e. the rotating axes
  • the rotational centers may be vertical or inclined.
  • FIG. 3A, FIG. 3B and FIG. 5 each illustrate only one lobe of each of a main rotor lobe 10a and a gate rotor interlobe 20a.
  • the main rotor 10 rotates counterclockwise, while the gate rotor 20 rotates clockwise.
  • the lobe tip point of the main rotor 10 (a main leading-side lobe tip point A1) coincides with a lobe root point of the gate rotor 20 (a gate trailing-side lobe root point A2).
  • the rotational angles of the two rotors at this time are defined as the reference positions, i.e. zero rotational angles.
  • the front side (the upper side in the drawings) in the rotational direction of the main rotor lobe 10a is referred to as "the leading-side.”
  • the lobe face (the upper side in the drawings) of the gate rotor interlobe 20a that faces the leading-side of the main rotor lobe 10a is referred to as "the trailing-side.”
  • the opposite side (the lower side in the drawings) from the leading-side of the main rotor lobe 10a i.e.
  • the trailing-side the opposite side (the lower side in the drawings) from the trailing-side of the gate rotor interlobe 20a, i.e. the lobe face of the gate rotor interlobe 20a that faces the trailing-side of the main rotor lobe 10a, is referred to as "the leading-side.”
  • leading-side lobe face is referred to as “the leading lobe face”
  • trailing-side lobe face is referred to as “the trailing lobe face.”
  • the main rotor 10 includes a main pitch circle 11 and a main lobe tip circle 12.
  • the gate rotor 20 includes a gate pitch circle 21, which is in contact with the main pitch circle 11 at a pitch point P, and a gate lobe bottom circle 22 in contact with the main lobe tip circle 12.
  • the gate trailing-side lobe root point A2 and the gate leading-side lobe root point B2 are positioned on the gate lobe bottom circle 22.
  • the pitch point P is a point obtained by internally dividing the segment, which connects the rotational center of the main rotor 10 and the rotational center of the gate rotor 20, by the ratio of the number of the teeth of the main rotor 10 (three in the example illustrated in FIG. 1A to FIG. 1C ) and the number of the teeth of the gate rotor 20 (six in the example illustrated in FIG. 1A to FIG. 1C ).
  • the main pitch circle 11 is an imaginary circle, the center of which is the rotational center of the main rotor 10 and which passes through the pitch point P.
  • the gate pitch circle 21 is an imaginary circle, the center of which is the rotational center of the gate rotor 20 and which passes through the pitch point P.
  • a part of the inner surface of the casing 3 (refer to FIG. 1A to FIG. 1C ) that faces the main rotor 10 is formed of a circle adjacent to the main lobe tip circle 12.
  • a part of the inner surface of the casing 3 that faces the gate rotor 20 is formed of a circle adjacent to the gate lobe tip circle 23.
  • the main rotor 10 and the gate rotor 20 rotate, the main pitch circle 11 and the gate pitch circle 21 being synchronized with each other.
  • the synchronization is effected by the contact between the lobe face of each of the main rotor lobes 10a and the lobe face of each of the gate rotor interlobes 20a. There are cases where a separate gear for synchronization is provided.
  • the main rotor lobe 10a includes the main leading-side lobe tip point A1 and the main trailing-side lobe tip point B1, which are positioned on the main lobe tip circle 12.
  • a main lobe outer peripheral surface (A1-B1) from the main leading-side lobe tip point A1 to the main trailing-side lobe tip point B1 forms an arc on the main lobe tip circle 12, and forms the lobe tip sealing surface "a" between itself and the inner surface of the casing 3 that encloses the main rotor 10.
  • a lobe of the gate rotor 20 includes the gate leading-side lobe tip point D2' or G2 and the gate trailing-side lobe tip point C2' or F2, which are positioned on the gate lobe tip circle 23.
  • the gate lobe outer peripheral surface (D2'/F2-C2'/G2) from the gate leading-side lobe tip point D2' or G2 to the gate trailing-side lobe tip point C2' or F2 forms an arc on the gate lobe tip circle 23, and forms the lobe tip sealing surface "a" between itself and the inner surface of the casing 3 that encloses the gate rotor 20.
  • the gate rotor interlobe 20a forms the inter-rotor sealing line "b" between itself and the trailing lobe face of the main rotor lobe 10a, at the gate leading-side lobe tip point D2' or in the gate leading-side lobe tip arc 24b.
  • the gate rotor interlobe 20a forms the inter-rotor sealing line "b" between itself and the leading lobe face of the main rotor lobe 10a, at the gate trailing-side lobe tip point C2' or in the gate trailing-side lobe tip arc 24a.
  • the gate rotor interlobe 20a forms the inter-rotor sealing line "b" between itself and the trailing lobe face of the main rotor lobe 10a at the gate leading-side lobe tip point D2' or the gate leading-side lobe tip arc 24b.
  • the main rotor lobe 10a further includes the main leading-side lobe root point C1', the main trailing-side lobe root point D1', and the main leading intermediate point E1.
  • the main leading-side lobe root point C1' and the main trailing-side lobe root point D1' are positioned on the main pitch circle 11.
  • the main leading intermediate point E1 lies between the main leading-side lobe tip point A1 and the main leading-side lobe root point C1' and is positioned at the intersection point of the main leading lobe face and the gate pitch circle 21 when the main rotor lobe 10a and the gate rotor interlobe 20a directly face each other.
  • the gate rotor interlobe 20a further includes the gate trailing-side lobe tip point C2' and the gate leading-side lobe tip point D2' positioned on the gate pitch circle 21.
  • the arc from the main leading-side lobe tip point A1 to the main leading intermediate point E1 and the arc from the gate trailing-side lobe root point A2 to the gate trailing-side lobe tip point C2' coincide with each other to become the same arc whose center is the pitch point P.
  • the radius of the arc is the length from the pitch point P to the main leading-side lobe tip point A1 (or the gate trailing-side lobe root point A2).
  • a main leading lobe face (E1-Cl') from the main leading intermediate point E1 to the main leading-side lobe root point C1' is determined as a first epicycloid curve traced by the gate trailing-side lobe tip point C2'.
  • the first epicycloid curve which is traced by the trailing-side lobe tip point C2' in the rotation phase section from a rotation phase at which the gate trailing-side lobe tip point C2' coincides with the main leading-side lobe root point C1' to a rotation phase at which the gate trailing-side lobe tip point C2' coincides with the main leading intermediate point E1, is the main leading lobe face (E1-C1') from the main leading-side lobe root point C1' to the main leading intermediate point E1.
  • epicycloid curve means a curve (the curve (E1-C1') in this example) in a coordinate system fixed to one rotating rotor, the curve being drawn by a point (the gate trailing-side lobe tip point C2' in this example) in a coordinate system fixed to the other rotating rotor when the main rotor 10 and the gate rotor 20 rotate in synchronization.
  • the gate trailing-side lobe tip point C2' and the main leading lobe face (E1-C1') of the lobe 10a of the main rotor 10 constantly contact each other while rotating.
  • an inter-rotor clearance at the inter-rotor sealing line "b" (refer to FIG. 1A to FIG. 1C ) in the part concerned can be kept slight.
  • the three points namely, the main trailing-side lobe tip point B1, the gate leading-side lobe tip point D2', and the intersection point Q between the surface of the casing 3 facing the main rotor 10 and the surface of the casing 3 facing the gate rotor 20, coincide with each other.
  • the main trailing lobe face (B1-D1') from the main trailing-side lobe tip point B1 to the main trailing-side lobe root point D1' is determined as a second epicycloid curve traced by the gate leading-side lobe tip point D2'.
  • the gate leading-side lobe tip point D2' and the trailing lobe face (B1-D1') of the main rotor lobe 10a constantly contact each other while rotating. Thereby, an inter-rotor clearance at the inter-rotor sealing line "b" in the part concerned can be kept slight.
  • the gate leading lobe face (B2-D2') from the gate leading-side lobe root point B2 to the gate leading-side lobe tip point D2' is a third epicycloid curve traced by the main trailing-side lobe tip point B1.
  • the main trailing-side lobe tip point B1 and the gate leading lobe face (B2-D2') of the gate rotor interlobe 20a constantly contact each other while rotating. Thereby, an inter-rotor clearance at the inter-rotor sealing line "b" in the part concerned can be kept slight.
  • a ratio L1:L2 between a distance L1 from B2 to B1 and a distance L2 from B1 to D2' may be set within the range of 2:8 to 7:3.
  • the main trailing-side lobe tip point B1 contacts the gate leading lobe face in the range from B2 to D2' on the gate leading lobe face (B2-D2').
  • the three points namely, the main trailing-side lobe tip point B1, the gate leading-side lobe tip point D2', and the intersection point Q of the surface of the casing 3 facing the main rotor 10 and the surface of the casing 3 facing the gate rotor 20, coincide with each other at the specific rotation phase of the rotors (this phase being referred to as "the three-point coincidence phase").
  • the lobe tip of the main rotor 10 and the lobe tip of the gate rotor 20 form seals between the lobe tips and the casing 3 in the rotation phase until immediately before the three-point coincidence phase.
  • the seals are continuously formed between the main trailing-side lobe tip point B1 and the leading lobe face of the gate rotor interlobe 20a and between the gate leading-side lobe tip point D2' and the trailing lobe face of the main rotor lobe 10a in the rotation phase immediately following the three-point coincidence phase.
  • this arrangement closes the blow hole so that deterioration in the efficiency of the compressor attributable to the leakage of a fluid can be made insignificant.
  • the phase of the trailing lobe face (B1-Dl') with respect to the leading lobe face (B2-D2') may be set such that the confining space that appears between the trailing lobe face (B1-D1') of the main rotor 10 and the leading lobe face (B2-D2') of the gate rotor 20 is minimized when the main rotor lobe 10a and the gate rotor interlobe 20a face each other.
  • the lobe 10a of the main rotor 10 is modified by the following (1) to (4) on the basis of the ideal lobe shape illustrated in FIG. 3A and FIG. 3B .
  • the distance r 1 is equal to the radius r 1 of the main leading-side lobe root arc 14a and the radius r 1 of the main trailing-side lobe root arc 14b, and also equal to the radius difference ⁇ r 1 of the main lobe bottom circle 13 and the radius difference ⁇ r 1 of the main lobe tip circle 12.
  • Each of the distance, the radius and the radius difference with the reference sign r 1 takes a value that is, for example, larger than 0% of the distance between the rotating axis of the main rotor 10 and the rotating axis of the gate rotor 20 and 20% or less of the distance between the rotating axis of the main rotor 10 and the rotating axis of the gate rotor 20.
  • interlobe 20a of the gate rotor 20 is modified by the following (5) to (8) on the basis of the ideal lobe shape illustrated in FIG. 3A and FIG. 3B .
  • the distance r 2 may be equal to the radius r 2 of the gate trailing-side lobe tip arc 24a and the radius r 2 of the gate leading-side lobe tip arc 24b, and also equal to the radius difference ⁇ r 2 of the gate lobe bottom circle 22 and the radius difference ⁇ r 2 of the gate lobe tip circle 23.
  • Each of the distance, the radius and the radius difference with the reference sign r 2 takes a value that is, for example, larger than 0% of the distance between the rotating axis of the main rotor 10 and the rotating axis of the gate rotor 20 and 20% or less of the distance between the rotating axis of the main rotor 10 and the rotating axis of the gate rotor 20.
  • the main rotor lobe 10a is created according to the foregoing procedure (the foregoing modification) on the basis of the lobe shape illustrated in FIG. 3A and FIG. 3B .
  • the radius of the main lobe bottom circle 13 is smaller than that of the main pitch circle 11 by the radius difference ⁇ r 1 .
  • the points of the leading lobe face and the trailing lobe face on the main pitch circle 11 are connected to the main lobe bottom circle 13 by the main leading-side lobe root arc 14a and the main trailing-side lobe root arc 14b.
  • the gate rotor interlobe 20a is created according to the foregoing procedure (the foregoing modification) on the basis of the lobe shape illustrated in FIG. 3A and FIG. 3B .
  • the radius of the gate lobe tip circle 23 is larger than that of the gate pitch circle 21 by the radius difference ⁇ r 2 .
  • the points of the leading lobe face and the trailing lobe face on the gate pitch circle 21 are connected to the gate lobe tip circle 23 by the gate trailing-side lobe tip arc 24a and the gate leading-side lobe tip arc 24b.
  • a ratio La:Lb between a distance La from B2 to B1 and a distance Lb from B1 to G2 may be set within the range of 1:9 to 6:4.
  • the main trailing-side lobe tip point B1 contacts the gate leading lobe face in the range from B2 to G2 on the gate leading lobe face (B2-G2).
  • the radius difference ⁇ r 1 of the main lobe bottom circle 13 of the main rotor 10 and the radii r 1 of the main leading-side lobe root arc 14a and the main trailing-side lobe root arc 14b may be set to be larger than the other radius difference ⁇ r 2 and the radius r 2 (i.e. the radius difference ⁇ r 2 of the gate lobe tip circle 23 and the radii r 2 of the gate trailing-side lobe tip arc 24a and the gate leading-side lobe tip arc 24b).
  • the radius difference ⁇ r 1 of the main lobe bottom circle 13 of the main rotor 10 and the radii r 1 of the main leading-side lobe root arc 14a and the main trailing-side lobe root arc 14b are set such that the main rotor lobe 10a is offset (shifted) to a side on which the main rotor lobe 10a is diminished or to a side on which the gate rotor interlobe 20a is enlarged, by a width that is adequate for avoiding the mutual interference between the lobe face of the main rotor lobe 10a and the lobe face of the gate rotor interlobe 20a.
  • FIG. 4 is an explanatory diagram illustrating the method for reducing the confining space.
  • the phase of the trailing lobe face with respect to the leading lobe face is set such that the confining space that appears between the trailing lobe face of the main rotor 10 and the leading lobe face of the gate rotor 20 is minimized when the main rotor lobe 10a and the gate rotor interlobe 20a directly face each other.
  • the flow passage area of the leakage of a fluid at the part concerned is minimized so that deterioration in the efficiency of the compressor can be suppressed.
  • FIG. 4 illustrates the main rotor lobe 10a and the gate rotor interlobe 20a directly facing each other.
  • the arc between the two sealing lines "b" illustrated in FIG. 1C corresponds to the arc between E1 and d2 in FIG. 4 .
  • the leading lobe face of the main rotor 10 and the trailing lobe face of the gate rotor 20 coincide with each other in the range of A1 to E1, and there would be no clearance in an ideal case.
  • B1' denotes a main trailing-side lobe tip point when the main trailing-side lobe tip point is set at a phase (position) relatively close to the main leading-side lobe tip point A1.
  • d1' and d2' denote a main trailing-side lobe root point and a gate leading-side lobe tip point, respectively, when the main trailing-side lobe tip point B1' is set.
  • reference sign 26 denotes the confining space when the main trailing-side lobe tip point B1' is set.
  • A1 denotes a main leading-side lobe tip point common to both of the case where the main trailing-side lobe tip point is set at B1' and the case where the main trailing-side lobe tip point is set at B1.
  • A2 denotes a gate trailing-side lobe root point that lies at the same phase in the foregoing both cases.
  • FIG. 4 illustrates the relative positions of the lobe tip circle and the trailing lobe face (A1-d1') of the main rotor 10 and the lobe bottom circle and the leading lobe face (A2-d2') of the gate rotor 20 in the confining space 26 between the trailing lobe face of the main rotor 10 and the leading lobe face of the gate rotor 20 when the main leading-side lobe tip point A1 and the main trailing-side lobe tip point B1' are at relatively close phases.
  • the relative positions thereof also change, as indicated by the lobe tip circle and the trailing lobe face (A1-d1) of the main rotor 10 and the lobe bottom circle and the leading lobe face (A2-d2) of the interlobe 20a.
  • the area of a confining space 25 that appears along A1-B1-d2 is smaller than the area of the confining space 26 that appears along A1-B1'-d2'.
  • phase of the trailing lobe face with respect to the leading lobe face is set such that the confining space 25 enclosed by the curve (A1-d1) and the curve (A2-d2) is minimized.
  • the deterioration in the efficiency of the compressor can be suppressed by minimization of the clearance between the main rotor 10 and the gate rotor 20 in the phase at which the main rotor lobe 10a and the gate rotor interlobe 20a directly face each other.
  • the screw rotor according to the foregoing embodiment may be described by any one of the following configurations 1 to 4.
  • a screw rotor includes a main rotor and a gate rotor each having a plurality of lobes or interlobes, and the main rotor and the gate rotor being meshed with each other and rotatable about a rotating axis of each thereof in an operating space formed by a casing, wherein
  • FIG. 2A is the explanatory diagram of a leakage path that is different from the one illustrated in FIG. 2B .
  • a clearance to the adjacent space, the volume of which increases, is left between the main rotor 1 and the gate rotor 2. The clearance leads to the leakage of a compressed fluid, resulting in deteriorated efficiency of a compressor.
  • the following configuration 2 may be adopted to implement a screw rotor capable of reducing the clearance that appears when the main rotor lobe and the gate rotor interlobe directly face each other, thereby reducing the leakage volume of a compressed fluid with resultant higher efficiency of the compressor.
  • a phase of a trailing lobe face of the main rotor with respect to a leading lobe face of the gate rotor is set such that a confining space that appears between the trailing lobe face and the leading lobe face is minimized when the main rotor lobe and the gate rotor interlobe directly face each other.
  • the leading lobe face and the trailing lobe face of the main rotor lobe are offset inward by a distance r 1
  • the main lobe bottom circle is set to be smaller than the main pitch circle by a radius difference ⁇ r 1
  • the main lobe tip circle is made smaller by the radius difference ⁇ r 1
  • the leading lobe face and the trailing lobe face are connected to the main lobe bottom circle by a main leading-side lobe root arc that has a radius r 1 and whose center is the main leading-side lobe root point C1' and a main trailing-side lobe root arc that has the radius r 1 and whose center is the main trailing-side lobe root point D1' as the center thereof
  • the leading lobe face and the trailing lobe face of the gate rotor interlobe are offset outward by a distance r 2
  • the gate lobe bottom circle is set to be larger
  • the radius difference ⁇ r 1 of the main lobe bottom circle of the main rotor and the radii r 1 of the main leading-side lobe root arc and the main trailing-side lobe root arc are set to be larger than the radius difference ⁇ r 2 and the radius r 2 , and the lobe face of the main rotor lobe or the gate rotor interlobe is offset to a side on which the main rotor lobe is diminished or to a side on which the gate rotor interlobe is enlarged, by an adequate width for avoiding the interference between the lobe face of the main rotor lobe and the lobe face of the gate rotor interlobe.
  • the interference can be suppressed when the distance between the two rotor axes fluctuate.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
EP15837048.6A 2014-08-28 2015-07-15 Schraubenrotor Withdrawn EP3187734A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014173541 2014-08-28
PCT/JP2015/070232 WO2016031413A1 (ja) 2014-08-28 2015-07-15 スクリューロータ

Publications (1)

Publication Number Publication Date
EP3187734A1 true EP3187734A1 (de) 2017-07-05

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Application Number Title Priority Date Filing Date
EP15837048.6A Withdrawn EP3187734A1 (de) 2014-08-28 2015-07-15 Schraubenrotor

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EP (1) EP3187734A1 (de)
JP (1) JP6273661B2 (de)
WO (1) WO2016031413A1 (de)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2486770A (en) * 1946-08-21 1949-11-01 Joseph E Whitfield Arc generated thread form for helical rotary members
JPS5618761B2 (de) * 1972-08-17 1981-05-01
JPS5617522B2 (de) * 1972-08-09 1981-04-23
SE386960B (sv) * 1974-06-24 1976-08-23 Atlas Copco Ab Rotorer for skuvrotormaskin
US4508496A (en) * 1984-01-16 1985-04-02 Ingersoll-Rand Co. Rotary, positive-displacement machine, of the helical-rotor type, and rotors therefor
JPS60178989A (ja) * 1984-02-21 1985-09-12 Hokuetsu Kogyo Co Ltd スクリユ・ロ−タ
KR100425414B1 (ko) * 2002-01-25 2004-04-08 이 재 영 스크류 압축기용 로우터의 치형
JP2012207660A (ja) * 2011-03-11 2012-10-25 Toyota Industries Corp スクリュポンプ

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WO2016031413A1 (ja) 2016-03-03
JP6273661B2 (ja) 2018-02-07

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